KR102244423B1 - Piston compressor - Google Patents

Abstract

(Task) Based on the control pressure, the moving object moves in the direction of the drive shaft center, thereby changing the communication angle around the drive shaft center where the first communication path and the second communication path communicate. It provides a piston type compressor that is changeable and can be miniaturized.
(Solution means) The compressor of the present invention includes a housing 1, a drive shaft 3, a fixed swash plate 5, a piston 7, a valve forming plate 9a as a discharge valve, and a control valve 13 ) And a moving body 10. In the drive shaft 3, the control pressure chamber 27 is formed in which the inside becomes the control pressure by being partitioned by the drive shaft 3 and the moving body 10 and connected to the control valve 13 through the control passage 13c. Has been.

Description

Piston compressor {PISTON COMPRESSOR}

The present invention relates to a piston type compressor.

Patent Document 1 discloses a conventional piston type compressor (hereinafter simply referred to as a compressor). This compressor includes a housing, a drive shaft, a fixed swash plate, a plurality of pistons, a discharge valve, and a control valve.

The housing has a cylinder block. In the cylinder block, a plurality of cylinder bores are formed, and a first communication path for communicating with the cylinder bores is formed. In addition, a suction chamber, a discharge chamber, a swash plate chamber, and a shaft hole are formed in the housing.

The drive shaft is rotatably supported in the shaft hole. The fixed swash plate is rotatable in the swash plate chamber by rotation of the drive shaft, and the inclination angle with respect to the plane perpendicular to the drive shaft is constant. The piston forms a compression chamber in the cylinder bore and is connected to the fixed swash plate. A reed valve type discharge valve for discharging the refrigerant in the compression chamber to the discharge chamber is formed between the compression chamber and the discharge chamber.

Further, in this compressor, a control pressure chamber is formed in the housing at a position between the suction chamber and the discharge chamber. In the control pressure chamber, the control valve controls the pressure of the refrigerant, so that the internal pressure becomes the control pressure. In the control pressure chamber, a control piston is formed.

And, in this compressor, a moving body is formed in a drive shaft. The moving body can rotate integrally with the drive shaft in the shaft hole. Further, the moving body is in contact with the control piston while the moving body is formed on the drive shaft. Accordingly, in this compressor, the moving body can be moved in the direction of the drive shaft center with respect to the drive shaft based on the control pressure. More specifically, by moving the control piston in the control pressure chamber based on the control pressure, the moving body can move in the direction of the drive shaft center with respect to the drive shaft. The moving body is provided with a second communication path communicating with the suction chamber. The second communication path is formed so that the communication angle around the drive shaft center with the first communication path per rotation of the drive shaft changes according to the position of the moving body in the drive shaft center direction.

In this compressor, the first communication path and the second communication path communicate, so that the refrigerant in the suction chamber is sucked into the compression chamber through the second communication path and the first communication path. At this time, the communication angle of the second communication path and the first communication path around the drive shaft center changes according to the position of the moving body in the direction of the driving axis, so that the flow rate of the refrigerant sucked into the compression chamber changes. In this way, in this compressor, it is possible to change the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber.

Japanese Published Patent Publication No. Hei 7-119631

By the way, in order to improve the mountability to a vehicle or the like, miniaturization is required for the compressor. In this regard, in the conventional compressor, not only a discharge chamber and a suction chamber, but also a control pressure chamber are formed in the housing. For this reason, since it is necessary to secure a space for forming the control pressure chamber in the housing, it is inevitable to increase the size of the housing. Accordingly, in this compressor, it is difficult to downsize.

The present invention has been made in view of the above-described conventional circumstances, and a piston type capable of changing the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber by moving the moving object in the direction of the drive shaft center based on the control pressure, and realizing miniaturization. It is a problem to be solved to provide a compressor.

It has a cylinder block in which a plurality of cylinder bores are formed, a suction chamber, a discharge chamber, a swash plate chamber, a housing in which shaft holes are formed,

A drive shaft rotatably supported in the shaft hole,

A fixed swash plate that is rotatable within the swash plate chamber by rotation of the drive shaft and has a constant inclination angle with respect to a plane perpendicular to the drive shaft,

A piston forming a compression chamber in the cylinder bore and connected to the fixed swash plate,

A discharge valve for discharging the refrigerant in the compression chamber to the discharge chamber,

A moving body formed on the drive shaft, integrally rotating with the drive shaft, and movable with respect to the drive shaft in a direction of a drive shaft center based on a control pressure,

And a control valve for controlling the control pressure,

In the cylinder block, a first communication path communicating with the cylinder bore is formed,

The moving body is provided with a second communication path intermittently communicating with the first communication path along with the rotation of the drive shaft,

As a piston type compressor in which the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber changes according to a position of the moving body in the direction of the drive shaft,

In the drive shaft, a control pressure chamber is formed in which the inside of the drive shaft becomes the control pressure by being partitioned by the drive shaft and the moving body and connected to the control valve through a control passage.

In the compressor of the present invention, the moving body moves in the direction of the drive shaft center based on the control pressure. Accordingly, in this compressor, the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber changes.

Here, in this compressor, the control pressure chamber is formed in the drive shaft by being partitioned by the drive shaft and the moving body. For this reason, in this compressor, the space for forming the control pressure chamber becomes unnecessary for the housing, and the housing can be downsized.

Accordingly, according to the compressor of the present invention, the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber can be changed by moving the moving object in the direction of the drive shaft center based on the control pressure, and further miniaturization can be realized.

In particular, in the compressor of the present invention, the control pressure chamber can be downsized by forming the control pressure chamber in the drive shaft. Accordingly, while reducing the flow rate of the refrigerant used as the control pressure by the control valve, the moving body can be suitably moved in the direction of the drive shaft center by the control pressure. For this reason, in this compressor, controllability can be made high.

The control passage includes an annular groove formed in an annular shape on the inner circumferential surface of the shaft hole or the outer circumferential surface of the drive shaft, a connection path formed in the housing and connecting the control valve and the annular groove, and an annular groove formed on the drive shaft and extending in the radial direction of the drive shaft It is desirable to have a path that communicates with the control pressure chamber. In this case, even if the drive shaft rotates, since the control pressure chamber and the control valve can always be connected by the control passage, the control pressure in the control pressure chamber can be suitably adjusted.

In the compressor of the present invention, in the drive shaft and in the moving body, a communication chamber that is partitioned from the control pressure chamber and communicates with the suction chamber and the second communication path may be formed. In addition, the first communication path and the second communication path may be communicated by the moving body. Further, it is preferable that the first communication path and the second communication path are not communicated with each other by the drive shaft.

In this case, the moving body communicates the first communication path and the second communication path, so that the refrigerant in the suction chamber can be sucked into the compression chamber through the communication chamber and the first and second communication paths. At this time, the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber by changing the flow rate of the refrigerant sucked into the compression chamber or discharging a part of the refrigerant sucked into the compression chamber into the communication chamber according to the position in the direction of the driving axis of the moving body Can change.

Further, the compressor of the present invention may further include a suction valve that sucks the refrigerant in the suction chamber into the compression chamber. The compression chamber in the compression stroke or the discharge stroke may be a first specific compression chamber. Further, the compression chamber in the re-expansion stroke or the suction stroke may be a second specific compression chamber. And, the second communication path communicates with the first communication path that communicates with the first specific compression chamber and the first communication path that communicates with the second specific compression chamber. It is also desirable to introduce a refrigerant into it.

In this case, it becomes possible to change the flow rate of the refrigerant introduced into the second specific compression chamber from the inside of the first specific compression chamber according to the position of the moving body in the direction of the drive shaft center. Accordingly, since the flow rate of the refrigerant sucked from the suction chamber to the second specific compression chamber through the suction valve changes, the flow rate of the refrigerant discharged from the first specific compression chamber to the discharge chamber can also be changed in this compressor.

According to the compressor of the present invention, the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber can be changed by moving the moving object in the direction of the drive shaft center based on the control pressure, and further miniaturization can be realized.

1 is a cross-sectional view of a piston type compressor of Example 1 at a maximum flow rate.
Fig. 2 is a cross-sectional view of the piston type compressor of Example 1 at a minimum flow rate.
3 is an exploded view showing a drive shaft, a moving body, and the like, relating to the piston-type compressor of the first embodiment.
4 is a cross-sectional view showing a cap, relating to the piston type compressor of Example 1. FIG.
5 is a cross-sectional view showing a cross section CC of FIG. 4 relating to the piston type compressor of Example 1. FIG.
Fig. 6 is a rear view of the piston type compressor of the first embodiment, as viewed from the rear side of the compressor.
Fig. 7 is a rear view of the piston type compressor according to the first embodiment, as viewed from the rear side of the compressor.
Fig. 8 is an enlarged cross-sectional view of a main part showing a drive shaft, a moving body, and the like at a maximum flow rate, relating to the piston type compressor of the first embodiment.
Fig. 9 is an enlarged cross-sectional view of a main part showing a drive shaft, a moving body, and the like at a minimum flow rate, relating to the piston type compressor of the first embodiment.
Fig. 10 is an enlarged cross-sectional view of a main part showing a cross section AA of Fig. 1 relating to the piston type compressor of the first embodiment.
Fig. 11 is an enlarged cross-sectional view of an essential part similar to Fig. 10 showing a state in which the moving object has moved forward rather than the position shown in Fig. 1, relating to the piston type compressor of the first embodiment.
Fig. 12 is an enlarged cross-sectional view of a main part showing a section taken along BB in Fig. 2, relating to the piston type compressor of the first embodiment.
13 is a cross-sectional view of the piston-type compressor of Example 2 at a maximum flow rate.
14 is a cross-sectional view of the piston-type compressor of Example 2 at a minimum flow rate.
Fig. 15 is an enlarged cross-sectional view of a main part showing a drive shaft, a moving body, and the like at a maximum flow rate, relating to the piston type compressor of the second embodiment.
Fig. 16 is an enlarged cross-sectional view of a main part, which relates to the piston type compressor of Example 2, showing a drive shaft, a moving body, and the like at a minimum flow rate.
Fig. 17 is an enlarged cross-sectional view of a main part showing a DD cross section of Fig. 13 relating to the piston type compressor of the second embodiment.
Fig. 18 is an enlarged cross-sectional view of an essential part similar to Fig. 17 showing a state in which the moving object has moved rearward than the position shown in Fig. 13, relating to the piston type compressor of the second embodiment.
Fig. 19 is an enlarged cross-sectional view of a main part showing the EE cross section of Fig. 14 relating to the piston type compressor of the second embodiment.

(Form for carrying out the invention)

Hereinafter, Examples 1 and 2 in which the present invention is embodied will be described with reference to the drawings. These compressors are single-headed piston compressors. These compressors are mounted on a vehicle and constitute a refrigeration circuit of an air conditioner.

(Example 1)

1 and 2, the compressor of the embodiment includes a housing 1, a drive shaft 3, a fixed swash plate 5, a plurality of pistons 7, a valve forming plate 9a, and A moving body 10 and a control valve 13 are provided. The valve forming plate 9a is an example of the "discharge valve" of the present invention.

The housing 1 has a front housing 17, a rear housing 19, and a cylinder block 21. In this embodiment, the side where the front housing 17 is located is the front side of the compressor, and the side where the rear housing 19 is located is the rear side of the compressor, and the front-rear direction of the compressor is defined. In addition, the upper and lower directions of the compressor are defined with the upper side of the paper in Figs. 1 and 2 as the upper side of the compressor, and the lower side of the paper as the lower side of the compressor. In addition, after FIG. 3, in correspondence with FIGS. 1 and 2, the front-rear direction and the up-down direction are displayed. In addition, the front-rear direction and the like in the embodiment is an example, and the posture of the compressor of the present invention is appropriately changed corresponding to the vehicle to be mounted.

The front housing 17 is integrally formed with the front wall 17a extending in the radial direction and the front wall 17a, and extends rearward from the front wall 17a in the direction of the drive shaft center O of the drive shaft 3 It has a circumferential wall 17b to be formed, and has a substantially cylindrical shape. The drive shaft center O extends parallel to the front-rear direction of the compressor.

A first boss portion 171, a second boss portion 172, and a first shaft hole 173 are formed in the front wall 17a. The first boss portion 171 protrudes toward the front in the direction of the drive shaft center O. A shaft sealing device 25 is formed in the first boss portion 171. The second boss portion 172 protrudes rearward in the direction of the drive shaft center O in the swash plate chamber 31 to be described later. The first shaft hole 173 penetrates the front wall 17a in the direction of the drive shaft center O.

In the rear housing 19, a suction chamber 28, a suction port 28a, a discharge chamber 29, and a discharge port 29a are formed. The suction chamber 28 is located on the center side of the rear housing 19. The suction port 28a communicates with the suction chamber 28, extends in the axial direction of the rear housing 19, and opens to the outside of the rear housing 19. The suction port 28a is connected to the evaporator through a pipe. Accordingly, the suction chamber 28 has a suction pressure by being sucked through the suction port 28a of the low-pressure refrigerant gas that has passed through the evaporator. The discharge chamber 29 is formed in an annular shape and is located on the outer peripheral side of the suction chamber 28. The discharge port 29a communicates with the discharge chamber 29, extends in the radial direction of the rear housing 19, and opens to the outside of the rear housing 19. The discharge port 29a is connected to the condenser through a pipe. The shapes of the suction port 28a and the discharge port 29a can be appropriately designed. In addition, illustration of piping, evaporator and condenser is omitted.

The cylinder block 21 is located between the front housing 17 and the rear housing 19. As shown in Figs. 10 to 12, cylinder bores 21a to 21f are formed in the cylinder block 21. The cylinder bores 21a to 21f are arranged at equiangular intervals in the circumferential direction, respectively. As shown in Figs. 1 and 2, the cylinder bores 21a to 21f extend in the direction of the drive shaft center O, respectively. Further, the number of cylinder bores 21a to 21f can be appropriately designed.

The cylinder block 21 is joined to the front housing 17 to form a swash plate chamber 31 between the front wall 17a and the circumferential wall 17b of the front housing 17. The swash plate chamber 31 communicates with the suction chamber 28 through a communication passage (not shown).

In addition, the second shaft hole 23 is formed in the cylinder block 21. The first shaft hole 173 and the second shaft hole 23 are examples of the "shaft hole" of the present invention. The 2nd shaft hole 23 is located on the center side of the cylinder block 21, and penetrates the cylinder block 21 in the drive shaft center (O) direction. The rear side of the second shaft hole 23 is located in the suction chamber 28 by joining the cylinder block 21 to the rear housing 19 via the valve forming plate 9a. Accordingly, the second shaft hole 23 communicates with the suction chamber 28.

On the other hand, an annular groove 24 is formed on the front side of the second shaft hole 23. The annular groove 24 is formed to be concave in an annular shape in the second shaft hole 23 and faces the inner peripheral surface of the second shaft hole 23. The annular groove 24 is connected to the connection path 26. The connection path 26 extends from the cylinder block 21 to the rear housing 19 in the direction of the drive shaft center O.

In addition, as shown in Figs. 10 to 12, the cylinder block 21 is provided with first communication paths 22a to 22f. One end side of the first communication paths 22a to 22f communicates with the cylinder bores 21a to 21f, respectively. The first communication paths 22a to 22f extend in the radial direction of the cylinder block 21, respectively. Accordingly, the other end side of the first communication paths 22a to 22f communicates with the second shaft hole 23.

1 and 2, the valve forming plate 9a is formed between the rear housing 19 and the cylinder block 21. The rear housing 19 and the cylinder block 21 are joined via this valve forming plate 9a.

The valve forming plate 9a has a valve plate 90, a discharge valve plate 92, and a retainer plate 93. The valve plate 90 is formed with six discharge holes 911 communicating with the cylinder bores 21a to 21f. The cylinder bores 21a to 21f communicate with the discharge chamber 29 through each discharge hole 911.

The discharge valve plate 92 is formed on the rear surface of the valve plate 90. The discharge valve plate 92 is formed with six discharge reed valves 92a capable of opening and closing each discharge hole 911 by elastic deformation. The retainer plate 93 is formed on the rear surface of the discharge valve plate 92. The retainer plate 93 regulates the maximum opening degree of the discharge reed valve 92a.

The drive shaft 3 is composed of a drive shaft main body 33 and a cap 35, and extends from the front side of the housing 1 toward the rear side in the drive shaft center O direction. The drive shaft main body 33 constitutes a front portion of the drive shaft 3. The drive shaft main body 33 has a screw portion 33a, a first diameter portion 33b, and a second diameter portion 33c. The screw portion 33a is located at the front end of the drive shaft main body 33, that is, at the front end of the drive shaft 3. Through this threaded portion 33a, the drive shaft 3 is connected to a pulley, an electromagnetic clutch, or the like (not shown). The first diameter portion 33b is continuous with the rear end of the threaded portion 33a and extends in the direction of the drive shaft center O.

The second diameter portion 33c is continuous with the rear end of the first diameter portion 33b and extends in the direction of the drive shaft center O. The second diameter portion 33c is formed to have a smaller diameter than the first diameter portion 33b. As shown in FIG. 3, the 1st shaft path 33d is formed in the 2nd diameter part 33c. The first shaft path 33d extends in the direction of the drive shaft center O in the second diameter part 33c, and opens to the rear end surface of the second diameter part 33c, that is, the rear end surface of the drive shaft main body 33. I'm doing it. Moreover, a 1st path 33e is formed in the 2nd diameter part 33c. As shown in Figs. 8 and 9, the first path 33e extends radially inside the second diameter portion 33c while communicating with the first shaft path 33d, and the second diameter portion 33c It is open to the outer peripheral surface of ).

1 and 2, the cap 35 constitutes a rear portion of the drive shaft 3. As shown in Figs. 1 to 5, the cap 35 has a cylindrical shape having substantially the same diameter as the second shaft hole 23, and extends in the direction of the drive shaft center O. 4 and 5, a guide window 35a is formed in the cap 35. The guide window 35a is formed over a half circumference of the cap 35 in the circumferential direction, and extends in the direction of the drive shaft center O. On the other hand, in the cap 35, a portion located on the opposite side of the guide window 35a with the drive shaft center O interposed therebetween is a body portion 35b. The main body 35b has a semicircular trough shape extending in the direction of the drive shaft center O facing the guide window 35a.

In addition, as shown in Fig. 4, the portion of the cap 35 that faces the guide window 35a in the rearward direction is the first regulation surface 301, and the portion of the cap 35 that faces the guide window 35a in the front direction is The portion facing is the second regulation surface 302. In addition, as shown in FIG. 3, in the cap 35, it is located between the first regulation surface 301 and the second regulation surface 302, and faces the guide window 35a, in the direction of the drive shaft center O. In the portion extending in the direction, that is, in the main body portion 35b, a cross section serving as the leading side when the drive shaft 3 rotates in the direction R1 to be described later is a guide surface 303.

In the cap 35, a second shaft path 35c is formed. The second shaft path 35c extends in the direction of the drive shaft center O and penetrates the cap 35 back and forth. The 2nd shaft path 35c is comprised by the 1st diameter part 351, the 2nd diameter part 352, and the 3rd diameter part 353. The first diameter portion 351, the second diameter portion 352, and the third diameter portion 353 are coaxial with each other.

The first diameter portion 351 is formed to have substantially the same diameter as the second diameter portion 33c of the drive shaft main body 33. The first diameter portion 351 is opened to the front end surface of the cap 35 and extends toward the rear. The second diameter portion 352 is connected to the rear end of the first diameter portion 351 and extends toward the rear. The second diameter portion 352 is substantially the same diameter as the first shaft path 33d shown in FIG. 3, and is formed to have a smaller diameter than the first diameter portion 351. Accordingly, between the first diameter portion 351 and the second diameter portion 352, a first end portion 354 shown in FIG. 4 is formed. Moreover, the 1st diameter part 351 and the 2nd diameter part 352 are in communication with the guide window 35a. Accordingly, the first and second diameter portions 351 and 352 communicate with the outside of the cap 35 at a location communicating with the guide window 35a. The third diameter portion 353 is connected to the rear end of the second diameter portion 352 and extends toward the rear, and opens to the rear end surface of the cap 35. The third diameter portion 353 is formed to have a smaller diameter than the second diameter portion 352. Accordingly, a second end portion 355 is formed between the second diameter portion 352 and the third diameter portion 353.

Further, on the front end side of the cap 35, a first annular recess 356 and a second annular recess 357 are formed. A first seal ring 358 is formed in the first annular concave groove 356, and a second seal ring 359 is formed in the second annular concave groove 357. The first and second seal rings 358 and 359 are made of a resin such as PTFE. In addition, on the front end side of the cap 35, between the first annular recess 356 and the second annular recess 357, that is, between the first seal ring 358 and the second seal ring 359. A second path 35d is formed at a position between them. The second path 35d extends in the radial direction inside the cap 35 while communicating with the first diameter portion 351, and opens to the outer peripheral surface of the cap 35.

8 and 9, the second diameter portion 33c of the drive shaft main body 33 is press-fitted into the cap 35. More specifically, the rear end side of the second diameter portion 33c is press-fit into the first diameter portion 351 of the second shaft path 35c. Then, the second diameter portion 33c is positioned within the first diameter portion 351 by the rear end of the second diameter portion 33c abutting the first end portion 354. At this time, the first path 33e and the second path 35d are matched and communicated. These 1st path 33e and 2nd path 35d are an example of the "path" of this invention. In this way, the drive shaft main body 33 and the cap 35 are integrated to form the drive shaft 3.

As shown in FIGS. 1 and 2, the drive shaft 3 carries the first diameter portion 33b of the drive shaft main body 33 to the first shaft hole 173, and the cap 35 is formed as a second shaft hole. It is inserted through the housing 1 so as to be rotatable by placing it on (23). Accordingly, the drive shaft 3 is rotatable around the drive shaft center O. More specifically, in this embodiment, the drive shaft 3 rotates in the R1 direction shown in FIGS. 10 to 12. Therefore, it can be said that the first path 33e and the second path 35d are formed on the drive shaft 3.

Here, as the cap 35 is supported by the second shaft hole 23, as shown in Figs. 8 and 9, the annular groove 24, the second path 35d, and the first path 33e face each other. . Accordingly, the annular groove 24 and the first shaft 33d communicate with each other through the first and second paths 33e and 35d. Then, the space between the inside of the second shaft hole 23 and the annular groove 24 is sealed by the first and second seal rings 358 and 359. In addition, since the cap 35 is supported by the second shaft hole 23, the rear end of the cap 35 protrudes from the second shaft hole 23 and extends into the suction chamber 28. Accordingly, the second shaft path 35c is connected to the suction chamber 28 through the third diameter portion 353. On the other hand, as shown in FIGS. 1 and 2, the drive shaft 3 is inserted through the shaft sealing device 25 in the first boss portion 171. Accordingly, the shaft sealing device 25 seals between the inside of the housing 1 and the outside of the housing 1.

In addition, since the cap 35 is supported by the second shaft hole 23, as shown in Figs. 10 to 12, the guide window 35a is re-expansion or suction in the first communication paths 22a to 22f. It faces the first communication paths 22a to 22f communicating with the stroke compression chambers 45a to 45f. On the other hand, the main body 35b faces the first communication paths 22a to 22f communicating with the compression chambers 45a to 45f in the compression stroke or the discharge stroke.

1 and 2, the fixed swash plate 5 is fixed to the drive shaft 3 by being pressed into the second diameter portion 33c of the drive shaft main body 33. At this time, the fixed swash plate 5 abuts against an end portion 33f formed between the second diameter portion 33c and the first diameter portion 33b, thereby being positioned relative to the drive shaft main body 33. In this way, the fixed swash plate 5 is arranged in the swash plate chamber 31, and by rotating the drive shaft 3, it is rotatable together with the drive shaft 3 in the swash plate chamber 31. Here, the fixed swash plate 5 has a constant inclination angle with respect to the plane perpendicular to the drive shaft 3. In addition, in the swash plate chamber 31, a thrust bearing 6 is formed between the second boss portion 172 and the fixed swash plate 5.

Each piston 7 is accommodated in the cylinder bore 21a-21f, respectively. Compression chambers 45a to 45f are respectively formed in cylinder bores 21a to 21f by the respective pistons 7 and valve forming plates 9a, as shown in Figs. 10 to 12. The compression chambers 45a to 45f communicate with the first communication paths 22a to 22f, respectively.

1 and 2, each piston 7 is provided with an engaging portion 7a. In the engaging portion 7a, hemispherical shoes 8a and 8b are formed, respectively. By these shoes 8a and 8b, the piston 7 is connected to the fixed swash plate 5. Accordingly, each of the shoes 8a and 8b functions as a conversion mechanism that converts the rotation of the fixed swash plate 5 into a reciprocating motion of the piston 7. For this reason, the piston 7 can reciprocate the inside of the cylinder bore 21a-21f between the top dead center of the piston 7 and the bottom dead center of the piston 7, respectively. Hereinafter, the top dead center of the piston 7 and the bottom dead center of the piston 7 will be described as the top dead center and the bottom dead center, respectively.

As shown in FIG. 3, the movable body 10 is constituted by the first movable body 11 and the second movable body 12. The first moving body 11 has a circumferential wall portion 11a and a standing wall portion 11b. 6 and 10 to 12, the circumferential wall portion 11a is formed in a semicircular trough shape having a substantially the same diameter as the cap 35, and slides with the front surface 111 and the rear surface 112 It has a face 113. The sliding surface 113 is connected to the front surface 111 and the back surface 112. Further, as shown in Figs. 8 and 9, the peripheral wall portion 11a extends in the direction of the drive shaft center O. Here, the length in the direction of the drive shaft center O in the peripheral wall portion 11a is set to be shorter than the length in the direction of the drive shaft center O in the guide window 35a. In addition, a second communication path 41 is formed in the peripheral wall portion 11a.

The second communication path 41 penetrates from the front surface 111 to the rear surface 112. Further, as shown in Figs. 1 to 3, the second communication path 41 is formed so as to extend in the front-rear direction in the circumferential wall portion 11a. Further, the second communication path 41 is gradually formed larger in the circumferential direction of the circumferential wall portion 11a as it goes from the rear end to the front end. That is, the first portion 411 formed small in the circumferential direction of the circumferential wall portion 11a is located at the rear end side of the second communication path 41, and the second portion 412 formed large in the circumferential direction of the circumferential wall portion 11a ) Is located on the front end side of the second communication path 41. In addition, the shape of the second communication path 41 can be appropriately designed.

As shown in Figs. 8 and 9, the upright wall portion 11b is integrally formed with the rear surface 112 of the circumferential wall portion 11a. The upright wall portion 11b is disposed on the rear side of the first moving body 11 and has a plate shape extending vertically and perpendicular to the drive shaft center O direction. As shown in FIG. 6, the notch 114 which forms a semicircular shape is formed in the upright wall part 11b. In addition, the shape of the cutout 114 can be appropriately designed, and the formation of the cutout 114 may be omitted.

As shown in Figs. 3 and 7 to 9, the second moving body 12 is a substantially cylinder having the same diameter as the second diameter portion 352 of the first shaft path 33d and the second shaft path 35c. It is formed in a shape. At the rear end of the second moving body 12, an engaging portion 12a forming a planar shape is formed. In addition, a communication path 12b is formed in the second moving body 12. The communication path 12b extends in the direction of the drive shaft center O in the second moving body 12 and opens to the rear end of the second moving body 12. In addition, the engaging portion 12a side in the communication path 12b is open to the outer peripheral surface of the second moving body 12. Here, as shown in Figs. 8 and 9, the communication path 12b does not penetrate the inside of the second moving body 12 in the direction of the drive shaft center O, but at the front end of the second moving body 12 It is not open. Accordingly, a first surface 121 and a second surface 122 forming a planar shape are formed on the second moving body 12. The first surface 121 constitutes a front end surface of the second movable body 12 and is facing forward. The second surface 122 is located in front of the communication path 12b and faces the rear. Further, the engaging portion 12a can be appropriately designed in shape as long as it can engage with the upright wall portion 11b.

Further, in the second movable body 12, a ring groove 12c is formed between the first surface 121 and the second surface 122, that is, at a location on the front side of the communication path 12b. . An O-ring 37 is formed in the ring groove 12c.

The second moving body 12 is provided with the cap 35 in a state in which the engaging portion 12a is directed toward the guide window 35a, that is, the communication path 12b is opposed to the guide window 35a. It is arranged in the 2 diameter part 352. In addition, in the cap 35, the 2nd moving body 12 is letting the front end side into the 1st shaft path 33d. Accordingly, in the first shaft path 33d, that is, in the drive shaft 3, a control pressure chamber 27 partitioned by the drive shaft main body 33 and the second moving body 12 is formed. The control pressure chamber 27 communicates with the annular groove 24 through the first path 33e and the second path 35d. A second air supply passage 13c serving as a control passage is formed by the connection passage 26, the annular groove 24, and the first and second passages 33e and 35d. Further, between the control pressure chamber 27 and the second diameter portion 352 is sealed with an O-ring 37.

Here, since the annular groove 24 is formed concave in a circular annular shape in the second shaft hole 23, even if the drive shaft 3 rotates, the annular groove 24 and the second path 35d and the first path (33e) always faces. For this reason, even if the drive shaft 3 rotates, the annular groove 24 and the first shaft path 33d, furthermore, the annular groove 24 and the control pressure chamber 27 are always in communication.

In addition, in the cap 35, that is, in the drive shaft 3, a communication chamber 39 is formed by a communication path 12b, a second diameter portion 352, and a third diameter portion 353. The communication chamber 39 is partitioned from the control pressure chamber 27 by the second moving body 12. That is, the communication chamber 39 and the control pressure chamber 27 are not in communication. On the other hand, the communication chamber 39 communicates with the suction chamber 28. Accordingly, the communication chamber 39 is at a suction pressure.

The first moving body 11 is formed in the guide window 35a in a state where the upright wall portion 11b is brought into the cap 35. And the 1st moving body 11 makes the sliding surface 113 abut against the guide surface 303 of the cap 35. Accordingly, the circumferential wall portion 11a of the first moving body 11 is located on the opposite side of the main body portion 35b of the cap 35 with the driving shaft O interposed therebetween, and is exposed into the second shaft hole 23. . Here, the circumferential wall portion 11a is formed in a semicircular trough shape having substantially the same diameter as the cap 35, so that the first moving body 11 is formed in the guide window 35a, so that the main body portion 35b Together with the second shaft hole (23) and constitutes a cylindrical body that forms almost the same diameter. Accordingly, the first moving body 11 matches the second shaft hole 23 together with the body portion 35b by the cap 35 being disposed in the second shaft hole 23.

Moreover, the 1st moving body 11 makes the upright wall part 11b abut against the engaging part 12a of the 2nd moving body 12 in the state formed in the guide window 35a. Accordingly, the first moving body 11 and the second moving body 12 are attached by engaging the upright wall portion 11b and the engaging portion 12a. In this way, the communication chamber 39 communicates with the second communication path 41 while facing the second communication path 41. That is, the communication chamber 39 communicates with the suction chamber 28 and the second communication path 41.

The moving body 10 is rotatable around the drive shaft center O together with the drive shaft 3 by rotating the cap 35 and further, the drive shaft 3 around the drive shaft center O. Here, by engaging the upright wall portion 11b and the engaging portion 12a, the second moving body 12 is in the first shaft path 33d and in the second diameter portion 352, the first moving body ( Independently from 11), rotation around the drive shaft center O is regulated.

In addition, in the movable body 10, suction pressure acts on the upright wall portion 11b of the first movable body 11 and the second surface 122 of the second movable body 12. On the other hand, the control pressure acts on the first surface 121 of the second moving body 12. In addition, the control pressure will be described later.

Then, by engaging the upright wall portion 11b and the engaging portion 12a, the first moving body 11 and the second moving body 12 can be moved integrally in the direction of the drive shaft center O. Specifically, the first moving body 11 is able to move back and forth in the guide window 35a in the direction of the drive shaft center O by guiding the sliding surface 113 to the guide surface 303. On the other hand, the second moving body 12 is movable back and forth in the drive shaft center O direction by sliding inside the first shaft path 33d and the second diameter portion 352. In this way, the moving body 10 can move back and forth in the direction of the drive shaft center O with respect to the drive shaft 3 in the shaft hole 23.

Further, the second communication path 41 intermittently communicates with the first communication paths 22a to 22f as shown in Figs. 10 to 12 when the drive shaft 3 rotates. In addition, the second communication path 41 communicates with the first communication paths 22a to 22f per rotation of the drive shaft 3 according to the position of the first moving body 11 in the guide window 35a. The communication angle around the driving shaft center O changes. Hereinafter, the communication angle around the drive shaft center O through which the first communication paths 22a to 22f and the second communication path 41 communicate with each other per rotation of the drive shaft 3 is simply described as a communication angle. In addition, in Figs. 4 to 9, for ease of explanation, in a state in which the drive shaft 3 and the fixed swash plate 5 are rotated around the drive shaft center O than in the state shown in Figs. 1 and 2, the cap ( 35) or the first and second moving bodies 11 and 12 are shown. In addition, in FIGS. 8-12, the shape of the 2nd communication path 41, etc. are simplified and shown in order to facilitate explanation. The same applies to Figs. 15 to 19 described later.

In addition, as shown in Figs. 8 and 9, in the cap 35, between the second end portion 355 and the upright wall portion 11b of the first moving body 11, the elastic support spring 43 is Is formed. The elastic support spring 43 elastically supports the first moving body 11 and the second moving body 12, that is, the moving body 10 toward the front of the cap 35.

1 and 2, the control valve 13 is formed in the rear housing 19. The control valve 13 is connected to the suction chamber 28 through a detection passage 13a formed in the rear housing 19. Further, the control valve 13 is connected to the discharge chamber 29 by a first air supply passage 13b formed in the rear housing 19. Further, the control valve 13 is connected to the control pressure chamber 27 through a connection path 26 and a second air supply passage 13c. A part of the refrigerant gas in the discharge chamber 29 is introduced into the control pressure chamber 27 through the first and second air supply passages 13b and 13c and the control valve 13. In addition, the control pressure chamber 27 is connected to the swash plate chamber 31 by a bleed passage (not shown). Accordingly, the refrigerant gas in the control pressure chamber 27 is led out to the suction chamber 28 through the extraction passage.

The control valve 13 adjusts the valve opening degree by sensing the suction pressure, which is the pressure of the refrigerant gas in the suction chamber 28 through the detection passage 13a. Accordingly, the control valve 13 adjusts the flow rate of the refrigerant gas introduced into the control pressure chamber 27 from the discharge chamber 29 via the first and second air supply passages 13b and 13c. Specifically, the control valve 13 increases the flow rate of the refrigerant gas introduced into the control pressure chamber 27 from the discharge chamber 29 through the first and second air supply passages 13b and 13c by increasing the valve opening degree. Let it. On the other hand, the control valve 13 reduces the flow rate of the refrigerant gas introduced into the control pressure chamber 27 from the discharge chamber 29 via the first and second air supply passages 13b and 13c by reducing the valve opening degree. In this way, the control valve 13 adjusts the flow rate of the refrigerant gas introduced into the control pressure chamber 27 from the discharge chamber 29 with respect to the flow rate of the refrigerant gas guided from the control pressure chamber 27 to the suction chamber 28. By changing, the control pressure, which is the pressure of the refrigerant gas in the control pressure chamber 27, is controlled. Further, the control pressure chamber 27 may be connected to the swash plate chamber 31 through a bleed passage.

In the compressor configured as described above, the fixed swash plate 5 rotates in the swash plate chamber 31 by rotating the drive shaft 3 around the drive shaft center O. Accordingly, the piston 7 reciprocates within the cylinder bore 21a to 21f between the top dead center and the bottom dead center. For this reason, in the compression chambers 45a to 45f, a re-expansion stroke for re-expansion of the refrigerant gas inside, a suction stroke for suctioning refrigerant gas from the suction chamber 28, a compression stroke for compressing the internal refrigerant gas, and compressed The discharge process in which the refrigerant gas is discharged to the discharge chamber 29 is repeatedly performed. The refrigerant gas in the discharge chamber 29 is discharged to the condenser through the discharge port 29a.

Specifically, in this compressor, when the drive shaft 3 is at the rotational angle shown in Figs. 1, 2, and 10 to 12, the compression chamber 45a has an initial stage of the re-expansion stroke or the suction stroke. do. Then, the suction stroke proceeds in the order of the compression chamber 45a, the compression chamber 45b, and the compression chamber 45c. That is, the compression chamber 45b becomes the intermediate stage of the suction stroke. Then, the compression chamber 45c becomes a later stage of the suction stroke, and the piston 7 is located at the bottom dead center. On the other hand, the compression process proceeds in the order of the compression chamber 45d, the compression chamber 45e, and the compression chamber 45f. That is, in the compression chamber 45f, the piston 7 is located at the top dead center in the step of shifting from the later stage of the compression stroke to the discharge stroke.

In this compressor, the first moving body 11 is formed in the guide window 35a, so that the first moving body 11 communicates with the compression chambers 45a to 45f of the re-expansion stroke or the suction stroke. It faces the furnaces 22a to 22f. More specifically, when the drive shaft 3 is at the rotation angle shown in Figs. 1, 2, and 10 to 12, the first moving body 11 is a first communication path communicating with the compression chamber 45a ( 22a), the first communication path 22b communicating with the compression chamber 45b adjacent to the compression chamber 45a, and the first communication communicating with the compression chamber 45c adjacent to the compression chamber 45b It faces the furnace 22c. And, when the drive shaft 3 rotates further in the R1 direction than in the state shown in FIG. 10, since the compression chamber 45f shifts to the initial stage of the re-expansion stroke or the suction stroke, the first moving body 11 is compressed. It faces the first communication path 22f communicating with the chamber 45f, the first communication path 22a communicating with the compression chamber 45a, and the first communication path 22b communicating with the compression chamber 45b. do. In this way, when the drive shaft 3 rotates, the first moving body 11 sequentially faces the first communication paths 22a to 22f communicating with the compression chambers 45a to 45f of the re-expansion stroke or the suction stroke. .

Accordingly, the refrigerant gas in the suction chamber 28 is passed through the communication chamber 39, the second communication path 41, and the first communication paths 22a to 22f in the compression chambers 45a to 45f of the suction stroke. Inhaled.

On the other hand, the main body portion 35b of the cap 35 is located on the opposite side of the guide window 35a, that is, on the opposite side of the first moving body 11 with the drive shaft center O interposed therebetween. For this reason, the main body 35b faces the first communication paths 22a to 22f communicating with the compression chambers 45a to 45f of the compression stroke or the discharge stroke among the first communication paths 22a to 22f. More specifically, when the drive shaft 3 is at the rotation angle shown in Figs. 1, 2, and 10 to 12, the main body 35b is a first communication path 22d communicating with the compression chamber 45d. ), and the first communication path 22e communicating with the compression chamber 45e, and the first communication path 22f communicating with the compression chamber 45f. In this way, the main body 35b sequentially faces the first communication paths 22a to 22f communicating with the compression chambers 45a to 45f in the compression stroke or the discharge stroke when the drive shaft 3 rotates.

And, in this compressor, by moving the moving body 10 relative to the drive shaft 3 in the direction of the drive shaft center O, from the suction chamber 28 to the compression chambers 45a to 45f per rotation of the drive shaft 3 It is possible to change the flow rate of the refrigerant gas to be sucked, and further, the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29.

Specifically, in the case of increasing the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29, the control valve 13 increases the valve opening degree, thereby increasing the control pressure chamber from the discharge chamber 29. The flow rate of the refrigerant gas introduced into (27) is increased. In this way, the control valve 13 increases the control pressure in the control pressure chamber 27. Accordingly, the variable differential pressure, which is the differential pressure between the control pressure and the suction pressure, increases.

For this reason, in the movable body 10, the second movable body 12 resists the elastic support force of the elastic support spring 43, and the inside of the first shaft 33d and the second diameter portion 352 from the position shown in FIG. 9 It starts to move backward in the direction of the drive shaft center (O). Accordingly, the first moving body 11 starts to move rearward in the guide window 35a in the direction of the drive shaft center O. For this reason, the 2nd communication path 41 moves relative to the 1st communication path 22a-22f rearward. In this way, in this compressor, the communication angle gradually increases.

And, as the variable differential pressure becomes maximum, as shown in FIG. 8, in the moving body 10, the first moving body 11 is in a state in which the inside of the guide window 35a is moved to the rearmost position, and the second regulation surface ( 302). Accordingly, the movement of the second moving body 12 to the rear in the first shaft path 33d and in the second diameter portion 352 is also regulated. In this way, the first moving body 11 moves the inside of the guide window 35a to the rearmost, so that in the second communication path 41, the first communication paths 22a to 22f and the second part 412 are You are in a state of communication. Accordingly, in this compressor, the communication angle is maximized.

For this reason, as shown in FIG. 10, the 1st moving body 11 makes the 1st communication paths 22a-22c and the 2nd communication path 41 communicate. That is, the first moving body 11 includes first communication paths 22a to 22f communicating with the compression chambers 45a to 45f at the initial stage of the re-expansion or suction stroke, and the compression at the intermediate stage of the suction stroke. First communication paths 22a to 22f communicating with the chambers 45a to 45f, first communication paths 22a to 22f communicating with the compression chambers 45a to 45f in the later stage of the suction stroke, and a second The communication path 41 is communicated. On the other hand, the main body portion 35b makes the first communication paths 22d to 22f and the second communication paths 41 non-communicating. That is, the main body 35b makes the first communication paths 22a to 22f communicating with the compression chambers 45a to 45f in the compression stroke or the discharge stroke and the second communication path 41 in non-communication.

In this way, when the communication angle is maximized, the compression chambers 45a to 45f have the communication chamber 39, the second communication path 41, and the first communication path between the initial stage and the latter stage of the suction stroke. Refrigerant gas is sucked from the suction chamber 28 through (22a to 22f). For this reason, the flow rate of the refrigerant gas sucked from the suction chamber 28 to the compression chambers 45a to 45f becomes the largest. In this way, in this compressor, the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 is maximized.

On the other hand, in the case of reducing the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29, the control valve 13 reduces the valve opening, thereby reducing the control pressure chamber 27 from the discharge chamber 29. ) To reduce the flow rate of the refrigerant gas introduced into it. In this way, the control valve 13 reduces the control pressure in the control pressure chamber 27. Accordingly, the variable differential pressure is reduced.

For this reason, in the moving body 10, the first and second moving bodies 11 and 12 start to move forward in the direction of the drive shaft center O from the position shown in Fig. 8 by the elastic support force of the elastic support spring 43. do. That is, while the first moving body 11 starts to move forward in the direction of the driving shaft O in the guide window 35a, the second moving body 12 is in the first shaft 33d and the second diameter The inside of the part 352 starts to move forward in the direction of the drive shaft center (O). Accordingly, the second communication path 41 moves forward relative to the first communication paths 22a to 22f. Therefore, in the second communication path 41, in a portion formed smaller in the circumferential direction of the circumferential wall portion 11a of the first moving body 11 than the second portion 412, the first communication passages 22a to 22f It is in a state of communication with. In this way, in this compressor, the communication angle gradually decreases.

In this state, as shown in FIG. 11, the first moving body 11 communicates the first communication paths 22a and 22b and the second communication path 41. That is, the first moving body 11 includes first communication paths 22a to 22f communicating with the compression chambers 45a to 45f at the initial stage of the re-expansion or suction stroke, and the compression at the intermediate stage of the suction stroke. The first communication paths 22a to 22f communicating with the threads 45a to 45f and the second communication path 41 are communicated. In addition, in this case, the main body portion 35b makes the first communication paths 22a to 22f communicating with the compression chambers 45a to 45f in the compression stroke or the discharge stroke, and the second communication path 41 in non-communication. do. Further, in this state, the first circumferential wall portion 11a of the first moving body 11 communicates with the compression chambers 45a to 45f in the later stage of the suction stroke, like the first communication path 22c. The communication paths 22a to 22f and the second communication path 41 become non-communication.

In this way, by decreasing the communication angle, in the compression chambers 45a to 45f, the communication chamber 39, the second communication path 41, and the first communication path ( 22a to 22f), the refrigerant gas is sucked from the suction chamber 28. For this reason, the flow rate of the refrigerant gas sucked from the suction chamber 28 to the compression chambers 45a to 45f is reduced compared to the case where the communication angle is at the maximum. In this way, in this compressor, the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 decreases.

Then, the control valve 13 further reduces the control pressure in the control pressure chamber 27, so that the variable differential pressure is minimized. Accordingly, as shown in FIG. 9, in the movable body 10, the first movable body 11 is in a state in which the inside of the guide window 35a is moved most forward, and comes into contact with the first regulation surface 301. Accordingly, the movement of the second moving body 12 forward in the first shaft path 33d and in the second diameter portion 352 is also regulated. In this way, by moving the first moving body 11 most forward through the guide window 35a, the second communication path 41 is formed with the first communication paths 22a to 22f at the first portion 411. You are in a state of communication. Accordingly, in this compressor, the communication angle is minimized.

For this reason, as shown in FIG. 12, the 1st moving body 11 makes the 1st communication path 22a and the 2nd communication path 41 communicate. That is, the first moving body 11 includes only the first communication paths 22a to 22f communicating with the compression chambers 45a to 45f in the initial stage of the re-expansion or suction stroke, and the second communication path 41 Communicate. Also at this time, the main body portion 35b makes the first communication paths 22a to 22f communicating with the compression chambers 45a to 45f in the compression stroke or the discharge stroke and the second communication path 41 in non-communication. Further, the first communication paths 22b and 22c and the second communication path 41 are not communicated with each other by the circumferential wall portion 11a. That is, the first communication paths 22a to 22f communicating with the compression chambers 45a to 45f in the intermediate stage of the suction stroke by the circumferential wall portion 11a, and the compression chambers 45a to at the later stage of the suction stroke. The first communication paths 22a to 22f communicating with 45f) and the second communication path 41 become non-communicating.

In this way, when the communication angle is minimized, the compression chambers 45a to 45f are only in the initial stage of the suction stroke, the communication chamber 39, the second communication path 41, and the first communication path 22a to Through 22f), the refrigerant gas is sucked from the suction chamber 28. For this reason, the flow rate of the refrigerant gas sucked from the suction chamber 28 to the compression chambers 45a to 45f becomes the smallest. In this way, in this compressor, the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 is minimized.

In this compressor, the control pressure chamber 27 is formed in the drive shaft 3 by being partitioned by the drive shaft main body 33 and the second moving body 12. For this reason, in this compressor, a space for forming the control pressure chamber 27 with respect to the housing 1 including the rear housing 19 is not required. For this reason, it is possible to downsize the housing 1.

Therefore, according to the compressor of Example 1, the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 by moving the moving body 10 in the direction of the drive shaft center O based on the control pressure is reduced. It is changeable and can realize miniaturization.

In particular, in this compressor, by forming the control pressure chamber 27 in the drive shaft 3, the control pressure chamber 27 can be downsized. Accordingly, while reducing the flow rate of the refrigerant gas, which becomes the control pressure by the control valve 13, the second moving body 12 and furthermore the moving body 10 are driven by the variable differential pressure between the control pressure and the suction pressure. It is possible to move appropriately in the O) direction. For this reason, in this compressor, controllability is improved.

In this compressor, the control valve 13 and the control pressure chamber 27 are provided with a second air supply passage 13c, that is, a connection passage 26, an annular groove 24, and the first and second passages 33e and 35d. It is connected through. For this reason, in this compressor, even if the drive shaft 3 rotates, it is possible to connect the control pressure chamber 27 and the control valve 13 at all times. For this reason, in this compressor, it is possible to suitably adjust the control pressure in the control pressure chamber 27.

Further, in this compressor, the space between the inside of the second shaft hole 23 and the annular groove 24 is sealed by the first and second seal rings 358 and 359. For this reason, the refrigerant gas flowing from the annular groove 24 to the control pressure chamber 27 via the second path 35d and the first path 33e is difficult to leak to the outside of the annular groove 24. Also in this respect, in this compressor, it is possible to suitably adjust the control pressure in the control pressure chamber 27.

In addition, in this compressor, inlet control to change the flow rate of the refrigerant gas introduced into the control pressure chamber 27 from the discharge chamber 29 via the first and second air supply passages 13b and 13c is performed by the control valve 13. I'm doing it. For this reason, the control pressure chamber 27 can be quickly brought to high pressure, and the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 can be rapidly increased.

(Example 2)

13 and 14, in the compressor of Example 2, in place of the valve formation plate 9a and the moving body 10 in the compressor of Example 1, the valve formation plate 9b and the moving body 14 ). The valve forming plate 9b is an example of the "discharge valve" and the "intake valve" of the present invention. Like the valve formation plate 9a, the valve formation plate 9b is also formed between the rear housing 19 and the cylinder block 21. Accordingly, also in this compressor, the rear housing 19 and the cylinder block 21 are joined via the valve forming plate 9b.

In addition to the valve plate 90, the discharge valve plate 92, and the retainer plate 93, the valve forming plate 9b has a suction valve plate 91. In the valve formation plate 9b, the valve plate 90 and the intake valve plate 91 are provided with six discharge holes 911 identical to those of the valve formation plate 9a. Further, in the valve plate 90, the discharge valve plate 92, and the retainer plate 93, six suction holes 910 communicating with the cylinder bores 21a to 21f are formed. Accordingly, in this compressor, the cylinder bores 21a to 21f communicate with the suction chamber 28 through each suction hole 910 and communicate with the discharge chamber 29 through each discharge hole 911. do.

The intake valve plate 91 is formed on the front surface of the valve plate 90. In the suction valve plate 91, six suction reed valves 91a capable of opening and closing each suction hole 910 by elastic deformation are formed. The opening degree of each suction reed valve 91a is regulated by the retainer groove 20 formed in the cylinder block 21.

The moving body 14 is composed of a first moving body 11 and a second moving body 16. Here, in this compressor, as compared with the compressor of the first embodiment, the length of the second communication path 41 in the front-rear direction is set to be shorter. In addition, as shown in FIGS. 15 and 16, in this compressor, the notch 114 is not formed with respect to the upright wall 11b of the first moving body 11.

The 2nd moving body 16 is formed in a substantially cylindrical shape which makes up substantially the same diameter as the 2nd diameter part 352 of the 1st shaft path 33d and the 2nd shaft path 35c. That is, the second moving body 16 is rigidly formed, and has a first surface 161 facing the front side and a second surface 162 facing the rear side. Further, at the rear end of the second moving body 16, an engaging portion 16a forming a planar shape is formed. Further, on the front side of the second moving body 16, a ring groove 16b is formed. An O-ring 37 is formed in the ring groove 16b. Moreover, also about the engaging part 16a, as long as it can engage with the upright wall part 11b, the shape can be designed suitably.

Also in this compressor, the 2nd moving body 16 is arrange|positioned in the 2nd diameter part 352 of the cap 35 with the engaging part 16a facing the guide window 35a side. And the 2nd moving body 16 is making the front end side enter into the 1st shaft path 33d. In this way, in this compressor, in the drive shaft 3, the control pressure chamber 27 divided by the drive shaft main body 33 and the second moving body 16 is formed.

Further, in the moving body 14, the first moving body 11 and the second moving body 16 are attached by engaging the upright wall portion 11b and the engaging portion 16a. Accordingly, suction pressure acts on the upright wall portion 11b and the second surface 162 of the second moving body 16. On the other hand, the control pressure acts on the first surface 161 of the second moving body 16. Here, in this compressor, the cutout portion 114 is not formed in the upright wall portion 11b, and the second moving body 16 is formed rigidly. For this reason, unlike the compressor of the first embodiment, in this compressor, the communication chamber 39 is not formed in the drive shaft 3. Accordingly, in this compressor, the suction chamber 28 and the second communication path 41 are not in communication.

In this compressor, the suction reed valve 91a shown in Figs. 13 and 14 opens each suction hole 910 so that the refrigerant gas at the suction pressure is transferred to the compression chambers 45a to 45f in the suction stroke. Inhaled. Here, among the compression chambers 45a to 45f, the compression chambers 45a to 45f in the compression stroke or the discharge stroke are defined as the first specific compression chamber 451, and the compression chamber in the re-expansion stroke or the suction stroke ( 45a to 45f) are defined as the second specific compression chamber 452.

Specifically, in this compressor, when the drive shaft 3 is at the rotation angle shown in Figs. 13, 14, and 17 to 19, the compression chamber 45a shifts from the later stage of the compression stroke to the discharge process. In the stage, the piston 7 is located at the top dead center. And the compression chamber 45b becomes an initial stage of a re-expansion process or a suction process. That is, the suction stroke proceeds in the order of the compression chamber 45b, the compression chamber 45c, and the compression chamber 45d. As a result, the compression chamber 45c becomes the intermediate stage of the suction stroke. Further, the compression chamber 45d becomes a later stage of the suction stroke, and the piston 7 is located at the bottom dead center. On the other hand, the compression process proceeds in the order of the compression chamber 45e, the compression chamber 45f, and the compression chamber 45a. Accordingly, the compression chamber 45e becomes the initial stage of the compression process, and the compression chamber 45f becomes the intermediate stage of the compression process. As described above, when the drive shaft 3 is at the rotation angle shown in Figs. 13, 14, and 17 to 19, the compression chamber 45e, the compression chamber 45f, and the compression chamber 45a are subjected to the first specific compression. It becomes the chamber 451, and the compression chambers 45b to 45d become the second specific compression chamber 452. And, among the first specific compression chambers 451, the inside of the compression chamber 45a becomes the highest pressure.

In addition, in this compressor, the cap 35 is supported by the second shaft hole 23, so that the guide window 35a, and furthermore, the first moving body 11 formed in the guide window 35a, is in a state of the highest pressure. First communication paths 22a to 22f communicating with the existing first specific compression chamber 451 and the second specific compression chamber 452 adjacent to each other in the first specific compression chamber 451 It faces the furnaces 22a to 22f and the first communication paths 22a to 22f communicating with the second specific compression chamber 452 adjacent to the second specific compression chamber 452. In addition, the main body portion 35b of the cap 35 has a first communication path 22a to 22f communicating with the first specific compression chamber 451 in a second high-pressure state, and a third high-pressure state. The first communication paths 22a to 22f communicating with the first specific compression chamber 451 in the first specific compression chamber 451 and the first communicating with the second specific compression chamber 452 adjacent to each other in the first specific compression chamber 451 It faces the communication paths 22a to 22f. That is, when the drive shaft 3 is at the rotation angle shown in Fig. 17, the guide window 35a and the first moving body 11 are the first communication path 22a, the first communication path 22b, and It faces the first communication path 22c. Further, the main body 35b faces the first communication path 22f, the first communication path 22e, and the first communication path 22d.

And, when the drive shaft 3 rotates in the R1 direction more than the state shown in FIG. 17, the compression chamber 45f becomes the first specific compression chamber 451 in the state of the highest pressure, and the compression chamber 45e becomes 2 It becomes the first specific compression chamber 451 in a state of high pressure in the second. For this reason, the guide window 35a and the first moving body 11 face the first communication path 22f, the first communication path 22a, and the first communication path 22b. And the main body part 35b faces the 1st communication path 22e, the 1st communication path 22d, and the 1st communication path 22c. In this way, the guide window 35a and the first moving body 11 are the first communication paths 22a to 22f communicating with the first specific compression chamber 451 in the state of the highest pressure by rotating the drive shaft 3. ), the first communication paths 22a to 22f communicating with the second specific compression chamber 452 adjacent to the first specific compression chamber 451, and the second specific compression chamber 452 adjacent to each other. The first communication paths 22a to 22f communicating with the second specific compression chamber 452 are sequentially opposed to each other. On the other hand, the main body 35b includes first communication paths 22a to 22f communicating with the first specific compression chamber 451 in a second high-pressure state, and a first specific compression chamber in a third high-pressure state. First communication paths 22a to 22f communicating with the compression chamber 451 and first communication paths 22a to 22f communicating with the second specific compression chamber 452 adjacent to each other in the first specific compression chamber 451 22f) in sequence. Other configurations of this compressor are the same as those of the first embodiment, and the same components are denoted by the same reference numerals, and detailed descriptions of the configuration are omitted.

In this compressor as well, by moving the moving body 14 in the direction of the drive shaft center O, the flow rate of the refrigerant gas sucked from the suction chamber 28 to the compression chambers 45a to 45f per rotation of the drive shaft 3, furthermore, Is, it is possible to change the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29.

Specifically, in the case of increasing the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29, the control pressure of the control pressure chamber 27 is reduced by the control valve 13, Reduce the differential pressure.

Therefore, in the moving body 14, the first and second moving bodies 11 and 16 start to move forward in the direction of the drive shaft center O from the position shown in Fig. 16 by the elastic support force of the elastic support spring 43. do. That is, while the first moving body 11 starts to move forward in the direction of the driving shaft O in the guide window 35a, the second moving body 16 is in the first shaft 33d and the second diameter The inside of the part 352 starts to move forward in the direction of the drive shaft center (O). Accordingly, the second communication path 41 moves forward relative to the first communication paths 22a to 22f, so that the communication angle gradually decreases in this compressor.

Then, by further reducing the control pressure in the control pressure chamber 27 by the control valve 13 and minimizing the variable differential pressure, the first moving body 11 is moved inside the guide window 35a as shown in FIG. 15. Is moved to the most forward position. As described above, in this compressor, compared with the compressor of the first embodiment, the length of the second communication path 41 in the front-rear direction is set to be shorter. For this reason, in the state in which the first moving body 11 has moved most forward through the guide window 35a, in the first moving body 11, the surface 111 of the peripheral wall portion 11a is the first communication path 22a. By opposing them to 22f to 22f), the first communication paths 22a to 22f and the second communication path 41 become non-communication. For this reason, the communication angle becomes minimum, that is, zero. Therefore, in this case, even if the drive shaft 3 rotates around the drive shaft center O, the second communication path 41 is in a state that is not in communication with any of the first communication paths 22a to 22f ( See Fig. 17).

In this way, when the communication angle is minimum, the piston 7 moves from the top dead center to the bottom dead center, and the volume of the compression chambers 45a to 45f expands, and the pressure in the compression chambers 45a to 45f is reduced. By lowering than (28), the suction reed valve 91a is opened, and the suction chamber 28 and the compression chambers 45a to 45f, more specifically, the suction chamber 28 and the second specific compression chamber 452, are in communication. do. For this reason, the refrigerant gas having a suction pressure is sucked from the suction chamber 28 into the compression chambers 45a to 45f. Accordingly, when the communication angle is the minimum, the flow rate of the refrigerant gas sucked from the suction chamber 28 to the compression chambers 45a to 45f becomes maximum. Then, the refrigerant gas sucked from the suction chamber 28 into the compression chambers 45a to 45f is compressed in the compression step and then discharged to the discharge chamber 29 by opening the discharge reed valve 92a in the discharge step. do. As a result, in this compressor, the flow rate of the refrigerant gas discharged to the discharge chamber 29 is maximized.

On the other hand, when the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 is reduced, the control valve 13 increases the control pressure of the control pressure chamber 27. Accordingly, the variable differential pressure increases.

For this reason, in the movable body 14, the second movable body 16 resists the elastic support force of the elastic support spring 43, and the inside of the first shaft 33d and the second diameter portion 352 from the position shown in FIG. 15 It starts to move backward in the direction of the drive shaft center (O). Accordingly, the first moving body 11 starts to move rearward in the guide window 35a in the direction of the drive shaft center O, so that the second communication path 41 is connected to the first communication paths 22a to 22f. It moves relative to the rear. For this reason, the 2nd communication path 41 is in a state which communicates with the 1st communication paths 22a-22f in the 1st part 411. Accordingly, in this compressor, the communication angle becomes larger than the minimum.

Accordingly, the second communication path 41 communicates with the first specific compression chamber 451 in the state of the highest pressure, like the first communication path 22a and the first communication path 22b shown in FIG. 18. The first communication paths 22a to 22f are communicated with each other and the first communication paths 22a to 22f communicating with the second specific compression chamber 452 adjacent to each other to the first specific compression chamber 451. For this reason, a part of the high-pressure refrigerant gas in the compression chamber 45a is introduced into the compression chamber 45b through the second communication path 41.

Here, in the state in which the second communication path 41 communicates with the first communication paths 22a to 22f at the first portion 411, like the first communication path 22c, it is in the middle stage of the suction stroke. The first communication paths 22a to 22f communicating with the existing compression chambers 45a to 45f face the surface 111 of the circumferential wall portion 11a, thereby becoming non-communicating with the second communication path 41. Further, like the first communication paths 22d to 22f, the first communication paths 22a to 22f communicating with the first specific compression chamber 451 in the second high-pressure state, and the third high-pressure state The first communication paths 22a to 22f communicating with the first specific compression chamber 451 in the first specific compression chamber 451 and the first communicating with the second specific compression chamber 452 adjacent to each other in the first specific compression chamber 451 The communication paths 22a to 22f are opposed to the main body portion 35b of the cap 35, so that the second communication path 41 is not in communication with each other.

In this way, when the communication angle becomes larger than the minimum, the refrigerant gas in the first specific compression chamber 451 having the highest pressure is introduced into the second specific compression chamber 452 through the second communication path 41, and the second It re-expands within the specific compression chamber 452. That is, the refrigerant gas in the compression chambers 45a to 45f in the discharge stroke is introduced into the compression chambers 45a to 45f in the initial stage of the re-expansion stroke or the suction stroke to re-expand. For this reason, even if the piston 7 moves from the top dead center to the bottom dead center, the suction reed valve 91a will not open unless the pressure in the second specific compression chamber 452 is lower than the suction pressure in the suction chamber 28. In the meantime, the refrigerant gas is not sucked into the second specific compression chamber 452 from the suction chamber 28. For this reason, in this compressor, the flow rate of the refrigerant gas sucked into the compression chambers 45a to 45f decreases during the suction stroke, so that the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 decreases. Decreases.

That is, in this compressor, since the communication angle becomes larger than the minimum, the amount of work when compressing the refrigerant gas is reduced and the amount of work when the refrigerant gas is re-expanded is reduced compared to the case where the communication angle is minimum do.

Then, when the variable differential pressure becomes maximum, as shown in FIG. 16, the first moving body 11 is in a state that has moved the inside of the guide window 35a to the rearmost position. Accordingly, the second communication path 41 is in a state in which the second communication path 41 communicates with the first communication paths 22a to 22f at the second portion 412. In this way, the communication angle is maximized.

Accordingly, the second communication path 41 communicates with the first communication paths 22a to 22c shown in FIG. 19. That is, the second communication path 41 is connected to the first communication paths 22a to 22f communicating with the first specific compression chamber 451 in the state of the highest pressure, and the first specific compression chamber 451. The first communication paths 22a to 22f communicating with the neighboring second specific compression chamber 452, and the first communicating passages 22a to 22f in communication with the second specific compression chamber 452 and the second specific compression chamber 452 adjacent to each other. It communicates with the communication paths 22a to 22f. Accordingly, a part of the high-pressure refrigerant gas in the compression chamber 45a is introduced into the compression chambers 45b and 45c through the second communication path 41. Also in this state, the first communication paths 22a to 22f communicating with the first specific compression chamber 451 in the second high-pressure state, and the first specific compression chamber in the third high-pressure state The first communication paths 22a to 22f communicating with the 451 and the first communication paths 22a to 22f communicating with the second specific compression chamber 452 adjacent to each other in the first specific compression chamber 451 In the case of, by opposing the main body portion 35b of the cap 35, the second communication path 41 becomes non-communicable.

In this way, in the state where the communication angle is maximum, through the second communication path 41, from the compression chambers 45a to 45f in the discharge stroke, the compression chambers 45a to in the initial stage of the re-expansion stroke or the suction stroke. The refrigerant gas is introduced into 45f) and the compression chambers 45a to 45f in the intermediate stage of the suction stroke. That is, the flow rate of the refrigerant gas introduced into the second specific compression chamber 452 from the first specific compression chamber 451 at the highest pressure increases. As a result, in this compressor, the flow rate of the refrigerant gas sucked into the compression chambers 45a to 45f during the suction stroke is further reduced, so that the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 This becomes the minimum. That is, in the state where the communication angle is at the maximum, the amount of work when the refrigerant gas is compressed is further reduced, and the amount of work when the refrigerant gas is re-expanded is further reduced. Other actions of this compressor are the same as those of the first embodiment.

In the above, the present invention has been described based on Examples 1 and 2, but the present invention is not limited to the above Examples 1 and 2, and it is to be understood that the present invention can be appropriately changed and applied within the scope not departing from the purpose. There is no need.

For example, the compressors of Examples 1 and 2 may be configured as a double-headed piston type compressor.

In addition, for the compressors of Examples 1 and 2, while facing the second shaft hole 23 at a position between the first seal ring 358 and the second seal ring 359 in the cap 35 , An annular groove communicating with the first and second paths 33e and 35d may be formed, and the annular groove and the control valve 13 may be connected by a connection path 26.

In addition, for the compressors of Examples 1 and 2, the formation of the annular groove 24 was omitted, and the first and second paths 33e and 35d and the connection path 26 were intermittently caused by the rotation of the drive shaft 3. By communicating with each other, the control pressure chamber 27 and the control valve 13 may be intermittently connected.

Further, with respect to the compressor of the first embodiment, the control valve 13 may have a configuration in which the communication angle increases by reducing the control pressure in the control pressure chamber 27. Further, with respect to the compressor of the second embodiment, the control valve 13 may increase the control pressure in the control pressure chamber 27, thereby increasing the communication angle.

In addition, with respect to the compressor of Example 1, the communication chamber 39 through the first communication paths 22a to 22f and the second communication path 41 from the inside of the compression chambers 45a to 45f due to the change in the communication angle. The flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f may be changed by changing the flow rate of the refrigerant gas discharged to the discharge chamber 29.

In addition, with respect to the compressor of the second embodiment, instead of the second communication path 41, a configuration in which refrigerant gas is introduced into the second specific compression chamber 452 from the second high-pressure first specific compression chamber 451 That is, the refrigerant gas may be introduced from the compression chambers 45a to 45f in the compression stroke to the compression chambers 45a to 45f in the re-expansion stroke or the suction stroke.

In addition, for the compressors of Examples 1 and 2, in place of each shoe 8a and 8b, while supporting the swinging plate through a thrust bearing on the rear side of the fixed swash plate 5, the swinging plate and the piston 7 A wobble-type conversion mechanism in which) is connected by a cone rod may be employed.

In addition, with respect to the compressors of Examples 1 and 2, the second moving bodies 12 and 16 do not slide with the second diameter portion 352, but the second moving bodies 12 and 16 and the second diameter portion 352 A gap may be formed between them.

In addition, in the compressors of Examples 1 and 2, the communication angle according to the position in the guide window 35a of the first moving body 11, that is, the position in the drive shaft center O direction of the moving bodies 10 and 14 By changing, the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29 is changed. However, the present invention is not limited thereto, and the communication area between the first communication paths 22a to 22f and the second communication path 41 changes according to the position of the moving bodies 10 and 14 in the direction of the drive shaft center O. A configuration may be employed in which the flow rate of the refrigerant gas discharged from the chambers 45a to 45f to the discharge chamber 29 is changed.

In addition, in the compressors of Examples 1 and 2, external control may be performed to control the control pressure by switching ON and OFF of the current to the control valve 13 from the outside, and the control pressure may be adjusted without depending on the current from the outside. You may perform internal control to control. Here, when the current to the control valve 13 is turned OFF to increase the valve opening degree, when the compressor is stopped, the valve opening degree becomes large, and the control pressure in the control pressure chamber 27 can be lowered. Therefore, starting shock can be reduced since the compressor can be started in a state where the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f is the minimum.

In addition, in the compressors of Examples 1 and 2, control valve 13 may perform extraction-side control to change the flow rate of the refrigerant gas drawn from the control pressure chamber 27 to the suction chamber 28 via the bleed passage. good. In this case, the compressor can reduce the amount of refrigerant gas in the discharge chamber 29 used in changing the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f to the discharge chamber 29. Can increase the efficiency of Further, in this case, if the current to the control valve 13 is turned off to increase the valve opening degree, when the compressor is stopped, the valve opening degree becomes large, and the control pressure of the control pressure chamber 27 can be lowered. Therefore, starting shock can be reduced since the compressor can be started in a state where the flow rate of the refrigerant gas discharged from the compression chambers 45a to 45f is the minimum.

Further, in the compressors of Examples 1 and 2, instead of the control valve 13, a three-way valve capable of adjusting the opening degree in both the extraction passage and the supply passage may be employed.

The present invention can be used in a vehicle air conditioner or the like.

1: housing
3: drive shaft
5: fixed swash plate
7: piston
9a: Valve forming plate (discharge valve)
9b: valve forming plate (discharge valve, suction valve)
10: moving object
13: control valve
13c: second air supply passage
14: moving object
21: cylinder block
21a∼21f: cylinder bore
22a∼22f: first communication path
23: 2nd shaft work (shaft work)
24: annular groove
26: connection path
27: control pressure chamber
28: suction chamber
29: discharge chamber
31: sergeant office
33e: first path (path)
35d: second path (path)
39: communication room
41: second communication path
45a∼45f: compression chamber
173: 1st shaft work (shaft work)
451: first specific compression chamber
452: second specific compression chamber
O: Drive shaft center

Claims (4)

It has a cylinder block in which a plurality of cylinder bores are formed, a suction chamber, a discharge chamber, a swash plate chamber, a housing in which a shaft hole is formed,
A drive shaft rotatably supported in the shaft hole,
A fixed swash plate that is rotatable within the swash plate chamber by rotation of the drive shaft and has a constant inclination angle with respect to a plane perpendicular to the drive shaft,
A piston forming a compression chamber in the cylinder bore and connected to the fixed swash plate,
A discharge valve for discharging the refrigerant in the compression chamber to the discharge chamber,
A moving body formed on the drive shaft, integrally rotating with the drive shaft, and movable with respect to the drive shaft in a direction of a drive shaft center based on a control pressure,
And a control valve for controlling the control pressure,
In the cylinder block, a first communication path communicating with the cylinder bore is formed,
The moving body is provided with a second communication path intermittently communicating with the first communication path along with the rotation of the drive shaft,
As a piston type compressor in which the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber changes according to a position of the moving body in the direction of the drive shaft,
In the drive shaft, a control pressure chamber is formed in which the inside of the drive shaft becomes the control pressure by being partitioned by the drive shaft and the moving body and connected to the control valve through a control passage.
The control passage comprises an annular groove formed in an annular shape on an inner circumferential surface of the shaft hole or an outer circumferential surface of the drive shaft,
A connection path formed in the housing and connecting the control valve and the annular groove,
It is formed on the drive shaft and has a path extending in a radial direction of the drive shaft to communicate with the annular groove and the control pressure chamber,
In the drive shaft and in the moving body, a communication chamber is formed that is partitioned from the control pressure chamber and communicates with the suction chamber and the second communication path,
The first communication path and the second communication path are communicated by the moving body,
The piston type compressor, characterized in that the first communication path and the second communication path are not communicated with each other by the drive shaft. It has a cylinder block in which a plurality of cylinder bores are formed, a suction chamber, a discharge chamber, a swash plate chamber, a housing in which a shaft hole is formed,
A drive shaft rotatably supported in the shaft hole,
A fixed swash plate that is rotatable within the swash plate chamber by rotation of the drive shaft and has a constant inclination angle with respect to a plane perpendicular to the drive shaft,
A piston forming a compression chamber in the cylinder bore and connected to the fixed swash plate,
A discharge valve for discharging the refrigerant in the compression chamber to the discharge chamber,
A moving body formed on the drive shaft, integrally rotating with the drive shaft, and movable with respect to the drive shaft in a direction of a drive shaft center based on a control pressure,
And a control valve for controlling the control pressure,
In the cylinder block, a first communication path communicating with the cylinder bore is formed,
The moving body is provided with a second communication path intermittently communicating with the first communication path along with the rotation of the drive shaft,
As a piston type compressor in which the flow rate of the refrigerant discharged from the compression chamber to the discharge chamber changes according to a position of the moving body in the direction of the drive shaft,
In the drive shaft, a control pressure chamber is formed in which the inside of the drive shaft becomes the control pressure by being partitioned by the drive shaft and the moving body and connected to the control valve through a control passage.
The control passage comprises an annular groove formed in an annular shape on an inner circumferential surface of the shaft hole or an outer circumferential surface of the drive shaft,
A connection path formed in the housing and connecting the control valve and the annular groove,
It is formed on the drive shaft and has a path extending in a radial direction of the drive shaft to communicate with the annular groove and the control pressure chamber,
Further provided with a suction valve for sucking the refrigerant in the suction chamber into the compression chamber,
The compression chamber in the compression stroke or the discharge stroke becomes a first specific compression chamber,
The compression chamber in the re-expansion stroke or the suction stroke becomes a second specific compression chamber,
The second communication path communicates with the first communication path that communicates with the first specific compression chamber and the first communication path that communicates with the second specific compression chamber. A piston type compressor for introducing a refrigerant into a second specific compression chamber. delete delete

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