U.S. patent application number 10/851870 was filed with the patent office on 2005-01-13 for displacement control mechanism for variable displacement compressor.
Invention is credited to Hirose, Tatsuya, Iida, Hidenori, Inoue, Yoshinori, Kawaguchi, Masahiro, Ota, Masaki, Umemura, Satoshi, Yoshida, Hiroyuki.
Application Number | 20050008499 10/851870 |
Document ID | / |
Family ID | 33095504 |
Filed Date | 2005-01-13 |
United States Patent
Application |
20050008499 |
Kind Code |
A1 |
Umemura, Satoshi ; et
al. |
January 13, 2005 |
Displacement control mechanism for variable displacement
compressor
Abstract
A displacement control mechanism used in a variable displacement
compressor for controlling a displacement of the compressor
includes a first control valve located on a supply passage and a
second control valve located on a first bleed passage. The second
control valve includes a backpressure chamber having substantially
the same pressure atmosphere as a region of the supply passage
downstream of the first control valve and a spool including a back
surface that is located in the backpressure chamber. The spool
reduces an opening degree of the first bleed passage when a
pressure in the backpressure chamber is increased. The spool blocks
a communication between the backpressure chamber and the first
bleed passage via a clearance formed around a cylindrical outer
peripheral surface of the spool in the second control valve when
the spool sets the first bleed passage at a minimum opening
degree.
Inventors: |
Umemura, Satoshi;
(Kariya-shi, JP) ; Kawaguchi, Masahiro;
(Kariya-shi, JP) ; Yoshida, Hiroyuki; (Kariya-shi,
JP) ; Ota, Masaki; (Kariya-shi, JP) ; Hirose,
Tatsuya; (Kariya-shi, JP) ; Inoue, Yoshinori;
(Kariya-shi, JP) ; Iida, Hidenori; (Kariya-shi,
JP) |
Correspondence
Address: |
WOODCOCK WASHBURN LLP
ONE LIBERTY PLACE, 46TH FLOOR
1650 MARKET STREET
PHILADELPHIA
PA
19103
US
|
Family ID: |
33095504 |
Appl. No.: |
10/851870 |
Filed: |
May 21, 2004 |
Current U.S.
Class: |
417/222.2 ;
417/269 |
Current CPC
Class: |
F04B 39/16 20130101;
F04B 2027/1868 20130101; F04B 2027/1859 20130101; F04B 2027/1827
20130101; F04B 27/1804 20130101; F04B 2027/1813 20130101; F04B
2027/1854 20130101; F04B 2027/1881 20130101; F04B 2027/1831
20130101; F04B 53/20 20130101 |
Class at
Publication: |
417/222.2 ;
417/269 |
International
Class: |
F04B 001/26; F04B
001/12 |
Foreign Application Data
Date |
Code |
Application Number |
May 23, 2003 |
JP |
2003-146952 |
Claims
What is claimed is:
1. A displacement control mechanism used in a variable displacement
compressor for controlling a displacement of the compressor, the
compressor partially forming a refrigerant circulation circuit of
an air-conditioner, the displacement of the compressor being varied
in accordance with a pressure in a crank chamber, the refrigerant
circulation circuit including a suction pressure region and a
discharge pressure region, the displacement control mechanism
comprising: a first bleed passage interconnecting the crank chamber
and the suction pressure region; a supply passage interconnecting
the crank chamber and the discharge pressure region; a first
control valve located on the supply passage for controlling an
opening degree of the supply passage; and a second control valve
located on the first bleed passage, the second control valve
including: a backpressure chamber having substantially the same
pressure atmosphere as a region of the supply passage downstream of
the first control valve; a valve chamber partially forming the
first bleed passage and communicating with the suction pressure
region; a valve hole partially forming the first bleed passage and
interconnecting the valve chamber and the crank chamber; and a
spool including a first valve portion located in the valve chamber
and a back surface located in the backpressure chamber and a
cylindrical outer peripheral surface, wherein the first valve
portion reduces an opening degree of the valve hole when a pressure
in the backpressure chamber that is applied to the back surface is
increased, wherein a second valve portion is formed in the spool to
block a communication between the backpressure chamber and the
valve chamber via a clearance formed around the cylindrical outer
peripheral surface of the spool in the second control valve when
the first valve portion sets the valve hole at a minimum opening
degree.
2. The displacement control mechanism according to claim 1, wherein
an annular movable step is provided in the cylindrical outer
peripheral surface of the spool, the movable step including a
movable wall surface that faces toward a side of the valve hole and
forms the second valve portion, an annular fixed step being
provided in the second control valve, the fixed step including a
fixed wall surface that faces the movable wall surface and forms a
valve seat for the second valve portion, the communication between
the backpressure chamber and the valve chamber being blocked by
contacting the movable wall surface with the fixed wall
surface.
3. The displacement control mechanism according to claim 2, wherein
a spring is located in the valve chamber for urging the spool in a
direction that increases the opening degree of the valve hole, the
movable wall surface including an inner region that is located
radially inwardly from an annular region of movable wall surface
that forms the second valve portion, the inner region forming a
spring seat for the spring.
4. The displacement control mechanism according to claim 1, further
comprising a filter located in the supply passage between the
discharge pressure region and the first control valve for removing
foreign substances in refrigerant gas, a width of the clearance
formed around the cylindrical outer peripheral surface of the spool
in the second control valve is larger than a diameter of the
foreign substances that pass through the filter.
5. The displacement control mechanism according to claim 1, wherein
the minimum opening degree of the valve hole by the first valve
portion is slightly larger than zero.
6. The displacement control mechanism according to claim 1, wherein
the minimum opening degree of the valve hole by the first vale
portion is zero, elasticity being provided to at least one of the
first valve portion, a valve seat for the first valve portion, the
second valve portion and a valve seat for the second valve portion,
the displacement control mechanism further comprising a second
bleed passage that interconnects the crank chamber and the suction
pressure region and includes a fixed throttle.
7. The displacement control mechanism according to claim 6, wherein
at least one of the first valve portion and the second valve
portion is formed by a ring-shaped lead.
8. The displacement control mechanism according to claim 6, wherein
at least one of the first valve portion and the second valve
portion is made of rubber.
9. The displacement control mechanism according to claim 6, wherein
the spool includes a large-diameter portion that forms the movable
wall surface, the large-diameter portion being fitted in a metallic
cylinder.
10. A displacement control mechanism used in a variable
displacement compressor for controlling a displacement of the
compressor, the compressor partially forming a refrigerant
circulation circuit of an air-conditioner, the displacement of the
compressor being varied in accordance with a pressure in a crank
chamber, the refrigerant circulation circuit including a suction
pressure region and a discharge pressure region, comprising: a
first bleed passage interconnecting the crank chamber and the
suction pressure region; a second bleed passage interconnecting the
crank chamber and the suction pressure region, the second bleed
passage having a fixed throttle; a supply passage interconnecting
the crank chamber and the discharge pressure region; a first
control valve located on the supply passage for controlling an
opening degree of the supply passage; and a second control valve
located on the first bleed passage, the second control valve
including: a backpressure chamber having substantially the same
pressure atmosphere as a region of the supply passage downstream of
the first control valve; a valve chamber partially forming the
first bleed passage and communicating with the crank chamber; a
valve hole partially forming the first bleed passage and
interconnecting the valve chamber and the suction pressure region;
and a spool including a valve portion located in the valve chamber,
a back surface located in the backpressure chamber and a
cylindrical outer peripheral surface, wherein the valve portion
closes the valve hole when a pressure in the backpressure chamber
that is applied to the back surface is increased, wherein the valve
portion simultaneously blocks a communication between the
backpressure chamber and the valve chamber via a clearance formed
around the cylindrical outer peripheral surface of the spool in the
second control valve when the valve portion closes the valve
hole.
11. The displacement control mechanism according to claim 10,
further comprising a filter located in the supply passage between
the discharge pressure region and the first control valve for
removing foreign substances in refrigerant gas, a width of the
clearance formed around the cylindrical outer peripheral surface of
the spool in the second control valve is larger than a diameter of
the foreign substances that pass through the filter.
12. The displacement control mechanism according to claim 10,
wherein the first bleed passage and the supply passage share a
common passage between the crank chamber and the valve chamber.
13. The displacement control mechanism according to claim 10,
wherein the second control valve is installed in the first control
valve.
14. The displacement control mechanism according to claim 10,
wherein a recess is formed on a surface of the spool that faces the
valve hole, the recess having a cross sectional area that is larger
than that of the valve hole.
15. The displacement control mechanism according to claim 10,
wherein a spool has a cylindrical shape with an opening that is
open to the valve hole, a spring being located in the spool for
urging the spool in a direction that increases an opening degree of
the valve hole.
16. A displacement control mechanism used in a variable
displacement compressor for controlling a displacement of the
compressor, the compressor partially forming a refrigerant
circulation circuit of an air-conditioner, the displacement of the
compressor being varied in accordance with a pressure in a crank
chamber of the compressor, the refrigerant circulation circuit
including a suction pressure region and a discharge pressure
region, comprising: a first bleed passage interconnecting the crank
chamber and the suction pressure region; a supply passage
interconnecting the crank chamber and the discharge pressure
region; a first control valve located on the supply passage for
controlling an opening degree of the supply passage; and a second
control valve located on the first bleed passage, the second
control valve including: a backpressure chamber having
substantially the same pressure atmosphere as a region of the
supply passage downstream of the first control valve; a spool
including a back surface that is located in the backpressure
chamber and a cylindrical outer peripheral surface, wherein the
spool reduces an opening degree of the first bleed passage when a
pressure in the backpressure chamber that is applied to the back
surface is increased, wherein the spool blocks a communication
between the backpressure chamber and the first bleed passage via a
clearance formed around the cylindrical outer peripheral surface of
the spool in the second control valve when the spool sets the first
bleed passage at a minimum opening degree.
17. The displacement control mechanism according to claim 16,
wherein the second control valve further includes: a valve chamber
partially forming the first bleed passage and communicating with
the suction pressure region; a valve hole partially forming the
first bleed passage and interconnecting the valve chamber and the
crank chamber; and wherein the spool includes a first valve portion
located in the valve chamber, wherein the first valve portion
reduces the opening degree of the valve hole when the pressure in
the backpressure chamber is increased, wherein a second valve
portion is formed in the spool to block a communication between the
backpressure chamber and the valve chamber via the clearance formed
around the cylindrical outer peripheral surface of the spool in the
second control valve when the first valve portion sets the valve
hole at the minimum opening degree.
18. The displacement control mechanism according to claim 17,
further comprising a filter located in the supply passage between
the discharge pressure region and the first control valve for
removing foreign substances in refrigerant gas, a width of the
clearance formed around the cylindrical outer peripheral surface of
the spool in the second control valve is larger than a diameter of
the foreign substances that pass through the filter.
19. The displacement control mechanism according to claim 16,
further comprising a second bleed passage interconnecting the crank
chamber and the suction pressure region, the second bleed passage
having a fixed throttle wherein a second control valve further
including: a valve chamber partially forming the first bleed
passage and communicating with the crank chamber; a valve hole
partially forming the first bleed passage and interconnecting the
valve chamber and the suction pressure region; and wherein the
spool includes a valve portion located in the valve chamber, the
spool having a cylindrical outer peripheral surface, wherein the
valve portion closes the valve hole when the pressure in the
backpressure chamber is increased, wherein the valve portion
simultaneously blocks a communication between the backpressure
chamber and the valve chamber via the clearance formed around the
cylindrical outer peripheral surface of the spool in the second
control valve when the valve portion closes the valve hole.
20. The displacement control mechanism according to claim 19,
further comprising a filter located in the supply passage between
the discharge pressure region and the first control valve for
removing foreign substances in refrigerant gas, a width of the
clearance formed around the cylindrical outer peripheral surface of
the spool in the second control valve is larger than a diameter of
the foreign substances that pass through the filter.
Description
BACKGROUND OF THE INVENTION
[0001] The present invention relates to a displacement control
mechanism for controlling the displacement of a variable
displacement compressor that forms a part of a refrigerant
circulation circuit of an air-conditioner. The displacement of the
compressor is varied in accordance with the pressure in a crank
chamber of the compressor.
[0002] There is known a control mechanism shown in FIG. 15.
According to the mechanism, the compressor displacement is
controlled by adjusting the pressure in crank chamber 153 (or crank
pressure Pc). Namely, in a swash plate type variable displacement
compressor (hereinafter the compressor), the crank chamber 153
communicates with a suction chamber 155 via a bleed passage 154. A
discharge chamber 151 of the compressor communicates with the crank
chamber 153 via a supply passage 152 on which a control valve 156
is arranged. The amount of refrigerant gas introduced into the
crank chamber 153 via the supply passage 152 is controlled by
adjusting the opening degree of the control valve 156, and the
crank pressure Pc is determined in accordance with the relation
between the amounts of refrigerant gas introduced into and bleeding
from the crank chamber 153.
[0003] A fixed throttle 158 is formed in the bleed passage 154 so
that the refrigerant gas bleeds slowly from the crank chamber 153
to the suction chamber 155. Thus, even when the amount of the
refrigerant gas supplied from the discharge chamber 151 to the
crank chamber 153 via the supply passage 152 is small, the crank
pressure Pc is steadily increased. Therefore, when the control
valve 156 increases the opening degree of the supply passage 152,
the crank pressure Pc is rapidly increased. Consequently,
appropriate response in decreasing the compressor displacement is
obtained.
[0004] Also, an amount of blow-by gas from a cylinder bore 157 to
the crank chamber 153 leaks to the suction chamber 155 via the
bleed passage 154. The refrigerant gas moves from the discharge
chamber 151 to the suction chamber 155 via the crank chamber 153 as
mentioned above, such movement of the refrigerant being a kind of
internal leaking. However, the amount of the above leaking blow-by
gas and the amount of the above moving refrigerant gas are reduced
as much as possible by the provision of the fixed throttle 158.
Consequently, decrease in efficiency of the compressor caused by
the provision of the displacement control mechanism is
prevented.
[0005] However, the fixed throttle 158 provided in the bleed
passage 154 causes the pressure in the crank chamber 153 to be
slowly reduced, thereby deteriorating the response of the
compressor in increasing the displacement. Especially, upon
starting the compressor, the crank pressure Pc tends to be
increased excessively because the liquid refrigerant accumulated in
the crank chamber 153 evaporates and the fixed throttle 158
prevents smooth flow of refrigerant gas from the crank chamber 153.
Therefore, even when the control valve 156 closes the supply
passage 152 so as to increase the displacement of the compressor in
response to the requirement for cooling shortly after starting the
compressor, it takes time before the displacement of the compressor
is actually increased, so that the cooling performance shortly
after a start-up of an air-conditioner deteriorates.
[0006] To solve such problems, it is proposed to provide a second
control valve 161 for controlling the opening degree of the bleed
passage 154 in addition to the control valve (first control valve)
156, as shown in FIG. 16 (e.g. Japanese Unexamined Patent
Publication 2002-21721). In the proposed structure, a region K is
provided in the supply passage 152 downstream of the position of
first control valve 156 (i.e. the position of valve opening
adjustment) and upstream of the fixed throttle 169, as shown in
FIG. 16. The second control valve 161 is a spool type valve that
includes a spool 162 and a backpressure chamber 166 into which the
pressure in the region K Is introduced. A valve chamber 167 of the
second control valve 161 forms a part of the bleed passage 154 and
communicates with the suction chamber 155. The valve chamber 167
also communicates with the crank chamber 153 via a valve hole 168
that forms the upstream part of the bleed passage 154.
[0007] The spool 162 is movably disposed in a spool-supporting
recess 164 that is formed in a compressor housing. The spool 162
includes a valve portion 162a that is located in the valve chamber
167 and a back surface 162b that is located in the backpressure
chamber 166. The spool 162 (or the valve portion 162a) is
positioned by various forces applied thereto such as urging force
based on the pressure in the backpressure chamber 166 acting on the
back surface 162b in the direction to close the valve, urging force
of a spring 165 acting in the valve opening direction and force of
the crank pressure Pc that is applied in the valve opening
direction.
[0008] When the first control valve 156 closes the supply passage
152, a pressure PdK in the backpressure chamber 166 of the second
control valve 161 is substantially the same as the crank pressure
Pc and, therefore, the spool 162 of the second control valve 161 is
positioned by the spring 165 where the valve hole 168 is wide
opened at a maximum opening degree. When the bleed passage 154 is
wide opened by the second control valve 161, flowing of the
refrigerant from the crank chamber 153 to the suction chamber 155
is promoted. Therefore, closing the supply passage 152 by the first
control valve 156 so as to increase the displacement of the
compressor shortly after starting the compressor, the displacement
of the compressor is immediately increased, so that the cooling
performance shortly after a start-up of air conditioner is
improved.
[0009] A spring having a small spring force is utilized as the
spring 165. Thus, when the supply passage 152 is opened even
slightly by the first control valve 156 and the pressure PdK in the
region K exceeds the crank pressure Pc, the spool 162 moves against
the urging force of the spring 165, and the valve portion 162a sets
the valve hole 168 at a minimum opening degree that is not zero.
Therefore, when the valve hole 168 is thus set at the minimum
opening degree that is not zero, the second control valve 161
functions similarly as the above-described fixed throttle 158 shown
in FIG. 15, and the decrease in the efficiency of the compressor
which is caused by having the displacement control mechanism is
prevented.
[0010] However, the second control valve 161 is arranged such that
the clearance between the outer peripheral surface of the spool 162
and the inner peripheral surface of the spool-supporting recess 164
is small, so that the fluid communication between the backpressure
chamber 166 and the valve chamber 167 via the clearance is blocked,
and the decrease in the efficiency of the compressor due to the
leak of the refrigerant gas from the backpressure chamber 166 to
the valve chamber 167 is prevented. However, foreign substances
tend to be caught between the outer peripheral surface of the spool
162 and the inner peripheral surface of the spool-supporting recess
164, thereby causing poor sliding movement of the spool 162.
[0011] In order to solve such problems, the alternative embodiment
of the above prior art reference proposes the use of a bellows
instead of the spool 162 and the spring 165. Using the bellows that
is elastic and stretchable and serves as a partition wall shutting
off the communication between the back pressure chamber and the
valve chamber without any sliding contact of moving part of the
second control valve with the compressor housing, the clearance
between the moving part of the second control valve and the
compressor housing is set large enough. However, the bellows
becomes larger with a decrease of its spring constant. Thus, in
comparison to the case that the spool 162 and the spring 165 are
used in combination, the second control valve having incorporated
therein a bellows is disadvantageously large-sized.
SUMMARY OF THE INVENTION
[0012] The present invention provides a displacement control
mechanism for a variable displacement compressor that prevents the
operation failure of the spool of a second control valve that
adjusts the opening degree of the bleed passage.
[0013] According to the present invention, a displacement control
mechanism is used in a variable displacement compressor for
controlling a displacement of the compressor. The compressor
partially forms a refrigerant circulation circuit of an
air-conditioner. The displacement of the compressor is varied in
accordance with a pressure in a crank chamber of the compressor.
The refrigerant circulation circuit includes a suction pressure
region and a discharge pressure region. The displacement control
mechanism includes a first bleed passage, a supply passage, a first
control valve and a second control valve. The first bleed passage
interconnects the crank chamber and the suction pressure region.
The supply passage interconnects the crank chamber and the
discharge pressure region. The first control valve is located on
the supply passage for controlling an opening degree of the supply
passage. The second control valve is located on the first bleed
passage. The second control valve also includes a backpressure
chamber and a spool. The backpressure chamber has substantially the
same pressure atmosphere as a region of the supply passage
downstream of the first control valve. The spool includes a back
surface that is located in the backpressure chamber. The spool has
a cylindrical outer peripheral surface. The spool reduces an
opening degree of the first bleed passage when a pressure in the
backpressure chamber that is applied to the back surface is
increased. The spool blocks a communication between the
backpressure chamber and the first bleed passage via a clearance
formed around the cylindrical outer peripheral surface of the spool
in the second control valve when the spool sets the first bleed
passage at a minimum opening degree.
BRIEF DISCRIPTION OF THE DRAWINGS
[0014] The features of the present invention that are believed to
be novel are set forth with particularity in the appended claims.
Aspect of the invention may best be understood by reference to the
following description of the presently preferred embodiments
together with the accompanying drawings in which:
[0015] FIG. 1 is a longitudinal cross-sectional view of a variable
displacement compressor according to a first preferred
embodiment;
[0016] FIG. 2 is a cross-sectional view of a first control
valve;
[0017] FIG. 3A is a partially enlarged cross sectional view of the
variable displacement compressor around a second control valve;
[0018] FIG. 3B is a schematic view showing cross section areas of a
valve chamber and a valve hole for explaining conditional
inequalities;
[0019] FIG. 4A is a cross-sectional view explaining an action of
the second control valve;
[0020] FIG. 4B is a cross-sectional view explaining the action of
the second control valve;
[0021] FIG. 5 is a partially enlarged cross-sectional view of a
variable displacement compressor around a second control valve
according to a second preferred embodiment;
[0022] FIG. 6 is a cross-sectional view explaining an action of the
second control valve;
[0023] FIG. 7 is a cross-sectional view of a first control valve
including a second control valve therein according to a third
preferred embodiment;
[0024] FIG. 8 is a partially enlarged cross-sectional view of the
first control valve including the second control valve therein
according to the third preferred embodiment;
[0025] FIG. 9 is a partially enlarged cross-sectional view of a
variable displacement compressor around a second control valve
according to a first alternative embodiment;
[0026] FIG. 10 is a partially enlarged cross-sectional view of a
variable displacement compressor around a second control valve
according to a second alternative embodiment;
[0027] FIG. 11 is a partially enlarged cross-sectional view of a
variable displacement compressor around a second control valve
according to a third alternative embodiment;
[0028] FIG. 12 is a partially enlarged cross-sectional view of a
variable displacement compressor around a second control valve
according to a fourth alternative embodiment;
[0029] FIG. 13 is a partially enlarged cross-sectional view of a
variable displacement compressor around a second control valve
according to a fifth alternative embodiment;
[0030] FIG. 14 is a partially enlarged cross-sectional view of a
variable displacement compressor around a second control valve
according to a sixth alternative embodiment;
[0031] FIG. 15 is a schematic view of a variable displacement
compressor according to prior art; and
[0032] FIG. 16 is a partially enlarged cross-sectional view of a
variable displacement compressor around a second control valve
according to prior art.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0033] The following will describe a preferred embodiment of the
present invention. In the first preferred embodiment, the present
invention is applied to a swash plate type variable displacement
compressor (hereinafter the compressor) that is used in a vehicle
air-conditioner for compressing refrigerant gas.
[0034] Referring to FIG. 1, the compressor includes a cylinder
block 1, a front housing 2, a valve plate assembly 3 and a rear
housing 4. In FIG. 1, the left side and the right side respectively
correspond to the front side and the rear side of the compressor.
The front housing 2 is fixed to the front end of the cylinder block
1, and the rear housing 4 is fixed to the rear end of the cylinder
block 1 via the valve plate assembly 3. A compressor housing
includes the cylinder block 1, the front housing 2 and the rear
housing 4. A crank chamber 5 is defined by the cylinder block 1 and
the front housing 2. A drive shaft 6 is rotatably supported in the
crank chamber 5. A lug plate 11 is rotatably fixed to the drive
shaft 6 in the crank chamber 5.
[0035] The front end of the drive shaft 6 is operatively connected
to a vehicle engine E as an external drive source via a power
transmission mechanism PT. The power transmission mechanism PT is a
clutch mechanism (e.g. an electromagnetic clutch) that selectively
transmits and blocks driving power according to electric control
from an external device, or a continuous transmission type
clutchless mechanism (e.g. the combination of belt and pulley) that
dispenses with the above clutch mechanism. In the first preferred
embodiment, the clutchless type power transmission mechanism PT is
utilized.
[0036] A swash plate 12 as a cam plate is accommodated in the crank
chamber 5. The swash plate 12 is slidably and inclinably supported
by the drive shaft 6. A hinge mechanism 13 is interposed between
the lug plate 11 and the swash plate 12. Thus, a hinge connection
between the lug plate 11 and the swash plate 12 via the hinge
mechanism 13 and the support of the swash plate 12 by the drive
shaft 6 allow the swash plate 12 to rotate integrally with the lug
plate 11 and the drive shaft 6 as well as to incline with respect
to the drive shaft 6 in accordance with the sliding movement of the
swash plate 1.2 relative to the drive shaft 6 in the axial
direction of the drive shaft 6.
[0037] A plurality of cylinder bores 1a are formed in the cylinder
block 1 extending axially through the cylinder block 1 and arranged
around the drive shaft 6. Single-headed pistons 20 are each
accommodated in the respective cylinder bores 1a for reciprocation
therein. The front and rear openings of the cylinder bores 1a are
respectively closed by the valve plate assembly 3 and the pistons
20. Compression chambers are defined in the cylinder bores 1a, and
the volume of the compression chambers is varied in accordance with
the reciprocating movement of the pistons 20. Each of the pistons
19 is engaged with the swash plate 12 via a pair of shoes 19, so
that the rotation of the swash plate 12 in accordance with the
drive shaft 6 is converted into reciprocating linear movement of
the pistons 20.
[0038] A suction chamber 21 and a discharge chamber 22 are defined
between the valve plate assembly 3 and the rear housing 4. The
suction chamber 21 is located in the middle region of the rear
housing 4 and is surrounded by the discharge chamber 22. A suction
port 23 and a suction valve 24 are formed in the valve plate
assembly 3 for each of the cylinder bores 1a. The suction valve 24
is adapted to open and close the suction port 23. A discharge port
25 and a discharge valve 26 are also formed in the valve plate
assembly 3 for each of the cylinder bores 1a. The suction chamber
21 communicates with each of the cylinder bores 1a via the
corresponding suction port 23, and each of the cylinder bores 1a
communicates with the discharge chamber 22 via the corresponding
discharge port 25.
[0039] As each of the pistons 20 moves from the top dead center
toward the bottom dead center, the refrigerant gas is drawn into
the corresponding cylinder bore 1a via the suction port 23 and the
suction valve 24. As each of the pistons 20 moves from the bottom
dead center toward the top dead center, the refrigerant gas
introduced into the cylinder bore 1a is compressed to a
predetermined pressure and is discharged into the discharge chamber
22 via the discharge port 25 and the discharge valve 26.
[0040] An inclination angle of the swash pate 12, which is defined
as an angle made between the swash plate 12 and a hypothetical
plane perpendicular to an axis L of the drive shaft 6 is varied in
accordance with the pressure in the crank chamber 5 (a crank
pressure Pc). The inclination angle of the swash plate 12 is
randomly determined between a minimum inclination angle as
indicated by a solid line in FIG. 1 and a maximum inclination angle
as indicated by a chain double-dashed line in FIG. 1.
[0041] A displacement control mechanism for controlling the crank
pressure Pc which is concerned with the controlling of the
inclination angle of the swash plate 12 includes a first bleed
passage 27, a second bleed passage 28, a supply passage 29, a first
control valve CV1 and a second control valve CV2. The first and
second bleed passages 27 and 28 interconnect the crank chamber 5
and the suction chamber 21 as a suction pressure (Ps) region. The
second control valve CV2 is arranged on the first bleed passage 27.
The second bleed passage 28 has a fixed throttle 28a and extends
through the cylinder block 1 and the valve plate assembly 3. The
fixed throttle 28a located in the second bleed passage 28 is formed
such that the part of the second bleed passage 28 extending through
the valve plate assembly 3 is narrower than that extending through
the cylinder block 1.
[0042] The supply passage 29 interconnects the discharge chamber 22
as a discharge pressure (Pd) region and the crank chamber 5. The
first control valve CV1 is arranged on the supply passage 29 for
adjusting the opening degree of the supply passage 29. The supply
passage 29 extends through the valve plate assembly 3 downstream of
the first control valve CV1 or on a side of the crank chamber 5.
The first control valve CV1 and the second control valve CV2
respectively adjust the opening degree of the supply passage 29 and
the first bleed passage 27. By so doing, the balance between the
amount of high-pressure discharge gas introduced from the discharge
chamber 22 into the crank chamber 5 via the supply passage 29 and
the amount of the refrigerant gas flowing from the crank chamber 5
into the suction chamber 21 via the first and second bleed passages
27 and 28 is controlled, and the crank pressure Pc is determined,
accordingly. Pressure difference between the crank pressure Pc and
the internal pressure in the cylinder bores 1a via the pistons 20
is changed in accordance with the variation of the crank pressure
Pc, and the inclination angle of the swash plate 12 is varied,
accordingly. Consequently, the stroke of pistons 20, that is, the
displacement of the compressor is adjusted.
[0043] For example, when the first control valve CV1 reduces the
opening degree of the supply passage 29 and the crank pressure Pc
is decreased, the inclination angle of the swash plate 12 is
increased, and the displacement of the compressor is increased. On
the other hand, when the first control valve CV1 increases the
opening degree of the supply passage 29 and the crank pressure Pc
is increased, the inclination angle of the swash plate 12 is
decreased, and the displacement of the compressor is decreased.
[0044] A refrigerant circulation circuit (or refrigerant cycle) of
the vehicle air-conditioner includes the above-described compressor
and an external refrigerant circuit 30. The external refrigerant
circuit 30 includes a gas cooler 31, an expansion valve 32 and an
evaporator 33. A circulation pipe 35 for the refrigerant is
provided on the downstream side of the external refrigerant circuit
30, interconnecting the outlet of the evaporator 33 and the suction
chamber 21 of the compressor. A circulation pipe 36 for the
refrigerant is provided on the upstream side of the external
refrigerant circuit 30, interconnecting the discharge chamber 22 of
the compressor and the inlet of the gas cooler 31.
[0045] As shown in FIG. 2, the first control valve CV1 includes a
supply valve portion in the upper half thereof as seen on the
drawing of FIG. 2 and a solenoid portion 60 in the lower half. The
supply valve portion adjusts the opening degree (throttle degree)
of the supply passage 29 that interconnects the discharge chamber
22 and the crank chamber 5. The solenoid portion 60 is an actuator
for controlling the operation of a valve rod 40 arranged in the
control valve CV1 in response to a control signal from an external
device. The valve rod 40 is a rod-like member which includes a
partition wall portion 41 at the top of the valve rod 40, a
connection part 42, a valve body 43 at the middle of the valve rod
40 and a guide rod 44 at the base of the valve rod 40. The valve
body 43 is a part of the guide rod 44.
[0046] A valve housing 45 for the first control valve CV1 includes
a valve body housing 45a forming its upper part and an actuator
housing 45b forming its lower part. A valve accommodation chamber
46, a communication passage 47 and a pressure sensing chamber 48
are defined in the valve body housing 45a in this order as seen
from the lower side of FIG. 2. The valve rod 40 is arranged in the
valve accommodation chamber 46 and the communication passage 47 for
movement in the direction of the axis of the valve housing 45, that
is, movement in the vertical direction as seen in FIG. 2. The
partition wall portion 41 of the valve rod 40 is inserted through
the communication passage 47 thereby to shut off the communication
between the pressure sensing chamber 48 and the communication
passage 47.
[0047] Ports 51 and 52 are formed through the peripheral wall of
the valve body housing 45a. The port 51 communicates with the valve
accommodation chamber 46, and the port 52 communicates with the
communication passage 47, respectively. The valve accommodation
chamber 46 communicates with the discharge chamber 22 of the
compressor via the port 51 and the upstream part of the supply
passage 29. The communication passage 47 communicates with the
crank chamber 5 of the compressor via the port 52 and the
downstream part of the supply passage 29. The valve accommodation
chamber 46 and the communication passage 47 form a part of the
supply passage 29.
[0048] The valve body 43 of the valve rod 40 is located in the
valve accommodation chamber 46. A valve seat 53 is formed at the
step portion located between the valve accommodation chamber 46 and
the communication passage 47, and the communication passage 47
functions as a valve hole. When the valve rod 40 moves upward from
the position of FIG. 2, where the communication passage 47 (or the
supply passage 29) is opened, to a position where the valve body 43
contacts the valve seat 53, that is, a planar surface 43a of the
valve body 43 contacts a planar surface 53a of the valve seat 53,
the communication passage 47 (the supply passage 29) is closed.
[0049] A bellows 50 is accommodated in the pressure sensing chamber
48. The upper end of the bellows 50 is fixed to the valve housing
45. The top of the partition wall portion 41 of the valve rod 40 is
fitted into the lower end of the bellows 50. A first pressure
chamber 54 that is located inside the bellows 50 and a second
pressure chamber 55 that is located outside the bellows 50 are
defined in the pressure sensing chamber 48 by the bellows 50 that
has a cylindrical shape with a bottom.
[0050] As shown in FIG. 1, a throttle 36a is formed in the
circulation pipe 36 between the discharge chamber 22 and the
external refrigerant circuit 30. Referring back to FIG. 2, the
first pressure chamber 54 communicates via a first pressure
introducing passage 37 with the discharge chamber 22 at a first
pressure monitoring point P1 that is located upstream of the
throttle 36a. The second pressure chamber 55 communicates via a
second pressure introducing passage 38 with the circulation pipe 36
at a second pressure monitoring point P2 that is located downstream
of the throttle 36a. Thus, a monitored pressure PdH at the first
pressure monitoring point P1 is introduced into the first pressure
chamber 54, and a monitored pressure PdL at the second pressure
monitoring point P2 is introduced into the second pressure chamber
55.
[0051] The lower end of the bellows 50 vertically moves in
accordance with the pressure difference (PdH-PdL) between the
pressures on opposite sides of the throttle 36a. Thus, positioning
of the valve rod 40 (the valve portion 43) is determined by varying
the pressure difference. The pressure difference (PdH-PdL) between
the pressures on opposite sides of the throttle 36a varies
depending on the refrigerant flow rate in the refrigerant
circulation circuit. For example, when the refrigerant flow rate is
increased, the pressure difference (PdH-PdL) is increased. On the
other hand, when the refrigerant flow rate is decreased, the
pressure difference (PdH-PdL) is decreased. The bellows 50 operates
on the valve body 43 such that the displacement of the compressor
is changed so as to cancel the variation of the pressure difference
(PdH-PdL).
[0052] The solenoid portion 60 of the first control valve CV1
includes an accommodation cylinder 61 that has a cylindrical shape
with a bottom in the middle of the actuator housing 45b. A fixed
core 62 of a column shape is fitted in the upper opening of the
accommodation cylinder 61. Thus, a solenoid chamber 63 is defined
in the lower portion of the accommodation cylinder 61.
[0053] A movable core 64 is axially movable and accommodated in the
solenoid chamber 63. A guide hole 65 extends through the center of
the fixed core 62 in the axial direction of the valve rod 40. The
guide rod 44 of the valve rod 40 is arranged in the guide hole 65
so as to move in the axial direction of the valve rod 40. The guide
rod 44 is fitted into the movable core 64. Thus, the movable core
64 and the valve rod 40 vertically move together. A spring 66 is
accommodated between the fixed core 62 and the movable core 64 in
the solenoid chamber 63 for urging the valve rod 40 in such
direction that causes the valve body 43 to move away from the valve
seat 53.
[0054] A coil 67 is wound around the outer periphery of the
accommodation cylinder 61 over a range covering the fixed core 62
and the movable core 64. Driving signal is transmitted from a
driving circuit 68a to the coil 67, based on the command from a
control device 68 in accordance with air-conditioning load. A
magnitude of the electromagnetic force (or electromagnetic
attraction) in accordance with an amount of electric power supplied
to the coil 67 is generated between the fixed core 62 and the
movable core 64. The electromagnetic force is transmitted to the
valve rod 40 (the valve body 43) through the movable core 64.
Controlling to energize the coil 67 is performed by adjusting the
voltage applied across the coil 67, and duty ratio is utilized in
the first preferred embodiment.
[0055] The solenoid portion 60 of the first control valve CV1
varies the electromagnetic force that is applied to the valve body
43 in accordance with the amount of the electric power supplied
from an external device. In the first control valve CV1, therefore,
control target (set pressure difference) for the pressure
difference (PdH-PdL) between the pressures on opposite sides of the
throttle 36a, that is, a standard for positioning the valve body 43
by the bellows 50 is changed by varying the electromagnetic force
that is applied to the valve body 43. To put in other words, the
first control valve CV1 is constructed to internally autonomously
position the valve rod 40 (the valve body 43) in accordance with
the variation of the pressure difference (PdH-PdL) between the
first and second pressure monitoring points P1 and P2 such that the
set pressure difference determined by the amount of the electric
power supplied to the coil 67 is maintained.
[0056] The set pressure difference of the first control valve CV1
is varied by adjusting the amount of the electric power supplied to
the coil 67 from the external device. For example, when the duty
ratio that is commanded from the control device 68 to the driving
circuit 68a is increased, electromagnetic urging force of the
solenoid portion 60 is increased, and the set pressure difference
of the first control valve CV1 is increased, accordingly. With the
set pressure difference of the first control valve CV1 thus
increased, the displacement of the compressor is increased. On the
other hand, when the duty ratio that is commanded from the control
device 68 to the driving circuit 68a is decreased, electromagnetic
urging force of the solenoid portion 60 is decreased, and the set
pressure difference of the first control valve CV1 is decreased.
When the set pressure difference of the first control valve CV1 is
decreased, the displacement of the compressor is decreased.
[0057] As shown in FIGS. 1, 3A, 4A and 4B, an accommodation hole 70
is formed in the rear housing 4 for accommodating therein the
second control valve CV2. The rear housing 4 functions also as a
valve housing for the second control valve CV2. In the drawings,
the cross section showing the second control valve CV2 is different
from that showing the first control valve CV1 and the suction
chamber 21. The first control valve CV1 protrudes from a rear end
4a of the rear housing 4 toward the rear side, and the
accommodation hole 70 is not covered with the first control valve
CV1.
[0058] The accommodation hole 70 is formed extending through the
rear end 4a and a front end of 4b of the rear housing 4 in parallel
with the axis L of the drive shaft 6 or in the horizontal direction
of as viewed in FIGS. 1, 3A, 4A and 4B. The front opening of the
accommodation hole 70 on the front end 4b of the rear housing 4 is
closed by the valve plate assembly 3. The accommodation hole 70
includes a valve chamber 71 that is a small-diameter hole, a
middle-diameter hole 72 whose diameter is greater than that of the
valve chamber 71, and a large-diameter hole 73 whose diameter is
still greater than that of the hole 73, in this order as seen from
the left side on the drawings. As seen from FIG. 3a, the valve
chamber 71, the middle-diameter hole 72 and the large-diameter hole
73 are formed coaxially.
[0059] A valve hole 27a is formed in the valve plate assembly 3
that partially defines the valve chamber 71 and the cylinder block
1. The valve chamber 71 communicates with the crank chamber 5 via
the valve hole 27a. The valve chamber 71 also communicates with a
communication hole 27b that is formed in the rear housing 4. The
communication hole 27b is opened into the valve chamber 71 through
a cylindrical inner peripheral surface 71a of the valve chamber 71.
The valve hole 27a, the valve chamber 71 and the communication hole
27b form the first bleed passage 27.
[0060] A spool 75 is received in the valve chamber 71 and the
middle-diameter hole 72 for movement in the horizontal direction as
seen in FIGS. 1, 3A, 4A and 4B. A stopper 76 is fixedly fitted in
the large-diameter hole 73. The stopper 76 is positioned by the
step portion that is located between the large-diameter hole 73 and
the middle-diameter hole 72 in the rear housing 4 for restricting
the movement of the spool 75 beyond the rear end of the
middle-diameter hole 72.
[0061] The spool 75 has a small-diameter portion 75a located on the
side of the valve chamber 71 and a large-diameter portion 75b
formed coaxially with the small-diameter portion 75a and located on
the side of the middle-diameter portion 72. The spool 75 has also
an annular-shaped movable step 78 formed between outer peripheral
surfaces 77a and 77b of the small-diameter portion 75a and the
large-diameter portion 75b of the spool 75. The movable step 78
includes a wall surface 78a that faces toward a side of the valve
plate assembly 3.
[0062] The large-diameter portion 75b of the spool 75 has a
cylindrical shape with an opening to the rear side, that is, to the
side of the stopper 76. The small-diameter portion 75a of the spool
75 is almost located in the valve chamber 71, and the
large-diameter portion 75b is accommodated in the middle-diameter
hole 72 for movement in the axial direction of the spool 75. The
small-diameter portion 75a is coaxial with the valve hole 27a, and
the diameter of the small-diameter portion 75a is larger than that
of the valve hole 27a. The front end of the small-diameter portion
75a forms a first valve portion 79 that adjusts the opening degree
of the valve hole 27a that communicates with the valve chamber 71,
that is, the opening degree of the first bleed passage 27. When the
first valve portion 79 approaches the valve plate assembly 3, the
opening degree of the valve hole 27a is decreased. On the other
hand, when the first valve portion 79 moves away from the valve
plate assembly 3, the opening degree of the valve hole 27a is
increased.
[0063] A backpressure chamber 80 is defined between the stopper 76
and the large-diameter portion 75b of the spool 75 in the
middle-diameter hole 72. The backpressure chamber 80 includes a
cylindrical inner space of the large-diameter portion 75b. The
spool 75 has a back surface 81 which includes the end surface of
the opening portion of the large-diameter portion 75b and the inner
bottom surface of the large-diameter portion 75b. Thus, the back
surface 81 of the spool 75 is located in the backpressure chamber
80.
[0064] In the supply passage 29, a pressure introducing passage 82
branches from the supply passage 29 at the region K that is located
on the side of the crank chamber 5, that is, downstream of the
position of valve opening adjustment in the first control valve CV1
(or the valve seat 53). The pressure introducing passage 82
communicates with the large-diameter hole 73 and is opened into an
inner peripheral surface 73a of the large diameter hole 73.
[0065] A communication groove 76a and a communication hole 76b are
formed in the stopper 76 to interconnect the pressure introducing
passage 82 and the middle-diameter hole 72. The communication
groove 76a is formed annularly throughout the outer peripheral
surface of the stopper 76 at a position facing the opening of the
pressure introducing passage 82. The communication hole 76b extends
through the stopper 76 between the communication groove 76a and an
end surface 76c of the stopper 76 on the side of the valve plate
assembly 3, The communication hole 76b is open at the center of the
end surface 76c.
[0066] Pressure PdK in the region K of the supply passage 29 is
introduced into the backpressure chamber 80 via the pressure
introducing passage 82, the communication groove 76a and the
communication hole 76b. Namely, the backpressure chamber 80 has the
same pressure atmosphere as the region K that is located downstream
of the position of valve opening adjustment in the control valve
CV1 in the supply passage 29. Force from the pressure PdK in the
backpressure chamber 80 urges the spool 75 toward the valve plate
assembly 3, that is, in the direction that causes the valve to be
closed. Namely, the spool 75 has the characteristics of decreasing
the opening degree of the valve hole 27a with an increase in the
pressure PdK in the backpressure chamber 80 that is applied to the
back surface 81.
[0067] The outer diameter of the large-diameter portion 75b of the
spool 75 is larger than the inner diameter of the valve chamber 71.
An annular fixed step 83 is formed between the valve chamber 71 and
the middle-diameter hole 72 in the second control valve CV2. The
fixed step 83 includes a wall surface 83a that faces the wall
surface 78a of the movable step 78 of the spool 75. When the spool
75 has reached the position closest to the valve plate assembly 3,
the wall surface 78a of the movable step 78 is brought into contact
with the wall surface 83a of the fixed step 83 to seat the spool
75. The axial length of the small-diameter portion 75a of the spool
75 is slightly smaller than that of the valve chamber 71. Thus,
with the spool 75 positioned closest to the valve plate assembly 3,
the wall surface 78a of the movable step 78 contacts the wall
surface 83a of the fixed step 83, and a slight clearance is formed
between the first valve portion 79 and the valve plate assembly 3.
Since the first bleed passage 27 is not closed even when the
opening of the valve hole 27a is reduced to the minimum and,
therefore, the crank chamber 5 keeps fluid communication with the
suction chamber 21 via the first bleed passage 27. The minimum
opening degree of the valve hole 27a is slightly larger than
zero.
[0068] The minimum clearance between the first valve portion 79 and
the valve plate assembly 3 functions as a throttle of the first
bleed passage 27. Thus, in consideration of the throttle of the
refrigerant gas in the first bleed passage 27 when the valve hole
27a is at the minimum opening degree, the diameter of the throttle
28a of the second bleed passage 28 is set smaller than that when
the second control valve CV2 and the first bleed passage 27 are not
hypothetically provided.
[0069] A spring 85 such as coil spring is located in a clearance 84
between the outer peripheral surface 77a of the small-diameter
portion 75a of the spool 75 and the inner peripheral surface 71a of
the valve chamber 71. The movable end of the spring 85 is in
contact with the wall surface 78a of the movable step 78 at a
region that is located radially inward from the region where the
wall surface 78a faces the wall surface 83a of the fixed step 83.
That is, the inner region of the wall surface 78a that is located
radially inward from the annular region of the wall surface 78a
that faces the wall surface 83a of the fixed step 83 forms a spring
seat 86 for the movable end of the spring 85. The fixed end of the
spring 85 is in contact with the valve plate assembly 3 at a
position surrounding the opening of the valve hole 27a. The spring
85 urges the spool 75 in the direction that causes the first valve
portion 79 to move so as to increases the opening degree of the
valve hole 27a.
[0070] A clearance 87 is formed between an outer peripheral surface
77b of the large-diameter portion 75b of the spool 75 and an inner
peripheral surface 72a of the middle-diameter hole 72, and the
clearance 87 is narrower than the clearance 84 between the outer
peripheral surface 77a of the small-diameter portion 75a and the
inner peripheral surface 71a of the valve chamber 71. A clearance
84a is formed between the spring 85 and the inner peripheral
surface 71a of the valve chamber 71 and, especially, is provided
such that the spring 85 freely extends and contracts in accordance
with the movement of the spool 75. The clearance 87 is also
narrower than the clearance 84a. Namely, the clearance 87 is the
narrowest of the all clearances that are around the cylindrical
outer peripheral surface 77 of the spool 75.
[0071] When the wall surface 78a of the movable step 78 is moved
away from the wall surface 83a of the fixed step 83 as shown in
FIG. 4B, the valve chamber 71 communicates with the backpressure
chamber 80 via the clearance between the wall surfaces 78a and 83a
and the clearance 87 of the spool 75. On the other hand, when the
wall surface 78a of the movable step 78 contacts the wall surface
83a of the fixed step 83 as shown in FIG. 3A, the communication
between the backpressure chamber 80 and the valve chamber 71 via
the clearance 87 of the spool 75 is shut off. Namely, the annular
region of the wall surface 78a of the movable step 78 that faces
the wall surface 83a of the fixed step 83 forms a second valve
portion 88 for shutting off the communication between the
backpressure chamber 80 and the valve chamber 71 via the clearance
87 of the spool 75. A valve seat 89 for the second valve portion 88
is formed by an annular region of the wall surface 83a of the fixed
step 83 that faces the second valve portion 88.
[0072] As shown in FIGS. 1 and 2, a filter 90 is arranged in the
supply passage 29 on the side of the discharge chamber 22, that is,
upstream of the first control valve CV1 for removing foreign
substances in the refrigerant gas. As shown in FIGS. 3A and 4, the
width of the clearance 87 between the large-diameter portion 75b of
the spool 75 and the inner peripheral surface 72a of the
accommodation hole 70 is larger than the diameter of the foreign
substances that pass through the filter 90. In other words, the
width of the clearance 87 is larger than the diameter of the mesh
openings of the filter 90. Namely, the clearance 87 that is the
narrowest clearance around the cylindrical outer peripheral surface
77 of the spool 75 is formed with a width that is larger than the
diameter of the foreign substances flowing through the clearance
87.
[0073] Referring to FIG. 3B, in the second control valve CV2, the
cross sectional area of the valve chamber 71 that is perpendicular
to the axial direction of the spool 75 is represented as SA, and
the cross sectional area of the valve hole 27a that is also
perpendicular to the axial direction of the spool 75 is represented
as SB, which is smaller than SA. A force for urging the spool 75
toward the valve plate assembly 3, that is, in the direction in
which the opening degree of the valve hole 27a is decreased in
response to the varying pressure difference between the pressure
PdK and the crank pressure Pc is expressed by "(PdK-PC)SB".
[0074] A force for urging the spool 75 in the direction which
causes the opening degree of the valve hole 27a to be decreased in
accordance with the pressure difference between the pressure PdK
and the suction pressure Ps, is expressed by "(PdK-Ps)(SA-SB)." The
urging force of the spring 85 is represented as "f". Conditional
inequality (1) for the minimum opening degree of the valve hole 27a
in the second control valve CV2 is expressed as follows:
(PdK-Ps)(SA-SB)+(Pdk-Pc)SB>f (1)
[0075] The backpressure chamber 80 is in constant communication
with the crank chamber 5 via the supply passage 29 and has the same
pressure atmosphere as the crank chamber 5. Thus, it is presumed
that the pressure PdK is substantially the same as the pressure Pc.
Therefore, the above inequality (1) is expressed as the following
conditional inequality (2):
(Pc-Ps)(SA-SB)>f (2)
[0076] The spring 85 for use in the illustrated embodiment has a
small set load and a low spring constant. It is understood,
therefore, from the above conditional inequality (2) that the valve
portion 79 reduces the opening degree of the valve hole 27a to the
minimum opening degree when the crank pressure Pc somewhat exceeds
the suction pressure Ps.
[0077] When a predetermined length of time or more has passed after
a stop of the vehicle engine E, the pressure is equalized at a low
value in the refrigerant circulation circuit and, therefore, the
crank pressure Pc becomes substantially the same as the suction
pressure Ps. Since the conditional inequality (2) is no more
effective, the spool 75 is moved by the urging force of the spring
85 until the spool 75 is brought into contact with the stopper 76,
as shown in FIG. 4A. With the spool 75 thus fully urged by the
spring 85, the valve portion 79 sets the opening degree of the
valve hole 27a at its maximum.
[0078] In a conventional compressor for a vehicle air-conditioner,
liquid refrigerant, existing on the low pressure side of the
external refrigerant circuit 30 with the vehicle engine E kept at a
stop for a long time, flows into the crank chamber 5 via the
suction chamber 21 due to the fluid communication between the crank
chamber 5 and the suction chamber 21 via the first and second bleed
passages 27 and 28. Especially, when the temperature in the engine
room where the compressor is located is lower than that in the
vehicle interior, a large amount of the liquid refrigerant flows
into the crank chamber 5 via the suction chamber 21 and is
accumulated in the crank chamber 5. Therefore, when the vehicle
engine E is started and the compressor is also started thereby
through the clutchless type power transmission mechanism PT, the
liquid refrigerant evaporates under the influence of heat generated
by the vehicle engine E and also of the stirring effect due to
stirring the liquid refrigerant by the swash plate 12, with the
result that the crank pressure Pc tends to be increased regardless
the opening degree of the valve hole 27a.
[0079] For example, when the vehicle engine E is started while the
vehicle interior is hot, the control device 68 is operated in
response to the cooling demand from the occupant of the vehicle to
command maximum duty ratio to the drive circuit 68a, and the set
pressure difference of the first control valve CV1 is set at the
maximum value for performing cooling as required. Accordingly, the
first control valve CV1 closes the supply passage 29, and no high
pressure refrigerant gas is supplied from the discharge chamber 22
to the crank chamber 5 and the backpressure chamber 80 of the
second control valve CV2. Therefore, even if evaporation of the
liquid refrigerant occurs in the crank chamber 5, the state where
the pressure difference between the crank pressure Pc and the
suction pressure Ps does not exceed the urging force f, that is,
the state where the conditional inequality (2) is not effective,
continues.
[0080] Consequently, the spool 75 of the second control valve CV2
is maintained in such a state that the first valve portion 79 fully
opens the first bleed passage 27 by the urging force f of the
urging spring 85, and the liquid refrigerant in the crank chamber
5, as well as the refrigerant gas evaporated from a part of the
liquid refrigerant, is immediately flown into the suction chamber
21 via the fully-opened first bleed passage 27. Thus, the crank
pressure Pc is maintained at a low value corresponding to that the
first control valve CV1 is closed, the compressor increases the
inclination angle of the swash plate 12 thereby to increase the
displacement of the compressor to its maximum.
[0081] If the first control valve CV1 remains closed even after the
liquid refrigerant is flown out from the crank chamber 5, the first
bleed passage 27 is fully opened by the first valve portion 79 of
the second control valve CV2 as described above. Thus, even if the
amount of blow-by gas from the cylinder bores 1a to the crank
chamber 5 is more than the amount initially designed, for example,
due to worn pistons 20, the blow-by gas is immediately flown into
the suction chamber 21 via the first and second bleed passages 27
and 28. Therefore, the crank pressure Pc is maintained at
substantially the same level as the suction pressure Ps, and the
maximum inclination angle of the swash plate 12, that is, the
maximum displacement operation (100% displacement operation) of the
compressor is maintained.
[0082] As described above, when the first valve portion 79 of the
second control valve CV2 sets the opening degree of the first bleed
passage 27 larger than the minimum opening degree, the second valve
portion 88 is moved away from the valve seat 89, and the
backpressure chamber 80 communicates with the valve chamber 71 via
the clearance 87 (refer to FIG. 4B). However, since the first
control valve CV1 is in its closed state when the backpressure
chamber 80 is in communication with the valve chamber 71, no
refrigerant gas in the discharge chamber 22 flows into the
backpressure chamber 80 via the first control valve CV1, and hence
there is no fear of a decrease in efficiency of the refrigerant
cycle caused by leakage of the refrigerant gas from the
backpressure chamber 80 to the valve chamber 71.
[0083] When the vehicle interior is cooled to a certain extent due
to the above maximum displacement operation of the compressor, the
control device 68 reduces the duty ratio that is commanded to the
drive circuit 68a from the maximum. Accordingly, the first control
valve CV1 is changed from the closed state and opens the supply
passage 29 so that the crank pressure Pc becomes higher than the
suction pressure Ps. The conditional inequality (2) is satisfied,
so that spool 75 moves against the urging force of the spring 85 in
the direction to reduce the valve opening and the first bleed
passage 27, that is, the valve hole 27a is substantially throttled
by the first valve portion 79.
[0084] Namely, when the supply passage 29 is opened by the first
control valve CV1 and the introduction of the refrigerant gas from
the discharge chamber 22 into the crank chamber 5 starts, the
amount of the refrigerant gas flown out from the crank chamber 5 to
the suction chamber 21 via the first bleed passage 27 is
substantially decreased in accordance with the above gas
introduction into the crank chamber 5. Thus, the crank pressure Pc
is rapidly increased, and the compressor immediately reduces the
inclination angle of the swash plate 12 so that the displacement of
the compressor is reduced.
[0085] Amount of the compressed refrigerant gas that leaks from the
discharge chamber 22 to the crank chamber 5 further to the suction
chamber 21 is reduced by decreasing the opening degree of the first
bleed passage 27 by the second control valve CV2, so that the
decrease in the efficiency of the refrigerant cycle is prevented.
Furthermore, although the refrigerant circulation circuit in the
first preferred embodiment is formed such that the refrigerant
circulation stops by operating the compressor at the minimum
displacement (so called an OFF operation of the clutchless
compressor), the OFF operation of the compressor is reliably
performed due to the substantial decrease in the opening degree of
the first bleed passage 27 by the second control valve CV2.
[0086] When the first valve portion 79 of the second control valve
CV2 sets the first bleed passage 27 at the minimum opening degree,
the second valve portion 88 contacts the valve seat 89 as described
above. Accordingly, the communication between the valve chamber 71
and the backpressure chamber 80 is shut off. Thus, the refrigerant
gas in the discharge chamber 22 is prevented from leaking from the
backpressure chamber 80 to the suction chamber 21 via the clearance
87, the valve chamber 71 and the communication hole 27b. Therefore,
the decrease in the efficiency of the refrigerant cycle is
prevented.
[0087] While the first control valve CV1 is opened, fine foreign
substances that are not removed by the filter 90 flow into the
second control valve CV2 together with the refrigerant gas and
possibly further into the clearance 87 of the spool 75. However,
since the width of the clearance 87 of the spool 75 is larger than
the diameter of the foreign substances that have passed through the
filter 90, the foreign substances are prevented from being caught
in the clearance 87, so that the spool 75 moves smoothly without
any operation failure. Even if the foreign substances remain in the
clearance 87 at the second valve portion 88 in contact with the
valve seat 89, such foreign substances are removed from the
clearance 87 by the flow of the refrigerant gas occurring when the
second control valve CV2 is opened as shown in FIG. 4B.
[0088] The following advantageous effects are obtained according to
the above-described first preferred embodiment of the present
invention.
[0089] (1) When the first valve portion 79 sets the valve hole 27a
at the minimum opening degree, the second valve portion 88 of the
spool 75 shuts off the communication between the backpressure
chamber 80 and the valve chamber 71 via the clearance 87 of the
spool 75 in the second control valve CV2. Thus, it is unnecessary
that the clearance 87 is set small, and the operation failure of
the spool 75 caused by the foreign substances caught in the
clearance 87 is prevented.
[0090] (2) The second valve portion 88 is formed by the wall
surface 78a of the movable step 78 on the cylindrical outer
peripheral surface 77 of the spool 75, and the valve seat 89 for
the second valve portion 88 is formed by the wall surface 83a of
the fixed step 83. In other words, the functions of the second
valve portion 88 and the valve seat 89 are provided to the second
control valve CV2 by simple structure such as the movable and fixed
steps 78 and 83 in the first preferred embodiment. Therefore, the
structure of the second control valve CV2 is simplified.
[0091] (3) The minimum opening degree of the valve hole 27a by the
first valve portion 79 of the second control valve CV2 is not zero.
Thus, it is not necessary to machine the first valve portion 79 and
the second valve portion 88 in the spool 75 at a very high
accuracy, and the manufacture of the spool 75 is easier.
Accordingly, in a structure in which the valve portions 79 and 88
provided in the spool 75 are required to be brought into contact
simultaneously with the valve plate assembly 3 and the valve seat
89 so as to shut off the fluid communication and, parts of the
control valve are required to be manufactured to a very high
standard of accuracy. Apparently, the structure will make it
troublesome and hence costly to manufacture valve parts such as
spool, valve seat and valve plate assembly.
[0092] (4) The second control valve CV2 includes the spring 85 for
urging the spool 75 in the direction to increase the valve opening,
and the urging force f of the spring 85 relates to the positioning
of the spool 75. Thus, the operating characteristics of the second
control valve CV2 is easily adjusted by changing the urging force f
of the spring 85, that is, by selecting an appropriate spring from
a group of springs having different characteristics.
[0093] (5) In the second control valve CV2, the wall surface 78a of
the movable step 78 that forms the second valve portion 88 is also
utilized as the spring seat 86 for the spring 85. Accordingly, in
comparison to a case in which a spring seat (a step) is provided
separately from the movable step 78, the structure of the spool 75
and the structure of the second control valve CV2 is
simplified.
[0094] (6) The filter 90 is provided between the discharge chamber
22 and the first control valve CV1, and the width of the clearance
87 of the spool 75 is larger than the diameter of the foreign
substances that pass through the filter 90. Thus, the foreign
substances whose diameter is larger than the width of the clearance
87 of the spool 75 will not be caught in the clearance 87, and the
operation failure of the spool 75 in the second control valve CV2
is prevented successfully.
[0095] The following will describe a second preferred embodiment
according to the present invention. In the following description
about the second preferred embodiment, only the difference thereof
from the first preferred embodiment will be described. Like or
corresponding elements or parts are referred to by like reference
numerals, and the detailed description thereof is omitted.
[0096] The valve hole 27a of the above-described first preferred
embodiment is arranged so as to interconnects the crank chamber 5
and the valve chamber 71. However, the valve hole 27a in the second
preferred embodiment is arranged so as to interconnects the suction
chamber 21 and the valve chamber 71 as shown in FIGS. 5 and 6.
Further, the communication hole 27b, which is arranged so as to
interconnect the suction chamber 21 and the valve chamber 71 in the
above-described first preferred embodiment, is modified in the
second preferred embodiment such that the communication hole 27b
interconnects the crank chamber 5 and the valve chamber 71.
[0097] The accommodation hole 70 of the second control valve CV2
extends in the vertical direction in FIGS. 5 and 6 and is open to
the outside of the compressor. The valve chamber 71 is located in
the upper side of the accommodation hole 70, the large-diameter
hole 73 is located in the lower side of the accommodation hole 70,
and the middle-diameter hole 72 is removed from the accommodation
hole 70.
[0098] The valve hole 27a is open in a ceiling surface 71b of the
valve chamber 71. The communication hole 27b is open in the inner
peripheral surface 71a of the valve chamber 71. The communication
hole 27b serves as a part of the region of the supply passage 29 on
the side of the crank chamber 5 with respect to the second control
valve CV2. The connection in the supply passage 29 between the
first and second control valves CV1 and CV2 is open in the inner
peripheral surface 73a of the large-diameter hole 73 of the second
control valve CV2.
[0099] A spool 91 having a cylindrical shape with a cover is
accommodated in the valve chamber 71 for movement in the vertical
direction as seen in FIGS. 5 and 6. The spool 91 is placed so as to
have its opening that faces downward. The diameter of the top
surface of the cylindrical spool 91 is larger than that of the
valve hole 27a. A region of the top surface of the spool 91 that
faces the ceiling surface 71b of the valve chamber 71 forms a valve
portion 92. A region of the ceiling surface 71b of the valve
chamber 71 that faces the valve portion 92 forms a valve seat 93
for the valve portion 92.
[0100] The spool 91 is formed with a flange 94 protruding radially
outwardly from the opening portion of the spool 91. A cylindrical
outer peripheral surface 77 of the spool 91 includes an outer
peripheral surface 77a of the flange 94 and an outer peripheral
surface 77b of the cylindrical portion that is located above the
flange 94 in the spool 91 as seen in FIGS. 5 and 6. The spool 91
inserts into the spring 85 that is located in the clearance 84
formed between the outer peripheral surface 77b of the spool 91 and
the inner peripheral surface 71a of the valve chamber 71. The upper
surface of the flange 94 forms the spring seat 86 for receiving the
movable end of the spring 85. A region on the ceiling surface 71b
outward from the valve seat 93 forms a spring seat for receiving
the fixed end of the spring 85.
[0101] A slope 91a is formed in the lower peripheral surface of the
flange 94. The slope 91a is formed such that the distance from its
sloped surface to the end surface 76c of the stopper 76 is
increasing as the diameter of the slope 91a is larger. The back
surface 81 of the spool 91 includes the inner ceiling surface of
the spool 91, the lower surface of the spool 91 and the slope 91a
of the spool 91. The back surface 81 is located in the backpressure
chamber 80. Although the valve chamber 71 and the backpressure
chamber 80 in the second preferred embodiment are in constant
communication with each other and share the same space, a region
adjacent to the back surface 81 of the spool 91 is referred to as
the backpressure chamber 80. The backpressure chamber 80 has the
same pressure atmosphere as the region K that is located downstream
of the position of valve opening adjustment (the valve seat 53) of
the first control valve CV1 in the supply passage 29.
[0102] In the second control valve CV2, the clearance 87 between
the outer peripheral surface 77a of the flange 94 and the inner
peripheral surface 71a of the valve chamber 71 is narrower than the
clearance 84 between the spring 85 and the inner peripheral surface
71a of the valve chamber 71. The width of the clearance 87 is
larger than the diameter of the foreign substances that are around
the cylindrical outer peripheral surface 77 of the spool 91 and
pass through the filter 90.
[0103] It is presumed that the pressure PdK in the backpressure
chamber 80 is substantially the same as the crank pressure Pc.
Thus, the spool 91 closes the valve hole 27a in such a manner that
the valve portion 92 contacts the valve seat 93 when the
conditional inequality (3) below is satisfied. Therefore, when the
crank pressure Pc somewhat exceeds the suction pressure Ps, the
second control valve CV2 closes the first bleed passage 27. In the
conditional inequality (3), the weight of the spool 91 is ignored,
and "SB" denotes the cross sectional area of the valve hole
27a.
(Pc-Ps)SB>f (3)
[0104] With the first control valve CV1 opened, the crank pressure
Pc is increased, so that the above conditional inequality (3) is
effective. Thus, the spool 91 is moved upward until the valve
portion 92 contacts the valve seat 93, so that the valve hole 27a
or the first bleed passage 27 is closed, as shown in FIG. 5. The
constant communication between the crank chamber 5 and the suction
chamber 21 is ensured by the second bleed passage 28.
[0105] The communication hole 27b partially forms the supply
passage 29 together with the valve chamber 71 and the backpressure
chamber 80. Thus, the refrigerant gas that flows into the
backpressure chamber 80 via the first control valve CV1 flows into
the crank chamber 5 via the valve chamber 71 and the communication
hole 27b. The refrigerant gas flowing into the valve chamber 71 is
guided by the slope 91a of the spool 91 so as to flow smoothly into
the communication hole 27b.
[0106] When the valve portion 92 of the spool 91 closes the valve
hole 27a, the communication between the backpressure chamber 80 and
the valve hole 27a via the clearance 87 of the spool 91 is shut off
simultaneously by the valve portion 92. Thus, the refrigerant gas
in the discharge chamber 22 is prevented from leaking from the
region K to the suction chamber 21 via the backpressure chamber 80,
the valve chamber 71 and the valve hole 27a, so that the decrease
in the efficiency of the refrigerant cycle is prevented.
[0107] When the first control valve CV1 is closed, that is, when
the supply passage 29 is closed, as shown in FIG. 6, the crank
pressure Pc is lowered, and the above conditional inequality (3) is
no more effective, so that the spool 91 moves downward and the
valve portion 92 moves away from the valve seat 93. Thus, the valve
hole 27a communicates with the communication hole 27b via the valve
chamber 71, and the first bleed passage 27 is wide opened.
Therefore, the refrigerant in the crank chamber 5 is immediately
flown out into the suction chamber 21.
[0108] The following advantageous effects are obtained according to
the second preferred embodiment.
[0109] (7) In the second control valve CV2, the valve portion 92 of
the spool 91 closes the valve hole 27a or the first bleed passage
27 and also simultaneously shuts off of the communication between
the backpressure chamber 80 and the valve hole 27a via the
clearance 87 of the spool 91. Thus, it is unnecessary that the
clearance 87 is set to be small, and the operation failure of the
spool 91 caused by foreign substances caught in the clearance 87 is
prevented.
[0110] (8) The first bleed passage 27 and the supply passage 29
share the communication hole 27b as a common part of the passages.
Namely, the communication hole 27b serves as the part of the first
bleed passage 27 and the supply passage 29 between the crank
chamber 5 and the valve chamber 71. Thus, since a part of the
supply passage 29 between the branch point of the pressure
introducing passage 82 and the crank chamber 5 in the first
preferred embodiment is removed from the supply passage 29, the
arrangement of the passages is simplified, and the structure of the
displacement control mechanism is simplified.
[0111] Now, a third preferred embodiment will be described with
reference to FIGS. 7 and 8. The third preferred embodiment differs
from the second preferred embodiment mainly in that the second
control valve CV2 is installed in the valve housing 45 of the first
control valve CV1. In the first control valve CV1 in the third
preferred embodiment, the relationship of upstream or downstream
between the ports 51 and 52 is reverse of the relationship in the
first control valve CV1 of FIG. 2. That is, the supply passage 29
is connected at the upstream side thereof (or the side of the
discharge chamber 22) to the port 52 and at the downstream side
thereof (or the side of the crank chamber 5) to the port 51.
[0112] A spool 96, a valve seat body 97 and the spring 85 of the
second control valve CV2 are accommodated in the valve
accommodation chamber 46 of the first control valve CV1. A through
hole 96a is formed in the middle of the spool 96. The valve rod 40
is inserted into the through hole 96a, and the spool 96 moves in
the axial direction of the valve rod 40. The valve seat body 97 is
located below the spool 96 and in contact with the fixed core 62 in
the valve accommodation chamber 46. The part of the valve
accommodation chamber 46 located above the top surface of the valve
seat body 97 forms the valve chamber 71. A recess 96b is formed on
the top surface of the spool 96 around the through hole 96a.
[0113] A port 98 is formed in the peripheral wall of the valve
housing 45 that surrounds the lower portion of the valve
accommodation chamber 46. The port 98 is connected to the first
bleed passage 27 on the side of the suction chamber 21. The valve
hole 27a is formed in the valve seat body 97 and interconnects the
port 98 and the valve chamber 71. The valve hole 27a is open at the
top surface of the valve seat body 97 between the inner peripheral
surface and the outer peripheral surface of the valve seat body 97.
A groove 96c is formed in the lower surface of the spool 96. The
groove 96c has an annular shape surrounding the through hole 96a
and has a part that faces the valve hole 27a of the valve seat body
97.
[0114] An annular region in the lower surface of the spool 96 that
is located radially outward of the groove 96c forms the valve
portion 92. An annular region in the top surface of the valve seat
body 97 that is located radially outward of the valve hole 27a and
faces the valve portion 92 forms the valve seat 93 for the valve
portion 92.
[0115] An annular region in the lower surface of the spool 96 that
is located radially inward of the groove 96c forms a valve portion
96d for the through hole 96a. An annual region in the top surface
of the valve seat body 97 that is located radially inward of the
valve hole 27a and faces the valve portion 96d forms the valve seat
97a for the valve portion 96d. With the valve portion 92 brought in
contact with the valve seat 93, the valve portion 96d contacts the
valve seat 97a, thereby shutting off the communication between the
valve hole 27a and the backpressure chamber 80 via the clearance
formed between the inner peripheral surface of the of the through
hole 96a of the spool 96 and the outer peripheral surface of the
guide rod 44 in the valve rod 40.
[0116] A flange 94 is formed at the top of the spool 96. The lower
surface of the flange 94 forms the spring seat 86 for receiving the
movable end of the spring 85. A region in the top surface of the
valve seat body 97 that is located radially outward of the valve
seat 93 forms the valve seat for receiving the fixed end of the
urging spring 85. The back surface 81 of the spool 96 is formed by
the top surface of the spool 96 and the bottom surface of the
recess 96b. The backpressure chamber 80 that is located between the
back surface 81 and the position of valve opening adjustment, or
the valve seat 53, of the first control valve CV1 forms a part of
the region K that is located downstream, that is, on the side of
the crank chamber 5, of the position of valve opening adjustment of
the first control valve CV1 in the supply passage 29. Namely, the
backpressure chamber 80 has the same pressure atmosphere as the
region K.
[0117] The cylindrical outer peripheral surface 77 of the spool 96
includes the outer peripheral surface 77a of the flange 94 and the
outer peripheral surface of the spool 96 that is located below the
flange 94. The spring 85 is located in the clearance 84 between the
outer peripheral surface 77b and the inner peripheral surface 71a
of the valve chamber 71. The clearance 87 between the outer
peripheral surface 77a of the flange 94 and the inner peripheral
surface 71a of the valve chamber 71 is narrower than the clearance
84a between the spring 85 and the inner peripheral surface 71a of
the valve chamber 71.
[0118] As shown in. FIG. 7, with the first control valve CV1
opened, the crank pressure Pc, which is considered to be
substantially the same as the pressure PdK in the backpressure
chamber 80, is increased, so that the spool 96 is moved downward
until the valve portion 92 contacts the valve seat 93. Thus, the
valve hole 27a is closed and the first bleed passage 27 is closed,
accordingly. Thus, the refrigerant gas that flows from the
discharge chamber 22 into the backpressure chamber 80 via the port
52 and the communication passage 47 flows into the crank chamber 5
via the port 51.
[0119] As shown in FIG. 8, with the first control valve CV1 closed,
that is, when the supply passage 29 is closed, on the other hand,
the crank pressure Pc is decreased. Accordingly, the spool 96 is
moved upward by the urging force of the spring 85, that is, the
valve portion 92 is moved away from the valve seat 93, so that the
valve hole 27a communicates with the port 51 and the first bleed
passage 27 is wide opened. Thus, the refrigerant in the crank
chamber 5 is immediately flown into the suction chamber 21 via the
port 51, the valve chamber 71 and the valve hole 27a.
[0120] According to the third preferred embodiment, the same
advantageous effects are obtained as those which have been
described in the second preferred embodiment. In addition, since
the first and second control valves CV1 and CV2 are formed as a
single unit, the first and second control valves CV1 and CV2 are
easily assembled to the rear housing 4 during manufacturing of the
compressor.
[0121] The preferred embodiment according to the present invention
is not limited to the above-described preferred embodiments, but it
may be modified in various ways as follows.
[0122] A first alternative embodiment is shown in FIG. 9 and is a
modification of the second preferred embodiment. In this
embodiment, the spool 91 is formed in the top surface thereof with
a recess 91b. A cross sectional area SC of the recess 91b that is
perpendicular to the axis of the spool 91 is larger than the cross
sectional area SB of the valve hole 27a that is perpendicular to
the axis of the spool 91. In the conditional inequality (3) for
closing the valve hole 27a, the pressure difference (Pc-Ps) is
multiplied by the cross sectional area SC of the recess 91b instead
of the cross sectional area SB of the valve hole 27a. Thus, even if
the urging force f of the spring 85 is set relatively large with
respect to a predetermined value of the pressure difference
(Pc-Ps), the second control valve CV2 closes.
[0123] As described above, when the air-conditioner is started, it
is desirable that the valve hole 27a is wide opened for allowing
the liquid refrigerant that is accumulated in the crank chamber 5
to flow out thereof. However, when the air-conditioner is stated,
the refrigerant gas in the suction chamber 21 is drawn into the
cylinder bores 1a and the suction pressure Ps is instantaneously
decreased, so that the spool 91 of the second control valve CV2 may
be moved toward the valve hole 27a thereby to decrease the opening
degree of the valve hole 27a. In the result, the efficiency of
flowing the liquid refrigerant is decreased. Thus, a relatively
large amount of the urging force of the spring 85 that acts on the
spool 91 in the direction which increases the opening degree of the
valve hole 27a is required. Therefore, the embodiment of FIG. 9,
wherein the spool 91 is formed in the top surface thereof with the
recess 91b, prevents a decrease in the efficiency of flowing the
liquid refrigerant, while ensuring the ease of closing operation of
the second control valve CV2.
[0124] Furthermore, in the first alternative embodiment shown in
FIG. 9, the communication hole 27b extends obliquely upward from
the valve chamber 71. There is a large space in the valve chamber
71 and the large-diameter hole 73 on the side of the communication
hole 27b. A wall 99 protrudes from the stopper 76 in the vertical
direction as seen on the drawing to the ceiling surface 71b of the
valve chamber 71. The wall 99 divides the valve chamber 71 into a
space that accommodates the spool 91 and a communication passage
100 that extends in the vertical direction on the drawing and
communicates with the communication hole 27b.
[0125] A hole 99a is formed through the wall 99 so that the
refrigerant gas that flows from the first control valve CV1 into
the backpressure chamber 80 via the communication hole 76b of the
stopper 76 and is guided toward the wall 99 by the slope 91c flows
toward the crank chamber 5 via the communication passage 100 and
the communication hole 27b. In addition to the hole 99a, another
hole 99b is formed through the wall 99 so that, when the second
control valve CV2 is opened, the refrigerant that flows from the
crank chamber 5 into the communication passage 100 via the
communication hole 27b flows into the suction chamber 21 via the
valve chamber 71 and the valve hole 27a. The hole 99b is formed
above the hole 99a. Even though the communication hole 27b extends
obliquely upward from the valve chamber 71, the provision of the
communication passage 100 and the though holes 99a and 99b helps to
facilitate the flow of the refrigerant gas in the first bleed
passage 27 and the supply passage 29.
[0126] A second alternative embodiment that is a modification of
the second preferred embodiment is shown in FIG. 10. This
alternative embodiment differs from the second preferred embodiment
in that the spool 91 is disposed in upside down relation, the
flange 94 is removed, and the spring 85 is accommodated within the
spool 91. In this case, the inner and outer diameters of the spool
91 are enlarged by the length of the removed flange 94 for the
valve chamber 71 having the same diameter as in the second
preferred embodiment. In the second alternative embodiment of FIG.
10, above conditional inequality (3) is used in such a way that the
pressure difference (Pc-Ps) is multiplied, not by the cross
sectional area SB of the valve hole 27a, but by a cross sectional
area SD of the inner space of the spool 91 that is perpendicular to
the axis of the spool 91 and is larger than the cross sectional
area SC of the recess 91b of the spool 91 having the flange 94 as
shown in FIG. 9. Therefore, the second alternative embodiment of
FIG. 10 prevents a decrease in the efficiency of flowing the liquid
refrigerant, while ensuring the ease of closing operation of the
second control valve CV2.
[0127] In the second alternative embodiment shown in FIG. 10, if
the slope 91c is further formed in the inner periphery and at the
open end of the spool 91, in the above conditional inequality (3),
the pressure difference (Pc-Ps) is multiplied by a cross sectional
area SE of the opening of the spool 91 that is perpendicular to the
axis of the spool 91 and is larger than the cross sectional area SD
of the inner space of the spool 91 that is located below the slope
91c. Therefore, the second alternative embodiment of FIG. 10
prevents a decrease in the efficiency of flowing the liquid
refrigerant, while ensuring the ease of closing operation of the
second control valve CV2.
[0128] In the first preferred embodiment, the minimum opening
degree of the valve hole 27a by the first valve portion 79 of the
second control valve CV2 is not zero. However, it is so arranged,
as shown in FIGS. 11 through 14, that the minimum opening degree of
the valve hole 27a by the first valve portion 79 is zero and also
that elasticity is provided to at least one of the first valve
portion 79, the valve seat or the valve plate assembly 3 for the
first valve portion 79, the second valve portion 88 and the valve
seat 89 for the second valve portion 88. In this case, the element
provided with the elasticity out of the above-named parts is
elastically deformable. By so arranging, the opening of the two
valve portions 79 and 88 formed in the single spool 75 can be
reduced to zero simultaneously without the need of machining the
spool 75 and the valve seat 89 (or the valve plate assembly 3) at a
very high accuracy.
[0129] In a third alternative embodiment shown in FIG. 11, the
second valve portion 88 of the second control valve CV2 is formed
by a ring-shaped lead 101. The small-diameter portion 75a has an
engaging protrusion 75c, and the large-diameter portion 75b has an
engaging recess 75d. In the spool 75, the large-diameter portion
75b and the small-diameter portion 75a are combined together such
that the engaging protrusion 75c is inserted into the engaging
recess 75d with the lead 101 held between the small-diameter
portion 75a and the large-diameter portion 75b. A slope 78b is
formed in the region of the wall surface 78a of the movable step 78
and is located outside the spring seat 86 for allowing the lead 101
to be deformed toward a space provided by forming the slope
78b.
[0130] In a fourth alternative embodiment shown in FIG. 12, the
first valve portion 79 of the second control valve CV2 is formed by
a lead 102. The lead 102 has a ring shape and is fitted around a
protrusion 75e formed at the center of the end surface of the
small-diameter portion 75a on the side thereof adjacent to the
valve plate assembly 3. A slope 75f is formed on the end surface of
the small-diameter portion 75a in the radially outward region
thereof for the same purpose as the slope 78b of FIG. 11.
[0131] Furthermore, in a fifth alternative embodiment shown in FIG.
13, the large-diameter portion 75b of the spool 75, that is, the
second valve portion 88 is made of rubber. As a further alternative
embodiment of the fifth alternative embodiment, the small-diameter
portion 75a, instead of the large-diameter portion 75b (the second
valve portion 88), of the spool 75 is made of rubber.
[0132] A sixth alternative embodiment that is a modification of the
fifth alternative embodiment is shown in FIG. 14. In this
embodiment, the large-diameter portion 75b is fitted in a cylinder
103 that is made of metal. The width of the clearance 87 between
the outer peripheral surface of the cylinder 103 and the inner
peripheral surface 72a of the middle-diameter hole 72 is larger
than the diameter of the foreign substances that pass through the
filter 90. The second valve portion 88 is formed protruding beyond
the cylinder 103.
[0133] In this embodiment, even though the rubber large-diameter
portion 75b is deformed when the rubber large-diameter portion 75b
contacts the valve seat 89 or the stopper 76, the cylinder 103
functions to restrict the deformation of the rubber large-diameter
portion 75b in the radially outward direction. Thus, the clearance
87 is formed without considering the deformation of the rubber
large-diameter portion 75b.
[0134] Also, the foreign substances are less liable to be attached
to the surface of the metallic cylinder 103 than to the surface of
rubber. Even if the foreign substances are accumulated in the
clearance 87 when the second valve portion 88 contacts the valve
seat 89, such foreign substances are easily flown from the
clearance 87 by the refrigerant gas when the second valve portion
88 is moved away from the valve seat 89. Additionally, since the
outer peripheral surface of the metallic cylinder 103 is less
susceptible to damage by the foreign substances, the endurance of
the spool 75 is extended.
[0135] In addition to the third through sixth alternative
embodiments shown in FIGS. 11 through 14, for example, the entire
spool 75 is made of rubber to provide elasticity to both the first
and second valve portions 79 and 88. Also, the valve seat for the
first valve portion 79 is formed by a lead or rubber to be provided
with elasticity. Furthermore, the valve seat 89 for the second
valve portion 88 is formed by a lead or rubber for the same
purpose. In still further alternative embodiment, elasticity is
provided to both the valve seat for the first valve portion 79 and
the valve seat 89 for the second valve portion 88.
[0136] In the above-described first and second preferred
embodiments, the backpressure chamber 80 of the second control
valve CV2 has the same pressure atmosphere as the region K that is
located downstream of the position of valve opening adjustment (the
valve seat 53) of the first control valve CV1 in the supply passage
29, and the backpressure chamber 80 is in constant communication
with the crank chamber 5 via the part of the supply passage 29.
However, in a seventh alternative embodiment, a passage that
interconnects the backpressure chamber 80 and the crank chamber 5
is provided independently of the supply passage 29. Namely, the
backpressure chamber 80 has the same pressure atmosphere via the
above passage and the crank chamber 5 as the region K that is
located downstream of the position of valve opening adjustment (the
valve seat 53) in the supply passage 29.
[0137] In each of the above-described preferred embodiments, the
backpressure chamber 80 of the second control valve CV2 is in
constant communication with the crank chamber 5 via the part of the
supply passage 29, and it is presumed that the pressure PdK in the
backpressure chamber 80 is substantially the same as the crank
pressure Pc. However, in an eighth alternative embodiment, a fixed
throttle is formed in the valve plate assembly 3 on the supply
passage 29, so that the pressure PdK in the backpressure chamber 80
is larger than the crank pressure Pc when the first control vale
CV1 is opened.
[0138] In this modification, when decreasing the displacement of
the compressor in a state in which the second control valve CV2 is
opened, the pressure PdK in the backpressure chamber 80 is rapidly
increased by opening the first control valve CV1, so that the
second control valve CV2 is closed. Thus, the displacement of the
compressor is immediately decreased.
[0139] In each of the above-described preferred embodiments, the
first control valve CV1 is so constructed that the pressure
difference (PdH-PdL) is detected between the pressure monitoring
points P1 and P2. However, the first control valve CV1 is so
constructed that only the suction pressure Ps is detected in a
ninth alternative embodiment. Namely, the first control valve CV1
is constructed to internally autonomously position the valve rod 40
in response to the variation of the suction pressure Ps such that a
control target or a set suction pressure for the suction pressure
Ps that is determined by the electromagnetic urging force of the
solenoid 60 is maintained.
[0140] Although the spring 85 of the second control valve CV2 is
provided by a coil spring in the above-described preferred
embodiments, the spring 85 includes a plate spring in a tenth
alternative embodiment.
[0141] In an eleventh alternative embodiment, the spring 85 in each
of the above-described preferred embodiments is removed from the
second control valve CV2. However, the provision of the spring 85
in the second control valve CV2 is desired because such spring
assists in smooth opening of the valve hole 27a and it is
preferable that the spring 85 is provided for stabilizing the
operation of the second control valve CV2.
[0142] In a twelfth alternative embodiment, the second bleed
passage 28 in the above-described first preferred embodiment is
removed. In a thirteenth alternative embodiment, clutch mechanism
such as an electromagnetic clutch is utilized as the power
transmission mechanism PT.
[0143] In a fourteenth alternative embodiment, the present
invention is applied to a wobble plate type variable displacement
compressor.
[0144] The present examples and embodiments are to be considered as
illustrative and not restrictive, and the invention is not to be
limited to the details given herein but may be modified within the
scope of the appended claims.
* * * * *