JPH04136487A - Variable displacement compressor - Google Patents

Abstract

PURPOSE:To make a thrust load zero and abolish a thrust bearing by making an oscillating member be in axial contact with a static member directly or through an intermediate member without a main shaft, and regulating a minimum volume position of a compressor. CONSTITUTION:When a main shaft 13 of a compressor is driven, a driving plate 14 and a swash plate 12 are rotated, and a piston support 21 is oscillated. A piston 31 is thus reciprocated in a cylinder, and a refrigerant is run into a suction port 301. In the case that a compressor capacity is varied from a maximum to minimum, a swash plate sleeve 15 is slid and a tilting angle of the swash plate 12 is gradually decreased. A support sleeve 25 engaged with the swash plate sleeve 15 through a roll bearing 29 is moved by means of a sliding pin 30 and a recession 251 of the support sleeve 25. An end 252 of the support sleeve 25 on the side of a cylinder head 4 is abutted against an end 202 of a bearing housing 201 of a cylinder block 2.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a variable capacity compressor used in automobile air conditioners and the like, and particularly relates to a method for regulating the minimum capacity of a compressor.

[Conventional technology]

Regarding the method of regulating the minimum capacity of conventional variable capacity compressors for automobile air conditioning, for example, it is described in Service Bulletin R32, E6 Air Conditioning Edition, pages E-45 to E-47, published by Nissan Motor Co., Ltd. in May 1999. There are examples where In this example, the movement of the hinge ball that moves along the drive shaft as the compressor capacity changes is regulated. In other words,
When the compressor capacity decreases, the hinge ball slides on the drive shaft toward the piston, and its minimum capacity is regulated by a retaining ring via a stroking spring. Further, a structure is disclosed in which a thrust bearing is installed at the end of the drive shaft of the compressor on the piston side.

[Problem to be solved by the invention]

In the above conventional technology, when the capacity of the compressor is controlled to decrease, a thrust load (or thrust force) is applied to the drive shaft in the direction from the drive hub to the piston.
acts. Therefore, a thrust bearing was required to receive this thrust load at the piston side end of the drive shaft.

An object of the present invention is to prevent thrust loads from being applied to the drive shaft when controlling the capacity of a variable capacity compressor.
This eliminates the need for thrust bearings.

[Means to solve the problem]

The above-mentioned problem has a variable capacity that includes a stationary member, a piston that reciprocates within the stationary member, and a swinging member that drives the piston, and that the swinging member is movable in the reciprocating direction of the piston. In the compressor, this is achieved by defining at least one limit of movement of the swinging member by contact between the swinging member and the stationary member.

The above-mentioned problem also includes a stationary member, a piston that reciprocates within the stationary member, and a swinging member that drives the piston, the swinging member being movable in the reciprocating direction of the piston. In the capacity compressor, this is achieved by defining at least one limit of movement of the swinging member by contact between the swinging member and the stationary member via an intermediate member.

The above problem also includes a stationary member, a piston that reciprocates within the stationary member, and a swinging member that drives the piston.
a rotating member driven by a main shaft for swinging the swinging member; a first support portion supporting the swinging member with a variable swing angle; In the variable capacity compressor, the swinging member is movable in the reciprocating direction of the piston, and at least one limit of movement of the swinging member is set by the swinging member. This is achieved by defining contact between the stationary member and the stationary member via an intermediate member.

The above problem also includes a stationary member, a piston that reciprocates within the stationary member, and a swinging member that drives the piston.
a rotating member driven by a main shaft for swinging the swinging member; a first support portion supporting the swinging member with a variable swing angle; in a variable displacement compressor, in which the swinging member is movable in the reciprocating direction of the piston, and at least one limit of movement of the swinging member is set to This is achieved by defining contact between the support part and the stationary member.

The above issues are also the same. a stationary member, a piston that reciprocates within the stationary member, and a swinging member that immediately moves the piston;
a rotating member driven by a main shaft for swinging the swinging member; a first support portion supporting the swinging member with a variable swing angle; In the variable displacement compressor, the swinging member is movable in the reciprocating direction of the piston, and the swinging member is movable in the reciprocating direction of the piston. This is achieved by defining contact between the support part and the stationary member.

The above problem also includes a stationary member, a piston that reciprocates within the stationary member, and a swinging member that drives the piston.
a rotating member driven by a main shaft for swinging the swinging member; a first support portion supporting the swinging member with a variable swing angle; in a variable displacement compressor, in which the swinging member is movable in the reciprocating direction of the piston, and at least one limit of movement of the swinging member is set to This is achieved by defining contact between the support part and the stationary member via an intermediate member.

The above problem also includes a stationary member, a piston that reciprocates within the stationary member, and a swinging member that drives the piston.
a rotating member driven by a main shaft for swinging the swinging member; a first support portion supporting the swinging member with a variable swing angle; In the variable displacement compressor, the swinging member is movable in the reciprocating direction of the piston, and the swinging member is movable in the reciprocating direction of the piston. This is achieved by defining contact between the support part and the stationary member via an intermediate member.

The above object is also achieved by the variable displacement compressor according to any one of claims 2 and 3, wherein the contact surface of the intermediate member with the swinging member is spherical.

The above issues are also the same. Claim 2, wherein the intermediate member is replaceable.
, 3, 6.7.

The above problem is further addressed by the swinging member at the contact position.

This is also achieved by the variable displacement compressor according to any one of claims 1 to 9, wherein a spring is attached to at least one of the intermediate member, the stationary member, and the first support portion.

[Effect]

When controlling the capacity of a variable capacity compressor, a swinging member including a piston support for moving a piston moves in the direction of the main axis while changing its inclination with respect to the main axis. Therefore, the movement of the swinging member in the main axis direction, that is, in the piston reciprocating direction, is
Limiting the contact of the stationary member 1, for example with the cylinder block, either directly or via an intermediate member, then defines the minimum capacity of the compressor. As a result, the thrust generated due to capacity control is transmitted from the swinging member to the stationary member, and the thrust load acting on the main shaft is eliminated.

〔Example〕

A first embodiment of the present invention will be described below with reference to FIGS. 1 to 6. Figures 1 and 2 show the overall structure of the variable displacement compressor of this embodiment. Figure 1 shows the state where the piston stroke is at its maximum, that is, the swash plate tilt angle is at its maximum. FIG. 2 shows a state where the swash plate tilt angle is at its minimum. Figure 3 shows ■-■ in Figure 2.
FIG. 4 to 6 are a front view and a sectional view showing the swash plate assembly, and FIGS. 5 and 6 are
-V line and VI-VI line sectional views.

The housing consists of a front housing 1 and a cylinder block 2. That is, a bowl-shaped front housing 1 is concentrically installed and fixed on one end side of a cylindrical cylinder block 2. A main shaft 13 is rotatably supported on the center line of the cylinder block 2 and the front housing 1 via radial needle roller bearings 18, 19. Inside the front housing 1 is a swash plate 12
It forms a diagonal chamber 10 containing a built-in. cylinder block 2
Inside, a plurality of cylinders 33 are arranged circumferentially around the main shaft 13 and parallel to the axis of the main shaft 13. The radial needle roller bearing 18 is housed in a bearing housing 201 disposed on the centerline of the cylinder block 2.

The portion where the main shaft 13 passes through the front housing 1 is supported by the radial needle roller bearing 19, and the drive plate 14 is press-fitted, pinned, or plastically connected at a position adjacent to the radial needle roller bearing 19 on the main shaft 13.
is fixed and rotates together with the main shaft 13. This drive plate 14 is formed with an ear portion 141.
41 is provided with a spherical seat 142. The hemispherical shoe 16 is rotatably fitted into the spherical seat 142.

Furthermore, the ears 141 of the drive plate 14 and the ears 121 (see FIG. 4) of the swash plate 12 have a structure in which their side surfaces contact each other and do not separate from each other. As a result, rotation of the main shaft 13 applies rotational force from the lug 141 on the drive plate 14 to the swash plate lug 121, and the swash plate 1
2 rotates.

A swash plate sleeve 15 is incorporated into the main shaft 13 at a position adjacent to the drive plate 14 so as to be slidable in the axial direction with respect to the main shaft 13, and the swash plate 12 is attached to the swash plate plug. 122 and swash plate sleeve pin 17 to be tiltably connected to the main body 013. That is, the swash plate 12 is rotatably fastened to the swash plate sleeve 15 by the swash plate sleeve pin ↓7 around the swash plate sleeve pin 17. Therefore, the rotation of the main shaft 13 causes the drive plate 14 to rotate, and at the same time the swash plate 1
2. The swash plate sleeve 15 rotates together.

An annular piston support 21 is adjacent to the surface of the swash plate 12 on the cylinder block 2 side via a thrust bearing 80 . On the inner circumferential side of the piston support 21, there is a third
As shown in the figure, an outer ring 22 is inserted, and an inner ring 23 is further arranged inside the outer ring 22, and these members are connected by a support sleeve pin (1) 24 to form a swinging member. are doing. The support sleeve pin (1) 24 has a cylindrical cross section at the portion that contacts the inner ring 23 and the outer ring 22, but the portion where it connects to the piston support 21 has a width across flats parallel to the axial direction of the main shaft 13. The support sleeve pin (1) 24 is prevented from rotating around the axis between the piston support 21 and the outer ring 22. A rolling bearing 29 is provided on the outer periphery of the swash plate sleeve 15.
A support sleeve 25 is fitted through the inner ring 23 and the support sleeve 25 through the support sleeve pin (1) 26.
It is fastened at a position shifted by 90 degrees in the circumferential direction from position 4. Therefore, the outer ring 22, the inner ring 23, and the support sleeve 25 constitute a universal joint with the support sleeve pin (1) 24 and the support sleeve pin (2) 26.

Piston support 21 and swash plate 1 configured as above
2 are rotatably engaged with each other by a swash plate sleeve 15 and a support sleeve 25. That is, the swash plate sleeve 15 is mechanically coupled to the support sleeve 25 via the elastic body 27 and the spring support bearing 28, and a rolling pair is formed between the two by the rolling bearing 29. The elastic body 27 includes the swash plate 12 and the swash plate sleeve 15. This is for applying preload between the swash plate 12 and the piston support 21. The swash plate 12 and the swash plate sleeve 15 exert a force that presses the swash plate sleeve 15 rightward in FIG. 1 due to the elastic force of the elastic body 27, and as shown in FIG. plug 122
As a result, the swash plate 12 and the swash plate sleeve 15 do not separate from each other, and the swash plate 12 makes a tilting movement about the swash plate sleeve pin 17. conduct. On the other hand, in the swash plate 12 and the piston support 21, a force is generated by the elastic body 27 that pushes the support sleeve 25 to the left. The elastic force acts in the order of support sleeve 25 → support sleeve pin (2) 26 → inner ring 23 → support sleeve pin (1) 24 → outer ring → piston support 21, and as a result, moves piston support 21 to the left, that is, to the swash plate. 21 side, and prevents the piston support 21 from separating from the swash plate 12. Further, a thrust bearing 80 is provided between the swash plate 12 and the piston support 21,
This facilitates rotation of the swash plate 12.

A recessed portion 25 is formed in the outer peripheral surface of the support sleeve 25 in the axial direction.
1 is formed, and the recessed portion 251 is slidable in the axial direction on a slide pin 30 fixed to the bearing housing 201 of the cylinder block 2. This allows the support sleeve pin (1) to be attached to the support sleeve 25 (
2), movement around the axis is restricted so that the piston support 21 coupled to the piston support 21 does not rotate around the main axis 13. One end of a plurality of connecting rods 32 having balls 321 and 322 at both ends is rotatably attached to the surface of the piston support 21 on the cylinder block 2 side, and the other end is attached to the center of the ball 322. A piston 31 is rotatably mounted around the piston.

The plurality of pistons 31 are assembled into a plurality of cylinders 33 provided in the cylinder block 2. piston 3
1 has piston rings 34 and 35 attached thereto.

Further, a suction valve plate 5, a cylinder head 4, a discharge valve plate 6, a packing 7, and a rear cover 3 are arranged in the cylinder block 2, and are arranged so as to surround the drive plate 14, the swash plate 12, the piston support 21, etc. The front housing 1 is integrally fixed to the rear cover 3 with bolts (not shown) or the like. The front housing 1 and the cylinder block 2 are kept airtight by an O-ring 38, and the rear cover 3 and the cylinder block 2 are kept airtight by an O-ring 39.

The rear cover 3 is provided with an inlet 301 and an outlet (not shown). This suction port 301 is connected to a suction passage 302, and connected to the suction chamber 8 via a control valve 400. The suction chamber 8 and the discharge chamber 9 communicate with a suction port 401 and a discharge port 402, respectively, via a suction valve plate 5 and a discharge valve plate 6, respectively. These suction ports 401 and discharge ports 402 are provided in the cylinder head 4 in correspondence with the cylinders 33, respectively.

The upstream side of the control valve 400 and the swash plate chamber 10 in the front housing 1 are connected to the rear cover 3. Stop pin 75 and main shaft 1
They communicate through a communication path (not shown) provided in the center of the two parts, and have the same pressure. In addition, the control valve 400
The downstream side thereof communicates with the suction chamber 8 .

The thrust force (axial force) that acts on the main shaft 13 when compressing gas passes through the drive plate 14 and is supported by a thrust bearing 42 installed between the drive plate 14 and the front housing 1. The thrust race on the front housing l side of the thrust bearing 42 has a spherical shape. The radial force (force in the radial direction) acting on the main shaft 13 is supported by two radial needle roller bearings 19 and 18 provided in the front housing 1 and the bearing housing 20 of the cylinder block 2.

With the configuration described above, when the main shaft 13 of the compressor is driven by the engine (not shown), the drive plate 14 and the swash plate 12 rotate, and the piston support 21 oscillates with respect to the rotation axis of the main shaft 13. Perform dynamic exercise. This rocking motion causes the piston 31 to reciprocate within the cylinder, and the refrigerant returned from the refrigeration cycle (not shown) is transferred to the suction port 3.
01, the control valve 400 is controlled (depressurized) to an appropriate pressure, and the rear cover 3
is introduced into a suction chamber 8 formed within. The refrigerant introduced into the suction chamber 8 is passed through the suction boat 401 of the cylinder head 4,
Via the suction valve plate 5.

It flows into the cylinder 33 and completes the suction stroke.

The refrigerant compressed by the piston 31 is delivered to the discharge port 4o2. After passing through Toroben board 6.

The liquid is discharged into a bath chamber 9 formed in the rear cover 3, and sent out from a discharge port (not shown) to a refrigeration cycle (not shown).

Capacity control of the compressor is performed by adjusting the differential pressure between the suction chamber 8 and the swash plate chamber 10, that is, the differential pressure between both sides of the piston 31, using a control valve 400 to control the pressure difference between each piston 31 and the connecting rod 32.
This is done by controlling the tilting moment of the swash plate 12 by changing the position and magnitude of the resultant force acting on the piston support 21 via the piston support 21 .

Next, a structure for regulating the minimum capacity of the compressor will be explained using FIGS. 7 and 8. Figure 7 is I-1 in Figure 1.
FIG. 8 is a cross-sectional view taken along the line ■--■ in FIG. 7, and shows a state in which the compressor capacity is decreasing. As described above, the slide pins 30 are fixed to the bearing housing 201 of the cylinder block 2 at two locations symmetrically with respect to the main shaft 13. On the other hand, support sleeves 2 are arranged so as to correspond to the slide pins 30, respectively.
A recessed portion 251 is formed in the outer peripheral surface of 5 in the axial direction.

Therefore, the engagement between the recessed portion 251 and the slide pin 30 prevents the support sleeve 25 from rotating around the axis of the main shaft 13. By preventing the support sleeve 25 from rotating around the main shaft 13, the piston support 21 is prevented from rotating around the shaft, and as the swash plate 12 rotates, the piston support 21 swings.

When the compressor capacity changes from the maximum to the minimum, the swash plate sleeve 15 slides from the left to the right in the eighth position, and the inclination angle of the swash plate 12 (swash plate tilt angle) gradually decreases. . The support sleeve 25 is engaged with the swash plate sleeve 15 by a rolling bearing 29, and together with the swash plate sleeve 15, the slide pin 30 and the recess 2 of the support sleeve 25 are connected to each other.
51 to move from left to right in the axial direction. Then (see Fig. 2), the cylinder head 4 of the support sleeve 25
Side end 252 and bearing housing 2 of cylinder block 2
When the ends 202 of 01 come into contact, the capacity of the compressor does not decrease any further, and as a result, the minimum capacity of the compressor is defined in this state.

At this time, the support sleeve 25 is attached to the cylinder block 2.
However, the swash plate sleeve 15 is free from the main shaft 13. Therefore, when the capacity is controlled to the minimum capacity side, the thrust force generated in the main shaft 13 in the direction from left to right in FIG. 8 becomes zero. That is, the thrust bearing conventionally installed at the right end of the main shaft 13 can be eliminated.

FIG. 9 is a partial sectional view showing another embodiment of the present invention. In this embodiment, the end 2 of the support sleeve 25
52 and the bearing housing end 202 of the cylinder block 2
A spring 50, which is an elastic body, is installed between the support sleeve 25 and the bearing housing. Alternatively, although not shown, a spring may be fixed to the neck portion 253 of the support sleeve 25, and the spring may be brought into contact with the cylinder block 2 and the slide pin 30. That is, the purpose is to install a spring between the support sleeve 25 and the cylinder block 2.

According to this embodiment, in addition to the effects of the embodiment described above,
It is possible to reduce the impact when the support sleeve 25 and cylinder block 2 come into contact at the minimum capacity, and when the capacity increases from the minimum capacity state, the spring force acts as an assist force, so the control It has the effect of improving sexual performance.

FIG. 10 shows a partially enlarged sectional view of another embodiment of the invention.

In this embodiment, the minimum capacity is regulated by the outer ring 26 and the cylinder block 2. Although not shown in Fig. 10, the length of the connecting rod is increased and the piston support 2
The space between the cylinder block 1 and the cylinder block 2 is expanded, and an annular tilting regulating floor 60 is provided as an intermediate member in the space. Although the tilting regulating floor 60 is fixed to the cylinder block 2, it is natural to prevent the tilting regulating floor 6o from interfering with the piston 31 when the piston 31 reaches the bottom dead center position. For example, the end of the cylinder block 2 on the swash plate chamber lo side may be extended so that the piston 31 does not protrude from the cylinder 33 even when the piston 31 reaches the bottom dead center position.

With the above configuration, when the compressor capacity becomes minimum, the outer ring 26 and the tilting restriction floor 60 come into contact at point A. This point A moves as the main shaft 13 rotates because the tilting restriction floor 6o is a flat surface, and returns to the original position when the main shaft 13 rotates once. At this time, a space exists between the tip end 252 of the support sleeve 25 and the bearing housing end 202 of the cylinder block 2, and the two do not come into direct contact with each other. Further, the minimum capacity of the compressor can be easily changed by changing the thickness of the tilting restriction bed 60. In this embodiment, the contact surface of the tilting regulating floor 6o with the outer ring 26 is a flat surface, but the present invention is not limited to this. For example, if the contact surfaces are mutually spherical, the contact state can be further improved. be able to.

As described above, according to this embodiment, since the tilting point can be controlled at a location with a large outer diameter, a stable contact state can be maintained, and the compressor can be easily adjusted by simply changing the thickness of the tilting regulating bed. You can change the minimum capacity.

All of the embodiments described above have described means and methods for regulating the minimum capacity position of the compressor by bringing the cylinder block, which is a stationary member, into contact with the piston support via an intermediate member.

FIG. 11 is a partially enlarged sectional view showing another embodiment of the present invention, in which the piston support is brought into direct contact with a stationary member to regulate the minimum capacity position.

By the method described above, a space is created between the piston support 21 and the end of the swash plate chamber LO side of the cylinder block 2, and the tilting restriction floor 60, which is an intermediate member, is fixed to the cylinder block 2 using the space.

A straw is attached to the support sleeve 25 via a retaining ring 62.
A king spring 61 is installed.

With the above configuration, when the swash plate tilting angle decreases, the stroking spring 61 first comes into contact with the cylinder block 2 and the slide pin 30, resisting the spring force of the stroking spring 61. When the support sleeve 25 further slides to the right and reaches the minimum capacity, the piston support 21 and the tilting restriction floor 60 come into contact.

The contact point between the piston support 21 and the tilting restriction floor 60 moves with the rotation of the main shaft, as described above. In this embodiment, the seat surface of the tilt control floor 60 is a flat surface, but it may be a spherical surface.

According to this embodiment, since the movement of the piston support can be directly regulated, it is possible to reliably determine the minimum capacity position, and furthermore, since the tilting can be regulated at a location with a large outer diameter, stability is excellent. There are effects such as

A similar effect can be obtained by interposing the stroke spring between the tilting regulating floor 60 and the piston support or the outer ring 21.

All of the embodiments described above are variable capacity compressors in which the swash plate tilting angle is changed by lowering the pressure at the cylinder suction port below the pressure in the swash plate chamber using a control valve while keeping the pressure in the swash plate chamber constant. I followed him, but the special public
As disclosed in Japanese Patent Application No. 95, etc., a variable capacity type is used in which the pressure at the cylinder inlet is kept constant and the pressure in the swash plate chamber is increased by using blow-by gas, discharge gas, etc., and the swash plate tilt angle is controlled. A similar effect can be obtained with a compressor.

FIG. 12 shows an example in which the present invention is applied to a conventional variable displacement compressor.

A sleeve 15 is incorporated into the main shaft 13 so as to be slidable in the axial direction with respect to the main shaft. This sleeve 15 and swash plate 1
2 is connected to the sleeve 15 by a sleeve pin 17.
In contrast, the swash plate 12 is rotatably engaged around the sleeve pin 17. At this time, when the sleeve 15 slides to the right in the figure, the inclination of the swash plate 12 becomes smaller. Further, a drive plate 14 is fixed to the main shaft 13 by press fitting, pins, or plastic coupling, and an ear portion 141 is formed on this drive plate 14, and a cam groove 142 is provided in this ear portion 141. Cam groove 142
A pivot pin 16 on the swash plate side is movably mounted inside. Furthermore, the lug portion 141 of the drive plate 14 and the swash plate lug shaft 121 have a structure such that their sides are in contact with each other. As a result, the rotation of the main shaft 13 causes the drive plate 14, swash plate 12, and sleeve 15 to rotate together.

A piston support 21 is held in contact with the swash plate 12 via a ball bearing 51. The ball bearing 51 is preloaded by a retaining ring 52 and is fixed to the nose of the swash plate.

The piston support 21 is provided with a rotation prevention mechanism consisting of a support pin 211, a slide ball 212, and a slide shoe 213, and this rotation prevention mechanism restricts movement around the axis so that the piston support 21 does not rotate around the main shaft 13. Ru.

In other words, the piston support 21 of the ball bearing 51
The outer ring on the side does not rotate and can be seen as part of the swinging member.

With the configuration described above, when the main shaft 13 rotates, the drive plate 14 and the swash plate 12 rotate, the histone support 21 performs a swinging motion, and the piston 31 reciprocates within the cylinder 33.

At the end of the cylinder block 2 on the swash plate chamber 10 side.

A tilting restriction floor 60 is fixed as an intermediate member.

Needless to say, this tilting regulating floor 60
It is installed so as not to interfere with the piston 31 when the piston reaches the bottom dead center position.

With the above configuration, when the compressor operates to reduce its capacity, the sleeve 15 moves on the main shaft 13 in the right direction in the figure, and the tilting angle of the swash plate 12 and the piston support 21 becomes small. Become. The minimum capacity position is determined by the piston support side (outer ring) of the ball bearing 51 coming into contact with the tilting regulation floor 60.

In this embodiment, the tilt restriction floor 6o is in contact with a part of the ball bearing, but the present invention is not limited to this, and the piston support may be brought into contact with the tilt restriction bed 60. Alternatively, a spring may be inserted between a swinging member such as a piston support and a tilting restriction floor.

〔Effect of the invention〕

According to the present invention, the minimum capacity position of the compressor can be regulated by bringing the swinging member into contact with the stationary member in the axial direction directly or via an intermediate member without intervening the main shaft. The thrust load acting on the main shaft can be reduced to zero, and the thrust bearing installed at the rear end of the main shaft can be eliminated.

[Brief explanation of drawings]

1 and 2 are longitudinal sectional views of a variable capacity compressor showing one embodiment of the present invention, and FIG. 1 shows the maximum capacity state,
FIG. 2 is a diagram showing the minimum capacity state, FIG. 3 is a sectional view taken along the line ■-■ in FIG. 2, FIG. 4 is a front view showing the swash plate assembly of the present invention, and FIGS. are the respective ■-V in Figure 4.
7 is a sectional view taken along line II and VI-Vl of FIG. 1, FIG. 8 is a sectional view taken along line ■-■ of FIG. FIG. 10 is a partially enlarged sectional view showing another embodiment of the present invention, FIG. 11 is a partially enlarged sectional view showing another embodiment of the present invention, and FIG. 12 is a partially enlarged sectional view showing another embodiment of the present invention. It is a longitudinal section showing still another example. 2... Stationary member (cylinder block), 12... Rotating member (swash plate), 13... Main shaft, 14... Drive plate, 15... Second support part (swash plate sleeve),
17... Swash plate sleeve pin, 21... Rocking member (piston support), 22... Outer ring, 23... Inner ring,
24... Support sleeve pin (1), 25... First support part (support sleeve), 26... Support sleeve pin (2), 30... Slide pin, 31...
... Piston, 33... Cylinder, 5o... Elastic body (spring), 60... Intermediate member (tilt regulating seat), 61...
- Stroking spring.

Claims (1)

[Claims] 1. A stationary member, a piston that reciprocates within the stationary member, and a swinging member that drives the piston, the swinging member being movable in the reciprocating direction of the piston. A variable displacement compressor, wherein at least one limit of movement of the swinging member is defined by contact between the swinging member and the stationary member. 2. A variable capacity compressor comprising a stationary member, a piston that reciprocates within the stationary member, and a swinging member that drives the piston, wherein the swinging member is movable in the reciprocating direction of the piston. A variable capacity compressor, wherein at least one limit of movement of the swinging member is defined by contact between the swinging member and the stationary member via an intermediate member. 3. A stationary member, a piston that reciprocates within the stationary member, a swinging member that drives the piston, a rotating member driven by a main shaft for swinging the swinging member, and the swinging member. a first support part that supports the rotary member in a variable swing angle, and a second support part that supports the rotary member in a variable tilt angle with respect to the main axis, and the swing member is arranged in the reciprocating direction of the piston. A variable capacity compressor that is movable, wherein at least one limit of movement of the swinging member is defined by contact between the swinging member and the stationary member via an intermediate member. compressor. 4. A stationary member, a piston that reciprocates within the stationary member, a swinging member that drives the piston, a rotating member driven by a main shaft for swinging the swinging member, and the swinging member. a first support part that supports the rotary member in a variable swing angle, and a second support part that supports the rotary member in a variable tilt angle with respect to the main axis, and the swing member is arranged in the reciprocating direction of the piston. A variable displacement compressor that is movable, wherein at least one limit of movement of the swinging member is defined by contact between the first support portion and the stationary member. 5. A stationary member, a piston that reciprocates within the stationary member, a swinging member that drives the piston, a rotating member driven by a main shaft for swinging the swinging member, and the swinging member. a first support part that supports the rotary member in a variable swing angle, and a second support part that supports the rotary member in a variable tilt angle with respect to the main axis, and the swing member is arranged in the reciprocating direction of the piston. A variable displacement compressor that is movable, wherein at least one limit of movement of the swinging member is defined by contact between the second support portion and the stationary member. 6. A stationary member, a piston that reciprocates within the stationary member, a swinging member that drives the piston, a rotating member driven by a main shaft for swinging the swinging member, and the swinging member. a first support part that supports the rotary member in a variable swing angle, and a second support part that supports the rotary member in a variable tilt angle with respect to the main axis, and the swing member is arranged in the reciprocating direction of the piston. In a movable variable displacement compressor, at least one limit of movement of the swinging member is defined by contact between the first support portion and the stationary member via an intermediate member. Variable displacement compressor. 7. A stationary member, a piston that reciprocates within the stationary member, a swinging member that drives the piston, a rotating member driven by a main shaft for swinging the swinging member, and the swinging member. a first support part that supports the rotary member in a variable swing angle, and a second support part that supports the rotary member in a variable tilt angle with respect to the main axis, and the swing member is arranged in the reciprocating direction of the piston. In a movable variable capacity compressor, at least one limit of movement of the swinging member is defined by contact between the second support portion and the stationary member via an intermediate member. Variable displacement compressor. 8. The variable displacement compressor according to claim 2 or 3, wherein the contact surface of the intermediate member with the swinging member has a spherical surface. 9. The variable displacement compressor according to any one of claims 2, 3, 6, and 7, wherein the intermediate member is replaceable. 10. Swinging member at contact position, intermediate member, stationary member, first
8. The variable displacement compressor according to claim 1, wherein a spring is attached to at least one of the supporting parts.