JP2018109364A - Variable displacement compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent delay in releasing a pressure in a control pressure chamber of a crank chamber and the like, in a variable displacement compressor.SOLUTION: A selector valve 350 is disposed at a crank chamber 140 side with respect to a control valve 300 of a pressure supply passage 145. The selector valve 350 is switched to a first state to communicate a first valve hole 104c and a second valve hole 151a, and a second state to communicate the second valve hole 151a and a pressure release hole 351a communicated to a suction chamber 141. The selector valve 350 includes a definition member 351, a first valve portion 352a, a second valve portion 352b, a shaft portion 352c, a communication passage 352d and an internal passage 352e. A sliding portion 352a1 of the first valve portion 352a has a reception face 352f with which a refrigerant flowing to a second region s12 through a first internal passage 352e1 is collided, and which receives a dynamic pressure directed to a direction separating from a second valve seat 151b around the second valve hole 151a. An outer diameter of a rear end portion 352a3 of the first valve portion 352a is smaller than an outer diameter of the sliding portion 352a1.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a variable capacity compressor whose discharge capacity changes according to the pressure of a control pressure chamber such as a crank chamber.

  As an example of this type of variable displacement compressor, a variable displacement compressor described in Patent Document 1 includes a control valve that controls the opening of a pressure supply passage that communicates a discharge chamber and a crank chamber, the control valve, And a switching valve including a spool having a first valve portion that opens and closes a pressure supply passage between the crank chamber and a second valve portion that opens and closes a pressure release passage communicating the crank chamber and the suction chamber. The spool is configured such that when the pressure in the pressure supply passage between the control valve and the switching valve is higher than the pressure in the crank chamber, the first valve portion opens the pressure supply passage to release the crank from the discharge chamber. The refrigerant is supplied to the chamber, and the second valve portion minimizes the opening of the pressure release passage. Further, when the pressure in the pressure supply passage between the control valve and the switching valve is lower than the pressure in the crank chamber, the spool closes the pressure supply passage and the crank chamber The refrigerant is prevented from flowing back to the control valve, and the second valve portion is configured to maximize the opening of the pressure release passage.

Japanese Patent Laid-Open No. 2006-108961

  In the conventional variable capacity compressor, when the control valve closes the pressure supply passage, the refrigerant in the pressure supply passage between the control valve and the switching valve flows to the suction chamber via the throttle passage. As a result, the pressure in the pressure supply passage between the control valve and the switching valve decreases to the pressure in the suction chamber, so that the spool moves in a direction that maximizes the opening of the pressure release passage. It has become.

  However, the pressure supply passage between the control valve and the switching valve also communicates with the internal passage of the spool having a passage sectional area larger than that of the throttle passage. For this reason, when the control valve closes the pressure supply passage, it flows into the pressure supply passage between the control valve and the switching valve from the crank chamber side via the internal passage (back flow). Due to the refrigerant, the pressure in the pressure supply passage between the control valve and the switching valve may not quickly decrease to the pressure in the suction chamber. Furthermore, the first valve portion of the spool has a sliding contact portion that is slidably supported on the inner peripheral surface of the storage chamber, and the internal passage is closer to the control valve (upstream side) than the sliding contact portion. An opening is formed in a region between the inner peripheral surface of the storage chamber and the outer peripheral surface of the spool (that is, a part of the pressure supply passage). For this reason, the refrigerant that has flowed (backflowed) into the region via the internal passage of the spool collides with the end of the sliding contact portion, and closes the pressure release passage in the spool (on the crank chamber side). There is a risk of applying a force in the direction toward the. As a result, there is a possibility that the movement of the spool, that is, the release pressure of the crank chamber may be delayed.

  Accordingly, an object of the present invention is to provide a variable capacity compressor capable of preventing a delay in releasing pressure in a control pressure chamber such as the crank chamber.

  According to one aspect of the present invention, the suction chamber into which the refrigerant is guided, the compression section that sucks and compresses the refrigerant in the suction chamber, the discharge chamber into which the refrigerant compressed by the compression section is discharged, and the control pressure chamber A variable capacity compressor is provided that has a discharge capacity that changes according to the pressure in the control pressure chamber. The variable capacity compressor includes a control valve, a switching valve, and a throttle passage. The control valve is provided in a pressure supply passage for supplying the refrigerant in the discharge chamber to the control pressure chamber, and controls the opening of the pressure supply passage. The switching valve is a switching valve provided closer to the control pressure chamber than the control valve in the pressure supply passage, and is a first valve hole communicating with the pressure supply passage between the control valve and the switching valve. A first state in which the second valve hole communicating with the pressure supply passage between the switching valve and the control pressure chamber communicates with the pressure relief hole communicated with the second valve hole and the suction chamber. The second state is switched to. The throttle passage communicates the pressure supply passage between the control valve and the switching valve and the suction chamber. The switching valve includes a partition member, a first valve portion, a second valve portion, a shaft portion, a communication passage, and an internal passage. The partition member partitions the first valve chamber having the first valve hole and the second valve chamber having the second valve hole and the pressure release hole. The first valve portion has an outer peripheral surface that is in sliding contact with an inner peripheral surface of the first valve chamber, and the first valve chamber is divided into a first region on the first valve hole side and a second region on the partition member side. A sliding portion that is partitioned into a first end portion that is formed at an end portion of the sliding portion on the first region side and that is separated from and in contact with a first valve seat around the first valve hole, and the first portion of the sliding portion. A cylindrical rear end portion extending from the two region sides toward the partition member side and having an outer diameter smaller than the outer diameter of the sliding portion is included. The second valve portion is disposed in the second valve chamber, and is separated from and in contact with a second valve seat around the second valve hole. The shaft portion connects the first valve portion and the second valve portion and penetrates the partition member. The communication path is a path for communicating the first region and the second region. The internal passage extends through the peripheral wall of the rear end portion to communicate the second region and the region in the rear end portion, and extends from the region in the rear end portion to the second valve portion. And a second internal passage having an open end on an end surface of the second valve portion on the second valve seat side. The switching valve is separated from the first valve seat and contacts the second valve seat when the pressure in the pressure supply passage between the control valve and the switching valve is higher than the pressure in the control pressure chamber. As a result, the first valve hole and the second valve hole are communicated with each other via the internal passage, and the communication between the second valve hole and the pressure release hole is blocked, and the control valve and the switching valve are connected to each other. When the pressure in the pressure supply passage is lower than the pressure in the control pressure chamber, the first valve hole and the second valve are brought into contact with the first valve seat and separated from the second valve seat. It operates so that the communication with the hole is blocked and the second valve hole and the pressure release hole are communicated. The sliding portion is a receiving surface on which a refrigerant flowing into the second region collides with the first internal passage, and has a receiving surface that receives a dynamic pressure in a direction away from the second valve seat.

  According to the variable capacity compressor according to the one aspect of the present invention, the first internal passage of the internal passage is divided into the second region of the first valve chamber, that is, the partition rather than the sliding portion. It opens to the member side (opposite side to the control valve side, downstream side). Then, when the control valve closes the pressure supply passage and the pressure in the pressure supply passage between the control valve and the switching valve decreases, the refrigerant is supplied to the second region via the first internal passage. Even if the refrigerant flows in (reverse flow), at least a part of the refrigerant flow collides with the receiving surface, and the so-called spool including the first valve portion, the shaft portion, and the second valve portion is A dynamic pressure is applied toward the direction away from the second valve seat via the receiving surface. Furthermore, since the outer diameter of the rear end portion through which the first internal passage passes is smaller than the outer diameter of the sliding portion, a part of the refrigerant flowing into the second region via the first internal passage is Even if it flows to the side opposite to the receiving surface, the movement of the spool in the direction away from the second valve seat is not hindered. For this reason, the switching valve moves the spool smoothly in the direction in which the second valve hole and the pressure release hole are communicated with each other by the dynamic pressure, and quickly changes from the first state to the second state. Switch to Therefore, a delay in releasing the control pressure chamber is prevented.

It is sectional drawing of the variable capacity compressor in one Embodiment of this invention. It is sectional drawing of the control valve of the said variable capacity compressor. FIG. 4 is a cross-sectional view of a switching valve of the variable capacity compressor, where (a) is a cross-sectional view showing a pressure supply state (first state) to the crank chamber, and (b) is a pressure release state (second state) from the crank chamber. FIG. It is a diagram which shows the correlation with the coil energization amount of the said control valve, and setting pressure. It is sectional drawing of the division member of the said switching valve. It is sectional drawing of the 1st valve part of the said switching valve. It is sectional drawing of the integral formation body of the 2nd valve part and axial part of the said switching valve. It is an expanded sectional view of the junction part of the 1st valve part of the above-mentioned change valve, and a shaft part. It is sectional drawing of the modification of the said switching valve. It is sectional drawing of the variable capacity compressor in the reference example of this invention, (a) is sectional drawing which shows the pressure supply state (1st state) to a crank chamber, (b) is the pressure release state from a crank chamber ( It is sectional drawing which shows a 2nd state.

Embodiments of the present invention will be described below in detail with reference to the accompanying drawings.
FIG. 1 illustrates a variable capacity clutchless compressor applied to a vehicle air conditioner system (air conditioner system).

  A variable capacity compressor 100 shown in FIG. 1 includes a cylinder block 101 having a plurality of cylinder bores 101a, a front housing 102 provided at one end of the cylinder block 101, and a valve plate 103 at the other end of the cylinder block 101. And a cylinder head 104 provided. A crank chamber 140 as a control pressure chamber is formed by the cylinder block 101 and the front housing 102, and the drive shaft 110 is provided across the crank chamber 140.

  A swash plate 111 is disposed around an intermediate portion in the extending direction of the axis O of the drive shaft 110. The swash plate 111 is connected to a rotor 112 fixed to the drive shaft 110 via a link mechanism 120, and the tilt angle of the swash plate 111 with respect to the axis O can be changed. The link mechanism 120 includes a first arm 112 a projecting from the rotor 112, a second arm 111 a projecting from the swash plate 111, and one end pivotable to the first arm 112 a via the first connecting pin 122. And a link arm 121 having the other end rotatably connected to the second arm 111a via a second connection pin 123.

  The through hole 111b of the swash plate 111 is formed in a shape that allows the swash plate 111 to tilt within a range between the maximum inclination angle and the minimum inclination angle, and the through hole 111b has a minimum inclination restriction portion (not shown) that contacts the drive shaft 110. ) Is formed. When the inclination angle of the swash plate 111 when the swash plate 111 is orthogonal to the drive shaft 110 is 0 deg, the minimum inclination restricting portion of the through hole 111b is formed so that the swash plate 111 can be inclined to approximately 0 deg. Further, the maximum inclination angle of the swash plate 111 is regulated by the swash plate 111 coming into contact with the rotor 112.

  Between the rotor 112 and the swash plate 111, an inclination-decreasing spring 114 that biases the swash plate 111 toward the minimum inclination angle is mounted, and between the swash plate 111 and the spring support member 116 provided on the drive shaft 110. Is attached with an inclination increasing spring 115 that urges the swash plate 111 in an increasing direction. Here, the biasing force of the tilt-increasing spring 115 at the minimum tilt angle is set larger than the biasing force of the tilt-decreasing spring 114, and when the drive shaft 110 is not rotating, the swash plate 111 is The urging force and the urging force of the inclination increasing spring 115 are positioned at an inclination angle that balances.

  One end of the drive shaft 110 extends through the boss portion 102a protruding outside the front housing 102 to the outside of the front housing 102, and is connected to a power transmission device (not shown). A shaft seal device 130 is inserted between the drive shaft 110 and the boss portion 102a to shut off the crank chamber 140 and the external space.

  A coupling body of the drive shaft 110 and the rotor 112 is supported by bearings 131 and 132 in the radial direction, and supported by a bearing 133 and a thrust plate 134 in the thrust direction. The power from the external drive source is transmitted to the power transmission device, and the drive shaft 110 can rotate in synchronization with the rotation of the power transmission device. The gap between the portion of the drive shaft 110 with which the thrust plate 134 abuts and the thrust plate 134 is adjusted to a predetermined gap by the adjustment screw 135.

  A piston 136 is disposed in the cylinder bore 101a, and an outer peripheral portion of the swash plate 111 is accommodated in an inner space of an end portion of the piston 136 that protrudes toward the crank chamber 140. The swash plate 111 includes a pair of shoes 137. It is comprised so that it may interlock with piston 136 via. The piston 136 reciprocates in the cylinder bore 101 a by the rotation of the swash plate 111. In the cylinder head 104, a suction chamber 141 is formed at the center, and a discharge chamber 142 that surrounds the radially outer side of the suction chamber 141 in a ring shape is defined.

  The suction chamber 141 and the cylinder bore 101a communicate with each other via a communication hole 103a provided in the valve plate 103 and a suction valve (not shown) formed in the suction valve forming plate 150. The discharge chamber 142 and the cylinder bore 101 a communicate with each other through a discharge valve (not shown) formed in the discharge valve forming plate 151 and a communication hole 103 b provided in the valve plate 103. The front housing 102, the center gasket (not shown), the cylinder block 101, the cylinder gasket 152, the suction valve forming plate 150, the valve plate 103, the discharge valve forming plate 151, the head gasket 153, and the cylinder head 104 are sequentially connected. The compressor housing is formed by being fastened by a plurality of through bolts 105.

  Further, a muffler is provided on the upper portion of the cylinder block 101 in FIG. The muffler is formed by fastening a lid member 106 where the discharge port 106a is opened and a forming wall 101b formed in the upper part of the cylinder block 101 with a bolt via a seal member (not shown). A discharge check valve 200 is disposed in a muffler space 143 surrounded by the lid member 106 and the forming wall 101b.

  The discharge check valve 200 is disposed at a connection portion between the communication path 144 that connects the discharge chamber 142 and the muffler space 143 and the muffler space 143, and is connected to the communication path 144 (upstream side) and the muffler space 143 (downstream side). It operates in response to the pressure difference. When the pressure difference is smaller than the predetermined value, the communication path 144 is shut off, and when the pressure difference is larger than the predetermined value, the communication path 144 is opened. Accordingly, the discharge chamber 142 is connected to the refrigerant circuit (the high-pressure side) of the air conditioner system via the discharge passage formed by the communication passage 144, the discharge check valve 200, the muffler space 143, and the discharge port 106a.

  In the cylinder head 104, a suction passage (not shown) and a suction passage constituted by a communication passage 104 a are linearly extended from the radially outer side of the cylinder head 104 so as to cross a part of the discharge chamber 142. The suction chamber 141 is connected to the suction side refrigerant circuit of the air conditioner system via the suction passage.

  The refrigerant on the low pressure side of the refrigerant circuit of the air conditioning system is guided to the suction chamber 141 through the suction passage. The refrigerant in the suction chamber 141 is sucked into the cylinder bore 101a by the reciprocating motion of the piston 136, compressed, and discharged into the discharge chamber 142. That is, in this embodiment, the cylinder bore 101a and the piston 136 constitute a compression unit that sucks and compresses the refrigerant in the suction chamber 141. Then, the refrigerant discharged to the discharge chamber 142 (refrigerant compressed by the compression unit) is guided to the high-pressure side of the refrigerant circuit of the air conditioner system through the discharge passage.

  A pressure supply passage 145 for supplying the refrigerant in the discharge chamber 142 to the crank chamber 140 is formed in the cylinder head 104. A control valve 300 and a switching valve 350 are provided in the pressure supply passage 145. The switching valve 350 is disposed downstream of the control valve 300 in the pressure supply passage 145 (on the crank chamber 140 side). Specifically, the control valve 300 is disposed in the accommodation hole 104b, and the switching valve 350 is disposed in the accommodation chamber 104c formed on the downstream side of the control valve 300 in the pressure supply passage 145.

  FIG. 2 is a cross-sectional view of the control valve 300. The control valve 300 is a valve that controls the opening area (opening degree) of the pressure supply passage 145. Specifically, as shown in FIG. 1, the accommodation hole 104b formed along the radial direction of the cylinder head 104. Is housed in. In the present embodiment, O-rings 300a to 300c are mounted on the control valve 300, and an A region communicating with the suction chamber 141 through the communication passage 104d is formed in the accommodation hole 104b by the O-rings 300a to 300c. A region B communicating with the discharge chamber 142 via the communication passage 104e and a region C communicating with the storage chamber 104c via the communication passage 104f are partitioned. The B region and the C region of the accommodation hole 104 b constitute a part of the pressure supply passage 145. The opening of the pressure supply passage 145 is adjusted in response to the pressure of the suction chamber 141 introduced through the communication passage 104d and the electromagnetic force generated by the current flowing through the solenoid in response to the external signal, The discharge gas introduction amount (pressure supply amount) is controlled.

  FIG. 3 is a cross-sectional view of the switching valve 350. The switching valve 350 is a valve that switches between a first state shown in FIG. 3A and a second state shown in FIG. In the present embodiment, the switching valve 350 includes a first valve portion 352a that opens and closes a pressure supply passage 145 between the control valve 300 and the crank chamber 140, and a pressure release passage 146 that communicates the crank chamber 140 and the suction chamber 141. Among them, a spool 352 having a second valve portion 352b for opening and closing a first pressure release passage 146a described later is included.

  The spool 352 moves according to the difference between the pressure in the pressure supply passage 145 between the control valve 300 and the switching valve 350 and the pressure in the crank chamber 140, whereby the switching valve 350 is controlled from the crank chamber 140 side. It has a function as a check valve for preventing the reverse flow of the refrigerant (fluid) toward the valve 300 and a function for controlling the discharge of the refrigerant from the crank chamber 140 to the suction chamber 141.

In the present embodiment, a first pressure release passage 146a and a second pressure release passage 146b are provided as the pressure release passage 146 for discharging the refrigerant in the crank chamber 140 to the suction chamber 141. The first pressure release passage 146a is opened and closed by the switching valve 350 via the switching valve 350. The second pressure relief passage 146b includes a communication passage 101c that extends through the end surface of the cylinder block 101 on the front housing 102 side and extends to the cylinder head 104 side, a space 101d that opens to the end surface of the cylinder block 101 on the cylinder head 104 side, and a valve plate The switching valve 350 is bypassed via a fixed throttle 103 c formed in 103.
The flow passage cross-sectional area of the first pressure relief passage 146a when opened by the switching valve 350 is set larger than the flow passage cross-sectional area of the fixed throttle 103c of the second pressure relief passage 146b.

  When the control valve 300 is closed and the pressure in the pressure supply passage 145 between the control valve 300 and the switching valve 350 becomes lower than the pressure in the crank chamber 140, the switching valve 350 closes the pressure supply passage 145. While preventing the reverse flow of the refrigerant from the crank chamber 140 toward the control valve 300, the opening of the first pressure release passage 146a is set to the maximum opening. As a result, the refrigerant in the crank chamber 140 is quickly discharged to the suction chamber 141 via the first pressure release passage 146a and the second pressure release passage 146b, and the pressure in the crank chamber 140 becomes equal to the pressure in the suction chamber 141. The inclination angle of the swash plate is maximized, and the piston stroke (discharge capacity) is maximized.

  When the control valve 300 is opened and the pressure in the pressure supply passage 145 between the control valve 300 and the switching valve 350 becomes higher than the pressure in the crank chamber 140, the switching valve 350 opens the pressure supply passage 145. The first pressure relief passage 146a is closed. As a result, the refrigerant in the discharge chamber 142 is supplied to the crank chamber 140 via the pressure supply passage 145, while the refrigerant in the crank chamber 140 is restricted from flowing out to the suction chamber 141, and the pressure in the crank chamber 140 increases. The pressure in the crank chamber 140 increases according to the opening of the control valve 300, the inclination angle of the swash plate 111 decreases from the maximum, and the piston stroke can be controlled variably.

  As described above, the variable capacity compressor 100 includes the suction chamber 141, the compression unit, the discharge chamber 142, and the crank chamber 140 as a control pressure chamber, and the discharge capacity changes according to the pressure of the crank chamber 140. In other words, it is a compressor whose discharge capacity is controlled by pressure regulation in the crank chamber 140. The structure and operation of the switching valve 350 will be described in detail later. First, the structure of the control valve 300 will be described in detail.

`` Control valve ''
The control valve 300 includes a valve unit and a drive unit (solenoid) that opens and closes the valve unit.

The valve unit of the control valve 300 includes a cylindrical valve housing 301. In the valve housing 301, a first pressure sensing chamber 302, a valve chamber 303, and a second pressure sensing chamber 307 are sequentially arranged in the axial direction. It is formed side by side.
The first pressure sensing chamber 302 communicates with the crank chamber 140 through a communication hole 301 a formed in the outer peripheral surface of the valve housing 301, an accommodation hole 104 b formed in the cylinder head 104, and a communication passage 104 f.

  The second pressure sensing chamber 307 communicates with the suction chamber 141 through a communication hole 301 e formed in the outer peripheral surface of the valve housing 301 and a communication passage 104 d formed in the cylinder head 104. The valve chamber 303 communicates with the discharge chamber 142 via a communication hole 301 b formed in the outer peripheral surface of the valve housing 301 and a communication passage 104 e formed in the cylinder head 104. The first pressure sensing chamber 302 and the valve chamber 303 can communicate with each other through a valve hole 301c.

  A support hole 301 d is formed between the valve chamber 303 and the second pressure sensing chamber 307. A bellows 305 is disposed in the first pressure sensing chamber 302. The bellows 305 has a built-in spring with a vacuum, and is disposed so as to be displaceable in the axial direction of the valve housing 301. It has a function.

  A cylindrical valve body 304 is accommodated in the valve chamber 303. The valve body 304 can slide in the support hole 301 d while the outer peripheral surface is in close contact with the inner peripheral surface of the support hole 301 d, and can move in the axial direction of the valve housing 301. One end of the valve body 304 can open and close the valve hole 301 c, and the other end of the valve body 304 protrudes into the second pressure sensing chamber 307. One end of a rod-shaped connecting portion 306 is fixed to one end of the valve body 304. The other end of the connecting portion 306 is disposed so as to be able to contact the bellows 305 and has a function of transmitting the displacement of the bellows 305 to the valve body 304.

  The drive unit of the control valve 300 has a cylindrical solenoid housing 312 that is coaxially connected to the other end of the valve housing 301. The solenoid housing 312 houses a molded coil 314 in which the electromagnetic coil is covered with resin. The solenoid housing 312 accommodates a cylindrical fixed core 310 concentrically with the mold coil 314, and the fixed core 310 extends from the valve housing 301 to the vicinity of the center of the mold coil 314. The end of the fixed core 310 on the side opposite to the valve housing 301 is surrounded by a cylindrical sleeve 313. The fixed core 310 has an insertion hole 310 a in the center, and one end of the insertion hole 310 a opens into the second pressure sensing chamber 307. A cylindrical movable core 308 is accommodated between the fixed core 310 and the closed end of the sleeve 313.

  A solenoid rod 309 is inserted into the insertion hole 310a, and one end of the solenoid rod 309 is fixed to the proximal end side of the valve body 304 by press fitting. The other end of the solenoid rod 309 is press-fitted into a through hole formed in the movable core 308, and the solenoid rod 309 and the movable core 308 are integrated. A release spring 311 is provided between the fixed core 310 and the movable core 308 to urge the movable core 308 in a direction away from the fixed core 310 (valve opening direction).

  The movable core 308, the fixed core 310, and the solenoid housing 312 are formed of a magnetic material and constitute a magnetic circuit. The sleeve 313 is made of a nonmagnetic material such as a stainless steel material. A control device provided outside the variable capacity compressor 100 is connected to the mold coil 314 via a signal line. The mold coil 314 generates an electromagnetic force F (i) when the control current I is supplied from the control device. The electromagnetic force F (i) of the mold coil 314 attracts the movable core 308 toward the fixed core 310 and drives the valve body 304 in the valve closing direction.

The valve body 304 of the control valve 300 includes an urging force fs due to the release spring 311, a force due to the pressure in the valve chamber 303 (discharge pressure Pd), the first pressure sensing chamber, in addition to the electromagnetic force F (i) due to the mold coil 314. A force due to the pressure 302 (crank chamber pressure Pc), a force due to the pressure in the second pressure sensing chamber 307 (suction pressure Ps), and a biasing force F due to a spring built in the bellows 305 act.
Here, the effective pressure receiving area Sb in the expansion / contraction direction of the bellows 305, the pressure receiving area Sv of the crank chamber acting on the valve body 304 from the valve hole 301c side, and the cross-sectional area Sr of the cylindrical outer peripheral surface of the valve body 304 are Sb = Sv = Sr. Therefore, the relationship between the forces acting on the valve body 304 is expressed by Equation 1. In Equation 1, “+” indicates the valve closing direction of the valve body 304, and “−” indicates the valve opening direction.

  The connecting body of the bellows 305, the connecting portion 306, and the valve body 304 reduces the pressure of the crank chamber 140 by reducing the opening of the pressure supply passage 145 in order to increase the discharge capacity when the pressure of the suction chamber 141 becomes higher than the set pressure. When the pressure in the suction chamber 141 falls below the set pressure, the opening of the pressure supply passage 145 is increased to increase the pressure in the crank chamber 140 in order to reduce the discharge capacity. That is, the control valve 300 autonomously controls the opening degree (opening area) of the pressure supply passage 145 so that the pressure in the suction chamber 141 approaches the set pressure.

  FIG. 4 is a diagram showing the correlation between the coil energization amount of the control valve 300 and the set pressure. Since the electromagnetic force of the mold coil 314 acts on the valve body 304 via the solenoid rod 309 in the valve closing direction, the force in the direction to reduce the opening of the pressure supply passage 145 when the energization amount to the mold coil 314 increases. Increases, and the set pressure changes in the decreasing direction as shown in FIG. The control device (drive unit) controls the energization to the mold coil 314 by pulse width modulation (PWM control) at a predetermined frequency in the range of 400 Hz to 500 Hz, for example, and the current value flowing through the mold coil 314 becomes a desired value. The pulse width (duty ratio) is changed as follows.

  When the air conditioning system is in operation, that is, in the operating state of the variable capacity compressor 100, the energization amount to the mold coil 314 is adjusted by the controller based on the air conditioning setting such as the set temperature and the external environment, and the pressure in the suction chamber 141 is energized. The discharge capacity is controlled so that the set pressure corresponds to the amount. Further, when the air conditioner system is not operated, that is, when the variable capacity compressor 100 is not operated, the control device turns off the energization to the mold coil 314. Thereby, the pressure supply passage 145 is opened by the release spring 311, and the discharge capacity of the variable capacity compressor 100 is controlled to the minimum state.

  Next, the structure and operation of the switching valve 350 will be described in detail with reference to FIGS. 1, 3, and 5-7. FIGS. 3A and 3B are longitudinal sectional views showing an example of the switching valve 350 disposed in the cylinder head 104, and FIG. 3A is a state of pressure supply to the crank chamber 140 (first state). 1 (b), and FIG. 3 (b) shows a pressure release state from the crank chamber 140 (second state). 5 to 7 are cross-sectional views of components of the switching valve 350, respectively.

`` Switching valve ''
As shown in FIGS. 1 and 3, the switching valve 350 is provided in the storage chamber 104 c formed on the crank chamber 140 side of the control valve 300 in the pressure supply passage 145, and has a first state and a second state. It is a valve that switches to. In the first state, the switching valve 350 is connected to the first valve hole 104c1 communicating with the pressure supply passage 145 between the control valve 300 and the switching valve 350, and the pressure supply passage 145 between the switching valve 350 and the crank chamber 140. The communicating second valve hole 151a is communicated, and in the second state, the second valve hole 151a and the pressure release hole 351a1 communicating with the suction chamber 141 are communicated.

  The switching valve 350 includes a partition member 351 (see FIGS. 3 and 5) fixed in the storage chamber 104c, and a spool 352 (see FIGS. 3 and 5) that is stored in the storage chamber 104c and moves in the axial direction of the storage chamber 104c. 7).

  The partition member 351 is a member that partitions the first valve chamber S1 having the first valve hole 104c1 and the second valve chamber S2 having the second valve hole 151a and the pressure release hole 351a1 communicating with the suction chamber 141. The storage chamber 104 c is formed on the open end face side of the cylinder head 104 and opens to the suction chamber 141.

  The first valve hole 104c1 opens on one end side in the moving direction of the spool 352 in the accommodation chamber 104c (first valve chamber S1). The first valve hole 104c1 communicates with the downstream side of the valve hole 301c of the control valve 300 via the communication path 104f. That is, the first valve hole 104c1 communicates with the discharge chamber 142 via the communication path 104f, the accommodation hole 104b, the control valve 300, and the communication path 104e.

  The second valve hole 151a opens to the other end side in the moving direction of the spool 352 in the accommodation chamber 104c (second valve chamber S2). The second valve hole 151 a communicates with the crank chamber 140 through a communication hole of the valve plate 103, a communication hole of the suction valve forming plate 150, a communication hole of the cylinder gasket 152, and a communication path 101 e formed in the cylinder block 101.

  The pressure release hole 351a1 is directly open to the suction chamber 141 in order to communicate the second valve chamber S2 and the suction chamber 141. In the present embodiment, the storage chamber 104c opens into the suction chamber 141, and the second valve chamber S2 and the suction chamber 141 communicate with each other through the pressure release hole 351a1, but the present invention is not limited to this. For example, the storage chamber 104c is not directly opened into the suction chamber 141, but a communication hole is formed in the wall (the wall at the open end of the cylinder head 104) between the suction chamber 141 and the storage chamber 104c. The second valve chamber S2 and the suction chamber 141 may be communicated with each other through the hole 351a1.

  The spool 352 includes a first valve portion 352a that is in contact with and away from the first valve seat 104c2 provided around the first valve hole 104c1, and a second valve that is in contact with and away from the second valve seat 151b provided around the second valve hole 151a. The unit 352b is integrally provided. When the pressure in the communication path 104f (the pressure supply path 145 between the control valve 300 and the switching valve 350) is higher than the pressure in the communication path 101e (the crank chamber 140), the spool 352 causes the pressure difference in FIG. As shown in FIG. 3A, the first valve portion 352a moves away from the first valve seat 104c2, and the second valve portion 352b contacts the second valve seat 151b. As a result, the spool 352 connects the first valve hole 104c1 and the second valve hole 151a through an internal passage 352e described later, and blocks communication between the second valve hole 151a and the pressure release hole 351a1.

  Further, when the pressure of the communication path 104f is lower than the pressure of the communication path 101e, the spool 352 moves to the right in FIG. 3 due to this pressure difference, and as shown in FIG. The part 352a contacts the first valve seat 104c2, and the second valve part 352b is separated from the second valve seat 151b. The first valve seat 104c2 and the second valve seat 151b are formed so as to be orthogonal to the moving direction (axial direction) of the spool 352, respectively. Thus, the spool 352 blocks communication between the first valve hole 104c1 and the second valve hole 151a and connects the second valve hole 151a and the pressure release hole 351a1.

Hereinafter, the configuration of the switching valve 350 will be described in more detail.
"Containment chamber and blocking member"
The storage chamber 104 c is formed in a stepped columnar shape along an axis parallel to the axis O of the drive shaft 110. Specifically, the storage chamber 104c has a large-diameter portion 104c3 on the open end surface side (side closer to the crank chamber 140) of the cylinder head 104 and a back side (side far from the crank chamber 140) that is continuous with the large-diameter portion 104c3. The small-diameter portion 104c4 extends in the direction and has a smaller diameter than the large-diameter portion 104c3. A part of the cylinder head 104 forming wall that forms the large-diameter portion 104c3 is notched on the open end face side, and the opening end side of the storage chamber 104c is directly open to the suction chamber 141.

  A second valve hole 151a is opened in the discharge valve forming plate 151, and a second valve seat 151b with which the second valve part 352b abuts is formed at the periphery of the opening of the second valve hole 151a. The large diameter portion 104c3 (second valve chamber S2) includes a second valve hole 151a, a communication hole of the valve plate 103, a communication hole of the suction valve forming plate 150, a communication hole of the cylinder gasket 152, and a communication formed in the cylinder block 101. The crank chamber 140 communicates with the passage 101e.

  A first valve seat 104c2 with which the first valve portion 352a abuts is formed on the end surface 104c21 in the axial direction constituting the small diameter portion 104c4. The first valve seat 104c2 is formed to be orthogonal to the axial direction of the storage chamber 104c. A first valve hole 104c1 is opened inside the first valve seat 104c2. The first valve hole 104c1 communicates with a region in the accommodation hole 104b downstream of the valve hole 301c of the control valve 300 via a communication path 104f extending coaxially with the accommodation chamber 104c. A region in the accommodation hole 104b downstream of the valve hole 301c of the control valve 300 communicates with the discharge chamber 142 via the control valve 300 and the communication path 104e, and the first valve hole 104c1 includes a pressure supply path including the communication path 104f. It communicates with the discharge chamber 142 via 145. The small diameter portion 104c4 (first valve chamber S1) constitutes a part of the pressure supply passage 145 and constitutes a so-called back pressure chamber of the switching valve 350.

`` Division member ''
The partition member 351 is made of, for example, a metal material, is press-fitted into the large-diameter portion 104c3 of the storage chamber 104c, has an open end on the second valve hole 151a side, and is formed in a substantially bottomed cylindrical shape. Specifically, the partition member 351 includes a cylindrical tubular body 351a and a disk-shaped end wall 351b provided at one end of the tubular body 351a on the first valve hole 104c1 side. The partition member 351 includes a first valve chamber S1 formed mainly by the small diameter portion 104c4 in the accommodation chamber 104c by press-fitting and fixing the cylindrical body 351a to the inner peripheral surface of the large diameter portion 104c3 of the accommodation chamber 104c. And a second valve chamber S2 on the discharge valve forming plate 151 side formed inside the cylindrical body 351a.

  A pressure release hole 351a1 is formed in the cylindrical body 351a of the partition member 351. The pressure release holes 351a1 are formed, for example, at a plurality of locations separated in the circumferential direction of the cylindrical body 351a, and extend in the radial direction of the cylindrical body 351a. The second valve chamber S2 communicates with the suction chamber 141 through the pressure release hole 351a1. The partition member 351 is positioned in the large-diameter portion 104c3 of the storage chamber 104c so that the other end 351a2 of the cylindrical body 351a contacts the discharge valve forming plate 151.

  An insertion hole 351b1 is formed at the center of the end wall 351b of the partition member 351. The spool 352 is inserted through the insertion hole 351b1. An annular projecting portion 351b2 that surrounds the insertion hole 351b1 and projects toward the first valve chamber S1 is formed on the surface of the end wall 351b of the partition member 351 opposite to the cylinder 351a.

"spool"
The spool 352 is disposed in the first valve chamber S1 and is in contact with the first valve seat 104c2, and the second valve portion 352b is disposed in the second valve chamber S2 and is in contact with and away from the second valve seat 151b. A shaft portion 352c that connects the first valve portion 352a and the second valve portion 352b, penetrates the partition member 351, and has a shaft outer diameter smaller than the outer diameter of the first valve portion 352a and the second valve portion 352b, Consists of.

  The first valve portion 352a opens and closes the first valve hole 104c1 by coming into contact with the first valve seat 104c2. Further, as shown in FIGS. 3 and 7, the outer edge portion of the second valve portion 352b on the second valve seat 151b side protrudes toward the second valve seat 151b and is larger than the inner diameter of the second valve hole 151a. An annular protrusion 352b1 having an inner diameter is formed. As the protruding portion 352b1 moves away from the second valve seat 151b, a gap (communication portion) G (see FIG. 3B) is formed between the second valve portion 352b and the second valve seat 151b. Then, the second valve hole 151a and the pressure release hole 351a1 communicate with each other through the gap G (that is, the switching valve 350 is switched to the second state shown in FIG. 3B). On the other hand, when the second valve portion 352b contacts the second valve seat 151b, the gap G between the second valve portion 352b and the second valve seat 151b is closed, and the second valve hole 151a and the pressure release hole 351a1. (That is, the switching valve 350 is switched to the first state shown in FIG. 3A). The shaft portion 352c is arranged so that one end portion thereof protrudes toward the first valve portion 352a side than the protruding portion 351b2 of the partition member 351.

  The first valve portion 352a includes a sliding portion 352a1, a front end portion 352a2, and a rear end portion 352a3.

  More specifically, the sliding portion 352a1 has an outer peripheral surface that is in sliding contact with the inner peripheral surface of the first valve chamber S1, and the first valve chamber S1 is on the first region S11 on the first valve hole 104c1 side and the partition member 351 side. And the second region S12. The sliding part 352a1 is formed in a substantially columnar shape and has an outer diameter larger than the outer diameter of the rear end part 352a3. The outer peripheral surface of the sliding part 352a1 is slidably supported on the inner peripheral surface of the first valve chamber S1. The outer edge corner of the sliding portion 352a1 on the first valve seat 104c2 side is chamfered and inclined over the entire circumference.

  In the present embodiment, a communication path 352d for communicating the first region S11 and the second region S12 is formed in the sliding part 352a1. The communication path 352d is made of, for example, a groove (slit) formed on the outer peripheral surface of the sliding portion 352a1. Although the number of the communication paths 352d may be one, in the present embodiment, the communication paths 352d are formed by grooves extending in the axial direction of the sliding portion 352a1 at a plurality of angular positions separated in the circumferential direction of the sliding portion 352a1. In addition, in the cross-sectional angle position shown in FIG. 3, although there is one communication path 352d, a plurality of communication paths are actually formed.

  The front end portion 352a2 is formed at an end portion of the sliding portion 352a1 on the first region S11 side and is in contact with and away from the first valve seat 104c2. The front end portion 352a2 protrudes in an annular shape from, for example, an end portion on the first region S11 side of the sliding portion 352a1.

  The rear end portion 352a3 extends from the second region S12 side of the sliding portion 352a1 toward the partition member 351 side and has a flush outer peripheral surface and is formed in a cylindrical shape. The outer diameter of the rear end portion 352a3 is smaller than the outer diameter of the sliding portion 352a1, and is formed to be approximately the same as the outer diameter of the annular projecting portion 351b2 of the partition member 351. As shown in FIG. 6, the inside of the cylindrical rear end portion 352a3 includes a large-diameter hole portion 352a31 on the shaft portion 352c side and a small-diameter hole portion 352a32 continuous to the large-diameter hole portion 352a31.

  The spool 352 is formed with an internal passage 352e for communicating the second region S12 and the second valve chamber S2 (second valve hole 151a). The internal passage 352e includes a first internal passage 352e1 and a second internal passage 352e2.

  The first internal passage 352e1 is a passage that penetrates the peripheral wall of the rear end portion 352a3 and communicates the second region S12 and the region in the rear end portion 352a3. The first internal passage 352e1 is formed, for example, at a plurality of angular positions that are separated in the circumferential direction of the rear end portion 352a3, and extends in the radial direction of the rear end portion 352a3. Thus, the first internal passage 352e1 opens to the second region S12 of the first valve chamber S1. That is, one end of the first internal passage 352e1 opens toward the partition member 351 side (on the opposite side to the control valve 300 side, downstream side) with respect to the sliding portion 352a1.

  The second internal passage 352e2 is a passage extending from a region in the rear end portion 352a3 to the second valve portion 352b and having an open end on the end surface of the second valve portion 352b on the second valve seat 151b side. The second internal passage 352e2, for example, the rear end portion 352a3, the shaft portion 352c, and the second valve portion 352b extends in the same diameter from the sliding portion 352a1 side to the second valve portion 352b side, and one end slides. It is closed by the portion 352a1, and the other end is opened on the end surface of the second valve portion 352b on the second valve seat 151b side. An annular protrusion 352b1 of the second valve portion 352b is disposed so as to surround the periphery of the other end opening of the second internal passage 352e2.

  The sliding portion 352a1 is a receiving surface 352f with which the refrigerant flowing into the second region S12 collides via the first internal passage 352e1, and is a receiving surface that receives dynamic pressure in a direction away from the second valve seat 151b. 352f. The sliding portion 352a1 receives the dynamic pressure via the receiving surface 352f when the control valve 300 closes the pressure supply passage 145 and the pressure of the pressure supply passage 145 between the control valve 300 and the switching valve 350 decreases. .

  In the present embodiment, the receiving surface 352f includes an end portion 352f1 exposed to the second region S12 in the sliding portion 352a1. In other words, the receiving surface 352f is configured by an annular end surface connected to the outer peripheral surface of the rear end portion 352a3 on the second valve seat 151b side of the sliding portion 352a1. In the present embodiment, the receiving surface 352f extends so as to be orthogonal to the sliding direction (axial direction) of the sliding portion 352a1.

  Here, the spool 352 can be formed of an appropriate material such as metal or resin, but it is desirable to form the spool 352 from a resin material in order to reduce the weight. In particular, the valve body including the second valve portion 352b and the shaft portion 352c is disposed in the second valve chamber S2 and is cooled by the suction refrigerant. Accordingly, a relatively inexpensive general-purpose engineering plastic (for example, polyamide-based resin (PA66 or the like)) can be employed as the material of the valve body including the second valve portion 352b and the shaft portion 352c. The first valve portion 352a is also preferably made of resin. As a material of the first valve portion 352a, for example, a polyamide-based resin (PA66 or the like) or a super engineering plastic (for example, PPS or the like) considering heat resistance strength can be adopted.

  In the present embodiment, the shaft portion 352c is formed as an integral part with the second valve portion 352b, while the first valve portion 352a is formed as a separate component. With the shaft portion 352c inserted into the insertion hole 351b1 of the partition member 351, the shaft portion 352c is fitted into the large-diameter hole portion 352a31 of the rear end portion 352a3 of the first valve portion 352a. The 1st valve part 352a is fixed to the valve body which consists of 2 valve parts 352b. When the spool 352 is formed of a resin material, the joining of the rear end portion 352a3 of the first valve portion 352a and the shaft portion 352c can be easily performed by ultrasonic welding, laser welding, or the like. In this case, as shown in FIG. 8, the joint portion J between the rear end portion 352a3 and the shaft portion 352c is separated from the contact portion C between the projecting portion 351b2 of the partition member 351 and the end surface of the rear end portion 352a3 in the axial direction. It is good to set to the position. Thereby, the thermal influence on the contact part C at the time of welding with the rear-end part 352a3 and the axial part 352c can be reduced or eliminated effectively.

  When the projecting portion 352b1 of the second valve portion 352b abuts on the second valve seat 151b, the end surface of the rear end portion 352a3 of the first valve portion 352a on the shaft portion 352c side is axially directed to the projecting portion 351b2 of the partition member 351. The axial press-fitting position of the second valve portion 352b with respect to the first valve portion 352a is adjusted so that the length of the partition member 351 in the axial direction is set.

"Pressure release passage and pressure supply passage"
As shown in FIG. 3B, when the second valve portion 352b is separated from the second valve seat 151b, the communication passage 101e, the communication hole of the cylinder gasket 152, the communication hole of the intake valve forming plate 150, and the valve plate 103 The communication hole, the second valve hole 151a, the gap G between the second valve portion 352b and the second valve seat 151b, the second valve chamber S2, and the pressure release hole 351a1 are the first communication between the crank chamber 140 and the suction chamber 141. A pressure relief passage 146a is configured. The refrigerant in the crank chamber 140 flows through the first pressure release passage 146a as shown by the thick arrow in FIG. 3B and is discharged to the suction chamber 141.

That is, by separating the second valve portion 352b from the second valve seat 151b, a gap G is formed between the second valve portion 352b and the second valve seat 151b, and the second valve hole 151a and the pressure release hole 351a1. And the opening of the first pressure release passage 146a becomes the maximum opening, and the refrigerant in the crank chamber 140 is discharged to the suction chamber 141.
In addition, after the second valve portion 352b is separated from the second valve seat 151b, the first valve portion 352a abuts on the first valve seat 104c2, the first valve hole 104c1 is closed, and the first valve hole 104c1 is included. The constructed pressure supply passage 145 will be closed.

  On the other hand, as shown in FIG. 3A, when the second valve portion 352b comes into contact with the second valve seat 151b, the gap G between the second valve portion 352b and the second valve seat 151b, that is, the second valve hole. By closing the communication portion between 151a and the pressure release hole 351a1, the first pressure release passage 146a including the gap G is closed. Therefore, when the second valve portion 352b contacts the second valve seat 151b, the fixed throttle 103c of the second pressure release passage 146b becomes the minimum opening in the pressure release passage 146, and the refrigerant in the crank chamber 140 enters the suction chamber 141. Emission is restricted.

  Here, when the second valve portion 352b comes into contact with the second valve seat 151b, the first valve portion 352a is separated from the first valve seat 104c2 and the first valve hole 104c1 is opened. Accordingly, the communication path 104e, the control valve 300, the accommodation hole 104b, the communication path 104f, the first valve hole 104c1, the first region S11 of the first valve chamber S1, the communication path 352d formed in the sliding portion 352a1, the first The second region S12 of the valve chamber S1, the first internal passage 352e1, the second internal passage 352e2, the second valve hole 151a, the communication hole of the valve plate 103, the communication hole of the suction valve forming plate 150, the communication hole of the cylinder gasket 152, The communication passage 101e constitutes a pressure supply passage 145 that allows the crank chamber 140 and the discharge chamber 142 to communicate with each other. The refrigerant in the discharge chamber 142 flows through the pressure supply passage 145 and is supplied to the crank chamber 140 as shown by a thick arrow in FIG.

  Thus, the second valve hole 151a, the communication hole of the valve plate 103, the communication hole of the suction valve forming plate 150, the communication hole of the cylinder gasket 152, and the communication path 101e are connected to the first pressure release path 146a and the pressure supply path 145. Also, when the pressure is released from the crank chamber 140 and when the pressure is supplied to the crank chamber 140, the flow direction of the refrigerant in the communication passage 101e is reversed. In other words, the communication passage 101e that allows the second valve hole 151a and the crank chamber 140 to communicate with each other constitutes a part of the pressure supply passage 145 (the first state shown in FIG. 3A), and the first The state is switched to a state (second state shown in FIG. 3B) constituting a part of the pressure release passage 146a.

  When the second valve portion 352b comes into contact with the second valve seat 151b and the first valve portion 352a is separated from the first valve seat 104c2, the communication passage 101e functions as the pressure supply passage 145. On the other hand, when the second valve portion 352b is separated from the second valve seat 151b and the first valve portion 352a contacts the first valve seat 104c2, the communication passage 101e functions as the first pressure release passage 146a.

"Aperture passage"
A region of the pressure supply passage 145 between the control valve 300 and the switching valve 350 communicates with the suction chamber 141 via the throttle passage 104h (see FIG. 1). The throttle passage 104h is provided to release the refrigerant in the pressure supply passage 145 between the control valve 300 and the switching valve 350 to the suction chamber 141 side when the control valve 300 is closed and the pressure supply passage 145 is closed. ing. Since the throttle passage 104h has a throttle, the amount of refrigerant flowing out from the pressure supply passage 145 to the suction chamber 141 through the throttle passage 104h is small. The passage sectional area of the internal passage 352e of the spool 352, the passage sectional area of the communication passage 352d formed in the sliding portion 352a1 of the spool 352, and the passage sectional area of the communication passage 104f are respectively the passage sectional area of the throttle passage 104h. It is set to be larger.

Here, when the control valve 300 is closed and the pressure supply passage 145 is closed in a state where the second valve portion 352b is in contact with the second valve seat 151b (first state shown in FIG. 3A). Thereafter, the refrigerant in the pressure supply passage 145 between the control valve 300 and the switching valve 350 flows into the suction chamber 141 through the throttle passage 104h, and the pressure supply passage 145 between the control valve 300 and the switching valve 350. The pressure of gradually decreases. Therefore, the refrigerant flows back through the internal passage 352e from the crank chamber 140 toward the suction chamber 141.
On the other hand, when the control valve 300 is opened and the pressure supply passage 145 is opened in a state where the first valve portion 352a is in contact with the first valve seat 104c2 (second state shown in FIG. 3B), Thereafter, the refrigerant from the discharge chamber 142 is supplied to the pressure supply passage 145 between the control valve 300 and the switching valve 350, and the pressure in the pressure supply passage 145 between the control valve 300 and the switching valve 350 increases. For this reason, the back pressure Pm acting on the end surface of the spool 352 on the first valve hole 104 c 1 side is higher than the pressure in the suction chamber 141.

"Spool behavior"
The end surface of the spool 352 on the first valve hole 104c1 side receives the pressure of the pressure supply passage 145 between the control valve 300 and the switching valve 350, so-called back pressure Pm. On the other hand, the end surface of the spool 352 on the second valve hole 151 a side receives the pressure Pc of the crank chamber 140. The spool 352 moves in the axial direction in response to a pressure difference ΔP (ΔP = Pm−Pc) between the back pressure Pm and the pressure Pc. The pressure receiving area s1 of the axial spool 352 that receives the back pressure Pm and the pressure receiving area s2 of the spool 352 that receives the pressure Pc of the crank chamber 140 are set to, for example, s1 = s2, but the operation of the spool 352 is performed. To adjust, s1> s2 or s1 <s2 can be set.

First, the switching operation from the second state to the first state will be described.
When the control valve 300 is opened while the first valve portion 352a is in contact with the first valve seat 104c2 (FIG. 3B, the second state), the back pressure Pm of the spool 352 increases. Thereafter, when the back pressure Pm becomes higher than the pressure Pc of the crank chamber 140 (in a state where Pm−Pc> 0), the first valve portion 352a starts to separate from the first valve seat 104c2. And when the 2nd valve part 352b contact | abuts to the 2nd valve seat 151b, the 1st valve part 352a will be in the state spaced apart to the maximum from the 1st valve seat 104c2 (2nd state-> 1st state). Thereby, the switching valve 350 is switched from the second state to the first state. As a result, the communication between the second valve hole 151a and the pressure release hole 351a1 is blocked, the communication path (first pressure release path 146a) between the crank chamber 140 and the suction chamber 141 is closed, and at the same time, the first valve hole 104c1 and the second valve hole 151a communicate with each other, and the communication path (pressure supply path 145) between the discharge chamber 142 and the crank chamber 140 is opened.

  That is, when the control valve 300 is opened, the first valve hole 104c1 is opened, and the communication path 104e, the control valve 300, the accommodation hole 104b, the communication path 104f, the first valve hole 104c1, the first region S11, and the sliding portion 352a1. The communication passage 352d formed in the gap, the gap between the sliding portion 352a1 and the inner peripheral surface of the first valve chamber S1, the second region S12, the first internal passage 352e1, the second internal passage 352e2, and the second valve hole 151a. The refrigerant in the discharge chamber 142 is supplied to the crank chamber 140 via the pressure supply passage 145 including the communication hole of the valve plate 103, the communication hole of the suction valve forming plate 150, the communication hole of the cylinder gasket 152, and the communication passage 101e. Become so.

  As a result, only the second pressure release passage 146b of the pressure release passage 146 is opened, and the minimum opening area of the pressure release passage 146 becomes the opening area of the fixed throttle 103c. For this reason, the pressure in the crank chamber 140 easily rises, the pressure in the crank chamber 140 rises according to the opening degree of the control valve 300, the inclination angle of the swash plate 111 decreases from the maximum, and the piston stroke is variable. Can be controlled.

Next, the switching operation from the first state to the second state will be described.
When the control valve 300 is closed while the second valve portion 352b is in contact with the second valve seat 151b (FIG. 3A, the first state), the back pressure Pm of the spool 352 gradually decreases. . Thereafter, when the back pressure Pm becomes lower than the pressure Pc in the crank chamber 140 (in a state where Pm−Pc <0), the refrigerant flows backward from the crank chamber 140 toward the suction chamber 141 through the internal passage 352e. However, the spool 352 is pressed by the backward flowing refrigerant and moves toward the first valve seat 104c2, and the second valve portion 352b starts to be separated from the second valve seat 151b. And when the 1st valve part 352a contact | abuts to the 1st valve seat 104c2, the 2nd valve part 352b will be in the state spaced apart to the maximum from the 2nd valve seat 151b (1st state-> 2nd state). As a result, the switching valve 350 is switched from the first state to the second state. As a result, the second valve hole 151a communicates with the pressure release hole 351a1, and the opening degree of the communication path (first pressure release path 146a) between the crank chamber 140 and the suction chamber 141 becomes the maximum opening degree. The communication between the valve hole 104c1 and the second valve hole 151a is blocked, and the communication path (pressure supply path 145) between the discharge chamber 142 and the crank chamber 140 is closed.

  That is, when the control valve 300 is closed, the second valve hole 151a and the pressure release hole 351a1 are communicated, the communication path 101e, the communication hole of the cylinder gasket 152, the communication hole of the suction valve forming plate 150, and the communication of the valve plate 103. The refrigerant in the crank chamber 140 enters the suction chamber 141 through the first pressure release passage 146a and the second pressure release passage 146b, each of which includes the hole, the second valve hole 151a, the second valve chamber S2, and the pressure release hole 351a1. It will be discharged.

  As a result, the supply of refrigerant from the discharge chamber 142 to the crank chamber 140 is stopped, while the refrigerant in the crank chamber 140 passes through the second pressure release passage 146b (fixed throttle 103c) and the first pressure release passage 146a. Immediately discharged into the suction chamber 141. For this reason, the pressure in the crank chamber 140 is equivalent to the pressure in the suction chamber 141, the inclination angle of the swash plate is maximized, and the piston stroke (discharge capacity) is maximized.

  By the way, in a state where the first valve portion 352a is separated from the first valve seat 104c2, the pressure supply passage 145 between the control valve 300 and the switching valve 350 has a passage sectional area larger than that of the throttle passage 104h via the communication passage 352d. The large internal passage 352e is also communicated. Therefore, when the second valve portion 352b is in contact with the second valve seat 151b (first state), the control valve 300 closes the pressure supply passage 145 and switches to the second state (that is, In a state where neither the first valve portion 352a nor the second valve portion 352b is in contact with the corresponding valve seat), a part of the refrigerant flowing into the second valve chamber S2 from the crank chamber 140 side is It flows backward toward the pressure supply passage 145 between the control valve 300 and the switching valve 350 via the internal passage 352e. Then, the reversely flowing refrigerant flows into the second region S12 of the first valve chamber S1 through the first internal passage 352e1 of the internal passage 352e as shown by the broken line arrow in FIG. A part of the refrigerant flowing into the second region S12 collides with the receiving surface 352f formed on the sliding portion 352a1. As a result, the spool 352 receives dynamic pressure in a direction away from the second valve seat 151b via the receiving surface 352f. On the other hand, a part of the refrigerant flowing into the second region S12 flows toward the partition member 351, but the outer diameter of the rear end portion 352a3 is smaller than the outer diameter of the sliding portion 352a1, so that the movement of the spool 352 is caused by this refrigerant flow. There is no inhibition. As a result, the spool 352 smoothly moves in the direction away from the second valve seat 151b (in other words, the direction approaching the first valve seat 104c2) by the dynamic pressure acting on the receiving surface 352f, and from the first state to the first state. Switch to state 2 immediately.

  In the variable capacity compressor 100 according to the present embodiment, the first internal passage 352e1 opens toward the partition member 351 side of the second region S12, that is, the sliding portion 352a1. Then, when the control valve 300 closes the pressure supply passage 145 and the pressure in the pressure supply passage 145 between the control valve 300 and the switching valve 350 decreases, the refrigerant enters the second region S12 via the first internal passage 352e1. Even if inflow (reverse flow) occurs, at least a part of the refrigerant flow collides with the receiving surface 352f, and the spool 352 receives dynamic pressure toward the direction away from the second valve seat 151b via the receiving surface 352f. Furthermore, since the outer diameter of the rear end 352a3 through which the first internal passage 352e1 passes is smaller than the outer diameter of the sliding portion 352a1, a part of the refrigerant flowing into the second region S12 via the first internal passage 352e1 is received. Even if it flows to the side opposite to the surface 352f, the movement of the spool 352 in the direction away from the second valve seat 151b is not hindered. For this reason, the switching valve 350 smoothly moves the spool 352 in the direction in which the second valve hole 151a and the pressure release hole 351a1 communicate with each other by the dynamic pressure, so that the switching from the first state to the second state can be quickly performed. Switch to Therefore, a delay in releasing the pressure in the crank chamber 140 is prevented.

"Operation of variable capacity compressor"
When the energization to the mold coil 314 of the control valve 300 is cut off while the variable capacity compressor 100 is in operation, the opening area of the control valve 300 is maximized, the pressure supply passage 145 is opened, and the spool of the switching valve 350 is opened. The back pressure Pm of 352 is increased. Therefore, when the first valve portion 352a is in contact with the first valve seat 104c2 (in the maximum discharge capacity state, in other words, in the second state), the spool 352 is brought into contact with the second valve seat 151b. Move in the direction of approach. The first valve portion 352a is separated from the first valve seat 104c2, and the second valve portion 352b abuts on the second valve seat 151b, thereby closing the first pressure release passage 146a.

  That is, when the control valve 300 is opened, the pressure release passage 146 is only the second pressure release passage 146b (the opening area of the pressure release passage is minimized), while the pressure that communicates the discharge chamber 142 and the crank chamber 140. The supply passage 145 is opened. As a result, the pressure in the crank chamber 140 increases, the inclination angle of the swash plate 111 decreases, and the discharge capacity is changed to the minimum and maintained (minimum discharge capacity state). Then, the dynamic pressure of the refrigerant flow flowing through the pressure supply passage 145 acts on the end surface of the first valve portion 352a on the first valve seat 104c2 side, so that the second valve portion 352b contacts the second valve seat 151b. In this state (minimum discharge capacity state, in other words, the first state), the dynamic pressure that presses the first pressure release passage 146a in the opening direction does not act on the second valve portion 352b, and the first release pressure The closed state (minimum discharge capacity state, the first state) of the pressure passage 146a is maintained.

  In the minimum discharge capacity state, the discharge check valve 200 blocks the connection portion (discharge path) between the communication path 144 and the muffler space 143, and the refrigerant gas discharged with the minimum discharge capacity flows to the external refrigerant circuit. Instead, it circulates through an internal circulation path constituted by the discharge chamber 142, the pressure supply passage 145, the crank chamber 140, the second pressure release passage 146b, the suction chamber 141, and the cylinder bore 101a. At this time, the refrigerant in the pressure supply passage 145 between the control valve 300 and the switching valve 350 slightly flows out to the suction chamber 141 through the throttle passage 104h.

  When energizing the mold coil 314 of the control valve 300 from this state (minimum discharge capacity state), the control valve 300 is closed and the pressure supply passage 145 is closed. Therefore, the refrigerant in the pressure supply passage 145 between the control valve 300 and the switching valve 350 flows out into the suction chamber 141 via the throttle passage 104h, and flows through the pressure supply passage 145 between the control valve 300 and the switching valve 350. The pressure (back pressure Pm) decreases. In response to the decrease in the back pressure Pm, the spool 352 receives the dynamic pressure via the receiving surface 352f and moves away from the second valve seat 151b, whereby the first valve portion 352a is moved to the first valve seat. 104c2 smoothly contacts. As a result, the pressure supply passage 145 is closed, and the refrigerant is prevented from flowing backward from the crank chamber 140 to the pressure supply passage 145 upstream of the switching valve 350 via the communication passage 101e. At the same time, the second valve portion 352b is separated from the second valve seat 151b, whereby the first pressure release passage 146a is opened.

When the mold coil 314 is energized and the control valve 300 is closed, the opening of the first pressure release passage 146a becomes the maximum opening, and the refrigerant in the crank chamber 140 flows through the two pressure release passages 146a and 146b. It is discharged into the suction chamber 141. The flow passage cross-sectional area of the first pressure relief passage 146a in the switching valve 350 is set to be larger than the flow passage cross-sectional area of the fixed throttle 103c (second pressure relief passage 146b). When the opening degree of the passage 146a is controlled to the maximum opening degree, the refrigerant in the crank chamber 140 quickly flows out to the suction chamber 141. As a result, the pressure in the crank chamber 140 decreases, and the discharge capacity increases rapidly from the minimum state to the maximum discharge capacity.
As a result, the pressure in the discharge chamber 142 is rapidly increased and the discharge check valve 200 is opened, and the refrigerant gas is discharged from the variable capacity compressor 100 so that the refrigerant circulates through the external refrigerant circuit. Becomes operational.

  When the air conditioner system is activated and the pressure in the suction chamber 141 decreases and reaches a set pressure set by the current flowing through the mold coil 314, the control valve 300 is opened. When the control valve 300 is opened, the back pressure Pm of the spool 352 of the switching valve 350 is increased, so that the switching valve 350 opens the pressure supply passage 145 and simultaneously closes the first pressure release passage 146a. At this time, by opening only the second pressure release passage 146b of the pressure release passage 146, the refrigerant in the crank chamber 140 is restricted from flowing out to the suction chamber 141, and the pressure in the crank chamber 140 is easily increased. Thus, the opening of the control valve 300 is adjusted and the discharge capacity is variably controlled so that the pressure in the suction chamber 141 maintains the set pressure. That is, the switching valve 350 operates in conjunction with the opening and closing of the control valve 300. When the control valve 300 is closed, the opening of the pressure release passage 146 is set to the maximum opening, and the control valve 300 is opened. If so, the opening of the pressure relief passage 146 is set to the minimum opening.

  In the present embodiment, the sliding portion 352a1 has an outer diameter larger than the outer diameter of the rear end portion 352a3, and the receiving surface 352f includes an end portion 352f1 exposed in the second region S12 in the sliding portion 352a1. It was. Thereby, the receiving surface 352f which makes the dynamic pressure which goes to the direction which leaves | separates from the 2nd valve seat 151b to the spool 352 can be formed easily.

  In the present embodiment, the receiving surface 352f extends so as to be orthogonal to the sliding direction (axial direction) of the sliding portion 352a1. Thereby, a force for moving the spool 352 in the sliding direction can be applied to the spool 352.

  In the present embodiment, the communication path 352d that connects the first region S11 and the second region S12 is formed in the sliding portion 352a1. Thereby, the communication path 352d can be easily formed. The communication path 352d is formed of a groove extending in the axial direction of the sliding portion 352a1 on the outer peripheral surface of the sliding portion 352a1. Thereby, the communication path 352d can be formed more easily.

  In the present embodiment, the outer edge corner portion on the first valve seat 104c2 side of the sliding portion 352a1 is chamfered and inclined over the entire circumference. Thereby, a refrigerant | coolant can be distribute | circulated smoothly from 1st area | region S11 to 2nd area | region S12.

"Modification"
In the present embodiment, the first valve seat 104c2 is formed so as to be orthogonal to the axial direction of the storage chamber 104c. However, as in the modification shown in FIG. 9, the peripheral edge of the first valve hole 104c1 May be formed in a conical surface shape away from the first valve hole 104c1 toward the inner peripheral surface side of the first valve chamber S1. In this case, the contact surface of the front end portion 352a2 of the first valve portion 352a is inclined according to the first valve seat 104c2. For example, in the first state shown in FIG. 9, when the control valve 300 is closed and a reverse flow of the refrigerant toward the control valve 300 occurs, a part of the refrigerant is connected to the communication path 352d, It flows into 1st area | region S11 through the clearance gap between the sliding part 352a1 and the internal peripheral surface of 1st valve chamber S1. However, in the present modification, the first valve seat 104c2 is formed in a conical surface, so that the refrigerant that has flowed back into the first region S11 smoothly moves toward the first valve hole 104c1 along the first valve seat 104c2. Flowing. Therefore, the refrigerant that has flowed back to the first region S11 collides with the first valve seat 104c2, changes the flow direction toward the end face of the spool 352, and presses the spool 352 in a direction approaching the second valve seat 151b by the refrigerant flow. Can be suppressed.

  In the present embodiment, the first internal passage 352e1 extends in the radial direction of the rear end portion 352a3. However, the present invention is not limited to this. For example, the first internal passage 352e1 approaches the receiving surface 352f toward the opening end on the second region S12 side. You may form so that it may extend | stretch. Thereby, it is possible to reliably cause the counterflowing refrigerant to collide with the receiving surface 352f.

  In the present embodiment, the communication path 352d is not limited to a groove, and may be a through hole that penetrates the sliding portion 352a1. The communication path 352d is formed in the sliding portion 352a1, but is not limited thereto, and bypasses the sliding portion 352a1 in the formation wall of the first valve chamber S1 (formation wall of the cylinder head 104). You may form so that it may penetrate. Further, a groove is formed on the outer peripheral surface of the sliding portion 352a1, and a concave portion is formed on the inner peripheral surface of the first valve chamber S1 corresponding to the groove, whereby the communication passage 352d is connected to the sliding portion 352a1 and the first portion. It may be formed in cooperation with the inner peripheral surface of the valve chamber S1.

  In addition, in the cross-sectional angular position shown in FIG. 3, the communication path 352d has the same angular position in the circumferential direction as one of the plurality of first internal paths 352e1 (first internal path 352e1 extending upward in the drawing). ing. In order to apply the dynamic pressure evenly to the receiving surface 352f in the circumferential direction, the plurality of communication passages 352d may be arranged at angular positions avoiding the angular position of the first internal passage 352e1. That is, the communication path 352d is located in the second area S12 at an angular position that avoids the opening angular position in the circumferential direction of the peripheral wall of the rear end 352a3 where the opening end of the first internal path 352e1 on the second area S12 side opens. It is good to form so that it may open.

  In the present embodiment, the shaft portion 352c is formed integrally with the second valve portion 352b, but is not limited thereto, and may be formed integrally with the first valve portion 352a.

  In this embodiment, the switching valve 350 is disposed in the cylinder head 104. However, the switching valve 350 is disposed in another housing component, for example, a cylinder block, or the switching valve 350 is accommodated in a dedicated valve housing. Or can be disposed in the compressor housing. Further, the control valve 300 can be a mechanical control valve that does not include a solenoid.

  In the present embodiment, the variable capacity compressor 100 is a swash plate type clutchless variable capacity compressor. However, the present invention is not limited thereto, and a variable capacity compressor equipped with an electromagnetic clutch, a variable capacity compressor driven by a motor, can do.

  Although the contents of the present invention have been specifically described with reference to the preferred embodiments, it is obvious that those skilled in the art can take various modifications based on the basic technical idea and teachings of the present invention. It is.

Reference example
Below, the reference example of the variable capacity compressor which concerns on this invention is demonstrated with reference to FIG. The variable capacity compressor 100 of the present reference example and the variable capacity compressor 100 of the embodiment of FIGS. 1 to 9 include the shape of the front end 352a2, the opening position of the first internal passage 352e1, and the second internal passage 352e2. The only difference is the position of the stretched end. In addition, the same code | symbol is attached | subjected to the element same as embodiment of FIGS. 1-9, description is abbreviate | omitted, and only a different part is demonstrated.
10 (a) and 10 (b) are cross-sectional views of a switching valve 350 according to a reference example, and FIG. 10 (a) shows a pressure supply state (first state) to the crank chamber 140. 10 (b) shows a pressure release state (second state) from the crank chamber 140.

  In this reference example, the front end portion 352a2 includes a cylindrical portion 352a21 projecting from an end portion of the sliding portion 352a1 on the first region S11 side, and a closing portion 352a22 that closes the first valve hole 104c1 side end of the cylindrical portion 352a21. It consists of. The outer edge portion of the end surface of the closing portion 352a22 on the first valve hole 104c1 side protrudes in an annular shape. In the first valve portion 352a, a portion protruding in an annular shape in the closing portion 352a22 of the front end portion 352a2 contacts and separates from the first valve seat 104c2.

  The first internal passage 352e1 penetrates not the peripheral wall of the rear end 352a3 but the peripheral wall of the cylindrical portion 352a21 of the front end 352a2. Therefore, the first internal passage 352e1 communicates the first region S11 and the region in the front end 352a2. Thus, the first internal passage 352e1 opens to the first region S11 in the first valve chamber S1. That is, one end of the first internal passage 352e1 opens toward the control valve 300 (upstream side) with respect to the sliding portion 352a1.

The second internal passage 352e2 is a passage extending from a region in the front end portion 352a2 to the second valve portion 352b and having an open end on the end surface of the second valve portion 352b on the second valve seat 151b side. The second internal passage 352e2 extends in the front end portion 352a2, the sliding portion 352a1, the shaft portion 352c, and the second valve portion 352b with substantially the same diameter from the sliding portion 352a1 side toward the second valve portion 352b side. One end of the second internal passage 352e2 is closed by the closing portion 352a22 of the front end portion 352a2, and the other end is opened on the end surface of the second valve portion 352b on the second valve seat 151b side.
Therefore, the internal passage 352e communicates the first region S11 and the second valve hole 151a by the first internal passage 352e1 and the second internal passage 352e2.

  As shown by a thick arrow in FIG. 10A, in the first state, the refrigerant in the discharge chamber 142 is communicated with the communication path 104e, the control valve 300, the accommodation hole 104b, the communication path 104f, the first valve hole 104c1, 1st region S11 of 1 valve chamber S1, 1st internal passage 352e1, 2nd internal passage 352e2, 2nd valve hole 151a, communication hole of valve plate 103, communication hole of intake valve formation board 150, communication hole of cylinder gasket 152 And is supplied to the crank chamber 140 via the communication passage 101e.

  10B, in the second state, the refrigerant in the crank chamber 140 causes the communication passage 101e, the communication hole of the cylinder gasket 152, the communication hole of the suction valve forming plate 150, the valve It is discharged to the suction chamber 141 via the communication hole of the plate 103, the second valve hole 151a, the gap G between the second valve portion 352b and the second valve seat 151b, the second valve chamber S2, and the pressure release hole 351a1. .

Further, when switching from the first state to the second state, the refrigerant that has flowed back via the internal passage 352e passes through the first internal passage 352e1 as shown by the broken line arrow in FIG. Through the first region S11 of the first valve chamber S1. A part of the refrigerant that has flowed into the first region S11 flows toward the first valve hole 104c1. Further, a part of the refrigerant flowing into the first region S11 also flows to the sliding portion 352a1 side, collides with the end portion 352f2 exposed in the first region S11 of the sliding portion 352a1, and the first valve hole of the spool 352. The movement to 104c1 side can be suppressed. However, since the communication hole 352d that connects the first region S11 and the second region S12 is opened in the sliding portion 352a1, the area of the end portion 352f2 where the refrigerant that has flowed to the sliding portion 352a1 collides is positively increased. Can be reduced. As a result, the spool 352 can be moved relatively smoothly in a direction approaching the first valve seat 104c2.
Therefore, also in the variable capacity compressor 100 according to this reference example, the problem according to the present invention can be solved in the same manner as the variable capacity compressor 100 of the embodiment of FIGS. Note that the variable capacity compressor according to this reference example can be appropriately applied to the modification applied in the variable capacity compressor 100 of the present embodiment.

101a ... Cylinder bore (compression part), 104c1 ... first valve hole, 104c2 ... first valve seat, 104h ... throttle passage, 136 ... piston (compression part), 141 ... suction chamber, 140 ... crank chamber (control pressure chamber), 142 ... discharge chamber, 145 ... pressure supply passage, 151a ... second valve hole, 151b ... second valve seat, 300 ... control valve, 350 ... switching valve, 351 ... partition member, 351a1 ... pressure release hole, 352a ... first Valve portion, 352a1 ... sliding portion, 352a2 ... front end portion, 352a3 ... rear end portion, 352b ... second valve portion, 352c ... shaft portion, 352d ... communication passage, 352e ... internal passage, 352e1 ... first internal passage, 352e2 ... second internal passage, 352f ... receiving surface, 352f1 ... end (exposed end), 100 ... variable capacity compressor, S1 ... first valve chamber, S11 ... first region, S12 ... second region, S2 ... Second Room

Claims (7)

A suction chamber into which the refrigerant is guided; a compression unit that sucks and compresses the refrigerant in the suction chamber; a discharge chamber into which the refrigerant compressed by the compression unit is discharged; and a control pressure chamber; A variable capacity compressor whose discharge capacity changes according to pressure,
A control valve that is provided in a pressure supply passage for supplying the refrigerant in the discharge chamber to the control pressure chamber, and controls the opening of the pressure supply passage;
A switching valve provided closer to the control pressure chamber than the control valve in the pressure supply passage, the first valve hole communicating with the pressure supply passage between the control valve and the switching valve; and the switching valve; A first state where the second valve hole communicating with the pressure supply passage between the control pressure chambers communicates, and a second state where the second valve hole communicates with the pressure relief hole communicating with the suction chamber. A switching valve that switches to
A throttle passage communicating the pressure supply passage between the control valve and the switching valve and the suction chamber;
Including
The switching valve is
A partition member partitioning into a first valve chamber having the first valve hole and a second valve chamber having the second valve hole and the pressure release hole;
A sliding portion having an outer peripheral surface slidably in contact with an inner peripheral surface of the first valve chamber and partitioning the first valve chamber into a first region on the first valve hole side and a second region on the partition member side; A front end portion formed at an end portion of the sliding portion on the first region side and being separated from and contacting a first valve seat around the first valve hole; and the partition member from the second region side of the sliding portion. A first valve portion including a cylindrical rear end portion extending toward the side and having an outer diameter smaller than the outer diameter of the sliding portion;
A second valve portion disposed in the second valve chamber and separated from and in contact with a second valve seat around the second valve hole;
A shaft portion connecting the first valve portion and the second valve portion and penetrating the partition member;
A communication path for communicating the first region and the second region;
A first internal passage passing through the peripheral wall of the rear end portion to communicate the second region and the region in the rear end portion; and extending from the region in the rear end portion to the second valve portion and the second valve An internal passage comprising a second internal passage having an open end on an end face of the portion on the second valve seat side;
And when the pressure in the pressure supply passage between the control valve and the switching valve is higher than the pressure in the control pressure chamber, the pressure valve is separated from the first valve seat and abuts on the second valve seat. The first valve hole and the second valve hole are communicated with each other through the internal passage, and the communication between the second valve hole and the pressure release hole is interrupted, and between the control valve and the switching valve. When the pressure in the pressure supply passage is lower than the pressure in the control pressure chamber, the first valve hole and the second valve hole are brought into contact with the first valve seat and separated from the second valve seat. And the second valve hole and the pressure release hole are communicated with each other,
The sliding portion is a receiving surface on which the refrigerant flowing into the second region collides via the first internal passage, and has a receiving surface that receives a dynamic pressure in a direction away from the second valve seat.
Variable capacity compressor. The receiving surface includes an end portion exposed to the second region of the sliding portion.
The variable capacity compressor according to claim 1.   The variable capacity compressor according to claim 1, wherein the communication path is formed in the sliding portion.   The variable capacity compressor according to claim 3, wherein the communication path includes a groove extending in an axial direction of the sliding portion on an outer peripheral surface of the sliding portion.   The variable capacity compressor according to any one of claims 1 to 4, wherein the first internal passage extends so as to approach the receiving surface toward an opening end on the second region side.   The said 1st valve seat is formed in the conical surface shape which leaves | separates from the said 1st valve hole, so that it goes to the inner peripheral surface side of the said 1st valve chamber from the periphery of the said 1st valve hole. The variable capacity compressor according to any one of the above.   The communication passage is opened to the second region at an angular position avoiding an opening angular position in the circumferential direction of the peripheral wall of the rear end portion where the opening end on the second region side of the first internal passage opens. The variable capacity compressor according to any one of claims 1 to 6.