CN114341493B - Piston compressor - Google Patents

Abstract

A piston compressor is provided with a movable body that is movable relative to a drive shaft in the axial direction of the drive shaft based on a control pressure. The moving body has a 1 st moving body portion and a 2 nd moving body portion. The 1 st moving body moves in the axial direction in the axial passage based on the control pressure. The 2 nd moving body is disposed on the guide window in a state of being engaged with the 1 st moving body and has a curved plate shape extending along an inner peripheral surface of the shaft hole. The 1 st moving body has an engaging portion exposed from the guide window. The 2 nd moving body part is provided with an engaged part engaged with the engaging part. The engaged portion is a plate-like portion protruding from an inner peripheral edge of the 2 nd communication path in the 2 nd moving body portion and bent toward an inside of the guide window.

Description

Piston compressor

Technical Field

The present disclosure relates to piston compressors.

Background

The housing of the piston compressor has a cylinder. The cylinder block has a plurality of cylinder bores formed therein. The housing is formed with a suction chamber, a discharge chamber, a swash plate chamber, and a shaft hole. In the piston compressor, for example, a refrigerant from the outside of the piston compressor may be sucked into the swash plate chamber. As described above, a piston compressor in which a swash plate chamber is used as a suction chamber has been conventionally known.

The drive shaft is rotatably supported in the shaft hole. In addition, the piston compressor is provided with a fixed swash plate. The fixed swash plate can be rotated in the swash plate chamber by rotation of the drive shaft. The fixed swash plate has a certain inclination angle with respect to a plane perpendicular to the drive shaft. In addition, the piston compressor includes a piston coupled to a fixed swash plate. The piston forms a compression chamber within the cylinder bore. The piston compressor further includes a discharge valve for discharging the refrigerant in the compression chamber to the discharge chamber.

Further, by fixing the swash plate rotation in accordance with the rotation of the drive shaft, each piston reciprocates between the top dead center and the bottom dead center in the corresponding cylinder bore. Here, the piston moves from the top dead center to the bottom dead center, and the compression chamber becomes a suction stroke. On the other hand, the piston moves from the bottom dead center to the top dead center, and the compression chamber is a compression stroke for compressing the sucked refrigerant. The compression chamber is a discharge stroke for discharging the refrigerant compressed in the compression chamber to the discharge chamber through the discharge valve.

Among such piston compressors, a piston compressor in which a moving body is provided on a drive shaft is disclosed in patent document 1, for example. The movable body rotates integrally with the drive shaft, and is movable relative to the drive shaft in the axial direction of the drive shaft based on a control pressure controlled by the control valve. In the cylinder block of the piston compressor of patent document 1, a plurality of 1 st communication passages are formed to communicate with a plurality of cylinder bores, respectively. Further, the moving body is formed with a 2 nd communication path intermittently communicating with the 1 st communication path in accordance with the rotation of the drive shaft.

When the piston moves from the top dead center to the bottom dead center and the compression chamber has a suction stroke, the 1 st communication path and the 2 nd communication path communicate with each other, and the refrigerant is sucked into the compression chamber. Here, the communication angle around the axis of the 1 st communication path and the 2 nd communication path, which are communicated with each other, can be changed for every 1 rotation of the drive shaft according to the position of the movable body in the axial direction of the drive shaft. This can change the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber.

Prior art literature

Patent literature

Patent document 1: japanese patent laid-open No. 5-306680

Disclosure of Invention

Problems to be solved by the invention

In a piston compressor as disclosed in patent document 1, a compression load, which is a load generated by a high-pressure refrigerant compressed in a compression chamber, acts on a moving body through a 1 st communication path communicating with the compression chamber in a compression stroke or a discharge stroke. Then, the movable body is pressed in the shaft hole in a direction intersecting the axial direction of the drive shaft, and the movable body is pressed against the inner peripheral surface of the shaft hole, so that the friction force between the movable body and the inner peripheral surface of the shaft hole when the movable body moves in the axial direction of the drive shaft increases. As a result, the movable body is less likely to move in the axial direction of the drive shaft, and the controllability may be degraded.

The purpose of the present disclosure is to provide a piston compressor that can exhibit high controllability and achieve miniaturization.

Means for solving the problems

The piston compressor for achieving the above object comprises: a housing having a cylinder block formed with a plurality of cylinder bores, and formed with a suction chamber, a discharge chamber, a swash plate chamber, and a shaft hole; a drive shaft rotatably supported in the shaft hole; a fixed swash plate rotatable in the swash plate chamber by rotation of the drive shaft, the fixed swash plate having a certain inclination angle with respect to a plane perpendicular to the drive shaft; a piston that forms a compression chamber in each cylinder bore and is connected to the fixed swash plate; a discharge valve for discharging the refrigerant in the compression chamber to the discharge chamber; a moving body provided on the drive shaft, integrally rotatable with the drive shaft, and movable relative to the drive shaft in an axial direction of the drive shaft based on a control pressure; and a control valve configured to control the control pressure. A1 st communication passage is formed in the cylinder block to communicate with the cylinder bore. A2 nd communication path intermittently communicating with the 1 st communication path is formed in the movable body in accordance with the rotation of the drive shaft. The piston compressor is configured to vary a flow rate of the refrigerant discharged from the compression chamber to the discharge chamber according to a position of the movable body in the axial direction. The drive shaft has: an axial passage extending in an axial direction of the drive shaft in the drive shaft and communicating with the suction chamber; and a guide window that communicates with the axial passage and that opens on an outer peripheral surface of a portion of the drive shaft that is located in the shaft hole, and that guides the movable body in the axial direction. The 1 st communication path and the 2 nd communication path are communicated with each other by the moving body. The 1 st communication path and the 2 nd communication path are not communicated with each other by the drive shaft. The moving body has: a 1 st moving body that is located in the axial passage and moves in the axial direction in the axial passage based on the control pressure; and a 2 nd movable body portion disposed on the guide window in a state of being engaged with the 1 st movable body portion and having a curved plate shape extending along an inner peripheral surface of the shaft hole, and formed in a state of being penetrated by the 2 nd communication path. The 1 st moving body portion has an engaging portion exposed from the guide window. The 2 nd moving body part is provided with an engaged part engaged with the engaging part. The engaged portion is plate-shaped protruding from an inner peripheral edge of the 2 nd communication path in the 2 nd moving body portion and bent toward an inside of the guide window.

Drawings

Fig. 1 is a side sectional view showing a piston compressor in an embodiment.

Fig. 2 is a side sectional view showing a state where the flow rate of the refrigerant gas discharged into the 1 st discharge chamber and the 2 nd discharge chamber is maximum.

Fig. 3 is a cross-sectional view taken along line 3-3 of fig. 1.

Fig. 4 is a cross-sectional view taken along line 4-4 of fig. 1.

Fig. 5 is a cross-sectional view taken along line 5-5 of fig. 2.

Fig. 6 is an exploded view showing the drive shaft, the movable body, and the suction valve member.

Fig. 7 is a side cross-sectional view of the drive shaft.

Fig. 8 is a cross-sectional view taken along line 8-8 of fig. 7.

Fig. 9 is an enlarged cross-sectional view of the periphery of the 2 nd moving body portion when the flow rate of the refrigerant gas discharged into the 2 nd discharge chamber is minimized.

Fig. 10 is a cross-sectional view showing an enlarged view of the periphery of the 2 nd moving body portion when the flow rate of the refrigerant gas discharged into the 2 nd discharge chamber is maximized.

Fig. 11 is an enlarged cross-sectional view of the periphery of the suction valve body when the flow rate of the refrigerant gas discharged into the 1 st discharge chamber is minimized.

Fig. 12 is an enlarged cross-sectional view of the periphery of the suction valve body when the flow rate of the refrigerant gas discharged into the 1 st discharge chamber is maximized.

Fig. 13 is an enlarged cross-sectional view showing a state in which the 1 st moving body and the 2 nd moving body are assembled.

Fig. 14 is a perspective view showing the 1 st moving body, the 2 nd moving body, and a part of the drive shaft.

Fig. 15 is a perspective view of the 2 nd moving body.

Fig. 16 is a perspective view showing a 2 nd moving body in another embodiment.

Detailed Description

An embodiment of the piston compressor will be described below with reference to fig. 1 to 15. The piston compressor of the present embodiment is mounted on a vehicle, for example. Also, a piston compressor is used for a vehicle air conditioner and compresses a refrigerant.

As shown in fig. 1 and 2, the piston compressor 10 includes a substantially cylindrical casing 11. The housing 11 includes a 1 st cylinder 12 and a 2 nd cylinder 13 connected to each other, a front housing 14 connected to the 1 st cylinder 12, and a rear housing 15 connected to the 2 nd cylinder 13. The 1 st cylinder 12, the 2 nd cylinder 13, the front case 14, and the rear case 15 are, for example, substantially cylindrical in shape made of a metal material formed of aluminum. The axial center of the 1 st cylinder 12, the axial center of the 2 nd cylinder 13, the axial center of the front case 14, and the axial center of the rear case 15 are respectively identical.

A 1 st valve port forming plate 16 of a substantially disc shape is interposed between the front case 14 and the 1 st cylinder 12. Thus, the front case 14 is coupled to the 1 st cylinder 12 via the 1 st valve port forming plate 16. Further, a 2 nd valve port forming plate 17 of a substantially circular plate shape is interposed between the rear case 15 and the 2 nd cylinder 13. Thus, the rear case 15 is coupled to the 2 nd cylinder 13 via the 2 nd valve port forming plate 17.

A 1 st cylinder concave portion 18 is formed in an end surface of the 1 st cylinder 12 opposite to the 2 nd cylinder 13. The 1 st cylinder concave portion 18 is circular-hole-shaped. The axial center of the 1 st cylinder concave portion 18 coincides with the axial center of the 1 st cylinder body 12. Further, a 1 st shaft hole 19 having a circular hole shape is formed in the center of the 1 st cylinder 12. The axial center of the 1 st axial hole 19 coincides with the axial center of the 1 st cylinder 12. The 1 st shaft hole 19 penetrates the 1 st cylinder 12 in the axial direction. One end of the 1 st shaft hole 19 opens at the bottom surface of the 1 st cylinder recess 18, and the other end of the 1 st shaft hole 19 opens at an end surface of the 1 st cylinder block 12 opposite to the 1 st valve port forming plate 16.

As shown in fig. 3, the 1 st cylinder block 12 has 1 st cylinder bores 20a, 20b, 20c, 20d, and 20e formed therein. The 1 st cylinder bores 20a, 20b, 20c, 20d, 20e are circular holes. The 1 st cylinder bores 20a, 20b, 20c, 20d, 20e have the same inner diameters. The 1 st cylinder bores 20a, 20b, 20c, 20d, 20e are disposed around the 1 st cylinder bore 19 at equal intervals in the circumferential direction of the 1 st cylinder block 12.

As shown in fig. 1 and 2, the 1 st cylinder bores 20a, 20b, 20c, 20d, and 20e penetrate the 1 st cylinder block 12 in the axial direction. One end of each 1 st cylinder hole 20a, 20b, 20c, 20d, 20e opens at the bottom surface of the 1 st cylinder recess 18, and the other end of each 1 st cylinder hole 20a, 20b, 20c, 20d, 20e opens at the end surface of the 1 st cylinder block 12 opposite to the 1 st valve port forming plate 16.

As shown in fig. 3, front side communication passages 21a, 21b, 21c, 21d, 21e are formed in the 1 st cylinder 12. Each front side communication passage 21a, 21b, 21c, 21d, 21e extends in the radial direction of the 1 st cylinder block 12 from the 1 st shaft hole 19 toward the corresponding 1 st cylinder hole 20a, 20b, 20c, 20d, 20 e. One end of each front communication passage 21a, 21b, 21c, 21d, 21e communicates with the 1 st shaft hole 19. The other ends of the front side communication passages 21a, 21b, 21c, 21d, 21e communicate with the corresponding 1 st cylinder bores 20a, 20b, 20c, 20d, 20 e.

As shown in fig. 1 and 2, the 1 st cylinder 12 has a suction port 22, a 1 st discharge passage 23, and a discharge port 24. The suction port 22 communicates with the 1 st cylinder recess 18. The suction port 22 extends in the radial direction of the 1 st cylinder 12 and opens to the outside of the 1 st cylinder 12. The suction port 22 is connected to an external refrigerant circuit, not shown. Specifically, the suction port 22 is connected to an evaporator constituting an external refrigerant circuit via a pipe not shown.

The 1 st discharge passage 23 penetrates the 1 st cylinder 12 in the axial direction on the radial outside of the 1 st cylinder 12 with respect to the 1 st cylinder recess 18. One end of the 1 st discharge passage 23 opens at an end face of the 1 st cylinder 12 corresponding to the 2 nd cylinder 13, and the other end of the 1 st discharge passage 23 opens at an end face of the 1 st cylinder 12 opposite to the 1 st valve port forming plate 16.

The discharge port 24 communicates with the 1 st discharge passage 23. The discharge port 24 extends in the radial direction of the 1 st cylinder 12 and opens to the outside of the 1 st cylinder 12. The discharge port 24 is connected to an external refrigerant circuit. Specifically, the discharge port 24 is connected to a condenser that constitutes an external refrigerant circuit via a pipe not shown.

A 2 nd cylinder concave portion 25 is formed in an end surface of the 2 nd cylinder 13 opposite to the 1 st cylinder 12. The 2 nd cylinder concave portion 25 is circular-hole-shaped. The axial center of the 2 nd cylinder concave portion 25 coincides with the axial center of the 2 nd cylinder body 13. Further, a cylindrical cylinder boss 26 is provided in a protruding manner on an end surface of the 2 nd cylinder block 13 facing the 2 nd valve port forming plate 17. The axis of the cylinder boss 26 coincides with the axis of the 2 nd cylinder 13.

A circular hole-shaped 2 nd shaft hole 27 is formed in the center of the 2 nd cylinder block 13. The axial center of the 2 nd axial hole 27 coincides with the axial center of the 2 nd cylinder 13. The 2 nd shaft hole 27 penetrates the 2 nd cylinder 13 in the axial direction. One end of the 2 nd shaft hole 27 opens at the bottom surface of the 2 nd cylinder concave portion 25, and the other end of the 2 nd shaft hole 27 opens at the tip end surface of the cylinder convex portion 26 through the inside of the cylinder convex portion 26. Thereby, a part of the 2 nd shaft hole 27 is formed inside the cylinder boss 26. The inner diameter of the 2 nd shaft hole 27 is the same as the inner diameter of the 1 st shaft hole 19.

As shown in fig. 4 and 5, the 2 nd cylinder block 13 has 2 nd cylinder bores 28a, 28b, 28c, 28d, 28e as cylinder bores. Therefore, the 2 nd cylinder 13 is a cylinder in which a plurality of cylinder bores are formed. The 2 nd cylinder bores 28a, 28b, 28c, 28d, 28e are circular holes. The inner diameters of the 2 nd cylinder bores 28a, 28b, 28c, 28d, 28e are the same, respectively. The inner diameters of the 2 nd cylinder bores 28a, 28b, 28c, 28d, 28e are the same as the inner diameters of the 1 st cylinder bores 20a, 20b, 20c, 20d, 20 e. The 2 nd cylinder bores 28a, 28b, 28c, 28d, 28e are disposed around the 2 nd cylinder bore 27 at equal intervals in the circumferential direction of the 2 nd cylinder block 13.

As shown in fig. 1 and 2, the 2 nd cylinder bores 28a, 28b, 28c, 28d, 28e penetrate the 2 nd cylinder block 13 in the axial direction. One end of each of the 2 nd cylinder bores 28a, 28b, 28c, 28d, 28e opens at the bottom surface of the 2 nd cylinder recess 25, and the other end of each of the 2 nd cylinder bores 28a, 28b, 28c, 28d, 28e opens at the end surface of the 2 nd cylinder block 13 opposite to the 2 nd valve port forming plate 17.

As shown in fig. 4 and 5, the 2 nd cylinder 13 is formed with rear side communication passages 29a, 29b, 29c, 29d, and 29e. The rear side communication passages 29a, 29b, 29c, 29d, 29e extend from the 2 nd shaft hole 27 toward the 2 nd cylinder holes 28a, 28b, 28c, 28d, 28e in the radial direction of the 2 nd cylinder block 13. One end of each of the rear communication passages 29a, 29b, 29c, 29d, 29e communicates with the 2 nd shaft hole 27. The other end of each rear side communication passage 29a, 29b, 29c, 29d, 29e communicates with the corresponding 2 nd cylinder hole 28a, 28b, 28c, 28d, 28e. Accordingly, each of the rear side communication passages 29a, 29b, 29c, 29d, 29e is a 1 st communication passage formed in the 2 nd cylinder block 13 and communicating with the corresponding 2 nd cylinder hole 28a, 28b, 28c, 28d, 28e.

As shown in fig. 1 and 2, the 2 nd discharge passage 30 is formed in the 2 nd cylinder 13. The 2 nd discharge passage 30 penetrates the 2 nd cylinder 13 in the axial direction on the radial outside of the 2 nd cylinder 13 with respect to the 2 nd cylinder recess 25. One end of the 2 nd discharge passage 30 opens at an end face of the 2 nd cylinder 13 opposed to the 1 st cylinder 12, and the other end of the 2 nd discharge passage 30 opens at an end face of the 2 nd cylinder 13 opposed to the 2 nd valve port forming plate 17.

A gasket 31 is interposed between the 1 st cylinder 12 and the 2 nd cylinder 13. Gasket 31 seals between 1 st cylinder 12 and 2 nd cylinder 13. The 1 st gasket hole 31a is formed in the gasket 31 to communicate the 1 st cylinder recess 18 with the 2 nd cylinder recess 25. Further, a 2 nd gasket hole 31b is formed in the gasket 31 to communicate the 1 st discharge passage 23 with the 2 nd discharge passage 30.

The swash plate chamber 32 is defined between the 1 st cylinder block 12 and the 2 nd cylinder block 13 by the 1 st cylinder recess 18, the 1 st gasket hole 31a, and the 2 nd cylinder recess 25. Accordingly, the swash plate chamber 32 is formed in the housing 11. The low-pressure refrigerant gas having passed through the evaporator is sucked from the external refrigerant circuit into the swash plate chamber 32 through the suction port 22. Therefore, the swash plate chamber 32 is used as a suction chamber for sucking the refrigerant gas from the outside of the piston compressor 10.

The 1 st cylinder bores 20a, 20b, 20c, 20d, and 20e and the 2 nd cylinder bores 28a, 28b, 28c, 28d, and 28e, respectively, face each other with the swash plate chamber 32 interposed therebetween in a state where the axes thereof coincide with each other. The 1 st shaft hole 19 and the 2 nd shaft hole 27 are opposed to each other with the swash plate chamber 32 interposed therebetween in a state where the axes thereof coincide with each other.

A circular hole-shaped front shaft hole 33 is formed in the center of the front case 14. The axial center of the front shaft hole 33 coincides with the axial center of the front case 14. Further, a cylindrical front boss 34 is provided in the front case 14 so as to protrude from an end surface on the opposite side of the 1 st valve port forming plate 16. The axis of the front boss 34 coincides with the axis of the front housing 14. One end of the front shaft hole 33 is open at an end face of the front case 14 opposite to the 1 st valve port forming plate 16, and the other end of the front shaft hole 33 is open at a tip end face of the front boss 34 through an inner side of the front boss 34. Thereby, the inner side of the front boss 34 forms a part of the front shaft hole 33.

An annular front recess 35 extending around the axis of the front case 14 is formed in an end surface of the front case 14 opposite to the 1 st valve port forming plate 16. The front concave portion 35 extends annularly around the front shaft hole 33. The 1 st discharge chamber 36 is partitioned between the front case 14 and the 1 st valve port forming plate 16 by the front concave portion 35 and the 1 st valve port forming plate 16. Therefore, the 1 st ejection chamber 36 extends annularly around the axial center of the front shaft hole 33.

The 1 st valve port forming plate 16 has a 1 st valve plate 37, a 1 st discharge valve plate 38, and a 1 st holding plate 39. The 1 st valve plate 37, the 1 st discharge valve plate 38, and the 1 st holding plate 39 are substantially disk-shaped. The 1 st valve plate 37 has 1 st discharge holes 37a communicating with the 1 st cylinder holes 20a, 20b, 20c, 20d, and 20e, respectively. The 1 st cylinder bores 20a, 20b, 20c, 20d, and 20e communicate with the 1 st discharge chamber 36 via the corresponding 1 st discharge bores 37a.

Valve plate 1 37 is engaged with an end surface of cylinder 1 12 opposite to front case 14. The 1 st holding plate 39 is joined to an end surface of the front case 14 opposite to the 1 st cylinder 12. The 1 st discharge valve plate 38 is interposed between the 1 st valve plate 37 and the 1 st holding plate 39. The 1 st discharge valve plate 38 is provided with a plurality of 1 st discharge reed valves 38a capable of opening and closing the 1 st discharge holes 37a, respectively. The 1 st retainer plate 39 restricts the maximum opening of the 1 st discharge reed valve 38a based on elastic deformation.

Further, a 1 st plate through hole 16a having a circular hole shape is formed in the center portion of the 1 st valve port forming plate 16. The 1 st plate through hole 16a penetrates the 1 st valve plate 37, the 1 st discharge valve plate 38, and the 1 st holding plate 39. The inner diameter of the 1 st plate through hole 16a is larger than the inner diameter of the 1 st shaft hole 19. The axial center of the 1 st plate through hole 16a coincides with the axial center of the 1 st shaft hole 19. The 1 st plate through hole 16a communicates the 1 st shaft hole 19 with the front shaft hole 33.

Further, a 1 st plate communication hole 16b is formed in the 1 st valve port forming plate 16. The 1 st plate communication hole 16b is located radially outward of the 1 st valve port forming plate 16 from each 1 st ejection hole 37 a. The 1 st plate communication hole 16b penetrates the 1 st valve plate 37, the 1 st discharge valve plate 38, and the 1 st holding plate 39. The 1 st plate communication hole 16b communicates the 1 st ejection chamber 36 with the 1 st ejection passage 23. The 1 st discharge chamber 36 communicates with the discharge port 24 via the 1 st plate communication hole 16b and the 1 st discharge passage 23.

A circular hole-shaped chamber forming recess 40 is formed in the center of the rear case 15. The axis of the chamber forming recess 40 coincides with the axis of the rear case 15. The inner diameter of the chamber forming recess 40 is slightly larger than the outer diameter of the cylinder boss 26.

An annular rear recess 41 extending around the axial center of the rear housing 15 is formed in an end surface of the rear housing 15 facing the 2 nd valve port forming plate 17. The rear recess 41 extends annularly around the chamber forming recess 40. Then, the rear recess 41 and the 2 nd valve port forming plate 17 define a 2 nd discharge chamber 42 as a discharge chamber between the rear case 15 and the 2 nd valve port forming plate 17. Therefore, the 2 nd ejection chamber 42 extends annularly around the axis of the chamber forming recess 40.

The 2 nd valve port forming plate 17 has a 2 nd valve plate 43, a 2 nd discharge valve plate 44, and a 2 nd holding plate 45. The 2 nd valve plate 43, the 2 nd discharge valve plate 44, and the 2 nd holding plate 45 are substantially disc-shaped. The 2 nd valve plate 43 has 2 nd discharge holes 43a formed therein to communicate with the 2 nd cylinder holes 28a, 28b, 28c, 28d, 28e, respectively. The 2 nd cylinder bores 28a, 28b, 28c, 28d, 28e communicate with the 2 nd discharge chamber 42 via the corresponding 2 nd discharge bores 43a.

The 2 nd valve plate 43 is joined to an end surface of the 2 nd cylinder block 13 opposite to the rear housing 15. The 2 nd holding plate 45 is engaged with an end surface of the rear case 15 opposite to the 2 nd cylinder 13. The 2 nd discharge valve plate 44 is interposed between the 2 nd valve plate 43 and the 2 nd holding plate 45. The 2 nd discharge valve plate 44 is provided with a plurality of 2 nd discharge reed valves 44a capable of opening and closing the 2 nd discharge holes 43a, respectively. The 2 nd holding plate 45 restricts the maximum opening of the 2 nd discharge reed valve 44a based on elastic deformation.

Further, a circular hole-shaped 2 nd plate through hole 17a is formed in the center of the 2 nd valve port forming plate 17. The 2 nd plate through hole 17a penetrates the 2 nd valve plate 43, the 2 nd discharge valve plate 44, and the 2 nd holding plate 45. The inner diameter of the 2 nd plate through hole 17a is the same as the inner diameter of the chamber forming recess 40. The axis of the 2 nd plate through hole 17a coincides with the axis of the chamber forming recess 40. The 2 nd plate through hole 17a communicates with the chamber forming recess 40.

Further, in the 2 nd valve port forming plate 17, a 2 nd plate communication hole 17b is formed. The 2 nd plate communication hole 17b is located radially outward of the 2 nd valve port forming plate 17 from each 2 nd discharge hole 43 a. The 2 nd plate communication hole 17b penetrates the 2 nd valve plate 43, the 2 nd discharge valve plate 44, and the 2 nd holding plate 45. The 2 nd plate communication hole 17b communicates the 2 nd ejection chamber 42 with the 2 nd ejection passage 30.

The 1 st ejection chamber 36 and the 2 nd ejection chamber 42 communicate with each other via the 1 st plate communication hole 16b, the 1 st ejection passage 23, the 2 nd gasket hole 31b, the 2 nd ejection passage 30, and the 2 nd plate communication hole 17 b. The 2 nd discharge chamber 42 communicates with the discharge port 24 via the 2 nd plate communication hole 17b, the 2 nd discharge passage 30, the 2 nd gasket hole 31b, and the 1 st discharge passage 23.

The cylinder boss 26 is inserted into the chamber forming recess 40 through the 2 nd plate through hole 17 a. The control pressure chamber 46 is partitioned by the top end surface of the cylinder boss 26 and the chamber forming recess 40. Therefore, in the rear case 15, a control pressure chamber 46 is formed. The control pressure chamber 46 is formed in a central portion of the rear case 15. The 2 nd discharge chamber 42 extends annularly around the control pressure chamber 46.

The piston compressor 10 includes a drive shaft 47. The drive shaft 47 is housed in the housing 11 such that the axial direction of the drive shaft 47 coincides with the axial direction of the housing 11. The drive shaft 47 is made of, for example, steel, and has rigidity capable of withstanding the compression load of the high-pressure refrigerant gas. The drive shaft 47 is inserted into the 1 st shaft hole 19, the 2 nd shaft hole 27, and the front shaft hole 33, and is rotatably supported in the 1 st shaft hole 19 and the 2 nd shaft hole 27. Thereby, the drive shaft 47 is rotatably supported by the housing 11. Accordingly, the 1 st shaft hole 19 and the 2 nd shaft hole 27 constitute a shaft hole 48 formed in the housing 11 and supporting the drive shaft 47.

One end of the drive shaft 47 is located in the front shaft hole 33, and the other end of the drive shaft 47 protrudes from the tip end surface of the cylinder boss 26 and is located in the control pressure chamber 46. A shaft seal device 49 is provided between the inner peripheral surface of the front shaft hole 33 and the outer peripheral surface of the drive shaft 47. The shaft seal 49 seals between the inside of the housing 11 and the outside of the housing 11. A screw hole 47a that opens at one end surface of the drive shaft 47 is formed in the drive shaft 47. A pulley and an electromagnetic clutch, not shown, are coupled to the screw hole 47a. The drive shaft 47 is connected to an engine of the vehicle via a pulley and an electromagnetic clutch.

The piston compressor 10 includes a fixed swash plate 50. The fixed swash plate 50 is fixed to the drive shaft 47 by being press-fitted into the drive shaft 47. The fixed swash plate 50 is accommodated in the swash plate chamber 32. The fixed swash plate 50 can rotate integrally with the drive shaft 47 in the swash plate chamber 32 by rotation of the drive shaft 47. The fixed swash plate 50 has a certain inclination angle with respect to a plane perpendicular to the drive shaft 47. The fixed swash plate 50 is supported by the 1 st cylinder block 12 via a 1 st thrust bearing 51 a. The fixed swash plate 50 is supported by the 2 nd cylinder block 13 via a 2 nd thrust bearing 51 b.

The piston compressor 10 includes a plurality of pistons 52 coupled to a fixed swash plate 50. Each piston 52 has a 1 st head 52a, a 2 nd head 52b, and a connecting portion 52c. Therefore, the piston compressor 10 of the present embodiment is a double-headed piston compressor. The 1 st head 52a of each piston 52 is accommodated in the corresponding 1 st cylinder hole 20a, 20b, 20c, 20d, 20 e. As shown in fig. 3, the 1 st compression chambers 53a, 53b, 53c, 53d, and 53e are formed in the 1 st cylinder bores 20a, 20b, 20c, 20d, and 20e, respectively, by the 1 st head 52a and the 1 st valve port forming plate 16. The 1 st compression chambers 53a, 53b, 53c, 53d, 53e are respectively connected to the front communication passages 21a, 21b, 21c, 21d, 21e.

As shown in fig. 1 and 2, the 2 nd head 52b of each piston 52 is accommodated in the corresponding 2 nd cylinder hole 28a, 28b, 28c, 28d, 28 e. As shown in fig. 4 and 5, the 2 nd head 52b and the 2 nd valve port forming plate 17 form 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e as compression chambers in the 2 nd cylinder bores 28a, 28b, 28c, 28d, and 28e, respectively. Accordingly, each piston 52 forms a 2 nd compression chamber 54a, 54b, 54c, 54d, 54e within the corresponding 2 nd cylinder bore 28a, 28b, 28c, 28d, 28 e. The 2 nd compression chambers 54a, 54b, 54c, 54d, 54e are respectively connected to the rear communication passages 29a, 29b, 29c, 29d, 29e.

As shown in fig. 1 and 2, the connection portion 52c connects the 1 st head 52a and the 2 nd head 52 b. A pair of hemispherical shoe portions 55 are provided in the connecting portion 52 c. Each piston 52 is engaged with the outer peripheral portion of the fixed swash plate 50 via a pair of shoe portions 55. The pair of shoe portions 55 converts the rotation of the fixed swash plate 50 into the reciprocation of each piston 52. Thus, the 1 st head 52a of each piston 52 reciprocates between the top dead center and the bottom dead center of the 1 st head 52a in the corresponding 1 st cylinder bore 20a, 20b, 20c, 20d, 20 e. The 2 nd head 52b of each piston 52 reciprocates between top dead center and bottom dead center of the 2 nd head 52b within the corresponding 2 nd cylinder bores 28a, 28b, 28c, 28d, 28 e.

When the swash plate 50 is fixed to rotate in the swash plate chamber 32 in accordance with the rotation of the drive shaft 47, the 1 st head 52a of each piston 52 reciprocates between the top dead center and the bottom dead center in the corresponding 1 st cylinder bore 20a, 20b, 20c, 20d, 20 e. In addition, with the rotation of the drive shaft 47, the 2 nd head 52b of each piston 52 reciprocates between the top dead center and the bottom dead center in the corresponding 2 nd cylinder bores 28a, 28b, 28c, 28d, 28 e. Accordingly, the re-expansion stroke, the suction stroke, the compression stroke, and the discharge stroke are repeated in the 1 st compression chambers 53a, 53b, 53c, 53d, and 53e and the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54 e.

In the re-expansion step, the refrigerant gas in each of the 1 st compression chambers 53a, 53b, 53c, 53d, 53e and each of the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e is re-expanded. In the suction stroke, refrigerant gas is sucked into the 1 st compression chambers 53a, 53b, 53c, 53d, 53e and the 2 nd compression chambers 54a, 54b, 54c, 54d, 54 e. In the compression stroke, the refrigerant gas in each of the 1 st compression chambers 53a, 53b, 53c, 53d, 53e and each of the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e is compressed.

In the discharge stroke, the refrigerant gas compressed in each of the 1 st compression chambers 53a, 53b, 53c, 53d, and 53e is discharged into the 1 st discharge chamber 36 by elastic deformation of the corresponding 1 st discharge reed valve 38 a. In the discharge stroke, the refrigerant gas compressed in each of the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e is discharged into the 2 nd discharge chamber 42 by elastic deformation of the corresponding 2 nd discharge reed valve 44 a. Therefore, each of the 2 nd discharge reed valves 44a is a discharge valve that discharges the refrigerant in the corresponding 2 nd compression chambers 54a, 54b, 54c, 54d, 54e to the 2 nd discharge chamber 42. The refrigerant gas discharged into the 1 st discharge chamber 36 is discharged to the condenser of the external refrigerant circuit through the 1 st plate communication hole 16b, the 1 st discharge passage 23, and the discharge port 24. The refrigerant gas discharged into the 2 nd discharge chamber 42 is discharged to the condenser of the external refrigerant circuit through the 2 nd plate communication hole 17b, the 2 nd discharge passage 30, the 2 nd gasket hole 31b, the 1 st discharge passage 23, and the discharge port 24.

The fixed swash plate 50 has a cylindrical swash plate boss 50a fixed to the outer peripheral surface of the drive shaft 47. The fixed swash plate 50 is fixed to the outer peripheral surface of the drive shaft 47 by a swash plate boss 50a, and is attached to the drive shaft 47. The swash plate boss 50a has a swash plate suction hole 56 formed therein. The swash plate suction hole 56 extends in the radial direction of the drive shaft 47 and penetrates the swash plate boss 50a. Therefore, the swash plate suction hole 56 communicates with the swash plate chamber 32.

As shown in fig. 6 and 7, an axial passage 57, a 1 st radial passage 58, a 2 nd radial passage 59, and a guide window 60 are formed in the drive shaft 47. The axial passage 57 has a circular hole shape. The axial passage 57 extends in the axial direction of the drive shaft 47 inside the drive shaft 47. The axial passage 57 opens at an end surface of the drive shaft 47 on the opposite side of the end surface where the screw hole 47a opens, and extends toward the screw hole 47 a. The axial passage 57 has a large passage 61 and a small passage 62 having an inner diameter smaller than the large passage 61. The large path 61 is located on the opposite side of the small path 62 from the screw hole 47 a. The large path 61 is opened at an end surface of the drive shaft 47 opposite to an end surface where the screw hole 47a is opened. The inner peripheral surface of the large path 61 and the inner peripheral surface of the small path 62 are connected by an annular stepped surface 63 extending in the radial direction of the drive shaft 47.

The 1 st radial path 58 extends in the radial direction of the drive shaft 47. One end of the 1 st radial path 58 is open to the inner peripheral surface of the small path 62, and the other end of the 1 st radial path 58 is open to the outer peripheral surface of the drive shaft 47. As shown in fig. 1 and 2, the fixed swash plate 50 is attached to the drive shaft 47 so that the swash plate suction hole 56 communicates with the 1 st radial path 58. Thus, the small passage 62 of the axial passage 57 communicates with the swash plate chamber 32 via the 1 st radial passage 58 and the swash plate suction hole 56.

As shown in fig. 6 and 7, the 2 nd radial path 59 extends in the radial direction of the drive shaft 47. The 2 nd radial path 59 is located in the drive shaft 47 closer to the screw hole 47a than the 1 st radial path 58. One end of the 2 nd radial path 59 opens at the inner peripheral surface of the small path 62, and the other end of the 2 nd radial path 59 opens at the outer peripheral surface of the drive shaft 47. As shown in fig. 3, the 2 nd radial path 59 extends in the radial direction of the drive shaft 47 at a position close to the small path 62, extends in the radial direction of the drive shaft 47 at a position close to the outer peripheral surface of the drive shaft 47, and extends in the circumferential direction of the drive shaft 47.

As shown in fig. 6 and 7, the guide window 60 is formed by cutting away a part of the outer peripheral surface of the drive shaft 47. The guide window 60 communicates with the large passage 61 of the axial passage 57 and opens on the outer peripheral surface of the drive shaft 47. The guide window 60 extends in the axial direction of the drive shaft 47. On the other hand, the drive shaft 47 has a main body 64 as a portion located on the opposite side of the guide window 60 with the axial center L1 of the drive shaft 47 interposed therebetween.

As shown in fig. 8, the guide window 60 is formed smaller than half a circumference in the circumferential direction of the drive shaft 47. Specifically, in the guide window 60, the area extending in the circumferential direction of the drive shaft 47 is 90 ° or more and less than 180 °. The body 64 has a semicircular gutter shape extending in the axial direction of the drive shaft 47. The main body 64 is formed larger than half a circumference in the circumferential direction of the drive shaft 47. Specifically, in the main body portion 64, the region extending in the circumferential direction of the drive shaft 47 is 180 ° or more and less than 270 °.

As shown in fig. 6 and 7, the guide window 60 is located on the opposite side of the 2 nd radial path 59 with respect to the axial center L1 of the drive shaft 47. Therefore, the guide windows 60 and the 2 nd radial path 59 are formed in the drive shaft 47 with a phase shift of about 180 °. The 1 st radial passage 58 is formed in the drive shaft 47 so as to be phase-shifted by about 90 ° with respect to the guide window 60 and the 2 nd radial passage 59.

The guide window 60 has a 1 st restricting surface 65, a 2 nd restricting surface 66, and a pair of 2 guide surfaces 67. The 1 st restriction surface 65 and the 2 nd restriction surface 66 extend in a planar shape in the radial direction of the drive shaft 47 and extend parallel to each other. The 1 st restriction surface 65 and the 2 nd restriction surface 66 face each other in the axial direction of the drive shaft 47. The 1 st restriction surface 65 is located closer to the opening of the large path 61 than the 2 nd restriction surface 66. The 2 nd restriction surface 66 is located closer to the step surface 63 than the 1 st restriction surface 65. The guide surface 67 connects the 1 st restriction surface 65 and the 2 nd restriction surface 66, and extends in a planar manner in the axial direction of the drive shaft 47. The guide surface 67 forms end surfaces of the body portion 64 on both sides in the circumferential direction of the drive shaft 47.

An annular fitting groove 68 is formed in the outer peripheral surface of the drive shaft 47. The fitting groove 68 is formed in the outer peripheral surface of the drive shaft 47 at a position closer to the end surface of the drive shaft 47 opposite to the end surface of the guide window 60 where the screw hole 47a opens. In the fitting groove 68, a seal ring 69 is fitted.

As shown in fig. 9 and 10, the large passage 61 of the axial passage 57 communicates with the control pressure chamber 46. The seal ring 69 seals between the outer peripheral surface of the drive shaft 47 and the inner peripheral surface of the 2 nd shaft hole 27. The guide window 60 is located in the 2 nd shaft hole 27. Therefore, the guide window 60 opens on the outer peripheral surface of the portion of the drive shaft 47 located in the shaft hole 48. The guide window 60 is opened in the 2 nd shaft hole 27, and is opposed to the rear side communication passages 29a, 29b, 29c, 29d, and 29e in the 2 nd shaft hole 27.

As shown in fig. 4 and 5, the guide window 60 is opposed to the rear communication paths 29a, 29b, 29c, 29d, 29e of the rear communication paths 29a, 29b, 29c, 29d, 29e that communicate with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e in the re-expansion stroke or the suction stroke. On the other hand, the main body 64 is opposed to the rear communication paths 29a, 29b, 29c, 29d, 29e that communicate with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e in the compression stroke or the discharge stroke.

As shown in fig. 11 and 12, the 2 nd radial path 59 is located in the 1 st axial hole 19. Therefore, the 2 nd radial passage 59 opens on the outer peripheral surface of the portion of the drive shaft 47 located in the shaft hole 48. The 2 nd radial passage 59 is opened in the 1 st shaft hole 19, and faces the front side communication passages 21a, 21b, 21c, 21d, 21e in the 1 st shaft hole 19. The 2 nd radial passage 59 communicates the front side communication passages 21a, 21b, 21c, 21d, 21e with the axial passage 57.

As shown in fig. 6, the piston compressor 10 includes a moving body 70. The moving body 70 has a 1 st moving body portion 71 and a 2 nd moving body portion 81. The 1 st movable body 71 has a 1 st main body 72 and a 1 st shaft 73. The 1 st main body 72 has a columnar shape. The 1 st shaft portion 73 has an elongated cylindrical shape having a smaller outer diameter than the 1 st body portion 72. The 1 st shaft 73 protrudes from the center of the 1 st end surface 72a of the 1 st body 72. The axial center of the 1 st main body 72 and the axial center of the 1 st shaft 73 coincide with each other. A suction valve element 74 is provided at the tip of the 1 st shaft 73. The suction valve element 74 has a cylindrical shape. The outer diameter of the suction valve element 74 is larger than the outer diameter of the 1 st shaft portion 73 and smaller than the outer diameter of the 1 st main body portion 72.

As shown in fig. 13, the 1 st movable body 71 is inserted into the axial passage 57 from the opening of the large passage 61 of the axial passage 57, and is positioned in the axial passage 57. The outer diameter of the 1 st main body 72 is almost the same as the inner diameter of the large passage 61 of the axial passage 57. An annular fitting groove 75 is formed in the outer peripheral surface of the 1 st main body 72. In the fitting groove 75, a seal ring 76 is provided. The seal ring 76 seals between the outer peripheral surface of the 1 st main body 72 and the inner peripheral surface of the large passage 61. An annular engaging groove 77 as an engaging portion is formed in the outer peripheral surface of the 1 st main body portion 72. The engagement groove 77 is formed in the outer peripheral surface of the 1 st main body 72 at a position closer to the 1 st shaft 73 than the fitting groove 75. The 1 st shaft portion 73 has an outer diameter smaller than the inner diameter of the minor passage 62 of the axial passage 57. As shown in fig. 11 and 12, the outer diameter of the intake valve element 74 is almost the same as the inner diameter of the small passage 62 of the axial passage 57.

As shown in fig. 14 and 15, the 2 nd moving body 81 is formed in a curved plate shape smaller than half a circumference in the circumferential direction of the drive shaft 47. The 2 nd movable body 81 is formed by press-forming a flat plate of a thin plate, for example. The 2 nd moving body 81 is disposed in the guide window 60 and extends around the axial center of the drive shaft 47 between the 2 guide surfaces 67. The circumferential direction of the 2 nd moving body 81 coincides with the circumferential direction of the drive shaft 47.

In the 2 nd moving body 81, a region of the 2 nd moving body 81 extending in the circumferential direction is 90 ° or more and less than 180 °. The 2 nd moving body 81 extends in the axial direction of the drive shaft 47 in the guide window 60. The length of the 2 nd moving body 81 in the axial direction of the driving shaft 47 is set shorter than the length of the guide window 60 in the axial direction of the driving shaft 47.

In the 2 nd movable body portion 81, a movable body passage 82 is formed. The moving body passage 82 penetrates the 2 nd moving body portion 81 in the plate thickness direction. Therefore, the 2 nd movable body portion 81 is formed with the movable body passage 82 penetrating therethrough. The moving body passage 82 is formed so that the flow path area in the circumferential direction of the 2 nd moving body 81 becomes larger as going from one end to the other end in the axial direction of the drive shaft 47 in the 2 nd moving body 81.

The moving body passage 82 has a large opening 83 formed so as to have a large flow passage area in the circumferential direction of the 2 nd moving body portion 81, and a small opening 84 formed so as to have a smaller flow passage area in the circumferential direction of the 2 nd moving body portion 81 than the large opening 83. The large opening 83 and the small opening 84 are arranged in the axial direction of the drive shaft 47 and communicate with each other. The small opening 84 is located closer to one end side of the large opening 83 in the axial direction of the drive shaft 47 in the 2 nd moving body 81. The large opening 83 has a rectangular shape when the movable body passage 82 is viewed in plan, and the longitudinal direction matches the circumferential direction of the 2 nd movable body 81.

The 2 nd moving body 81 has 2 guide portions 85 that form both edge portions of the moving body passage 82 located on both sides in the circumferential direction of the 2 nd moving body 81 and are guided by the 2 guide surfaces 67. The 2 guide portions 85 are paired. Each guide portion 85 is in the form of an elongated thin plate. One of the 2 guide portions 85 forms one edge portion located in the circumferential direction of the 2 nd movable body portion 81, out of the large opening 83 and the small opening 84. The other of the 2 guide portions 85 forms the other edge portion of the large opening portion 83 located in the circumferential direction of the 2 nd moving body portion 81.

The 2 nd movable body 81 has a 1 st curved portion 81a and a 2 nd curved portion 81b each of which is formed in a curved plate shape and which is located on both sides of the movable body passage 82 in the axial direction of the drive shaft 47. The 1 st curved portion 81a and the 2 nd curved portion 81b face each other in the axial direction of the drive shaft 47 through the movable body passage 82. The 1 st curved portion 81a and the 2 nd curved portion 81b connect the 2 guide portions 85 to each other. The edge of the movable body passage 82 formed by the 1 st curved portion 81a extends in a direction perpendicular to the axial direction of the drive shaft 47 when the movable body passage 82 is viewed in plan view, and forms an edge of the large opening 83. The edge of the movable body passage 82 formed by the 2 nd bent portion 81b extends in a direction diagonal to the axial direction of the drive shaft 47 when the movable body passage 82 is viewed in plan, and forms an edge of the small opening 84. The 2 guide portions 85, the 1 st curved portion 81a, and the 2 nd curved portion 81b form an inner peripheral edge 82a of the moving body passage 82.

The 2 nd moving body 81 has an engagement protrusion 86 as an engaged portion engaged with the engagement groove 77 of the 1 st moving body 71. The engagement protrusion 86 is a flat plate shape protruding from the central portion in the circumferential direction of the 2 nd moving body 81 at the edge portion of the moving body passage 82 formed by the 1 st curved portion 81 a. Therefore, the engagement protrusion 86 protrudes from the inner peripheral edge 82a of the moving body passage 82. The engagement protrusion 86 extends from the 1 st bending portion 81a in the axial direction of the drive shaft 47, then bends toward the inside of the guide window 60, and extends toward the inside of the guide window 60. Therefore, the engagement protrusion 86 is disposed at a position overlapping the inside of the guide window 60 in the radial direction of the drive shaft 47. The plate thickness direction of the tip end portion of the engagement protrusion 86 coincides with the axial direction of the drive shaft 47. The tip end portion of the engagement protrusion 86 can be engaged with the engagement groove 77 of the 1 st main body 72.

One of the 2 guide portions 85 has a step portion 87 continuous with the moving body passage 82 and recessed in a direction away from the inner peripheral surface of the shaft hole 48. The step 87 is an elongated thin plate that forms a part of one of the 2 guide portions 85. Therefore, a part of one outer surface of the 2 guide portions 85 is recessed in a direction away from the inner peripheral surface of the shaft hole 48. In the present embodiment, a portion of one of the 2 guide portions 85 close to the small opening portion 84 becomes a stepped portion 87.

When the drive shaft 47 rotates in the direction of arrow R1 shown in fig. 14, the guide portion 85 having the stepped portion 87 among the 2 guide portions 85 is disposed so as to be positioned on the leading side in the rotation direction of the drive shaft 47 with respect to the guide window 60. The 2 nd movable body 81 is disposed with respect to the guide window 60 so that the large opening 83 is located closer to the 1 st restricting surface 65 than the small opening 84. The guide portion 85 located on the leading side in the rotation direction of the drive shaft 47 among the 2 guide portions 85 has a stepped portion 87.

The stepped portion 87 overlaps the guide surface 67 of the guide window 60 in the circumferential direction of the drive shaft 47, and is located on the guide surface 67. Accordingly, the distance from the stepped portion 87 to the inner peripheral surface of the shaft hole 48 is set to be a distance at which the stepped portion 87 is located on the guide surface 67. The stepped portion 87 is guided by the guide surface 67.

As shown in fig. 11 and 12, the suction valve element 74 is located in the small passage 62 of the axial passage 57. As shown in fig. 13, the 1 st body 72 of the 1 st movable body 71 is located in the large path 61 of the axial path 57. The engagement groove 77 is partially exposed from the guide window 60 at all times regardless of the circumferential direction of the 1 st movable body 71 when inserted into the axial passage 57. The suction pressure acts on the 1 st end surface 72a of the 1 st body 72 from the swash plate chamber 32 through the swash plate suction hole 56, the 1 st radial passage 58, and the axial passage 57. On the other hand, the control pressure of the control pressure chamber 46 acts on the 2 nd end surface 72b on the opposite side of the 1 st shaft portion 73 in the 1 st main body portion 72.

As shown in fig. 9 and 10, the 2 nd moving body 81 is disposed in the guide window 60, is located on the opposite side of the main body 64 of the drive shaft 47 with the axis L1 of the drive shaft 47 interposed therebetween, and is exposed into the 2 nd shaft hole 27. The 2 nd moving body 81 extends along the inner peripheral surface of the 2 nd shaft hole 27. The 2 nd movable body 81 is provided in the guide window 60, and thus cooperates with the main body 64 to form a cylindrical body having an outer diameter substantially equal to the inner diameter of the 2 nd shaft hole 27.

As shown in fig. 13, the 2 nd movable body 81 is inserted into the engagement groove 77 through the engagement protrusion 86, and is disposed on the guide window 60 in a state of being engaged with the 1 st movable body 71. In this way, by assembling the 1 st moving body 71 and the 2 nd moving body 81, the 1 st moving body 71 and the 2 nd moving body 81 can be integrally moved in the axial direction of the drive shaft 47. The moving body passage 82 of the 2 nd moving body 81 communicates with the axial passage 57.

In the large path 61, a biasing spring 88 is housed. One end of the biasing spring 88 is supported on the stepped surface 63. The other end of the biasing spring 88 is supported by the 1 st end surface 72a of the 1 st main body 72. The urging spring 88 urges the 1 st main body 72 toward the control pressure chamber 46 against the control pressure of the control pressure chamber 46.

As shown in fig. 4 and 5, the rotation of the drive shaft 47 is transmitted to the 2 nd moving body 81 via the guide surface 67. Thereby, the 2 nd moving body 81 can rotate integrally with the drive shaft 47. At this time, the engagement groove 77 engages with the engagement projection 86, so that the 1 st movable body 71 is restricted from rotating independently with respect to the 2 nd movable body 81 in the axial passage 57. Therefore, the moving body 70 is provided on the drive shaft 47 and rotates integrally with the drive shaft 47. Then, by the rotation of the drive shaft 47, the movable body 70 rotates integrally with the drive shaft 47, and the movable body passage 82 intermittently communicates with the rear side communication passages 29a, 29b, 29c, 29d, and 29e. Therefore, the moving body passage 82 is a 2 nd communication passage that intermittently communicates with the rear side communication passages 29a, 29b, 29c, 29d, 29e in accordance with the rotation of the drive shaft 47. As shown in fig. 3, the 2 nd radial passage 59 intermittently communicates with the front side communication passages 21a, 21b, 21c, 21d, and 21e by rotation of the drive shaft 47.

As shown in fig. 1 and 2, the piston compressor 10 includes a control valve 89. The control valve 89 is provided to the rear housing 15. The piston compressor 10 further includes a detection passage 90 connecting the swash plate chamber 32 and the control valve 89. The detection passage 90 penetrates the rear case 15 and the 2 nd cylinder 13. Further, the 1 st air supply passage 91 and the 2 nd air supply passage 92 are formed in the rear case 15. The 1 st air supply passage 91 connects the 2 nd discharge chamber 42 to the control valve 89. The 2 nd air supply passage 92 connects the control pressure chamber 46 and the control valve 89 to each other.

Part of the refrigerant gas in the 2 nd discharge chamber 42 is introduced into the control pressure chamber 46 through the 1 st gas supply passage 91, the control valve 89, and the 2 nd gas supply passage 92. The control pressure chamber 46 is connected to the swash plate chamber 32 through an evacuation passage, not shown. Thereby, the refrigerant gas in the control pressure chamber 46 is discharged to the swash plate chamber 32 through the suction passage.

The control valve 89 adjusts the valve opening by sensing the suction pressure, which is the pressure of the refrigerant gas in the swash plate chamber 32, through the detection passage 90. Thereby, the control valve 89 adjusts the flow rate of the refrigerant gas introduced from the 2 nd discharge chamber 42 to the control pressure chamber 46 through the 1 st gas supply passage 91, the control valve 89, and the 2 nd gas supply passage 92. When the valve opening degree of the control valve 89 increases, the flow rate of the refrigerant gas introduced from the 2 nd discharge chamber 42 to the control pressure chamber 46 through the 1 st gas supply passage 91, the control valve 89, and the 2 nd gas supply passage 92 increases. When the valve opening degree of the control valve 89 decreases, the flow rate of the refrigerant gas introduced from the 2 nd discharge chamber 42 to the control pressure chamber 46 through the 1 st gas supply passage 91, the control valve 89, and the 2 nd gas supply passage 92 decreases. In this way, the control valve 89 changes the flow rate of the refrigerant gas introduced from the 2 nd discharge chamber 42 into the control pressure chamber 46 with respect to the flow rate of the refrigerant gas discharged from the control pressure chamber 46 into the swash plate chamber 32, thereby controlling the control pressure that is the pressure of the refrigerant gas in the control pressure chamber 46.

In fig. 3, 4 and 5, the rotation direction of the drive shaft 47 is shown by an arrow R1. When the drive shaft 47 is at the rotation angle shown in fig. 3, 4 and 5, the 1 st compression chamber 53a shown in fig. 3 is at the initial stage of the re-expansion stroke or the intake stroke. Accordingly, the 1 st compression chamber 53b located at the rear side in the rotation direction of the drive shaft 47 among the 1 st compression chambers 53b and 53e adjacent to the 1 st compression chamber 53a in the circumferential direction of the drive shaft 47 is in a state in which the intake stroke is advanced as compared with the 1 st compression chamber 53a, and is in the middle stage of the intake stroke. In the 1 st compression chamber 53c located at the rear side in the rotation direction of the drive shaft 47, out of the 1 st compression chambers 53a and 53c adjacent to the 1 st compression chamber 53b in the circumferential direction of the drive shaft 47, the 1 st head 52a of the piston 52 is set to a bottom dead center, and a state of transition from the intake stroke to the compression stroke is set. Accordingly, in compression chamber 1, 53c is in a state of transition from the latter stage of the intake stroke to the initial stage of the compression stroke. Further, the 1 st compression chamber 53d located at the rear side in the rotation direction of the drive shaft 47 among the 1 st compression chambers 53b and 53d adjacent to the 1 st compression chamber 53c in the circumferential direction of the drive shaft 47 is in a state in which the compression stroke has progressed as compared with the 1 st compression chamber 53c, and is in the middle stage of the compression stroke. In the 1 st compression chamber 53e located at the rear side in the rotation direction of the drive shaft 47, out of the 1 st compression chambers 53c and 53e adjacent to the 1 st compression chamber 53d in the circumferential direction of the drive shaft 47, the 1 st head 52a of the piston 52 is at the top dead center, and is shifted from the latter stage of the compression stroke to the discharge stroke.

Here, the 2 nd radial passage 59 communicates with the front side communication passages 21a, 21b, 21c, 21d, 21e that communicate with the 1 st compression chambers 53a, 53b, 53c, 53d, 53e in the initial stage of the re-expansion stroke or the intake stroke. The 2 nd radial passage 59 is opposed to the front communication passages 21a, 21b, 21c, 21d, 21e communicating with the 1 st compression chambers 53a, 53b, 53c, 53d, 53e in the middle stage of the suction stroke.

Therefore, when the rotation angle of the drive shaft 47 is in the state shown in fig. 3, the 1 st compression chamber 53a is in the early stage of the re-expansion stroke or the intake stroke, and the 1 st compression chamber 53b is in the middle stage of the intake stroke, so the 2 nd radial passage 59 is opposed to the front side communication passages 21a, 21 b. When the drive shaft 47 rotates further than the position shown in fig. 3, the 2 nd radial passage 59 faces the front side communication passages 21a and 21 e.

At this time, the 1 st compression chamber 53e communicating with the front communication passage 21e becomes an initial stage of the re-expansion stroke or the intake stroke, and the 1 st compression chamber 53a communicating with the front communication passage 21a becomes a middle stage of the intake stroke. As described above, the 2 nd radial passage 59 sequentially opposes the front side communication passages 21a, 21b, 21c, 21d, 21e communicating with the 1 st compression chambers 53a, 53b, 53c, 53d, 53e in the initial stage of the re-expansion stroke or the intake stroke, in accordance with the rotation of the drive shaft 47. The 2 nd radial passage 59 is formed to be opposed to the front side communication passages 21a, 21b, 21c, 21d, and 21e which communicate with the 1 st compression chambers 53a, 53b, 53c, 53d, and 53e in the middle stage of the suction stroke in order, in association with the rotation of the drive shaft 47.

When the 1 st compression chambers 53a, 53b, 53c, 53d, 53e are in the intake stroke, the discharge stroke, and the like as shown in fig. 3, the 2 nd compression chamber 54a shown in fig. 4 and 5 is in the middle stage of the compression stroke. Further, the 2 nd compression chamber 54b located at the rear side in the rotation direction of the drive shaft 47 among the 2 nd compression chambers 54b and 54e adjacent to the 2 nd compression chamber 54a in the circumferential direction of the drive shaft 47 is in a state in which the compression stroke has progressed as compared with the 2 nd compression chamber 54a, and is in a later stage of the compression stroke. In the 2 nd compression chamber 54c located at the rear side in the rotation direction of the drive shaft 47, out of the 2 nd compression chambers 54a and 54c adjacent to the 2 nd compression chamber 54b in the circumferential direction of the drive shaft 47, the 2 nd head 52b of the piston 52 is at the top dead center, and is shifted from the discharge stroke to the early stage of the re-expansion stroke or the intake stroke. Further, the 2 nd compression chamber 54d located at the rear side in the rotation direction of the drive shaft 47 among the 2 nd compression chambers 54b and 54d adjacent to the 2 nd compression chamber 54c in the circumferential direction of the drive shaft 47 is in a state in which the intake stroke is advanced as compared with the 2 nd compression chamber 54c, and is in the middle stage of the intake stroke. Further, the 2 nd compression chamber 54e located at the rear side in the rotation direction of the drive shaft 47 among the 2 nd compression chambers 54c and 54e adjacent to the 2 nd compression chamber 54d in the circumferential direction of the drive shaft 47 is in a state in which the intake stroke is further advanced than the 2 nd compression chamber 54d, and is in a later stage of the intake stroke. That is, the 2 nd compression chambers 54a, 54b of the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e are in a high-pressure state, and the 2 nd compression chambers 54c, 54d, 54e of the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e are in a low-pressure state.

Here, by providing the 2 nd movable body 81 in the guide window 60, the 2 nd movable body 81 is opposed to the rear communication paths 29a, 29b, 29c, 29d, 29e communicating with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e in the re-expansion stroke or the suction stroke. Thus, when the drive shaft 47 is at the rotation angle shown in fig. 4 and 5, the 2 nd moving body 81 is opposed to the rear communication path 29c communicating with the 2 nd compression chamber 54c, the rear communication path 29d communicating with the 2 nd compression chamber 54d, and the rear communication path 29e communicating with the 2 nd compression chamber 54 e.

On the other hand, the main body 64 of the drive shaft 47 faces the rear communication passages 29a, 29b, 29c, 29d, 29e communicating with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e in the compression stroke or the discharge stroke. Thus, when the drive shaft 47 is at the rotation angle shown in fig. 4 and 5, the main body 64 faces the rear communication passage 29a communicating with the 2 nd compression chamber 54a and the rear communication passage 29b communicating with the 2 nd compression chamber 54 b.

The 2 nd moving body 81 sequentially faces the rear communication passages 29a, 29b, 29c, 29d, and 29e communicating with the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e in the re-expansion stroke or the suction stroke, in accordance with the rotation of the drive shaft 47. The main body 64 is rotated by the drive shaft 47, and sequentially faces the rear communication passages 29a, 29b, 29c, 29d, and 29e that communicate with the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e in the compression stroke or the discharge stroke.

Here, the end surface of the main body 64 located on the rear side in the rotation direction of the drive shaft 47 is located between the rear side communication passage 29c communicating with the 2 nd compression chamber 54c in the re-expansion stroke or the suction stroke and the rear side communication passage 29b communicating with the 2 nd compression chamber 54b which becomes the latter stage of the compression stroke. The main body 64 is formed to extend more than half a circumference in the circumferential direction of the drive shaft 47 along the inner circumferential surface of the shaft hole 48 from the rear communication passage 29c communicating with the 2 nd compression chamber 54c in the re-expansion stroke or the suction stroke to the rear communication passage 29b communicating with the 2 nd compression chamber 54b which is the later stage of the compression stroke. The end surface of the main body 64 on the leading side in the rotation direction of the drive shaft 47 is located at a position between the rear communication path 29a communicating with the 2 nd compression chamber 54a which is the middle stage of the compression stroke and the rear communication path 29e communicating with the 2 nd compression chamber 54e which is the later stage of the suction stroke. In the present embodiment, the end surface of the main body 64 on the leading side in the rotation direction of the drive shaft 47 is opposed to the rear communication passage 29e communicating with the 2 nd compression chamber 54e which is the later stage of the suction stroke.

Next, the operation of the present embodiment will be described.

In the piston compressor 10 of the present embodiment, the communication area between the rear communication passages 29a, 29b, 29c, 29d, 29e and the moving body passage 82 changes every 1 rotation of the drive shaft 47 according to the position of the 2 nd moving body portion 81 in the guide window 60. In addition, according to the position of the suction valve body 74 in the small passage 62, the communication area between the 2 nd radial passage 59 and the axial passage 57 changes, and the communication area between the front side communication passages 21a, 21b, 21c, 21d, 21e and the 2 nd radial passage 59 changes every 1 rotation of the drive shaft 47.

For example, when the valve opening degree of the control valve 89 is reduced, the flow rate of the refrigerant gas introduced from the 2 nd discharge chamber 42 to the control pressure chamber 46 is reduced, and the variable differential pressure, which is the difference between the control pressure acting on the 1 st main body portion 72 and the suction pressure, is reduced. Then, the force generated by combining the biasing force of the biasing spring 88 and the suction pressure acting on the 1 st end surface 72a of the 1 st body portion 72 overcomes the control pressure acting on the 2 nd end surface 72b of the 1 st body portion 72, and the 1 st movable body portion 71 moves toward the control pressure chamber 46. Thus, the 2 nd guide portions 85 of the 2 nd movable body 81 are guided by the 2 guide surfaces 67 in the guide window 60, and the 2 nd movable body 81 moves toward the 1 st restricting surface 65. The movable body passage 82 moves relative to the rear side communication passages 29a, 29b, 29c, 29d, 29e toward the 1 st restriction surface 65. Thereby, the 2 nd moving body 81 is guided by the 2 nd guide surfaces 67. Therefore, the guide window 60 guides the moving body 70 in the axial direction of the drive shaft 47.

Then, the movable body passage 82 moves relative to the rear side communication passages 29a, 29b, 29c, 29d, and 29e toward the 1 st restricting surface 65, and the rear side communication passages 29a, 29b, 29c, 29d, and 29e communicate with the movable body passage 82 at a position close to the small opening 84 in the movable body passage 82. Thus, the communication area between each of the rear communication passages 29a, 29b, 29c, 29d, and 29e and the movable body passage 82 gradually decreases for every 1 rotation of the drive shaft 47.

Further, the 1 st movable body 71 moves toward the control pressure chamber 46, and the suction valve element 74 moves toward the large passage 61 in the small passage 62 of the axial passage 57. Thus, in the small passage 62, the suction valve element 74 starts to close the 2 nd radial passage 59, and the communication area between the axial passage 57 and the 2 nd radial passage 59 becomes smaller.

When the valve opening degree of the control valve 89 is further reduced and the control pressure of the control pressure chamber 46 is further reduced, the variable differential pressure becomes minimum. As a result, as shown in fig. 9, the 1 st movable body 71 is moved to the maximum extent in the large passage 61 toward the control pressure chamber 46. As a result, the 2 nd movable body 81 is moved toward the 1 st restricting surface 65 to the greatest extent in the guide window 60, and the 1 st curved portion 81a of the 2 nd movable body 81 comes into contact with the 1 st restricting surface 65. By the abutment of the 1 st curved portion 81a of the 2 nd movable body 81 with the 1 st restricting surface 65, the movement of the 1 st movable body 71 toward the control pressure chamber 46 is restricted. As a result, the rear side communication passages 29a, 29b, 29c, 29d, 29e communicate with the small opening 84 in the moving body passage 82, and the communication area between the rear side communication passages 29a, 29b, 29c, 29d, 29e and the moving body passage 82 is minimized every 1 rotation of the drive shaft 47.

When the drive shaft 47 is at the rotation angle shown in fig. 4, for example, in a state where the 1 st curved portion 81a of the 2 nd movable body portion 81 is in contact with the 1 st restricting surface 65, the 2 nd movable body portion 81 communicates the rear side communication passage 29c and the movable body passage 82 with each other. At this time, the 2 nd compression chamber 54c, which is communicated with the rear communication passage 29c, is in a state of transition from the discharge stroke to the early stage of the re-expansion stroke or the intake stroke. The 2 nd movable body 81 is configured such that the rear side communication passages 29d and 29e and the movable body passage 82 are not communicated with each other by the outer surface of the 2 nd bent portion 81 b. That is, the 2 nd movable body 81 communicates only the rear communication passages 29a, 29b, 29c, 29d, 29e and the movable body passage 82, which communicate with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e in the initial stage of the re-expansion stroke or the intake stroke.

The main body 64 of the drive shaft 47 is opposed to the rear communication passages 29a, 29b, 29c, 29d, and 29e communicating with the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e in the compression stroke and the discharge stroke. Thus, the main body 64 of the drive shaft 47 prevents the rear communication passages 29a, 29b, 29c, 29d, 29e and the movable body passage 82, which communicate with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e in the compression stroke or the discharge stroke, from communicating with each other. That is, the rear communication passages 29a, 29b, 29c, 29d, 29e are not communicated with the movable body passage 82 by the drive shafts 47 by exposing the drive shafts 47 to the rear communication passages 29a, 29b, 29c, 29d, 29 e.

In this way, when the variable differential pressure is minimum, the refrigerant gas is sucked from the swash plate chamber 32 through the swash plate suction port 56, the 1 st radial passage 58, the axial passage 57, the movable body passage 82, and the rear side communication passages 29a, 29b, 29c, 29d, and 29e only when the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e are in the initial stage of the suction stroke. As a result, the flow rate of the refrigerant gas sucked from the swash plate chamber 32 into the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e is minimized, and the flow rate of the refrigerant gas discharged from the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e into the 2 nd discharge chamber 42 is minimized.

At this time, the stepped portion 87 faces the rear communication passages 29a, 29b, 29c, 29d, 29e at the timing before the movable body passage 82 faces the rear communication passages 29a, 29b, 29c, 29d, 29e with the rotation of the drive shaft 47. Between the inner peripheral surface of the shaft hole 48 and the stepped portion 87, the flow path is used as a flow path for guiding the refrigerant gas from the moving body passage 82 to the rear side communication passages 29a, 29b, 29c, 29d, and 29 e. Therefore, the refrigerant gas is sucked from the movable body passage 82 into the rear side communication passages 29a, 29b, 29c, 29d, and 29e at a timing before the movable body passage 82 faces the rear side communication passages 29a, 29b, 29c, 29d, and 29e in accordance with the rotation of the drive shaft 47.

Further, when the variable differential pressure is minimized and the 1 st movable body 71 is moved toward the control pressure chamber 46 to the maximum extent in the large passage 61, the suction valve element 74 closes the 2 nd radial passage 59 in the small passage 62 as shown in fig. 11. Thus, the communication area between the axial passage 57 and the 2 nd radial passage 59 is minimized, that is, substantially zero. As a result, when the variable differential pressure is minimum, the flow rate of the refrigerant gas sucked from the swash plate chamber 32 into the 1 st compression chambers 53a, 53b, 53c, 53d, and 53e becomes substantially zero, and the flow rate of the refrigerant gas discharged from the 1 st compression chambers 53a, 53b, 53c, 53d, and 53e into the 1 st discharge chamber 36 becomes substantially zero. Therefore, when the variable differential pressure is minimum, the 1 st compression chambers 53a, 53b, 53c, 53d, and 53e are in the cylinder stop state in which suction work and compression work are not performed. As described above, the flow rate of the refrigerant gas discharged from each 1 st compression chamber 53a, 53b, 53c, 53d, 53e and each 2 nd compression chamber 54a, 54b, 54c, 54d, 54e to each 1 st discharge chamber 36 and each 2 nd discharge chamber 42 decreases.

For example, when the valve opening degree of the control valve 89 is increased, the flow rate of the refrigerant gas introduced from the 2 nd discharge chamber 42 to the control pressure chamber 46 increases, and the variable differential pressure increases. The control pressure acting on the 2 nd end surface 72b of the 1 st main body portion 72 overcomes the force obtained by combining the biasing force of the biasing spring 88 and the suction pressure acting on the 1 st end surface 72a of the 1 st main body portion 72, and the 1 st movable body portion 71 moves toward the side opposite to the control pressure chamber 46. Thereby, the 2 nd guide portions 85 of the 2 nd movable body portion 81 are guided by the 2 nd guide surfaces 67 in the guide window 60, and the 2 nd movable body portion 81 moves toward the 2 nd restricting surface 66, and the movable body passage 82 moves toward the 2 nd restricting surface 66 with respect to the rear side communication passages 29a, 29b, 29c, 29d, 29 e. Thereby, the 1 st movable body 71 moves in the axial direction of the drive shaft 47 in the axial passage 57 based on the control pressure. Therefore, the moving body 70 can move relative to the drive shaft 47 in the axial center direction of the drive shaft 47 based on the control pressure.

Then, the movable body passage 82 moves relative to the rear side communication passages 29a, 29b, 29c, 29d, and 29e toward the 2 nd restricting surface 66, and the rear side communication passages 29a, 29b, 29c, 29d, and 29e communicate with the movable body passage 82 at a position near the large opening 83 in the movable body passage 82. Thus, the communication area between each of the rear communication passages 29a, 29b, 29c, 29d, 29e and the movable body passage 82 increases gradually for every 1 rotation of the drive shaft 47.

Further, the 1 st movable body 71 moves toward the side opposite to the control pressure chamber 46, and the suction valve element 74 moves toward the side opposite to the large passage 61 in the small passage 62 of the axial passage 57. In the small passage 62, the intake valve element 74 starts to open the 2 nd radial passage 59, the communication area between the axial passage 57 and the 2 nd radial passage 59 gradually increases, and the communication area between the front side communication passages 21a, 21b, 21c, 21d, 21e and the 2 nd radial passage 59 becomes larger than zero. As a result, the refrigerant gas is sucked from the swash plate chamber 32 through the swash plate suction port 56, the 1 st radial passage 58, the axial passage 57, the 2 nd radial passage 59, and the front communication passages 21a, 21b, 21c, 21d, 21e for each of the 1 st compression chambers 53a, 53b, 53c, 53d, 53e in the initial stage of the suction stroke or in the middle stage of the suction stroke. As a result, suction work and compression work are performed in the 1 st compression chambers 53a, 53b, 53c, 53d, and 53e, and the flow rate of the refrigerant gas discharged from the 1 st compression chambers 53a, 53b, 53c, 53d, and 53e to the 1 st discharge chamber 36 increases.

When the valve opening degree of the control valve 89 is further increased and the control pressure of the control pressure chamber 46 is further increased, the variable differential pressure becomes maximum. As a result, as shown in fig. 10, the 1 st movable body 71 is moved to the side opposite to the control pressure chamber 46 to the greatest extent in the large passage 61. As a result, the 2 nd movable body 81 is moved toward the 2 nd restricting surface 66 to the maximum extent in the guide window 60, and the 2 nd curved portion 81b of the 2 nd movable body 81 is in contact with the 2 nd restricting surface 66. By the abutment of the 2 nd bent portion 81b of the 2 nd movable body 81 with the 2 nd restricting surface 66, the movement of the 1 st movable body 71 toward the opposite side of the control pressure chamber 46 is restricted. As a result, the rear side communication passages 29a, 29b, 29c, 29d, and 29e communicate with the large opening 83 in the moving body passage 82, and the communication area between the rear side communication passages 29a, 29b, 29c, 29d, and 29e and the moving body passage 82 is maximized every 1 rotation of the drive shaft 47.

When the drive shaft 47 is at the rotation angle shown in fig. 5, for example, in a state where the 2 nd bent portion 81b of the 2 nd movable body 81 is in contact with the 2 nd restricting surface 66, the 2 nd movable body 81 communicates the rear side communication passages 29c, 29d, 29e with the movable body passage 82. That is, the 2 nd movable body 81 communicates the rear side communication passages 29a, 29b, 29c, 29d, 29e and the movable body passage 82, which communicate with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e in the initial stage of the re-expansion stroke or the suction stroke. The 2 nd movable body 81 communicates the rear communication passages 29a, 29b, 29c, 29d, 29e and the movable body passage 82, which communicate with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e in the middle stage of the intake stroke. The 2 nd movable body 81 communicates the rear communication passages 29a, 29b, 29c, 29d, 29e and the movable body passage 82, which communicate with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e in the latter stage of the intake stroke. Therefore, the movable body 70 communicates with the rear communication passages 29a, 29b, 29c, 29d, 29e and the movable body passage 82, which communicate with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54 e.

The main body 64 of the drive shaft 47 is opposed to the rear communication passages 29a, 29b, 29c, 29d, and 29e communicating with the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e in the compression stroke and the discharge stroke. Therefore, the rear side communication passages 29a, 29b, 29c, 29d, 29e and the movable body passage 82, which communicate with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e, are not communicated with each other by the drive shaft 47.

As described above, the variable differential pressure is maximized, and the refrigerant gas in the swash plate chamber 32 is sucked into the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e from the initial stage to the later stage of the suction stroke. Therefore, the flow rate of the refrigerant gas sucked into the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e increases, and the flow rate of the refrigerant gas discharged from the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e to the 2 nd discharge chamber 42 becomes maximum.

Further, the variable differential pressure is maximized, and the 1 st movable body 71 is moved to the side opposite to the control pressure chamber 46 to the maximum extent in the large passage 61, so that the intake valve element 74 maximizes the opening degree of the 2 nd radial passage 59 in the small passage 62, as shown in fig. 12. As a result, the communication area between the axial passage 57 and the 2 nd radial passage 59 is maximized, and the communication area between the front side communication passages 21a, 21b, 21c, 21d, 21e and the 2 nd radial passage 59 is maximized. As a result, the flow rate of the refrigerant gas sucked into each 1 st compression chamber 53a, 53b, 53c, 53d, 53e is maximized, and therefore, the flow rate of the refrigerant gas discharged from each 1 st compression chamber 53a, 53b, 53c, 53d, 53e into each 1 st discharge chamber 36 is maximized.

As described above, in the piston compressor 10 of the present embodiment, the flow rate of the refrigerant gas discharged from the 1 st compression chambers 53a, 53b, 53c, 53d, 53e and the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e to the 1 st discharge chamber 36 and the 2 nd discharge chamber 42 varies according to the position of the movable body 70 in the axial direction of the drive shaft 47.

For example, part of the high-pressure refrigerant gas compressed in the compression stroke flows into the 2 nd shaft hole 27 via the rear communication passages 29a, 29b, 29c, 29d, and 29e communicating with the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e in the compression stroke or the discharge stroke. At this time, in the 2 nd shaft hole 27, the main body 64 of the drive shaft 47 is opposed to the rear communication passages 29a, 29b, 29c, 29d, 29e communicating with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e in the compression stroke or the discharge stroke. Thus, the main body 64 prevents the rear communication passages 29a, 29b, 29c, 29d, 29e and the movable body passage 82, which communicate with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e in the compression stroke or the discharge stroke, from communicating with each other. Further, since the drive shaft 47 is made of steel, the drive shaft 47 receives compression loads from the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e in the compression stroke or the discharge stroke. Therefore, the compression load is less likely to act on the 2 nd movable body 81. Thus, the movable body 70 is easily movable in the axial direction of the drive shaft 47.

Further, a part of the high-pressure refrigerant gas compressed in the compression stroke flows into the 1 st shaft hole 19 via the front communication passages 21a, 21b, 21c, 21d, 21e communicating with the 1 st compression chambers 53a, 53b, 53c, 53d, 53e in the compression stroke or the discharge stroke. At this time, the drive shaft 47 also receives compression loads from the 1 st compression chambers 53a, 53b, 53c, 53d, 53e in the compression stroke or the discharge stroke. Therefore, the compression load is hard to act on the suction valve element 74.

The following effects can be obtained in the above embodiments.

(1) In order to improve the controllability of the conventional piston compressor described in the related art, it is conceivable to enlarge the pressure receiving area of the control pressure in the moving body so that the moving body can be moved in the axial direction of the drive shaft by a larger thrust force. However, if the pressure receiving area of the control pressure in the moving body is increased, the moving body is increased in size, and the shaft hole is also increased in size with the increase in size of the moving body, so that the piston compressor is increased in size. In contrast, the present embodiment can achieve high controllability and miniaturization.

Specifically, by the 1 st movable body 71 moving in the axial direction of the drive shaft 47 in the axial passage 57 based on the control pressure, the 2 nd movable body 81 moves in the axial direction of the drive shaft 47 integrally with the 1 st movable body 71 in the guide window 60. Further, according to the position of the 2 nd movable body 81 in the axial direction of the drive shaft 47, the communication angle around the axial center at which the rear side communication passages 29a, 29b, 29c, 29d, 29e communicate with the movable body passage 82 changes every 1 revolution of the drive shaft 47. Thereby, the flow rate of the refrigerant gas discharged from each of the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e to the 2 nd discharge chamber 42 changes.

Here, the engagement groove 77 for engaging the 2 nd movable body 81 with the 1 st movable body 71 is formed at a position of the 1 st movable body 71 exposed from the guide window 60. The engagement protrusion 86 engaged with the engagement groove 77 is flat plate-shaped protruding from the inner peripheral edge 82a of the moving body passage 82 in the 2 nd moving body portion 81 and bent toward the inside of the guide window 60. Accordingly, the engagement protrusion 86 does not protrude outward of the 2 nd moving body 81, so that the 2 nd moving body 81 can be made compact, contributing to downsizing of the piston compressor 10.

By exposing the drive shaft 47 to the rear communication passages 29a, 29b, 29c, 29d, and 29e, the rear communication passages 29a, 29b, 29c, 29d, and 29e and the movable body passage 82 do not communicate with each other by the drive shaft 47, and the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e move from the bottom dead center to the top dead center by the piston 52, and the compression stroke or the discharge stroke is performed. As a result, the compression load, which is the load generated by the high-pressure refrigerant gas compressed in each of the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e, acts on the drive shaft 47 via the corresponding rear communication passage 29a, 29b, 29c, 29d, and 29e, while the compression load is less likely to act on the moving body 70. Accordingly, the movable body 70 is easily moved in the axial direction of the drive shaft 47, and therefore, the movable body 70 does not need to be enlarged more than necessary in order to obtain a large thrust. Therefore, high controllability can be exhibited and miniaturization can be achieved.

(2) The engagement protrusion 86 protrudes from the edge of the moving body passage 82 formed by the 1 st curved portion 81a of the 2 nd moving body 81. Accordingly, for example, the 2 nd movable body 81 is less likely to tilt in the axial direction of the drive shaft 47 than in a configuration in which the engagement protrusion 86 protruding from the edge of the movable body passage 82 formed in the 2 nd bent portion 81b is engaged with the engagement groove 77. Therefore, the 2 nd movable body 81 can be restrained from moving in the axial direction of the drive shaft 47 in a state of being inclined with respect to the axial direction of the drive shaft 47.

(3) The engagement protrusion 86 protrudes from a central portion in the circumferential direction of the 2 nd moving body 81 at an edge portion of the moving body passage 82 formed by the 1 st curved portion 81a of the 2 nd moving body 81. Accordingly, for example, the 2 nd movable body portion 81 is less likely to tilt with respect to the axial direction of the drive shaft 47 than in the case where the edge portion of the movable body passage 82 formed by the 1 st curved portion 81a of the engagement protrusion 86 protrudes from a position displaced from the central portion in the circumferential direction of the 2 nd movable body portion 81. Therefore, the 2 nd movable body 81 can be restrained from moving in the axial direction of the drive shaft 47 in a state of being inclined with respect to the axial direction of the drive shaft 47.

(4) The 2 nd moving body 81 is a curved plate extending along the inner peripheral surface of the shaft hole 48. In order to secure the rigidity of the 2 nd movable body 81, for example, it is conceivable to increase the width of the 2 nd movable body 81 of the 2 guide portions 85 in the circumferential direction. However, the width of the 2 nd moving body 81 of the moving body passage 82 in the circumferential direction is reduced by increasing the width of the 2 nd moving body 81 of the 2 guide portions 85, so that the flow passage area of the moving body passage 82 is reduced. As a result, the refrigerant gas is less likely to be sucked from the movable body passage 82 into the rear side communication passages 29a, 29b, 29c, 29d, and 29e, and the controllability may be reduced.

Therefore, one of the 2 guide portions 85 has a stepped portion 87 continuous with the moving body passage 82 and recessed in a direction away from the inner peripheral surface of the shaft hole 48. Therefore, the space between the inner peripheral surface of the shaft hole 48 and the stepped portion 87 can be used as a flow path for guiding the refrigerant gas from the moving body passage 82 to the rear side communication passages 29a, 29b, 29c, 29d, 29 e. Therefore, even if the width of the 2 nd movable body 81 of the 2 nd guide portions 85 in the circumferential direction is increased to secure the rigidity of the 2 nd movable body 81, the difficulty in sucking the refrigerant gas from the movable body passage 82 into the rear side communication passages 29a, 29b, 29c, 29d, and 29e is suppressed.

(5) For example, when the drive shaft 47 is at the rotation angle shown in fig. 4 and 5, the main body 64 is formed to extend more than half a circle in the circumferential direction of the drive shaft 47 along the inner circumferential surface of the shaft hole 48 from the rear communication passage 29c communicating with the 2 nd compression chamber 54c in the re-expansion stroke or the suction stroke to the rear communication passage 29b communicating with the 2 nd compression chamber 54b which is the later stage of the compression stroke. Accordingly, the boundary between the body 64 and the 2 nd movable body 81 in the circumferential direction of the drive shaft 47 does not face the rear communication passages 29a, 29b, 29c, 29d, 29e communicating with the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e which are the later stages of the compression stroke, as the drive shaft 47 rotates. Therefore, even if the refrigerant gas is caused to flow backward from the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e, which are the later stages of the compression stroke, toward the corresponding rear side communication passages 29a, 29b, 29c, 29d, 29e, the refrigerant gas can be prevented from leaking to the axial passage 57 through the boundary between the body portion 64 and the 2 nd movable body portion 81 in the circumferential direction of the drive shaft 47.

Therefore, the compression pressure in each of the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e, which is the later stage of the compression stroke, is suppressed from decreasing, and therefore, the movement of the 2 nd head portion 52b of the piston 52, which reciprocates in each of the 2 nd cylinder bores 28a, 28b, 28c, 28d, 28e, from the top dead center to the bottom dead center is easy to proceed. As a result, the power consumed by the piston compressor 10 can be suppressed. In addition, since leakage of the high-temperature refrigerant gas into the axial passage 57 is suppressed, a decrease in compression performance of the piston compressor 10 can be suppressed.

(6) The guide portion 85 located on the leading side in the rotation direction of the drive shaft 47 among the 2 guide portions 85 has a stepped portion 87. Accordingly, the stepped portion 87 faces the rear communication passages 29a, 29b, 29c, 29d, and 29e at the timing before the movable body passage 82 faces the rear communication passages 29a, 29b, 29c, 29d, and 29e in accordance with the rotation of the drive shaft 47. Therefore, for example, even if the width of the 2 nd movable body 81 in the circumferential direction of the 2 nd guide portion 85 is increased in order to secure the rigidity of the 2 nd movable body 81, the timing of the suction of the refrigerant gas from the movable body passage 82 to the rear side communication passages 29a, 29b, 29c, 29d, 29e can be prevented from being delayed.

(7) In the case where the body portion 64 is formed to extend more than half a circumference in the circumferential direction of the drive shaft 47 along the inner circumferential surface of the shaft hole 48, the 2 nd moving body portion 81 is formed less than half a circumference in the circumferential direction of the drive shaft 47. Therefore, if the opening area of the movable body passage 82 is to be ensured, the width of the 2 nd movable body portion 81 of the 2 guide portions 85 in the circumferential direction may be reduced, and the rigidity of the 2 nd movable body portion 81 may be lowered. Therefore, in the present embodiment, since one of the 2 guide portions 85 has the stepped portion 87 which is continuous with the movable body passage 82 and is recessed in a direction away from the inner peripheral surface of the shaft hole 48, it is possible to use between the inner peripheral surface of the shaft hole 48 and the stepped portion 87 as a flow path for guiding the refrigerant gas from the movable body passage 82 to the rear side communication passages 29a, 29b, 29c, 29d, 29 e. Therefore, the width of the 2 nd moving body 81 in the circumferential direction of the 2 nd guide 85 can be increased in order to secure the rigidity of the 2 nd moving body 81.

(8) The main body 64 is formed to extend more than half a circumference in the circumferential direction of the drive shaft 47 along the inner circumferential surface of the shaft hole 48. Therefore, for example, the rigidity of the main body 64 can be increased as compared with a case where the main body 64 is formed to extend less than half a circumference in the circumferential direction of the drive shaft 47 along the inner circumferential surface of the shaft hole 48. Therefore, the rigidity of the main body 64 against the compression load from the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e in the compression stroke and the discharge stroke is easily ensured.

The above embodiment can be modified as follows. The above-described embodiments and the following modifications can be combined with each other within a range that is not technically contradictory.

As shown in fig. 16, the 2 nd movable body 81 may be configured as follows: one of the 2 guide portions 85 has an elongated thin plate-like bent portion 93 bent toward the other of the 2 guide portions 85. The bending portion 93 forms a part of one of the 2 guide portions 85. The bending portion 93 is bent along one of the 2 guide surfaces 67. Further, a step 87 recessed in a direction away from the inner peripheral surface of the shaft hole 48 may be formed in an edge portion of the bent portion 93 on the opposite side to the other of the 2 guide portions 85. The stepped portion 87 is continuous with the moving body passage 82. The 2 nd movable body 81 may further include a reinforcing rib 94 for reinforcing the 2 nd movable body 81. The reinforcing rib 94 is, for example, a thin and long sheet-like member connecting the 1 st curved portion 81a and the 2 nd curved portion 81 b. Accordingly, the rigidity of the 2 nd movable body 81 can be further ensured.

In the embodiment, the distance between the step 87 and the inner peripheral surface of the shaft hole 48 may be adjusted so that the space between the step 87 and the inner peripheral surface of the shaft hole 48 functions as a restriction portion provided between the movable body passage 82 and the rear side communication passages 29a, 29b, 29c, 29d, and 29 e. Accordingly, the flow rate of the refrigerant gas discharged from each of the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e to the 2 nd discharge chamber 42 can be easily minimized.

In the embodiment, the distance from the stepped portion 87 to the inner peripheral surface of the shaft hole 48 may be set to a distance at which the stepped portion 87 is located inside the guide window 60 without being located on the guide surface 67. In short, the step 87 may be configured not to be guided by the guide surface 67. Therefore, it is sufficient if at least a part of one of the 2 guide portions 85 is guided by one of the 2 guide surfaces 67.

In the embodiment, the other of the 2 guide portions 85 may have a stepped portion 87. That is, the stepped portion 87 may be formed in a guide portion located on the rear side in the rotation direction of the drive shaft 47 among the 2 guide portions 85.

In the embodiment, one of the 2 guide portions 85 may be a stepped portion 87 in addition to a portion near the small opening portion 84 and a portion near the large opening portion 83. That is, most of the 2 guide portions 85 may be the stepped portions 87.

In the embodiment, the guide window 60 may extend across half the circumference in the circumferential direction of the drive shaft 47. That is, the main body 64 may be formed to extend over a half circumference in the circumferential direction of the drive shaft 47. In this case, the 2 nd moving body 81 is also formed in a curved plate shape extending across half the circumference in the circumferential direction of the drive shaft 47.

In the embodiment, the guide window 60 may extend less than half a circumference in the circumferential direction of the drive shaft 47. That is, the main body portion 64 may be formed to extend less than half a circumference in the circumferential direction of the drive shaft 47. In this case, the 2 nd moving body 81 is formed in a curved plate shape having a larger than half circumference in the circumferential direction of the drive shaft 47.

In the embodiment, for example, an engagement hole having a long four-sided hole shape in plan view may be formed in the outer peripheral surface of the 1 st main body 72 of the 1 st movable body 71, and the 2 nd movable body 81 may be engaged with the 1 st movable body 71 by engaging the engagement protrusion 86 with the engagement hole.

In the embodiment, for example, the engagement protrusion 86 may protrude from the edge of the movable body passage 82 formed by the 2 nd bent portion 81 b. For example, the engaging protrusions 86 may protrude from the edges of the movable body passage 82 formed by the 2 guide portions 85, respectively.

In the embodiment, for example, the engaging protrusion 86 may protrude from a position offset from the center portion in the circumferential direction of the 2 nd movable body 81 at the edge portion of the movable body passage 82 formed by the 1 st curved portion 81 a.

In the embodiment, the engaging protrusion 86 may be, for example, a curved plate. In other words, the engagement protrusion 86 may be a plate-like shape protruding from the inner peripheral edge 82a of the movable body passage 82 in the 2 nd movable body portion 81 and bent toward the inside of the guide window 60.

In the embodiment, for example, the flow rate of the refrigerant gas sucked from the swash plate chamber 32 into the 1 st compression chambers 53a, 53b, 53c, 53d, and 53e may be changed by rotating the drive shaft 47 by 1 turn by the movable body 70. Further, the flow rate of the refrigerant gas sucked from the swash plate chamber 32 into the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e may be changed by rotating the drive shaft 47 by 1 turn by the suction valve member 74.

In the embodiment, the 2 nd radial passage 59 may be formed in the drive shaft 47 so as to suck the refrigerant gas into the 1 st compression chambers 53a, 53b, 53c, 53d, and 53e from the initial stage of the suction stroke to the later stage of the suction stroke through the front side communication passages 21a, 21b, 21c, 21d, and 21 e. The 2 nd radial passage 59 may be formed in the drive shaft 47 so as to suck the refrigerant gas only into the 1 st compression chambers 53a, 53b, 53c, 53d, 53e in the initial stage of the suction stroke through the front communication passages 21a, 21b, 21c, 21d, 21 e.

In the embodiment, the casing 11 may be provided with a suction chamber communicating with the suction port 22 in addition to the swash plate chamber 32, and the refrigerant gas in the suction chamber may be sucked into the 1 st compression chambers 53a, 53b, 53c, 53d, 53e and the 2 nd compression chambers 54a, 54b, 54c, 54d, 54 e. In this case, the suction chamber needs to communicate with the axial passage 57.

In the embodiment, the moving body 70 may be configured to circulate a part of the refrigerant gas compressed in the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e in the compression stroke to the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e in the re-expansion stroke or the suction stroke. With this configuration, the flow rate of the refrigerant gas discharged from the 2 nd compression chambers 54a, 54b, 54c, 54d, and 54e to the 2 nd discharge chamber 42 can be changed every 1 revolution of the drive shaft 47.

In the embodiment, the control valve 89 may be an external control valve that controls the control pressure by switching ON (ON) and OFF (OFF) of the current from the outside, or may be an internal control valve that controls the control pressure independently of the current from the outside. Here, when the control valve 89 is an external control valve, if the control valve 89 decreases the valve opening degree by turning off the current to the control valve 89, the valve opening degree becomes smaller at the time of stopping the piston compressor 10, and the control pressure of the control pressure chamber 46 can be made lower. Accordingly, the piston compressor 10 can be started in a state where the flow rate of the refrigerant gas discharged from the 1 st compression chambers 53a, 53b, 53c, 53d, 53e and the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e to the 1 st discharge chamber 36 and the 2 nd discharge chamber 42 is minimized, and therefore, the starting shock can be reduced.

In the embodiment, the control valve 89 may perform the following outlet side control: the flow rate of the refrigerant gas led from the control pressure chamber 46 to the swash plate chamber 32 through the suction passage is changed. In this case, the amount of refrigerant gas in the 2 nd discharge chamber 42 used when the flow rate of refrigerant gas discharged from each 1 st compression chamber 53a, 53b, 53c, 53d, 53e and each 2 nd compression chamber 54a, 54b, 54c, 54d, 54e to each 1 st discharge chamber 36 and 2 nd discharge chamber 42 is changed can be reduced, and therefore, the efficiency of the piston compressor 10 can be improved. In this case, if the valve opening is increased by turning off the current to the control valve 89, the valve opening increases at the time of stopping the piston compressor 10, and the control pressure of the control pressure chamber 46 can be reduced. Accordingly, the piston compressor 10 can be started in a state where the flow rate of the refrigerant gas discharged from the 1 st compression chambers 53a, 53b, 53c, 53d, 53e and the 2 nd compression chambers 54a, 54b, 54c, 54d, 54e to the 1 st discharge chamber 36 and the 2 nd discharge chamber 42 is minimized, and therefore, the starting shock can be reduced.

In the embodiment, the control valve 89 may be a three-way valve whose opening degree can be adjusted in both the suction passage and the supply passage.

In the embodiment, the number of cylinder bores may be appropriately changed.

In the embodiment, the inside diameters of the 1 st cylinder bores 20a, 20b, 20c, 20d, 20e and the inside diameters of the 2 nd cylinder bores 28a, 28b, 28c, 28d, 28e may be different.

In the embodiment, for example, the suction port 22 and the discharge port 24 may be formed in the 2 nd cylinder 13.

In the embodiment, the 1 st radial passage 58 may be formed to penetrate the drive shaft 47 in the radial direction.

In the embodiment, the shape of the 2 nd radial path 59 may be changed as appropriate.

In the embodiment, the piston compressor 10 may be, for example, a single-head piston compressor in which the 1 st compression chambers 53a, 53b, 53c, 53d, and 53e are omitted.

In the embodiment, the piston compressor 10 may be configured such that the pulley and the electromagnetic clutch are not connected to the drive shaft 47, and the drive shaft 47 is connected to the engine of the vehicle via a normal power transmission type clutch-free mechanism.

In the embodiment, the object to be mounted of the piston compressor 10 is not limited to the vehicle, and may be any object. Therefore, the piston compressor 10 can be used for an air conditioner other than a vehicle.

Claims (3)

1. A piston compressor is provided with:

A housing having a cylinder block formed with a plurality of cylinder bores, and formed with a suction chamber, a discharge chamber, a swash plate chamber, and a shaft hole;

a drive shaft rotatably supported in the shaft hole;

a fixed swash plate rotatable in the swash plate chamber by rotation of the drive shaft, the fixed swash plate having a certain inclination angle with respect to a plane perpendicular to the drive shaft;

a piston that forms a compression chamber in each of the cylinder bores and is connected to the fixed swash plate;

a discharge valve for discharging the refrigerant in the compression chamber to the discharge chamber;

a moving body provided on the drive shaft, integrally rotatable with the drive shaft, and movable relative to the drive shaft in an axial direction of the drive shaft based on a control pressure; and

a control valve configured to control the control pressure,

a 1 st communication passage communicating with the cylinder bore is formed in the cylinder block,

forming a 2 nd communication path intermittently communicating with the 1 st communication path in association with rotation of the drive shaft in the moving body,

the piston compressor is configured to change a flow rate of the refrigerant discharged from the compression chamber to the discharge chamber according to a position of the movable body in the axial direction,

The drive shaft has: an axial passage extending in an axial direction of the drive shaft in the drive shaft and communicating with the suction chamber; and a guide window that communicates with the axial passage and that opens on an outer peripheral surface of a portion of the drive shaft that is located in the shaft hole, and that guides the movable body in the axial direction,

the 1 st communication path and the 2 nd communication path are communicated with each other by the moving body,

the 1 st communication path and the 2 nd communication path are not communicated with each other by the drive shaft,

the moving body has:

a 1 st moving body that is located in the axial passage and moves in the axial direction in the axial passage based on the control pressure; and

a 2 nd movable body portion disposed in the guide window in a state of being engaged with the 1 st movable body portion and having a curved plate shape extending along an inner peripheral surface of the shaft hole, and formed in a state of being penetrated by the 2 nd communication passage,

the 1 st moving body part is provided with an engaging part exposed from the guide window,

the 2 nd moving body part is provided with a clamped part clamped with the clamping part,

the engaged portion is plate-shaped protruding from an inner peripheral edge of the 2 nd communication path in the 2 nd moving body portion and bent toward an inside of the guide window.

2. The piston compressor of claim 1,

the 2 nd movable body part has a 1 st curved part and a 2 nd curved part which are curved plate-like and respectively form two edge parts of the 2 nd communication path which are positioned at two sides of the axial direction,

the edge portion of the 2 nd communication path formed by the 1 st bent portion extends in a direction perpendicular to the axial direction when the 2 nd communication path is viewed in plan,

the edge portion of the 2 nd communication path formed by the 2 nd bent portion extends in a direction oblique to the axial direction when the 2 nd communication path is viewed in plan,

the engaged portion protrudes from an edge portion of the 2 nd communication path formed by the 1 st bent portion.

3. The piston compressor of claim 2,

the engaged portion protrudes from a central portion in a circumferential direction of the 2 nd moving body portion at an edge portion of the 2 nd communication path formed at the 1 st bent portion.

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