U.S. patent application number 10/635042 was filed with the patent office on 2004-04-01 for channel selectory value and method of driving the same, compressor with the channel selector valve, and device for controlling refrigerating cycle.
Invention is credited to Aoki, Tadashi, Ito, Hiroshi, Kiuchi, Nobuyuki, Kubota, Shigeru, Nakahara, Seiichi, Noda, Mitsuaki, Suzuki, Kenji, Yoshizawa, Yoshitaka.
Application Number | 20040060308 10/635042 |
Document ID | / |
Family ID | 27528802 |
Filed Date | 2004-04-01 |
United States Patent
Application |
20040060308 |
Kind Code |
A1 |
Yoshizawa, Yoshitaka ; et
al. |
April 1, 2004 |
Channel selectory value and method of driving the same, compressor
with the channel selector valve, and device for controlling
refrigerating cycle
Abstract
Upon a selector operation of a valve such as a four-way selector
valve provided in a refrigerating cycle for selecting a channel of
fluid, prevention of environmental pollution and energy saving and
the like are effectively achieved. A sliding valve is coupled with
a piston in a housing of a channel selector valve provided in a
refrigerating cycle and the sliding valve moves due to a difference
in pressure and so on at both sides of the piston, thereby a
channel of fluid is selected. A processing section of a control
device is constituted with microcomputers of an indoor and outdoor
control sections, while a detecting section of the control device
includes temperature sensor, detection means for detecting
pressure, detection means for detecting flow rate, detection means
for detecting voltage/current, and detection means for detecting
frequency. Driving sections of an electrically-driven expansion
valve, an indoor heat exchanger, an outdoor heat exchanger and a
compressor are means that function in response to execution of
control programs so that physical quantity, such as pressure,
differential pressure and flow rate in the channel selector valve
provided in the refrigerating cycle, and a rate of change in
physical quantity, such as a rate of change in pressure, a rate of
change in differential pressure and a rate of change in flow rate,
are controlled, thereby a channel of the fluid is selected by the
channel selector valve.
Inventors: |
Yoshizawa, Yoshitaka;
(Saitama, JP) ; Suzuki, Kenji; (Saitama, JP)
; Noda, Mitsuaki; (Saitama, JP) ; Kubota,
Shigeru; (Saitama, JP) ; Aoki, Tadashi;
(Tokyo, JP) ; Ito, Hiroshi; (Saitama, JP) ;
Kiuchi, Nobuyuki; (Saitama, JP) ; Nakahara,
Seiichi; (Saitama, JP) |
Correspondence
Address: |
BUTZEL LONG
350 SOUTH MAIN STREET
SUITE 300
ANN ARBOR
MI
48104
US
|
Family ID: |
27528802 |
Appl. No.: |
10/635042 |
Filed: |
August 5, 2003 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
10635042 |
Aug 5, 2003 |
|
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|
09743079 |
Jan 2, 2001 |
|
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6684651 |
|
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09743079 |
Jan 2, 2001 |
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PCT/JP99/03557 |
Jul 1, 1999 |
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Current U.S.
Class: |
62/160 ;
62/228.3; 62/324.6 |
Current CPC
Class: |
F16K 11/0655 20130101;
Y10T 137/86839 20150401; F25B 41/26 20210101 |
Class at
Publication: |
062/160 ;
062/324.6; 062/228.3 |
International
Class: |
F25B 013/00; F25B
001/00; F25B 049/00 |
Foreign Application Data
Date |
Code |
Application Number |
Jul 2, 1998 |
JP |
10-187835 |
Oct 30, 1998 |
JP |
10-310635 |
Dec 28, 1998 |
JP |
10-372440 |
Jun 28, 1999 |
JP |
11-181366 |
Jun 29, 1999 |
JP |
11-183418 |
Claims
1. A channel selector valve for selecting a channel of fluid
characterized in that the channel is selected by employing
non-electric motive power.
2. The channel selector valve according to claim 1, wherein a drive
source provided separately from the channel selector valve
generates said non-electric motive power, by which the channel is
passively selected.
3. The channel selector valve according to claim 2, wherein the
drive source comprises at least one of element components in a
refrigerating cycle having the channel selector valve and the
channel is passively selected by using the motive power generated
by said at least one of the element components.
4. The channel selector valve according to claim 3, wherein said
motive power is generated due to a change in physical quantity,
which arises in the refrigerating cycle from an action of said at
least one of the element components.
5. The channel selector valve according to claim 4, wherein said
change in physical quantity is at least one change among changes in
pressure, differential pressure and flow rate of fluid in the
channel selector valve, said changes arising from an action of said
at least one of the element components.
6. A channel selector valve for selecting a channel of fluid
comprising: a movable member moving between a first position and a
second position in a housing of the channel selector valve; and
driving means for driving the movable member between the first
position and the second position by employing non-electric motive
power, wherein a first selector port out of two selector ports of
the housing communicates with a main port of the housing through
the interior of the housing when the movable member is situated at
the first position, while a second selector port out of the two
selector ports of the housing communicates with a main port of the
housing through the interior of the housing when the movable member
is situated at the second position.
7. The channel selector valve according to claim 6, wherein a drive
source generating said non-electric motive power comprises at least
one of element components in a refrigerating cycle having the
channel selector valve, a change in physical quantity, which arises
in the refrigerating cycle from an action of said at least one of
element components, is employed as at least a part of said motive
power, thereby the channel is passively selected.
8. The channel selector valve according to claim 7, wherein said
change in physical quantity is at least one change among changes in
pressure, differential pressure and flow rate of fluid in the
channel selector valve, said changes arising from an action of said
at least one of the element components.
9. A channel selector valve constituted as a four-way selector
valve by combining a first and second three-way selector valves,
each of which is constituted by the channel selector valve
according to claim 6, 7 or 8.
10. The channel selector valve according to claim 9, wherein the
channel selector valve is constituted as a four-way selector valve
by the first and second three-way selector valves, the main port of
the first three-way selector valve is an inlet port formed in the
housing, through which fluid introduced from the exterior to the
interior of the housing of the first three-way selector valve
passes, while the main port of the second three-way selector valve
is an outlet port formed in the housing, through which the fluid
discharged from the interior to the exterior of the housing of the
second three-way selector valve passes, the first selector port of
the first three-way selector valve is connected to the second
selector port of the second three-way selector valve, while the
second selector port of the first three-way selector valve is
connected to the first selector port of the second three-way
selector valve, the movable member of the second three-way selector
valve moves to the second position when the movable member of the
first three-way selector valve moves to the first position, while
the movable member of the second three-way selector valve moves to
the first position when the movable member of the first three-way
selector valve moves to the second position.
11. The channel selector valve according to claim 10, wherein said
driving means of the first three-way selector valve comprises: a
first drive mechanism that moves the movable member situated at the
first position of the first three-way selector valve to the second
position when a difference between a fluid pressure at the first
selector port in the first three-way selector valve and a fluid
pressure at the second selector port cancels out; and a
second-drive mechanism that moves the movable member situated at
the second position of the first three-way selector valve to the
first position when a difference between a fluid pressure at the
first selector port in the first three-way selector valve and a
fluid pressure at the second selector port cancels out.
12. The channel selector valve according to claim 11, wherein the
first and second three-way selector valves are constructed so that
the main port is isolated from the second selector port when the
movable member is situated between the first position and a third
position where is nearer to the second position than the first
position, while that the main port is isolated from the first
selector port when the movable member is situated between the
second position and a fourth position where is between the second
position and the third position, the first drive mechanism
comprises first storing means for storing energizing force to move
the movable member of the first three-way selector valve from the
first position to the fourth position, by a fluid pressure being
higher than a first predetermined value of the main port, when the
movable member of the first three-way selector valve is situated at
the first position, said energizing force being less than the first
predetermined value, and the second drive mechanism comprises
second storing means for storing energizing force to move the
movable member of the first three-way selector valve from the
second position to the third position, by a fluid pressure being
higher than a second predetermined value of the main port, when the
movable member of the first three-way selector valve is situated at
the second position, said energizing force being less than the
second predetermined value.
13. The channel selector valve according to claim 6, 7 or 8,
wherein the main port is an inlet port formed in the housing,
through which fluid introduced from the exterior to the interior of
the housing passes, the housing further comprises an outlet port,
through which the fluid discharged from the interior to the
exterior of the housing passes, when the movable member is situated
at the first position, the inlet port and the first selector port
are communicated with each other inside the housing, while the
outlet port and the second selector port are communicated with each
other inside the housing, when the movable member is situated at
the second position, the inlet port and the second selector port
are communicated with each other inside the housing, while the
outlet port and the first selector port are communicated with each
other inside the housing.
14. The channel selector valve according to claim 13, wherein the
movable member partitions the interior of the housing into a first
and second pressure chambers and also forms a first and second
spaces in the first pressure chamber, the inlet port is formed in
the housing so as to communicate with the first space and the
outlet port is formed in the housing so as to communicate with the
second space, when the movable member is situated at the first
position, the fluid introduced from the exterior of the housing
into the first space by way of the inlet port is discharged to the
first selector port, while the fluid discharged from the second
space to the exterior of the housing by way of the outlet port is
introduced from the second selector port, when the movable member
is situated at the second position, the fluid introduced from the
exterior of the housing into the first space by way of the inlet
port is discharged to the second selector port, while the fluid
discharged from the second space to the exterior of the housing by
way of the outlet port is introduced from the first selector
port.
15. A method of driving the channel selector valve as claimed in
claim 14, comprising the steps of: communicating the first space to
the second pressure chamber through an equalizing path formed in
the movable member; energizing the movable member in a direction of
moving from the second position to the first position by energizing
means for energizing; and applying a force to the movable member
from the first pressure chamber side by fluid introduced from the
exterior of the housing into the first space by way of the inlet
port, said force being stronger than a resultant force consisting
of an energizing force by said energizing means and a force applied
to the movable member by fluid in the second pressure chamber
introduced from the first space by way of said equalizing path,
thereby the movable member moves from the first position to the
second position.
16. The channel selector valve according to claim 14, wherein the
housing has a valve seat disposed in the first pressure chamber,
the outlet port and the two selector ports are disposed on the
valve seat, the second space moves on the valve seat responding to
a movement of the movable member moving between the first and
second positions, and a place with which the outlet port
communicates by way of the second space is selected to be either
the first selector port or the second selector port.
17. A method of driving the channel selector valve as claimed in
claim 16, comprising the steps of: communicating the first space to
the second pressure chamber through an equalizing path formed in
the movable member; energizing the movable member in a direction of
moving from the second position to the first position by energizing
means for energizing; and applying a force to the movable member
from the first pressure chamber side by fluid introduced from the
exterior of the housing into the first space by way of the inlet
port, said force being stronger than a resultant force consisting
of an energizing force by said energizing means, a force applied to
the movable member by fluid in the second pressure chamber
introduced from the first space by way of said equalizing path, and
a static friction force between the valve seat and the movable
member, whereby the movable member moves from the first position to
the second position and the movable member is kept staying at the
second position by the static friction force between the valve seat
and the movable member against an energizing force of the
energizing means, after a difference between a pressure of fluid in
the first space and that in the second pressure chamber decreases
due to circulation of fluid between the first space and the second
pressure chamber through the equalizing path.
18. The channel selector valve according to claim 14 or 16, wherein
the driving means comprises: a third drive mechanism that moves the
movable member from one position out of the first and second
positions toward an opposite position; and a fourth drive mechanism
that moves the movable member from the opposite position toward the
one position, wherein the third and fourth drive mechanisms employ
a change in physical quantity of the interior of the housing due to
fluid introduced into the interior of the housing at least as a
part of the motive power.
19. The channel selector valve according to claim 18, wherein the
movable member partitions the interior of the housing into the
first pressure chamber, the second pressure chamber, and a third
pressure chamber situated so that the first pressure chamber is
sandwiched between the second and third pressure chambers, the
channel selector valve further comprises a non-electrically-driven
pilot valve that selectively communicates the outlet port to either
the second pressure chamber or the third pressure chamber, said
pilot valve comprises: a second housing having a second main port
that is provided outside the housing and communicates with the
outlet port; and a selector valeve element that patitions the
interior of the second housing into a fourth pressure chamber
communicating with the third pressure chamber and a fifth pressure
chamber communicating with the second pressure chamber, and that is
movable in the second housing between a fifth position where the
second main port communicates with the fourth pressure chamber and
a sixth position where the second main port communicates with the
fifth pressure chamber, due to a difference between a pressure of
fluid in the second pressure chamber and that in the third pressure
chamber.
20. The channel selector valve according to claim 19, further
comprising second driving means to move the selector valve element
from one position out of the fifth and sixth positions to an
opposire position when the difference between a pressure of fluid
in the second pressure chamber and that in the third pressure
chamber cancels out.
21. The channel selector valve according to claim 20, wherein the
movable member has a first equalizing path communicating the first
space to the second pressure chamber and a second equalizing path
communicating the first space to the third pressure chamber, the
movable member has a first subvalve that isolates the third
pressure chamber from the fourth pressure chamber when the movable
member is situated at the first position and that communicates the
third pressure chamber to the fourth pressure chamber when the
movable member is situated at the second position, and has a second
subvalve that communicates the second pressure chamber to the fifth
pressure chamber when the movable member is situated at the first
position and that isolates the second pressure chamber from the
fifth pressure chamber when the movable member is situated at the
second position, the pilot valve communicates the second main port
to the fourth pressure chamber when the selector valve element is
situated between the fifth position and a seventh position located
nearer to the sixth position than the fifth position, and
communicates the second main port to the fifth pressure chamber
when the selector valve element is situated between the sixth
position and a eighth position located between the sixth position
and the seventh position, and the second driving means has third
and fourth storing means for storing energizing force, the third
storing means for storing energizing force stores an energizing
force, which is less than a third predetermined value, to move the
selector valve element from the fifth position to the eighth
position due to a fluid pressure in the fifth pressure chamber
exceeding the third predetermined value when the selector valve
element is situated at the fifth position, and the fourth storing
means for storing energizing force stores an energizing force,
which is less than a fourth predetermined value, to move the
selector valve element from the sixth position to the seventh
position due to a fluid pressure in the fourth pressure chamber
exceeding the fourth predetermined value when the selector valve
element is situated at the sixth position.
22. The channel selector valve according to claim 19, wherein a
third main port communicating with the inlet port is further formed
in the second housing, the third main port communicates with the
fifth pressure chamber when the selector valve element is situated
between the fifth and seventh positions and communicates with the
fourth pressure chamber when the selector valve element is situated
between the sixth and eighth positions, and the channel selector
valve further comprises second driving means for moving the
selector valve element either from the fifth position to the eighth
position or from the sixth position to the seventh position when
the difference between a pressure of fluid in the second pressure
chamber and that in the third pressure chamber cancels out.
23. The channel selector valve according to claim 22, wherein the
second driving means has third and fourth storing means for storing
energizing force, the third storing means for storing energizing
force stores an energizing force, which is less than a third
predetermined value, to move the selector valve element from the
fifth position to the eighth position due to a fluid pressure in
the fifth pressure chamber exceeding the third predetermined value
when the selector valve element is situated at the fifth position,
and the fourth storing means for storing energizing force stores an
energizing force, which is less than a fourth predetermined value,
to move the selector valve element from the sixth position to the
seventh position due to a fluid pressure in the fourth pressure
chamber exceeding the fourth predetermined value when the selector
valve element is situated at the sixth position.
24. The channel selector valve according to claim 14 or 16, wherein
the driving means comprises: a third drive mechanism to move the
movable member from one position out of the first and second
positions to an opposite position; and a fourth drive mechanism to
move the movable member from the opposite position to the one
position, wherein one drive mechanism out of the third and fourth
drive mechanisms employs a change in physical quantity of the
interior of the housing due to fluid introduced into the interior
of the housing at least as a part of the motive power, while an
opposite drive mechanism employs an energizing force that is
applied to the movable member by energizing means received in the
interior of the housing at least as a part of the motive power.
25. The channel selector valve according to claim 24, further
comprising a latch mechanism that selectively controls a movement
of the movable member from one position out of the first and second
positions toward an opposite position.
26. The channel selector valve according to claim 25, wherein the
latch mechanism selectively performs a first and second states, in
the first state, a movement of the movable member to the opposite
position by the driving means is controlled at the first position,
and in the second state, a movement of the movable member from the
one position to the opposite position by the driving means is
allowed.
27. The channel selector valve according to claim 26, wherein the
latch mechanism comprises a latch piece that moves in the housing
following a movement of the movable member between the first and
second positions, and in a first state of the latch mechanism, a
movement of the latch piece is controlled, thereby a movement of
the movable member is controlled at the one position.
28. A method of driving the channel selector valve as claimed in
claim 26 or 27, wherein when the movable member, a movement of
which to the opposite position is controlled by the latch mechanism
and situated at the one position, is moved to the opposite
position, the movable member is once moved by the driving means in
a direction of moving from the opposite position to the one
position, then is moved from the one position to the opposite
position, and when the movable member situated at the opposite
position is moved to the one position, the movable member is once
moved by the driving means in a direction of moving from the one
position to the opposite position, then is moved from the opposite
position to the one position.
29. The channel selector valve according to claim 24, further
comprising: a valve-opening member that moves from a valve-closing
position to a valve-opening position by the motive power while the
third drive mechanism generates the motive power; a pilot path that
is opened from a valve closing state thereof by the valve-opening
member moved from the valve-closing position to the valve-opening
position; an attenuation mechanism acting when the pilot path is
open, which attenuates the motive power generated by the fourth
drive mechanism so as to prevent the movable member from moving
from the opposite position to the one position; and a second latch
mechanism to selectively control a movement of the valve-opening
member from the valve-closing position to the valve-opening
position.
30. The channel selector valve according to claim 29, wherein the
second latch mechanism alternately repeats a third and fourth
states, in the third state, a movement of the valve-opening member
to the valve-opening position is controlled at the valve-closing
position, and in the fourth state, a movement of the valve-opening
member from the valve-closing position to the valve-opening
position is allowed.
31. A method of driving the channel selector valve as claimed in
claim 29 or 30, wherein when the movable member situated at the one
position is moved to the opposite position, a generation of the
motive power by the third drive mechanism is once halted, then the
generation thereof by the third drive mechanism is started again
and then, the motive power generated by the third drive mechanism
is maintained to be a predetermined value exceeding the motive
power, which is generated by the fourth drive mechanism and
attenuated by the attenuation mechanism, and when the movable
member situated at the opposite position is moved to the one
position, a generation of the motive power by the third drive
mechanism is halted, then the movable member is moved from the
opposite position to the one position by the fourth drive
mechanism.
32. The channel selector valve according to claim 24, wherein the
driving means comprises a communication pipe that always
communicates the second pressure chamber to the first selector port
outside the housing.
33. The channel selector valve according to claim 24, wherein the
driving means comprises a state-holding mechanism to hold the
movable member, which is moved from the first position to the
second position, at the second position.
34. The channel selector valve according to claim 33, wherein the
state-holding mechanism comprises: a state-holding selector valve
provided in the second pressure chamber, which by a selecting
action of a second selector valve element selects either a first
state or a second state, in said first state the second pressure
chamber communiates with the exterior of the housing through a
first introducing port and in said second state the second pressure
chamber communicates with the exterior of the housing through a
second introducing port; and energizing means for energizing the
selector valve, which energizes the second selector valve element
so that the state-holding selector valve in the second state
selects the first state, the movable member allows the energizing
means for energizing the selector valve to energize the second
selector valve element when the movable menber is situated at the
first position, while the movable member makes the second selector
valve element act a selection so that the state-holding selector
valve selects the second state against an energizing by the
energizing means for energizing the selector valve when the movable
menber is situated at the second position.
35. The channel selector valve according to claim 34, wherein the
energizing means energizes the movable member in a direction of
moving from the second position to the first position, and a
pressure of fluid, which is introduced from the exterior of the
housing into the first space by way of the inlet port, acts on the
movable member in a direction of moving from the first position to
the second position.
36. A method of driving the channel selector valve as claimed in
claim 35, wherein when the movable member moves from the first
position to the second position, a pressure of fluid introduced
into the first space from the exterior of the housing by way of the
inlet port is set higher than a predetermined value, so that a
force, which is applied to the movable member by fluid existing in
the first space in a direction from the first position to, the
second position, is set stronger than a force, which is applied to
the movable member by fluid existing in the place to which the
second pressure chamber is communicated in a direction from the
second position to the first position, after the movable member has
moved from the first position to the second position, a pressure of
fluid existing in the first space and a pressure of fluid existing
in the second pressure chamber are set so that the movable member
is kept staying at the second position.
37. The channel selector valve according to claim 7, wherein the
element component is an electrically-driven expansion valve
provided in the refrigerating cycle and the change in physical
quantity is a change in pressure of fluid due to a change in an
opening ratio of the electrically-driven expansion valve.
38. The channel selector valve according to claim 7, wherein the
element component is a compressor provided in the refrigerating
cycle and the change in physical quantity is a change in a
frequency of a mechanical oscillation generated by the
compressor.
39. The channel selector valve according to claim 7, wherein the
element component is a heat exchanger provided in the refrigerating
cycle and the change in physical quantity is a change in pressure
of fluid due to a change in the amount of heat exchange by the heat
exchanger.
40. The channel selector valve according to claim 13, wherein the
housing is formed cylindrical, at least the two selector ports are
formed at a valve seat situated at one end of the housing in a
direction of a central axis of the housing, the movable member is
constructed by a main valve element, which is received in the
housing and rotative around the central axis, the main valve
element is provided with communication means for selectively
communicating a selector port out of the two selector ports to the
main port, the main valve element rotates and displaces around the
central axis so as to move between the first and second positions,
when the main valve element is situated at the first position, a
first selector port out of the two selector ports is communicated
to the main port by the communication means, and when the main
valve element is situated at the second position, a second selector
port out of the two selector ports is communicated to the main port
by the communication means.
41. The channel selector valve according to claim 40, wherein at
least one port out of the inlet port and the outlet port is formed
at the valve seat, an end surface of the main valve element in a
direction of the central axis sits down on the valve seat, said end
surface is provided with second communication means for selectively
communicating said one port to a first selector port out of the two
selector ports, when the main valve element is situated at the
first position, the second communication means communicates the
second selector port to said one port, and when the main valve
element is situated at the second position, the second
communication means communicates the first selector port to said
one port.
42. The channel selector valve according to claim 41, wherein the
opposite port is formed at an opposite end of the housing in a
direction of the central axis, and the communication means has a
communication channel that communicates one end surface side of the
main valve element to an opposite end surface side of the main
valve element in the interior of the housing.
43. The channel selector valve according to claim 40, further
comprising conversion means for converting a moving direction,
which converts a movement of the main valve element in a direction
of the central axis with respect to the housing into a movement in
a rotational direction around the central axis, wherein the main
valve element is movable in a direction of the central axis in the
interior of the housing, and the driving means makes the main valve
element have a reciprocating motion in a direction of the central
axis with respect to the housing.
44. The channel selector valve according to claim 43, wherein the
conversion means for converting a moving direction comprises: a cam
groove that is provided in one out of the main valve element and
the housing, and extends over a whole circumference of the
rotational direction; and a cam follower pin that is provided in
another out of the main valve element and the housing, and moves in
the cam groove, the cam groove has a first and second cam grooves
continuing with each other in the rotational direction, said first
cam groove is formed inclined so as to part from the valve seat in
a direction of the central axis as being displaced in the
rotarional direction, while said second cam groove is formed
inclined so as to move nearer to the valve seat in a direction of
the central axis as being displaced in the rotational
direction.
45. The channel selector valve according to claim 44, wherein the
cam groove is provided in the housing, the housing comprises an
outer housing and an inner housing received in the outer housing,
the inner housing comprises a first half and a second half divided
in a direction of the central axis in a state that the inner
housing is received in the outer housing, and each guide, which
constitutes the cam groove in a state that an end of the first half
and an end of the second half are joined with each other, is formed
at the respective ends of the first and second halves.
46. The channel selector valve according to claim 44 or 45, wherein
at least one port out of the inlet port and the outlet port is
formed at the valve seat, second communication means is formed at
an end surface of the main valve element, the end surface faces the
valve seat, said second communication means selectively
communicates the opposite port to a first selector port out of the
two selector ports in a state that the end surface sits down on the
valve seat, when the main valve element is situated at the first
position, the second selector port is communicated to the opposite
port by the second communication means of the main valve elemnt,
and the end surface of which sits down on the valve seat, and when
the main valve element is situated at the second position, the
first selector port is communicated to the opposite port by the
second communication means of the main valve elemnt, and the end
surface of which sits down on the valve seat.
47. The channel selector valve according to claim 46, wherein the
opposite port is formed at an opposite end side of the housing in a
direction of the central axis, and the communication means
comprises: a communication channel that communicates one end
surface side of the main valve element to an opposite end surface
side of the main valve element in the housing; a subvalve that
opens and closes the communication channel; subvalve energizing
means for energizing the subvalve toward a direction of closing;
and valve opening means for opening the subvalve against an
energizing force by the subvalve energizing means in a state that
the one end surface of the main valve element sits down on the
valve seat.
48. The channel selector valve according to claim 47, wherein the
housing is disposed so that the opposite end of the housing is
situated lower than one end of the housing in a direction of the
central axis, and the driving means employs an own weight of the
main valve element at least as a part of the motive power.
49. The channel selector valve according to claim 47 or 48, wherein
the driving means employs an energizing force by energizing means
for energizing main valve element, which energizes the main valve
element to part from the valve seat in a direction of the central
axis, as a part of the motive power.
50. The channel selector valve according to claim 47 or 48, wherein
the driving means comprises second energizing means for energizing
the main valve element, which energizes the main valve element to
move nearer to the valve seat in a direction of the central
axis.
51. The channel selector valve according to claim 50, wherein the
driving means comprises energizing means for energizing the main
valve element, which energizes the main valve element to part from
the valve seat in a direction of the central axis, due to a
resultant force of an energizing force by the energizing means for
energizing the main valve element and an energizing force by the
second energizing means for energizing the main valve element, the
cam follower pin is situated at an intermediate position of the cam
groove except end portions of one end side and an opposite end side
of the housing in a direction of the central axis, and the main
valve element is situated at a neutral position halfway within a
reciprocating motion in a direction of the central axis when the
cam follower pin is situated at the intermediate position.
52. The channel selector valve according to claim 51, wherein an
end portion of the one end side of the housing in a direction of
the central axis out of the cam groove is provided with a groove
that continues to a join, at which one end of the first cam groove
being situated at the one end side of the housing is connected to
one end of the second cam groove, the groove is formed so that the
one end surface of the main valve element sits down on the valve
seat in a state that the cam follower pin is situated at the
groove, the groove is disposed being displaced to the lower course
than the join in the rotational direction, and when the main valve
element moves in the direction away from the valve seat in a
direction of the central axis, a movement of the cam follower pin
is controlled from the groove to a cam groove out of the first and
second cam grooves, which is situated at the upper course than the
groove in the rotational direction.
53. The channel selector valve according to claim 51 or 52, wherein
an end portion of the opposite end side of the housing in a
direction of the central axis out of the cam groove is provided
with a second groove that continues to a join, at which an opposite
end of the first cam groove being situated at the opposite end side
of the housing is connected to an opposite end of the second cam
groove, the second groove is formed so that the main valve element
is the farthest away from the valve seat in a state that the cam
follower pin is situated at the second groove, the second groove is
disposed being displaced to the lower course than the second join
in the rotational direction, and when the main valve element moves
in the direction nearer to the valve seat in a direction of the
central axis, a movement of the cam follower pin is controlled from
the second groove to a cam groove out of the first and second cam
grooves, which is situated at the upper course than the second
groove in the rotational direction.
54. The channel selector valve as claimed in any one of claims
40-53, wherein slide means for decreasing a sliding resistance
between the housing and the main valve element is provided
therebetween.
55. A compressor with the channel selector valve as claimed in any
one of claims 10-14, 16, 18-27, 29-30, 32-35, and 37-54,
comprising: a compressor housing having an inlet, which is
connected to the outlet port; a low pressure chamber that is
provided in the interior of the compressor housing and communicates
with the inlet; a high pressure chamber that is provided in the
interior of the compressor housing and partitioned off from the low
pressure chamber; and a compressing section that is provided in the
interior of the compressor housing, compresses fluid introduced
into the low pressure chamber from the inlet, and guides the fluid
into the high pressure chamber, wherein a part of the compressor
housing partitioning the high pressure housing therein is
integrally formed with a part of the housing having the inlet port
therein, thereby the interior of the part of the housing
communicates with the high pressure chamber.
56. A device for controlling a refrigerating cycle, which controls
a channel selector valve communicated to the refrigerating cycle,
characterized in that: the device controls at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control the refrigerating cycle; and
the device controls the channel selector valve by controlling the
functional components.
57. A device for controlling a refrigerating cycle, which controls
a channel selector valve communicated to the refrigerating cycle,
characterized in that: the device controls at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control the refrigerating cycle; and
the device generates a non-electrical motive power by controlling
the functional components and passively controls the channel
selector valve by employing the motive power.
58. A device for controlling a refrigerating cycle, which controls
a channel selector valve communicated to the refrigerating cycle,
comprising: a microcomputer that controls at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control the refrigerating cycle; and a
control program, by which the microcomputer performs a processing
that controls the functional components so as to generate a
non-electrical motive power for passively controlling the channel
selector valve.
59. A device for controlling a refrigerating cycle, which controls
a channel selector valve communicated to the refrigerating cycle,
characterized in that: the device controls at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control the refrigerating cycle; the
non-electrical motive power generated by controlling the functional
components is a physical quantity or a rate of change in a physical
quantity generated by the refrigerating cycle; and the device
passively controls the channel selector valve by the physical
quantity or the rate of change in a physical quantity.
60. A device for controlling a refrigerating cycle, which controls
a channel selector valve communicated to the refrigerating cycle,
comprising: a microcomputer that controls at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control the refrigerating cycle; and a
control program, by which the microcomputer performs a processing
that controls the functional components so as to allow the
refrigerating cycle to generate a physical quantity or a rate of
change in a physical quantity as a non-electrical motive power for
passively controlling the channel selector valve.
61. The device for controlling a refrigerating cycle as claimed in
any one of claims 57-60, wherein the physical quantity, which is a
base for controlling the functional components to generate the
non-electrical motive power, is a parameter selected from the group
consisting of a pressure, temperature, rate of flow, voltage,
current, electrical frequency and mechanical oscillation frequency
with respect to a control of the refrigerating cycle.
62. The device for controlling a refrigerating cycle as claimed in
any one of claims 57-60, wherein the physical quantity, which is
the non-electrical motive power and is generated by the
refrigerating cycle, is a pressure, differential pressure or rate
of flow with respect to fluid existing in the channel selector
valve, and the rate of change in a physical quantity, which is the
non-electrical motive power and is generated by the refrigerating
cycle, is a rate of change in pressure, rate of change in
differential pressure or rate of change in rate of flow with
respect to the fluid.
63. A device for controlling a refrigerating cycle, which controls
a channel selector valve communicated to the refrigerating cycle,
comprising a control section that receives input signals sent from
an operation command section for commanding an operational
condition of the refrigerating cycle and a physical quantity
detector section for detecting a physical quantity generated by the
refrigerating cycle, wherein the control section sends output
signals to a driving section that drives a drive source of at least
one of a plurality of functional components communicated to the
refrigerating cycle so as to control said functional component, and
the device generates a non-electrical motive power by controlling
the refrigerating cycle and passively controls the channel selector
valve by the motive power.
64. The device for controlling a refrigerating cycle according to
claim 63, wherein the control section controls at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to start an operation of the
refrigerating cycle, thereby controlling the channel selector valve
in a state corresponding to the start of an operation, which is
commanded by the operation command section.
65. The device for controlling a refrigerating cycle according to
claim 64, wherein the control section starts to operate a
compressor communicated to the refrigerating cycle in a direction
of inverse rotation when the control section decides to select the
channel selector valve on the basis of a command of the operation
command section.
66. The device for controlling a refrigerating cycle according to
claim 63, wherein the control section controls at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to operate the refrigerating cycle,
thereby controlling the channel selector valve in a state
corresponding to the operation, which is commanded by the operation
command section.
67. The device for controlling a refrigerating cycle according to
claim 63, wherein the control section controls at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to halt an operation of the refrigerating
cycle, thereby controlling the channel selector valve in a state
corresponding to the halt of the operation, which is commanded by
the operation command section.
68. The device for controlling a refrigerating cycle as claimed in
any one of claims 63-67, wherein the channel selector valve is
constructed in a manner that a movable member moves so as to select
a channel, and the control section comprises at least one unit
selected from the group consisting of: a memory unit for memorizing
position data of the movable member of the channel selector valve;
a comparison unit and a judge unit for comparing and judging,
respectively, the position data and operation command data; and a
learning unit learning on the basis of physical quantity data by a
control of functional components and control data of the channel
selector valve.
69. The device for controlling a refrigerating cycle according to
claim 68, wherein the control section receives the input signals,
performs a predetermined processing and judges whether a channel is
to be changed or not to be changed by the channel selector valve,
then confirms a position on the basis of present position data,
then sends the output signals to the driving section so as to
control the functional components in the refrigerating cycle, then
receives new input signals after a predetermined period of time,
confirms a position of the movable member, and sets position data
of said position as new present position data when said position is
changed to a new position.
70. The device for controlling a refrigerating cycle according to
claim 69, wherein the control section confirms a position of the
movable member by at least one temperature detection means for
detecting temperature, at least one pressure detection means for
detecting pressure, at least one magnetism detection means for
detecting magnetism, at least one current detection means for
detecting current or a combination thereof after a predetermined
period of time, and then installs position data corresponding to
said position into the memory unit of the control section.
71. A device for controlling a refrigerating cycle, which controls
a channel selector valve that is communicated to a refrigerating
cycle and selects a channel by a movement of a movable member,
comprising: a microcomputer that controls at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control the refrigerating cycle; and a
control program, by which the microcomputer performs a processing
consisting of the steps of: receiving input signals; confirming a
position by taking out present position data of a movable member
installed in a memory unit; carrying out an operation to decide
whether the movable member is to be moved of not to be moved,
comparing, and judging; selecting and deciding a driving section;
outputting drive signals to the driving section selected and
decided; judging a position of the movable member by input signals
after a predetermined period of time, with or without moving a
position of the movable member by a physical quantity generated by
at least one functional component that is selected and decided in
said step of selecting and deciding or a rate of the physical
quantity; and installing position data of a position of the movable
member into the memory unit when said position is changed to a new
position, in order to control the driving section for driving the
functional component so that the position of the movable member is
to be moved or not to be moved.
72. A device for controlling a refrigerating cycle, which controls
a channel selector valve communicated to the refrigerating cycle,
comprising: a control section that receives input signals sent from
an operation command section for commanding an operation state of
the refrigerating cycle and from a physical quantity detector
section for detecting a physical quantity generated by the
refrigerating cycle, wherein the control section sends output
signals to a driving section that drives a drive source of at least
one of a plurality of functional components communicated to the
refrigerating cycle so as to control said functional component and
to control the refrigerating cycle, and when judging to select a
channel by using the channel selector valve on the basis of a
command of the operation command section, the control section sends
output signals to a driving section for driving a power source of a
compressor so as to start an operation of the compressor of the
refrigerating cycle and starts an operation of the refrigerant
cycle so as to generate a motive power exceeding a first
predetermined motive power, thereby the channel selector valve is
passively controlled.
73. A device for controlling a refrigerating cycle, which controls
a channel selector valve communicated to the refrigerating cycle,
comprising: a control section that receives input signals sent from
an operation command section for commanding an operation state of
the refrigerating cycle and from a physical quantity detector
section for detecting a physical quantity generated by the
refrigerating cycle, wherein the control section sends output
signals to a driving section that drives a drive source of at least
one of a plurality of functional components communicated to the
refrigerating cycle so as to control said functional component and
to control the refrigerating cycle, and when judging to select a
channel by using the channel selector valve on the basis of a
command of the operation command section, the control section sends
output signals to a driving section for driving a power source of a
compressor so as to start an operation of the compressor in a
direction of inverse rotation and starts an operation of the
refrigerant cycle so as to generate a motive power exceeding a
third predetermined motive power, thereby the channel selector
valve is passively controlled.
74. The device for controlling a refrigerating cycle according to
claim power of the channel selector valve, then operates the
refrigerating cycle for a fourth predetermined period of time, then
halts the operation of the refrigerating cycle for a fifth
predetermined period of time, and then starts an operation of the
compressor with a first predetermined capacity so that a motive
power exceeding a first predetermined motive power is generated as
an internal motive power of the channel selector valve.
78. The device for controlling a refrigerating cycle according to
claim 72, wherein the control section sends output signals to a
throttle device driving section so that an opening ratio of a
throttle device of the refrigerating cycle is almost fully opened
or almost fully closed.
79. The device for controlling a refrigerating cycle according to
claim 72, wherein the control section sends output signals to a
heat exchanger motor driving section so that a heat exchanger motor
of the refrigerating cycle is kept halted.
80. The device for controlling a refrigerating cycle according to
claim 72, 75, 76 or 77, wherein once the control section starts an
operation of the compressor, the control section sends output
signals to the compressor driving section after a first
predetermined period of time and drives the power source of the
compressor so that a motive power exceeding a second predetermined
motive power is generated, thereby operating the refrigerating
cycle.
81. The device for controlling a refrigerating cycle according to
claim 78, wherein once the control section starts an operation of
the compressor, the control section sends output signals to the
throttle device driving section so as to set the opening ratio of
the throttle device a predetermined opening ratio after a first
predetermined period of time.
82. The device for controlling a refrigerating cycle according to
claim 79, wherein once the control section starts an operation of
the compressor, the control section sends output signals to the
heat exchanger motor driving section after a second predetermined
period of time so as to start an operation of the heat exchanger
motor, sends output signals to the compressor driving section so as
to generate a motive power lower than a first predetermined motive
power, and drives the power source of the compressor so as to
generate a motive power exceeding a second predetermined motive
power, thereby operating the refrigerating cycle.
83. The device for controlling a refrigerating cycle according to
claim 80, 81 or 82, wherein when the control section performs a
predetermined processing and judges to select a channel by the
channel selector valve or to halt an operation of the refrigerating
cycle, the control section sends output signals to the compressor
driving section: to drive the power source of the compressor with a
third predetermined capacity so as to generate a motive power lower
than a second predetermined motive power; or to halt the operation
of the compressor, thereby halting the operation of the
refrigerating cycle.
84. The device for controlling a refrigerating cycle according to
claim 72, wherein when the control section performs a predetermined
processing and judges to select a channel by the channel selector
valve or to halt an operation of the refrigerating cycle, the
control section sends output signals to the compressor driving
section to halt the operation of the compressor, then keeps the
refrigerating cycle standby for a third predetermined period of
time, then sends output signals to the compressor driving section
to start the operation of the compressor, then renews position data
in a memory unit to a first or second position after a first
predetermined period of time, thereby halting the operation of the
compressor again.
85. The device for controlling a refrigerating cycle according to
claim 72, 74 or 84, wherein when positional data memorized by a
memory unit of the control section indicate a first or second
position, the control section starts an operation of the
refrigerating cycle so that a motive power exceeding a first
predetermined motive power is generated as an internal motive power
of the channel selector valve.
86. A device for controlling a refrigerating cycle, which controls
a channel selector valve communicated to the refrigerating cycle,
comprising: a control section that receives input signals sent from
an operation command section for commanding an operation state of
the refrigerating cycle and from a physical quantity detector
section for detecting a physical quantity generated by the
refrigerating cycle, wherein the control section sends output
signals to a driving section that drives a drive source of at least
one of a plurality of functional components communicated to the
refrigerating cycle so as to control said functional component and
to control the refrigerating cycle, and when judging not to select
a channel by using the channel selector valve on the basis of a
command of the operation command section, the control section sends
output signals to a driving section for driving a power source of a
compressor so as to start an operation of the compressor of the
refrigerating cycle and starts an operation of the refrigerant
cycle so as to generate a motive power lower than a first
predetermined motive power, thereby the channel selector valve is
passively controlled.
87. The device for controlling a refrigerating cycle according to
claim 86, wherein the control section starts an operation of the
compressor with a second predetermined capacity.
88. A device for controlling a refrigerating cycle, which controls
a channel selector valve communicated to the refrigerating cycle,
comprising: a control section that receives input signals sent from
an operation command section for commanding an operation state of
the refrigerating cycle and from a physical quantity detector
section for detecting a physical quantity generated by the
refrigerating cycle, wherein the control section sends output
signals to a driving section that drives a drive source of at least
one of a plurality of functional components communicated to the
refrigerating cycle so as to control said functional component and
to control the refrigerating cycle, and when judging not to select
a channel by using the channel selector valve on the basis of a
command of the operation command section, the control section sends
output signals to a driving section for driving a power source of a
compressor so as to start an operation of the compressor of the
refrigerating cycle and starts an operation of the refrigerant
cycle so as to generate a motive power exceeding a first
predetermined motive power, thereby the channel selector valve is
passively controlled.
89. The device for controlling a refrigerating cycle according to
claim 88, wherein when the control section performs a predetermined
processing and judges to halt an operation of the refrigerating
cycle, the control section sends output signals to the compressor
driving section so as to halt the operation of the compressor, then
keeps the refrigerating cycle standby for a third predetermined
period of time without renewing position data in a memory unit.
Description
TECHNICAL FIELD
[0001] The present invention relates to a channel selector valve
and, more specifically, to a channel selector valve, which is used
to reverse channels for fluid discharged from a compressor and for
fluid sucked into the compressor, and to a device for controlling a
refrigerating cycle.
BACKGROUND ART
[0002] In general, as to an air conditioner for both cooling and
heating, a four-way selector valve selects a circulating direction
of a refrigerant in such a manner that upon cooling the refrigerant
flows from a compressor, by way of an outdoor heat exchanger, a
throttle valve and an indoor heat exchanger, then flows back to the
compressor, and that upon heating the refrigerant flows from a
compressor, by way of an indoor heat exchanger, a throttle valve
and an outdoor heat exchanger, then flows back to the
compressor.
[0003] The four-way selector valve, used for selecting a
circulating direction of a refrigerant in a refrigerating cycle
described above, includes the so-called sliding-type four-way
selector valve.
[0004] As to the sliding-type four-way selector valve, a valve
element is moved inside the valve housing so that one port,
communicating with an inlet through a space formed inside the valve
element, is switched from a first port to a second port out of the
two ports and simultaneously that another port, communicating with
an outlet through a space formed outside the valve element, is
switched from the second port to the first port out of the two
ports.
[0005] As disclosed, for example, in Japanese Patent Publication
No. S35-12689 and Japanese Utility Model Publication No. S55-53825,
as to a conventional four-way selector valve, a magnet coil formed
outside of the valve housing is provided with electricity so as to
selectively decompress either valve chamber between two valve
chambers disposed at both sides of a central valve chamber, out of
three valve chambers in the valve housing, then the valve element
placed in the central valve chamber is slided due to the
differential pressure generated between the decompressed valve
chamber and the central valve chamber.
[0006] In Japanese Patent Publication No. H7-99296, there is
disclosed a five-way valve, in which a valve element in a valve
chamber is slided with the aid of a plunger of a magnet coil
inserted in a valve housing, with supplying electricity to the
magnet coil disposed outside the valve housing.
[0007] As a conventional art similar to the above four or five-way
valve, in Japanese Utility Model Laid-Open No. S58-42465, there is
disclosed a four-way selector valve, in which with supplying
electricity to heaters in operation chambers formed both sides of a
valve housing, two operation rods, each inserted from the
respective operation chamber into the valve housing, are
alternately slided so that a valve element in the valve housing is
slided.
[0008] Every conventional four or five-way valve mentioned above
needs electricity to be supplied to a magnet coil upon selecting by
the valve, consequently, there has been a room for improvement in
these valves from the viewpoints of prevention of the environmental
pollution and energy saving.
[0009] Besides the four or five-way valves, for example, in
Japanese Utility Model Laid-Open No. H3-119689, there is disclosed
a four-way selector valve, in which wax thermoelements are disposed
at both sides of a valve housing instead of a magnet coil, and with
supplying electricity to heaters of the wax thermoelements, a valve
element in the valve housing is slided with the aid of a shaft,
inserted from the outside of the valve housing into the inside
thereof.
[0010] In Japanese Patent No. 2757997, there is disclosed a
four-way selector valve, in which a pair of differential pressure
chambers partitioned by partition wall plates is formed at
respective sides of a valve chamber in a valve housing so that each
differential pressure chamber can selectively communicate with the
valve chamber by switching a substitute valve formed on the
respective partition wall plate, and a constant-temperature heater
of each slow operation element disposed at both sides of the valve
housing is supplied with electricity so that each operation shaft
inserted from the respective side of the valve housing into the
respective differential pressure chamber is slided. In this
four-way selector valve, the constant-temperature heater of each
slow operation element is supplied with electricity so as to slide
each operation shaft and to open either substitute valve, thereby
both partition wall plates slide within the valve housing together
with the valve element in such a manner that the partition wall
plates move nearer to the opened substitute valve.
[0011] Each conventional four-way selector valve mentioned above
does not employ a magnet coil, however, needs electricity to be
supplied to the heaters in order to operate the swiching valve,
consequently, there has been a room for improvement in these valves
similarly to the aforementioned conventional four or five-way
valve.
[0012] On the other hand, as to a four-way selector valve disclosed
in Japanese Patent Publication No. H7-43188, although a valve
element is slided by supplying electricity to a magnet coil, a
permanent magnet attracts the slided valve element so that a
position of the valve element after supplying electricity is
maintained, thereby saving a further supply of electricity to the
magnet coil, then only a tentative electrical supply is performed
to another magnet coil for demagnetization when the valve element
is moved from the slided position back to an original position
before the slide.
[0013] As to a four-way selector valve disclosed in Japanese Patent
Application Laid-Open No. H9-72633, a position of a valve element
after slide is maintained by an intermittent electrical supply to a
magnet coil, in the four-way selector valve that is similar to one
described in Japanese Patent Publication No. S35-12689.
[0014] Since each four-way selector valve, disclosed in Japanese
Patent Publication No. H7-43188 or Japanese Patent Application
Laid-Open No. H9-72633, does not need a continuous electrical
supply to the magnet coil, it has some effect from the viewpoints
of prevention of the environmental pollution and energy saving.
[0015] Certainly, the four-way selector valve, disclosed in
Japanese Patent Publication No. H7-43188 or Japanese Patent
Application Laid-Open No. H9-72633, restricts an amount of
electrical supply to the magnet coil, however, it still needs some
amount of electrical supply. Therefore, from the viewpoints of a
vigorous promotion with respect to prevention of the environmental
pollution and energy saving, there has been a room for further
improvement in the valves described above.
[0016] Therefore, as to a selecting operation of a channel selector
valve for fluid, such as a four-way selector valve, which is
provided in a refrigerating cycle, it is an objective of the
present invention to solve the above problems and to provide a
channel selector valve that can effectively contribute for
prevention of the environmental pollution and energy saving, a
method of driving the channel selector valve, a compressor that
works excellently with using the channel selector valve, and a
device for controlling a refrigerating cycle.
DISCLOSURE OF INVENTION
[0017] In order to attain the above objective, each invention as
described in claims 1-14, 16, 18-27, 29, 30, 32-35 and 37-54
relates to a channel selector valve, each invention as described in
claims 15, 17, 28, 31 and 36 relates to a method of driving the
channel selector valve, an invention as described in claim 55
relates to a compressor with the channel selector valve, and each
invention as described in claims 56-89 relates to a device for
controlling a refrigerating cycle.
[0018] A channel selector valve of the present invention as
described in claim 1 is a channel selector valve for selecting a
channel of fluid characterized in that the channel is selected by
employing non-electric motive power.
[0019] The channel selector valve of the present invention as
described in claim 2 is the channel selector valve of the present
invention as described in claim 1, wherein a drive source provided
separately from the channel selector valve generates said
non-electric motive power, by which the channel is passively
selected.
[0020] The channel selector valve of the present invention as
described in claim 3 is the channel selector valve of the present
invention as described in claim 2, wherein the drive source
comprises at least one of element components in a refrigerating
cycle having the channel selector valve and the channel is
passively selected by using the motive power generated by said at
least one of the element components.
[0021] The channel selector valve of the present invention as
described in claim 4 is the channel selector valve of the present
invention as described in claim 3, wherein said motive power is
generated due to a change in physical quantity, which arises in the
refrigerating cycle from an action of said at least one of the
element components.
[0022] The channel selector valve of the present invention as
described in claim 5 is the channel selector valve of the present
invention as described in claim 4, wherein said change in physical
quantity is at least one change among changes in pressure,
differential pressure and flow rate of fluid in the channel
selector valve, said changes arising from an action of said at
least one of the element components.
[0023] A channel selector valve of the present invention as
described in claim 6 is a channel selector valve comprising: a
movable member moving between a first position and a second
position in a housing of the channel selector valve; and driving
means for driving the movable member between the first position and
the second position by employing non-electric motive power, wherein
a first selector port out of two selector ports of the housing
communicates with a main port of the housing through the interior
of the housing when the movable member is situated at the first
position, while a second selector port out of the two selector
ports of the housing communicates with a main port of the housing
through the interior of the housing when the movable member is
situated at the second position.
[0024] The channel selector valve of the present invention as
described in claim 7 is the channel selector valve of the present
invention as described in claim 6, wherein a drive source
generating said non-electric motive power comprises at least one of
element components in a refrigerating cycle having the channel
selector valve, a change in physical quantity, which arises in the
refrigerating cycle from an action of said at least one of element
components, is employed as at least a part of said motive power,
thereby the channel is passively selected.
[0025] The channel selector valve of the present invention as
described in claim 8 is the channel selector valve of the present
invention as described in claim 7, wherein said change in physical
quantity is at least one change among changes in pressure,
differential pressure and flow rate of fluid in the channel
selector valve, said changes arising from an action of said at
least one of the element components.
[0026] A channel selector valve of the present invention as
described in claim 9 is a channel selector valve constituted as a
four-way selector valve by combining a first and second three-way
selector valves, each of which is constituted by the channel
selector valve according to claim 6, 7 or 8.
[0027] The channel selector valve of the present invention as
described in claim 10 is the channel selector valve of the present
invention as described in claim 9, wherein the channel selector
valve is constituted as a four-way selector valve by the first and
second three-way selector valves,
[0028] the main port of the first three-way selector valve is an
inlet port formed in the housing, through which fluid introduced
from the exterior to the interior of the housing of the first
three-way selector valve passes, while the main port of the second
three-way selector valve is an outlet port formed in the housing,
through which the fluid discharged from the interior to the
exterior of the housing of the second three-way selector valve
passes,
[0029] the first selector port of the first three-way selector
valve is connected to the second selector port of the second
three-way selector valve, while the second selector port of the
first three-way selector valve is connected to the first selector
port of the second three-way selector valve,
[0030] the movable member of the second three-way selector valve
moves to the second position when the movable member of the first
three-way selector valve moves to the first position, while the
movable member of the second three-way selector valve moves to the
first position when the movable member of the first three-way
selector valve moves to the second position.
[0031] The channel selector valve of the present invention as
described in claim 11 is the channel selector valve of the present
invention as described in claim 10, wherein said driving means of
the first three-way selector valve comprises:
[0032] a first drive mechanism that moves the movable member
situated at the first position of the first three-way selector
valve to the second position when a difference between a fluid
pressure at the first selector port in the first three-way selector
valve and a fluid pressure at the second selector port cancels out;
and
[0033] a second drive mechanism that moves the movable member
situated at the second position of the first three-way selector
valve to the first position when a difference between a fluid
pressure at the first selector port in the first three-way selector
valve and a fluid pressure at the second selector port cancels
out.
[0034] The channel selector valve of the present invention as
described in claim 12 is the channel selector valve of the present
invention as described in claim 11, wherein the first and second
three-way selector valves are constructed so that the main port is
isolated from the second selector port when the movable member is
situated between the first position and a third position where is
nearer to the second position than the first position, while that
the main port is isolated from the first selector port when the
movable member is situated between the second position and a fourth
position where is between the second position and the third
position,
[0035] the first drive mechanism comprises first storing means for
storing energizing force to move the movable member of the first
three-way selector valve from the first position to the fourth
position, by a fluid pressure being higher than a first
predetermined value of the main port, when the movable member of
the first three-way selector valve is situated at the first
position, said energizing force being less than the first
predetermined value, and
[0036] the second drive mechanism comprises second storing means
for storing energizing force to move the movable member of the
first three-way selector valve from the second position to the
third position, by a fluid pressure being higher than a second
predetermined value of the main port, when the movable member of
the first three-way selector valve is situated at the second
position, said energizing force being less than the second
predetermined value.
[0037] The channel selector valve of the present invention as
described in claim 13 is the channel selector valve of the present
invention as described in claim 6, 7 or 8, wherein the main port is
an inlet port formed in the housing, through which fluid introduced
from the exterior to the interior of the housing passes,
[0038] the housing further comprises an outlet port, through which
the fluid discharged from the interior to the exterior of the
housing passes,
[0039] when the movable member is situated at the first position,
the inlet port and the first selector port are communicated with
each other inside the housing, while the outlet port and the second
selector port are communicated with each other inside the
housing,
[0040] when the movable member is situated at the second position,
the inlet port and the second selector port are communicated with
each other inside the housing, while the outlet port and the first
selector port are communicated with each other inside the
housing.
[0041] The channel selector valve of the present invention as
described in claim 14 is the channel selector valve of the present
invention as described in claim 13, wherein the movable member
partitions the interior of the housing into a first and second
pressure chambers and also forms a first and second spaces in the
first pressure chamber,
[0042] the inlet port is formed in the housing so as to communicate
with the first space and the outlet port is formed in the housing
so as to communicate with the second space,
[0043] when the movable member is situated at the first position,
the fluid introduced from the exterior of the housing into the
first space by way of the inlet port is discharged to the first
selector port, while the fluid discharged from the second space to
the exterior of the housing by way of the outlet port is introduced
from the second selector port,
[0044] when the movable member is situated at the second position,
the fluid introduced from the exterior of the housing into the
first space by way of the inlet port is discharged to the second
selector port, while the fluid discharged from the second space to
the exterior of the housing by way of the outlet port is introduced
from the first selector port.
[0045] A method of driving a channel selector valve as described in
claim 15 is a method of driving the channel selector valve of the
present invention as described in claim 14, comprising the steps
of:
[0046] communicating the first space to the second pressure chamber
through an equalizing path formed in the movable member;
[0047] energizing the movable member in a direction of moving from
the second position to the first position by energizing means for
energizing; and
[0048] applying a force to the movable member from the first
pressure chamber side by fluid introduced from the exterior of the
housing into the first space by way of the inlet port, said force
being stronger than a resultant force consisting of an energizing
force by said energizing means and a force applied to the movable
member by fluid in the second pressure chamber introduced from the
first space by way of said equalizing path,
[0049] thereby the movable member moves from the first position to
the second position.
[0050] The channel selector valve of the present invention as
described in claim 16 is the channel selector valve of the present
invention as described in claim 14, wherein the housing has a valve
seat disposed in the first pressure chamber, the outlet port and
the two selector ports are disposed on the valve seat, the second
space moves on the valve seat responding to a movement of the
movable member moving between the first and second positions, and a
place with which the outlet port communicates by way of the second
space is selected to be either the first selector port or the
second selector port.
[0051] A method of driving a channel selector valve as described in
claim 17 is a method of driving the channel selector valve of the
present invention as described in claim 16, comprising the steps
of:
[0052] communicating the first space to the second pressure chamber
through an equalizing path formed in the movable member;
[0053] energizing the movable member in a direction of moving from
the second position to the first position by energizing means for
energizing; and
[0054] applying a force to the movable member from the first
pressure chamber side by fluid introduced from the exterior of the
housing into the first space by way of the inlet port, said force
being stronger than a resultant force consisting of an energizing
force by said energizing means, a force applied to the movable
member by fluid in the second pressure chamber introduced from the
first space by way of said equalizing path, and a static friction
force between the valve seat and the movable member,
[0055] whereby the movable member moves from the first position to
the second position and
[0056] the movable member is kept staying at the second position by
the static friction force between the valve seat and the movable
member against an energizing force of the energizing means, after a
difference between a pressure of fluid in the first space and that
in the second pressure chamber decreases due to circulation of
fluid between the first space and the second pressure chamber
through the equalizing path.
[0057] The channel selector valve of the present invention as
described in claim 18 is the channel selector valve of the present
invention as described in claim 14 or 16, wherein the driving means
comprises:
[0058] a third drive mechanism that moves the movable member from
one position out of the first and second positions toward an
opposite position; and
[0059] a fourth drive mechanism that moves the movable member from
the opposite position toward the one position,
[0060] wherein the third and fourth drive mechanisms employ a
change in physical quantity of the interior of the housing due to
fluid introduced into the interior of the housing at least as a
part of the motive power.
[0061] The channel selector valve of the present invention as
described in claim 19 is the channel selector valve of the present
invention as described in claim 18, wherein
[0062] the movable member partitions the interior of the housing
into the first pressure chamber, the second pressure chamber, and a
third pressure chamber situated so that the first pressure chamber
is sandwiched between the second and third pressure chambers,
[0063] the channel selector valve further comprises a
non-electrically-driven pilot valve that selectively communicates
the outlet port to either the second pressure chamber or the third
pressure chamber, said pilot valve comprises:
[0064] a second housing having a second main port that is provided
outside the housing and communicates with the outlet port; and
[0065] a selector valeve element that patitions the interior of the
second housing into a fourth pressure chamber communicating with
the third pressure chamber and a fifth pressure chamber
communicating with the second pressure chamber, and that is movable
in the second housing between a fifth position where the second
main port communicates with the fourth pressure chamber and a sixth
position where the second main port communicates with the fifth
pressure chamber, due to a difference between a pressure of fluid
in the second pressure chamber and that in the third pressure
chamber.
[0066] The channel selector valve of the present invention as
described in claim 20 is the channel selector valve of the present
invention as described in claim 19, further comprising second
driving means to move the selector valve element from one position
out of the fifth and sixth positions to an opposire position when
the difference between a pressure of fluid in the second pressure
chamber and that in the third pressure chamber cancels out.
[0067] The channel selector valve of the present invention as
described in claim 21 is the channel selector valve of the present
invention as described in claim 20, wherein
[0068] the movable member has a first equalizing path communicating
the first space to the second pressure chamber and a second
equalizing path communicating the first space to the third pressure
chamber,
[0069] the movable member has a first subvalve that isolates the
third pressure chamber from the fourth pressure chamber when the
movable member is situated at the first position and that
communicates the third pressure chamber to the fourth pressure
chamber when the movable member is situated at the second position,
and has a second subvalve that communicates the second pressure
chamber to the fifth pressure chamber when the movable member is
situated at the first position and that isolates the second
pressure chamber from the fifth pressure chamber when the movable
member is situated at the second position,
[0070] the pilot valve communicates the second main port to the
fourth pressure chamber when the selector valve element is situated
between the fifth position and a seventh position located nearer to
the sixth position than the fifth position, and communicates the
second main port to the fifth pressure chamber when the selector
valve element is situated between the sixth position and a eighth
position located between the sixth position and the seventh
position, and
[0071] the second driving means has third and fourth storing means
for storing energizing force,
[0072] the third storing means for storing energizing force stores
an energizing force, which is less than a third predetermined
value, to move the selector valve element from the fifth position
to the eighth position due to a fluid pressure in the fifth
pressure chamber exceeding the third predetermined value when the
selector valve element is situated at the fifth position, and
[0073] the fourth storing means for storing energizing force stores
an energizing force, which is less than a fourth predetermined
value, to move the selector valve element from the sixth position
to the seventh position due to a fluid pressure in the fourth
pressure chamber exceeding the fourth predetermined value when the
selector valve element is situated at the sixth position.
[0074] The channel selector valve of the present invention as
described in claim 22 is the channel selector valve of the present
invention as described in claim 19, wherein
[0075] a third main port communicating with the inlet port is
further formed in the second housing,
[0076] the third main port communicates with the fifth pressure
chamber when the selector valve element is situated between the
fifth and seventh positions and communicates with the fourth
pressure chamber when the selector valve element is situated
between the sixth and eighth positions,
[0077] and the channel selector valve further comprises second
driving means for moving the selector valve element either from the
fifth position to the eighth position or from the sixth position to
the seventh position when the difference between a pressure of
fluid in the second pressure chamber and that in the third pressure
chamber cancels out.
[0078] The channel selector valve of the present invention as
described in claim 23 is the channel selector valve of the present
invention as described in claim 22, wherein the second driving
means has third and fourth storing means for storing energizing
force,
[0079] the third storing means for storing energizing force stores
an energizing force, which is less than a third predetermined
value, to move the selector valve element from the fifth position
to the eighth position due to a fluid pressure in the fifth
pressure chamber exceeding the third predetermined value when the
selector valve element is situated at the fifth position, and
[0080] the fourth storing means for storing energizing force stores
an energizing force, which is less than a fourth predetermined
value, to move the selector valve element from the sixth position
to the seventh position due to a fluid pressure in the fourth
pressure chamber exceeding the fourth predetermined value when the
selector valve element is situated at the sixth position.
[0081] The channel selector valve of the present invention as
described in claim 24 is the channel selector valve of the present
invention as described in claim 14 or 16, wherein the driving means
comprises:
[0082] a third drive mechanism to move the movable member from one
position out of the first and second positions to an opposite
position; and
[0083] a fourth drive mechanism to move the movable member from the
opposite position to the one position,
[0084] wherein one drive mechanism out of the third and fourth
drive mechanisms employs a change in physical quantity of the
interior of the housing due to fluid introduced into the interior
of the housing at least as a part of the motive power, while an
opposite drive mechanism employs an energizing force that is
applied to the movable member by energizing means received in the
interior of the housing at least as a part of the motive power.
[0085] The channel selector valve of the present invention as
described in claim 25 is the channel selector valve of the present
invention as described in claim 24, further comprising a latch
mechanism that selectively controls a movement of the movable
member from one position out of the first and second positions
toward an opposite position.
[0086] The channel selector valve of the present invention as
described in claim 26 is the channel selector valve of the present
invention as described in claim 25, wherein the latch mechanism
selectively performs a first and second states,
[0087] in the first state, a movement of the movable member to the
opposite position by the driving means is controlled at the first
position, and
[0088] in the second state, a movement of the movable member from
the one position to the opposite position by the driving means is
allowed.
[0089] The channel selector valve of the present invention as
described in claim 27 is the channel selector valve of the present
invention as described in claim 26, wherein the latch mechanism
comprises a latch piece that moves in the housing following a
movement of the movable member between the first and second
positions, and in a first state of the latch mechanism, a movement
of the latch piece is controlled, thereby a movement of the movable
member is controlled at the one position.
[0090] A method of driving a channel selector valve as described in
claim 28 is a method of driving the channel selector valve of the
present invention as described in claim 26 or 27, wherein
[0091] when the movable member, a movement of which to the opposite
position is controlled by the latch mechanism and situated at the
one position, is moved to the opposite position, the movable member
is once moved by the driving means in a direction of moving from
the opposite position to the one position, then is moved from the
one position to the opposite position,
[0092] and when the movable member situated at the opposite
position is moved to the one position, the movable member is once
moved by the driving means in a direction of moving from the one
position to the. opposite position, then is moved from the opposite
position to the one position.
[0093] The channel selector valve of the present invention as
described in claim 29 is the channel selector valve of the present
invention as described in claim 24, further comprising:
[0094] a valve-opening member that moves from a valve-closing
position to a valve-opening position by the motive power while the
third drive mechanism generates the motive power;
[0095] a pilot path that is opened from a valve closing state
thereof by the valve-opening member moved from the valve-closing
position to the valve-opening position;
[0096] an attenuation mechanism acting when the pilot path is open,
which attenuates the motive power generated by the fourth drive
mechanism so as to prevent the movable member from moving from the
opposite position to the one position; and
[0097] a second latch mechanism to selectively control a movement
of the valve-opening member from the valve-closing position to the
valve-opening position.
[0098] The channel selector valve of the present invention as
described in claim 30 is the channel selector valve of the present
invention as described in claim 29, wherein the second latch
mechanism alternately repeats a third and fourth states,
[0099] in the third state, a movement of the valve-opening member
to the valve-opening position is controlled at the valve-closing
position, and
[0100] in the fourth state, a movement of the valve-opening member
from the valve-closing position to the valve-opening position is
allowed.
[0101] A method of driving a channel selector valve as described in
claim 31 is a method of driving the channel selector valve of the
present invention as described in claim 29 or 30, wherein
[0102] when the movable member situated at the one position is
moved to the opposite position, a generation of the motive power by
the third drive mechanism is once halted, then the generation
thereof by the third drive mechanism is started again and then, the
motive power generated by the third drive mechanism is maintained
to be a predetermined value exceeding the motive power, which is
generated by the fourth drive mechanism and attenuated by the
attenuation mechanism,
[0103] and when the movable member situated at the opposite
position is moved to the one position, a generation of the motive
power by the third drive mechanism is halted, then the movable
member is moved from the opposite position to the one position by
the fourth drive mechanism.
[0104] The channel selector valve of the present invention as
described in claim 32 is the channel selector valve of the present
invention as described in claim 24, wherein the driving means
comprises a communication pipe that always communicates the second
pressure chamber to the first selector port outside the
housing.
[0105] The channel selector valve of the present invention as
described in claim 33 is the channel selector valve of the present
invention as described in claim 24, wherein the driving means
comprises a state-holding mechanism to hold the movable member,
which is moved from the first position to the second position, at
the second position.
[0106] The channel selector valve of the present invention as
described in claim 34 is the channel selector valve of the present
invention as described in claim 33, wherein the state-holding
mechanism comprises:
[0107] a state-holding selector valve provided in the second
pressure chamber, which by a selecting action of a second selector
valve element selects either a first state or a second state, in
said first state the second pressure chamber communiates with the
exterior of the housing through a first introducing port and in
said second state the second pressure chamber communicates with the
exterior of the housing through a second introducing port; and
[0108] energizing means for energizing the selector valve, which
energizes the second selector valve element so that the
state-holding selector valve in the second state selects the first
state,
[0109] the movable member allows the energizing means for
energizing the selector valve to energize the second selector valve
element when the movable menber is situated at the first position,
while the movable member makes the second selector valve element
act a selection so that the state-holding selector valve selects
the second state against an energizing by the energizing means for
energizing the selector valve when the movable menber is situated
at the second position.
[0110] The channel selector valve of the present invention as
described in claim 35 is the channel selector valve of the present
invention as described in claim 34, wherein the energizing means
energizes the movable member in a direction of moving from the
second position to the first position, and a pressure of fluid,
which is introduced from the exterior of the housing into the first
space by way of the inlet port, acts on the movable member in a
direction of moving from the first position to the second
position.
[0111] A method of driving a channel selector valve as described in
claim 36 is a method of driving the channel selector valve of the
present invention as described in claim 35, wherein
[0112] when the movable member moves from the first position to the
second position, a pressure of fluid introduced into the first
space from the exterior of the housing by way of the inlet port is
set higher than a predetermined value, so that a force, which is
applied to the movable member by fluid existing in the first space
in a direction from the first position to the second position, is
set stronger than a force, which is applied to the movable member
by fluid existing in the place to which the second pressure chamber
is communicated in a direction from the second position to the
first position,
[0113] after the movable member has moved from the first position
to the second position, a pressure of fluid existing in the first
space and a pressure of fluid existing in the second pressure
chamber are set so that the movable member is kept staying at the
second position.
[0114] The channel selector valve of the present invention as
described in claim 37 is the channel selector valve of the present
invention as described in claim 7, wherein the element component is
an electrically-driven expansion valve provided in the
refrigerating cycle and the change in physical quantity is a change
in pressure of fluid due to a change in an opening ratio of the
electrically-driven expansion valve.
[0115] The channel selector valve of the present invention as
described in claim 38 is the channel selector valve of the present
invention as described in claim 7, wherein the element component is
a compressor provided in the refrigerating cycle and the change in
physical quantity is a change in a frequency of a mechanical
oscillation generated by the compressor.
[0116] The channel selector valve of the present invention as
described in claim 39 is the channel selector valve of the present
invention as described in claim 7, wherein the element component is
a heat exchanger provided in the refrigerating cycle and the change
in physical quantity is a change in pressure of fluid due to a
change in the amount of heat exchange by the heat exchanger.
[0117] The channel selector valve of the present invention as
described in claim 40 is the channel selector valve of the present
invention as described in claim 13, wherein
[0118] the housing is formed cylindrical,
[0119] at least the two selector ports are formed at a valve seat
situated at one end of the housing in a direction of a central axis
of the housing,
[0120] the movable member is constructed by a main valve element,
which is received in the housing and rotative around the central
axis,
[0121] the main valve element is provided with communication means
for selectively communicating a selector port out of the two
selector ports to the main port,
[0122] the main valve element rotates and displaces around the
central axis so as to move between the first and second positions,
when the main valve element is situated at the first position, a
first selector port out of the two selector ports is communicated
to the main port by the communication means, and when the main
valve element is situated at the second position, a second selector
port out of the two selector ports is communicated to the main port
by the communication means.
[0123] The channel selector valve of the present invention as
described in claim 41 is the channel selector valve of the present
invention as described in claim 40, wherein
[0124] at least one port out of the inlet port and the outlet port
is formed at the valve seat,
[0125] an end surface of the main valve element in a direction of
the central axis sits down on the valve seat,
[0126] said end surface is provided with second communication means
for selectively communicating said one port to a first selector
port out of the two selector ports,
[0127] when the main valve element is situated at the first
position, the second communication means communicates the second
selector port to said one port, and when the main valve element is
situated at the second position, the second communication means
communicates the first selector port to said one port.
[0128] The channel selector valve of the present invention as
described in claim 42 is the channel selector valve of the present
invention as described in claim 41, wherein the opposite port is
formed at an opposite end of the housing in a direction of the
central axis, and the communication means has a communication
channel that communicates one end surface side of the main valve
element to an opposite end surface side of the main valve element
in the interior of the housing.
[0129] The channel selector valve of the present invention as
described in claim 43 is the channel selector valve of the present
invention as described in claim 40, further comprising conversion
means for converting a moving direction, which converts a movement
of the main valve element in a direction of the central axis with
respect to the housing into a movement in a rotational direction
around the central axis, wherein the main valve element is movable
in a direction of the central axis in the interior of the housing,
and the driving means makes the main valve element have a
reciprocating motion in a direction of the central axis with
respect to the housing.
[0130] The channel selector valve of the present invention as
described in claim 44 is the channel selector valve of the present
invention as described in claim 43, wherein
[0131] the conversion means for converting a moving direction
comprises:
[0132] a cam groove that is provided in one out of the main valve
element and the housing, and extends over a whole circumference of
the rotational direction; and
[0133] a cam follower pin that is provided in another out of the
main valve element and the housing, and moves in the cam
groove,
[0134] the cam groove has a first and second cam grooves continuing
with each other in the rotational direction, said first cam groove
is formed inclined so as to part from the valve seat in a direction
of the central axis as being displaced in the rotarional direction,
while said second cam groove is formed inclined so as to move
nearer to the valve seat in a direction of the central axis as
being displaced in the rotarional direction.
[0135] The channel selector valve of the present invention as
described in claim 45 is the channel selector valve of the present
invention as described in claim 44, wherein
[0136] the cam groove is provided in the housing,
[0137] the housing comprises an outer housing and an inner housing
received in the outer housing,
[0138] the inner housing comprises a first half and a second half
divided in a direction of the central axis in a state that the
inner housing is received in the outer housing, and
[0139] each guide, which constitutes the cam groove in a state that
an end of the first half and an end of the second half are joined
with each other, is formed at the respective ends of the first and
second halves.
[0140] The channel selector valve of the present invention as
described in claim 46 is the channel selector valve of the present
invention as described in claim 44 or 45, wherein
[0141] at least one port out of the inlet port and the outlet port
is formed at the valve seat,
[0142] second communication means is formed at an end surface of
the main valve element, the end surface faces the valve seat, said
second communication means selectively communicates the opposite
port to a first selector port out of the two selector ports in a
state that the end surface sits down on the valve seat,
[0143] when the main valve element is situated at the first
position, the second selector port is communicated to the opposite
port by the second communication means of the main valve elemnt,
and the end surface of which sits down on the valve seat, and
[0144] when the main valve element is situated at the second
position, the first selector port is communicated to the opposite
port by the second communication means of the main valve elemnt,
and the end surface of which sits down on the valve seat.
[0145] The channel selector valve of the present invention as
described in claim 47 is the channel selector valve of the present
invention as described in claim 46, wherein the opposite port is
formed at an opposite end side of the housing in a direction of the
central axis, and the communication means comprises:
[0146] a communication channel that communicates one end surface
side of the main valve element to an opposite end surface side of
the main valve element in the housing;
[0147] a subvalve that opens and closes the communication
channel;
[0148] subvalve energizing means for energizing the subvalve toward
a direction of closing; and
[0149] valve opening means for opening the subvalve against an
energizing force by the subvalve energizing means in a state that
the one end surface of the main valve element sits down on the
valve seat.
[0150] The channel selector valve of the present invention as
described in claim 48 is the channel selector valve of the present
invention as described in claim 47, wherein the housing is disposed
so that the opposite end of the housing is situated lower than one
end of the housing in a direction of the central axis, and the
driving means employs an own weight of the main valve element at
least as a part of the motive power.
[0151] The channel selector valve of the present invention as
described in claim 49 is the channel selector valve of the present
invention as described in claim 47 or 48, wherein the driving means
employs an energizing force by energizing means for energizing main
valve element, which energizes the main valve element to part from
the valve seat in a direction of the central axis, as a part of the
motive power.
[0152] The channel selector valve of the present invention as
described in claim 50 is the channel selector valve of the present
invention as described in claim 47 or 48, wherein the driving means
comprises second energizing means for energizing the main valve
element, which energizes the main valve element to move nearer to
the valve seat in a direction of the central axis.
[0153] The channel selector valve of the present invention as
described in claim 51 is the channel selector valve of the present
invention as described in claim 50, wherein the driving means
comprises energizing means for energizing the main valve element,
which energizes the main valve element to part from the valve seat
in a direction of the central axis, due to a resultant force of an
energizing force by the energizing means for energizing the main
valve element and an energizing force by the second energizing
means for energizing the main valve element, the cam follower pin
is situated at an intermediate position of the cam groove except
end portions of one end side and an opposite end side of the
housing in a direction of the central axis, and the main valve
element is situated at a neutral position halfway within a
reciprocating motion in a direction of the central axis when the
cam follower pin is situated at the intermediate position.
[0154] The channel selector valve of the present invention as
described in claim 52 is the channel selector valve of the present
invention as described in claim 51, wherein
[0155] an end portion of the one end side of the housing in a
direction of the central axis out of the cam groove is provided
with a groove that continues to a join, at which one end of the
first cam groove being situated at the one end side of the housing
is connected to one end of the second cam groove,
[0156] the groove is formed so that the one end surface of the main
valve element sits down on the valve seat in a state that the cam
follower pin is situated at the groove,
[0157] the groove is disposed being displaced to the lower course
than the join in the rotational direction, and
[0158] when the main valve element moves in the direction away from
the valve seat in a direction of the central axis, a movement of
the cam follower pin is controlled from the groove to a cam groove
out of the first and second cam grooves, which is situated at the
upper course than the groove in the rotational direction.
[0159] The channel selector valve of the present invention as
described in claim 53 is the channel selector valve of the present
invention as described in claim 51 or 52, wherein
[0160] an end portion of the opposite end side of the housing in a
direction of the central axis out of the cam groove is provided
with a second groove that continues to a join, at which an opposite
end of the first cam groove being situated at the opposite end side
of the housing is connected to an opposite end of the second cam
groove,
[0161] the second groove is formed so that the main valve element
is the farthest away from the valve seat in a state that the cam
follower pin is situated at the second groove,
[0162] the second groove is disposed being displaced to the lower
course than the second join in the rotational direction, and
[0163] when the main valve element moves in the direction nearer to
the valve seat in a direction of the central axis, a movement of
the cam follower pin is controlled from the second groove to a cam
groove out of the first and second cam grooves, which is situated
at the upper course than the second groove in the rotational
direction.
[0164] The channel selector valve of the present invention as
described in claim 54 is the channel selector valve of the present
invention as described in any one of claims 40-53, wherein slide
means for decreasing a sliding resistance between the housing and
the main valve element is provided therebetween.
[0165] A compressor with a channel selector valve as described in
claim 55 is a compressor with the channel selector valve as
described in any one of claims 10-14, 16, 18-27, 29-30, 32-35, and
37-54, comprising:
[0166] a compressor housing having an inlet, which is connected to
the outlet port;
[0167] a low pressure chamber that is provided in the interior of
the compressor housing and communiates with the inlet;
[0168] a high pressure chamber that is provided in the interior of
the compressor housing and partitioned off from the low pressure
chamber; and
[0169] a compressing section that is provided in the interior of
the compressor housing, compresses fluid introduced into the low
pressure chamber from the inlet, and guides the fluid into the high
pressure chamber,
[0170] wherein a part of the compressor housing partitioning the
high pressure housing therein is integrally formed with a part of
the housing having the inlet port therein, thereby the interior of
the part of the housing communicates with the high pressure
chamber.
[0171] A device for controlling a refrigerating cycle described in
claim 56 is a device for controlling a refrigerating cycle, which
controls a channel selector valve communicated to the refrigerating
cycle, characterized in that:
[0172] the device controls at least one of a plurality of
functional components communicated to the refrigerating cycle so as
to control the refrigerating cycle; and
[0173] the device controls the channel selector valve by
controlling the functional components.
[0174] A device for controlling a refrigerating cycle described in
claim 57 is a device for controlling a refrigerating cycle, which
controls a channel selector valve communicated to the refrigerating
cycle, characterized in that:
[0175] the device controls at least one of a plurality of
functional components communicated to the refrigerating cycle so as
to control the refrigerating cycle; and
[0176] the device generates a non-electrical motive power by
controlling the functional components and passively controls the
channel selector valve by employing the motive power.
[0177] A device for controlling a refrigerating cycle described in
claim 58 is a device for controlling a refrigerating cycle, which
controls a channel selector valve communicated to the refrigerating
cycle, comprising:
[0178] a microcomputer that controls at least one of a plurality of
functional components communicated to the refrigerating cycle so as
to control the refrigerating cycle; and
[0179] a control program, by which the microcomputer performs a
processing that controls the functional components so as to
generate a non-electrical motive power for passively controlling
the channel selector valve.
[0180] A device for controlling a refrigerating cycle described in
claim 59 is a device for controlling a refrigerating cycle, which
controls a channel selector valve communicated to the refrigerating
cycle, characterized in that:
[0181] the device controls at least one of a plurality of
functional components communicated to the refrigerating cycle so as
to control the refrigerating cycle;
[0182] the non-electrical motive power generated by controlling the
functional components is a physical quantity or a rate of change in
a physical quantity generated by the refrigerating cycle; and
[0183] the device passively controls the channel selector valve by
the physical quantity or the rate of change in a physical
quantity.
[0184] A device for controlling a refrigerating cycle described in
claim 60 is a device for controlling a refrigerating cycle, which
controls a channel selector valve communicated to the refrigerating
cycle, comprising:
[0185] a microcomputer that controls at least one of a plurality of
functional components communicated to the refrigerating cycle so as
to control the refrigerating cycle; and
[0186] a control program, by which the microcomputer performs a
processing that controls the functional components so as to allow
the refrigerating cycle to generate a physical quantity or a rate
of change in a physical quantity as a non-electrical motive power
for passively controlling the channel selector valve.
[0187] The device for controlling a refrigerating cycle as
described in claim 61 is the device for controlling a refrigerating
cycle as described in any one of claims 57-60, wherein the physical
quantity, which is a base for controlling the functional components
to generate the non-electrical motive power, is a parameter
selected from the group consisting of a pressure, temperature, rate
of flow, voltage, current, electrical frequency and mechanical
oscillation frequency with respect to a control of the
refrigerating cycle.
[0188] The device for controlling a refrigerating cycle as
described in claim 62 is the device for controlling a refrigerating
cycle as described in any one of claims 57-60, wherein
[0189] the physical quantity, which is the non-electrical motive
power and is generated by the refrigerating cycle, is a pressure,
differential pressure or rate of flow with respect to fluid
existing in the channel selector valve, and
[0190] the rate of change in a physical quantity, which is the
non-electrical motive power and is generated by the refrigerating
cycle, is a rate of change in pressure, rate of change in
differential pressure or rate of change in rate of flow with
respect to the fluid.
[0191] A device for controlling a refrigerating cycle described in
claim 63 is a device for controlling a refrigerating cycle, which
controls a channel selector valve communicated to the refrigerating
cycle, comprising a control section that receives input signals
sent from an operation command section for commanding an
operational condition of the refrigerating cycle and a physical
quantity detector section for detecting a physical quantity
generated by the refrigerating cycle,
[0192] wherein the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component, and
the device generates a non-electrical motive power by controlling
the refrigerating cycle and passively controls the channel selector
valve by the motive power.
[0193] The device for controlling a refrigerating cycle as
described in claim 64 is the device for controlling a refrigerating
cycle as described in claim 63, wherein the control section
controls at least one of a plurality of functional components
communicated to the refrigerating cycle so as to start an operation
of the refrigerating cycle, thereby controlling the channel
selector valve in a state corresponding to the start of an
operation, which is commanded by the operation command section.
[0194] The device for controlling a refrigerating cycle as
described in claim 65 is the device for controlling a refrigerating
cycle as described in claims 64, wherein the control section starts
to operate a compressor communicated to the refrigerating cycle in
a direction of inverse rotation when the control section decides to
select the channel selector valve on the basis of a command of the
operation command section.
[0195] The device for controlling a refrigerating cycle as
described in claim 66 is the device for controlling a refrigerating
cycle as described in claims 63, wherein the control section
controls at least one of a plurality of functional components
communicated to the refrigerating cycle so as to operate the
refrigerating cycle, thereby controlling the channel selector valve
in a state corresponding to the operation, which is commanded by
the operation command section.
[0196] The device for controlling a refrigerating cycle as
described in claim 67 is the device for controlling a refrigerating
cycle as described in claims 63, wherein the control section
controls at least one of a plurality of functional components
communicated to the refrigerating cycle so as to halt an operation
of the refrigerating cycle, thereby controlling the channel
selector valve in a state corresponding to the halt of the
operation, which is commanded by the operation command section.
[0197] The device for controlling a refrigerating cycle as
described in claim 68 is the device for controlling a refrigerating
cycle as described in any one of claims 63-67, wherein the channel
selector valve is constructed in a manner that a movable member
moves so as to select a channel, and the control section comprises
at least one unit selected from the group consisting of: a memory
unit for memorizing position data of the movable member of the
channel selector valve; a comparison unit and a judge unit for
comparing and judging, respectively, the position data and
operation command data; and a learning unit learning on the basis
of physical quantity data by a control of functional components and
control data of the channel selector valve.
[0198] The device for controlling a refrigerating cycle as
described in claim 69 is the device for controlling a refrigerating
cycle as described in claims 68, wherein the control section
receives the input signals, performs a predetermined processing and
judges whether a channel is to be changed or not to be changed by
the channel selector valve,
[0199] then confirms a position on the basis of present position
data,
[0200] then sends the output signals to the driving section so as
to control the functional components in the refrigerating
cycle,
[0201] then receives new input signals after a predetermined period
of time, confirms a position of the movable member, and sets
position data of said position as new present position data when
said position is changed to a new position.
[0202] The device for controlling a refrigerating cycle as
described in claim 70 is the device for controlling a refrigerating
cycle as described in claims 69, wherein the control section
confirms a position of the movable member by at least one
temperature detection means for detecting temperature, at least one
pressure detection means for detecting pressure, at least one
magnetism detection means for detecting magnetism, at least one
current detection means for detecting current or a combination
thereof after a predetermined period of time, and then installs
position data corresponding to said position into the memory unit
of the control section.
[0203] A device for controlling a refrigerating cycle as described
in claim 71, which controls a channel selector valve that is
communicated to a refrigerating cycle and selects a channel by a
movement of a movable member, comprises:
[0204] a microcomputer that controls at least one of a plurality of
functional components communicated to the refrigerating cycle so as
to control the refrigerating cycle; and
[0205] a control program, by which the microcomputer performs a
processing consisting of the steps of:
[0206] receiving input signals;
[0207] confirming a position by taking out present position data of
a movable member installed in a memory unit;
[0208] carrying out an operation to decide whether the movable
member is to be moved of not to be moved, comparing, and
judging;
[0209] selecting and deciding a driving section;
[0210] outputting drive signals to the driving section selected and
decided;
[0211] judging a position of the movable member by input signals
after a predetermined period of time, with or without moving a
position of the movable member by a physical quantity generated by
at least one functional component that is selected and decided in
said step of selecting and deciding or a rate of the physical
quantity; and
[0212] installing position data of a position of the movable member
into the memory unit when said position is changed to a new
position,
[0213] in order to control the driving section for driving the
functional component so that the position of the movable member is
to be moved or not to be moved.
[0214] A device for controlling a refrigerating cycle as described
in claim 72, which controls a channel selector valve communicated
to the refrigerating cycle, comprises:
[0215] a control section that receives input signals sent from an
operation command section for commanding an operation state of the
refrigerating cycle and from a physical quantity detector section
for detecting a physical quantity generated by the refrigerating
cycle,
[0216] wherein the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component and
to control the refrigerating cycle, and when judging to select a
channel by using the channel selector valve on the basis of a
command of the operation command section, the control section sends
output signals to a driving section for driving a power source of a
compressor so as to start an operation of the compressor of the
refrigerating cycle and starts an operation of the refrigerant
cycle so as to generate a motive power exceeding a first
predetermined motive power, thereby the channel selector valve is
passively controlled.
[0217] A device for controlling a refrigerating cycle as described
in claim 73, which controls a channel selector valve communicated
to the refrigerating cycle, comprises:
[0218] a control section that receives input signals sent from an
operation command section for commanding an operation state of the
refrigerating cycle and from a physical quantity detector section
for detecting a physical quantity generated by the refrigerating
cycle,
[0219] wherein the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component and
to control the refrigerating cycle, and when judging to select a
channel by using the channel selector valve on the basis of a
command of the operation command section, the control section sends
output signals to a driving section for driving a power source of a
compressor so as to start an operation of the compressor in a
direction of inverse rotation and starts an operation of the
refrigerant cycle so as to generate a motive power exceeding a
third predetermined motive power, thereby the channel selector
valve is passively controlled.
[0220] The device for controlling a refrigerating cycle as
described in claim 74 is the device for controlling a refrigerating
cycle as described in claim 72 or 73, wherein
[0221] the channel selector valve selects a channel by moving the
movable member between the first and second positions in response
to an internal motive power,
[0222] the control section memorizes position data corresponding to
the first or second position of the movable member in a memory unit
thereof,
[0223] the control section starts an operation of the refrigerating
cycle when the position data indicates the second or first
position,
[0224] halts the operation of the refrigerating cycle with renewing
position data in the memory unit to the first or second position,
respectively, after a first predetermined period of time, and
[0225] keeps the operation of the refrigerating cycle standby
during a third predetermined period of time.
[0226] The device for controlling a refrigerating cycle as
described in claim 75 is the device for controlling a refrigerating
cycle as described in claim 72, wherein the control section
operates the compressor in a specific frequency immediately after
starting the operation of the compressor and starts an operation of
the refrigerating cycle so that a motive power exceeding a first
predetermined motive power is generated as an internal motive power
of the channel selector valve.
[0227] The device for controlling a refrigerating cycle as
described in claim 76 is the device for controlling a refrigerating
cycle as described in claim 72, wherein the control section starts
an operation of the compressor with a first predetermined
capacity.
[0228] The device for controlling a refrigerating cycle as
described in claim 77 is the device for controlling a refrigerating
cycle as described in claim 72, wherein the control section starts
an operation of the compressor with a second predetermined capacity
so that a motive power lower than a first predetermined motive
power is generated as an internal motive power of the channel
selector valve,
[0229] then operates the refrigerating cycle for a fourth
predetermined period of time,
[0230] then halts the operation of the refrigerating cycle for a
fifth predetermined period of time, and
[0231] then starts an operation of the compressor with a first
predetermined capacity so that a motive power exceeding a first
predetermined motive power is generated as an internal motive power
of the channel selector valve.
[0232] The device for controlling a refrigerating cycle as
described in claim 78 is the device for controlling a refrigerating
cycle as described in claim 72, wherein the control section sends
output signals to a throttle device driving section so that an
opening ratio of a throttle device of the refrigerating cycle is
almost fully opened or almost fully closed.
[0233] The device for controlling a refrigerating cycle as
described in claim 79 is the device for controlling a refrigerating
cycle as described in claim 72, wherein the control section sends
output signals to a heat exchanger motor driving section so that a
heat exchanger motor of the refrigerating cycle is kept halted.
[0234] The device for controlling a refrigerating cycle as
described in claim 80 is the device for controlling a refrigerating
cycle as described in claim 72, 75, 76 or 77, wherein once the
control section starts an operation of the compressor, the control
section sends output signals to the compressor driving section
after a first predetermined period of time and drives the power
source of the compressor so that a motive power exceeding a second
predetermined motive power is generated, thereby operating the
refrigerating cycle.
[0235] The device for controlling a refrigerating cycle as
described in claim 81 is the device for controlling a refrigerating
cycle as described in claim 78, wherein once the control section
starts an operation of the compressor, the control section sends
output signals to the throttle device driving section so as to set
the opening ratio of the throttle device a predetermined opening
ratio after a first predetermined period of time.
[0236] The device for controlling a refrigerating cycle as
described in section to halt the operation of the compressor, then
keeps the refrigerating cycle standby for a third predetermined
period of time, then sends output signals to the compressor driving
section to start the operation of the compressor, then renews
position data in a memory unit to a first or second position after
a first predetermined period of time, thereby halting the operation
of the compressor again.
[0237] The device for controlling a refrigerating cycle as
described in claim 85 is the device for controlling a refrigerating
cycle as described in claim 72, 74 or 84, wherein when positional
data memorized by a memory unit of the control section indicate a
first or second position, the control section starts an operation
of the refrigerating cycle so that a motive power exceeding a first
predetermined motive power is generated as an internal motive power
of the channel selector valve.
[0238] A device for controlling a refrigerating cycle described in
claim 86, which controls a channel selector valve communicated to
the refrigerating cycle, comprises:
[0239] a control section that receives input signals sent from an
operation command section for commanding an operation state of the
refrigerating cycle and from a physical quantity detector section
for detecting a physical quantity generated by the refrigerating
cycle,
[0240] wherein the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component and
to control the refrigerating cycle, and when judging not to select
a channel by using the channel selector valve on the basis of a
command of the operation command section, the control section sends
output signals to a driving section for driving a power source of a
compressor so as to start an operation of the compressor of the
refrigerating cycle and starts an operation of the refrigerant
cycle so as to generate a motive power lower than a first
predetermined motive power, thereby the channel selector valve is
passively controlled.
[0241] The device for controlling a refrigerating cycle as
described in claim 87 is the device for controlling a refrigerating
cycle as described in claim 86, wherein the control section starts
an operation of the compressor with a second predetermined
capacity.
[0242] A device for controlling a refrigerating cycle described in
claim 88, which controls a channel selector valve communicated to
the refrigerating cycle, comprises:
[0243] a control section that receives input signals sent from an
operation command section for commanding an operation state of the
refrigerating cycle and from a physical quantity detector section
for detecting a physical quantity generated by the refrigerating
cycle,
[0244] wherein the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component and
to control the refrigerating cycle, and when judging not to select
a channel by using the channel selector valve on the basis of a
command of the operation command section, the control section sends
output signals to a driving section for driving a power source of a
compressor so as to start an operation of the compressor of the
refrigerating cycle and starts an operation of the refrigerant
cycle so as to generate a motive power exceeding a first
predetermined motive power, thereby the channel selector valve is
passively controlled.
[0245] The device for controlling a refrigerating cycle as
described in claim 89 is the device for controlling a refrigerating
cycle as described in claim 88, wherein when the control section
performs a predetermined processing and judges to halt an operation
of the refrigerating cycle,
[0246] the control section sends output signals to the compressor
driving section so as to halt the operation of the compressor, then
keeps the refrigerating cycle standby for a third predetermined
period of time without renewing position data in a memory unit.
[0247] According to a channel selector valve of the present
invention as described in claim 1, a channel selection of fluid by
the channel selector valve is performed by employing non-electric
motive power.
[0248] According to the channel selector valve of the present
invention as described in claim 2, in the channel selector valve of
the present invention as described in claim 1, a channel selection
of fluid by the channel selector valve is passively performed using
motive power generated by a non-electrically-driven drive source
provided separately from the channel selector valve.
[0249] According to the channel selector valve of the present
invention as described in claim 3, in the channel selector valve of
the present invention as described in claim 2, at least one of
element components in a refrigerating cycle having the channel
selector valve generates a motive power, by which a channel
selection of fluid by the channel selector valve is passively
performed.
[0250] According to the channel selector valve of the present
invention as described in claim 4, in the channel selector valve of
the present invention as described in claim 3, a change in physical
quantity genarated in the refrigerating cycle due to an action of
at least one element component in the refrigerating cycle
constitutes at least a part of a motive power that is used for a
channel selection of fluid by the channel selector valve.
[0251] According to the channel selector valve of the present
invention as described in claim 5, in the channel selector valve of
the Present invention as described in claim 4, when at least one
change among changes in pressure, differential pressure and flow
rate of fluid in the channel selector valve arising from an action
of the element component in the refrigerating cycle takes place,
the change as a change in a physical quantity arising in the
refrigerating cycle is used for a selection of a channel by the
channel selector valve.
[0252] According to a channel selector valve of the present
invention as described in claim 6, a selection of a place where a
main port formed in the housing is communicated to through the
interior of the housing between two selector ports is achieved by
moving a movable member between the first and second positions by
driving means that uses non-electric motive power.
[0253] According to the channel selector valve of the present
invention as described in claim 7, in the channel selector valve of
the present invention as described in claim 6, a motive power,
which is used for selecting a channel of fluid by the channel
selector valve, includes a change in a physical quantity generated
due to an action of at least one of element components in a
refrigerating cycle, thereby a channel selection of the fluid is
passively performed by using the motive power.
[0254] According to the channel selector valve of the present
invention as described in claim 8, in the channel selector valve of
the present invention as described in claim 7, when at least one
change among changes in pressure, differential pressure and flow
rate of fluid in the channel selector valve, which is generated by
an action of at least one element component in the refrigerating
cycle, takes place, the change as a change in physical quantity
generated in the refrigerating cycle is used for a selection of a
channel by the channel selector valve.
[0255] According to a channel selector valve of the present
invention as described in claim 9, when a first and second
three-way selector valves constituted by the channel selector valve
according to claim 6, 7 or 8 are combined, a channel selector valve
is constructed as a four-way selector valve.
[0256] According to the channel selector valve of the present
invention as described in claim 10, in the channel selector valve
of the present invention as described in claim 9, the first
selector port of the first three-way selector valve is connected to
the second selector port of the second three-way selector valve,
while the second selector port of the first three-way selector
valve is connected to the first selector port of the second
three-way selector valve, the main port of the first three-way
selector valve is an inlet port formed in the housing, through
which fluid introduced from the exterior to the interior of the
housing of the first three-way selector valve passes, while the
main port of the second three-way selector valve is an outlet port
formed in the housing, through which the fluid discharged from the
interior to the exterior of the housing of the second three-way
selector valve passes, then, the movable member of the second
three-way selector valve moves to the second position when the
movable member of the first three-way selector valve moves to the
first position, while the movable member of the second three-way
selector valve moves to the first position when the movable member
of the first three-way selector valve moves to the second position,
thereby the channel selector valve is constituted as a four-way
selector valve by the first and second three-way selector
valves.
[0257] According to the channel selector valve of the present
invention as described in claim 11, in the channel selector valve
of the present invention as described in claim 10, when a
difference between a pressure of fluid at the first selector port
and that at the second selector port cancels out, the movable
member of the first three-way selector valve situated at the first
position is moved to the second position by a first drive mechanism
of the first three-way selector valve, while the movable member of
the first three-way selector valve situated at the second position
is moved to the first position by a second drive mechanism.
[0258] According to the channel selector valve of the present
invention as described in claim 12, in the channel selector valve
of the present invention as described in claim 11, in the first
three-way selector valve, when a fluid pressure at the main port
exceeds a first predetermined value, the movable member is situated
at the first position by the fluid pressure, thereby the main port
communicates with the first selector port and an energizing force
is stored in a first storing means for storing energizing force,
while when a fluid pressure at the main port is lower than a first
predetermined value, the movable member is moved from the first
position to the fourth position against the fluid pressure at the
main port by the energizing force stored in the first storing means
for storing energizing force, thereby a place where the main port
is communicated to is switched from the first selector port to the
second selector port.
[0259] Then, in a state that the movable member is situated at the
fourth position, when the fluid pressure at the main port exceeds a
second predetermined value, the movable member is moved from the
fourth position to the second position by the fluid pressure and an
energizing force is stored in the second storing means for storing
energizing force, while when a fluid pressure at the main port is
lower than the second predetermined value, the movable member is
moved from the second position to the third position against the
fluid pressure at the main port by the energizing force stored in
the second storing means for storing energizing force, thereby a
place where the main port is communicated to is switched from the
second selector port to the first selector port.
[0260] According to the channel selector valve of the present
invention as described in claim 13, in the channel selector valve
of the present invention as described in claim 6, 7 or 8, out of an
inlet port formed in the housing, through which fluid introduced
from the exterior to the interior of the housing passes, and an
outlet port, through which the fluid discharged from the interior
to the exterior of the housing passes, the inlet port is set to be
the main port, then, when the movable member is situated at the
first position, the inlet port and the first selector port are
communicated with each other inside the housing, while the outlet
port and the second selector port are communicated with each other
inside the housing, on the other hand, when the movable member is
situated at the second position, the inlet port and the second
selector port are communicated with each other inside the housing,
while the outlet port and the first selector port are communicated
with each other inside the housing.
[0261] According to the channel selector valve of the present
invention as described in claim 14, in the channel selector valve
of the present invention as described in claim 13, the movable
member is moved between the first and second position by changing a
difference between a pressure of fluid introduced from the exterior
of the housing and a pressure of fluid discharged to the exterior
of the housing by using a motive power generated by a
non-electrically-driven drive, thereby a linear slide-type four-way
selector valve is constructed by the channel selector valve.
[0262] According to a method of driving the channel selector valve
of the present invention as described in claim 15, when the channel
selector valve of the present invention as described in claim 14 is
drived, when there is no difference between a pressure of fluid in
the first space and a pressure of fluid in the second pressure
chamber, the movable member energized by the energizing means is
situated at the first position, thereby the first selector port is
set to be a place where the fluid, which is introduced from the
exterior of the housing to the first space by way of the inlet
port, is discharged to, while the second selector port is set to be
a place where the fluid, which is discharged from the second space
to the exterior of the housing by way of the outlet port, is
introduced from.
[0263] When a pressure of the fluid, which is introduced from the
exterior of the housing to the first space of the first pressure
chamber by way of the inlet port, is raised so that a force, which
exceeds a resultant force of the energizing force by the enrgizing
means and a force that the fluid in the second pressure chamber
acts on the movable member, is acted on the movable member from the
first pressure chamber side, the movable member situated at the
first position by the energizing force by the enrgizing means moves
to the second position against the energizing force by the
enrgizing means, thereby the second selector port is set to be a
place where the fluid, which is introduced from the exterior of the
housing to the first space by way of the inlet port, is discharged
to, while the first selector port is set to be a place where the
fluid, which is discharged from the second space to the exterior of
the housing by way of the outlet port, is introduced from.
[0264] Then, when the movable member moves from the first position
to the second position, since a pressure of the fluid in the second
pressure chamber is compressed to become high, a pressure of the
fluid, which is introduced from the exterior of the housing into
the first space of the first pressure chamber by way of the inlet
port, is set high so that the force, which exceeds a resultant
force of the energizing force by the enrgizing means and a force
that the fluid in the second pressure chamber acts on the movable
member, is acted on the movable member from the first pressure
chamber side, thereby the movable member moved from the first
position is held at the second position.
[0265] According to the channel selector valve of the present
invention as described in claim 16, in the channel selector valve
of the present invention as described in claim 14, when a force
acted on the movable member from the first pressure chamber side by
a pressure of the fluid, which is introduced into the first space
of the housing by way of the inlet port, is equal to or lower than
a resultant force of the energizing force by the energizing means,
a force that the fluid in the second pressure chamber acts on the
movable member and a static friction force between the valve seat
and the movable member, the movable member stays at the first
position.
[0266] Therefore, the first selector port is set to be a place
where the fluid, which is introduced from the exterior of the
housing to the first space by way of the inlet port, is discharged
to, while the second selector port is set to be a place where the
fluid, which is discharged from the second space to the exterior of
the housing by way of the outlet port, is introduced from.
[0267] On the other hand, when a force acted on the movable member
from the first pressure chamber side by a pressure of the fluid,
which is introduced into the first space of the housing by way of
the inlet port, exceeds a resultant force of the energizing force
by the energizing means, a force that the fluid in the second
pressure chamber acts on the movable member and a static friction
force between the valve seat and the movable member, the movable
member moves to the second position against the energizing force by
the energizing means.
[0268] Therefore, the second selector port is set to be a place
where the fluid, which is introduced from the exterior of the
housing to the first space by way of the inlet port, is discharged
to, while the first selector port is set to be a place where the
fluid, which is discharged from the second space to the exterior of
the housing by way of the outlet port, is introduced from.
[0269] Then, after the movable member moves to the second position,
when a force acted on the movable member from the first pressure
chamber side by a pressure of the fluid, which is introduced into
the first space of the housing by way of the inlet port, exceeds a
force, which is resulted by subtracting a static friction force
between the valve seat and the movable member from a resultant
force consisting of the energizing force by the energizing means
and a force that the fluid in the second pressure chamber acts on
the movable member, the movable member keeps staying at the second
position against the energizing force by the energizing means.
[0270] According to a method of driving the channel selector valve
of the present invention as described in claim 17, when the channel
selector valve of the present invention as described in claim 16 is
drived, if the movable member moves from the first position to the
second position, the fluid in the second pressure chamber is
compressed to give a change in pressure with respect to fluid in
the first space, however, since the first space communicates with
the second pressure chamber through the equalizing path, a pressure
of fluid in the first space becomes close to that in the second
pressure chamber.
[0271] Then, the force acted on the movable member by the fluid in
the first space soon becomes eqaul to the resultant force
consisting of the energizing force by the energizing means and the
force that the fluid in the second pressure chamber acts on the
movable member, then becomes even lower than that, resulting in
that the movable member is ready to move toward the first position
from the second position, however, the static friction force
between the valve seat and the movable member acts against the
energizing force by the energizing means even after a difference
between the pressure of the fluid in the first space and that in
the second pressure chamber decreases, thereby the movable member
is held at the second position by the static friction force.
[0272] According to the channel selector valve of the present
invention as described in claim 18, in the channel selector valve
of the present invention as described in claim 14 or 16, when a
physical quantity in the housing is changed by the fluid, which is
introduced from the exterior into the interior of the housing by
way of an inlet port of the housing, the change in physical
quantity is utilized as at least a part of a motive power for
moving the movable member between the first and second position, by
third and fourth drive mechanisms.
[0273] According to the channel selector valve of the present
invention as described in claim 19, in the channel selector valve
of the present invention as described in claim 18, when the
selector valve element of the pilot valve is situated at the fifth
position, the outlet port communicates with the third pressure
chamber through the second main port of the pilot valve and the
fourth pressure chamber, while when the selector valve element of
the pilot valve is situated at the sixth position, the outlet port
communicates with the second pressure chamber through the second
main port of the pilot valve and the fifth pressure chamber.
[0274] Therefore, if a pressure of the fluid at the inlet port from
which the fluid is introduced exceeds a pressure of the fluid at
the outlet port from which the fluid is discharged, the selector
valve element of the pilot valve is moved between the fifth and
sixth position so that either the second pressure chamber or the
third pressure chamber, placed sandwiching the first pressure
chamber with each other, is selected as a chamber, a fluid pressure
of which is lower than that in the first space of the first
pressure chamber, thereby a direction of the movable member to move
by a difference in pressure of the fluid is selected between a
direction from the first position to the second position and that
from the second position to the first position.
[0275] According to the channel selector valve of the present
invention as described in claim 20, in the channel selector valve
of the present invention as described in claim 19, when a
difference between a pressure of fluid in the second pressure
chamber and that in the third pressure chamber cancels out, the
selector valve element is moved from one to another between the
fifth and sixth positions by second driving means.
[0276] According to the channel selector valve of the present
invention as described in claim 21, in the channel selector valve
of the present invention as described in claim 20, when the
selector valve element of the pilot valve is situated at the
seventh position, the second main port communicating with the
outlet port communicates with the fourth pressure chamber
communicating with the third pressure chamber, thereby the outlet
port communicates with the third pressure chamber through the pilot
valve.
[0277] In this state, when a pressure of the fluid in the first
space of the first pressure chamber communicating with the inlet
port increases to exceed a pressure of the fluid in the third
pressure chamber communicating with the outlet port, the movable
member moves so that the volume of the third pressure chamber
decreases, resulting in that the volume of the second pressure
chamber increases, in other words, the movable member moves from
the second position to the first position, then the third pressure
chamber is isolated from the fourth pressure chamber by a first
subvalve while the second pressure chamber is communicated to the
fifth pressure chamber by a second subvalve.
[0278] Then, a pressure of the fluid in the second pressure chamber
communicating with the first space by a first equalizing path
increases in response to an increases in that in the first space,
thereby when a pressure of the fluid in the fifth pressure chamber
communicating with the second pressure chamber increases and
exceeds a third predetermined value, the selector valve element
situated at the seventh position moves to the fifth position and an
energizing force is stored in a third storing means for storing
energizing force.
[0279] Thereafter, when a pressure of the fluid in the second or
fifth pressure chamber becomes lower than a third predetermined
value due to a decrease in a pressure of the fluid in the first
space, the selector valve element is moved from the fifth position
to the eighth position against a pressure of the fluid in the fifth
pressure chamber by an energizing force of the third storing means
for storing energizing force, thereby the second main port
communicating with the outlet port communicates with the fifth
pressure chamber communicating with the second pressure chamber,
resulting in that the outlet port communicates with the second
pressure chamber through the pilot valve.
[0280] In this state, when a pressure of the fluid in the first
space of the first pressure chamber communicating with the inlet
port increases to exceed a pressure of the fluid in the second
pressure chamber communicating with the outlet port, the movable
member moves so that the volume of the second pressure chamber
decreases, resulting in that the volume of the third pressure
chamber increases, in other words, the movable member moves from
the first position to the second position, then the third pressure
chamber is communicated to the fourth pressure chamber by a first
subvalve while the second pressure chamber is isolated from the
fifth pressure chamber by a second subvalve.
[0281] Then, a pressure of the fluid in the third pressure chamber
communicating with the first space by a second equalizing path
increases in response to an increases in that in the first space,
thereby when a pressure of the fluid in the fourth pressure chamber
communicating with the third pressure chamber increases and exceeds
a fourth predetermined value, the selector valve element situated
at the eighth position moves to the sixth position and an
energizing force is stored in a fourth storing means for storing
energizing force.
[0282] Thereafter, when a pressure of the fluid in the third or
fourth pressure chamber becomes lower than a fourth predetermined
value due to a decrease in a pressure of the fluid in the first
space, the selector valve element is moved from the sixth position
to the seventh position against a pressure of the fluid in the
fourth pressure chamber by an energizing force of the fourth
storing means for storing energizing force, thereby the second main
port communicating with the outlet port communicates with the
fourth pressure chamber communicating with the third pressure
chamber, resulting in that the outlet port communicates with the
third pressure chamber through the pilot valve.
[0283] Therefore, in this state, when a pressure of the fluid in
the first space of the first pressure chamber communicating with
the inlet port increases to exceed a pressure of the fluid in the
third pressure chamber communicating with the outlet port, the
movable member moves from the second position to the first
position.
[0284] According to the channel selector valve of the present
invention as described in claim 22, in the channel selector valve
of the present invention as described in claim 19, when a
difference between a pressure of fluid in the second pressure
chamber and that in the third pressure chamber cancels out, the
selector valve element is moved from one to another between the
fifth and sixth positions by second driving means.
[0285] When the selector valve element of the pilot valve is
situated at the fifth position, the inlet port communicates with
the second pressure chamber through the third main port of the
pilot valve and the fifth pressure chamber, while when the selector
valve element of the pilot valve is situated at the sixth position,
the inlet port communicates with the third pressure chamber through
the third main port of the pilot valve and the fourth pressure
chamber.
[0286] According to the channel selector valve of the present
invention as described in claim 23, in the channel selector valve
of the present invention as described in claim 22, when the
selector valve element of the pilot valve is situated at the
seventh position, the third main port communicating with the inlet
port communicates with the fifth pressure chamber communicating
with the second pressure chamber, thereby the inlet port
communicates with the second pressure chamber through the pilot
valve.
[0287] In this state, when a pressure of the fluid in the first
space of the first pressure chamber communicating with the inlet
port increases, the movable member moves so that the volume of the
second pressure chamber increases, resulting in that the volume of
the third pressure chamber decreases, in other words, the movable
member moves from the second position to the first position.
[0288] Then, a pressure of the fluid in the second pressure chamber
communicating with the first space by a first equalizing path
increases in response to an increases in that in the first space,
thereby when a pressure of the fluid in the fifth pressure chamber
communicating with the second pressure chamber increases and
exceeds a third predetermined value, the selector valve element
situated at the seventh position moves to the fifth position and an
energizing force is stored in a third storing means for storing
energizing force.
[0289] Thereafter, when a pressure of the fluid in the second or
fifth pressure chamber becomes lower than a third predetermined
value due to a decrease in a pressure of the fluid in the first
space, the selector valve element is moved from the fifth position
to the eighth position against a pressure of the fluid in the fifth
pressure chamber by an energizing force of the third storing means
for storing energizing force, thereby the third main port
communicating with the inlet port communicates with the fourth
pressure chamber communicating with the third pressure chamber,
resulting in that the inlet port communicates with the third
pressure chamber through the pilot valve.
[0290] In this state, when a pressure of the fluid in the first
space of the first pressure chamber communicating with the inlet
port increases, the movable member moves so that the volume of the
third pressure chamber increases, resulting in that the volume of
the second pressure chamber decreases, in other words, the movable
member moves from the first position to the second position.
[0291] Then, a pressure of the fluid in the third pressure chamber
communicating with the first space by a second equalizing path
increases in response to an increases in that in the first space,
thereby when a pressure of the fluid in the fourth pressure chamber
communicating with the third pressure chamber increases and exceeds
a fourth predetermined value, the selector valve element situated
at the eighth position moves to the sixth position and an
energizing force is stored in a fourth storing means for storing
energizing force.
[0292] Thereafter, when a pressure of the fluid in the third or
fourth pressure chamber becomes lower than a fourth predetermined
value due to a decrease in a pressure of the fluid in the first
space, the selector valve element is moved from the sixth position
to the seventh position against a pressure of the fluid in the
fourth pressure chamber by an energizing force of the fourth
storing means for storing energizing force, thereby the third main
port communicating with the inlet port communicates with the fifth
pressure chamber communicating with the second pressure chamber,
resulting in that the inlet port communicates with the second
pressure chamber through the pilot valve.
[0293] Therefore, in this state, when a pressure of the fluid in
the first space of the first pressure chamber communicating with
the inlet port increases, the movable member moves from the second
position to the first position.
[0294] According to the channel selector valve of the present
invention as described in claim 24, in the channel selector valve
of the present invention as described in claim 14 or 16, when an
internal pressure of the housing is changed by the fluid, which is
introduced from the exterior of the housing into the interior
thereof through the inlet port of the housing, one drive mechanism
out of the third and fourth drive mechanisms of the driving means
moves the movable member between the first and second positions by
employing a change in physical quantity in the housing as at least
a part of a motive power.
[0295] When the movable member is moved by the one drive mechanism,
an energizing force is stored in the energizing means received in
the housing, then another drive mechanism out of the third and
fourth drive mechanisms moves the movable member between the first
and second positions by employing the energizing force stored in
the energizing means as at least a part of a motive power.
[0296] According to the channel selector valve of the present
invention as described in claim 25, in the channel selector valve
of the present invention as described in claim 24, a latch
mechanism selectively controls a movement of the movable member,
which is moved by the driving means from one position to another
position between the first and second positions, thereby the
movable member situated at either the first or second position is
stayed at one position or moved to another position
selectively.
[0297] According to the channel selector valve of the present
invention as described in claim 26, in the channel selector valve
of the present invention as described in claim 25, the latch
mechanism performs the first state, in which the movable member
that is moved from one position to another position between the
first and second positions by the driving means is held at the one
position, while the latch mechanism performs the second state, in
which the movable member that is allowed to move from one position
to another position between the first and second positions moves
from the one position to the another position.
[0298] According to the channel selector valve of the present
invention as described in claim 27, in the channel selector valve
of the present invention as described in claim 26, when a movement
of a latch piece is controled, a movement of the movable member, to
which the latch piece follow, is controlled at one position.
[0299] According to a method of driving the channel selector valve
of the present invention as described in claim 28, in the channel
selector valve of the present invention as described in claim 26 or
27, before the movable member is moved from one position to another
position by the driving means, the movable member is once moved in
a direction of moving from the another position to the one
position, then a control of a movement of the movable member at the
one position by the latch mechanism is removed, thereby allowing
the movable member to move from the one position to the another
position.
[0300] Moreover, when the movable member is moved from the one
position toward the another position after the movable member is
moved from the another position to the one position by the driving
means, a movement of the movable member is controlled by the latch
mechanism, thereby the movable member is held at the one
position.
[0301] According to the channel selector valve of the present
invention as described in claim 29, when the third drive mechanism
generates a motive power in order to move the movable member of the
channel selector valve of the present invention as described in
claim 24 from one position to another position between the first
and second positions, a valve-opening member is about to move from
a valve-closing position to a valve-opening position by the motive
power, thereby this movement of the valve-opening member is
selectively controlled by the second latch mechanism.
[0302] Here, when the second latch mechanism controls a movement of
the valve-opening member, since the valve-opening member is held at
the valve-closing position and does not move to the valve-opening
position, the pilot valve is held in its closed state and an
attenuation mechanism does not act, thereby a motive power
generated by the fourth drive mechanism is not attenuated and a
movement of the movable member from the another position to the one
position between the first and second positions by the motive power
generated by the fourth drive mechanism is prohibited.
[0303] To the contrary, when the second latch mechanism does not
control a movement of the valve-opening member from the
valve-closing position to the valve-opening position, the
valve-opening member moves from the valve-closing position to the
valve-opening position, the pilot valve is opened by this
valve-opening member that has moved to the valve-opening position,
thereby the attenuation mechanism acts so as to attenuate the
motive power generated by the fourth drive mechanism and a movement
of the movable member from the another position to the one position
between the first and second positions by the motive power
generated by the fourth drive mechanism is allowed.
[0304] According to the channel selector valve of the present
invention as described in claim 30, in the channel selector valve
of the present invention as described in claim 29, if the second
latch mechanism alternately repeats the third and fourth states,
when the movable member is moved from one position to another
position by a motive power generated by the third drive mechanism,
a state that a movement of the movable member from the another
position to the one position by a motive power generated by the
fourth drive mechanism is allowed and a state that a movement of
the movable member from the another position to the one position by
a motive power generated by the fourth drive mechanism is
prohibited are alternately produced.
[0305] According to a method of driving the channel selector valve
of the present invention as described in claim 31, in the channel
selector valve of the present invention as described in claim 29 or
30, when a drive source of the third drive mechanism is allowed to
generate a motive power again after the generation of a motive
power by the drive source of the third drive mechanism is halted,
the second latch mechanism is transferred between a state in which
a movement of the valve-opening member from the valve-closing
position to the valve-opening position is controlled and a state in
which said control is removed, thereby the system can be
transferred from one state, in which the movable member can move
from the another position to the one position by using a motive
power generated by the fourth drive mechanism, to another state in
which the movable member cannot move from the another position to
the one position, or the system can be transferred from the another
state to the one state.
[0306] According to the channel selector valve of the present
invention as described in claim 32, in the channel selector valve
of the present invention as described in claim 24, if the movable
member keeps staying at the first position, a place where the
fluid, which is introduced from the exterior of the housing into
the first space by way of the inlet port, is discharged to is the
first selector port, in addition, a place where the fluid, which is
discharged from the second space to the exterior of the housing by
way of the outlet port, is introduced from is still the second
selector port, therefore a pressure of the fluid in the second
pressure chamber communicating with the first selector port by way
of the communication pipe becomes equal to a pressure of the fluid
in the first space communicating with the first selector port or
that at the inlet port.
[0307] Therefore, as long as a force applied to the movable member
from the first pressure chamber side due to a pressure of the fluid
introduced into the first space of the housing by way of the inlet
port is lower than a resultant force of the energizing force by the
energizing means and a force that the fluid in the second pressure
chamber acts on the movable member, or is lower than a force
consisting of said resultant force and a static friction force
between the seat valve and the movable member, the movable member
keeps staying at the first position, consequently, a place, to
which the inlet port or the outlet port is communicated, is not
selected (i.e. not changed).
[0308] To the contrary, when a force applied to the movable member
from the first pressure chamber side due to a pressure of the fluid
introduced into the first space of the housing by way of the inlet
port exceeds a resultant force of the energizing force by the
energizing means and a force that the fluid in the second pressure
chamber acts on the movable member, or exceeds a force consisting
of said resultant force and a static friction force between the
seat valve and the movable member, the movable member moves from
the first position to the second position, thereby a place where
the fluid, which is introduced from the exterior of the housing
into the first space by way of the inlet port, is discharged to is
selected to be the second selector port, in addition, a place where
the fluid, which is discharged from the second space to the
exterior of the housing by way of the outlet port, is introduced
from is selected to be the first selector port.
[0309] Therefore, a pressure of the fluid in the second pressure
chamber communicating with the first selector port by way of the
communication pipe becomes equal to a pressure of the fluid at the
outlet port communicating with the first selector port, then said
pressure becomes different from a pressure of the fluid at the
inlet port communicating with the first space.
[0310] Consequently, as long as a pressure of the fluid at the
inlet port is thereafter kept so that a force applied to the
movable member from the first pressure chamber side due to a
difference between a pressure of the fluid at the outlet port and
that at the inlet port exceeds a resultant force consisting of the
energizing force by the energizing means and a force that the fluid
in the second pressure chamber acts on the movable member, or
exceeds a force, which is resulted by subtracting a static friction
force between the valve seat and the movable member from said
resultant force consisting of the energizing force by the
energizing means and a force that the fluid in the second pressure
chamber acts on the movable member, the movable member keeps
staying at the second position against an energizing force by the
energizing means, thereby a place to which the inlet port or the
outlet port is communicated is kept as selected (i.e. as
changed).
[0311] Then, after the movable member has moved to the second
position, when a pressure of the fluid at the inlet port decreases
so that a force applied to the movable member from the first
pressure chamber side due to a difference between a pressure of the
fluid at the outlet port and that at the inlet port is lower than a
resultant force consisting of the energizing force by the
energizing means and a force that the fluid in the second pressure
chamber acts on the movable member, or is lower than a force, which
is resulted by subtracting a static friction force between the
valve seat and the movable member from said resultant force
consisting of the energizing force by the energizing means and a
force that the fluid in the second pressure chamber acts on the
movable member, the movable member moves from the second position
to the first position by an energizing force of the energizing
means.
[0312] Thereby, a place where the fluid, which is introduced from
the exterior of the housing into the first space by way of the
inlet port, is discharged to is selected to be the first selector
port, in addition, a place where the fluid, which is discharged
from the second space to the exterior of the housing by way of the
outlet port, is introduced from is selected to be the second
selector port.
[0313] According to the channel selector valve of the present
invention as described in claim 33, in the channel selector valve
of the present invention as described in claim 24, if the movable
member is moved from the first position to the second position so
that a channel of the fluid is selected by the channel selector
valve using a motive power generated by a non-electrically-driven
drive source, the movable member is held at the second position by
a state-holding mechanism.
[0314] According to the channel selector valve of the present
invention as described in claim 34, in the channel selector valve
of the present invention as described in claim 33, when the movable
member is situated at the first position, an energizing of a second
selector valve element by energizing means for energizing the
selector valve is allowed, thereby a state-holding selector valve
is set in a first state in which the second pressure chamber is
communicated to the exterior of the housing through a first
introducing port, while when the movable member is situated at the
second position, against the energizing by the energizing means for
energizing the selector valve, the state-holding selector valve is
set in a second state in which the second pressure chamber is
communicated to the exterior of the housing through a second
introducing port.
[0315] Whether the movable member is situated at the first position
or the second position depends upon whether a force applied to the
movable member from the first space side is higher or not than a
force applied to the movable member from the second pressure
chamber side, as a result of taking the following forces into
consideration, said following forces are a force applied to the
movable member by the fluid in the first space, a force applied to
the movable member by the fluid flowed into the second pressure
chamber, a static friction force between the valve seat and the
movable member, and an energizing force by the energizing
means.
[0316] Therefore, when the movable member is situated at the first
position, as long as a pressure of the fluid at the inlet port
communicating with the first space is set so that a force applied
to the movable member from the second pressure chamber side, which
depends on a pressure of the fluid at a place to which the first
introducing port communicating with the second pressure chamber is
communicated, exceeds a force applied to the movable member from
the first space side, the movable member keeps staying at the first
position, thereby the first selector port out of the two selector
ports formed in the housing communicates with the inlet port
through the first space, while the second selector port out of the
two selector ports communicates with the outlet port through the
second space.
[0317] On the other hand, when a pressure of the fluid in the first
space increases so that a force applied to the movable member from
the first space side exceeds a force applied to the movable member
from the second pressure chamber side, which depends on a pressure
of the fluid at a place to which the first introducing port
communicating with the second pressure chamber is communicated, the
movable member moves from the first position to the second position
in the housing, thereby the first selector port out of the two
selector ports formed in the housing communicates with the outlet
port through the first space, while the second selector port out of
the two selector ports communicates with the inlet port through the
second space, and a place to which the second pressure chamber is
communicated is selected from the first introducing port to the
second introducing port.
[0318] Here, if a pressure of the fluid in a place to which the
second introducing port is communicated is set lower to some extent
than that in a place to which the first introducing port is
communicated, even when a pressure of the fluid in the first space
decreases to some extent, a force applied to the movable member
from the first space side exceeds a force applied to the movable
member from the second pressure chamber side, thereby the movable
member keeps staying at the second position.
[0319] However, when a pressure of the fluid in the first space
markedly decreases so that a force applied to the movable member
from the second pressure chamber side exceeds a force applied to
the movable member from the first space side, the movable member
moves from the second position to the first position in the
housing, thereby the first selector port out of the two selector
ports formed in the housing communicates with the inlet port
through the first space, while the second selector port out of the
two selector ports communicates with the outlet port through the
second space, and a place to which the second pressure chamber is
communicated is selected from the second introducing port to the
first introducing port.
[0320] Since a pressure of the fluid in a place to which the first
introducing port is communicated is set higher to some extent than
that in a place to which the second introducing port is
communicated, even when a pressure of the fluid in the first space
is kept very low after the movable member has moved from the second
position to the first position, a force applied to the movable
member from the second pressure chamber side exceeds a force
applied to the movable member from the first space side, thereby
the movable member keeps staying at the first position.
[0321] According to the channel selector valve of the present
invention as described in claim 35, in the channel selector valve
of the present invention as described in claim 34, when the movable
member is situated at the first position, as long as a force
applied to the movable member by the fluid in the first space is
lower than a resultant force of the energizing force by the
energizing means and a force applied to the movable member by the
fluid, which flowed into the second pressure chamber from a place
to which the first introducing port is communicated, or is lower
than a force consisting of said resultant force and a static
friction force between the seat valve and the movable member, the
movable member keeps staying at the first position.
[0322] On the other hand, a pressure of the fluid in the first
space increases so that a force applied to the movable member by
the fluid in the first space exceeds a resultant force of the
energizing force by the energizing means and a force applied to the
movable member by the fluid, which flowed into the second pressure
chamber from a place to which the first introducing port is
communicated, or exceeds a force consisting of said resultant force
and a static friction force between the seat valve and the movable
member, the movable member moves from the first position to the
second position in the housing.
[0323] Here, if a pressure of the fluid in a place to which the
second introducing port is communicated is set lower to some extent
than that in a place to which the first introducing port is
communicated, even when a pressure of the fluid in the first space
decreases to some extent, a force applied to the movable member
from the first space side exceeds a resultant force consisting of
the energizing force by the energizing means and a force applied to
the movable member by the fluid flowed into the second pressure
chamber, or exceeds a force, which is resulted by subtracting a
static friction force between the valve seat and the movable member
from said resultant force consisting of the energizing force by the
energizing means and a force applied to the movable member by the
fluid flowed into the second pressure chamber, thereby the movable
member keeps staying at the second position.
[0324] Since a pressure of the fluid in a place to which the first
introducing port is communicated is set higher to some extent than
that in a place to which the second introducing port is
communicated, even when a pressure of the fluid in the first space
is kept very low after the movable member has moved from the second
position to the first position, a resultant force consisting of the
energizing force by the energizing means and a force applied to the
movable member by the fluid flowed into the second pressure
chamber, or a force, which is resulted by subtracting a static
friction force between the valve seat and the movable member from
said resultant force consisting of the energizing force by the
energizing means and a force applied to the movable member by the
fluid flowed into the second pressure chamber, exceeds a force
applied to the movable member from the first space side, thereby
the movable member keeps staying at the first position.
[0325] According to a method of driving the channel selector valve
of the present invention as described in claim 36, when the channel
selector valve of the present invention as described in claim 35 is
drived, a pressure of fluid introduced into the first space from
the exterior of the housing by way of the inlet port is set higher
than a predetermined value, so that a force, which is applied to
the movable member by fluid existing in the first space in a
direction from the first position to the second position, is set
stronger than a force, which is applied to the movable member by
fluid existing in the place to which the second pressure chamber is
communicated in a direction from the second position to the first
position, thereby the movable:member moves from the first position
to the second position, in addition thereafter, a pressure of fluid
existing in the first space and a pressure of fluid existing in the
second pressure chamber are set so that the movable member is kept
staying at the second position.
[0326] According to the channel selector valve of the present
invention as described in claim 37, in the channel selector valve
of the present invention as described in claim 7, an opening ratio
of the electrically-driven expansion valve in the refrigerating
cycle is changed to change a pressure of fluid in the refrigerating
cycle, thereby a balance, between a force that the fluid in the
channel selector valve is applied to the movable member to move
from the first position to the second position and a force that the
fluid in the channel selector valve is applied to the movable
member to move from the second position to the first position,
changes, thereby the movable member moves between the first and
second positions.
[0327] According to the channel selector valve of the present
invention as described in claim 38, in the channel selector valve
of the present invention as described in claim 7, when a frequency
of an oscillation generated by the compressor in the refrigerating
cycle is changed, a member that responds only to a specific
frequency produces a change in condition, then a pressure of the
fluid in the second pressure chamber changes, thereby a balance,
between a force that the fluid in the channel selector valve is
applied to the movable member to move from the first position to
the second position and a force that the fluid in the channel
selector valve is applied to the movable member to move from the
second position to the first position, changes, thereby the movable
member moves between the first and second positions.
[0328] According to the channel selector valve of the present
invention as described in claim 39, in the channel selector valve
of the present invention as described in claim 7, a heat-exchange
capacity by the heat exchanger in the refrigerating cycle is
adjusted and a difference in fluid pressure is changed by a
difference in amount of heat exchange by the heat exchanger, then a
pressure of the fluid in the refrigerating cycle changes, thereby a
balance, between a force that the fluid in the channel selector
valve is applied to the movable member to move from the first
position to the second position and a force that the fluid in the
channel selector valve is applied to the movable member to move
from the second position to the first position, changes, thereby
the movable member moves between the first and second
positions.
[0329] According to the channel selector valve of the present
invention as described in claim 40, in the channel selector valve
of the present invention as described in claim 13, a rotary-type
four-way selector valve is constructed by the channel selector
valve, in which when the main valve element as the movable member
rotates around the central axis in the housing so as to move
between the first and second positions, a place to which the inlet
port as the main port is communicated by communication means
provided in the main valve element is selected between a first
selector port and a second selector port out of two selector ports
provided at an end side of the housing.
[0330] According to the channel selector valve of the present
invention as described in claim 41, in the channel selector valve
of the present invention as described in claim 40, one port formed
on the valve seat out of the inlet port and the outlet port
communicates with a first selector port of the valve seat when the
main valve elemnet is situated at the first position, while
communicates with a second selector port of the valve seat when the
main valve elemnet is situated at the second position, not by
communication means but by second communication means formed at one
end surface of the main valve element that sits down on the valve
seat.
[0331] According to the channel selector valve of the present
invention as described in claim 42, in the channel selector valve
of the present invention as described in claim 41, by a
communication channel for communicating one end surface side of the
main valve element to another end surface side thereof, when the
main valve element is situated at the first position, the second
selector port formed on the valve seat at one end side of the
housing communicates with another port formed at another end side
of the housing, while when the main valve element is situated at
the second position, the second selector port formed on the valve
seat at one end side of the housing communicates with the first
selector port formed on the valve seat.
[0332] According to the channel selector valve of the present
invention as described in claim 43, in the channel selector valve
of the present invention as described in claim 40, when the main
valve element is moved in a direction of the central axis of the
housing by the driving means, this movement is transformed into a
rotation around the central axis of the housing by the conversion
means of moving direction, thereby the main valve element is
rotated between the first and second positions.
[0333] According to the channel selector valve of the present
invention as described in claim 44, in the channel selector valve
of the present invention as described in claim 43, while the main
valve element moves in a direction of the central axis of the
housing, in the inside of the cam groove provided in one out of the
main valve element and the housing, a cam follower pin provided in
another out of the main valve element and the housing moves,
thereby a movement of the main valve element in a direction of the
central axis of the housing is transformed into a rotation around
the central axis of the housing.
[0334] Then, the cam groove has a first and second cam grooves
continuing with each other in the rotational direction of the main
valve element, since the first cam groove is formed inclined so as
to part from the valve seat in a direction of the central axis as
being displaced in the rotarional direction, while the second cam
groove is formed inclined so as to move nearer to the valve seat in
a direction of the central axis as being displaced in the
rotarional direction, when the main valve element proceeds and
returns in a direction of the central axis of the housing, the main
valve element rotates between the first and second positions, with
the cam follower pin being guided along the first and second cam
grooves.
[0335] According to the channel selector valve of the present
invention as described in claim 45, in the channel selector valve
of the present invention as described in claim 44, the cam follower
pin formed on the main valve element is disposed between a first
and second half of an inner housing, then each end of the first and
second half is joined together, thereby the main valve element is
received in the inner housing and by the inner housing the main
valve element is movable in a direction of the central axis of the
housing and is supported rotatably around the central axis.
[0336] According to the channel selector valve of the present
invention as described in claim 46, in the channel selector valve
of the present invention as described in claim 44 or 45, when the
main valve element, which is moved in a direction of the central
axis by the driving means, rotates around the central axis of the
housing with its movement being transformed by the conversion means
of moving direction, one end surface of the main valve element sits
down on the valve seat only when situating at the first or the
second position, thereby one port of the valve seat selectively
communicates with one out of the first selector port and the second
selector port of the valve seat, by second communication means
formed at one end surface of the main valve element.
[0337] According to the channel selector valve of the present
invention as described in claim 47, in the channel selector valve
of the present invention as described in claim 46, when the main
valve element is situated at the first or second position where one
end surface of the main valve element sits down on the valve seat,
the communication channel is opened by a subvalve opened by the
valve-opening means, then one end surface side of the main valve
element communicates with another end surface side thereof, and by
this communication channel another port, which is formed at another
end side of the housing and forms a main port, communicates with
the second selector port formed on the valve seat when the main
valve element is situated at the first position, while communicates
with the first selector port formed on the valve seat when the main
valve element is situated at the second position.
[0338] According to the channel selector valve of the present
invention as described in claim 48, in the channel selector valve
of the present invention as described in claim 47, when the main
valve element sat down on the valve seat is moved in the direction
away from the valve seat by the driving means, an own weight of the
main valve is utilized as at least a part of non-electric motive
power.
[0339] According to the channel selector valve of the present
invention as described in claim 49, in the channel selector valve
of the present invention as described in claim 47 or 48, when the
main valve element sat down on the valve seat is moved in the
direction away from the valve seat by the driving means, an
energizing force stored in the energizing means for energizing the
main valve element is utilized as at least a part of non-electric
motive power.
[0340] According to the channel selector valve of the present
invention as described in claim 50, in the channel selector valve
of the present invention as described in claim 47 or 48, when the
main valve element away from the valve seat is moved in the
direction nearer to the valve seat by the driving means, an
energizing force stored in the second energizing means for
energizing the main valve element is utilized as at least a part of
non-electric motive power.
[0341] According to the channel selector valve of the present
invention as described in claim 51, in the channel selector valve
of the present invention as described in claim 50, when a pressure
of the fluid at one port exceeds that at another port, the main
valve element, situated at an intermediate position by a resultant
force of an energizing force of the energizing means for energizing
the main valve element and that of the second energizing means for
energizing the main valve element, moves in the direction away from
the valve seat with rotating against the energizing force of the
second energizing means for energizing the main valve element.
[0342] To the contrary, when a pressure of the fluid at one port is
lower than that at another port, the main valve element situated at
a neutral position, one end surface of which is away from the valve
seat, moves in the direction nearer to the valve seat with rotating
against the energizing force of the energizing means for energizing
the main valve element.
[0343] According to the channel selector valve of the present
invention as described in claim 52, in the channel selector valve
of the present invention as described in claim 51, whether the cam
follower pin, situated at an intermediate position of the cam
groove, is in the first cam groobe or in the second cam groove,
when a pressure of the fluid at one port is lower than that at
another port, the main valve element situated at the neutral
position moves in the direction nearer to the valve seat, then the
cam follower pin moves to the groove by way of either one end of
the first cam groove or that of the second cam groove, thereby the
main valve element rotates to be situated at either the first or
second position.
[0344] Then, in a state that the cam follower pin is situated in
the groove, when a state that a pressure of the fluid at the one
port is lower than that at the another port is canceled, the cam
follower pin situated in the groove moves to another end side of
the cam groove by way of one end of the cam groove out of the first
and second cam grooves, which is situated at a down stream side in
the direction of the rotation, thereby the main valve element
rotates around the cental axis from the first or second position
and the main valve element moves away from the valve seat to be
situated at the neutral position.
[0345] According to the channel selector valve of the present
invention as described in claim 53, in the channel selector valve
of the present invention as described in claim 51 or 52, whether
the cam follower pin, situated at an intermediate position of the
cam groove, is in the first cam groobe or in the second cam groove,
when a pressure of the fluid at one port is higher than that at
another port, the main valve element situated at the neutral
position moves in the direction away from the valve seat, then the
cam follower pin moves to the second groove by way of either
another end of the first cam groove or that of the second cam
groove, thereby the main valve element rotates to be situated at an
intermediate position between the first and second positions around
the central axis.
[0346] Then, in a state that the cam follower pin is situated in
the second groove, when a state that a pressure of the fluid at the
one port is higher than that at the another port is canceled, the
cam follower pin situated in the second groove moves to another end
side of the cam groove by way of one end of the cam groove out of
the first and second cam grooves, which is situated at a down
stream side in the direction of the rotation, thereby the main
valve element rotates around the cental axis from the intermediate
position between the first and second positions and the main valve
element moves nearer to the valve seat to be situated at the
neutral position.
[0347] According to the channel selector valve of the present
invention as described in claim 54, in the channel selector valve
of the present invention as described in any one of claims 40-53,
when the main valve element moves in a direction of the central
axis or rotates around the central axis with respect to the
housing, a sliding resistance between the housing and the main
valve element is reduced by slide means.
[0348] According to a compressor with the channel selector valve of
the present invention as described in claim 55, a compressor
housing part, in which a high pressure chamber from which the fluid
compressed by a compressing section of the compessor is introduced
is formed, is integrally formed with a housing part, in which an
inlet port is provided, out of the housing of the channel selector
valve as described in any one of claims 10-14, 16, 18-27, 29-30,
32-35, and 37-54, thereby the compressor housing is integrated with
the housing of the channel selector valve.
[0349] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 56, the channel
selector valve is controlled by controlling the functional
components for controlling the operation of the refrigerating
cycle.
[0350] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 57, the functional
component is controlled to control an operation of the
refrigerating cycle, thereby generating a non-electrical motive
power, by which the channel selector valve is passively
controlled.
[0351] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 58, by using a
microcomputer, which controls an operation of the refrigerating
cycle, the functional component is controlled to control an
operation of the refrigerating cycle, thereby generating a
non-electrical motive power, by which the channel selector valve is
passively controlled.
[0352] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 59, the functional
component is controlled to control an operation of the
refrigerating cycle, thereby a physical quantity or a rate of
change in the physical quantity is generated as a non-electrical
motive power, by which the channel selector valve is passively
controlled.
[0353] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 60, by using a
microcomputer, which controls an operation of the refrigerating
cycle, the functional component is controlled to control an
operation of the refrigerating cycle, thereby a physical quantity
or a rate of change in the physical quantity is generated as a
non-electrical motive power, by which the channel selector valve is
passively controlled.
[0354] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 61, the device
acts similarly to the device described in claim 57, 58, 59 or 60,
in order to generate a non-electrical motive power for controlling
the channel selector valve, the functional component is controlled
on the basis of a physical quantity, which concerns with a control
of an operation of the refrigerating cycle, selected from the group
consisting of a pressure, temperature, rate of flow, voltage,
current, electrical frequency and mechanical oscillation
frequency.
[0355] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 62, the device
acts similarly to the device described in claim 57, 58, 59 or 60,
the physical quantity, which is the non-electrical motive power and
is generated by the refrigerating cycle, is a pressure,
differential pressure or rate of flow with respect to fluid
existing in the channel selector valve, and the rate of change in a
physical quantity, which is the non-electrical motive power and is
generated by the refrigerating cycle, is a rate of change in
pressure, rate of change in differential pressure or rate of change
in rate of flow with respect to the fluid.
[0356] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 63, an operational
condition of the refrigerating cycle is commanded from an operation
command section and a physical quantity generated by the
refrigerating cycle is detected in a physical quantity detector
section, then the control section receives input signals sent from
the operation command section and the physical quantity detector
section. Then, the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component, and
the device generates a non-electrical motive power by controlling
the refrigerating cycle and passively controls the channel selector
valve by said motive power.
[0357] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 64, the device
acts similarly to the device described in claim 63, the control
section controls at least one of a plurality of functional
components communicated to the refrigerating cycle so as to start
an operation of the refrigerating cycle, thereby controlling the
channel selector valve in a state corresponding to the start of an
operation, which is commanded by the operation command section.
[0358] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 65, the device
acts similarly to the device described in claim 64, the control
section starts to operate a compressor communicated to the
refrigerating cycle in a direction of inverse rotation when the
control section decides to select the channel selector valve on the
basis of a command of the operation command section, thereby a
channel is selected by the cahnnel selector valve.
[0359] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 66, the device
acts similarly to the device described in claim 63, the control
section controls at least one of a plurality of functional
components communicated to the refrigerating cycle so as to operate
the refrigerating cycle, thereby controlling the channel selector
valve in a state corresponding to the operation, which is commanded
by the operation command section.
[0360] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 67, the device
acts similarly to the device described in claim 63, the control
section controls at least one of a plurality of functional
components communicated to the refrigerating cycle so as to halt an
operation of the refrigerating cycle, thereby controlling the
channel selector valve in a state corresponding to the halt of the
operation, which is commanded by the operation command section.
[0361] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 68, the device
acts similarly to the device as described in any one of claims
63-67, the channel selector valve is constructed in a manner that a
movable member moves so as to select a channel, and the control
section comprises at least one unit selected from the group
consisting of: a memory unit for memorizing position data of the
movable member of the channel selector valve; a comparison unit and
a judge unit for comparing and judging, respectively, the position
data and operation command data; and a learning unit learning on
the basis of physical quantity data by a control of functional
components and control data of the channel selector valve.
[0362] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 69, the device
acts similarly to the device as described in claim 68, the control
section receives the input signals, performs a predetermined
processing and judges whether a channel is to be changed or not to
be changed by the channel selector valve, then confirms a position
on the basis of present position data, then sends the output
signals to the driving section so as to control the functional
components in the refrigerating cycle, then receives new input
signals after a predetermined period of time, confirms a position
of the movable member, and sets position data of said position as
new present position data when said position is changed to a new
position.
[0363] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 70, the device
acts similarly to the device as described in claim 69, the control
section confirms a position of the movable member by at least one
temperature detection means, at least one pressure detection means,
at least one magnetic detection means, at least one current
detection means or a combination thereof after a predetermined
period of time, and then installs position data corresponding to
said position into the memory unit of the control section.
[0364] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 71, a microcomputer
that controls the refrigerating cycle is used, thereby controlling
at least one of a plurality of functional components communicated
to the refrigerating cycle so as to control the refrigerating
cycle, and in order to control the driving section for driving the
functional component so that the position of the movable member is
to be moved or not to be moved, the microcomputer performs a
processing consisting of the steps of:
[0365] receiving input signals; confirming a position by taking out
present position data of a movable member installed in a memory
unit; carrying out an operation to decide whether the movable
member is to be moved of not to be moved, comparing, and judging;
selecting and deciding a driving section; outputting drive signals
to the driving section selected and decided; judging a position of
the movable member by input signals after a predetermined period of
time, with or without moving a position of the movable member by a
physical quantity generated by at least one functional component
that is selected and decided in said step of selecting and deciding
or a rate of the physical quantity; and installing position data of
a position of the movable member into the memory unit when said
position is changed to a new position.
[0366] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 72, an operational
condition of the refrigerating cycle is commanded from an operation
command section and a physical quantity generated by the
refrigerating cycle is detected in a physical quantity detector
section, then the control section receives input signals sent from
the operation command section and the physical quantity detector
section. Then, the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component for
controlling an operation of the refrigerating cycle, and when
judging to select a channel by using the channel selector valve on
the basis of a command of the operation command section, the
control section sends output signals to a driving section for
driving a power source of a compressor so as to start an operation
of the compressor of the refrigerating cycle and starts an
operation of the refrigerant cycle so as to generate a motive power
exceeding a first predetermined motive power, thereby the channel
selector valve is passively controlled.
[0367] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 73, an operational
condition of the refrigerating cycle is commanded from an operation
command section and a physical quantity generated by the
refrigerating cycle is detected in a physical quantity detector
section, then the control section receives input signals sent from
the operation command section and the physical quantity detector
section. Then, the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component for
controlling an operation of the refrigerating cycle, and when
judging to select a channel by using the channel selector valve on
the basis of a command of the operation command section, the
control section sends output signals to a driving section for
driving a power source of a compressor so as to start an operation
of the compressor in a direction of inverse rotation and starts an
operation of the refrigerant cycle so as to generate a motive power
exceeding a third predetermined motive power, thereby the channel
selector valve is passively controlled.
[0368] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 74, the device
acts similarly to the device as described in claim 72 or 73, the
channel selector valve selects a channel by moving the movable
member between the first and second positions in response to an
internal motive power, the control section memorizes position data
corresponding to the first or second position of the movable member
in a memory unit thereof, the control section starts an operation
of the refrigerating cycle when the position data indicates the
second or first position, halts the operation of the refrigerating
cycle with renewing position data in the memory unit to the first
or second position, respectively, after a first predetermined
period of time, and keeps the operation of the refrigerating cycle
standby during a third predetermined period of time.
[0369] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 75, the device
acts similarly to the device as described in claim 72, the control
section operates the compressor in a specific frequency immediately
after starting the operation of the compressor and starts an
operation of the refrigerating cycle so that a motive power
exceeding a first predetermined motive power is generated as an
internal motive power of the channel selector valve.
[0370] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 76, the device
acts similarly to the device as described in claim 72, the control
section starts an operation of the compressor with a first
predetermined capacity.
[0371] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 77, the device
acts similarly to the device as described in claim 72, the control
section starts an operation of the compressor with a second
predetermined capacity so that a motive power lower than a first
predetermined motive power is generated as an internal motive power
of the channel selector valve, then operates the refrigerating
cycle for a fourth predetermined period of time, then halts the
operation of the refrigerating cycle for a fifth predetermined
period of time, and then starts an operation of the compressor with
a first predetermined capacity so that a motive power exceeding a
first predetermined motive power is generated as an internal motive
power of the channel selector valve.
[0372] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 78, the device
acts similarly to the device as described in claim 72, the control
section sends output signals to a throttle device driving section
so that an opening ratio of a throttle device of the refrigerating
cycle is almost fully opened or almost fully closed.
[0373] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 79, the device
acts similarly to the device as described in claim 72, the control
section sends output signals to a heat exchanger motor driving
section so that a heat exchanger motor of the refrigerating cycle
is kept halted.
[0374] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 80, the device
acts similarly to the device as described in claim 72, 75, 76 or
77, once the control section starts an operation of the compressor,
the control section sends output signals to the compressor driving
section after a first predetermined period of time and drives the
power source of the compressor so that a motive power exceeding a
second predetermined motive power is generated, thereby operating
the refrigerating cycle.
[0375] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 81, the device
acts similarly to the device as described in claim 78, once the
control section starts an operation of the compressor, the control
section sends output signals to the throttle device driving section
so as to set the opening ratio of the throttle device a
predetermined opening ratio after a first predetermined period of
time.
[0376] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 82, the device
acts similarly to the device as described in claim 79, once the
control section starts an operation of the compressor, the control
section sends output signals to the heat exchanger motor driving
section after a second predetermined period of time so as to start
an operation of the heat exchanger motor, sends output signals to
the compressor driving section so as to generate a motive power
lower than a first predetermined motive power, and drives the power
source of the compressor so as to generate a motive power exceeding
a second predetermined motive power, thereby operating the
refrigerating cycle.
[0377] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 83, the device
acts similarly to the device as described in claim 80, 81 or 82,
when the control section performs a predetermined processing and
judges to select a channel by the channel selector valve or to halt
an operation of the refrigerating cycle, the control section sends
output signals to the compressor driving section: to drive the
power source of the compressor with a third predetermined capacity
so as to generate a motive power lower than a second predetermined
motive power; or to halt the operation of the compressor, thereby
halting the operation of the refrigerating cycle.
[0378] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 84, the device
acts similarly to the device as described in claim 72, when the
control section performs a predetermined processing and judges to
select a channel by the channel selector valve or to halt an
operation of the refrigerating cycle, the control section sends
output signals to the compressor driving section to halt the
operation of the compressor, then keeps the refrigerating cycle
standby for a third predetermined period of time, then sends output
signals to the compressor driving section to start the operation of
the compressor, then renews position data in a memory unit to a
first or second position after a first predetermined period of
time, thereby halting the operation of the compressor again.
[0379] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 85, the device
acts similarly to the device as described in claim 72, 74 or 84,
when positional data memorized by a memory unit of the control
section indicate a first or second position, the control section
starts an operation of the refrigerating cycle so that a motive
power exceeding a first predetermined motive power is generated as
an internal motive power of the channel selector valve.
[0380] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 86, an operational
condition of the refrigerating cycle is commanded from an operation
command section and a physical quantity generated by the
refrigerating cycle is detected in a physical quantity detector
section, then the control section receives input signals sent from
the operation command section and the physical quantity detector
section. Then, the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component for
controlling an operation of the refrigerating cycle, and when
judging not to select (i.e. not to switch) a channel by using the
channel selector valve on the basis of a command of the operation
command section, the control section sends output signals to a
driving section for driving a power source of a compressor so as to
start an operation of the compressor of the refrigerating cycle and
starts an operation of the refrigerant cycle so as to generate a
motive power lower than a first predetermined motive power, thereby
the channel selector valve is passively controlled.
[0381] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 87, the device
acts similarly to the device as described in claim 86, the control
section starts an operation of the compressor with a second
predetermined capacity.
[0382] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 88, an operational
condition of the refrigerating cycle is commanded from an operation
command section and a physical quantity generated by the
refrigerating cycle is detected in a physical quantity detector
section, then the control section receives input signals sent from
the operation command section and the physical quantity detector
section. Then, the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component for
controlling an operation of the refrigerating cycle, and when
judging not to select (i.e. not to switch) a channel by using the
channel selector valve on the basis of a command of the operation
command section, the control section sends output signals to a
driving section for driving a power source of a compressor so as to
start an operation of the compressor of the refrigerating cycle and
starts an operation of the refrigerant cycle so as to generate a
motive power exceeding a first predetermined motive power, thereby
the channel selector valve is passively controlled.
[0383] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 89, the device
acts similarly to the device as described in claim 88, when the
control section performs a predetermined processing and judges to
halt an operation of the refrigerating cycle, the control section
sends output signals to the compressor driving section so as to
halt the operation of the compressor, then keeps the refrigerating
cycle standby for a third predetermined period of time without
renewing position data in a memory unit.
BRIEF DESCRIPTION OF THE DRAWINGS
[0384] FIG. 1 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a first embodiment of the present invention.
[0385] FIG. 2 is a view illustrating a schematic constitution of a
refrigerating cycle, in which a sectional view of the channel
selector valve of FIG. 1 in a cooling mode is shown.
[0386] FIG. 3 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a second embodiment of the present invention.
[0387] FIG. 4 is a front view illustrating a modified example of a
channel selector valve according to the first or second embodiment
of the present invention.
[0388] FIG. 5 is a side view of the channel selector valve of FIG.
4.
[0389] FIG. 6 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a third embodiment of the present invention.
[0390] FIG. 7 is a view illustrating a schematic constitution of a
refrigerating cycle, in which a sectional view of the channel
selector valve of FIG. 6 in a cooling mode is shown.
[0391] FIG. 8 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a fourth embodiment of the present invention.
[0392] FIG. 9 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a fifth embodiment of the present invention.
[0393] FIG. 10 is a view illustrating a schematic constitution of a
refrigerating cycle, in which a sectional view of the channel
selector valve of FIG. 9 in a cooling mode is shown.
[0394] FIG. 11 is an enlarged sectional view of a primary part of a
latch mechanism of FIG. 9.
[0395] FIG. 12 is an enlarged development of a primary part of an
inner cylinder of FIG. 11.
[0396] FIG. 13 is an enlarged sectional view of a primary part of a
latch mechanism of FIG. 9.
[0397] FIG. 14 is an enlarged sectional view of a primary part of a
latch mechanism of FIG. 9.
[0398] FIG. 15 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a sixth embodiment of the present invention.
[0399] FIG. 16 is a view illustrating a schematic constitution of a
latch mechanism usable instead of the latch mechanism of FIGS. 9 or
15.
[0400] FIG. 17 is a development of a cam groove, along which a cam
follower pin of FIG. 16 moves.
[0401] FIG. 18 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a seventh embodiment of the present invention.
[0402] FIG. 19 is an enlarged sectional view of a primary part of a
pilot valve mechanism of FIG. 18.
[0403] FIG. 20 is an enlarged sectional view of a primary part of a
pilot valve mechanism of FIG. 18.
[0404] FIG. 21 is an enlarged sectional view of a primary part of a
pilot valve mechanism of FIG. 18.
[0405] FIG. 22 is a view illustrating a schematic constitution of a
refrigerating cycle, in which a sectional view of the channel
selector valve of FIG. 18 in a cooling mode is shown.
[0406] FIG. 23 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a eighth embodiment of the present invention.
[0407] FIG. 24 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a ninth embodiment of the present invention.
[0408] FIG. 25 is a view illustrating a schematic constitution of a
refrigerating cycle, in which a sectional view of the channel
selector valve of FIG. 24 in a cooling mode is shown.
[0409] FIG. 26 is an enlarged sectional view of a primary part of a
state-holding selector valve of FIG. 24.
[0410] FIG. 27 is an enlarged sectional view of a primary part of a
state-holding selector valve of FIG. 24.
[0411] FIG. 28 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a tenth embodiment of the present invention.
[0412] FIG. 29 is an enlarged sectional view of a pilot oscillating
valve of FIG. 28.
[0413] FIG. 30 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a eleventh embodiment of the present invention.
[0414] FIG. 31 is an enlarged sectional view of a differential
pressure selector valve of FIG. 30.
[0415] FIG. 32 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a twelveth embodiment of the present invention.
[0416] FIG. 33 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a thirteenth embodiment of the present invention.
[0417] FIG. 34 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a fourteenth embodiment of the present invention.
[0418] FIG. 35 is a view illustrating a schematic constitution of a
refrigerating cycle employing a rotary channel selector valve, to
which a channel selector valve of the present invention can be
applied.
[0419] FIG. 36 is a sectional view of a channel selector valve
according to a fifteenth embodiment of the present invention, which
can be employed as the rotary channel selector valve of FIG.
35.
[0420] FIG. 37 is a side view of an upper inner housing of FIG.
36.
[0421] FIG. 38 is a side view of a lower inner housing of FIG.
36.
[0422] FIG. 39 is a side view of each upper and lower inner housing
of FIG. 36 in a state of each of them being inserted in the outer
housing of FIG. 36.
[0423] FIG. 40 is a plan view of a valve seat of FIG. 36.
[0424] FIG. 41 is a sectional view taken along A-A line of FIG.
36.
[0425] FIG. 42 is a sectional view of a channel selector valve of
FIG. 36 in a cooling mode.
[0426] FIG. 43 is a sectional view of a channel selector valve of
FIG. 36 in a heating mode.
[0427] FIG. 44 is a development of a cam groove of FIG. 39.
[0428] FIG. 45 is a view illustrating a relative positional
relationship between a main valve element and a valve seat with
respect to their direction of rotation.
[0429] FIG. 46 is a sectional view of a channel selector valve
according to a sixteenth embodiment of the present invention, which
can be employed as the rotary channel selector valve of FIG.
35.
[0430] FIG. 47 is a sectional view of a channel selector valve
according to a seventeenth embodiment of the present invention,
which can be employed as the rotary channel selector valve of FIG.
35.
[0431] FIG. 48 is a sectional view of a channel selector valve
according to a eighteenth embodiment of the present invention,
which can be employed as the rotary channel selector valve of FIG.
35.
[0432] FIG. 49 is a development of a cam groove of FIG. 48.
[0433] FIG. 50 is a sectional view of a channel selector valve of
FIG. 48 in a cooling mode.
[0434] FIG. 51 is a development of a cam groove of FIG. 48.
[0435] FIG. 52 is a sectional view of a channel selector valve of
FIG. 48 upon switching between a cooling and heating mode.
[0436] FIG. 53 is a sectional view of a channel selector valve of
FIG. 48 in a heating mode.
[0437] FIG. 54 is a sectional view of a channel selector valve
according to a nineteenth embodiment of the present invention,
which can be employed as the rotary channel selector valve of FIG.
35.
[0438] FIG. 55 is a side view of a rotating central shaft of FIG.
54.
[0439] FIG. 56 is a development of a cam groove of FIG. 55.
[0440] FIG. 57 is an enlarged sectional view of a primary part of a
main valve element of FIG. 54.
[0441] FIG. 58 is a sectional view of a channel selector valve
according to a twentieth embodiment of the present invention, which
can be employed as the rotary channel selector valve of FIG.
35.
[0442] FIG. 59 is a development of a cam groove of FIG. 58.
[0443] FIG. 60 is a view illustrating a schematic constitution of a
refrigerating cycle employing a compressor with a channel selector
valve according to a twenty first embodiment of the present
invention.
[0444] FIG. 61 is a view illustrating a schematic constitution of a
refrigerating cycle employing a compressor with a channel selector
valve according to a twenty second embodiment of the present
invention.
[0445] FIG. 62 is a block diagram according to an embodiment of a
device for controlling a refrigerating cycle of the present
invention.
[0446] FIG. 63 is a block diagram illustrating an example of a
refrigerating cycle according to an embodiment of the present
invention.
[0447] FIG. 64 is a block diagram principally illustrating an
electric system of an indoor and outdoor control according to an
embodiment of the present invention.
[0448] FIG. 65 is a block diagram illustrating a flow of signal and
action according to an embodiment of a device for controlling a
refrigerating cycle of the present invention.
[0449] FIG. 66 is a part of a flow chart of a main routine
according to an embodiment of the present invention.
[0450] FIG. 67 is another part of a flow chart of a main routine
according to an embodiment of the present invention.
[0451] FIG. 68 is a flow chart of a sub-routine for a channel
selector valve according to the first embodiment of the present
invention.
[0452] FIG. 69 is a flow chart of steps of transferring liquid
refrigerant according to an embodiment of the present
invention.
[0453] FIG. 70 is a flow chart of a sub-routine for a channel
selector valve according to the second embodiment of the present
invention.
[0454] FIG. 71 is a flow chart of a sub-routine for a channel
selector valve according to the third embodiment of the present
invention.
[0455] FIG. 72 is a flow chart of a sub-routine when a position of
a capillary tube according to the third embodiment of the present
invention is exchanged with that of an electrically-driven
expansion valve.
[0456] FIG. 73 is a flow chart of a sub-routine for a channel
selector valve according to the fourth embodiment of the present
invention.
[0457] FIG. 74 is a flow chart of a sub-routine for a channel
selector valve according to the fifth embodiment of the present
invention.
[0458] FIG. 75 is a flow chart of a sub-routine for a channel
selector valve according to the seventh embodiment of the present
invention.
BEST MODE FOR CARRING OUT THE INVENTION
[0459] In the following, the channel selector valve and the method
of driving the same according to the present invention will be
explained with reference to the attached drawings.
[0460] FIG. 1 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
a first embodiment of the present invention. The channel selector
valve according to the first embodiment constitutes a refrigerating
cycle A together with a compressor 4, an indoor heat exchanger 9A,
an outdoor heat exchanger 9B and a throttle 10 of an
electrically-driven expansion valve or a capillary tube, wherein
the throttle 10 is provided between the indoor heat exchanger 9A
and the outdoor heat exchanger 9B.
[0461] The channel selector valve according to the first
embodiment, an operating state of which in the heating mode is
shown in FIG. 1 with a sectional view thereof, has a cylindrical
reversing valve housing 1, to both ends of which stoppers 2 and 3
are firmly fixed.
[0462] An outlet pipe 5 communicating with an outlet (not shown in
the figure) of the compressor 4 is connected to one side of the
periphery of the reversing valve housing 1, while an inlet pipe 6
communicating with an inlet (not shown in the figure) of the
compressor 4 and two pipes 7 and 8 disposed at both sides of the
inlet pipe 6 in an axial direction of the reversing valve housing 1
are connected to an opposite side of the periphery of the reversing
valve housing 1, wherein the pipes 7 and 8 constitute the
refrigerating cycle A together with the channel selector valve and
the compressor 4 and are connected to two heat exchangers 9A and 9B
disposed indoors and outdoors, respectively, which are utilized
reversibly as a condenser or an evaporator.
[0463] Inner ends of the inlet pipe 6 and the pipes 7 and 8 are
connected to three through holes 11a, 11b and 11c on a selector
valve seat 11 firmly fixed in the reversing valve housing 1,
respectively, and a continuous smooth surface 11d is formed on the
inner side of the valve seat 11.
[0464] In the reversing valve housing 1, there is provided a piston
cylinder 12 (corresponding to the movable member) between the valve
seat 11 and the stopper 3, which partitions the reversing valve
housing 1 into a high pressure chamber R.sub.1 (corresponding to
the first pressure chamber) and a pressure-transducing chamber
R.sub.2 (corresponding to the second pressure chamber). There is
provided a compression spring 13 (corresponding to energizing
means) between the piston cylinder 12 and the stopper 3, thereby
the piston cylinder 12 is always energized toward the high pressure
chamber R.sub.1.
[0465] On the valve seat 11, there is provided a slide valve 27
having a communication cavity 27a, which is joined to the piston
cylinder 12 in use of a connecting shaft 28 and slides on the
smooth surface lid in response to the movement of the piston 12 in
the reversing valve housing 1, thereby the through hole 11a
corresponding to the inlet pipe 6 alternatively communicates with
the through hole 11b or 11c, each of which puts the through hole
11a therebetween and corresponds to the respective pipe 7 or 8 for
the respective heat exchanger.
[0466] FIG. 2 is a view illustrating a schematic constitution of a
refrigerating cycle, in which a sectional view of the channel
selector valve in a cooling mode is shown.
[0467] That is, the piston cylinder 12 can move between a first
position and a second position: at said first position, the piston
cylinder 12 is prevented from moving further toward the stopper 2
because an end of the connecting shaft 28 abuts on the stopper 2 as
shown in FIG. 1; and at said second position, the piston cylinder
12 is prevented from moving further toward the stopper 3 because
the piston cylinder 12 abuts on the stopper 3 as shown in FIG.
2.
[0468] As shown in FIG. 1, when the piston cylinder 12 is at the
first position, the slide valve 27 communicates the through hole
11a corresponding to the inlet pipe 6 to the through hole 11c
corresponding to the pipe 8 through a low-pressure side closed
space (hereinafter, a closed space) S1 (corresponding to the second
space), which is formed in the high pressure chamber R.sub.1 by the
cavity 27a and the smooth surface 11d of the valve seat 11, while
the through hole 11b corresponding to the pipe 7 communicates with
the outlet pipe 5 through a high pressure side closed space
(hereinafter, a high pressure space) S2 (corresponding to the first
space), which is formed in the high pressure chamber R.sub.1 by the
slide valve 27 and isolated from the closed space S1.
[0469] Then, as shown in FIG. 2, when the piston cylinder 12 is at
the second position, the slide valve 27 communicates the through
hole 11a corresponding to the inlet pipe 6 to the through hole 11b
corresponding to the pipe 7 through the closed space S1, while the
through hole 11c corresponding to the pipe 8 communicates with the
outlet pipe 5 through the high pressure space S2.
[0470] Further, an end of a channel 14 (corresponding to the
communication pipe) is connected to the stopper 3, while the
opposite end of the channel 14 is connected to the pipe 7 by way of
the outside of the reversing valve housing 1, whereby the
pressure-transducing chamber R.sub.2 always communicates with the
pipe 7 through the channel 14.
[0471] As to the first embodiment, the reversing valve housing 1
and the stoppers 2 and 3 constitute the housing described in the
claims of this specification, a portion of the reversing valve
housing 1, to which the outlet pipe 5 connected to the outlet of
the compressor 4 is connected, corresponds to the inlet port
described in the claims of this specification, while the through
hole 11a on the valve seat 11, to which the inlet pipe 6 connected
to the inlet of the compressor 4 is connected, corresponds to the
outlet port described in the claims of this specification.
[0472] Further, as to the channel selector valve according to the
first embodiment, the through holes 11b and 11c of the valve seat
11, to which the pipe 7 connected to the indoor heat exchanger 9A
and the pipe 8 connected to the outdoor heat exchanger 9B are
connected respectively, correspond to the two selector ports
described in the claims of this specification.
[0473] In the following, an operation of the channel selector valve
according to the first embodiment constructed as described above
will be explained.
[0474] When the operation of the compressor 4 is halted, as shown
in FIG. 1, the piston cylinder 12 energized by the compression
spring 13 is at the first position, the inlet pipe 6 communicates
with the pipe 8 through the closed space S1, while the outlet pipe
5 communicates with the pipe 7 through the high pressure space
S2.
[0475] When the compressor 4 starts to operate, a refrigerant
discharged from the compressor 4 flows into the high pressure space
S2 through the outlet pipe 5. At that time, if a force F1
(hereinafter, forward drive force) applied to the piston cylinder
12 from the high pressure chamber R.sub.1 due to the pressure of
the refrigerant is equal to or less than the resultant force
F2+Fs+Ff, the piston cylinder 12 does not move from the first
position, wherein F2 (hereinafter, backward drive force) is the
force applied to the piston cylinder 12 from the
pressure-transducing chamber R.sub.2 due to the pressure of the
refrigerant in the pressure-transducing chamber R.sub.2, Fs is the
energizing force by the compression spring 13, and Ff is the static
friction force between the smooth surface 11d of the valve seat 11
and the slide valve 27.
[0476] On the other hand, if the forward drive force F1 is greater
than the resultant force F2+Fs+Ff, the piston cylinder 12 moves
from the first position to the second position as shown in FIGS. 1
and 2, respectively.
[0477] If the piston cylinder 12 does not move from the first
position, as shown in FIG. 1, the inlet pipe 6 keeps communicating
with the pipe 8 through the closed space S1, while the outlet pipe
5 keeps communicating with the pipe 7 through the high pressure
space S2.
[0478] Then, since the pipe 7 communicating with the high pressure
space S2 always communicates with the pressure-transducing chamber
R.sub.2 through the channel 14, the pressure of the refrigerant in
the high pressure chamber R.sub.1 becomes equal to that of the
refrigerant in pressure-transducing chamber R.sub.2.
[0479] Consequently, as long as the pressure of the refrigerant
discharged from the compressor 4 is restrained so that the forward
drive force F1 is equal to or less than the resultant force
F2+Fs+Ff, the piston cylinder 12 keeps staying at the first
position, thereby the inlet pipe 6 keeps communicating with the
pipe 8 through the closed space S1, while the outlet pipe 5 keeps
communicating with the pipe 7 through the high pressure space
S2.
[0480] To the contrary, when the piston cylinder 12 moves from the
first position to the second position, as shown in FIG. 2, the
outlet pipe 5 communicates with the pipe 8 through the high
pressure space S2, while the inlet pipe 6 communicates with the
pipe 7 through the closed space S1.
[0481] Then, the pressure of the refrigerant in the high pressure
chamber R.sub.1, which becomes equal to that of the refrigerant at
the outlet of the compressor 4 since the pressure-transducing
chamber R.sub.2 always communicates with the inlet pipe 6 through
the pipe 7 and the channel 14, becomes greater than the pressure of
the refrigerant in the pressure-transducing chamber R.sub.2, which
becomes equal to that of the refrigerant at the inlet of the
compressor 4 since the pressure-transducing chamber R.sub.2
communicates with the inlet of the compressor 4, by a difference
between an outlet pressure and an inlet pressure of the refrigerant
due to an operation of the compressor 4.
[0482] Consequently, as long as the pressure of the refrigerant
discharged from the compressor 4 is kept high so that the forward
drive force F1 is greater than a force F2+Fs-Ff, the piston
cylinder 12 keeps staying at the second position, thereby the
outlet pipe 5 keeps communicating with the pipe 8 through the high
pressure space S2, while the inlet pipe 6 keeps communicating with
the pipe 7 through the closed space S1.
[0483] Therefore, if the refrigerant, the pressure of which is such
that the forward drive force F1 is equal to or less than the
resultant force F2+Fs+Ff, flows into the high pressure space S2
through the outlet pipe 5 upon start of operation of the compressor
4, the piston cylinder 12 is situated at the first position as
shown in FIG. 1.
[0484] To the contrary, if the refrigerant, the pressure of which
is such that the forward drive force F1 is greater than the
resultant force F2+Fs+Ff, flows into the high pressure space S2
through the outlet pipe 5 upon start of operation of the compressor
4, the piston cylinder 12 is situated at the second position as
shown in FIG. 2.
[0485] Then afterward, the pressure of the refrigerant, which is
discharged from the compressor and flows into the high pressure
space S2 through the outlet pipe 5, is lowered by, for example,
stopping the operation of the compressor 4 so that the forward
drive force F1 is equal to or less than the force F2+Fs-Ff, the
piston cylinder 12 moves from the second position to the first
position.
[0486] Therefore, when the refrigerating cycle A is operated in the
heating mode, the number of revolution of the compressor 4 upon
start of its operation is restrained to keep the pressure of the
refrigerant discharged from the compressor 4 low so that the
forward drive force F1 is equal to or less than the resultant force
F2+Fs+Ff, thereby the piston cylinder 12 is kept staying at the
first position even after start of the operation of the compressor
4.
[0487] On the other hand, when the refrigerating cycle A is
operated in the cooling mode, the number of revolution of the
compressor 4 upon start of its operation is raised to increase the
pressure of the refrigerant discharged from the compressor 4 so
that the forward drive force F1 is greater than the resultant force
F2+Fs+Ff, thereby the piston cylinder 12 is moved from the first
position to the second position upon start of the operation of the
compressor 4.
[0488] Then, once the piston cylinder 12 is moved to the second
position, as long as the the forward drive force F1 is greater than
the force F2+Fs-Ff, the piston cylinder 12 is kept staying at the
second position even if the number of revolution of the compressor
4 is lowered, thereby the refrigerating cycle A is kept being
operated in the cooling mode.
[0489] Thus, according to the first embodiment, the piston cylinder
12 that partitions the interior of the reversing valve housing 1
into the high pressure chamber R.sub.1 and the pressure-transducing
chamber R.sub.2 is moved between the first and second positions,
and the slide valve 27 joined to the piston cylinder 12 is slided
on the smooth surface 11d of the valve seat 11, thereby the closed
space S1, formed by the cavity 27a of the slide valve 27 and the
smooth surface 11d, communicates the through hole 11a corresponding
to the inlet pipe 6 to either the through hole 11b corresponding to
the pipe 7 or the through hole 11c corresponding to the pipe 8. In
order to achieve the above operation, the following constitution is
employed as to the channel selector valve.
[0490] That is, the channel 14 always communicates the pipe 7 to
the pressure-transducing chamber R.sub.2 outside the reversing
valve housing 1, and when the piston cylinder 12 is situated at the
first position, the pressure of the refrigerant in the
pressure-transducing chamber R.sub.2 is set equal to that of the
refrigerant in the high pressure space S2 of the high pressure
chamber R.sub.1 that communicates with the pressure-transducing
chamber R.sub.2 through the pipe 7 and the channel 14, thereby the
piston cylinder 12 is kept at the first position.
[0491] To the contrary, when the piston cylinder 12 is situated at
the second position, the pressure of the refrigerant in the
pressure-transducing chamber R.sub.2 is set equal to that of the
refrigerant at the inlet pipe 6 that communicates with the
pressure-transducing chamber R.sub.2 through the pipe 7 and the
channel 14, i.e. that of the refrigerant at the inlet of the
compressor 4 so that the pressure of the refrigerant in the
pressure-transducing chamber R.sub.2 is lower than that of the
refrigerant in the high pressure chamber R.sub.1, the piston
cylinder 12 is kept at the second position due to a differnce
between the pressure of the refrigerant in the high pressure
chamber R.sub.1 and that of the refrigerant in pressure-transducing
chamber R.sub.2.
[0492] Therefore, the heating mode, in which the refrigerant
discharged from the compressor 4 is supplied to the indoor heat
exchanger 9A by way of the pipe 7, and the cooling mode, in which
the refrigerant discharged from the compressor 4 is supplied to the
outdoor heat exchanger 9B by way of the pipe 8, can be selected by
changing the pressure of the discharged refrigerant upon start of
operation of the compressor 4 and the selected state can be
maintained without using any exclusive power source such as an
electromagnetic solenoid.
[0493] According to the first embodiment, the indoor heat exchanger
9A is connected to the pipe 7 while the outdoor heat exchanger 9B
is connected to the pipe 8, and when the piston cylinder 12 is
energized by the compression spring 13 to be situated at the first
position, the outlet pipe 5 communicates with the indoor heat
exchanger 9A through the high pressure space S2 and the pipe 7
while the inlet pipe 6 communicates with the outdoor heat exchanger
9B through the closed space S1 and the pipe 8, therefore, the
following advantage is obtained when the refrigerating cycle A is
used mainly in the heating mode.
[0494] That is, upon start of operation of the refrigerating cycle
A in the cooling mode, the pressure of the refrigerant discharged
from the compressor 4 upon start of operation of the compressor 4
is set high so that the forward drive force F1 becomes greater than
the resultant force F2+Fs+Ff, thereby the piston cylinder 12 is
moved from the first position to the second position.
[0495] However, when the refrigerating cycle A is started to
operate in the heating mode, which is more frequently employed than
the cooling mode, the piston cylinder 12 is situated at the first
position, then the operation of the refrigerating cycle A in the
heating mode is started, thereafter the piston cylinder 12 is still
kept being situated at the first position, thereby the
refrigerating cycle A can be maintained in operation in the heating
mode without raising the pressure of the discharged refrigerant
upon start of operation of the compressor 4 up to as high as the
pressure required upon start of operation of the refrigerating
cycle A in the cooling mode. Therefore, the advantage described
above can be obtained.
[0496] In contrast with the first embodiment, FIG. 3 is a view
illustrating a schematic constitution of a refrigerating cycle
employing a channel selector valve according to a second embodiment
of the present invention. As to the second embodiment, the outdoor
heat exchanger 9B is connected to the pipe 7 while the indoor heat
exchanger 9A is connected to the pipe 8, and when the piston
cylinder 12 is energized by the compression spring 13 to be
situated at the first position, the outlet pipe 5 communicates with
the outdoor heat exchanger 9B through the high pressure space S2
and the pipe 7 while the inlet pipe 6 communicates with the indoor
heat exchanger 9A through the closed space S1 and the pipe 8,
therefore, the following advantage is obtained when the
refrigerating cycle A is used mainly in the cooling mode.
[0497] That is, upon start of operation of the refrigerating cycle
A in the heating mode, the pressure of the refrigerant discharged
from the compressor 4 upon start of operation of the compressor 4
is set high so that the forward drive force F1 becomes greater than
the resultant force F2+Fs+Ff, thereby the piston cylinder 12 is
moved from the first position to the second position.
[0498] However, when the refrigerating cycle A is started to
operate in the cooling mode, which is more frequently employed than
the heating mode, the piston cylinder 12 is situated at the first
position, then the operation of the refrigerating cycle A in the
cooling mode is started, thereafter the piston cylinder 12 is still
kept being situated at the first position, thereby the
refrigerating cycle A can be maintained in operation in the cooling
mode without raising the pressure of the discharged refrigerant
upon start of operation of the compressor 4 up to as high as the
pressure required upon start of operation of the refrigerating
cycle A in the heating mode. Therefore, the advantage described
above can be obtained.
[0499] As to the above channel selector valve according to the
first and second embodiments, as shown in FIG. 4 (front view) and
FIG. 5 (side view), a delay chamber 14', the inner diameter of
which is larger than that of the channel 14, may be provided so
that a period of time, required for the refrigerant pressure in the
pressure-transducing chamber R.sub.2 to be equal to the pressure in
the high pressure space S2 with which the pressure-transducing
chamber R.sub.2 communicates through the pipe 7 and the channel 14,
is made longer by another period of time required for the delay
chamber 14' to be filled with the refrigerant when the pressure of
the refrigerant discharged from the compressor 4 is raised so that
the forward drive force F1 is higher than the resultant force
F2+Fs+Ff.
[0500] The delay chamber 14' described above gives an advantage
that the piston cylinder 12 can easily move from the first position
to the second position since a differential pressure between the
refrigerant in the high pressure chamber R.sub.1 and that in the
pressure-transducing chamber R.sub.2 is easily occurred because the
refrigerant pressure in the pressure-transducing chamber R.sub.2
does not increase in a short period time even if the refrigerant
pressure in the high pressure space S2 is raised.
[0501] The structure of the delay chamber 14' is not limited to
that shown in FIGS. 4 and 5, in which the delay chamber 14' is
attached to the reversing valve housing 1 by a belt 1'.
[0502] In the following, a channel selector valve according to a
third embodiment of the present invention will be explained with
reference to FIGS. 6 and 7.
[0503] FIG. 6 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
the third embodiment of the present invention, in which the same
abbreviation numerals with those used for the corresponding
identical members or parts of the channel selector valve according
to the first embodiment shown in FIG. 1 are used.
[0504] The channel selector valve according to the third
embodiment, a state in operation in the hearting mode of which is
shown in FIG. 6 by its sectional view, is different from the
channel selector valve according to the first embodiment in a point
that the channel 14 always communicating the pressure-transducing
chamber R.sub.2 to the pipe 7 by way of the outside of the
reversing valve housing 1 is omitted.
[0505] Furthermore, the channel selector valve according to the
third embodiment shown in FIG. 6 is different from the channel
selector valve according to the first embodiment shown in FIG. 1 in
a point that the piston cylinder 12 is provided with a through hole
12.sub.1 (corresponding to an equalizing path), the inner diameter
of which is designed in such a manner that a flow rate of the
refrigerant flowing through the through hole 12.sub.1 is much
smaller than that of the refrigerant flowing through the pipe 7 or
8, thereby the high pressure chamber R.sub.1 always communicates
with the pressure-transducing chamber R.sub.2 through the through
hole 12.sub.1 in the reversing valve housing 1.
[0506] The channel selector valve according to the third embodiment
is similar to that according to the first embodiment in points
that: the housing described in claims of the channel selector valve
comprises the reversing valve housing 1 and the stoppers 2 and 3; a
part of the reversing valve housing 1, to which the outlet pipe 5
communicating with the outlet of the compressor 4 is connected,
corresponds to the inlet port described in claims; the through hole
11a of the valve seat 11, to which the inlet pipe 6 communicating
with the inlet of the compressor 4 is connected, corresponds to the
outlet port described in claims; and through holes 11b and 11c of
the valve seat 11, to which the pipes 7 and 8 connecting with the
indoor and outdoor heat exchangers 9A and 9B, respectively, are
connected, correspond to the respective two selector ports
described in claims.
[0507] In the following, an operation of the channel selector valve
according to the third embodiment constructed as described above
will be explained.
[0508] As shown in FIG. 6, when the operation of the compressor 4
is halted, the piston cylinder 12 is at the first position due to
the energizing force Fs of the compression spring 13, thereby the
inlet pipe 6 communicates with the pipe 8 through the closed space
S1 and the outlet pipe 5 communicates with the pipe 7 through the
high pressure space S2.
[0509] When the compressor 4 starts to operate, if the forward
drive force F1 is equal to or less than the resultant force
F2+Fs+Ff, the piston cylinder 12 does not move and stays at the
first position, therefore the inlet pipe 6 keeps communicating with
the pipe 8 through the closed space S1 and the outlet pipe 5 keeps
communicating with the pipe 7 through the high pressure space
S2.
[0510] In this situation, the pressure of the refrigerant in the
high pressure chamber R.sub.1 increases due to the refrigerant
flowed into the high pressure space S2 from the compressor 4
through the outlet pipe 5 and exceeds the pressure of the
refrigerant in the pressure-transducing chamber R.sub.2, while the
refrigerant gradually flows into the pressure-transducing chamber
R.sub.2 from the high pressure space S2 through the through hole
12.sub.1 of the piston cylinder 12, as a result when the time
passes, the pressure of the refrigerant in the high pressure space
S2 becomes equal to that of the refrigerant in the
pressure-transducing chamber R.sub.2.
[0511] Therefore, as long as the pressure of the refrigerant
discharged from the compressor 4 is restrained so that the forward
drive force F1 is equal to or less than the resultant force
F2+Fs+Ff, the piston cyliner 12 keeps staying at the first
position, as a result, the outlet pipe 5 keeps communicating with
the pipe 7 through the high pressure space S2 and the inlet pipe 6
keeps communicating with the pipe 8 through the closed space
S1.
[0512] To the contrary, when the forward drive force F1 exceeds the
resultant force F2+Fs+Ff, the piston cylinder 12 moves from the
first position, as shown in FIG. 7 illustrating a schematic
constitution of a refrigerating cycle in which a sectional view of
the channel selector valve in a cooling mode is shown, the piston
cylinder 12 abuts on the stopper 3, thereby the piston cylinder 12
is situated at the second position by being restricted its further
movement toward the stopper 3, that is, the outlet pipe 5
communicates with the pipe 8 through the high pressure space S2 and
the inlet pipe 6 communicates with the pipe 7 through the closed
space S1.
[0513] Thereafter, if the compressor 4 is kept in operation with
keeping a difference between the high and low pressures so that the
static friction force Ff exceeds the energizing force Fs due to the
compression spring 13, the piston cylinder 12 keeps staying at the
second position.
[0514] Similarly to the function of the channel selector valve
according to the first embodiment, by employing the channel
selector valve according to the third embodiment, the heating mode,
in which the refrigerant discharged from the compressor 4 is
supplied to the indoor heat exchanger 9A by way of the pipe 7, and
the cooling mode, in which the refrigerant discharged from the
compressor 4 is supplied to the outdoor heat exchanger 9B by way of
the pipe 8, can be selected by changing the pressure of the
discharged refrigerant upon start of operation of the compressor 4
and the selected state can be maintained without using any
exclusive power source such as an electromagnetic solenoid.
[0515] According to the third embodiment, the indoor heat exchanger
9A is connected to the pipe 7 while the outdoor heat exchanger 9B
is connected to the pipe 8, and when the piston cylinder 12 is
energized by the compression spring 13 to be situated at the first
position, the outlet pipe 5 communicates with the indoor heat
exchanger 9A through the high pressure space S2 and the pipe 7
while the inlet pipe 6 communicates with the outdoor heat exchanger
9B through the closed space S1 and the pipe 8, therefore, the
advantage that is the same with that of the channel selector valve
according to the first embodiment is obtained when the
refrigerating cycle A is used mainly in the heating mode.
[0516] In contrast with the third embodiment, FIG. 8 is a view
illustrating a schematic constitution of a refrigerating cycle
employing a channel selector valve according to a fourth embodiment
of the present invention. As to the fourth embodiment, the outdoor
heat exchanger 9B is connected to the pipe 7 while the indoor heat
exchanger 9A is connected to the pipe 8, and when the piston
cylinder 12 is energized by the compression spring 13 to be
situated at the first position, the outlet pipe 5 communicates with
the outdoor heat exchanger 9B through the high pressure space S2
and the pipe 7 while the inlet pipe 6 communicates with the indoor
heat exchanger 9A through the closed space S1 and the pipe 8,
therefore, the advantage that is the same with that of the channel
selector valve according to the second embodiment is obtained when
the refrigerating cycle A is used mainly in the cooling mode.
[0517] As to each channel selector valve according to the first to
fourth embodiments, when the compressor 4 is in operation, a
pressure of the refrigerant discharged from the compressor 4
flowing into the high pressure space S2 through the outlet pipe 5
is higher than another pressure of the refrigerant in the closed
space S1 communicating with the inlet of the compressor 4 through
the inlet pipe 6 whether the piston cylinder 12 is at the first
position or the second position, therefore, the slide valve 27 is
pressed onto the valve seat 11 by a force corresponding to a
difference between these two pressures of the refrigerant.
[0518] Consequently, when the compressor 4 is in operation, a
static friction force between the slide valve 27 and the smooth
surface 11d of the valve seat 11 increases by a quantity
corresponding to the differnce in pressure between the refrigerant
in the high pressure space S2 and that in the closed space S1,
which is a basis for a force to press the slide valve 27 onto the
valve seat 11.
[0519] Therefore, when the piston cylinder 12 is moved between the
first and second positions in order to switch the operation mode of
the refrigerating cycle A between the heating mode and the cooling
mode, preferably, the static friction force between the slide valve
27 and the smooth surface 11d of the valve seat 11 is reduced or
removed by reducing or removing the differnce in pressure between
the refrigerant in the high pressure space S2 and that in the
closed space S1 through, for example, a tentative stop of the
operation of the compressor 4.
[0520] In the above third or fourth embodiment, the equalizing path
is constituted by the through hole 12.sub.1 of the piston cylinder
12. However, the equalizing path provided for the movable member is
not limited to the through hole described above and may be a path
formed between the other member or may be constituted in
combination with a path and a through hole.
[0521] In the following, a channel selector valve according to a
fifth embodiment of the present invention will be explained with
reference to FIGS. 9 to 14.
[0522] FIG. 9 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
the fifth embodiment of the present invention, in which the same
abbreviation numerals with those used for the corresponding
identical members or parts of the channel selector valve according
to the first embodiment shown in FIG. 1 are used.
[0523] The channel selector valve according to the fifth
embodiment, a state in operation in the hearting mode of which is
shown in FIG. 9 by its sectional view, constitutes the
refrigerating cycle A together with the compressor 4, the indoor
heat exchanger 9A, the outdoor heat exchanger 9B and the capillary
tube 10B that is provided between the indoor heat exchanger 9A and
the outdoor heat exchanger 9B.
[0524] The channel selector valve according to the fifth embodiment
is different from the channel selector valve according to the first
embodiment shown in FIG. 1 in a point that the reversing valve
housing 1 is provided with a latch mechanism 32 (corresponding to
the latch mechanism described in claims 25 to 28) at one end
thereof, which includes a seal housing 32a that seals one end of
the reversing valve housing 1 instead of the stopper 3.
[0525] As to the channel selector valve according to the fifth
embodiment, the piston cylinder 12 can move between a first
position and a second position: at said first position, the piston
cylinder 12 is prevented from moving further toward the stopper 2
because an end of the connecting shaft 28 abuts on the stopper 2 as
shown in FIG. 9; and at said second position, the piston cylinder
12 is prevented from moving further toward the seal housing 32a
because the piston cylinder 12 abuts on the seal housing 32a as
shown in FIG. 10. FIG. 10 is a view illustrating a schematic
constitution of a refrigerating cycle, in which a sectional view of
the channel selector valve of FIG. 9 in a cooling mode is
shown.
[0526] The latch mechanism 32 comprises the seal housing 32a, a
guide cylinder 32c received in the seal housing 32a, a part of
which protrudes toward the inside of the pressure-transducing
chamber R.sub.2 of the reversing valve housing 1, a latch piece
32k, and a coil spring 32p.
[0527] The seal housing 32a has a hollow cylindrical shape with one
end open and the opposite end closed, as shown in FIG. 11 (an
enlarged sectional view of a primary part of a latch mechanism of
FIG. 9), at a periphery near the closed end of the seal housing
32a, there is provided a port 32b for commucicating the interior of
the seal housing 32a with the exterior thereof, to which a channel
14B connected to the inlet pipe 6 is connected.
[0528] The guide cylinder 32c consists of two layers, i.e. an outer
cylinder 32d and an inner cylinder 32e in which a cam groove 32f
for the latch action is formed.
[0529] FIG. 12 is an enlarged development of a primary part of an
inner cylinder 32e. As shown in FIG. 12, the cam groove 32f is
formed in a shape of a deformed saw blade, in which shallow grooves
32g and deep grooves 32h are arranged in a circumferential
direction of the inner cylinder 32e at intervals of 90.degree. and
a connection groove 32j connects the shallow groove 32g with the
adjoining deep groove 32h.
[0530] The latch piece 32k has a flat cylindrical shape and its
diameter is formed so that the latch piece 32k is movable in an
axial direction within the inner cylinder 32e of the guide cylinder
32c. At each circumferential position located in a circumferential
direction of the latch piece 32k at intervals of 90.degree., a
respective cam follower pin 32m that can be inserted into the cam
groove 32f of the inner cylinder 32e is formed. Inside the latch
piece 32k, a through hole 32n is formed throughout both ends
thereof.
[0531] The coil spring 32p is provided between the latch piece 32k
and the closed opposite end of the seal housing 32a, by an elastic
force of which the latch piece 32k is energized toward the open end
of the seal housing 32a.
[0532] As to the latch mechanism 32, the cam follower pin 32m of
the latch piece 32k energized by the elastic force of the coil
spring 32p is guided by a first inclined plane 32j.sub.1 of the
connection groove 32j of the cam groove 32f so as to abut on a
stopper plane 32j.sub.2 so that the latch piece 32k is situated at
a deregulation position of the inner cylinder 32e, that is, in the
vicinity of the end of the inner cylinder 32e at the high pressure
chamber R.sub.1 side.
[0533] When the cam follower pin 32m of the latch piece 32k
situated at the deregulation position abuts on the stopper plane
32j.sub.2 by way of the first inclined plane 32j.sub.1 of the
connection groove 32j facing the deep groove 32h, that is, when the
cam follower pin 32m is situated at a position "a" in a locus of
the cam follower pin 32m shown with an imaginary lines (i.e.
alternate long and short dash lines or alternate long and two short
dashes lines) in FIG. 12, the latch piece 32k is moved toward the
closed end of the seal housing 32a against the elastic force by the
coil spring 32p, thereby the latch mechanism 32 performs the
following action.
[0534] That is, the cam follower pin 32m is guided by the stopper
plane 32j.sub.2 so as to move from the position "a" to a position
"b", then guided by a second inclined plane 32j.sub.3 of the
connection groove 32j facing the stopper plane 32j.sub.2 so as to
move from the position "b" to a position "c", thereby the cam
follower pin 32m abuts on a stopper plane 32g.sub.1 of the shallow
groove 32g.
[0535] Then, in this state, as long as a force to move the latch
piece 32k toward the closed end of the seal housing 32a affects the
latch piece 32k, as shown in FIG. 12, the movement of the latch
piece 32k is restrained at a first regulation position where is a
first stroke L1 off from the deregulation position, shown with an
imaginary line (i.e. alternate long and two short dashes line) in
FIG. 13, toward the closed end of the seal housing 32a.
[0536] When the cam follower pin 32m of the latch piece 32k
situated at the deregulation position abuts on the stopper plane
32j.sub.2 by way of the first inclined plane 32j.sub.1 of the
connection groove 32j facing the shallow groove 32g, that is, when
the cam follower pin 32m is situated at a position "e" in a locus
of the cam follower pin 32m shown with an imaginary lines (i.e.
alternate long and short dash lines or alternate long and two short
dashes lines) in FIG. 12, the latch piece 32k is moved toward the
closed end of the seal housing 32a against the elastic force by the
coil spring 32p, thereby the latch mechanism 32 performs the
following action.
[0537] That is, the cam follower pin 32m is guided by the stopper
plane 32j.sub.2 so as to move from the position "e" to a position
"f", then guided by the second inclined plane 32j.sub.3 of the
connection groove 32j facing the stopper plane 32j.sub.2 so as to
move from the position "f" to a position "g", thereby the cam
follower pin 32m reaches an end of the deep groove 32h.
[0538] Then, as long as a force to move the latch piece 32k toward
the closed end of the seal housing 32a affects the latch piece 32k,
as shown in FIG. 14, the movement of the latch piece 32k is
restrained at a second regulation position where is a second stroke
L2 off from the deregulation position, shown with an imaginary line
(i.e. alternate long and two short dashes line) in FIG. 14, toward
the closed end of the seal housing 32a.
[0539] Here, the second stroke L2 is set a little longer than a
distance between the first position and the second position of the
piston cylinder 12, while the first stroke L1 is set much shorter
than said distance.
[0540] In the state that the movement of the latch piece 32k is
restrained at the first regulation position, when a force to move
the latch piece 32k toward the closed end of the seal housing 32a
does not affect, the cam follower pin 32m of the latch piece 32k
energized by the elastic force of the coil spring 32p is guided by
the first inclined plane 32j.sub.1 of the connection groove 32j of
the cam groove 32f so as to move from a position "d" to a position
"e" in FIG. 12 and abuts on the stopper plane 32j.sub.2, thereby
the latch piece 32k comes back to the deregulation position shown
in FIG. 11.
[0541] Similarly, in the state that the movement of the latch piece
32k is restrained at the second regulation position, when a force
to move the latch piece 32k toward the closed end of the seal
housing 32a does not affect, the cam follower pin 32m of the latch
piece 32k energized by the elastic force of the coil spring 32p is
guided by the first inclined plane 32j.sub.1 of the connection
groove 32j of the cam groove 32f so as to move from a position "h"
to a position "i" in FIG. 12 and abuts on the stopper plane
32j.sub.2, thereby the latch piece 32k comes back to the
deregulation position shown in FIG. 11.
[0542] Furthermore, the latch mechanism 32 is constituted so that
the pressure-transducing chamber R.sub.2 communicates with the
channel 14B through the port 32b, the interior of the seal housing
32a and the through hole 32n of the latch piece 32k no matter where
the latch piece 32k is situated at the deregulation position, the
first regulation position or the second regulation position.
[0543] In the channel selector valve according to the fifth
embodiment, as shown in FIG. 11 and so on, a pin 12e is provided on
an end of the piston cylinder 12 at the pressure-transducing
chamber R.sub.2 side, which is formed so that an end of the pin 12e
is a little spaced from an end of the latch piece 32k situated at
the deregulation position thereof as shown in FIG. 11.
[0544] As to the channel selector valve according to the fifth
embodiment, the reversing valve housing 1, the stopper 2 and the
seal housing 32a of the latch mechanism 32 constitute the housing
described in claims of the present invention, a part of the
reversing valve housing 1, to which the outlet pipe 5 connected to
the outlet of the compressor 4 is connected, corresponds to the
inlet port described in claims, and the through hole 11a of the
valve seat 11, to which the inlet pipe 6 connected to the inlet of
the compressor 4 is connected, corresponds to the outlet port
described in claims.
[0545] Furthermore, as to the channel selector valve according to
the fifth embodiment, through holes 11b and 11c of the valve seat
11, to which the pipes 7 and 8 connecting with the indoor and
outdoor heat exchangers 9A and 9B, respectively, are connected,
correspond to the respective two selector ports described in
claims.
[0546] In the following, an operation of the channel selector valve
according to the fifth embodiment constructed as described above
will be explained.
[0547] When the operation of the compressor 4 is halted, as shown
in FIG. 9, the piston cylinder 12 energized by the compression
spring 13 is at the first position, the inlet pipe 6 communicates
with the pipe 8 through the closed space S1, while the outlet pipe
5 communicates with the pipe 7 through the high pressure space
S2.
[0548] In this state, although the pin 12e of the piston cylinder
12 abuts on the latch piece 32k, the latch piece 32k is energized
by the coil spring 32p to be situated at the deregulation position
shown in FIG. 11.
[0549] When the compressor 4 starts to operate, the refrigerant
discharged from the compressor 4 flows into the high pressure space
S2 through the outlet pipe 5, while the refrigerant pressure in the
pressure-transducing chamber R.sub.2, which communicates with the
channel 14B through the port 32b of the latch mechanism 32, the
interior of the seal housing 32a and the through hole 32n of the
latch piece 32k, becomes equal to the refrigerant pressure in the
inlet pipe 6 connected to the channel 14B.
[0550] Therefore, the pressure of the refrigerant flowed into the
high pressure space S2 exceeds the refrigerant pressure in the the
pressure-transducing chamber R.sub.2 by a difference between the
discharge pressure and the suction pressure of the refrigerant due
to the compressor 4, thereby the forward drive force F1 exceeds the
resultant force F2+Fs+Ff.
[0551] Consequently, the piston cylinder 12 tends to move from the
first position to the second position in the reversing valve
housing 1, then the pin 12e of the piston cylinder 12 pushes the
latch piece 32k and then, the latch piece 32k tends to move toward
the closed end of the seal housing 32a against the energizing force
by the coil spring 32p.
[0552] Here, when the cam follower pin 32m guided by the first
inclined plane 32j.sub.1 of the connection groove 32j moves from
the position "d" to the position "e" in FIG. 12, that is, when the
latch piece 32k is at the deregulation position after coming back
from the first regulation position, thereafter, the latch piece 32k
moves toward the closed end of the seal housing 32a while the cam
follower pin 32m is guided by the second inclined plane 32j.sub.3
to reach the position "g", i.e. the end of the deep groove 32h, by
way of the position "e" and the position "f" in FIG. 12, thereby
the latch piece 32k reaches the second regulation position as shown
in FIG. 14.
[0553] Therefore, a move stroke of the latch piece 32k toward the
closed end of the seal housing 32a becomes equal to the second
stroke L2, as a result, the piston cylinder 12 reaches the second
position after leaving the first position as shown in FIG. 10.
[0554] On the other hand, when the cam follower pin 32m guided by
the first inclined plane 32j.sub.1 of the connection groove 32j
moves from the position "h" to the position "i" in FIG. 12, that
is, when the latch piece 32k is at the deregulation position after
coming back from the second regulation position, thereafter, the
latch piece 32k moves toward the closed end of the seal housing 32a
while the cam follower pin 32m is guided by the second inclined
plane 32j.sub.3 to move from the position "b" in FIG. 12 to the
position "c" where the cam follower pin 32m abuts on the stopper
plane 32g.sub.1 of the shallow groove 32g, thereby the movement of
the latch piece 32k is restrained at the first regulation position
as shown in FIG. 13.
[0555] Therefore, a move stroke of the latch piece 32k toward the
closed end of the seal housing 32a becomes equal to the first
stroke L1, as a result, even if the piston cylinder 12 tends to
move from the first position thereof, the movement of the piston
cylinder 12 is restrained by the latch piece 32k, the movement of
which is restrained at the first regulation position, thereby the
piston cylinder 12 hardly moves and keeps staying at the first
position as shown in FIG. 9.
[0556] That is, the latch piece 32k, restrained its movement toward
the closed end of the seal housing 32a at the first regulation
position, substantially keeps the piston cylinder 12 that pushes
the latch piece 32k by the pin 12e from moving toward the second
position, i.e. keeps the piston cylinder 12 staying at the first
position, therefore, the outlet pipe 5 keeps communicating with the
pipe 7 through the high pressure space S2 while the inlet pipe 6
keeps communicating with the pipe 8 through the closed space
S1.
[0557] To the contrary, when the piston cylinder 12 reaches the
second position after pushing the latch piece 32k up to the second
regulation position by the pin 12e, as shown in FIG. 10, the outlet
pipe 5 communicates with the pipe 8 through the high pressure space
S2 while the inlet pipe 6 communicates with the pipe 7 through the
closed space S1.
[0558] When the compressor 4 starts to operate, the piston cylinder
12 that tends to move from the first position to the second
position pushes the latch piece 32k, which comes back to the
deregulation position from the second regulation position, by a pin
12e toward the closed end of the seal housing 32a, as shown in FIG.
13, the movement of the latch piece 32k is restrained at the frist
regulation position by the latch mechanism 32, therefore, the
piston cylinder 12 hardly moves toward the second position and
keeps staying at the first position as shown in FIG. 9.
[0559] Thereafter, the pressure of the refrigerant, which is
discharged from the compressor 4 and flows into the high pressure
space S2 through the outlet pipe 5, is reduced by stopping the
operation of the compressor 4 or the like so that the forward drive
force F1 is equal to or less than the force F2+Fs-Ff, the latch
piece 32k situated at the first regulation position moves toward
the high pressure chamber R.sub.1 by an energizing force due to the
coil spring 32p and comes back to the deregulation position as
shown in FIG. 11.
[0560] On the other hand, when the compressor 4 starts to operate,
the piston cylinder 12 that tends to move from the first position
to the second position pushes the latch piece 32k, which is at the
deregulation position after coming back from the first regulation
position, by a pin 12e toward the closed end of the seal housing
32a, as shown in FIG. 14, the latch piece 32k reaches the second
regulation position, therefore, the piston cylinder 12 reaches the
second position as shown in FIG. 10.
[0561] Thereafter, the pressure of the refrigerant, which is
discharged from the compressor 4 and flows into the high pressure
space S2 through the outlet pipe 5, is reduced by stopping the
operation of the compressor 4 or the like so that the forward drive
force F1 is equal to or less than the force F2+Fs-Ff, the latch
piece 32k situated at the second regulation position moves toward
the high pressure chamber R.sub.1 by an energizing force due to the
coil spring 32p and comes back to the deregulation position as
shown in FIG. 11.
[0562] Therefore, when the refrigerating cycle A is operated in the
heating mode, the latch piece 32k can be set at the deregulation
position after coming back from the second regulation position,
then the compressor 4 is started to operate, thereby the piston
cylinder 12 can be kept at the first position during the operation
of the compressor 4.
[0563] On the other hand, when the refrigerating cycle A is
operated in the cooling mode, the latch piece 32k can be set at the
deregulation position after coming back from the first regulation
position, then the compressor 4 is started to operate, thereby the
piston cylinder 12 can be moved from the first position to the
second position immediately after the operation of the compressor
4.
[0564] Once the piston cylinder 12 finishes to move to the second
position, as long as the forward drive force F1 exceeds the force
F2+Fs-Ff, the piston cylinder 12 is kept staying at the second
position even if the number of revolution of the compressor 4 is
reduced, thereby the refrigerating cycle A is kept operating in the
cooling mode.
[0565] Thus, in the fifth embodiment, the pressure-transducing
chamber R.sub.2 of the reversing valve housing 1 always
communicates with the inlet pipe 6, and the move stroke of the
latch piece 32k, which is pushed by a pin 12e of the piston
cylinder 12 that moves from the first position to the second
position, is set to be either the second stroke L2 corresponding to
the second regulation position, which allows the piston cylinder 12
to reach the second position, or the first stroke L1 corresponding
to the first regulation position, which does not allow the piston
cylinder 12 to reach the second position, with being alternately
controlled by the latch mechanism 32.
[0566] The latch piece 32k can be set at the deregulation position
after coming back from the second regulation position, then the
compressor 4 is started to operate, thereby the piston cylinder 12
can be kept at the first position. Further, the latch piece 32k can
be set at the deregulation position after coming back from the
first regulation position, then the compressor 4 is started to
operate, thereby the piston cylinder 12 can be moved from the first
position to the second position, and thereafter, the piston
cylinder 12 can be kept at the second position as long as the
operation of the compressor 4 is not halted.
[0567] Therefore, the heating mode, in which the refrigerant
discharged from the outlet pipe 5 is supplied to the indoor heat
exchanger 9A by way of the pipe 7, and the cooling mode, in which
the refrigerant discharged from the outlet pipe 5 is supplied to
the outdoor heat exchanger 9B by way of the pipe 8, can be selected
by controlling the number of times of the operation start of the
compressor 4 and the selected state can be maintained without using
any exclusive power source such as an electromagnetic solenoid.
[0568] In contrast with the fifth embodiment, FIG. 15 is a view
illustrating a schematic constitution of a refrigerating cycle
employing a channel selector valve according to a sixth embodiment
of the present invention. As to the sixth embodiment, the outdoor
heat exchanger 9B is connected to the pipe 7 while the indoor heat
exchanger 9A is connected to the pipe 8, and when the piston
cylinder 12 is restrained by the latch mechanism 32 and situated at
the first position, the outlet pipe 5 communicates with the outdoor
heat exchanger 9B through the high pressure chamber R.sub.1 and the
pipe 7 while the inlet pipe 6 communicates with the indoor heat
exchanger 9A through the closed space S1 and the pipe 8.
[0569] The latch mechanism 32 is not limited to such a mechanism
that the latch piece 32k alternately moves between the second and
first regulation positions by way of the deregulation position as
described above, instead, a mechanism in which the second and first
regulation positions are randomly selected by using a torque driver
may be employed.
[0570] FIG. 16 is a view illustrating a schematic constitution of a
latch mechanism usable instead of the latch mechanism described
above. FIG. 17 is a development of a cam groove, along which a cam
follower pin of FIG. 16 moves. As shown in FIG. 16, an end 12a of
the pin 12e of the piston cylinder 12 is inserted into a bearing
32r of the latch piece 32k so as to rotatively connect the latch
piece 32k with the pin 12e, and as shown in FIG. 17, the cam groove
32f, along which the cam follower pin 32m of the latch piece 32k
moves, is formed as a limited path inclined with respect to an
axial direction of the inner cylinder 32e, thereby forming the
shallow groove 32g in the middle of the limited path and the deep
groove 32h at an end of the limited path.
[0571] With the construction mentioned above, the pressure of the
refrigerant, which is discharged from the compressor 4 and flows
into the high pressure space S2 through the outlet pipe 5, is
raised so as to increase a moving rate of the piston cylinder 12
from the first position to the second position, then the latch
piece 32k has a large rotation moment and then, the cam follower
pin 32m reaches the deep groove 32h at the end of the cam groove
32f after passing through the shallow groove 32g, thereby the
piston cylinder 12 is situated at the second position.
[0572] On the contrary, the pressure of the refrigerant, which is
discharged from the compressor 4 and flows into the high pressure
space S2 through the outlet pipe 5, is reduced so as to decrease a
moving rate of the piston cylinder 12 from the first position to
the second position, then the latch piece 32k has only a small
rotation moment and then, the cam follower pin 32m cannot pass
through the shallow groove 32g and stays at the shallow groove 32g,
thereby the piston cylinder 12 stays at the first position since
its movement toward the second position is restrained.
[0573] Then, whether the cam follower pin 32m is situated at either
the shallow groove 32g or the deep groove 32h, when the operation
of the compressor 4 is halted, the latch piece 32k comes back to
its original position (i.e. a light end of its locus in FIG. 17)
due to an energizing force by the coil spring 32p, thereafter, when
the compressor 4 is started to operate, the cam follower pin 32m
can move to either the shallow groove 32g or the deep groove 32h
depending upon the pressure of the discharged refrigerant.
[0574] With the construction mentioned above, the piston cylinder
12 can be situated at the desired position out of the first and
second positions only by increasing or decreasing the pressure of
the refrigerant discharged from the compressor 4, furthermore, when
the cam follower pin 32m is moved from the shallow groove 32g to
the deep groove 32h or from the deep groove 32h to the shallow
groove 32g, the operation of the compressor 4 is neither needed to
be started nor needed to be halted in order to rotate the latch
piece 32k for resetting the present position, resulting in an
advantage for the operation.
[0575] In the following, a channel selector valve according to a
seventh embodiment of the present invention will be explained with
reference to FIGS. 18 to 22.
[0576] FIG. 18 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
the seventh embodiment of the present invention, in which the same
abbreviation numerals with those used for the corresponding
identical members or parts of the refrigerating cycle according to
the fifth embodiment shown in FIG. 9 are used.
[0577] The channel selector valve according to the seventh
embodiment, a state in operation in the hearting mode of which is
shown in FIG. 18 by its sectional view, is different from the
channel selector valve according to the fifth embodiment shown in
FIG. 9 in a point that instead of the latch mechanism 32, there is
provided a pilot valve mechanism 33 having another latch mechanism
34 (corresponding to the second latch mechanism described in claims
29 and 30), a constitution of which is similar to the latch
mechanism 32, and the stopper 3 instead of the seal housing 32a of
the latch mechanism 32 seals one end of the reversing valve housing
1.
[0578] FIG. 19 is an enlarged sectional view of a primary part of
the pilot valve mechanism of FIG. 18. As shown in FIG. 19, the
pilot valve mechanism 33 comprises: a diaphragm 33a for
partitioning the interior of the pressure-transducing chamber
R.sub.2 into a main chamber R.sub.3 near the high pressure chamber
R.sub.1 for allowing the piston cylinder 12 to move between the
first and second positions and a sub chamber R.sub.4 near the
stopper 3; a valve block 33b integrally formed with the diaphragm
33a; a pilot valve element 33e (corresponding to the pilot valve
described in claim 29) received into the valve block 33b; a bellows
33g disposed in the sub chamber R.sub.4; and a pin 33h for
retracting (i.e. for opening or closing) the pilot valve element
33e.
[0579] In the interior of the valve block 33b, there are provided a
pilot path 33c with its one end open to the sub chamber R.sub.4 and
an open path 33d being open to the main chamber R.sub.3 extending
from the opposite end of the pilot path 33c to a circumferential
surface of the valve block 33b, while the pilot valve element 33e
is disposed at a crossing between the pilot path 33c and the open
path 33d and energized by the coil spring 33f from the opposite end
of the pilot path 33c toward the one end thereof so as to close the
pilot path 33c.
[0580] The bellows 33g is fixed on an inner face of the stopper 3
at one end thereof and expands or contracts so as to allow an
opposite end thereof to move nearer to or away from the diaphragm
33a or the valve block 33b. The bellows 33g partitions the interior
space of the sub chamber R.sub.4 into a first space R.sub.41, (i.e.
a space inside of the bellows 33g) and a second space R.sub.42
(i.e. a space outside of the bellows 33g).
[0581] The first space R.sub.41 always communicates with the outlet
pipe 5 through a channel 14D connected from the outside of the
reversing valve housing 1 by way of the stopper 3 and one end of
the bellows 33g, while the second space R.sub.42 always
communicates with the inlet pipe 6 through a channel 14B connected
from the outside of the reversing valve housing 1 by way of the
stopper 3.
[0582] The pin 33h arises from a plate 33j fixed at the opposite
end of the bellows 33g and inserted into the pilot path 33c from an
end thereof.
[0583] Although the latch mechanism 34 is not shown in detail in
FIGS. 18 and 19, it comprises elements corresponding to the guide
cylinder 32c, the latch piece 32k and the coil spring 32p of the
latch mechanism 32 of the channel selector valve according to the
fifth and sixth embodiments. In detail, an element corresponding to
the guide cylinder 32c of the latch mechanism 32 is formed near one
end of the valve block 33b, while an element corresponding to the
coil spring 32p of the latch mechanism 32 is not shown in FIGS. 18
and 19.
[0584] The latch piece 34a of the latch mechanism 34 of the seventh
embodiment, which corresponds to the latch piece 32k of the latch
mechanism 32, is formed slidable with respect to the one end of the
valve block 33b, wherein a deregulation position of the latch piece
34a is a position where the latch piece 34a protrudes from the one
end of the valve block 33b toward the the sub chamber R.sub.4 as
shown in FIG. 19, while a second regulation position of the latch
piece 34a is a position where the latch piece 34a is moved from the
deregulation position, shown in FIG. 20 with imaginary lines
(alternate long and two short dashes lines), toward the one end of
the valve block 33b by a second stroke L2, that is, where an end
face of the latch piece 34a is the same plane with that of the one
end of the valve block 33b, as shown in FIG. 20.
[0585] As shown in FIG. 21, a first regulation position of the
latch piece 34a is a positon where the latch piece 34a is moved
from the deregulation position, shown in FIG. 21 with imaginary
lines (alternate long and two short dashes lines), toward the one
end of the valve block 33b by a first stroke L1, which is shorter
than the second stroke L2, that is, where an end face of the latch
piece 34a is a little shifted from the deregulation position toward
the one end of the valve block 33b.
[0586] In the pilot valve mechanism 33 with the latch mechanism 34
constructed as describe above, when the bellows 33g is compressed,
the end face of the latch piece 34a situated at the deregulation
position abuts on the plate 33j and the pin 33h is apart from the
pilot valve element 33e, thereby the pilot path 33c is closed by
the pilot valve element 33e.
[0587] In the pilot valve mechanism 33, when the bellows 33g
expands and the plate 33j pushes the latch piece 34a situated at
the deregulation position and also when the latch piece 34a has
come back to the deregulation position from the second regulation
position, the latch piece 34a pushed by the plate 33j is kept from
moving further at the first regulation position where the latch
piece 34a has moved from the deregulation position toward the one
end of the valve block 33b by the first stroke, that is, the pin
33h of the plate 33j, the move of which is restrained by the latch
piece 34a situated at the first regulation position, is kept being
apart from the pilot valve element 33e, thereby the pilot path 33c
is kept closed by the pilot valve element 33e.
[0588] Further, in the pilot valve mechanism 33, when the bellows
33g expands and the plate 33j pushes the latch piece 34a situated
at the deregulation position and also when the latch piece 34a has
come back to the deregulation position from the first regulation
position, the latch piece 34a pushed by the plate 33j reaches the
second regulation position where the latch piece 34a is moved from
the deregulation position toward the one end of the valve block 33b
by the second stroke L2, then the pin 33h of the plate 33j comes in
contact with the pilot valve element 33e, allowing the pilot valve
element 33e to be apart from the opposite end of the pilot path 33c
by overcoming an energizing force due to the coil spring 33f,
thereby the pilot path 33c is opened by the pilot valve element
33e.
[0589] As shown in FIG. 19, in the channel selector valve according
to the seventh embodiment, the diaphragm 33a of the pilot valve
mechanism 33 receives an end of a compression spring 13 instead of
the seal housing 32a of the fifth or sixth embodiment.
[0590] In the channel selector valve according to the seventh
embodiment, the pilot path described in claim 29 consists of the
pilot path 33c and the open path 33d, while the valve opener
described in claim 29 consists of the pin 33h and the plate
33j.
[0591] Further, the channel selector valve according to the seventh
embodiment is constituted similarly to that according to the fifth
embodiment shown in FIG. 9, except the points mentioned above,
while the channel selector valve according to the seventh
embodiment is different from that according to the fifth embodiment
in a point that the housing described in claims consists of the
reversing valve housing 1 and the stoppers 2 and 3.
[0592] In addition, the channel selector valve according to the
seventh embodiment is similar to that according to the fifth
embodiment in points that: a part of the reversing valve housing 1,
to which the outlet pipe 5 communicating with the outlet of the
compressor 4 is connected, corresponds to the inlet port described
in claims; the through hole 11a of the valve seat 11, to which the
inlet pipe 6 communicating with the inlet of the compressor 4 is
connected, corresponds to the outlet port described in claims; and
through holes 11b and 11c of the valve seat 11, to which the pipes
7 and 8 connecting with the indoor and outdoor heat exchangers 9A
and 9B, respectively, are connected, correspond to the respective
two selector ports described in claims.
[0593] In the following, an operation of the channel selector valve
according to the seventh embodiment constructed as described above
will be explained.
[0594] When the operation of the compressor 4 is halted, as shown
in FIG. 18, the piston cylinder 12 energized by the compression
spring 13 is situated at the first position, the inlet pipe 6
communicates with the pipe 8 through the closed space S1, and the
outlet pipe 5 communicates with the pipe 7 through the high
pressure space S2.
[0595] In this situation, the pilot valve element 33e energized by
the coil spring 33f closes the pilot path 33c, therefore, the main
chamber R.sub.3 of the pressure-transducing chamber R.sub.2 does
not communicate with the sub chamber R.sub.4.
[0596] When the compressor 4 starts to operate, the refrigerant
discharged from the compressor 4 flows into the high pressure space
S2 through the outlet pipe 5, then a pressure of an inner space of
the bellows 33g communicating with the outlet pipe 5 through the
channel 14D, that is, an inner pressure of the first space
R.sub.41, becomes equal to the pressure of the refrigerant in the
outlet pipe 5, while an inner pressure of the second space R.sub.42
becomes equal to the pressure of the refrigerant in the inlet pipe
6, with which the second space R.sub.42 communicates through the
channel 14B.
[0597] Then, since the inner pressure of the first space R.sub.41
exceeds that of the second space R.sub.42, the bellows 33g expands,
then the plate 33j moves toward the diaphragm 33a in the sub
chamber R.sub.4 so as to reduce the second space R.sub.42, thereby
the plate 33j moves the latch piece 34a, situated at the
deregulation position and protruding toward the inside of the sub
chamber R.sub.4 from the diaphragm 33a, in a retreating direction
from the inside of the sub chamber R.sub.4 as shown in FIG. 19.
[0598] At this time, if the movement of the latch piece 34a by the
plate 33j takes place after the latch pieced 34a has come back from
the first regulation position to the deregulation position, the
movement of the latch piece 34a in the retreating direction is
restrained at the second regulation position by the latch mechanism
34, therefore, a stroke of the latch piece 34a in the retreating
direction becomes equal to the second stroke L2.
[0599] As a result, as shown in FIG. 20, the pin 33h, connected to
the plate 33j and inserted into the pilot path 33c, comes in
contact with the pilot valve element 33e, then the the pilot valve
element 33e is moved being apart from the opposite end of the pilot
path 33c by overcoming an energizing force due to the coil spring
33f, thereby the pilot path 33c opens.
[0600] As a result, the main chamber R.sub.3 communicates with the
second space R.sub.42 of the sub chamber R.sub.4 through the pilot
path 33c and the open path 33d, then the main chamber R.sub.3
communicates with the inlet pipe 6, which always communicates with
the second space R.sub.42, thereby an inner pressure of the main
chamber R.sub.3 becomes equal to the pressure of the refrigerant in
the inlet pipe 6, which is much lower than the pressure of the
refrigerant flowed into the high pressure space S2.
[0601] Therefore, the pressure of the refrigerant in the main
chamber R.sub.3 of the pressure-transducing chamber R.sub.2 becomes
less than the pressure of the refrigerant in the high pressure
chamber R.sub.1, then the piston cylinder 12 moves from the first
position to the second position in the main chamber R.sub.3 as
shown in FIG. 22 (cooling mode), wherein the outlet pipe 5
communicates with the pipe 8 through the high pressure space S2,
while the inlet pipe 6 communicates with the pipe 7 through the
closed space S1.
[0602] To the contrary, if the movement of the latch piece 34a in
the retreating direction by the plate 33j takes place after the
latch pieced 34a has come back from the second regulation position
to the deregulation position, the movement of the latch piece 34a
in the retreating direction is restrained at the first regulation
position, therefore, a stroke of the latch piece 34a in the
retreating direction becomes equal to the first stroke L1.
[0603] As a result, as shown in FIG. 21, since the pin 33h can not
come into contact with the pilot valve element 33e and is kept
apart therefrom, the pilot valve element 33e keeps closing the
pilot path 33c due to the energizing force by the coil spring 33f,
therefore, the main chamber R.sub.3 is kept insulated from the
second space R.sub.42 of the sub chamber R.sub.4 and the piston
cylinder 12 is kept staying at the first position, thereby the
outlet pipe 5 communicates with the pipe 7 through the high
pressure space S2, while the inlet pipe 6 communicates with the
pipe 8 through the closed space S1.
[0604] That is, when the latch piece 34a, which has come back to
the deregulation position from the second regulation position, is
moved in the retreating direction due to the movement of the plate
33j upon starting of the operation of the compressor 4, as shown in
FIG. 21, the movement of the latch piece 34a is restrained at the
first regulating pisition due to the latch mechanism 34, then the
pilot valve element 33e energized by the coil spring 33f closes the
pilot path 33c, thereby the piston cylinder 12 keeps staying at the
first position as shown in FIG. 18.
[0605] Thereafter, the inner pressure of the first space R.sub.41,
exceeding the inner pressure of the second space R.sub.42 of the
sub chamber R.sub.4, is reduced so as to be close to the inner
pressure of the second space R.sub.42, by tentatively halting the
operation of the compressor 4 and the like, thereby the first space
R.sub.41 is reduced and the second space R.sub.42 is expanded. As a
result, as shown in FIG. 19, the latch piece 34a situated at the
first regulaion position by the plate 33j advances into the inside
of the sub chamber R.sub.4 and comes back to the deregulation
position, while the plate 33j is moved in the direction away from
the diaphragm 33a by the latch piece 34a.
[0606] To the contrary, when the latch piece 34a, which has come
back to the deregulation position from the first regulation
position, is moved in the retreating direction due to the movement
of the plate 33j upon starting of the operation of the compressor
4, the movement of the latch piece 34a is restrained only at the
second regulating pisition, therefore, the pilot valve element 33e
is moved in the direction away from the opposite end of the pilot
path 33c by the pin 33h connected to the plate 33j, by overcoming
the energizing force due to the coil spring 33f, thereby the pilot
path 33c is opened and the piston cylinder 12 is situated at the
second position as shown in FIG. 22.
[0607] Again thereafter, the inner pressure of the first space
R.sub.41, exceeding the inner pressure of the second space R.sub.42
of the sub chamber R.sub.4, is reduced so as to be close to the
inner pressure of the second space R.sub.42, by tentatively halting
the operation of the compressor 4 and the like, thereby the first
space R.sub.41 is reduced and the second space R.sub.42 is
expanded. As a result, as shown in FIG. 19, the latch piece 34a
situated at the second regulaion position by the plate 33j advances
into the inside of the sub chamber R.sub.4 and comes back to the
deregulation position, while the plate 33j is moved in the
direction away from the diaphragm 33a by the latch piece 34a.
[0608] Then, the pin 33h connected to the plate 33j is apart from
the pilot valve element 33e and then, the pilot valve element 33e,
which has been moved in the direction away from the opposite end of
the pilot path 33c by the pin 33h, closes the pilot path 33c by the
energizing force due to the coil spring 33f, thereby the piston
cylinder 12 moves from the second position to the first position as
shown in FIG. 18.
[0609] The channel selector valve according to the seventh
embodiment constracted as described above gives a similar effect
with that of the channel selector valve according to the fifth
embodiment.
[0610] In contrast with the seventh embodiment, FIG. 23 is a view
illustrating a schematic constitution of a refrigerating cycle
employing a channel selector valve according to a eighth embodiment
of the present invention. As to the eighth embodiment, the outdoor
heat exchanger 9B is connected to the pipe 7 while the indoor heat
exchanger 9A is connected to the pipe 8, and when the piston
cylinder 12 is restrained by the latch mechanism 32 and situated at
the first position, the outlet pipe 5 communicates with the outdoor
heat exchanger 9B through the high pressure space S2 and the pipe 7
while the inlet pipe 6 communicates with the indoor heat exchanger
9A through the closed space S1 and the pipe 8.
[0611] In the following, a channel selector valve, in which the
channel is selected by controlling an opening ratio of an
electrically-driven expansion valve, according to a ninth
embodiment of the present invention will be explained with
reference to FIGS. 24 to 27.
[0612] FIG. 24 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
the ninth embodiment of the present invention, in which the same
abbreviation numerals with those used for the corresponding
identical members or parts of the refrigerating cycle according to
the first embodiment shown in FIG. 1 are used.
[0613] The channel selector valve according to the ninth
embodiment, a state in operation in the hearting mode of which is
shown in FIG. 24 by its sectional view, constitutes the
refrigerating cycle A together with the compressor 4, the indoor
heat exchanger 9A, the outdoor heat exchanger 9B, an
electrically-driven expansion valve 10A and a capillary tube 10B,
wherein the electrically-driven expansion valve 10A and the
capillary tube 10B are provided between the indoor heat exchanger
9A and the outdoor heat exchanger 9B.
[0614] The channel selector valve according to the ninth embodiment
is different from that according to the first embodiment shown in
FIG. 1 in a point that a part of a housing 29a of a state-holding
selector valve 29 is inserted into the inside of the reversing
valve housing 1 through a stopper 3 that seals one end of the
reversing valve housing 1.
[0615] In the channel selector valve according to the ninth
embodiment, as shown in FIG. 25, i.e. a view illustrating a
schematic constitution of a refrigerating cycle in which a
sectional view of the channel selector valve of FIG. 24 in a
cooling mode is shown, the piston cylinder 12 can move between a
second position where the piston cylinder abuts on the stopper 3 to
be restrained from moving further toward the stopper 3 and a first
position where an end of a connecting shaft 28 abuts on a stopper 2
so that the piston cylinder 12 is restrained from moving further
toward the stopper 2.
[0616] As shown in FIG. 24, the state-holding selector valve 29
comprises the housing 29a, a selector valve element 29e received in
the housing 29a (corresponding to the second selector valve
element) and a coil spring 29k (corresponding to energizing means
for energizing the selector valve).
[0617] As shown in FIG. 26, the housing 29a has a cylindrical shape
with its one end closed and an open end of the housing 29a is
inserted into the inside of the pressure-transducing chamber
R.sub.2 of the reversing valve housing 1, and a first port 29b for
communicating the interior of the housing 29a to the exterior
thereof is provided near the closed end of the housing 29a.
[0618] The first port 29b is connected to a channel 14A from the
outside of the housing 29a and as shown in FIG. 24, the channel 14A
is connected to a position situated between the electrically-driven
expansion valve 10A and the capillary tube 10B.
[0619] As shown in FIG. 26, a second port 29c for communicating the
interior of the housing 29a to the exterior thereof is provided at
a position where is a little nearer to the stopper 2 than the
position of the first port 29b.
[0620] The second port 29c is connected to a channel 14B from the
outside of the housing 29a and as shown in FIG. 24, the channel 14B
is connected to an inlet pipe 6.
[0621] Further, as shown in FIG. 26, a third port 29d for
communicating the interior of the housing 29a to the
pressure-transducing chamber R.sub.2 is provided at the same
circumferential position with that of the second port 29c.
[0622] The selector valve element 29e has an outer diameter
corresponding to an inner diameter of the housing 29a, a pin 29f is
formed at an end of the selector valve element 29e, and the pin 29f
passes through a stopper ring 29g engaged with the housing 29a and
protrudes toward the outside of an open end of the housing 29a.
[0623] Further, a ring-shaped groove 29h is formed on a
circumferential surface of the selector valve element 29e and a
through hole 29j is formed passing through the inside of the
selector valve element 29e and the pin 29f.
[0624] One end of the coil spring 29k is inserted into the through
hole 29j of the selector valve element 29e and locked at a level
difference in the through hole 29j, while an opposite end of the
coil spring 29k is abuts on the closed end of the housing 29a. The
coil spring 29k energizes the selector valve element 29e toward a
direction in which a level difference between the selector valve
element 29e and the pin 29f abuts on the stopper ring 29g, that is,
a direction in which the selector valve element 29e protrudes
toward the pressure-transducing chamber R.sub.2 from the open end
of the housing 29a.
[0625] As to the state-holding selector valve 29, in a first state
that the level difference between the selector valve element 29e
and the pin 29f abuts on the stopper ring 29g due to the energizing
force by the coil spring 29k, the selector valve element 29e is
situated at a position where is nearer to the open end of the
housing 29a than the first port 29b, the first port 29b
communicates with the pressure-transducing chamber R.sub.2 through
the through hole 29j, and the ring-shaped groove 29h connects only
to the third port 29d so that the second port 29c is closed by the
circumferential surface of the selector valve element 29e.
[0626] Further, as to the state-holding selector valve 29, as shown
in FIG. 27, in a second state that the level difference between the
selector valve element 29e and the pin 29f is apart from the
stopper ring 29g toward the closed end of the housing 29a, the
first port 29b is closed by the circumferential surface of the
selector valve element 29e, the ring-shaped groove 29h connectes to
both the second port 29c and the third port 29d so that the second
port 29c communicates with the pressure-transducing chamber R.sub.2
through the ring-shaped groove 29h and the third port 29d.
[0627] In the following, an operation of the channel selector valve
according to the ninth embodiment constracted as described above
will be explained.
[0628] When the operation of the compressor 4 is halted, as shown
in FIG. 24, the piston cylinder 12 is situated at the first
position by energizing the compression spring 13, then the inlet
pipe 6 communicates with the pipe 8 through the closed space S1
while the outlet pipe 5 communicates with the pipe 7 through the
high pressure space S2.
[0629] This situation corresponds to the first state of the
state-holding selector valve 29, in which the selector valve
element 29e is energized by the coil spring 29k so that the channel
14A communicates with the pressure-transducing chamber R.sub.2
through the first port 29b, then the pressure-transducing chamber
R.sub.2 communicates with a position situated between the
electrically-driven expansion valve 10A and the capillary tube 10B
in the refrigerating cycle A, to which the channel 14A is
connected.
[0630] Therefore, when the compressor 4 starts to operate, if the
refrigerant pressure, at the position situated between the
electrically-driven expansion valve 10A and the capillary tube 10B
in the refrigerating cycle A, is much the same with the pressure of
the refrigerant flowed into the high pressure space S2, that is, if
the forward drive force F1 is equal to or less than the resultant
force F2+Fs+Ff, the piston cylinder 12 stays at the first
position.
[0631] Then, since the piston cylinder 12 stays at the first
position, as shown in FIG. 26, the selector valve element 29e is
kept to be energized by the coil spring 29k, as a result, the
state-holding selector valve 29 keeps its first state, in which the
pressure-transducing chamber R.sub.2 communicates with the channel
14A.
[0632] Therefore, even after the compressor 4 starts to operate, as
long as the pressure of the refrigerant discharged from the
compressor 4 and the refrigerant pressure at the position situated
between the electrically-driven expansion valve 10A and the
capillary tube 10B are set so that the forward drive force F1 is
equal to or less than the resultant force F2+Fs+Ff, the piston
cylinder 12 keeps staying at the first position, as a result, the
inlet pipe 6 keeps communicating with the pipe 8 through the closed
space S1 while the outlet pipe 5 keeps communicating with the pipe
7 through the high pressure space S2.
[0633] To the contrary, if the refrigerant pressure, at the
position situated between the electrically-driven expansion valve
10A and the capillary tube 10B in the refrigerating cycle A, is
much lower than the pressure of the refrigerant flowed into the
high pressure space S2, that is, if the forward drive force F1
exceeds the resultant force F2+Fs+Ff, the piston cylinder 12 moves
from the first position and situated at the second position as
shown in FIG. 25.
[0634] When the piston cylinder 12 moves to the second position,
the piston cylinder 12 pushes the pin 29f toward the closed end of
the housing 29a, as shown in FIG. 27, the selector valve element
29e is in selecting operation by the pin 29f against the energizing
force due to the coil spring 29k, then the state-holding selector
valve 29 is changed to be in the second state in which the
pressure-transducing chamber R.sub.2 communicates with the channel
14B from the first state in which the pressure-transducing chamber
R.sub.2 communicates with the channel 14A.
[0635] Then, the pressure-transducing chamber R.sub.2 communicates
with the inlet pipe 6 to which the channel 14B is connected and the
refrigerant pressure in the pressure-transducing chamber R.sub.2
becomes equal to the pressure of the refrigerant in the inlet pipe
6, which is much lower than the pressure of the refrigerant flowed
into the high pressure space S2.
[0636] Therefore, the refrigerant pressure in the high pressure
chamber R.sub.1 exceeds the refrigerant pressure in the
pressure-transducing chamber R.sub.2 by a difference between the
refrigerant pressure in the outlet pipe 5 and the refrigerant
pressure in the inlet pipe 6, thereby the piston cylinder 12 keeps
staying at the second position.
[0637] Then, since the piston cylinder 12 keeps staying at the
second position, through the selecting operation of the selector
valve element 29e against the energizing force due to the coil
spring 29k, by the pin 29f pushed by the piston cylinder 12, the
state-holding selector valve 29 is maintained in the second state,
in which the pressure-transducing chamber R.sub.2 communicates with
the channel 14B.
[0638] That is, when the compressor 4 starts to operate, if the
refrigerant pressure, at the position situated between the
electrically-driven expansion valve 10A and the capillary tube 10B
in the refrigerating cycle A, is set so that the resultant force
F2+Fs+Ff is equal to or more than the forward drive force F1, as
shown in FIG. 24, the piston cylinder 12 keeps staying at the first
position and the state-holding selector valve 29 is maintained in
the first state.
[0639] To the contrary, when the compressor 4 starts to operate, if
the refrigerant pressure, at the position situated between the
electrically-driven expansion valve 10A and the capillary tube 10B
in the refrigerating cycle A, is set so that the resultant force
F2+Fs+Ff is less than the forward drive force F1, as shown in FIG.
25, the piston cylinder 12 moves from the first position to the
second position and the state-holding selector valve 29 is changed
from the first state to the second state, thereby the piston
cylinder 12 is kept staying at the second position.
[0640] Thereafter, the pressure of the refrigerant, which is
discharged from the compressor 4 and flows into the high pressure
space S2 through the outlet pipe 5, is reduced by stopping the
operation of the compressor 4 or the like so that the forward drive
force F1 is equal to or less than the force F2+Fs-Ff, thereby the
piston cylinder 12 moves from the second position to the first
position as shown in FIG. 24.
[0641] When the piston cylinder 12 is moved from the second
position to the first position, the energizing force due to the
coil spring 29k affects the selector valve element 29e, which has
been in its action by the pin 29f, then the state-holding selector
valve 29 is changed to be in the first state in which the
pressure-transducing chamber R.sub.2 communicates with the channel
14A from the second state in which the pressure-transducing chamber
R.sub.2 communicates with the channel 14B.
[0642] Therefore, when the refrigerating cycle A is operated in the
heating mode, the refrigerant pressure, at the position situated
between the electrically-driven expansion valve 10A and the
capillary tube 10B in the refrigerating cycle A, is set high by
controlling the electrically-driven expansion valve 10A into its
closed side upon starting of operation of the compressor 4 so that
the resultant force F2+Fs+Ff is equal to or more than the forward
drive force F1, thereby the piston cylinder 12 is kept staying at
the first position.
[0643] On the other hand, when the refrigerating cycle A is
operated in the cooling mode, the refrigerant pressure, at the
position situated between the electrically-driven expansion valve
10A and the capillary tube 10B in the refrigerating cycle A, is set
low by controlling the electrically-driven expansion valve 10A into
its open side upon starting of operation of the compressor 4 so
that the resultant force F2+Fs+Ff is less than the forward drive
force F1, thereby the piston cylinder 12 is moved from the first
position to the second position right after the operation of the
compressor 4.
[0644] Then, once the piston cylinder 12 is moved to the second
position, as long as the the forward drive force F1 is greater than
the force F2+Fs-Ff, the piston cylinder 12 is kept staying at the
second position even if the opening ratio of the
electrically-driven expansion valve 10A is throttled, thereby the
piston cylinder 12 is kept staying at the second position and the
refrigerating cycle A is kept being operated in the cooling
mode.
[0645] Thus, in the ninth embodiment, there is provided the
state-holding selector valve 29, by which the pressure-transducing
chamber R.sub.2 of the reversing valve housing 1 is selectively
connected to either the position situated between the
electrically-driven expansion valve 10A and the capillary tube 10B
in the refrigerating cycle A or the inlet pipe 6 through the
channel 14A or 14B.
[0646] Therefore, the heating mode, in which the refrigerant
discharged from the compressor 4 is supplied to the indoor heat
exchanger 9A by way of the pipe 7, and the cooling mode, in which
the refrigerant discharged from the compressor 4 is supplied to the
outdoor heat exchanger 9B by way of the pipe 8, can be selected by
a change in the pressure of the discharged refrigerant or by a
change in the pressure of the refrigerant at the position situated
between the electrically-driven expansion valve 10A and the
capillary tube 10B upon start of operation of the compressor 4 and
the selected state can be maintained, without using any exclusive
power source such as an electromagnetic solenoid.
[0647] According to the ninth embodiment, since a power for the
selection operation of the channel selector valve is obtained from
a change in the refrigerant pressure in the high pressure chamber
R.sub.1 of the reversing valve housing 1 and in the
pressure-transducing chamber R.sub.2 by controlling the open ratio
of the electrically-driven expansion valve 10A, there is no
necessity of using an electrically-driven drive source such as an
electromagnetic solenoid, which has been explained in the prior art
section of the present specification.
[0648] In the following, a channel selector valve, in which the
channel is selected by a change in a oscillational frequency
generated by a compressor, according to a tenth embodiment of the
present invention will be explained with reference to FIGS. 28 and
29.
[0649] FIG. 28 is a view illustrating a schematic constitution of a
refrigerating cycle employing the channel selector valve according
to the tenth embodiment of the present invention, in which the same
abbreviation numerals with those used for the corresponding
identical members or parts of the refrigerating cycle according to
the ninth embodiment shown in FIG. 24 are used.
[0650] As shown in FIG. 28, the channel selector valve according to
the tenth embodiment is different from the channel selector valve
according to the ninth embodiment shown in FIG. 24 in points that a
state-holding selector valve 29A without the first port 29b (of the
state-holding selector valve 29) is employed instead of the
state-holding selector valve 29, that a channel 14C diverged from
the channel 14B is connected to the pressure-transducing chamber
R.sub.2 through the stopper 3 from the outside of the reversing
valve housing 1, and that a pilot oscillation valve 30 is provided
in the channel 14C.
[0651] As shown in FIG. 29, the pilot oscillation valve 30
comprises a housing 30a, an oscillator 30d received in the housing
30a, a ball valve 30f received in the oscillator 30d, and coil
springs 30g, 30h and 30j.
[0652] A first port 30b, which communicates the interior of the
pressure-transducing chamber R.sub.2 to the interior of the housing
30a, is formed at one end surface of the housing 30a, while a
second port 30c communicating with the channel 14B is formed at an
opposite end surface of the housing 30a.
[0653] The oscillator 30d has a flange 30e at the center in the
length direction of its cross section and the coil springs 30g and
30h are provided at both sides of the oscillator 30d in the length
direction of its cross section, wherein the coil spring 30g is
provided between the flange 30e and the one end surface of the
housing 30a, while the coil spring 30h is provided between the
flange 30e and the opposite end surface of the housing 30a.
[0654] The coil springs 30j are provided between the flange 30e and
an inner wall of the housing 30a with leaving a space in the
circumferential direction of the housing 30a, while the ball valve
30f is partially buried in an end surface of the oscillator 30d,
said end surface being situated at the opposite end surface of the
housing 30a.
[0655] The oscillator 30d is movable in directions of three
dimensions by the coil springs 30g, 30h and 30j and supported by
elastic forces of the coil springs 30g, 30h and 30j so as to come
back to a standard position where the ball valve 30f closes the
second port 30c.
[0656] According to the pilot oscillation valve 30 constructed as
mentioned above, when an oscillation having a specific frequency is
generated in the housing 30a, the oscillator 30d resonates because
a balance among the elastic forces of the coil springs 30g, 30h and
30j is lost, thereby the oscillator 30d periodically moves on a
specific three-dimensional locus and the ball valve 30f opens the
second port 30c.
[0657] On the other hand, according to the pilot oscillation valve
30, when an oscillation having a different frequency from the
specific frequency is generated in the housing 30a or when no
oscillation takes place in the housing 30a, the oscillator 30d is
situated at the standard position by the elastic forces of the coil
springs 30g, 30h and 30j so that the ball valve 30f keeps closing
the second port 30c.
[0658] In the following, an operation of the channel selector valve
according to the tenth embodiment constructed as described above
will be explained.
[0659] When the operation of the compressor 4 is halted, as shown
in FIG. 28, the piston cylinder 12 is situated at the first
position, the inlet pipe 6 communicates with the pipe 8 while the
outlet pipe 5 communicates with the pipe 7, then in this situation
the oscillator 30d of the pilot oscillation valve 30 is situated at
the standard position and the ball valve 30f closes the second port
30c.
[0660] Then, when the compressor 4 starts to operate, an
oscillation of the compressor 4 is propagated to the reversing
valve housing 1, the stopper 3 and the housing 30a through the
inlet valve 6 and the channel 14C, thereby the housing 30a
oscillates with a frequency corresponding to the oscillation of the
compressor 4.
[0661] If the oscillation of the housing 30a has not the specific
frequency, the oscillator 30d is situated at the standard position
and the ball valve 30f closes the second port 30c, that is, the
pressure-transducing chamber R.sub.2 is isolated from the inlet
pipe 6, therefore, the piston cylinder 12 is kept staying at the
first position as long as the forward drive force F1 is equal to or
less than the resultant force F2+Fs+Ff.
[0662] If the piston cylinder 12 is kept staying at the first
position, the selector valve element 29e is kept energized by the
coil spring 29k, therefore, the state-holding selector valve 29
keeps staying in the first state, in which the pressure-transducing
chamber R.sub.2 is isolated from the channel 14B and the
refrigerant pressure in the pressure-transducing chamber R.sub.2
does not change, thereby the piston cylinder 12 keeps staying at
the first position.
[0663] On the contrary, if the oscillation of the housing 30a has
the specific frequency, the oscillator 30d resonates and the ball
valve 30f opens the second port 30c, then the pressure-transducing
chamber R.sub.2 communicates with the inlet pipe 6 of the
compressor 4 through the pilot oscillation valve. 30 and the
channel 14C, thereby the refrigerant pressure in the
pressure-transducing chamber R.sub.2 becomes equal to the
refrigerant pressure in the inlet pipe 6, which is much lower than
the pressure of the refrigerant flowed into the high pressure space
S2.
[0664] Therefore, the forward drive force F1 exceeds the resultant
force F2+Fs+Ff, as a result, the piston cylinder 12 moves from the
first position to the second position.
[0665] When the piston cylinder 12 moves from the first position to
the second position, the pin 29f, which is pushed toward the closed
end of the housing 29a by the piston cylinder, makes the selector
valve element 29e be in selecting operation against the energizing
force due to the coil spring 29k, then the state-holding selector
valve 29 changes its state from the first state to the second state
so as to communicate the the pressure-transducing chamber R.sub.2
to the channel 14B, that is, the pressure-transducing chamber
R.sub.2 communicates with the inlet pipe 6 through a different path
from the path of the pilot oscillation valve 30 and the channel
14C.
[0666] Therefore, thereafter, even if the oscillation of the
compressor 4 changes, that is, the oscillation frequency of the
housing 30a is changed from the specific frequency and the
oscillator 30d comes back to the standard position and then the
ball valve 30f closes the second port 30c, the refrigerant pressure
in the the pressure-transducing chamber R.sub.2 is kept equal to
the refrigerant pressure in the inlet pipe 6, thereby the piston
cylinder 12 keeps staying at the second position.
[0667] Further, thereafter, if the pressure of the refrigerant
flowed into the high pressure space S2 from the compressor 4
through the outlet pipe 5 is reduced by tentatively halting the
operation of the compressor 4 and the like so as to move the piston
cylinder 12 from the second position to the first position, the
state-holding selector valve 29 changes its state from the second
state to the first state by the energizing force due to the coil
spring 29k, said energizing force affecting the selector valve
element 29e that has been made be in selecting operation by the pin
29f, thereby the oscillator 30d comes back to the standard position
and the ball valve 30f keeps closing the second port 30c.
[0668] Consequently, when the refrigerating cycle A is operated in
the heating mode, the number of revolution of the compressor 4 upon
start of its operation is set so that the housing 30a oscillates
with a frequency, which is different from the specific frequency,
by the oscillation of the compressor 4 propagated through the
reversing valve housing 1, stopper 3, the inlet pipe 6 and the
channel 14C, thereby the piston cylinder 12 can be kept staying at
the first position.
[0669] On the other hand, when the refrigerating cycle A is
operated in the cooling mode, the number of revolution of the
compressor 4 upon start of its operation is set so that the housing
30a oscillates with the specific frequency by the oscillation of
the compressor 4 propagated through the reversing valve housing 1,
stopper 3, the inlet pipe 6 and the channel 14C, thereby the piston
cylinder 12 can be moved from the first position to the second
position right after the operation of the compressor 4.
[0670] Then, once the piston cylinder 12 is moved to the second
position, as long as the compressor 4 keeps operating, the piston
cylinder 12 is kept staying at the second position even if the
oscillation of the compressor 4 changes and the oscillation
frequency of the housing 30a changes from the specific frequency,
thereby the refrigerating cycle A is kept operating in the cooling
mode.
[0671] The channel selector valve according to the tenth embodiment
constructed as described above gives a similar effect with that
according to the ninth embodiment.
[0672] According to the tenth embodiment, since a power for the
selection operation of the channel selector valve is obtained from
a change in the refrigerant pressure in the high pressure chamber
R.sub.1 of the reversing valve housing 1 and in the
pressure-transducing chamber R.sub.2 by the pilot oscillation valve
30, in which the pilot oscillation valve 30 opens or closes
depending upon a change in the frequency of the oscillation
generated by the compressor 4, therefore similarly to the ninth
embodiment, there is no necessity of using an electrically-driven
drive source such as an electromagnetic solenoid, which has been
explained in the prior art section of the present
specification.
[0673] In addition, according to the tenth embodiment, upon
starting of the operation of the compressor 4 there is no necessity
of adjusting the pressure of the refrigerant, which is introduced
into the pressure-transducing chamber R.sub.2 through the channel
14A by opening or closing of the electrically-driven expansion
valve 10A in the refrigerating cycle A, said adjusting is needed in
the ninth embodiment, therefore, the constitution of the channel
selector valve according to the tenth embodiment becomes simple
since there is no electrically-driven expansion valve 10A needed in
the refrigerating cycle A, thereby the selector operation of the
channel selector valve for selecting the heating and cooling modes
can be more easily performed.
[0674] In the ninth and tenth embodiments, the piston cylinder 12
may be provided with a pin instead of providing the selector valve
element 29e with the pin 29f.
[0675] In the following, a channel selector valve, in which the
channel is selected by adjusting a heat-exchange capacity by heat
exchangers, according to a eleventh embodiment of the present
invention will be explained with reference to FIGS. 30 and 31.
[0676] FIG. 30 is a view illustrating a schematic constitution of a
refrigerating cycle employing the channel selector valve according
to the eleventh embodiment of the present invention, in which the
same abbreviation numerals with those used for the corresponding
identical members or parts of the refrigerating cycle according to
the ninth embodiment shown in FIG. 24 are used.
[0677] As shown in FIG. 30, the channel selector valve according to
the eleventh embodiment is different from the channel selector
valve according to the ninth embodiment shown in FIG. 24 in points
that the electrically-driven expansion valve 10A is omitted and
that a differential pressure selector valve 40 is provided between
the outle pipe 5 and the inlet pipe 6.
[0678] As shown in FIG. 31, the differential pressure selector
valve 40 comprises the housing 40a, a bellows 40b received in the
housing 40a, a valve element 40f for opening or closing a valve
port 40e that partitions the housing 40a into a first chamber 40c
and a second chamber 40d by expansion and contraction of the
bellows 40b, and a pilot valve 40h, which opens or closes a pilot
path 40g that passes through the valve element 40f and communicates
with the interior of the bellows 40b, by opening and closing action
of the valve element 40f, wherein the bellows 40b is energized by a
coil spring 40j in a direction of expansion and contraction of the
bellows 40b, and the valve element 40f is energized toward a
direction of closing the valve port 40e by the energized force.
[0679] The first chamber 40c is connected to the channel 14A, the
second chamber 40d communicates with the inlet pipe 6 through the
channel 14D, and the interior of the bellows 40b communicates with
the outlet pipe 5 through the channel 14E.
[0680] In the following, an operation of the channel selector valve
according to the eleventh embodiment will be explained. The bellows
40b, into which the refrigerant is introduced from the outlet pipe
5 through the channel 14E, keeps its contracted state as long as a
differential pressure between the refrigerant in the bellows 40b
and the refrigerant in the second chamber 40d, which is introduced
from the inlet pipe 6 through the channel 14D, is equal to or lower
than the energizing force by the coil spring 40j, then the valve
element 40f keeps closing the valve port 40e, on the other hand,
when said differential pressure exceeds the energizing force by the
coil spring 40j, the bellows 40b expands and the valve element 40f
opens the valve port 40e.
[0681] Here, if a differential pressure of the refrigerant, which
exceeds the energizing force by the coil spring 40j, is defined as
a differential pressure threshold Pk, Pk is determined from a
relation with the energizing force by the coil spring 40j, however
usually, the differential pressure of the refrigerant is not set to
be Pk, that is, a usual differential pressure of the refrigerant is
kept to be lower than the energizing force by the coil spring
40j.
[0682] When the refrigerating cycle A is operated in the heating
mode, the differential pressure of the refrigerant is controlled to
be lower than the energizing force by the coil spring 40j, thereby
the valve element 40f closes the valve port 40e and the refrigerant
discharged from the compressor 4 is introduced into the
pressure-transducing chamber R.sub.2 through the outlet pipe 5, the
channel 14E, the interior of the bellows 40b, the pilot path 40g of
the valve element 40f, and the channel 14A, thereby the refrigerant
pressure in the high pressure chamber R.sub.1 is made to be equal
to the refrigerant pressure in the pressure-transducing chamber
R.sub.2, therefore the piston cylinder 12 is made situated at the
first position.
[0683] On the other hand, when the refrigerating cycle A is
operated in the cooling mode, the differential pressure of the
refrigerant is once controlled to be Pk that is higher than the
energizing force by the coil spring 40j, thereby the valve element
40f opens the valve port 40e due to the expansion of the bellows
40b and the pilot valve 40h closes the pilot path 40g, then the
pressure-transducing chamber R.sub.2 communicates with the inlet
pipe 6 through the channel 14A, the valve port 40e, the channel 14D
and then, the refrigerant pressure in the pressure-transducing
chamber R.sub.2 is made lower than the refrigerant pressure in the
high pressure chamber R.sub.1, thereby the piston cylinder 12 is
moved from the first position to the second position.
[0684] Once the piston cylinder 12 is moved to the second position,
thereafter, the piston cylinder 12 is kept staying at the second
position by the state-holding selector valve 29, therefore the
cooling mode is maintained even if the refrigerant pressure is
controlled to be lower than the energizing force by the coil spring
40j.
[0685] In order to control the refrigerant pressure to be the
differential pressure threshold Pk, the easiest method is to change
a heat-exchange capacity of the indoor heat exchanger 9A and the
outdoor heat exchanger 9B. For example, if an operation of an air
blower of the indoor heat exchanger 9A or the outdoor heat
exchanger 9B is halted, the thermal conduction therein is impeded
and the efficiency of heat exchange is decreased, as a result, the
refrigerant pressure increases while the pressure of the
refrigerant sucked into the compressor 4 is lowered, thereby the
differential pressure of the refrigerant is easily made to be
Pk.
[0686] The channel selector valve according to the eleventh
embodiment constructed as described above gives a similar effect
with that according to the ninth or tenth embodiment.
[0687] According to the eleventh embodiment, since a power for the
selection operation of the channel selector valve is obtained by
changing the differential pressure between the refrigerant in the
high pressure chamber R.sub.1 of the reversing valve housing 1 and
the refrigerant in the pressure-transducing chamber R.sub.2, due to
the change in the refrigerant pressure generated by the change in
the efficiency of heat exchange in the indoor heat exchanger 9A or
the outdoor heat exchanger 9B, therefore, similarly to the channel
selector valve according to the ninth or tenth embodiment, there is
no necessity of using an electrically-driven drive source such as
an electromagnetic solenoid, which has been explained in the prior
art section of the present specification.
[0688] In the following, a channel selector valve according to a
twelfth embodiment of the present invention, in which a selection
operation is performed by two three-way selector valves, will be
explained with reference to FIG. 32.
[0689] FIG. 32 is a view illustrating a schematic constitution of a
refrigerating cycle employing a channel selector valve according to
the twelfth embodiment of the present invention, in which the same
abbreviation numerals with those used for the corresponding
identical members or parts of the channel selector valve according
to the first embodiment shown in FIG. 1 are used.
[0690] The channel selector valve according to the twelfth
embodiment, a state in operation in the hearting mode of which is
shown in FIG. 32 by its sectional view, is different from the
channel selector valve according to the first embodiment shown in
FIG. 1 in points that a four-way selector valve is constituted by
two three-way selector valves, i.e. a first three-way selector
valve 41 and a second three-way selector valve 42, which are
connected in parallell to a series circuit comprising an indoor
heat exchanger 9A, a throttle 10 and an outdoor heat exchanger 9B
and that the two three-way selector valves, i.e. a first three-way
selector valve 41 and a second three-way selector valve 42 are
connected to a compressor 4.
[0691] As shown in FIG. 32, the first three-way selector valve 41
comprises a reversing valve housing 1 (corresponding to a housing),
an outlet pipe 5, pipe 7A and pipe 7B, which are connected to the
reversing valve housing 1, and a piston 41a (corresponding to a
movable member) that allows the outlet pipe 5 to communicate with
either the pipe 7A or the pipe 7B through the interior of the
reversing valve housing 1.
[0692] The reversing valve housing 1 of the first three-way
selector valve 41 has a cylindrical shape, in which a large
diameter cylinder 1a is sandwiched by two small diameter cylinders
1b and 1c, wherein the pipes 7A and 7B are connected to the small
diameter cylinder 1b and 1c, respectively, and the outlet pipe 5 is
connected to the large diameter cylinder 1a.
[0693] In the interior of the small diameter cylinders 1b and 1c,
there are provided bearings 41b and 41c, respectively, by which a
slide shaft 41d is supported rotatively and slidably in an axial
direction, in addition, there are provided channels 41e and 41f
passing through between each end of the bearings 41b and 41c,
respectively.
[0694] On a circumferential surface of the slide shaft 41d, there
are put stoppers 41g and 41h (for example, E-rings) in the axial
direction with leaving a space therebetween, then a coil spring 41j
(corresponding to second storing means for storing energizing
force) is provided between the stoppers 41g and the bearing 41b,
while a coil spring 41k (corresponding to first storing means for
storing energizing force) is provided between the stoppers 41h and
the bearing 41c, said coil springs 41j and 41k being put on the
slide shaft 41d.
[0695] The piston 41a is formed to have a diameter, which is larger
than that of the small diameter cylinders 1b and 1c but smaller
than that of the large diameter cylinder 1a, and is received in the
large diameter cylinder 1a. The piston 41a is put on the slide
shaft 41d so as to be slidable in the axial direction of the slide
shaft 41d between the stopper 41g and the stopper 41h, then there
is provided an O-ring 41m for sealing between the piston 41a and
the slide shaft 41d.
[0696] The outlet pipe 5 is connected to an outlet (not shown in
the figure) of the compressor 4, the pipe 7A is connected to the
indoor heat exchanger 9A while the pipe 8A is connected to the
outdoor heat exchanger 9B.
[0697] In the first three-way selector valve 41 thus formed, when a
force larger than an elastic force of the coil spring 41k is
applied on an end surface of the slide shaft 41d at the small
diameter cylinder 1b side, the slide shaft 41d moves toward the
small diameter cylinder 1c side.
[0698] Then, the piston 41a moves to the first position where the
piston 41a pushed by the stopper 41g closes a valve port 1e, which
is formed by a level difference between the large diameter cylinder
1a and the small diameter cylinder 1c, and opens a valve port 1d,
which is formed by a level difference between the large diameter
cylinder 1a and the small diameter cylinder 1b, thereby the outlet
pipe 5 communicates with the pipe 7A through the channel 41e of the
bearing 41b.
[0699] When the piston 41a is at the first position, the coil
spring 41k is pressed by the stopper 41h to be compressed, thereby
the coil spring 41k is in a state that the coil spring 41k stores
an energized force to move the slide shaft 41d toward the small
diameter cylinder 1b side.
[0700] Then, in a state shown in FIG. 32, if a force applied on the
end surface of the slide shaft 41d at the small diameter cylinder
1b side is removed, the stopper 41h is pushed by the elastic force
of the coil spring 41k so that the slide shaft 41d moves toward the
small diameter cylinder 1b side.
[0701] Then, by a sliding resistance between the O-ring 41m and the
slide shaft 41d, the piston 41a together with the slide shaft 41d
moves to the second position where the piston 41a opens the valve
port 1e and closes the valve port 1d, thereby the outlet pipe 5
communicates with the pipe 8A through the channel 41f of the
bearing 41c.
[0702] However, in a state that the slide shaft 41d merely moves
toward the small diameter cylinder 1b side by the elastic force of
the coil spring 41k, the piston 41a does not move with relation to
the slide shaft 41d, therefore, the piston 41a abuts on the stopper
41g and is apart from the stopper 41h, while the coil spring 41j
extends.
[0703] Then, when a force larger than the elastic force of the coil
spring 41j is applied on an end surface of the slide shaft 41d at
the small diameter cylinder 1c side, only the slide shaft 41d moves
toward the small diameter cylinder 1b side until the stopper 41h
abuts on the piston 41a, thereby the stopper 41g is apart from the
piston 41a toward the small diameter cylinder 1b side.
[0704] Then, the coil spring 41j is pressed by the stopper 41g to
be compressed, thereby the coil spring 41j is in a state that the
coil spring 41j stores an energized force to move the slide shaft
41d toward the small diameter cylinder 1c side.
[0705] Then, in this state, if a force applied on the end surface
of the slide shaft 41d at the small diameter cylinder 1c side is
removed, the slide shaft 41d moves toward the small diameter
cylinder 1c side by the elastic force of the coil spring 41j.
[0706] Then, by a sliding resistance between the O-ring 41m and the
slide shaft 41d, the piston 41a together with the slide shaft 41d
moves to the first position where the piston 41a closes the valve
port 1e and opens the valve port 1d, thereby the outlet pipe 5
communicates with the pipe 7A through the channel 41e of the
bearing 41b.
[0707] However, in a state that the slide shaft 41d merely moves
toward the small diameter cylinder 1c side by the elastic force of
the coil spring 41j, the piston 41a does not move with relation to
the slide shaft 41d, therefore, the piston 41a abuts on the stopper
41h and is apart from the stopper 41g, while the coil spring 41k
extends.
[0708] Then, when a force larger than the elastic force of the coil
spring 41k is applied on an end surface of the slide shaft 41d at
the small diameter cylinder 1b side, only the slide shaft 41d moves
toward the small diameter cylinder 1c side until the stopper 41g
abuts on the piston 41a, thereby the stopper 41h is apart from the
piston 41a toward the small diameter cylinder 1c side.
[0709] Then, the coil spring 41k is pressed by the stopper 41g to
be compressed, thereby the coil spring 41k comes back to the state
shown in FIG. 32, in which the coil spring 41k stores an energized
force to move the slide shaft 41d toward the small diameter
cylinder 1b side.
[0710] On the other hand, the second three-way selector valve 42
comprises a reversing valve housing 1 (corresponding to a housing),
an inlet pipe 6, pipe 7B and pipe 8B, which are connected to the
reversing valve housing 1, and two pistons 42a and 42b
(corresponding to a movable member) that allows the inlet pipe 6 to
communicate with either the pipe 7B or the pipe 8B through the
interior of the reversing valve housing 1.
[0711] The reversing valve housing 1 of the second three-way
selector valve 42 has a cylindrical shape, in which a small
diameter cylinder If is sandwiched by two large diameter cylinders
1g and 1h, wherein the pipes 7B and 8B are connected to the small
diameter cylinder 1g and 1h, respectively, and the inlet pipe 6 is
connected to the small diameter cylinder 1f.
[0712] In the reversing valve housing 1, there is provided a slide
shaft 42c movable in a thrust direction, on which stoppers 42d,
42e, 42f and 42g (for example, E-rings) are put in the axial
direction with leaving a space therebetween.
[0713] Each piston 42a and 42b is formed to have a diameter, which
is larger than that of the small diameter cylinder 1f but smaller
than that of the large diameter cylinders 1g and 1h, the pistons
42a and 42b are received in the large diameter cylinders 1g and 1h,
respectively. The piston 42a is put on the slide shaft 42c so as to
be slidable in the axial direction of the slide shaft 42c between
the stopper 42d and the stopper 42e, while the piston 42b is put on
the slide shaft 42c so as to be slidable in the axial direction of
the slide shaft 42c between the stopper 42f and the stopper
42g.
[0714] In the large diameter cylinder 1g, there is received a coil
spring 42h for energizing the piston 42a toward the large diameter
cylinder 1h side, while in the large diameter cylinder 1h, there is
received a coil spring 42j for energizing the piston 42b toward the
large diameter cylinder 1g side, wherein there are provided O-rings
42k and 42m for sealing between each piston 42a and 42b and the
slide shaft 42c.
[0715] The inlet pipe 6 is connected to a inlet (not shown in the
figure) of the compressor 4, the pipe 7B is connected to the indoor
heat exchanger 9A and the pipe 7A of the first three-way selector
valve 41, while the pipe 8B is connected to the outdoor heat
exchanger 9B and the pipe 8A of the first three-way selector valve
41.
[0716] In the second three-way selector valve 42 constructed as
described above, when a force stronger than an elestic force by the
coil spring 42j is applied to the slide shaft 42c from the large
diameter cylinder 1g side, the slide shaft 42c pushed by the
stopper 42d slides toward the large diameter cylinder 1h side.
[0717] Then, the piston 42b pushed by the stopper 42f moves to the
second position where the piston 42b opens a valve port 1m formed
by a level difference between the small diameter cylinder 1f and
the large diameter cylinder 1h, while the piston 42a moves to the
second position where the piston 42a closes a valve port 1k formed
by a level difference between the small diameter cylinder 1f and
the large diameter cylinder 1g by a sliding resistance between the
O-ring 42k and the slide shaft 42c, thereby the inlet pipe 6 is
communicated to the pipe 8B.
[0718] Then, at the second position of the piston 42a, the coil
spring 42j is pressed by the piston 42b to be compressed, thereby
the coil spring 42j is in a state that the coil spring 42j stores
an energized force to move the piston 42b toward the large diameter
cylinder 1g side.
[0719] Then, in the second three-way selector valve 42, in the
state shown in FIG. 32, if a force applied to the slide shaft 42c
from the large diameter cylinder 1g side is removed, the piston 42b
is pressed by the elastic force of the coil spring 42j and moves
toward the first position where the piston 42b closes the valve
port 1m, that is, the slide shaft 42c moves toward the large
diameter cylinder 1g side.
[0720] Then, until the slide shaft 42c is on a half way of moving
toward the large diameter cylinder 1g side, due to the sliding
resistance between the O-ring 42k and the slide shaft 42c, the
piston 42a together with the slide shaft 42c moves to the first
position where the piston 42a opens the valve port 1k, thereby the
inlet pipe 6 is communicated to the pipe 7B.
[0721] Then, in this state, if the slide shaft 42c moves further
toward the large diameter cylinder 1g side, an elastic force
stronger than the sliding resistance between the O-ring 42k and the
slide shaft 42c acts from the coil spring 42h to the piston 42a.
Due to this elastic force, the piston 42a stops at the first
position, while only the slide shaft 42c moves toward the large
diameter cylinder 1g side, then the stopper 42d that has abutted on
the piston 42a is away from the piston 42a, while the stopper 42e
that has been away from the piston 42a comes in contact with the
piston 42a.
[0722] In this state, if a force stronger than the elastic force by
the coil spring 42h is applied from the large diameter cylinder 1h
side to the slide shaft 42c, the piston 42a is pressed by the
stopper 42e to move toward the large diameter cylinder 1g side,
thereby the coil spring 42h is pressed by the piston 42a to be
compressed and the coil spring 42h is in a state that the coil
spring 42h stores the energizing force to move the piston 42a
toward the large diameter cylinder 1h side.
[0723] At the same time, since at the first position where the
piston 42b closes the valve port 1m the piston 42b is controlled
from moving further toward the large diameter cylinder 1g side, the
stopper 42f that has abutted on the piston 42b is away from the
piston 42b, while the stopper 42g that has been away from the
piston 42b comes in contact with the piston 42b.
[0724] In this state, if the force applied from the large diameter
cylinder 1h side to the slide shaft 42c is removed, the piston 42a
is pressed by the elastic force of the coil spring 42h, thereby the
piston 42a moves to the second position where where the piston 42a
closes the valve port 1k and the slide shaft 42c moves toward the
large diameter cylinder 1h side.
[0725] Then, until the slide shaft 42c is on a half way of moving
toward the large diameter cylinder 1h side, due to the sliding
resistance between the O-ring 42m and the slide shaft 42c, the
piston 42b together with the slide shaft 42c moves to the second
position where the piston 42b opens the valve port 1m, thereby the
inlet pipe 6 is communicated to the pipe 8B.
[0726] Then, in this state, if the slide shaft 42c moves further
toward the large diameter cylinder 1h side, an elastic force
stronger than the sliding resistance between the O-ring 42m and the
slide shaft 42c acts from the coil spring 42j to the piston 42b.
Due to this elastic force, the piston 42b stops at the second
position, while only the slide shaft 42c moves toward the large
diameter cylinder 1h side, then the stopper 42g that has abutted on
the piston 42b is away from the piston 42b, while the stopper 42f
that has been away from the piston 42b comes in contact with the
piston 42b.
[0727] In this state, if a force stronger than the elastic force by
the coil spring 42j is applied from the large diameter cylinder 1g
side to the slide shaft 42c, the piston 42b is pressed by the
stopper 42f to move toward the large diameter cylinder 1h side,
thereby the coil spring 42j is pressed by the piston 42b to be
compressed and the coil spring 42j is in a state that the coil
spring 42j stores the energizing force to move the piston 42b
toward the large diameter cylinder 1g side.
[0728] At the same time, since at the second position where the
piston 42a closes the valve port 1k the piston 42a is controlled
from moving further toward the large diameter cylinder 1h side, the
stopper 42e that has abutted on the piston 42a is away from the
piston 42a, while the stopper 42d that has been away from the
piston 42a comes in contact with the piston 42a, thereby coming
back to the state shown in FIG. 32.
[0729] In the following, an operation of the channel selector valve
according to the twelfth embodiment constructed as described above
will be explained.
[0730] When the operation of the compressor 4 is halted, the coil
springs 41j and 41k of the first three-way selector valve 41 as
well as the coil springs 42h and 42j of the second three-way
selector valve 42 are all extended and are in a state to have no
energizing force, that is, the piston 41a of the first three-way
selector valve 41 and the piston 42a of the second three-way
selector valve 42 are located at each same positions with those
during an ex-operation of the compressor 4.
[0731] In a state that the piston 41a of the first three-way
selector valve 41 is at the first position and the pistons 42a and
42b of the second three-way selector valve 42 are at their second
position, when the compressor 4 starts to operate, a high pressure
refrigerant discharged from the compressor 4 flows into the large
diameter cylinder 1a of the first three-way selector valve 41
through the outlet pipe 5 and then, further flows into the indoor
heat exchanger 9A through the valve port 1d, the channel 41e of the
bearing 41b and the pipe 7A.
[0732] Then, the refrigerant flowed into the indoor heat exchanger
9A flows into the pipe 8B of the second three-way selector valve 42
by way of the throttle 10, the outdoor heat exchanger 9B, and then,
flows back to the inlet of the compressor 4 by way of the valve
port 1m and the inlet pipe 6, thereby the refrigerating cycle A is
in the heating mode.
[0733] At this time, in the first three-way selector valve 41,
since the refrigerant pressure in the pipe 7A communicating with
the outlet of the compressor 4 is higher than that in the pipe 8A
communicating with the inlet of the compressor 4 through the second
three-way selector valve 42, the slide shaft 41d is pressed toward
the small diameter cylinder 1c side by a force stronger than the
elastic force of the coil spring 41k causing the coil spring 41k to
be compressed, thereby the coil spring 41k stores the energizing
force to energize the slide shaft 41d toward the small diameter
cylinder 1b side.
[0734] On the other hand, in the second three-way selector valve
42, since the refrigerant pressure in the pipe 7B communicating
with the outlet of the compressor 4 through the first three-way
selector valve 41 is higher than that in the pipe 8B communicating
with the inlet of the compressor 4, the slide shaft 42c is applied
by a force stronger than the elastic force of the coil spring 42j
from the large diameter cylinder 1g side, causing the piston 42b to
be pressed toward the large diameter cylinder 1h side and the coil
spring 42j to be compressed, thereby the coil spring 42j stores the
energizing force to energize the piston 42b toward the large
diameter cylinder 1g side.
[0735] Thereafter, when the operation of the compressor 4 is
halted, in the first three-way selector valve 41, the piston 41a
together with the slide shaft 41d moves toward the small diameter
cylinder 1b side by the energizing force stored in the coil spring
41k, thereby the piston 41a is situated at the second position.
[0736] On the other hand, in the second three-way selector valve
42, by the energizing force stored in the coil spring 42j, the
piston 42b moves toward the large diameter cylinder 1g side and is
situated at the first position, while the slide shaft 42c and the
piston 42a move together with the piston 42b, thereby the piston
42a is situated at the first position.
[0737] In this state, when the compressor 4 starts to operate, a
high pressure refrigerant discharged from the compressor 4 flows
into the large diameter cylinder 1a of the first three-way selector
valve 41 through the outlet pipe 5 and then, further flows into the
outdoor heat exchanger 9B through the valve port 1e, the channel
41f of the bearing 41c and the pipe 8A.
[0738] Then, the refrigerant flowed into the outdoor heat exchanger
9B flows into the pipe 7B of the second three-way selector valve 42
by way of the throttle 10, the indoor heat exchanger 9A, and then,
flows back to the inlet of the compressor 4 by way of the valve
port 1k and the inlet pipe 6, thereby the refrigerating cycle A is
in the cooling mode.
[0739] At this time, in the first three-way selector valve 41,
since the refrigerant pressure in the pipe 8A communicating with
the outlet of the compressor 4 is higher than that in the pipe 7A
communicating with the inlet of the compressor 4 through the second
three-way selector valve 42, the slide shaft 41d is pressed toward
the small diameter cylinder 1b side by a force stronger than the
elastic force of the coil spring 41j causing the coil spring 41j to
be compressed, thereby the coil spring 41j stores the energizing
force to energize the slide shaft 41d toward the small diameter
cylinder 1c side.
[0740] On the other hand, in the second three-way selector valve
42, since the refrigerant pressure in the pipe 8B communicating
with the outlet of the compressor 4 through the first three-way
selector valve 41 is higher than that in the pipe 7B communicating
with the inlet of the compressor 4, the slide shaft 42c is applied
by a force stronger than the elastic force of the coil spring 42h
from the large diameter cylinder 1h side, causing the piston 42a to
be pressed toward the large diameter cylinder 1g side and the coil
spring 42h to be compressed, thereby the coil spring 42h stores the
energizing force to energize the piston 42a toward the large
diameter cylinder 1h side.
[0741] Thereafter, when the operation of the compressor 4 is
halted, in the first three-way selector valve 41, the piston 41a
together with the slide shaft 41d moves toward the small diameter
cylinder 1c side by the energizing force stored in the coil spring
41j, thereby the piston 41a is situated at the first position.
[0742] On the other hand, in the second three-way selector valve
42, by the energizing force stored in the coil spring 42h, the
piston 42a moves toward the large diameter cylinder 1h side and is
situated at the second position, while the slide shaft 42c and the
piston 42b move together with the piston 42a, thereby the piston
42b is situated at the second position.
[0743] Thus, according to the twelfth embodiment, the four-way
selector valve, which selects the channel of the refrigerant in the
refrigerating cycle A, is constituted by the first three-way
selector valve 41 and the second three-way selector valve 42, which
select a path of the refrigerant upon halting of the operation of
the compressor 4 by using the energizing force that is stored
during the operation of the compressor 4.
[0744] Therefore, the heating mode, in which the refrigerant
discharged from the outlet pipe 5 is supplied to the indoor heat
exchanger 9A by way of the pipe 7A of the first three-way selector
valve 41, and the cooling mode, in which the refrigerant discharged
from the outlet pipe 5 is supplied to the outdoor heat exchanger 9B
by way of the pipe 8A of the first three-way selector valve 41, can
be selected by controlling the number of times of the operation
start of the compressor 4 and the selected state can be maintained
without using any exclusive power source such as an electromagnetic
solenoid.
[0745] Moreover, according to the twelfth embodiment, since the
selection of communication for the outlet pipe 5 of the first
three-way selector valve 41 and the inlet pipe 6 of the second
three-way selector valve 42 is performed according to a start and
halt of the operation of the compressor 4, neither power source for
an electric drive nor control by an electric signal for selecting
the channel of the refrigerant is needed, therefore, the channel
selector valve according to the twelfth embodiment is
advantageous.
[0746] In the following, a channel selector valve according to a
thirteenth embodiment of the present invention, in which a
selection operation is performed by a four-way selector valve that
uses a three-way selector valve as a pilot valve thereof, will be
explained with reference to FIG. 33.
[0747] FIG. 33 is a view illustrating a schematic constitution of a
refrigerating cycle A employing the channel selector valve
according to the thirteenth embodiment of the present invention, in
which the same abbreviation numerals with those used for the
corresponding identical members or parts of the channel selector
valve according to the third embodiment shown in FIG. 6 are
used.
[0748] The channel selector valve according to the thirteenth
embodiment, an operational state of which in the heating mode is
shown by a sectional view in FIG. 33, comprises a slide-type
four-way selector valve 43 and a three-way selector valve
(corresponding to the pilot valve) 44 that functions as a pilot
valve for the slide-type four-way selector valve 43.
[0749] The slide-type four-way selector valve 43 is different from
the channel selector valve according to the third embodiment shown
in FIG. 6 in points that a second piston cylinder 12' forming a
second pressure-transducing chamber (corresponding to the third
pressure chamber) R.sub.5, which faces a pressure-transducing
chamber R.sub.2 with putting a high pressure chamber R.sub.1
therebetween, is provided between a valve seat 11 and a stopper 2
in a reversing valve housing 1, that a second connecting shaft 28'
connects a slide valve 27 to the second piston cylinder 12', and
that the compression spring 13, which energizes a piston cylinder
12 to move from the second position toward the first position, is
omitted.
[0750] In the slide-type four-way selector valve 43, there are
provided a through hole (corresponding to the first equalizing
path) 12.sub.1 in the piston cylinder 12 and a second through hole
(corresponding to the second equalizing path) 12.sub.1' in the
second piston cylinder 12'. The high-pressure chamber R.sub.1
always communicates with the second pressure-transducing chamber
R.sub.5 through the second through hole 12.sub.1'.
[0751] One end of a channel 14F is connected to an inlet pipe 6
that is connected to an inlet of the compressor 4, then a valve
seat 2a is formed on the stopper 2 to which one end of a channel
14G is connected from the outside, while a valve seat 3a is formed
on a stopper 3 to which one end of a channel 14H is connected from
the outside.
[0752] In the piston cylinder 12, there is provided a subvalve
(correspondong to the first subvalve) 12.sub.2, which is apart from
the valve seat 3a of the stopper 3 when the piston cylinder 12 is
at the first position as shown in FIG. 33 and communiates the
channel 14H to the pressure-transducing chamber R.sub.2, while in
the second piston cylinder 12' there is provided a second subvalve
12.sub.2', which sits on the valve seat 2a of the stopper 2 when
the piston cylinder 12 is at the first position as shown in FIG. 33
and makes the channel 14G insulated from the second
pressure-transducing chamber R.sub.5.
[0753] To the contrary, when the piston cylinder 12 is at the
second position, that is, the inlet pipe 6 communicates with the
pipe 7 through a closed space S1 while the outlet pipe 5
communicates with the pipe 8 through a high pressure space S2, the
subvalve 12.sub.2 sits on the valve seat 3a of the stopper 3 so as
to make the channel 14H insulated from the pressure-transducing
chamber R.sub.2 while the second subvalve 12.sub.2' is apart from
the valve seat 2a of the stopper 2 so as to communicate the channel
14G to the second pressure-transducing chamber R.sub.5.
[0754] In the slide-type four-way selector valve 43, the piston
cylinder 12 and the second piston cylinder 12' constitute the
movable member described in the claims.
[0755] The three-way selector valve 44 is provided outside of the
slide-type four-way selector valve 43 and comprises a housing
(corresponding to the second housing) 44a, to which each end of the
channels 14F, 14G and 14H is connected, and two pistons
(corresponding to the selector valve element) 44b and 44c, which
make the channel 14F communicate with either the channel 14G or the
channel 14H by a selector operation.
[0756] The housing 44a has a cylindrical shape, in which a small
diameter cylinder 1f is sandwiched by two large diameter cylinders
1g and 1h, to which each opposite end of the channels 14H and 14G
are connected, respectively, while the channel 14F is connected to
the small diameter cylinder 1f.
[0757] In the housing 44a, there is provided a slide shaft 44d
movable in a thrust direction, on which stoppers 44e, 44f, 44g and
44h (for example, E-rings) are put in the axial direction with
leaving a space therebetween.
[0758] An outer diameter of each of pistons 44b and 44c is formed
larger than an inner diameter of the small diameter cylinder 1f and
smaller than an inner diameter of the large diameter cylinder 1g
and 1h, the pistons 44b and 44c are received in the large diameter
cylinders 1g and 1h, respectively. The pistons 44b and 44c are
attached to the slide shaft 44d so that the piston 44b can slide in
an axial direction of the slide shaft 44d between the stoppers 44e
and 44f, while the piston 44c can slide in an axial direction of
the slide shaft 44d between the stoppers 44g and 44h.
[0759] A coil spring 44j, which energizes the slide shaft 44d
toward the large diameter cylinder 1h side through the stopper 44e,
is received in the large diameter cylinder 1g, while a coil spring
44k, which energizes the slide shaft 44d toward the large diameter
cylinder 1g side through the stopper 44h, is received in the large
diameter cylinder 1h. O-rings 44m and 44n for sealing are provided
between the slide shaft 44d and the pistons 44b and 44c,
respectively.
[0760] In the large diameter cylinder 1g, there is provided a
ring-shaped stopper 44p, an inner diameter of which is larger than
an outer diameter of the stopper 44e and smaller than an outer
diameter of the piston 44b, while in the large diameter cylinder
1h, there is provided a ring-shaped stopper 44r, an inner diameter
of which is larger than an outer diameter of the stopper 44h and
smaller than an outer diameter of the piston 44c.
[0761] As shown in FIG. 33, in the stopper 44r there is provided a
through hole 44t that allows the both sides of the stopper 44r to
communicate with each other when the piston 44c abuts on the
stopper 44r, likewise a the stopper 44p is provided with a through
hole 44s.
[0762] In the three-way selector valve 44 thus constructed, when a
force stronger than an elastic force of the coil spring 44k is
applied to the slide shaft 44d from the large diameter cylinder 1g
side, the slide shaft 44d slides toward the large diameter cylinder
1h side.
[0763] Then, the piston 44c is pushed by the stopper 44g to open a
valve port 1m formed by a level difference between the small
diameter cylinder 1f and the large diameter cylinder 1h and moves
to the second position where the piston 44c abuts on the stopper
44r, while the piston 44b is pushed by the stopper 44e to close a
valve port 1k formed by a level difference between the small
diameter cylinder 1f and the large diameter cylinder 1g and moves
to the second position where the piston 44b is apart from the
stopper 44p, thereby the channel 14F communicates with the channel
14G through the small diameter cylinder 1f, the large diameter
cylinder 1h and the through hole 44t of the stopper 44r.
[0764] When the piston 44b is situated at the second position, the
coil spring 44k is pressed by the stopper 44h to be compressed,
then the coil spring 44k is in a state to store an energizing force
to slide the stopper 44h toward the large diameter cylinder 1g
side.
[0765] As to the three-way selector valve 44, in a state shown in
FIG. 33, if a force applied to the slide shaft 44d from the large
diameter cylinder 1g side is removed, the slide shaft 44d is pushed
by the elastic force of the coil spring 44k through the stopper 44h
to move toward the large diameter cylinder 1g side, thereby the
piston 44c together with the slide shaft 44d closes the valve port
1m by a sliding resistance between the O-ring 44n and the slide
shaft 44d and moves to the first position where the piston 44c is
apart from the stopper 44r.
[0766] While, by a sliding resistance between the O-ring 44m and
the slide shaft 44d that moves toward the large diameter cylinder
1g side, the piston 44b together with the slide shaft 44d opens the
valve port 1k and moves to the first position where the piston 44b
abuts on the stopper 44p, thereby the channel 14F communicates with
the channel 14H through the small diameter cylinder 1f, the large
diameter cylinder 1g and the through hole 44s of the stopper
44p.
[0767] However, in a state that the slide shaft 44d only has slided
toward the large diameter cylinder 1g side by the elastic force of
the coil spring 44k, the pistons 44b and 44c do not move relatively
with respect to the slide shaft 44d, therefore the piston 44b abuts
on the stopper 44e to be apart from the stopper 44f while the
piston 44c abuts on the stopper 44g to be apart from the stopper
44h.
[0768] In this state, if a force stronger than the elastic force of
the coil spring 44j is applied to the slide shaft 44d from the
large diameter cylinder 1h side, the slide shaft 44d further moves
toward the large diameter cylinder 1g side, thereby the coil spring
44j is pressed by the stopper 44e to be compressed and is in a
state to store the energizing force to move the stopper 44e toward
the large diameter cylinder 1h side.
[0769] At this time, since the piston 44c, situated at the first
position where the puston 44c closes the valve port 1m, is
controlled to move further toward the large diameter cylinder 1g
side, the stopper 44g that has abutted on the piston 44c is away
from the piston 44c, while the stopper 44h that has been away from
the piston 44c abuts on the piston 44c.
[0770] Then, in this state, if a force applied to the slide shaft
44d from the large diameter cylinder 1h side is removed, the slide
shaft 44d is pushed by the elastic force of the coil spring 44j
through the stopper 44e to move toward the large diameter cylinder
1h side, thereby the piston 44b together with the slide shaft 44d
closes the valve port 1k by a sliding resistance between the O-ring
44m and the slide shaft 44d and moves to the second position where
the piston 44b is apart from the stopper 44p.
[0771] While, by a sliding resistance between the O-ring 44n and
the slide shaft 44d that moves toward the large diameter cylinder
1h side, the piston 44c together with the slide shaft 44d opens the
valve port 1m and moves to the second position where the piston 44c
abuts on the stopper 44r, thereby the channel 14F communicates with
the channel 14G through the small diameter cylinder 1f, the large
diameter cylinder 1h and the through hole 44t of the stopper
44r.
[0772] However, in a state that the slide shaft 44d only has slided
toward the large diameter cylinder 1h side by the elastic force of
the coil spring 44j, the pistons 44b and 44c do not move relatively
with respect to the slide shaft 44d, therefore the piston 44b abuts
on the stopper 44f to be apart from the stopper 44e while the
piston 44c abuts on the stopper 44h to be apart from the stopper
44g.
[0773] In this state, if a force stronger than the elastic force of
the coil spring 44k is applied to the slide shaft 44d from the
large diameter cylinder 1g side, the slide shaft 44d further moves
toward the large diameter cylinder 1h side, thereby the coil spring
44k is pressed by the stopper 44h to be compressed and is in a
state to store the energizing force to move the stopper 44h toward
the large diameter cylinder 1g side.
[0774] At this time, since the piston 44b, situated at the second
position where the puston 44b closes the valve port 1k, is
controlled to move further toward the large diameter cylinder 1h
side, the stopper 44f that has abutted on the piston 44b is away
from the piston 44b, while the stopper 44e that has been away from
the piston 44b abuts on the piston 44b, thereby coming back to the
state shown in FIG. 33.
[0775] As to the slide-type four-way selector valve 43, a permanent
magnet M is disposed at an inner bottom of the second piston
cylinder 12', then a hall device H is disposed at an outer
circumferential bottom of the reversing valve housing 1 near the
pipe 8. When the piston cylinder 12 and the piston cylinder 12'
(the movable member) are at the first position, a magnetic field
due to the permanent magnet M is not detected by the hall device H,
on the other hand, when the piston cylinder 12 and the piston
cylinder 12' are at the second position, a magnetic field due to
the permanent magnet M is detected by the hall device H. A signal
detected by the hall device H is inputted into a detecting element
C3 of a controller C (described later) in FIG. 62, by which it is
detected whether the piston cylinder 12 and the second piston
cylinder 12' are situated at the first position or the second
position.
[0776] In the following, an operation of the channel selector valve
according to the thirteenth embodiment constructed as described
above will be explained.
[0777] When the operation of the compressor 4 is halted, the piston
cylinder 12 and the second piston cylinder 12' of the slide-type
four-way selector valve 43 keep their positions during an
ex-operation of the compressor 4, while the pistons 44b and 44c
have moved to the second position if they were at the first
position during an ex-operation of the compressor 4, on the other
hand the pistons 44b and 44c have moved to the first position if
they were at the second position during an ex-operation of the
compressor 4.
[0778] As shown in FIG. 33, in a state that the refrigerating cycle
A is in the heating mode, if the operation of the compressor 4 is
halted, the piston cylinder 12 of the slide-type four-way selector
valve 43 does not move and stays at the first position shown in
FIG. 33, while the pistons 44b and 44c of the three-way selector
valve 44 move from the second position shown in FIG. 33 to the
first position since the force applied to the slide shaft 44d from
the large diameter cylinder 1g is removed.
[0779] Therefore, the small diameter cylinder 1f of the three-way
selector valve 44, which communicates with the inlet pipe 6 through
the channel 14F, communicates with the large diameter cylinder 1g
through the valve port 1k, which is opened by the piston 44b
situated at the first position, while the large diameter cylinder
1g communicates with the pressure-transducing chamber R.sub.2 of
the slide-type four-way selector valve 43 through the valve seat 3a
that is opend by the subvalve 12.sub.2 and the channel 14H, thereby
the inlet pipe 6 communicates with the pressure-transducing chamber
R.sub.2 through the three-way selector valve 44.
[0780] In this state, if the compressor 4 starts to operate, the
high pressure refrigerant discharged from the compressor 4 flows
into the high pressure space S2 of the slide-type four-way selector
valve 43 by way of the outlet pipe 5, then further flows into the
indoor heat exchanger 9A through the pipe 7 and then, this
refrigerant flows into the closed space S1 through the throttle 10,
the outdoor heat exchanger 9B and the pipe 8, then flows back to
the inlet of the compressor 4 by way of the inlet pipe 6, thereby
the refrigerating cycle A is in the heating mode.
[0781] At this time, since an amount of the refrigerant that can
pass through the through hole 12.sub.1 of the piston cylinder 12 is
small, an increment in the pressure of the refrigerant in the
pressure-transducing chamber R.sub.2 of the slide-type four-way
selector valve 43 upon starting of the operation of the compressor
4 is small, therefore a differnce in the pressure between the
refrigerant in the pressure-transducing chamber R.sub.2
communicating with the inlet pipe 6 through the three-way selector
valve 44 and the refrigerant in the high pressure space S2 becomes
large.
[0782] Therefore, the piston cylinder 12 and the second piston
cylinder 12' of the slide-type four-way selector valve 43 move from
the first position shown in FIG. 33 to the second position, the
high pressure refrigerant that is discharged from the compressor 4
and flowed into the high pressure space S2 by way of the outlet
pipe 5 flows into the outdoor heat exchanger 9B through the pipe 8
and then, this refrigerant flows back to the inlet of the
compressor 4 by way of the throttle 10, the indoor heat exchanger
9A, the pipe 7, closed space S1 and the inlet pipe 6, thereby the
refrigerating cycle A is in the cooling mode.
[0783] At this time, in the slide-type four-way selector valve 43,
accompanying with that the piston cylinder 12 and the second piston
cylinder 12' move to the second position, the subvalve 12.sub.2
closes the valve seat 3a that has been opened while the second
subvalve 12.sub.2' opens the valve seat 2a that has been closed,
therefore by the high pressure refrigerant flowed from the high
pressure space S2 through the through hole 12.sub.1' of the second
piston cylinder 12', the refrigerant pressure in the second
pressure-transducing chamber R.sub.5 gradually increases.
[0784] Then, in the three-way selector valve 44, since the pressure
of the refrigerant in the large diameter cylinder 1h that
communiates with the second pressure-transducing chamber R.sub.5
through the valve seat 2a opened by the second subvalve 12.sub.2'
and the channel 14G is higher than that in the small diameter
cylinder 1f that communicates with the inlet pipe 6 through the
channel 14F, due to a difference between the pressure of the
refrigerant in the large diameter cylinder 1g and that in the large
diameter cylinder 1h, a force stronger than the elastic force of
the coil spring 44j is applied to the slide shaft 44d from the
large diameter cylinder 1h side.
[0785] Accordingly, the slide shaft 44d moves toward the large
diameter cylinder 1g side, then the coil spring 44j is compressed
and stores the energizing force to energize the piston 44c toward
the large diameter cylinder 1h side.
[0786] Thereafter, when the operation of the compressor 4 is
halted, in the three-way selector valve 44, due to the energizing
force stored in the coil spring 44j, the pistons 44b and 44c
together with the slide shaft 44d move toward the large diameter
cylinder 1h side to be situated at the second position, while in
the slide-type four-way selector valve 43, the piston cylinder 12
and the second piston cylinder 12' are kept staying at their second
position.
[0787] Then, the small diameter cylinder 1f of the three-way
selector valve 44 communicating with the inlet pipe 6 through the
channel 14F communicates with the large diameter cylinder 1h
through the valve port 1m that is opend by the piston 44b situated
at the second position. The large diameter cylinder 1h communicates
with the the second pressure-transducing chamber R.sub.5 of the
slide-type four-way selector valve 43 through the valve seat 2a
opend by the second subvalve 12.sub.2' and the channel 14G, thereby
the inlet pipe 6 communicates with the second pressure-transducing
chamber R.sub.5 through the three-way selector valve 44.
[0788] In this state, if the compressor 4 starts to operate, the
high pressure refrigerant discharged from the compressor 4 flows
into the high pressure space S2 of the slide-type four-way selector
valve 43 by way of the outlet pipe 5, then further flows into the
outdoor heat exchanger 9B through the pipe 8 and then, this
refrigerant flows into the closed space S1 through the throttle 10,
the indoor heat exchanger 9A and the pipe 7, then flows back to the
inlet of the compressor 4 by way of the inlet pipe 6, thereby the
refrigerating cycle A is in the cooling mode.
[0789] At this time, since an amount of the refrigerant that can
pass through the through hole 12.sub.1' of the second piston
cylinder 12' is small, an increment in the pressure of the
refrigerant in the second pressure-transducing chamber R.sub.5 of
the slide-type four-way selector valve 43 upon starting of the
operation of the compressor 4 is small, therefore a differnce in
the pressure between the refrigerant in the second
pressure-transducing chamber R.sub.5 communicating with the inlet
pipe 6 through the three-way selector valve 44 and the refrigerant
in the high pressure space S2 becomes large.
[0790] Therefore, the piston cylinder 12 and the second piston
cylinder 12' of the slide-type four-way selector valve 43 move from
the second position to the first position shown in FIG. 33, the
high pressure refrigerant that is discharged from the compressor 4
and flowed into the high pressure space S2 by way of the outlet
pipe 5 flows into the indoor heat exchanger 9A through the pipe 7
and then, this refrigerant flows back to the inlet of the
compressor 4 by way of the throttle 10, the outdoor heat exchanger
9B, the pipe 8, closed space S1 and the inlet pipe 6, thereby the
refrigerating cycle A is in the heating mode.
[0791] At this time, in the slide-type four-way selector valve 43,
accompanying with that the piston cylinder 12 and the second piston
cylinder 12' move to the first position, the subvalve 12.sub.2
opens the valve seat 3a that has been closed while the second
subvalve 12.sub.2' closes the valve seat 2a that has been opened,
therefore by the high pressure refrigerant flowed from the high
pressure space S2 through the through hole 12.sub.1 of the piston
cylinder 12, the refrigerant pressure in the pressure-transducing
chamber R.sub.2 gradually increases.
[0792] Then, in the three-way selector valve 44, since the pressure
of the refrigerant in the large diameter cylinder 1g that
communiates with the pressure-transducing chamber R.sub.2 through
the valve seat 3a opened by the second subvalve 12.sub.2 and the
channel 14H is higher than that in the small diameter cylinder 1f
that communicates with the inlet pipe 6 through the channel 14F,
due to a difference between the pressure of the refrigerant in the
large diameter cylinder 1g and that in the large diameter cylinder
1h, a force stronger than the elastic force of the coil spring 44k
is applied to the slide shaft 44d from the large diameter cylinder
1g side.
[0793] Accordingly, the slide shaft 44d moves toward the large
diameter cylinder 1h side, then the coil spring 44k is compressed
and stores the energizing force to energize the piston 44b toward
the large diameter cylinder 1g side.
[0794] Thereafter, when the operation of the compressor 4 is
halted, in the three-way selector valve 44, due to the energizing
force stored in the coil spring 44k, the pistons 44b and 44c
together with the slide shaft 44d move toward the large diameter
cylinder 1g side to be situated at the first position, while in the
slide-type four-way selector valve 43, the piston cylinder 12 and
the second piston cylinder 12' are kept staying at the first
position.
[0795] Thus, according to the thirteenth embodiment, the slide-type
four-way selector valve 43, which makes the piston cylinder 12 and
the second piston cylinder 12' select to be either the first
position or the second position by using a difference between the
pressure of the refrigerant in the high pressure space S2 and that
in either the pressure-transducing chamber R.sub.2 or the second
pressure-transducing chamber R.sub.5, performs its selector
operation by using the three-way selector valve 44, which makes the
inlet pipe 6 communicate with either the pressure-transducing
chamber R.sub.2 or the second pressure-transducing chamber R.sub.5
by using the energizing force stored during the operation of the
compressor 4.
[0796] Therefore, the heating mode, in which the refrigerant
discharged from the outlet pipe 5 is supplied to the indoor heat
exchanger 9A by way of the pipe 7, and the cooling mode, in which
the refrigerant discharged from the outlet pipe 5 is supplied to
the outdoor heat exchanger 9B by way of the pipe 8, can be selected
by controlling the number of times of the operation start of the
compressor 4 and the selected state can be maintained without using
any exclusive power source such as an electromagnetic solenoid.
[0797] Moreover, according to the thirteenth embodiment, since the
selection of communication for the outlet pipe 5 and the inlet pipe
6 of the slide-type four-way selector valve 43 is performed
according to a start and halt of the operation of the compressor 4,
neither power source for an electric drive nor control by an
electric signal for selecting the channel of the refrigerant is
needed, therefore, the channel selector valve according to the
thirteenth embodiment is advantageous.
[0798] In the thirteenth embodiment described above, the present
invention is applied to the slide-type four-way selector valve 43,
in which the through holes 12.sub.1 and 12.sub.1' are provided in
the piston cylinder 12 and the second piston cylinder 12',
respectively. Instead, the present invention can also be applied to
a slide-type four-way selector valve, in which no through hole is
provided in the piston cylinder.
[0799] In the following, such a channel selector valve mentioned
right above according to a fourteenth embodiment of the present
invention will be explained with reference to FIG. 34.
[0800] FIG. 34 is a view illustrating a schematic constitution of a
refrigerating cycle A employing the channel selector valve
according to the fourteenth embodiment of the present invention, in
which the same abbreviation numerals with those used for the
corresponding identical members or parts of the channel selector
valve according to the thirteenth embodiment shown in FIG. 33 are
used.
[0801] The channel selector valve according to the fourteenth
embodiment, an operational state in the cooling mode of which is
shown in FIG. 34 by its sectional view, is different from the
channel selector valve according to the thirteenth embodiment shown
in FIG. 33 in points that the through holes 12.sub.1 and 12.sub.1'
in the piston cylinder 12 and the second piston cylinder 12',
respectively, are omitted in the slide-type four-way selector valve
43 and that the subvalves 12.sub.2 and 12.sub.2' are also omitted
in the slide-type four-way selector valve 43.
[0802] Moreover, the channel selector valve according to the
fourteenth embodiment is different from the channel selector valve
according to the thirteenth embodiment shown in FIG. 33 in points
that a three-way selector valve (corresponding to the pilot valve)
45, which functions as a pilot valve of the slide-type four-way
selector valve 43, is provided instead of the three-way selector
valve 44.
[0803] The three-way selector valve 45 comprises a housing
(corresponding to the second housing) 45a, to which each one end of
channels 14F, 14G and 14H is connected, and a piston (corresponding
to the selector valve element) 45r, which makes the channel 14F
communicate with either the channel 14G or the channel 14H.
[0804] The housing 45a has a cylindrical shape, in which a large
diameter cylinder 45b is sandwiched by two small diameter cylinders
45c and 45d, and a slide shaft 45e is received in the housing 45a
so as to be movable in a thrust direction.
[0805] In the small diameter cylinder 45c, there is received a coil
spring (corresponding to fourth storing means for storing
energizing force) 45f, which energizes the slide shaft 45e toward
the small diameter cylinder 45d side, while in the small diameter
cylinder 45d, there is received a coil spring (corresponding to
third storing means for storing energizing force) 45g, which
energizes the slide shaft 45e toward the small diameter cylinder
45c side.
[0806] On a circumferential surface of the slide shaft 45e, there
are formed circular grooves 45h and 45j leaving a space
therebetween in an axial direction, then one end surface of the
slide shaft 45e communicates with the circular groove 45h near said
one end surface through a channel 45k formed in the slide shaft
45e, while an opposite end surface of the slide shaft 45e
communicates with the circular groove 45j near said opposite end
surface through a channel 45m formed in the slide shaft 45e.
[0807] In addition, between the circular grooves 45h and 45j of the
slide shaft 45e, stoppers 45n and 45p, such as E-rings, are put on
the slide shaft 45e leaving a space therebetween in an axial
direction.
[0808] An outer diameter of the piston 45r is formed larger than an
inner diameter of the small diameter cylinders 45c and 45d and
smaller than an inner diameter of the large diameter cylinder 45b.
The piston 45r is received in the large diameter cylinder 45b and
attached to the slide shaft 45e so that the piston 45r can slide in
an axial direction of the slide shaft 45e between the stoppers 45n
and 45p.
[0809] Between the piston 45r and the slide shaft 45e, there is
provided an O-ring 45s for sealing.
[0810] Each opposite end of the channels 14G and 14H is connected
to the respective small diameter cylinders 45c and 45d of the
housing 45a so that each opening of the channels 14G and 14H faces
the respective end surfaces of the slide shaft 45e, in addition,
each opposite end of the channel 14F that is branched off into two
ways is connected to the respective small diameter cylinders 45c
and 45d of the housing 45a so that each opening of the branched
channels faces the circumferential surface of the slide shaft 45e,
while an outlet pipe 5 of the slide-type four-way selector valve 43
is connected to the large diameter cylinder 45b through the channel
14J.
[0811] In the three-way selector valve 45 thus constructed, as
shown in FIG. 34, when a force stronger than an elastic force by a
coil spring 45g is applied to an end surface of the slide shaft 45e
at the small diameter cylinder 45c side, the slide shaft 45e moves
toward the small diameter cylinder 45d side.
[0812] Then, the piston 45r is pushed by the stopper 45n to close a
valve port 45v formed by a level difference between the small
diameter cylinder 45d and the large diameter cylinder 45b and moves
to the second position where the piston 45r opens a valve port 45t
formed by a level difference between the small diameter cylinder
45c and the large diameter cylinder 45b, thereby the channel 14J
communicates with the channel 14H through the large diameter
cylinder 45b, the valve port 45t and the small diameter cylinder
45c.
[0813] When the piston 45r is at the second position, the opening
of the channel 14F connected to the small diameter cylinder 45c is
closed by the circumferential surface of the slide shaft 45e,
thereby the channel 14F connected to the small diameter cylinder
45c is insulated from the channel 14H, while the opening of the
channel 14F connected to the small diameter cylinder 45d faces the
circular groove 45j of the slide shaft 45e, thereby the channel 14F
connected to the small diameter cylinder 45d communicates with the
channel 14G through the circular groove 45j and the channel
45m.
[0814] When the piston 45r is at the second position, the coil
spring 45g is pushed by the end surface of the slide shaft 45e at
the small diameter cylinder 45d side to be compressed and is in a
state to store an enrgizing force to move the slide shaft 45e
toward the small diameter cylinder 45c side.
[0815] In a state of the three-way selector valve 45 shown in FIG.
34, when the force applied to the end surface of the slide shaft
45e at the small diameter cylinder 45c side is removed, the slide
shaft 45e is pressed by the elastic force of the coil spring 45g
and moves toward the small diameter cylinder 45c side.
[0816] Then, by a sliding resistance between the O-ring 45s and the
slide shaft 45e, the piston 45r together with the slide shaft 45e
moves to the first position where the piston 45r opens the valve
port 45v and closes the valve port 45t, thereby the channel 14J
communicates with the channel 14G through the large diameter
cylinder 45b, the valve port 45v and the small diameter cylinder
45d.
[0817] When the piston 45r is at the first position, the opening of
the channel 14F connected to the small diameter cylinder 45c faces
the circular groove 45h of the slide shaft 45e, thereby the channel
14F connected to the small diameter cylinder 45c communicates with
the channel 14H through the circular groove 45h and the channel
45k, while the opening of the channel 14F connected to the small
diameter cylinder 45d is closed by the circumferential surface of
the slide shaft 45e, thereby the channel 14F connected to the small
diameter cylinder 45d is insulated from the channel 14G.
[0818] However, in a state that the slide shaft 45e only has slided
toward the small diameter cylinder 45c side by the elastic force of
the coil spring 45g, the piston 45r does not move relatively with
respect to the slide shaft 45e, therefore the piston 45r abuts on
the stopper 45n to be apart from the stopper 45p while the coil
spring 45f in the small diameter cylinder 45c is extended.
[0819] Then, in this state, if a force stronger than the elastic
force by the coil spring 45f is applied to the end surface of the
slide shaft 45e at the small diameter cylinder 45d side, only the
slide shaft 45e further moves toward the small diameter cylinder
45c side until the stopper 45p abuts on the piston 45r, thereby the
stopper 45n is away from the piston 45r toward the small diameter
cylinder 45c side.
[0820] Then, the coil spring 45f is pushed by the end surface of
the slide shaft 45e at the small diameter cylinder 45c side to be
compressed and is in a state to store an enrgizing force to move
the slide shaft 45e toward the small diameter cylinder 45d
side.
[0821] In this state, if the force that has been applied to the end
surface of the slide shaft 45e at the small diameter cylinder 45d
side is removed, the slide shaft 45e moves toward the small
diameter cylinder 45d side by the elastic force of the coil spring
45f.
[0822] Then, by a sliding resistance between the O-ring 45s and the
slide shaft 45e, the piston 45r together with the slide shaft 45e
moves to the second position where the piston 45r closes the valve
port 45v and opens the valve port 45t, thereby the channel 14J
communicates with the channel 14H through the large diameter
cylinder 45b, the valve port 45t and the small diameter cylinder
45c.
[0823] When the piston 45r is at the second position, the opening
of the channel 14F connected to the small diameter cylinder 45c is
closed by the circumferential surface of the slide shaft 45e,
thereby the channel 14F connected to the small diameter cylinder
45c is insulated from the channel 14H, while the opening of the
channel 14F connected to the small diameter cylinder 45d faces the
circular groove 45j of the slide shaft 45e, thereby the channel 14F
connected to the small diameter cylinder 45d communicates with the
channel 14G through the circular groove 45j and the channel
45m.
[0824] However, in a state that the slide shaft 45e only has slided
toward the small diameter cylinder 45d side by the elastic force of
the coil spring 45f, the piston 45r does not move relatively with
respect to the slide shaft 45e, therefore the piston 45r abuts on
the stopper 45p to be apart from the stopper 45n while the coil
spring 45g in the small diameter cylinder 45d is extended.
[0825] Then, in this state, if a force stronger than the elastic
force by the coil spring 45g is applied to the end surface of the
slide shaft 45e at the small diameter cylinder 45c side, only the
slide shaft 45e further moves toward the small diameter cylinder
45d side until the stopper 45n abuts on the piston 45r, thereby the
stopper 45p is away from the piston 45r toward the small diameter
cylinder 45d side.
[0826] Then, the coil spring 45g is pushed by the end surface of
the slide shaft 45e at the small diameter cylinder 45d side to be
compressed and comes back to the state to store an enrgizing force
to move the slide shaft 45e toward the small diameter cylinder 45c
side as shown in FIG. 34.
[0827] In the following, an operation of the channel selector valve
according to the fourteenth embodiment constructed as described
above will be explained.
[0828] When the operation of the compressor 4 is halted, the piston
cylinder 12 and the second piston cylinder 12' of the slide-type
four-way selector valve 43 keep their positions during an
ex-operation of the compressor 4, while the piston 45r of the
three-way selector valve 45 has moved to the second position if it
was at the first position during an ex-operation of the compressor
4, on the other hand the piston 45r has moved to the first position
if it was at the second position during an ex-operation of the
compressor 4.
[0829] As shown in FIG. 34, in a state that the refrigerating cycle
A is in the heating mode, if the operation of the compressor 4 is
halted, the piston cylinders 12 and the second piston cylinder 12'
of the slide-type four-way selector valve 43 do not move and stays
at the first position shown in FIG. 34, while the piston 45r of the
three-way selector valve 45 move from the second position shown in
FIG. 34 to the first position since the force applied to the end
surface of the slide shaft 45e at the small diameter cylinder 45c
side is removed.
[0830] Therefore, the small diameter cylinder 45d of the three-way
selector valve 45, which communicates with the second
pressure-transducing chamber R.sub.5 of the slide-type four-way
selector valve 43 through the channel 14G, communicates with the
large diameter cylinder 45b through the valve port 45v that is
opened by the piston 45r situated at the first position, then the
large diameter cylinder 45b communicates with the outlet pipe 5
through the channel 14J, thereby the outlet pipe 5 communicates
with the second pressure-transducing chamber R.sub.5 through the
three-way selector valve 45.
[0831] Then, the small diameter cylinder 45c of the three-way
selector valve 45, which communicates with the pressure-transducing
chamber R.sub.2 of the slide-type four-way selector valve 43
through the channe 14H, communicates with the inlet pipe 6 through
the channel 45k, the circular groove 45h and the channel 14F,
thereby the inlet pipe 6 communicates with the pressure-transducing
chamber R.sub.2 through the three-way selector valve 45.
[0832] In this state, when the compressor 4 starts to operate, a
high pressure refrigerant discharged from the compressor 4 flows
into the large diameter cylinder 45b of the three-way selector
valve 45 through the outlet pipe 5 and the channel 14J, thereby a
difference between the pressure of the refrigerant in the small
diameter cylinder 45c that communicates with the channel 14F
through the channel 45k and the circular groove 45h and the
pressure of high pressure refrigerant in the large diameter
cylinder 45b becomes large.
[0833] Thereby, the coil spring 45f is pushed by the end surface of
the slide shaft 45e at the small diameter cylinder 45c side to be
compressed, then the coil spring 45f stores an energizing force to
slide the slide shaft 45e toward the small diameter cylinder 45d
side.
[0834] Moreover, since the outlet pipe 5 communicates with the
second pressure-transducing chamber R.sub.5 through the three-way
selector valve 45, the pressure of the refrigerant in the second
pressure-transducing chamber R.sub.5 increases so as to become
equal to that in the high pressure space S2, while, since the inlet
pipe 6 communicates with the pressure-transducing chamber R.sub.2
through the three-way selector valve 45, the pressure of the
refrigerant in the pressure-transducing chamber R.sub.2 decreases
to increase its difference from the pressure of the refrigerant in
the high pressure space S2.
[0835] Therefore, the piston cylinder 12 and the second piston
cylinder 12' of the slide-type four-way selector valve 43 move from
the first position shown in FIG. 34 to the second position, then
the high pressure refrigerant, which is discharged from the
compressor 4 and flowed into the high pressure space S2 through the
outlet pipe 5, flows into the outdoor heat exchanger 9B from the
pipe 8, then this refrigerant further flows into the closed space
S1 by way of the throttle 10, the indoor heat exchanger 9A and the
pipe 7 and then, comes back to the inlet of the compressor 4
through the inlet pipe 6, thereby the refrigerating cycle A is in
the cooling mode.
[0836] Thereafter, when the operation of the compressor 4 is
halted, in the three-way selector valve 45, by the energizing force
stored in the coil spring 45f, the piston 45r together with the
slide shaft 45e moves toward the small diameter cylinder 45d side
to be situated at the second position, while in the slide-type
four-way selector valve 43, the piston cylinder 12 and the second
piston cylinder 12' are kept staying at the second position.
[0837] Therefore, the small diameter cylinder 45c of the three-way
selector valve 45, which communicates with the pressure-transducing
chamber R.sub.2 of the slide-type four-way selector valve 43
through the channel 14H, communicates with the large diameter
cylinder 45b through the valve port 45t that is opened by the
piston 45r situated at the second position, then the large diameter
cylinder 45b communicates with the outlet pipe 5 through the
channel 14J, thereby the outlet pipe 5 communicates with the
pressure-transducing chamber R.sub.2 through the three-way selector
valve 45.
[0838] Then, the small diameter cylinder 45d of the three-way
selector valve 45, which communicates with the second
pressure-transducing chamber R.sub.5 of the slide-type four-way
selector valve 43 through the channe 14G, communicates with the
inlet pipe 6 through the channel 45m, the circular groove 45j and
the channel 14F, thereby the inlet pipe 6 communicates with the
second pressure-transducing chamber R.sub.5 through the three-way
selector valve 45.
[0839] In this state, when the compressor 4 starts to operate, a
high pressure refrigerant discharged from the compressor 4 flows
into the large diameter cylinder 45b of the three-way selector
valve 45 through the outlet pipe 5 and the channel 14J, thereby a
difference between the pressure of the refrigerant in the small
diameter cylinder 45d that communicates with the channel 14F
through the channel 45m and the circular groove 45j and the
pressure of high pressure refrigerant in the large diameter
cylinder 45b becomes large.
[0840] Thereby, the coil spring 45g is pushed by the end surface of
the slide shaft 45e at the small diameter cylinder 45d side to be
compressed, then the coil spring 45g stores an energizing force to
slide the slide shaft 45e toward the small diameter cylinder 45c
side.
[0841] Moreover, since the outlet pipe 5 communicates with the
pressure-transducing chamber R.sub.2 through the three-way selector
valve 45, the pressure of the refrigerant in the
pressure-transducing chamber R.sub.2 increases so as to become
equal to that in the high pressure space S2, while, since the inlet
pipe 6 communicates with the second pressure-transducing chamber
R.sub.5 through the three-way selector valve 45, the pressure of
the refrigerant in the second pressure-transducing chamber R.sub.5
decreases to increase its difference from the pressure of the
refrigerant in the high pressure space S2.
[0842] Therefore, the piston cylinder 12 and the second piston
cylinder 12' of the slide-type four-way selector valve 43 move from
the second position to the first position shown in FIG. 34, then
the high pressure refrigerant, which is discharged from the
compressor 4 and flowed into the high pressure space S2 through the
outlet pipe 5, flows into the indoor heat exchanger 9A from the
pipe 7, then this refrigerant further flows into the closed space
S1 by way of the throttle 10, the outdoor heat exchanger 9B and the
pipe 8 and then, comes back to the inlet of the compressor 4
through the inlet pipe 6, thereby the refrigerating cycle A is in
the heating mode.
[0843] Thereafter, when the operation of the compressor 4 is
halted, in the three-way selector valve 45, by the energizing force
stored in the coil spring 45g, the piston 45r together with the
slide shaft 45e moves toward the small diameter cylinder 45c side
to be situated at the first position, while in the slide-type
four-way selector valve 43, the piston cylinder 12 and the second
piston cylinder 12' are kept staying at the first position.
[0844] The channel selector valve according to the fourteenth
embodiment constracted as described above gives a similar effect
with that of the channel selector valve according to the thirteenth
embodiment.
[0845] In the aforementioned embodiments from the first to the
fourteenth embodiment, a channel selector valve constructed by
employing a three-way selector valve and a slide-type four-way
selector valve has been explained. In the following, an embodiment,
in which the present invention is applied to a rotary channel
selector valve that performs its channel selector operation by
rotation of a main valve element in a valve housing will be
explained.
[0846] In the following, a schematic constitution of a
refrigerating cycle A employing a rotary channel selector valve
will be explained with reference to FIG. 35, in which the same
abbreviation numerals with those used for the corresponding
identical members or parts of the channel selector valve according
to the thirteenth embodiment shown in FIG. 33 are used.
[0847] In FIG. 35, a channel of the refrigerant in the cooling mode
is shown by solid lines while that in the heating mode is shown by
broken lines. In this refrigerating cycle A, a place where the high
pressure refrigerant discharged from the compressor 4 is guided to
and a place where the refrigerant to be sucked by the compressor 4
by way of an accumulator 200 is guided from are mutually selected
out of the indoor heat exchanger 9A and the outdoor heat exchanger
9B by a rotary four-way selector valve 50, and an
electrically-driven expansion valve 10A is provided between the
indoor heat exchanger 9A and the outdoor heat exchanger 9B.
Pressure sensors Pc and Pc' are disposed at the indoor heat
exchanger 9A and the outdoor heat exchanger 9B, respectively, to
detect each pressure, thereby a position of the movable member can
be detected. These pressure sensors may be disposed at a channel
near the rotary four-way selector valve 50.
[0848] In the following, a channel selector valve according to a
fifteenth embodiment of the present invention, which can be used as
the rotary four-way selector valve 50 shown in FIG. 35, will be
explained with reference to FIGS. 36 to 45.
[0849] FIG. 36 is a sectional view of the channel selector valve 51
according to a fifteenth embodiment of the present invention, in
which a columnar main valve element 55 is received in a cylindrical
valve housing 53 rotatively and movable in a direction of a
rotation axis, an open end of the valve housing 53 is closed by a
valve seat 57, and a coil spring 59 that energizes the main valve
element 55 to be apart from the valve seat 57 is received in the
valve housing 53.
[0850] In detail, the valve housing 53 consists of an outer housing
53a and two inner housings 53b and 53c upper and lower, out of
which the outer housing 53a has a cylindrical shape with one end
open and an opposite end closed, the opposite end of the outer
housing 53a is connected to the outlet pipe 5.
[0851] The inner housings 53b and 53c have a cyrindrical shape and
an outer diameter so as to be received inside of the outer housing
53a. As shown in FIG. 37, at one end of the upper inner housing
53b, a first inclined end surface 53d and a second inclined end
surface 53e are formed two for each alternately in a
circumferential direction of the upper inner housing 53b such that
a peak and a valley are continued with a cycle of 90.degree., while
at one end of the second inclined end surface 53e, which
constitutes the valley in combination with one end of the first
inclined end surface 53d, there is formed a groove 53f extending in
an axial direction of the upper inner housing 53b.
[0852] As shown in FIG. 38, the lower inner housing 53c is
constituted up and down symmetrical with respect to the upper inner
housing 53b.
[0853] Then, as shown in FIG. 39, the upper and lower inner
housings 53b and 53c are received in the outer housing 53a on a
condition that the ends of them are faced with each other so that
the peak fits with the valley.
[0854] Then, as shown in FIG. 39, a first cam groove 53g is formed
between the first inclined end surface 53d of the upper inner
housing 53b and the second inclined end surface 53e of the lower
inner housing 53c, likewise a second cam groove 53h is formed
between the second inclined end surface 53e of the upper inner
housing 53b and the first inclined end surface 53d of the lower
inner housing 53c.
[0855] Therefore, as shown in FIG. 36, when the upper and lower
inner housings 53b and 53c are received in the outer housing 53a to
constitute the valve housing 53, a cam groove 53j, consisting of
the first and second cam grooves 53g and 53h and the groove 53f, is
formed on an inner circumferential surface of the valve housing
53.
[0856] As shown in FIG. 40, in the valve seat 57, there are formed
a first selector port 57a to which the pipe 7 is connected from the
bottom side and a second selector port 57b to which the pipe 8 is
connected from the bottom side, at positions facing with each other
sandwiching a center of the valve seat 57, in addition, two ports
57c of the low pressure side are formed at positions shifted by a
phase of 90.degree. in a circumferential direction of the valve
seat 57 from the first and second selector ports 57a and 57b, then
each of two ports 57c of the low pressure side are connected to a
respective pipe out of two pipes, which are formed by branching the
inlet pipe 6, from the bottom side of the valve seat 57.
[0857] As shown in FIG. 40, a ring-shape groove 57e is formed near
a periphery of the valve seat 57, into which an end of the coil
spring 59 is inserted, then in this ring-shape groove 57e, there is
received a thrust bearing (corresponding to slide means) 58 to
prevent a pinch between one end of the coil spring 59 and the
bottom of the ring-shape groove 57e from occurring and to smooth a
rotation of the main valve element 55 with respect to the valve
housing 53, when an opposite end of the coil spring 59 adheres to
the main valve element 55 and rotates together with the main valve
element 55.
[0858] As shown in FIG. 41, the main valve element 55 is provided
with a low-pressure side communication groove 55a and a
high-pressure side communication channel 55b.
[0859] The low pressure side communication groove 55a is formed to
be opened at an end surface of the main valve element 55 at the
valve seat 57 side, and when said end surface abuts on the alve
seat 57, at a first rotation position of the main valve element 55,
the first selector port 57a and the two ports 57c of the low
pressure side communicate with each other by the low pressure side
communication groove 55a, while at a second rotation position of
the main valve element 55, the second selector port 57b and the two
ports 57c of the low pressure side communicate with each other by
the low pressure side communication groove 55a.
[0860] As shown in FIG. 36, the high pressure side communication
channel 55b has a chamber 55d, which is opened at an opposite end
to the valve seat 57 side of the main valve element 55 through the
valve port 55c, and an inner channel 55e shown in FIG. 41, then
this inner channel 55e is opened at an end surface of the main
valve element 55 at the valve seat 57 side keeping away from the
low pressure side communication groove 55a and communicates with
the chamber 55d in the main valve element 55.
[0861] As shown in FIG. 36, a shaft 55f is inserted into the center
of the main valve element 55 to be movable in an axial direction,
and when the valve element 55 is apart from the valve seat 57, an
assistant valve element 55g attached to an end of the shaft 55f at
the valve port 55c side closes the valve port 55c to make the high
pressure side communication channel 55b be isolated, then an end of
the shaft 55f abuts on the valve seat 57 allowing the assistant
valve element 55g to open the valve port 55c when the main valve
element 55 is seated on the valve seat 57, as shown in FIGS. 42 and
43, thereby the high pressure side communication channel 55b is in
an opened state.
[0862] There are provided each guide pin (corresponding to cam
follower pins) 55h at a circumferential surface position and a
position shifted by a phase of 180.degree. therefrom of the main
valve element 55. As shown in FIG. 36, these guide pins 55h are
inserted into the cam groove 53j under a condition that the main
valve element 55 is received in the valve housing 53.
[0863] In the following, an operation of the channel selector valve
51 according to the fifteenth embodiment constructed as described
above will be explained.
[0864] When the operation of the compressor 4 is halted, as shown
in FIG. 36, the main valve element 55 is apart from the valve seat
57 due to the energizing force of the coil spring 59, then the
assistant valve element 55g closes the valve port 55c, while the
two guide pins 55h of the main valve element 55 are situated at the
groove 53f of the upper inner housing 53b, at which divisions of
90.degree. and 270.degree. are shown in FIG. 44, i.e. at which the
cam groove 53j of the cam housing 53 is the farthest apart from the
valve seat 57.
[0865] In FIG. 44, the divisions of angle indicate a rotational
position of the guide pin 55h in the cam groove 53j.
[0866] In the refrigerating cycle A is in the heating mode, when
the operation of the compressor 4 is halted and each guide pin 55h
is situated at the groove 53f of the upper inner housing 53b where
the divisions of 90.degree. or 270.degree. are shown in FIG. 44, as
shown in a figure at the right end of FIG. 45, the low pressure
side communication groove 55a of the main valve element 55 faces
the first and second selector ports 57a and 57b, respectively, of
the valve seat 57.
[0867] In this state, when the compressor 4 starts to operate,
since the assistant valve element 55g closes the valve port 55c,
the high pressure refrigerant flowed into the valve housing 53 from
the compressor 4 acts so as to move the main valve element 55
toward the valve seat 57 side against the energizing force of the
coil spring 59.
[0868] Then, each guide pin 55h situated at the groove 53f of
90.degree. (or 270.degree.) of the upper inner housing 53b moves on
the second cam groove 53h along the first inclined end surface 53d
of the lower inner housing 53c, then is situated at the groove 53f
of the lower inner housing 53c, at which the angle divisions of
180.degree. (or 0.degree.) is shown in FIG. 44.
[0869] Then, as each guide pin 55h moves on the second cam groove
53h, the main valve element 55 moves toward the valve seat 57 side
with rotating, and when rotates by 90.degree., as shown in FIG. 42,
the main valve element 55 sits down on the valve seat 57 to reach
the first position, thereby an end of the shaft 55f abuts on the
valve seat 57 allowing the assistant valve element 55g to open the
valve port 55c.
[0870] In this situation, as shown in a figure at left end of FIG.
45, the low pressure side communication groove 55a faces the first
selector port 57a and the two low pressure side ports 57c, while
the inner channel 55e faces the second selector port 57b.
[0871] Therefore, as shown in FIG. 42, the outlet pipe 5
communicates with the pipe 8 through the high pressure side
communication channel 55b and the second selector port 57b, while
the inlet pipe 6 communicates with the pipe 7 through the low
pressure side communication groove 55a and the two low pressure
side ports 57c.
[0872] Consequently, the high pressure refrigerant from the
compressor 4 flows into the outdoor heat exchanger 9B from the pipe
8 by way of the outlet pipe 5, high pressure side communication
channel 55b and the second selector port 57b, then passes through
the throttle 10, the indoor heat exchanger 9A, pipe 7, the first
selector port 57a, the low pressure side communication groove 55a,
the two low pressure side ports 57c and the inlet pipe 6, and
finally comes back to the inlet of the compressor 4, thereby the
refrigerating cycle A is in the cooling mode.
[0873] Thereafter, when the operation of the compressor 4 is
halted, the pressure of the refrigerant flowed into the valve
housing 53 decreases, thereby the energizing force of the coil
spring 59 acts to move the main valve element 55 being away from
the valve seat 57.
[0874] Then, each guide pin 55h situated at the groobe 53f of
180.degree. (or 0.degree.) of the lower inner housing 53 moves on
the first cam groove 53g along the first inclined end surface 53d
of the upper inner housing 53b, then is situated at the groove 53f
of 270.degree. (or 90.degree.) of the upper inner housing 53b.
[0875] Then, as each guide pin 55h moves on the first cam groove
53g, the main valve element 55 moves toward the outlet pipe 5 side
with rotating in the valve housing 53, and when rotates by
90.degree., the main valve element 55 reaches a first intermediate
position where the main valve element is the farthest away from the
valve seat 57, thereby the assistant valve element 55g of the shaft
55f, an end of which is apart from the valve seat 57, closes the
valve port 55c.
[0876] In this situation, as shown in the second figure from the
left of FIG. 45, the low-pressure side communication groove 55a
faces the first and second selector ports 57a and 57b,
respectively.
[0877] In this state, when the compressor 4 starts to operate, each
guide pin 55h situated at the groove 53f of 270.degree. (or
90.degree.) of the upper inner housing 53b moves on the second cam
groove 53h, then is situated at the groove 53f of 0.degree. (or
180.degree.) of the lower inner housing 53c.
[0878] Then, as each guide pin 55h moves on the second cam groove
53h, the main valve element 55 moves toward the valve seat 57 side
with rotating in the valve housing 53, and when rotates by
90.degree., as shown in FIG. 43, the main valve element 55 sits
down on the valve seat 57 to reach the second position, thereby an
end of the shaft 55f abuts on the valve seat 57 allowing the
assistant valve element 55g to open the valve port 55c.
[0879] In this situation, as shown in a second figure from the
right end of FIG. 45, the low pressure side communication groove
55a faces the second selector port 57b and the two low pressure
side ports 57c, while the inner channel 55e faces the first
selector port 57a.
[0880] Therefore, as shown in FIG. 43, the outlet pipe 5
communicates with the pipe 7 through the high pressure side
communication channel 55b and the first selector port 57a, while
the inlet pipe 6 communicates with the pipe 8 through the second
selector port 57b, the low pressure side communication groove 55a
and the two low pressure side ports 57c.
[0881] Consequently, the high pressure refrigerant from the
compressor 4 flows into the indoor heat exchanger 9A from the pipe
7 by way of the outlet pipe 5, high pressure side communication
channel 55b and the first selector port 57a, then passes through
the throttle 10, the outdoor heat exchanger 9B, pipe 8, the second
selector port 57b, the low pressure side communication groove 55a,
the two low pressure side ports 57c and the inlet pipe 6, and
finally comes back to the inlet of the compressor 4, thereby the
refrigerating cycle A is in the heating mode.
[0882] Thereafter, when the operation of the compressor 4 is
halted, the pressure of the refrigerant flowed into the valve
housing 53 decreases, thereby the energizing force of the coil
spring 59 acts to move each guide pin 55h, situated at the groove
53f of 0.degree. (or 180.degree.) of the lower inner housing 53c,
on the first cam groove 53g so as to be situated at the groove 53f
of 90.degree. (or 270.degree.) of the upper inner housing 53b.
[0883] Then, as each guide pin 55h moves on the first cam groove
53g, the main valve element 55 moves toward the outlet pipe 5 side
with rotating in the valve housing 53, and when rotates by
90.degree., as shown in FIG. 36, the main valve element 55 reaches
a second intermediate position where the main valve element 55 is
the farthest away from the valve seat 57, thereby the assistant
valve element 55g of the shaft 55f, an end of which is apart from
the valve seat 57, closes the valve port 55c.
[0884] Thereby, as shown in a figure at the right end of FIG. 45,
the system comes back to an initial state, in which the low
pressure communication groove 55a faces the first and second valve
ports 57a and 57b, respectively.
[0885] Thus according to the channel selector valve 51 of the
fifteenth embodiment, by using a differential pressure generated
due to the refrigerant flow discharged from the compressor 4 and
the energizing force due to the coil spring 59 disposed between the
main valve element 55 and the valve seat 57, the main valve element
55 is moved in the direction nearer to or away from the valve seat
57, while each guide pin 55h is moved along the cam groove 53j and
the main valve element 55 is allowed to rotate with respect to the
valve housing 53, theteby the main valve element 55 is moved
between the first and second positions.
[0886] Therefore, a place, with which the outlet pipe 5 or the
inlet pipe 6 communicates is selected through the low pressure side
communication groove 55a and the high pressure side communication
channel 55b, is selected between either the first selector port 57a
or the second selector port 57b of the valve seat 57, thereby the
heating mode, in which the refrigerant discharged from the outlet
pipe 5 is supplied to the indoor heat exchanger 9A by way of the
pipe 7, and the cooling mode, in which the refrigerant discharged
from the outlet pipe 5 is supplied to the outdoor heat exchanger 9B
by way of the pipe 8, can be selected by starting and halting the
operation of the compressor 4, and the selected state can be
maintained without using any exclusive power source such as an
electromagnetic solenoid.
[0887] Moreover, according to the fifteenth embodiment, since the
selection of communication for the outlet pipe 5 and the inlet pipe
6 in the channel selector valve 51 is performed according to a
start and halt of the operation of the compressor 4, neither power
source for an electric drive nor control by an electric signal for
selecting the channel of the refrigerant is needed, therefore, the
channel selector valve 51 according to the fifteenth embodiment is
advantageous.
[0888] In addition, in the channel selector valve 51 according to
the fifteenth embodiment, the groove 53f of the cam groove 53j
formed in the valve housing 53 is provided not at a junction
between an end of the first inclined end surface 53d and an end of
the second inclined end surface 53e but at the end of the second
inclined end surface 53e, thereby the channel selector valve 51 has
an advantage as follows.
[0889] That is, when the main valve element 55 moves in the
direction nearer to or away from the valve seat 57, each guide pin
55h, which has moved from the first inclined end surface 53d to the
groove 53f, is prevented from coming back to the first inclined end
surface 53d and is securely moved to the second inclined end
surface 53e, then the rotational direction of the main valve
element 55 is limited to one direction, thereby the selection of
the modes of the refrigerating cycle A can be securely performed by
controlling the number of start and halt of the operation of the
compressor 4.
[0890] In the channel selector valve 51 according to the fifteenth
embodiment described above, the movement of the main valve element
55 in the direction away from the valve seat 57 is performed by the
energizing force of the coil spring 59 disposed between the main
valve element 55 and the valve seat 57. Instead, like a channel
selector valve 61 according to a sixtennth embodiment of the
present invention shown in FIG. 46, a position of the valve housing
53 may be set upside down such that the outlet pipe 5 is situated
below in a vertical direction, then the movement of the main valve
element 55 in the direction away from the valve seat 57 may be
performed by an own weight of the main valve element 55.
[0891] If the channel selector valve 61 is constructed as described
above, the assistant valve element 55g opens the valve port 55c by
an own weight of the shaft 55f even if the main valve element 57
does not sit down on the valve seat 57, after the high pressure
refrigerant discharged from the compressor 4 flows into the valve
housing 53 through the outlet pipe 5 upon the start of the
operation of the compressor 4, the assistant valve element 55g
opens the valve port 55c against the own weight of the shaft 55f,
by the pressure of the high pressure refrigerant flowed into the
valve housing 53, until the main valve element 55 sits down on the
valve seat 57.
[0892] The channel selector valve 61 according to the sixteenth
embodiment constracted as described above gives a similar effect
with that of the channel selector valve 51 according to the
fifteenth embodiment. Moreover, in the channel selector valve 61
according to the sixteenth embodiment, since the movement of the
main valve element 55 in the direction away from the valve seat 57
is performed by an own weight of the main valve element 55, the
coil spring 59 can be omitted, resulting in a reduction of the cost
of the channel selector valve.
[0893] As shown in FIG. 47, in a channel selector valve 71
according to the seventeenth embodiment of the present invention,
the coil spring 59 provided between the main valve element 55 and
the valve seat 57, which is employed in the channel selector valve
51 according to the fifteenth embodiment shown in FIG. 36, is
replaced by a second coil spring 73 provided between the main valve
element 55 and an closed end of the outer housing 53a, to which the
outlet pipe 5 is connected, thereby the main valve element 55 is
energized toward the valve seat 57 side by an energizing force due
to the second coil spring 73.
[0894] When the channel selector valve 71 is constructed as
described above, the movement of the main valve element 55 between
the first and the second positions is performed in such a manner
that the compressor 4, the outlet of which is connected to the
outlet pipe 5, is operated in a direction of inverse rotation so as
to decrease the pressure of the refrigerant exsisted in a space
between the closed end of the outer housing 53a and the main valve
element 55, thereby the main valve element 55 is moved in the
direction away from the valve seat 57 against the energizing force
of the second coil spring 73.
[0895] The channel selector valve 71 according to the seventeenth
embodiment constracted as described above gives a similar effect
with that of the channel selector valve 51 according to the
fifteenth embodiment. Moreover, in the channel selector valve 71
according to the seventeenth embodiment, since the main valve
element 55 moves between the first and the second positions even if
the compressor 4 is not rotated in a normal direction, when the
refrigerating cycle A is operated again in the same operational
mode with the former mode, no pre-operation of the compressor 4
with the rotation in a normal direction is needed for a channel
selection, i.e. the so-called dummy operation of the compressor 4
can be omitted, therefore the channel selector valve 71 is
advantageous in this respect.
[0896] In the following, a channel selector valve according to a
eighteenth embodiment of the present invention, which can be
employed as the rotary four-way selector valve 50 shown in FIG. 35,
will be explained with reference to FIGS. 48 to 53.
[0897] FIG. 48 is a sectional view of a channel selector valve
according to the eighteenth embodiment of the present invention, in
which the same abbreviation numerals with those used for the
corresponding identical members or parts of the channel selector
valve 51 according to the fifteenth embodiment shown in FIG. 36 are
used.
[0898] The channel selector valve 81 according to the eighteenth
embodiment shown in FIG. 48 is different from the channel selector
valve 51 according to the fifteenth embodiment shown in FIG. 36 in
a point that a second coil spring 73 is provided between the main
valve element 55 and an closed end of the outer housing 53a, to
which the outlet pipe 5 is connected, so as to energize the main
valve element 55 to move in the direction nearer to the valve seat
57, and except this point the channel selector valve 81 is
constructed similarly to the channel selector valve 51.
[0899] In the channel selector valve 81 according to the eighteenth
embodiment constructed as described above, when the operation of
the compressor 4 is halted, the main valve element 55 is situated
at an intermediate position in a region of its movement in the
direction nearer to or away from the valve seat 57, by a balance
between an energizing force due to the coil spring 59 and that due
to the second coil spring 73, while each guide pin 55h is situated
at an intermediate position between the first cam groove 53g and
the second cam groove 53h of the cam groove 53j as shown in FIGS.
49 and 51.
[0900] Divisions of angle of FIG. 44 indicate a rotational position
of the guide pin 55h of the main valve element 55 in the cam groove
53j.
[0901] When the operation of the compressor 4 is halted after the
refrigerating cycle A has been in the cooling mode, and assuming
that each guide pin is situated at an intermediate position of the
first cam groove 53g where is forward by 30.degree. from the groove
53f of the upper inner housing 53b at which a division 90.degree.
(or 270.degree.) is shown in FIG. 49, when the compressor 4 starts
to operate, the following steps will take place.
[0902] That is, since the assistant valve element 55g closes the
valve port 55c, the high pressure refrigerant flowed into the valve
housing 53 from the compressor 4 acts to move the main valve
element 55 toward the valve seat 57 side against the energizing
force of the coil spring 59.
[0903] Then, each guide pin 55h situated at an intermediate
position of the first cam groove 53g moves on the first cam groove
53g along the second inclined end surface 53e of the lower inner
housing 53c, then is situated at the groove 53f of 0.degree. (or
180.degree.) of the lower inner housing 53c, while the main valve
element 55 sits down on the valve seat 57 to reach the first
position as shown in FIG. 50, thereby the refrigerating cycle A is
in the cooling mode.
[0904] Thereafter, when the operation of the compressor 4 is
halted, since the pressure of the refrigerant flowed into the valve
housing 53 decreases, the energizing force of the coil spring 59
acts to part the main valve element 55 from the valve seat 57.
[0905] Then, each guide pin 55h, situated at the groove 53f of
0.degree. (180.degree.) of the lower inner housing 53c, moves on
the first cam groove 53g along the first inclined end surface 53d
of the upper inner housing 53b and comes back to an intermediate
position of the first cam groove 53g shown in FIG. 49, thereby the
main valve element 55 comes back to the intermediate position where
the energizing force of the coil spring 59 balances with that of
the second coil spring 73.
[0906] Thereafter, when the compressor 4 starts to operate again,
the main valve element 55 comes back to the first position
similarly to the operation described above, thereby the
refrigerating cycle A is in the cooling mode.
[0907] To the contrary, when the compressor 4 is operated in a
direction of inverse rotation, the pressure of the refrigerant
exsisted in a space between the closed end of the outer housing 53a
and the main valve element 55 is decreased, thereby the main valve
element 55 is moved in the direction away from the valve seat 57
against the energizing force of the second coil spring 73.
[0908] Then, each guide pin 55h situated at an intermediate
position of the first cam groove 53g moves on the first cam groove
53g along the first inclined end surface 53d of the upper inner
housing 53b, then is situated at the groove 53f of the upper inner
housing 53b where a division of 90.degree. (or 270.degree.) is
shown in FIG. 51.
[0909] While the main valve element 55 reaches a point where is the
farthest away from the valve seat 57 as shown in FIG. 52.
[0910] Thereafter, when the operation of the compressor 4 is
halted, since the decrease in the pressure of the refrigerant in
the space between the closed end of the outer housing 53a and the
main valve element 55 becomes zero, the main valve element 55 moves
in the direction nearer to the valve seat 57 by the enegizing force
of the second coil spring 73.
[0911] Then, each guide pin 55h situated at the groove 53f of
90.degree. (or 270.degree.) of the upper inner housing 53b moves on
the second cam groove 53h, then is situated at an intermediate
position of the second cam groove 53h, at which each guide pin 55h
proceeds by 30.degree. toward the groove 53f of 180.degree. (or
0.degree.) of the lower inner housing 53c side as shown in FIG. 51,
thereby the main valve element 55 further rotates by 60.degree.
from the state shown in FIG. 48 so as to reach said intermediate
position.
[0912] Thereafter, when the compressor 4 starts to operate again,
since the assistant valve element 55g closes the valve port 55c,
the high pressure refrigerant flowed into the valve housing 53 from
the compressor 4 acts to move the main valve element 55 toward the
valve seat 57 side aginst the energizing force of the coil spring
59.
[0913] Then, each guide pin 55h situated at an intermediate
position of the second cam groove 53h moves on the second cam
groove 53h along the first inclined end surface 53d of the lower
inner housing 53c, then is situated at the groove 53f of
180.degree. (or 0.degree.) of the lower inner housing 53c, while
the main valve element 55 sits down on the valve seat 57 to reach
the second position as shown in FIG. 53, thereby the refrigerating
cycle A is in the heating mode.
[0914] Thereafter, when the operation of the compressor 4 is
halted, since the pressure of the refrigerant flowed into the valve
housing 53 decreases, the energizing force of the coil spring 59
acts to part the main valve element 55 from the valve seat 57.
[0915] Then, each guide pin 55h, situated at the groove 53f of
180.degree. (0.degree.) of the lower inner housing 53c, moves on
the first cam groove 53g and reaches to an intermediate position of
the first cam groove 53g, at which each guide pin 55h proceeds by
60.degree. toward the groove 53f of 270.degree. (or 90.degree.) of
the upper inner housing 53b side as shown in FIG. 51, thereby the
main valve element 55 further rotates by 180.degree. from the state
shown in FIG. 48 so as to reach said intermediate position
[0916] Thereafter, the compressor 4 starts to operate again, by the
high pressure refrigerant flowed into the valve housing 53, the
main valve element 55 moves in the direction nearer to the valve
seat 57 against the energizing force of the coil spring 59.
[0917] Then, each guide pin 55h situated at an intermediate
position of the first cam groove 53g shown in FIG. 51 moves on the
first cam groove 53g along the second inclined end surface 53e of
the lower inner housing 53c and comes back to the groove 53f of
180.degree. (or 0.degree.) of the lower inner housing 53c, while
the main valve element 55 comes back to the second position shown
in FIG. 53, thereby the refrigerating cycle A is in the heating
mode.
[0918] To the contrary, when the compressor 4 is operated in a
direction of inverse rotation, the pressure of the refrigerant
exsisted in a space between the closed end of the outer housing 53a
and the main valve element 55 is decreased, and the main valve
element 55 moves in the direction away from the valve seat 57
against the energizing force of the second coil spring 73, then
each guide pin 55h, which has been situated at an intermediate
position of the first cam groove 53g shown in FIG. 51, is situated
at the groove 53f of 270.degree. (or 90.degree.) of the upper inner
housing 53b.
[0919] Then, the main valve 55 further rotates by 180.degree. from
the state shown in FIG. 52 and reaches the farthest position from
the valve seat 57.
[0920] Thereafter, when the operation of the compressor 4 is
halted, each guide pin 55h moves on the second cam groove 53h from
the groove 53f of 270.degree. (or 90.degree.) of the upper inner
housing 53b and is situated at an intermediate position of the
second cam groove 53h, at which each guide pin 55h proceeds by
30.degree. toward the groove 53f of 0.degree. (or 180.degree.) of
the lower inner housing 53c side, thereby the main valve element 55
further rotates by 240.degree. from the state shown in FIG. 48 and
reaches said intermediate position.
[0921] Then, when the compressor 4 starts to operate again, by the
high pressure refrigerant flowed into the valve housing 53, the
main valve element 55 moves in the direction nearer to the valve
seat 57 against the energizing force of the coil spring 59.
[0922] Then, each guide pin 55h situated at an intermediate
position of the second cam groove 53h moves on the second cam
groove 53h along the first inclined end surface 53d of the lower
inner housing 53c and is situated at the groove 53f of 0.degree.
(or 180.degree.) of the lower inner housing 53c, while the main
valve element 55 sits down on the valve seat 57 and reaches the
first position as shown in FIG. 50, thereby the refrigerating cycle
A is in the cooling mode.
[0923] Thereafter, when the operation of the compressor 4 is
halted, since the pressure of the refrigerant flowed into the valve
housing 53 decreases, the energizing force of the coil spring 59
acts to part the main valve element 55 from the valve seat 57,
while each guide pin 55h, which has been situated at the groove 53f
of 0.degree. (or 180.degree.) of the lower inner housing 53c, moves
on the first cam groove 53g and comes back to the intermediated
position of the first cam groove 53g shown in FIG. 49, thereby the
main valve element 55 comes back to said intermediate position
shown in FIG. 48.
[0924] The channel selector valve 81 according to the eighteenth
embodiment constracted as described above gives a similar effect
with that of the channel selector valve 51 according to the
fifteenth embodiment. Moreover, in the channel selector valve 81
according to the eighteenth embodiment, since by using a balance
between the energizing forces of the coil spring 59 and the second
coil spring 73, the main valve element 55 is situated at the
intermediate position in a range of the movement in the direction
nearer to or away from the valve seat 57, thereby no pre-operation
of the compressor 4 with the rotation in a normal direction is
needed for a channel selection, i.e. the so-called dummy operation
of the refrigerating cycle A can be omitted similarly to the
channel selector valve 71 according to the seventeenth embodiment,
therefore the channel selector valve 81 is advantageous in this
respect.
[0925] In the aforementioned channel selector valves 51, 61, 71 and
81, each guide pin 55h of the main valve element 55 is moved along
the cam groove 53j of the housing 53 so that the movement of the
main valve element 55 in the direction nearer to or away from the
valve seat 57 is transformed to the rotation of the main valve
element 55 in a circumferential direction, instead the arrangement
of the guide pin and the cum groove may be set inversely between
the main valve element 55 and the valve housing 53.
[0926] A channel selector valve according to a nineteenth
embodiment shown in FIG. 54 has such a construction mentioned just
above, and in the channel selector valve 91 according to the
nineteenth embodiment, a rotating shaft 93 of a main valve element
55 is provided at the center of a valve seat 57, a cam groove 53j
is formed on the circumferential surface of the rotating shaft 93
as shown in FIGS. 55 and 56, then a hollow 55k (shown in FIG. 57)
into which one half of a guide ball 95 is inserted, another half of
the guide ball 95 being inserted into the cam groove 53j, is formed
in a shaft hole 55j of the main valve element 55 shown in FIG. 54,
into which the rotating shaft 93 is inserted.
[0927] In the channel selector valve 91 according to the nineteenth
embodiment, constitutions of a low pressure side communication
groove and a high pressure side communication channel of the main
valve element 55 are different from those of the channel selector
valves 51, 61, 71 and 81 according to the fifteenth to eighteenth
embodiments, respectively, however the primary part of the channel
selector valve 91 is the constitution for transforming the movement
of the main valve element 55 in the direction nearer to or away
from the valve seat 57 to the rotation of the main valve element 55
in a circumferential direction and is not a structure of the main
valve element 55 for channel selection, therefore an explanation of
the structure of the main valve element 55 will be omitted.
[0928] The channel selector valve 91 according to the nineteenth
embodiment constracted as described above gives a similar effect
with that of the channel selector valve 51 according to the
fifteenth embodiment.
[0929] In the aforementioned channel selector valves 51, 61, 71, 81
and 91 according to the fifteenth to nineteenth embodiments,
respectively, the cam groove 53j is formed over whole circumference
of the valve housing 53 and the rotating shaft 53, instead the cam
groove 53j may be formed on a partial circumference thereof.
[0930] A channel selector valve according to a twentieth embodiment
shown in FIG. 58 has such a construction mentioned just above, and
the channel selector valve 101 according to the twentieth
embodiment is different from the channel selector valve 51
according to the sixteenth embodiment shown in FIG. 36 in points
that each guide pin has a rectangular shape in its top view and is
attached to the main valve element 55 to move rotatively and that
the cam groove 53k on the inner circumferential surface of the
valve housing 53 is not formed over the whole circumference of the
valve housing 53 but formed devided in two independently with each
other.
[0931] In the channel selector valve 101 according to the twentieth
embodiment, when the main valve element 55 moves in the direction
nearer to or away from the valve seat 57, as shown in FIG. 59, each
guide pin 55h moves back and forth in a X-shape channel along the
cam groove 53k with changing its direction properly, thereby the
main valve element 55 rotatively moves back and forth within the
predetermined angles with respect to the valve housing 53.
[0932] In the channel selector valve 101 according to the twentieth
embodiment, constitutions of a low pressure side communication
groove and a high pressure side communication channel of the main
valve element 55 and constitutions of a port of a valve seat 57 and
so on are different from those of the channel selector valves 51,
61, 71, 81 and 91 according to the fifteenth to nineteenth
embodiments, respectively.
[0933] However the primary part of the channel selector valve 101
is the constitution for transforming the movement of the main valve
element 55 in the direction nearer to or away from the valve seat
57 to the rotation of the main valve element 55 in a
circumferential direction and is not a structure of the main valve
element 55 or the valve seat 57 for channel selection, therefore an
explanation of the structure of the main valve element 55 and the
valve seat 57 will be omitted.
[0934] The channel selector valve 101 according to the twentieth
embodiment constructed as described above gives a similar effect
with that of the channel selector valve 51 according to the
fifteenth embodiment.
[0935] In the above, preferred embodiments of the channel selector
valve according to the present invention are explained, then in the
following, a preferred embodiment of a compressor with a channel
selector valve according to the present invention will be
explained.
[0936] FIG. 60 is a view illustrating a schematic constitution of a
refrigerating cycle employing a compressor with a channel selector
valve according to a twenty first embodiment of the present
invention, in which the same abbreviation numerals with those used
for the corresponding identical members or parts of the
refrigerating cycle according to the fifth embodiment shown in FIG.
9 are used.
[0937] The compressor with a channel selector valve according to a
twenty first embodiment, an operation state of which in the heating
mode is shown by its sectional view in FIG. 60, is constructed by
integrating the channel selector valve according to the fifth
embodiment of the present invention shown in FIG. 9 with a
compressor body 4A shown in FIG. 60.
[0938] The compressor body 4A comprises: a compressor housing 4a; a
low pressure chamber 4b provided in the compressor housing 4a
communicating with the inlet pipe 6; a high pressure chamber 4c
provided in the compressor housing 4a and partitioned from the low
pressure chamber 4b; and a compressing section 4d provided in the
compressor housing 4a, which compresses a refrigerant introduced
from the inlet pipe 6 into the low pressure chamber 4b and guides
the refrigerant to the high pressure chamber 4c.
[0939] The compressor body 4A constructed as described above
integrates the compressor housing 4a part, which partitions the
high pressure chamber 4c of the compressor housing 4a in the
interior thereof, with the reversing valve housing 1 in the channel
selector valve according to the fifth embodiment and communicates
the high pressure chamber 4c to the high pressure chamber R.sub.1
of the reversing valve housing 1.
[0940] Consequently, in the compressor body 4A, the part that
partitions the high pressure chamber 4c of the compressor housing
4a in the interior thereof functions as the outlet pipe 5 that
guides a high pressure refrigerant compressed in the compressing
section 4d to the high pressure chamber R.sub.1 of the reversing
valve housing 1.
[0941] As to the compressor with a channel selector valve according
to a twenty first embodiment constructed as described above, the
compressor body 4A is operated similarly to the operation of the
compressor 4 in the refrigerating cycle according to the fifth
embodiment, thereby the piston cylinder 12 of the reversing valve
housing 1 can be selected between the first and second
positions.
[0942] According to the compressor with a channel selector valve of
the twenty first embodiment thus constructed, the same effect with
that of the channel selector valve according to the fifth
embodiment can be obtained, moreover, since the channel selector
valve is integrated with the compressor, a laying pipes for
connection can be omitted, thereby the construction can be
simplified.
[0943] The above construction prevents a leak of the refrigerant
from occurring at a connection point of a pipe laying between the
high pressure chambers 4c and R.sub.1, thereby contributing to
prevention of atmospheric pollution, and since there is no current
conducting part for an electromagnetic solenoid and the like around
the compressor that generates oscillation, the above construction
also prevents an occurrence of an electrical fault due to failure
in current conduction at an electric contact and a breaking of
electric wire and the like, thereby reliance of the operation can
be improved.
[0944] A channel selector valve, which is integrated with the
compressor body 4A to construct the compressor with a channel
selector valve, is not limited to the channel selector valve
according to the fifth embodiment shown in FIG. 9, which is
employed in the compressor with a channel selector valve of the
twenty first embodiment, instead, may be the channel selector valve
according to the seventh embodiment of the present invention shown
in FIG. 18, as shown in FIG. 61, i.e. a view illustrating a
schematic constitution of a refrigerating cycle employing a
compressor with a channel selector valve according to a twenty
second embodiment of the present invention.
[0945] Moreover, although figures are omitted here, the channel
selector valve according to sixth or eighth embodiment shown in
FIG. 15 or 23, respectively, may be integrated with the compressor
body 4A to construct the compressor with a channel selector valve.
Furthermore, each channel selector valve explained in the
respective embodiment up to the twentieth embodiment may be
integrated with the compressor body 4A to construct the compressor
with a channel selector valve.
[0946] When a channel selector valve except the channel selector
valve according to the fifth embodiment is integrated with the
compressor body 4A to construct the compressor with a channel
selector valve, pipes and channels directly or indirectly connected
to the pressure-transducing chamber R.sub.2 and the second
pressure-transducing chamber R.sub.5 in each channel selector valve
according to the respective embodiment is connected likewise in the
compressor with a channel selector valve integrally constructed
with the compressor body.
[0947] As to the compressor with the channel selector valve
according to the embodiment, except the channel selector valve
according to the fifth embodiment, integrally constructed with the
compressor body 4A including the compressor with the channel
selector valve according to the twenty first or twenty second
embodiment, the channel selector valve integrated with the
compressor body 4A to construct the compressor with the channel
selector valve is separately constituted from the compressor 4,
then the similar operation with that performed with respect to the
refrigerating cycle A is performed, thereby an operation of the
channel selector valve can be carried out.
[0948] By the compressor with the channel selector valve according
to the embodiment, except the channel selector valve according to
the fifth embodiment, integrally constructed with the compressor
body 4A including the compressor with the channel selector valve
according to the twenty first or twenty second embodiment, a
similar effect with that of the compressor with the channel
selector valve according to the twenty first embodiment can be
obtained.
[0949] In each embodiment mentioned above, a channel selector valve
for use to reverse a channel of the refrigerant in the
refrigerating cycle and a compressor with a channel selector valve
in which the channel selector valve is integrated are explained.
However, the present invention can be widely applied to a channel
selector valve for use to select a channel of various fluid, for
example, liquid such as pressure oil and water or gas except
refrigerant, a different type of channel selector valve or a
compressor with a channel selector valve in which such a channel
selector valve is integrated.
[0950] In the following, preferred embodiments of a device for
controlling a refrigerating cycle according to the present
invention will be explained with reference to the drawings.
[0951] FIG. 63 is a block diagram illustrating an example of a
refrigerating cycle according to an embodiment of the present
invention, which comprises a heat pump-type air conditioner
consisting of an indoor unit (inside of alternate long and short
dash line in the figure) and an outdoor unit (outside of alternate
long and short dash line in the figure). In FIG. 63, an
abbreviation numeral 4 denotes a compressor, 9A an indoor heat
exchanger loaded in the indoor unit, 9B an outdoor heat exchanger
loaded in the outdoor unit, 10A an electrically-driven expansion
valve as a throttle device, 200 an accumulator, and 100 a channel
selector valve. In the following embodiments, a word an
electrically-driven expansion valve will be used for an explanation
on the structure and a word throttle device will be used for an
explanation on the function. Here, the throttle device is not
limited to an electrically-driven expansion valve and may be other
constitution.
[0952] An outlet of the compressor 4 is connected to the channel
selector valve 100 while an inlet of the compressor 4 is connected
to the channel selector valve 100 by way of the accumulator 200.
The channel selector valve 100 is connected to the indoor heat
exchanger 9A and the outdoor heat exchanger 9B through a pipe for
heat exchanger while the electrically-driven expansion valve 10A is
provided between the indoor heat exchanger 9A and the outdoor heat
exchanger 9B. Thereby, the compressor 4, the channel selector valve
100, accumulator 200, the indoor heat exchanger 9A, the outdoor
heat exchanger 9B and the electrically-driven expansion valve 10A
constitute the refrigerating cycle A. In the refrigerating cycle A
according to this embodiment, the channel selector valve 100 is any
one of the various types of channel selector valve according to the
following embodiments.
[0953] The compressor 4 compresses the refrigerant and the
compressed refrigerant is guided into the channel selector valve
100. As will be explaned later, the channel selector valve selects
a channel in response to an operation mode, and the refrigerant
discharged from the compressor 4 is guided into either the indoor
heat exchanger 9A or the outdoor heat exchanger 9B in response to a
channel selected. That is, in the heating mode, as shown in FIG. 63
by arrows, the compressed refrigerant is guided from the channel
selector valve 100 into the indoor heat exchanger 9A, which
functions as a condenser, the refrigerant guided from the indoor
heat exchanger 9A is guided into the outdoor heat exchanger 9B,
which functions as an evaporator through the electrically-driven
expansion valve 10A. Then, the refrigerant evaporated in the
outdoor heat exchanger 9B is guided into the compressor 4 by way of
the channel selector valve 100 and the accumulator 200. On the
other hand,. in the cooling mode, as shown by broken lines in FIG.
63, the refrigerant compressed in the compressor 4 is circulated in
order of the channel selector valve 100, the outdoor heat exchanger
9B, the electrically-driven expansion valve 10A, the indoor heat
exchanger 9A, the channel selector valve 100, the accumulator 200,
and the compressor 4, wherein the outdoor heat exchanger 9B
functions as a condenser while the indoor heat exchanger 9A
functions as a evaporator.
[0954] The indoor unit is provided with a cross flow fan 91A for
sending air passing through the indoor heat exchanger 9A, and a
heat exchanger motor 92A for rotating the cross flow fan 91A is
controlled its rotation by an indoor control section 300
constituted with a microcomputer and the like through a driver 301,
thereby a heat exchange capacity of the indoor heat exchanger 9A is
controlled. An indoor temperature Ta is detected by a temperature
sensor 302 while a temperature Tc of the indoor heat exchanger 9A
is detected by a temperature sensor 303. A receiver section 304
receives signals of a remote control 500 such as an infrared-type,
thereby the selection and setting of an operation in the indoor
control section 300 can be carried out by a remote control.
[0955] The outdoor unit is provided with a fan 91B for sending air
passing through the outdoor heat exchanger 9B, and a heat exchanger
motor 92B for rotating the fan 91B is controlled its rotation by an
outdoor control section 400 constituted with a microcomputer and
the like through a driver 401, thereby a heat exchange capacity of
the outdoor heat exchanger 9B is controlled. An outdoor temperature
Ta is detected by a temperature sensor 402 while a temperature Tc
of the outdoor heat exchanger 9B is detected by a temperature
sensor 403. An outdoor control section 400 controls an opening
ratio of the electrically-driven expansion valve 10A through a
driver 404. Further, the outdoor control section 400 detects a
temperature Td at the outlet of the compressor 4 by a temperature
sensor 405 and controls the compressor 4 by a three-phase
electrical power supplied from an inverter module explained
later.
[0956] FIG. 64 is a block diagram principally illustrating an
electric system of an indoor control section 300 and outdoor
control section 400. The indoor control section 300 has a power
relay 310 for performing an on-off action of a main power source. A
single-phase alternating current of 100 V is supplied to an AC/DC
converter 320 through the power relay 310, transformed into various
predetermined direct current voltages by the AC/DC converter 320
and supplied to a microcomputer 330 and so on. The single-phase
alternating current of 100 V supplied through the power relay 310
is also supplied to the outdoor control section 400 through a lead
21 for supplying power.
[0957] In the outdoor control section 400, an alternating current
supplied is passed through a noise filter 410, rectified in a
voltage doubler rectifier circuit 420 and smoothed by a smoothing
capacitor 430, thereby a predetermined direct current volage is
geneated. A current by the direct current thus generated is
supplied to an inverter module 450 through a shunt resistor 440. A
three-phase power is generated by the inverter module 450 and
supplied to the compressor 4. On the other hand, an output from the
smoothing capacitor 430 is transformed into a predetermined
internal direct current voltage by a DC/DC converter 460 and
supplied to a microcomputer 470 and so on. The microcomputer 470
outputs drive signals to the inverter module 450 so as to control
an operation of the compressor 4. A capacity of the compressor 4 to
compress the refrigerant is controlled by a frequency (Hz) of the
drive signal, that is, the higher the frequency (Hz), the higher
the capacity of compression. For example, if set 30 Hz as a first
predetermined capacity and 10 Hz as a second predetermined
capacity, the pressure of the refrigerant at the first
predetermined capacity is higher than that at the second
predetermined capacity. The microcomputer 470 performs a serial
communication with the microcomputer 330 through a communication
lead 22 so as to carry out a transfer of data.
[0958] FIG. 62 is a block diagram according to an embodiment of a
device for controlling a refrigerating cycle of the present
invention, in which each element of the block diagram corresponds
to the respective element or a combination of each element in FIGS.
63 and 64. In the refrigerating cycle A, the identical element with
that of FIG. 63 has the same abbreviation numeral with that of FIG.
63. A control device C shown by an alternate long and short dash
line in FIG. 62 corresponds to the indoor control section 300 and
the outdoor control section 400, in which a processing section C1
of the control device C corresponds to the microcompnter 330 of the
indoor control section 300 and the microcompnter 470 of the outdoor
control section 400. An input section C2 corresponds to the
receiver section 304 of the indoor unit or a manual switch that is
not shown in the figure, a detector section C3 corresponds to the
temperature sensors 302, 303, 402, 403, 405, pressure detection
means for detecting pressure, flow rate detection means for
detecting flow rate, voltage/current detection means for detecting
voltage/current or frequency detection means for detecting
frequency, each means being not shown in the figure.
[0959] An electrically-driven expansion valve driving section C4,
indoor heat exchanger driving section C5, outdoor heat exchanger
driving section C6 and compressor driving section C7 are means to
function when a control program according to each embodiment
mentioned later is carried out. Each driving section mentioned
above is a driver shown in FIG. 63.
[0960] The electrically-driven expansion valve driving section C4
outputs control signals to an electrically-driven expansion valve
drive source (e.g. stepping motor) 404 and controls an opening
ratio of a throttle of the electrically-driven expansion valve 10A
through the electrically-driven expansion valve drive source 404.
The indoor heat exchanger driving section C5 outputs control
signals to an indoor heat exchanger drive source (e.g. fan motor)
301 that drives the cross flow fan 91A so as to operate or halt it
in response to the control signal and controls a heat exchange
capacity of the indoor heat exchanger 9A by the number of
revolution. The outdoor heat exchanger driving section C6 outputs
control signals to an outdoor heat exchanger drive source (e.g. fan
motor) 401 that drives the cross flow fan 91B so as to operate or
halt it in response to the control signal and controls a heat
exchange capacity of the outdoor heat exchanger 9B by the number of
revolution. The compressor driving section C7 outputs control
signals to a compressor power source (e.g. inverter module or
motor) 450 that controls the compressor 4 for a normal rotation,
inverse rotation, start, halt and selection of its capacity. The
compressor power source 450 is not limited to a motor and may be an
engine.
[0961] Thus, in the refrigerating cycle A, an opening of the
throttle of the electrically-driven expansion valve 10A is
controlled, thereby a flow rate and a rate of change in a flow rate
in the refrigerating cycle A is controlled. The indoor heat
exchanger 9A and the outdoor heat exchanger 9B are drived or halted
and heat exchange capacity thereof is controlled, thereby a
pressure of the refrigerant in the indoor heat exchanger 9A, the
outdoor heat exchanger 9B and the refrigerating cycle A is
controlled. A normal rotation, inverse rotation, start, halt and
selection of its capacity of the compressor 4 are controlled,
thereby a pressure and a rate of change in a pressure of the
refrigerant, and a flow rate and a rate of change in a flow rate of
the refrigerant in the refrugerating cycle A are controlled.
Consequently, a physical quantity such as a pressure, differential
pressure and flow rate, and a rate of change in a physical quantity
such as a rate of change in pressure, rate of change in
differential pressure and rate of change in flow rate in the
channel selector valve 100 in the refrigerating cycle A are
controlled. Accordingly, in each embodiment of a channel selector
valve mentioned later, non-electrical motive power is generated due
to the physical quantity or the rate of change in the physical
quantity mentioned above, then a channel is changed by the channel
selector valve 100.
[0962] The control device C controls a functional component such as
the electrically-driven expansion valve 10A, indoor heat exchanger
9A, outdoor heat exchanger 9B and compressor 4 in order to generate
non-electrical motive power on the basis of a physical quantity
concerning an operation control of the refrigerating cycle such as
a pressure, temperature, flow rate, voltage, current, electric
frequency and mechanical oscillation frequency. The refrigerating
cycle is not limited to a heat pump-type air-conditioner and may be
a heat pump-type chiller unit, engine drive-type or car
air-conditioner.
[0963] FIG. 65 is a block diagram illustrating a flow of signal and
action according to an embodiment of a device for controlling a
refrigerating cycle of the present invention, in which an
instruction for a heating or cooling operation by the remote
control 500 and so on, or a demand for change of a channel by the
channel selector valve through a change of the operation mode is
inputted in the control section C. Then, as a first step, the
control section C outputs signals with respect to "control of the
compressor", "control of the heat exchanger" or "control of the
throttle device". Then, as a result of various controls mentioned
above, as a second step, a state of the physical quantity or the
rate of change in the physical quantity of the refrigerating cycle
changes, thereby, as a third step, a selector operation is carried
out in a channel selector valve 100 according to each embodiment
described later. The electrically-driven expansion valve 10A is an
example of the throttle device.
[0964] Thus, in the present invention, an electric conduction to an
electromagnetic coil by e.g. a relay contact or a
semiconductor-type switch is not employed in order to select a
channel by the channel selector valve.
[0965] In the following, some actual examples of control operation
corresponding to the channel selector valve 100 or 50 according to
the embodiment mentioned above will be explained.
[0966] In the following, a control operation of the control device
C that controls the channel selector valve according to the first
embodiment will be explained with reference to a flow chart. The
processing section C1 of the control device C performs a control
action by the microcomputer 330 of the indoor control section 300
and the microcomputer 470 of the outdoor control section 400. These
microcomputers 330 and 470 in cooperation perform a control
corresponding to each flow chart explained below with performing a
transfer of data by a serial communication.
[0967] FIGS. 66 and 67 are a part of a flow chart of a main
routine, which is common as to the channel selector valve according
to each embodiment from the first to twenty second embodiment. In
the main routine, a power-on reset at a first priority level sets a
first start, then at step S11 "initialization processing-1" such as
a whole clear of RAM is performed so as to proceed to step S23. A
second priority level by a reset of a watchdog timer or a calling
off of a wait sets a second start, then "initialization
processing-2" such as a partial clear of RAM is performed to
proceed to step S13.
[0968] At step S13, an initialization processing of the control
device is performed, then at step S14 an input processing of an
operation instriction, which inputs operation signals by the remote
control 500 or a switch, is performed, then at step S15 an input
processing, which inputs a physical quantity concerning an
operation control of the refrigerating cycle such as a pressure,
temperature, flow rate, voltage, current, electric frequency and
mechanical oscillation frequency is performed, and then at step S16
a general processing, which performs computation, comparison,
judgement, determination of a control condition of the
refrigerating cycle and so on, is performed so as to proceed to
step S17.
[0969] At step S17, it is judged whether a data is normal or
abnormal as a result of the processing. If abnormal, in step S18 it
is judged whether a degree of the abnormality requires a standby or
not, then if required, the standby is set, and if not required, an
operation of the refrigerating cycle is halted at step S19, then
the system proceeds to step S101 in FIG. 67. At step S101, it is
judged whether the command is "select channel" or not, then if so,
the system proceeds to step S102, and if not so, the system
proceeds to step S105. At step S102 the operation is set standby
for a third predetermined period of time (about 30 seconds), at
step S103 an operation of the compressor 4 is started with a second
predetermined capacity (e.g. 10 Hz), and at step S104 the position
data is set to be the first position after a first predetermined
period of time (about 10 seconds), then the system proceeds to step
S108. At step 108, an operation of the refrigerating cycle is
halted, then the system proceeds to step S109 in FIG. 66. At step
S109, the system is on standby for a predetermined period of time
until restart, then comes back to step S14.
[0970] On the other hand, if a data is normal at step S17, it is
judged whether an operation of the refrigerating cycle is to be
started or not, and if not, the system comes back to step S14, and
if to be started, the system proceeds to step S111. At step S111,
by each sub routine mentioned later, a drive processing of the
functional component such as the compressor, electrically-driven
expansion valve and heat exchange motor in response to each
embodiment and a detection processing for detecting a position of
the movable member (e.g. the piston cylinder 12) of the channel
selector valve are performed, thereby a control of selection of the
channel selector valve according to each embodiment is carried
out.
[0971] At step S112, it is judged whether a position data of the
movable member of the channel selector valve coincides with a
command data or not, then if not, the system proceeds to step S19,
and if coincides, various output processing such as a display is
performed at step S113, then the system proceeds to step S114. At
step S114, it is judged whether an operation of the refrigerating
cycle is to be continued or not, then if not, the system proceeds
to step S19, and if to be continued, at step S115 it is judged
whether the command is "select channel" or not. If not, the system
comes back to step S14, while if so, the system performs a
processing of an operation or halt of the compressor in response to
each embodiment at step S116, then comes back to step S14.
[0972] FIG. 68 is a flow chart of a sub-routine (step S111) for a
channel selector valve (FIGS. 1 and 2) according to the first
embodiment of the present invention. At step S21, it is watched
whether an operation of the refrigerating cycle is to be started or
not, and if to be started, it is judged whether the command is
"select channel" or not at step S22. If not, an operation of the
compressor 4 is started with a second predetermined capacity (e.g.
10 Hz), then the system proceeds to step S26, while if the command
is "select channel", a processing for transferring the liquid
refrigerant in FIG. 69 is performed at step S24, then an operation
of the compressor 4 is started with a first predetermined capacity
(e.g. 30 Hz) at step S25 and then, the system proceeds to step S26.
Here, the step S23 corresponds to claim 87 and the step S25
correspomds to claim 76.
[0973] At step S26 a drive processing (normal processing) of the
throttle device is performed, at step S27 a drive processing
(normal processing) of the heat exchanger motor is performed, and
at step S28 a detection processing of a position of the channel
selector valve is performed, thereby the system comes back to a
main routine. In this detection processing of a position of the
channel selector valve, a state of a channel in the channel
selector valve, i.e. a position of the movable member is detected
by comparing a temperature Tc of the indoor heat exchanger 9A with
a temperature Tc' of the outdoor heat exchanger 9B. The state of a
channel in the channel selector valve may be detected by comparing
a pressure of the indoor heat exchanger 9A with a pressure of the
outdoor heat exchanger 9B. When a slide valve 27 of the channel
selector valve moves, there is a short cycle mode (a phenomenon
that a high pressure side is connected to a low pressure side) even
though it appears in a short period of time. At this time, there is
a load change of the compressor 4, which appears as a fluctuation
in a load current. Therefore, such a method may be employed that a
state of selection of the channel selector valve is detected by
watching the load current when the command "select channel" by the
channel selector valve is set. For this purpose, the load current
is watched by detecting a voltage between both ends of a shunt
resistor shown in FIG. 64.
[0974] A processing for transferring a liquid refrigerant shown in
FIG. 69 corresponds to claim 77. At step S241 an operation of the
compressor 4 is started with a second predetermined capacity (e.g.
10 Hz), at step S242 an operation of the refrigerating cycle is
performed for a fourth predetermined period of time (equal to or
longer than about three minutes), and at step S243 an operation of
the refrigerating cycle is halted for a fifth predetermined period
of time (shorter than about three minutes), then the system comes
back to the former routine. This processing for transferring a
liquid refrigerant may be omitted, although the movable member
easily moves, if this processing is included.
[0975] In the processing of an operation or halt of the compressor
at step S116 of the main routine, the compressor 4 is operated with
a third predetermined capacity (e.g. 5 Hz) in the first embodiment
and the system comes back to step S14, which corresponds to claim
83.
[0976] With the processings described above, when a channel is not
swithed by the channel selector valve, the movable member is held
at the first position at step S23, while when a channel is
switched, the movable member is moved from the first position to
the second position at step S25.
[0977] If a connection relationship between the pipes 7 and 8 and
heat exchangers 9A and 9B in the first embodiment is reversed, a
control of the system can be performed in such a manner that the
piston cylinder 12 is situated at the second position in the
heating mode and that the piston cylinder 12 is situated at the
first position in the cooling mode.
[0978] FIG. 70 is a flow chart of a sub-routine (step S111 in FIG.
66) for a channel selector valve (FIGS. 9 to 14) according to the
fifth embodiment of the present invention. At step S31 it is
watched whether an operation of the refrigerating cycle is to be
started or not, and if to be started, it is judged whether the
command is "select channel" or not at step S32. If the command is
not "select channel", it is judged whether the position data is the
first position or not, and if not the first position, the system
proceeds to step S38, while if the first position, an operation of
the compressor 4 is started with a first predetermined capacity
(e.g. 30 Hz) at step S34 and the position data is renewed to the
second position after a first predetermined period of time (e.g.
about 10 seconds) at step S35. Then, at step S36 an operaion of the
refrigerating cycle is halted, at step S37 the operation is set
standby for a third predetermined period of time (about 30 seconds)
and then, the system proceeds to step S38. At step S38 an operation
of the compressor 4 is started with a second predetermined capacity
(e.g. 10 Hz), at step S39 the compressor 4 is operated with a
predetermined capacity (corresponding to a load) after a first
predetermined period of time (about 10 seconds) and then, the
system proceeds to step S308.
[0979] On the other hand, if the command is "select channel" at
step S32, it is judged whether the position data is the second
position or not at step S301, and if not the second position, the
system proceeds to step S306, while if the second position, an
operation of the compressor 4 is started with a second
predetermined capacity (e.g. 10 Hz) at step S302, then the position
data is renewed to the first position after a first predetermined
period of time (about 10 seconds) at step S303. Then, at step S304
an operation of the refrigerating cycle is halted, at step S305 the
operation is set standby for a third predetermined period of time
(about 30 seconds), and the system proceeds to step S306. At step
S306 an operation of the compressor 4 is started with a first
predetermined capacity (e.g. 30 Hz), at step S307 the compressor 4
is operated with a predetermined capacity (corresponding to a load)
after a first predetermined period of time (about 10 seconds), then
the system proceeds to step S308.
[0980] At step S308 a drive processing (normal processing) of the
throttle device is performed, at step S309 a drive processing
(normal processing) of the heat exchanger motor is performed, and
at step S310 a detection processing of a position of the channel
selector valve is performed similarly to the step S28, then the
system comes back to the main routine (FIG. 66). The steps S34 to
S37 and S302 to S305 correspond to claim 74.
[0981] In the processing of an operation or halt of the compressor
at step S116 of the main routine, a processing to halt an operation
of the compressor 4 is performed in the fifth embodiment and
following each embodiment starting with the ninth embodiment, and
then the system comes back to step S14, which corresponds to claim
83.
[0982] In the channel selector valve according to the fifth
embodiment, if a connection relationship between the pipes 7 and 8
and heat exchangers 9A and 9B is reversed, a position of selection
of a channel is reversed in response to the operation mode.
[0983] A processing to perform a control of selection of the
cahnnel selector valve according to the thirteenth embodiment and
the channel selector valve 51 according to the fifteenth embodiment
is similar to a control of the channel selector valve according to
the fifth embodiment shown in FIG. 70, in which the channel
selector valve 51 is controlled by controlling an operation of the
compressor 4.
[0984] FIG. 71 is a flow chart of a sub-routine (step S111 in FIG.
66) for a channel selector valve (FIGS. 24 to 27) according to the
ninth embodiment of the present invention. At step S41 it is
watched whether an operation of the refrigerating cycle is to be
started or not, and if to be started, it is judged whether the
command is "select channel" or not at step S42. If the command is
not "select channel", an opening ratio of the electrically-driven
expansion valve is set almost fully closed, at step S44 an
operation of the compressor 4 is started with a second
predetermined capacity (e.g. 10 Hz), at step S45 the opening ratio
of the electrically-driven expansion valve is set back to a
predetermined opening ratio (corresponding to a load) after a first
predetermined period of time (about 10 seconds), then the system
proceeds to step S49.
[0985] On the other hand, if the command is "select channel" at
step S42, the opening ratio of the electrically-driven expansion
valve is set almost fully opened at step S46, an operation of the
compressor 4 is started with a first predetermined capacity (e.g.
30 Hz) at step S47, the opening ratio of the electrically-driven
expansion valve is set back to a predetermined opening ratio
(corresponding to a load) after a first predetermined period of
time (about 10 seconds) at step S48, then the system proceeds to
step S49.
[0986] At step S49 a drive processing (normal processing) of the
throttle device is performed, and at step S401 a detection
processing of a position of the channel selector valve is performed
similarly to the step S28, then the system comes back to the main
routine (FIG. 66). The steps S43 and S46 correspond to claim 78,
while the step S48 corresponds to claim 81.
[0987] In FIGS. 24 and 25, the capillary tube 10B is provided
between the channel 14A and the indoor heat exchanger 9A and the
electrically-driven expansion valve 10A is provided between the
channel 14A and the outdoor heat exchanger 9B. Instead, positions
of the capillary tube 10B and the electrically-driven expansion
valve 10A can be changed with each other. In this case, a control
can be performed by replaceing steps S42, S43 and S46 in a flow
chart shown in FIG. 71 with steps S42', S43' and S46' in a flow
chart shown in FIG. 72. That is, if the command is not "select
channel" at step S42', an opening ratio of the electrically-driven
expansion valve is set almost fully opened at step S43', then the
system proceeds to step S44, while if the command is "select
channel" at step S42', an opening ratio of the electrically-driven
expansion valve is set almost fully closed at step S46', then the
system proceeds to step S47.
[0988] FIG. 73 is a flow chart of a sub-routine (step S111 in FIG.
66) for a channel selector valve according to the tenth embodiment
(FIGS. 28 and 29) of the present invention. At step S51 it is
watched whether an operation of the refrigerating cycle is to be
started or not, and if to be operated, it is judged whether the
command is "select channel" or not at step S52. If the command is
not to swtch a channel, at step S53 an operation of the compressor
4 is started with a second predetermined capacity (e.g. 10 Hz), at
step S54 a drive processing (normal processing) of the
electrically-driven expansion valve is performed, at step S55 a
drive processing (normal processing) of the heat exchanger motor is
performed, and at step S56 the compressor 4 is operated with a
predetermined capacity (corresponding to a load) after a first
predetermined period of time (about 10 seconds), then the system
proceeds to step S502.
[0989] On the other hand, if the command is "select channel" at
step S52, an operation of the compressor 4 is started at step S57
and drived at a specific frequency. Then, at step S58 a drive
processing (normal processing) of the throttle device is performed,
at step S59 a drive processing (normal processing) of the heat
exchanger motor is performed, and at step S501 the compressor 4 is
operated with a predetermined capacity (corresponding to a load)
after a first predetermined period of time (about 10 seconds), then
the system proceeds to step S502. At step S502 a detection
processing of a position of the channel selector valve is performed
similarly to the step S28, then the system comes back to the main
routine (FIG. 66). The step S57 corresponds to claim 75 and the
step S501 corresponds to claim 80.
[0990] With the processings mentioned above, a control of selection
of the channel selector valve is carried out by resonating the
pilot oscillation valve 30 with the compressor 4.
[0991] FIG. 74 is a flow chart of a sub-routine (step S111 in FIG.
66) for a channel selector valve according to the eleventh
embodiment (FIGS. 30 and 31) of the present invention. At step S61
it is watched whether an operation of the refrigerating cycle is to
be started or not, and if to be started, it is judged whether the
command is "select channel" or not at step S62. If the command is
not "select channel", at step S63 a drive processing (normal
processing) of the heat exchanger motor is performed, at step S64
an operation of the compressor 4 is started with a second
predetermined capacity (e.g. 10 Hz), at step S65 the compressor 4
is operated with a predetermined capacity (corresponding to a load)
after a first predetermined period of time (about 10 seconds), and
at step S66 a drive processing (normal processing) of the throttle
device is performed, then the system proceeds to step S603.
[0992] On the other hand, if the command is "select channel" at
step S62, at step S67 an operation of the heat exchanger motor is
kept halted, at step S68 an operation of the compressor 4 is
started with a first predetermined capacity (e.g. 30 Hz), and at
step S69 an operation of the heat exchanger motor is started after
a second predetermined period of time (about 20 seconds), then an
operation of the heat exchanger motor is started. Then, at step
S601 the compressor 4 is operated with a capacity required to hold
the movable member (e.g. the piston cylinder 12) at the second
position, and at step S602 a drive processing (normal processing)
of the throttle device is performed, then the system proceeds to
step S603. At step S603 a detection processing of a position of the
channel selector valve is performed similarly to the step S28, then
the system comes back to the main routine (FIG. 66). The step 67
corresponds to claim 79 and the steps S69 and S601 correspond to
claim 82.
[0993] With the processings mentioned above, a control of selection
of the channel selector valve is carried out by controlling the
heat exchanger.
[0994] In the first to eleventh embodiments mentioned above, the
channel selector valve constructed by employing a slide-type
four-way selector valve is explained. In the following, an
embodiment, in which the present invention is applied to a rotary
channel selector valve that performs its channel selector operation
by rotation of a main valve element in a valve housing will be
explained.
[0995] A schematic constitution of a refrigerating cycle A
employing a rotary channel selector valve will be explained with
reference to FIG. 35, in which the same abbreviation numerals with
those used for the corresponding identical members or parts of the
refrigerating cycle A shown in FIG. 63 are used.
[0996] In FIG. 35, a channel of the refrigerant in the cooling mode
is shown by solid lines while that in the heating mode is shown by
broken lines. In this refrigerating cycle A, a place where the high
pressure refrigerant discharged from the compressor 4 is guided to
and a place where the refrigerant to be sucked by the compressor 4
by way of an accumulator 200 is guided from are mutually selected
out of the indoor heat exchanger 9A and the outdoor heat exchanger
9B by a rotary four-way selector valve 50, and an
electrically-driven expansion valve 10A is provided between the
indoor heat exchanger 9A and the outdoor heat exchanger 9B.
Pressure sensors Pc and Pc' are disposed at the indoor heat
exchanger 9A and the outdoor heat exchanger 9B, respectively, to
detect each pressure, thereby a position of the movable member can
be detected. These pressure sensors may be disposed at a channel
near the rotary four-way selector valve 50.
[0997] FIG. 75 is a flow chart of a sub-routine (step S111 in FIG.
66) for a channel selector valve 81 according to the eighteen
embodiment of the present invention. At step S71 a judge processing
of an operation command by a microcomputer is performed, and at
step S72 it is judged whether an opeation mode required is the
cooling mode or not. If the cooling mode is required, processings
starting from step S73 are performed, on the other hand if the
heating mode is required, processings starting from step S703 are
performed.
[0998] At step S73 it is judged whether a position data is the
first position or not, and if not, the system proceeds to step S78,
on the other hand if the first position, at step S74 an operation
of the compressor 4 is started in its inverse direction, then at
step S75 the position data is renewed into the second position
after a first predetermined period of time (e.g. 10 seconds). Then,
at step S76 an operation of the refrigerating cycle is halted,. an
at step S77 an operation thereof is set standby for a third
predetermined period of time (about 30 seconds), then the system
proceeds to step S78. At step S78 an operation of the compressor 4
is started with a first predetermined capacity (e.g. 30 Hz), then
at step S79 the compressor 4 is operated with a predetermined
capacity (corresponding to a load) after a first predetermined
period of time (e.g. 10 seconds). Then, at step S701 it is watched
whether there is an indication of halt of an operation (cooling
operation) or not, and if there is, at step S702, an operation of
the compressor 4 is halted and the system is set standby for a
third predetermined period of time (about 30 seconds) with keeping
the position data to be the second position, then the system comes
back to the former routine.
[0999] On the other hand, at step S72 if the heating mode is
required, at step S703 it is judged whether a position data is the
second position or not, and if not, the system proceeds to step
S708, on the other hand if the second position, at step S704 an
operation of the compressor 4 is started in its inverse direction,
then at step S705 the position data is renewed into the first
position after a first predetermined period of time (e.g. 10
seconds). Then, at step S706 an operation of the refrigerating
cycle is halted, an at step S707 an operation thereof is set
standby for a third predetermined period of time (about 30
seconds), then the system proceeds to step S708. At step S708 an
operation of the compressor 4 is started with a first predetermined
capacity (e.g. 30 Hz), then at step S709 the compressor 4 is
operated with a predetermined capacity (corresponding to a load)
after a first predetermined period of time (e.g. 10 seconds). Then,
at step S710 it is watched whether there is an indication of halt
of an operation (heating operation) or not, and if there is, at
step S711, an operation of the compressor 4 is halted and the
system is set standby for a third predetermined period of time
(about 30 seconds) with keeping the position data to be the first
position, then the system comes back to the former routine.
Industrial Applicability
[1000] According to a channel selector valve of the present
invention as described in claim 1, since a channel selection of
fluid by the channel selector valve is performed by employing
non-electric motive power, there is no necessity of using an
electrically-driven drive source such as an electromagnetic
solenoid, resulting in decreasing cause of fault to occur,
improving a reliability of the operation, contributing to
prevention of environmental pollution due to an operation at a
power plant and powerful promotion of energy saving and the
like.
[1001] According to the channel selector valve of the present
invention as described in claim 2, in the channel selector valve of
the present invention as described in claim 1, a channel selection
of fluid by the channel selector valve is passively performed using
motive power generated by a non-electrically-driven drive source
provided separately from the channel selector valve, therefore
there is no necessity for the channel selector valve to have a
source for generating motive power.
[1002] According to the channel selector valve of the present
invention as described in claim 3, in the channel selector valve of
the present invention as described in claim 2, at least one of
element components in a refrigerating cycle having the channel
selector valve is used as the drive source, therefore there is no
necessity to newly provide a drive source for selecting a channel
by a channel selector valve.
[1003] According to the channel selector valve of the present
invention as described in claim 4, in the channel selector valve of
the present invention as described in claim 3, the element
component in the refrigerating cycle acts so that a change in a
physical quantity is generated in the refrigerating cycle,
therefore a selection of a channel of fluid by the channel selector
valve is performed as a consequence.
[1004] According to the channel selector valve of the present
invention as described in claim 5, in the channel selector valve of
the present invention as described in claim 4, at least one change
among changes in pressure, differential pressure and flow rate of
fluid in the channel selector valve arising from an action of the
element component in the refrigerating cycle is used, therefore a
selection of a channel by the channel selector valve can be easily
performed by using such a change in physical quantity generated in
the refrigerating cycle as motive power.
[1005] According to a channel selector valve of the present
invention as described in claim 6, a selection of a place where a
main port is communicated to between two selector ports, which is
achieved by moving a movable member between the first and second
positions, can be performed without using electric motive power,
resulting in decreasing cause of fault to occur. Therefore, there
is no necessity of a drive source to genarate electric motive
power, resulting in decreasing cause of fault to occur, improving a
reliability of the operation, contributing to prevention of
environmental pollution due to an operation at a power plant and
powerful promotion of energy saving and the like.
[1006] According to the channel selector valve of the present
invention as described in claim 7, in the channel selector valve of
the present invention as described in claim 6, the element
component in the refrigerating cycle acts so that a change in a
physical quantity is generated in the refrigerating cycle,
therefore a selection of a channel of fluid by the channel selector
valve is performed as a consequence without a drive source newly
provided.
[1007] According to the channel selector valve of the present
invention as described in claim 8, in the channel selector valve of
the present invention as described in claim 7, at least one change
among changes in pressure, differential pressure and flow rate of
fluid in the channel selector valve arising from an action of the
element component in the refrigerating cycle is used, therefore a
selection of a channel by the channel selector valve can be easily
performed by using such a change in physical quantity generated in
the refrigerating cycle as motive power.
[1008] According to a channel selector valve of the present
invention as described in claim 9, a first and second three-way
selector valves constituted by the channel selector valve according
to claim 6, 7 or 8 are combined, therefore a four-way selector
valve, which can select a channel of fluid, is easily constructed
without using electric motive power by a simple combination of
valves usable separately.
[1009] According to the channel selector valve of the present
invention as described in claim 10, in the channel selector valve
of the present invention as described in claim 9, an action of a
first three-way selector valve is incorporated with that of a
second three-way selector valve so that the channel selector valve
functions securely as a four-way selector valve by the
combination.
[1010] According to the channel selector valve of the present
invention as described in claim 11, in the channel selector valve
of the present invention as described in claim 10, the movable
member of the first three-way selector valve situated at the first
position is moved to the second position by a first drive mechanism
of the first three-way selector valve, while the movable member of
the first three-way selector valve situated at the second position
is moved to the first position by a second drive mechanism, a
pressure of fluid at the first selector port is set equal to that
at the second selector port, thereby a movement of the movable
member of the second three-way selector valve is passively
performed.
[1011] According to the channel selector valve of the present
invention as described in claim 12, in the channel selector valve
of the present invention as described in claim 11, a pressure of
fluid at the main port is suitably adjusted in response to a
position of the movable member of the first three-way selector
valve, and an energizing force to move the movable member of the
first three-way selector valve to a different position is stored in
storing means for storing energizing force, the movable member of
the first three-way selector valve is moved by the energizing force
without using electric motive power, thereby the movable member of
the second three-way selector valve can be passively moved without
using electric motive power.
[1012] According to the channel selector valve of the present
invention as described in claim 13, in the channel selector valve
of the present invention as described in claim 6, 7 or 8, by using
a channel selector valve that solely constructs a four-way selector
valve, a place where fluid introduced from the exterior of the
housing flows to and a place where fluid discharged to the exterior
of the housing is introduced from can be selected without using
electric motive power.
[1013] According to the channel selector valve of the present
invention as described in claim 14, in the channel selector valve
of the present invention as described in claim 13, the movable
member can be moved without using electric motive power due to a
difference between a pressure of fluid introduced from the exterior
of the housing and a pressure of fluid discharged to the exterior
of the housing, which is generated between the first space of the
first pressure chamber partitioned by the movable member in the
housing and the second pressure chamber, thereby a channel of fluid
can be selected.
[1014] According to a method of driving the channel selector valve
of the present invention as described in claim 15, when the channel
selector valve of the present invention as described in claim 14 is
drived, even if there is no difference between a pressure of fluid
in the first space and a pressure of fluid in the second pressure
chamber, the movable member can be moved from the second position
to the first position by an energizing force of the energizing
means, and a difference between a pressure of fluid in the first
space and a pressure of fluid in the second pressure chamber is set
in response to the energizing force of the energizing means so that
the movable member is held at the first or second position, thereby
a selection state of a channel of fluid can be maintained.
[1015] According to the channel selector valve of the present
invention as described in claim 16, in the channel selector valve
of the present invention as described in claim 14, the movable
member easily can be kept being situated at the first or second
position by making use of a static friction force between the valve
seat and the movable member.
[1016] According to a method of driving the channel selector valve
of the present invention as described in claim 17, when the channel
selector valve of the present invention as described in claim 16 is
drived, a selection of a channel of fluid that is achieved by
moving the movable member from the first position to the second
position is carried out by using a change in pressure of fluid in
the first space without using electric motive power generated by an
electrically-driven drive source such as an electromagnetic
solenoid and the like, thereafter a selection state, in which the
movable member is situated at the second position, can be
maintained.
[1017] According to the channel selector valve of the present
invention as described in claim 18, in the channel selector valve
of the present invention as described in claim 14 or 16, the
movable member can be moved between the first and second positions
by making use of an internal pressure of the housing, which is
changed by fluid introduced from the exterior into the interior of
the housing by way of an inlet port of the housing, without using
electric motive power generated by an electrically-driven drive
source such as an electromagnetic solenoid and the like.
[1018] According to the channel selector valve of the present
invention as described in claim 19, in the channel selector valve
of the present invention as described in claim 18, a selector valve
element of a non-electrically-driven pilot valve is moved between a
fifth position and a sixth position, thereby a place in which a
pressure of fluid is lower than that in the first space of the
first pressure chamber is selected between the second pressure
chamber and the third pressure cahmber, which are partitioned by
the movable member and situated sandwiching the first pressure
chamber therebetween, the movable member is moved by a motive power
as low as a power required to perform a selection of the selector
valve element of the pilot valve, and a selection of a channel of
fluid can be carried out.
[1019] According to the channel selector valve of the present
invention as described in claim 20, in the channel selector valve
of the present invention as described in claim 19, when a
difference between a pressure of fluid in the second pressure
chamber and that in the third pressure chamber cancels out, the
selector valve element is moved from one to another between the
fifth and sixth positions by second driving means, thereby the
movable member can be moved from one to another between the first
and second positions without using electric motive power.
[1020] According to the channel selector valve of the present
invention as described in claim 21, in the channel selector valve
of the present invention as described in claim 20, a difference in
a pressure of fluid is generated between a fourth pressure chamber
and a fifth pressure chamber of the pilot valve with making these
chambers be communicated to or isolated with the second or third
pressure chamber, by using a first or second subvalve in response
to a movement of the movable member, and an energizing force is
suitably stored to third or fourth storing means for storing
energizing force, thereby a movement of the selector valve element
in the pilot valve over a range from a fifth position to an eighth
position, which is for generating a difference in a pressure of
fluid between the third and second pressure chambers, said
difference being transformed into a motive power to move the
movable member, can be performed without using electric motive
power.
[1021] According to the channel selector valve of the present
invention as described in claim 22, in the channel selector valve
of the present invention as described in claim 19, when a
difference between a pressure of fluid in the second pressure
chamber and that in the third pressure chamber cancels out, the
selector valve element is moved from one to another between the
fifth and sixth positions by second driving means, thereby the
movable member can be moved from one to another between the first
and second positions without using electric motive power.
[1022] According to the channel selector valve of the present
invention as described in claim 23, in the channel selector valve
of the present invention as described in claim 22, an energizing
force is suitably stored to third or fourth storing means for
storing energizing force of the pilot valve by using a difference
in a pressure of fluid generated between a second pressure chamber
and a third pressure chamber, thereby the selector valve element is
moved to a seventh or eighth position when a difference between a
pressure of fluid in the second pressure chamber and that in the
third pressure chamber cancels out, thereby making a change in a
difference in pressure between fluid in a fourth pressure chamber
of the pilot valve, which communicates with the third pressure
chamber, and fluid in a fifth pressure chamber of the pilot valve,
which communicates with the second pressure chamber, thereby the
movable member can be moved from one to another between the first
and second positions without using electric motive power.
[1023] According to the channel selector valve of the present
invention as described in claim 24, in the channel selector valve
of the present invention as described in claim 14 or 16, the
movable member is moved from one to another between the first and
second positions by changing a pressure of fluid introduced from
the exterior to the interior of the housing by way of an inlet port
of the housing, while the movable member is moved from another to
one between the first and second positions only or supplementarily
by using an energizing force stored in the energizing means,
thereby a selection of a channel by the channel selector valve can
be easily and securely achieved without using electric motive
power.
[1024] According to the channel selector valve of the present
invention as described in claim 25, in the channel selector valve
of the present invention as described in claim 24, the movable
member situated at either the first or second position is stayed at
one position or moved to another position selectively, thereby a
selection of a channel by the channel selector valve can be
securely achieved without using electric motive power.
[1025] According to the channel selector valve of the present
invention as described in claim 26, in the channel selector valve
of the present invention as described in claim 25, the latch
mechanism selectively performs the first or second state, thereby a
selection of a channel by the channel selector valve can be
securely achieved without using electric motive power.
[1026] According to the channel selector valve of the present
invention as described in claim 27, in the channel selector valve
of the present invention as described in claim 26, a selection of a
channel by the channel selector valve can be achieved without
directly affecting a large impact to the movable member, that is,
without directly applying a control to a movement of the movable
member.
[1027] According to a method of driving the channel selector valve
of the present invention as described in claim 28, in the channel
selector valve of the present invention as described in claim 26 or
27, after a control of a movement of the movable member situated at
one position by the latch mechanism is removed, the movable member
can be securely moved from the one position to another position, in
addition, the latch mechanism can control a movement of the movable
member, that is, securely control the movable member to be situated
at the one position.
[1028] According to the channel selector valve of the present
invention as described in claim 29, in the channel selector valve
of the present invention as described in claim 24, when the second
latch mechanism controls a movement of a valve-opening member, the
movable member, which is moved from one position to another
position by the third drive mechanism, can move from the another
position to the one position by the fourth drive mechanism, while
to the contrary, when the second latch mechanism does not control a
movement of a valve-opening member, the movable member, which is
moved from one position to another position by the third drive
mechanism, can be held at the another position by using a motive
power of the third drive mechanism without using an exclusive drive
source and the like.
[1029] According to the channel selector valve of the present
invention as described in claim 30, in the channel selector valve
of the present invention as described in claim 29, a state, in
which the movable member moved from one position to another
position by the third drive mechanism is held at the another
position, can be mutually produced whenever the third drive
mechanism generates a motive power.
[1030] According to a method of driving the channel selector valve
of the present invention as described in claim 31, in the channel
selector valve of the present invention as described in claim 29 or
30, the second latch mechanism is transferred between a state in
which a movement of the valve-opening member from the valve-closing
position to the valve-opening position is controlled and a state in
which said control is removed, thereby the system can be
transferred from one state, in which the movable member can move
from the another position to the one position by using a motive
power generated by the fourth drive mechanism, to another state in
which the movable member cannot move from the another position to
the one position, or the system can be transferred from the another
state to the one state.
[1031] According to the channel selector valve of the present
invention as described in claim 32, in the channel selector valve
of the present invention as described in claim 24, a selection,
which is achieved by moving the movable member between the first
and second positions, of a place to which the fluid introduced from
the exterior of the housing into the first space by way of the
inlet port is discharged and a place from which the fluid
discharged from the second space to the exterior of the housing by
way of the outlet port is intriduced, is carried out by a change in
pressure of the fluid introduced into the first space without
usirig an exclusive drive source such as an electromagnetic
solenoid.
[1032] According to the channel selector valve of the present
invention as described in claim 33, in the channel selector valve
of the present invention as described in claim 24, the movable
member moved from the first position to the second position by
using a motive power generated by a non-electrically-driven drive
source can be held at the second position even if the motive power
is not continuously supplied.
[1033] According to the channel selector valve of the present
invention as described in claim 34, in the channel selector valve
of the present invention as described in claim 33, a force applied
to the movable member is adjusted by fluid in the first space,
thereby a selection of a channel by the channel selector valve can
be securely achieved without using an electrically-driven drive
source.
[1034] According to the channel selector valve of the present
invention as described in claim 35, in the channel selector valve
of the present invention as described in claim 34, a force applied
to the movable member is adjusted by fluid in the first space,
thereby a selection of a channel by the channel selector valve can
be securely achieved without using an electrically-driven drive
source, in addition, even if a force applied to the movable member
by a pressure of fluid in the first space becomes equal to a force
applied to the movable member by a pressure of fluid in the second
space, an energizing force of the energizing means moves the
movable member to the first position, thereby the first position
can be set as an initial position of the movable member.
[1035] According to a method of driving the channel selector valve
of the present invention as described in claim 36, when the channel
selector valve of the present invention as described in claim 35 is
drived, a force applied to the movable member in a direction from
the first to second position is set to exceed a force applied to
the movable member in a direction from the second to first
position, thereby the movable member is moved from the first
position to the second position, then the force applied to the
movable member in a direction from the first to second position can
be lowered as long as said force corresponds to a pressure to hold
the movable member at the second position, therefore a degree of
freedom in an operation of the refrigerating cycle can be raised
after the movable member is moved to the second position.
[1036] According to the channel selector valve of the present
invention as described in claim 37, in the channel selector valve
of the present invention as described in claim 7, an opening ratio
of the electrically-driven expansion valve is changed to change a
pressure of fluid, thereby the movable member easily moves between
the first and second positions and a selection of a channel by the
channel selector valve can be securely achieved without using
electric motive power.
[1037] According to the channel selector valve of the present
invention as described in claim 38, in the channel selector valve
of the present invention as described in claim 7, a frequency of an
oscillation generated by the compressor is changed, thereby the
movable member easily moves between the first and second positions
and a selection of a channel by the channel selector valve can be
securely achieved without using electric motive power.
[1038] According to the channel selector valve of the present
invention as described in claim 39, in the channel selector valve
of the present invention as described in claim 7, a difference in
fluid pressure is changed, for example, by changing an efficiency
of heat exchange by the heat exchanger, thereby the movable member
easily moves between the first and second positions and a selection
of a channel by the channel selector valve can be securely achieved
without using electric motive power.
[1039] According to the channel selector valve of the present
invention as described in claim 40, in the channel selector valve
of the present invention as described in claim 13, a space required
for the movable member to move between the first and second
positions can be set smaller than that in a case of a linear
slide-type channel selector valve. Also, the main valve element is
moved by using a difference between a pressure of fluid introduced
from the exterior of the housing and that of fluid discharged to
the exterior of the housing, which is generated between the second
pressure chamber and the first space in the first pressure chamber
partitioned by the main valve element, thereby a channel of fluid
can be selected.
[1040] According to the channel selector valve of the present
invention as described in claim 41, in the channel selector valve
of the present invention as described in claim 40, a pressure of
fluid, which flows into second communication means formed at one
end surface of the main valve element for communicating the ports
of the valve seat with each other, is utilized so as to generate a
rotative thrust of the main valve element, thereby the main valve
element can be rotated without using electric motive power and a
channel of fluid can be selected.
[1041] According to the channel selector valve of the present
invention as described in claim 42, in the channel selector valve
of the present invention as described in claim 41, a fluid in the
inlet port and a fluid in the outlet port, which are formed at a
reverse side of the housing with each other, generate a difference
in pressure of the fluid between both sides of the housing
sandwiching the main valve element, and by utilizing this
difference in pressure the main valve element can be rotated
between the first and second positions without using electric
motive power.
[1042] According to the channel selector valve of the present
invention as described in claim 43, in the channel selector valve
of the present invention as described in claim 40, the main valve
element is moved in a direction of the central axis of the housing
by using non-electric motive power so as to transform this movement
in a direction of the central axis into a rotation in a direction
of circumference of the housing by the conversion means of moving
direction, thereby the main valve element is rotated between the
first and second positions and a channel of fluid can be
selected.
[1043] According to the channel selector valve of the present
invention as described in claim 44, in the channel selector valve
of the present invention as described in claim 43, a movement of
the cam follower pin in the cam groove transforms a movement of the
main valve element in a direction of the central axis by using
non-electric motive power into a rotation in a direction of
circumference of the housing, thereby a channel of fluid can be
selected without using electric motive power.
[1044] According to the channel selector valve of the present
invention as described in claim 45, in the channel selector valve
of the present invention as described in claim 44, when a cam
groove is formed in the housing, a guide of the first half of the
inner housing is joined with a guide of the second half of the
inner housing, thereby the cam follower pin of the main valve
element disposed in the housing can be easily disposed in the cam
groove.
[1045] According to the channel selector valve of the present
invention as described in claim 46, in the channel selector valve
of the present invention as described in claim 44 or 45, the end
surface of the main valve element, on which the second
communication means is formed for communicating the ports of the
valve seat with each other, is away from the valve seat at a
position except the first and second positions where the ports can
communicates with each other by the second communication means,
thereby an equalization of a pressure of the fluid in each port, in
a state that the ports cannot communicate with each other, can be
easily achieved without using electric motive power.
[1046] According to the channel selector valve of the present
invention as described in claim 47, in the channel selector valve
of the present invention as described in claim 46, when the main
valve element is situated at a position except the first and second
positions, where the main valve element is away from the valve seat
so that the ports cannot communicate with each other by the second
communication means, a communication channel, which selectively
communicates the opposite port formed at the opposite end side of
the housing to the two selector ports formed at the valve seat at
the one end side of the housing, is closed by the subvalve
energized toward a direstion of closing by the subvalve energizing
means, thereby an unnecessary communication between the opposite
port and the selector port, in a state that is not a normal
selection state, can be prevented from occurring.
[1047] According to the channel selector valve of the present
invention as described in claim 48, in the channel selector valve
of the present invention as described in claim 47, a part of a
movement of the main valve element toward a direction of the
central axis of the housing, which is needed to rotate the main
valve element, is achieved by moving the main valve element away
from the valve seat with an own weight of the main valve, thereby
non-electric motive power required to move the main valve element
can be reduced.
[1048] According to the channel selector valve of the present
invention as described in claim 49, in the channel selector valve
of the present invention as described in claim 47 or 48, a movement
of the main valve element in the direction away from the valve
seat, which is needed for the movable member to rotate for moving
from one to another between the first and second positions, is
performed only or supplementarily by using an energizing force
stored in the energizing means for energizing the main valve
element, thereby a selection of a channel by the channel selector
valve can be easily and securely achieved without using electric
motive power.
[1049] According to the channel selector valve of the present
invention as described in claim 50, in the channel selector valve
of the present invention as described in claim 47 or 48, a movement
of the main valve element in the direction nearer to the valve
seat, which is needed for the movable member to rotate for moving
from another to one between the first and second positions, is
performed only or supplementarily by using an energizing force
stored in the second energizing means for energizing the main valve
element, thereby a selection of a channel by the channel selector
valve can be easily and securely achieved without using electric
motive power.
[1050] According to the channel selector valve of the present
invention as described in claim 51, in the channel selector valve
of the present invention as described in claim 50, the main valve
element is moved in the direction nearer to the valve seat or in
the direction away from the valve seat by using non-electric motive
power, thereby it is easily to set up whether the main valve
element is repeatedly rotated at the same position out of either
the first or second position or is rotated at a different
position.
[1051] According to the channel selector valve of the present
invention as described in claim 52, in the channel selector valve
of the present invention as described in claim 51, when the cam
follower pin is placed in the groove of the cam groove in order to
situate the main valve element at one position out of the first and
second positions, the main valve element is prevented from rotating
at another position out of the first and second positions upon a
next rotation of the main valve element.
[1052] According to the channel selector valve of the present
invention as described in claim 53, in the channel selector valve
of the present invention as described in claim 51 or 52, when the
cam follower pin is placed in the second groove of the cam groove
in order to situate the main valve element at another position,
which is different from the former position, out of the first and
second positions, the main valve element is prevented from coming
back to the former position upon a next rotation of the main valve
element.
[1053] According to the channel selector valve of the present
invention as described in claim 54, in the channel selector valve
of the present invention as described in any one of claims 40-53, a
movement of the main valve element in the direction nearer to or
away from the valve seat, which is needed to rotate the main valve
element between the first and second positions, can be performed by
smoothly rotating the main valve element between the first and
second positions with the aid of the slide means that reduces a
sliding resistance between the main valve element and the
housing.
[1054] According to a compressor with the channel selector valve of
the present invention as described in claim 55, a compressor, with
which the channel selector valve as described in any one of claims
10-14, 16, 18-27, 29-30, 32-35, and 37-54 is integrated, can be
easily constructed, in addition, since there is no necessity to use
a pipe for forming a high pressure chamber inside, reducing pipe
laying and pipe joining around the compressor, thereby reducing
leak of fluid at the joining portion of pipes and contributing to
prevention of air pollution when the fluid is some kind of
refrigerant. Moreover, since there is no current conducting part
for an electromagnetic solenoid and the like around the compressor
that generates oscillation, the above construction also prevents an
occurrence of an electrical fault due to failure in current
conduction at an electric contact and a breaking of electric wire
and the like, thereby reliance of the operation can be
improved.
[1055] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 56, since the
channel selector valve is controlled by controlling the functional
components for controlling the operation of the refrigerating
cycle, upon a selector operation of a valve such as a four-way
selector valve provided in the refrigerating cycle for selecting a
channel of fluid, prevention of environmental pollution and energy
saving and the like are effectively achieved.
[1056] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 57, the functional
component is controlled to control an operation of the
refrigerating cycle, thereby generating a non-electrical motive
power, by which the channel selector valve is passively controlled,
therefore, upon a selector operation of a valve such as a four-way
selector valve provided in the refrigerating cycle for selecting a
channel of fluid, prevention of environmental pollution and energy
saving and the like are effectively achieved.
[1057] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 58, by using a
microcomputer, which controls an operation of the refrigerating
cycle, the functional component is controlled to control an
operation of the refrigerating cycle, thereby generating a
non-electrical motive power, by which the channel selector valve is
passively controlled, therefore, upon a selector operation of a
valve such as a four-way selector valve provided in the
refrigerating cycle for selecting a channel of fluid, prevention of
environmental pollution and energy saving and the like are
effectively achieved.
[1058] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 59, the functional
component is controlled to control an operation of the
refrigerating cycle, thereby a physical quantity or a rate of
change in the physical quantity is generated as a non-electrical
motive power, by which the channel selector valve is passively
controlled, therefore, upon a selector operation of a valve such as
a four-way selector valve provided in the refrigerating cycle for
selecting a channel of fluid, prevention of environmental pollution
and energy saving and the like are effectively achieved.
[1059] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 60, by using a
microcomputer, which controls an operation of the refrigerating
cycle, the functional component is controlled to control an
operation of the refrigerating cycle, thereby a physical quantity
or a rate of change in the physical quantity is generated as a
non-electrical motive power, by which the channel selector valve is
passively controlled, therefore, upon a selector operation of a
valve such as a four-way selector valve provided in the
refrigerating cycle for selecting a channel of fluid, prevention of
environmental pollution and energy saving and the like are
effectively achieved.
[1060] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 61, the device
acts similarly to the device described in claim 57, 58, 59 or 60,
in addition, in order to generate a non-electrical motive power for
controlling the channel selector valve, the functional component is
controlled on the basis of a physical quantity, which concerns with
a control of an operation of the refrigerating cycle, selected from
the group consisting of a pressure, temperature, rate of flow,
voltage, current, electrical frequency and mechanical oscillation
frequency, therefore, upon a selector operation of a valve such as
a four-way selector valve provided in the refrigerating cycle for
selecting a channel of fluid, prevention of environmental pollution
and energy saving and the like are effectively achieved.
[1061] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 62, the device
acts similarly to the device described in claim 57, 58, 59 or 60,
in addition, the physical quantity, which is the non-electrical
motive power and is generated by the refrigerating cycle, is a
pressure, differential pressure or rate of flow with respect to
fluid existing in the channel selector valve, and the rate of
change in a physical quantity, which is the non-electrical motive
power and is generated by the refrigerating cycle, is a rate of
change in pressure, rate of change in differential pressure or rate
of change in rate of flow with respect to the fluid, therefore,
upon a selector operation of a valve such as a four-way selector
valve provided in the refrigerating cycle for selecting a channel
of fluid, prevention of environmental pollution and energy saving
and the like are effectively achieved.
[1062] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 63, an operational
condition of the refrigerating cycle is commanded from an operation
command section and a physical quantity generated by the
refrigerating cycle is detected in a physical quantity detector
section, then the control section receives input signals sent from
the operation command section and the physical quantity detector
section. Then, the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component, and
the device generates a non-electrical motive power by controlling
the refrigerating cycle and passively controls the channel selector
valve by said motive power, therefore, upon a selector operation of
a valve such as a four-way selector valve provided in the
refrigerating cycle for selecting a channel of fluid, prevention of
environmental pollution and energy saving and the like are
effectively achieved.
[1063] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 64, the device
acts similarly to the device described in claim 63, the control
section controls at least one of a plurality of functional
components communicated to the refrigerating cycle so as to start
an operation of the refrigerating cycle, thereby controlling the
channel selector valve in a state corresponding to the start of an
operation, which is commanded by the operation command section,
therefore, upon a selector operation of a valve such as a four-way
selector valve provided in the refrigerating cycle for selecting a
channel of fluid, prevention of environmental pollution and energy
saving and the like are effectively achieved.
[1064] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 65, the device
acts similarly to the device described in claim 64, in addition,
the control section starts to operate a compressor communicated to
the refrigerating cycle in a direction of inverse rotation when the
control section decides to select the channel selector valve on the
basis of a command of the operation command section, thereby a
channel is selected by the cahnnel selector valve, therefore, upon
a selector operation of a valve such as a four-way selector valve
provided in the refrigerating cycle for selecting a channel of
fluid, prevention of environmental pollution and energy saving and
the like are effectively achieved.
[1065] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 66, the device
acts similarly to the device described in claim 63, in addition,
the control section controls at least one of a plurality of
functional components communicated to the refrigerating cycle so as
to operate the refrigerating cycle, thereby controlling the channel
selector valve in a state corresponding to the operation, which is
commanded by the operation command section, therefore, upon a
selector operation of a valve such as a four-way selector valve
provided in the refrigerating cycle for selecting a channel of
fluid, prevention of environmental pollution and energy saving and
the like are effectively achieved.
[1066] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 67, the device
acts similarly to the device described in claim 63, in addition,
the control section controls at least one of a plurality of
functional components communicated to the refrigerating cycle so as
to halt an operation of the refrigerating cycle, thereby
controlling the channel selector valve in a state corresponding to
the halt of the operation, which is commanded by the operation
command section, therefore, upon a selector operation of a valve
such as a four-way selector valve provided in the refrigerating
cycle for selecting a channel of fluid, prevention of environmental
pollution and energy saving and the like are effectively
achieved.
[1067] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 68, the device
acts similarly to the device as described in any one of claims
63-67, in addition, the channel selector valve is constructed in a
manner that a movable member moves so as to select a channel, and
the control section comprises at least one unit selected from the
group consisting of: a memory unit for memorizing position data of
the movable member of the channel selector valve; a comparison unit
and a judge unit for comparing and judging, respectively, the
position data and operation command data; and a learning unit
learning on the basis of physical quantity data by a control of
functional components and control data of the channel selector
valve, therefore, upon a selector operation of a valve such as a
four-way selector valve provided in the refrigerating cycle for
selecting a channel of fluid, prevention of environmental pollution
and energy saving and the like are effectively achieved, and in
addition, a secure control of the refrigerating cycle can be
performed.
[1068] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 69, the device
acts similarly to the device as described in claim 68, in addition,
the control section receives the input signals, performs a
predetermined processing and judges whether a channel is to be
changed or not to be changed by the channel selector valve, then
confirms a position on the basis of present position data, then
sends the output signals to the driving section so as to control
the functional components in the refrigerating cycle, then receives
new input signals after a predetermined period of time, confirms a
position of the movable member, and sets position data of said
position as new present position data when said position is changed
to a new position, therefore, upon a selector operation of a valve
such as a four-way selector valve provided in the refrigerating
cycle for selecting a channel of fluid, prevention of environmental
pollution and energy saving and the like are effectively achieved,
and in addition, a secure control of the refrigerating cycle can be
performed.
[1069] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 70, the device
acts similarly to the device as described in claim 69, in addition,
the control section confirms a position of the movable member by at
least one temperature detection means, at least one pressure
detection means, at least one magnetic detection means, at least
one current detection means or a combination thereof after a
predetermined period of time, and then installs position data
corresponding to said position into the memory unit of the control
section, therefore, upon a selector operation of a valve such as a
four-way selector valve provided in the refrigerating cycle for
selecting a channel of fluid, prevention of environmental pollution
and energy saving and the like are effectively achieved, and in
addition, a secure control of the refrigerating cycle can be
performed.
[1070] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 71, a microcomputer
that controls the refrigerating cycle is used, thereby controlling
at least one of a plurality of functional components communicated
to the refrigerating cycle so as to control the refrigerating
cycle, and in order to control the driving section for driving the
functional component so that the position of the movable member is
to be moved or not to be moved, the microcomputer performs a
processing consisting of the steps of:
[1071] receiving input signals; confirming a position by taking out
present position data of a movable member installed in a memory
unit; carrying out an operation to decide whether the movable
member is to be moved. of not to be moved, comparing, and judging;
selecting and deciding a driving section; outputting drive signals
to the driving section selected and decided; judging a position of
the movable member by input signals after a predetermined period of
time, with or without moving a position of the movable member by a
physical quantity generated by at least one functional component
that is selected and decided in said step of selecting and deciding
or a rate of the physical quantity; and installing position data of
a position of the movable member into the memory unit when said
position is changed to a new position,
[1072] therefore, upon a selector operation of a valve such as a
four-way selector valve provided in the refrigerating cycle for
selecting a channel of fluid, prevention of environmental pollution
and energy saving and the like are effectively achieved, and in
addition, a secure control of the refrigerating cycle can be
performed.
[1073] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 72, an operational
condition of the refrigerating cycle is commanded from an operation
command section and a physical quantity generated by the
refrigerating cycle is detected in a physical quantity detector
section, then the control section receives input signals sent from
the operation command section and the physical quantity detector
section. Then, the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component for
controlling an operation of the refrigerating cycle, and when
judging to select a channel by using the channel selector valve on
the basis of a command of the operation command section, the
control section sends output signals to a driving section for
driving a power source of a compressor so as to start an operation
of the compressor of the refrigerating cycle and starts an
operation of the refrigerant cycle so as to generate a motive power
exceeding a first predetermined motive power, thereby the channel
selector valve is passively controlled. Therefore, upon a selector
operation of a valve such as a four-way selector valve provided in
the refrigerating cycle for selecting a channel of fluid,
prevention of environmental pollution and energy saving and the
like are effectively achieved, and in addition, a secure control of
the refrigerating cycle can be performed.
[1074] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 73, an operational
condition of the refrigerating cycle is commanded from an operation
command section and a physical quantity generated by the
refrigerating cycle is detected in a physical quantity detector
section, then the control section receives input signals sent from
the operation command section and the physical quantity detector
section. Then, the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component for
controlling an operation of the refrigerating cycle, and when
judging to select a channel by using the channel selector valve on
the basis of a command of the operation command section, the
control section sends output signals to a driving section for
driving a power source of a compressor so as to start an operation
of the compressor in a direction of inverse rotation and starts an
operation of the refrigerant cycle so as to generate a motive power
exceeding a third predetermined motive power, thereby the channel
selector valve is passively controlled. Therefore, upon a selector
operation of a valve such as a four-way selector valve provided in
the refrigerating cycle for selecting a channel of fluid,
prevention of environmental pollution and energy saving and the
like are effectively achieved, and in addition, a secure control of
the refrigerating cycle can be performed.
[1075] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 74, the device
acts similarly to the device as described in claim 72 or 73, in
addition, the channel selector valve selects a channel by moving
the movable member between the first and second positions in
response to an internal motive power, the control section memorizes
position data corresponding to the first or second position of the
movable member in a memory unit thereof, the control section starts
an operation of the refrigerating cycle when the position data
indicates the second or first position, halts the operation of the
refrigerating cycle with renewing position data in the memory unit
to the first or second position, respectively, after a first
predetermined period of time, and keeps the operation of the
refrigerating cycle standby during a third predetermined period of
time. Therefore, upon a selector operation of a valve such as a
four-way selector valve provided in the refrigerating cycle for
selecting a channel of fluid, prevention of environmental pollution
and energy saving and the like are effectively achieved, and in
addition, a secure control of the refrigerating cycle can be
performed.
[1076] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 75, the device
acts similarly to the device as described in claim 72, in addition,
the control section operates the compressor in a specific frequency
immediately after starting the operation of the compressor and
starts an operation of the refrigerating cycle so that a motive
power exceeding a first predetermined motive power is generated as
an internal motive power of the channel selector valve. Therefore,
upon a selector operation of a valve such as a four-way selector
valve provided in the refrigerating cycle for selecting a channel
of fluid, prevention of environmental pollution and energy saving
and the like are effectively achieved.
[1077] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 76, the device
acts similarly to the device as described in claim 72, in addition,
the control section starts an operation of the compressor with a
first predetermined capacity, therefore, upon a selector operation
of a valve such as a four-way selector valve provided in the
refrigerating cycle for selecting a channel of fluid, prevention of
environmental pollution and energy saving and the like are
effectively achieved.
[1078] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 77, the device
acts similarly to the device as described in claim 72, in addition,
the control section starts an operation of the compressor with a
second predetermined capacity so that a motive power lower than a
first predetermined motive power is generated as an internal motive
power of the channel selector valve, then operates the
refrigerating cycle for a fourth predetermined period of time, then
halts the operation of the refrigerating cycle for a fifth
predetermined period of time, and then starts an operation of the
compressor with a first predetermined capacity so that a motive
power exceeding a first predetermined motive power is generated as
an internal motive power of the channel selector valve. Therefore,
upon a selector operation of a valve such as a four-way selector
valve provided in the refrigerating cycle for selecting a channel
of fluid, prevention of environmental pollution and energy saving
and the like are effectively achieved.
[1079] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 78, the device
acts similarly to the device as described in claim 72, in addition,
the control section sends output signals to a throttle device
driving section so that an opening ratio of a throttle device of
the refrigerating cycle is almost fully opened or almost fully
closed, therefore, upon a selector operation of a valve such as a
four-way selector valve provided in the refrigerating cycle for
selecting a channel of fluid, prevention of environmental pollution
and energy saving and the like are effectively achieved.
[1080] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 79, the device
acts similarly to the device as described in claim 72, in addition,
the control section sends output signals to a heat exchanger motor
driving section so that a heat exchanger motor of the refrigerating
cycle is kept halted, therefore, upon a selector operation of a
valve such as a four-way selector valve provided in the
refrigerating cycle for selecting a channel of fluid, prevention of
environmental pollution and energy saving and the like are
effectively achieved.
[1081] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 80, the device
acts similarly to the device as described in claim 72, 75, 76 or
77, in addition, once the control section starts an operation of
the compressor, the control section sends output signals to the
compressor driving section after a first predetermined period of
time and drives the power source of the compressor so that a motive
power exceeding a second predetermined motive power is generated,
thereby operating the refrigerating cycle. Therefore, upon a
selector operation of a valve such as a four-way selector valve
provided in the refrigerating cycle for selecting a channel of
fluid, prevention of environmental pollution and energy saving and
the like are effectively achieved, and in addition, a secure
control of the refrigerating cycle can be performed.
[1082] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 81, the device
acts similarly to the device as described in claim 78, in addition,
once the control section starts an operation of the compressor, the
control section sends output signals to the throttle device driving
section so as to set the opening ratio of the throttle device a
predetermined opening ratio after a first predetermined period of
time, therefore, upon a selector operation of a valve such as a
four-way selector valve provided in the refrigerating cycle for
selecting a channel of fluid, prevention of environmental pollution
and energy saving and the like are effectively achieved, and in
addition, a secure control of the refrigerating cycle can be
performed.
[1083] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 82, the device
acts similarly to the device as described in claim 79, in addition,
once the control section starts an operation of the compressor, the
control section sends output signals to the heat exchanger motor
driving section after a second predetermined period of time so as
to start an operation of the heat exchanger motor, sends output
signals to the compressor driving section so as to generate a
motive power lower than a first predetermined motive power, and
drives the power source of the compressor so as to generate a
motive power exceeding a second predetermined motive power, thereby
operating the refrigerating cycle. Therefore, upon a selector
operation of a valve such as a four-way selector valve provided in
the refrigerating cycle for selecting a channel of fluid,
prevention of environmental pollution and energy saving and the
like are effectively achieved, and in addition, a secure control of
the refrigerating cycle can be performed.
[1084] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 83, the device
acts similarly to the device as described in claim 80, 81 or 82, in
addition, when the control section performs a predetermined
processing and judges to select a channel by the channel selector
valve or to halt an operation of the refrigerating cycle, the
control section sends output signals to the compressor driving
section: to drive the power source of the compressor with a third
predetermined capacity so as to generate a motive power lower than
a second predetermined motive power; or to halt the operation of
the compressor, thereby halting the operation of the refrigerating
cycle. Therefore, upon a selector operation of a valve such as a
four-way selector valve provided in the refrigerating cycle for
selecting a channel of fluid, prevention of environmental pollution
and energy saving and the like are effectively achieved.
[1085] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 84, the device
acts similarly to the device as described in claim 72, in addition,
when the control section performs a predetermined processing and
judges to select a channel by the channel selector valve or to halt
an operation of the refrigerating cycle, the control section sends
output signals to the compressor driving section to halt the
operation of the compressor, then keeps the refrigerating cycle
standby for a third predetermined period of time, then sends output
signals to the compressor driving section to start the operation of
the compressor, then renews position data in a memory unit to a
first or second position after a first predetermined period of
time, thereby halting the operation of the compressor again.
Therefore, upon a selector operation of a valve such as a four-way
selector valve provided in the refrigerating cycle for selecting a
channel of fluid, prevention of environmental pollution and energy
saving and the like are effectively achieved, and in addition, a
secure control of the refrigerating cycle can be performed.
[1086] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 85, the device
acts similarly to the device as described in claim 72, 74 or 84, in
addition, when positional data memorized by a memory unit of the
control section indicate a first or second position, the control
section starts an operation of the refrigerating cycle so that a
motive power exceeding a first predetermined motive power is
generated as an internal motive power of the channel selector
valve. Therefore, upon a selector operation of a valve such as a
four-way selector valve provided in the refrigerating cycle for
selecting a channel of fluid, prevention of environmental pollution
and energy saving and the like are effectively achieved, and in
addition, a secure control of the refrigerating cycle can be
performed.
[1087] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 86, an operational
condition of the refrigerating cycle is commanded from an operation
command section and a physical quantity generated by the
refrigerating cycle is detected in a physical quantity detector
section, then the control section receives input signals sent from
the operation command section and the physical quantity detector
section. Then, the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component for
controlling an operation of the refrigerating cycle, and when
judging not to select (i.e. not to switch) a channel by using the
channel selector valve on the basis of a command of the operation
command section, the control section sends output signals to a
driving section for driving a power source of a compressor so as to
start an operation of the compressor of the refrigerating cycle and
starts an operation of the refrigerant cycle so as to generate a
motive power lower than a first predetermined motive power, thereby
the channel selector valve is passively controlled. Therefore, upon
a selector operation of a valve such as a four-way selector valve
provided in the refrigerating cycle for selecting a channel of
fluid, prevention of environmental pollution and energy saving and
the like are effectively achieved.
[1088] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 87, the device
acts similarly to the device as described in claim 86, in addition,
the control section starts an operation of the compressor with a
second predetermined capacity, therefore, upon a selector operation
of a valve such as a four-way selector valve provided in the
refrigerating cycle for selecting a channel of fluid, prevention of
environmental pollution and energy saving and the like are
effectively achieved.
[1089] According to a device for controlling a refrigerating cycle
of the present invention as described in claim 88, an operational
condition of the refrigerating cycle is commanded from an operation
command section and a physical quantity generated by the
refrigerating cycle is detected in a physical quantity detector
section, then the control section receives input signals sent from
the operation command section and the physical quantity detector
section. Then, the control section sends output signals to a
driving section that drives a drive source of at least one of a
plurality of functional components communicated to the
refrigerating cycle so as to control said functional component for
controlling an operation of the refrigerating cycle, and when
judging not to select (i.e. not to switch) a channel by using the
channel selector valve on the basis of a command of the operation
command section, the control section sends output signals to a
driving section for driving a power source of a compressor so as to
start an operation of the compressor of the refrigerating cycle and
starts an operation of the refrigerant cycle so as to generate a
motive power exceeding a first predetermined motive power, thereby
the channel selector valve is passively controlled. Therefore, upon
a selector operation of a valve such as a four-way selector valve
provided in the refrigerating cycle for selecting a channel of
fluid, prevention of environmental pollution and energy saving and
the like are effectively achieved.
[1090] According to the device for controlling a refrigerating
cycle of the present invention as described in claim 89, the device
acts similarly to the device as described in claim 88, in addition,
when the control section performs a predetermined processing and
judges to halt an operation of the refrigerating cycle, the control
section sends output signals to the compressor driving section so
as to halt the operation of the compressor, then keeps the
refrigerating cycle standby for a third predetermined period of
time without renewing position data in a memory unit. Therefore,
upon a selector operation of a valve such as a four-way selector
valve provided in the refrigerating cycle for selecting a channel
of fluid, prevention of environmental pollution and energy saving
and the like are effectively achieved, and in addition, a secure
control of the refrigerating cycle can be performed.
* * * * *