U.S. patent application number 14/946165 was filed with the patent office on 2016-06-02 for variable displacement type swash plate compressor.
This patent application is currently assigned to KABUSHIKI KAISHA TOYOTA JIDOSHOKKI. The applicant listed for this patent is KABUSHIKI KAISHA TOYOTA JIDOSHOKKI. Invention is credited to Kazunari HONDA, Kei NISHII, Takahiro SUZUKI, Shinya YAMAMOTO, Hideharu YAMASHITA.
Application Number | 20160153436 14/946165 |
Document ID | / |
Family ID | 55968416 |
Filed Date | 2016-06-02 |
United States Patent
Application |
20160153436 |
Kind Code |
A1 |
SUZUKI; Takahiro ; et
al. |
June 2, 2016 |
VARIABLE DISPLACEMENT TYPE SWASH PLATE COMPRESSOR
Abstract
A mobile body and a swash plate are coupled to each other via a
columnar coupling pin provided on an outer peripheral part of the
swash plate. An insertion hole through which the coupling pin is
passed is formed in the swash plate. The insertion hole has a guide
surface for guiding the coupling pin and for changing the
inclination angle of the swash plate following movement of a mobile
body to the axial direction of a rotation shaft. The guide surface
has a flat surface part which is inclined to a moving direction of
the mobile body. The flat surface part is set such that a
perpendicular line of the flat surface part and an axial line of
the rotation shaft cross in a region surrounded by a sliding part,
viewed from a direction orthogonal to both an axial direction of
the rotation shaft and a first direction.
Inventors: |
SUZUKI; Takahiro;
(Kariya-shi, JP) ; YAMAMOTO; Shinya; (Kariya-shi,
JP) ; YAMASHITA; Hideharu; (Kariya-shi, JP) ;
HONDA; Kazunari; (Kariya-shi, JP) ; NISHII; Kei;
(Kariya-shi, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
KABUSHIKI KAISHA TOYOTA JIDOSHOKKI |
Aichi-ken |
|
JP |
|
|
Assignee: |
KABUSHIKI KAISHA TOYOTA
JIDOSHOKKI
Aichi-ken
JP
|
Family ID: |
55968416 |
Appl. No.: |
14/946165 |
Filed: |
November 19, 2015 |
Current U.S.
Class: |
92/13 |
Current CPC
Class: |
F04B 2027/1813 20130101;
F04B 27/1804 20130101; F04B 2027/1831 20130101; F04B 27/18
20130101 |
International
Class: |
F04B 27/14 20060101
F04B027/14; F04B 27/08 20060101 F04B027/08 |
Foreign Application Data
Date |
Code |
Application Number |
Nov 27, 2014 |
JP |
2014-240293 |
Claims
1. A variable displacement type swash plate compressor comprising:
a housing in which there are formed a suction chamber, a discharge
chamber, a swash plate chamber communicated with the suction
chamber, and cylinder bores; a rotation shaft, which is
rotationally supported by the housing; a swash plate, which is
rotatable in the swash plate chamber by rotation of the rotation
shaft; a link mechanism, which is provided between the rotation
shaft and the swash plate and permits change of an inclination
angle of the swash plate to a first direction orthogonal to an
axial line of the rotation shaft; a piston, which is housed to
reciprocate in the cylinder bore; a converting mechanism, which
reciprocates, by rotation of the swash plate, the piston in the
cylinder bore by a stroke according to the inclination angle of the
swash plate; an actuator, which is located in the swash plate
chamber, changes the inclination angle of the swash plate; and a
control mechanism that controls the actuator, wherein the actuator
has a partitioning body, which is provided in the rotation shaft, a
mobile body, which can move along an axial line of the rotation
shaft in the swash plate chamber, a control pressure chamber, which
is partitioned by the partitioning body and the mobile body, moves
the mobile body by introducing a refrigerant from the discharge
chamber, and a coupling member, which is provided, between the
mobile body and the swash plate, on an outer side in a radial
direction from an insertion hole of the swash plate through which
the rotation shaft is passed, the mobile body has a sliding part
that slides on the rotation shaft or on the partitioning body
following movement along an axial line of the rotation shaft, the
swash plate has a guide surface for guiding the coupling member and
for changing the inclination angle of the swash plate following
movement of the mobile body along an axial line of the rotation
shaft, and the guide surface is set such that a perpendicular line
or a normal line of the guide surface and an axial line of the
rotation shaft cross in a region surrounded by the sliding part,
viewed from a direction orthogonal to both the axial line of the
rotation shaft and the first direction.
2. The variable displacement type swash plate compressor according
to claim 1, wherein the guide surface is set such that the
perpendicular line or the normal line of the guide surface and the
axial line of the rotation shaft cross in the region surrounded by
the sliding part, viewed from a direction orthogonal to both the
axial line of the rotation shaft and the first direction when the
inclination angle of the swash plate is a maximum inclination
angle.
3. The variable displacement type swash plate compressor according
to claim 1, wherein the guide surface is set such that the
perpendicular line or the normal line of the guide surface and the
axial line of the rotation shaft cross in the region surrounded by
the sliding part, viewed from a direction orthogonal to both the
axial line of the rotation shaft and the first direction when the
inclination angle of the swash plate is between a minimum
inclination angle and a maximum inclination angle.
4. The variable displacement type swash plate compressor according
to claim 1, wherein the guide surface is set such that the
perpendicular line or the normal line of the guide surface and the
axial line of the rotation shaft cross in the region surrounded by
the sliding part, viewed from a direction orthogonal to both the
axial line of the rotation shaft and the first direction when the
inclination angle of the swash plate is a minimum inclination
angle.
5. The variable displacement type swash plate compressor according
to claim 1, wherein the guide surface is set such that the
perpendicular line or the normal line of the guide surface and the
axial line of the rotation shaft cross in the region surrounded by
the sliding part, viewed from a direction orthogonal to both the
axial line of the rotation shaft and the first direction in a whole
range in which the inclination angle of the swash plate can be
changed.
6. The variable displacement type swash plate compressor according
to claim 1, wherein the guide surface comprises a flat surface
part, and the flat surface part is set such that the perpendicular
line of the guide surface and the axial line of the rotation shaft
cross in the region surrounded by the sliding part, viewed from the
direction orthogonal to both the axial line of the rotation shaft
and the first direction.
7. The variable displacement type swash plate compressor according
to claim 1, wherein the guide surface comprises a curved surface
part, and the curved surface part is set such that the normal line
of the guide surface and the axial line of the rotation shaft cross
in the region surrounded by the sliding part, viewed from the
direction orthogonal to both the axial line of the rotation shaft
and the first direction.
Description
BACKGROUND OF THE INVENTION
[0001] The present invention relates to a variable displacement
type swash plate compressor.
[0002] A compressor of this kind has been disclosed in Japanese
Laid-Open Patent Publication No. 52-131204. The compressor of this
kind has a swash plate and a mobile body that moves to an axial
direction of a rotation shaft for changing an inclination angle of
the swash plate. The compressor further has, in the housing, a
control pressure chamber into which a control gas is introduced.
The mobile body moves to the axial direction of the rotation shaft,
when the pressure inside the control pressure chamber is changed
following the introduction of the control gas. Following the
movement to the axial direction of the rotation shaft, the mobile
body transmits force to a center part of the swash plate to change
the inclination angle of the swash plate. As a result, the
inclination angle of the swash plate is changed.
[0003] The above configuration of transmitting force from the
mobile body to the center part of the swash plate requires large
force for changing the inclination angle of the swash plate. For
this purpose, it is considered appropriate to transmit force of
changing the inclination angle of the swash plate from the mobile
body to the outer peripheral part of the swash plate. According to
this configuration, the inclination angle of the swash plate can be
changed with smaller force than that for transmitting force from
the mobile body to the center part of the swash plate. Therefore, a
flow rate of the control gas introduced into the control pressure
chamber necessary to change the inclination angle of the swash
plate can be minimized.
[0004] However, according to the configuration of transmitting
force of changing the inclination angle of the swash plate from the
mobile body to the outer peripheral part of the swash plate, moment
works to incline the mobile body to a moving direction of the
mobile body following the change of the inclination angle of the
swash plate. When the mobile body is inclined, the mobile body and
the rotation shaft are brought into contact with each other at two
points on both sides sandwiching the rotation shaft. In this case,
force for supporting the inclination of the mobile body is
generated at contact points between the mobile body and the
rotation shaft and a twist occurs by frictional force generated by
this force. A sliding resistance increases by this twist, and the
mobile body becomes unable to move smoothly to an axial direction
of the rotation shaft. As a result, the inclination angle of the
swash plate becomes unable to be smoothly changed.
SUMMARY OF THE INVENTION
[0005] An object of the present invention is to provide a variable
displacement type swash plate compressor capable of smoothly
changing the inclination angle of the swash plate.
[0006] In order to solve the above problem, according to a first
aspect of the present invention, there is provided a variable
displacement type swash plate compressor including: a housing in
which there are formed a suction chamber, a discharge chamber, a
swash plate chamber communicated with the suction chamber, and
cylinder bores; a rotation shaft, which is rotatably supported by
the housing; a swash plate, which is rotatable in the swash plate
chamber by rotation of the rotation shaft; a link mechanism, which
is provided between the rotation shaft and the swash plate and
permits change of an inclination angle of the swash plate to a
first direction orthogonal to an axial line of the rotation shaft;
a piston, which is housed to reciprocate in the cylinder bore; a
converting mechanism, which reciprocates, by rotation of the swash
plate, the piston in the cylinder bore by stroke according to the
inclination angle of the swash plate; an actuator, which is located
in the swash plate chamber and changes the inclination angle of the
swash plate; and a control mechanism which controls the actuator.
The actuator has: a partitioning body which is provided in the
rotation shaft; a mobile body, which can move along an axial line
of the rotation shaft in the swash plate chamber; a control
pressure chamber, which is partitioned by the partitioning body and
the mobile body and moves the mobile body by introducing a
refrigerant from the discharge chamber; and a coupling member,
which is provided, between the mobile body and the swash plate, on
an outer side in a radial direction from an insertion hole of the
swash plate through which the rotation shaft is passed. The mobile
body has a sliding part that slides on the rotation shaft or on the
partitioning body following movement along an axial line of the
rotation shaft. The swash plate has a guide surface for guiding the
coupling member and for changing the inclination angle of the swash
plate following movement of the mobile body along an axial line of
the rotation shaft. The guide surface is set such that a
perpendicular line or a normal line of the guide surface and an
axial line of the rotation shaft cross in a region surrounded by
the sliding part, as viewed from a direction orthogonal to both the
axial line of the rotation shaft and the first direction.
BRIEF DESCRIPTION OF THE DRAWINGS
[0007] FIG. 1 is a side sectional view illustrating a variable
displacement type swash plate compressor according to the present
invention;
[0008] FIG. 2 is a schematic view illustrating a relationship
between a control pressure chamber, a pressure adjusting chamber, a
suction chamber, and a discharge chamber;
[0009] FIG. 3 is an enlarged side sectional view illustrating a
periphery of a coupling pin;
[0010] FIG. 4 is a side sectional view illustrating a compressor
when an inclination angle of a swash plate is a minimum inclination
angle;
[0011] FIG. 5 is an enlarged side sectional view illustrating a
periphery of a coupling pin according to another example;
[0012] FIG. 6 is an enlarged side sectional view illustrating a
periphery of a coupling pin according to still another example;
[0013] FIG. 7 is an enlarged side sectional view illustrating a
periphery of a coupling pin according to still another example;
[0014] FIG. 8 is an enlarged side sectional view illustrating a
periphery of a coupling pin according to still another example;
[0015] FIG. 9 is an enlarged side sectional view illustrating a
periphery of a coupling pin according to still another example;
and
[0016] FIG. 10 is an enlarged side sectional view illustrating a
periphery of a coupling pin according to still another example.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0017] Hereinafter, a preferred embodiment of a variable
displacement type swash plate compressor according to the present
invention will be described with reference to FIGS. 1 to 4. In the
following description, the variable displacement type swash plate
compressor will be simply referred to as a compressor. The
compressor is used for a vehicle air conditioner. Further, a left
side in FIG. 1 will be defined as a front side, and a right side
will be defined as a rear side.
[0018] As illustrated in FIG. 1, a housing 11 of a compressor 10 is
configured by a first cylinder block 12 and a second cylinder block
13, which are joined to each other, a front housing 14, which is
joined to a front end of the first cylinder block 12, and a rear
housing 15, which is joined to a rear end of the second cylinder
block 13.
[0019] A first valve/port forming body 16 is present between the
front housing 14 and the first cylinder block 12. A second
valve/port forming body 17 is present between the rear housing 15
and the second cylinder block 13.
[0020] A suction chamber 14a and a discharge chamber 14b are
partitioned between the front housing 14 and the first valve/port
forming body 16. The discharge chamber 14b is located on an outer
side in the radial direction of the suction chamber 14a. A suction
chamber 15a and a discharge chamber 15b are partitioned between the
rear housing 15 and the second valve/port forming body 17. A
pressure adjusting chamber 15c is formed in the rear housing 15.
The pressure adjusting chamber 15c is located at the center of the
rear housing 15. The suction chamber 15a is located on an outer
side in the radial direction of the pressure adjusting chamber 15c.
The discharge chamber 15b is located on an outer side in the radial
direction of the suction chamber 15a. The discharge chambers 14b
and 15b are connected to each other via a discharge passage not
illustrated. The discharge passage is connected to an external
refrigerant circuit not illustrated. The discharge chambers 14b and
15b are discharge pressure regions.
[0021] In the first valve/port forming body 16, there are formed a
suction port 16a, which communicates with the suction chamber 14a,
and a discharge port 16b, which communicates with the discharge
chamber 14b. In the second valve/port forming body 17, there are
formed a suction port 17a, which communicates with the suction
chamber 15a, and a discharge port 17b, which communicates with the
discharge chamber 15b. In each of the suction ports 16a and 17a, a
suction valve mechanism not illustrated is provided. In each of the
discharge ports 16b and 17b, a discharge valve mechanism not
illustrated is provided.
[0022] In the housing 11, a rotation shaft 21 having an axial line
L is rotatably supported. The rotation shaft 21 has a front end,
which is positioned near a front end of the housing 11, and a rear
end, which is positioned near a rear end of the housing 11. A front
end of the rotation shaft 21 is passed through a shaft hole 12h,
which is formed in the first cylinder block 12. The front end of
the rotation shaft 21 is located in the front housing 14. A rear
end of the rotation shaft 21 is passed through a shaft hole 13h
which is formed in the second cylinder block 13. The rear end of
the rotation shaft 21 is located in the pressure adjusting chamber
15c.
[0023] The front end of the rotation shaft 21 is rotatably
supported by the first cylinder block 12 via the shaft hole 12h,
and the rear end of the rotation shaft 21 is rotatably supported by
the second cylinder block 13 via the shaft hole 13h. A lip seal
type shaft seal device 22 is present between the front housing 14
and the rotation shaft 21. An engine for a vehicle as an external
driving source is coupled to the front end of the rotation shaft 21
for operation, via a power transmission mechanism not illustrated.
The power transmission mechanism is an all-time transmission type
clutchless mechanism configured by combination of a belt and a
pulley, for example.
[0024] In the housing 11, a swash plate chamber 24, which is
partitioned by the first cylinder block 12, and the second cylinder
block 13 are formed. In the swash plate chamber 24, a swash plate
23, which rotates by obtaining driving force from the rotation
shaft 21 and moves by inclination with respect to the rotation
shaft 21, is housed. In the swash plate 23, an insertion hole 23a,
through which the rotation shaft 21 is passed, is formed. The swash
plate 23 is fitted to the outer peripheral surface of the rotation
shaft 21 by passing the rotation shaft 21 through the insertion
hole 23a.
[0025] In the first cylinder block 12, a plurality of first
cylinder bores 12a are formed (only one first cylinder bore 12a is
illustrated in FIG. 1). The plurality of first cylinder bores 12a
penetrate through the first cylinder block 12 in the axial
direction, and are located around the rotation shaft 21. Each first
cylinder bore 12a communicates with the suction chamber 14a via the
suction port 16a and communicates with the discharge chamber 14b
via the discharge port 16b. In the second cylinder block 13, a
plurality of second cylinder bores 13a are formed (only one second
cylinder bore 13a is illustrated in FIG. 1). The plurality of
second cylinder bores 13a penetrate through the second cylinder
block 13 in the axial direction and are located around the rotation
shaft 21. Each second cylinder bore 13a communicates with the
suction chamber 15a via the suction port 17a and communicates with
the discharge chamber 15b via the discharge port 17b. The first
cylinder bore 12a and the second cylinder bore 13a are located at
the front and the back to form a pair. In both the first cylinder
bore 12a and the second cylinder bore 13a that form the pair, a
double-headed piston 25 is housed to reciprocate in forward and
backward directions. The compressor 10 is a double-headed piston
type swash plate compressor.
[0026] Each double-headed piston 25 is held at an outer peripheral
part of the swash plate 23 via a pair of shoes 26. When the swash
plate 23 rotates together with the rotation shaft 21, the rotation
of the swash plate 23 is converted into reciprocal linear motion of
the double-headed piston 25 via the shoes 26. Therefore, the pair
of shoes 26 is a conversion mechanism that reciprocates the
double-headed piston 25 by the rotation of the swash plate 23 in
the first cylinder bore 12a and the second cylinder bore 13a. A
space surrounded by the double-headed piston 25 in each first
cylinder bore 12a and the first valve/port forming body 16 is a
first compression chamber 20a. A space surrounded by the
double-headed piston 25 in each second cylinder bore 13a and the
second valve/port forming body 17 is a second compression chamber
20b.
[0027] In the first cylinder block 12, a first large-diameter hole
12b is formed. The first large-diameter hole 12b is continuous to
the shaft hole 12h and has an inner diameter larger than that of
the shaft hole 12h. The first large-diameter hole 12b communicates
with the swash plate chamber 24. The swash plate chamber 24 and the
suction chamber 14a communicate with each other by a suction
passage 12c that penetrates through the first cylinder block 12 and
the first valve/port forming body 16.
[0028] In the second cylinder block 13, a second large-diameter
hole 13b is formed. The second large-diameter hole 13b is
continuous to the shaft hole 13h and has an inner diameter larger
than that of the shaft hole 13h. The second large-diameter hole 13b
communicates with the swash plate chamber 24. The swash plate
chamber 24 and the suction chamber 15a communicate with each other
by a suction passage 13c that penetrates through the second
cylinder block 13 and the second valve/port forming body 17.
[0029] On the peripheral wall of the second cylinder block 13, a
suction opening 13s is formed. The suction opening 13s is connected
to the external refrigerant circuit. A refrigerant gas is suctioned
into the swash plate chamber 24 from the external refrigerant
circuit via the suction opening 13s and is then suctioned into the
suction chambers 14a and 15a via the suction passages 12c and 13c.
Accordingly, the suction chambers 14a and 15a and the swash plate
chamber 24 are suction pressure regions, and their pressures are
substantially equal.
[0030] From the outer peripheral surface of the rotation shaft 21,
a ring-shaped flange part 21f protrudes. The flange part 21f is
located in the first large-diameter hole 12b. A first thrust
bearing 27a is provided between the flange part 21f of the rotation
shaft 21 and the first cylinder block 12. A circular cylindrical
supporting member 39 is press-fitted to the rear end of the
rotation shaft 21. A ring-shaped flange part 39f protrudes from the
outer peripheral surface of the supporting member 39. The flange
part 39f is located in the second large-diameter hole 13b. A second
thrust bearing 27b is provided between the flange part 39f of the
supporting member 39 and the second cylinder block 13.
[0031] In the swash plate chamber 24, an actuator 30 capable of
changing the inclination angle of the swash plate 23 is housed. The
actuator 30 changes the inclination angle of the swash plate 23 to
a first direction (a vertical direction in FIG. 1) orthogonal to
the axial line L of the rotation shaft 21. The actuator 30 is
provided between the flange part 21f of the rotation shaft 21 and
the swash plate 23. The actuator 30 has a ring-shaped partitioning
body 31 that can rotate integrally with the rotation shaft 21.
Further, the actuator 30 has a bottomed circular-cylindrical mobile
body 32. The mobile body 32 is located between the flange part 21f
and the partitioning body 31. The mobile body 32 is movable to the
axial direction of the rotation shaft 21 in the swash plate chamber
24.
[0032] The mobile body 32 is formed by a circular ring-shaped
bottom part 32a and a circular cylinder part 32b. The bottom part
32a has a through-hole 32e through which the rotation shaft 21
passes. The circular cylinder part 32b extends from an outer
peripheral edge of the bottom part 32a to the axial direction of
the rotation shaft 21. The inner peripheral surface of the circular
cylinder part 32b can move by sliding to an outer peripheral edge
of the partitioning body 31. Accordingly, the mobile body 32 is
integrally rotatable with the rotation shaft 21 via the
partitioning body 31. A portion between the inner peripheral
surface of the circular cylinder part 32b and the outer peripheral
edge of the partitioning body 31 is sealed by a seal member 33. A
portion between the inner peripheral surface of the through-hole
32e and the outer peripheral surface of the rotation shaft 21 is
sealed by a seal member 34. The actuator 30 has a control pressure
chamber 35, which is partitioned by the partitioning body 31, and
the mobile body 32.
[0033] In the rotation shaft 21, a first shaft inner passage 21a
extending along the axial direction of the rotation shaft 21 is
formed. A rear end of the first shaft inner passage 21a is opened
to the pressure adjusting chamber 15c. Further, in the rotation
shaft 21, a second shaft inner passage 21b extending to a radial
direction of the rotation shaft 21 is formed. The second shaft
inner passage 21b has one end part, which communicates with a front
end of the first shaft inner passage 21a, and the other end part,
which is opened to the control pressure chamber 35. Accordingly,
the control pressure chamber 35 and the pressure adjusting chamber
15c communicate with each other via the first shaft inner passage
21a and the second shaft inner passage 21b.
[0034] As illustrated in FIG. 2, the pressure adjusting chamber 15c
and the suction chamber 15a communicate with each other via a bleed
passage 36. The bleed passage 36 is provided with an orifice 36a. A
flow rate of the refrigerant gas that flows in the bleed passage 36
is squeezed by the orifice 36a. Further, the pressure adjusting
chamber 15c and the discharge chamber 15b communicate with each
other via a supply passage 37. On the supply passage 37, there is
provided an electromagnetic control valve 37s as a control
mechanism that controls the actuator 30. The control valve 37s
adjusts the opening of the supply passage 37 based on the pressure
of the suction chamber 15a. The control valve 37s adjusts a flow
rate of the refrigerant gas that flows in the supply passage
37.
[0035] From the discharge chamber 15b, the refrigerant gas is
introduced into the control pressure chamber 35 via the supply
passage 37, the pressure adjusting chamber 15c, the first shaft
inner passage 21a, and the second shaft inner passage 21b. Further,
from the control pressure chamber 35, the refrigerant gas is
discharged to the suction chamber 15a via the second shaft inner
passage 21b, the first shaft inner passage 21a, the pressure
adjusting chamber 15c, and the bleed passage 36. The pressure
inside the control pressure chamber 35 is changed by these items.
By the pressure difference between the control pressure chamber 35
and the swash plate chamber 24, the mobile body 32 moves to the
partitioning body 31 in the axial direction of the rotation shaft
21. Accordingly, the refrigerant gas that is introduced into the
control pressure chamber 35 is the control gas used for movement
control of the mobile body 32.
[0036] As illustrated in FIG. 1, in the swash plate chamber 24, a
lug arm 40 is located between the swash plate 23 and the flange
part 39f. The lug arm 40 is a link mechanism that permits change of
the inclination angle of the swash plate 23. The lug arm 40 is bent
in approximately an L shape from an upper end toward a lower end. A
weight part 40w is formed on the upper end of the lug arm 40. The
weight part 40w protrudes to the front of the swash plate 23 by
passing through a groove part 23b of the swash plate 23.
[0037] The upper end of the lug arm 40 is coupled to the upper end
of the swash plate 23 by a columnar first pin 41, which is located
to cross the inside of the groove part 23b. Accordingly, the upper
end of the lug arm 40 is supported on the swash plate 23 to be able
to oscillate around a first oscillation center M1 that matches the
axis center of the first pin 41. The lower end of the lug arm 40 is
coupled to the supporting member 39 by a columnar second pin 42.
Accordingly, the lower end of the lug arm 40 is supported on the
supporting member 39 to be able to oscillate around a second
oscillation center M2 that matches the axis center of the second
pin 42.
[0038] From a front end of the circular cylinder part 32b of the
mobile body 32, a coupling part 32c protrudes toward the swash
plate 23. A columnar coupling pin 43 as a coupling member is
press-fitted and fixed to the coupling part 32c. Further, a
long-hole shaped insertion hole 23h through which the coupling pin
43 can be passed is formed in the swash plate 23. The insertion
hole 23h is formed on an outer side in the radial direction from
the insertion hole 23a of the swash plate 23 (a lower side in FIG.
1). The coupling part 32c is coupled to a lower end of the swash
plate 23 via the coupling pin 43. The coupling pin 43 is held on
the swash plate 23 so as to be able to move by sliding in the
insertion hole 23h.
[0039] As illustrated in FIG. 3, the insertion hole 23h has a guide
surface 44 for guiding the coupling pin 43 and for changing the
inclination angle of the swash plate 23 following movement of the
mobile body 32 to the axial direction of the rotation shaft 21. The
guide surface 44 is located near the mobile body 32 in the
insertion hole 23h. The guide surface 44 has a flat surface part
44a that is inclined to the moving direction of the mobile body 32
(the axial direction of the rotation shaft 21).
[0040] The mobile body 32 has a sliding part 32s that slides on the
rotation shaft 21 following the movement of the mobile body 32 to
the axial direction of the rotation shaft 21. The sliding part 32s
is an inner peripheral surface of the through-hole 32e of the
bottom part 32a and extends along the axial direction of the
rotation shaft 21.
[0041] In this case, following the change of the inclination angle
of the swash plate 23, a point at which a perpendicular line L1 of
the flat surface part 44a and the axial line L of the rotation
shaft 21 cross is set as an intersection P1, viewed from a
direction orthogonal to both an axial direction of the rotation
shaft 21 and the first direction (a vertical direction), that is, a
depth direction on the paper surface in FIG. 3. An inclination
angle .theta.1 of the flat surface part 44a is set such that, when
the inclination angle of the swash plate 23 is a maximum
inclination angle, the intersection P1 is located in a region Z1
surrounded by the sliding part 32s, viewed from the direction
orthogonal to both the axial direction of the rotation shaft 21 and
the first direction.
[0042] The inclination angle .theta.1 is the inclination when the
inclination angle of the swash plate 23 is a maximum inclination
angle and is the inclination of the swash plate 23 with respect to
a direction orthogonal to the axial direction of the rotation shaft
21. The region Z1 is a region in which the sliding part 32s extends
in the axial direction of the rotation shaft 21 and is indicated by
dot hatching in FIG. 3.
[0043] In the compressor 10, when the opening of the control valve
37s is reduced, the flow rate of the refrigerant gas, which is
introduced from the discharge chamber 15b into the control pressure
chamber 35 via the supply passage 37, the pressure adjusting
chamber 15c, the first shaft inner passage 21a, and the second
shaft inner passage 21b becomes small. Then, when the refrigerant
gas is discharged from the control pressure chamber 35 to the
suction chamber 15a via the second shaft inner passage 21b, the
first shaft inner passage 21a, the pressure adjusting chamber 15c,
and the bleed passage 36, the pressure in the control pressure
chamber 35 becomes substantially equal to the pressure in the
suction chamber 15a. Accordingly, when the pressure difference
between the control pressure chamber 35 and the swash plate chamber
24 becomes small, the swash plate 23 pulls the mobile body 32 via
the coupling pin 43 by the compression reactive force from the
double-headed piston 25 that operates on the swash plate 23, and
the mobile body 32 moves to make the bottom part 32a approach the
partitioning body 31.
[0044] As illustrated in FIG. 4, when the mobile body 32 moves to
make the bottom part 32a approach the partitioning body 31, the
coupling pin 43 moves by sliding on the inner side of the insertion
hole 23h, and the swash plate 23 oscillates around the first
oscillation center M1. Then, the lug arm 40 approaches the flange
part 39f while oscillating around the second oscillation center M2,
following the oscillation of the swash plate 23 around the first
oscillation center M1. Accordingly, the inclination angle of the
swash plate 23 becomes small, and the stroke of the double-headed
piston 25 becomes small so that the discharge volume decreases.
[0045] When the opening of the control valve 37s is increased, the
flow rate of the refrigerant gas, which is introduced from the
discharge chamber 15b into the control pressure chamber 35 via the
supply passage 37, the pressure adjusting chamber 15c, the first
shaft inner passage 21a, and the second shaft inner passage 21b
becomes large. Therefore, the pressure in the control pressure
chamber 35 becomes substantially equal to the pressure in the
discharge chamber 15b. Accordingly, when the pressure difference
between the control pressure chamber 35 and the swash plate chamber
24 becomes large, the mobile body 32 moves to separate the bottom
part 32a from the partitioning body 31, while pulling the swash
plate 23 via the coupling pin 43.
[0046] As illustrated in FIG. 1, when the mobile body 32 moves to
separate the bottom part 32a from the partitioning body 31, the
coupling pin 43 moves by sliding on the inner side of the insertion
hole 23h, and the swash plate 23 oscillates around the first
oscillation center M1 in an opposite direction to that when the
inclination angle of the swash plate 23 reduces. Then, following
the oscillation of the swash plate 23 around the first oscillation
center M1, the lug arm 40 oscillates around the second oscillation
center M2 in an opposite direction to that when the inclination
angle of the swash plate 23 reduces. Accordingly, the inclination
angle of the swash plate 23 becomes large, and the stroke of the
double-headed piston 25 becomes large so that the discharge volume
increases.
[0047] Next, the operation of the compressor 10 will be described
with reference to FIG. 3.
[0048] As illustrated in FIG. 3, following the change of the
inclination angle of the swash plate 23, force F0 works from the
coupling pin 43 to the swash plate 23, on the perpendicular line L1
of the flat surface part 44a. On the other hand, force F1 as
reactive force of the force F0 works from the coupling pin 43 to
the mobile body 32, along the perpendicular line L1. In this case,
the intersection P1 at which the perpendicular line L1 of the flat
surface part 44a and the axial line L of the rotation shaft 21
cross following the change of the inclination angle of the swash
plate 23 is located, in the axial direction of the rotation shaft
21, in the region Z1 surrounded by the sliding part 32s as a
sliding portion of the rotation shaft 21 and the mobile body 32. At
this time, resultant force F3 of the force F1 that works from the
coupling pin 43 to the mobile body 32 and the force F2 that moves
the mobile body 32 to the axial direction of the rotation shaft 21
by the pressure of the control pressure chamber 35 is generated on
a perpendicular line L2 including the intersection P1. Force F4 in
the opposite direction that balances with the resultant force F3 is
also generated on the perpendicular line L2. As a result, all the
forces applied to the mobile body 32 are balanced on the
perpendicular line L2 including the intersection P1. Therefore, on
the mobile body 32, there occurs no moment that inclines the mobile
body 32 to a moving direction. Accordingly, the inclination angle
of the swash plate 23 can be smoothly changed.
[0049] The inclination .theta.1 of the flat surface part 44a is set
such that, when the inclination angle of the swash plate 23 is a
maximum inclination angle, the intersection P1 is located in the
region Z1 surrounded by the sliding part 32s. Therefore, there
occurs no moment that inclines the mobile body 32 to a moving
direction when the inclination angle is the maximum inclination
angle at which driving force that is generated in the mobile body
32 becomes maximum. As a result, the inclination angle of the swash
plate 23 can be easily changed to the maximum inclination angle and
can be smoothly reduced from the maximum inclination angle.
[0050] Therefore, in the above embodiment, the following effects
can be obtained.
[0051] (1) The flat surface part 44a is set such that, viewed from
the direction orthogonal to both the axial direction of the
rotation shaft 21 and the first direction, the intersection of the
perpendicular line L1 of the flat surface part 44a with the axial
line L of the rotation shaft 21 is located in the region Z1
surrounded by the sliding part 32s. Following the change of the
inclination angle of the swash plate 23, the force F0 works from
the coupling pin 43 to the swash plate 23, on the perpendicular
line L1 of the flat surface part 44a. On the other hand, the force
F1 as reactive force of the force F0 works from the coupling pin 43
to the mobile body 32, along the perpendicular line L1. In this
case, the intersection P1 of the perpendicular line L1 of the flat
surface part 44a (the force F1 that works from the coupling pin 43
to the mobile body 32) with the axial line L of the rotation shaft
21 following the change of the inclination angle of the swash plate
23 is located, in the axial direction of the rotation shaft 21, in
the region Z1 surrounded by the sliding part 32s as a sliding
portion of the rotation shaft 21 and the mobile body 32. At this
time, the resultant force F3 of the force F1 that works from the
coupling pin 43 to the mobile body 32 and the force F2 that moves
the mobile body 32 to the axial direction of the rotation shaft 21
by the pressure of the control pressure chamber 35 is generated on
the perpendicular line L2 including the intersection P1. The force
F4 in the opposite direction that balances with the resultant force
F3 is also generated on the perpendicular line L2. As a result, all
the forces applied to the mobile body 32 are balanced on the
perpendicular line L2 including the intersection P1.
[0052] Therefore, on the mobile body 32, there occurs no moment
that inclines the mobile body 32 to a moving direction.
Accordingly, the inclination angle of the swash plate 23 can be
smoothly changed.
[0053] (2) The inclination angle .theta.1 of the flat surface part
44a is set such that, when the inclination angle of the swash plate
23 is a maximum inclination angle, the intersection P1 is located
in the region Z1 surrounded by the sliding part 32s. According to
this, there occurs no moment that inclines the mobile body 32 to a
moving direction when the inclination angle is the maximum
inclination angle at which driving force that is generated in the
mobile body 32 becomes maximum. As a result, the inclination angle
of the swash plate 23 can be easily changed to the maximum
inclination angle and can be smoothly reduced from the maximum
inclination angle.
[0054] (3) The guide surface 44 has the flat surface part 44a that
is inclined to the moving direction of the mobile body 32.
According to this, the shape of the guide surface 44 can be
simplified. That is, because the moment that inclines the mobile
body 32 to a moving direction is suppressed, the shape of the guide
surface 44 is not complicated. Accordingly, productivity
improves.
[0055] (4) According to the double-headed piston type swash plate
compressor using the double-headed piston 25, the swash plate
chamber 24 cannot be made to function as a control chamber for
changing the inclination angle of the swash plate 23, unlike the
variable displacement type swash plate compressor having a
single-headed piston. Therefore, in the present embodiment, the
inclination angle of the swash plate 23 is changed by changing the
pressure of the control pressure chamber 35 that is partitioned by
the mobile body 32. The control pressure chamber 35 is a space
smaller than the swash plate chamber 24. Therefore, the volume of
the refrigerant gas introduced into the control pressure chamber 35
can be small, so that responsiveness when changing the inclination
angle of the swash plate 23 is satisfactory. Further, because the
inclination angle of the swash plate 23 can be smoothly changed,
the volume of the refrigerant gas introduced into the control
pressure chamber 35 can be suppressed to the minimum necessary.
[0056] The above embodiment may be changed as follows.
[0057] As illustrated in FIG. 5, the flat surface part 44a may be
set such that, when the inclination angle of the swash plate 23 is
between a minimum inclination angle and a maximum inclination
angle, the intersection P1 is located in the region Z1 surrounded
by the sliding part 32s. In this case, the inclination .theta.1 of
the flat surface part 44a is set such that the intersection P1 is
located in the region Z1, viewed from the direction orthogonal to
both the axial direction of the rotation shaft 21 and the first
direction, that is, a depth direction on the paper surface in FIG.
5. The inclination .theta.1 is the inclination to the direction
orthogonal to the axial line L of the rotation shaft 21 when the
inclination angle of the swash plate 23 is between the minimum
inclination angle and the maximum inclination angle. According to
this, the mobile body 32 can be smoothly moved between the minimum
inclination angle and the maximum inclination angle in which use
frequency is the highest. Accordingly, control of the flow rate of
the refrigerant gas introduced into the control pressure chamber 35
can be simplified.
[0058] As illustrated in FIG. 6, the flat surface part 44a may be
set such that, when the inclination angle of the swash plate 23 is
a minimum inclination angle, the intersection P1 is located in the
region Z1 surrounded by the sliding part 32s. In this case, the
inclination .theta.1 of the flat surface part 44a is set such that
the intersection P1 is located in the region Z1 surrounded by the
sliding part 32s, viewed from the direction orthogonal to both the
axial line L of the rotation shaft 21 and the first direction, that
is, a depth direction on the paper surface in FIG. 6. The
inclination .theta.1 is the inclination to the direction orthogonal
to the axial line L of the rotation shaft 21 when the inclination
angle of the swash plate 23 is the minimum inclination angle.
According to this, there occurs no moment that inclines the mobile
body 32 to a moving direction when the inclination angle of the
swash plate 23 is the minimum inclination angle. Therefore, the
inclination angle of the swash plate 23 can be smoothly increased,
also at the starting time of the compressor 10.
[0059] As illustrated in FIG. 7, the guide surface 44 may have a
curved surface part 44b. The curved surface part 44b is formed in
an arc shape that passes on a virtual circle R1. Following the
change of the inclination angle of the swash plate 23, the force F0
works from the coupling pin 43 to the swash plate 23, on a normal
line L3 of the curved surface part 44b. On the other hand, the
force F1 as reactive force of the force F0 that works from the
coupling pin 43 to the swash plate 23 works from the coupling pin
43 to the mobile body 32 along the normal line L3. In this case, an
intersection P2 of the normal line L3 of the curved surface part
44a (the force F1 that works from the coupling pin 43 to the mobile
body 32) with the axial line L of the rotation shaft 21 following
the change of the inclination angle of the swash plate 23 is
located in the region Z1 surrounded by the sliding part 32s.
According to this, even when the inclination angle of the swash
plate 23 is changed, when the coupling pin 43 is being guided by
the curved surface part 44b, the intersection P2 is not easily
located outward from the region Z1 surrounded by the sliding part
32s of the rotation shaft 21 and the mobile body 32. As a result,
even when the inclination angle of the swash plate 23 is changed,
the moment that inclines the mobile body 32 to the moving direction
can be easily suppressed, and the inclination angle of the swash
plate 23 can be smoothly changed.
[0060] As illustrated in FIG. 8, the flat surface part 44a may be
set such that, when the inclination angle of the swash plate 23 is
a minimum inclination angle, the intersection P1 is located in a
region Z2 surrounded by a sliding part 32S that slides on the
partitioning body 31, following the movement of the mobile body 32
to the axial direction of the rotation shaft 21. In this case, the
inclination .theta.1 of the flat surface part 44a is set such that
the intersection P1 is located in the region Z2, viewed from the
direction orthogonal to both the axial line L of the rotation shaft
21 and the first direction, that is, a depth direction on the paper
surface in FIG. 8. The inclination .theta.1 is the inclination to
the direction orthogonal to the axial line L of the rotation shaft
21 when the inclination angle of the swash plate 23 is the minimum
inclination angle. Further, the inclination .theta.1 of the flat
surface part 44a may be set such that, when the inclination angle
of the swash plate 23 is a maximum inclination angle, the
intersection P1 is located in the region Z2 surrounded by the
sliding part 32S that slides on the partitioning body 31, following
the movement of the mobile body 32 to the axial direction of the
rotation shaft 21. Further, the inclination .theta.1 of the flat
surface part 44a may be set such that, when the inclination angle
of the swash plate 23 is between the minimum inclination angle and
the maximum inclination angle, the intersection P1 is located in
the region Z2 surrounded by the sliding part 32S that slides on the
partitioning body 31, following the movement of the mobile body 32
to the axial direction of the rotation shaft 21.
[0061] As illustrated in FIGS. 9 and 10, the guide surface 44 may
have a cam surface, which is a combination of the flat surface part
44a and the curved surface part 44b. For example, as illustrated in
FIG. 9, when the inclination angle of the swash plate 23 increases
to become a maximum inclination angle, the coupling pin 43 is
guided by the curved surface part 44b, and as illustrated in FIG.
10, when the inclination angle of the swash plate 23 reduces to
become a minimum inclination angle, the coupling pin 43 is guided
by the flat surface part 44a. In this case, the inclination
.theta.1 of the flat surface part 44a is set such that, when the
inclination angle of the swash plate 23 is the minimum inclination
angle, the intersection P1 is located in the region Z1 surrounded
by the sliding part 32s, viewed from the direction orthogonal to
both the axial line L of the rotation shaft 21 and the first
direction, that is, a depth direction on the paper surface in FIG.
10. The inclination .theta.1 is the inclination to the direction
orthogonal to the axial line L of the rotation shaft 21 when the
inclination angle of the swash plate 23 is the minimum inclination
angle. According to this, there occurs no moment that inclines the
mobile body 32 to a moving direction, in a whole range in which the
inclination angle of the swash plate 23 can be changed.
Accordingly, the inclination angle of the swash plate 23 can be
smoothly reduced.
[0062] In the swash plate 23, a groove through which the coupling
pin 43 can be passed may be formed in place of the insertion hole
23h.
[0063] The coupling pin 43 may be fixed to the coupling part 32c by
using a screw.
[0064] The coupling pin 43 may not be fixed to the coupling part
32c. For example, the coupling pin 43 may be slidably held in an
insertion hole of the coupling part 32c by inserting the coupling
pin 43 into the insertion hole.
[0065] By providing an orifice in the supply passage 37, which
communicates the pressure adjusting chamber 15c with the discharge
chamber 15b, the electromagnetic control valve 37s may be provided
on the bleed passage 36, which communicates the pressure adjusting
chamber 15c with the suction chamber 15a.
[0066] The compressor 10 may be a single-headed piston type swash
plate compressor, which uses a single-headed piston.
[0067] The compressor 10 may obtain driving force from an external
driving source via a clutch.
* * * * *