JP2015183614A - Variable displacement swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable displacement swash plate compressor for enabling an instant change of the inclination of a swash plate into a maximum inclination while maintaining operation efficiency.SOLUTION: A valve element 74 has a first valve part 75 having an end face seal portion 75s for abutting on a seat portion 71e of a first valve seat part 71 to close an extraction passage, and a second valve part 76 having an outer face seal portion 76s for entering into a second valve hole 72h to close an air supply passage. When the valve opening of the first valve part 75 is maximum, a seal length L1 of the outer face seal portion 76s along the moving direction of the valve element 74 is smaller than a distance L2 between the end face seal portion 75s and the seat portion 71e along the moving direction of the valve element 74.

Description

  The present invention relates to a variable displacement swash plate compressor in which a piston moored to a swash plate reciprocates with a stroke corresponding to the inclination angle of the swash plate.

  For example, Patent Document 1 discloses a variable displacement swash plate compressor in which a movable body capable of changing the tilt angle of a swash plate is connected to a swash plate. The moving body is movable in the axial direction of the rotation shaft by changing the pressure inside the control pressure chamber as the refrigerant gas is introduced into the control pressure chamber formed in the housing. . And the inclination angle of a swash plate is changed with the movement to the axial direction of the rotating shaft in this moving body.

  Specifically, when the pressure in the control pressure chamber increases and the pressure in the control pressure chamber approaches the pressure in the discharge pressure region, the moving body moves toward one end in the axial direction of the rotation shaft. The inclination angle of the swash plate increases with the movement of the rotary shaft toward one end in the axial direction of the moving body. When the pressure in the control pressure chamber decreases and the pressure in the control pressure chamber approaches the pressure in the suction pressure region, the moving body moves to the other axial end of the rotating shaft. The inclination angle of the swash plate decreases with the movement of the rotating shaft toward the other end in the axial direction of the moving body. When the inclination angle of the swash plate decreases, the piston stroke decreases and the discharge capacity decreases. When the inclination angle of the swash plate increases, the piston stroke increases and the discharge capacity increases. The variable displacement swash plate compressor includes a displacement control valve, and the pressure of the control pressure chamber is controlled by the displacement control valve.

JP-A-1-190972

  By the way, in such a variable capacity swash plate compressor, when a throttle is provided in the middle of the air supply passage from the discharge pressure region to the control pressure chamber, the control pressure is supplied from the discharge pressure region through the air supply passage. Since the flow rate of the refrigerant gas supplied to the chamber is suppressed by the throttle, it is easy to maintain the inclination angle of the swash plate at an intermediate inclination angle between the maximum inclination angle and the minimum inclination angle. Therefore, the operation with the intermediate discharge capacity can be performed efficiently.

  However, if a throttle is provided in the air supply passage, for example, when an operation command with the maximum discharge capacity is sent from the control computer, the pressure in the control pressure chamber can be immediately brought close to the pressure in the discharge pressure region. Can not. Therefore, the inclination angle of the swash plate cannot be immediately changed to the maximum inclination angle, and it takes time to operate at the maximum discharge capacity.

  In addition, the refrigerant gas supplied from the discharge pressure region to the control pressure chamber via the air supply passage is a compressed refrigerant gas. Therefore, during operation of the variable displacement swash plate compressor, the operation efficiency of the variable displacement swash plate compressor becomes worse as the flow rate of the refrigerant gas supplied to the control pressure chamber increases.

  The present invention has been made to solve the above-mentioned problems, and its purpose is to provide a variable capacity swash plate type capable of immediately changing the tilt angle of the swash plate to the maximum tilt angle while maintaining operating efficiency. It is to provide a compressor.

  A variable capacity swash plate compressor that solves the above-mentioned problems is a swash plate that is housed in a housing and rotates by obtaining a driving force from a rotating shaft, and an inclination angle with respect to the rotating shaft is changed. A piston that is connected to the swash plate and is capable of changing an inclination angle of the swash plate, and is partitioned by the moving body and introduced with a refrigerant gas to change the internal pressure, thereby A control pressure chamber that moves a moving body in a direction in which a rotation axis of the rotation shaft extends and changes an inclination angle of the swash plate; and a capacity control valve that controls a pressure of the control pressure chamber, and the piston includes the piston A variable displacement swash plate compressor that reciprocates at a stroke corresponding to the inclination angle of the swash plate, wherein the displacement control valve includes a valve element that reciprocates when energized by an electromagnetic solenoid, and a suction pressure region from the control pressure chamber. Extraction passage to reach A first valve seat portion having a first valve hole forming a part, a second valve seat portion having a second valve hole forming a part of an air supply passage extending from a discharge pressure region to the control pressure chamber, The valve body includes a first valve portion having an end face seal portion that contacts the first valve seat portion and closes the extraction passage, and enters the inside of the second valve hole to access the air supply passage. A second valve portion having an outer surface seal portion to be closed, and when the valve opening degree of the first valve portion is maximum, the seal length along the moving direction of the valve body in the outer surface seal portion is: The distance is shorter than the distance between the end face seal portion and the first valve seat portion.

  According to this, for example, the second valve portion is in contact with the end surface around the second valve hole in the second valve seat portion, so that the first valve portion has a first surface seal portion that closes the air supply passage. The valve opening degree in the second valve part when the first valve part is moving toward the first valve seat part from the state in which the valve opening degree of the valve part is maximum can be reduced. As a result, the flow rate of the refrigerant gas supplied to the control pressure chamber can be reduced during the operation of the variable capacity swash plate compressor. When the end face seal portion of the first valve portion comes into contact with the first valve seat portion, the outer seal portion of the second valve portion pops out from the second valve hole, and the valve opening degree of the second valve portion is maximized. Become. As a result, the flow rate of the refrigerant gas supplied from the discharge pressure region to the control pressure chamber via the air supply passage increases, so that the inclination angle of the swash plate can be immediately changed to the maximum inclination angle. As a result, the tilt angle of the swash plate can be immediately changed to the maximum tilt angle while maintaining the operation efficiency of the variable capacity swash plate compressor.

  In the variable displacement swash plate compressor, the valve body has a protruding portion that protrudes from the end face seal portion toward the first valve seat portion and enters the inside of the first valve hole to close the extraction passage. And the second valve portion is preferably opened when the protruding portion enters the first valve hole.

  According to this, compared with the case where the valve body does not have a protruding portion, the timing at which the extraction passage is closed can be advanced during the operation of the variable displacement swash plate compressor, via the extraction passage. The amount of refrigerant gas discharged from the control pressure chamber to the suction pressure region can be reduced. As a result, the flow rate of the refrigerant gas supplied from the discharge pressure region to the control pressure chamber via the air supply passage can be reduced in order to maximize the tilt angle of the swash plate, and the variable capacity swash plate compressor can be operated. Efficiency can be improved.

  In the variable displacement swash plate type compressor, the second valve seat portion is separate from the valve housing, and between the first valve seat portion and the second valve seat portion in the valve housing. It is preferable that a biasing member that biases the second valve seat portion toward the stepped portion of the valve housing is provided.

  This makes it easier to adjust the clearance between the second valve hole and the outer seal portion of the second valve portion than when the second valve seat portion is integrally formed with the valve housing. be able to. Therefore, the leakage of the refrigerant gas between the second valve hole and the outer surface seal portion of the second valve portion can be suppressed.

In the variable displacement swash plate compressor, it is preferable that the valve body has an outer surface expanding portion that expands in a tapered shape from the outer surface sealing portion toward the end surface sealing portion.
According to this, in the state where the second valve seat portion is accommodated in the valve housing, the axial center of the second valve seat portion and the valve body can be aligned by bringing the outer surface enlarged portion into contact with the inner surface of the second valve hole. it can. That is, the second valve seat portion and the valve body can be easily centered. Therefore, the leakage of the refrigerant gas between the second valve hole and the outer surface seal portion of the second valve portion can be suppressed.

  In the variable displacement swash plate compressor, the first valve seat is separate from the valve housing and is press-fitted into a press-fitting portion of the valve housing, and the biasing member is the first valve It is preferable that the seat portion has a free length before being pressed into the press-fitting portion.

  According to this, since the urging force of the urging member does not act on the first valve seat part when performing the press-fitting work on the press-fitting part in the first valve seat part, the press-fitting to the press-fitting part in the first valve seat part is performed. Can be easily performed.

  The variable displacement swash plate compressor includes a press-fitting member that is press-fitted into a press-fitting part of the valve housing, and the first valve seat part is separate from the valve housing, and the first valve seat part, The urging member and the second valve seat portion are disposed between the stepped portion and the press-fitting member, and the urging member is free in a state before the press-fitting member is press-fitted into the press-fitting portion. It is preferable that it is long.

  According to this, since the urging force of the urging member does not act on the press-fitting member when performing the press-fitting operation on the press-fitting part in the press-fitting member, the press-fitting to the press-fitting part in the press-fitting member can be easily performed.

  According to the present invention, it is possible to immediately change the inclination angle of the swash plate to the maximum inclination angle while maintaining the operation efficiency.

The sectional side view which shows the double-headed piston type swash plate type compressor in embodiment. Sectional drawing of a capacity control valve when the inclination angle of a swash plate is the minimum inclination angle. Sectional drawing of a capacity | capacitance control valve when the inclination angle of a swash plate is a maximum inclination angle. The side sectional view showing a double-headed piston type swash plate type compressor when the inclination angle of the swash plate is the maximum inclination angle. The graph which shows the relationship between the displacement of a valve body, and the valve opening degree of a 1st valve part and a 2nd valve part. (A) is a partial expanded sectional view which shows the state before the 1st valve seat part is press-fitted in a press-fit part, (b) is the partial enlarged view which shows the state which the 2nd valve seat part and the outer surface expansion part are contacting. Sectional drawing. (A) is a partial enlarged sectional view of the capacity control valve when the swash plate has a minimum inclination angle in another embodiment, and (b) is a partial enlarged sectional view of the capacity control valve when the swash plate has a maximum inclination angle. The graph which shows the relationship between the displacement of the valve body in another embodiment, and the valve opening degree of a 1st valve part and a 2nd valve part. (A) is a partial expanded sectional view of the capacity control valve in another embodiment, (b) is a partially expanded sectional view showing a state before the press-fitting member in another embodiment is press-fitted into the press-fitting part.

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 FIG. 1, the housing 11 of the variable capacity swash plate compressor 10 includes a first cylinder block 12 and a second cylinder block 13 joined together, and a first cylinder block 12 on the front side (one side). The front housing 14 is joined, and the rear housing 15 is joined to the second cylinder block 13 on the rear side (the other side).

  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 along the direction in which the central axis L extends (the axial direction of the rotary shaft 21), and the front end portion side located on the front side (one side) of the housing 11 is connected to the first cylinder block 12. The shaft hole 12h is inserted therethrough. The front end of the rotating shaft 21 is located in the front housing 14. Further, in the rotating shaft 21, the other end side along the direction in which the central axis L extends, and the rear end portion side located on the rear side (the other side) of the housing 11 is provided through the second cylinder block 13. The shaft hole 13h is inserted. 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 crank chamber 24 defined by the first cylinder block 12 and the second cylinder block 13 is formed in the housing 11. The crank chamber 24 accommodates a swash plate 23 that rotates by obtaining a driving force from the rotating shaft 21 and that can tilt in the axial direction with respect to the rotating 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.

  In the first cylinder block 12, a plurality of first cylinder bores 12a penetratingly formed in the axial direction of the first cylinder block 12 are arranged around the rotation shaft 21 (only one first cylinder bore 12a is shown in FIG. 1). . 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. In the second cylinder block 13, a plurality of second cylinder bores 13a penetratingly formed in the axial direction of the second cylinder block 13 are arranged around the rotation shaft 21 (only one second cylinder bore 13a is shown in FIG. 1). . 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 able to reciprocate in the front-rear direction.

  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 large-diameter hole 12b that is continuous with the shaft hole 12h and has a larger diameter than the shaft hole 12h. The first large diameter hole 12 b communicates with the crank chamber 24. The crank chamber 24 and the suction chamber 14a communicate with each other through a suction passage 12c that passes through the first cylinder block 12 and the first valve / port forming body 16.

  The second cylinder block 13 is formed with a second large-diameter hole 13b that is continuous with the shaft hole 13h and has a larger diameter than the shaft hole 13h. The second large diameter hole 13 b communicates with the crank chamber 24. The crank 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. Then, the refrigerant gas sucked into the crank 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. Therefore, the suction chambers 14a and 15a and the crank chamber 24 are in the suction pressure region, and the pressures are almost equal.

  An annular flange portion 21f disposed in the first large-diameter hole 12b protrudes from the rotary 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. A cylindrical support member 39 is press-fitted on the rear end side of the rotary shaft 21. From the outer peripheral surface of the support member 39, an annular flange portion 39f disposed in the second large-diameter hole 13b is projected. A second thrust bearing 27 b is disposed between the flange portion 39 f and the second cylinder block 13 in the axial direction of the rotary shaft 21.

  An annular fixed body 31 that can rotate integrally with the rotary shaft 21 is fixed to the rear side of the flange portion 21 f of the rotary shaft 21 and to the front side of the swash plate 23. Between the flange portion 21f and the fixed body 31, a bottomed cylindrical moving body 32 that is movable in the axial direction of the rotary shaft 21 with respect to the fixed body 31 is disposed.

  The moving body 32 is formed of an annular bottom portion 32a having an insertion hole 32e through which the rotation shaft 21 is inserted, and a cylindrical portion 32b extending along the axial direction of the rotation shaft 21 from the outer peripheral edge of the bottom portion 32a. The inner peripheral surface of the cylindrical portion 32 b is slidable with respect to the outer peripheral edge of the fixed body 31. Thereby, the moving body 32 can rotate integrally with the rotating shaft 21 via the fixed body 31. The space between the inner peripheral surface of the cylindrical portion 32 b and the outer peripheral edge of the fixed body 31 is sealed with a seal member 33, and the space between the insertion hole 32 e and the rotary shaft 21 is sealed with a seal member 34. A control pressure chamber 35 is defined between the fixed body 31 and the moving body 32.

  A first in-shaft passage 21 a extending along the axial direction of the rotation shaft 21 is formed in the rotation shaft 21. The rear end of the first in-axis passage 21a opens to the pressure adjustment chamber 15c. Further, the rotation shaft 21 is formed with a second in-axis passage 21 b extending along the radial direction of the rotation shaft 21. One end of the second in-shaft passage 21 b communicates with the tip of the first in-shaft passage 21 a, and the other end opens to the control pressure chamber 35. Therefore, the control pressure chamber 35 and the pressure adjustment chamber 15c communicate with each other via the first in-axis passage 21a and the second in-axis passage 21b.

  In the crank chamber 24, a lug arm 40 is disposed between the swash plate 23 and the flange portion 39f. 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 FIG. 1) of the swash plate 23 by a first pin 41 that traverses the inside of 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 side of the lug arm 40 is connected to the support member 39 by the second pin 42. Thereby, 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 39 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 FIG. 1) 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.

  Control of the pressure in the control pressure chamber 35 is performed by introducing refrigerant gas from the discharge chamber 15b to the control pressure chamber 35 and discharging refrigerant gas from the control pressure chamber 35 to the suction chamber 15a. Therefore, the refrigerant gas introduced into the control pressure chamber 35 is a control gas that controls the pressure of the control pressure chamber 35. The moving body 32 moves in the axial direction of the rotating shaft 21 with respect to the fixed body 31 in accordance with the pressure difference between the control pressure chamber 35 and the crank chamber 24. The rear housing 15 is assembled with an electromagnetic capacity control valve 50 for controlling the pressure in the control pressure chamber 35. The capacity control valve 50 is electrically connected to the control computer 50c. An air conditioner switch 50s is signal-connected to the control computer 50c.

  As shown in FIG. 2, the valve housing 50 h of the capacity control valve 50 includes a cylindrical first housing 51 in which the electromagnetic solenoid 53 is accommodated, and a cylindrical second housing 52 that is assembled to the first housing 51. . The electromagnetic solenoid 53 has a fixed iron core 54 and a movable iron core 55 that is attracted to the fixed iron core 54 based on excitation by current supply to the coil 53c. The electromagnetic force of the electromagnetic solenoid 53 attracts the movable iron core 55 toward the fixed iron core 54. The electromagnetic solenoid 53 receives energization control (duty ratio control) of the control computer 50c. Between the fixed iron core 54 and the movable iron core 55, a spring 56 that urges the movable iron core 55 in a direction in which the movable iron core 55 is separated from the fixed iron core 54 is disposed.

  A driving force transmission rod 57 is attached to the movable iron core 55. The driving force transmission rod 57 can move integrally with the movable iron core 55. The fixed iron core 54 includes a small-diameter portion 54a located inside the coil 53c, and a large-diameter portion 54b that protrudes from the opening of the first housing 51 opposite to the movable iron core 55 and has a larger diameter than the small-diameter portion 54a. It is configured. A concave portion 54c is formed on the end surface of the large diameter portion 54b opposite to the small diameter portion 54a. A stepped portion 541c is formed on the inner wall of the recessed portion 54c, and the second housing 52 is fitted and fixed to the recessed portion 54c while being in contact with the stepped portion 541c.

  A storage chamber 59 is formed on the opposite side of the second housing 52 from the electromagnetic solenoid 53. A pressure sensitive mechanism 60 is accommodated in the accommodation chamber 59. The pressure sensing mechanism 60 is coupled to a bellows 61, a pressure receiving body 62 that is coupled to one end of the bellows 61 and is press-fitted into an opening of the second housing 52 opposite to the first housing 51, and the other end of the bellows 61. And a spring 64 that urges the pressure receiving body 62 and the connecting body 63 away from each other in the bellows 61.

  In the bellows 61, the pressure receiving body 62 is integrally formed with a stopper 62 a that protrudes toward the connecting body 63. Further, the connecting body 63 is formed with a stopper 63 a that protrudes toward the stopper 62 a of the pressure receiving body 62. The stopper 62a of the pressure receiving body 62 and the stopper 63a of the connecting body 63 define the shortest length of the bellows 61.

  A valve chamber 65 is formed closer to the first housing 51 than the accommodation chamber 59 in the second housing 52. The valve chamber 65 is continuous with the storage chamber 59 and has a smaller diameter than the storage chamber 59. Further, a supply chamber 66 is formed closer to the first housing 51 than the valve chamber 65 in the second housing 52. The supply chamber 66 is continuous with the valve chamber 65 and has a smaller diameter than the valve chamber 65. A step portion 52 f is formed between the valve chamber 65 and the supply chamber 66 in the second housing 52.

  An annular first valve seat portion 71 is disposed near the accommodation chamber 59 in the valve chamber 65. The first valve seat 71 is separate from the second housing 52. A first valve hole 71 h is formed at the center of the first valve seat 71. The first valve hole 71h allows the valve chamber 65 and the storage chamber 59 to communicate with each other. An annular second valve seat portion 72 is disposed near the supply chamber 66 in the valve chamber 65. The second valve seat portion 72 is a separate body from the second housing 52. A second valve hole 72 h is formed at the center of the second valve seat portion 72. The second valve hole 72h allows the valve chamber 65 and the supply chamber 66 to communicate with each other.

  In the valve chamber 65, an urging spring 73 as an urging member is interposed between the first valve seat portion 71 and the second valve seat portion 72. The urging spring 73 urges the second valve seat portion 72 toward the stepped portion 52 f of the second housing 52. The second valve seat portion 72 is positioned by being pressed against the stepped portion 52 f by the biasing force of the biasing spring 73. The first valve seat 71 is press-fitted into the inner surface of the valve chamber 65 on the side of the storage chamber 59 near the storage chamber 59 in the valve chamber 65. Therefore, the inner surface of the valve chamber 65 on the side of the storage chamber 59 forms a press-fit portion 65a into which the first valve seat portion 71 is press-fitted.

  A back pressure chamber 67 is defined between the recess 54 c and the end surface of the second housing 52 on the electromagnetic solenoid 53 side. The back pressure chamber 67 and the storage chamber 59 communicate with each other via a communication passage 52 r formed in the second housing 52.

  A valve body 74 extending from the storage chamber 59 to the back pressure chamber 67 is stored in the second housing 52. The valve body 74 includes a first valve portion 75 and a second valve portion 76 that are accommodated in the valve chamber 65. The first valve portion 75 has an end surface seal portion 75 s that can abut on a seat portion 71 e that is an end surface around the first valve hole 71 h in the first valve seat portion 71. The first valve portion 75 has an annular protrusion 75f that protrudes from the end seal portion 75s and enters the first valve hole 71h. The second valve portion 76 has an outer surface seal portion 76s that enters the second valve hole 72h.

  The valve body 74 has an annular outer surface expanding portion 74a that expands in a tapered shape from the outer surface sealing portion 76s toward the end surface sealing portion 75s. The outer surface enlarged portion 74a is inclined linearly. The valve body 74 has a reduced diameter portion 74b that is disposed in the supply chamber 66 and has an outer diameter that is smaller than that of the outer seal portion 76s. Further, the valve body 74 has a diameter-expanded portion 74c that is continuous with the diameter-reduced portion 74b and that is larger in diameter than the diameter-reduced portion 74b. The enlarged diameter portion 74 c protrudes into the back pressure chamber 67 through the bottom portion of the second housing 52. An annular first working surface 741 that is a step is formed between the outer surface seal portion 76s and the reduced diameter portion 74b of the valve body 74, and between the reduced diameter portion 74b and the enlarged diameter portion 74c of the valve body 74. An annular second working surface 742 that is a step is formed on the surface. The pressure receiving areas of the first working surface 741 and the second working surface 742 are the same.

  The driving force transmission rod 57 passes through the fixed iron core 54 and projects into the back pressure chamber 67. The end of the driving force transmission rod 57 on the back pressure chamber 67 side is in contact with the enlarged diameter portion 74 c of the valve body 74.

  A rod 74e protrudes from the end surface of the valve body 74 on the side of the storage chamber 59. The rod 74e is connected to the connecting body 63 so that the end on the connecting body 63 side can come into contact with and separate from the connecting body 63. In addition, a return spring 77 that urges the valve body 74 toward the electromagnetic solenoid 53 is interposed between the projecting portion 75 f and the connecting body 63.

  The second housing 52 is formed with a communication hole 521 that communicates with the storage chamber 59. The second housing 52 is formed with a communication hole 522 that communicates with the valve chamber 65. Furthermore, a communication hole 523 that communicates with the supply chamber 66 is formed in the second housing 52. The storage chamber 59 communicates with the suction chamber 15a through the communication hole 521 and the passage 81. Further, the valve chamber 65 communicates with the pressure adjusting chamber 15 c via the communication hole 522 and the passage 82. Therefore, the second shaft passage 21b, the first shaft passage 21a, the pressure adjustment chamber 15c, the passage 82, the communication hole 522, the valve chamber 65, the first valve hole 71h, the storage chamber 59, the communication hole 521, and the passage 81 are A bleed passage from the control pressure chamber 35 to the suction chamber 15a is formed.

  The supply chamber 66 communicates with the discharge chamber 15 b through the communication hole 523 and the passage 83. Therefore, the discharge chamber 15b and the control pressure chamber 35 include the passage 83, the communication hole 523, the supply chamber 66, the second valve hole 72h, the valve chamber 65, the communication hole 522, the passage 82, the pressure adjustment chamber 15c, and the first shaft. The passage 21a communicates with the second in-axis passage 21b. Therefore, the passage 83, the communication hole 523, the supply chamber 66, the second valve hole 72h, the valve chamber 65, the communication hole 522, the passage 82, the pressure adjustment chamber 15c, the first in-shaft passage 21a, and the second in-shaft passage 21b are: An air supply passage extending from the discharge chamber 15b to the control pressure chamber 35 is formed.

  The bellows 61 expands and contracts in the moving direction of the valve body 74 by sensing the pressure applied to the bellows 61 in the accommodation chamber 59 and the pressure applied to the enlarged diameter portion 74c of the valve body 74 in the back pressure chamber 67, respectively. The expansion and contraction of the bellows 61 is used for positioning the valve body 74 and contributes to the control of the valve opening degree of the first valve portion 75 and the second valve portion 76. The valve opening degrees of the first valve portion 75 and the second valve portion 76 are determined by the balance of the electromagnetic force generated by the electromagnetic solenoid 53, the biasing force of the spring 56, and the biasing force of the pressure-sensitive mechanism 60.

  The first valve portion 75 is in a closed state in which the protruding portion 75f enters the first valve hole 71h to close the extraction passage, and the protruding portion 75f jumps out of the first valve hole 71h, thereby extracting air. The valve is opened to open the passage. When the outer seal portion 76s enters the second valve hole 72h, the second valve portion 76 enters a closed state in which the air supply passage is closed, and the outer seal portion 76s jumps out of the second valve hole 72h. Thus, the valve is opened to open the air supply passage.

  In the variable capacity swash plate compressor 10 having the above configuration, the movable iron core 55 is separated from the fixed iron core 54 by the spring force of the spring 56 when the air conditioner switch 50 s is turned off and the energization of the electromagnetic solenoid 53 is stopped. At the same time, the urging force of the return spring 77 moves the valve element 74 toward the electromagnetic solenoid 53. Thereby, the end face seal portion 75s is separated from the seat portion 71e, and the projecting portion 75f jumps out of the first valve hole 71h. In the state where the air conditioner switch 50s is turned off and the energization to the electromagnetic solenoid 53 is stopped, the end face seal portion 75s is the most separated state from the seat portion 71e, and the valve opening degree of the first valve portion 75 is It is the maximum time.

  At this time, the outer surface seal portion 76s enters the second valve hole 72h, and the space between the outer surface seal portion 76s and the second valve hole 72h is sealed. The seal length L1 along the moving direction of the valve body 74 in the outer surface seal portion 76s is shorter than the distance L2 along the moving direction of the valve body 74 between the end surface seal portion 75s and the seat portion 71e. . In this embodiment, the seal length L1 along the moving direction of the valve body 74 in the outer surface seal portion 76s when the valve opening degree of the first valve portion 75 is maximum is the valve opening degree of the first valve portion 75. The distance L3 is the same as the distance L3 along the moving direction of the valve body 74 between the protrusion 75f and the first valve seat 71 when. Further, since the pressure receiving areas of the first working surface 741 and the second working surface 742 are the same, the valve body 74 senses the pressure of the refrigerant gas supplied to the supply chamber 66, so that the valve body 74 The movement is suppressed.

  When the valve opening degree of the first valve portion 75 increases, the control pressure chamber 35 to the second shaft passage 21b, the first shaft passage 21a, the pressure adjustment chamber 15c, the passage 82, the communication hole 522, the valve chamber 65, the first The flow rate of the refrigerant gas discharged to the suction chamber 15a through the valve hole 71h, the storage chamber 59, the communication hole 521, and the passage 81 increases, and the pressure in the control pressure chamber 35 approaches the pressure in the suction chamber 15a.

  As shown in FIG. 1, the pressure in the control pressure chamber 35 approaches the pressure in the suction chamber 15a, and the pressure difference between the control pressure chamber 35 and the crank chamber 24 is reduced. The moving body 32 moves so that the swash plate 23 pulls the moving body 32 and the bottom 32a of the moving body 32 approaches the fixed body 31 due to the compression reaction force from. Then, the swash plate 23 swings around the first swing center M1. As the swash plate 23 swings around the first swing center M1, both ends of the lug arm 40 swing around the first swing center M1 and the second swing center M2, respectively. The flange portion 39f of 39 is approached. Thereby, 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. The lug arm 40 comes into contact with the flange portion 39f of the support member 39 when the inclination angle of the swash plate 23 reaches the minimum inclination angle. By the contact between the lug arm 40 and the flange portion 39f, the inclination angle of the swash plate 23 is maintained at the minimum inclination angle.

  As shown in FIG. 3, in the variable displacement swash plate compressor 10 configured as described above, when the air conditioner switch 50 s is turned on and current is supplied to the electromagnetic solenoid 53, the electromagnetic force of the electromagnetic solenoid 53 The movable iron core 55 is attracted toward the fixed iron core 54 against the spring force. Then, the driving force transmission rod 57 presses the valve element 74 against the spring force of the return spring 77.

  When the valve body 74 is pressed, the projecting portion 75f enters the first valve hole 71h, and the outer surface seal portion 76s jumps out of the second valve hole 72h. Further, when the valve body 74 is pressed, the end face seal portion 75s comes into contact with the seat portion 71e and the amount of protrusion from the second valve hole 72h in the outer surface seal portion 76s increases. Then, from the control pressure chamber 35, the second shaft passage 21b, the first shaft passage 21a, the pressure adjustment chamber 15c, the passage 82, the communication hole 522, the valve chamber 65, the first valve hole 71h, the storage chamber 59, the communication hole 521. In addition, the flow rate of the refrigerant gas discharged to the suction chamber 15a via the passage 81 is reduced. From the discharge chamber 15b to the passage 83, the communication hole 523, the supply chamber 66, the second valve hole 72h, the valve chamber 65, the communication hole 522, the passage 82, the pressure adjustment chamber 15c, the first in-axis passage 21a, and the second shaft By supplying the refrigerant gas to the control pressure chamber 35 through the passage 21b, the pressure in the control pressure chamber 35 approaches the pressure in the discharge chamber 15b.

  As shown in FIG. 4, when the pressure in the control pressure chamber 35 approaches the pressure in the discharge chamber 15b and the pressure difference between the control pressure chamber 35 and the crank chamber 24 increases, the moving body 32 pulls the swash plate 23. However, the moving body 32 moves so that the bottom 32 a of the moving body 32 is separated from the fixed body 31. Then, the swash plate 23 swings around the first swing center M1 in the direction opposite to the direction when the tilt angle of the swash plate 23 is decreased. As the swash plate 23 swings around the first swing center M1 in the direction opposite to the direction in which the tilt angle is decreased, both ends of the lug arm 40 are moved to the first swing center M1 and the second swing center, respectively. The swash plate 23 swings around the moving center M2 in the direction opposite to the direction when the inclination angle of the swash plate 23 is decreased, and the lug arm 40 is separated from the flange portion 39f of the support member 39. 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. The moving body 32 comes into contact with the flange portion 21f when the inclination angle of the swash plate 23 reaches the maximum inclination angle. By the contact between the moving body 32 and the flange portion 21f, the inclination angle of the swash plate 23 is maintained at the maximum inclination angle.

Next, the operation of this embodiment will be described.
In FIG. 5, the relationship between the displacement of the valve body 74 in the moving direction of the valve body 74 and the valve opening degrees of the first valve portion 75 and the second valve portion 76 in the present embodiment is indicated by a solid line. Further, as a comparative example of the present embodiment, the first valve portion 75 does not have the protruding portion 75f, and further, the second valve portion 76 is around the second valve hole 72h in the second valve seat portion 72. The relationship between the displacement of the valve body 74 and the valve opening degrees of the first valve portion 75 and the second valve portion 76 in the case of having an end surface seal portion that closes the air supply passage by contacting the end surface. It is indicated by a two-dot chain line.

  As shown in FIG. 5, the second valve portion 76 is in contact with the end surface around the second valve hole 72 h in the second valve seat portion 72, so that the second valve portion 76 has an end surface seal portion that closes the air supply passage. When the first valve portion 75 is moving toward the seat portion 71e from the maximum valve opening degree of the first valve portion 75, the valve opening degree of the second valve portion 76 is reduced. As a result, the flow rate of the refrigerant gas supplied to the control pressure chamber 35 is reduced during the operation of the variable capacity swash plate compressor 10.

  When the end surface seal portion 75s of the first valve portion 75 comes into contact with the seat portion 71e, the outer surface seal portion 76s of the second valve portion 76 jumps out of the second valve hole 72h, and the valve opening of the second valve portion 76 is performed. The degree is maximized. As a result, the flow rate of the refrigerant gas supplied from the discharge chamber 15b to the control pressure chamber 35 through the air supply passage increases, so that the inclination angle of the swash plate 23 is immediately changed to the maximum inclination angle, and operation at the maximum discharge capacity is performed. Done.

  As shown in FIG. 6A, the second valve seat portion 72 is placed on the stepped portion 52f of the second housing 52, the valve body 74 is accommodated in the second housing 52, and the second In a state where the biasing spring 73 is placed on the valve seat 72, the first valve seat 71 is press-fitted into the press-fit portion 65a. At this time, the urging spring 73 has a free length in a state before the first valve seat portion 71 is press-fitted into the press-fit portion 65a. When the first valve seat portion 71 is press-fitted into the press-fit portion 65a, a biasing force that presses the second valve seat portion 72 against the stepped portion 52f is generated in the biasing spring 73.

  As shown in FIG. 6B, the first valve seat portion 71 is press-fitted into the press-fit portion 65a, and the second valve seat portion 72 is pressed against the stepped portion 52f by the biasing force of the biasing spring 73. Then, the valve body 74 is pressed toward the bottom of the second housing 52. Then, the outer surface enlarged portion 74a comes into contact with the inner surface of the second valve hole 72h, and the axial centers of the second valve seat portion 72 and the valve body 74 coincide. As a result, leakage of the refrigerant gas between the second valve hole 72h and the outer surface seal portion 76s of the second valve portion 76 is suppressed.

In the above embodiment, the following effects can be obtained.
(1) The valve body 74 is in contact with the seat portion 71e of the first valve seat portion 71 and enters the inside of the second valve hole 72h and the first valve portion 75 having the end face seal portion 75s that closes the extraction passage. And a second valve portion 76 having an outer surface seal portion 76s for closing the air supply passage. When the valve opening degree of the first valve portion 75 is the maximum, the seal length L1 along the moving direction of the valve body 74 in the outer surface seal portion 76s is that of the valve body 74 between the end surface seal portion 75s and the seat portion 71e. It is shorter than the distance L2 along the moving direction. According to this, for example, the second valve portion 76 is in contact with the end surface around the second valve hole 72h in the second valve seat portion 72, thereby comparing with a case where the second valve portion 76 has an end surface seal portion that closes the air supply passage. The valve opening degree in the second valve part 76 when the first valve part 75 is moving toward the seat part 71e from the maximum valve opening degree of the first valve part 75 can be reduced. As a result, the flow rate of the refrigerant gas supplied to the control pressure chamber 35 can be reduced during the operation of the variable capacity swash plate compressor 10. When the end surface seal portion 75s of the first valve portion 75 comes into contact with the seat portion 71e, the outer surface seal portion 76s of the second valve portion 76 jumps out of the second valve hole 72h, and the valve opening of the second valve portion 76 is performed. The degree is maximized. As a result, the flow rate of the refrigerant gas supplied from the discharge chamber 15b to the control pressure chamber 35 via the air supply passage increases, so that the inclination angle of the swash plate 23 can be immediately changed to the maximum inclination angle. As a result, it is possible to immediately change the inclination angle of the swash plate 23 to the maximum inclination angle while maintaining the operation efficiency of the variable displacement swash plate compressor 10.

  (2) The valve body 74 has a protruding portion 75f that protrudes from the end face seal portion 75s and enters the first valve hole 71h to close the extraction passage. When the protruding portion 75f enters the first valve hole 71h, the second valve portion 76 opens. According to this, as compared with the case where the valve body 74 does not have the protruding portion 75f, the timing at which the extraction passage is closed can be advanced during the operation of the variable displacement swash plate compressor 10, and the extraction passage The amount of refrigerant gas discharged from the control pressure chamber 35 to the suction chamber 15a can be reduced. As a result, the flow rate of the refrigerant gas supplied from the discharge chamber 15b to the control pressure chamber 35 via the air supply passage can be reduced in order to make the inclination angle of the swash plate 23 the maximum inclination angle, and the variable capacity swash plate compressor The operating efficiency of 10 can be improved.

  (3) The second valve seat 72 is separate from the second housing 52, and the second valve seat 72 is located between the first valve seat 71 and the second valve seat 72 in the second housing 52. A biasing spring 73 that biases the seat portion 72 toward the stepped portion 52 f of the second housing 52 is provided. According to this, compared with the case where the second valve seat portion 72 is formed integrally with the second housing 52, the clearance between the second valve hole 72h and the outer surface seal portion 76s of the second valve portion 76 is adjusted. Can be made easy. Therefore, leakage of the refrigerant gas between the second valve hole 72h and the outer surface seal portion 76s of the second valve portion 76 can be suppressed.

  (4) The valve body 74 has an outer surface expanding portion 74a that expands in a tapered shape from the outer surface sealing portion 76s toward the end surface sealing portion 75s. According to this, in a state where the second valve seat portion 72 is accommodated in the second housing 52, the second valve seat portion 72 and the valve body 74 are brought into contact with the inner surface of the second valve hole 72h with the outer surface enlarged portion 74a. Can be aligned. That is, the centering of the second valve seat portion 72 and the valve body 74 can be easily performed. Therefore, leakage of the refrigerant gas between the second valve hole 72h and the outer surface seal portion 76s of the second valve portion 76 can be suppressed.

  (5) The first valve seat 71 is separate from the second housing 52 and is press-fitted into the press-fit portion 65a of the second housing 52. The biasing spring 73 is press-fitted by the first valve seat 71. In a state before being press-fitted into the portion 65a, the length is free. According to this, since the urging force of the urging spring 73 does not act on the first valve seat portion 71 when performing the press-fitting work to the press-fit portion 65a in the first valve seat portion 71, the first valve seat portion 71 It is possible to easily press-fit the press-fitting portion 65a.

  (6) In the variable displacement swash plate compressor 10 employing the double-headed piston 25, the crank chamber 24 is controlled in order to change the inclination angle of the swash plate 23 like the variable displacement swash plate compressor having a single-headed piston. It cannot function as a pressure chamber. Therefore, in the variable displacement swash plate compressor 10 employing the double-headed piston 25, the inclination angle of the swash plate 23 is changed by changing the pressure in the control pressure chamber 35 partitioned by the moving body 32. Since the control pressure chamber 35 is a smaller space than the crank chamber 24, the amount of refrigerant gas introduced into the control pressure chamber 35 is small, and the operation efficiency of the variable capacity swash plate compressor 10 is improved. To do.

In addition, you may change the said embodiment as follows.
As shown in FIGS. 7A and 7B, a valve body 74A in which the protruding portion 75f does not protrude from the end face seal portion 75s may be applied. In this case, the first valve portion 75 is in a closed state in which the end surface seal portion 75s is in contact with the seat portion 71e to close the extraction passage, and the end surface seal portion 75s is separated from the seat portion 71e. The valve opening state opens the extraction passage.

  In FIG. 8, the relationship between the displacement of the valve body 74A in the moving direction of the valve body 74A and the valve opening degrees of the first valve portion 75 and the second valve portion 76 in the present embodiment is indicated by a solid line. As a comparative example of the present embodiment, the second valve portion 76 has an end surface seal portion that closes the air supply passage by contacting the end surface of the second valve seat portion 72 around the second valve hole 72h. The relationship between the displacement of the valve body 74A and the valve openings of the first valve portion 75 and the second valve portion 76 is indicated by a two-dot chain line.

  As shown in FIG. 8, the second valve portion 76 is in contact with an end surface around the second valve hole 72 h in the second valve seat portion 72, thereby comparing with a case where the second valve portion 76 has an end surface seal portion that closes the air supply passage. When the first valve portion 75 is moving toward the seat portion 71e from the maximum valve opening degree of the first valve portion 75, the valve opening degree of the second valve portion 76 is reduced. As a result, the flow rate of the refrigerant gas supplied to the control pressure chamber 35 is reduced during the operation of the variable capacity swash plate compressor 10. When the end surface seal portion 75s of the first valve portion 75 comes into contact with the seat portion 71e, the outer surface seal portion 76s of the second valve portion 76 jumps out of the second valve hole 72h, and the valve opening of the second valve portion 76 is performed. The degree is maximized. As a result, the flow rate of the refrigerant gas supplied from the discharge chamber 15b to the control pressure chamber 35 through the air supply passage increases, so that the inclination angle of the swash plate 23 is immediately changed to the maximum inclination angle, and operation at the maximum discharge capacity is performed. Done.

  As shown in FIG. 9A, an annular press-fitting member 78 that is press-fitted into the press-fit portion 65a may be further provided. And the 1st valve-seat part 71 does not need to be press-fit in the press-fit part 65a. The first valve seat portion 71, the urging spring 73, and the second valve seat portion 72 are disposed between the step portion 52f and the press-fitting member 78.

  As shown in FIG. 9B, the biasing spring 73 may have a free length before the press-fitting member 78 is press-fitted into the press-fitting portion 65a. According to this, since the urging force of the urging spring 73 does not act on the press-fitting member 78 when performing the press-fitting work on the press-fitting part 65a of the press-fitting member 78, the press-fitting member 78 can be easily pressed into the press-fitting part 65a. It can be carried out.

  When the press-fitting member 78 is press-fitted into the press-fitting portion 65 a, the first valve seat portion 71 is assembled in a state of being urged by the press-fitting member 78 by the urging force of the urging spring 73. Therefore, since it is not necessary to press-fit the first valve seat 71 into the press-fit portion 65a in order to assemble the first valve seat 71, the first valve seat 71 is not restrained with respect to the second housing 52, and the first The operation | work which aligns the axial center of the 1 valve seat part 71 and the valve body 74 can be made easy.

  In the embodiment, the urging spring 73 is not free length before the first valve seat portion 71 is press-fitted into the press-fit portion 65a, and the first valve seat portion 71 is free from the urging spring 73. An urging force may be acting.

In the embodiment, the outer surface enlarged portion 74a may not be formed between the outer surface seal portion 76s and the end surface seal portion 75s in the valve body 74.
In the embodiment, the second valve seat portion 72 may be integrally formed with the second housing 52.

In the embodiment, the driving force transmission rod 57 may be integrated with the valve body 74.
In the embodiment, the storage chamber 59 may communicate with the suction chamber 14a through the communication hole 521 and the passage 81. In short, an extraction passage from the control pressure chamber 35 to the suction pressure region is formed. That's fine.

  In the embodiment, the discharge chamber 14b and the control pressure chamber 35 are provided with the passage 83, the communication hole 523, the supply chamber 66, the second valve hole 72h, the valve chamber 65, the communication hole 522, the passage 82, the pressure adjustment chamber 15c, You may communicate via the 1 axis | shaft channel | path 21a and the 2nd axis | shaft channel | path 21b.

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

  DESCRIPTION OF SYMBOLS 10 ... Variable displacement type swash plate compressor, 11 ... Housing, 14a, 15a ... Suction chamber which is suction pressure area, 14b, 15b ... Discharge chamber which is discharge pressure area, 15c ... Pressure which forms extraction passage and supply passage Adjusting chamber, 21 ... rotating shaft, 21a ... first in-shaft passage forming bleed passage and supply passage, 21b ... second in-shaft passage forming bleed passage and supply passage, 23 ... swash plate, 25 ... piston Double head piston, 32 ... moving body, 35 ... control pressure chamber, 50 ... displacement control valve, 50h ... valve housing, 52f ... stepped portion, 53 ... electromagnetic solenoid, 59 ... storage chamber forming a bleed passage, 65 ... bleed A valve chamber forming a passage and an air supply passage, 65a ... a press-fitting portion, 66 ... a supply chamber forming an air supply passage, 71 ... a first valve seat portion, 71h ... a first valve hole, 72 ... a second valve seat portion, 72h ... second valve hole, 73 ... biasing member Urging springs 74, 74A ... valve body, 74a ... outer surface enlarged portion, 75 ... first valve portion, 75f ... projecting portion, 75s ... end face seal portion, 76 ... second valve portion, 76s ... outer surface seal portion, 78 ... Press-fitting member, 81 ... Passage forming a bleed passage, 82 ... Passage forming a bleed passage and a supply passage, 83 ... Passage forming a supply passage, 521 ... Communication hole forming a bleed passage, 522 ... Bleak Communication holes forming passages and air supply passages, 523... Communication holes forming air supply passages.

Claims (6)

A swash plate that is housed in a housing and rotates by obtaining a driving force from a rotating shaft, and an inclination angle with respect to the rotating shaft is changed, a piston moored to the swash plate, and a swash plate that is connected to the swash plate A movable body that can change the inclination angle of the swash plate, and is moved by the movable body in a direction in which the rotation axis of the rotating shaft extends by being divided by the movable body and changing the internal pressure by introducing refrigerant gas. And a control pressure chamber that changes the tilt angle of the swash plate, and a capacity control valve that controls the pressure of the control pressure chamber, and the piston reciprocates at a stroke corresponding to the tilt angle of the swash plate Type swash plate compressor,
The capacity control valve is
A valve body that reciprocates by energization of an electromagnetic solenoid; a first valve seat having a first valve hole that forms a part of a bleed passage extending from the control pressure chamber to a suction pressure region; and the control pressure from a discharge pressure region. A second valve seat portion having a second valve hole that forms part of the air supply passage leading to the chamber,
The valve body has a first valve portion having an end face seal portion that contacts the first valve seat portion and closes the extraction passage, and an outer surface that enters the inside of the second valve hole and closes the supply passage. A second valve portion having a seal portion,
The seal length along the moving direction of the valve body in the outer surface seal portion when the valve opening degree of the first valve portion is maximum is based on the distance between the end surface seal portion and the first valve seat portion. Is a variable capacity swash plate compressor characterized in that it is also shorter. The valve body has a protruding portion that protrudes from the end face seal portion toward the first valve seat portion and enters the inside of the first valve hole to close the extraction passage,
2. The variable displacement swash plate compressor according to claim 1, wherein the second valve portion opens when the protruding portion enters the first valve hole. 3.   The second valve seat portion is separate from the valve housing, and the second valve seat portion is disposed between the first valve seat portion and the second valve seat portion in the valve housing. 3. The variable capacity swash plate compressor according to claim 1, further comprising an urging member that urges toward a step portion of the housing.   4. The variable capacity swash plate compressor according to claim 3, wherein the valve body has an outer surface expanding portion that expands in a tapered shape from the outer surface sealing portion toward the end surface sealing portion. 5.   The first valve seat portion is separate from the valve housing, and is press-fitted into the press-fit portion of the valve housing, and the biasing member is press-fitted into the press-fit portion with the first valve seat portion. The variable capacity swash plate compressor according to claim 3 or 4, wherein the compressor has a free length in the previous state. A press-fitting member that is press-fitted into the press-fitting portion of the valve housing;
The first valve seat is separate from the valve housing;
The first valve seat portion, the biasing member, and the second valve seat portion are disposed between the stepped portion and the press-fit member,
The variable displacement swash plate compressor according to claim 3 or 4, wherein the urging member has a free length before the press-fitting member is press-fitted into the press-fitting portion.