JP2003129951A - Variable displacement compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To inexpensively manufacture a detent mechanism of an oscillation plate constituted by a constant velocity universal joint and having a simple structure in an oscillation plate type variable displacement compressor. SOLUTION: A plurality of guide grooves 6a are formed directly on a ball- shaped outer peripheral face of the oscillation plate 6 driving a piston 8. A plurality of guide grooves 1a parallel with a drive shaft 4 are formed directly on an inner face of a housing 1 corresponding to the guide grooves 6a. One steel ball 15 is inserted between the guide grooves 1a and 6a, respectively, to constitute the constant velocity universal joint by arranging the centers of all the steel balls 15 on the same plane by a retainer 17. Consequently, when a drive plate 5 rotates together with the drive shaft 4, the movement performed by the oscillation plate 6 becomes pure oscillation movement and does not include components of reciprocating rotary movement at all, thereby causing no vibration and noise. Since the detent mechanism is formed in an outer peripheral part of the oscillation plate 6 in this way, it is unnecessary to provide a complicated structural part in a central part.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a variable capacity compressor mainly used for compressing an arbitrary amount of refrigerant in an air conditioner, and in particular, it includes a rocking plate inclined with respect to a drive shaft. A plurality of pistons are reciprocated by the oscillating plate, and the inclination angle of the oscillating plate can be changed steplessly in order to change the discharge capacity. "Plate type variable capacity compressor".

[0002]

2. Description of the Related Art In a conventional oscillating plate type variable displacement compressor, as an anti-rotation mechanism for preventing rotation of the oscillating plate, for example, as described in Japanese Patent No. A fork-shaped holding portion protruding in a radial direction from one location is slidably engaged with one guide rail mounted on the inner surface of the casing so as to be parallel to the drive shaft. It is commonly used. However, when this type of detent mechanism is used, the motion of the oscillating plate does not become a pure oscillating motion that does not include any rotational direction component, and in addition to the oscillating motion, a reciprocating rotary motion of a minute angle is also possible. A certain rotational vibration occurs. When the drive shaft rotates at a high speed, this rotational vibration may increase the load of sliding parts such as the engaging part of the holding part and the guide rail of the rotation stop mechanism, or increase the vibration of the entire compressor. Undesired problems occur.

This is because the anti-rotation mechanism described above does not have so-called "constant speed", and in the universal joint mechanism that does not have constant speed like the well-known hook joint, the input If the output shaft is tilted with respect to the input shaft even if the rotary motion of constant speed is applied to the shaft, the rotary motion of constant speed does not appear on the output shaft, and the rotary motion of which the rotary speed fluctuates is taken out. For the same reason. This problem is an obstacle to realizing a high degree of quietness and reliability, or a reduction in size and weight, which has been particularly needed in recent years in refrigerant compressors for vehicles and the like.

On the other hand, paying attention to this problem, as described in, for example, Japanese Patent Laid-Open No. 5-133425, as a detent mechanism for connecting a rocking plate and a compressor housing,
The so-called "constant speed universal joint" is used to allow only pure oscillating motion of the oscillating plate and prevent the generation of reciprocating rotational motion components, which results from the non-uniform speed of the detent mechanism as described above. Attempts have been made to eliminate the problem, but in this improvement plan, a constant velocity universal joint mechanism is provided in the central portion of the oscillating plate, whereby the oscillating plate and the compressor housing, which is a detent member, are connected. It is connected. This constant velocity universal joint mechanism is provided on the outer periphery of the drive shaft, is rotatable and axially slidable with respect to the drive shaft, and has a guide groove for a plurality of balls on its outer periphery. Since the support sleeve is included, another problem arises in that the drive shaft has a double structure, the structure of the compressor is complicated, the body size is increased, and the manufacturing cost is increased.

Further, such a detent mechanism is provided with a CO
Considering the case where ₂ is applied to a compressor that uses refrigerant, the torque applied to the drive shaft generally increases as compared to a compressor that uses freon as a refrigerant, and accordingly, it adds to the rotation stop mechanism of the swaying plate. The load also increases. In this case, it is advantageous that the load receiving portion of the detent becomes smaller toward the outside of the center of the drive shaft because the load becomes smaller. However, the detent mechanism arranged at the center of the oscillating plate is a compressor. Due to the limitation of the physique, it is necessary to dispose in a space of a limited size inside the rocking plate, which imposes an unfavorable condition as a mechanism for receiving a high load.

[0006]

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems in the prior art, and an object thereof is to solve those problems by a novel means.

[0007]

As a means for solving this problem, the present invention provides an oscillating plate type variable displacement compressor as set forth in claim 1 of the appended claims.

In the oscillating plate type variable displacement compressor of the present invention, a constant velocity universal joint for connecting the oscillating plate to the housing side is provided on the outer peripheral portion of the oscillating plate in order to prevent rotation of the oscillating plate. Since the anti-rotation mechanism is provided, the oscillating plate makes only a pure oscillating motion that does not include a component of reciprocating rotational motion. Therefore, it is possible to reliably prevent the generation of vibration, noise, and the like from the detent mechanism and the compressor as a whole. Further, this detent mechanism has a simple structure and does not require a complicated structure in the central portion of the rocking plate, and is configured only on the outer peripheral portion of the rocking plate, so that it is easy to manufacture. As a result, the cost is not increased and the thickness in the radial direction can be reduced, so that the entire compressor including the rotation stopping mechanism can be downsized. Further, since the rocker plate side and the housing side guide grooves are engaged with each other through the steel balls, friction is reduced, sliding is performed smoothly, and power loss can be suppressed to a low level.

More specifically, in the oscillating plate type variable displacement compressor according to claim 2, the inner surface of the housing is formed into a cylindrical shape, and a plurality of guide grooves parallel to the drive shaft are formed in the inner surface of the housing. Make the outer peripheral surface of the corresponding oscillating plate spherical, and also form the same number of guide grooves in it, insert steel balls between these guide grooves, and use the retainers to center all the steel balls on the same plane. By arranging a mechanism similar to a "double offset type" constant velocity universal joint on the outer periphery of the oscillating plate, the number of parts is reduced, the structure is simplified, and the physique is made smaller. The cost can be reduced while making it easy.

In this case, the annular retainer has a spherical outer peripheral surface capable of sliding in contact with the cylindrical inner surface of the housing, and a spherical outer peripheral surface capable of sliding contact with the spherical outer peripheral surface of the oscillating plate. By providing the inner peripheral surface of the retainer, the retainer can be always in line contact with the inner surface of the housing by the spherical outer peripheral surface, and can be in sliding contact with the outer peripheral surface of the oscillating plate by the spherical inner peripheral surface. Smooth sliding occurs in the area of without a large gap. Therefore, the possibility that vibration and noise will be generated from the detent mechanism is also reduced in this respect.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The accompanying drawings show a preferred embodiment of an oscillating plate type variable displacement compressor of the present invention. In FIG. 1, which shows a vertical cross-sectional structure of the entire compressor in an operating state that provides the maximum discharge capacity, 1 is a front housing that is a part of the outer shell of the compressor, and 2 is provided so as to be inserted into the front housing 1. 2 shows a middle housing as a closed cylinder block. Middle housing 2
In the inside of, in the horizontal direction in FIG.
A plurality of (for example, five) cylinder bores 21 are formed substantially uniformly around the center line. A rear housing 3 is integrated with the front housing 1 and the middle housing 2 by fastening means such as through bolts (not shown). A suction chamber 31 as a space is formed in the outer peripheral portion inside the rear housing 3, and
A discharge chamber 32 as a space is formed in the central portion.

Reference numeral 4 is a drive shaft for receiving rotational power from an external power source, and a disc portion 4a is integrally formed so as to be orthogonal to it. Two arms 41 are formed in parallel with each other at a predetermined distance from a part of the outer circumference of the disk portion 4a so as to project in the axial direction. The drive shaft 4 is supported by the integrated front housing 1 and middle housing 2 via radial bearings 402 and 404, and is also supported by a thrust bearing 403 supporting the back surface of the disc portion 4a. The front housing 1 also supports the direction. In addition, a shaft sealing device 401 is provided on the outer side of these bearing portions.
Is provided to prevent fluid from leaking to the outside from around the drive shaft 4.

A drive plate 5 has an arm portion 5c protruding forward from a part thereof. The arm portion 5c is formed with a long hole 51 having a predetermined shape serving as a cam, and the arm pin 42 fixed to the arm 41 on the drive shaft 4 side is slidably engaged with the long hole 51. . Thereby the drive plate 5 can rotate with the drive shaft 4. A swing plate 6 that does not rotate is supported on the drive plate 5 via bearings 501 and 601.

In the illustrated embodiment, the bearing 501 is a metal surface type radial bearing,
601 is a roller type thrust bearing,
The drive plate 5 includes bearings 501 and 601,
The drive nut 5 is inserted into the recess formed in the rocking plate 6 together with the drive nut 502 which is screwed into the screw formed on the outer peripheral surface of the cylindrical portion 5b of the drive plate 5, and the circlip 602 prevents the retainer from coming off. Has been done.

The same number of spherical recesses 6a as the cylinder bores 21 are formed in the periphery of the oscillating plate 6, and the spherical end portions 71 formed at one end of the piston rods 7 of the same number are engaged therewith. is doing. The pistons 8 slidably inserted into the respective cylinder bores 21 are also formed with spherical recesses 8a, and the spherical end portions 72 formed at the other ends of the piston rods 7 are engaged with them. I am fit.

Reference numeral 9 is a valve port plate made of a thick plate, and at least one intake port 9a and at least one discharge port 9b are opened so as to penetrate through the valve port plate at positions corresponding to the respective cylinder bores 21. Each suction port 9a of the valve port plate 9 is closed from the cylinder bore 21 side by a reed valve-shaped suction valve 20 formed in each part of a suction valve plate 19 made of one thin spring steel plate. Further, each of the discharge ports 9b is formed by a reed valve-shaped discharge valve portion formed in the peripheral portion of the discharge valve plate 10 which is also made of one thin spring steel plate, and thus the discharge chamber 3 is provided.
Blocked from side 2. Discharge valve plate 10
Are simultaneously fixed when the valve retainer 11 protecting it is screwed onto the valve port plate 9. Further, when the middle housing 2 and the rear housing 3 are fastened and integrated, the valve port plate 9 and the suction valve plate 19 are sandwiched and fixed between them.

Reference numeral 13 denotes a sleeve loosely fitted to the drive shaft 4 so that it can freely slide on the drive shaft 4 in the axial direction by its center hole, and its outer shape is spherical. , This spherical outer surface is the drive plate 5 described above.
Slidably engages a cylindrical inner surface formed in the center of the cylindrical portion 5b. As shown in FIG. 5, the cylindrical portion 5b of the drive plate 5 is pivotally attached to the sleeve 13 by two sleeve pins 14 in a direction orthogonal to the drive shaft 4. Therefore, when the sleeve 13 slides on the drive shaft 4 in the axial direction, the drive plate 5 and the swing plate 6 can rotate around the sleeve pin 14. The length of each piston rod 7 is constant, and since the arm pin 42 attached to the drive shaft 4 side is engaged with the long hole 51 of the drive plate 5, the drive shaft 5 moves as the sleeve 13 moves. The tilt angles of the drive plate 5 and the oscillating plate 6 with respect to 4 change, and the strokes of all pistons 8 change at the same time by the same amount. As a result, the discharge capacity of the compressor changes continuously.

The rocking plate 6 rotates together with the drive shaft 4 and the drive plate 5 while permitting the tilting of the rocking plate 6 with respect to the drive shaft 4 and the rocking motion of the rocking plate 6 by the rotation of the drive plate 5. Must be prevented, the rocking plate 6 is provided with a rotation stopping mechanism, but as described above,
In a conventional oscillating plate type variable displacement compressor, the detent mechanism does not have a uniform speed, so the compressor may cause vibration and noise, or when a detent mechanism with a uniform speed is used. Causes the cost to rise due to the complicated mechanism,
There was a problem that the physique of the compressor became large.

In order to solve these problems, in the present invention, a detent mechanism having a constant velocity can be supplied inexpensively as a small structure which is easy to manufacture and has a simple structure.
In order to reduce friction of the sliding portion and reduce power loss, inner and outer guide grooves, a plurality of steel balls bridging them, and a retainer for holding the steel balls are provided on the outer peripheral portion of the rocking plate 6. It is characterized in that it is equipped with a detent mechanism.

More specifically, referring to the illustrated embodiment,
First, a plurality of guide grooves 1a, for example, seven guide grooves 1a are formed in parallel with the drive shaft 4 on the cylindrical inner surface of the front housing 1. Although not an essential requirement, the plurality of guide grooves 1a are evenly arranged so that the same angular interval is formed between the adjacent guide grooves 1a around the drive shaft 4, as shown in FIG. Is desirable. The cross-sectional shape of the guide groove 1a is an arc shape.

The oscillating plate 6 has a spherical portion 6b on at least a part of its outer peripheral surface, and this spherical outer peripheral surface 6b.
Corresponding to the plurality of guide grooves 1a provided on the housing side, in parallel to the central axis of the rocking plate 6, the same number of guide grooves 6a as the guide grooves 1a on the housing side, for example, seven guide grooves 6a are provided. It is formed. As shown in FIG. 5, the cross-sectional shape of the guide groove 6a is also arcuate.

Then, in order to interlock and connect between the guide groove 1a on the housing side and the corresponding guide groove 6a on the rocking plate side, one steel ball 15 is inserted. The radius of the steel balls 15 depends on the guide grooves 1a and 6a with which they engage.
The radius is slightly smaller than the radius of the arc-shaped cross section.

The number of the steel balls 15 is the same as the number of the guide grooves 1a and 6a on the housing 1 side and the rocking plate 6 side, for example, seven, so that the centers of all the steel balls 15 are substantially formed. A ring-shaped retainer 17 is used to arrange them on the same plane. As shown in FIG. 3, when the rocking plate 6 tilts with respect to an imaginary plane orthogonal to the drive shaft 4, the retainer 17 is tilted by a half angle thereof, so that the retainer 17 of the front housing 1 is tilted. A spherical outer peripheral surface 171 slidable in contact with the inner surface, a spherical inner peripheral surface 172 slidable with respect to the spherical outer peripheral surface 6b of the rocking plate 6, and the centers of all the steel balls 15 are substantially formed. The plurality of holes 173, which are circular, for example, are provided so that the steel balls 15 can be gently held so as to be aligned on the same plane.

As is clear from the above description, the radius of the inner surface of the front housing 1 is substantially the same as the radius of the spherical outer peripheral surface 171 of the retainer 17, but slightly larger than that, and the retainer 17 has a larger radius. The radius of the spherical inner peripheral surface 172 is substantially the same as the radius of the spherical outer peripheral surface 6b of the oscillating plate 6, but slightly larger than that.

Next, the operation of the oscillating plate type variable displacement compressor of the illustrated embodiment will be described. When the drive shaft 4 is rotationally driven by an external power source such as an internal combustion engine or a motor mounted on the vehicle via a belt transmission device or the like, or directly, the arm is attached to the disc portion 4a of the drive shaft 4. The drive plate 5 connected via 41, the arm pin 42, the long hole 51, the arm portion 5c and the like rotates integrally with the drive shaft 4. However, since the oscillating plate 6 is supported by the drive plate 5 via the bearings 501 and 601, the oscillating plate 6 does not rotate, and the drive plate 5 is inclined with respect to an imaginary plane orthogonal to the drive shaft 4. Only when it is in motion, the rocking motion corresponding to the tilt angle is performed. As a result, the plurality of pistons 8 connected to the swing plate 6 via the piston rods 7 reciprocate in the respective cylinder bores 21.

Among the plurality of pistons 8, the working chamber formed on the top surface of the one in the suction stroke expands to a low pressure, so that the fluid in the suction chamber 31 to be compressed, for example, the air conditioner. The refrigerant flows in by opening the suction valve 20 provided at the suction port 9a of the valve port plate 9. On the contrary, since the working chamber formed on the top surface of the piston 8 in the pumping stroke is contracted, the fluid inside thereof is compressed and becomes high pressure, and the discharge provided in the discharge port 9b of the valve port plate 9 is discharged. The valve portion of the valve plate 10 is pushed open to be discharged into the discharge chamber 32. The discharge capacity in that case is approximately proportional to the stroke length of the piston 8 determined by the tilt angles of the drive plate 5 and the oscillating plate 6.

As described above, when the tilt angles of the drive plate 5 and the oscillating plate 6 are changed, the discharge capacity of the compressor changes. Therefore, in order to control the discharge capacity, all the compressors in the illustrated embodiment are controlled. The pressure in the front housing chamber 1b, which is the back pressure of the piston 8, is changed by using a pressure control valve or the like (not shown). Normally, an intermediate pressure between the high pressure in the discharge chamber 32 and the low pressure in the suction chamber 31 is introduced from the pressure control valve into the front housing chamber 1b. For example,
When the pressure in the front housing chamber 1b, that is, the back pressure of the piston 8, is increased, the balance with the pressure in the working chamber formed on the top surface of each piston 8 is lost, so that a new balance can be obtained. The average position of the plurality of pistons 8 moves toward a position close to the valve port plate 9. At the same time, the strokes of all the pistons 8 are shortened all at once, so that the discharge capacity of the compressor is continuously reduced.

FIG. 2 shows a state in which the stroke of the piston 8 becomes substantially zero and the discharge capacity also becomes substantially zero. In this case, the pressure inside the front housing chamber 1b is maximized, and the tilt angles of the drive plate 5 and the rocking plate 6 are substantially zero (actually, the drive shaft 4).
Side arm pin 42 is the long hole 5 on the drive plate 5 side.
By touching the end of 1, the tilt angle of about several degrees remains. ), Even if the drive plate 5 rotates together with the drive shaft 4, the swing plate 6 does not swing and is substantially stationary. Therefore, all the pistons 8 are substantially at the position of the top dead center and do not reciprocate in the cylinder bore 21.

On the contrary, when a pressure control valve (not shown) is operated to reduce the pressure in the front housing chamber 1b, the back pressure acting on the piston 8 becomes small,
The strokes of all the pistons 8 are increased all at once,
The discharge capacity of the compressor increases infinitely. At this time,
The inclination angle between the drive plate 5 and the oscillating plate 6 increases, and the amplitude of the oscillating motion of the oscillating plate 6 also increases. Figure 1
The pressure in the front housing chamber 1b is minimized, the tilt angle between the drive plate 5 and the rocking plate 6 is maximized, and the stroke of the piston 8 and the discharge capacity of the compressor are maximized. There is.

Since the feature of the present invention resides in the constant speed detent mechanism provided for the oscillating plate 6, only the part of the detent mechanism in FIG. 1 showing the state of the maximum discharge capacity is enlarged. What is shown is FIG. Further, FIG. 4 is an enlarged view of only the portion of the rotation stopping mechanism in FIG. 2 showing the state in which the discharge capacity is substantially zero. Note that FIG. 5 is a cross-sectional side view corresponding to the state where the discharge capacity shown in FIG. 4 is substantially zero.

As is apparent from these drawings, in the detent mechanism of the illustrated embodiment, even if the oscillating plate 6 tries to follow the drive plate 5 and rotate together, the outer peripheral surface 6
Since the guide groove 6a formed in b is engaged with the guide groove 1a provided on the inner surface of the front housing 1 which is a stopper body via the steel ball 15, the rotational movement of the rocking plate 6 is prevented. Only the oscillating movement of the oscillating plate 6 is permitted.

This detent action has a plurality of guide grooves 1a formed on the inner surface of the front housing 1 around the drive shaft 4 in parallel therewith, and the same number of steel balls 15 which can be engaged with them. A known "double offset type" constant velocity universal joint, which is composed of the same number of guide grooves 6a formed directly on the outer peripheral surface 6b of the rocking plate 6 itself so as to be able to engage with these steel balls 15. Since it is performed by a mechanism similar to, the reciprocating rotary motion of the oscillating plate 6 is completely blocked, and no component of the rotary motion remains. Therefore, the motion of the oscillating plate 6 becomes a pure oscillating motion, and there is no fear of generating secondary vibration or noise.

Further, in this detent mechanism, it is not necessary to provide a complicated structural portion in the central portion of the rocking plate 6, and the steel ball 15 and the guide grooves 1a and 6a are provided in the outer peripheral portion of the rocking plate 6. Further, since the guide grooves 1a and 6a are formed directly on the housing 1 and a part of the swing plate 6, it is not necessary to newly provide a special part. Therefore, compared with the conventional example in which they are provided in the central portion of the oscillating plate 6, not only the compressor can be manufactured easily and it can be provided at low cost, but the number of steel balls 15 and the guide grooves 1a and 6a is increased. Since the load that each steel ball 15 bears becomes small, the diameter of the steel ball 15 can be made small and the thickness of the retainer 17 can be made thin to increase the size of the compressor by the detent mechanism. Can be avoided.

In the illustrated embodiment, a mechanism similar to a "double offset type" constant velocity universal joint is applied to a detent mechanism for the oscillating plate 6 in the oscillating plate type variable displacement compressor. Is a universal joint having constant velocity, such as the “Burfield type” which is well known as a constant velocity universal joint, and by providing the universal joint on the outer peripheral portion of the oscillating plate 6, the present invention is similarly provided. The purpose can be achieved.
However, some modifications may be required depending on the type of constant velocity universal joint.

In the illustrated embodiment, the pressure in the front housing chamber 1b is changed as a means for changing the inclination angles of the drive plate 5 and the rocking plate 6 to change the discharge capacity of the compressor. However, since the present invention is not characterized by this means,
It goes without saying that other means than the illustrated embodiments which can achieve the same purpose can be adopted.

[Brief description of drawings]

FIG. 1 is a vertical sectional front view showing a preferred embodiment of an oscillating plate type variable displacement compressor of the present invention.

FIG. 2 is a vertical sectional front view showing another operating state of the embodiment shown in FIG.

FIG. 3 is a vertical sectional front view showing an enlarged main part of FIG.

FIG. 4 is a vertical sectional front view showing an enlarged main part of FIG.

5 is a cross-sectional side view taken along the line AA shown in FIG.

[Explanation of symbols]

1 ... Front housing 1a ... Steel ball guide groove on the housing side 1b ... Front housing room 4 ... Drive shaft 5 ... Drive plate 6 ... rocking plate 6a ... Steel ball guide groove on rocker plate side 7 ... Piston rod 8 ... Piston 13 ... Sleeve 14 ... Sleeve pin 15 ... Steel ball 17 ... Retainer 21 ... Cylinder bore

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Shigeru Kamiya             1-1, Showa-cho, Kariya city, Aichi stock market             Inside the company DENSO (72) Inventor Masafumi Inoue             1-1, Showa-cho, Kariya city, Aichi stock market             Inside the company DENSO (72) Inventor Shigehide Kimura             14 Iwatani Shimohakaku-cho, Nishio-shi, Aichi Stock Association             Company Japan Auto Parts Research Institute F term (reference) 3H076 AA06 BB41 CC20 CC32 CC83

Claims (3)

[Claims] 1. A drive shaft which is supported by a housing through a bearing to receive rotational power from a power source, and a drive plate which is connected to the drive shaft and is rotatable and tiltable with respect to the drive shaft. , A rocking plate which has the same inclination angle but is prevented from rotating by being supported by the drive plate through a bearing, and a fluid which is connected to the rocking plate and reciprocates and is inserted into the cylinder bore. Detent mechanism including a piston for sucking and compressing the rocking member and a constant velocity universal joint provided on the outer peripheral portion of the rocking plate to prevent the rocking plate from rotating and connecting the rocking plate to the housing side. An oscillating plate type variable displacement compressor comprising: 2. The housing according to claim 1, wherein the housing has a cylindrical inner surface at a portion corresponding to the outer peripheral surface of the swing plate, and the outer peripheral surface of the swing plate has a spherical outer shape. The constant velocity universal joint has a plurality of guide grooves formed parallel to the drive shaft on the cylindrical inner surface of the housing itself and the spherical outer peripheral surface of the swing plate itself. A plurality of guide grooves formed corresponding to the guide grooves, steel balls mounted one by one between the corresponding guide grooves, and the center of all the steel balls being the same virtual plane An oscillating plate type variable displacement compressor, comprising an annular retainer inserted between an outer peripheral surface of the oscillating plate and an inner surface of the housing to be disposed above. 3. The spherical retainer according to claim 2, wherein the annular retainer slides on a spherical outer peripheral surface of the housing, which is slidable in contact with a cylindrical inner surface of the housing, and a spherical outer peripheral surface of the swing plate. An oscillating plate type variable displacement compressor having a spherical inner peripheral surface capable of making dynamic contact.