JP2017218926A - Variable displacement compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable displacement compressor having a simple structure and an easy layout of a valve gear.SOLUTION: A variable displacement compressor comprises a control valve 300 arranged at a pressure supply passage communicating between a discharge chamber 142 and a crank chamber 140; a selector valve 350 arranged at a lower side of a gravity weight direction than an axis line of a driving shaft 110 and installed closer to a crank chamber 140 than the control valve 300 at the pressure supply passage and having a communication part communicated with a suction chamber; and an orifice passage 320 communicating a pressure supply passage 145a between the control valve 300 and the selector valve 350 with a suction chamber 141. When the control valve 300 closes the pressure supply passage, the selector valve 350 shuts off a communication between a pressure supply passage 145a between the control valve 300 and the selector valve 350 and a pressure supply passage 145b between the selector valve 350 and the crank chamber 140 and at the same time causes the pressure supply passage 145b between the selector valve 350 and the crank chamber 140 to be communicated with the suction chamber 141 through the communication part.SELECTED DRAWING: Figure 9

Description

  The present invention relates to a variable capacity compressor, and more particularly to a variable capacity compressor in which a discharge capacity is controlled by regulating a crank chamber.

  As an example of this type of variable capacity compressor, a variable capacity compressor described in Patent Document 1 includes a supply passage for supplying refrigerant in a discharge pressure region to a crank chamber, and a passage cross-sectional area of the supply passage. 1 control valve, a discharge passage for discharging the refrigerant in the crank chamber to the suction pressure region, a second control valve for adjusting a passage cross-sectional area of the discharge passage, and between the first control valve and the crank chamber in the supply passage And a check valve that prevents the reverse flow of the refrigerant from the crank chamber toward the first control valve.

JP 2011-185138 A

  By the way, the first valve device for controlling the supply of the refrigerant to the crank chamber, the second valve device for controlling the discharge of the refrigerant from the crank chamber, and the first valve for preventing the reverse flow of the refrigerant from the crank chamber to the first valve device. In a variable capacity compressor provided with a three-valve device individually, the structure of the variable capacity compressor must be complicated. Also, the variable capacity compressor is required to be downsized like many other devices, and it is difficult to lay out the second valve device and the third valve device in the variable capacity compressor.

  Accordingly, an object of the present invention is to provide a variable capacity compressor having a simple structure and a simple valve device layout.

  According to one aspect of the present invention, a variable capacity compressor whose discharge capacity is controlled by pressure regulation in a crank chamber includes a control valve provided in a pressure supply passage that connects the discharge chamber and the crank chamber, and an axis of a drive shaft. A switching valve disposed on the lower side in the gravitational direction, provided on the crank chamber side than the control valve in the pressure supply passage and having a communication portion communicating with the suction chamber, and the control valve and the switching valve And a throttle passage communicating the suction chamber with the pressure supply passage therebetween. The switching valve includes a pressure supply passage between the control valve and the switching valve and a pressure supply passage between the switching valve and the crank chamber when the control valve closes the pressure supply passage. The communication is cut off, and the pressure supply passage between the switching valve and the crank chamber and the suction chamber are communicated with each other via the communication portion.

  In the variable capacity compressor, the switching valve has a function of controlling discharge of the refrigerant from the crank chamber when the control valve closes the pressure supply passage, and a refrigerant directed from the crank chamber to the control valve. It has a function of preventing the backflow. For this reason, the structure of the variable displacement compressor is simplified and the layout of the valve device in the variable displacement compressor is facilitated as compared with the case where the valve devices having the respective functions are individually provided.

It is sectional drawing of the variable capacity compressor which concerns on embodiment of this invention. It is sectional drawing which shows the structure of the control valve of the said variable capacity compressor. It is a figure which shows the relationship between the coil energization amount in the said control valve, and setting pressure. FIG. 4 is a cross-sectional view of a main part of the control valve, where (a) shows a state where the throttle passage is opened, and (b) shows a state where the throttle passage is closed. It is sectional drawing which shows the structure of the switching valve which concerns on 1st Embodiment, (a) shows the pressure supply state to a crank chamber, (b) shows the pressure release state from the said crank chamber. It is a figure which shows the valve assembly (valve housing, valve body, and 1st valve seat formation part) of the said switching valve. It is a figure for demonstrating the positioning method of the said valve assembly. It is a figure for demonstrating operation | movement of the said variable capacity compressor (the said control valve, the said switching valve). It is a figure for demonstrating operation | movement of the said variable capacity compressor (the said control valve, the said switching valve). It is a figure for demonstrating operation | movement of the said variable capacity compressor (the said control valve, the said switching valve). It is sectional drawing which shows the structure of the switching valve which concerns on 2nd Embodiment. It is sectional drawing which shows the structure of the switching valve which concerns on 3rd Embodiment. It is sectional drawing which shows the structure of the switching valve which concerns on 4th Embodiment. It is sectional drawing which shows the structure of the switching valve which concerns on 5th Embodiment. It is sectional drawing which shows the structure of the switching valve which concerns on 6th Embodiment, (a) shows the pressure supply state to a crank chamber, (b) shows the pressure release state from the said crank chamber.

  Hereinafter, a variable capacity compressor according to an embodiment of the present invention will be described with reference to the accompanying drawings. The variable capacity compressor according to the embodiment is configured as a clutchless compressor mainly applied to a vehicle air conditioner system.

[First Embodiment]
"Overall configuration of variable capacity compressor"
FIG. 1 is a cross-sectional view of a variable capacity compressor 100 according to an embodiment of the present invention. The variable capacity compressor 100 includes a cylinder block 101 in which a plurality of cylinder bores 101 a are formed, a front housing 102 provided on one end side of the cylinder block 101, and a valve plate 103 on the other end side of the cylinder block 101. Cylinder head 104. A crank chamber 140 is formed by the cylinder block 101 and the front housing 102, and a drive shaft 110 is provided across the crank chamber 140.

  A swash plate 111 is disposed around an intermediate portion of the drive shaft 110 in the axial direction. The swash plate 111 is connected to a rotor 112 fixed to the drive shaft 110 via a link mechanism 120, and an angle of the swash plate 111 with respect to the axis of the drive shaft 110 (an inclination angle of the swash plate 111) 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 side rotating with respect to the first arm 112 a via the first connecting pin 122. A link arm 121 that is movably connected and whose other end is rotatably connected to the second arm 111 a via a second connection pin 123.

  The through hole 111b of the swash plate 111 through which the drive shaft 110 is inserted is formed in a shape that allows the swash plate 111 to tilt within a range of a maximum inclination angle and a minimum inclination angle. The through hole 111b is formed with a minimum tilt angle restricting portion that comes into contact with the drive shaft 110. When the inclination angle of the swash plate 111 when the swash plate 111 is orthogonal to the drive shaft 110 (the axis thereof) is set to 0 °, the minimum inclination restriction portion of the through hole 111b has an inclination angle of the swash plate 111 of approximately 0 °. It is in contact with the drive shaft 110 and is configured to restrict further tilting of the swash plate 111. When the inclination angle of the swash plate 111 reaches the maximum inclination angle, the swash plate 111 is brought into contact with the rotor 112 and further tilting is restricted.

  The drive shaft 110 includes a tilt angle reducing spring 114 that biases the swash plate 111 in a direction that decreases the tilt angle of the swash plate 111, and a tilt angle increasing spring 115 that biases the swash plate 111 in a direction that increases the tilt angle of the swash plate 111. And are attached. The inclination decreasing spring 114 is disposed between the swash plate 111 and the rotor 112, and the inclination increasing spring 115 is attached between the swash plate 111 and a spring support member 116 fixed to the drive shaft 110.

  Here, when the tilt angle of the swash plate 111 is the minimum tilt angle, the biasing force of the tilt angle increasing spring 115 is set to be larger than the biasing force of the tilt angle decreasing spring 114, and the drive shaft 110 is rotating. When not, the swash plate 111 is positioned at an inclination angle at which the urging force of the inclination angle decreasing spring 114 and the urging force of the inclination angle increasing spring 115 balance.

  One end (the left end in FIG. 1) of the drive shaft 110 extends through the inside of the boss portion 102 a protruding outside the front housing 102 to the outside of the front housing 102. A power transmission device (not shown) is connected to the one end of the drive shaft 110. A shaft seal device 130 is provided between the drive shaft 110 and the boss portion 102a, and the crank chamber 140 is shut off from the external space.

  The coupling body composed of the drive shaft 110 and the rotor 112 fixed to the drive shaft 110 is supported by bearings 131 and 132 in the radial direction, and supported by the bearing 133 and the thrust plate 134 in the thrust direction. The drive shaft 110 is configured to rotate in synchronization with the rotation of the power transmission device when power from an external drive source is transmitted to the power transmission device. The clearance between the other end of the drive shaft 110, that is, the end on the thrust plate 134 side, and the thrust plate 134 is adjusted to a predetermined clearance by an adjustment screw 135.

  A piston 136 is disposed in each cylinder bore 101a. The inner space formed in the protruding portion that protrudes into the crank chamber 140 of the piston 136 accommodates the outer peripheral portion of the swash plate 111 and its vicinity, and the swash plate 111 is connected to the piston 136 via a pair of shoes 137. It is configured to work with. The piston 136 reciprocates in the cylinder bore 101a by the rotation of the swash plate 111 accompanying the rotation of the drive shaft 110. That is, the rotational movement of the drive shaft 110 is converted into the reciprocating movement of the piston 136 by a conversion mechanism including the swash plate 111, the link mechanism 120, a pair of shoes 137, and the like.

  In the cylinder head 104, a suction chamber 141 disposed in the center and a discharge chamber 142 surrounding the suction chamber 141 in an annular shape are 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 via a discharge valve (not shown) formed on the discharge valve forming plate 151 and a communication hole 103 b provided on the valve plate 103.

  A front housing 102, a center gasket (not shown), a cylinder block 101, a cylinder gasket 152, a suction valve forming plate 150, a valve plate 103, a discharge valve forming plate 151, a head gasket 153, and a cylinder head 104 are connected in order. The compressor body is formed by being fastened by the through bolts 105. The drive shaft 110 is rotatably supported by the compressor body.

  A muffler is provided on the upper portion of the cylinder block 101. The muffler is formed by fastening a lid member 106 in which a discharge port 106a is formed and a muffler forming wall 101b formed in the upper part of the cylinder block 101 with a bolt through a seal member (not shown).

  A muffler space 143 surrounded by the lid member 106 and the muffler forming wall 101 b communicates with the discharge chamber 142 via the communication path 144, and the discharge check valve 200 is disposed in the muffler space 143. The discharge check valve 200 is disposed at a connection portion between the communication path 144 and the muffler space 143. The discharge check valve 200 operates in response to a pressure difference between the communication path 144 (upstream side) and the muffler space 143 (downstream side), and closes the communication path 144 when the pressure difference is smaller than a predetermined value. When the pressure difference is larger than a predetermined value, the communication path 144 is opened.

  The communication passage 144, the discharge check valve 200, the muffler space 143, and the discharge port 106a constitute a discharge passage of the variable capacity compressor 100. The discharge chamber 142 is connected to the refrigerant circuit (the high pressure side) of the air conditioner system via the discharge passage.

  The cylinder head 104 is formed with a suction passage including a suction port (not shown) and a communication passage 104a. The suction passage extends linearly from the outside in the radial direction of the cylinder head 104 so as to cross a part of the discharge chamber 142. The suction chamber 141 is connected to the refrigerant circuit (low pressure side) of the air conditioner system via the suction passage.

  In the cylinder block 101 and the cylinder head 104, a pressure supply passage 145 (described later) that connects the discharge chamber 142 and the crank chamber 140 is formed, and a control valve 300 is provided in the pressure supply passage 145. In the present embodiment, the control valve 300 is disposed in the first accommodation hole 104b that constitutes a part of the pressure supply passage 145, and is configured to be able to adjust the opening degree (passage cross-sectional area) of the pressure supply passage 145. ing. The first accommodation hole 104 b is formed in the cylinder head 104 so as to extend in the radial direction of the cylinder head 104. The first accommodation hole 104b communicates with the suction chamber 141 through the communication path 104c.

  The control valve 300 opens the pressure supply passage 145 according to the pressure of the suction chamber 141 introduced through the communication passage 104c and the electromagnetic force generated by the current flowing through the solenoid based on the external signal (passage cross-sectional area). Thus, the introduction amount (pressure supply amount) of the refrigerant (discharge gas) in the discharge chamber 142 into the crank chamber 140 is controlled. The control valve 300 will be described in detail later.

  A switching valve 350 is disposed downstream of the control valve 300 (crank chamber 140 side) in the pressure supply passage 145. The switching valve 350 is disposed in the second accommodation hole 104 d that constitutes a part of the pressure supply passage 145. In the present embodiment, the second accommodation hole 104 d has an opening on the mating surface side of the cylinder head 104 with the cylinder block 101 and communicates with the suction chamber 141. Specifically, the second accommodation hole 104 d opens to the suction chamber 141.

  In the present embodiment, the pressure supply passage 145 includes the first accommodation hole 104b, the second accommodation hole 104d, the communication passage 104f that connects the discharge chamber 142 and the first accommodation hole 104b, the first accommodation hole 104b, and the second accommodation hole. The communication passage 104e communicates with 104d, and the communication passage 101c communicates with the second accommodation hole 104d and the crank chamber 140. The communication paths 104e and 104f are formed in the cylinder head 104, and the communication path 101c is formed in the cylinder block 101.

  In the following description, a region between the control valve 300 and the switching valve 350 in the pressure supply passage 145 is referred to as a “pressure supply passage 145 a between the control valve 300 and the switching valve 350”, and the pressure supply passage 145. The region between the switching valve 350 and the crank chamber 140 is referred to as a “pressure supply passage 145b between the switching valve 350 and the crank chamber 140”.

  In the present embodiment, the pressure supply passage 145a between the control valve 300 and the switching valve 350 is a region on the downstream side (switching valve 350 side) of the valve hole 301c in the control valve 300, in the first accommodation hole 104b. A region downstream of the control valve 300, a communication passage 104e, and a partial region of the second accommodation hole 104d are configured. The pressure supply passage 145b between the switching valve 350 and the crank chamber 140 is a plate-like member (suction valve formation plate 150, valve plate 103, discharge valve formation) disposed between the cylinder head 104 and the cylinder block 101. Plate 151 and the like) and a communication path 101c.

  The switching valve 350 is configured to be able to switch the pressure supply passage 145b between the switching valve 350 and the crank chamber 140 from a state communicating with the discharge chamber 142 to a state communicating with the suction chamber 141 or vice versa. The switching valve 350 communicates the crank chamber 140 and the suction chamber 141 via the switching valve 350 via the switching valve 350 in conjunction with the opening and closing of the control valve 300. The first pressure release passage 146a, in other words, the first pressure release passage 146a between the switching valve 350 and the crank chamber 140 is switched. The configuration and operation of the switching valve 350 will be described in detail later, but the outline will be described as follows. That is, the switching valve 350 has a communication portion (which corresponds to a third port 351a1 described later) that communicates with the suction chamber 141. When the control valve 300 is open, the switching valve 350 communicates the pressure supply passage 145a between the control valve 300 and the switching valve 350 and the pressure supply passage 145b between the switching valve 350 and the crank chamber 140. ing. When the control valve 300 is closed and the pressure supply passage 145 is closed, the pressure supply passage 145a between the control valve 300 and the switching valve 350, and the pressure supply passage 145b between the switching valve 350 and the crank chamber 140, And the pressure supply passage 145b between the switching valve 350 and the crank chamber 140 and the suction chamber 141 are communicated with each other through the communication portion.

  The crank chamber 140 is always in communication with the suction chamber 141 by a second pressure relief passage 146b that passes through a communication passage 101d, a space 101e, and a fixed throttle 103c formed in the valve plate 103. That is, the variable capacity compressor 100 includes a first pressure release passage 146a opened and closed by the switching valve 350 and a second pressure release passage 146b that is always open as a pressure release passage communicating the crank chamber 140 and the suction chamber 141. And have. Here, the minimum passage sectional area of the first pressure relief passage 146a is set larger than the passage sectional area of the fixed throttle 103c of the second pressure relief passage 146b.

  Further, the pressure supply passage 145a between the control valve 300 and the switching valve 350 and the suction chamber 141 are configured to communicate with each other by a throttle passage 320 (described later) passing through the control valve 300. For this reason, when the control valve 300 is closed and the pressure supply passage 145 is closed, the pressure in the pressure supply passage 145 a between the control valve 300 and the switching valve 350 becomes lower than the pressure in the crank chamber 140. In this case, the switching valve 350 closes the pressure supply passage 145 (blocks the communication between the pressure supply passage 145a and the pressure supply passage 145a) and prevents the reverse flow of the refrigerant from the crank chamber 140 toward the control valve 300. Thus, the opening degree of the first pressure relief passage 146a is set to the maximum opening degree. Specifically, the switching valve 350 is in a state where the pressure supply passage 145b between the switching valve 350 and the crank chamber 140 is in communication with the suction chamber 141 (that is, the first release between the switching valve 350 and the crank chamber 140). Switch to pressure passage 146a). As a result, the pressure release passage communicating the crank chamber 140 and the suction chamber 141 is constituted by the first pressure release passage 146a and the second pressure release passage 16b, so that the passage sectional area of the pressure release passage is maximized. Become. Of course, the passage sectional area of the first pressure relief passage 146a is also maximized. Therefore, the refrigerant in the crank chamber 140 immediately flows out (discharges) 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. It becomes equivalent. Then, the inclination angle of the swash plate 111 is maximized, and the stroke of the piston 136 (that is, the discharge capacity of the variable displacement compressor 100) is maximized.

  On the other hand, when the control valve 300 is opened and the pressure supply passage 145 is opened, the pressure in the pressure supply passage 145a between the control valve 300 and the switching valve 350 increases, and the pressure between the control valve 300 and the switching valve 350 is increased. When the pressure in the supply passage 145a becomes higher than the pressure in the crank chamber 140, the switching valve 350 opens the pressure supply passage 145 and closes the first pressure release passage 146a. Specifically, the pressure supply passage 145b between the switching valve 350 and the crank chamber 140 is switched to a state where the pressure supply passage 145b communicates with the discharge chamber 142 (that is, the pressure supply passage 145a between the switching valve 350 and the crank chamber 140). As a result, the pressure relief passage is constituted by only the second pressure relief passage 146b, and the passage sectional area of the pressure relief passage is minimized. Of course, the passage sectional area of the first pressure relief passage 146a is also minimized. Accordingly, 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. It becomes easy. For this reason, the pressure in the crank chamber 140 increases according to the opening degree of the control valve 300, the inclination angle of the swash plate 111 decreases from the maximum, and the stroke of the piston 136 can be variably controlled.

  Thus, the variable capacity compressor 100 is a compressor whose discharge capacity is controlled by pressure regulation in the crank chamber 140. Note that lubricating oil is sealed inside the variable displacement compressor 100, and the variable displacement compressor 100 has an internal structure by the oil agitation accompanying the rotation of the drive shaft 110 and the oil movement accompanying the movement of the refrigerant gas. Is lubricated.

“Basic configuration of control valve 300”
FIG. 2 is a cross-sectional view showing the configuration of the control valve 300, and FIG. 3 is a view showing the relationship between the coil energization amount (current I) and the set pressure. As shown in FIG. 2, in this embodiment, 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 has a cylindrical valve housing 301. Inside the valve housing 301, a first pressure sensing chamber 302, a valve chamber 303, and a second pressure sensing chamber 307 are formed side by side in the axial direction from one end (lower end) side.

  The first pressure sensing chamber 302 communicates with the crank chamber 140 through a communication hole 301a, a first accommodation hole 104b, a communication passage 104e, a second accommodation hole 104d, and a communication passage 101c formed on the outer peripheral surface of the valve housing 301. ing. The second pressure sensing chamber 307 communicates with the suction chamber 141 through a communication hole 301e, a first accommodation hole 104b, and a communication passage 104c formed on the outer peripheral surface of the valve housing 301. The valve chamber 303 communicates with the discharge chamber 142 via a communication hole 301b, a first accommodation hole 104b, and a communication passage 104f formed on the outer peripheral surface of the valve housing 301. The first pressure sensing chamber 302 and the valve chamber 303 are configured to communicate with each other via 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 is evacuated and incorporates a spring. The bellows 305 is configured to be displaceable in the axial direction of the valve housing 301, and has a function as pressure sensing means for receiving the pressure in the first pressure sensing chamber 302, that is, the pressure in the crank chamber 140.

  A cylindrical valve body 304 is accommodated in the valve chamber 303. The valve body 304 is configured such that its outer peripheral surface is in close contact with the inner peripheral surface of the support hole 301d and is slidable in the support hole 301d, and is movable in the axial direction of the valve housing 301. One end (lower end) of the valve body 304 can open and close the valve hole 301 c, and the other end (upper end) of the valve body 304 protrudes into the second pressure sensing chamber 307.

  At the one end of the valve body 304, a rod-like connecting portion 306 is formed to project. An end (tip) 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 has a cylindrical solenoid housing 312. The solenoid housing 312 is coaxially connected to the other end (upper end) of the valve housing 301. The solenoid housing 312 accommodates a molded coil 314 in which the electromagnetic coil is covered with resin. In the solenoid housing 312, a cylindrical fixed core 310 concentric with the mold coil 314 is accommodated inside the mold coil 314. The fixed core 310 extends from the valve housing 301 to the vicinity of the center of the molded coil 314. The end of the solenoid housing 312 opposite to the valve housing 301 is closed by a bottomed cylindrical sleeve 313 provided so as to surround the fixed core 310.

  The fixed core 310 has an insertion hole 310 a in the center, and one end (lower end) of the insertion hole 310 a opens into the second pressure-sensitive chamber 307. A cylindrical movable core 308 is accommodated between the fixed core 310 and the closed end (bottom) of the sleeve 313.

  A solenoid rod 309 is inserted through the insertion hole 310a. One end (lower end) of the solenoid rod 309 is press-fitted and fixed to the other end of the valve body 304, and the other end (upper end) of the solenoid rod 309 is fitted (press-fitted) into a through hole formed in the movable core 308. Yes. That is, the valve body 304, the movable core 308, and the solenoid rod 309 are integrated. A forced release spring 311 is provided between the fixed core 310 and the movable core 308 to urge the movable core 308 in the direction away from the fixed core 310 (the 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. On the other hand, the sleeve 313 is made of a non-magnetic stainless steel material.

  The mold coil 314 is connected to a control device (not shown) provided outside the variable capacity compressor 100 via a signal line or the like. The mold coil 314 generates an electromagnetic force F (I) when a control current I is supplied from the control device. When the mold coil 314 generates the electromagnetic force F (I), the movable core 308 is attracted toward the fixed core 310, and the valve body 304 moves in the valve closing direction.

  In addition to the electromagnetic force F (I) generated by the mold coil 314, the valve body 304 of the control valve 300 includes a biasing force f generated by the forced release spring 311, a force generated by the pressure in the valve chamber 303 (discharge pressure Pd), A force due to the pressure in the chamber 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 of the bellows 305, the seal area Sv which is the area of the valve hole 301c shielded by the valve body 304, and the cross-sectional area Sr of the cylindrical outer peripheral surface of the valve body 304 are Sb = Sv = Sr. The balance of the forces acting on the valve body 304 is expressed by the following formula (1), and the following formula (2) is obtained by modifying the following formula (1). In the expressions (1) and (2), “+” indicates the valve closing direction of the valve element 304, and “−” indicates the valve opening direction of the valve element 304.

F (I) −f + Ps · Sb−F = 0 (1)
Ps = (F + f−F (I)) / Sb (2)

  The connecting body of the bellows 305, the connecting portion 306, and the valve body 304 increases the discharge capacity when the pressure in the suction chamber 141 becomes higher than the set pressure set by the current flowing through the mold coil 314 (that is, the control current I). When the pressure supply passage 145 is reduced in opening (passage cross-sectional area) to lower the pressure in the crank chamber 140 and the pressure in the suction chamber 141 falls below the set pressure, the pressure supply passage 145 The pressure in the crank chamber 140 is increased by increasing the opening degree (passage cross-sectional area). That is, the control valve 300 autonomously controls the opening degree (passage cross-sectional area) of the pressure supply passage 145 so that the pressure in the suction chamber 141 approaches 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 direction of decreasing as shown in FIG. The control device controls energization to the mold coil 314 by pulse width modulation (PWM control) at a predetermined frequency in the range of, for example, 400 Hz to 500 Hz, and pulses so that the current value flowing through the mold coil 314 becomes a desired value. Change the width (duty ratio).

  When the air conditioning system is in operation, that is, when the variable capacity compressor 100 is in operation, the control device adjusts the energization amount to the mold coil 314 based on the air conditioning settings (setting temperature, etc.) and the external environment in the air conditioning system. . Thereby, the discharge capacity is controlled so that the pressure in the suction chamber 141 becomes a set pressure corresponding to the energization amount. On the other hand, 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. As a result, the pressure supply passage 145 is opened by the forced release spring 311, and the discharge capacity of the variable capacity compressor 100 is controlled to the minimum state.

"Throttle passage 320"
In the present embodiment, the throttle passage 320 is configured to communicate the area of the pressure supply passage 145 a between the control valve 300 and the switching valve 350 and the suction chamber 141 via the inside of the control valve 300. ing. 4 is a cross-sectional view of the main part of the control valve 300. FIG. 4A shows a state in which the throttle passage 320 is opened, and FIG. 4B shows a state in which the throttle passage 320 is closed. ing.

  When the control valve 300 is closed and the pressure supply passage 145 is closed, the throttle passage 320 allows the refrigerant in the region of the pressure supply passage 145a between the control valve 300 and the switching valve 350 to escape to the suction chamber 141 side. Is provided.

  In the present embodiment, as shown in FIG. 4A, the throttle passage 320 is formed in a communication hole 304 a that forms an internal space of the integrated valve body 304 and the connection portion 306, and the connection portion 306. A communication hole 306a that connects the first pressure sensing chamber 302 and the communication hole 304a, a communication hole 309a that is formed inside the press-fitting portion that is press-fitted into the valve body 304 of the solenoid rod 309, and that is connected to the communication hole 304a; A cylindrical recess 304b formed at the other end (upper end) of the body 304, and a communication hole 309b formed at a portion of the solenoid rod 309 located in the recess 304b to communicate between the communication hole 309a and the recess 304b. A communication hole 301e formed in the outer peripheral surface of the valve housing 301 and a communication passage 104c (see FIG. 1) formed in the cylinder head 104 are configured.

  Accordingly, as shown in FIG. 4B, when the surface on the other end side of the valve body 304 (that is, the annular surface around the recess 304 b) 304 c abuts the lower end surface of the fixed core 310, the throttle passage 320. Is closed, and the communication between the suction chamber 141 and the first pressure sensing chamber 302, which is the region of the pressure supply passage 145a between the control valve 300 and the switching valve 350, is blocked.

  On the other hand, as shown in FIG. 4A, when the surface (annular surface) 304c on the other end side of the valve body 304 is separated from the lower end surface of the fixed core 310, the throttle passage 320 is opened, and the throttle passage 320 is opened. The first pressure sensing chamber 302 and the suction chamber 141 communicate with each other. Here, the communication hole 309b formed in the solenoid rod 309 is formed to function as a “throttle portion” when the throttling passage 320 is opened. The opening area of the communication hole 309b is set as small as possible in consideration of the outflow (discharge) property of the refrigerant to the suction chamber 141 in the region of the pressure supply passage 145a between the control valve 300 and the switching valve 350. The throttle portion may be provided in the communication hole 306a, the communication hole 304a, or the communication hole 309a.

  In the control valve 300, when the mold coil 314 is demagnetized, the one end of the valve body 304 is separated from the periphery of the valve hole 301c by the urging force of the forcible release spring 311, and the valve opening degree is maximized. That is, the pressure supply passage 145 is opened to the maximum. At this time, as shown in FIG. 4B, the surface 304 c on the other end side of the valve body 304 comes into contact with the lower end surface of the fixed core 310, and the throttle passage 320 is closed. On the other hand, when a current value such that an electromagnetic force exceeding the urging force of the forced release spring 311 acts on the mold coil 314, the one end of the valve body 304 moves in a direction to close the valve hole 301c, and FIG. As shown, the surface 304c on the other end side of the valve body 304 is separated from the lower end surface of the fixed core 310, and the throttle passage 320 is opened.

  Therefore, in the present embodiment, valve means (valve mechanism) for opening and closing the throttle passage 320 is constituted by the surface 304c on the other end side of the valve body 304 of the control valve 300 and the fixed core 310 (lower end surface thereof). The The throttle passage 320 is closed only when the variable capacity compressor 100 in which the mold coil 314 is demagnetized is in an inoperative state (OFF), and the operation state of the variable capacity compressor 100 in which the mold coil 314 is excited ( ON) is in an open state (open state), and the suction chamber 141 communicates with the region of the pressure supply passage 145a between the control valve 300 and the switching valve 350.

“Configuration and operation of switching valve 350”
FIG. 5 is a cross-sectional view showing the configuration of the switching valve 350 (the switching valve according to the first embodiment) arranged in the cylinder head 104, and FIG. 5A shows a state in which the discharge gas is supplied to the crank chamber 140. FIG. 5B shows a state in which the refrigerant flows out of the crank chamber 140 (pressure release state from the crank chamber 140).

  The switching valve 350 includes a valve housing 351, a valve body 352 accommodated in the valve housing 351, a first valve seat forming portion 353, and a second valve seat forming portion 151a.

  The valve body 352 includes a first valve portion 352a disposed on one end side of the valve housing 351, a second valve portion 352b disposed on the other end side of the valve housing 351, a first valve portion 352a, and a second valve portion. And a shaft portion 352c connecting the 352b. The first valve seat forming portion 353 is disposed on the one end side of the valve housing 351. In the present embodiment, the first valve seat forming portion 353 is formed separately from the valve housing 351 and is fixed to the one end side of the valve housing 351. The second valve seat forming portion 354 is disposed on the other end side of the valve housing 351. In the present embodiment, a part of the discharge valve forming plate 151 constitutes the second valve seat forming portion 151a. That is, the discharge valve forming plate 151 is used as the second valve seat forming portion 151a.

  The valve housing 351 has a cylindrical peripheral wall 351a and a partition wall 351b disposed at an intermediate position in the axial direction within the peripheral wall 351a. A first valve seat forming portion 353 is fitted and fixed to the opening on the one end side of the peripheral wall 351a of the valve housing 351, and the opening on the other end side of the peripheral wall 351a of the valve housing 351 is a second valve seat forming portion 151a. It is blocked by (discharge valve forming plate 151). An insertion hole 351b1 is formed in the partition wall 351b.

  The interior of the valve housing 351 is surrounded by a first valve chamber 351c surrounded by a first valve seat forming portion 353, a peripheral wall 351a and a partition wall 351b, and a second valve seat forming portion 151a, a peripheral wall 351a and a partition wall 351b. It is partitioned into a second valve chamber 351d. In other words, the peripheral wall 351a of the valve housing 351 has an inner space that constitutes the first valve chamber 351c and the second valve chamber 351d, and the first valve chamber 351c and the second valve chamber 351d are partitioned walls 351b. It is divided by. The first valve portion 352a of the valve body 352 is disposed in the first valve chamber 351c, the second valve portion 352b of the valve body 352 is disposed in the second valve chamber 351d, and the shaft portion 352c of the valve body 352 is the partition wall. It is inserted through an insertion hole 351b1 formed in 351b.

  The first valve seat forming portion 353 is formed with a first port 353a and a first valve seat 353b. That is, the first valve chamber 351c has a first port 353a and a first valve seat 353b. The first port 353a is formed through the first valve seat forming portion 353, opens into the first valve chamber 351c, and communicates with the pressure supply passage 145a between the control valve 300 and the switching valve 350. The first valve seat 353b is formed around the first port 353a on the surface of the first valve seat forming portion 353 on the first valve chamber 351c side. The first port 353a is opened and closed by the one end surface 352a1 of the first valve portion 352a being separated from and contacting the first valve seat 353b.

  A second port 151a1 and a second valve seat 151a2 are formed in the second valve seat forming portion 151a (discharge valve forming plate 151). That is, the second valve chamber 351d has a second port 151a1 and a second valve seat 151a2. The second port 151a1 is formed through the second valve seat forming portion 151a, opens to the second valve chamber 351d, and communicates with the pressure supply passage 145b between the switching valve 350 and the crank chamber 140. The second valve seat 151a2 is formed around the second port 151a1 on the surface of the second valve seat forming portion 151a on the second valve chamber 351d side. The second port 151a1 is opened and closed by the one end surface 352b1 of the second valve portion 352b coming into contact with the second valve seat 151a2. In addition, although the discharge valve formation board 151 is used as the 2nd valve seat formation part 151a here, it is not restricted to this. Other plate-like members arranged between the cylinder block 101 and the cylinder head 104, that is, the valve plate 103 and the head gasket 153 may be used as the second valve seat forming portion 151a.

  Further, a third port 351a1 that connects the second valve chamber 351d and the suction chamber 141 is formed in the peripheral wall 351a of the valve housing 351. That is, the second valve chamber 351d has a third port 351a1 in addition to the second port 151a1 and the second valve seat 151a2.

  In addition, the valve housing 351, the 1st valve seat formation part 353, and the valve body 352 are formed, for example with metal materials, such as an aluminum type and a brass type.

  As described above, the valve body 352 is disposed in the first valve chamber 351c and separated from and in contact with the first valve seat 353b, and the valve body 352 is disposed in the second valve chamber 351d and separated from the second valve seat 151a2. It includes a second valve portion 352b that contacts, and a shaft portion 352c that connects the first valve portion 352a and the second valve portion 352b and is inserted into an insertion hole 351b1 formed in the partition wall 351b. In the present embodiment, the first valve portion 352a and the shaft portion 352c of the valve body 352 are integrally formed. The second valve portion 352b of the valve body 352 is formed separately from the first valve portion 352a and the shaft portion 352c, and is press-fitted and fixed to the shaft portion 352c.

  Specifically, the valve body 352 is formed by press-fitting the shaft portion 352c into a through hole formed in the second valve portion 352b, and the one end surface 352b1 of the second valve portion 352b is the second valve seat 151a2. At the same time, the other end surface 352a2 of the first valve portion 352a is in contact with one end surface (the surface on the first valve chamber 351c side) 351b2 of the partition wall 351b with respect to the through hole of the second valve portion 352b. The press-fitting position in the axial direction of the shaft portion 352c is adjusted. Hereinafter, a description will be given with reference to FIG.

  First, the one end surface 352b1 of the second valve portion 352b is placed on a horizontal plane. Next, the second valve portion 352b is accommodated in the valve housing 351 with the other end surface 351a3 of the valve housing 351 facing downward, in other words, the second valve portion 352b is provided in the second valve chamber 351d. The surface 351a3 on the other end side of the valve housing 351 is placed on the same horizontal plane so as to be located in the space.

  Next, an integrally formed product of the first valve portion 352a and the shaft portion 352c is inserted from the one end side of the valve housing 351 (the space side serving as the one valve chamber 351c), and the shaft portion 352c is inserted through the insertion hole 351b1.

  Next, the tip of the shaft portion 352c is aligned with the through hole of the second valve portion 352b, and the other end surface 352a2 of the first valve portion 352a is aligned with one end surface (surface on the first valve chamber 351c side) 351b2 of the partition wall 351b. Until the abutment, the integrally formed product is pressed downward to press-fit the shaft portion 352c into the through hole of the second valve portion 352b.

  Then, the first valve seat forming portion 353 is press-fitted and fitted into the opening on the one end side of the valve housing 351, whereby the valve assembly 350a including the valve housing 351, the valve body 352, and the first valve seat forming portion 353 is formed. Is completed. A predetermined range on the first valve seat forming portion 353 side of the valve assembly 350a is accommodated (fitted) in the second accommodation hole 104d, and then the opening on the other end side of the valve housing 351 (the peripheral wall 351a) The switching valve 350 is configured by being closed by the valve seat forming portion 151a.

  In the present embodiment, the axial position adjustment of the first valve portion 352a and the second valve portion 352b is completed at the stage of the valve assembly 350a. Therefore, by using a test jig or the like, whether or not the contact state between the one end surface 352a1 of the first valve portion 352a and the first valve seat 353b is appropriate in the state of the valve assembly 350a (leakage of refrigerant or the like). Whether or not one end surface 352b1 of the second valve portion 352b can properly contact the second valve seat 151a2 (whether or not a refrigerant or the like can leak), and / or It is possible to inspect whether or not communication between the first valve chamber 351c and the second valve chamber 351d is properly blocked.

  With reference to FIG.5 and FIG.6, the structure of the valve body 352 is further demonstrated. The first valve portion 352a of the valve body 352 has one end portion (valve seat side portion) 352a3 on the first valve seat 353b side, the other end portion (partition wall side portion) 352a4 on the partition wall 351b side, and one end portion 352a3. It is comprised by the intermediate part (intermediate site | part) 352a5 arrange | positioned between the other end part 352a4. The outer diameter of the intermediate portion 352a5 is larger than the outer diameter of the valve seat side portion 352a3 and the outer diameter of the partition wall side portion 352a4, and the outer peripheral surface of the intermediate portion 352a5 has a predetermined gap on the inner peripheral surface of the first valve chamber 351c. Has and is supported.

  The second valve portion 352b of the valve body 352 is formed in a bottomed cylindrical shape, the through-hole into which the shaft portion 352c is press-fitted is formed in the bottom wall, and an annular opening end surface is formed in the second valve seat 151a2. One end face 352b1 is in contact with and separated from the other.

  Further, the valve body 352 has an internal passage 352d. The internal passage 352d includes a first passage 352d1 extending in the axial direction and a second passage 352d2 connected to the first passage 352d1. One end of the first passage 352d1 opens to the end surface of the shaft portion 352c press-fitted into the second valve portion 352b, and the other end of the first passage 352d1 is closed. The second passage 352d2 is formed in the valve seat side portion 352a3 of the first valve portion 352a and communicates the first passage 352d1 and the first valve chamber 351c.

  Accordingly, when the one end surface 352a1 of the first valve portion 352a is separated from the first valve seat 353b and the one end surface 352b1 of the second valve portion 352b contacts the second valve seat 151a2, the second port 151a1 and the third port 351a1. The first port 353a and the second port 151a1 communicate with each other via the internal passage 352d. On the other hand, when one end surface 352a1 of the first valve portion 352a abuts on the first valve seat 353b and closes the first port 353a, the one end surface 352b1 of the second valve portion 352b is separated from the second valve seat 151a2 and second. The port 151a1 and the third port 351a1 communicate with each other.

  Here, when the one end surface 352b1 of the second valve portion 352b contacts the second valve seat 151a2, the other end surface 352a2 of the first valve portion 352a is one end surface of the partition wall 351b (the surface on the first valve chamber 351c side). Since it contacts 351b2, the communication between the first valve chamber 351c and the second valve chamber 351d through the insertion hole 351b1 is blocked. Therefore, the flow through the insertion hole 351b1 from the first valve chamber 351c to the second valve chamber 351d is blocked.

  The internal passage 352d further includes a third passage 352d3 that communicates the first passage 352d1 and the first valve chamber 351c, in addition to the second passage 352d2. The third passage 352d3 is formed in the partition wall side portion 352a4 of the first valve portion 352a, and communicates the first passage 352d1 and the first valve chamber 351c.

  Therefore, when the other end surface 352a2 of the first valve portion 352a is in contact with the one end surface 351b2 of the partition wall 351b, the outer peripheral surface of the intermediate portion 352a5 of the first valve portion 352a and the inner peripheral surface of the first valve chamber 351c. A refrigerant flow is formed between the clearance and the outer peripheral surface of the partition wall side portion 352a4 of the first valve portion 352a and the inner peripheral surface of the first valve chamber 351c. For this reason, even if the foreign material etc. are contained in the refrigerant | coolant which flowed into the 1st valve chamber 351c from the 1st port 353a, the retention of the said foreign material etc. which inhibits the movement of the valve body 352 is prevented.

  Thus, the switching valve 350 closes the pressure supply passage 145 by closing the first port 353a with the end face 352a1 of the first valve portion 352a coming into contact with the first valve seat 353b by the movement of the valve body 352. At this time, in the switching valve 350, the one end surface 352b1 of the second valve portion is separated from the second valve seat 151a2, and the second port 151a1 and the third port 351a1 communicate with each other. As a result, the pressure supply passage 145b between the switching valve 350 (second port 151a1) and the crank chamber 140 communicates with the suction chamber 141, and the pressure supply passage 145b is connected to the switching valve 350 (second port 151a1). The first pressure relief passage 146a with the crank chamber 140 is switched to.

  On the other hand, the switching valve 350 opens the pressure supply passage 145 by opening the first port 353a by separating the one end surface 352a1 of the first valve portion 352a from the first valve seat 353b by the movement of the valve body 352. At this time, in the switching valve 350, the one end surface 352b1 of the second valve portion 352b abuts on the second valve seat 151a2 to cut off the communication between the second port 151a1 and the third port 351a1, and the first port 353a. And the second port 151a1 communicate with each other via the internal passage 352d. As a result, the first pressure relief passage 146a between the switching valve 350 (second port 151a1) and the crank chamber 140 communicates with the discharge chamber 142, and the first pressure relief passage 146a is connected to the switching valve 350 ( The pressure supply passage 145b between the second port 151a1) and the crank chamber 140 is switched (returned).

The operation of the switching valve 350 will be described in more detail.
One end surface of the valve body 352 (one end surface 352a1 of the first valve portion 352a) receives pressure (pressure of the pressure supply passage 145a) Pc ′ on the first port 353a side. The other end surface of the valve body 352 (one end surface 352b1 of the second valve portion 352b) receives the pressure on the second port 151a1 side (pressure in the pressure supply passage 145b), that is, the pressure Pc of the crank chamber 140. Further, since the second valve chamber 351d communicates with the suction chamber 141 via the third port 351a1, the pressure Ps of the suction chamber 141 acts on the valve body 352.

  Here, the pressure receiving area of the pressure Pc ′ when the one end surface 352a1 of the first valve portion 352a contacts the first valve seat 353b is S1, and the one end surface 352b1 of the second valve portion 352b is in contact with the second valve seat 151a2. The pressure receiving area of the pressure Pc at the time of contact is S2, and the area defined by the diameter of the contact portion when the other end surface 352a2 of the first valve portion 352a contacts the one end surface 351b2 of the partition wall 351b is S3.

  In a state where the one end surface 352a1 of the first valve portion 352a is in contact with the first valve seat 353b, the pressure Pc of the crank chamber 140 is the pressure Ps of the suction chamber 141, and therefore one end surface 352a1 of the first valve portion 352a. Is a condition for separating the first valve seat 353b from the following equation (3).

Pc ′ · S1> Ps · S1 + f + F1 (3)
Here, f is a frictional force, and F1 is a force due to dynamic pressure acting on the one end surface 352b1 of the second valve portion 352b when the refrigerant flow from the second port 151a1 side collides.

  Therefore, the control valve 300 is opened (that is, the pressure supply passage 145 is opened), and the refrigerant (discharge gas) in the discharge chamber 142 is supplied to the pressure supply passage 145a between the control valve 300 and the switching valve 350. By raising Pc ′, the one end surface 352a1 of the first valve portion 352a can be separated from the first valve seat 353b, and the one end surface 352b1 of the second valve portion 352b can be brought into contact with the second valve seat 151a2.

  Further, a condition for maintaining a state in which the one end surface 352b1 of the second valve portion 352b is in contact with the second valve seat 151a2 and the other end surface 352a2 of the first valve portion 352a is in contact with the one end surface 351b2 of the partition wall 351b. Becomes the following formula (4).

Pc ′ · S3 + F2> Ps · (S3−S2) + Pc · S2 (4)
Here, F2 is a force due to dynamic pressure acting on the one end surface 352a1 of the first valve portion 352a when the refrigerant flow from the first port 353a collides.
However, since S3 = S2, (Pc′−Pc) · S2 + F2> 0 (4 ′)

  If the pressure supply passage 145 is open, that is, if the refrigerant is flowing through the pressure supply passage 145, Pc ′> Pc is established, so that the force due to the static pressure difference (Pc′−Pc) and the force F2 due to the dynamic pressure are Thus, the valve body 352 is held in a state in which the one end surface 352b1 of the second valve portion 352b abuts (presses) the second valve seat 151a2.

  The condition for separating the one end surface 352b1 of the second valve portion 352b from the second valve seat 151a2 may be that the left side of the equation (4 ′) is negative.

  When the control valve 300 is closed (that is, the pressure supply passage 145 is closed), the refrigerant (discharge gas) in the discharge chamber 142 is not supplied to the pressure supply passage 145a between the control valve 300 and the switching valve 350. = 0. In addition, the refrigerant in the pressure supply passage 145a flows out (is discharged) to the suction chamber 141 through the throttle passage 320, so that Pc ′ <Pc. As a result, the left side of the expression (4 ′) becomes negative, the one end surface 352b1 of the second valve portion 352b is separated from the second valve seat 151a2, and the one end surface 352a1 of the first valve portion 352a is separated from the first valve seat. It abuts on 353b.

  Therefore, when the control valve 300 is closed and the pressure supply passage 145 is closed while the one end surface 352b1 of the second valve portion 352b is in contact with the second valve seat 151a2, the one end surface 352b1 of the second valve portion 352b is The condition for separating from the two valve seats 151a2 is expressed by the following expression (5).

Pc · S2 + F3> Pc ′ · S2 + f (5)
(Pc−Pc ′) · S2 + F3> f (5 ′)
Here, F3 is a force due to the dynamic pressure acting on the end surface of the first passage 352d1 when the refrigerant flowing back through the internal passage 352d (first passage 352d1) collides.

  The refrigerant in the pressure supply passage 145a flows into the suction chamber 141 via the throttle passage 320 and Pc ′ <Pc. The one end surface 352b1 of the second valve portion 352b is made to be the second valve by the force due to the static pressure difference (Pc−Pc ′) and the force F3 due to the dynamic pressure generated by the refrigerant flowing back through the internal passage 352d (first passage 352d1). The one end surface 352a1 of the first valve portion is in contact with the first valve seat 353b, being separated from the seat 151a2.

  Thus, the switching valve 350 uses the increase in the pressure Pc ′ on the first port 353a side that acts on the one end surface 352a1 of the first valve portion 352a when the control valve 300 opens the pressure supply passage 145. The body 352 is moved so that the one end surface 352b1 of the second valve portion 352b contacts the second valve seat 151a2. Thereby, the communication between the second port 151a1 and the third port 351a1 is blocked, and the first port 353a and the second port 151a1 are connected via the internal passage 352d. As a result, the first pressure relief passage 146a between the switching valve 350 and the crank chamber 140 is switched to the pressure supply passage 145b.

  In addition, the switching valve 350 utilizes the decrease in the pressure Pc ′ on the first port 353a side that acts on the one end surface 352a1 of the first valve portion 352a when the control valve 300 closes the pressure supply passage 145. The one end surface 352a1 of the first valve portion 352a is brought into contact with the first valve seat 353b. As a result, the first port 353a is closed and the second port 151a1 and the third port 351a1 communicate with each other. As a result, the pressure supply passage 145b between the switching valve 350 and the crank chamber 140 is switched to the first pressure release passage 146a. The pressure receiving areas S1, S2, and S3 of the valve body 352 can be adjusted as appropriate based on the smooth operation of the valve body 352.

“Installation of switching valve 350”
The valve assembly 350a is installed in the second accommodation hole 104d from the side of the mating surface (hereinafter referred to as “open end surface”) 104g of the cylinder head 104 with the cylinder block 101. Specifically, the second accommodation hole 104d is formed as a cylindrical hole having an opening on the open end face 104g side (cylinder block 101 side) of the cylinder head 104 (see FIG. 5). One end of the communication path 104e is opened in the bottom wall 104d1 of the second accommodation hole 104d. The valve assembly 350a is configured so that the one end surface 351a2 of the valve housing 351 faces the bottom wall 104d1 of the second accommodation hole 104d, in other words, the first valve seat forming portion 353 is disposed at the bottom of the second accommodation hole 104d. It is installed in the second accommodation hole 104d so as to face the wall 104d1, and the outer peripheral surface of the valve housing 351 is fitted to the inner peripheral wall 104d2 of the second accommodation hole 104d.

  The switching valve 350 is arranged in a region below the gravity direction from the axis of the drive shaft 110 (see FIG. 1). More specifically, the second receiving hole 104d having an opening on the open end surface 104g side of the cylinder head 104 is provided at a position farther from the cylinder block 101 than the open end surface 104g of the cylinder head 104, and the suction chamber 141 ( The inner wall). In the valve assembly 350a, the one end side (the first valve seat forming portion 353 side) of the peripheral wall 351a of the valve housing 351 is press-fitted into the inner peripheral wall 104d2 of the second housing hole 104d, and the above-mentioned peripheral wall 351a of the valve housing 351 The other end protrudes into the suction chamber 141, and the third port 351 a 1 is located in the suction chamber 141.

  Further, the valve assembly 350a is positioned in the cylinder head 104 such that the surface 351a3 on the other end side of the valve housing 351 contacts the second valve seat forming portion 151a (discharge valve forming plate 151). Hereinafter, a method for positioning the valve assembly 350a will be described with reference to FIG.

  First, the valve assembly 350a is temporarily press-fitted into the second accommodation hole 104d so that the other end surface 351a3 of the valve housing 351 protrudes from the open end surface 104g of the cylinder head 104 by a predetermined amount h.

  Next, the compressor body is assembled. That is, the front housing 102, the cylinder block 101, the suction valve forming plate 150, the valve plate 103, the discharge valve forming plate 151, the cylinder head 104, and the like are sequentially connected. Accordingly, the other end surface 351a3 of the valve housing 351 protruding from the open end surface 104g of the cylinder head 104 abuts on the second valve seat forming portion 151a (discharge valve forming plate 151).

  Then, the compressor main body is fastened with a plurality of through bolts 105 to form a variable capacity compressor 100. As a result, the valve assembly 350a is pushed into the back side of the second housing hole 104d, and the surface 351a3 on the other end side of the valve housing 351 contacts the second valve seat forming portion 151a (discharge valve forming plate 151). In other words, the valve assembly 350a is positioned in a state where the other end surface 351a3 of the valve housing 351 presses the second valve seat forming portion 151a (discharge valve forming plate 151).

  In this way, simultaneously with the assembly of the compressor main body (or the variable capacity compressor 100), between the outer peripheral surface of the valve housing 351 and the inner peripheral wall 104d2 of the second accommodation hole 104d, and the other of the valve housing 351. Since the space between the end-side surface 351a3 and the second valve seat forming portion 151a can be sealed, there is no need to provide a separate seal member or the like, and the structure is simplified.

"Operation of variable capacity compressor 100"
FIG. 8 shows a state where the variable capacity compressor 100 is stopped, such as when the engine of the vehicle is stopped. In this state, the energization to the mold coil 314 of the control valve 300 is OFF, the control valve 300 opens the pressure supply passage 145 to the maximum (maximum passage cross-sectional area), and the throttle passage 320 is closed. It has been. In the switching valve 350, the one end surface 352b1 of the second valve portion 352b abuts on the second valve seat 151a2, the communication between the second port 151a1 and the third port 351a1 is blocked, and the first port 353a and the second port 151a1 are disconnected. Are in communication via the internal passage 352d. For this reason, the crank chamber 140 and the suction chamber 141 communicate with each other only through the second pressure relief passage 146b, and the opening degree (passage cross-sectional area) of the pressure relief passage connecting the crank chamber 140 and the suction chamber 141 is Minimal.

  When the vehicle engine is started in the above state and the drive shaft 110 of the variable displacement compressor 100 rotates, the discharge check valve 200 closes the discharge passage and the throttle passage 320 is closed. All of the discharged refrigerant (refrigerant in the discharge chamber 142) is supplied to the crank chamber 140 via the pressure supply passage 145. Therefore, the pressure in the crank chamber 140 is reliably increased, the inclination angle of the swash plate 111 is minimized, and the stroke (discharge capacity) of the piston 136 is minimized. At this time, the variable capacity compressor 100 is in a non-operating state. The compressed and discharged refrigerant contains oil and has an internal circulation path constituted by a discharge chamber 142, a pressure supply passage 145, a crank chamber 140, a second pressure release passage 146b, a suction chamber 141, and a cylinder bore 101a. It circulates and lubricates the inside of the variable capacity compressor 100.

  Next, when the air conditioner system is activated, a current flows through the mold coil 314 of the control valve 300, the valve body 304 closes the valve hole 301c, and at the same time the throttle passage 320 opens. In this case, the compressed and discharged refrigerant is not supplied to the pressure supply passage 145a between the control valve 300 and the switching valve 350, and also. The refrigerant in the pressure supply passage 145a flows out to the suction chamber 141 through the throttle passage 320. As a result, the pressure in the pressure supply passage 145a becomes equal to that of the suction chamber 141. At this time, in the switching valve 350, the refrigerant flows backward from the second port 151a1 side to the first valve chamber 351c via the internal passage 352d (first passage 352d1), and this internal passage 352d (first passage 352d1). Due to the refrigerant that flows backward, a dynamic pressure that moves the valve body 352 toward the first valve seat 353b is generated.

  For this reason, the valve body 352 has a first force due to a force caused by a difference (static pressure difference) between the pressure on the second port 151a1 side and the pressure on the first port 353a side and a force caused by dynamic pressure caused by the refrigerant flowing backward in the internal passage 352d. The first valve portion 352a moves toward the valve seat 353b, the one end surface 352a1 of the first valve portion 352a comes into contact with the first valve seat 353b, the first port 353a is closed, and the second port 151a1 and the third port 351a1 communicate with each other. That is, the switching valve 350 switches the pressure supply passage 145b to the first pressure release passage 146a. As a result, the crank chamber 140 and the suction chamber 141 communicate with each other through the first pressure release passage 146a and the second pressure release passage 146b, and the opening degree (passage of the pressure release passage that connects the crank chamber 140 and the suction chamber 141 with each other) (Cross-sectional area) is maximized (see FIG. 9).

  Therefore, the refrigerant in the crank chamber 140 quickly flows out (discharges) into the suction chamber 141, and the pressure in the crank chamber 140 becomes equal to the pressure in the suction chamber 141. For this reason, the inclination angle of the swash plate 111 is maximized, and the stroke (discharge capacity) of the piston 136 is maximized. Also. The discharge check valve 200 is opened, the refrigerant circulates through the air conditioner system, and the air conditioner system is activated. Here, when the liquid refrigerant is stored in the crank chamber 140, the liquid refrigerant flows through the internal passage 352d. In this case, the density of the refrigerant becomes remarkably larger than that in the gas state, and the dynamic pressure increases, so that the valve body 352 can be reliably moved in the direction toward the first valve seat 353b.

  Thereafter, when the pressure in the suction chamber 141 decreases to a set pressure set by the current flowing through the mold coil 314, the valve body 304 of the control valve 300 opens the valve hole 301c, whereby the compressed and discharged refrigerant is transferred to the control valve. 300 is supplied to the pressure supply passage 145a between the switching valve 350 and the pressure in the pressure supply passage 145a increases. Accordingly, the pressure on the first port 353a acting on the valve body 352 exceeds the pressure on the suction chamber 141 acting on the opposite side, and the one end surface 352a1 of the first valve portion 352a is separated from the first valve seat 353b. The one end surface 352b1 of the second valve portion 352b contacts the second valve seat 151a2. That is, the switching valve 350 switches the first pressure release passage 146a to the pressure supply passage 145b. For this reason, the crank chamber 140 and the suction chamber 141 communicate with each other only through the second pressure relief passage 146b, and the opening degree (passage cross-sectional area) of the pressure relief passage that communicates the crank chamber 140 with the suction chamber 141 is minimized. (See FIG. 10). Therefore, the pressure in the crank chamber 140 increases in accordance with the adjustment of the opening degree (passage cross-sectional area) of the pressure supply passage 145 by the control valve 300, the inclination angle of the swash plate 111 decreases, and the stroke of the piston 136 (discharge capacity). Decreases, and the discharge capacity control state is entered.

  As described above, in the present embodiment, when the control valve 300 closes the pressure supply passage 145, the switching valve 350 provides the discharge chamber 142 with the pressure supply passage 145b between the switching valve 350 and the crank chamber 140. The state of communication is switched from the state of communication to the state of communication with the suction chamber 141 (that is, the first pressure release passage 146a). Thereby, the reverse flow of the refrigerant from the crank chamber 140 side to the control valve 300 is prevented, and the opening degree (passage cross-sectional area) of the pressure release passage becomes larger than when the pressure supply passage 145 is open ( Maximum). That is, the switching valve 350 has a function of controlling the discharge of the refrigerant from the crank chamber 140 and a function of preventing the reverse flow of the refrigerant from the crank chamber 149 toward the control valve 300. For this reason, it is not necessary to provide a dedicated check valve, and the layout in the variable capacity compressor is facilitated.

  Further, when the control valve 300 closes the pressure supply passage, the switching valve 350 is not limited to the force due to the difference (static pressure difference) between the pressure on the second port 151a1 side and the pressure on the first port 353a side, but also on the second port The valve element 352 is moved using the force by the dynamic pressure generated by the flow of the refrigerant from the 151a1 side to the first valve chamber 351c via the internal passage 352d. For this reason, switching from the pressure supply passage 145a to the first pressure release passage 146a is quickly performed. In particular, when the variable capacity compressor 100 is started in a state where the liquid refrigerant is stored in the crank chamber 140, the switching valve 350 operates quickly and reliably, and the liquid refrigerant in the crank chamber 140 is transferred to the suction chamber 141. It is discharged promptly.

[Second Embodiment]
FIG. 11 is a cross-sectional view showing a configuration of a switching valve 350B according to the second embodiment. When the second accommodation hole 104d and the communication path 104e are formed substantially coaxially, the switching valve may be configured such that the bottom wall 104d1 of the second accommodation hole 104d functions as the first valve seat forming portion. In this case, the valve housing 351 and the valve body 352 constitute a valve assembly 350a, and the opening of the communication passage 104e in the bottom wall 104d1 of the second accommodation hole 104d serves as the first port, and the bottom wall 104d1 of the second accommodation hole 104d. The periphery of the opening of the communication passage 104e is the first valve seat where the one end surface 352a1 of the first valve portion 352a is separated from and connected to. This eliminates the need for a dedicated part for the first valve seat forming portion, and simplifies the configuration of the valve assembly 350a.

[Third Embodiment]
FIG. 12 is a cross-sectional view showing a configuration of a switching valve 350C according to the third embodiment. When the second housing hole 104d and the communication path 104e are formed substantially coaxially, the switching valve is configured such that the bottom wall 104d1 of the second housing hole 104d functions as the first valve seat forming portion, and The inner side of the peripheral wall 351a of the valve housing 351 may be formed so as to constitute only the second valve chamber 351d. Also in this case, the valve assembly 350a is configured by the valve housing 351 and the valve body 352, as in the second embodiment. The second accommodation hole 104d includes, for example, a large-diameter hole 104d21 and a small-diameter hole 104d22 having a smaller diameter than the large-diameter hole 104d21 in order from the open end surface 104g side (cylinder block 101 side) of the cylinder head 104. Formed to have. The outer peripheral surface of the peripheral wall 351a of the valve housing 351 is press-fitted into the inner peripheral surface of the large diameter hole portion 104d21, and the outer peripheral surface of the first valve portion 352a is a predetermined gap between the inner peripheral surface of the small diameter hole portion 104d22. It is configured to be supported with a gap. Even if it does in this way, like the said 2nd Embodiment, the components for the said 1st valve seat formation part become unnecessary, and the structure of the valve assembly 350a is simplified.

[Fourth Embodiment]
FIG. 13 is a cross-sectional view showing a configuration of a switching valve 350D according to the fourth embodiment. The valve assembly 350a including the valve housing 351, the valve body 352, and the first valve seat forming portion 353 may be configured to be detachable from the second accommodation hole 104d. In this case, as shown in FIG. 13, a sealing member 160 having elasticity such as an O-ring is preferably disposed between the peripheral wall 351a of the valve housing 351 and the inner peripheral wall 104d2 of the second accommodation hole 104d.

  More preferably, the urging member 170 is disposed between the bottom wall 104d1 of the second accommodation hole 104d and the one end surface 351a2 of the valve housing 351. The biasing member 170 moves the valve assembly 350a to the second valve seat forming portion 151a so that the surface 351a3 on the other end side of the valve housing 351 presses the valve plate 103 via the second valve seat forming portion 151a. Energize towards. The biasing member 170 is not particularly limited, and may be a wave washer, a disc spring, and / or a coil spring.

  The biasing member 170 causes the surface 352a3 on the other end side of the valve housing 351 to protrude from the open end surface 104g of the cylinder head 104 by a predetermined amount h ′ when the valve assembly 350a is inserted into the second accommodation hole 104d. The other end surface 352 a 3 of the valve housing 351 is pressed so that the other end surface 352 a 3 of the valve housing 351 can move to the open end surface 104 g of the cylinder head 104. The valve assembly 350a inserted into the second accommodation hole 104d is formed on the other end surface 352a3 of the valve housing 351 when the compressor body is formed, specifically, when the plurality of through bolts 105 are fastened. Is pushed into the back side of the second accommodation hole 104d. Accordingly, the valve assembly 350a is installed at an appropriate position in the second accommodation hole 104d, and the other end surface 351a3 of the valve housing 351 is interposed via the second valve seat forming portion 151a (discharge valve forming plate 151). To press the valve plate 103.

  When the valve assembly 350a is inserted into the second housing hole 104d, the elasticity of the seal member 160 such as an O-ring disposed between the peripheral wall 351a of the valve housing 351 and the inner peripheral wall 104d2 of the second housing hole 104d. It is held in the second accommodation hole 104d by force. Therefore, when the open end surface 104g of the cylinder head 104 is directed downward in the direction of gravity, the valve assembly 350a and the biasing member 170 do not fall out of the second accommodation hole 104d, and the variable capacity compressor 100 The assembling property of this is not impaired.

[Fifth Embodiment]
FIG. 14 is a cross-sectional view showing a configuration of a switching valve 350E according to the fifth embodiment. Similarly to the first valve seat forming portion 353 fixed to the one end side of the valve housing 351, the second valve seat forming portion 354 may be fixed to the other end side of the peripheral wall 351a of the valve housing 351. In this case, the second housing hole 104d is formed, for example, in the open end surface 104g of the cylinder head 104, and the inside of the second housing hole 104d and the suction chamber 141 are partitioned, and the second housing hole 104d and the suction chamber 141 are separated from each other. Are configured to communicate with each other via the communication path 104h.

  Seal members 160 and 161 such as an O-ring are disposed between the peripheral wall 351a of the valve housing 351 and the inner peripheral wall 104d2 of the second accommodation hole 104d. The seal member 160 blocks communication between the pressure supply passage 145a and the suction chamber 141 through a gap between the peripheral wall 351a of the valve housing 351 and the inner peripheral wall 104d2 of the second accommodation hole 104d. The seal member 161 is connected to the valve housing 351. The communication between the pressure supply passage 145b and the suction chamber 141 through the gap between the peripheral wall 351a of the second housing hole 104d and the inner peripheral wall 104d2 of the second accommodation hole 104d is blocked. The valve assembly 350a is held in the second accommodation hole 104d by the elastic force of the seal members 160 and 161.

[Sixth Embodiment]
FIG. 15 is a cross-sectional view illustrating a configuration of a switching valve 350F according to the sixth embodiment. 15A shows a pressure supply state to the crank chamber 140, and FIG. 15B shows a pressure release state pressure from the crank chamber 140. FIG. The switching valve 350F according to the sixth embodiment is arranged not on the cylinder head 104 but on the lower side in the gravity direction than the axis of the drive shaft 110 in the cylinder block 101.

  The switching valve 350F includes a third accommodation hole 101f formed in the cylinder block 101, a ring-shaped member 355, a valve body 352, and a suction valve forming plate 150.

  The third housing hole 101f is formed in the surface on the other end side of the cylinder block 101 (a mating surface with the cylinder head 104) 101g. The third housing hole 101f is formed in a bottomed stepped circular hole shape, and has a large diameter hole portion 101f1 that opens to the surface 101g on the other end side of the cylinder block 101, and a smaller diameter than the large diameter hole portion 101f1. With a small-diameter hole 101f2. In addition, the opening of the large-diameter hole portion 101f1 of the third accommodation hole 101f is closed by the suction valve forming plate 150.

  The ring-shaped member 355 is attached to the large-diameter hole portion 101f1 of the third accommodation hole 101f. The ring-shaped member 355 partitions the first valve chamber 101f3 and the second valve chamber 101f4 in the third accommodation hole 101f. The first valve chamber 101f3 is surrounded by the inner peripheral wall of the large-diameter hole 101f1, the ring-shaped member 355 and the suction valve forming plate 150, and the second valve chamber 101f4 is the inner peripheral wall of the small-diameter hole 101f2 and the ring-shaped member. 355 and the bottom wall 101f5 of the third accommodation hole 101f. That is, the ring-shaped member 355 corresponds to the partition wall 351b of the valve housing 351 described above.

  Similar to the first embodiment, the valve body 352 includes a first valve portion 352a, a second valve portion 352b, a shaft portion 352c that connects the first valve portion 352a and the second valve portion 352b, and an internal passage 352d (352d1, 352d2, 352d3). The first valve portion 352a is accommodated in the first valve chamber 101f3, the second valve portion 352b is accommodated in the second valve chamber 101f4, and the shaft portion 352c is inserted into the hole (insertion hole) 355a of the ring-shaped member 355. Has been.

  A region (blocking portion) 150a that closes the opening of the large-diameter hole portion 101f1 of the third accommodation hole 101f in the suction valve forming plate 150, in other words, the wall of the first valve chamber 101f3 includes the first port 150a1 and the first port 150a1. One valve seat 150a2 is formed. The first port 150a1 is formed through the suction valve forming plate 150, opens to the first valve chamber 101f3, and communicates with the pressure supply passage 145a between the control valve 300 and the switching valve 350. The first valve seat 150 a 2 is formed around the first port 150 a 1 in the closing portion 150 a of the suction valve forming plate 150. And the 1st port 150a1 is opened and closed when the one end surface 352a1 of the 1st valve part 352a of the valve body 352 contacts / separates to the 1st valve seat 150a2. That is, in this embodiment, the intake valve forming plate 150 (the closed portion 150a thereof) is used as the first valve seat forming portion. However, the present invention is not limited to this, and a plate-like member other than the intake valve forming plate 150, such as the valve plate 103, the cylinder gasket 152, or the discharge valve forming plate 151, disposed between the cylinder block 101 and the cylinder head 104 is used. The first valve seat forming portion may be used.

  The bottom wall 101f5 of the third housing hole 101f, in other words, the wall portion of the second valve chamber 101f4 is connected to a communication passage 101c 'that communicates the crank chamber 140 and the third housing hole 101f (second valve chamber 101f4). A second port 101f5a constituting one end is opened. A second valve seat 101f5b is formed around the second port 101f5a in the bottom wall 101f5 of the third accommodation hole 101f. And the 2nd port 101f5a is opened and closed by the one end surface 352b1 of the 2nd valve part 352b of the valve body 352 contacting / separating to the 2nd valve seat 101f5b. That is, in the present embodiment, the bottom wall 101f5 of the third housing hole 101f has a function as the second valve seat forming portion.

  The suction chamber 141 and the third accommodation hole 101f (second valve chamber 101f4) communicate with the inner peripheral wall of the small-diameter hole portion 101f2 of the third accommodation hole 101f, that is, the other wall portion of the second valve chamber 101f4. A third port 101f2a that constitutes one end of the communicating path 104h 'is opened.

  In the present embodiment, the valve body 352 and the ring-shaped member 355 are disposed in the third accommodation hole 101f as a valve assembly 350a ′. The assembly of the valve assembly 350a ′ and the installation of the valve assembly 350a ′ in the third accommodation hole 101f are performed as follows. Also in this embodiment, the first valve portion 352a and the shaft portion 352c of the valve body 352 are integrally formed, and the shaft portion 352c is inserted into a through hole (press-fit hole) formed in the second valve portion 352b of the valve body 352. The valve body 352 is formed by press fitting.

  First, in a state where the shaft portion 352c of the valve body 352 is inserted through the hole (insertion hole) 355a of the ring-shaped member 355, the through hole of the second valve portion 352b is temporarily press-fitted into the shaft portion 352c, and the valve assembly. 350a 'is formed. When the valve assembly 350a ′ in the temporarily press-fitted state is accommodated in the third accommodation hole 101f, the ring-shaped member 355 contacts the connection part (step surface) between the large diameter hole part 101f1 and the small diameter hole part 101f2, In addition, a predetermined gap is provided between the other end surface 352a2 of the first valve portion 352a and the one end surface 355b1 of the ring-shaped member 355 in a state where the one end surface 352b1 of the second valve portion 352b is in contact with the second valve seat 101f5b. Formed to have.

  Next, the temporarily press-fitted valve assembly 350a ′ is accommodated in the third accommodation hole 101f, and the first valve portion 352a is in a state where one end surface 352b1 of the second valve portion 352b is in contact with the second valve seat 101f5b. The press-fitting position of the shaft portion 352c with respect to the through hole of the second valve portion 352b is adjusted so that the other end surface 352a2 contacts the one end surface 355b1 of the ring-shaped member 355.

  Thus, when the one end surface 352b1 of the second valve portion 352b contacts the second valve seat 101f5b, the other end surface 352a2 of the first valve portion 352a contacts the one end surface 355b1 of the ring-shaped member 355, and the ring-shaped member 355. The communication between the first valve chamber 101f3 and the second valve chamber 101f4 through the hole (insertion hole) 355a is blocked.

  When the control valve 300 opens the pressure supply passage 145, the switching valve 350F moves the valve body 352 using the increase in the pressure Pc ′ on the first port 150a1 side that acts on the one end surface 352a1 of the first valve portion 352a. Thus, the one end surface 352b1 of the second valve portion 352b is brought into contact with the second valve seat 101f5b. Thereby, the communication between the second port 101f5a and the third port 101f2a is blocked, and the first port 150a1 and the second port 101f5a communicate with each other via the internal passage 352d. As a result, the first pressure release passage 146a between the switching valve 350F (second port 101f5a) and the crank chamber 140 is switched to the pressure supply passage 145b.

  Further, the switching valve 350F uses the decrease in the pressure Pc ′ on the first port side that acts on the one end surface 352a1 of the first valve portion 352a when the control valve 300 closes the pressure supply passage 145, to switch the valve body 352. The first end 352a1 of the first valve portion 352a is brought into contact with the first valve seat 150a2. Thereby, the first port 150a1 is closed, and the second port 101f5a and the third port 101f2a communicate with each other. As a result, the pressure supply passage 145b between the switching valve 350F (second port 101f5a) and the crank chamber 140 is switched to the first pressure release passage 146a.

  When the one end surface 352b1 of the second valve portion 352b contacts the second valve seat 101f5b, the other end surface 352a2 of the first valve portion 352a contacts the one end surface 355b1 of the ring-shaped member 355, and thus the first valve chamber 101f3. To the second valve chamber 101f4 through the insertion hole 355a is blocked.

  As mentioned above, although embodiment of this invention was described, this invention is not limited to the above-mentioned embodiment, Based on the technical idea of this invention, a various deformation | transformation and change are possible. Some of them are listed below.

  In the switching valve, when one end surface 352b1 of the second valve portion 352b is formed with a groove or a throttle passage, and the one end surface 352b1 of the second valve portion 352b contacts the second valve seat, the second port and The third port may be configured not to be completely blocked. Moreover, it is good also as a structure to which slight leakage is accept | permitted when the one end surface 352a of the 1st valve part 352a contact | abuts to the said 1st valve seat. Furthermore, when the other end surface 352a2 of the first valve portion 352a abuts on the partition wall 351b of the valve housing 351 or the one end surface of the ring-shaped member 355, a slight flow from the first valve chamber to the second valve chamber. May be allowed.

  In the switching valve, the peripheral wall 351a and the partition wall 351b of the valve housing 351 may be configured as separate members. In this case, the first valve seat forming portion or the second valve seat forming portion may be integrally formed with the peripheral wall 351a.

  The throttle passage 320 may be configured to communicate the pressure supply passage 145 a between the control valve 300 and the switching valve 350 and the suction chamber 141 without passing through the control valve 300. For example, the throttle passage 320 passes through the inside of the switching valve and is throttled when the other end surface 352a2 of the first valve portion 352a abuts on the partition wall 351b of the valve housing 351 or the one end surface of the ring-shaped member 355. A part may be formed.

  The control valve 300 may be a mechanical control valve without a solenoid, or may be an electromagnetic valve without a pressure sensitive member such as a bellows.

  The variable capacity compressor is not limited to a swash plate type clutchless compressor, and may be a variable capacity compressor equipped with an electromagnetic clutch or a variable capacity compressor driven by a motor.

  DESCRIPTION OF SYMBOLS 100 ... Variable capacity compressor, 101 ... Cylinder block, 102 ... Front housing, 104 ... Cylinder head, 110 ... Drive shaft, 140 ... Crank chamber, 104d ... Second accommodation hole, 141 ... Suction chamber, 142 ... Discharge chamber, 145a , 145b ... pressure supply passage, 146a, 146b ... pressure release passage, 151 ... discharge valve forming plate, 151a ... second valve seat forming portion, 151a1 ... second port, 151a2 ... second valve seat, 300 ... control valve, 350 Switch valve 350a Valve assembly 351 Valve housing 351a Circumferential wall 351a1 Third port 351b Partition wall 351b1 Insertion hole 351c First valve chamber 351d Second valve chamber 352 ... Valve, 352a ... First valve part, 352b ... Second valve part, 352c ... Shaft part, 353 ... First valve seat forming part, 353a ... First port, 353b The first valve seat

Claims (17)

A variable capacity compressor whose discharge capacity is controlled by pressure regulation in the crank chamber,
A control valve provided in a pressure supply passage communicating the discharge chamber and the crank chamber;
A switching valve that is disposed below the axis of the drive shaft in the direction of gravity, is provided on the crank chamber side of the control valve in the pressure supply passage, and has a communication portion that communicates with the suction chamber;
A throttle passage communicating the pressure supply passage between the control valve and the switching valve and the suction chamber;
Including
The switching valve includes a pressure supply passage between the control valve and the switching valve and a pressure supply passage between the switching valve and the crank chamber when the control valve closes the pressure supply passage. The communication is cut off, and the pressure supply passage between the switching valve and the crank chamber and the suction chamber are communicated with each other via the communication portion.
Variable capacity compressor.   The switching valve communicates the pressure supply passage between the switching valve and the crank chamber to the suction chamber when the control valve closes the pressure supply passage, so that the control valve The variable capacity compressor according to claim 1, wherein a passage sectional area of a pressure release passage communicating the crank chamber and the suction chamber is increased as compared to when the passage is open. The switching valve is
A first port chamber having a first port communicating with the pressure supply passage between the control valve and the switching valve and a first valve seat provided around the first port;
A second port communicating with the pressure supply passage between the switching valve and the crank chamber; a second valve seat provided around the second port; and a third port communicating with the suction chamber. A valve chamber;
A first valve portion disposed in the first valve chamber and separated from and contacting the first valve seat; a second valve portion disposed in the second valve chamber and separated from and contacted by the second valve seat; and the second valve A valve body having an internal passage for communicating the second port and the first valve chamber when a portion is in contact with the second valve seat;
Including
When the control valve closes the pressure supply passage, a decrease in pressure on the first port side and a dynamic pressure due to the flow of refrigerant from the second port side to the first valve chamber via the internal passage. Utilizing the first valve portion to contact the first valve seat to close the first port, and separating the second valve portion from the second valve seat to the second port and the third A communication port, thereby blocking communication between the pressure supply passage between the control valve and the switching valve and the pressure supply passage between the switching valve and the crank chamber, and the switching Communicating the pressure supply passage between the valve and the crank chamber and the suction chamber, and maximizing the passage sectional area of the pressure release passage communicating the crank chamber and the suction chamber;
When the control valve opens the pressure supply passage, the first valve portion is separated from the first valve seat by utilizing the pressure increase on the first port side, and the first port is opened to open the first port. The first port and the second port are communicated with each other through the internal passage, and the communication between the second port and the third port is blocked by bringing the second valve portion into contact with the second valve seat or As a result, the pressure supply passage between the control valve and the switching valve communicates with the pressure supply passage between the switching valve and the crank chamber, and the pressure release passage. Configured to minimize the passage cross-sectional area of
The variable capacity compressor according to claim 1 or 2. The first valve chamber and the second valve chamber are partitioned by a partition wall;
The valve body has a shaft portion that connects the first valve portion and the second valve portion and is inserted into an insertion hole formed in the partition wall, and the second valve portion is the second valve. When contacting the seat, the first valve portion is configured to contact the partition wall and block communication between the first valve chamber and the second valve chamber via the insertion hole.
The variable capacity compressor according to claim 3. The switching valve is
A valve housing having an inner space constituting the second valve chamber and having a peripheral wall formed with the third port, and the partition wall;
A first valve seat forming portion in which the first port and the first valve seat are formed and forming the first valve chamber together with the valve housing;
A second valve seat forming portion in which the second port and the second valve seat are formed and forming the second valve chamber together with the valve housing;
Including
The valve housing and the valve body are configured as a valve assembly, and the valve body is formed of the first valve portion and the second valve portion as separate parts, and the first valve portion and the second valve portion. And the relative position in the axial direction is adjustable.
The variable capacity compressor according to claim 4. The switching valve is
A valve housing having an inner space constituting the first valve chamber and the second valve chamber and having a peripheral wall formed with the third port, and the partition wall;
A first valve seat forming portion in which the first port and the first valve seat are formed and forming the first valve chamber together with the valve housing;
A second valve seat forming portion in which the second port and the second valve seat are formed and forming the second valve chamber together with the valve housing;
Including
The valve housing, the valve body, and the first valve seat forming portion are configured as a valve assembly, and the valve body includes the first valve portion and the second valve portion that are formed as separate parts, and The relative position in the axial direction between the valve portion and the second valve portion is configured to be adjustable.
The variable capacity compressor according to claim 4.   The variable capacity compressor according to claim 6, wherein the first valve seat forming portion is integrally formed with the valve housing. The rotary shaft is provided on one end side of the cylinder block, the front housing that forms the crank chamber in cooperation with the cylinder block, and the suction chamber provided on the other end side of the cylinder block. The discharge chamber is rotatably supported by a compressor body including a cylinder head having a compartment formed therein,
The control valve and the switching valve are disposed in the cylinder head,
The variable capacity compressor according to any one of claims 1 to 7. The rotary shaft is provided on one end side of the cylinder block, the front housing that forms the crank chamber in cooperation with the cylinder block, and the suction chamber provided on the other end side of the cylinder block. The discharge chamber is rotatably supported by a compressor body including a cylinder head having a compartment formed therein,
The valve assembly of the valve housing and the valve body is disposed in a receiving hole formed in the cylinder head so as to constitute a part of the pressure supply passage,
The receiving hole has an opening on the mating surface side of the cylinder head with the cylinder block, and is formed so that a bottom wall thereof functions as the first valve seat forming portion, and between the cylinder block and the cylinder head. Is used as the second valve seat forming portion,
The variable capacity compressor according to claim 5. The rotary shaft is provided on one end side of the cylinder block, the front housing that forms the crank chamber in cooperation with the cylinder block, and the suction chamber provided on the other end side of the cylinder block. The discharge chamber is rotatably supported by a compressor body including a cylinder head having a compartment formed therein,
The valve assembly of the valve housing, the valve body, and the first valve seat forming portion is disposed in a receiving hole formed in the cylinder head so as to constitute a part of the pressure supply passage,
The accommodation hole has an opening on a mating surface side of the cylinder head with the cylinder block, and the valve assembly includes the accommodation hole so that the first valve seat forming portion faces the bottom wall of the accommodation hole. A plate-like member disposed between the cylinder block and the cylinder head is used as the second valve seat forming portion,
The variable capacity compressor according to claim 6 or 7. A biasing member disposed between the bottom wall of the receiving hole and the valve assembly, and biasing the valve assembly toward the second valve seat forming portion;
An elastic seal member disposed between the assembly and the inner peripheral wall of the accommodation hole;
The variable capacity compressor according to claim 10, comprising: The suction chamber is formed in the cylinder head;
The receiving hole opens into the suction chamber;
The valve assembly is disposed in the accommodation hole so that the third port is located in the suction chamber.
The variable capacity compressor according to any one of claims 9 to 11. The switching valve is
A first valve seat forming portion in which the first port and the first valve seat are formed and forming the first valve chamber together with the partition wall;
A second valve seat forming portion in which the second port and the second valve seat are formed and forming the second valve chamber together with the partition wall;
Including
The partition wall and the valve element are configured as a valve assembly, and the first valve part and the second valve part are formed by separate parts of the first valve part and the second valve part. And the relative position in the axial direction is adjustable.
The variable capacity compressor according to claim 4. The rotary shaft is provided on one end side of the cylinder block, the front housing that forms the crank chamber in cooperation with the cylinder block, and the suction chamber provided on the other end side of the cylinder block. The discharge chamber is rotatably supported by a compressor body including a cylinder head having a compartment formed therein,
The control valve is disposed in the cylinder head;
The switching valve is disposed in the cylinder block;
The variable capacity compressor according to any one of claims 1 to 4 and 13. The rotary shaft is provided on one end side of the cylinder block, the front housing that forms the crank chamber in cooperation with the cylinder block, and the suction chamber provided on the other end side of the cylinder block. The discharge chamber is rotatably supported by a compressor body including a cylinder head having a compartment formed therein,
The partition wall and the valve assembly of the valve body are disposed in an accommodation hole formed in the cylinder block so as to constitute a part of the pressure supply passage,
The receiving hole has an opening on a mating surface of the cylinder block with the cylinder head, and a bottom wall thereof is formed to function as the second valve seat forming portion, and is formed between the cylinder block and the cylinder head. The arranged plate-like member is used as the first valve seat forming portion,
The variable capacity compressor according to any one of claims 1 to 4 and 13.   The said throttle passage is formed so that the pressure supply path between the said control valve and the said switching valve and the said suction chamber may be connected via the inside of the said control valve. The variable capacity compressor as described in any one.   The variable displacement compressor according to claim 16, wherein the control valve has a valve mechanism configured to close the throttle passage when the pressure supply passage is fully opened.