JPH03141877A - Compressor with swash plate - Google Patents

Abstract

PURPOSE:To reduce abnormal wear, sticking, etc., of a gliding member and prevent generation of contacting noise by arranging retainer and No.1 bearing means between a swash plate and the gliding member, and furnishing No.2 bearing means between the insides of retainer plates and the swash plate. CONSTITUTION:Between a swash a plate 9 and irregularly formed steel balls 20, 21 are furnished retainer plates 18, 19, which support the steel balls 20, 21 slidably, and rolling bearings 16, 17 which support them in such a way as rotatable relative to the swash plate 9. Ball bearings 24, 25 to support the retainer plates 18. 19 rotatably are arranged between the insides of these retainer plates 18, 19 and the swash plate 9. Thus the swash plate 9 rotates through the rolling bearings 16, 17, so that abnormal wear, sticking, etc., of the irregularly formed steel balls 20, 21 will be reduced, and also provision of ball bearings 24, 25 enables bearing the load inward directed in the radial direction of the retainer plates 18, 19 which should achieve generation of contacting noise.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a swash plate compressor, and particularly to a swash plate compressor suitable for use in an air conditioner for an automobile.

[Conventional technology]

Conventionally, swash plate compressors used in automobile air conditioners are disclosed in Japanese Patent Application Laid-open No. 50-97914 and Japanese Patent Application Laid-Open No. 59-511.
It is common to use a fixed swash plate balanced type as described in No. 74 and the like. As shown in FIG. 6, this swash plate compressor is rotatably supported by left and right cylinder blocks 51A and 51B, and radial bearings 52 and 53 provided at the center of each of the left and right cylinder blocks 51A and 51B. a swash plate 55 that is press-fitted into the center of the shaft 54; and a swash plate 55 that is arranged circumferentially around the shaft 54 on both sides of the swash plate 55, and the left and right cylinder blocks 51^ are arranged by rotation of the swash plate 55. , 51B, each of which reciprocates in the axial direction, and is arranged between the swash plate 55 and the pistons 56.57, converting the rotational movement of the swash plate 55 into the reciprocating movement of the pistons 56.57. ball 58
59 and slippers 60 and 61, and a valve plate and an end cover (not shown) are arranged at both ends of the cylinder blocks 51A and 51B, respectively.

Furthermore, ring-shaped protrusions 62, 63 and 64, 65 are provided at the center of the cylinder blocks 51A, 51B and the center of the swash plate 55, respectively, and these protrusions 62, 63 and 64, 65 face each other alternately.
Between 2 and 64 and between 63 and 65 are inner thrust races 66, 67 and thrust rollers 68.
2 consisting of 69 and outer thrust race 70.71
A pair of thrust bearings are arranged.

When the rotational force from the crank pulley of the vehicle is transmitted to the shaft 54 via a V-belt and a magnetic clutch (not shown), the pistons 56 and 57 reciprocate in the axial direction due to the rotation of the swash plate 55, and the refrigerant in the refrigeration cycle is Compress the gas and send it to the condenser.

In addition, as a sliding member that converts the rotational motion of the swash plate into reciprocating motion of the piston, a hemispherical sliding member whose surface in contact with the swash plate is a plane parallel to the side surface of the swash plate and whose surface in contact with the piston is a spherical surface is used. It is possible to arrange the balls 58, 59 and slippers 60, 61 in place of the balls 58, 59 and slippers 60, 61, for example, according to JP-A-56-13847.
This is done as described in No. 4.

On the other hand, regarding the structure of the part that converts the rotational motion of the swash plate into the reciprocating motion of the piston in a swash plate compressor, there is a structure described in JP-A-55-114888, which describes the structure of the ball of the swash plate compressor. A hemispherical sliding member corresponding to 58.59 is slidably supported on an annular floating disk (retainer plate), and a roller bearing is arranged between the floating disk and the swash plate. .

[Problem to be solved by the invention]

In conventional swash plate compressors, lubricating oil is supplied during compression of refrigerant gas using lubricating oil contained in refrigerant gas moving within the refrigeration cycle. This can cause a lack of refrigerant or blockage in the cycle during high-speed rotation.
The necessary lubricating oil is supplied to the swash plate 55 and slippers 60, 61 (sixth
Figure) or swash plate and hemispherical sliding member (Japanese Patent Laid-Open No. 56-1
38474), slippers 60.6
There has been a problem in that abnormal wear of the hemispherical or hemispherical sliding members, sticking accidents, etc. occur.

When the structure described in JP-A-55-114888 is applied to a swash plate type compressor, by arranging roller bearings between the floating disk and the swash plate, the above-mentioned slipper 60, 61 or hemispherical sliding Problems such as abnormal wear of parts and sticking accidents can be reduced.

However, in this case, since the hemispherical sliding member slides in the radial direction on the floating disk as the swash plate rotates, a corresponding radial load acts on the floating disk, causing a radial There is a problem in that the inner diameter side of the floating disk comes into contact with the center portion of the rotating swash plate due to the load directed inward, and this contact generates abnormal noise.

An object of the present invention is to provide a swash plate compressor that reduces abnormal wear of sliding members, sticking accidents, etc., and generates less contact noise.

Another object of the present invention is to provide a swash plate compressor that reliably supplies lubricating oil to parts that require oiling, such as sliding members and bearings, even during high-speed rotation or when there is a shortage of refrigerant in the cycle, thereby improving durability. It is to be.

[Means for Solving the Problems] In order to achieve the above object, the present invention includes a cylinder block, a shaft rotatably supported by the cylinder block, a swash plate fixed to the shaft, and a cylinder block that is rotatably supported by the cylinder block. In the swash plate compressor, the swash plate compressor includes a plurality of pistons that reciprocate in the axial direction within the cylinder block, and a sliding member that is disposed between the swash plate and the pistons and converts rotational movement of the swash plate into reciprocating movement of the pistons. A retainer plate that slidably supports the sliding member and a first bearing means that rotatably supports the retainer plate with respect to the swash plate are disposed between the swash plate and the sliding member, and the retainer plate A swash plate type compressor is provided, in which a second bearing means for rotatably supporting the retainer plate is arranged between the inner diameter side of the retainer plate and the swash plate.

Preferably, the sliding member is a deformed sphere whose surface in contact with the retainer plate has a plane parallel to the retainer plate, and whose surface in contact with the piston is a spherical surface having a concave portion.

Further, the present invention provides a runner means having a helically cut groove at least on the end face at one end of the shaft, the periphery of the runner means is communicated with the low pressure port, and the runner is provided at the center of the shaft. A swash plate compressor is provided with an axial oil supply hole connected to a groove of the means, and a radial oil supply hole connected to the axial oil supply hole adjacent to a location around the shaft that requires oil supply.

[Effect]

In the present invention configured in this way, by disposing the first bearing means between the swash plate and the sliding member via the retainer plate, the swash plate rotates via the first bearing means. Abnormal wear of sliding members, sticking accidents, etc. can be reduced, and by arranging the second bearing means between the inner diameter side of the retainer plate and the swash plate, the rotation of the swash plate can be reduced without hindering the rotation of the swash plate. Since the load directed toward is supported, abnormal contact noise can be prevented.

In addition, by providing a runner means that communicates with the low pressure port at one end of the shaft, and providing an axial oil supply hole connected to the groove of the runner means and a radial oil supply hole connected to this, it can be used as a simple pump when the shaft rotates. The functioning runner means forcibly sucks up the lubricating oil accumulated in the low pressure port and directs it into the axial oil supply hole. The oil accumulated in the axial oil supply hole is scattered and supplied to the oil-requiring locations from the radial oil supply hole by centrifugal force when the shaft rotates. The amount of oil supplied to the locations that require lubrication increases as the shaft rotates at high speed, and since lubricating oil cooled by low-pressure refrigerant is supplied, the durability of the locations that require lubrication is improved.

By making the irregularly shaped sphere of the sliding member so that the surface in contact with the retainer plate has a plane parallel to the retainer plate, no slipper is required and the number of parts can be reduced, and by making the surface in contact with the piston a spherical surface with a recess, Since the recess on the piston side that receives the spherical surface can be made into a spherical surface that does not require relief, the number of man-hours required for machining the spherical surface of the recess on the piston side can be reduced by one time, and the recess of the irregularly shaped sphere also functions as an oil sump. This improves the sliding properties of the spherical contact area and improves durability.

〔Example〕

An embodiment of the present invention will be described below with reference to FIGS. 1 to 3.

In FIG. 1, the swash plate type compressor of this embodiment is a fixed swash plate balance type that compresses refrigerant gas on both sides of the swash plate, and is composed of a shaft 1, a central hole 2.
3 are installed in the left and right cylinder blocks 4 and 5, radial bearings 6 and 7 are respectively installed in the cylinder block center hole 2° 3 and support the shaft 1 in a rotatable manner, and the radial bearings 6 and 7 are press-fitted and fixed to the center part 8 of the shaft 1. The swash plate 9 is assembled on both sides of the swash plate 9 so as to straddle the swash plate 9, and is arranged circumferentially around the shaft 1, and the left and right cylinder blocks 4 are assembled by rotating the swash plate 9. , 5, and a cylinder block 4.
, 5, and includes valve plates 12, 13 and end covers 14, 15 provided at both ends of the valves.

Between the swash plate 9 and the pistons 10.11, there are a rolling bearing 16.17, a retainer plate 18° 19, and a deformed steel ball 2 for converting the rotational movement of the swash plate 9 into reciprocating movement of the piston 10.11.
0.21 is placed.

The rolling bearing 16.17 and the retainer plates 18-19 are mounted parallel to the swash plate 9, as shown in FIG. 2, and the rolling bearing 16.17 is held in an internal retainer 22.23. A ball bearing 24.25 is arranged on the central portion 9a of the swash plate 9, and a rolling bearing 16.1
The inner diameter side of the retainer plate 18.19 is directly connected to the outer races 24a, 25a of the ball bearings 24.25 via the inner peripheral part of the internal retainer 22.23 and the distance piece 26.27 that supports this. is held in

Further, the swash plate 9 is preferably made of a sintered alloy, for example, which requires minimal post-processing, and the rolling surface on which the rolling bearings 16 and 17 slide is provided with backing plates 16a and 17 made of steel plates.
A is attached. Note that the rolling bearings 16 and 17 may be ball bearings.

The deformed steel balls 20 and 21 are formed using a special forging method, and each
The surface in contact with the retainer plate 18.19 has planes 20a, 21a parallel to the retainer plate, and the surface in contact with the piston 10.11 consists of a spherical surface 20b, 21b with recesses 28, 29.

One end of the shaft 1 projects outward beyond the end of the cylinder block 11 and the valve plate 13, and a cantilever thrust bearing mechanism 30 is provided at this projecting end. The end cover 15 also has an adjustment nut 3L for adjusting the thrust preload of the cantilever thrust bearing mechanism 30.
is provided.

The cantilever thrust bearing mechanism 30 has a center race 32 that is inserted into the end of the shaft 1 and receives a thrust load, and further has a center race retainer 3 at the end of the shaft 1.
3 is inserted, and a threaded portion 34 is provided at the end of the shaft 1, and the center race 32 is inserted between the stepped portion 36 of the shaft 1 and the center race retainer 33 by tightening a lock nut/runner 35 to the threaded portion 34. Clamped and fixed. The cantilever thrust bearing mechanism 30 also includes inner races 37 located on both sides of the center race 32.
and an outer race 38, and needle bearings 39 and 40 disposed therebetween.

Attach the adjusting nut 31 to the threaded portion 4 in the center of the end cover 15.
1, the tip of the adjustment nut 31 comes into contact with the outer race 38, and the cantilever thrust bearing mechanism 30 is pressed against the valve plate 13. As a result, the cantilever thrust bearing mechanism 30 supports the thrust load acting on the shaft 1 in both left and right directions between the valve plate 13 and the end cover 15. Further, by adjusting the screwing amount of the adjustment nut 31, the thrust preload of the cantilever thrust bearing mechanism 30 is adjusted.

An O-ring 42 is disposed in the groove of the end cover 15 between the head 31a of the adjustment nut 31 and the end cover 15 to keep the interior of the compressor confidential.

A through bolt 43 is provided on the left and right end covers 14.15, and by tightening this through bolt 43 to the shell 44, a tightening force is applied to the end cover 14°t5, and the end cover 14°15 and the cylinder block are tightened. 4,
sandwiching and fixing the valve plate 12.13 between the
It constitutes a compressor assembly.

As shown in FIG. 3, a plurality of spiral grooves 45 and 46 are cut on the outer periphery and end face of the lock nut/runner 35, and the grooves 45 and 46 are formed in a spiral shape that runs counter to the direction of rotation of the shaft 1.
It communicates with a low-pressure boat 48 in the rear cover 15 through a hole 47 made in the rear cover 15 . Furthermore, the low pressure port 48 communicates with the cylinder low pressure section via a hole 48A formed in the cylinder block 5.

An axial oil supply hole 49 is provided at the center of the shaft 1,
All of the grooves 46 on the end surface of the lock nut/runner 35 mentioned above are connected to the oil supply hole 49 at their centers. The shaft 1 also has radial bearings 6 and 7 around the shirt 11 that require oiling, ball bearings 24 and 25 (including rolling bearings 16 and 17 and deformed steel balls 20 and 21), and needle bearings 39 and 40. Correspondingly, a plurality of radial oil supply holes 50 which are connected to the axial oil supply hole 49 are provided.

A pulley 51 and a magnetic clutch 52 are attached to the end of the shaft 1 on the end cover 14 side as usual. Rotational force from a crank pulley of the vehicle is transmitted to the pulley 51 via a V-belt (not shown). Therefore,
By turning on the magnetic clutch 52, the shaft 1 rotates, and the rotation of the swash plate 9 causes the pistons 10.11 to reciprocate in the axial direction, compressing the refrigerant gas in the refrigeration cycle and sending it to a condenser (not shown).

In the swash plate compressor of this embodiment configured as described above, a retainer plate 18 is provided between the swash plate 9 and the deformed steel balls 20 and 21.
．． Since the rolling bearings 16 and 17 are arranged through the deformed steel balls 20 and 19, the swash plate 9 rotates when the shaft 1 rotates.
The deformed steel balls 20 and 21 are not transmitted to the retainer plate 18.
．． With only a slight radial sliding relative to 19, the rotational movement of the swash plate 9 is converted into a reciprocating movement of the piston 10.11.

Therefore, even if a lubricating oil shortage occurs, the probability of occurrence of abnormal wear, sticking accidents, etc. of the deformed steel balls 20, 21, which are sliding members, is reduced, and durability can be improved. Also, when the compressor is started, the ambient temperature is low and the piston 10.
Although the starting torque tends to increase due to thermal contraction of the bearings 11, such starting torque can be reduced by arranging the rolling bearings 22 and 23.

In addition, since a cantilever thrust bearing mechanism 30 is provided at the end of the shaft 1 to support thrust loads acting on the shaft 1 in both left and right directions, the cantilever thrust bearing mechanism 30 has a Cylinder block 4.
5 and the swash plate 9, and the tightening of the through bolt 43 is no longer affected by load fluctuations due to force fluctuations, etc., and the thrust preload fluctuations are reduced. The occurrence of abnormal noise during operation can be reduced, reliability can be improved, and durability can be improved.

Furthermore, since the end cover 15 is provided with an adjustment nut 31 for adjusting the thrust preload, the cantilever thrust bearing mechanism 3
It becomes possible to adjust the thrust preload of 0 from the outside, and the thrust preload can be freely adjusted by rotating the adjustment nut 31 after the compressor is assembled. Therefore, the work required to adjust the thrust preload at the intermediate assembly stage, which was conventionally required, is no longer necessary, and the assembly time can be significantly shortened. Further, by detecting the torque of the adjustment nut, the thrust preload can be known, and an accurate thrust preload can be set.

Further, according to this embodiment, the retainer plate 18.19 provided parallel to the swash plate 7 and the ball bearing 24.2 fixed to the swash plate 9 on the inner diameter side of the rolling bearing 16.17.
5 outer lace 24a.

25a, so when the swash plate 9 rotates, the retainer plate 18
．． 19 and the rolling bearing 16.17, the radially inward load acts on this ball bearing 24.25.
The retainer plates 18, 19 and rolling bearings 16, 17 can prevent abnormal noise from occurring due to contact between the swash plate 9 and the retainer plates 18, 19 and the rolling bearings 16, 17 without inhibiting the rotational movement of the swash plate 9.

Further, a helical groove 45° 46 is provided on the outer periphery and end face of the lock nut/runner 35 provided at one end of the shaft 1, and an oil supply hole 4 connected to the helical groove 45° 46 is provided in the shaft 1.
9.50, the spiral grooves 45 and 46 function as pumping means, and the pumping action of the spiral grooves forcibly sucks up the lubricating oil accumulated in the low pressure port 48 and sends it to the axial oil supply hole 49. , this oil is further added to shaft 1
Radial bearings 6, 7 and ball bearings 24.2, which are important points for oiling from radial oil supply hole 50 due to centrifugal force during rotation of
Around 5 (rolling bearing 16.17 and deformed steel ball 20.
21), the needle bearings 39 and 40 are splashed with oil. At this time, the amount of oil supplied increases as the shaft 1 rotates at high speed, and the lubricating oil cooled by the low-pressure refrigerant in the low-pressure boat 48 is supplied, so the durability of the points requiring oil supply is dramatically improved. Can be done.

Furthermore, since the deformed steel balls 20.21, which are sliding members, are shaped to have flat surfaces 20a, 21a and spherical surfaces 20b, 21b, slippers that would be necessary if the sliding members were made of balls are no longer necessary. , the number of parts can be reduced. Moreover, the spherical surface 20b.

Since the recesses 28 and 29 are provided in 21b, the spherical surface 20b
, 21b on the piston 10.11 side can be made into a spherical shape that does not require relief, and the number of man-hours required for machining the spherical surface of the piston side recess can be reduced by one time.
．． Since 29 has the function of an oil reservoir, by injecting lubricating oil into this and assembling, the lubrication effect of the spherical contact portion is improved, and from this point of view as well, durability can be improved.

FIG. 4 shows a modification of the swash plate portion of the present invention. This embodiment includes a retainer plate 18 or 19, an internal retainer 22 or 23, and a distance piece 26 or 27 shown in FIG.
, and the outer race 24a or 25a of the ball bearing 24 or 25 are used, and the rolling bearing 17 is held against the swash plate 9 and the ball bearing 81 by this member 80. This embodiment also provides the same effects as the first embodiment and has an economical advantage because the number of parts can be reduced.

FIG. 5 shows a modification of the deformed steel ball of the present invention. The required shape of the deformed steel ball is that the other side is flat and the other side can be in line contact with the spherical recess on the piston side. Other shapes are possible. That is, the deformed steel ball 8 in FIG. 5(a)
5 has a flat surface 85a, and the other side has a spherical surface 85b and a flat surface 85c. The deformed steel ball 86 in FIG. 6(b) is
One side has a flat surface 86a and a recess 86b is provided on that surface, and the other side is a spherical surface 86c and has a recess 86d. With these shapes as well, the same effects as in the first embodiment can be obtained.

〔Effect of the invention〕

According to the present invention, since the first bearing means is arranged between the swash plate and the sliding member via the retainer plate, and the second bearing means is arranged between the inner diameter side of the retainer plate and the swash plate, the sliding member Abnormal wear, sticking accidents, etc. can be reduced, and abnormal contact noise can be prevented.

In addition, a runner means is provided at one end of the shaft, and an axial oil supply hole and a radial oil supply hole are provided in the shaft.
As the shaft rotates, the lubricating oil accumulated in the low-pressure port is forcibly sucked up and dispersed to the areas that require lubrication, increasing the lubrication effect of the areas that require lubrication and greatly improving durability.

Furthermore, since the irregularly shaped sphere of the sliding member has a spherical shape with a flat surface and a recess, the number of parts can be reduced and the number of man-hours required for machining the spherical surface of the recess on the piston side can be reduced, which is an economical advantage. Since it functions as an oil reservoir, the lubrication effect is improved and the durability of the layer can be improved.

[Brief explanation of the drawing]

FIG. 1 is a sectional view of a swash plate compressor according to an embodiment of the present invention, FIG. 2 is an enlarged excerpt of the main parts of the swash plate compressor shown in FIG. FIG. 4 is a perspective view showing an enlarged runner portion shown in the figure; FIG. 4 is a sectional view of a swash plate portion according to another embodiment of the present invention; FIGS.
b) is a diagram showing a modified example of a deformed steel ball, and FIG. 6 is a sectional view of a conventional swash plate compressor. Explanation of symbols 1...Shaft 4.5...Cylinder block 9...Swash plate 10.11...Piston 13...Valve plate 15...End cover 16.17...Rolling bearing ( first bearing means) 18
．． 19... Retainer plate 20. 21... Deformed steel ball (sliding member) Qa, 21a.
...Flat surface Ob, 21b...Spherical surface 4.25...Ball bearing (second bearing means) 8
．． 29... Recess 0... Cantilever thrust bearing mechanism 5... Lock nut and runner (runner means) 6...
Spiral groove 7... Hole 9... Axial oil supply hole 0... Radial oil supply hole

Claims (6)

[Claims] (1) A cylinder block, a shaft rotatably supported by the cylinder block, a swash plate fixed to the shaft, a plurality of pistons that reciprocate in the cylinder block in the axial direction by rotation of the swash plate, and a swash plate. and a sliding member disposed between the swash plate and the piston to convert rotational motion of the swash plate into reciprocating motion of the piston, the sliding member being slidably disposed between the swash plate and the sliding member. A supporting retainer plate and a first bearing means for rotatably supporting the retainer plate with respect to the swash plate are disposed, and the retainer plate is rotatably supported between the inner diameter side of the retainer plate and the swash plate. A swash plate type compressor, characterized in that a second bearing means is disposed to support the swash plate compressor. (2) In the swash plate compressor according to claim 1, a runner means having a spirally cut groove at least on an end face is provided at one end of the shaft on the low pressure port side, and the periphery of the runner means is provided at one end of the shaft on the low pressure port side. an axial oil supply hole connected to the groove of the runner means is provided in the center of the shaft, and a radial oil supply hole connected to the axial oil supply hole is provided adjacent to a location around the shaft that requires oil supply. A swash plate compressor characterized by the following: (3) In the swash plate compressor according to claim 1, the sliding member is a deformed sphere whose surface in contact with the retainer plate has a plane parallel to the retainer plate, and whose surface in contact with the piston is a spherical surface having a concave portion. A swash plate compressor characterized by: (4) A cylinder block, a shaft rotatably supported by the cylinder block, a swash plate fixed to the shaft, a plurality of pistons that reciprocate in the cylinder block in the axial direction by rotation of the swash plate, and a swash plate. and a sliding member disposed between the piston and the piston to convert rotational motion of the swashplate into reciprocating motion of the piston, wherein one end of the shaft has a helically cut groove at least on the end surface. A runner means is provided, and the periphery of the runner means is communicated with the low pressure port, and an axial oil supply hole is provided in the center of the shaft that connects to the groove of the runner means, and is located adjacent to a location around the shaft that requires oil supply. A swash plate compressor, characterized in that a radial oil supply hole is provided that is continuous with the axial oil supply hole. (5) A cylinder block, a shaft rotatably supported by the cylinder block, a swash plate fixed to the shaft, a plurality of pistons that reciprocate in the cylinder block in the axial direction by rotation of the swash plate, and a swash plate. and a sliding member disposed between the piston and the piston to convert rotational motion of the swash plate into reciprocating motion of the piston, and a valve plate and an end cover located at both ends of the cylinder block. project outward beyond the cylinder block and valve plate, and at this projecting end,
A cantilever thrust bearing means is provided to support thrust loads in both directions acting on the shaft between the valve plate and the end cover, and a lock is provided at one end of the shaft to fix and hold the cantilever thrust bearing means to the shaft. A runner means that also serves as a nut and has a helically cut groove on at least an end face is provided, the periphery of the runner means is communicated with the low pressure port, and an axial groove connected to the groove of the runner means is provided at the center of the shaft. A swash plate compressor characterized in that a lubrication hole is provided, and a radial lubrication hole connected to the axial lubrication hole is provided adjacent to a lubrication required location including the sliding member and thrust bearing means around the shaft. . (6) A cylinder block, a shaft rotatably supported by the cylinder block, a swash plate fixed to the shaft, a plurality of pistons that reciprocate in the cylinder block in the axial direction by rotation of the swash plate, and a swash plate. and a sliding member disposed between the swash plate and the piston to convert rotational motion of the swash plate into reciprocating motion of the piston, the sliding member being slidably disposed between the swash plate and the sliding member. A supporting retainer plate and a bearing means for rotatably supporting the retainer plate with respect to the swash plate are disposed, and the sliding member is arranged such that a surface in contact with the retainer plate has a plane parallel to the retainer plate, and A swash plate compressor characterized in that the surface in contact with the piston is a deformed sphere consisting of a spherical surface having a concave portion.