JP2015175269A - Swash plate type variable displacement compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a swash plate type variable displacement compressor that can exhibit excellent performance for a long time while reducing the manufacturing cost in a compressor varying a discharge capacity with the usage of an actuator.SOLUTION: A throttle hole 57 is formed at a connection part 133 in a compressor of this invention. The throttle hole 57 is extended from a control pressure chamber 13b side to an inside of an outer sliding part 51c. In this compressor, refrigerant gas is discharged from the inside of the control pressure chamber 13b to a swash plate chamber 25 through the throttle hole 57 in addition to each opening adjustment of a high pressure passage 15b and a low pressure control valve 15c when adjusting a pressure in the control pressure chamber 13b. Lubricating oil is discharged together with the refrigerant gas from the throttle hole 57. Thereby, in the compressor, the lubricating oil is hardly stored in the control pressure chamber 13b, and shortage of the lubricating oil in the swash plate chamber 25 hardly occurs.

Description

  The present invention relates to a variable displacement swash plate compressor.

  Patent Document 1 discloses a conventional variable displacement swash plate compressor (hereinafter referred to as a compressor). In this compressor, a suction chamber, a discharge chamber, a swash plate chamber, a center bore, and a plurality of cylinder bores are formed in a housing. The swash plate chamber and the center bore communicate with each other. A drive shaft is rotatably supported by the housing. In the swash plate chamber, there is provided a swash plate that can be rotated by the rotation of the drive shaft. A link mechanism is provided between the drive shaft and the swash plate. The link mechanism allows a change in the inclination angle of the swash plate. Here, the inclination angle is an angle of the swash plate with respect to a direction orthogonal to the drive axis of the drive shaft. In each cylinder bore, a piston is accommodated so as to be able to reciprocate. The pair of shoes for each piston, as a conversion mechanism, reciprocates each piston within the cylinder bore with a stroke corresponding to the inclination angle by the rotation of the swash plate. The actuator changes the tilt angle. The control mechanism controls the actuator.

  The actuator has a first moving body, a second moving body, and a control pressure chamber. The first moving body and the second moving body are inserted through the drive shaft while being aligned in the axial direction, and are movable in the drive axis direction. The first moving body is located in the center bore. A thrust bearing is provided between the first moving body and the second moving body. A swash plate is engaged with the second moving body so that the inclination angle can be changed. The control pressure chamber moves the first moving body and the second moving body by the internal pressure.

  The control mechanism adjusts the pressure of the refrigerant in the control pressure chamber by performing communication control between the control pressure chamber and the discharge chamber, as well as performing communication control between the control pressure chamber and the discharge chamber. The control mechanism includes an O-ring and a pair of sealing rings. The O-ring and each sealing ring are located between the outer peripheral surface of the first moving body and the inner peripheral surface of the center bore. The space between the control pressure chamber and the swash plate chamber is sealed by the O-ring and each sealing ring.

  In this compressor, the control mechanism increases the pressure in the control pressure chamber by introducing the refrigerant in the discharge chamber into the control pressure chamber. Thereby, the first moving body moves in the center bore in the direction of the driving axis, and moves the second moving body in the direction of the driving axis. The second moving body increases the inclination angle of the swash plate through the link mechanism. Thus, with this compressor, it is possible to increase the discharge capacity per rotation of the drive shaft.

JP-A-8-105384

  In the conventional compressor, when changing the discharge capacity, the control mechanism seals between the control pressure chamber and the swash plate chamber, and controls the control pressure by each communication control between the suction chamber, the discharge chamber, and the control pressure chamber. Adjust the room pressure. For this reason, in this compressor, the process and means which prevent the leakage of a refrigerant | coolant from a control pressure chamber are needed, and manufacturing cost rises.

  In this compressor, when the refrigerant in the discharge chamber is introduced into the control pressure chamber, the lubricating oil also flows into the control pressure chamber together with the refrigerant. The lubricating oil that has flowed into the control pressure chamber is stored in the control pressure chamber. As a result, in this compressor, the lubricating oil in the swash plate chamber tends to be insufficient, and the lubrication of the thrust bearing and the like tends to be insufficient in the swash plate chamber. For this reason, in this compressor, it is difficult to maintain performance over a long period of time.

  The present invention has been made in view of the above-described conventional situation, and in a compressor that changes the discharge capacity using an actuator, it achieves high performance over a long period of time while reducing the manufacturing cost. It is an object to be solved to provide a variable capacity swash plate compressor.

The capacity-variable swash plate compressor of the present invention includes a housing in which a suction chamber, a discharge chamber, a swash plate chamber and a cylinder bore are formed, a drive shaft rotatably supported by the housing, and rotation of the drive shaft. A swash plate rotatable within a plate chamber, and a link mechanism provided between the drive shaft and the swash plate and allowing a change in the inclination angle of the swash plate with respect to a direction perpendicular to the drive axis of the drive shaft; A piston housed reciprocally in the cylinder bore, a conversion mechanism for reciprocating the piston in the cylinder bore with a stroke corresponding to the inclination angle by rotation of the swash plate, and the inclination angle being changeable An actuator, and a control mechanism for controlling the actuator,
The swash plate chamber communicates with the suction chamber;
The actuator is partitioned by a partition provided on the drive shaft in the swash plate chamber, a movable body movable in the direction of the drive axis in the swash plate chamber, and the partition and the movable body. A control pressure chamber for moving the moving body by an internal pressure,
The control mechanism communicates with the discharge chamber and the control pressure chamber, communicates with an air supply passage for introducing the refrigerant in the discharge chamber into the control pressure chamber, the control pressure chamber, and the swash plate chamber, A bleed passage for discharging the refrigerant in the control pressure chamber to the swash plate chamber,
The bleed passage has a communication passage that is formed in at least one of the moving body and the partition body and discharges lubricating oil from the control pressure chamber together with the refrigerant to the swash plate chamber.

  In the compressor of the present invention, the air supply passage introduces the refrigerant in the discharge chamber into the control pressure chamber, thereby increasing the pressure in the control pressure chamber. Further, the refrigerant in the control pressure chamber is discharged to the swash plate chamber through the extraction passage, thereby reducing the pressure in the control pressure chamber. In this compressor, the extraction passage has a communication passage. The communication path is formed in at least one of the moving body or the partition body. For this reason, in this compressor, it is possible to adjust the pressure in the control pressure chamber by discharging the refrigerant from the control pressure chamber to the swash plate chamber through the communication passage. Thus, in this compressor, the moving body of the actuator is moved by the changed pressure in the control pressure chamber, the link mechanism allows the inclination angle of the swash plate to be changed, and the discharge capacity per one rotation of the drive shaft can be changed. It is. As described above, in this compressor, when adjusting the pressure in the control pressure chamber, the refrigerant flows out from the control pressure chamber to the swash plate chamber through the communication passage, so that the processing and means for sealing the control pressure chamber are simple. Or it becomes unnecessary.

  In addition, the communication path discharges lubricating oil together with the refrigerant from the control pressure chamber to the swash plate chamber. For this reason, in this compressor, even when the lubricating oil flows into the control pressure chamber together with the refrigerant when the refrigerant in the discharge chamber is introduced into the control pressure chamber, the lubricating oil is inclined from the control pressure chamber together with the refrigerant through the communication path. It will be discharged to the board room. For this reason, in this compressor, it is difficult for the lubricating oil to be stored in the control pressure chamber, and a shortage of lubricating oil in the swash plate chamber is unlikely to occur.

  Therefore, the compressor of the present invention exhibits high performance over a long period of time while realizing a reduction in manufacturing cost in a compressor that changes the discharge capacity using an actuator.

  In the compressor of the present invention, the partition body may have an outer sliding portion that extends in the direction of the drive axis and slidably surrounds the moving body. The moving body includes a first cylindrical portion disposed on the swash plate side around the drive shaft, a second cylindrical portion having a cylindrical shape whose diameter is larger than that of the first cylindrical portion, the first cylindrical portion, and the second cylindrical portion. It can have a connection part which connects a cylindrical part. The communication passage is formed in the second cylindrical portion or the connecting portion so that the lubricating oil discharged together with the refrigerant from the communication passage is supplied to the sliding portion between the moving body and the outer sliding portion. Is preferred.

  In this case, the sliding portion between the moving body and the outer sliding portion can be suitably lubricated by the lubricating oil discharged together with the refrigerant from the communication path. Thereby, in this compressor, a movable body can slide suitably in an outside sliding part. For this reason, in this compressor, the discharge capacity per one rotation of the drive shaft can be suitably changed over a long period of time.

  In the compressor of the present invention, the partition body can be fixed to the drive shaft. A thrust bearing that supports a thrust force acting on the drive shaft may be provided between the partition body and the housing. In addition, a radial bearing that supports a radial force acting on the drive shaft may be provided between the housing and the drive shaft. In addition, a shaft seal device that ensures airtightness between the inside and the outside of the housing can be provided between the housing and the drive shaft. And it is also preferable that the communicating path is formed in the partition body so that the lubricating oil discharged together with the refrigerant from the communicating path is supplied to the thrust bearing, the radial bearing or the shaft seal device.

  In this case, the thrust bearing, the radial bearing or the shaft seal device is suitably lubricated by the lubricating oil discharged together with the refrigerant from the communication path. For this reason, in this compressor, seizure or the like hardly occurs in the thrust bearing or the like, and durability can be increased.

  In the compressor according to the present invention, the movable body includes a peripheral wall that extends in the drive axis direction and surrounds the partition body while sliding with the partition body, and a bottom wall that extends from the peripheral wall toward the drive shaft. obtain. And it is also preferable that the communication path is formed in the partition body so that the lubricating oil discharged together with the refrigerant from the communication path is supplied to the sliding portion between the peripheral wall and the partition body.

  In this case, the sliding portion between the peripheral wall and the partition body can be suitably lubricated by the lubricating oil discharged together with the refrigerant from the communication path. Thereby, in this compressor, a surrounding wall can slide a division body suitably. For this reason, in this compressor, the discharge capacity per one rotation of the drive shaft can be suitably changed over a long period of time.

  In the compressor according to the present invention, the movable body includes a peripheral wall that extends in the drive axis direction and surrounds the partition body while sliding with the partition body, and a bottom wall that extends from the peripheral wall toward the drive shaft. obtain. Furthermore, a thrust bearing that supports a thrust force acting on the drive shaft may be provided between the moving body and the housing. And it is also preferable that the communicating path is provided in the partition body so that the lubricating oil discharged together with the refrigerant from the communicating path is supplied to the thrust bearing.

  Also in this case, the thrust bearing is suitably lubricated by the lubricating oil discharged together with the refrigerant from the communication path. For this reason, in this compressor, seizure hardly occurs in the thrust bearing, and durability can be increased.

  The compressor of the present invention exhibits high performance over a long period of time while realizing a reduction in manufacturing cost in a compressor that changes the discharge capacity using an actuator.

FIG. 1 is a cross-sectional view of the compressor of the first embodiment at the maximum capacity. FIG. 2 is a schematic diagram illustrating a control mechanism according to the compressor of the first embodiment. FIG. 3 is an enlarged cross-sectional view of a main part illustrating the actuator in the compressor according to the first embodiment. FIG. 4 is a cross-sectional view of the compressor according to the first embodiment when the capacity is minimum. FIG. 5 is an enlarged cross-sectional view of a main part illustrating an actuator according to the compressor of the second embodiment. FIG. 6 is an enlarged cross-sectional view of a main part illustrating the actuator in the compressor according to the third embodiment. FIG. 7 is an enlarged cross-sectional view of a main part illustrating an actuator according to the compressor of the fourth embodiment. FIG. 8 is a cross-sectional view of the compressor of the fifth embodiment at the maximum capacity. FIG. 9 is a schematic diagram illustrating a control mechanism according to the compressor of the fifth embodiment. FIG. 10 is an essential part enlarged cross-sectional view showing an actuator in the compressor of the fifth embodiment. FIG. 11 is a cross-sectional view of the compressor of the fifth embodiment when the capacity is minimum. FIG. 12 is an enlarged cross-sectional view of a main part illustrating an actuator according to the compressor of the sixth embodiment.

  Embodiments 1 to 6 embodying the present invention will be described below with reference to the drawings. The compressors of Examples 1 to 4 are variable capacity single-head swash plate compressors. On the other hand, the compressors of Examples 5 and 6 are variable capacity double-head swash plate compressors. All of these compressors are mounted on a vehicle, and constitute a refrigeration circuit of a vehicle air conditioner.

Example 1
As shown in FIG. 1, the compressor according to the first embodiment includes a housing 1, a drive shaft 3, a swash plate 5, a link mechanism 7, a plurality of pistons 9, a pair of shoes 11 a and 11 b, and an actuator 13. And a control mechanism 15 shown in FIG.

  As shown in FIG. 1, the housing 1 includes a front housing 17 located in front of the compressor, a rear housing 19 located behind the compressor, and a cylinder block located between the front housing 17 and the rear housing 19. 21 and an annuloplasty plate 23.

  The front housing 17 includes a front wall 17a that extends in the vertical direction of the compressor in front and a peripheral wall 17b that is integrated with the front wall 17a and extends rearward from the front of the compressor. The front housing 17 has a substantially cylindrical shape with a bottom by the front wall 17a and the peripheral wall 17b. A swash plate chamber 25 is formed in the front housing 17 by the front wall 17a and the peripheral wall 17b.

  A boss 17c that protrudes forward is formed on the front wall 17a. A shaft seal device 27 is provided in the boss 17c to ensure airtightness between the inside of the housing 1 and the outside. Further, a first shaft hole 17d extending in the front-rear direction of the compressor is formed in the boss 17c. A first sliding bearing 29a is provided in the first shaft hole 17d. The first sliding bearing 29a corresponds to the radial bearing in the present invention. Further, a rolling bearing can be adopted instead of the first sliding bearing 29a.

  A suction port 250 communicating with the swash plate chamber 25 is formed in the peripheral wall 17b. Through this suction port 250, the swash plate chamber 25 is connected to an evaporator (not shown). Thus, since the low-pressure refrigerant gas that has passed through the evaporator flows into the swash plate chamber 25 through the suction port 250, the pressure in the swash plate chamber 25 becomes lower than that in the discharge chamber 35 described later.

  A part of the control mechanism 15 is provided in the rear housing 19. The rear housing 19 is formed with a first pressure adjustment chamber 31a, a suction chamber 33, and a discharge chamber 35. The first pressure adjustment chamber 31 a is located at the center portion of the rear housing 19. The discharge chamber 35 is annularly positioned on the outer peripheral side of the rear housing 19. The suction chamber 33 is formed in an annular shape between the first pressure adjustment chamber 31 a and the discharge chamber 35 in the rear housing 19. The discharge chamber 35 is connected to a discharge port (not shown).

  In the cylinder block 21, the same number of cylinder bores 21a as the pistons 9 are formed at equal angular intervals in the circumferential direction. The front end side of each cylinder bore 21 a communicates with the swash plate chamber 25. Further, the cylinder block 21 is formed with a retainer groove 21b that regulates a maximum opening degree of a suction reed valve 41a described later.

  Further, the cylinder block 21 is provided with a second shaft hole 21c that communicates with the swash plate chamber 25 and extends in the front-rear direction of the compressor. A second sliding bearing 29b is provided in the second shaft hole 21c. Note that a rolling bearing may be employed instead of the second sliding bearing 29b.

  The cylinder block 21 has a spring chamber 21d. The spring chamber 21d is located between the swash plate chamber 25 and the second shaft hole 21c. A return spring 37 is disposed in the spring chamber 21d. The return spring 37 urges the swash plate 5 having the smallest inclination angle toward the front of the swash plate chamber 25. Further, a suction passage 39 communicating with the swash plate chamber 25 is formed in the cylinder block 21.

  The valve forming plate 23 is provided between the rear housing 19 and the cylinder block 21. The valve forming plate 23 includes a valve plate 40, a suction valve plate 41, a discharge valve plate 43, and a retainer plate 45.

  The valve plate 40, the discharge valve plate 43, and the retainer plate 45 are formed with the same number of intake ports 40a as the cylinder bores 21a. The valve plate 40 and the intake valve plate 41 are formed with the same number of discharge ports 40b as the cylinder bores 21a. Each cylinder bore 21a communicates with the suction chamber 33 through each suction port 40a, and communicates with the discharge chamber 35 through each discharge port 40b. Further, the valve plate 40, the suction valve plate 41, the discharge valve plate 43, and the retainer plate 45 are formed with a first communication hole 40c and a second communication hole 40d. The suction chamber 33 and the suction passage 39 communicate with each other through the first communication hole 40c. Thereby, the swash plate chamber 25 and the suction chamber 33 communicate with each other.

  The intake valve plate 41 is provided on the front surface of the valve plate 40. The suction valve plate 41 is formed with a plurality of suction reed valves 41a capable of opening and closing each suction port 40a by elastic deformation. The discharge valve plate 43 is provided on the rear surface of the valve plate 40. The discharge valve plate 43 is formed with a plurality of discharge reed valves 43a capable of opening and closing each discharge port 40b by elastic deformation. The retainer plate 45 is provided on the rear surface of the discharge valve plate 43. The retainer plate 45 regulates the maximum opening degree of the discharge reed valve 43a.

  The drive shaft 3 is inserted from the boss 17c side toward the rear side of the housing 1. The front end side of the drive shaft 3 is inserted into the shaft sealing device 27 in the boss 17c, and is supported by the first sliding bearing 29a in the first shaft hole 17d. The rear end side of the drive shaft 3 is pivotally supported by the second sliding bearing 29b in the second shaft hole 21c. Thus, the drive shaft 3 is supported so as to be rotatable around the drive axis O <b> 1 with respect to the housing 1. A second pressure adjusting chamber 31b is defined between the rear end of the drive shaft 3 in the second shaft hole 21c. The second pressure regulation chamber 31b communicates with the first pressure regulation chamber 31a through the second communication hole 40d. These first and second pressure adjusting chambers 31a and 31b form a pressure adjusting chamber 31.

  O-rings 49 a and 49 b are provided at the rear end of the drive shaft 3. Thereby, each O-ring 49a, 49b is located between the drive shaft 3 and the 2nd shaft hole 21c, and seals between the swash plate chamber 25 and the pressure regulation chamber 31.

  A link mechanism 7, a swash plate 5, and an actuator 13 are attached to the drive shaft 3. The link mechanism 7 includes a lug plate 51, a pair of lug arms 53 formed on the lug plate 51, and a pair of swash plate arms 5 e formed on the swash plate 5. In this compressor, the lug plate 51 constitutes the link mechanism 7 and also functions as a partition body in the present invention. In the figure, only one of the lug arm 53 and the swash plate arm 5e is shown. The same applies to FIG.

  The lug plate 51 has a substantially annular shape, and is disposed in front of the swash plate 5 in the swash plate chamber 25. As shown in FIG. 3, the lug plate 51 has a fixed portion 51a, a fixed flange portion 51b, and an outer sliding portion 51c. The fixing portion 51 a is located at the center of the lug plate 51. An insertion hole 51d is provided through the fixed portion 51a. The drive shaft 3 is press-fitted into the insertion hole 51a. Thereby, the lug plate 51 is fixed to the drive shaft 3 and can rotate integrally with the drive shaft 3.

  The fixed flange portion 51b is located at the front end of the lug plate 51, and extends radially outward from the fixed portion 51a. The outer sliding part 51c is located on the outer peripheral side of the fixed part 51a, extends in the direction of the drive axis O1 from the tip of the fixed flange part 51b, and has a cylindrical shape concentric with the drive axis O1. The inside of the outer sliding portion 51 c communicates with the swash plate chamber 25 and is a part of the swash plate chamber 25. A thrust bearing 55 is provided between the lug plate 51 and the front wall 17a.

  Each lug arm 53 extends rearward from the outer sliding portion 51c. A guide surface 51e is provided at a position between the lug arms 53 in the outer sliding portion 51c. The guide surface 51e is inclined downward from the front end side toward the rear end side.

  As shown in FIG. 1, the swash plate 5 has an annular flat plate shape and has a front surface 5a and a rear surface 5b. On the front surface 5a, a weight portion 5c that protrudes toward the front of the swash plate 5 is formed. The weight portion 5c comes into contact with the lug plate 51 when the inclination angle of the swash plate 5 becomes maximum. An insertion hole 5 d is formed at the center of the swash plate 5. The drive shaft 3 is inserted through the insertion hole 5d.

  Each swash plate arm 5e is formed on the front surface 5a. Each swash plate arm 5e extends forward from the front surface 5a. The swash plate 5 is provided with a substantially hemispherical convex portion 5g protruding from the front surface 5a. The convex portion 5g is located between the swash plate arms 5e.

  In this compressor, by inserting each swash plate arm 5e between each lug arm 53, the lug plate 51 and the swash plate 5 are connected. As a result, the swash plate 5 can rotate in the swash plate chamber 25 together with the lug plate 51. As described above, the lug plate 51 and the swash plate 5 are connected to each other so that the front end side of each swash plate arm 5e comes into contact with the guide surface 51e. Then, as each swash plate arm 5e slides on the guide surface 51e, the swash plate 5 maintains the top dead center position T with respect to the inclination angle of the swash plate 5 with respect to the direction orthogonal to the drive axis O1. The maximum inclination angle shown in the figure can be changed to the minimum inclination angle shown in FIG.

  The actuator 13 includes a lug plate 51, a moving body 13a, and a control pressure chamber 13b.

  As shown in FIG. 3, the moving body 13 a is inserted through the drive shaft 3 and can move in the direction of the drive axis O <b> 1 while being in sliding contact with the drive shaft 3. The moving body 13 a has a cylindrical shape that is coaxial with the drive shaft 3, and includes a first cylindrical portion 131, a second cylindrical portion 132, and a connecting portion 133. The first cylindrical portion 131 is located on the swash plate 5 side in the moving body 13 a and is slidably provided on the drive shaft 3. An O-ring 49 c is provided on the inner peripheral surface of the first cylindrical portion 131.

  An action part 134 is integrally formed at the rear end of the first cylindrical part 131. As shown in FIG. 1, the action part 134 extends vertically from the drive axis O1 side toward the top dead center position T side of the swash plate 5, and is in contact with the convex part 5g. Thereby, the movable body 13a can rotate integrally with the lug plate 51 and the swash plate 5.

  As shown in FIG. 3, the second cylindrical portion 132 is located in front of the moving body 13a. The second cylindrical portion 132 is formed with a larger diameter than the first cylindrical portion 131. An O-ring 49 d is provided on the outer peripheral surface of the second cylindrical portion 132. The connecting portion 133 is located between the first cylindrical portion 131 and the second cylindrical portion 132, and extends while gradually increasing the diameter from the rear to the front of the movable body 13a. The connecting portion 133 has a rear end continuous with the first cylindrical portion 131 and a front end continuous with the second cylindrical portion 132.

  The outer sliding portion 51c of the lug plate 51 encloses the moving body 13a by allowing the second cylindrical portion 132 and the connecting portion 133 to enter the inside, and accommodates the second cylindrical portion 132 and the connecting portion therein. It is possible to do. Accordingly, the second cylindrical portion 132 can slide on the outer sliding portion 51c, that is, on the inner wall 510 of the outer sliding portion 51c.

  The control pressure chamber 13 b is formed between the second cylindrical portion 132, the connecting portion 133, and the drive shaft 3 in the outer sliding portion 51 c and is partitioned from the swash plate chamber 25. The control pressure chamber 13b and the swash plate chamber 25 are sealed by O-rings 49c and 49d.

  A throttle hole 57 is formed on the front end side of the connecting portion 133, that is, on the side close to the second cylindrical portion 132 in the connecting portion 133. The throttle hole 57 corresponds to the communication path in the present invention.

  The throttle hole 57 extends at the connecting portion 133 so as to be inclined upward from the front end side toward the rear end side. More specifically, in this throttle hole 57, the lubricating oil discharged together with the refrigerant gas from the throttle hole 57 is supplied to the sliding portion between the second cylindrical portion 132 and the inner wall 510 of the outer sliding portion 51c. It extends. As described above, since the inside of the outer sliding portion 51 c communicates with the swash plate chamber 25, the control pressure chamber 13 b and the swash plate chamber 25 communicate with each other through the throttle hole 57. Note that the throttle hole 57 may be formed in the second cylindrical portion 132.

  As shown in FIG. 1, in the drive shaft 3, an axial path 3a extending in the direction of the drive axis O1 from the rear end to the front end of the drive shaft 3, and a drive shaft extending in the radial direction from the front end of the axial path 3a. 3 is formed on the outer peripheral surface of the main body 3. The rear end of the axis 3 a is open to the pressure adjustment chamber 31. On the other hand, the path 3b is open to the control pressure chamber 13b. The pressure adjusting chamber 31 and the control pressure chamber 13b communicate with each other by the axial path 3a and the radial path 3b.

  The drive shaft 3 is connected to a pulley or an electromagnetic clutch (not shown) by a screw portion 3e formed at the tip.

  Each piston 9 is housed in each cylinder bore 21a, and can reciprocate in each cylinder bore 21a. Each piston 9 and the valve forming plate 23 define a compression chamber 59 in each cylinder bore 21a.

  Further, each piston 9 is provided with an engaging portion 9a. In the engaging portion 9a, hemispherical shoes 11a and 11b are respectively provided. Each shoe 11 a, 11 b converts the rotation of the swash plate 5 into the reciprocating motion of each piston 9. Each of these shoes 11a and 11b corresponds to a conversion mechanism in the present invention. Thus, each piston 9 can reciprocate within the cylinder bore 21a with a stroke corresponding to the inclination angle of the swash plate 5.

  As shown in FIG. 2, the control mechanism 15 includes a low pressure passage 15a, a high pressure passage 15b, a low pressure control valve 15c, a high pressure control valve 15d, an axial passage 3a, a radial passage 3b, and the throttle hole 57. It is configured.

  The low pressure passage 15 a is connected to the pressure adjustment chamber 31 and the suction chamber 33. Thus, the control pressure chamber 13b, the pressure adjusting chamber 31, and the suction chamber 33 are in communication with each other by the low pressure passage 15a, the axial passage 3a, and the radial passage 3b. The low pressure passage 15a, the axial path 3a, the radial path 3b, and the throttle hole 57 form a bleed passage in the present invention.

  The high-pressure passage 15 b is connected to the pressure adjustment chamber 31 and the discharge chamber 35. The control pressure chamber 13b, the pressure adjustment chamber 31, and the discharge chamber 35 are communicated with each other by the high pressure passage 15b, the axial path 3a, and the radial path 3b. The high pressure passage 15b, the axial path 3a, and the radial path 3b form an air supply path in the present invention.

  The low pressure control valve 15c is provided in the low pressure passage 15a. The low pressure control valve 15c can adjust the opening of the low pressure passage 15a based on the pressure in the suction chamber 33. The high pressure control valve 15d is provided in the high pressure passage 15b. The high pressure control valve 15 d can adjust the opening degree of the high pressure passage 15 b based on the pressure in the suction chamber 33.

  In this compressor, a pipe connected to the evaporator is connected to the suction port 250 shown in FIG. 1, and a pipe connected to the condenser is connected to the discharge port. The condenser is connected to the evaporator via a pipe and an expansion valve. These compressors, evaporators, expansion valves, condensers and the like constitute a refrigeration circuit for a vehicle air conditioner. In addition, illustration of an evaporator, an expansion valve, a condenser, and each piping is abbreviate | omitted.

  In the compressor configured as described above, when the drive shaft 3 rotates, the swash plate 5 rotates and each piston 9 reciprocates in each cylinder bore 21a. For this reason, the compression chamber 59 changes the volume according to the piston stroke. Therefore, the refrigerant gas sucked into the swash plate chamber 25 from the evaporator through the suction port 250 is compressed in the compression chamber 59 from the suction passage 39 through the suction chamber 33. The refrigerant gas compressed in the compression chamber 59 is discharged to the discharge chamber 35 and discharged from the discharge port to the condenser.

  In this compressor, it is possible to change the discharge capacity by changing the inclination angle of the swash plate 5 by the actuator 13 and increasing / decreasing the stroke of the piston 9.

  Specifically, in this compressor, in the control mechanism 15, the high pressure control valve 15d shown in FIG. 2 adjusts the opening of the high pressure passage 15b, whereby the pressure in the pressure adjustment chamber 31 and thus in the control pressure chamber 13b. Is increased by the refrigerant gas in the discharge chamber 35. Moreover, the pressure in the control pressure chamber 13b is lowered by adjusting the opening of the low pressure passage 15a by the low pressure control valve 15c.

  Further, in this compressor, the refrigerant gas in the control pressure chamber 13 b is discharged through the throttle hole 57 into the outer sliding portion 51 c and eventually into the swash plate chamber 25. Thus, in this compressor, the pressure in the control pressure chamber 13b is adjusted by adjusting the opening degrees of the high-pressure passage 15b and the low-pressure control valve 15c and discharging the refrigerant gas through the throttle hole 57.

  Here, if the high-pressure control valve 15d decreases the opening of the high-pressure passage 15b or the low-pressure control valve 15c increases the opening of the low-pressure passage 15a, the pressure in the control pressure chamber 13b decreases. At this time, the refrigerant gas in the control pressure chamber 13 b is discharged to the swash plate chamber 25 through the throttle hole 57 as described above. For this reason, the pressure difference between the control pressure chamber 13b and the swash plate chamber 25 is reduced. Therefore, as shown in FIG. 1, due to the piston compression force acting on the swash plate 5, in the actuator 13, the moving body 13a slides outward from the swash plate 5 side toward the lug plate 51 side in the direction of the drive axis O1. It slides in the part 51c.

  At the same time, in this compressor, the guide surface 51e is slid so that each swash plate arm 5e is remote from the drive axis O1. For this reason, in the swash plate 5, the bottom dead center side is swung clockwise while substantially maintaining the top dead center position T. Thus, in this compressor, the inclination angle of the swash plate 5 with respect to the drive axis O1 of the drive shaft 3 increases. Thereby, in this compressor, the stroke of piston 9 increases and the discharge capacity per one rotation of drive shaft 3 becomes large. The inclination angle of the swash plate 5 shown in FIG. 1 is the maximum inclination angle in this compressor.

On the other hand, if the high-pressure control valve 15d shown in FIG. 2 increases the opening of the high-pressure passage 15b or the low-pressure control valve 15c decreases the opening of the low-pressure passage 15a, the pressure in the control pressure chamber 13b increases. . For this reason, the pressure difference between the control pressure chamber 13b and the swash plate chamber 25 increases. Also at this time, the refrigerant gas is discharged to the swash plate chamber 25 through the throttle hole 57. As a result, as shown in FIG. 4, the moving body 13a slides in the outer sliding portion 51c in the direction of the drive axis O1 toward the swash plate 5 side while being remote from the lug plate 51.
Thereby, in this compressor, the action part 134 presses the convex part 5g toward the rear of the swash plate chamber 25. For this reason, the sliding surface 51b is slid so that each swash plate arm 5e comes close to the drive axis O1. Thereby, in the swash plate 5, the bottom dead center side swings counterclockwise while maintaining the top dead center position T substantially. Thus, in this compressor, the inclination angle of the swash plate 5 with respect to the drive axis O1 of the drive shaft 3 decreases. Thereby, in this compressor, the stroke of the piston 9 is reduced, and the discharge capacity per one rotation of the drive shaft 3 is reduced. The inclination angle of the swash plate 5 shown in FIG. 4 is the minimum inclination angle in this compressor.

  Thus, in this compressor, in adjusting the pressure in the control pressure chamber 13b, in addition to adjusting the opening degrees of the high pressure passage 15b and the low pressure control valve 15c, the swash plate chamber is formed from the control pressure chamber 13b through the throttle hole 57. The refrigerant gas is discharged to 25. Therefore, in this compressor, it is not necessary to completely seal the control pressure chamber 13b when adjusting the pressure in the control pressure chamber 13b, and only the control pressure chamber 13b is sealed by the O-rings 49c and 49d. Is enough.

  The throttle hole 57 discharges the lubricating oil together with the refrigerant gas from the control pressure chamber 13c to the swash plate chamber. For this reason, in this compressor, even when the lubricating oil flows into the control pressure chamber 13b together with the refrigerant gas when the refrigerant gas in the discharge chamber 35 is introduced into the control pressure chamber 13b, the lubricating oil remains in the throttle hole. Through 57, the refrigerant gas is discharged from the control pressure chamber 13b to the swash plate chamber 25.

  Here, in this compressor, the throttle hole 57 is formed in the connecting portion 133. For this reason, in this compressor, the lubricating oil can be suitably discharged from the throttle hole 57 by the centrifugal force when the moving body 13a rotates. For this reason, in this compressor, it is difficult for the lubricating oil to be stored in the control pressure chamber 13b, and a shortage of lubricating oil in the swash plate chamber 25 is difficult to occur.

  Here, in this compressor, in the throttle hole 57, the lubricating oil discharged together with the refrigerant gas from the throttle hole 57 is supplied to the sliding portion between the second cylindrical portion 132 and the inner wall 510 of the outer sliding portion 51c. It extends like so. For this reason, in this compressor, when the inclination angle of the swash plate 5 decreases from the maximum state, that is, toward the swash plate 5 side, the moving body 13a moves in the outer sliding portion 51c in the direction of the drive axis O1. When sliding, the sliding portion between the second cylindrical portion 132 and the inner wall 510 of the outer sliding portion 51c is suitably lubricated by the lubricating oil discharged from the throttle hole 57. For this reason, in this compressor, the 2nd cylindrical part 132 can slide suitably on the inner wall 510 of the outer side sliding part 51c. For this reason, in this compressor, the discharge capacity per rotation of the drive shaft 3 can be suitably changed over a long period of time.

  Therefore, the compressor according to the first embodiment exhibits high performance over a long period of time while realizing a reduction in manufacturing cost in the compressor that changes the discharge capacity using the actuator 13.

(Example 2)
As shown in FIG. 5, in the compressor of the second embodiment, a throttle hole 61 is provided instead of the throttle hole 57 in the compressor of the first embodiment. The throttle hole 61 is formed in the fixed flange portion 51 b of the lug plate 51. The throttle hole 61 extends from the control pressure chamber 13 b side to the front wall 17 a side so that the lubricating oil discharged together with the refrigerant gas from the throttle hole 61 is supplied to the thrust bearing 55, and in the vicinity of the thrust bearing 55. It is open at. As a result, the control pressure chamber 13 b and the swash plate chamber 25 communicate with each other through the throttle hole 61. In this compressor, the bleed passage in the present invention is formed by the low pressure passage 15a, the axial passage 3a, the radial passage 3b, and the throttle hole 61. In addition, you may form the aperture hole 61 in the fixing | fixed part 51a. Other configurations of the compressor are the same as those of the compressor according to the first embodiment, and the same components are denoted by the same reference numerals and detailed description thereof is omitted.

  In this compressor, when adjusting the pressure in the control pressure chamber 13b, in addition to adjusting the opening degree of the high pressure passage 15b and the low pressure control valve 15c, the refrigerant gas is transferred from the control pressure chamber 13b to the swash plate chamber 25 through the throttle hole 61. Is discharged. Here, in this compressor, the throttle hole 61 is formed in the fixed flange portion 51 b so that the lubricating oil discharged together with the refrigerant gas from the throttle hole 61 is supplied to the thrust bearing 55. Therefore, in this compressor, the thrust bearing 55 can be lubricated by the lubricating oil discharged from the throttle hole 61. For this reason, in this compressor, seizure hardly occurs in the thrust bearing 55, and durability can be increased. Other functions of this compressor are the same as those of the compressor of the first embodiment.

(Example 3)
As shown in FIG. 6, in the compressor of the third embodiment, a throttle hole 63 is provided instead of the throttle hole 57 in the compressor of the first embodiment. The throttle hole 63 is formed in the fixed flange portion 51 b of the lug plate 51. The throttle hole 63 extends from the control pressure chamber 13b side to the drive shaft 3 side so that the lubricating oil discharged together with the refrigerant gas from the throttle hole 61 is supplied to the first sliding bearing 29a. As a result, the control pressure chamber 13 b and the swash plate chamber 25 communicate with each other through the throttle hole 63. In this compressor, the bleed passage in the present invention is formed by the low pressure passage 15a, the axial passage 3a, the radial passage 3b, and the throttle hole 63. In addition, you may form the aperture hole 63 in the fixing | fixed part 51a. Other configurations of this compressor are the same as those of the compressor of the first embodiment.

  In this compressor, when adjusting the pressure in the control pressure chamber 13b, in addition to adjusting the opening degree of the high pressure passage 15b and the low pressure control valve 15c, the refrigerant gas is transferred from the control pressure chamber 13b to the swash plate chamber 25 through the throttle hole 63. Is discharged. Here, in this compressor, the throttle hole 63 is formed in the fixed flange portion 51b so that the lubricating oil discharged together with the refrigerant gas from the throttle hole 63 is supplied to the first sliding bearing 29a. Therefore, in this compressor, the first sliding bearing 29a can be lubricated by the lubricating oil discharged from the throttle hole 63. For this reason, in this compressor, seizure hardly occurs between the drive shaft 3 and the first sliding bearing 29a, and durability can be increased. Other functions of this compressor are the same as those of the compressor of the first embodiment.

Example 4
As shown in FIG. 7, in the compressor of the fourth embodiment, the shapes of the front housing 17 and the lug plate 51 in the compressor of the first embodiment are partially changed, and each of the shaft seal device 27 and the first sliding bearing 29a is changed. The arrangement has been changed. Specifically, in this compressor, the shaft seal device 27 is formed in the first shaft hole 17d by expanding the first shaft hole 17d in the front housing 17 as compared with the compressor of the first embodiment. It is placed inside. As a result, the shaft seal device 27 faces the swash plate chamber 25. Further, in this compressor, the first sliding bearing 29a is arranged between the front wall 17a and the fixed flange portion 51b by extending the lug plate 51 forward as compared with the compressor of the first embodiment. Yes.

  Further, in this compressor, a throttle hole 65 is provided instead of the throttle hole 57 in the compressor of the first embodiment. The throttle hole 65 is formed in the fixed flange portion 51 b of the lug plate 51. The throttle hole 65 extends from the control pressure chamber 13 b side toward the front housing 17 side so that the lubricating oil discharged together with the refrigerant gas from the throttle hole 65 is supplied to the shaft seal device 27. As a result, the control pressure chamber 13 b and the swash plate chamber 25 communicate with each other through the throttle hole 65. In this compressor, the extraction passage in the present invention is formed by the low-pressure passage 15a, the axial passage 3a, the radial passage 3b, and the throttle hole 65. Other configurations of this compressor are the same as those of the compressor of the first embodiment.

  In this compressor, when adjusting the pressure in the control pressure chamber 13b, in addition to adjusting the opening degree of the high pressure passage 15b and the low pressure control valve 15c, the refrigerant gas is transferred from the control pressure chamber 13b to the swash plate chamber 25 through the throttle hole 65. Is discharged. Here, in this compressor, the throttle hole 65 is formed in the fixed flange portion 51 b so that the lubricating oil discharged together with the refrigerant gas from the throttle hole 65 is supplied to the shaft seal device 27. For this reason, in this compressor, the shaft seal device 27 can be lubricated by the lubricating oil discharged from the throttle hole 65. For this reason, in this compressor, between the shaft seal device 27 and the drive shaft 3 is suitably lubricated.

  Further, in this compressor, the first sliding bearing 29a is disposed between the front wall 17a and the fixed flange portion 51b while the shaft sealing device 27 is disposed in the first shaft hole 17d. For this reason, in this compressor, it is possible to arrange the shaft seal device 27 and the lug plate 51 close to each other as compared with the compressor of the first embodiment, and to shorten the boss 17c. Is possible. Thereby, in this compressor, compared with the compressor of Example 1, size reduction is possible. Other functions of this compressor are the same as those of the compressor of the first embodiment.

(Example 5)
As shown in FIG. 8, the compressor of the fifth embodiment includes a housing 10, a drive shaft 30, a swash plate 50, a link mechanism 70, a plurality of pistons 90, a pair of shoes 110a and 110b, and an actuator 160. And a control mechanism 150 shown in FIG.

  As shown in FIG. 8, the housing 10 includes a front housing 117 located in front of the compressor, a rear housing 119 located behind the compressor, and a first housing located between the front housing 117 and the rear housing 119. 2 cylinder blocks 121 and 123 and first and second valve forming plates 139 and 141.

  The front housing 117 is formed with a boss 117a that protrudes forward. A shaft seal device 125 is provided in the boss 117a to ensure airtightness between the inside and the outside of the housing 10. In the front housing 117, a first suction chamber 127a and a first discharge chamber 129a are formed. The first suction chamber 127 a is located on the inner peripheral side of the front housing 117. The first discharge chamber 129a is formed in an annular shape, and is located on the outer peripheral side of the first suction chamber 127a in the front housing 117.

  Further, the front housing 117 is formed with a first front communication path 118a. The first front side communication path 118 a has a front end side communicating with the first discharge chamber 129 a and a rear end side opened to the rear end of the front housing 117.

  The rear housing 119 is provided with part of the control mechanism 150 described above. The rear housing 119 is formed with a second suction chamber 127b, a second discharge chamber 129b, and a pressure adjustment chamber 131. The pressure adjustment chamber 131 is located in the center portion of the rear housing 119. The second suction chamber 127 b is formed in an annular shape, and is located on the outer peripheral side of the pressure adjustment chamber 131 in the rear housing 119. The second discharge chamber 129b is also formed in an annular shape, and is located on the outer peripheral side of the second suction chamber 127b in the rear housing 119.

  Further, the rear housing 119 is formed with a first rear communication path 120a. The rear end side of the first rear side communication passage 120 a communicates with the second discharge chamber 129 b, and the front end side opens at the front end of the rear housing 119.

  A swash plate chamber 330 is formed between the first cylinder block 121 and the second cylinder block 123.

  In the first cylinder block 121, a plurality of first cylinder bores 121a are formed in parallel at equal angular intervals in the circumferential direction. The first cylinder block 121 is formed with a first shaft hole 121b through which the drive shaft 30 is inserted. A first sliding bearing 122a is provided in the first shaft hole 121b.

  Further, the first cylinder block 121 is formed with a first recess 121c that communicates with the first shaft hole 121b and is coaxial with the first shaft hole 121b. The first recess 121 c communicates with the swash plate chamber 330 and is a part of the swash plate chamber 330. A first thrust bearing 135a is provided at the front end of the first recess 121c. Further, the first cylinder block 121 is formed with a first communication path 137a that communicates the swash plate chamber 330 and the first suction chamber 127a. Further, the first cylinder block 121 is provided with a first retainer groove 121e for restricting the maximum opening degree of each first suction reed valve 691a described later.

  Further, a second front side communication path 118b is formed in the first cylinder block 121. The front end of the second front side communication path 118 b is open to the front end side of the first cylinder block 121, and the rear end is open to the rear end side of the first cylinder block 121.

  Similarly to the first cylinder block 121, a plurality of second cylinder bores 123 a are formed in the second cylinder block 123. Each second cylinder bore 123a is paired with each first cylinder bore 121a at the front and rear.

  The second cylinder block 123 is formed with a second shaft hole 123b through which the drive shaft 3 is inserted. The second shaft hole 123b communicates with the pressure adjustment chamber 131 on the rear end side. A second sliding bearing 122b is provided in the second shaft hole 123. In addition, it may replace with said 1st sliding bearing 122a and said 2nd sliding bearing 22b, and may each provide a rolling bearing.

  The second cylinder block 123 has a second recess 123c that communicates with the second shaft hole 123b and is coaxial with the second shaft hole 123b. The second recess 123 c is also in communication with the swash plate chamber 330 and is a part of the swash plate chamber 330. A second thrust bearing 135b is provided at the rear end of the second recess 123c. The second thrust bearing 135b corresponds to the thrust bearing in the present invention. Further, the second cylinder block 123 is formed with a second communication path 137b that communicates the swash plate chamber 330 and the second suction chamber 127b. Further, the second cylinder block 123 is provided with a second retainer groove 123e for restricting the maximum opening degree of each second suction reed valve 711a described later.

  In the second cylinder block 123, a discharge port 126, a merged discharge chamber 128, a third front side communication path 118c, a second rear side communication path 120b, and a suction port 330a are formed. The discharge port 126 and the merged discharge chamber 128 communicate with each other. The merging / discharging chamber 128 is connected to a condenser (not shown) constituting a pipe line via a discharge port 126.

  The front end side of the third front side communication path 118 c is open to the front end of the second cylinder block 123, and the rear end side communicates with the merged discharge chamber 128. The third front-side communication path 118c communicates with the rear end side of the second front-side communication path 118b by joining the first cylinder block 121 and the second cylinder block 123 together.

  An evaporator (not shown) that configures a pipe line is connected to the suction port 330a. Thereby, the swash plate chamber 330 and the evaporator are connected via the suction port 330a.

  The first valve forming plate 139 is provided between the front housing 117 and the first cylinder block 121. The second valve forming plate 141 is provided between the rear housing 119 and the second cylinder block 123.

  The first valve forming plate 139 includes a first valve plate 690, a first suction valve plate 691, a first discharge valve plate 692, and a first retainer plate 693. The first valve plate 690, the first discharge valve plate 692, and the first retainer plate 693 have the same number of first suction holes 690a as the first cylinder bores 121a. The first valve plate 690 and the first intake valve plate 691 are formed with the same number of first discharge holes 690b as the first cylinder bores 121a. Further, a first suction communication hole 690 c is formed in the first valve plate 690, the first suction valve plate 691, the first discharge valve plate 692, and the first retainer plate 693. The first valve plate 690 and the first suction valve plate 691 are formed with a first discharge communication hole 690d.

  Each first cylinder bore 121a communicates with the first suction chamber 127a through each first suction hole 690a. Each first cylinder bore 121a communicates with the first discharge chamber 129a through each first discharge hole 690b. The first suction chamber 127a and the first communication path 137a communicate with each other through the first suction communication hole 690c. The first front communication path 118a and the second front communication path 118b communicate with each other through the first discharge communication hole 690d.

  The first suction valve plate 691 is provided on the rear surface of the first valve plate 690. The first suction valve plate 691 is formed with a plurality of first suction reed valves 691a capable of opening and closing the first suction holes 690a by elastic deformation. The first discharge valve plate 692 is provided on the front surface of the first valve plate 690. The first discharge valve plate 692 is formed with a plurality of first discharge reed valves 692a capable of opening and closing each first discharge hole 690b by elastic deformation. The first retainer plate 693 is provided on the front surface of the first discharge valve plate 692. The first retainer plate 693 regulates the maximum opening of each first discharge reed valve 692a.

  The second valve forming plate 141 includes a second valve plate 710, a second suction valve plate 711, a second discharge valve plate 712, and a second retainer plate 713. In the second valve plate 710, the second discharge valve plate 712, and the second retainer plate 713, the same number of second suction holes 710a as the second cylinder bores 123a are formed. The second valve plate 710 and the second intake valve plate 711 are formed with the same number of second discharge holes 710b as the second cylinder bores 123a. Further, a second suction communication hole 710c is formed in the second valve plate 710, the second suction valve plate 711, the second discharge valve plate 712, and the second retainer plate 713. A second discharge communication hole 710d is formed in the second valve plate 710 and the second suction valve plate 711.

  Each second cylinder bore 123a communicates with the second suction chamber 127b through each second suction hole 710a. Each second cylinder bore 123a communicates with the second discharge chamber 129b through each second discharge hole 710b. The second suction chamber 127b and the second communication path 137b communicate with each other through the second suction communication hole 710c. The first rear communication path 120a and the second rear communication path 120b communicate with each other through the second discharge communication hole 710d.

  The second intake valve plate 711 is provided on the front surface of the second valve plate 710. The second suction valve plate 711 is formed with a plurality of second suction reed valves 711a that can open and close the second suction holes 710a by elastic deformation. The second discharge valve plate 712 is provided on the rear surface of the second valve plate 710. In the second discharge valve plate 712, a plurality of second discharge reed valves 712a capable of opening and closing each second discharge hole 710b by elastic deformation are formed. The second retainer plate 713 is provided on the rear surface of the second discharge valve plate 712. The second retainer plate 713 regulates the maximum opening of each second discharge reed valve 712a.

  In this compressor, a first discharge communication path 118 is formed by the first front communication path 118a, the first discharge communication hole 690d, the second front communication path 118b, and the third front communication path 118c. Further, a second discharge communication path 120 is formed by the first rear communication path 120a, the second discharge communication hole 710d, and the second rear communication path 120b.

  In this compressor, the first and second suction chambers 127a and 127b and the swash plate chamber 330 communicate with each other through the first and second communication paths 137a and 137b and the first and second suction communication holes 690c and 710c. Therefore, the pressures in the first and second suction chambers 127a and 127b and the swash plate chamber 330 are substantially equal. Since the low-pressure refrigerant gas that has passed through the evaporator flows into the swash plate chamber 330 through the suction port 330a, the respective pressures in the swash plate chamber 330 and the first and second suction chambers 127a and 127b are the first, second, and second pressures. The pressure is lower than that in the discharge chambers 129a and 129b.

  The drive shaft 30 includes a drive shaft main body 300, a first support member 143a, and a second support member 143b. The drive shaft main body 300 extends from the front side to the rear side of the housing 1, is inserted rearward from the boss 117a, and is inserted into the first and second sliding bearings 122a and 122b. As a result, the drive shaft main body 300 and thus the drive shaft 30 are pivotally supported by the housing 10 so as to be rotatable around the drive axis O2. The front end of the drive shaft main body 300 is located in the boss 117 a and the rear end protrudes into the pressure adjustment chamber 131.

  The drive shaft main body 300 is provided with a swash plate 50, a link mechanism 70, and an actuator 160. The swash plate 50, the link mechanism 70, and the actuator 160 are disposed in the swash plate chamber 330, respectively.

  The first support member 143a is press-fitted to the front end side of the drive shaft main body 300 and is located in the first shaft hole 121b. The first support member 143a is formed with a flange 430 that contacts the first thrust bearing 135a and an attachment portion (not shown) through which a second pin 147b described later is inserted. Further, the front end of the first return spring 144a is fixed to the first support member 143a. The first return spring 144a extends from the first support member 143a side toward the swash plate chamber 330 side in the direction of the drive axis O2.

  As shown in FIG. 10, the second support member 143b is press-fitted to the rear end side of the drive shaft main body 300, and is located in the second shaft hole 123b. A flange 431 that contacts the second thrust bearing 135b is formed at the front end of the second support member 143b. The second support member 143b is provided with O-rings 73a and 73b.

  As shown in FIG. 8, the swash plate 50 has an annular flat plate shape and has a front surface 50a and a rear surface 50b. The front surface 50 a faces the front of the compressor in the swash plate chamber 330. The rear surface 50 b faces the rear of the compressor in the swash plate chamber 330.

  The swash plate 50 is fixed to the ring plate 145. The ring plate 145 is formed in an annular flat plate shape, and an insertion hole 145a is formed at the center. The swash plate 50 is attached to the drive shaft 30 by inserting the drive shaft main body 300 through the insertion hole 145 a in the swash plate chamber 330.

  The link mechanism 70 has a lug arm 149. The lug arm 149 is disposed in front of the swash plate 50 in the swash plate chamber 330, and is located between the swash plate 50 and the first support member 143a. The lug arm 149 is formed to be substantially L-shaped from the front end side toward the rear end side. A weight portion 149 a is formed on the rear end side of the lug arm 149. The weight portion 149a extends approximately half a circumference in the circumferential direction of the actuator 160. The shape of the weight portion 149a can be designed as appropriate.

  The rear end side of the lug arm 149 is connected to one end side of the ring plate 145 by the first pin 147a. Thereby, the front end side of the lug arm 149 is arranged around the first swing axis M1 with respect to one end side of the ring plate 145, that is, the swash plate 50, with the axis of the first pin 147a as the first swing axis M1. It is supported so that it can swing. The first swing axis M1 extends in a direction orthogonal to the drive axis O2 of the drive shaft 30.

  The front end side of the lug arm 149 is connected to the first support member 143a by the second pin 147b. As a result, the front end side of the lug arm 149 swings around the second swing axis M2 with respect to the first support member 143a, that is, the drive shaft 30, with the second pivot 147b being the second pivot axis M2. It is supported movably. The second swing axis M2 extends in parallel with the first swing axis M1. The link mechanism 70 is constituted by the lug arm 149 and the first and second pins 147a and 147b.

  The weight portion 149a is provided to extend to the rear end side of the lug arm 149, that is, the opposite side of the second swing axis M2 with respect to the first swing axis M1. For this reason, the lug arm 149 is supported on the ring plate 145 by the first pin 147a, so that the weight portion 149a passes through the groove portion 145b of the ring plate 145 and is placed on the rear surface of the ring plate 145, that is, the rear surface 50b side of the swash plate 50. To position. The centrifugal force generated by the rotation of the swash plate 50 around the drive axis O2 also acts on the weight portion 149a on the rear surface 50b side of the swash plate 50.

  In this compressor, the swash plate 50 and the drive shaft 30 are connected by the link mechanism 70, so that the swash plate 50 can rotate with the drive shaft 30. Further, both ends of the lug arm 149 swing around the first swing axis M1 and the second swing axis M2, respectively, so that the inclination angle of the swash plate 50 can be changed.

  Each piston 90 has a first head 90a on the front end side and a second head 90b on the rear end side. Each first head 90a is accommodated in each first cylinder bore 121a so as to reciprocate. The first compression chambers 121d are defined in the first cylinder bores 121a by the first heads 90a and the first valve forming plate 139, respectively. Each second head 90b is accommodated in each second cylinder bore 123a so as to reciprocate. The second compression chambers 123d are defined in the second cylinder bores 123a by the second heads 90b and the second valve forming plate 141, respectively.

  In addition, an engaging portion 90 c is formed at the center of each piston 90. In each engagement portion 90c, hemispherical shoes 110a and 110b are provided, respectively. The rotation of the swash plate 50 is converted into the reciprocating motion of the piston 90 by these shoes 110a and 110b. The shoes 110a and 110b correspond to the conversion mechanism in the present invention. Thus, in this compressor, the first and second heads 90a and 90b can reciprocate in the first and second cylinder bores 121a and 123a, respectively, with a stroke corresponding to the inclination angle of the swash plate 50. . As shown in FIG. 10, in this compressor, as the inclination angle of the swash plate 50 becomes smaller, the top dead center position of the second head 90b than the top dead center position of the first head 90a. Moves greatly.

  The actuator 160 is disposed in the swash plate chamber 330. The actuator 160 is located on the rear side of the swash plate 50 and can enter the second recess 123c. As shown in FIG. 10, the actuator 13 includes a moving body 160a, a partition body 160b, and a control pressure chamber 160c. The control pressure chamber 160c is formed between the movable body 160a and the partition body 160b.

  The moving body 160a includes an inner sliding portion 161, a bottom wall 162, a peripheral wall 163, and a connecting portion 164. The inner sliding portion 161 is located at the rear end of the moving body 160a. The drive shaft main body 300 is inserted through the inner sliding portion 161. Thus, the inner sliding portion 161 is slidably provided on the drive shaft main body 300. The inner sliding portion 161 is provided with an O-ring 73c. The bottom wall 162 extends from the rear end of the peripheral wall 161 toward the drive shaft main body 300 at the rear end of the moving body 160a. The bottom wall 162 is continuous with the inner sliding portion 161. The peripheral wall 163 extends from the tip of the bottom wall 162 toward the front end in the direction of the drive axis O2. Thus, the peripheral wall 163 has a cylindrical shape that is concentric with the drive axis O2. As shown in FIG. 8, the connecting portion 164 is formed at the front end of the peripheral wall 163.

  As shown in FIG. 10, the partition body 160 b has a disk shape having substantially the same diameter as the inner diameter of the movable cylinder portion 163. A fixing portion 165 is provided on the center side of the partition body 160b. The drive shaft main body 300 is press-fitted into the fixed portion 165 to be fixed to the drive shaft 30. An O-ring 73d is provided on the outer peripheral surface of the partition 160b. The partition 160b may be provided on the drive shaft 30 so as to be movable in the direction of the drive axis O2.

  As shown in FIG. 8, a second return spring 144b is provided between the partition 160b and the ring plate 145. Specifically, the rear end of the second return spring 144b is fixed to the partition body 160b, and the front end of the second return spring 144b is fixed to the other end side of the ring plate 145.

  As described above, when the drive shaft main body 30 is inserted into the inner sliding portion 161 and the fixed portion 165, the moving body 160a is linked to the swash plate 50 with the swash plate 50 interposed therebetween. It is arranged in a state facing the mechanism 70. On the other hand, the partition 160 b is disposed in the moving body 160 a behind the swash plate 50, and its periphery is surrounded by the peripheral wall 163. Thereby, a control pressure chamber 160c is formed between the moving body 160a and the partition body 160b. The control pressure chamber 160c is partitioned from the swash plate chamber 330 by the moving body 160a and the partition body 160b.

  As shown in FIG. 10, a throttle hole 75 is formed in the partition 160b. The throttle hole 75 extends from the control pressure chamber 160c side toward the swash plate chamber 330 side. More specifically, the throttle hole 75 is inclined from the control chamber 160c side so that the lubricating oil discharged together with the refrigerant gas from the throttle hole 75 is supplied to the sliding portion between the inner wall 136a of the peripheral wall 163 and the partition 160b. It extends so as to be inclined upward toward the board chamber 330 side. The control pressure chamber 160 c and the swash plate chamber 330 communicate with each other through the throttle hole 75.

  As shown in FIG. 8, the other end side of the ring plate 145 is connected to the connecting portion 164 of the moving body 160a by a third pin 147c. Thereby, the other end side of the ring plate 145, that is, the swash plate 50 is supported by the movable body 160a so as to be swingable around the action axis M3, with the axis of the third pin 147c as the action axis M3. . The action axis M3 extends in parallel with the first and second oscillation axes M1 and M2. Thus, the moving body 160a is connected to the swash plate 50.

  Further, in the drive shaft main body 300, an axis 30a extending in the direction of the drive axis O from the rear end toward the front, and a path extending in the radial direction from the front end of the axis 30a and opening on the outer peripheral surface of the drive shaft main body 300. 30b. The rear end of the axial path 30 a is open to the pressure adjustment chamber 131. On the other hand, the path 30b is open to the control pressure chamber 160c. Thus, the control pressure chamber 160c communicates with the pressure adjustment chamber 131 through the radial path 30b and the axial path 30a.

  A screw portion 30 d is formed at the tip of the drive shaft main body 300. The drive shaft 30 is connected to a pulley or an electromagnetic clutch (not shown) via the screw portion 30d.

  As shown in FIG. 9, the control mechanism 150 includes a low pressure passage 150a, a high pressure passage 150b, a low pressure control valve 150c, a high pressure control valve 150d, an axial passage 30a, a radial passage 30b, and the throttle hole 75. It is configured.

  The low pressure passage 150a is connected to the pressure adjustment chamber 131 and the second suction chamber 127b. Thereby, the control pressure chamber 160b, the pressure adjustment chamber 131, and the second suction chamber 127b are in communication with each other by the low pressure passage 150a, the axial passage 30a, and the radial passage 30b. The low pressure passage 150a, the axial passage 30a, the radial passage 30b, and the throttle hole 75 form an extraction passage in the present invention.

  The high-pressure passage 150b is connected to the pressure adjustment chamber 131 and the second discharge chamber 129b. The high pressure passage 150b, the axial path 30a, and the radial path 30b communicate with the control pressure chamber 160c, the pressure adjustment chamber 131, and the second discharge chamber 129b. The high pressure passage 150b, the axial passage 30a, and the radial passage 30b form an air supply passage in the present invention.

  The low pressure control valve 150c is provided in the low pressure passage 150a. The low pressure control valve 150c can adjust the opening of the low pressure passage 150a based on the pressure in the second suction chamber 127b. The high pressure control valve 150d is provided in the high pressure passage 150b. The high pressure control valve 150d can adjust the opening of the high pressure passage 150b based on the pressure in the second suction chamber 127b.

  In this compressor, piping connected to the evaporator is connected to the suction port 330 a shown in FIG. 8, and piping connected to the condenser is connected to the discharge port 126. The condenser is connected to the evaporator via a pipe and an expansion valve.

  In the compressor configured as described above, when the drive shaft 30 rotates, the swash plate 50 rotates, and each piston 90 reciprocates in the first and second cylinder bores 121a and 123a. For this reason, the first and second compression chambers 121d and 123d change in volume according to the piston stroke. For this reason, in this compressor, the suction stroke for sucking the refrigerant gas into the first and second compression chambers 121d and 123d, and the compression stroke for compressing the refrigerant gas in the first and second compression chambers 121d and 123d are compressed. The discharge stroke and the like in which the refrigerant gas is discharged into the first and second discharge chambers 129a and 129b are repeatedly performed.

  The refrigerant gas discharged into the first discharge chamber 129a reaches the merged discharge chamber 128 via the first discharge communication path 118. Similarly, the refrigerant gas discharged into the second discharge chamber 129b reaches the merged discharge chamber 128 via the second discharge communication path 120. Then, the refrigerant gas reaching the merged discharge chamber 128 is discharged from the discharge port 126 to the condenser.

  During these suction strokes and the like, a piston compression force that reduces the inclination angle of the swash plate 50 acts on the rotating body including the swash plate 50, the ring plate 145, the lug arm 149, and the first pin 147a. And also in this compressor, if the inclination angle of the swash plate 50 is changed, it is possible to perform capacity control by increasing or decreasing the stroke of the piston 90.

  Specifically, in the control mechanism 150, the high-pressure control valve 150d shown in FIG. 9 adjusts the opening of the high-pressure passage 150b, so that the pressure in the pressure adjustment chamber 131 and thus the pressure in the control pressure chamber 160b is changed to the second discharge chamber. It is raised by the refrigerant gas in 129b. Moreover, the pressure in the control pressure chamber 160b is lowered by adjusting the opening of the low pressure passage 150a by the low pressure control valve 150c.

  Further, also in this compressor, the refrigerant gas in the control pressure chamber 160 c is discharged to the swash plate chamber 330 through the throttle hole 75. Thus, in this compressor, the pressure in the control pressure chamber 160c is adjusted by adjusting the opening degree of the high pressure passage 150b and the low pressure control valve 150c and discharging the refrigerant gas through the throttle hole 75.

  Here, if the high-pressure control valve 150d decreases the opening of the high-pressure passage 150b or the low-pressure control valve 150c increases the opening of the low-pressure passage 150a, the pressure in the control pressure chamber 160c decreases. At this time, the refrigerant gas in the control pressure chamber 160 c is discharged to the swash plate chamber 330 through the throttle hole 75 as described above. For this reason, the pressure in the control pressure chamber 160c becomes low, and the pressure difference with the swash plate chamber 330 becomes small. Therefore, due to the piston compression force acting on the swash plate 50, as shown in FIG. 11, in the actuator 160, the moving body 160a moves in the second recess 123c toward the front side.

  Thereby, the other end side of the ring plate 145, that is, the other end side of the swash plate 50 is swung clockwise around the action axis M3 while resisting the urging force of the second return spring 144b. The rear end of the lug arm 149 swings clockwise around the first swing axis M1, and the front end of the lug arm 149 swings counterclockwise around the second swing axis M2. For this reason, the lug arm 149 approaches the flange 430 of the first support member 163a. As a result, the swash plate 50 swings with the operating axis M3 as the operating point and the first swinging axis M1 as the fulcrum. For this reason, the inclination angle of the swash plate 50 with respect to the drive axis O2 of the drive shaft 30 decreases, and the stroke of the piston 90 decreases. For this reason, in this compressor, the discharge capacity per one rotation of the drive shaft 30 becomes small. The inclination angle of the swash plate 50 shown in FIG. 11 is the minimum inclination angle in this compressor.

  Here, in this compressor, the centrifugal force acting on the weight portion 149a is also applied to the swash plate 50. For this reason, in this compressor, it is easy to displace the swash plate 50 in the direction to decrease the inclination angle.

  Further, as the inclination angle of the swash plate 50 decreases, the ring plate 145 contacts the rear end of the first return spring 144a. As a result, the first return spring 144a is elastically deformed, and the rear end of the first return spring 144a approaches the first support member 143a.

  Here, in this compressor, the inclination angle of the swash plate 50 is reduced, and the stroke of the piston 90 is reduced, whereby the top dead center position of the second head 90b is remote from the second valve forming plate 141. For this reason, in this compressor, when the inclination angle of the swash plate 50 approaches zero degrees, the compression work is slightly performed on the first compression chamber 121d side, while the compression work is performed on the second compression chamber 123d side. Disappear.

  On the other hand, if the high-pressure control valve 150d shown in FIG. 9 increases the opening of the high-pressure passage 150b or the low-pressure control valve 150c decreases the opening of the low-pressure passage 150a, the pressure in the control pressure chamber 160c increases. The pressure difference with the swash plate chamber 330 becomes large. Also at this time, the refrigerant gas in the control pressure chamber 160 c is discharged to the swash plate chamber 330 through the throttle hole 75. Therefore, against the piston compressive force acting on the swash plate 50, in the actuator 160, as shown in FIG. 8, the moving body 160a moves in the second recess 123c toward the rear side.

  As a result, the moving body 160a pulls the lower end side of the swash plate 50 to the rear side of the swash plate chamber 330 through the connecting portion 164 at the action axis M3. As a result, the other end of the swash plate 50 swings counterclockwise around the action axis M3. In addition, the rear end of the lug arm 149 swings counterclockwise around the first swing axis M1, and the front end of the lug arm 149 swings clockwise around the second swing axis M2. Therefore, the lug arm 149 is separated from the flange 430 of the first support member 163a. As a result, the swash plate 50 oscillates in the opposite direction to the case where the inclination angle becomes smaller with the action axis M3 and the first oscillation axis M1 as the action point and the fulcrum, respectively. For this reason, the inclination angle of the swash plate 5 with respect to the drive axis O2 of the drive shaft 30 increases, and the stroke of the piston 90 increases, so that the discharge capacity per one rotation of the drive shaft 30 increases. The inclination angle of the swash plate 50 shown in FIG. 8 is the maximum inclination angle in this compressor.

  Thus, in this compressor, in adjusting the pressure in the control pressure chamber 160c, in addition to adjusting the opening degree of the high pressure passage 150b and the low pressure control valve 150c, the swash plate chamber is formed from the control pressure chamber 160c through the throttle hole 75. The refrigerant gas is discharged to 330. Therefore, in this compressor, it is not necessary to completely seal the control pressure chamber 160c when adjusting the pressure in the control pressure chamber 160c, and only the control pressure chamber 160c is sealed by the O-rings 73c and 74d. Is enough.

  Also in this compressor, even when the lubricating oil flows into the control pressure chamber 160c together with the refrigerant gas when the refrigerant gas in the second discharge chamber 129b is introduced into the control pressure chamber 160c, Through the throttle hole 75, the refrigerant gas is discharged from the control pressure chamber 160c to the swash plate chamber 330. For this reason, similarly to the compressor of the first embodiment, in this compressor, it is difficult for the lubricating oil to be stored in the control pressure chamber 160c, and the lubricating oil shortage in the swash plate chamber 330 is difficult to occur.

  Here, as shown in FIG. 10, in this compressor, in the throttle hole 75, the lubricating oil discharged together with the refrigerant gas from the throttle hole 75 is supplied to the sliding portion between the inner wall 163a of the peripheral wall 163 and the partition 160b. As described above, the slope extends upward from the control chamber 160c side toward the swash plate chamber 330 side. Therefore, in this compressor, when the inclination angle of the swash plate 5 increases from the minimum state, that is, when the moving body 160a moves backward in the second recess 123c, The lubricating oil that has flowed out together with the refrigerant gas lubricates the inside of the peripheral wall 163. Here, in the peripheral wall 163, the front side of the partition body 160 b communicates with the swash plate chamber 330. And in this compressor, since the inner wall 163a of the cylinder part 163 is lubricated suitably with lubricating oil, the surrounding wall 163 can slide suitably the outer peripheral surface of the division body 160b. For this reason, in this compressor, the discharge capacity per rotation of the drive shaft 30 can be suitably changed over a long period of time.

(Example 6)
As shown in FIG. 12, in the compressor of the sixth embodiment, a throttle hole 77 is provided instead of the throttle hole 75 in the compressor of the fifth embodiment. The throttle hole 77 is formed in the bottom wall 162 of the moving body 160a. The throttle hole 77 extends from the control pressure chamber 160c side to the second thrust bearing 135b side so that the lubricating oil discharged together with the refrigerant gas from the throttle hole 77 is supplied to the second thrust bearing 135b. Thereby, the control pressure chamber 160 c and the swash plate chamber 330 communicate with each other through the throttle hole 77. In this compressor, the extraction passage in the present invention is formed by the low-pressure passage 150a, the axial passage 30a, the radial passage 30b, and the throttle hole 77. Other configurations of this compressor are the same as those of the compressor of the fifth embodiment.

  In this compressor, in adjusting the pressure in the control pressure chamber 160c, in addition to adjusting the opening degree of the high pressure passage 150b and the low pressure control valve 150c, the refrigerant gas is transferred from the control pressure chamber 160c to the swash plate chamber 330 through the throttle hole 77. Is discharged. Here, in this compressor, the throttle hole 77 is moved from the control pressure chamber 160c side to the second thrust bearing 135b side so that the lubricating oil discharged together with the refrigerant gas from the throttle hole 77 is supplied to the second thrust bearing 135b. It extends towards. Therefore, in this compressor, when the moving body 160a moves rearward in the second recess 123c, the lubricating oil in the control pressure chamber 160c and the refrigerant gas are throttled toward the second thrust bearing 135b. 77 will be discharged. Here, in this compressor, the moving body 160a and the second thrust bearing 135b gradually approach each other as the moving body 160a moves rearward in the second recess 123c. Thereby, in this compressor, the second thrust bearing 135b can be suitably lubricated by the lubricating oil discharged from the throttle hole 77. For this reason, in this compressor, seizure hardly occurs in the second thrust bearing 135b, and durability can be increased. Other functions of this compressor are the same as those of the compressor of the fifth embodiment.

  In the above, the present invention has been described with reference to the first to sixth embodiments. However, the present invention is not limited to the first to sixth embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

  For example, the compressor may be configured by appropriately combining the compressors of the first to fourth embodiments. Further, the compressor may be configured by combining the compressor of the fifth embodiment and the compressor of the sixth embodiment.

  Furthermore, a three-way valve may be adopted instead of the low pressure control valves 15a and 150a and the high pressure control valves 15b and 150b. In this case, the three-way valve corresponds to the control valve in the present invention. Further, the high pressure control valves 15b and 150b may be disposed only in the high pressure passages 15b and 150b.

  Further, in the compressors of the fifth and sixth embodiments, the compressor may be configured such that the compression chamber is formed only in one of the first cylinder block 121 or the second cylinder block 123.

  The present invention can be used for an air conditioner or the like.

DESCRIPTION OF SYMBOLS 1 ... Housing 3 ... Drive shaft 3a ... Axis (air supply passage, extraction passage)
3b ... Path (supply passage, extraction passage)
5 ... Swash plate 7 ... Link mechanism 9 ... Piston 10 ... Housing 11a, 11b ... Shoe (conversion mechanism)
DESCRIPTION OF SYMBOLS 13 ... Actuator 13a ... Moving body 13b ... Control pressure chamber 15 ... Control mechanism 15a ... Low-pressure passage (bleeding passage)
15b ... High-pressure passage (air supply passage)
21a ... Cylinder bore 25 ... Swash plate chamber 29a ... First sliding bearing (radial bearing)
30 ... Drive shaft 30a ... Axis (air supply passage, bleed passage)
30b ... Path (supply passage, extraction passage)
33 ... Suction chamber 35 ... Discharge chamber 50 ... Swash plate 51 ... Lug plate (partition body)
51c ... Outer sliding part 57 ... Restriction hole (communication path)
61 ... Restriction hole (communication path)
63 ... Restriction hole (communication path)
65 ... Restriction hole (communication path)
70 ... Link mechanism 75 ... Restriction hole (communication path)
77 ... Restriction hole (communication path)
90 ... Piston 110a, 110b ... Shoe (conversion mechanism)
121a ... first cylinder bore 121d ... first compression chamber 123a ... second cylinder bore 123d ... second compression chamber 127a ... first suction chamber 127b ... second suction chamber 129a ... first discharge chamber 129b ... second discharge chamber 131 ... first Cylindrical part 132 ... 2nd cylindrical part 133 ... Connection part 135b ... 2nd thrust bearing (thrust bearing)
DESCRIPTION OF SYMBOLS 150 ... Control mechanism 160 ... Actuator 160a ... Moving body 160b ... Partition body 160c ... Control pressure chamber 330 ... Swash plate chamber O1 ... Drive axis O2 ... Drive axis

Claims (5)

A housing in which a suction chamber, a discharge chamber, a swash plate chamber and a cylinder bore are formed; a drive shaft rotatably supported by the housing; a swash plate rotatable in the swash plate chamber by rotation of the drive shaft; and the drive A link mechanism that is provided between the shaft and the swash plate and allows the inclination angle of the swash plate to be changed with respect to a direction orthogonal to the drive axis of the drive shaft; and a piston that is housed in the cylinder bore so as to be reciprocally movable A conversion mechanism for reciprocating the piston in the cylinder bore with a stroke corresponding to the inclination angle by rotation of the swash plate, an actuator capable of changing the inclination angle, and a control mechanism for controlling the actuator. Prepared,
The swash plate chamber communicates with the suction chamber;
The actuator is partitioned by a partition provided on the drive shaft in the swash plate chamber, a movable body movable in the direction of the drive axis in the swash plate chamber, and the partition and the movable body. A control pressure chamber for moving the moving body by an internal pressure,
The control mechanism communicates with the discharge chamber and the control pressure chamber, communicates with an air supply passage for introducing the refrigerant in the discharge chamber into the control pressure chamber, the control pressure chamber, and the swash plate chamber, A bleed passage for discharging the refrigerant in the control pressure chamber to the swash plate chamber,
The bleed passage has a communication passage that is provided in at least one of the moving body and the partition body and has a communication path that discharges lubricating oil from the control pressure chamber together with the refrigerant to the swash plate chamber. Type swash plate compressor. The partition has an outer sliding portion that extends in the direction of the drive axis and slidably surrounds the movable body,
The movable body includes a first cylindrical portion disposed on the swash plate side around the drive shaft, a second cylindrical portion having a cylindrical shape whose diameter is larger than that of the first cylindrical portion, and the first cylindrical portion. A connecting portion for connecting the second cylindrical portion;
The communication passage is connected to the second cylindrical portion or the connection portion so that the lubricating oil discharged together with the refrigerant from the communication passage is supplied to a sliding portion between the moving body and the outer sliding portion. 2. The variable capacity swash plate compressor according to claim 1, wherein the compressor is perforated. The partition is fixed to the drive shaft;
A thrust bearing that supports a thrust force acting on the drive shaft is provided between the partition body and the housing,
A radial bearing for supporting a radial force acting on the drive shaft is provided between the housing and the drive shaft,
Between the housing and the drive shaft, there is provided a shaft seal device that ensures airtightness between the inside and the outside of the housing,
The said communicating path is pierced in the said division body so that the said lubricating oil discharged | emitted with the said refrigerant | coolant from the said communicating path may be supplied to the said thrust bearing, a radial bearing, or the said shaft seal device. Variable capacity swash plate compressor. The movable body includes a peripheral wall that extends in the drive axis direction and surrounds the partition body while sliding with the partition body, and a bottom wall that extends from the peripheral wall toward the drive shaft.
The said communicating path is drilled in the said division body so that the said lubricating oil discharged | emitted with the said refrigerant | coolant from the said communication path may be supplied to the sliding location of the said surrounding wall and the said dividing body. Variable capacity swash plate compressor. The movable body includes a peripheral wall that extends in the drive axis direction and surrounds the partition body while sliding with the partition body, and a bottom wall that extends from the peripheral wall toward the drive shaft.
A thrust bearing that supports a thrust force acting on the drive shaft is provided between the moving body and the housing,
2. The variable displacement swash plate compressor according to claim 1, wherein the communication passage is formed in the partition so that the lubricating oil discharged together with the refrigerant from the communication passage is supplied to the thrust bearing. .

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