JP3320587B2 - Swash plate compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swash plate type compressor and, more particularly, to an improvement in a structure for preventing a piston from rotating in a swash plate type compressor.

[0002]

2. Description of the Related Art A compressor used in an air conditioner for a vehicle includes a fixed displacement swash plate type compressor having a swash plate having a fixed inclination angle with respect to a drive shaft, and an inclination angle with respect to the drive shaft in order to adjust a discharge refrigerant amount. A variable displacement swash plate type compressor having a variable swash plate is known.

[0003] For example, the variable displacement swash plate compressor includes a drive shaft rotatably driven by an engine transmitted through a belt, a pulley, and the like, and a disc-shaped inclined shaft attached to the drive shaft at a variable inclination angle. When the drive shaft is rotated, the swash plate in an inclined state rotates together with the drive shaft while performing a so-called razor motion. The variable displacement swash plate type compressor has a plurality of cylinder chambers and respective pistons slidingly moved along the cylinder chambers. The rotating swash plate and the piston described above are moved through a piston rod. Some are directly slidably connected without using.

In such a compressor in which the swash plate and the piston are directly connected, each piston has a piston head reciprocating in a cylinder chamber, and a substantially U-shaped section engaged with the swash plate.
And an engagement portion in the shape of a letter. For example, substantially hemispherical shoes are fitted into two spherical concave portions formed at positions opposing each other on the inner surfaces of both sides of the engaging portion, and the front and back flat surfaces of the swash plate are sandwiched by these two shoes. Here, the sliding surfaces formed on the front and back surfaces of the outer edge portion of the swash plate are in sliding contact with the corresponding flat portions of the shoe, respectively, and the piston is formed in a spherical concave portion formed on the engaging portion. Slidably contact the spherical surface of the corresponding shoe. In this way, the piston is slidably connected to the swash plate at the engagement portion.

Therefore, when the swash plate is rotated by rotating the drive shaft, the piston slidably connected to the swash plate slides on the outer edge of the rotating swash plate closest to the cylinder chamber side. Is moved to the top dead center position, and is moved to the bottom dead center position when the rotating swash plate comes into sliding contact with the outer edge farthest from the cylinder chamber side. That is, by making the swash plate inclined with respect to the drive shaft and the piston whose sliding direction is regulated by the cylinder chamber in sliding contact, the swash plate's slewing rotation is converted into a reciprocating motion of the piston. Will be.

When the piston is reciprocated in this manner, the refrigerant sucked from the suction port in the compressor is compressed and then discharged to the discharge port, so that the refrigerant circulates and functions as a compressor.

When the piston is reciprocated by rotating the inclined swash plate, FIG.
As shown in FIG.
An axial force acts via the pistons 123
Is located at the top or bottom dead center side along the cylinder chamber,
It slides in the direction perpendicular to the plane of FIG. In addition, FIG.
It is the figure which looked at piston 123 from back in the direction of an axis. In this case, the flat surface of the outer edge of the swash plate moves at a high speed between the two shoes 71 and 72 in the direction of arrow A and slides with each other.
In order to exert a force for rotating 3 in the B direction, it is necessary to regulate the rotation of this piston.

Therefore, as shown in FIG.
By providing a rectangular parallelepiped convex portion 124 on the outer peripheral surface of the casing 23 and forming a sliding groove 127 on the inner peripheral surface of the casing 112 so as to engage with the convex portion 124 so as to be movable in the axial direction, the piston 123 is stopped. By doing so, it is possible to prevent a situation in which the piston 123 largely rotates and a part of the piston 123 locally hits the swash plate, and wear powder is generated at that time, which adversely affects the piston operation. .

[0009]

However, in such a conventional piston detent structure, the processing of the rectangular parallelepiped convex portion 124 and the sliding groove 127 is performed at both end surfaces 124a, 124b in the circumferential direction. , 127a, 127b
In addition to the above, there is processing of the top 124c and the bottom 127c,
In each case, since the processing is a flat surface, a large amount of tool feed is required, and the same processing is required for the number of arranged pistons, for example, at five places.

Further, in order not to add unnecessary resistance to the reciprocating motion of the piston, a certain amount of clearance is required between the convex portion 124 and the sliding groove 127. In this case, the end faces of the convex portion 124 and the sliding groove 127 are abutted against each other, and there is a possibility that abnormal noise may occur.

On the other hand, as shown in FIG. 6, on the rear surface of the piston 133 facing the inner peripheral surface of the casing 112, the rotation range of the piston
In order to avoid interference between the engaging portion of the swash plate 3 and the peripheral edge of the swash plate, a rotation regulating convex curved surface 134 is provided. By making the radius of curvature larger than the radius of curvature Rp of the surface and smaller than the inner radius of curvature R2 of the inner peripheral surface of the casing 112, the inner peripheral surface of the casing 112 and the rotation regulating convex curved surface 134 are brought into close contact with the surface. There is one in which noise and wear are suppressed by causing interference (see Japanese Patent Application Laid-Open No. 6-346844).

However, the method disclosed in Japanese Patent Application Laid-Open No.
In the piston detent structure described in Japanese Patent Application Publication No. 4 (1999), when the swash plate rotates the piston 133 to, for example, a position shown by a two-dot chain line in FIG. When the rotation is large, a part of the piston may locally hit the swash plate as described above.
Must be placed as close as possible to the inner peripheral surface of the

For this reason, the clearance space 13 formed between the rotation regulating convex curved surface 134 and the inner peripheral surface of the casing 112.
5 is a very narrow space, and the lubricating oil in the crank chamber, which is splashed by the rotation of the swash plate,
5 and it is not possible to sufficiently lubricate the contact portion C between the rotation regulating convex curved surface 134 and the inner peripheral surface of the casing 112. In addition, due to such insufficient lubrication of the contact portion C, abrasion occurs at the contact portion C and adversely affects the operation of the piston. There is a fear.

The present invention has been made in view of the above-mentioned problems of the prior art, and it is an object of the present invention to secure sufficient lubrication to suppress generation of abnormal noise and wear, and at a low cost. An object of the present invention is to provide a swash plate compressor capable of reliably and smoothly restricting rotation of a piston.

[0015]

According to the present invention, there is provided a drive shaft rotatably mounted on a casing, a swash plate provided in a crank chamber of the casing and connected to the drive shaft. A plurality of cylinder chambers formed in the casing, and a plurality of pistons reciprocated in the axial direction inside the cylinder chamber via shoes arranged in contact with the front and back surfaces of the swash plate by rotation of the swash plate. In the swash plate type compressor having a piston, the piston includes a piston head that reciprocates in the cylinder chamber, and an engagement portion that engages with the swash plate via the shoe, and an outer surface of the engagement portion of the piston that faces the casing. , the detent portion in which the convex curved surface is formed to have a radius of curvature larger than the piston head radius provided, a inner circumferential surface of the casing opposite the detent of the piston the piston Trying rotating the piston axis
In the region where the detent portion contacts, a concave portion having a concave curved surface having an inner radius of curvature larger than the piston head radius is provided at a predetermined distance from the convex curved surface of the detent portion of the piston. A swash plate type compressor in which an oil groove is formed near the center in the circumferential direction of the concave portion.

[0016] The concave curved surface of the concave portion of the casing formed opposite to the detent portion of the piston constitutes a part of a cylindrical inner surface formed over the entire circumference along the inner peripheral surface of the casing. May be.

[0017]

According to the present invention constructed as described above, the swash plate in a state in which the drive shaft is rotated and inclined is slid by the swash plate.
The piston is reciprocated by applying an axial force to the piston.In this way, when the rotational motion of the inclined swash plate is converted into the reciprocating motion of the piston, the swash plate moves with respect to the piston. , An axial force acts via the shoe,
The piston reciprocates along the cylinder chamber.

In this case, since the swash plate slides between the two shoes at high speed in the circumferential direction, a force for rotating the piston about the piston axis is exerted through both the shoes.
Then, when the piston is rotated, the detent portion formed on the outer surface of the engagement portion of the piston is rotated about the piston axis, and the convex curved surface of the detent portion smoothly faces the concave curved surface of the concave portion. The pistons are brought into contact with each other so that the rotation of the piston is reliably and smoothly regulated.

Further, the lubricating oil blown off by the centrifugal force due to the rotation of the swash plate flows in the circumferential direction from a gap formed on the side opposite to the side where the detent portion of the piston comes into contact with the inner peripheral surface of the casing, and the oil groove is formed. The lubricating oil flows in from the axial direction, and the oil groove formed near the center in the circumferential direction of the concave portion functions as an oil reservoir for the lubricating oil flowing in. Thereby, the supply of the lubricating oil to the portion where the detent portion of the piston contacts the inner peripheral surface of the casing is always ensured, and the sliding portion is sufficiently lubricated.

The occurrence of abnormal noise and abrasion can be prevented by the smooth rotation of the piston by the smooth surface contact and the sufficient lubrication of the sliding part.

[0021]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a schematic sectional view of a variable displacement swash plate type compressor according to one embodiment of the present invention, FIG. 2 (A) is a front view of the piston shown in FIG. 1, and FIG. 2 (B) is a left side view thereof. FIG. 3 is an upper half sectional view taken along the line D in FIG. 1, and FIG. 4 is an enlarged view of a main part for explaining a piston detent structure shown in FIG.

The variable displacement swash plate type compressor of this embodiment shown in FIG. 1 has a cylindrical casing 12 with a rear head 10 and a front head 11 attached to both ends at each end. The cylinder chamber 13,
A crank chamber 14 is provided. The rear head 10
Is attached to the right end of the casing 12 in the figure via a valve seat 16 and is integrally connected to the front head 11 provided on the left end of the figure by bolts (not shown). Valve forming plates (not shown) are provided on both sides of the valve seat 16, and a retainer 18 is attached to the discharge valve side.

A front shaft side of a drive shaft 19 provided through the inside of the casing 12 protrudes through the front head 11, and a pulley 20 is connected to an end. An electromagnetic clutch 2 is provided between the drive shaft 19 and the pulley 20.
The electromagnetic clutch 27 is turned on when cooling is required, and the rotation of the engine is transmitted through a belt (not shown) mounted on the pulley 20. When cooling is not required, if the electromagnetic clutch 27 is turned off, the connection between the engine and the compressor is cut off, and only the pulley 20 idles without the drive shaft 19 rotating.

A plurality of cylinder chambers 13 are formed in the casing 12 at equal intervals in the circumferential direction, and a piston 23 is installed in each of the cylinder chambers 13. Each of these pistons 23 has a piston head 23a that reciprocates in the cylinder chamber 13, and an engaging portion 23b that engages with the swash plate 25 via substantially hemispherical shoes 71 and 72 and has a substantially U-shaped cross section. Consists of Shoe 7 is inserted into spherical concave portions 23c and 23d formed opposite to the inner surfaces on both sides of the engaging portion 23b.
1, 72 are fitted, and these two shoes 71, 7 are fitted.
The front and back surfaces of the swash plate 25 are sandwiched by the two flat portions and slidably contact with each other.

The left portion of the drive shaft 19 in the figure is supported by the front head 11 via a bearing 26.
A rotating member 28 that is rotated by the drive shaft 19 is provided inward. A sleeve 29 is provided on the inner end side of the rotary member 28 so as to be slidable in the axial direction. The outer peripheral surface of the sleeve 29 is formed in an arc shape, and the outer surface of the sleeve 29 is swingably inclined on the outer surface. The concave inner surface of the plate 25 is in contact.
The swash plate 25 and the rotating member 28 have links 30b,
30a is protruded, and these two links 30b, 30a
The rotating member 28 is connected to the long hole 31 by the pin member 32.
The swash plate 25 is rotated by the rotation of.

Therefore, the swash plate 25 is
With the movement of the drive shaft 19 in the axial direction, it is tilted with the pin member 32 as a fulcrum, and the tilt angle (referred to the tilt angle with respect to a plane orthogonal to the axis of the drive shaft 19) can be adjusted. The maximum inclination angle of the swash plate 25 is given at a position where the balancer 25a of the swash plate 25 contacts the rotating member 28 (the state of FIG. 1).

In the variable displacement swash plate compressor, a control valve Cv is provided in the rear head 10, and the pressure in the crank chamber 14 is adjusted in accordance with the suction pressure of the returning refrigerant to change the angle of the swash plate 25. The amount of refrigerant discharged from the compressor is adjusted so that the suction pressure of the compressor is kept constant.

A suction port 33 and a discharge port 34 are provided in the rear head 10.
Returned refrigerant flows from the evaporator, and the refrigerant is sucked against the elastic closing force of a plurality of suction valves formed in a circumferential direction on a valve forming plate (not shown) on the left side surface of the valve seat 16 in the drawing. The gas flows into the cylinder chamber 13 in the suction process sequentially from the port 33a.
The refrigerant compressed by the piston is supplied to the valve seat 1
6, discharge is performed against the elastic closing force of a plurality of discharge valves formed circumferentially on a valve forming plate (not shown) on the right side surface in the drawing.

In this embodiment, as shown in FIGS. 2A and 2B, the casing 12 of the engaging portion 23b of the piston 23 is provided.
A detent portion 82 is provided on the outer surface facing the. An arc-shaped convex surface 82a as a convex curved surface is formed on the detent portion 82, and the arc-shaped convex surface 82a has a radius of curvature R1 larger than the radius Rp of the piston head.

On the other hand, as shown in FIG. 3, a concave portion 83 having an arcuate concave surface 83a as a concave curved surface is formed on the inner peripheral surface of the casing 12 facing the rotation preventing portion 82 of the piston 23. Note that, in FIG. 3, the swash plate 25 is not shown in order to avoid complicating the drawing, and in FIG. 1, the case where five pistons are uniformly arranged in the circumferential direction as in this embodiment. In FIG. 2, both pistons at the top dead center position and the bottom dead center position do not appear in the vertical sectional view, but both pistons are described for easy understanding.

The arc-shaped convex surface 82a of the detent portion 82 of the piston 23 and the arc-shaped concave surface 83a of the inner peripheral surface of the casing 12 are arranged so as to be separated by a predetermined distance L as shown in FIG. Therefore, when the piston 23 is caused to reciprocate by rotating the inclined swash plate 25, the flat surfaces of the outer edges of the swash plate 25 correspond to the two shoes 71, 72.
Even if a force is applied to rotate the piston 23 in the direction E shown in FIG.
Can smoothly contact the arcuate concave surface 83a of the concave portion 83 to restrict the rotation of the piston 23.

In this embodiment, in particular, an oil groove 83b extending in the axial direction is formed near the center of the concave portion 83 in the circumferential direction.
The groove wall surface of the oil groove 83b is formed of a casting surface obtained when the casing 12 is formed, and the groove shape can be changed as appropriate. The splash of the lubricating oil in the crank chamber which has been blown off by the centrifugal force due to the rotation of the swash plate is, for example, as shown in FIG. When the arcuate concave surface 83a comes into contact, it flows in the circumferential direction from the gap on the opposite side as shown by the arrow F in the figure, and also flows in from the axial direction of the oil groove 83b, and the oil groove 83b flows in. It can function as an oil sump for lubricating oil. As a result, the supply of the lubricating oil to the contact portion C (arrow G in the figure) is ensured, and the sliding portion can be sufficiently lubricated.

Here, the arcuate concave surface 83a of the concave portion 83 is
When the piston 23 attempts to rotate to the left or right, the arc-shaped convex surface 82a of the detent portion 82
In other words, it is formed only in a region that contacts the oil groove 83b formed of a casting surface obtained at the time of molding, that is, a region opposed to the vicinity of the circumferential end of the arc-shaped convex surface 82a on both sides thereof.
Therefore, only the minimally necessary portion is machined as the arcuate concave surface 83a, and the cost can be reduced by saving the machining time.

Moreover, the arcuate concave surface 83a of the concave portion 83 is
As shown in FIG. 3, the casing 12 is configured to form a part of a cylindrical inner surface formed over the entire circumference along the inner peripheral surface of the casing 12. That is, the center of the arcuate concave surface 83a coincides with the center axis of the drive shaft 19. With such an arcuate concave surface 83a of the concave portion 83, the arcuate concave surface 83a can be machined for all pistons (five pistons arranged evenly in the circumferential direction) at one time, so that the number of machining steps can be further reduced. Reduction can be achieved.

The axial length of the concave portion 83 formed on the inner peripheral surface of the casing 12 is at least
Is set to a length that does not interfere with the rotation stop portion 82 of the piston 23 due to the reciprocation of the piston 23. Also,
The aforementioned (curvature) radii R1, R2, Rp and the distance L are appropriately adjusted based on design specifications.

Next, the operation of this embodiment will be described. When the electromagnetic clutch 27 is turned on and the drive shaft 19 is rotated by the engine via the belt and the pulley, the rotating member 28 is rotated accordingly, and the swash plate 25 is also rotated via both the links 30a and 30b and the pin member 32. Rotate. If the swash plate 25 is inclined with respect to the drive shaft 19, the swash plate 25 rotates in a whisker-like manner, and the piston 23 reciprocates accordingly, whereby the suction, compression and discharge of the refrigerant are performed.

Here, when the heat load in the cooling cycle is large, the pressure of the return refrigerant returns at a relatively high pressure. In this case, a relatively high suction pressure is introduced into the crank chamber 14 by the action of the control valve Cv, so that the internal pressure becomes substantially equal to the suction pressure. For this reason, even in the piston 23 in the suction process, there is almost no pressure difference between the front and rear, and the piston 23 can smoothly retreat in the cylinder chamber 13 of the cylinder 15, and the stroke of the piston 23 increases. When compression is performed in this state, the amount of discharged refrigerant increases, the amount of refrigerant circulating in the cooling cycle increases, an appropriate amount of refrigerant is discharged again according to the heat load, and the suction pressure of the compressor gradually decreases. Finally, a constant suction pressure is maintained.

On the other hand, when the heat load in the cooling cycle is small, the pressure of the return refrigerant does not provide a sufficient amount of superheat and returns at a low pressure. In this case, the high-pressure refrigerant compressed by the piston 23 and guided to the discharge port 34 is introduced into the crank chamber 14 by the operation of the control valve Cv, and the internal pressure of the crank chamber 14 is increased. As a result, a difference occurs in the moment of the force applied to each of the plurality of pistons 23 centering on the pin 32, and each piston 2
The pressure balance before and after 3 changes, and the inclination angle of the swash plate 25 decreases.

As described above, the suction, compression, and discharge of the refrigerant are performed only when the swash plate 25 in the inclined state is reciprocated by applying an axial force to the piston 23 by the rotational motion of the swash plate. In this case,
The flat surface of the outer edge of the swash plate 25 slides between the shoes 71 and 72 in the circumferential direction at a high speed, and the two shoes 71 and 72 move at high speed.
A force acts to rotate the piston 23 around the piston axis via 72.

Such a rotational force is caused by a difference in a local sliding state when sliding while pressing the flat portion of the shoe, a difference in a sliding speed based on a difference in distance from the center of rotation, and the like. It is thought to happen. For example, when the piston 23 is rotated in the direction E shown in FIG.
The detent portion 82 provided on the outer surface of the third engaging portion 23b
Are rotated about the piston axis, and the detent portions 82
The contact portion C near the left end in the circumferential direction is in contact with the arcuate concave surface 83a of the concave portion 83 so as to make smooth surface contact, and the rotation of the piston 23 is reliably and smoothly regulated.

The splash of the lubricating oil in the crank chamber, which was blown off by the centrifugal force due to the rotation of the swash plate,
3, the lubricating oil flows in from the axial direction of the oil groove 83b, and the lubricating oil also flows in from the axial direction of the oil groove 83b.
b can function as a sump for the lubricating oil that has flowed in. Thereby, the supply of the lubricating oil to the contact portion C can be always ensured, and the sliding portion can be sufficiently lubricated.

Accordingly, the occurrence of abnormal noise and abrasion can be prevented by preventing the rotation of the piston by such smooth surface contact and by sufficiently lubricating the sliding portion.

The embodiments described above are described for the purpose of facilitating the understanding of the present invention, but not for limiting the present invention. Therefore, each element disclosed in the above embodiment is intended to include all design changes and equivalents belonging to the technical scope of the present invention.

For example, in the above-described embodiment, the concave portion 83 formed opposite the detent portion 82 of each piston 23
Although the center axis of the circular concave surface 83a is made to coincide with the center axis of the drive shaft 19, the present invention is not limited to such a configuration, and the detent portions 82 of each piston 23 are not limited to such a configuration.
It is also possible to configure so as to face each other and form respective arcuate concave surfaces centered on different central axes.

The variable capacity swash plate type compressor has been described above as an example. However, the present invention can be applied not only to the variable capacity type compressor but also to a fixed capacity swash plate type compressor. Further, the piston can be applied to a piston having piston heads on both sides in the axial direction of the engaging portion with the swash plate.

[0046]

As described above, according to the present invention, when the swash plate slides between the two shoes at high speed in the circumferential direction and the piston is rotated through both the shoes, The rotation preventing portion formed on the outer surface of the engaging portion of the piston facing the casing is rotated about the piston axis so that the convex curved surface of the rotation preventing portion makes smooth surface contact with the concave curved surface of the concave portion. As a result, the rotation of the piston can be reliably and smoothly regulated.

Further, the lubricating oil blown off by the centrifugal force due to the rotation of the swash plate flows in the circumferential direction from a gap formed on the side opposite to the side where the detent portion of the piston comes into contact with the inner peripheral surface of the casing, and the oil groove is formed. The lubricating oil flows in from the axial direction, and the oil groove can function as an oil reservoir for the lubricating oil flowing in. Thereby, the supply of the lubricating oil to the portion where the detent portion of the piston and the inner peripheral surface of the casing abut can be always secured, and the lubrication of the sliding portion can be sufficiently performed.

Therefore, the occurrence of abnormal noise and abrasion can be prevented by the rotation stop of the piston due to the smooth surface contact and the sufficient lubrication of the sliding part.

Further, the detent portion formed on the piston and the concave portion formed on the casing are both easily processed, so that the number of steps and the product cost can be reduced. In addition, the arcuate concave surface of the concave portion is formed on both sides of the oil groove in a region where the convex curved surface of the detent portion comes into contact with the casing when the piston rotates left or right, so that the convex concave surface is processed. Is the minimum necessary part, and the cost can be further reduced by saving the processing time.

If the concave curved surface of the casing is configured to form a part of a cylindrical surface formed over the entire circumference along the inner peripheral surface of the casing, the concave curved surface for all the pistons can be processed at one time. And the number of processing steps can be further reduced.

[Brief description of the drawings]

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

2A is a front view of the piston shown in FIG. 1, and FIG. 2B is a left side view of the same.

FIG. 3 is an upper half sectional view taken along line D in FIG. 1;

FIG. 4 is an enlarged view of a main part for explaining a piston detent structure shown in FIG. 3;

FIG. 5 is a view of a piston of a conventional swash plate type compressor as viewed from the rear in the axial direction.

FIG. 6 is a view of a piston of a conventional swash plate compressor as viewed from the rear in the axial direction.

[Explanation of symbols]

12: Casing, 13: Cylinder chamber, 14: Crank chamber, 19: Drive shaft, 23: Piston, 23a: Piston head, 23b: Engagement part, 23c, 23d: Spherical recess, 25: Swash plate, 71, 72 ... Shoe, 82 ...
Detent part, 82a: arc convex surface (convex curved surface), 83: concave portion, 83a: arc concave surface (concave curved surface), 83b: oil groove, L: distance, R1, R2: radius of curvature, Rp
... the radius of the piston.

────────────────────────────────────────────────── ─── Continuation of front page (56) References JP-A-6-346844 (JP, A) JP-A-6-66253 (JP, A) JP-A-7-189898 (JP, A) JP-A-54- 162217 (JP, A) Japanese Utility Model 6-25573 (JP, U) Japanese Utility Model 63-93480 (JP, U) Japanese Utility Model Utility Model 62-133393 (JP, U) (58) Field surveyed (Int. ⁷ , DB name) B60H 1/32 613 B60H 1/00 F25B 31/00 F04B 27/08 F04B 39/00

Claims (2)

(57) [Claims] 1. A rotatably mounted shaft around a casing (12).
Provided in the drive shaft (19) and the crank chamber (14) of the casing (12)
A swash plate (25) connected to the drive shaft (19)
A plurality of cylinder chambers (13) formed in the swash plate (2).
5) By rotating the swash plate (25), it is placed in contact with both front and back surfaces
The inside of the cylinder chamber (13) through the shoes (71, 72)
With a plurality of pistons (23) reciprocated in the axial direction
In the swash plate compressor, the piston (23) is a piston that reciprocates in the cylinder chamber (13).
Head (23a) and the swash plate (25) via the shoes (71, 72).
An engagement portion (23b) to be engaged with the casing (12) of the engagement portion (23b) of the piston (23).
On the facing outer surface, a curve larger than the piston head radius (Rp)
Detent with a convex curved surface (82a) having a radius of curvature (R1)
Part (82), and the casing (1) facing the detent part (82) of the piston (23).
2) Inner circumferenceAnd the piston (23) rotates around the piston axis.
The area where the detent part (82) comes into contact when trying to move
Inner radius of curvature larger than the piston head radius (Rp)
A concave portion (83) on which a concave curved surface (83a) having (R2) is formed,
Predetermined from the convex curved surface (82a) of the detent part (82) of the piston (23)
A distance (L) apart and the concave portion (83)
The oil groove (83b) is formed near the center in the circumferential direction of the
Swash plate compressor. 2. A concave curved surface (83) of a concave portion (83) of a casing (12) formed to face a detent portion (82) of a piston (23).
The swash plate compressor according to claim 1, wherein a) forms a part of a cylindrical inner surface formed over the entire circumference along the inner peripheral surface of the casing (12).