JP2007046472A - Method for machining piston used in piston type compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To avoid formation of a tool mark of a type which easily causes wear of a projected spherical part of a shoe provided therewith or a recessed spherical surface shape seat formed on a piston. <P>SOLUTION: A cutting tool 47 rotatably supported at an upper end part of a column 43 obtains rotary driving force from an electric motor 44 via a drive pulley 45, a timing belt 50 and a driven pulley 49. The cutting tool 47 rotates around a center axis line L1 of a shaft 471. The cutting tool 47 provides a spherical cutting surface by rotation. A cutting edge of the cutting tool 47 exists on a front surface side of the column 43 the cutting edge draws a spherical trajectory having a spherical center on the center axis line L1 of the shaft 471 when the cutting tool 47 rotates. The cutting tool 47 moves toward the center axis line L1 with rotating to cut and form recessed spherical surface shape seat surfaces 25, 26. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a piston used in a piston-type compressor in which gas is compressed by rotating a cam body and reciprocating the piston so that the piston is fitted to a convex spherical portion of a shoe having a convex spherical shape. The present invention relates to a method for processing a concave spherical bearing surface formed on the surface.

For example, Patent Document 1 discloses a processing method of a concave spherical seating surface formed on a piston used in a piston-type compressor. In the machining method disclosed in Patent Document 1, a tool having an arcuate blade portion is to be machined while rotating the piston around a rotation axis passing through the center of a piston-side receiving seat (concave spherical seating surface). The receiving seat (concave spherical seating surface) is processed by parallel translation to the side. The accuracy of the sphere radius of the seating surface (true sphere accuracy) is the profile of the arcuate blade (arc shape of the blade edge) and the maximum distance (maximum rotation radius) between the edge of the arcuate blade and the rotation axis. It depends on. If the radius of the arc of the cutting edge and the maximum distance (maximum turning radius) coincide with each other with high accuracy, the true spherical accuracy of the concave spherical shape increases.
Japanese Patent Laid-Open No. 10-220354

  The convex spherical surface portion of the shoe slides with respect to the receiving seat (concave spherical surface) by the rotation of the swash plate. Therefore, the true spherical accuracy of the receiving seat (concave spherical seating surface) is as high as possible, and the seating surface should be as smooth as possible. However, when the receiving seat is processed by the arcuate blade portion, the tool mark may be markedly attached to the concave spherical seating surface. This tool mark is a streak pattern that mainly faces in a direction orthogonal to the direction of rotation of the piston that rotates about the rotation axis. Such tool marks are worn on the bearing surface or the convex spherical surface of the shoe when the piston compressor is at high speed and high load, or when there is little lubricating oil between the concave spherical bearing surface and the shoe. It becomes easy to do.

  An object of the present invention is to avoid generation of a tool mark of a type that easily causes wear on a convex spherical surface portion of a shoe or a concave spherical bearing surface formed on a piston.

  According to the present invention, a convex spherical surface of a pair of shoes each having a convex spherical surface is fitted to a pair of concave spherical bearing surfaces formed on a piston, and the shoe is a cam of a cam body. A piston used in a piston-type compressor that is interposed between a surface and the piston and compresses gas when the cam body rotates and the piston reciprocates, and the concave spherical seat The invention of claim 1 is directed to a piston processing method used in a piston-type compressor that forms the seating surface using a cutting blade on a processing wall surface of a receiving wall of the piston, which is a place for forming a surface. Applying a cutting blade that brings a cutting spherical surface having the same shape as the spherical surface of the seating surface by rotation to the workpiece wall surface of the receiving wall, while rotating the cutting blade around a rotation axis that intersects the seating surface, The cutting blade There the nest so as to be directed relative to the interior of the wall, move and forming the bearing surface of one of said piston and said cutting tool relative to the other.

  When one of the cutting blade and the piston is moved with respect to the other so that the cutting blade is relatively directed to the inside of the receiving wall, the cutting blade is placed on the receiving wall while the piston is stationary. When moved toward the inside, when the piston is moved so that the cutting blade is relatively directed toward the interior of the receiving wall with the cutting blade stationary, the cutting blade is placed inside the receiving wall. This includes any case where both the piston and the cutting blade move together so as to face. When one of the cutting blade and the piston is moved with respect to the other while rotating the cutting blade, a spherical seating surface having a rotation axis as a radial line is formed. The higher the true circular accuracy of the arc of the cutting edge of the cutting blade, the higher the true spherical accuracy of the concave spherical bearing surface. The tool mark has a streak pattern that approximates a radial shape or a concentric shape, but the closer the radius line and the rotation axis that pass through the center of the spherical surface of the concave spherical seat surface and the deepest bottom part of the seat surface are to be parallel, The position of the center of the streak pattern that approximates a radial shape or a concentric shape is close to the radial line. Such a tool mark is used for the bearing surface or the convex spherical surface of the shoe even when the piston compressor is high speed and high load, or when there is little lubricating oil between the concave spherical seating surface and the shoe. It is advantageous for avoiding wear.

  In a preferred example, one of the cutting blade and the piston is moved with respect to the other in the direction of the rotation axis so that the cutting blade is relatively directed toward the inside of the receiving wall. The seating surface is formed.

  The closer the rotation axis and the central axis of the piston are to be parallel, the more the center position of the streak pattern that approximates the radial or concentric shape is the center of the concave spherical seating surface and the deepest bottom part of the seating surface. Close to the radius line that passes.

In a preferred example, the rotation axis is parallel to the central axis of the piston.
The position of the center of the streak pattern that approximates a radial shape or a concentric shape is closest to the radial line. Such a tool mark is used for the bearing surface or the convex spherical surface of the shoe even when the piston compressor is high speed and high load, or when there is little lubricating oil between the concave spherical seating surface and the shoe. Most advantageous for avoiding wear.

In a preferred example, the rotation axis coincides with the central axis of the piston.
The deepest bottom portion of the seating surface is located on the central axis of the piston. A seating surface that provides such a positional relationship is preferable for smoothly moving the piston.

The present invention has an excellent effect that it is possible to avoid generation of a tool mark that easily causes wear on the convex spherical surface portion of the shoe or the concave spherical bearing surface formed on the piston.

Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.
FIG. 4 shows the variable displacement piston compressor 10. The cylinder block 11, the front housing 12 connected to the front end of the cylinder block 11, and the rear housing 13 connected to the rear end of the cylinder block 11 constitute an entire housing of the variable displacement piston compressor 10. A rotating shaft 14 is rotatably supported by the front housing 12 and the cylinder block 11 that form the control pressure chamber 121. The rotating shaft 14 projecting outside from the control pressure chamber 121 obtains driving force from a vehicle engine (not shown), which is an external drive source, via a pulley (not shown) and a belt (not shown).

  A rotating support 15 is fixed to the rotating shaft 14, and a swash plate 16 as a cam body is supported on the rotating shaft 14 so as to be slidable and tiltable in the axial direction of the rotating shaft 14. The head of the guide pin 17 fixed to the swash plate 16 is slidably fitted into a guide hole 151 formed in the rotary support 15. The swash plate 16 can be tilted in the axial direction of the rotary shaft 14 by the linkage of the guide hole 151 and the guide pin 17 and can rotate integrally with the rotary shaft 14.

  When the diameter center portion of the swash plate 16 moves to the rotation support 15 side, the inclination angle of the swash plate 16 increases. The maximum inclination angle of the swash plate 16 is regulated by the contact between the rotary support 15 and the swash plate 16. The solid line position of the swash plate 16 in FIG. 4 indicates the maximum tilt angle position of the swash plate 16. When the diameter center portion of the swash plate 16 moves to the cylinder block 11 side, the inclination angle of the swash plate 16 decreases. The chain line position of the swash plate 16 in FIG. 4 indicates the minimum tilt angle position of the swash plate 16.

  Pistons 18 are accommodated in a plurality of cylinder bores 111 penetrating the cylinder block 11. The piston 18 includes a columnar head portion 19 that is fitted into the cylinder bore 111 and a shoe holding portion 20 that is continuous with the head portion 19. The shoe holding portion 20 includes a first receiving wall 21 that is continuous with the head 19, a second receiving wall 22 that faces the first receiving wall 21, a first receiving wall 21, and a second receiving wall 22. And a connecting portion 23 for connecting the two. The outer peripheral portion of the swash plate 16 enters between the first receiving wall 21 and the second receiving wall 22. A hemispherical shoe 24 </ b> A is interposed between the cam surface 161 of the swash plate 16 and the first receiving wall 21, and a hemisphere between the cam surface 162 of the swash plate 16 and the second receiving wall 22. A shaped shoe 24B is interposed.

  Concave surfaces 25 and 26 are formed on the opposing surfaces 211 and 221 of the first receiving wall 21 and the second receiving wall 22. The convex spherical surface portion 241 of the shoe spherical shape of the shoe 24A is slidably fitted to the seat surface 25, and the flat portion 242 of the planar shape of the shoe 24A is in surface contact with the cam surface 161 of the swash plate 16. Yes. The convex spherical surface portion 241 of the shoe spherical surface of the shoe 24B is slidably fitted to the seating surface 26, and the flat surface portion 242 of the shoe 24B is in surface contact with the cam surface 162 of the swash plate 16. Yes. The center of the spherical surface of the concave spherical seating surface 25 and the center of the spherical surface of the concave spherical seating surface 26 are matched. The spherical center Eo of the seating surfaces 25 and 26 is illustrated in FIGS. 4 and 1A.

The rotational movement of the swash plate 16 is converted into the back-and-forth reciprocating movement of the piston 18 via the shoes 24A and 24B, and the piston 18 reciprocates in the cylinder bore 111.
A suction chamber 30 and a discharge chamber 31 are defined in the rear housing 13. The gaseous refrigerant in the suction chamber 30 is sucked into the compression chamber 112 by pushing the suction valve 33 away from the suction port 32 by the backward movement of the piston 18 (movement from the right side to the left side in FIG. 4). The gaseous refrigerant sucked into the compression chamber 112 is discharged into the discharge chamber 31 by pushing the discharge valve 35 away from the discharge port 34 by the forward movement of the piston 18 (movement from the left side to the right side in FIG. 4). The suction chamber 30 and the discharge chamber 31 are connected by an external refrigerant circuit 36. A heat exchanger 37 for removing heat from the refrigerant, an expansion valve 38, and a heat exchanger 39 for transferring ambient heat to the refrigerant are interposed on the external refrigerant circuit 36. The refrigerant in the discharge chamber 31 flows into the suction chamber 30 via the heat exchanger 37, the expansion valve 38 and the heat exchanger 39.

  The discharge chamber 31 and the control pressure chamber 121 are connected by a supply passage 27. The control pressure chamber 121 and the suction chamber 30 are connected by a discharge passage 28. The refrigerant in the control pressure chamber 121 flows out to the suction chamber 30 through the discharge passage 28.

  The electromagnetic capacity control valve 29 interposed on the supply passage 27 changes in a direction in which the valve opening decreases as the current value increases in the excited state. The refrigerant in the control pressure chamber 121 flows out to the suction chamber 30 through the discharge passage 28, and this refrigerant outflow works so as to lower the pressure in the control pressure chamber 121. Therefore, the inclination angle of the swash plate 16 increases in accordance with the current value, and the discharge capacity increases. The capacity control valve 29 has a maximum valve opening by demagnetization. Accordingly, the inclination angle of the swash plate 16 is minimized and the discharge capacity is minimized.

  FIG. 1A shows a processing apparatus 40 for forming the seating surfaces 25 and 26. Hereinafter, the configuration of the processing apparatus 40 will be described. The base 42 constituting the processing device 40 is reciprocated linearly by a reciprocating drive device 41. A column 43 is erected on the table 42, and an electric motor 44 is supported on the table 42. The axial direction of the output shaft 441 of the electric motor 44 is matched with the reciprocating direction of the table 42.

  The output shaft 441 of the electric motor 44 projects from the front side of the support 43 (left side in FIG. 1A) to the back side of the support 43 (right side in FIG. 1A). The output shaft 441 is rotatably supported on the support post 43 via a radial bearing 46, and a drive pulley 45 is fixed to a protruding end portion of the output shaft 441 protruding from the back surface of the support post 43.

  As shown in FIGS. 1B and 2B, a cutting blade 47 is rotatably supported on the upper end portion of the support column 43 via a radial bearing 48. A shaft 471 of the cutting blade 47 is rotatably supported by the support column 43 via a radial bearing 48 in a state parallel to the output shaft 441. A driven pulley 49 is fixed to the projecting end portion of the shaft 471 projecting from the back surface of the column 43. As shown in FIG. 2B, a timing belt 50 is hung on the driven pulley 49 and the driving pulley 45. The rotation of the output shaft 441 is transmitted to the cutting blade 47 through the driving pulley 45, the timing belt 50, and the driven pulley 49. As a result, the cutting blade 47 rotates about the central axis L1 of the shaft 471.

  The cutting blade 47 is rotated to provide a cutting spherical surface having the same shape as the spherical surfaces of the seating surfaces 25 and 26 (a cutting spherical surface having the same radius as that of the spherical surfaces of the seating surfaces 25 and 26). The cutting blade 47 is illustrated by the rotation locus of the cutting edge when it is rotating. The cutting edge of the cutting blade 47 is on the front side of the support post 43, and when the cutting blade 47 rotates, the cutting blade 47 draws a spherical locus having a spherical center on the central axis L1 of the shaft 471. The distance (radius) between the spherical locus and the center of the spherical surface is equal to the spherical radius of the virtual spherical surface E (shown in FIGS. 1A and 2C) that coincides with the concave spherical bearing surfaces 25 and 26. .

The reciprocating drive device 41 and the electric motor 44 are controlled by the control computer C. A method for forming the seating surfaces 25 and 26 will be described below.
As shown in FIGS. 1 (a) and 2 (c), the piston 18 is fixed. A cutting blade 47 is disposed between the first receiving wall 21 and the second receiving wall 22 so as to face the second receiving wall 22, and the center axis L 1 of the shaft 471 and the center axis L 2 of the piston 18 are arranged. Are matched. The center axis L2 of the piston 18 is the center axis of the columnar head 19 (the center of the cylindrical circumferential surface of the head 19).

  Next, the electric motor 44 is operated to rotate the cutting blade 47, and the table 42 is moved forward (moved from the right side to the left side in FIG. 1A) while the cutting blade 47 is rotating. Accordingly, the cutting edge of the cutting blade 47 moves in the direction of the central axis L1 of the shaft 471 (the direction of the central axis L2 of the piston 18) and toward the inside of the second receiving wall 22. When the cutting edge of the cutting blade 47 enters the second receiving wall 22, the facing surface 221 of the second receiving wall 22 is cut into a concave spherical shape. If the cutting blade 47 is moved until the arc center of the arc-shaped cutting edge of the cutting blade 47 coincides with the spherical center Eo of the virtual spherical surface E, a desired seating surface 26 is obtained.

  FIG. 1B shows a state in which a desired seating surface 26 is formed on the opposing surface 221 of the second receiving wall 22. The central axis L2 of the piston 18 passes through the spherical surface center Eo of the concave spherical seat surface 26 and the deepest bottom portion 261 of the seat surface 26.

  After the desired seating surface 26 is formed, the table 42 is moved backward (moved from the left side to the right side in FIG. 1A). As a result, the cutting edge of the cutting blade 47 moves in the direction of the central axis L1 of the shaft 471 (the direction of the central axis L2 of the piston 18) and away from the second receiving wall 22. After the cutting blade 47 returns to the position shown in FIG. 1A, the cutting blade 47 is removed from between the first receiving wall 21 and the second receiving wall 22, and the machining device 40 or the piston 18 is moved to the position shown in FIG. The arrangement direction is changed from the arrangement direction of a) and (b) to the arrangement direction reversed left and right, and the formation of the seat surface 25 is performed in the same manner as the formation of the seat surface 26.

  The reciprocating drive device 41, the base 42, and the support column 43 constitute a parallel moving unit that translates the cutting blade 47 toward the inside of the receiving walls 21 and 22. The facing surface 211 of the first receiving wall 21 is a processing wall surface where the seating surface 25 is formed, and the facing surface 221 of the second receiving wall 22 is a processing surface where the seating surface 26 is formed. It is a wall surface. The central axis L2 of the piston 18 that coincides with the central axis L1 of the shaft 471 of the cutting blade 47 is a rotational axis that intersects the seating surfaces 25 and 26. The cutting blade 47 is rotated about the rotation axis (center axis L2) as the rotation center. When the seating surface 25 is formed, the cutting blade 47 moves in the direction of the rotation axis (center axis L2) and toward the inside of the first receiving wall 21 while matching the center axis L1 of the shaft 471 with the center axis L2. Is done. Further, when the seat surface 26 is formed, the cutting blade 47 is directed in the direction of the rotation axis (center axis L2) and toward the inside of the second receiving wall 22 with the center axis L1 of the shaft 471 aligned with the center axis L2. Moved.

In the first embodiment, the following effects can be obtained.
(1) When the cutting blade 47 is rotated and moved in the direction of the rotation axis (center axis L2), spherical seating surfaces 25 and 26 having the rotation axis (center axis L2) as a radial line are formed. When a tool mark is generated on the bearing surfaces 25 and 26 formed by cutting with the cutting blade 47, the tool mark approximates a radial shape illustrated in FIG. 3A or a concentric circular shape illustrated in FIG. 3B. It becomes a streak pattern. The center of rotation of the cutting blade 47 is the center axis L1 of the shaft 471, and the center axis L1 coincides with the center axis L2 of the piston 18. That is, the rotation axis (center axis L2) passes through the spherical center Eo of the concave spherical seating surfaces 25 and 26 and the deepest bottom portions 251 and 261 of the seating surfaces 25 and 26. Therefore, the position of the center of the streak pattern that approximates the radial shape or the concentric shape substantially coincides with the central axis L <b> 2 of the piston 18.

  The shoes 24A and 24B rotate on the seating surfaces 25 and 26 due to the influence of the peripheral speed difference of the rotating swash plate 16, or swing when the inclination direction of the rotating swash plate 16 changes. That is, the convex spherical surface portions 241 of the shoes 24A and 24B that move in this manner are in sliding contact with tool marks as exemplified in FIGS. 3 (a) and 3 (b). However, tool marks (tool marks as illustrated in FIGS. 3A and 3B) generated on the seating surfaces 25 and 26 formed by cutting with the cutting blade 47 are streak patterns that do not deviate in a specific direction. is there. Therefore, the tool marks illustrated in FIGS. 3 (a) and 3 (b) are used when the variable displacement piston compressor 10 is at a high speed and a high load, or when the concave spherical seating surfaces 25 and 26 and the shoe 24A, Even when the amount of lubricating oil is small with respect to 24B, it is advantageous for avoiding wear of the seating surfaces 25, 26 or the convex spherical surface portion 241 of the shoes 24A, 24B.

  (2) The higher the perfect circle accuracy of the arc of the cutting edge of the cutting blade 47, the higher the true spherical accuracy of the concave spherical seating surfaces 25, 26. That is, by improving the accuracy of the circular arc of the cutting edge of the cutting blade 47, the accuracy of the spherical shape of the concave spherical seating surfaces 25, 26 can be increased.

  (3) The deepest bottom portions 251 and 261 of the seat surfaces 25 and 26 are located on the central axis L <b> 2 of the piston 18. The seating surfaces 25 and 26 that provide such a positional relationship are preferable for smoothly reciprocating the piston 18 in the cylinder bore 111.

  (4) The configuration in which the cutting blade 47 is rotationally driven by using the timing belt 50 makes it possible to keep the drive source (electric motor 44) of the cutting blade 47 and the cutting blade 47 away. By moving the drive source (electric motor 44) away from the cutting blade 47, it becomes easy to place the cutting blade 47 in a limited space between the first receiving wall 21 and the second receiving wall 22.

In the present invention, the following embodiments are also possible.
As shown in FIGS. 5A and 5B, the impeller 51 having the blades 511 is fixed to the cutting blade 47, and oil is supplied to the supply passage 53 in the support column 43 by the pump 52 to impeller 51. You may make it rotate. The impeller 51 and the cutting blade 47 rotate integrally. The pump 52 sucks oil from the oil tank 54 and supplies it to the supply passage 53. The oil used to rotate the impeller 51 is collected in the oil tank 54 via the discharge passage 55. The support 43 is moved by the same drive mechanism as in the first embodiment.

  Also in this embodiment, the same effect as the first embodiment can be obtained. Further, since the supply passage 53 and the discharge passage 55 are built in the column 43, the space occupied by the cutting blade 47 and the members in the vicinity thereof is further reduced as compared with the case of the first embodiment. Therefore, it becomes easier to arrange the cutting blade 47 in a limited space between the first receiving wall 21 and the second receiving wall 22 than in the first embodiment.

  In the first embodiment, the center axis L1 of the shaft 471 and the center axis L2 of the piston 18 are made to coincide with each other, but the center axis L1 and the center axis L2 are spaced apart from each other in parallel to center the cutting blade 47. You may make it translate in the direction of the axis line L1. That is, the deepest bottom portions 251 and 261 of the seating surfaces 25 and 26 may not be on the central axis L <b> 2 of the piston 18.

  As shown in FIG. 6, the central axis L1 of the shaft 471 may be inclined with respect to the central axis L2 of the piston 18. That is, it is only necessary that the central axis L1 of the shaft 471 intersects the seating surfaces 25 and 26, and the angle θ formed by the central axis L1 and the central axis L2 may be in the range of 0 ° to 25 °, for example. In this case, the moving direction of the cutting blade 47 when cutting the receiving walls 21 and 22 may be the direction of the central axis L1 or the direction of the central axis L2.

  In the first embodiment, the cutting blade 47 is moved without moving the piston 18 (with the piston 18 fixed), but the piston 18 is not moved (with the cutting blade 47 fixed) without moving the piston 18. The seating surfaces 25 and 26 may be formed by cutting.

The present invention may be applied to a piston used for a fixed capacity type piston compressor.
The present invention may be applied to a double-headed piston having a pair of heads at the front and rear.
The technical idea that can be grasped from the embodiment described above will be described below.

  [1] The seating surface according to any one of claims 1 to 4, wherein the seating surface is formed by using a parallel moving means that fixes the piston and translates the cutting blade toward the inside of the receiving wall. The processing method of the piston used for the piston type compressor of description.

  [2] The seat according to any one of [1] to [4] and [1], wherein the seat surface is formed by a belt-conduction cutting device that transmits the rotation of the electric motor to the cutting blade via a timing belt. Processing method of piston used in the piston type compressor.

It is easy to arrange the cutting blade 47 in a limited space between the first receiving wall 21 and the second receiving wall 22.
[3] The seat according to any one of claims 1 to 4, and [1], wherein the seating surface is formed by a hydraulic cutting device that rotates an impeller by supplying oil to rotate a cutting blade. Processing method of piston used in the piston type compressor.

  It is easy to arrange the cutting blade 47 in a limited space between the first receiving wall 21 and the second receiving wall 22.

A 1st embodiment is shown and (a) is a side view. (B) is a fragmentary sectional side view. (A) is a front view of a processing apparatus. (B) is a rear view of a processing apparatus. (C) is a partial plan view. (A), (b) is a perspective view which shows the example of a tool mark. The whole sectional view of a variable capacity type piston type compressor. Another embodiment is shown, (a) is a sectional side view. (B) is a back sectional view. The fragmentary sectional side view which shows another embodiment.

Explanation of symbols

  10: Variable displacement piston compressor. 16 ... A swash plate as a cam body. 161, 162: Cam surface. 18 ... Piston. 21: First receiving wall. 22: Second receiving wall. 211, 221 ... Opposing surfaces as work walls. 24A, 24B ... Shoe. 241 ... convex spherical surface portion. 25, 26 ... Seat surface. 251,261 ... bottom part. 47: Cutting blade. L1 is a central axis serving as a rotation axis. L2 is the central axis of the piston.

Claims (4)

The convex spherical portions of a pair of shoes having convex spherical surface portions are fitted to a pair of concave spherical surface seats formed on a piston, and the shoe is connected to the cam surface of the cam body and the cam surface. A piston used in a piston-type compressor that is interposed between a piston and compresses gas when the cam body rotates and the piston reciprocates, forming the concave spherical seating surface In the processing method of the piston used for the piston type compressor that forms the seating surface by using a cutting blade on the processing wall surface of the receiving wall of the piston that is a place to perform,
Applying a cutting blade that brings a cutting spherical surface having the same shape as the spherical surface of the seating surface by rotation to the workpiece wall surface of the receiving wall, while rotating the cutting blade around a rotation axis that intersects the seating surface, A piston used in a piston-type compressor that moves one of the cutting blade and the piston with respect to the other to form the seat surface so that the cutting blade is relatively directed to the inside of the receiving wall. Processing method.   The seating surface is formed by moving one of the cutting blade and the piston with respect to the other so that the cutting blade is directed relatively to the inside of the receiving wall in the direction of the rotation axis. The processing method of the piston used for the piston type compressor of Claim 1.   The method for processing a piston for use in a piston compressor according to claim 2, wherein the rotation axis is parallel to a central axis of the piston.   The method for processing a piston used in a piston compressor according to claim 3, wherein the rotation axis coincides with a central axis of the piston.

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