KR20060057626A - Variable displacement swash plate type compressor - Google Patents

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

VARIABLE DISPLACEMENT SWASH PLATE TYPE COMPRESSOR

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

As shown in FIG. 9, in this kind of swash plate type compressor, the swash plate 92 is rotatably connected to the drive shaft 91. On the outer circumferential portion of the swash plate 92, a migrating piston 94 is moored through a pair of shoes 93A and 93B each forming a hemispherical shape. Therefore, when the swash plate 92 rotates by the rotation of the drive shaft 91, the swash plate 92 slides with respect to each shoe 93A, 93B, and the piston 94 moves reciprocally linearly, and the refrigerant gas is compressed. This is done.

The shoes 93A and 93B are centered on their axis S (a line of curvature P of the spherical surface and perpendicular to the sliding surface with the swash plate 92) according to the relative rotation with the swash plate 92. One rotational motion is performed. The rotational movement of the shoes 93A and 93B centered on the axis S is a total of the shoes 93A, as a total from the difference in the peripheral speed of the outer peripheral side in the inner and outer circumferences of the swash plate 92 becomes large. It is implemented in the same state as the rotational force in one direction about the axis S with respect to 93B).

In short, the swash plate type compressor shown in FIG. 9 has a configuration in which the shoes 93A and 93B slide directly with respect to the swash plate 92. Therefore, the shoes 93A and 93B had to make the rotational movement around the axis S unnecessary by sliding based on the relative rotation with the swash plate 92. Therefore, especially the mechanical loss in the sliding part of the piston 94 and the shoe 93B of the side which receives a compression reaction force becomes large, and there existed a problem which generate | occur | produced a problem, such as a press in this sliding part.

In order to solve such a problem, the technique as shown in FIG. 10 is proposed, for example (refer patent document 1). That is, the step part 90a is formed in the center part in the center part in the back surface (surface facing the figure right side) of the swash plate (henceforth 1st swash plate 90). On the outside of the stepped portion 90a in the first swash plate 90, an annular sliding plate (hereinafter referred to as a second swash plate 95) is rotated relative to the first swash plate 90 at a coaxial position. This is possibly supported. The outer circumferential 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, slippage occurs between the first swash plate 90 and the second swash plate 95, and the rotational speed of the second swash plate 95 is rotated by the first swash plate 90. It is lower than speed. Therefore, the relative rotational speeds of the second swash plate 95 and the second shoe 93B are lower than the relative rotational speeds of the second shoe 93B and the first swash plate 90. As a result, the rotational movement of the 2nd shoe 93B centered on the axis S resulting from the relative rotation of the 2nd swash plate 95 and the 2nd shoe 93B can be suppressed, and the above-mentioned mechanical hand The occurrence of a seal or a problem can be suppressed.

Here, it is also proposed to interpose a transmission element between the first swash plate 90 and the second swash plate 95 between the first shoe 93A and the second shoe 93B (see Patent Document 2, for example). ]. Moreover, in patent document 2, the race by the side of the 2nd shoe 93B which a thrust bearing has can be grasped | ascertained as the 2nd swash plate 95. Moreover, in FIG. In this case, the slip between the first swash plate 90 and the second swash plate 95 becomes good, so that the relative rotational speeds of the second swash plate 95 and the second shoe 93B are adjusted with the second shoe 93B. It is possible to lower the relative rotation speed of the first swash plate 90 larger than that.

By the way, in addition to the 1st swash plate 90, in the swash plate structure provided with the 2nd swash plate 95 and the rolling element further, between the 1st shoe 93A and the 2nd shoe 93B in a swash plate structure The thickness becomes thicker. Therefore, the 1st swash plate 90 which inclines with respect to the drive shaft 91 is a side opposite to the 2nd swash plate 95 in the outer peripheral edge part corresponding to the vicinity of the piston 94 (state of FIG. 10) in a top dead center position. The convex-angle part 90b of this will protrude largely toward the radial direction (upper drawing) of the drive shaft 91. FIG. Moreover, the 2nd swash plate 95 which inclines with respect to the drive shaft 91 is a side opposite to the 1st swash plate 90 in the outer peripheral edge part corresponding to the vicinity of the piston 94 (state not shown) in a bottom dead center position. The convex-angle part 95b of protrudes large toward the radial direction of the drive shaft 91. As shown in FIG.

If the convex angle portion 90b of the first swash plate 90 and the convex angle portion 95b of the second swash plate 95 protrude largely in the radial direction of the drive shaft 91, in order to avoid interference with this protruding portion, the piston It is necessary to make thin the thickness of the part corresponding to this protrusion part in 94, or to enlarge the piston 94 in radial direction. The thinning of the piston 94 leads to a decrease in durability, and the enlargement of the piston 94 leads to the problem that the swash plate type compressor is enlarged. Therefore, in the related art, when the thickness of the swash plate structure is to be increased, the radiuses of the first swash plate 90 and the second swash plate 95 are reduced, and the above-mentioned convex angle parts 90b and 95b and the piston 94 are described. ) To avoid interference.

However, when the radius of the 1st swash plate 90 and the 2nd swash plate 95 is made small, the 2nd shoe 93B which receives a big compression reaction force especially in the piston 94 in the vicinity of a top dead center position (compression stroke). The contact area of the 2nd swash plate 95 became narrow, and there existed a problem that the durability of the 2nd swash plate 95 and the 2nd shoe 93B fell.

Recently, it has become common to use carbon dioxide as a refrigerant in a refrigeration circuit. When a carbon dioxide refrigerant is used, the pressure in the refrigerating circuit is much higher than when a freon refrigerant (for example, R134a) is used. Accordingly, even in the swash plate type compressor, the compression reaction force acting on the piston 94 increases, so that the above-described problem (the durability of the second swash plate 95 and the second shoe 93B is lowered) does not arise.

Patent Document 1: Japanese Patent Application Laid-open No. Hei 8-338363 (No. 4 page, Fig. 1)

Patent Document 2: Japanese Patent Application Laid-open No. Hei 8-28447 (3rd page, Fig. 1)

Disclosure of the Invention

An object of the present invention is to provide a variable displacement swash plate type compressor which can improve the durability of a swash plate and a shoe while suppressing a decrease in the durability and enlargement of a piston.

In order to achieve the above object, the invention, the swash plate is integrally rotatably connected to the drive shaft, the piston is mooring through the shoe to the swash plate, by the rotation of the swash plate according to the rotation of the drive shaft, A variable displacement swash plate type compressor in which reciprocating linear motion is performed to compress gas and the discharge capacity is changed by changing the inclination angle of the swash plate, and the variable capacity type having an inclined surface formed on a part of the entire circumference of the outer peripheral portion of the swash plate Provide a swash plate compressor.

By providing the inclined surface at the projected convex angle portion of the outer circumferential edge portion of the swash plate which is inclined with respect to the drive shaft, the swash plate can be made larger in diameter while suppressing the decrease in durability and enlargement of the piston. Therefore, a large compression reaction force acting on the swash plate through the shoe can be preferably received. This leads to an improvement in the durability of the swash plate and the shoe.

In a preferable example, the inclined surface is formed in the convex-angle part on the opposite side to the said piston in the part corresponding to the said piston in the top dead center position in the outer peripheral edge part of the said swash plate. That is, in the part of the outer peripheral edge part of the swash plate corresponding to the range of the circumferential direction of the swash plate which arrange | positions a piston at top dead center position, the inclined surface is formed in the convex-angle part on the opposite side to a piston.

In the swash plate which is inclined with respect to the drive shaft, the convex angle portion opposite to the piston protrudes largely toward the radial direction of the drive shaft at the outer peripheral edge portion corresponding to the piston at the top dead center position. Therefore, a large compression reaction force acting on the swash plate can be preferably received through the shoe of the piston near the top dead center position. This leads to an improvement in the durability of the swash plate and the shoe.

In a preferable example, the inclined surface is formed in the convex-angle part on the said piston side in the part corresponding to the said piston in the bottom dead center position in the outer peripheral edge part of the said swash plate. That is, in the part of the outer peripheral edge part of the swash plate corresponding to the range of the circumferential direction of the swash plate which arrange | positions a piston at a bottom dead center position, the inclined surface is formed in the convex-angle part on the piston side.

In the swash plate, at the outer circumferential edge portion corresponding to the piston at the bottom dead center position, the convex angle portion on the piston side protrudes greatly toward the radial direction of the drive shaft. Therefore, by chamfering the protruding portion of the swash plate, the first swash plate can be made large in diameter while suppressing deterioration and increase in durability of the piston.

In a preferable example, the swash plate is composed of a first swash plate which is rotatably connected to the drive shaft and a second swash plate supported by the first swash plate, and the first and second swash plates contact the first swash plate. The piston is moored through the first shoe and the second shoe on the side receiving the compression reaction force against the second swash plate, and on the outer circumferential edge of the first swash plate, a portion corresponding to the piston at the top dead center position is provided. The inclined surface is formed in the convex-angle part on the opposite side to the said 2nd swash plate. That is, in the part of the outer peripheral part of the 1st swash plate corresponding to the range of the circumferential direction of the 1st swash plate which arranges a piston in a top dead center position, the inclined surface is formed in the convex-angle part on the opposite side to a 1st swash plate.

As for the 1st swash plate which inclines with respect to a drive shaft, the convex-angle part on the opposite side to a 2nd swash plate will protrude largely toward the radial direction of a drive shaft in the outer peripheral edge part corresponding to the piston in a top dead center position. Therefore, by chamfering the protrusion part in a 1st swash plate, a 1st swash plate can be made large diameter, suppressing the fall of piston durability and enlargement. Therefore, support of the second swash plate by the first swash plate is preferable, and a large compression reaction force acting on the second swash plate through the second shoe of the piston in the vicinity of the top dead center position is achieved by the first swash plate through the second swash plate. It can receive preferably. This leads to an improvement in the durability of the second swash plate and the second shoe.

In a preferable example, the inclined surface is formed in the convex-angle part by the side of the said 2nd swash plate in the part corresponding to the said piston in the bottom dead center position in the outer peripheral edge part of a said 1st swash plate. That is, in the part of the outer peripheral part of the 1st swash plate corresponding to the range of the circumferential direction of the 1st swash plate which arrange | positions a piston in a bottom dead center position, the inclined surface is formed in the convex-angle part on the 2nd swash plate side.

In the swash plate, at the outer circumferential edge portion corresponding to the piston at the bottom dead center position, the convex angle portion on the piston side protrudes greatly toward the radial direction of the drive shaft. Therefore, by chamfering the protrusion part in a swash plate, a 1st swash plate can be made large diameter, suppressing the fall of piston durability and enlargement.

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

When a carbon dioxide refrigerant is used, the pressure in the refrigerating circuit is much higher than when a freon refrigerant (for example, R134a) is used. Therefore, even in the variable displacement swash plate type compressor, the compression reaction force acting on the piston is increased, thereby increasing the pressure contact force between the swash plate and the shoe. In this aspect, incorporating the invention as described in any one of Claims 1-5 is especially effective in improving the durability of a swash plate and a shoe, suppressing the fall of piston durability and enlargement.

1 is a longitudinal cross-sectional view of a variable displacement swash plate compressor of a first embodiment of the present invention.

2 is an enlarged view of the main portion of FIG. 1, in which the first and second swash plates do not have a cross section; FIG.

3 is a longitudinal sectional view of a variable displacement swash plate compressor of a second embodiment of the present invention.

FIG. 4 is an enlarged view of the main portion of FIG. 3, wherein the first and second swash plates do not have a cross section (partly broken), and some first and second shoes have a cross section; FIG.

Fig. 5 is an enlarged view of the main portion showing the swash plate structure of the third embodiment of the present invention.

6 is a longitudinal cross-sectional view of a variable displacement swash plate compressor of a fourth embodiment of the present invention.

Fig. 7 A-A cross sectional view of Fig. 6.

8 is an enlarged cross-sectional view of the main portion of FIG. 6.

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

Fig. 10 is a partial cross-sectional view showing a conventional technology.

To practice the invention  Best form for

The first to fourth embodiments of the present invention are described below in which the present invention is embodied as a swash plate compressor of a variable displacement type constituting a refrigeration circuit of a vehicle air conditioner.

A first embodiment will be described with reference to FIGS. 1 and 2. Fig. 1 shows a longitudinal sectional view of a swash plate type compressor (hereinafter simply referred to as compressor 10) of a variable displacement type. 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 bonded and fixed to the front end of the cylinder block 11, and a valve at the rear end of the cylinder block 11. The rear housing 14 joined and fixed through the port forming body 13 is provided.

In the housing of the compressor 10, a crank chamber 15 is partitioned and formed between the cylinder block 11 and the front housing 12. The drive shaft 16 is rotatably arranged between the cylinder block 11 and the front housing 12 so as to pass through the crank chamber 15. The engine E, which is the driving drive source of the vehicle, is operatively connected to the drive shaft 16 through a power transmission mechanism PT of the clutchless type (normally transmission type). Therefore, at the time of operation of the engine E, the drive shaft 16 is always rotated by receiving power from the engine E. FIG.

The rotor 17 is fixed to the drive shaft 16 in the crank chamber 15 so as to be integrally rotatable. In the crank chamber 15, the 1st swash plate 18 which comprises substantially disk shape is accommodated. In the center portion of the first swash plate 18, an insertion through hole 18a is formed to penetrate. The drive shaft 16 is inserted through the insertion hole 18a of the first swash plate 18. The first swash plate 18 is slidably and tiltably supported by the drive shaft 16 via the insertion hole 18a. A hinge mechanism 19 is interposed between the rotor 17 and the first swash plate 18.

The hinge mechanism 19 includes two rotor side protrusions 41 (one of which is not shown on the front side of the surface) formed on the rear surface of the rotor 17 and a front surface of the first swash plate 18. It consists of the swash plate side protrusion 42 which protruded toward the rotor 17 side. The swash plate side protrusion 42 enters between the two rotor side protrusions 41 at the distal end 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.

A substantially cylindrical support portion 39 protrudes from the rear center portion of the first swash plate 18 so as to surround the drive shaft 16. On the outer side of the support part 39 in the first swash plate 18, in the state in which the support part 39 is inserted into the support hole 51a formed by penetrating the center part of the second swash plate 51 having a disc shape. It is arranged. As the 2nd swash plate 51, the thing of the substantially same radius as the 1st swash plate 18 is used.

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

The second swash plate 51 includes the first swash plate 18 so as to be able to rotate relative to the first swash plate 18 and to be tilted integrally by interposing the radial bearing 52 and the thrust bearing 53; It is supported by the support part 39).

The cam part 43 is formed in the base of the rotor side protrusion 41. As shown in FIG. The cam surface 43a is formed in the rear end surface from the cam part 43 toward the 1st swash plate 18. As shown in FIG. The tip end of the swash plate side protrusion 42 is slidably in contact with the cam surface 43a of the cam portion 43. Therefore, the hinge mechanism 19 has the first swash plate 18 and the tip end of the swash plate side projection 42 being moved in the contact / separation direction with respect to the drive shaft 16 on the cam surface 43a of the cam portion 43. The tilting of the second swash plate 51 is guided.

In the cylinder block 11, the several cylinder bore 22 penetrates in the front-back direction (left-right direction of the paper surface) around the axis line L of the drive shaft 16 at the same angular interval. The migrating piston 23 is housed 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 blocked by the front face of the valve port forming body 13 and the piston 23, and the cylinder bore 22 moves in the front and rear directions of the piston 23. The compression chamber 24 whose volume changes according to this is partitioned.

The piston 23 is connected to the circumferential head part 37 inserted into the cylinder bore 22, and the neck part 38 located in the crank chamber 15 on the outer side of the cylinder bore 22 in succession in the front-rear direction. It is done. The head portion 37 and the neck portion 38 are made of an aluminum metal material (pointing to pure aluminum or an aluminum alloy). A pair of shoe seats 38a are formed concave inside the neck portion 38. In the neck portion 38, a hemispherical first shoe 25A and a second shoe 25B are incorporated. The first shoe 25A and the second shoe 25B are made of an iron metal material. In addition, in this specification, "a hemisphere" does not mean only having divided | segmented the sphere into two, but refers to what provided with a part of the spherical surface of a sphere.

The first shoe 25A and the second shoe 25B each have a hemispherical surface 25a and are spherically supported by the corresponding shoe seats 38a. The hemispherical surface 25a of the 1st shoe 25A and the hemispherical surface 25a of the 2nd shoe 25B exist on the same spherical surface centering on the point P. As shown in FIG. Each piston 23 is moored to the outer peripheral portions of the first swash plate 18 and the second swash plate 51 via the first shoe 25A and the second shoe 25B. 25 A of 1st shoes located on the opposite side to the compression chamber 24 have the sliding contact surface 25b of planar shape on the opposite side to the hemispherical surface 25a, and is in contact with the front surface of the 1st swash plate 18. As shown in FIG. In other words, the second shoe 25B on the side of the compression chamber 24 has a sliding contact surface 25b on the opposite side to the hemispherical surface 25a, and is in contact with the rear surface of the second swash plate 51.

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, 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. The rotation speed of the second swash plate 51 is lower than the rotation speed of the first swash plate 18. Therefore, the relative rotation speed of the second swash plate 51 and the second shoe 25B is lower than the relative rotation speed of the second shoe 25B and the first swash plate 18. Therefore, the line passing through the curvature center point P of the axis line S; hemispherical surface 25a resulting from the relative rotation of the 2nd swash plate 51 and the 2nd shoe 25B, and perpendicular | vertical to the sliding contact surface 25b. The rotational motion of the 2nd shoe 25B centering on (circle) can be suppressed, and the occurrence of a mechanical loss and a problem resulting from this rotational motion can be suppressed.

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

Carbon dioxide is used as the refrigerant in the refrigeration circuit. The refrigerant gas introduced into the suction chamber 26 from an external circuit not shown is moved through the suction port 28 and the suction valve 29 by moving from the top dead center position of each piston 23 toward the bottom dead center position. It is sucked into the compression chamber 24. 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, and is discharged through the discharge port 30 and the discharge valve 31. It is discharged to the discharge chamber 27. The refrigerant gas in the discharge chamber 27 is discharged to the external circuit.

In the housing of the compressor 10, a bleeding passage 32, an air supply passage 33, and a control valve 34 are formed. The bleeding 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 disposed.

By adjusting the opening degree of the control valve 34 by the feed control from the outside, the amount of introduction of the discharge gas of high pressure into the crank chamber 15 through the air supply passage 33 and the crank chamber via the bleeding passage 32 are provided. The balance of the gas introduction amount from 15 is controlled, and the internal pressure of the crank chamber 15 is determined. With the change of the internal pressure of the crank chamber 15, the difference between the internal pressure of the rank chamber 15 and the internal pressure of the compression chamber 24 is changed, and the inclination angles of the first swash plate 18 and the second swash plate 51 are changed. As a result, the stroke of the piston 23, 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 angles of the first swash plate 18 and the second swash plate 51 are 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 rises. Therefore, the inclination angles of the first swash plate 18 and the second swash plate 51 decrease, the stroke of the piston 23 decreases, and the discharge capacity of the compressor 10 is reduced.

And as shown in FIG. 1 and FIG. 2, the support part 39 which supports the 2nd swash plate 51 by the 1st swash plate 18 is with respect to the center axis M1 of the 1st swash plate 18, It is formed eccentrically to the piston 23A side located in the top dead center position. In other words, when the support part 39 sees the radial direction of the 1st swash plate 18 from the center axis M1, the site | part side (hinge mechanism 19 side) which hangs the piston 23 also to a top dead center position. ) Is eccentrically formed. Accordingly, the second swash plate 51, the radial bearing 52, and the thrust bearing 53 (retainer 53b) are eccentric with respect to the piston 23A at the top dead center position with respect to the first swash plate 18. have. Accordingly, the center axis M2 of the second swash plate 51, the radial bearing 52, and the thrust bearing 53 is located at the top dead center position with respect to the center axis M1 of the first swash plate 18. The first shoe 25A and the second shoe 25B included in the 23A are deviated in parallel by a slight amount (for example, 0.05 to 5 mm. .

Therefore, in the outer peripheral edge part of the 2nd swash plate 51, the part corresponding to piston 23A vicinity in a top dead center position is the diameter of the 1st swash plate 18 from the outer peripheral edge part of the 1st swash plate 18. FIG. Slightly out of the direction. Thus, 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 and the second swash plate ( The contact area of 51) is widened.

Moreover, in the outer peripheral edge part of the 2nd swash plate 51, the part corresponding to the piston 23B vicinity which exists in the bottom dead center position is a diameter of the 1st swash plate 18 rather than the outer peripheral edge part of the 1st swash plate 18. It is located inside the direction. In short, the portion of the outer circumferential edge portion of the second swash plate 51 corresponding to the vicinity of the hinge mechanism 19 is located inside the radial direction of the first swash plate 18 than the outer circumferential edge portion of the first swash plate 18. . 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 and the second swash plate of the piston 23 in the vicinity of the bottom dead center position. The contact area of 51 becomes narrow. However, the compression reaction force acting on the second shoe 25B of the piston 23 near the bottom dead center position is much more than the compression reaction force acting on the second shoe 25B of the piston 23 near the top dead center position. small. For this reason, even if the contact area of the 2nd shoe 25B and the 2nd swash plate 51 of the piston 23 located in the bottom dead center position becomes narrow, durability of the 2nd swash plate 51 and the 2nd shoe 25B will be carried out. There's nothing wrong with that.

In the outer peripheral edge part of the 1st swash plate 18, in the part corresponding to the piston 23A in a top dead center position, and the part located before and behind the circumferential direction with respect to this part, the convex on the opposite side to the 2nd swash plate 51 An inclined surface (chamfered) is formed in each portion 18b. That is, in the part of the outer peripheral edge part of the 2nd swash plate 51 corresponding to the hinge mechanism 19 vicinity, the inclined surface (chamfering) is formed in the convex-angle part 18b on the opposite side to the 2nd swash plate 51. As shown in FIG. That is, in the part of the outer peripheral edge part of the 1st swash plate 18 corresponding to the range of the circumferential direction of the 1st swash plate 18 which arrange | positions the piston 23 in a top dead center position, the convex-angle part on the opposite side to the piston 23A. An inclined surface is formed at 18b. The inclined surface (chamfered) of the convex-angle part 18b is formed so that the part corresponding to the piston 23A in a top dead center position may become largest, and it becomes small gradually as it moves away from this part to the circumferential direction. The inclined surface (chamfer) of the convex-angle part 18b is formed in the range of 1/4 accompaniment area | region to the accompaniment area which made the part corresponding to the piston 23A in a top dead center position intermediate.

In the outer peripheral edge part of the 1st swash plate 18, in the part corresponding to the piston 23B in a bottom dead center position, and the part located in the circumferential direction back and forth with respect to this part, the convex angle part of the 2nd swash plate 51 side An inclined surface (chamfered) is formed at 18c. That is, in the part of the outer peripheral edge part of the 1st swash plate 18 corresponding to the range of the circumferential direction of the 1st swash plate 18 which arrange | positions the piston 23B at a bottom dead center position, the convex-angle part on the opposite side to the piston 23B. An inclined surface is formed at 18c.

This inclined surface (chamfering) is formed so that the part corresponding to the piston 23B in a bottom dead center position may become largest, and it becomes small gradually as it moves away from this part to the circumferential direction. The inclined surface (chamfer) of the convex-angle part 18c is formed in the range of 1/4 accompaniment area | region to the accompaniment area which made the part corresponding to the piston 23B in a bottom dead center position intermediate. In addition, the inclined surface (chamfering) of the convex corner portion 18c is approximately the same size as the inclined surface (chamfering) of the convex corner portion 18b in consideration of the weight balance around the central axis M1 of the first swash plate 18. Formed.

In this embodiment of the above structure, the following effects are obtained.

(1-1) The first swash plate 18 and the second swash plate 51 by disposing the second swash plate 51 on the piston 23A side at the top dead center position with respect to the first swash plate 18. Even if it is not hardened | cured substantially, the contact area of the 2nd shoe 25B and the 2nd swash plate 51 of the piston 23 located in the top dead center position can be enlarged. Therefore, the contact sliding property of the 2nd swash plate 51 and the 2nd shoe 25B becomes favorable, and the 2nd swash plate 51 and the 2nd shoe 25B are suppressed, suppressing the fall of the durability of the piston 23, and enlargement. It can improve the durability.

(1-2) In the swash plate structure provided with the thrust bearing 53 in addition to the 1st swash plate 18 and the 2nd swash plate 51 like this embodiment, the 1st shoe 25A in this swash plate structure ) And the thickness between the second shoe 25B. In this conditionally strict configuration, the second swash plate 51 is eccentric with respect to the first swash plate 18, and the second shoe 25B and the second swash plate 51 of the piston 23 located near the top dead center position. It is particularly effective to increase the durability of the second swash plate 51 and the second shoe 25B while suppressing a decrease in the durability and enlargement of the piston 23.

(1-3) In the peripheral part of the 1st swash plate 18, in the part corresponding to the piston 23A in a top dead center position, the inclined surface is in the convex-angle part 18b on the opposite side to the 2nd swash plate 51. Formed. Moreover, in the outer peripheral edge part of the 1st swash plate 18, the inclined surface is formed in the convex-angle part 18c by the side of the 2nd swash plate 51 in the part corresponding to the piston 23B in a bottom dead center position. As for the 1st swash plate 18 which inclines with respect to the drive shaft 16, in the outer peripheral edge part corresponding to the piston 23A in a top dead center position, the convex-angle part 18b on the opposite side to the 2nd swash plate 51, The drive shaft 16 is protruded largely toward the diameter direction. Moreover, in the 1st swash plate 18, in the outer peripheral edge part corresponding to the piston 23B in a bottom dead center position, the convex-angle part 18c by the 2nd swash plate 51 side makes the radial direction of the drive shaft 16 stand. It will protrude greatly.

Therefore, by forming an inclined surface in the protruding portions (parts of the entire circumferences of the convex angle portions 18b and 18c) in the first swash plate 18, the first and the reduction of durability of the piston 23 and the increase in size are suppressed. The swash plate 18 can be made large diameter. Therefore, the support of the second swash plate 51 by the first swash plate 18 is adapted, and acts on the second swash plate 51 via the second shoe 25B of the piston 23 in the vicinity of the top dead center position. A large compression reaction force can be preferably received by the first swash plate 18 via the second swash plate 51. This leads to the improvement of 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 refrigerating circuit is much higher than when a freon refrigerant (for example, R134a) is used. Therefore, the compression reaction force acting on the piston 23 also increases in the compressor, so that the pressure contact force between the second swash plate 51 and the second shoe 25B becomes strong. In this aspect, embodying the present invention is particularly effective for improving the durability of the second swash plate 51 and the second shoe 25B while suppressing the decrease and the increase in the durability of the piston 23.

Next, a second embodiment of the present invention will be described with reference to FIGS. 3 and 4. In addition, in this embodiment, only the difference with 1st Embodiment is demonstrated, the same code | symbol is attached | subjected to the same or equivalent member, and detailed description is abbreviate | omitted.

In the first shoe 25A and the second shoe 25B, the first shoe 25A located on the side of the hinge mechanism 19, that is, on the opposite side to the compression chamber 24, is located on the opposite side to the hemispherical surface 25a. In the sliding contact surface 25b, it contacts with the front surface of the outer peripheral part 18-1 of the 1st swash plate 18 so that sliding is possible. In addition, the second shoe 25B on the side opposite to the hinge mechanism 19, that is, on the compression chamber 24 side, receives the compression reaction force on the sliding contact surface 25b on the side opposite to the hemisphere 25a. The back surface of the outer peripheral part 51-2 of the swash plate 51 is slidably abutted. The sliding contact surface 25b of the 1st shoe 25A has the medium shape which the center part protruded toward the 1st swash plate 18 side (refer FIG. 4, In FIG. 4, the used shape is exaggeratedly drawn). . The sliding contact surface 25b of the 2nd shoe 25B has comprised 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 2nd swash plate 51 are mentioned in detail. The radial bearing 52A which consists of rolling bearings is interposed between the inner peripheral surfaces of the support hole 51a. The radial bearing 52A has an outer race 52a attached to the inner circumferential surface of the support hole 51a on the second swash plate 51 and an inner side attached to the outer circumferential surface of the support portion 39 on the first swash plate 18. It consists of the race 52b and the roller 52c as a transmission element interposed between the outer race 52a and the inner race 52b.

Between the outer periphery 18-1 of the 1st swash plate 18 and the outer periphery 51-2 of the 2nd swash plate 51 between the 1st shoe 25A and the 2nd shoe 25B, the thrust which consists of a rolling bearing The strut bearing 53 is interposed. The thrust bearing 53 has a plurality of rollers 53a as a transmission element, and the plurality of rollers 53a are held in a rotatable manner by the holder 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 carburizing heat treatment on a base made of mild steel such as SPC. Chamfering is applied to each end of both ends of the roller 53a so that the roller 53a does not collide with the second swash plate 51 and the race 55 to damage the second swash plate 51 and the race 55. It is.

At the outermost circumference of the outer circumferential portion 18-1 on the rear surface of the first swash plate 18, an engaging locking portion 18d which is formed in an annular shape toward the second swash plate 51 side protrudes. The lace 55 is disposed inside the locking piece 18d, and the lace 55 is caught on the first swash plate 18 in the radially outer side by abutting the outer peripheral edge thereof with the locking piece 18d. It is fixed. The race 55 is guided to the locking fastening portion 18d to allow relative rotation with respect to the first swash plate 18.

The second swash plate 51 is interposed by the radial bearing 52A and the thrust bearing 53 so that the first swash plate 18 can be rotated relative to the first swash plate 18 and can be tilted integrally. Supported. Accordingly, when the first swash plate 18 rotates, a cloud occurs between the first swash plate 18 and the second swash plate 51 due to the action of the radial bearing 52A and the thrust bearing 53, and the faces are separated from each other. The mechanical loss due to slipping is changed to the mechanical loss due to rolling, and the occurrence of mechanical loss in the compressor can be significantly suppressed.

The plate thickness Y1 of the inner circumferential portion 51-1 supported by the radial bearing 52A in the second swash plate 51 receives the support of the thrust bearing 53 in the second swash plate 51. It is thicker than the plate | board thickness Y2 of the outer peripheral part 51-2. In detail, the plate | board thickness Y2 of the outer peripheral part 51-2 of the 2nd swash plate 51 is half or more of the plate | board thickness X of the outer peripheral part 18-1 of the 1st swash plate 18, and It is set thinner than the plate | board thickness X of the outer peripheral part 18-1 of the 1st swash plate 18. FIG. In addition, the plate thickness Y1 of the inner circumferential portion 51-1 of the second swash plate 51 is thicker than the plate thickness X of the outer circumferential portion 18-1 of the first swash plate 18.

The inner circumferential portion 51-1 of the second swash plate 51 protrudes to the opposite side from the cylindrical first protruding portion 56 formed by protruding toward the first swash plate 18 and the first swash plate 18. By providing the formed 2nd cylindrical protrusion part 57, plate | board thickness is thicker than the outer peripheral part 51-2 of the 2nd swash plate 51 (Y1> Y2). The first protruding portion 56 and the second protruding portion 57 are disposed coaxially with the support hole 51a, and the inner circumferential surfaces of the first protruding portion 56 and the second protruding portion 57 are provided. Constitutes a part of the inner circumferential surface of the support hole 51a. The outer diameter Z2 of the second projecting portion 57 is smaller than the outer diameter Z1 of the first projecting portion 56. Moreover, the taper-shaped chamfer is given to the outer peripheral angle 57a of the front end surface in the 2nd protrusion shape part 57 at the whole.

In 2nd Embodiment, the same effect as 1st Embodiment is acquired, and the following effects are shown.

(2-1) 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, The thrust bearing 53 which supports the 2nd swash plate 51 so that relative rotation is possible with respect to the 1st swash plate 18 is arrange | positioned. The second swash plate 51 is rotated relative to the first swash plate 18 between the inner circumferential portion (support portion 39) of the first swash plate 18 and the inner circumferential portion 51-1 of the second swash plate 51. 52 A of radial bearings which can support this are arrange | positioned.

Therefore, by the action of the thrust bearing 53 and the radial bearing 52A, between the outer peripheral part 18-1 of the 1st swash plate 18 and the outer peripheral part 51-2 of the 2nd swash plate 51, and 1st The rotational resistance which arises between the inner peripheral part (support part 39) of the 1st swash plate 18, and the inner peripheral part 51-1 of the 2nd swash plate 51 can be reduced effectively. Therefore, even in the compressor 10 used in the refrigeration circuit using carbon dioxide as the refrigerant, the slip between the first swash plate 18 and the second swash plate 51 can be regarded as a mechanical loss caused by the cloud. As a result, occurrence of problems such as mechanical loss or seizure can be effectively suppressed.

(2-2) The plate thickness Y2 of the outer circumferential portion 51-2 in the second swash plate 51 is half of the plate thickness X of the outer circumferential portion 18-1 in the first swash plate 18. It is the above and thinner than the plate | board thickness X of the outer peripheral part 18-1. Increasing the size of the piston 23 In the end, if the size of the compressor is to be avoided, the space between the first shoe 25A and the second shoe 25B is limited. In this limited space, when the plate | board thickness X of the outer peripheral part 18-1 of the 1st swash plate 18 is thickened, the plate | board thickness Y2 of the outer peripheral part 51-2 of the 2nd swash plate 51 is made thin. On the contrary, when the plate | board thickness Y2 of the outer peripheral part 51-2 of the 2nd swash plate 51 is thickened, the plate | board thickness X of the outer peripheral part 18-1 of the 1st swash plate 18 will be made thinner. There is a need.

In view of the compression reaction force, both the first swash plate 18 and the second swash plate 51 need to secure the strength by making the plate thickness X, Y2 of the outer peripheral portions 18-1, 51-2 as thick as possible. However, in the first swash plate 18 to which power is transmitted from the drive shaft 16, the second swash plate which is to be secured to the first swash plate 18 to secure the plate thickness X of the outer peripheral portion 18-1. Priority should be given to securing the plate | board thickness Y2 of the outer peripheral part 51-2 in (51). It is preferable in such a meaning that the plate thickness Y2 of the outer circumferential portion 51-2 in the second swash plate 51 is the plate thickness X of the outer circumferential portion 18-1 in the first swash plate 18. It is set to half or more and thinner than the plate | board thickness X of the outer peripheral part 18-1.

(2-3) In the second swash plate 51, the plate thickness Y1 of the inner circumferential portion 51-1 is thicker than the plate thickness Y2 of the outer circumferential portion 51-2. By the thick inner circumferential portion 51-1, the support of the second swash plate 51 by the radial bearing 52A is stabilized, and the slippage between the first swash plate 18 and the second swash plate 51 is better. It can be done. Moreover, the outer peripheral part 51 of the 1st swash plate 18 which is more rigid than the 2nd swash plate 51 by the outer peripheral part 51-2 of the 2nd swash plate 51 relatively thin with respect to the inner peripheral part 51-1 It is easy to secure the plate thickness of 18-1).

(2-4) The plate thickness Y2 of the outer peripheral portion 51-2 of the second swash plate 51 is thinner than the plate thickness X of the outer peripheral portion 18-1 of the first swash plate 18. Therefore, the thin outer peripheral part 51-2 of the 2nd swash plate 51 makes it easy to ensure the plate | board thickness of the outer peripheral part 18-1 of the 1st swash plate 18 more rigidly than the 2nd swash plate 51. FIG. Become. In the second swash plate 51, the plate thickness Y1 of the inner circumferential portion 51-1 is thicker than the plate thickness X of the outer circumferential portion 18-1 of the first swash plate 18. Therefore, the support of the second swash plate 51 by the radial bearing 52A is further stabilized.

(2-5) In the 1st protrusion shape part 56 and the 2nd protrusion shape part 57 which comprise the inner peripheral part 51-1 of the 2nd swash plate 51, the 2nd protrusion shape part 57 The outer diameter Z2 is smaller than the outer diameter Z1 of the first protruding portion 56. The second protruding portion 57 is very 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 (state in FIG. 3). Therefore, making the second protruding portion 57 smaller than the first protruding portion 56 from the piston 23 avoids the interference between the second swash plate 51 and the piston 23, It becomes effective to make it thickening the plate | board thickness Y1 of the inner peripheral part 51-1 of the 2nd swash plate 51.

(2-6) In the 2nd protrusion-shaped part 57 which comprises the inner peripheral part 51-1 of the 2nd swash plate 51, the chamfer is formed in the outer peripheral angle 57a of a front end surface. For example, in the state where the discharge capacity of the compressor is at a maximum, a part of the outer circumferential angle 57a of the front end face is very close to the piston 23B at the bottom dead center position. Therefore, forming the chamfer at the outer circumferential angle 57a of the tip end surface of the second protruding portion 57 avoids the interference between the second swash plate 51 and the piston 23, and the second swash plate 51. It becomes effective to make thickening the plate | board thickness Y1 of the inner periphery part 51-1 of the inside.

(2-7) On the outer circumferential edge of the first swash plate 18, the portion corresponding to the piston 23A at the top dead center position is inclined to the convex angle portion 18b opposite to the second swash plate 51 (chamfered). ) Is carried out. Therefore, the 1st swash plate 18 and the 2nd swash plate 51 can be made large diameter, suppressing the fall of the durability of the piston 23, and enlargement. Therefore, the contact sliding property of the 2nd swash plate 51 and the 2nd shoe 25B becomes favorable, and the 2nd swash plate 51 and the 2nd shoe 25B are suppressed, suppressing the fall of the durability of the piston 23, and enlargement. It can improve the durability.

That is, the 1st swash plate 18 which inclines with respect to the drive shaft 16 is the convex-angle part 18b on the opposite side to the 2nd swash plate 51 in the outer peripheral edge corresponding to the piston 23A in a top dead center position. ) Is largely projected toward the radial direction of the drive shaft 16. In the first swash plate 18, when the convex angle portion 18b on the side opposite to the second swash plate 51 is largely projected in the radial direction, in order to avoid interference with the protruding portion, the piston 23 is connected to this protruding portion. It is conceivable to make the thickness of the corresponding neck portion 38 thin 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 the enlargement of the compressor.

In order to solve this problem, it is conceivable to reduce the radius of the first swash plate 18 to avoid the interference between the convex angle portion 18b and the piston 23 described above. However, when the radius of the first swash plate 18 is made small, the radius of the second swash plate 51, which requires the support by the first swash plate 18, must also be made small. Therefore, especially in the piston 23 located near the top dead center position (compression stroke), the contact area between the second shoe 25B and the second swash plate 51 subjected to a large compression reaction force is narrowed, and the second swash plate There is a problem that the durability of the 51 and the second shoe 25B is lowered.

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

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

Here, for example, when the roller 53a of the thrust bearing 53 is directly driven on the first swash plate 18, a part of the first swash plate 18 (the piston 23 located near the top dead center position) is provided. A large compression reaction force is applied to the corresponding portion), and the portion is locally deteriorated in wear. 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 causes the surface pressure to decrease by interposing the race 55. Since it lowers and acts on the 1st swash plate 18, it can suppress that the 1st swash plate 18 locally wear-deteriorates. Moreover, in the race 55 relatively rotating with respect to the 1st swash plate 18, the site | part which large compressive reaction force acts through the roller 53a changes sequentially, and the lace 55 is prevented from locally deteriorating abrasion. can do.

(2-10) In the outer peripheral part 18-1 of the 1st swash plate 18, the locking part 18d protrudes and is formed toward the 2nd swash plate 51 side, and is matched with the locking fixing part 18d. The race 55 is locked to the first swash plate 18 by the contact with the outside in the radial direction.

Here, the first swash plate 18 is formed, for example, by forming the locking portion at the inner circumferential portion of the first swash plate 18 to secure the race 55 to the first swash plate 18 in the radially inner side. When the lubricating oil (freezer base oil) adhered to the plate moves in the radially outward direction by the action of centrifugal force, the entry between the first swash plate 18 and the race 55 of this lubricating oil is impeded by the locking portion. However, according to this embodiment which locks the race 55 to the 1st swash plate 18 from the radial direction outer side, it is the locking part 18d that the lubricating oil between the 1st swash plate 18 and the race 55 enters. Can be prevented from being impeded by, and the slipping between the first swash plate 18 and the race 55 can be improved.

(2-11) The jamming government (18d) is in an annular shape. Therefore, the locking fixation of the race 55 by the locking fastening portion 18d is performed stably, and the slippage 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. 5. In addition, in this embodiment, only a difference with 2nd Embodiment is demonstrated, the same code | symbol is attached | subjected to the same or considerable member, and detailed description is abbreviate | omitted.

In this embodiment, the support part 39 is not eccentric with respect to the center axis M1 of the 1st swash plate 18. In short, the second swash plate 51 and 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, in the outer peripheral edge of the 1st swash plate 18, the part corresponding to the piston 23B in a bottom dead center position is the 2nd swash plate with the convex-angle part 18c by the 2nd swash plate 51 side in a radial direction. Since it does not protrude more than 51, as shown in FIG. 5, even if it does not chamfer the convex-angle part 18c, there is no problem.

In addition, in this embodiment, the PCD of the thrust bearing 53 has the 1st shoe 25A and 1st centering on the center axis line M1, M2 of the 1st swash plate 18 and the 2nd swash plate 51. Moreover, in FIG. It is larger than the diameter of the virtual cylinder which passes the center point P of 2 shoe | mouth 25B. In this way, the thrust bearing 53 (roller 53a) can receive the compression reaction force transmitted through the 2nd swash plate 51 preferably, and durability will improve. In addition, the "PCD" of the thrust bearing 53 means the center of the thrust bearing 53 (center axis line M1, M2 of the 1st swash plate 18 and the 2nd swash plate 51) as a center axis line, and a roller In 53a, the diameter of the virtual cylinder passing through the midpoint on the rotating center axis is indicated.

Next, 4th Embodiment of this invention is described with reference to FIGS. In addition, in this embodiment, only the difference with 1st, 2nd embodiment is demonstrated, the same code | symbol is attached | subjected to the same or considerable member, and detailed description is abbreviate | omitted.

While the rotor 17 is stopped on the drive shaft 16, the swash plate 58 is supported in the axial direction of the drive shaft 16 in a slewable and tiltable manner. The connecting pieces 59 and 60 are stopped on the swash plate 58, and the guide pins 61 and 62 are stopped on the connecting pieces 59 and 60. The rotor 17 is provided with a pair of guide holes 171 (only one of them). The head part of the guide pins 61 and 62 is slidably fitted into the guide hole 171. The swash plate 58 is tiltable in the axial direction of the drive shaft 16 by the linkage of the guide hole 171 and the guide pins 61, 62 and is integrally rotatable with the drive shaft 16. The tilting of the swash plate 58 is guided by the slide guide relation 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 the hinge mechanism 19A.

The solid line position of the swash plate 58 in FIG. 6 indicates the maximum inclined state of the swash plate 58. When the central portion of the swash plate 58 moves to the cylinder block 11 side, the inclination angle of the swash plate 58 decreases. The dashed line position of the swash plate 58 of FIG. 6 represents the minimum inclination state of the swash plate 58.

In the outer circumferential edge portion of the swash plate 58, a portion corresponding to the piston 23A at the top dead center position and a portion located before and after the circumferential direction with respect to the portion, the convex angle portion 58a opposite to the piston 23 An inclined surface is formed in the. That is, in the part of the outer peripheral edge part of the swash plate 58 corresponding to the hinge mechanism 19A vicinity, the inclined surface is formed in the convex-angle part 58a by the hinge mechanism 19A side. That is, in the part of the outer periphery of the swash plate 58 corresponding to the range of the circumferential direction of the swash plate 58 which arranges the piston 23A at the top dead center position, the convex angle part 58a opposite to the piston 23 is provided. An inclined surface is formed. As shown in FIG. 7, the inclined surface of the convex-angle part 58a is formed so that the part corresponding to the piston 23 in a top dead center position may become largest, and it may become small gradually as it moves away from this part to the circumferential direction.

As shown in FIG. 8, the inclined surface formed in the convex-angle part 58a has the center axis M3 parallel to the axis line L of the drive shaft 16, when the swash plate 58 is in the maximum inclination state. It is on the circumferential surface of the cylinder C. In the example to show, the center axis line M3 is shift | deviated to the drive shaft 16 side from the piston 23A side in the top dead center position with respect to the axis line L. In FIG. The diameter of the virtual cylinder C is made into the diameter of the swash plate 58 or more.

As for the swash plate 58 which inclines with respect to the drive shaft 16, the convex-angle part 58a on the opposite side to the piston 23 is the drive shaft 16 in the outer peripheral edge part corresponding to the piston 23A in a top dead center position. Protrudes largely in the radial direction. Therefore, by forming the inclined surface in the protruding portion (part of the convex corner portion 58a) in the swash plate 58, the swash plate 58 can be made large in diameter while suppressing the decrease in durability and the enlargement of the piston 23. . Therefore, a large compression reaction force acting on the swash plate 58 through the second shoe 25B of the piston 23 near the top dead center position can be preferably received. This leads to the improvement of the durability of the swash plate 58.

Moreover, it can implement also in the following aspects, for example in the range which does not deviate from the meaning of this invention.

(1) In 1st Embodiment, the radial bearing 52 is removed and the 2nd swash plate 51 is slid by the support part 39.

(2) In the first embodiment, the thrust bearing 53 is removed and the second swash plate 51 is directly slid to 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 to fix the second swash plate 51. To be rotatable integrally with the first swash plate 18.

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

2, the 2nd swash plate 51 which inclines with respect to the drive shaft 16 is a convex angle part by the 1st swash plate 18 side in the outer peripheral edge part corresponding to the piston 23A in a top dead center position. Is largely projected toward the radial direction of the drive shaft 16. Moreover, the 2nd swash plate 51 has the convex-angle part on the opposite side to the 1st swash plate 18 toward the radial direction of the drive shaft 16 in the outer peripheral edge part corresponding to the piston 23B in a bottom dead center position. It will protrude greatly. Therefore, by forming the inclined surface (chamfered) in the protruding portion (a part of the convex angle part) in these second swash plate 51, the second swash plate 51 is enlarged while suppressing the deterioration and increase in durability of the piston 23. can do. Therefore, the contact area of the 2nd shoe 25B and the 2nd swash plate 51 of the piston 23 located in the top dead center position can be made wider, and the 2nd swash plate 51 and the 2nd shoe 25B of Durability can be further improved.

(4) In 1st Embodiment, although two sheets of the 1st swash plate 18 and the 2nd swash plate 51 were used, it changed, for example, between the 2nd swash plate 51 and the 2nd shoe 25B. You may arrange | position a 3rd swash plate. In short, the swash plate structure to which the present invention can be applied is not limited to using only two sheets of the first swash plate and the second swash plate, and may be provided with a plurality of swash plates, such as three sheets, four sheets, or five sheets described above. .

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

(6) The present invention is not limited to being applied to a refrigerant compressor used in a refrigeration circuit, and may be applied to, for example, an air compressor.

(7) Change 2nd Embodiment and make sliding contact surface 25b of 1st shoe 25A into planar shape, for example as shown in FIG.

(8) The second embodiment is changed and, for example, as shown in FIG. 5, the sliding contact surface 25b of the second shoe 25B is recessed while the center portion is recessed. By doing in this way, the 2nd shoe 25B which reciprocates linearly with the piston 23 can be reduced in weight, the inertia force of the 2nd shoe 25B can be reduced, and the 1st swash plate 18 and the 2nd swash plate Change of the inclination angle of 51 In other words, the discharge capacity of the compressor can be smoothly changed.

(9) In the second and third embodiments, the thrust bearing 53 is changed to a rolling bearing provided with a ball as a transmission element.

(10) In the second and third embodiments, the thrust bearing 53 is changed to a slip bearing.

(11) In the second and third embodiments, the radial bearing 52A was configured to receive only a radial load (load in the direction perpendicular to the central axis M2) acting on the second swash plate 51. By changing this, for example, by arranging the roller 52c with respect to the center axis line M2 of the 2nd swash plate 51, the radial bearing 52A is not only radial load but thrust load (center axis line M2). ), Which also receives the load in the direction along

(12) In the second and third embodiments, the thrust bearing 53 was configured to receive only a thrust load acting on the second swash plate 51. By changing this and placing the roller 53a inclined with respect to the other side of the 2nd swash plate 51, it is set as the structure which receives not only a thrust load but also a radial load.

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

(14) In the second and third embodiments, the locking fastening portion 18d is deleted, and a locking fastening portion is formed on the inner circumference of the first swash plate 18 (for example, it is caught on the base of the support portion 39). By both sides), so that the lace 55 is fixed to the first swash plate 18 in the radially inner side.

Claims (6)

The swash plate is integrally rotatably connected to the drive shaft, and the swash plate is moored through the shoe to the swash plate, and by the rotation of the swash plate according to the rotation of the drive shaft, the piston reciprocates linearly, thereby compressing the gas. In the variable displacement swash plate type compressor in which the discharge capacity is changed by changing the inclination angle of the swash plate, A variable displacement swash plate type compressor, characterized in that an inclined surface is formed on a part of the entire circumference of the circumference of the swash plate. The method of claim 1, A variable displacement swash plate type compressor in which an inclined surface is formed at a convex angle portion opposite to the piston at a portion corresponding to the piston at the top dead center position at an outer peripheral edge of the swash plate. The method according to claim 1 or 2, The variable displacement swash plate type compressor in which the inclined surface is formed in the convex-angle part of the said piston side in the part corresponding to the said piston in the lower dead center position in the outer peripheral edge part of the said swash plate. The method according to any one of claims 1 to 3, The swash plate comprises a first swash plate which is integrally rotatably connected to a drive shaft, and a second swash plate supported by the first swash plate, wherein the first and second swash plates have a first shoe which abuts against the first swash plate, And a piston is moored through a second shoe on the side receiving the compression reaction force against the second swash plate, and at a portion of the outer circumferential edge of the first swash plate corresponding to the piston at a top dead center position. A variable displacement swash plate type compressor in which an inclined surface is formed at the convex angle portion opposite to the swash plate. The method of claim 4, wherein The variable displacement swash plate type compressor of which the inclined surface is formed in the convex angle part of the said 2nd swash plate side in the part corresponding to the said piston in the bottom dead center position in the outer peripheral edge part of a said 1st swash plate. The method according to any one of claims 1 to 5, The gas is a refrigerant used in a refrigeration circuit, the carbon dioxide is used as the refrigerant variable displacement swash plate type compressor.

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