JP2018155228A - Variable displacement swash plate type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To smoothly vary a tilt angle of a swash plate.SOLUTION: A valve element 56 opens and closes a discharge passage 55 on the basis of the pressure difference between a pressure on a control pressure chamber 35 side of a throttle hole 56h in a control passage 29 and a pressure on a pressure adjustment chamber side of the throttle hole 56h in the control passage 29. A refrigerant gas liquified in the control pressure chamber 35 is discharged to the control passage 29, and is discharged to a back pressure chamber 50 through the discharge passage 55 together with the refrigerant gas. The back pressure chamber 50 is communicated with a swash plate chamber 24 through a gap 52 which functions as a throttle, and thereby, the pressure in the back pressure chamber 50 is higher than the pressure in the swash plate chamber 24, and the back pressure chamber 50 moves a moving body 32 so as to reduce a tilt angle of a swash plate 23 by increase in the pressure in an inside thereof. Accordingly, the moving body 32 is rapidly moved so as to reduce the tilt ange of the swash plate 23. Further, the liquid refrigerant discharged to the back pressure chamber 50 is discharged to the swash plate chamber 24 through the gap 52.SELECTED DRAWING: Figure 4

Description

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

  In general, a housing of a variable displacement swash plate compressor includes a cylinder block, a front housing connected to one end of the cylinder block, and a rear housing connected to the other end of the cylinder block. A suction chamber and a discharge chamber are formed in the rear housing. A rotating shaft is rotatably supported in the housing. A swash plate chamber is formed between the front housing and the cylinder block in the housing. The swash plate chamber accommodates a swash plate that rotates by obtaining a driving force from the rotary shaft and tiltable with respect to the direction of the rotary shaft. In the cylinder block, a plurality of cylinder bores penetrating along the axial direction of the cylinder block and communicating with the suction chamber and the discharge chamber are formed around the rotation shaft. A piston is accommodated in each cylinder bore so as to be able to reciprocate. Each piston is anchored to the outer periphery of the swash plate via a pair of shoes. And the rotational motion of the swash plate accompanying rotation of a rotating shaft is converted into the reciprocating linear motion of a piston through a shoe.

  Here, in order to change the inclination angle of a swash plate, what equipped the actuator in the swash plate chamber is disclosed by patent document 1, for example. Such an actuator includes a partition body provided on the rotation shaft, a moving body that moves in the rotation axis direction of the rotation shaft in the swash plate chamber, and a control pressure chamber that is partitioned by the partition body and the moving body. The swash plate chamber is a suction pressure region in which refrigerant gas is drawn from the external refrigerant circuit. The cylinder block is formed with a suction passage that communicates the swash plate chamber and the suction chamber.

  Further, a pressure adjusting chamber is provided in the housing. The pressure adjusting chamber and the discharge chamber communicate with each other through an air supply passage. An orifice is provided on the supply passage. Further, the pressure adjusting chamber and the suction chamber communicate with each other through an extraction passage. An electromagnetic control valve as a control mechanism is provided on the extraction passage. The control valve adjusts the opening degree of the extraction passage based on the pressure in the suction chamber. As a result, the flow rate of the refrigerant gas flowing through the extraction passage is adjusted, and the pressure in the pressure adjustment chamber is controlled. The rotary shaft is formed with a control passage that is formed in the shaft of the rotary shaft and communicates the pressure adjustment chamber and the control pressure chamber.

  Then, supply of refrigerant gas from the discharge chamber to the control pressure chamber via the air supply passage, pressure adjustment chamber and control passage, and discharge from the control pressure chamber to the suction chamber via the control passage, pressure adjustment chamber and extraction passage And the pressure in the control pressure chamber is changed. The moving body moves in the axial direction of the rotation axis with respect to the partition body in accordance with the pressure difference between the control pressure chamber and the swash plate chamber. As the moving body moves in the axial direction of the rotation shaft, the inclination angle of the swash plate is changed.

JP-A-52-131204

  However, in the actuator configured as described above, the control pressure chamber is supplied with the high-temperature and high-pressure refrigerant gas from the discharge chamber, but the refrigerant gas in the swash plate chamber has a lower temperature than the refrigerant gas in the discharge chamber. There is a possibility that the refrigerant gas in the pressure chamber is cooled and condensed by the refrigerant gas in the swash plate chamber and is liquefied. As described above, the refrigerant gas in the control pressure chamber may be cooled and condensed by the refrigerant gas in the suction pressure region to be liquefied. The liquid refrigerant liquefied in the control pressure chamber is less likely to be discharged from the control pressure chamber to the suction chamber through the control passage, the pressure adjustment chamber, and the bleed passage compared to the refrigerant gas, so that the pressure change in the control pressure chamber is smooth. This is not done, and the inclination angle of the swash plate cannot be changed smoothly.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a variable displacement swash plate compressor that can smoothly change the inclination angle of the swash plate.

  A variable capacity swash plate compressor that solves the above problems includes a housing having a cylinder block in which a suction pressure region, a discharge pressure region, and a plurality of cylinder bores are formed, and a rotating shaft that is rotatably supported by the housing; A swash plate that is rotated by obtaining a driving force from the rotation shaft and can be tilted with respect to the direction of the rotation axis of the rotation shaft, and the swash plate is accommodated from outside through a suction port formed in the housing. A swash plate chamber for taking in refrigerant; a piston that is reciprocally stored in the cylinder bore; and is anchored to the swash plate; and an actuator that can change an inclination angle of the swash plate, and the actuator is mounted on the rotating shaft. A partition body provided, a movable body movable in the rotational axis direction, and partitioned by the partition body and the movable body, and the movable body is moved by an internal pressure. A pressure adjusting chamber that is provided in the housing and communicates with the suction pressure region and the discharge pressure region, and is formed in the shaft of the rotating shaft, and includes the control pressure chamber and the pressure A control passage that communicates with the adjustment chamber; and a control mechanism that controls the pressure of the pressure adjustment chamber. The rotation axis of the movable body is controlled by controlling the pressure of the pressure adjustment chamber by the control mechanism. The variable displacement swash plate compressor in which the tilt angle of the swash plate is changed with the movement in the direction and the piston reciprocates at a stroke corresponding to the tilt angle of the swash plate, the housing and the moving body A back pressure chamber that is partitioned between the throttle, a throttle that communicates the back pressure chamber and the swash plate chamber, and a shaft that is formed in the shaft of the rotating shaft and that opens to the outer peripheral surface of the rotating shaft and the control passage. And a discharge passage communicating with the back pressure chamber A valve body that is disposed in the control passage and opens and closes the discharge passage, and a throttle hole that is formed in the valve body and forms a part of the control passage. Based on the differential pressure between the pressure on the control pressure chamber side with respect to the throttle hole in the control passage and the pressure on the pressure adjustment chamber side with respect to the throttle hole in the control passage, the discharge passage is opened and closed, and the back pressure chamber Moves the moving body so as to reduce the inclination angle of the swash plate by increasing the internal pressure.

  For example, when reducing the pressure in the control pressure chamber, the pressure in the pressure adjustment chamber is controlled by the control mechanism so as to decrease the pressure in the pressure adjustment chamber, and the refrigerant gas in the control pressure chamber is supplied to the control passage, the throttle hole, and the pressure. It is discharged to the suction pressure area through the adjustment chamber. At this time, the pressure on the control pressure chamber side with respect to the throttle hole in the control passage is higher than the pressure on the pressure adjustment chamber side with respect to the throttle hole in the control passage. Then, based on the differential pressure between the pressure on the control pressure chamber side with respect to the throttle hole in the control passage and the pressure on the pressure adjustment chamber side with respect to the control passage, the valve body moves in a direction to open the discharge passage. At this time, even if liquefied liquid refrigerant exists in the control pressure chamber, the liquid refrigerant is discharged to the control passage and is discharged together with the refrigerant gas to the back pressure chamber through the discharge passage.

  Here, since the back pressure chamber communicates with the swash plate chamber via a restriction, the pressure in the back pressure chamber is higher than the pressure in the swash plate chamber, and the back pressure chamber The moving body is moved so as to reduce the inclination angle. Thereby, the moving body moves quickly so as to reduce the inclination angle of the swash plate. Further, since the liquid refrigerant discharged to the back pressure chamber is discharged to the swash plate chamber via the throttle, the pressure in the control pressure chamber can be changed smoothly. As a result, the inclination angle of the swash plate can be changed smoothly.

  In the variable displacement swash plate compressor, the housing has a recess in which the movable body is arranged so that the movable body can protrude and retract, the movable body has a bottomed cylindrical shape, and the inner peripheral surface of the concave portion and the A radial bearing is provided between the outer peripheral surface of the movable body and the outer peripheral surface of the movable body is slidable, and a gap between the outer peripheral surface of the movable body and the radial bearing functions as the diaphragm. Good.

  According to this, as the moving body moves, the outer peripheral surface of the moving body slides on the radial bearing, so that sliding heat is generated between the radial bearing and the outer peripheral surface of the moving body. Is warmed. Thereby, it becomes difficult to condense the refrigerant gas in the control pressure chamber, and the refrigerant gas can be prevented from being liquefied.

  In the variable displacement swash plate compressor, the housing has a recess in which the movable body is arranged so that the movable body can protrude and retract, the movable body has a bottomed cylindrical shape, and the inner peripheral surface of the concave portion and the Between the outer peripheral surface of the moving body, there is provided a seal ring that seals between the inner peripheral surface of the recess and the outer peripheral surface of the moving body and has a joint, and the joint functions as the diaphragm. Good.

  According to this, since the portion other than the joint is sealed between the inner peripheral surface of the recess and the outer peripheral surface of the moving body, the pressure in the back pressure chamber rises more efficiently than the pressure in the swash plate chamber. The moving body can be easily moved so as to reduce the inclination angle of the swash plate by the pressure of the back pressure chamber.

  In the variable displacement swash plate compressor, the housing has a concave portion in which the movable body is disposed so that the movable body can protrude and retract, and the movable body has a bottomed cylindrical shape. A coating layer slidable on the other is formed on one of the outer peripheral surfaces of the movable body, and the gap between the coating layer and the other may function as the diaphragm.

  According to this, since it is not necessary to interpose another member between the inner peripheral surface of the recess and the outer peripheral surface of the moving body in order to form the diaphragm, the variable capacity swash plate compression is performed in the radial direction of the rotating shaft. The size of the machine can be reduced. In addition, as the moving body moves, the outer peripheral surface of the moving body slides on the inner peripheral surface of the concave portion, so that sliding heat is generated between the inner peripheral surface of the concave portion and the outer peripheral surface of the moving body. The moving body is warmed. Thereby, it becomes difficult to condense the refrigerant gas in the control pressure chamber, and the refrigerant gas can be prevented from being liquefied.

  According to this invention, the inclination angle of the swash plate can be changed smoothly.

A side sectional view showing a variable capacity type swash plate type compressor in an embodiment. The side sectional view showing a variable capacity type swash plate type compressor when the inclination angle of the swash plate is the minimum inclination angle. The partial expanded sectional view of a variable capacity type swash plate type compressor. The partial expanded sectional view of a variable capacity type swash plate type compressor. The partial expanded sectional view of the variable capacity | capacitance type swash plate type compressor in another embodiment. The perspective view of a seal ring. The partial expanded sectional view of the variable capacity type | mold swash plate type compressor in another embodiment.

Hereinafter, an embodiment embodying a variable displacement swash plate compressor will be described with reference to FIGS. The variable capacity swash plate compressor is used in a vehicle air conditioner.
As shown in FIGS. 1 and 2, the housing 11 of the variable capacity swash plate compressor 10 includes a first cylinder block 12 and a second cylinder block 13 as cylindrical cylinder blocks connected to each other, and a first cylinder. A front housing 14 connected to the block 12 and a rear housing 15 connected to the second cylinder block 13 are provided.

  A first valve / port forming body 16 is interposed between the front housing 14 and the first cylinder block 12. A second valve / port forming body 17 is interposed between the rear housing 15 and the second cylinder block 13.

  A suction chamber 14 a and a discharge chamber 14 b are defined between the front housing 14 and the first valve / port forming body 16. The discharge chamber 14b is disposed on the outer peripheral side of the suction chamber 14a. A suction chamber 15 a and a discharge chamber 15 b are defined between the rear housing 15 and the second valve / port forming body 17. Further, the rear housing 15 is formed with a pressure adjusting chamber 15c. The pressure adjustment chamber 15c is located at the center of the rear housing 15, and the suction chamber 15a is disposed on the outer peripheral side of the pressure adjustment chamber 15c. Further, the discharge chamber 15b is disposed on the outer peripheral side of the suction chamber 15a. The discharge chambers 14b and 15b are connected to each other via a discharge passage (not shown). The discharge passage is connected to an external refrigerant circuit (not shown). Each discharge chamber 14b, 15b is a discharge pressure area.

  The first valve / port forming body 16 is formed with a suction port 16a communicating with the suction chamber 14a and a discharge port 16b communicating with the discharge chamber 14b. The second valve / port forming body 17 is formed with a suction port 17a communicating with the suction chamber 15a and a discharge port 17b communicating with the discharge chamber 15b. Each suction port 16a, 17a is provided with a suction valve mechanism (not shown), and each discharge port 16b, 17b is provided with a discharge valve mechanism (not shown).

  A rotating shaft 21 is rotatably supported in the housing 11. In the rotary shaft 21, one end side in the rotary axis direction (the axial direction of the rotary shaft 21), which is the direction in which the rotary axis L extends, and the front end side located on the front side (one side) of the housing 11 are the first cylinder. The shaft 12 is inserted into a shaft hole 12 h penetrating the block 12. The front end of the rotating shaft 21 is located in the front housing 14. Further, in the rotating shaft 21, the rear end side located on the other end side in the rotating axis direction and located on the rear side (the other side) of the housing 11 is inserted into the shaft hole 13 h penetrating the second cylinder block 13. Has been. The rear end of the rotary shaft 21 is located in the pressure adjustment chamber 15c.

  The rotary shaft 21 has a front end portion rotatably supported by the first cylinder block 12 via the shaft hole 12h and a rear end portion side rotatably supported by the second cylinder block 13 via the shaft hole 13h. ing. A lip seal type shaft seal device 22 is interposed between the front housing 14 and the rotary shaft 21. A vehicle engine E as an external drive source is operatively connected to the front end of the rotating shaft 21 via a power transmission mechanism PT. In the present embodiment, the power transmission mechanism PT is a constant transmission type clutchless mechanism (for example, a combination of a belt and a pulley).

  A swash plate chamber 24 defined by the first cylinder block 12 and the second cylinder block 13 is formed in the housing 11. The swash plate chamber 24 accommodates a swash plate 23 that rotates by obtaining a driving force from the rotary shaft 21 and can be tilted with respect to the rotational axis direction of the rotary shaft 21. The swash plate 23 is formed with an insertion hole 23a through which the rotary shaft 21 can be inserted. The swash plate 23 is attached to the rotating shaft 21 by inserting the rotating shaft 21 into the insertion hole 23 a.

  The first cylinder block 12 includes a plurality of first cylinder bores 12a as cylinder bores formed through the first cylinder block 12 in the axial direction around the rotating shaft 21 (only one first cylinder bore 12a in FIGS. 1 and 2). (Shown) Each first cylinder bore 12a communicates with the suction chamber 14a via the suction port 16a and also communicates with the discharge chamber 14b via the discharge port 16b.

  The second cylinder block 13 includes a plurality of second cylinder bores 13a as cylinder bores formed in the axial direction of the second cylinder block 13 around the rotating shaft 21 (only one second cylinder bore 13a in FIGS. 1 and 2). (Shown) Each second cylinder bore 13a communicates with the suction chamber 15a via the suction port 17a and also communicates with the discharge chamber 15b via the discharge port 17b.

  The 1st cylinder bore 12a and the 2nd cylinder bore 13a are arranged so that it may become a pair in front and back. In the first cylinder bore 12a and the second cylinder bore 13a as a pair, a double-headed piston 25 as a piston is accommodated so as to be reciprocable in the front-rear direction. That is, the variable capacity swash plate compressor 10 of this embodiment is a double-headed piston swash plate compressor.

  Each double-headed piston 25 is anchored to the outer peripheral portion of the swash plate 23 via a pair of shoes 26. Then, the rotational motion of the swash plate 23 accompanying the rotation of the rotating shaft 21 is converted into the reciprocating linear motion of the double-headed piston 25 via the shoe 26.

  A first compression chamber 20a is defined in each first cylinder bore 12a by a double-headed piston 25 and a first valve / port forming body 16. In each second cylinder bore 13a, a second compression chamber 20b is defined by a double-headed piston 25 and a second valve / port forming body 17.

  The first cylinder block 12 is formed with a first recess 12b that is continuous with the shaft hole 12h and has a larger diameter than the shaft hole 12h. The first recess 12 b opens into the swash plate chamber 24.

  The second cylinder block 13 is formed with a second recess 13b that is continuous with the shaft hole 13h and has a larger diameter than the shaft hole 13h. The second recess 13 b opens into the swash plate chamber 24. The first recess 12b and the second recess 13b have their openings facing each other in the direction of the rotation axis of the rotation shaft 21.

  The swash plate chamber 24 and the suction chamber 14 a communicate with each other through a suction passage 12 c that passes through the first cylinder block 12 and the first valve / port forming body 16. The swash plate chamber 24 and the suction chamber 15a communicate with each other through a suction passage 13c that passes through the second cylinder block 13 and the second valve / port forming body 17.

  A suction port 13 s is formed in the peripheral wall of the second cylinder block 13. The suction port 13s is connected to an external refrigerant circuit. The swash plate chamber 24 takes in the refrigerant gas from the external refrigerant circuit via the suction port 13s. The refrigerant gas sucked into the swash plate chamber 24 from the external refrigerant circuit through the suction port 13s is sucked into the suction chambers 14a and 15a through the suction passages 12c and 13c. Accordingly, the suction port 13s, the swash plate chamber 24, the plurality of suction passages 12c and 13c, and the suction chambers 14a and 15a are suction pressure regions, and the suction chambers 14a and 15a and the swash plate chamber 24 have substantially the same pressure. .

  The rotating shaft 21 has an annular flange portion 21f disposed in the first recess 12b. The flange portion 21f is a separate member from the rotating shaft 21, and constitutes a part of the rotating shaft 21 by being press-fitted into the rotating shaft 21. A first thrust bearing 27 a is disposed between the flange portion 21 f and the first cylinder block 12 in the axial direction of the rotary shaft 21. An annular flange portion 21g disposed in the second recess 13b is projected from the rear end side of the rotary shaft 21. A second thrust bearing 27 b is disposed between the flange portion 21 g and the second cylinder block 13 in the axial direction of the rotary shaft 21.

  In the swash plate chamber 24, an actuator 30 capable of changing the inclination angle of the swash plate 23 with respect to the rotation axis direction of the rotation shaft 21 in the swash plate 23 is disposed. The actuator 30 is disposed on the rear side of the flange portion 21 f and on the front side of the swash plate 23.

  The actuator 30 has an annular partition body 31 provided on the rotary shaft 21 so as to be integrally rotatable. The partition body 31 is formed with an insertion hole 31h into which the rotation shaft 21 is inserted. The rotating shaft 21 is press-fitted into the insertion hole 31 h, so that the partition body 31 is integrated with the rotating shaft 21.

  The actuator 30 includes a bottomed cylindrical moving body 32 that is disposed between the flange portion 21 f and the partition body 31 and is movable in the swash plate chamber 24 in the rotation axis direction of the rotation shaft 21. The moving body 32 is disposed inside the first recess 12b so as to be able to appear and retract with respect to the first recess 12b. The moving body 32 includes an annular bottom 32a having an insertion hole 32e through which the rotation shaft 21 is inserted, and a cylindrical tube portion 32b extending in the rotation axis direction of the rotation shaft 21 from the outer peripheral edge of the bottom 32a. The moving body 32 can rotate integrally with the rotating shaft 21. The space between the inner peripheral surface of the cylindrical portion 32 b and the outer peripheral surface of the partition body 31 is sealed with a seal member 33, and the space between the through hole 32 e and the rotary shaft 21 is sealed with a seal member 34. The actuator 30 has a control pressure chamber 35 partitioned by the partition body 31 and the moving body 32.

  As shown in FIGS. 3 and 4, a radial bearing 51 is provided between the inner peripheral surface 121 b of the first recess 12 b and the outer peripheral surface 32 d of the moving body 32. The radial bearing 51 is disposed near the opening of the first recess 12b. The radial bearing 51 is a cylindrical plain bearing. The outer peripheral surface 32 d of the moving body 32 can slide on the inner peripheral surface 51 a of the radial bearing 51.

  A space opposite to the swash plate chamber 24 from the radial bearing 51 in the first recess 12 b is a back pressure chamber 50 defined between the first recess 12 b and the moving body 32. The swash plate chamber 24 and the back pressure chamber 50 communicate with each other via a gap 52 between the outer peripheral surface 32 d of the moving body 32 and the inner peripheral surface 51 a of the radial bearing 51. The gap 52 formed by the radial bearing 51 functions as a throttle that allows the back pressure chamber 50 and the swash plate chamber 24 to communicate with each other. The back pressure chamber 50 moves the moving body 32 so as to reduce the inclination angle of the swash plate 23 as the internal pressure increases.

  As shown in FIGS. 1 and 2, in the swash plate chamber 24, a lug arm 40 is disposed between the swash plate 23 and the flange portion 21g. The lug arm 40 is formed in a substantially L shape from one end to the other end. A weight portion 40 a is formed at one end of the lug arm 40. The weight part 40 a passes through the groove part 23 b of the swash plate 23 and is located on the front side of the swash plate 23.

  One end side of the lug arm 40 is connected to the upper end side (the upper side in FIGS. 1 and 2) of the swash plate 23 by a first pin 41 crossing the groove 23b. Thus, one end side of the lug arm 40 is supported so as to be swingable around the first swing center M1 with respect to the swash plate 23 with the axis of the first pin 41 as the first swing center M1. The other end of the lug arm 40 is connected by a second pin 42 to a support member (not shown) provided integrally with the rotary shaft 21. Thus, the other end side of the lug arm 40 is supported so as to be swingable around the second swing center M2 with respect to the support member, with the axis of the second pin 42 as the second swing center M2.

  A connecting portion 32 c that protrudes toward the swash plate 23 is provided at the tip of the cylindrical portion 32 b of the moving body 32. A moving body side insertion hole 32h into which the third pin 43 can be inserted is formed in the connecting portion 32c. Further, a swash plate side insertion hole 23h through which the third pin 43 can be inserted is formed on the lower end side (lower side in FIGS. 1 and 2) of the swash plate 23. The connecting portion 32 c is connected to the lower end side of the swash plate 23 by the third pin 43.

  A control passage 29 that connects the control pressure chamber 35 and the pressure adjustment chamber 15c is formed in the rotary shaft 21. The control passage 29 is formed in the shaft of the rotary shaft 21. The control passage 29 is formed by a first in-axis passage 29 a extending in the axial direction of the rotation shaft 21 and a second in-axis passage 29 b communicating with the first in-axis passage 29 a and extending in the radial direction of the rotation shaft 21. Yes. One end of the second in-axis passage 29 b communicates with the first in-axis passage 29 a and the other end opens into the control pressure chamber 35. The rear end of the first in-axis passage 29a opens to the pressure adjustment chamber 15c. Therefore, the control pressure chamber 35 and the pressure adjusting chamber 15c communicate with each other via the first in-axis passage 29a and the second in-axis passage 29b.

  As shown in FIGS. 3 and 4, the rotary shaft 21 is formed with a discharge passage 55 that communicates the control passage 29 and the back pressure chamber 50. The discharge passage 55 is formed in the shaft of the rotary shaft 21. The discharge passage 55 extends in the direction of the rotation axis of the rotary shaft 21 and communicates with the front end of the first in-shaft passage 29a. The discharge passage 55 extends in the radial direction of the rotary shaft 21, and includes the shaft passage 55a and the back pressure chamber 50. It is formed from a communicating path 55b. The axial path 55a has a smaller diameter than the first in-axis passage 29a. Therefore, an annular stepped portion 55 c extending in the radial direction of the rotating shaft 21 is formed between the first in-axis passage 29 a and the axial path 55 a in the shaft of the rotating shaft 21. An end portion of the radial path 55 b opposite to the axial path 55 a is open to the outer peripheral surface of the rotating shaft 21 and communicates with the back pressure chamber 50.

  A valve body 56 for opening and closing the discharge passage 55 is disposed in the first in-shaft passage 29a. The valve body 56 is a spool valve, and is movable in the rotation axis direction of the rotation shaft 21 in the first shaft passage 29a.

  The valve body 56 includes a disc-shaped valve portion 56a capable of contacting the stepped portion 55c, a columnar connecting portion 56b extending from the valve portion 56a in the direction of the rotation axis of the rotating shaft 21, and a valve portion 56a in the connecting portion 56b. Is provided with a bottomed cylindrical guide portion 56c connected to the opposite end portion. The outer diameter of the valve part 56a is smaller than the outer diameter of the guide part 56c. Therefore, there is a gap between the outer peripheral surface of the valve portion 56a and the inner peripheral surface of the first in-axis passage 29a.

  The end of the connecting portion 56b opposite to the valve portion 56a is connected to the center of the bottom of the guide portion 56c. The outer peripheral surface of the guide part 56c is slidable on the inner peripheral surface of the first in-axis passage 29a. The valve body 56 moves in the direction of the rotation axis of the rotary shaft 21 through the inside of the first shaft passage 29a while the outer peripheral surface of the guide portion 56c is guided by the inner peripheral surface of the first shaft passage 29a. When the valve body 56 moves, the valve body 56 is prevented from being inclined with respect to the rotation axis of the rotation shaft 21.

  The valve body 56 is configured such that the surface of the valve portion 56a opposite to the connecting portion 56b abuts on the step portion 55c, thereby blocking communication between the first in-shaft passage 29a and the shaft passage 55a. The closed valve is closed. Therefore, the surface of the valve portion 56a opposite to the connecting portion 56b is an end face seal portion 56s that seals between the control passage 29 and the discharge passage 55 by contacting the stepped portion 55c. On the other hand, the end face seal portion 56s is separated from the stepped portion 55c so that the valve body 56 is allowed to communicate with the first in-shaft passage 29a and the axial passage 55a and opens the discharge passage 55. .

  A throttle hole 56h is formed at the bottom of the guide portion 56c. The throttle hole 56 h forms a part of the control passage 29. The valve body 56 opens and closes the discharge passage 55 based on the differential pressure between the pressure on the control pressure chamber 35 side of the control passage 29 with respect to the control hole 29 and the pressure on the pressure adjustment chamber 15c side of the control passage 29 with respect to the pressure adjustment chamber 15c. To do.

  As shown in FIGS. 1 and 2, a cylindrical stopper member 57 is press-fitted into the rear end of the first in-axis passage 29a. The inside of the stopper member 57 forms a part of the control passage 29. An urging spring 58 is interposed between the valve body 56 and the stopper member 57. The urging spring 58 urges the valve body 56 in a direction to close the discharge passage 55.

  The load applied to the valve body 56 based on the pressure on the control pressure chamber 35 side relative to the throttle hole 56h in the control passage 29 is applied to the valve body 56 based on the pressure on the pressure adjustment chamber 15c side relative to the throttle hole 56h in the control passage 29. The load applied may be smaller than the sum of the load applied to the valve body 56 based on the urging force of the urging spring 58. In this case, the valve body 56 is positioned in a state where the end face seal portion 56s is in contact with the stepped portion 55c, and the gap between the control passage 29 and the discharge passage 55 is sealed by the end face seal portion 56s.

  On the other hand, the load applied to the valve body 56 based on the pressure on the control pressure chamber 35 side with respect to the throttle hole 56h in the control passage 29 is based on the pressure on the pressure adjustment chamber 15c side with respect to the throttle hole 56h in the control passage 29. The load applied to 56 and the load applied to the valve body 56 based on the urging force of the urging spring 58 may be larger than the sum. In this case, the valve body 56 moves in a direction in which the end face seal portion 56s is separated from the stepped portion 55c, the first in-shaft passage 29a communicates with the axial passage 55a, and the control pressure chamber 35 and the back pressure chamber 50 are connected. It communicates via the control passage 29 and the discharge passage 55.

  The control pressure chamber 35 and the pressure adjustment chamber 15c are configured such that the valve body 56 is positioned in a state where the end face seal portion 56s is in contact with the stepped portion 55c, the second in-axis passage 29b, the first in-axis passage. Communication is made through a passage closer to the control pressure chamber 35 than the throttle hole 56h in 29a, a throttle hole 56h, and a passage closer to the pressure adjustment chamber 15c than the throttle hole 56h in the first in-axis passage 29a. In addition, the control pressure chamber 35 and the pressure adjustment chamber 15c are configured so that the valve body 56 moves in the direction in which the end face seal portion 56s moves away from the stepped portion 55c. Communication is made through a passage closer to the control pressure chamber 35 than the throttle hole 56h in 29a, a throttle hole 56h, and a passage closer to the pressure adjustment chamber 15c than the throttle hole 56h in the first in-axis passage 29a.

  The pressure adjusting chamber 15c and the suction chamber 15a communicate with each other via the extraction passage 36. The extraction passage 36 is provided with an electromagnetic control valve 36s. The control valve 36s can adjust the opening degree of the extraction passage 36 based on the pressure in the suction chamber 15a. Then, the flow rate of the refrigerant gas flowing through the extraction passage 36 is adjusted by the control valve 36s, and the pressure in the pressure adjustment chamber 15c is controlled. Therefore, the control valve 36s is a control mechanism that controls the pressure in the pressure regulation chamber 15c. Further, the pressure adjustment chamber 15 c and the discharge chamber 15 b communicate with each other via an air supply passage 37. The air supply passage 37 is provided with an orifice 37a, and the flow rate of the refrigerant gas flowing through the air supply passage 37 is restricted by the orifice 37a.

  Then, supply of the refrigerant gas from the discharge chamber 15b to the control pressure chamber 35 via the air supply passage 37, the pressure adjustment chamber 15c, the first in-shaft passage 29a and the second in-shaft passage 29b, The refrigerant gas is discharged into the suction chamber 15a through the biaxial passage 29b, the first axial passage 29a, the pressure adjustment chamber 15c, and the extraction passage 36. Thereby, the pressure of the control pressure chamber 35 is controlled.

  When the valve opening of the control valve 36s is increased, the refrigerant discharged from the control pressure chamber 35 to the suction chamber 15a through the second shaft inner passage 29b, the first shaft inner passage 29a, the pressure adjusting chamber 15c, and the extraction passage 36. The gas flow rate increases. As a result, the pressure in the pressure adjusting chamber 15c is substantially equal to the pressure in the suction chamber 15a, and the pressure in the control pressure chamber 35 is also substantially equal to the pressure in the suction chamber 15a. Therefore, since the pressure difference between the control pressure chamber 35 and the swash plate chamber 24 is reduced, the swash plate 23 is moved through the third pin 43 by the compression reaction force from the double-headed piston 25 acting on the swash plate 23. The moving body 32 moves so that the bottom 32a of the moving body 32 approaches the partition body 31.

  As shown in FIG. 2, when the moving body 32 moves so that the bottom 32a of the moving body 32 approaches the partition body 31, the swash plate 23 swings around the first swing center M1. As the swash plate 23 swings around the first swing center M1, the lug arm 40 swings around the second swing center M2, and the lug arm 40 approaches the flange portion 21g. Thereby, the inclination angle of the swash plate 23 becomes small. When the inclination angle of the swash plate 23 is reduced, the stroke of the double-headed piston 25 is reduced and the discharge capacity is reduced.

  When the valve opening of the control valve 36s is decreased, the refrigerant discharged from the control pressure chamber 35 to the suction chamber 15a through the second shaft passage 29b, the first shaft passage 29a, the pressure adjustment chamber 15c, and the extraction passage 36. Gas flow is reduced. The refrigerant gas is supplied from the discharge chamber 15b to the control pressure chamber 35 via the air supply passage 37, the pressure adjustment chamber 15c, the first in-shaft passage 29a, and the second in-shaft passage 29b, thereby controlling the control pressure. The pressure in the chamber 35 is substantially equal to the pressure in the discharge chamber 15b. Therefore, the pressure difference between the control pressure chamber 35 and the swash plate chamber 24 is increased, so that the moving body 32 pulls the swash plate 23 via the third pin 43, while the bottom 32 a of the moving body 32 is separated from the partition body 31. Move away.

  As shown in FIG. 1, when the moving body 32 moves so that the bottom 32 a of the moving body 32 is separated from the partition body 31, the swash plate 23 moves around the first swing center M <b> 1 when the tilt angle of the swash plate 23 is decreased. It swings in the direction opposite to the swing direction. As the swash plate 23 swings in the direction opposite to the swing direction when the tilt angle of the swash plate 23 decreases, the lug arm 40 moves around the second swing center M2 around the first swing center M1. 23 swings in the direction opposite to the swinging direction when the tilt angle is decreased, and the lug arm 40 is separated from the flange portion 21g. Thereby, the inclination angle of the swash plate 23 is increased, the stroke of the double-headed piston 25 is increased, and the discharge capacity is increased.

  Thus, the variable displacement swash plate compressor 10 is controlled by controlling the pressure in the discharge chamber 15b introduced into the pressure adjustment chamber 15c and the pressure in the suction chamber 15a derived from the pressure adjustment chamber 15c by the control valve 36s. The pressure in the control pressure chamber 35 is controlled. Then, with the pressure difference between the control pressure chamber 35 and the swash plate chamber 24, the moving body 32 moves in the direction of the rotation axis of the rotation shaft 21 with respect to the partition body 31. Therefore, the control pressure chamber 35 moves the moving body 32 by the internal pressure. The refrigerant gas supplied to the control pressure chamber 35 is a control gas used for performing movement control of the moving body 32. As the moving body 32 moves in the direction of the rotation axis of the rotary shaft 21, the tilt angle of the swash plate 23 is changed, and the double-headed piston 25 reciprocates with a stroke corresponding to the tilt angle of the swash plate 23.

Next, the operation of this embodiment will be described.
When reducing the pressure in the control pressure chamber 35 in order to reduce the discharge capacity, the valve opening of the control valve 36s is increased and the pressure in the pressure adjustment chamber 15c is decreased so as to decrease the pressure in the pressure adjustment chamber 15c. The refrigerant gas in the control pressure chamber 35 is discharged to the suction chamber 15a through the control passage 29, the pressure adjustment chamber 15c, and the extraction passage 36. At this time, the pressure on the control pressure chamber 35 side with respect to the throttle hole 56h in the control passage 29 is higher than the pressure on the pressure adjustment chamber 15c side with respect to the throttle hole 56h in the control passage 29.

  The load applied to the valve body 56 based on the pressure on the control pressure chamber 35 side relative to the throttle hole 56h in the control passage 29 is applied to the valve body 56 based on the pressure on the pressure adjustment chamber 15c side relative to the throttle hole 56h in the control passage 29. In some cases, the applied load and the load applied to the valve body 56 based on the urging force of the urging spring 58 may be larger than the sum. In this case, as shown in FIG. 4, the valve body 56 moves in a direction to open the discharge passage 55. That is, the valve body 56 moves in a direction in which the end face seal portion 56 s is separated from the stepped portion 55 c, and the control pressure chamber 35 and the back pressure chamber 50 communicate with each other via the control passage 29 and the discharge passage 55.

  At this time, the refrigerant gas in the control pressure chamber 35 may be cooled and condensed by the refrigerant gas in the swash plate chamber 24, and liquefied liquid refrigerant may exist in the control pressure chamber 35. In this case, the liquefied liquid refrigerant is discharged to the control passage 29 and discharged to the back pressure chamber 50 through the discharge passage 55 together with the refrigerant gas.

  Here, since the back pressure chamber 50 communicates with the swash plate chamber 24 through a gap 52 that functions as a throttle, the pressure in the back pressure chamber 50 is higher than the pressure in the swash plate chamber 24. Then, the back pressure chamber 50 moves the moving body 32 so as to reduce the inclination angle of the swash plate 23 as the internal pressure increases. Thereby, the moving body 32 moves quickly so as to reduce the inclination angle of the swash plate 23. Further, the liquid refrigerant discharged into the back pressure chamber 50 is discharged into the swash plate chamber 24 through the gap 52 together with the refrigerant gas.

In the above embodiment, the following effects can be obtained.
(1) The valve body 56 is based on the differential pressure between the pressure on the control pressure chamber 35 side of the control passage 29 relative to the throttle hole 56h and the pressure on the pressure adjustment chamber 15c side of the control passage 29 relative to the throttle hole 56h. 55 is opened and closed. The load applied to the valve body 56 based on the pressure on the control pressure chamber 35 side relative to the throttle hole 56h in the control passage 29 is applied to the valve body 56 based on the pressure on the pressure adjustment chamber 15c side relative to the throttle hole 56h in the control passage 29. It may be larger than the applied load. In this case, the valve body 56 moves in a direction to open the discharge passage 55. At this time, even if liquefied liquid refrigerant exists in the control pressure chamber 35, the liquefied liquid refrigerant is discharged to the control passage 29 and discharged to the back pressure chamber 50 through the discharge passage 55 together with the refrigerant gas. The Here, since the back pressure chamber 50 communicates with the swash plate chamber 24 through a gap 52 that functions as a throttle, the pressure in the back pressure chamber 50 is higher than the pressure in the swash plate chamber 24. Then, the back pressure chamber 50 moves the moving body 32 so as to reduce the inclination angle of the swash plate 23 as the internal pressure increases. Thereby, the moving body 32 moves quickly so as to reduce the inclination angle of the swash plate 23. Further, since the liquid refrigerant discharged to the back pressure chamber 50 is discharged to the swash plate chamber 24 through the gap 52, the pressure of the control pressure chamber 35 can be changed smoothly. As a result, the inclination angle of the swash plate 23 can be changed smoothly.

  (2) A radial bearing 51 is provided between the inner peripheral surface 121b of the first recess 12b and the outer peripheral surface 32d of the moving body 32, on which the outer peripheral surface 32d of the moving body 32 can slide. The gap 52 formed by the radial bearing 51 functions as a diaphragm. According to this, the outer peripheral surface 32d of the moving body 32 slides on the radial bearing 51 as the moving body 32 moves, so that the sliding between the radial bearing 51 and the outer peripheral surface 32d of the moving body 32 occurs. Heat is generated and the moving body 32 is warmed. Thereby, it becomes difficult for the refrigerant gas in the control pressure chamber 35 to condense, and the refrigerant gas can be prevented from being liquefied.

  (3) The discharge passage 55 opens to the outer peripheral surface of the rotary shaft 21 and communicates with the back pressure chamber 50. According to this, the liquid refrigerant flowing through the discharge passage 55 moves to the outside in the radial direction of the rotation shaft 21 in the discharge passage 55 due to the centrifugal force of the rotation shaft 21, and thus is easily discharged to the back pressure chamber 50.

  (4) In the present embodiment, in order to decrease the discharge capacity in the variable displacement swash plate compressor 10, when the pressure in the control pressure chamber 35 is decreased, the valve opening of the control valve 36s is increased, The refrigerant gas in the control pressure chamber 35 is discharged to the suction chamber 15a via the second in-shaft passage 29b, the first in-shaft passage 29a, the pressure adjustment chamber 15c, and the extraction passage 36. At this time, the load applied to the valve body 56 based on the pressure on the control pressure chamber 35 side relative to the throttle hole 56h in the control passage 29 is a valve based on the pressure on the pressure adjustment chamber 15c side relative to the throttle hole 56h in the control passage 29. When the sum of the load applied to the body 56 and the load applied to the valve body 56 based on the urging force of the urging spring 58 becomes larger, the valve body 56 opens the discharge passage 55. Therefore, a part of the refrigerant gas in the control pressure chamber 35 is also discharged to the back pressure chamber 50 through the discharge passage 55, and therefore passes through the control valve 36s as compared with the configuration in which the discharge passage 55 is not provided. The flow rate of the refrigerant gas is reduced. Therefore, even if the valve opening degree of the control valve 36s is small, the pressure in the control pressure chamber 35 can be reduced, so that the control valve 36s can be downsized.

In addition, you may change the said embodiment as follows.
As shown in FIG. 5, a seal ring 61 may be provided instead of the radial bearing 51 between the inner peripheral surface 121 b of the first recess 12 b and the outer peripheral surface 32 d of the moving body 32. The seal ring 61 is made of resin. An annular mounting groove 32f in which the seal ring 61 is mounted is formed in a portion of the outer peripheral surface 32d of the movable body 32 on the bottom 32a side.

  As shown in FIG. 6, the seal ring 61 has a joint 62. The joint 62 has a crank shape. The joint 62 is formed by a first notch 62a, a second notch 62b, and a third notch 62c. The first notch 62 a is formed on the inner peripheral surface of the seal ring 61 and extends linearly in a direction intersecting the circumferential direction of the seal ring 61. The first notch 62 a extends from the inner peripheral surface of the seal ring 61 to the center in the thickness direction of the seal ring 61. The second notch 62 b is formed on the outer peripheral surface of the seal ring 61 and is disposed at a position shifted in the circumferential direction of the seal ring 61 with respect to the first notch 62 a and intersects the circumferential direction of the seal ring 61. It extends in a straight line. The second notch 62 b extends from the outer peripheral surface of the seal ring 61 to the center in the thickness direction of the seal ring 61. The third notch 62c extends in the circumferential direction of the seal ring 61 at the center in the thickness direction of the seal ring 61, and ends of the first notch 62a and the second notch 62b on the center side in the thickness direction of the seal ring 61 are connected to each other. Are connected.

  As shown in FIG. 5, in a state where the seal ring 61 is mounted in the mounting groove 32 f, the outer peripheral surface of the seal ring 61 is located on the outer side in the radial direction of the rotary shaft 21 than the outer peripheral surface 32 d of the moving body 32. The third notch 62c of the joint 62 is also located on the outer side in the radial direction of the rotating shaft 21 with respect to the outer peripheral surface 32d of the moving body 32. The seal ring 61 seals between the inner peripheral surface 121b of the first recess 12b and the outer peripheral surface 32d of the moving body 32 except for the joint 62. The swash plate chamber 24 and the back pressure chamber 50 communicate with each other through a joint 62. The abutment 62 functions as a throttle that allows the back pressure chamber 50 and the swash plate chamber 24 to communicate with each other.

  According to this, since the portion excluding the joint 62 is sealed between the inner peripheral surface 121b of the first recess 12b and the outer peripheral surface 32d of the moving body 32 by the seal ring 61, the pressure in the back pressure chamber 50 is inclined. The moving body 32 can be easily moved so that the pressure rises more efficiently than the pressure in the plate chamber 24 and the inclination angle of the swash plate 23 is reduced by the pressure in the back pressure chamber 50.

  As shown in FIG. 7, as shown by dot hatching in FIG. 7 without providing the radial bearing 51 and the seal ring 61 between the inner peripheral surface 121b of the first recess 12b and the outer peripheral surface 32d of the moving body 32. In addition, a coating layer 32 g may be formed on the outer peripheral surface 32 d of the moving body 32. And the outer peripheral surface 32d of the moving body 32 may be slidable on the inner peripheral surface 121b of the first recess 12b. The coating layer 32g is formed of, for example, a fluororesin. A gap 71 between the inner peripheral surface 121b of the first recess 12b and the outer peripheral surface 32d of the moving body 32 functions as a diaphragm. According to this, since it is not necessary to intervene another member between the inner peripheral surface 121b of the first recess 12b and the outer peripheral surface 32d of the moving body 32 in order to form a diaphragm, in the radial direction of the rotary shaft 21 The variable capacity swash plate compressor 10 can be downsized. Further, as the moving body 32 moves, the outer peripheral surface 32d of the moving body 32 slides on the inner peripheral surface 121b of the first recess 12b, so that the inner peripheral surface 121b of the first recess 12b and the moving body 32 Sliding heat is generated between the outer peripheral surface 32d and the moving body 32 is warmed. Thereby, it becomes difficult for the refrigerant gas in the control pressure chamber 35 to condense, and the refrigerant gas can be prevented from being liquefied.

  In the embodiment, without providing the radial bearing 51 or the seal ring 61 between the inner peripheral surface 121b of the first recess 12b and the outer peripheral surface 32d of the moving body 32, the inner peripheral surface 121b of the first recess 12b A coating layer may be formed. And the outer peripheral surface 32d of the moving body 32 may be slidable on the inner peripheral surface 121b of the first recess 12b. In this case, the gap between the inner peripheral surface 121b of the first recess 12b and the outer peripheral surface 32d of the moving body 32 functions as a diaphragm. In short, one of the inner peripheral surface 121b of the first recess 12b or the outer peripheral surface 32d of the moving body 32 is formed with a slidable coating layer on the other side, and the gap between the coating layer and the other serves as a diaphragm. It only has to be functional.

  In the embodiment, the moving body 32 itself may be formed of a material having good sliding properties such as a fluororesin. And the outer peripheral surface 32d of the moving body 32 may be slidable on the inner peripheral surface 121b of the first recess 12b. In this case, the gap between the outer peripheral surface 32d of the moving body 32 and the inner peripheral surface 121b of the first recess 12b functions as a diaphragm. In short, the moving body 32 has at least the outer peripheral surface 32d of the moving body 32 made of a material having good slidability, and the gap 71 between the inner peripheral surface 121b of the first recess 12b and the outer peripheral surface 32d of the moving body 32 is reduced. As long as it functions.

  In the embodiment, the radial bearing 51 may not be a plain bearing, for example, a ball bearing. In the case of a ball bearing, the gap formed by the ball bearing itself also functions as a stop.

In the embodiment, the valve body 56 may not be a spool valve, and may be a reed valve, for example.
In the embodiment, an electromagnetic control valve is provided on the air supply passage that communicates the pressure adjustment chamber 15c and the discharge chamber 15b, and an orifice is provided in the extraction passage that communicates the pressure adjustment chamber 15c and the suction chamber 15a. The provided structure may be sufficient.

  In the embodiment, the variable capacity swash plate compressor 10 is a double-headed piston swash plate compressor that employs a double-headed piston 25, but may be a single-headed piston swash plate compressor that employs a single-headed piston. .

  In the embodiment, a driving force may be obtained from an external driving source via a clutch.

  DESCRIPTION OF SYMBOLS 10 ... Variable displacement type swash plate compressor, 11 ... Housing, 12 ... 1st cylinder block as a cylinder block, 12a ... 1st cylinder bore as a cylinder bore, 12b ... 1st recessed part as a recessed part, 13 ... 1st cylinder block as a cylinder block 2 cylinder block, 13a ... 2nd cylinder bore as cylinder bore, 13s ... Suction port, 14a, 15a ... Suction chamber which is suction pressure area, 14b, 15b ... Discharge chamber which is discharge pressure area, 15c ... Pressure adjustment chamber, 21 ... Rotating shaft, 23 ... swash plate, 24 ... swash plate chamber as suction pressure region, 25 ... double-headed piston as piston, 29 ... control passage, 30 ... actuator, 31 ... partition body, 32 ... moving body, 32d ... outer peripheral surface, 32g ... coating layer, 35 ... control pressure chamber, 36s ... control valve as control mechanism, 50 ... back pressure chamber, 51 ... radial valve Rings, the gap functioning as 52,71 ... diaphragm, 55 ... exhaust passage, 56 ... valve body, 56h ...... throttle hole, 61 ... seal ring 62 ... abutment which functions as a throttle, 121b ... inner circumferential surface.

Claims (4)

A housing having a cylinder block in which a suction pressure region, a discharge pressure region, and a plurality of cylinder bores are formed;
A rotating shaft rotatably supported by the housing;
A swash plate that is rotated by obtaining a driving force from the rotating shaft and can be tilted with respect to the rotating axis direction of the rotating shaft;
A swash plate chamber that houses the swash plate and takes in refrigerant from the outside through a suction port formed in the housing;
A piston housed in the cylinder bore so as to be reciprocable and moored to the swash plate;
An actuator capable of changing an inclination angle of the swash plate,
The actuator is
A partition provided on the rotating shaft;
A movable body movable in the rotational axis direction;
A control pressure chamber partitioned by the partition body and the moving body and moving the moving body by an internal pressure;
A pressure adjusting chamber provided in the housing and communicating with the suction pressure region and the discharge pressure region;
A control passage formed in the shaft of the rotary shaft and communicating the control pressure chamber and the pressure adjustment chamber;
A control mechanism for controlling the pressure in the pressure regulation chamber,
By controlling the pressure of the pressure adjusting chamber by the control mechanism, the tilt angle of the swash plate is changed as the movable body moves in the rotational axis direction, and the piston is tilted to the tilt angle of the swash plate. A variable displacement swash plate compressor that reciprocates with a corresponding stroke,
A back pressure chamber defined between the housing and the moving body;
A throttle communicating the back pressure chamber and the swash plate chamber;
A discharge passage formed in the shaft of the rotating shaft, opening in the outer peripheral surface of the rotating shaft and communicating the control passage and the back pressure chamber;
A valve body disposed in the control passage and opening and closing the discharge passage;
A throttle hole formed in the valve body and forming a part of the control passage,
The valve body opens and closes the discharge passage based on a differential pressure between a pressure on the control pressure chamber side with respect to the throttle hole in the control passage and a pressure on the pressure adjustment chamber side with respect to the throttle hole in the control passage. And
The back pressure chamber is a variable capacity swash plate compressor that moves the moving body so as to reduce an inclination angle of the swash plate when an internal pressure increases. The housing has a recess in which the movable body is arranged so that it can appear and disappear,
The moving body has a bottomed cylindrical shape,
Between the inner peripheral surface of the recess and the outer peripheral surface of the moving body, a radial bearing is provided on which the outer peripheral surface of the moving body can slide,
The variable capacity swash plate compressor according to claim 1, wherein a gap between an outer peripheral surface of the movable body and the radial bearing functions as the throttle. The housing has a recess in which the movable body is arranged so that it can appear and disappear,
The moving body has a bottomed cylindrical shape,
Between the inner peripheral surface of the recess and the outer peripheral surface of the movable body, a seal ring is provided that seals between the inner peripheral surface of the concave portion and the outer peripheral surface of the movable body and has a joint.
The variable capacity swash plate compressor according to claim 1, wherein the joint serves as the throttle. The housing has a recess in which the movable body is arranged so that it can appear and disappear,
The moving body has a bottomed cylindrical shape,
One of the inner peripheral surface of the recess or the outer peripheral surface of the movable body is formed with a slidable coating layer on the other,
The variable capacity swash plate compressor according to claim 1, wherein a gap between the coating layer and the other functions as the throttle.