WO2005024233A1

WO2005024233A1 - Variable displacement swash plate type compressor

Info

Publication number: WO2005024233A1
Application number: PCT/JP2004/011373
Authority: WO
Inventors: Hajime Kurita; Takayuki Imai; Masakazu Murase; Tetsuhiko Fukanuma; Masaki Ota; Fuminobu Enokijima
Original assignee: Kabushiki Kaisha Toyota Jidoshokki
Priority date: 2003-09-02
Filing date: 2004-08-06
Publication date: 2005-03-17
Also published as: JPWO2005024233A1; EP1669600A1; US20070081904A1; KR20060057626A

Abstract

A variable displacement swash plate type compressor, wherein a first swash plate (18) is connected to a drive shaft (16) so as to be rotated integrally with each other and double-head pistons (23) are anchored to the first swash plate (18) through shoes (25A) and (25B). The pistons (23) are reciprocatingly moved in the linear direction by the rotation of the first swash plate (18) according to the rotation of the drive shaft (16) to compress refrigerant gas. An annular second swash plate (51) is supported on the first swash plate (18) rotatably relative to each other through a ball bearing (52). The second swash plate (51) is disposed between the first swash plate (18) and the shoes (25B) on a compressive load receiving side slidably on the first swash plate (18) and the shoes (25B). Sloped faces (chamfered parts) are formed at the projected corner parts (18b) and (18c) of the first swash plate (18). Accordingly, the durability of the swash plates and the shoes can be increased.

Description

Specification

Variable capacity swash plate compressor

Technical field

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

Background art

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 rotatable. A single-headed piston 94 is moored around the outer periphery 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 each of the shoes 93A and 93B, and the piston 94 reciprocates linearly to compress the refrigerant gas.

[0003] The shears 93A and 93B center on their own axis S (the line passing through the center of curvature P of the spherical surface and perpendicular to the sliding surface with the swash plate 92) in accordance with the relative rotation with the swash plate 92. A rotational movement will be performed. The rotation of the shafts 93A and 93B about the axis S is, as a whole, in one direction around the axis S with respect to the shafts 93A and 93B due to the difference in peripheral speed between the inner and outer peripheries of the swash plate 92 on the outer peripheral side. This is performed in a state equivalent to the application of a rotational force to the motor.

[0004] That is, the swash plate type compressor shown in FIG. 9 has a configuration in which the shoes 93A and 93B slide directly on the swash plate 92. Therefore, the slides 93A and 93B had to wastefully perform the rotational movement about the axis S by sliding based on the relative rotation with the swash plate 92. Therefore, there is a problem in that mechanical loss is particularly large in a sliding portion between the piston 94 and the shoe 93B on the side receiving the compression reaction force, and problems such as seizure occur in the sliding portion. .

[0005] In order to solve such a problem, for example, a technique as shown in FIG. 10 has been proposed (for example, see Patent Document 1). That is, a step portion 90a is provided in the center of the rear surface of the swash plate (hereinafter referred to as a first swash plate 90) (facing surface on the right side in the drawing) in an annular shape. Outside the stepped portion 90a of the first swash plate 90, an annular sliding plate (hereinafter referred to as a second swash plate 95) is supported so as to be rotatable relative to the first swash plate 90 at a coaxial position. . 2nd swashplate 95 The outer peripheral portion is slidably provided between the first swash plate 90 and the second shoe 93B between the first swash plate 90 and the second shoe 93B.

[0006] Therefore, when the first swash plate 90 rotates, a slippage occurs between the first swash plate 90 and the second swash plate 95, and the rotation speed of the second swash plate 95 becomes the rotation speed of the first swash plate 90. Lower than. Therefore, the relative rotational speed between the second swash plate 95 and the second swash plate 93B is lower than the relative rotational speed between the second swash plate 93B and the first swash plate 90. As a result, the rotational movement of the second shoe 93B about the axis S, which is caused by the relative rotation between the second swash plate 95 and the second shoe 93B, can be suppressed. Generation can be suppressed.

[0007] Here, it has also been proposed to interpose a rolling element between the first swash plate 90 and the second swash plate 95 between the first shoe 93A and the second shoe 93B [for example, see Patent Reference 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. By doing so, the sliding between the first swash plate 90 and the second swash plate 95 is improved, and the relative rotation speed between the second swash plate 95 and the second swash plate 93B is reduced. The rotation speed relative to the one swash plate 90 can be greatly reduced.

[0008] However, in the swash plate structure including the second swash plate 95 and the rolling elements in addition to the first swash plate 90, the first swash plate structure includes a first swash plate 93A and a second swash plate 93B. It becomes thicker. Therefore, the first swash plate 90 inclined with respect to the drive shaft 91 is provided at the outer peripheral edge corresponding to the vicinity of the piston 94 (the state in FIG. 10) at the top dead center position, on the side opposite to the second swash plate 95. The convex corner portion 90b protrudes largely in the radial direction of the drive shaft 91 (upward in the drawing). Further, the second swash plate 95 inclined with respect to the drive shaft 91 has a convex portion on the opposite side to the first swash plate 90 at an outer peripheral edge corresponding to the vicinity of a piston 94 (not shown) at the bottom dead center position. The corner portion 95b protrudes largely in the radial direction of the drive shaft 91.

[0009] When the convex corner portion 90b of the first swash plate 90 and the convex corner portion 95b of the second swash plate 95 protrude greatly in the radial direction of the drive shaft 91, the piston 94 is moved in order to avoid interference with the protruding portion. In this case, it is necessary to reduce the thickness of the portion corresponding to the protruding portion or to increase the size of the piston 94 in the radial direction. Reducing the thickness of the piston 94 leads to a decrease in durability, and increasing the size of the piston 94 leads to an increase in the size of the swash plate compressor. Therefore, conventionally, when the thickness of the swash plate structure must be increased, the radius of the first swash plate 90 and the second swash plate 95 is reduced. Thus, the interference between the convex corners 90b and 95b and the piston 94 described above is avoided.

[0010] However, when the radius of the first swash plate 90 and the second swash plate 95 is reduced, especially near the top dead center position,

At the piston 94 in the (compression stroke), the contact area between the second shoe 93B, which receives a large compression reaction force, and the second swash plate 95 is reduced, and the durability of the second swash plate 95 and the second shoe 93B is reduced. There was a problem.

In recent years, the use of carbon dioxide as a refrigerant in a refrigeration circuit has been generalized. When a carbon dioxide refrigerant is used, the pressure in the refrigeration circuit becomes much higher than when a chlorofluorocarbon refrigerant (eg, R134a) is used. Therefore, even in a swash plate compressor, the compression reaction force acting on the piston 94 becomes large, and the above-mentioned problem (the durability of the second swash plate 95 and the second shoe 93B is reduced) has been widely taken up. Was.

Patent document 1: JP-A-8-338363 (page 4, FIG. 1)

Patent Document 2: JP-A-8-28447 (page 3, FIG. 1)

Disclosure of the invention

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

[0013] In order to achieve the above object, the invention provides a drive shaft, wherein a swash plate is integrally rotatably connected to the drive shaft, and a piston is moored to the swash plate via a shoe. With the rotation of the swash plate, the piston is reciprocated linearly to compress the gas, and the displacement is changed by changing the inclination angle of the swash plate. In addition, the present invention provides a variable displacement type swash plate compressor in which an inclined surface is provided on a part of the entire outer peripheral edge of the swash plate.

[0014] By providing an inclined surface at the projecting corner of the outer peripheral edge of the swash plate that is inclined with respect to the drive shaft, the diameter of the swash plate can be increased while suppressing the decrease in the durability and the size of the piston. be able to. 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 the shoe.

[0015] In a preferred example, a slope corresponding to the piston located at the top dead center position is provided at an outer peripheral edge of the swash plate at a convex corner opposite to the piston. Toes In other words, an inclined surface is provided at a convex corner on the side opposite to the piston in a portion of an outer peripheral edge of the swash plate corresponding to a circumferential range of the swash plate in which the piston is disposed at the top dead center position.

[0016] In the swash plate inclined with respect to the drive shaft, at the outer peripheral edge portion corresponding to the piston at the top dead center position, a convex corner opposite to the piston protrudes largely in the radial direction of the drive shaft. It will be. Therefore, a large compression reaction force acting on the swash plate can be suitably received through the piston shaft near the top dead center position. This leads to improved durability of the swash plate and the shoe.

[0017] In a preferred example, a slope corresponding to the piston at the bottom dead center position is provided at a convex corner on the piston side at an outer peripheral edge of the swash plate. That is, at the outer peripheral edge 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, a slope is provided at the convex corner on the piston side.

[0018] In the swash plate, at the outer peripheral portion corresponding to the piston at the bottom dead center position, the convex portion on the piston side protrudes largely 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 the decrease in the durability and the size of the piston.

[0019] In a preferred example, the swash plate includes a first swash plate integrally rotatably connected to a drive shaft, and a second swash plate supported by the first swash plate. A piston is moored to the second swash plate via a first shoe in contact with the first swash plate and a second shoe on a side receiving a compression reaction force in contact with the second swash plate. On the outer peripheral edge of the first swash plate, a portion corresponding to the piston at the top dead center position is provided with an inclined surface at a convex corner opposite to the second swash plate. In other words, 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 top dead center position, the slope is inclined to a convex corner opposite to the first swash plate. Is provided.

[0020] The first swash plate inclined with respect to the drive shaft has a convex corner on the outer peripheral edge corresponding to the piston at the top dead center position, which is opposite to the second swash plate, in the radial direction of the drive shaft. It will protrude greatly toward it. Therefore, by chamfering the protruding portion of the first swash plate, it is possible to increase the diameter of the first swash plate while suppressing the durability and the size of the piston from being reduced. Therefore, the support of the second swash plate by the first swash plate is preferable, and the second shot of the piston near the top dead center position is suitable. A large compression reaction force acting on the second swash plate via the first swash plate can be suitably received by the first swash plate via the second swash plate. This leads to improved durability of the second swash plate and the second shoe.

[0021] In a preferred example, a slope corresponding to the piston at the bottom dead center position is provided on the outer peripheral edge portion of the first swash plate at a convex corner on the second swash plate side. ing. That is, in the outer peripheral portion of the first swash plate corresponding to the circumferential range of the first swash plate in which the piston is arranged at the bottom dead center position, a slope is provided at the convex corner on the second swash plate side. ing.

[0022] In the swash plate, at the outer peripheral edge corresponding to the piston at the bottom dead center position, the convex portion on the piston side protrudes largely 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 the decrease in the durability and the size of the piston.

[0023] In a preferred example, the gas is a refrigerant used in a refrigeration circuit, and carbon dioxide is used as the refrigerant.

[0024] When a carbon dioxide refrigerant is used, the pressure in the refrigeration circuit is significantly higher than when a chlorofluorocarbon refrigerant (for example, R134a) is used. Therefore, also in the variable displacement type swash plate type compressor, the compression reaction force acting on the piston increases, and the pressing force between the swash plate and the shoe increases. In such an embodiment, embodying the invention described in claim 1 in any one of claims 1 to 5 is to improve the durability of the swash plate and the shoe by suppressing the decrease in the durability and the size of the piston. Is particularly effective.

Brief Description of Drawings

FIG. 1 is a longitudinal sectional view of a variable displacement swash plate type compressor according to a first embodiment of the present invention.

FIG. 2 is an enlarged view of a main part of FIG. 1, without a cross section of first and second swash plates.

FIG. 3 is a longitudinal sectional view of a variable displacement swash plate type 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 cross-sectioned (partially broken), and some of the first and second shows are cross-sections.

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 type compressor according to a fourth embodiment of the present invention.

FIG. 7 is a sectional view taken along line A—A in FIG. 6. FIG. 8 is an enlarged sectional view of a main part of FIG. 6.

FIG. 9 is a longitudinal sectional view of a conventional variable displacement swash plate type compressor.

FIG. 10 is a partial sectional view showing a conventional technique.

BEST MODE FOR CARRYING OUT THE INVENTION

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

The 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 bar and a housing 12 joined and fixed to the front end of the cylinder block 11, and a valve port at the rear end of the cylinder block 11. And a rear housing 14 joined and fixed via a formed body 13.

[0029] In the housing of the compressor 10, a crank chamber 15 is defined between the cylinder block 11 and the front housing 12. 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 via a power transmission mechanism PT of an engine E force clutchless type (constant transmission type) which is a traveling drive source of the vehicle. Therefore, during the operation of the engine E, the drive shaft 16 is constantly rotated by receiving the power supply from the engine E.

[0030] A rotor 17 is fixed to the drive shaft 16 in the crank chamber 15 so as to be able to rotate. In the crank chamber 15, a first swash plate 18 having a substantially disk shape is accommodated. At the center of the first swash plate 18, a through hole 18a is formed. The drive shaft 16 is passed through the through hole 18a of the first swash plate 18. The first swash plate 18 is slidably and tiltably supported on the drive shaft 16 via a through hole 18a. A hinge mechanism 19 is interposed between the rotor 17 and the first swash plate 18.

[0031] The hinge mechanism 19 includes two rotor-side projections 41 (one of which is not shown on the front side of the drawing) projecting from the rear surface of the rotor 17, and a rotor projection 41 on the front surface of the first swash plate 18. And a swash plate side projection 42 protruding toward the 17th side. The swash plate side projection 42 has two It enters between the protrusions 41 on the data side. Therefore, 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.

[0032] At the center of the rear surface of the first swash plate 18, a substantially cylindrical support portion 39 is provided so as to surround the drive shaft 16. Outside the support portion 39 of the first swash plate 18, a disc-shaped second swash plate 51 is disposed in a state where the support portion 39 is inserted through a support hole 51a formed through the center thereof. ing. As the second swash plate 51, one having a radius substantially equal to that of the first swash plate 18 is used.

[0033] 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 51a 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 retainer 53b.

[0034] The second swash plate 51 is supported via the radial bearing 52 and the thrust bearing 53, so that the second swash plate 18 can be rotated relative to the first swash plate 18 and tilted integrally therewith. Supported by Part 39).

A cam portion 43 is formed at the base of the rotor-side projection 41. A cam surface 43a is formed on a rear end surface of the cam portion 43 facing the first swash plate 18. The tip of the swash plate side projection 42 is slidably abutted against the cam surface 43a of the force portion 43. Accordingly, the hinge mechanism 19 moves the first swash plate 18 and the second swash plate 51 by moving the tip of the swash plate-side protrusion 42 on the cam surface 43a of the cam portion 43 in the direction of contact with and separation from the drive shaft 16. Guide the tilt.

[0036] A plurality of cylinder bores 22 are formed in the cylinder block 11 around the axis L of the drive shaft 16 at equal angular intervals in the front-rear direction (lateral direction on the paper). The single-headed piston 23 is accommodated in each cylinder bore 22 so as to be movable in the front-rear direction. The front-rear opening of the cylinder bore 22 is 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-rear direction is defined in the cylinder bore 22. Have been.

[0037] The piston 23 has a cylindrical head 37 inserted into the cylinder bore 22 and a neck 38 located outside the cylinder bore 22 and located in the crank chamber 15 connected in the front-rear direction. Head 37 The neck 38 is made of an aluminum-based metallic material (pure aluminum or an aluminum alloy). Inside the neck portion 38, a pair of shoe seats 38a are recessed. Inside the neck portion 38, a first show 25A and a second show 25B that form a hemisphere are provided. The first shoe 25A and the second shoe 25B are made of an iron-based metal material. In this specification, the term “hemisphere” refers to a sphere having a part of the spherical surface, which does not mean only a bisected sphere.

[0038] The first shoe 25A and the second shoe 25B are each spherically received by the corresponding shoe seat 38a with a hemispherical surface 25a. The hemispherical surface 25a of the first show 25A and the hemispherical surface 25a of the second show 25B exist on the same spherical surface with the point P as the center. Each piston 23 is moored to the outer periphery of the first swash plate 18 and the second swash plate 51 via the first shower 25A and the second shower 25B. The first shoe 25A located on the opposite side to the compression chamber 24 is in contact with the front surface of the first swash plate 18 with a planar sliding contact surface 25b on the opposite side to the hemispherical surface 25a. The second shoe 25B on the compression chamber 24 side, that is, on 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 hemispheric surface 25a.

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

[0040] In the housing of the compressor 10, a suction chamber 26 and a discharge chamber 27 are separately formed between the valve / port forming body 13 and the rear housing 14. The valve port forming body 13 is formed with a suction port 28 and a suction valve 29 so as to be located between the compression chamber 24 and the suction chamber 26. The discharge port 30 and the discharge valve 31 are respectively formed in the valve port forming body 13 so as to be located between the compression chamber 24 and the discharge chamber 27. [0041] Carbon dioxide is used as a refrigerant in the refrigeration circuit. External circuit (not shown) Force Refrigerant gas introduced into the suction chamber 26 moves from the top dead center position to the bottom dead center position side of each piston 23, and is sucked into the compression chamber 24 via the suction port 28 and the suction valve 29. Is done. The refrigerant gas sucked into the compression chamber 24 is compressed to a predetermined pressure by moving from the bottom dead center position of the piston 23 to the top dead center position side, and is discharged through the discharge port 30 and the discharge valve 31 to the discharge chamber 27. Is discharged. The refrigerant gas in the discharge chamber 27 is led to an external circuit.

[0042] In the housing of the compressor 10, a bleed passage 32, an air supply passage 33, and a control valve 34 are provided. The bleed 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 well-known control valve 34 composed of a solenoid valve is provided.

By adjusting the opening of the control valve 34 by external power supply control, the amount of high-pressure discharge gas introduced into the crank chamber 15 through the air supply passage 33 and the crank through the bleed passage 32 The balance with the amount of gas led out from the chamber 15 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 in accordance with the change in the internal pressure of the crank chamber 15, and as a result, the inclination angles of the first swash plate 18 and the second swash plate 51 are changed. The stroke of the piston 23 or the displacement of the compressor is adjusted.

For example, when the valve opening of the control valve 34 decreases, the internal pressure of the crank chamber 15 decreases. Therefore, the inclination angles of the first swash plate 18 and the second swash plate 51 increase, the stroke of the piston 23 increases, and the discharge capacity of the compressor 10 increases. Conversely, when the valve opening of the control valve 34 increases, the internal pressure of the crank chamber 15 increases. Therefore, the inclination angle of the first swash plate 18 and the second swash plate 51 decreases, the stroke of the piston 23 decreases, and the displacement of the compressor 10 decreases.

Now, 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 located at the top dead center with respect to the center axis Ml of the first swash plate 18. It is eccentrically provided on the piston 23A side at the position. Stated another way, the support portion 39 is provided eccentrically on the side (the 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 center axis Ml. Has been. Therefore, the second swash plate 51, the radial bearing 52, and the thrust bearing 53 (retainer 53b) are located at the top dead center with respect to the first swash plate 18. It is eccentric to the piston 23A side. Therefore, the center axis M2 of the second swash plate 51, the radial bearing 52, and the thrust bearing 53 is, with respect to the center axis Ml of the first swash plate 18, the first shoe 25A of the piston 23A at the top dead center position and It is slightly parallel (for example, 0.055 mm; exaggerated in the drawing) to the center point P side of the second show 25B.

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

In the outer peripheral edge of the second swash plate 51, the portion corresponding to the vicinity of the piston 23 B at the bottom dead center position has a larger diameter than the outer peripheral edge of the first swash plate 18. It will be located inside the direction. That is, the portion of the outer peripheral edge of the second swash plate 51 corresponding to the vicinity of the hinge mechanism 19 is located radially inward of the first swash plate 18 from the outer peripheral edge 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 becomes smaller. 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. Les ,. 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 smaller, there is no limitation on the durability of the second swash plate 51 and the second shoe 25B. No problem.

[0048] In the outer peripheral edge of the first swash plate 18, a portion corresponding to the piston 23A at the top dead center position and a portion located in front and rear of the portion in the circumferential direction are opposite to the second swash plate 51. An inclined surface (chamfered) is provided on the convex corner portion 18b. That is, in the outer peripheral edge portion of the second swash plate 51 corresponding to the vicinity of the hinge mechanism 19, a slope (chamfer) is provided at the convex corner 18b opposite to the second swash plate 51. 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 23 is arranged at the top dead center position, the convex angle portion 18b opposite to the piston 23A is formed. An inclined surface is provided. The slope (chamfer) of the convex corner 18b is The portion corresponding to the piston 23A at the top dead center position is provided so as to become gradually smaller as it becomes circumferentially farther from the largest portion. The inclined surface (chamfer) of the convex corner portion 18b is provided within a quarter-peripheral region with a portion corresponding to the piston 23A at the top dead center position being in the middle.

[0049] In the outer peripheral edge of the first swash plate 18, a portion corresponding to the piston 23B at the bottom dead center position and a portion located in front and rear of the portion in the circumferential direction are provided with a protrusion on the second swash plate 51 side. An inclined surface (chamfer) is provided at the corner 18c. In other words, in the portion of the outer peripheral edge of the first swash plate 18 corresponding to the circumferential range of the first swash plate 18 in which the piston 23B is arranged at the bottom dead center position, the protrusion 23c on the opposite side to the piston 23B is formed. An inclined surface is provided.

The inclined surface (chamfer) is provided so that a portion corresponding to the piston 23B at the bottom dead center position is the largest, and gradually becomes smaller as the portion is circumferentially separated from the portion. The inclined surface (chamfered) of the convex corner portion 18c is provided within a quarter-peripheral region with a portion corresponding to the piston 23B at the bottom dead center position as a center. 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 center axis Ml of the first swash plate 18. Has been.

The present embodiment having the above configuration has the following effects.

(1-1) By disposing the second swash plate 51 eccentrically on the piston 23A side located at the top dead center position with respect to the first swash plate 18, the first swash plate 18 and the second swash plate 51 are arranged. 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 without increasing the diameter of the piston. 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 reduced while the durability and the size of the piston 23 are reduced. Performance can be improved.

(1_2) As in the present embodiment, in the swash plate structure including the thrust bearing 53 in addition to the first swash plate 18 and the second swash plate 51, the first shower 25A and the The thickness between 2 SHU and 25B becomes thicker. In such a conditionally strict configuration, the second swash plate 51 is eccentric with respect to the first swash plate 18 so that the second shroud 25B and the second swash plate 51 of the piston 23 near the top dead center position are connected to each other. The contact area of the second swash plate 51 and the second shoe 25B can be improved while suppressing the decrease in the durability and the size of the piston 23. It is effective for

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

[0053] Accordingly, by providing an inclined surface at the protruding portion (a part of the entire circumference of the convex corners 18b, 18c) of the first swash plate 18, it is possible to suppress a decrease in the durability and an increase in size of the piston 23, The diameter of the first swash plate 18 can be increased. Therefore, the support of the second swash plate 51 by the first swash plate 18 becomes preferable, 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 an improvement in the durability of the second swash plate 51.

(1-4) Carbon dioxide is used as the refrigerant in the refrigeration circuit. When a carbon dioxide refrigerant is used, the pressure in the refrigeration circuit is much higher than when a chlorofluorocarbon refrigerant (for example, R134a) is used. Therefore, also in the compressor, the compression reaction force acting on the piston 23 increases, and the pressing force between the second swash plate 51 and the second shoe 25B increases. In this embodiment, embodying the present invention 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 size of the piston 23. Becomes effective.

Next, a second embodiment of the present invention will be described with reference to FIG. 3 and FIG. In the present embodiment, only differences from the first embodiment will be described, and the same or corresponding parts will be denoted by the same reference characters and detailed description thereof will be omitted.

[0056] 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 side opposite to the compression chamber 24, has a first sliding contact surface 25b opposite to the hemispheric surface 25a. The swash plate 18 is slidably abutted against the front surface of the outer peripheral portion 18-1. Also hinge machine The second shoe 25B on the side opposite to the structure 19, that is, on the compression chamber 24 side and receiving the compression reaction force, has an outer peripheral portion 51-2 of the second swash plate 51 on a sliding contact surface 25b opposite to the hemispheric surface 25a. It is slidably abutted against the rear surface of the. The sliding surface 25b of the first shoe 25A has a middle-high shape whose central portion protrudes toward the first swash plate 18 (see FIG. 4. The middle-high shape is exaggerated in FIG. 4). The sliding surface 25b of the second shoe 25B has a planar shape.

[0057] Between the support portion 39 constituting the inner peripheral portion of the first swash plate 18 and the inner peripheral portion 51-1 of the second swash plate 51, specifically, the outer peripheral surface of the support portion 39 and the second swash plate 51 A radial bearing 52A composed of a rolling bearing is interposed between the support hole 51a and the inner peripheral surface of the support hole 51a. The radial bearing 52A has an outer race 52a attached to the inner peripheral surface of the support hole 51a in the second swash plate 51, and an inner race 52b attached to the outer peripheral surface of the support portion 39 in the first swash plate 18. And a plurality of rollers 52c as rolling elements interposed between the outer race 52a and the inner race 52b.

[0058] 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 between the first shoe 25A and the second shoe 25B, a thrust made of a rolling bearing is provided. Bearing 53 is interposed. The thrust bearing 53 has a plurality of rollers 53a as rolling elements, and the plurality of rollers 53a are rotatably held by a retainer 53b. 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 a carburizing heat treatment. The corners at both ends of the roller 53a are chamfered to prevent the roller 53a from hitting the second swash plate 51 and the race 55 to damage the second swash plate 51 and the race 55. .

At the rear surface of the first swash plate 18, an annular locking portion 18 d protrudes from the outermost periphery of the outer peripheral portion 18-1 toward the second swash plate 51. The race 55 is disposed inside the locking portion 18d, and the race 55 is locked to the first swash plate 18 on the radially outer side by abutment of the outer peripheral edge thereof with the locking portion 18d. The race 55 is rotatable relative to the first swash plate 18 by being guided by the locking portion 18d.

[0060] The second swash plate 51 is supported by the first swash plate 18 via the radial bearing 52A and the thrust bearing 53 so that the second swash plate 51 can rotate relative to the first swash plate 18 and can be tilted integrally. Is held. Therefore, when the first swash plate 18 rotates, the radial bearing 52A and the thrust bearing 53 act to cause a rolling between the first swash plate 18 and the second swash plate 51, thereby causing the surfaces to face each other. Mechanical loss due to slippage is replaced by mechanical loss due to rolling, and the occurrence of mechanical loss in the compressor can be greatly suppressed.

The thickness Y1 of the inner peripheral portion 51-1, which is supported by the radial bearing 52A in the second swash plate 51, is the thickness Y2 of the outer peripheral portion 51-2, which is supported by the thrust bearing 53 in the second swash plate 51. It is thicker than it is. Specifically, the thickness Y2 of the outer peripheral portion 51-2 of the second swash plate 51 is at least half the 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 thinner than the thickness of 1. The thickness Y1 of the inner peripheral portion 51-1 of the second swash plate 51 is larger than the thickness X of the outer peripheral portion 18-1 of the first swash plate 18.

[0062] The inner peripheral portion 51-1 of the second swash plate 51 has a cylindrical first protruding portion 56 protruding from the first swash plate 18 side and a protruding portion on the opposite side to the first swash plate 18. The second swash plate 51 has a greater thickness than the outer peripheral portion 51-2 of the second swash plate 51 by providing the cylindrical second projecting portion 57 (Y1> Y2). The first protrusion 56 and the second protrusion 57 are disposed coaxially with the support hole 51a, and the inner peripheral surfaces of the first protrusion 56 and the second protrusion 57 are formed on the inner periphery of the support hole 51a. Form a part of the surface. The outer diameter Z2 of the second protrusion 57 is smaller than the outer diameter Z1 of the first protrusion 56. Further, the outer peripheral angle 57a of the distal end surface of the second projecting portion 57 is chamfered in a tapered shape as a whole.

In the second embodiment, the same effects as those of 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, a second swash plate 18 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. A thrust bearing 53 that supports the plate 51 so as to be rotatable relative to the first swash plate 18 is provided. The second swash plate 51 is 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 52A is provided for supporting as much as possible.

Therefore, by the action of the thrust bearing 53 and the radial bearing 52A, 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 and the first swash plate 18 The force S can effectively reduce the rotational resistance generated between the inner peripheral portion (support portion 39) and the inner peripheral portion 51-1 of the second swash plate 51. Therefore, even in the compressor 10 used for 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 a mechanical loss due to rolling. As a result, it is possible to effectively suppress problems such as mechanical loss and seizure. Wear.

(2-2) The thickness Y2 of the outer peripheral portion 51-2 of the second swash plate 51 is equal to or more than half the thickness X of the outer peripheral portion 18-1 of the first swash plate 18 and the thickness of the outer peripheral portion 18_1. It is thinner than thickness X. In order to avoid increasing the size of the bistone 23, that is, increasing the size of the compressor, the space between the first shoe 25Α and the second shoe 25Β will be limited. In this limited space, if the thickness X of the outer peripheral portion 18-1 of the first swash plate 18 is increased, the thickness Υ2 of the outer peripheral portion 51-2 of the second swash plate 51 must be reduced. (2) When the thickness Υ2 of the outer peripheral portion 51-2 of the swash plate 51 is increased, the thickness X of the outer peripheral portion 18-1 of the first swash plate 18 needs to be reduced.

[0066] From the standpoint of receiving the compression reaction force, the first swash plate 18 and the second swash plate 51 both secure the strength by increasing the thicknesses X and Υ2 of the outer peripheral portions 18-1, 51-2 as much as possible. In the first swash plate 18 to which the necessary force S is transmitted from the drive shaft 16, the thickness X of the outer peripheral portion 18-1 can be secured by sliding with respect to the first swash plate 18. The priority should be given to securing the thickness 51 of the outer peripheral portion 51-2 of the plate 51. In this sense, the force of the second swash plate 51 is set such that the thickness Υ2 of the outer peripheral portion 51-2 is equal to or more than half the thickness X of the outer peripheral portion 18-1 of the first swash plate 18 and the outer peripheral portion 18-1 It is to be set thinner than the sheet thickness X of.

(2-3) In the second swash plate 51, the plate thickness Y1 of the inner peripheral portion 51-1 is larger than the plate thickness Υ2 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 °, and can further improve the sliding between the first swash plate 18 and the second swash plate 51. Further, the outer peripheral portion 51-2 of the second swash plate 51, which is relatively thinner than the inner peripheral portion 51-1, allows the outer peripheral portion 18- of the first swash plate 18 to be stronger in strength than the second swash plate 51. (1) It is easy to secure the plate thickness.

(2-4) The thickness Υ2 of the outer peripheral portion 51-2 of the second swash plate 51 is smaller than the 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 facilitates securing the thickness of the outer peripheral portion 18-1 of the first swash plate 18, which is stricter in strength than the second swash plate 51. In the second swash plate 51, the thickness Y1 of the inner peripheral portion 51-1 is larger than the thickness X of the outer peripheral portion 18-1 of the first swash plate 18. Therefore, the support of the second swash plate 51 by the radial bearing 52 ° is further stabilized.

[0069] (2-5) In the first projecting portion 56 and the second projecting portion 57 constituting the inner peripheral portion 51-1 of the second swash plate 51, the outer diameter of the second projecting portion 57 Ζ2 Is smaller than the outer diameter Z1 of the first protrusion 56. Part of the second protruding portion 57 comes extremely close to the piston 23B at the bottom dead center position, for example, in a state where the discharge capacity of the compressor 10 is maximum (the state in FIG. 3). Therefore, making the second projecting portion 57 smaller in diameter than the first projecting portion 56 and separating it from the piston 23 avoids the interference between the second swash plate 51 and the bistone 23 and reduces the second swash plate. This is effective in increasing the thickness Y1 of the inner peripheral portion 51-1 of the plate 51.

[0070] (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 an outer peripheral angle 57a of the tip end surface. In the second protruding portion 57, for example, when the discharge capacity of the compressor is at a maximum, a part of the outer peripheral angle 57a of the distal end surface is extremely close to the piston 23B at the bottom dead center position. Therefore, providing a chamfer at the outer peripheral angle 57a of the distal end surface of the second projecting portion 57 avoids interference between the second swash plate 51 and the piston 23 and reduces the inner peripheral portion 51a of the second swash plate 51. This is effective in achieving a balance between increasing the thickness of Y1.

[0071] (2-7) A portion of the outer peripheral edge of the first swash plate 18 corresponding to the piston 23A at the top dead center position has an inclined surface (a convex corner portion 18b opposite to the second swash plate 51). Chamfer). Therefore, the diameter of the first swash plate 18 and the second swash plate 51 can be increased while suppressing a decrease in durability and an increase in size of the piston 23. Accordingly, 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 reduced while suppressing the decrease in the durability and the size of the piston 23. Can be improved.

[0072] That is, the first swash plate 18 inclined with respect to the drive shaft 16 has a convex corner 18b (chamfered) opposite to the second swash plate 51 at the outer peripheral edge corresponding to the piston 23A at the top dead center position. (No state) Force Forcedly protrudes radially of drive shaft 16. When the convex corner 18b on the first swash plate 18 opposite to the second swash plate 51 protrudes largely in the radial direction, a neck 38 of the piston 23 corresponding to the protruding portion is formed in order to avoid interference with the protruding portion. It is conceivable to reduce the wall thickness or increase the diameter of the neck 38 in the radial direction. However, reducing the thickness of the neck 38 reduces the durability of the piston 23, and increasing the size of the neck 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 above-mentioned interference between the convex corner 18b and the piston 23. However, if the radius of the first swash plate 18 is reduced, the radius of the second swash plate 51 which needs to be supported by the first swash plate 18 must be reduced. What? Therefore, in particular, in the piston 23 near the top dead center position (compression stroke), the contact area between the second swash plate 51 and the second swash plate 51 receiving a large compression reaction force is reduced, and the second swash plate 51 and the second swash plate 51 There is a problem that the durability of the 2 SH 25B is reduced.

(2-8) The roller 52c is used as a rolling element of the radial bearing 52A. A rolling bearing using the roller 52c as a rolling element has better load resistance than, for example, a case using a ball as a rolling element. This leads to a reduction in the size of the radial bearing 52A and a reduction in the size of the compressor 10.

(2-9) The race 55 is interposed between the roller 53a 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, in a configuration in which 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 (corresponding to the piston 23 near the top dead center position) is used. However, a large compression reaction force is concentrated on the portion where the heat is applied, and there is a problem that the portion is locally worn and deteriorated. However, in the present embodiment, the race 55 is interposed between the roller 53a and the first swash plate 18, and the compression reaction force acting on the roller 53a reduces the surface pressure through the race 55. Then, since the first swash plate 18 acts on the first swash plate 18, it is possible to suppress the first swash plate 18 from being locally worn and deteriorated. Further, in the race 55 that rotates relative to the first swash plate 18, the portions where a large compression reaction force acts via the rollers 53a are sequentially switched, so that it is possible to prevent the race 55 from being locally worn and deteriorated.

[0077] (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 abuts against the locking portion 18d. As a result, the race 55 is locked to the first swash plate 18 on the radially outer side.

Here, for example, in a configuration in which a 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 radial inside, the first swash plate 18 When the lubricating oil (refrigerant oil) attached to the cylinder moves radially outward due to the action of centrifugal force, the lubricating oil enters between the first swash plate 18 and the race 55 at the locking portion. It will be hindered. According to the present embodiment in which the race 55 is locked to the first swash plate 18 on the radial outside, the lubricating oil enters between the first swash plate 18 and the race 55 by the locking portion 18d. It is possible to prevent the swash plate from being hindered and to make the sliding between the first swash plate 18 and the race 55 good. (2-11) The locking portion 18d has an annular shape. Accordingly, the locking of the race 55 by the locking portion 18d is performed stably, 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. Note that, in the present embodiment, only differences from the second embodiment will be described, and the same or corresponding members will be denoted by the same reference characters and detailed description thereof will be omitted.

In the present embodiment, the support portion 39 is not eccentric with respect to the center axis Ml of the first swash plate 18. That is, 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, on the outer peripheral edge of the first swash plate 18, a portion corresponding to the piston 23B at the bottom dead center position is such that the convex corner portion 18c on the second swash plate 51 side is radially larger than the second swash plate 51. Since it does not protrude, there is no problem if the chamfered portion 18c is not chamfered as shown in FIG.

In the present embodiment, the PCD force of the thrust bearing 53 is set at the center point of the first shoe 25A and the second shoe 25B about the central axis Ml, M2 of the first swash plate 18 and the second swash plate 51. It is made larger than the diameter of the virtual cylinder passing through P. In this way, the thrust bearing 53 (the 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 means that the center of the thrust bearing 53 (the center axes Ml and M2 of the first swash plate 18 and the second swash plate 51) is the center axis, and the roller 53a is on the rotation center axis. Refers to the diameter of the virtual cylinder passing through the intermediate point.

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

The drive shaft 16 has the rotor 17 fixed thereto, and the swash plate 58 supported so as to be slidable and tiltable in the axial direction of the drive shaft 16. Connecting pieces 59 and 60 are fixed to the swash plate 58, and guide pins 61 and 62 are fixed to the connecting pieces 59 and 60. The rotor 17 has a pair of guide holes 171 (only one is shown). 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 rotates integrally with the drive shaft 16 by linking the guide hole 171 and the guide pins 61 and 62. It is possible. 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.

[0085] The solid line position of the swash plate 58 in Fig. 6 indicates the maximum inclination state of the swash plate 58. When the center of the swash plate 58 moves toward the cylinder block 11, the inclination angle of the swash plate 58 decreases. The dashed line position of the swash plate 58 in FIG. 6 indicates the minimum inclination state of the swash plate 58.

[0086] In the outer peripheral edge of the swash plate 58, a portion corresponding to the piston 23A at the top dead center position and a portion located in the front and rear direction with respect to the portion are provided with a convex corner portion 58a opposite to the piston 23. Is provided with an inclined surface. That is, in the outer peripheral edge portion of the swash plate 58 corresponding to the vicinity of the hinge mechanism 19A, an inclined surface is provided at the convex corner portion 58a on the hinge mechanism 19A side. In other words, at the outer peripheral edge of the swash plate 58 corresponding to the circumferential range of the swash plate 58 in which the piston 23A is arranged at the top dead center position, an inclined surface is provided at the convex corner 58a opposite to the piston 23. ing. As shown in FIG. 7, the inclined surface of the convex corner portion 58a is provided so that the portion corresponding to the piston 23 at the top dead center position becomes gradually smaller as it is further away in the circumferential direction from the largest portion. Have been.

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

[0088] The swash plate 58 inclined with respect to the drive shaft 16 has a convex corner portion 58a opposite to the piston 23 at the outer peripheral edge corresponding to the piston 23A at the top dead center position. Will protrude greatly. Therefore, by providing an inclined surface at a protruding portion (a part of the convex corner portion 58a) of the swash plate 58, it is possible to increase the diameter of the swash plate 58 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 near the top dead center position. This leads to improved durability of the swash plate 58.

[0089] Note that, for example, the following embodiments can be implemented without departing from the spirit of the present invention. The

(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 omitted, and the second swash plate 51 is replaced with the first swash plate.

Slide directly to 18.

(3) In the first embodiment, the radial bearing 52 and the thrust bearing 53 are omitted, and the second swash plate 51 is fixed to the first swash plate 18 so that the second swash plate 51 is connected to the first swash plate 18. Be able to rotate integrally.

[0091] In this case, on the outer peripheral edge of the second swash plate 51, a slope (chamfer) is formed at the convex corner on the first swash plate 18 side with respect to the portion corresponding to the piston 23A at the top dead center position. To be provided. In addition, on the outer peripheral edge of the second swash plate 51, a slope (chamfer) is provided at a convex corner opposite to the first swash plate 18 with respect to a portion corresponding to the piston 23B at the bottom dead center position. .

[0092] Referring to FIG. 2, the second swash plate 51 inclined with respect to the drive shaft 16 has a convex angle on the first swash plate 18 side at the outer peripheral edge corresponding to the piston 23A at the top dead center position. The portion protrudes largely in the radial direction of the drive shaft 16. In the second swash plate 51, a convex corner on the outer peripheral edge corresponding to the piston 23B at the bottom dead center position, opposite to the first swash plate 18, protrudes largely in the radial direction of the drive shaft 16. Will be done. Therefore, by providing an inclined surface (chamfer) at the protruding portion (a part of the convex corner portion) of the second swash plate 51, it is possible to suppress the durability and size of the piston 23 from being reduced and increase the size of the second swash plate 51. Can be increased in size. 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 can be further increased. Can be improved.

[0093] (4) In the first embodiment, two sheets, the first swash plate 18 and the second swash plate 51, are used. However, this is changed to, for example, the second swash plate 51 and the second swash plate 51. The third swash plate may be placed between the swash plate and the 25B. In other words, the swash plate structure to which the present invention can be applied is not limited to the structure using only the first swash plate and the second swash plate. It may have a plurality of swash plates.

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

[0095] (6) The present invention is not limited to application to a refrigerant compressor used in a refrigeration circuit, but may be applied to, for example, an air compressor.

(7) The second embodiment is changed, for example, as shown in FIG. 5, the sliding surface 25b of the first shoe 25A is made flat.

[0096] (8) The second embodiment is changed, for example, as shown in Fig. 5, the sliding contact surface 25b of the second shoe 25B is formed in a concave shape with a concave central portion. In this way, the weight of the second shoe 25B reciprocating linearly with the piston 23 can be reduced, the inertia force of the second shoe 25B can be reduced, and the first swash plate 18 and the second swash plate 51 can be reduced. The change of the inclination angle, that is, the change of the displacement of the compressor, can be performed 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 plain 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 center axis M2) acting on the second swash plate 51. By changing this, for example, by arranging the roller 52c so as to be inclined with respect to the center axis M2 of the second swash plate 51, not only the radial load but also the thrust load (in the direction along the center axis M2) can be adjusted. Load).

(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, by arranging the rollers 53a so as to be inclined with respect to the board surface of the second swash plate 51, a configuration in which not only a thrust load but also a radial load can be received.

(13) In the second and third embodiments, the race 55 is eliminated, and the roller 53 a of the thrust bearing 53 is directly rolled on the first swash plate 18.

(14) In the second and third embodiments, the locking portion 18d is omitted, and a locking portion is provided on the inner peripheral portion of the first swash plate 18 (for example, the base of the support portion 39 also serves as the locking portion). By that, The swash plate 55 is to be locked to the first swash plate 18 on the radial inside.

Claims

The scope of the claims

[1] A swash plate is integrally rotatably connected to the drive shaft, and a piston is moored to the swash plate via a shoe. The rotation of the swash plate with the rotation of the drive shaft causes the swash plate to rotate. The gas is compressed by the reciprocating linear movement of the ston, and the displacement of the swash plate is changed by changing the inclination angle of the swash plate.

A swash plate type variable capacity compressor, wherein an inclined surface is provided on a part of the entire outer peripheral edge of the swash plate.

2. The slope according to claim 1, wherein, at an outer peripheral edge of the swash plate, a portion corresponding to the piston at a top dead center position is provided with an inclined surface at a convex corner opposite to the piston. Variable capacity swash plate compressor.

3. The outer peripheral edge of the swash plate, wherein a portion corresponding to the piston at a bottom dead center position is provided with a slope at a convex corner on the piston side. The variable displacement type swash plate type compressor according to any one of the preceding items.

[4] The swash plate includes a first swash plate connected to a drive shaft so as to be integrally rotatable, and a second swash plate supported by the first swash plate. The biston is moored through a first shoe that contacts the first swash plate and a second shoe that receives a compression reaction force that contacts the second swash plate. 4. A part of the outer peripheral edge corresponding to the piston at the top dead center position is provided with an inclined surface at a convex corner opposite to the second swash plate. 2. The variable displacement type swash plate type compressor according to item 1.

[5] The outer peripheral edge of the first swash plate, a portion corresponding to the piston at the bottom dead center position is provided with an inclined surface at a convex corner on the second swash plate side. 4. The variable capacity swash plate compressor described in 4.

6. The variable displacement swash plate compression according to claim 1, wherein the gas is a refrigerant used in a refrigeration circuit, and carbon dioxide is used as the refrigerant.