U.S. patent application number 14/780710 was filed with the patent office on 2016-03-10 for variable displacement swash plate type 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, Hiromichi OGAWA, Masaki OTA, Takahiro SUZUKI, Shinya YAMAMOTO, Hideharu YAMASHITA, Yusuke YAMAZAKI.
Application Number | 20160069334 14/780710 |
Document ID | / |
Family ID | 51624177 |
Filed Date | 2016-03-10 |
United States Patent
Application |
20160069334 |
Kind Code |
A1 |
SUZUKI; Takahiro ; et
al. |
March 10, 2016 |
VARIABLE DISPLACEMENT SWASH PLATE TYPE COMPRESSOR
Abstract
Provided is a compressor, in which the inclination angle of a
swash plate is changed by an actuator, ensuring stability on a
product-by-product basis while realizing reduction in size. In the
compressor, when pressure in a control pressure chamber increases,
a movable body moves toward a flange. At this time, the movable
body pulls the opposite end side of a swash plate rearward in a
swash plate chamber via first and second pulling arms. A link
mechanism permits increase of the inclination angle of the swash
plate until reaching a maximum value. When the pressure in the
control pressure chamber reaches a required control pressure, a
rear wall of the movable body which has moved rearward in the swash
plate chamber abuts a front face of the flange. This makes it
possible in this compressor to restrict the maximum value of the
inclination angle of the swash plate.
Inventors: |
SUZUKI; Takahiro;
(Kariya-shi, JP) ; YAMAMOTO; Shinya; (Kariya-shi,
JP) ; HONDA; Kazunari; (Kariya-shi, JP) ;
OGAWA; Hiromichi; (Kariya-shi, JP) ; YAMASHITA;
Hideharu; (Kariya-shi, JP) ; OTA; Masaki;
(Kariya-shi, JP) ; NISHII; Kei; (Kariya-shi,
JP) ; YAMAZAKI; Yusuke; (Kariya-shi, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
KABUSHIKI KAISHA TOYOTA JIDOSHOKKI |
Aichi |
|
JP |
|
|
Assignee: |
KABUSHIKI KAISHA TOYOTA
JIDOSHOKKI
Aichi
JP
KABUSHIKI KAISHA TOYOTA JIDOSHOKKI
Aichi
JP
|
Family ID: |
51624177 |
Appl. No.: |
14/780710 |
Filed: |
March 25, 2014 |
PCT Filed: |
March 25, 2014 |
PCT NO: |
PCT/JP2014/058297 |
371 Date: |
September 28, 2015 |
Current U.S.
Class: |
417/218 |
Current CPC
Class: |
F04B 2027/1813 20130101;
F04B 27/1045 20130101; F04B 2027/1827 20130101; F04B 27/18
20130101; F04B 2027/1895 20130101; F04B 27/1804 20130101; F04B
27/1054 20130101; F04B 2027/1831 20130101; F04B 27/1081 20130101;
F04B 53/14 20130101 |
International
Class: |
F04B 27/18 20060101
F04B027/18; F04B 53/14 20060101 F04B053/14; F04B 27/10 20060101
F04B027/10 |
Foreign Application Data
Date |
Code |
Application Number |
Mar 29, 2013 |
JP |
2013-070750 |
Jun 20, 2013 |
JP |
2013-129901 |
Feb 25, 2014 |
JP |
2014-033591 |
Claims
1. A variable displacement swash plate type compressor comprising:
a housing in which a suction chamber, a discharge chamber, a swash
plate chamber, and a cylinder bore are formed; a drive shaft
extending along a drive axis and rotatably supported in the
housing; a swash plate rotatable in the swash plate chamber along
with rotation of the drive shaft; a link mechanism that is provided
between the drive shaft and the swash plate and permits change of
an inclination angle of the swash plate in a direction
perpendicular to the drive axis of the drive shaft; a piston
reciprocally accommodated in the cylinder bore; a conversion
mechanism that reciprocates the piston in the cylinder bore along
with rotation of the swash plate at a stroke corresponding to the
inclination angle; an actuator capable of changing the inclination
angle; and a control mechanism that controls the actuator, wherein
the suction chamber and the swash plate chamber communicate with
each other, the actuator includes a partition body provided on the
drive shaft, a movable body that is movable along the drive axis of
the drive shaft in the swash plate chamber and provided with a
coupling portion to be coupled to the swash plate, and a control
pressure chamber that is defined by the partition body and the
movable body and moves the movable body by introducing a
refrigerant from the discharge chamber, and a maximum inclination
restriction member that rotates synchronously with the drive shaft
and restricts a maximum value of the inclination angle by abutting
the movable body is provided on the drive shaft.
2. The variable displacement swash plate type compressor according
to claim 1, wherein: the drive shaft includes a drive shaft body
and a cap that is press-fitted to the drive shaft body and located
in the swash plate chamber; and the cap is the maximum inclination
restriction member.
3. The variable displacement swash plate type compressor according
to claim 1, wherein: the compressor further comprises a circlip
that is fitted to the drive shaft and located in the swash plate
chamber; and the circlip is the maximum inclination restriction
member.
Description
TECHNICAL FIELD
[0001] The present invention relates to a variable displacement
swash plate type compressor.
BACKGROUND ART
[0002] A conventional variable displacement swash plate type
compressor (hereinafter referred to as a compressor) is disclosed
in Patent Literature 1. This compressor includes a suction chamber,
a discharge chamber, a swash plate chamber, and plural cylinder
bores, which are formed in a housing. A drive shaft is rotatably
supported in the housing. The swash plate chamber accommodates a
swash plate, which is rotatable along with rotation of the drive
shaft. A link mechanism is provided between the drive shaft and
swash plate. The link mechanism permits change of the inclination
angle of the swash plate. The inclination angle is defined as an
angle of the swash plate with respect to a direction perpendicular
to the drive axis of the drive shaft. A piston is reciprocally
accommodated in each of the cylinder bores. A pair of shoes
provided for each piston serves as a conversion mechanism and
reciprocates the piston in each of the cylinder bores along with
rotation of the swash plate at a stroke corresponding to the
inclination angle. An actuator is capable of changing the
inclination angle by changing the volume of a control pressure
chamber. The actuator is controlled by a control mechanism.
[0003] In this compressor, the control mechanism raises the
pressure in the control pressure chamber by using the pressure of
refrigerant in the discharge chamber and thereby increases the
inclination angle of the swash plate via the link mechanism. At
this time, when the link mechanism is pushed by the swash plate due
to the pressure in the control pressure chamber and when the length
of the link mechanism in an axial direction of the drive shaft is
minimized, the inclination angle cannot be increased any further.
In other words, in this compressor, the maximum inclination angle
is restricted by pushing the link mechanism by the swash plate. In
this way, in this compressor, discharge capacity per rotation of
the drive shaft can be increased to the maximum.
CITATION LIST
Patent Literature
[0004] Patent Literature 1: Japanese Patent Laid-Open No.
5-172052
SUMMARY OF INVENTION
Technical Problem
[0005] In a compressor in which the inclination angle of the swash
plate is changed by an actuator as described above, a required
control pressure, which is the pressure in the control pressure
chamber required to increase the inclination angle of the swash
plate to the maximum value, is preset. If the compressor is
configured such that a discharge refrigerant pressure, i.e. the
pressure of refrigerant in the discharge chamber, is introduced to
the control pressure chamber, the required control pressure is set
lower than an upper limit of the discharge refrigerant
pressure.
[0006] In the conventional compressor described above, since the
maximum value of the inclination angle is restricted by pushing the
link mechanism by the swash plate, a pressure in excess of the
required control pressure is applied to the swash plate and the
link mechanism. This makes it necessary to secure strength of the
swash plate and the link mechanism of the compressor sufficiently
to endure this pressure, and, as a result, it is inevitable to
increase the size of the swash plate chamber and thus the size of
the compressor.
[0007] Furthermore, in the conventional compressor described above,
since the maximum value of the inclination angle is restricted by
the link mechanism, which is formed by assembling plural parts in
the axial direction of the drive shaft, dispersion in the maximum
value of the inclination angle is likely to occur due to
dimensional tolerance and the like of the swash plate and the link
mechanism in the axial direction of the drive shaft. Thus, it is
difficult to maintain the quality of each individual
compressor.
[0008] The present invention has been made in view of the
conventional circumstances described above, and an object of the
invention is to provide a compressor, in which the inclination
angle of a swash plate is changed by an actuator, ensuring
excellent quality stability on a product-by-product basis while
realizing reduction in size.
Solution to Problem
[0009] A variable displacement swash plate type compressor
according to the present invention comprises: a housing in which a
suction chamber, a discharge chamber, a swash plate chamber, and a
cylinder bore are formed; a drive shaft extending along a drive
axis and rotatably supported in the housing; a swash plate
rotatable in the swash plate chamber along with rotation of the
drive shaft; a link mechanism that is provided between the drive
shaft and the swash plate and permits change of an inclination
angle of the swash plate in a direction perpendicular to the drive
axis of the drive shaft; a piston reciprocally accommodated in the
cylinder bore; a conversion mechanism that reciprocates the piston
in the cylinder bore along with rotation of the swash plate at a
stroke corresponding to the inclination angle; an actuator capable
of changing the inclination angle; and a control mechanism that
controls the actuator,
[0010] wherein the suction chamber and the swash plate chamber
communicate with each other,
[0011] the actuator includes a partition body provided on the drive
shaft, a movable body that is movable along the drive axis of the
drive shaft in the swash plate chamber and provided with a coupling
portion to be coupled to the swash plate, and a control pressure
chamber that is defined by the partition body and the movable body
and moves the movable body by introducing a refrigerant from the
discharge chamber, and
[0012] a maximum inclination restriction member that rotates
synchronously with the drive shaft and restricts a maximum value of
the inclination angle by abutting the movable body is provided on
the drive shaft.
[0013] In the compressor according to the present invention, the
required control pressure is also set lower than the upper limit of
the discharge refrigerant pressure. In this compressor, the movable
body of the actuator moves when the refrigerant is introduced into
the control pressure chamber from the discharge chamber. Thereby,
the inclination angle of the swash plate changes in this
compressor. In the compressor, the maximum value of the inclination
angle of the swash plate is restricted as the movable body abuts
the maximum inclination restriction member. That is, in this
compressor, although the movable body and the swash plate are
coupled to each other via the coupling portion, the swash plate
does not push the link mechanism using the pressure in the control
pressure chamber in order to restrict the maximum value of the
inclination angle. Consequently, in this compressor, pressure in
excess of the required control pressure does not act on the swash
plate and the link mechanism, and therefore, it is not necessary to
ensure the strength of the swash plate and the link mechanism more
than required. Thus, the compressor eliminates the need to upsize
the swash plate chamber.
[0014] Also, in the compressor, the maximum value of the
inclination angle is restricted by having the movable body abut the
maximum inclination restriction member rather than by use of the
link mechanism. Consequently, even if the swash plate and the link
mechanism have dimensional tolerance and the like in the axial
direction of the drive shaft, such tolerance does not cause
dispersion in the maximum value of the inclination angle.
[0015] Furthermore, since the maximum inclination restriction
member rotates synchronously with the drive shaft, even when the
movable body abuts the maximum inclination restriction member,
rotation of the movable body and the swash plate is not restricted
by the maximum inclination restriction member.
[0016] Thus, the compressor according to the present invention, in
which the inclination angle of the swash plate is changed by the
actuator, ensures excellent quality stability on a
product-by-product basis while realizing reduction in size.
[0017] In the compressor according to the present invention,
various members may be employed as the maximum inclination
restriction member as long as the members have sufficient strength
to endure pressure in excess of the required control pressure and
are rotatable synchronously with the drive shaft. Furthermore, for
example, a protrusion or the like may be formed on the movable body
exclusively for the purpose of abutting the maximum inclination
restriction member.
[0018] In the compressor according to the present invention, the
drive shaft may include a drive shaft body and a cap that is
press-fitted to the drive shaft body and located in the swash plate
chamber. It is preferable that the cap is the maximum inclination
restriction member. In this case, by having the movable body abut
the cap, it is possible to restrict the maximum value of the
inclination angle. Furthermore, when the cap is the maximum
inclination restriction member, it is possible to adjust a position
where the movable body abuts the cap depending on the shape of the
cap and the position where the cap is press-fitted to the drive
shaft body. Thus, the compressor is able to suitably restrict the
maximum value of the inclination angle.
[0019] The compressor according to the present invention may
comprise a circlip that is fitted to the drive shaft and located in
the swash plate chamber. It is also preferable that the circlip is
the maximum inclination restriction member. Also in this case, it
is possible to adjust a position where the movable body abuts the
circlip depending on the position where the circlip is fitted to
the drive shaft body. Thus, this compressor is also able to
suitably restrict the maximum value of the inclination angle.
Advantageous Effects of Invention
[0020] The compressor according to the present invention, in which
the inclination angle of the swash plate is changed by the
actuator, ensures excellent quality stability on a
product-by-product basis while realizing reduction in size.
BRIEF DESCRIPTION OF DRAWINGS
[0021] FIG. 1 is a sectional view of a compressor according to
Embodiment 1 at the time of maximum displacement.
[0022] FIG. 2 is a schematic diagram showing a control mechanism of
the compressor according to Embodiment 1.
[0023] FIG. 3 is a perspective view showing a movable body of the
compressor according to Embodiment 1 when viewed from the
front.
[0024] FIG. 4 is a sectional view of the compressor according to
Embodiment 1 at the time of minimum displacement.
[0025] FIG. 5 is an enlarged sectional view showing principal part
of a compressor according to Embodiment 2 at the time of maximum
displacement.
DESCRIPTION OF EMBODIMENTS
[0026] Embodiments 1 and 2, which embody the present invention,
will be described below with reference to the drawings. The
compressors according to Embodiments 1 and 2 are variable
displacement double head swash plate type compressors. These
compressors are both mounted on vehicles and constitute
refrigeration circuits of vehicle air-conditioning apparatus.
Embodiment 1
[0027] As shown in FIG. 1, a compressor according to Embodiment 1
comprises a housing 1, a drive shaft 3, a swash plate 5, a link
mechanism 7, plural pistons 9, a pair of shoes 11a and 11b, and an
actuator 13 as well as a control mechanism 15 which is shown in
FIG. 2.
[0028] As shown in FIG. 1, the housing 1 includes a front housing
17 located at a front position in the compressor, a rear housing 19
located at a rear position in the compressor, first and second
cylinder blocks 21 and 23 located between the front housing 17 and
the rear housing 19, and first and second valve forming plates 39
and 41.
[0029] A boss 17a, which protrudes frontward, is formed in the
front housing 17. A shaft seal device 25 is provided in the boss
17a. A first suction chamber 27a and a first discharge chamber 29a
are formed in the front housing 17. The first suction chamber 27a
is located on an inner peripheral side in the front housing 17. The
first discharge chamber 29a is formed into an annular shape and
located on an outer peripheral side of the first suction chamber
27a in the front housing 17.
[0030] A first front-side communication passage 18a is formed in
the front housing 17. The front end of the first front-side
communication passage 18a communicates with the first discharge
chamber 29a, and the rear end thereof opens at the rear end of the
front housing 17.
[0031] The control mechanism 15 described above is provided in the
rear housing 19. Also, a second suction chamber 27b, a second
discharge chamber 29b, and a pressure regulation chamber 31 are
formed in the rear housing 19. The pressure regulation chamber 31
is located in the central part of the rear housing 19. The second
suction chamber 27b is formed into an annular shape and located on
an outer peripheral side of the pressure regulation chamber 31 in
the rear housing 19. The second discharge chamber 29b is also
formed into an annular shape and located on an outer peripheral
side of the second suction chamber 27b in the rear housing 19.
[0032] A first rear-side communication passage 20a is formed in the
rear housing 19. The rear end of the first rear-side communication
passage 20a communicates with the second discharge chamber 29b, and
the front end thereof opens at the front end of the rear housing
19.
[0033] A swash plate chamber 33 is formed between the first
cylinder block 21 and the second cylinder block 23. The swash plate
chamber 33 is located at an approximate center in the front-rear
direction of the housing 1.
[0034] Plural first cylinder bores 21a are formed parallel to one
another at equal angular intervals in a circumferential direction
in the first cylinder block 21. Also, a first shaft hole 21b is
formed in the first cylinder block 21 to allow the drive shaft 3 to
be inserted therethrough. A first sliding bearing 22a is provided
on the first shaft hole 21b. A roller bearing may be provided
instead of the first sliding bearing 22a.
[0035] The first cylinder block 21 has a first recess 21c, which
communicates with the first shaft hole 21b and is coaxial with the
first shaft hole 21b. The first recess 21c communicates with the
swash plate chamber 33 and forms part of the swash plate chamber
33. The first recess 21c is shaped such that its diameter becomes
smaller toward the front end in a stepwise manner. A first thrust
bearing 35a is provided on a front end of the first recess 21c. A
first connecting passage 37a is formed in the first cylinder block
21 to allow the swash plate chamber 33 to communicate with the
first suction chamber 27a. Also, a first retainer groove 21e is
provided in the first cylinder block 21 to restrict a maximum
opening degree of respective first suction reed valves 391a
described later.
[0036] A second front-side communication passage 18b is formed in
the first cylinder block 21. The front end of the second front-side
communication passage 18b opens at the front end of the first
cylinder block 21, and the rear end thereof opens at the rear end
of the first cylinder block 21.
[0037] Similarly to the first cylinder block 21, plural second
cylinder bores 23a are formed in the second cylinder block 23. The
second cylinder bores 23a are respectively paired with the first
cylinder bores 21a in the front-rear direction. The first cylinder
bores 21a and the second cylinder bores 23a are equal in
diameter.
[0038] Also, a second shaft hole 23b is formed in the second
cylinder block 23 to allow the drive shaft 3 to be inserted
therethrough. The rear end of the second shaft hole 23b
communicates with the pressure regulation chamber 31. A second
sliding bearing 22b is provided on the second shaft hole 23b. A
roller bearing may be provided instead of the second sliding
bearing 22b.
[0039] The second cylinder block 23 has a second recess 23c, which
communicates with the second shaft hole 23b and is coaxial with the
second shaft hole 23b. The second recess 23c also communicates with
the swash plate chamber 33 and forms part of the swash plate
chamber 33. Accordingly, the front end of the second shaft hole 23b
communicates with the swash plate chamber 33. The second recess 23c
is shaped such that its diameter becomes smaller toward the rear
end in a stepwise manner. A second thrust bearing 35b is provided
on the rear end of the second recess 23c. A second connecting
passage 37b is formed in the second cylinder block 23 to allow the
swash plate chamber 33 to communicate with the second suction
chamber 27b. Also, a second retainer groove 23e is provided in the
second cylinder block 23 to restrict a maximum opening degree of
second suction reed valves 411a described later.
[0040] The second cylinder block 23 includes an outlet port 230, a
confluence discharge chamber 231, a third front-side communication
passage 18c, a second rear-side communication passage 20b, and an
inlet port 330. The outlet port 230 and the confluence discharge
chamber 231 communicate with each other. Via the outlet port 230,
the confluence discharge chamber 231 is connected to a condenser
(not shown) making up a refrigeration circuit.
[0041] The front end of the third front-side communication passage
18c opens to the front end of the second cylinder block 23, and the
rear end thereof communicates with the confluence discharge chamber
231. The third front-side communication passage 18c communicates
with the rear end of the second front-side communication passage
18b when the first cylinder block 21 and the second cylinder block
23 are joined together.
[0042] The front end of the second rear-side communication passage
20b communicates with the confluence discharge chamber 231, and the
rear end thereof opens to the rear end of the second cylinder block
23.
[0043] The inlet port 330 is formed in the second cylinder block
23. Via the inlet port 330, the swash plate chamber 33 is connected
to an evaporator (not shown) making up the refrigeration
circuit.
[0044] The first valve forming plate 39 is provided between the
front housing 17 and the first cylinder block 21. Also, the second
valve forming plate 41 is provided between the rear housing 19 and
the second cylinder block 23.
[0045] The first valve forming plate 39 includes a first valve
plate 390, a first suction valve plate 391, a first discharge valve
plate 392, and a first retainer plate 393. First suction ports
390a, the number of which is equal to the number of the first
cylinder bores 21a, are formed in the first valve plate 390, the
first discharge valve plate 392, and the first retainer plate 393.
First discharge ports 390b, the number of which is equal to the
number of the first cylinder bores 21a, are formed in the first
valve plate 390 and the first suction valve plate 391. A first
suction communication hole 390c is formed in the first valve plate
390, the first suction valve plate 391, the first discharge valve
plate 392, and the first retainer plate 393. A first discharge
communication hole 390d is formed in the first valve plate 390 and
the first suction valve plate 391.
[0046] The first cylinder bores 21a communicate with the first
suction chamber 27a through the respective first suction ports
390a. Also, the first cylinder bores 21a communicate with the first
discharge chamber 29a through the respective first discharge ports
390b. The first suction chamber 27a communicates with the first
connecting passages 37a through the first suction communication
hole 390c. The first front-side communication passage 18a
communicates with the second front-side communication passage 18b
through the first discharge communication hole 390d.
[0047] The first suction valve plate 391 is provided on the rear
face of the first valve plate 390. The first suction valve plate
391 has the plural first suction reed valves 391a which are capable
of opening and closing the respective first suction ports 390a by
elastic deformation. The first discharge valve plate 392 is
provided on the front face of the first valve plate 390. The first
discharge valve plate 392 has plural first discharge reed valves
392a which are capable of opening and closing the respective first
discharge ports 390b by elastic deformation. The first retainer
plate 393 is provided on the front face of the first discharge
valve plate 392. The first retainer plate 393 restricts a maximum
opening degree of the respective first discharge reed valves
392a.
[0048] The second valve forming plate 41 includes a second valve
plate 410, a second suction valve plate 411, a second discharge
valve plate 412, and a second retainer plate 413. Second suction
ports 410a, the number of which is equal to the number of the
second cylinder bores 23a, are formed in the second valve plate
410, the second discharge valve plate 412, and the second retainer
plate 413. Second discharge ports 410b, the number of which is
equal to the number of the second cylinder bores 23a, are formed in
the second valve plate 410 and the second suction valve plate 411.
A second suction communication hole 410c is formed in the second
valve plate 410, the second suction valve plate 411, the second
discharge valve plate 412, and the second retainer plate 413. A
second discharge communication hole 410d is formed in the second
valve plate 410 and the second suction valve plate 411.
[0049] The second cylinder bores 23a communicate with the second
suction chamber 27b through the respective second suction ports
410a. Also, the second cylinder bores 23a communicate with the
second discharge chamber 29b through the respective second
discharge ports 410b. The second suction chamber 27b communicates
with the second connecting passages 37b through the second suction
communication hole 410c. The first rear-side communication passage
20a communicates with the second rear-side communication passage
20b through the second discharge communication hole 410d.
[0050] The second suction valve plate 411 is provided on the front
face of the second valve plate 410. The second suction valve plate
411 is provided with the plural second suction reed valves 411a
which are capable of opening and closing the respective second
suction ports 410a by elastic deformation. Also, the second
discharge valve plate 412 is provided on the rear face of the
second valve plate 410. The second discharge valve plate 412 is
provided with plural second discharge reed valves 412a which are
capable of opening and closing the respective second discharge
ports 410b by elastic deformation. The second retainer plate 413 is
provided on the rear face of the second discharge valve plate 412.
The second retainer plate 413 restricts a maximum opening degree of
each of the second discharge reed valves 412a.
[0051] In the compressor, a first discharge communication passage
18 is formed by the first front-side communication passage 18a, the
first discharge communication hole 390d, the second front-side
communication passage 18b, and the third front-side communication
passage 18c. Also, a second discharge communication passage 20 is
formed by the first rear-side communication passage 20a, the second
discharge communication hole 410d, and the second rear-side
communication passage 20b.
[0052] Also, in the compressor, the first and second suction
chambers 27a and 27b and the swash plate chamber 33 communicate
with each other via the first and second connecting passages 37a
and 37b and the first and second suction communication holes 390c
and 410c. Consequently, the pressure in the first and second
suction chambers 27a and 27b and the swash plate chamber 33 are
substantially equal. Because a low-pressure refrigerant gas which
has passed through an evaporator flows into the swash plate chamber
33 through the inlet port 330, the pressure in the swash plate
chamber 33 and the first and second suction chambers 27a and 27b is
lower than the pressure in the first and second discharge chambers
29a and 29b.
[0053] The drive shaft 3 is made up of a drive shaft body 30
extending along a drive axis O, a first support member 43a, and a
second support member 43b. A first small-diameter portion 30a is
formed on the front end side of the drive shaft body 30, and a
second small-diameter portion 30b is formed on the rear end side of
the drive shaft body 30. The drive shaft body 30 extends rearward
from the front side of the housing 1 by being inserted rearward
from the boss 17a through the first and second sliding bearings 22a
and 22b. Consequently, the drive shaft body 30 and thus the drive
shaft 3 are supported by the housing 1 so as to be rotatable around
[[a] ] the drive axis O. The front end of the drive shaft body 30
is located in the boss 17a and the rear end thereof protrudes into
the pressure regulation chamber 31.
[0054] The swash plate 5, the link mechanism 7, and the actuator 13
are provided on the drive shaft body 30. The swash plate 5, the
link mechanism 7, and the actuator 13 are all disposed in the swash
plate chamber 33.
[0055] The first support member 43a is press-fitted to the first
small-diameter portion 30a of the drive shaft body 30 and located
inside of the first sliding bearing 22a in the first shaft hole
21b. Also, the first support member 43a includes a flange 430
configured to abut the first thrust bearing 35a, and a mounting
portion (not shown) configured to allow a second pin 47b, which
will be described later, to be inserted therethrough. A front end
of a first return spring 44a is fixed to the first support member
43a. The first return spring 44a extends from the first support
member 43a toward the swash plate chamber 33 along the drive axis
O.
[0056] The second support member 43b is press-fitted to the rear
end of the second small-diameter portion 30b of the drive shaft
body 30, and is located in the second shaft hole 23b. The second
support member 43b corresponds to a cap according to the present
invention. A flange 431 is formed on the front end of the second
support member 43b. The flange 431 has a flat-shaped front face
431a. The flange 431 protrudes into the second recess 23c and abuts
the second thrust bearing 35b. Also, the rear end of the second
support member 43b protrudes into the pressure regulation chamber
31. In the second support member 43b, a first slide member 432 and
a second slide member 433 made of resin are provided in the rear of
the flange 431. The first and second slide members 432 and 433 are
in contact with and slidable along an inner circumferential surface
of the second shaft hole 23b.
[0057] The second sliding bearing 22b is press-fitted into the rear
end of the second shaft hole 23b. Thereby, the second sliding
bearing 22b is provided in the second shaft hole 23b.
[0058] The swash plate 5 has a flat annular shape and includes a
front face 5a and a rear face 5b. The front face 5a faces frontward
of the compressor in the swash plate chamber 33. Also, the rear
face 5b faces rearward of the compressor in the swash plate chamber
33.
[0059] The swash plate 5 is fixed to a ring plate 45. The ring
plate 45 has a flat annular shape with an insertion hole 45a formed
in the center. The swash plate 5 is attached to the drive shaft 3
by inserting the drive shaft body 30 through the insertion hole 45a
in the swash plate chamber 33.
[0060] The link mechanism 7 has a lug arm 49. In the swash plate
chamber 33, the lug arm 49 is placed frontward relative to the
swash plate 5 and located between the swash plate 5 and the first
support member 43a. The lug arm 49 is formed so as to be
substantially L-shaped from the front end toward the rear end. As
shown in FIG. 4, the lug arm 49 abuts the flange 430 of the first
support member 43a when the inclination angle of the swash plate 5
with respect to a direction perpendicular to the drive axis O
becomes a minimum. A weight 49a is formed at the rear end of the
lug arm 49. The weight 49a extends approximately half around a
circumference of the actuator 13. The shape of the weight 49a may
be designed as appropriate.
[0061] As shown in FIG. 1, the rear end side of the lug arm 49 is
connected to one end side of the ring plate 45 with a first pin
47a. When the axis of the first pin 47a is defined as a first pivot
axis M1, the rear end side of the lug arm 49 is supported around
the first pivot axis M1 so as to be pivotable with respect to the
one end side of the ring plate 45, i.e., the swash plate 5. The
first pivot axis M1 extends in a direction perpendicular to the
drive axis O of the drive shaft 3.
[0062] The front end of the lug arm 49 is connected to the first
support member 43a via the second pin 47b. When the axis of the
second pin 47b is defined as a second pivot axis M2, the front end
of the lug arm 49 is supported around the second pivot axis M2 so
as to be pivotable with respect to the first support member 43a,
i.e., the drive shaft 3. The second pivot axis M2 extends parallel
to the first pivot axis M1. The link mechanism 7 according to the
present invention is made up of the lug arm 49, the first and
second pins 47a and 47b, and, in addition, first and second pulling
arms 132 and 133 and a third pin 47c, which will be described
later.
[0063] The weight 49a is provided so as to extend at the rear end
of the lug arm 49, i.e., on the opposite side of the second pivot
axis M2 with reference to the first pivot axis M1. As the lug arm
49 is supported by the ring plate 45 with the first pin 47a, the
weight 49a passes through a groove 45b in the ring plate 45 and
reaches the rear face side of the ring plate 45, i.e., the side of
the rear face 5b of the swash plate 5. Therefore, a centrifugal
force produced by rotation of the swash plate 5 around the drive
axis O also acts on the weight 49a at the side of the rear face 5b
of the swash plate 5.
[0064] In this compressor, the swash plate 5 is able to rotate
together with the drive shaft 3 as the swash plate 5 is connected
to the drive shaft 3 by the link mechanism 7. Also, the swash plate
5 is able to change its inclination angle due to the pivotal
movement of both ends of the lug arm 49 around the first pivot axis
M1 and the second pivot axis M2, respectively.
[0065] The pistons 9 each has a first head 9a at its front end and
a second head 9b at its rear end. The first head 9a is reciprocally
accommodated in each of the first cylinder bores 21a. The first
head 9a and the first valve forming plate 39 define a first
compression chamber 21d in each of the first cylinder bores 21a.
The second head 9b is reciprocally accommodated in each of the
second cylinder bores 23a. The second head 9b and the second valve
forming plate 41 define a second compression chamber 23d in each of
the second cylinder bores 23a.
[0066] An engaging portion 9c is formed in the middle of each of
the pistons 9. Hemispherical shoes 11a and 11b are provided in each
of the engaging portions 9c. The shoes 11a and 11b convert rotation
of the swash plate 5 into reciprocating movement of the pistons 9.
The shoes 11a and 11b correspond to a conversion mechanism
according to the present invention. Thereby, the first and second
heads 9a, 9b are able to reciprocate in the first and second
cylinder bores 21a, 23a at a stroke corresponding to the
inclination angle of the swash plate 5.
[0067] Here, in the compressor, when the stroke of the pistons 9
changes according to the change in the inclination angle of the
swash plate 5, respective top dead center positions of the first
heads 9a and the second heads 9b move. Specifically, as the
inclination angle of the swash plate 5 decreases, the top dead
center positions of the first and second heads 9a and 9b move such
that the volume of the second compression chamber 23d becomes
larger than the volume of the first compression chamber 21d.
[0068] As shown in FIG. 1, the actuator 13 is placed in the swash
plate chamber 33. The actuator 13 is located rearward of the swash
plate 5 in the swash plate chamber 33 and capable of advancing into
the second recess 23c. The actuator 13 includes a movable body 13a,
a partition body 13b, and a control pressure chamber 13c. The
control pressure chamber 13c is formed between the movable body 13a
and the partition body 13b.
[0069] As shown in FIG. 3, the movable body 13a includes a rear
wall 130, a circumferential wall 131, a first pulling arm 132, and
a second pulling arm 133. The rear wall 130 is located at a rear
position in the movable body 13a and extends radially in a
direction away from the drive axis O. The rear wall 130 has an
insertion hole 130a through which the second small-diameter portion
30b of the drive shaft body 30 is inserted. The circumferential
wall 131 continues from an outer circumferential edge of the rear
wall 130 and extends frontward in the movable body 13a.
[0070] Both of the first pulling arm 132 and the second pulling arm
133 are formed at the front end of the circumferential wall 131.
The first pulling arm 132 and second pulling arm 133 of the
circumferential wall 131 are placed so as to face each other across
the drive axis O and protrude frontward in the movable body 13a.
These first and second pulling arms 132 and 133 correspond to a
coupling portion according to the present invention. A first pin
hole 132a and a second pin hole 133a are bored through the first
pulling arm 132 and the second pulling arm 133, respectively. The
movable body 13a is formed into a bottomed cylindrical shape by the
rear wall 130, the circumferential wall 131, and the first and
second pulling arms 132 and 133.
[0071] As shown in FIG. 1, the partition body 13b is formed into a
disk shape having a diameter that is substantially equal to the
inside diameter of the movable body 13a. A second return spring 44b
is provided between the partition body 13b and the ring plate 45.
Specifically, the rear end of the second return spring 44b is fixed
to the partition body 13b and the front end of the second return
spring 44b is fixed to the opposite end side of the ring plate
45.
[0072] The second small-diameter portion 30b of the drive shaft
body 30 is inserted through the movable body 13a and the partition
body 13b. The movable body 13a is accommodated in the second recess
23c and faces the link mechanism 7 across the swash plate 5. The
partition body 13b is placed in the movable body 13a at a position
rearward of the swash plate 5, and its periphery is surrounded by
the circumferential wall 131. Consequently, the control pressure
chamber 13c is formed between the movable body 13a and the
partition body 13b. The control pressure chamber 13c is separated
from the swash plate chamber 33 by the rear wall 130 and the
circumferential wall 131 of the movable body 13a and the partition
body 13b.
[0073] In the compressor, a required control pressure, which is the
pressure in the control pressure chamber 13c required to increase
the inclination angle of the swash plate 5 to a maximum value, is
preset to the control pressure chamber 13c. The required control
pressure is set lower than the upper limit of the discharge
refrigerant pressure, i.e., the upper limit of the pressure of
refrigerant gas in the first discharge chamber 29a and the second
discharge chamber 29b.
[0074] In the compressor, due to the insertion of the second
small-diameter portion 30b, the movable body 13a is able to rotate
together with the drive shaft 3 and move along the drive axis O of
the drive shaft 3 in the swash plate chamber 33. On the other hand,
the partition body 13b is fixed to the second small-diameter
portion 30b in the state that the second small-diameter portion 30b
has been inserted therethrough. The partition body 13b is thus only
able to rotate together with the drive shaft 3, and not able to
move in the same manner as the movable body 13a. As a result, the
movable body 13a moves along the drive axis O relative to the
partition body 13b. The partition body 13b may be provided on the
drive shaft body 30 so as to be movable along the drive axis O.
[0075] The first and second pulling arms 132 and 133 are connected
with the opposite end side of the ring plate 45 by the third pin
47c. The third pin 47c extends from the first pin hole 132a, which
is shown in FIG. 3, to the second pin hole 133a through the
opposite end side of the ring plate 45. As shown in FIG. 1, when
the axis of the third pin 47c is defined as an action axis M3, the
opposite end side of the ring plate 45, i.e., the swash plate 5 is
supported by the movable body 13a so as to be pivotable around the
action axis M3. The action axis M3 extends parallel to the first
and second pivot axes M1 and M2. The movable body 13a is thus
coupled to the swash plate 5.
[0076] The second small-diameter portion 30b has an axial path 3a,
which extends frontward from the rear end along the drive axis O,
and a radial path 3b, which extends in a radial direction from the
front end of the axial path 3a and opens in an outer
circumferential surface of the drive shaft body 30. The rear end of
the axial path 3a opens to the pressure regulation chamber 31. The
radial path 3b opens to the control pressure chamber 13c. The
control pressure chamber 13c thus communicates with the pressure
regulation chamber 31 through the radial path 3b and the axial path
3a.
[0077] A threaded portion 3d is formed on a tip end of the drive
shaft body 30. Via the threaded portion 3d, the drive shaft 3 is
connected to a pulley or an electro-magnetic clutch (not
shown).
[0078] As shown in FIG. 2, the control mechanism 15 includes a
low-pressure passage 15a, a high-pressure passage 15b, a control
valve 15c, an orifice 15d, the axial path 3a, and the radial path
3b.
[0079] The low-pressure passage 15a is connected to the pressure
regulation chamber 31 and the second suction chamber 27b. Through
the low-pressure passage 15a, the axial path 3a, and the radial
path 3b, the control pressure chamber 13c, the pressure regulation
chamber 31, and the second suction chamber 27b communicate with one
another. The high-pressure passage 15b is connected to the pressure
regulation chamber 31 and the second discharge chamber 29b. Through
the high-pressure passage 15b, the axial path 3a, and the radial
path 3b, the control pressure chamber 13c, the pressure regulation
chamber 31, and the second discharge chamber 29b communicate with
one another. The orifice 15d is provided in the high-pressure
passage 15b.
[0080] The control valve 15c is provided on the low-pressure
passage 15a. The control valve 15c is able to adjust an opening
degree of the low-pressure passage 15a based on the pressure in the
second suction chamber 27b.
[0081] In the compressor, the inlet port 330 shown in FIG. 1 is
connected with a pipe leading to the evaporator while the outlet
port 230 is connected with a pipe leading to the condenser. The
condenser is connected to the evaporator through a pipe and an
expansion valve. The compressor, the evaporator, the expansion
valve, the condenser, etc. make up the refrigeration circuit of
vehicle air-conditioning apparatus. Illustration of the evaporator,
the expansion valve, the condenser, and the pipes is omitted.
[0082] In the compressor configured as described above, by rotation
of the drive shaft 3, the swash plate 5 rotates and the pistons 9
reciprocate in the first and second cylinder bores 21a and 23a.
Thereby, the first and second compression chambers 21d and 23d
change their volumes according to the piston stroke. In the
compressor, a suction phase for sucking refrigerant gas into the
first and second compression chambers 21d and 23d, a compression
phase for compressing the refrigerant gas in the first and second
compression chambers 21d and 23d, and a discharge phase for
discharging the compressed refrigerant gas into the first and
second discharge chambers 29a and 29b take place repeatedly.
[0083] The refrigerant gas discharged into the first discharge
chamber 29a passes through the first discharge communication
passage 18 and reaches the confluence discharge chamber 231.
Similarly, the refrigerant gas discharged into the second discharge
chamber 29b passes through the second discharge communication
passage 20 and reaches the confluence discharge chamber 231. After
reaching the confluence discharge chamber 231, the refrigerant gas
is discharged to the condenser through the outlet port 230.
[0084] While these suction phase and so forth take place, a piston
compression force to reduce the inclination angle of the swash
plate 5 is applied to a rotational body, which is made up of the
swash plate 5, the ring plate 45, the lug arm 49, and the first pin
47a. When the inclination angle of the swash plate 5 is changed,
the stroke of the pistons 9 increases or decreases, and thereby, it
is possible to control the displacement.
[0085] Specifically, when the control valve 15c, which is shown in
FIG. 2, of the control mechanism 15 increases the opening degree of
the low-pressure passage 15a, the pressure in the pressure
regulation chamber 31, and thus the pressure in the control
pressure chamber 13c become substantially equal to the pressure in
the second suction chamber 27b. Due to the piston compression force
acting on the swash plate 5, the movable body 13a of actuator 13
moves frontward in the swash plate chamber 33 as shown in FIG.
4.
[0086] Consequently, in the compressor, the movable body 13a pushes
the swash plate 5 at the opposite end side frontward in the swash
plate chamber 33 at the action axis M3 via the first and second
pulling arms 132 and 133. Thus, in the compressor, the opposite end
side of the ring plate 45, in other words, the opposite end side of
the swash plate 5, pivots clockwise around the action axis M3
against a biasing force of the second return spring 44b. Also, the
rear end of the lug arm 49 pivots counterclockwise around the first
pivot axis M1 and the front end of the lug arm 49 pivots
counterclockwise around the second pivot axis M2. The lug arm 49
comes close to the flange 430 of the first support member 43a.
Thereby, the swash plate 5 pivots using the action axis M3 as a
point of action and using the first pivot axis M1 as a fulcrum.
This reduces the inclination angle of the swash plate 5 with
respect to the direction perpendicular to the drive axis O of the
drive shaft 3 and decreases the stroke of the pistons 9. Therefore,
discharge capacity of the compressor per rotation of the drive
shaft 3 decreases. The inclination angle of the swash plate 5 shown
in FIG. 4 is the minimum value in this compressor.
[0087] Here, in this compressor, the centrifugal force acting on
the weight 49a is also applied to the swash plate 5. Thus, the
swash plate 5 of this compressor is easily displaced toward a
direction of reducing the inclination angle.
[0088] When the inclination angle of the swash plate 5 decreases,
the ring plate 45 abuts the rear end of the first return spring
44a. The first return spring 44a thus deforms elastically and the
rear end of the first return spring 44a comes close to the first
support member 43a.
[0089] In this compressor, as the inclination angle of the swash
plate 5 becomes smaller and the stroke of the pistons 9 decreases,
the top dead center position of the second heads 9b moves away from
the second valve forming plate 41. Thus, in the compressor, when
the inclination angle of the swash plate 5 approaches 0 degrees,
compression work is performed slightly in the first compression
chamber 21d, whereas compression work is not performed in the
second compression chamber 23d.
[0090] When the control valve 15c shown in FIG. 2 reduces the
opening degree of the low-pressure passage 15a, the pressure in the
pressure regulation chamber 31 increases due to the pressure of the
refrigerant gas in the second discharge chamber 29b, and thereby
the pressure in the control pressure chamber 13c increases. Thus,
the movable body 13a of the actuator 13 moves in a rearward in the
swash plate chamber 33, i.e., toward the flange 431 of the second
support member 43b, as shown in FIG. 1, against the piston
compression force acting on the swash plate 5.
[0091] Consequently, in the compressor, the movable body 13a pulls
the opposite end side of the swash plate 5 rearward in the swash
plate chamber 33 at the action axis M3 via the first and second
pulling arms 132 and 133. Thus, in the compressor, the opposite end
side of the swash plate 5 pivots counterclockwise around the action
axis M3. Also, the rear side of the lug arm 49 pivots clockwise
around the first pivot axis M1 and the front end of the lug arm 49
pivots clockwise around the second pivot axis M2. The lug arm 49
moves away from the flange 430 of the first support member 43a.
Thereby, the swash plate 5 pivots in a direction opposite to the
above-described direction in the case of reducing the inclination
angle, using the action axis M3 as a point of action and using the
first pivot axis M1 as a fulcrum. This increases the inclination
angle of the swash plate 5 with respect to the direction
perpendicular to the drive axis O of the drive shaft 3.
[0092] Here, in the compressor, the movable body 13a moves towards
the flange 431 and pulls the opposite end side of the swash plate 5
rearward in the swash plate chamber 33 via the first and second
pulling arms 132 and 133 until the pressure in the control pressure
chamber 13c reaches the required control pressure. Thus, the link
mechanism 7 permits increase of the inclination angle of the swash
plate 5 until it reaches the maximum value. The discharge capacity
of the compressor per rotation of the drive shaft 3 increases as
the stroke of the pistons 9 increases. When the pressure in the
control pressure chamber 13c reaches the required control pressure,
the inclination angle of the swash plate 5 reaches the maximum
value as shown in FIG. 1.
[0093] In the compressor, while the required control pressure of
the control pressure chamber 13c is set lower than the upper limit
of the discharge refrigerant pressure as described above, the
refrigerant gas is introduced into the control pressure chamber 13c
from the second discharge chamber 29b through the high-pressure
passage 15b and the like. Therefore, in the compressor, even after
the inclination angle of the swash plate 5 reaches the maximum
value as described above, the pressure in the control pressure
chamber 13c continues to increase beyond the required control
pressure.
[0094] In this regard, in the compressor, when the pressure in the
control pressure chamber 13c increases and reaches the required
control pressure, the movable body 13a moves rearward in the swash
plate chamber 33 and the rear wall 130 abuts the front face 431a of
the flange 431. This allows the compressor to restrict the maximum
value of the inclination angle of the swash plate 5. That is, in
this compressor, although the movable body 13a and the swash plate
5 are coupled to each other via the first and second pulling arms
132 and 133, for restricting the maximum value of the inclination
angle, the swash plate 5 does not push the lug arm 49 of the link
mechanism 7 due to the pressure in the control pressure chamber
13c. In this compressor, the pressure in excess of the required
control pressure acts on the flange 431 and thus on the second
support member 43b, but does not act on the swash plate 5 or the
lug arm 49 of the link mechanism 7 via the first and second pulling
arms 132 and 133. Therefore, it is not necessary in this compressor
to ensure the strength of the swash plate 5 and the lug arm 49 more
than required. Thus, the compressor eliminates the need to upsize
the swash plate chamber 33.
[0095] In the compressor, the maximum value of the inclination
angle is restricted by the rear wall 130 of the movable body 13a
and the flange 431 abutting each other, not by the link mechanism
7. Therefore, in the compressor, even if the swash plate 5 and the
link mechanism 7 have dimensional tolerance and the like in the
direction of the drive axis O, such tolerance does not cause
dispersion in the maximum value of the inclination angle.
[0096] In the compressor, since the second support member 43b is
press-fitted to the drive shaft body 30, the second support member
43b including the flange 431 rotates synchronously with the drive
shaft body 30. Therefore, in the compressor, even when the rear
wall 130 abuts the flange 431, the rotation of the movable body 13a
and even the swash plate 5 is not restricted by the flange 431.
[0097] Therefore, the compressor according to Embodiment 1, in
which the inclination angle of the swash plate 5 is changed by the
actuator 13, ensures excellent quality stability on a
product-by-product basis while realizing reduction in size.
[0098] In particular, in this compressor, the maximum value of the
inclination angle is restricted by having the flange 431 of the
second support member 43b abut the rear wall 130 of the movable
body 13a. Therefore, in this compressor, it is possible to adjust
the position where the rear wall 130 abuts the flange 431 depending
on the thickness of the flange 431 and the shape of the second
support member 43b by itself. Furthermore, in this compressor, it
is also possible to adjust the position where the rear wall 130
abuts the flange 431 depending on the position where the second
support member 43b is press-fitted to the second small-diameter
portion 30b of the drive shaft body 30. Thus, the compressor is
capable of suitably restricting the maximum value of the
inclination angle.
Embodiment 2
[0099] In the compressor according to Embodiment 2, as shown in
FIG. 5, a circlip 51 is fitted to the second small-diameter portion
30b of the drive shaft body 30. More specifically, the circlip 51
is fitted to the second small-diameter portion 30b at a position
between the second support member 43b and the movable body 13a.
Thereby, the circlip 51 is located in the second recess 23c, i.e.,
in the swash plate chamber 33. The shape of the circlip 51 may be
designed as appropriate. For ease of explanation, illustration of
the pistons 9, the shoes 11a and 11b and the like are omitted in
this figure. The other components of the compressor are the same as
those of the compressor according to Embodiment 1, and, with
respect to the same components, same reference numerals are used
and detailed description thereof is omitted.
[0100] In this compressor, when the pressure in the control
pressure chamber 13c increases and reaches the required control
pressure, the rear wall 130 of the movable body 13a which has moved
rearward in the swash plate chamber 33 abuts the circlip 51. This
allows the compressor to restrict the maximum value of the
inclination angle of the swash plate 5 without having the swash
plate 5 push the link mechanism 7.
[0101] Also, in the compressor, it is possible to adjust the
position at which the rear wall 130 abuts the circlip 51 depending
on the position where the circlip 51 is press-fitted to the second
small-diameter portion 30b. Thus, the maximum value of the
inclination angle can be suitably restricted in this compressor.
The other operations of this compressor are the same as those of
the compressor according to Embodiment 1.
[0102] Although present invention has been described above by
referring to Embodiments 1 and 2, needless to say, the present
invention is not limited to Embodiments 1 and 2 described above and
may be modified and applied as appropriate without departing from
the gist of the present invention.
[0103] For example, a protrusion may be provided on the rear wall
130 of the movable body 13a exclusively for the purpose of abutting
the flange 431 or the circlip 51. Also, the protrusion may be
configured to be able to abut the second thrust bearing 35b. In
this case, the second thrust bearing 35b corresponds to the maximum
inclination restriction member according to the present
invention.
[0104] Furthermore, the compressor may be configured as a variable
displacement single head swash plate type compressor by forming
cylinder bores only in either of the first cylinder block 21 and
second the cylinder block 23.
[0105] Also, the control mechanism 15 may be configured such that
the control valve 15c is provided in the high-pressure passage 15b
while the orifice 15d is provided in the low-pressure passage 15a.
In this case, it is possible to adjust the opening degree of the
high-pressure passage 15b using the control valve 15c. Thereby, the
pressure in the control pressure chamber 13c can be increased
quickly due to the pressure of refrigerant gas in the second
discharge chamber 29b, and the discharge capacity can be increased
quickly.
INDUSTRIAL APPLICABILITY
[0106] The present invention is applicable to air-conditioning
apparatus and the like.
REFERENCE SIGNS LIST
[0107] 1 Housing [0108] 3 Drive shaft [0109] 5 Swash plate [0110] 7
Link mechanism [0111] 9 Piston [0112] 11a, 11b Shoe (conversion
mechanism) [0113] 13 Actuator [0114] 13a Movable body [0115] 13b
Partition body [0116] 13c Control pressure chamber [0117] 15
Control mechanism [0118] 21a First cylinder bore [0119] 21d First
compression chamber [0120] 23a Second cylinder bore [0121] 23d
Second compression chamber [0122] 27a First suction chamber [0123]
27b Second suction chamber [0124] 29a First discharge chamber
[0125] 29b Second discharge chamber [0126] 33 Swash elate chamber
[0127] 43b Second support member (maximum inclination restriction
member, cap) [0128] 51 Circlip (maximum inclination restriction
member) [0129] 130 Rear wall (movable body) [0130] 131
Circumferential wall (movable body) [0131] 132 First pulling arm
(coupling portion) [0132] 133 Second pulling arm (coupling portion)
[0133] O Drive axis
* * * * *