JPWO2005024233A1 - Variable capacity swash plate compressor - Google Patents

Abstract

A first swash plate 18 is coupled to the drive shaft 16 so as to be integrally rotatable. A single-headed piston 23 is moored to the first swash plate 18 via shoes 25A and 25B. The piston 23 is reciprocated linearly by the rotation of the first swash plate 18 accompanying the rotation of the drive shaft 16, and the refrigerant gas is compressed. An annular second swash plate 51 is supported on the first swash plate 18 via a ball bearing 52 so as to be relatively rotatable. The second swash plate 51 is slidably disposed with respect to the first swash plate 18 and the shoe 25B between the first swash plate 18 and the shoe 25B on the side receiving the compression load. The convex corners 18b and 18c of the first swash plate 18 are provided with inclined surfaces (chamfering). Therefore, the durability of the swash plate and the shoe is improved.

Description

  The present invention relates to a variable capacity swash plate type compressor that constitutes a refrigeration circuit and compresses refrigerant gas, for example.

  As shown in FIG. 9, in this type of swash plate compressor, a swash plate 92 is connected to a drive shaft 91 so as to be integrally rotatable. A single-headed piston 94 is moored on the outer peripheral portion of the swash plate 92 via a pair of hemispherical shoes 93A and 93B. Accordingly, when the swash plate 92 is rotated by the rotation of the drive shaft 91, the swash plate 92 slides with respect to the shoes 93A and 93B, and the piston 94 is reciprocated linearly to compress the refrigerant gas.

  The shoes 93 </ b> A and 93 </ b> B perform a rotational movement around its own axis S (line passing through the center of curvature P of the spherical surface and perpendicular to the sliding surface with the swash plate 92) in response to relative rotation with the swash plate 92. It will be. The rotational movement of the shoes 93A and 93B around the axis S is total in one direction around the axis S with respect to the shoes 93A and 93B due to the difference in peripheral speed at which the outer peripheral side of the inner and outer periphery of the swash plate 92 becomes larger. This is performed in a state that is synonymous with the application of the rotational force.

  That is, the swash plate compressor shown in FIG. 9 has a configuration in which the shoes 93A and 93B are slid directly with respect to the swash plate 92. Therefore, the shoes 93A and 93B have to uselessly rotate about the axis S by sliding based on relative rotation with the swash plate 92. Therefore, in particular, there is a problem that the mechanical loss at the sliding portion between the piston 94 and the shoe 93B on the side receiving the compression reaction force becomes large, and problems such as seizure occur at the sliding portion.

  In order to solve such a problem, for example, a technique as shown in FIG. 10 has been proposed [see, for example, Patent Document 1]. That is, a stepped portion 90a is provided in an annular shape at the center of the rear surface (the surface facing the right side of the drawing) of the swash plate (hereinafter referred to as the first swash plate 90). In the first swash plate 90, an annular sliding plate (hereinafter referred to as a second swash plate 95) is supported on the outer side of the stepped portion 90 a so as to be rotatable relative to the first swash plate 90 at a coaxial position. Yes. The outer peripheral portion of the second swash plate 95 is slidably disposed with respect to the first swash plate 90 and the second shoe 93B between the first swash plate 90 and the second shoe 93B.

  Therefore, when the first swash plate 90 rotates, slip occurs between the first swash plate 90 and the second swash plate 95, and the rotation speed of the second swash plate 95 is lower than the rotation speed of the first swash plate 90. Is done. Therefore, the relative rotational speed between the second swash plate 95 and the second shoe 93B is lower than the relative rotational speed between the second shoe 93B and the first swash plate 90. As a result, the rotational movement of the second shoe 93B around the axis S caused by the relative rotation between the second swash plate 95 and the second shoe 93B can be suppressed, and the above-described mechanical loss and malfunction can be prevented. Can be suppressed.

  Here, it has also been proposed that a rolling element be interposed between the first swash plate 90 and the second swash plate 95 between the first shoe 93A and the second shoe 93B [see, for example, Patent Document 2]. ]. In Patent Document 2, the race on the second shoe 93B side of the thrust bearing can be grasped as the second swash plate 95. In this way, the slip between the first swash plate 90 and the second swash plate 95 becomes good, and the relative rotational speed between the second swash plate 95 and the second shoe 93B is set to the second shoe 93B and the first shoe. The rotational speed relative to the swash plate 90 can be greatly reduced.

  However, in the swash plate structure including the first swash plate 90, the second swash plate 95, and the rolling element, the thickness between the first shoe 93A and the second shoe 93B in the swash plate structure is increased. End up. Therefore, the first swash plate 90 that is inclined with respect to the drive shaft 91 is convex on the opposite side of the second swash plate 95 at the outer peripheral edge corresponding to the vicinity of the piston 94 (state of FIG. 10) at the top dead center position. The corner portion 90b greatly protrudes in the radial direction of the drive shaft 91 (upward in the drawing). The second swash plate 95 inclined with respect to the drive shaft 91 has a convex angle opposite to the first swash plate 90 at the outer peripheral edge corresponding to the vicinity of the piston 94 (not shown) at the bottom dead center position. The portion 95b protrudes greatly in the radial direction of the drive shaft 91.

  When the convex corner portion 90b of the first swash plate 90 and the convex corner portion 95b of the second swash plate 95 project greatly in the radial direction of the drive shaft 91, the projecting portion of the piston 94 projects to avoid interference with the projecting portion. It is necessary to reduce the thickness of the part corresponding to the part or to enlarge the piston 94 in the radial direction. The reduction in the thickness of the piston 94 leads to a decrease in durability, and the increase in the size of the piston 94 leads to an increase in the size of the swash plate compressor. Therefore, in the prior art, when the thickness of the swash plate structure has to be increased, the radii of the first swash plate 90 and the second swash plate 95 are reduced, and the convex corners 90b and 95b and the piston described above are reduced. 94 to avoid interference with 94.

  However, if the radii of the first swash plate 90 and the second swash plate 95 are reduced, the second shoe 93B and the second oblique plate which receive a large compression reaction force in the piston 94 near the top dead center position (compression stroke). There is a problem that the contact area with the plate 95 becomes narrow, and the durability of the second swash plate 95 and the second shoe 93B decreases.

In recent years, it is becoming common to use carbon dioxide as a refrigerant in a refrigeration circuit. When the carbon dioxide refrigerant is used, the pressure in the refrigeration circuit is much higher than when the chlorofluorocarbon refrigerant (for example, R134a) is used. Therefore, even in the swash plate compressor, the compression reaction force acting on the piston 94 is increased, and the above-described problem (the durability of the second swash plate 95 and the second shoe 93B is reduced) has been greatly taken up. .
JP-A-8-338363 (page 4, FIG. 1) JP-A-8-28447 (page 3, FIG. 1)

  An object of the present invention is to provide a variable displacement swash plate compressor capable of improving the durability of a swash plate and a shoe while suppressing a decrease in the durability and an increase in size of a piston.

  In order to achieve the above object, according to the present invention, a swash plate is connected to a drive shaft so as to be integrally rotatable, and a piston is moored to the swash plate via a shoe, and the swash plate according to the rotation of the drive shaft. Is a variable displacement swash plate compressor in which the piston is reciprocated linearly to compress the gas and the discharge angle is changed by changing the inclination angle of the swash plate. Provided is a variable displacement swash plate compressor in which an inclined surface is provided on a part of the entire outer periphery of a plate.

  By providing an inclined surface at the protruding corner portion of the outer peripheral edge portion of the swash plate that is inclined with respect to the drive shaft, the diameter of the swash plate can be increased while suppressing a decrease in durability and an increase in size of the piston. Therefore, a large compression reaction force acting on the swash plate via the shoe can be suitably received. This leads to improved durability of the swash plate and shoe.

  In a preferred example, an inclined surface is provided at a convex corner on the opposite side of the piston at a portion corresponding to the piston at the top dead center position on the outer peripheral edge of the swash plate. That is, an inclined surface is provided at the convex corner on the opposite side of the piston at the outer peripheral edge portion of the swash plate corresponding to the circumferential range of the swash plate in which the piston is disposed at the top dead center position.

  In the swash plate inclined with respect to the drive shaft, the convex corner on the side opposite to the piston protrudes greatly in the radial direction of the drive shaft at the outer peripheral edge corresponding to the piston at the top dead center position. . Therefore, a large compression reaction force acting on the swash plate can be suitably received through the shoe of the piston near the top dead center position. This leads to improved durability of the swash plate and shoe.

  In a preferred example, an inclined surface is provided at a convex angle portion on the piston side at a portion corresponding to the piston at the bottom dead center position in the outer peripheral edge portion of the swash plate. In other words, an inclined surface is provided at the convex angle portion on the piston side at the outer peripheral edge portion of the swash plate corresponding to the circumferential range of the swash plate in which the piston is disposed at the bottom dead center position.

  In the swash plate, at the outer peripheral edge corresponding to the piston at the bottom dead center position, the convex angle portion on the piston side greatly protrudes in the radial direction of the drive shaft. Therefore, by chamfering the protruding portion of the swash plate, it is possible to increase the diameter of the first swash plate while suppressing a decrease in durability and an increase in size of the piston.

  In a preferred example, the swash plate includes a first swash plate coupled to a drive shaft so as to be integrally rotatable, and a second swash plate supported by the first swash plate. A piston is moored to the plate via a first shoe that contacts the first swash plate and a second shoe that receives the compression reaction force that contacts the second swash plate, and the first swash plate An inclined surface is provided at a convex corner on the opposite side of the second swash plate at a portion corresponding to the piston at the top dead center position on the outer peripheral edge. In other words, in the outer peripheral edge portion of the first swash plate corresponding to the circumferential range of the first swash plate in which the piston is disposed at the top dead center position, an inclined surface is formed at the convex corner on the opposite side of the first swash plate. Is provided.

  The first swash plate inclined with respect to the drive shaft has a convex corner on the opposite side of the second swash plate at the outer peripheral edge corresponding to the piston at the top dead center position, and increases in the radial direction of the drive shaft. It will protrude. Therefore, by chamfering the protruding portion of the first swash plate, the diameter of the first swash plate can be increased while suppressing a decrease in the durability and an increase in size of the piston. Accordingly, the second swash plate is preferably supported by the first swash plate, and a large compression reaction force acting on the second swash plate via the second shoe of the piston near the top dead center position is applied to the second swash plate. Through the first swash plate. This leads to improved durability of the second swash plate and the second shoe.

  In a preferred example, an inclined surface is provided at a convex corner portion on the second swash plate side at a portion corresponding to the piston at the bottom dead center position in the outer peripheral edge portion of the first swash plate. In other words, an inclined surface is provided at the convex corner on the second swash plate side at the outer peripheral edge portion of the first swash plate corresponding to the circumferential range of the first swash plate in which the piston is disposed at the bottom dead center position. ing.

  In the swash plate, at the outer peripheral edge corresponding to the piston at the bottom dead center position, the convex angle portion on the piston side greatly protrudes in the radial direction of the drive shaft. Therefore, by chamfering the protruding portion of the swash plate, it is possible to increase the diameter of the first swash plate while suppressing a decrease in durability and an increase in size of the piston.

  In a preferred example, the gas is a refrigerant used in a refrigeration circuit, and carbon dioxide is used as the refrigerant.

  When the carbon dioxide refrigerant is used, the pressure in the refrigeration circuit is much higher than when the chlorofluorocarbon refrigerant (for example, R134a) is used. Accordingly, even in the capacity variable swash plate compressor, the compression reaction force acting on the piston is increased, so that the pressure contact force between the swash plate and the shoe is increased. In such an aspect, the invention according to any one of claims 1 to 5 is embodied in order to improve the durability of the swash plate and the shoe while suppressing the decrease in the durability and the enlargement of the piston. Especially effective.

FIG. 1 is a longitudinal sectional view of a variable displacement swash plate compressor according to a first embodiment embodying the present invention.
FIG. 2 is an enlarged view of the main part of FIG.
[FIG. 3] A longitudinal sectional view of a variable displacement swash plate compressor according to a second embodiment of the present invention.
FIG. 4 is an enlarged view of a main part of FIG. 3, in which the first and second swash plates are not sectioned (partially broken), and a part of the first and second shoes are sectioned.
FIG. 5 is an enlarged view of a main part showing a swash plate structure according to a third embodiment of the present invention.
FIG. 6 is a longitudinal sectional view of a variable displacement swash plate compressor according to a fourth embodiment of the present invention.
FIG. 7 is a sectional view taken along line AA in FIG.
FIG. 8 is an enlarged cross-sectional view of the main part of FIG.
FIG. 9 is a longitudinal sectional view of a conventional variable displacement swash plate compressor.
FIG. 10 is a partial sectional view showing a conventional technique.

  Hereinafter, the first to fourth embodiments in which the present invention is embodied in a variable capacity swash plate compressor constituting a refrigeration circuit of a vehicle air conditioner will be described.

  A first embodiment will be described with reference to FIGS. 1 and 2. FIG. 1 is a longitudinal sectional view of a variable capacity swash plate compressor (hereinafter simply referred to as a compressor 10). In FIG. 1, the left side is the front of the compressor and the right side is the rear of the compressor.

  As shown in FIG. 1, the housing of the compressor 10 includes a cylinder block 11, a front housing 12 joined and fixed to the front end of the cylinder block 11, and a valve / port forming body 13 at the rear end of the cylinder block 11. And a rear housing 14 fixedly joined.

  A crank chamber 15 is defined between the cylinder block 11 and the front housing 12 in the housing of the compressor 10. A drive shaft 16 is rotatably disposed between the cylinder block 11 and the front housing 12 so as to pass through the crank chamber 15. The drive shaft 16 is operatively connected to an engine E, which is a travel drive source of the vehicle, via a clutchless type (always transmission type) power transmission mechanism PT. Accordingly, when the engine E is in operation, the drive shaft 16 is always rotated by receiving power from the engine E.

  A rotor 17 is fixed to the drive shaft 16 in the crank chamber 15 so as to be integrally rotatable. A first swash plate 18 having a substantially disk shape is accommodated in the crank chamber 15. An insertion hole 18 a is formed through the central portion of the first swash plate 18. The drive shaft 16 is inserted through the insertion hole 18 a of the first swash plate 18. The first swash plate 18 is supported by the drive shaft 16 through the insertion hole 18a so as to be slidable and tiltable. A hinge mechanism 19 is interposed between the rotor 17 and the first swash plate 18.

  The hinge mechanism 19 protrudes toward the rotor 17 on the front surface of the first swash plate 18 and two rotor-side protrusions 41 (one on the front side of the paper is not shown) protruding from the rear surface of the rotor 17. The swash plate side protrusion 42 is provided. The front end side of the swash plate side protrusion 42 enters between the two rotor side protrusions 41. Accordingly, the rotational force of the rotor 17 is transmitted to the first swash plate 18 via the rotor side protrusion 41 and the swash plate side protrusion 42.

  A support portion 39 having a substantially cylindrical shape protrudes from the central portion of the rear surface of the first swash plate 18 so as to surround the drive shaft 16. A disc-shaped second swash plate 51 is disposed outside the support portion 39 in the first swash plate 18 in a state where the support portion 39 is inserted into a support hole 51 a formed through the center portion of the first swash plate 18. . As the second swash plate 51, one having substantially the same radius as the first swash plate 18 is used.

  A radial bearing 52 is interposed between the outer peripheral surface of the support portion 39 and the inner peripheral surface of the support hole 51 a of the second swash plate 51. A thrust bearing 53 is interposed between the rear surface of the first swash plate 18 and the front surface of the second swash plate 51. The thrust bearing 53 has a plurality of rollers 53a as rolling elements, and the plurality of rollers 53a are rotatably held by a cage 53b.

  The second swash plate 51 is rotated relative to the first swash plate 18 via the radial bearing 52 and the thrust bearing 53, and can be tilted integrally with the first swash plate 18 (support portion 39). Is supported by.

  A cam portion 43 is formed at the base of the rotor side protrusion 41. A cam surface 43 a is formed on the rear end surface of the cam portion 43 facing the first swash plate 18. The tip of the swash plate side protrusion 42 is slidably contacted with the cam surface 43 a of the cam portion 43. Therefore, the hinge mechanism 19 moves the tip of the swash plate side protrusion 42 on the cam surface 43 a of the cam portion 43 in the contact / separation direction with respect to the drive shaft 16, whereby the first swash plate 18 and the second swash plate 51. Guide the tilt.

  In the cylinder block 11, around the axis L of the drive shaft 16, a plurality of cylinder bores 22 are formed to penetrate in the front-rear direction (the left-right direction in the drawing) at equal angular intervals. The single-headed piston 23 is accommodated in each cylinder bore 22 so as to be movable in the front-rear direction. The front and rear openings of the cylinder bore 22 are closed by the front end face of the valve / port forming body 13 and the piston 23, and a compression chamber 24 whose volume changes in accordance with the movement of the piston 23 in the front and rear direction is defined in the cylinder bore 22. Has been.

  The piston 23 includes a columnar head portion 37 inserted into the cylinder bore 22 and a neck portion 38 positioned in the crank chamber 15 outside the cylinder bore 22 in the front-rear direction. The head portion 37 and the neck portion 38 are made of an aluminum-based metal material (referring to pure aluminum or an aluminum alloy). A pair of shoe seats 38 a are recessed in the neck portion 38. Inside the neck portion 38, a first shoe 25A and a second shoe 25B having a hemispherical shape are housed. The first shoe 25A and the second shoe 25B are made of an iron-based metal material. In the present specification, the “hemisphere” does not mean only a half of a sphere, but a part having a part of a spherical surface of a sphere.

  The first shoe 25A and the second shoe 25B are each spherically received by a corresponding shoe seat 38a with a hemispherical surface 25a. The hemispherical surface 25a of the first shoe 25A and the hemispherical surface 25a of the second shoe 25B exist on the same spherical surface with the point P as the center. Each piston 23 is anchored to the outer periphery of the first swash plate 18 and the second swash plate 51 via the first shoe 25A and the second shoe 25B. The first shoe 25A located on the opposite side of the compression chamber 24 is in contact with the front surface of the first swash plate 18 with a planar sliding contact surface 25b opposite to the hemispherical surface 25a. The second shoe 25B on the side of the compression chamber 24, that is, the side receiving the compression reaction force, is in contact with the rear surface of the second swash plate 51 with a sliding contact surface 25b opposite to the hemispherical surface 25a.

  When the first swash plate 18 is rotated by the rotation of the drive shaft 16, the piston 23 is reciprocated linearly in the front-rear direction. Here, when the first swash plate 18 rotates, slippage occurs between the first swash plate 18 and the second swash plate 51 by the action of the radial bearing 52 and the thrust bearing 53, and the rotational speed of the second swash plate 51. Is lower than the rotational speed of the first swash plate 18. Accordingly, the relative rotational speed between the second swash plate 51 and the second shoe 25B is lower than the relative rotational speed between the second shoe 25B and the first swash plate 18. Therefore, the second shoe centered on the axis S (line passing through the center of curvature P of the hemispherical surface 25a and perpendicular to the sliding contact surface 25b) due to relative rotation between the second swash plate 51 and the second shoe 25B. The rotational motion of 25B can be suppressed, and the occurrence of mechanical loss and malfunction due to the rotational motion can be suppressed.

  In the housing of the compressor 10, a suction chamber 26 and a discharge chamber 27 are respectively formed between the valve / port forming body 13 and the rear housing 14. A suction port 28 and a suction valve 29 are formed in the valve / port forming body 13 so as to be positioned between the compression chamber 24 and the suction chamber 26. A discharge port 30 and a discharge valve 31 are formed in the valve / port forming body 13 so as to be positioned between the compression chamber 24 and the discharge chamber 27.

  Carbon dioxide is used as the refrigerant in the refrigeration circuit. Refrigerant gas introduced into the suction chamber 26 from an external circuit (not shown) is sucked into the compression chamber 24 via the suction port 28 and the suction valve 29 by movement from the top dead center position to the bottom dead center position of each piston 23. Is done. The refrigerant gas sucked into the compression chamber 24 is compressed to a predetermined pressure by the movement from the bottom dead center position of the piston 23 to the top dead center position side, and enters the discharge chamber 27 via the discharge port 30 and the discharge valve 31. Discharged. The refrigerant gas in the discharge chamber 27 is led to an external circuit.

  In the housing of the compressor 10, an extraction passage 32, an air supply passage 33, and a control valve 34 are provided. The extraction passage 32 connects the crank chamber 15 and the suction chamber 26. The air supply passage 33 connects the discharge chamber 27 and the crank chamber 15. In the middle of the air supply passage 33, a known control valve 34 made of an electromagnetic valve is disposed.

  By adjusting the opening degree of the control valve 34 by external power supply control, the amount of high-pressure discharge gas introduced into the crank chamber 15 via the air supply passage 33 and the crank chamber 15 via the extraction passage 32 are adjusted. The balance with the amount of gas discharged is controlled, and the internal pressure of the crank chamber 15 is determined. The difference between the internal pressure of the crank chamber 15 and the internal pressure of the compression chamber 24 is changed according to the change of the internal pressure of the crank chamber 15, and the inclination angle of the first swash plate 18 and the second swash plate 51 is changed. The stroke, that is, the discharge capacity of the compressor is adjusted.

  For example, when the valve opening degree of the control valve 34 decreases, the internal pressure of the crank chamber 15 decreases. Therefore, the inclination angle of the first swash plate 18 and the second swash plate 51 is increased, the stroke of the piston 23 is increased, and the discharge capacity of the compressor 10 is increased. On the contrary, when the valve opening degree of the control valve 34 increases, the internal pressure of the crank chamber 15 increases. Therefore, the inclination angles of the first swash plate 18 and the second swash plate 51 are reduced, the stroke of the piston 23 is reduced, and the discharge capacity of the compressor 10 is reduced.

  As shown in FIGS. 1 and 2, the support portion 39 that supports the second swash plate 51 in the first swash plate 18 is at the top dead center position with respect to the central axis M <b> 1 of the first swash plate 18. It is eccentrically provided on the piston 23A side. In other words, the support part 39 is provided eccentrically on the part side (hinge mechanism 19 side) that brings the piston 23 to the top dead center position when the radial direction of the first swash plate 18 is viewed from the central axis M1. It has been. Accordingly, the second swash plate 51, the radial bearing 52, and the thrust bearing 53 (the cage 53b) are eccentric to the piston 23A side at the top dead center position with respect to the first swash plate 18. Therefore, the center axis M2 of the second swash plate 51, the radial bearing 52, and the thrust bearing 53 is set to the first shoe 25A and the first shoe 25A provided in the piston 23A at the top dead center position with respect to the center axis M1 of the first swash plate 18. The two shoes 25B are shifted in parallel by a slight amount (for example, 0.05 to 5 mm, exaggerated in the drawing) on the center point P side.

  Therefore, in the outer peripheral edge of the second swash plate 51, the portion corresponding to the vicinity of the piston 23A at the top dead center position slightly protrudes from the outer peripheral edge of the first swash plate 18 in the radial direction of the first swash plate 18. Yes. Therefore, for example, compared with the case where the second swash plate 51 is not eccentric with respect to the first swash plate 18, the second shoe 25B of the piston 23 near the top dead center position and the second swash plate 51 The contact area is widened.

  In the outer peripheral edge of the second swash plate 51, the portion corresponding to the vicinity of the piston 23B at the bottom dead center position is located on the radially inner side of the first swash plate 18 relative to the outer peripheral edge of the first swash plate 18. Will be. That is, the portion of the outer peripheral edge portion of the second swash plate 51 corresponding to the vicinity of the hinge mechanism 19 is located on the inner side in the radial direction of the first swash plate 18 than the outer peripheral edge portion of the first swash plate 18. Therefore, for example, as compared with the case where the second swash plate 51 is not eccentric with respect to the first swash plate 18, the second shoe 25B of the piston 23 near the bottom dead center position and the second swash plate 51 The contact area is reduced. However, the compression reaction force acting on the second shoe 25B of the piston 23 near the bottom dead center position is much smaller than the compression reaction force acting on the second shoe 25B of the piston 23 near the top dead center position. . For this reason, even if the contact area between the second shoe 25B of the piston 23 near the bottom dead center position and the second swash plate 51 becomes narrow, there is no problem with respect to the durability of the second swash plate 51 and the second shoe 25B. Will not occur.

  On the outer peripheral edge of the first swash plate 18, a convex angle on the side opposite to the second swash plate 51 is formed in a portion corresponding to the piston 23 </ b> A at the top dead center position and a portion positioned in the front and rear in the circumferential direction. The part 18b is provided with an inclined surface (chamfering). That is, in the portion of the outer peripheral edge portion of the second swash plate 51 corresponding to the vicinity of the hinge mechanism 19, the convex corner portion 18 b on the side opposite to the second swash plate 51 is provided with an inclined surface (chamfering). In other words, the portion of the outer peripheral edge portion of the first swash plate 18 corresponding to the circumferential range of the first swash plate 18 in which the piston 23 is disposed at the top dead center position is inclined to the convex corner portion 18b opposite to the piston 23A. A surface is provided. The inclined surface (chamfer) of the convex corner portion 18b is provided such that the portion corresponding to the piston 23A at the top dead center position is the largest, and gradually decreases from the portion in the circumferential direction. The inclined surface (chamfering) of the convex corner portion 18b is provided in a range from a quarter-circumferential region to a semi-circular region with the portion corresponding to the piston 23A at the top dead center position in the middle.

On the outer peripheral edge portion of the first swash plate 18, a convex angle portion 18 c on the second swash plate 51 side is formed at a portion corresponding to the piston 23 </ b> B at the bottom dead center position and a portion positioned in the circumferential direction with respect to the portion. An inclined surface (chamfering) is provided on the surface. That is, at the outer peripheral edge portion of the first swash plate 18 corresponding to the circumferential range of the first swash plate 18 in which the piston 23B is disposed at the bottom dead center position, the piston 23B is inclined to the convex corner 18c opposite to the piston 23B. A surface is provided.
The inclined surface (chamfer) is provided such that the portion corresponding to the piston 23B at the bottom dead center position is the largest, and gradually decreases as the portion moves away from the portion in the circumferential direction. The inclined surface (chamfering) of the convex corner portion 18c is provided in a range from a quarter-circumferential region to a semi-circular region, with the portion corresponding to the piston 23B at the bottom dead center position in the middle. The inclined surface (chamfer) of the convex corner portion 18c is provided with substantially the same size as the inclined surface (chamfer) of the convex corner portion 18b in consideration of the weight balance around the central axis M1 of the first swash plate 18. It has been.

In the present embodiment having the above-described configuration, the following effects are obtained.
(1-1) The second swash plate 51 and the second swash plate 51 are arranged by decentering the second swash plate 51 toward the piston 23A at the top dead center position with respect to the first swash plate 18. Even if the diameter is not increased, the contact area between the second shoe 25B of the piston 23 near the top dead center position and the second swash plate 51 can be increased. Therefore, the contact slidability between the second swash plate 51 and the second shoe 25B is improved, and the durability of the second swash plate 51 and the second shoe 25B is improved while suppressing the decrease in the durability and the increase in size of the piston 23. Can be improved.

  (1-2) In the swash plate structure including the thrust bearing 53 in addition to the first swash plate 18 and the second swash plate 51 as in the present embodiment, the first shoe 25A and the second shoe 25B in the swash plate structure. The thickness between the two will increase. In such a conditionally strict configuration, the second swash plate 51 is eccentric with respect to the first swash plate 18, and the second shoe 25B of the piston 23 and the second swash plate 51 in the vicinity of the top dead center position. The wide contact area is particularly effective in improving the durability of the second swash plate 51 and the second shoe 25B while suppressing the decrease in the durability and the increase in size of the piston 23.

  (1-3) In the outer peripheral edge portion of the first swash plate 18, an inclined surface is provided on the convex corner portion 18 b on the side opposite to the second swash plate 51 at a portion corresponding to the piston 23 </ b> A at the top dead center position. ing. Further, in the outer peripheral edge of the first swash plate 18, an inclined surface is provided on the convex corner 18 c on the second swash plate 51 side at a portion corresponding to the piston 23 </ b> B at the bottom dead center position. The first swash plate 18 inclined with respect to the drive shaft 16 has a convex corner portion 18b opposite to the second swash plate 51 at the outer peripheral edge corresponding to the piston 23A at the top dead center position. It protrudes greatly in the radial direction. Further, in the first swash plate 18, the convex corner 18 c on the second swash plate 51 side protrudes greatly in the radial direction of the drive shaft 16 at the outer peripheral edge corresponding to the piston 23 </ b> B at the bottom dead center position. It becomes.

  Therefore, by providing an inclined surface on the protruding portion of the first swash plate 18 (a part of the entire circumference of the convex corner portions 18b and 18c), the first inclined plate 18 is suppressed while suppressing a decrease in durability and an increase in size of the piston 23. The diameter of the plate 18 can be increased. Accordingly, it is preferable to support the second swash plate 51 by the first swash plate 18, and a large compression reaction force acting on the second swash plate 51 via the second shoe 25B of the piston 23 near the top dead center position is obtained. It can be suitably received by the first swash plate 18 via the second swash plate 51. This leads to improved durability of the second swash plate 51.

  (1-4) Carbon dioxide is used as a refrigerant in the refrigeration circuit. When the carbon dioxide refrigerant is used, the pressure in the refrigeration circuit is much higher than when the chlorofluorocarbon refrigerant (for example, R134a) is used. Therefore, also in the compressor, the compression reaction force acting on the piston 23 is increased, so that the pressure contact force between the second swash plate 51 and the second shoe 25B is increased. The embodiment of the present invention in such an aspect is particularly effective in improving the durability of the second swash plate 51 and the second shoe 25B while suppressing the decrease in the durability and the increase in size of the piston 23.

  Next, a second embodiment of the present invention will be described with reference to FIGS. In the present embodiment, only differences from the first embodiment will be described, and the same or equivalent members will be denoted by the same reference numerals and detailed description thereof will be omitted.

  In the first shoe 25A and the second shoe 25B, the first shoe 25A located on the hinge mechanism 19 side, that is, on the opposite side to the compression chamber 24, is arranged on the sliding contact surface 25b on the opposite side to the hemispherical surface 25a. It is slidably contacted with the front surface of the outer peripheral portion 18-1. Further, the second shoe 25B on the side opposite to the hinge mechanism 19, that is, on the side of the compression chamber 24 and receiving the compression reaction force, is the outer peripheral portion of the second swash plate 51 on the sliding contact surface 25b on the side opposite to the hemispherical surface 25a. It is slidably contacted with the rear surface of 51-2. The slidable contact surface 25b of the first shoe 25A has a middle-high shape in which the central portion protrudes toward the first swash plate 18 (see FIG. 4. The middle-high shape is exaggerated in FIG. 4). The sliding contact surface 25b of the second shoe 25B has a planar shape.

  Between the support part 39 which comprises the inner peripheral part of the 1st swash plate 18, and the inner peripheral part 51-1 of the 2nd swash plate 51, the outer peripheral surface of the support part 39 and the support hole 51a of the 2nd swash plate 51 in detail. A radial bearing 52 </ b> A made of a rolling bearing is interposed between the inner peripheral surface and the inner peripheral surface. The radial bearing 52A includes an outer race 52a attached to the inner peripheral surface of the support hole 51a in the second swash plate 51, an inner race 52b attached to the outer peripheral surface of the support portion 39 in the first swash plate 18, and an outer race. A plurality of rollers 52c serving as rolling elements are interposed between the inner race 52b and the inner race 52b.

  Between the first shoe 25A and the second shoe 25B, a thrust bearing 53 made of a rolling bearing is provided between the outer peripheral portion 18-1 of the first swash plate 18 and the outer peripheral portion 51-2 of the second swash plate 51. Intervened. The thrust bearing 53 has a plurality of rollers 53a as rolling elements, and the plurality of rollers 53a are held by a cage 53b so as to be able to rotate. In the thrust bearing 53, an annular race 55 is interposed between the roller 53a and the first swash plate 18. The race 55 is formed by subjecting a base material made of mild steel such as SPC to carburizing heat treatment. The corners of both ends of the roller 53a are chamfered so that the roller 53a does not hit the second swash plate 51 and the race 55 and damage the second swash plate 51 and the race 55.

  On the rear surface of the first swash plate 18, an outer peripheral portion 18-1 is provided with an annular locking portion 18 d that protrudes toward the second swash plate 51 side. The race 55 is disposed on the inner side of the locking portion 18d, and the race 55 is locked to the first swash plate 18 on the outer side in the radial direction by the contact between the outer peripheral edge and the locking portion 18d. The race 55 is rotatable relative to the first swash plate 18 by being guided by the locking portion 18d.

  The second swash plate 51 is supported by the first swash plate 18 so as to be rotatable relative to the first swash plate 18 and tilted integrally with each other through the radial bearing 52A and the thrust bearing 53. . Accordingly, when the first swash plate 18 rotates, the radial bearing 52A and the thrust bearing 53 cause rolling between the first swash plate 18 and the second swash plate 51, and mechanical loss due to slippage between the surfaces. However, the mechanical loss due to the rolling is replaced, and the occurrence of the mechanical loss in the compressor can be greatly suppressed.

  The plate thickness Y1 of the inner peripheral portion 51-1 that receives the support of the radial bearing 52A in the second swash plate 51 is thicker than the plate thickness Y2 of the outer peripheral portion 51-2 that receives the support of the thrust bearing 53 in the second swash plate 51. Has been. Specifically, the plate thickness Y2 of the outer peripheral portion 51-2 of the second swash plate 51 is more than half of the plate thickness X of the outer peripheral portion 18-1 of the first swash plate 18, and the outer peripheral portion 18- of the first swash plate 18. It is set to be thinner than the plate thickness X of 1. Further, the plate thickness Y1 of the inner peripheral portion 51-1 of the second swash plate 51 is thicker than the plate thickness X of the outer peripheral portion 18-1 of the first swash plate 18.

  The inner peripheral portion 51-1 of the second swash plate 51 includes a cylindrical first protrusion 56 protruding from the first swash plate 18 and a cylinder protruding from the opposite side of the first swash plate 18. The plate-like second projecting portion 57 is provided so that the plate thickness is thicker than the outer peripheral portion 51-2 of the second swash plate 51 (Y1> Y2). The first protrusion 56 and the second protrusion 57 are arranged coaxially with the support hole 51a, and the inner peripheral surfaces of the first protrusion 56 and the second protrusion 57 are the inner periphery of the support hole 51a. Configure part of the surface. The outer diameter Z2 of the second projecting portion 57 is smaller than the outer diameter Z1 of the first projecting portion 56. Further, the outer peripheral angle 57a of the tip surface of the second projecting portion 57 is entirely chamfered.

In the second embodiment, the same effects as in the first embodiment can be obtained, and the following effects can be obtained.
(2-1) Between the first shoe 25A and the second shoe 25B, there is a second slant between the outer peripheral portion 18-1 of the first swash plate 18 and the outer peripheral portion 51-2 of the second swash plate 51. A thrust bearing 53 that supports the plate 51 so as to be rotatable relative to the first swash plate 18 is disposed. The second swash plate 51 can be rotated relative to the first swash plate 18 between the inner peripheral portion (support portion 39) of the first swash plate 18 and the inner peripheral portion 51-1 of the second swash plate 51. A radial bearing 52 </ b> A for supporting is disposed.

  Accordingly, due to the action of the thrust bearing 53 and the radial bearing 52A, the outer peripheral portion 18-1 of the first swash plate 18 and the outer peripheral portion 51-2 of the second swash plate 51 and the inner peripheral portion of the first swash plate 18 are obtained. The rotational resistance generated between the (supporting portion 39) and the inner peripheral portion 51-1 of the second swash plate 51 can be effectively reduced. Therefore, even in the compressor 10 used in the refrigeration circuit using carbon dioxide as a refrigerant, the slip between the first swash plate 18 and the second swash plate 51 can be set as a mechanical loss due to rolling. As a result, the occurrence of defects such as mechanical loss and seizure can be effectively suppressed.

  (2-2) In the second swash plate 51, the plate thickness Y2 of the outer peripheral portion 51-2 is more than half the plate thickness X of the outer peripheral portion 18-1 of the first swash plate 18, and the plate thickness of the outer peripheral portion 18-1. It is thinner than X. To avoid an increase in the size of the piston 23, that is, an increase in the size of the compressor, the space between the first shoe 25A and the second shoe 25B is limited. In this limited space, if the plate thickness X of the outer peripheral portion 18-1 of the first swash plate 18 is increased, it is necessary to decrease the plate thickness Y2 of the outer peripheral portion 51-2 of the second swash plate 51. When the thickness Y2 of the outer peripheral portion 51-2 of the two swash plate 51 is increased, it is necessary to reduce the plate thickness X of the outer peripheral portion 18-1 of the first swash plate 18.

  From the viewpoint of receiving the compression reaction force, it is necessary to secure the strength of both the first swash plate 18 and the second swash plate 51 by increasing the plate thicknesses X and Y2 of the outer peripheral portions 18-1 and 51-2 as much as possible. However, in the first swash plate 18 to which power is transmitted from the drive shaft 16, the plate thickness X of the outer peripheral portion 18-1 is secured on the outer periphery of the second swash plate 51 that may slide with respect to the first swash plate 18. Priority should be given to securing the thickness Y2 of the part 51-2. In this sense, it is preferable that the thickness Y2 of the outer peripheral portion 51-2 of the second swash plate 51 is equal to or more than half the plate thickness X of the outer peripheral portion 18-1 of the first swash plate 18, and the outer peripheral portion 18-1. The thickness is set to be thinner than the plate thickness X.

  (2-3) In the second swash plate 51, the plate thickness Y1 of the inner peripheral portion 51-1 is thicker than the plate thickness Y2 of the outer peripheral portion 51-2. The thick inner peripheral portion 51-1 stabilizes the support of the second swash plate 51 by the radial bearing 52 </ b> A, and can further improve the slip between the first swash plate 18 and the second swash plate 51. In addition, the outer peripheral portion 18-1 of the first swash plate 18 that is stricter in strength than the second swash plate 51 by the outer peripheral portion 51-2 of the second swash plate 51 that is relatively thin with respect to the inner peripheral portion 51-1. It is easy to secure the plate thickness.

  (2-4) The plate thickness Y2 of the outer peripheral portion 51-2 of the second swash plate 51 is made thinner than the plate thickness X of the outer peripheral portion 18-1 of the first swash plate 18. Therefore, the thin outer peripheral portion 51-2 of the second swash plate 51 makes it easy to ensure the thickness of the outer peripheral portion 18-1 of the first swash plate 18 that is stricter in strength than the second swash plate 51. In the second swash plate 51, the plate thickness Y1 of the inner peripheral portion 51-1 is thicker than the plate thickness X of the outer peripheral portion 18-1 of the first swash plate 18. Accordingly, the support of the second swash plate 51 by the radial bearing 52A is further stabilized.

  (2-5) In the first protrusion 56 and the second protrusion 57 constituting the inner peripheral part 51-1 of the second swash plate 51, the outer diameter Z2 of the second protrusion 57 is the first protrusion. The outer diameter Z1 of the portion 56 is made smaller. For example, in the state where the discharge capacity of the compressor 10 is maximum (the state shown in FIG. 3), a part of the second protruding portion 57 is extremely close to the piston 23 </ b> B at the bottom dead center position. Therefore, separating the second projecting portion 57 from the piston 23 with a smaller diameter than the first projecting portion 56 avoids the interference between the second swash plate 51 and the piston 23 and the second swash plate 51. This is effective in achieving both thickening the plate thickness Y1 of the inner peripheral portion 51-1.

  (2-6) In the second protruding portion 57 constituting the inner peripheral portion 51-1 of the second swash plate 51, a chamfer is provided at the outer peripheral angle 57a of the distal end surface. In the second projecting portion 57, for example, a part of the outer peripheral angle 57a of the front end surface is extremely close to the piston 23B at the bottom dead center position in a state where the discharge capacity of the compressor is maximum. Therefore, providing a chamfer at the outer peripheral angle 57 a of the tip surface of the second projecting portion 57 avoids interference between the second swash plate 51 and the piston 23, and the inner peripheral portion 51-of the second swash plate 51. This is effective in achieving both the increase of the plate thickness Y1 of 1.

  (2-7) On the outer peripheral edge of the first swash plate 18, an inclined surface (chamfered) is formed on the convex corner portion 18 b on the opposite side to the second swash plate 51 at a portion corresponding to the piston 23 </ b> A at the top dead center position. It has been subjected. Accordingly, it is possible to increase the diameter of the first swash plate 18 and the second swash plate 51 while suppressing a decrease in durability and an increase in size of the piston 23. Therefore, the contact slidability between the second swash plate 51 and the second shoe 25B is improved, and the durability of the second swash plate 51 and the second shoe 25B is improved while suppressing the decrease in the durability and the increase in size of the piston 23. Can be improved.

  That is, the first swash plate 18 inclined with respect to the drive shaft 16 has a convex corner portion 18b on the opposite side of the second swash plate 51 on the outer peripheral edge corresponding to the piston 23A at the top dead center position (in a state without chamfering). ) Greatly protrudes in the radial direction of the one drive shaft 16. In the first swash plate 18, when the convex corner portion 18b opposite to the second swash plate 51 protrudes greatly in the radial direction, the neck portion 38 corresponding to the protruding portion in the piston 23 is avoided in order to avoid interference with the protruding portion. It is conceivable to reduce the thickness of the neck portion or to enlarge the neck portion 38 in the radial direction. However, the thinning of the neck portion 38 leads to a decrease in the durability of the piston 23, and the enlargement of the neck portion 38 leads to an increase in the size of the compressor.

  In order to solve such a problem, it is conceivable to reduce the radius of the first swash plate 18 to avoid the interference between the convex corner portion 18b and the piston 23 described above. However, if the radius of the first swash plate 18 is reduced, the radius of the second swash plate 51 that needs to be supported by the first swash plate 18 must be reduced. Therefore, in particular, in the piston 23 in the vicinity of the top dead center position (compression stroke), the contact area between the second shoe 25B receiving the large compression reaction force and the second swash plate 51 becomes narrow, and the second swash plate 51 and the second swash plate 51 There is a problem that the durability of the two shoes 25B is lowered.

  (2-8) A roller 52c is used as a rolling element of the radial bearing 52A. The rolling bearing using the roller 52c as the rolling element has excellent load resistance as compared with, for example, a case where a ball is used as the rolling element. This leads to downsizing of the radial bearing 52A and thus downsizing of the compressor 10.

  (2-9) A race 55 is interposed between the roller 53 a of the thrust bearing 53 and the first swash plate 18. The race 55 is rotatable relative to the first swash plate 18.

  Here, for example, when the roller 53a of the thrust bearing 53 is directly rolled on the first swash plate 18, a part of the first swash plate 18 (a part corresponding to the piston 23 near the top dead center position). As a result, a large compression reaction force is applied to the region, and there is a problem that the portion is locally worn out. However, in the present embodiment, the race 55 is interposed between the roller 53 a and the first swash plate 18, and the compression reaction force acting on the roller 53 a reduces the surface pressure through the race 55. Since it acts on the 1st swash plate 18, it can suppress that the 1st swash plate 18 wears out locally. Further, in the race 55 that rotates relative to the first swash plate 18, a portion where a large compression reaction force acts through the rollers 53 a is sequentially replaced, and the race 55 can be prevented from being locally worn out.

  (2-10) A locking portion 18d protrudes from the outer peripheral portion 18-1 of the first swash plate 18 toward the second swash plate 51, and the race 55 is brought into contact with the locking portion 18d. Is locked to the first swash plate 18 on the radially outer side.

  Here, for example, in a configuration in which the locking portion is provided on the inner peripheral portion of the first swash plate 18 to lock the race 55 to the first swash plate 18 on the inner side in the radial direction, the first swash plate 18 is attached. When the lubricating oil (refrigerating machine oil) moves radially outward by the action of centrifugal force, the entry of the lubricating oil between the first swash plate 18 and the race 55 is hindered by the locking portion. However, according to the present embodiment in which the race 55 is locked to the first swash plate 18 on the outer side in the radial direction, the entry of the lubricating oil between the first swash plate 18 and the race 55 is inhibited by the locking portion 18d. Therefore, the slip between the first swash plate 18 and the race 55 can be improved.

  (2-11) The locking portion 18d has an annular shape. Therefore, the race 55 is stably locked by the locking portion 18d, and the sliding between the race 55 and the first swash plate 18 is further improved.

  Next, a third embodiment of the present invention will be described with reference to FIG. In the present embodiment, only differences from the second embodiment will be described, and the same or equivalent members will be denoted by the same reference numerals, and detailed description thereof will be omitted.

  In the present embodiment, the support portion 39 is not eccentric with respect to the central axis M <b> 1 of the first swash plate 18. In other words, the second swash plate 51, the radial bearing 52A (see FIG. 3) and the thrust bearing 53 (including the race 55) are not eccentric with respect to the first swash plate 18. In this case, at the outer peripheral edge of the first swash plate 18, the portion corresponding to the piston 23 </ b> B at the bottom dead center position is such that the convex corner portion 18 c on the second swash plate 51 side is larger than the second swash plate 51 in the radial direction. Since it does not protrude, there is no problem even if the chamfered portion 18c is not chamfered as shown in FIG.

  In the present embodiment, the PCD of the thrust bearing 53 passes through the center point P of the first shoe 25A and the second shoe 25B around the center axes M1 and M2 of the first swash plate 18 and the second swash plate 51. It is larger than the diameter of the virtual cylinder. In this way, the thrust bearing 53 (roller 53a) can suitably receive the compression reaction force transmitted through the second swash plate 51, and the durability is improved. The “PCD” of the thrust bearing 53 is the center axis of the thrust bearing 53 (center axes M1 and M2 of the first swash plate 18 and the second swash plate 51), and the intermediate axis on the rotation center axis of the roller 53a. It refers to the diameter of a virtual cylinder that passes through a point.

  Next, a fourth embodiment of the present invention will be described with reference to FIGS. In the present embodiment, only differences from the first and second embodiments will be described, and the same or equivalent members will be denoted by the same reference numerals and detailed description thereof will be omitted.

  A rotor 17 is fixed to the drive shaft 16 and a swash plate 58 is supported so as to be slidable and tiltable in the axial direction of the drive shaft 16. Connection pieces 59 and 60 are fixed to the swash plate 58, and guide pins 61 and 62 are fixed to the connection pieces 59 and 60. A pair of guide holes 171 (only one is shown) is formed in the rotor 17. The heads of the guide pins 61 and 62 are slidably fitted into the guide holes 171. The swash plate 58 can be tilted in the axial direction of the drive shaft 16 and can rotate integrally with the drive shaft 16 by linking the guide hole 171 and the guide pins 61 and 62. The tilt of the swash plate 58 is guided by the slide guide relationship between the guide hole 171 and the guide pins 61 and 62 and the slide support action of the drive shaft 16. The connecting pieces 59 and 60, the guide pins 61 and 62, and the guide hole 171 constitute a hinge mechanism 19A.

  The solid line position of the swash plate 58 in FIG. 6 indicates the maximum tilt angle state of the swash plate 58. When the center portion of the swash plate 58 moves toward the cylinder block 11, the inclination angle of the swash plate 58 decreases. The chain line position of the swash plate 58 in FIG. 6 indicates the minimum tilt angle state of the swash plate 58.

  In the outer peripheral edge portion of the swash plate 58, a portion corresponding to the piston 23A at the top dead center position and a portion positioned in the circumferential direction front and rear with respect to the portion are inclined on the convex angle portion 58a on the opposite side to the piston 23. Is provided. That is, in the portion of the outer peripheral edge portion of the swash plate 58 corresponding to the vicinity of the hinge mechanism 19A, an inclined surface is provided on the convex corner portion 58a on the hinge mechanism 19A side. That is, an inclined surface is provided on the convex corner 58a on the side opposite to the piston 23 in the outer peripheral edge portion of the swash plate 58 corresponding to the circumferential range of the swash plate 58 in which the piston 23A is disposed at the top dead center position. ing. As shown in FIG. 7, the inclined surface of the convex corner portion 58a is provided such that the portion corresponding to the piston 23 at the top dead center position is the largest, and gradually decreases as it moves away from the portion in the circumferential direction. Yes.

  As shown in FIG. 8, the inclined surface provided in the convex angle portion 58 a is arranged around the virtual cylinder C having a central axis M <b> 3 parallel to the axis L of the drive shaft 16 when the swash plate 58 is in the maximum inclination state. Is on the surface. In the illustrated example, the central axis M3 is shifted with respect to the axis L from the piston 23A side at the top dead center position to the drive shaft 16 side. The diameter of the virtual cylinder C is equal to or larger than the diameter of the swash plate 58.

  The swash plate 58 inclined with respect to the drive shaft 16 has a convex corner 58a opposite to the piston 23 at the outer peripheral edge corresponding to the piston 23A at the top dead center position toward the radial direction of the drive shaft 16. It will protrude greatly. Therefore, by providing an inclined surface at the protruding portion (a part of the convex corner portion 58a) of the swash plate 58, the diameter of the swash plate 58 can be increased while suppressing a decrease in durability and an increase in size of the piston 23. . Therefore, a large compression reaction force acting on the swash plate 58 can be suitably received through the second shoe 25B of the piston 23 in the vicinity of the top dead center position. This leads to an improvement in durability of the swash plate 58.

In addition, for example, the following modes can be implemented without departing from the spirit of the present invention.
(1) In the first embodiment, the radial bearing 52 is deleted, and the second swash plate 51 is slid by the support portion 39.

(2) In the first embodiment, the thrust bearing 53 is deleted, and the second swash plate 51 is slid directly on the first swash plate 18.
(3) In the first embodiment, the radial bearing 52 and the thrust bearing 53 are deleted, and the second swash plate 51 is fixed to the first swash plate 18 so that the second swash plate 51 is replaced with the first swash plate 18. Make it possible to rotate together.

  In this case, an inclined surface (chamfering) is provided at a convex corner portion on the first swash plate 18 side with respect to a portion corresponding to the piston 23A at the top dead center position on the outer peripheral edge portion of the second swash plate 51. In addition, an inclined surface (chamfered) is provided at a convex corner on the opposite side of the first swash plate 18 with respect to the portion corresponding to the piston 23B at the bottom dead center position at the outer peripheral edge of the second swash plate 51. .

  Referring to FIG. 2, the second swash plate 51 inclined with respect to the drive shaft 16 is driven by the convex corner on the first swash plate 18 side at the outer peripheral edge corresponding to the piston 23 </ b> A at the top dead center position. The shaft 16 protrudes greatly in the radial direction. In the second swash plate 51, the convex corner on the side opposite to the first swash plate 18 protrudes greatly in the radial direction of the drive shaft 16 at the outer peripheral edge corresponding to the piston 23 </ b> B at the bottom dead center position. Will be. Therefore, providing the inclined surface (chamfering) to the protruding portion (a part of the convex corner portion) of the second swash plate 51 makes the second swash plate 51 large while suppressing a decrease in durability and an increase in size of the piston 23. Can be Therefore, the contact area between the second shoe 25B of the piston 23 near the top dead center position and the second swash plate 51 can be further increased, and the durability of the second swash plate 51 and the second shoe 25B is further improved. Can be made.

  (4) In the first embodiment, two sheets of the first swash plate 18 and the second swash plate 51 are used, but this is changed, for example, between the second swash plate 51 and the second shoe 25B. A third swash plate may be arranged between them. That is, the swash plate structure to which the present invention can be applied is not limited to one using only the first swash plate and the second swash plate, but the above-described three, four, five, etc. A plurality of swash plates may be provided.

  (5) The present invention is applied to a variable displacement swash plate compressor having a double-headed piston. In this case, the second swash plate may be disposed only on one side of the front and rear surfaces of the first swash plate, or the second swash plate may be disposed on both sides of the front and rear surfaces of the first swash plate. Also good.

(6) The present invention is not limited to being applied to a refrigerant compressor used in a refrigeration circuit, and may be applied to an air compressor, for example.
(7) The second embodiment is changed, and the sliding contact surface 25b of the first shoe 25A is made flat, for example, as shown in FIG.

  (8) The second embodiment is changed, for example, as shown in FIG. 5, the sliding contact surface 25 b of the second shoe 25 </ b> B is formed in a concave shape with a depressed central portion. In this way, the weight of the second shoe 25B that reciprocates linearly with the piston 23 can be reduced, the inertial force of the second shoe 25B can be reduced, and the inclination of the first swash plate 18 and the second swash plate 51 can be reduced. The angle can be changed smoothly, that is, the discharge capacity of the compressor can be changed smoothly.

(9) In the second and third embodiments, the thrust bearing 53 is changed to a rolling bearing provided with balls as rolling elements.
(10) In the second and third embodiments, the thrust bearing 53 is changed to a sliding bearing.

  (11) In the second and third embodiments, the radial bearing 52A is configured to receive only a radial load (a load in a direction orthogonal to the central axis M2) acting on the second swash plate 51. By changing this, for example, by disposing the roller 52c so as to be inclined with respect to the central axis M2 of the second swash plate 51, the radial bearing 52A is not only a radial load but also a thrust load (a load in the direction along the central axis M2). ) To be accepted.

  (12) In the second and third embodiments, the thrust bearing 53 is configured to receive only the thrust load acting on the second swash plate 51. By changing this, for example, the roller 53a is disposed so as to be inclined with respect to the surface of the second swash plate 51 so that not only the thrust load but also the radial load can be received.

(13) In the second and third embodiments, the race 55 is deleted, and the roller 53a of the thrust bearing 53 is configured to roll directly on the first swash plate 18.
(14) In the second and third embodiments, the locking portion 18d is deleted, and a locking portion is provided on the inner peripheral portion of the first swash plate 18 (for example, the base portion of the support portion 39 is also used as the locking portion). Thus, the race 55 is locked to the first swash plate 18 on the radially inner side.

Claims (6)

A swash plate is connected to the drive shaft so as to be integrally rotatable, and a piston is moored to the swash plate via a shoe. The piston is reciprocated linearly by the rotation of the swash plate as the drive shaft rotates. In the capacity variable swash plate compressor in which the gas is compressed and the discharge capacity is changed by changing the inclination angle of the swash plate,
The capacity-variable swash plate compressor is characterized in that an inclined surface is provided on a part of the entire outer periphery of the swash plate. 2. The variable capacity type according to claim 1, wherein the outer peripheral edge of the swash plate is provided with an inclined surface at a convex corner opposite to the piston at a portion corresponding to the piston at the top dead center position. Swash plate compressor. The inclined surface is provided in the convex-angle part at the side of the said piston in the part corresponding to the said piston in the bottom dead center position in the outer periphery part of the said swash plate. The capacity variable type swash plate compressor described in the paragraph. The swash plate includes a first swash plate coupled to a drive shaft so as to be integrally rotatable, and a second swash plate supported by the first swash plate. The piston is moored via a first shoe that contacts the first swash plate and a second shoe that receives the compression reaction force that contacts the second swash plate, and at the outer periphery of the first swash plate, The inclined surface is provided in the convex angle part on the opposite side to a said 2nd swash plate in the part corresponding to the said piston in a top dead center position. Variable capacity swash plate compressor. The inclined surface is provided in the convex-angle part by the side of the said 2nd swash plate in the part corresponding to the said piston in a bottom dead center position in the outer periphery part of the said 1st swash plate. Variable capacity swash plate compressor. The variable capacity swash plate compressor according to any one of claims 1 to 5, wherein the gas is a refrigerant used in a refrigeration circuit, and carbon dioxide is used as the refrigerant.

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