JP2017218925A - Variable displacement compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable displacement compressor having a simple structure and an easy layout for a valve gear.SOLUTION: A variable displacement compressor 100 comprises a control valve 300 for opening or closing a valve hole arranged at a pressure supply passage communicating between a discharging chamber 142 and a crank chamber 140 to open or close the pressure supply passage; and a selector valve 350 arranged at the crank chamber 140 side from the valve hole of the control valve 300 at the pressure supply passage. The control valve 300 and the selector valve 350 are constituted as one valve gear 200. The selector valve 350 has a communication part communicated with a suction chamber 141. When the control valve 300 closes the pressure supply passage, a communication between the pressure supply passage between the valve hole of the control valve 300 and the selector valve 350 and a pressure supply passage 145a between the selector valve 350 and the crank chamber 140 is shut off and the pressure supply passage 145a between the selector valve 350 and the crank chamber 140 and the suction chamber 141 are communicated through the communicating part.SELECTED DRAWING: Figure 1

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. The variable capacity compressor is also required to be downsized like many other devices, and it is difficult to lay out the valve devices 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 displacement compressor, the discharge capacity of which is controlled by adjusting the pressure in the crank chamber, opens and closes the valve hole disposed in the pressure supply passage that connects the discharge chamber and the crank chamber. A control valve configured to open and close the pressure supply passage, and a switching valve provided closer to the crank chamber than the valve hole of the control valve in the pressure supply passage, the communication portion communicating with the suction chamber And when the control valve closes the pressure supply passage, a pressure supply passage between the valve hole of the control valve and the switching valve, and a pressure supply between the switching valve and the crank chamber The switching valve configured to block communication with the passage, and to connect the pressure supply passage between the switching valve and the crank chamber and the suction chamber via the communication portion. , The control valve and the switching And it is configured as a single valve device and.

  In the variable capacity compressor, the one valve device functions to control the supply of refrigerant to the crank chamber (the control valve) and to control the discharge of refrigerant from the crank chamber (the switching valve). And a function of preventing the back flow of the refrigerant from the crank chamber toward the control valve (the switching valve). 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 valve apparatus with which the control valve and switching valve of the said variable capacity compressor were integrated. It is the elements on larger scale of FIG. 2, and is a figure which shows the bellows which comprises the said control valve. It is a figure which shows the relationship between the coil energization amount in the said control valve, and setting pressure. It is sectional drawing which shows the small assembly of the said switching valve. It is sectional drawing which shows the assembly of the said small assembly of the said switching valve, and the said bellows. It is a figure for demonstrating a throttle path, (a) shows the state which the throttle path was closed, (b) and (c) show the state where the throttle path was opened. It is a figure for demonstrating operation | movement of the said variable capacity compressor. It is a figure for demonstrating operation | movement of the said variable capacity compressor. It is a figure for demonstrating operation | movement of the said variable capacity compressor. It is principal part sectional drawing which shows the structure of the valve apparatus which concerns on 2nd Embodiment. It is principal part sectional drawing which shows the structure of the valve apparatus which concerns on 3rd Embodiment.

  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 (not shown), a suction valve forming plate (not shown), a valve plate 103, a discharge valve forming plate (not shown), a head gasket (not shown). (Omitted), the cylinder heads 104 are sequentially connected and fastened by a plurality of through bolts 105 to form a compressor body. 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 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. . Specifically, the control valve 300 opens and closes the pressure supply passage 145 by opening and closing a valve hole 301c (described later) disposed in the pressure supply passage 145, and adjusts the opening of the valve hole 301c. The passage cross-sectional area of the pressure supply passage 145 is configured to be adjustable. The 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 accommodation hole 104b communicates with the suction chamber 141 through the communication path 104c and the communication path 104d.

  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. In the present embodiment, the switching valve 350 is configured integrally with the control valve 300 and is disposed in the accommodation hole 104b. That is, the control valve 300 and the switching valve 350 are configured as one valve device 200, and the valve device 200 is disposed in the accommodation hole 104b.

  In the present embodiment, the pressure supply passage 145 includes (a part of) the accommodation hole 104b, the communication passage 104f that communicates the discharge chamber 142 and the accommodation hole 104b, and the communication passage 104g that communicates the accommodation hole 104b and the crank chamber 140. Contains. The communication path 104 f is formed in the cylinder head 104. The communication passage 104g is formed in the cylinder head 104 and the cylinder block 101, and has a cylinder head side passage portion and a cylinder block side passage portion.

  In the following description, an area between the switching valve 350 and the crank chamber 140 in the pressure supply passage 145, that is, a passage portion mainly constituted by the communication passage 104g is referred to as “the switching valve 350 and the crank chamber 140. The pressure supply passage 145a between "is called.

  The switching valve 350 communicates the pressure supply passage 145a between the switching valve 350 and the crank chamber 140 with the crank chamber 140 and the suction chamber 141 via the switching valve 350 in conjunction with opening and closing of the control valve 300. The first pressure release passage 146a is configured to be switched. In the present embodiment, the first pressure release passage 146a includes a communication passage 104g, a switching valve 350, and a communication passage 104d.

  The configuration and operation of the switching valve 350 will be described in detail later, but the outline will be described as follows. The switching valve 350 has a communication portion (which corresponds to a third port 351a2 described later) that communicates with the suction chamber 141 via the communication passage 104d. When the control valve 300 is open, the switching valve 350 is an area between the valve hole 301c of the control valve 300 and the switching valve 350 in the pressure supply passage 145 (hereinafter referred to as “the valve hole 301c of the control valve 300 and the switching valve 350”). A pressure supply passage 145a between the switching valve 350 and the crank chamber 140. When the control valve 300 is closed and the pressure supply passage 145 is closed, the pressure supply passage between the valve hole 301c of the control valve 300 and the switching valve 350, and the pressure between the switching valve 350 and the crank chamber 140 are set. The communication with the supply passage 145a is blocked, and the pressure supply passage 145a between the switching valve 350 and the crank chamber 140 and the suction chamber 141 are communicated with each other through the communication portion. As a result, the pressure supply passage 145 a between the switching valve 350 and the crank chamber 140 is switched to the first pressure release passage 146 a between the switching valve 350 and the crank chamber 140.

  The crank chamber 140 is always in communication with the suction chamber 141 by a second pressure relief passage 146b that passes through the communication passage 101c, the space 101d, and the fixed throttle 103c formed in the valve plate 103. That is, the variable capacity compressor 100 is formed by the switching valve 350 when the control valve 300 closes the pressure supply passage as a pressure release passage communicating the crank chamber 140 and the suction chamber 141 (in other words, the switching valve A first pressure relief passage 146a (which is opened and closed by a valve 350) and a second pressure relief passage 146b which is always open. 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 between the valve hole 301 c of the control valve 300 and the switching valve 350 and the suction chamber 141 are configured to communicate with each other through a throttle passage 320 that passes through the control valve 300. The throttle passage 320 will be described in detail later.

  Since the pressure supply passage between the valve hole 301c of the control valve 300 and the switching valve 350 communicates with the suction chamber 141 by a throttle passage 320 passing through the control valve 300, the control valve 300 is closed and pressure supply is performed. When the passage 145 is closed, the pressure in the pressure supply passage between the valve hole 301 c of 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 blocks communication between the pressure supply passage between the valve hole 301 c of the control valve 300 and the switching valve 350 and the pressure supply passage 145 a between the switching valve 350 and the crank chamber 140. The reverse flow of the refrigerant from the crank chamber 140 side toward the control valve 300 is prevented. The switching valve 350 switches the pressure supply passage 145 a between the switching valve 350 and the crank chamber 140 to a first pressure release passage 146 a between the switching valve 350 and the crank chamber 140. 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 146b, so that the passage sectional area of the pressure release passage is maximized. Become. 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 between the valve hole 301c of the control valve 300 and the switching valve 350 increases. When the pressure in the pressure supply passage between the valve hole 301 c of the control valve 300 and the switching valve 350 becomes higher than the pressure in the crank chamber 140, the switching valve 350 is switched between the valve hole 301 c of the control valve 300 and the switching valve 350. And the pressure supply passage 145a between the switching valve 350 and the crank chamber 140 are communicated with each other. That is, the switching valve 350 switches the first pressure release passage 146 a between the switching valve 350 and the crank chamber 140 to the pressure supply passage 145 a between the switching valve 350 and the crank chamber 140. As a result, the pressure release passage is configured by only the second pressure release passage 146b, and the passage sectional area of the pressure release passage is minimized. Therefore, while the refrigerant in the discharge chamber 142 is supplied to the crank chamber 140 via the pressure supply passage 145, 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 to do. Therefore, 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 (that is, the variable displacement compressor 100). Is in the discharge capacity control state).

  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.

“Configuration of Valve Device 200 (Control Valve 300 and Switching Valve 350)”
FIG. 2 is a cross-sectional view showing the valve device 200 in which the control valve 300 and the switching valve 350 are integrated. As described above, the valve device 200 is disposed in the accommodation hole 104 b formed in the cylinder head 104. Hereinafter, the control valve 300 and the switching valve 350 will be described in this order.

"Control valve 300"
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 is configured to communicate with the crank chamber 140 via the switching valve 350. The second pressure sensing chamber 307 communicates with the suction chamber 141 through a communication hole 301 a formed in the valve housing 301, a receiving hole 104 b, and a communication path 104 c formed in the cylinder head 104. The valve chamber 303 communicates with the discharge chamber 142 via a communication hole 301 b formed in the valve housing 301, a receiving hole 104 b, and a communication path 104 f formed in the cylinder head 104. 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.

  In the first pressure sensing chamber 302, a bellows 305 is disposed as a pressure sensing displacement member (pressure sensing means). The bellows 305 is evacuated and contains a biasing member. The bellows 305 is configured to be displaced (specifically, contracted and expanded) in the axial direction of the valve housing 301 in response to the pressure in the first pressure sensing chamber 302, that is, the pressure in the crank chamber 140. .

  FIG. 3 is a partially enlarged view of FIG. 2 and shows the configuration of the bellows 305. As shown in FIG. 3, the bellows 305 includes a bellows-shaped bellows main body 305a, a first end member 305b provided on one end of the bellows main body 305a, and the other end of the bellows main body 305a. A second end member 305c, and a spring (biasing member) 305d that biases the first end member 305b and the second end member 305c away from each other. The first end member 305b and the second end member 305c are fixed to the bellows body 305a, for example, by welding.

  The first end member 305b includes a closing portion 305b1 that closes the one end side of the bellows body 305a, and a stopper 305b2 that protrudes from the closing portion 305b1 toward the inside of the bellows body 305a. The second end member 305c includes a closing portion 305c1 that closes the other end of the bellows body 305a, and a stopper 305c2 that protrudes from the closing portion 305c1 toward the inside of the bellows body 305a. The amount of contraction in the axial direction of the bellows 305 (the bellows body 305a) is regulated by the stopper 305b2 of the first end member 305b and the stopper 305c2 of the second end member 305c coming into contact with each other.

  The second end member 305c has a cylindrical portion 305c3 that protrudes from the closing portion 305c1 to the side opposite to the stopper 305c2. As will be described later, the cylindrical portion 305c3 serves as a component of the switching valve 350, forms the first valve chamber 351c of the switching valve 350, and configures the first valve seat 305c31 and the first port 352c32.

  Returning to FIG. 2, 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 is formed to 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. The end portion (tip end) of the connecting portion 306 is disposed so as to be able to contact the bellows 305, and the connecting portion 306 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 321 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 (upper end) of the valve body 304, and the other end (upper end) of the solenoid rod 309 is fitted (press-fit) into a through hole formed in the movable core 308. ) 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 nonmagnetic material such as a 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), and a first pressure sensing pressure. 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)

  Therefore, 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), the connecting body of the bellows 305, the connecting portion 306, and the valve body 304 has a discharge capacity. In order to increase the pressure, the opening of the valve hole 301c, that is, the opening (passage cross-sectional area) of the pressure supply passage 145 is reduced to lower the pressure of the crank chamber 140, and the pressure of the suction chamber 141 is lower than the set pressure. In order to decrease the discharge capacity, the opening of the valve hole 301c, that is, the opening of the pressure supply passage 145 (passage cross-sectional area) is increased to increase the pressure in the crank chamber 140. 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.

  FIG. 4 is a diagram showing the relationship between the coil energization amount (current I) and the set pressure. Since the electromagnetic force of the mold coil 314 acts on the valve body 304 via the solenoid rod 309 in the valve closing direction, the force in the direction to reduce the opening of the pressure supply passage 145 when the energization amount to the mold coil 314 increases. Increases, and the setting 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 conditioner system is in operation, that is, when the variable capacity compressor 100 is in operation, the control device adjusts the amount of current supplied to the mold coil 314 based on the air conditioning setting (set temperature, etc.) in the air conditioner system and the external environment. To do. 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 to the maximum by the forced release spring 311 and the discharge capacity of the variable capacity compressor 100 is controlled to the minimum state.

"Switching valve 350"
The configuration of the switching valve 350 will be described with reference to FIGS. FIG. 5 is a cross-sectional view showing a subassembly 350A of the switching valve 350, and FIG. 6 is a cross-sectional view showing an assembly 350B of the subassembly 350A and bellows 305 of the switching valve 350.

  In the present embodiment, the switching valve 350 includes a cylindrical valve housing 351, a valve body 352 housed in the valve housing 351, a cylindrical portion 305c3 of a bellows 305 press-fitted to one end of the valve housing 351, a valve The valve seat forming portion 353 is press-fitted to the other end of the housing 351 (see FIG. 6). The valve body 352 includes a first valve portion 352a disposed on the 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 352. It has a shaft portion 352c that connects the valve portion 352b (see FIG. 5). As described above, the cylindrical portion 305c3 is formed on the second end member 305c provided on the other end side of the bellows body 305a. In addition, the part except the cylindrical part 305c3 in the switching valve 350 comprises the small assembly 350A (refer FIG. 5).

  The valve housing 351 includes a peripheral wall 351a and a partition wall 351b disposed at an intermediate position in the axial direction within the peripheral wall 351a. A fitting hole 351a1 into which the cylindrical portion 305c3 is press-fitted is formed on one end side of the peripheral wall 351a, and a through hole (insertion hole) 351b1 penetrating in the axial direction is formed in the partition wall 351b. Has been.

  The interior of the valve housing 351 is partitioned into a first valve chamber 351c and a second valve chamber 351d by a partition wall 351b. More specifically, the first valve chamber 351c is formed by the end surface of the cylindrical portion 305c3, the peripheral wall 351a, and the partition wall 351b, and the second valve chamber 351d is formed by the valve seat forming portion 353, the peripheral wall 351a, and the partition wall 351b. Has been. And the 1st valve part 352a of the valve body 352 is arrange | positioned in the 1st valve chamber 351c, the 2nd valve part 352b of the valve body 352 is arrange | positioned in the 2nd valve chamber 351d, and the through-hole (insertion hole) of the partition wall 351b A shaft portion 352c of the valve body 352 is inserted into the shaft 351b1.

  The end surface of the cylindrical portion 305c3 constitutes a first valve seat 305c31 in which the one end surface 352a1 of the first valve portion 352a of the valve body 352 contacts and separates, and the internal space of the cylindrical portion 305c3 opens to the inside of the first valve seat 305c31. The first port 352c32 is configured. That is, the first valve chamber 351c has a first port 352c32 and a first valve seat 305c31. The first port 352c32 is connected to the first pressure sensing chamber 302, that is, the pressure supply passage between the valve hole 301c of the control valve 300 and the switching valve 350 through a communication hole 305c33 formed in the peripheral wall of the cylindrical portion 305c3. It communicates (see FIG. 2). The first port 305c32 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 305c31.

  In the valve seat forming portion 353, a second valve seat 353a with which one end surface 352b1 of the second valve portion 352b is separated from and in contact with each other, and a second port 353b is formed inside the second valve seat 353a. That is, the second valve chamber 351d has a second port 353b and a second valve seat 353a. The second port 353b communicates with a pressure supply passage 145a between the switching valve 350 and the crank chamber 140. The second port 353b is opened and closed by the one end surface 352b1 of the second valve portion 352b being separated from and contacting the second valve seat 353a.

  In addition, a third port 351a2 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 351a2 in addition to the second port 353b and the second valve seat 353a.

  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 305c31, and the valve body 352 is disposed in the second valve chamber 351d and separated from the second valve seat 353a. 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 one end surface 352b1 of the second valve portion 352b is formed in the second valve seat 353a. 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.

  Here, a specific method of assembling the small assembly 350A of the switching valve 350 will be described. First, the integrally formed product of the first valve portion 352a and the shaft portion 352c is inserted into the insertion hole 351b1 formed in the partition wall 351b so that the one end side (first valve) of the valve housing 351 is formed. Inserted into the valve housing 351 from the chamber 351c) side.

  Next, with the shaft portion 352c inserted into the insertion hole 351b1, the tip of the shaft portion 352c is aligned with the through hole of the second valve portion 352b, and the shaft portion 352c is aligned with the through hole of the second valve portion 352b. Temporarily press fit.

  Next, the valve seat forming portion 353 is press-fitted and fixed to the other end of the valve housing 351.

  Finally, with the one end surface 352b1 of the second valve portion 352b in contact with the second valve seat 353a of the valve seat forming portion 353, 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 one end surface 352a1 of the first valve part 352a is pressed until it abuts, and the axial press-fitting position of the shaft part 352c with respect to the through hole of the second valve part 352b is adjusted.

  The cylindrical portion of the bellows 305 is inserted into the opening on the first valve chamber 351c side of the small assembly 350A assembled as described above, that is, the fitting hole 351a1 formed on the one end side of the peripheral wall 351a of the valve housing 351. The switching valve 350 is completed by press-fitting 305c3.

  Here, the press-fitting of the cylindrical portion 305c3 into the small assembly 350A (the fitting hole 351a1 thereof) may be performed before the second end member 305c is integrated with the bellows body 305a, or the second end. It may be performed after the member 305c is integrated with the bellows body 305a. In the former case, the bellows 305 is assembled after the cylindrical portion 305c3 is press-fitted and fixed to the small assembly 350A to form an assembly 350B of the bellows 305 and the switching valve 350. In the latter case, the cylindrical portion 305c3 is assembled after the bellows 305 is assembled. Is press-fitted and fixed to the small assembly 350A to form an assembly 350B of the bellows 305 and the switching valve 350.

  Thereafter, the one end side of the valve housing 351 of the switching valve 350 is press-fitted and fixed to the one end (lower end) of the valve housing 301 of the control valve 300, whereby the valve housing 301 of the control valve 300 and the valve housing 351 of the switching valve 350 are fixed. Are connected to complete the valve device 200 in which the control valve 300 and the switching valve 350 are integrated (see FIG. 2).

  With reference to FIG.5 and FIG.6, the structure of the valve body 352 of the switching valve 350 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 305c31 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. Have and be 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 353a. The one end surface 352b1 which contacts and separates is comprised.

  Further, the valve body 352 has an internal passage 352d. The internal passage 352d includes a first passage 352d1 extending in the axial direction through the first valve portion 352a and the shaft portion 352c, and a second passage 352d2 connected to the first passage 352d1. One end of the first passage 352d1 opens at the distal 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 305c31 and the one end surface 352b1 of the second valve portion 352b contacts the second valve seat 353a, the second port 353b and the third port 351a2 are provided. The first port 305c32 and the second port 353b 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 305c31 and the first port 305c32 is closed, the one end surface 352b1 of the second valve portion 352b is separated from the second valve seat 353a. The 2 port 353b and the third port 351a2 communicate with each other.

  Here, when the one end surface 352b1 of the second valve portion 352b contacts the second valve seat 353a, the other end surface 352a2 of the first valve portion 352a is the one end surface of the partition wall 351b (the surface on the first valve chamber 351c side). ) Abuts on 351b2. For this reason, the communication through the insertion hole 351b1 between the first valve chamber 351c and the second valve chamber 351d is blocked, and thereby the flow through the insertion hole 351b1 from the first valve chamber 351c to the second valve chamber 351d. Is cut off.

  In addition to the second passage 352d2, the internal passage 352d further includes a third passage 352d3 that communicates the first passage 352d1 and the first valve chamber 351c. 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 305c32, the retention of the said foreign material etc. which inhibits the movement of the valve body 352 is prevented.

  As described above, the switching valve 350 closes the pressure supply passage 145 by closing the first port 305c32 with the end face 352a1 of the first valve portion 352a coming into contact with the first valve seat 305c31 by the movement of the valve body 352. At this time, one end surface 352b1 of the second valve portion 352b is separated from the second valve seat 353a, and the second port 353b and the third port 351a2 communicate with each other. As a result, the pressure supply passage 145a between the switching valve 350 (second port 353b) and the crank chamber 140 communicates with the suction chamber 141 via the third port 351a2, and the pressure supply passage 145a is connected to the switching valve 350. The first pressure release passage 146a between the (second port 353b) and the crank chamber 140 is switched.

  On the other hand, the switching valve 350 opens the pressure supply passage 145 by opening the first port 305c32 by separating the one end surface 352a1 of the first valve portion 352a from the first valve seat 305c31 by the movement of the valve body 352. At this time, one end surface 352b1 of the second valve portion 352b abuts on the second valve seat 353a to block communication between the second port 353b and the third port 351a2, and the first port 305c32 and the second port 353b Communicates via the internal passage 352d of the valve body 352. As a result, the first pressure release passage 146a between the switching valve 350 (second port 353b) and the crank chamber 140 becomes the pressure supply passage 145a between the switching valve 350 (second port 353b) and the crank chamber 140. Switched (returned).

"Throttle passage 320"
The throttle passage 320 will be described with reference to FIG. FIG. 7A shows a state where the throttle passage 320 is closed, and FIGS. 7B and 7C show a state where the throttle passage 320 is opened. 7A corresponds to FIG. 8 in “Operation of the variable capacity compressor 100” described later, FIG. 7B corresponds to FIG. 9, and FIG. 7C corresponds to FIG. Corresponding. As described above, the throttle passage 320 communicates the suction chamber 141 with the pressure supply passage between the valve hole 301 c of the control valve 300 and the switching valve 350 via the inside of the control valve 300. The throttle passage 320 is configured to supply the pressure between the valve hole 301c of the control valve 300 and the switching valve 350 when the valve body 304 of the control valve 300 closes the valve hole 301c (when the pressure supply passage 145 is closed). The refrigerant in the passage has a function of escaping to the suction chamber 141 side. Here, the pressure supply passage between the valve hole 301c of the control valve 300 and the switching valve 350 is a region constituted by the first pressure sensing chamber 302, the communication hole 305c33, and the first port 305c32.

  As shown in FIG. 7B, the throttle passage 320 is formed in the communication hole 304 a that forms the inner space of the valve body 304 and the connection portion 306 of the control valve 300, and the first pressure sensing chamber. 302, the communication hole 306a that communicates with the communication hole 304a, the communication hole 309a that is press-fitted into the valve body 304, is formed inside the press-fitting portion of the solenoid rod 309, and is connected to the communication hole 304a; A cylindrical recess 304b formed on the other end (upper end) side, a communication hole 309b formed in a portion of the solenoid rod 309 located in the recess 304b and communicating between the communication hole 309a and the recess 304b, a second A pressure sensing chamber 307, a communication hole 301a 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 included.

  As shown in FIG. 7A, the surface of the valve body 304 on the other end side (that is, an annular surface around the recess 304 b, hereinafter referred to as “the other end surface of the valve body 304”) 304 c is fixed core 310. When the first pressure sensitive chamber 302 and the suction chamber 141 are in contact with each other, the throttle passage 320 is closed. On the other hand, when the other end surface (the annular surface) 304 c of the valve body 304 is separated from the end surface of the fixed core 310, the throttle passage 320 is opened, and the first pressure sensing chamber 302 and the suction chamber 141 are connected via the throttle passage 320. Communicate. Here, when the other end surface 304c of the valve body 304 is separated from the other end of the fixed core 310, there are a case shown in FIG. 7B and a case shown in FIG. 7C. 7C shows a case where the valve body 304 of the control valve 300 opens the valve hole 301c and the variable displacement compressor 100 is in the discharge capacity control state.

  When the first pressure sensing chamber 302 is in communication with the suction chamber 141 via the throttle passage 320 in the discharge capacity control state, the refrigerant (discharge gas) in the discharge chamber 142 to be supplied to the crank chamber 140. A part of the refrigerant flows directly into the suction chamber 141 via the throttle passage 320, and the efficiency of the variable capacity compressor 100 is deteriorated. For this reason, in this embodiment, the communication hole 309b is formed so as to serve as a throttle portion. The passage cross-sectional area of the communication hole 309b (throttle portion) is set as small as possible in consideration of the refrigerant discharge (outflow) property from the first pressure sensing chamber 302. The throttle portion is not limited to the communication hole 309b, and may be provided at any one of the communication hole 306a, the communication hole 304a, and 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 forced release spring 311 and the opening degree of the valve hole 301c is maximized. That is, the pressure supply passage 145 is opened to the maximum. At this time, as shown in FIG. 7A, the other end surface 304c of the valve body 304 abuts on the end surface of the fixed core 310, and the throttle passage 320 is closed. On the other hand, when a current that causes an electromagnetic force exceeding the urging force of the forced release spring 311 to flow is applied to the mold coil 314, the one end of the valve body 304 moves in a direction to close the valve hole 301c, and FIG. ), (C), the other end surface 304c of the valve body 304 is separated from the end surface of the fixed core 310, and the throttle passage 320 is opened.

  Therefore, in this embodiment, the other end surface 304c of the valve body 304 of the control valve 300 and the fixed core 310 (the end surface of the fixed core 310) constitute valve means (valve mechanism) for opening and closing the throttle passage 320. The restriction passage 320 is closed only when the mold coil 314 is demagnetized and the variable capacity compressor 100 is in an inoperative state (OFF), and the mold coil 314 is excited and the variable capacity compressor 100 is operated. In the state (ON), the first pressure sensitive chamber 302 and the suction chamber 141 communicate with each other in an open state (open state).

"Operation of switching valve 350"
Hereinafter, the operation of the switching valve 350 will be described.
One end surface of the valve body 352 (one end surface 352a1 of the first valve portion 352a) receives the pressure (pressure of the first pressure sensing chamber 302) Pc ′ on the first port 305c32a 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 353b side (pressure of the pressure supply passage 145a), that is, the pressure Pc of the crank chamber 140. In addition, since the second valve chamber 351d communicates with the suction chamber 141 via the third port 351a2, the pressure Ps of the suction chamber 141 acts on the valve body 352.

  Here, S1 is 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 305c31, and the one end surface 352b1 of the second valve portion 352b contacts the second valve seat 353a. 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 305c31, the pressure Pc of the crank chamber 140 is the pressure Ps of the suction chamber 141. Therefore, one end surface 352a1 of the first valve portion 352a. Is the condition for separating the first valve seat 305c31 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 side of the second valve portion 352b when the refrigerant flow from the second port 353b side collides.

  Therefore, the control valve 300 opens the valve hole 301c (that is, opens the pressure supply passage 145) to supply the refrigerant (discharge gas) in the discharge chamber 142 to the first pressure sensing chamber 302, and the first port 305c32a side. By increasing the pressure Pc ′, the one end surface 352a1 of the first valve portion 352a can be separated from the first valve seat 305c31, and the one end surface 352b1 of the second valve portion 352b can be brought into contact with the second valve seat 353a. .

  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 353a 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 by dynamic pressure that acts on the one end surface 352a1 side of the first valve portion 352a when the refrigerant flow from the first port 305c32 side 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, so that the force due to the static pressure difference (Pc′−Pc) and the force F2 due to the dynamic pressure are F2. 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 353a.

  The condition for separating the one end surface 352b1 of the second valve portion 352b from the second valve seat 353a may be that the left side of the expression (4 ′) is negative.

  When the control valve 300 closes the valve hole 301c (that is, closes the pressure supply passage 145), the refrigerant (discharge gas) in the discharge chamber 142 is not supplied to the first pressure sensing chamber 302, so F2 = 0. Further, the refrigerant in the first pressure sensing chamber 302 flows out (is discharged) to the suction chamber 141 via 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 353a, and the one end surface 352a1 of the first valve portion 352a is the first valve seat. It abuts on 305c31.

  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 353a, the one end surface 352b1 of the second valve portion 352b is the first one. The condition for separating from the two valve seats 353a 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 dynamic pressure acting on the end surface (closed end) of the internal passage 352d when the refrigerant flowing back through the internal passage 352d (first passage 352d1) collides.

  The refrigerant in the first pressure sensing chamber 302 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 352a is in contact with the first valve seat 305c31, being separated from the seat 353a.

  Thus, when the control valve 300 opens the valve hole 301c and opens the pressure supply passage 145, the switching valve 350 has the pressure Pc ′ on the first port 305c32 side that acts on the one end surface 352a1 of the first valve portion 352a. The valve body 352 is moved using the ascending position so that the one end surface 352a1 of the first valve portion 352a is separated from the first valve seat 305c31 and the one end surface 352b1 of the second valve portion 352b is in contact with the second valve seat 353a. Let Thereby, the communication between the second port 353b and the third port 351a2 is blocked, and the first port 305c32a and the second port 353b communicate with each other via the internal passage 352d. As a result, the first pressure release passage 146a between the switching valve 350 (second port 353b) and the crank chamber 140 becomes the pressure supply passage 145a between the switching valve 350 (second port 353b) and the crank chamber 140. Can be switched.

  In addition, when the control valve 300 closes the valve hole 301c and closes the pressure supply passage 145, the switching valve 350 reduces the pressure Pc ′ on the first port 305c32 side that acts on the one end surface 352a1 of the first valve portion 352a. The valve body 352 is moved by utilizing it so that the one end surface 352b1 of the second valve portion 352b is separated from the second valve seat 353a and the one end surface 352a1 of the first valve portion 352a is brought into contact with the first valve seat 305c31. As a result, the first port 305c32 is closed and the second port 353b and the third port 351a2 communicate with each other. As a result, the pressure supply passage 145a between the switching valve 350 (second port 353b) and the crank chamber 140 becomes the first pressure release passage 146a between the switching valve 350 (second port 353b) and the crank chamber 140. Can be switched. 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.

"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 power supply to the mold coil 314 of the control valve 300 is turned off. In this case, in the control valve 300, the one end face of the valve body 304 is separated from the periphery of the valve hole 301c by the urging force of the forced release spring 311, and the opening degree of the valve hole 301c is maximized. That is, the control valve 300 opens the pressure supply passage 145 to the maximum (the cross-sectional area of the passage is maximized). At this time, the other end surface 304c of the valve body 304 abuts on the end surface of the fixed core 310, and the throttle passage 320 is closed.

  In the switching valve 350, the one end surface 352b1 of the second valve portion 352b abuts on the second valve seat 353a, and the communication between the second port 353b and the third port 351a2 is blocked, and the first port 305c32 and the second port 352c32 The port 353b communicates with 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 It is the minimum.

  When the engine of the vehicle starts in the above state and the drive shaft 110 of the variable capacity compressor 100 rotates, the discharge check valve 200 closes the discharge passage and the throttle passage 320 is closed. All of the compressed and discharged refrigerant (refrigerant in the discharge chamber 142) is supplied to the crank chamber 140 via the pressure supply passage 145 (see the arrow in FIG. 8). 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 other end surface 304c of the valve body 304 is separated from the end surface of the fixed core 310. The throttle passage 320 opens. In this case, the compressed and discharged refrigerant is not supplied to the first pressure sensing chamber 302 of the control valve 300, and the refrigerant in the pressure supply passage between the valve hole 301c of the control valve 300 and the switching valve 350 is not Then, it flows into the suction chamber 141 through the throttle passage 320. As a result, the pressure in the pressure supply passage between the valve hole 301 c of the control valve 300 and the switching valve 350 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 353b side toward the first valve chamber 351c via the internal passage 352d. The refrigerant that flows (backflows) through the internal passage 352d generates dynamic pressure that moves the valve body 352 toward the first valve seat 305c31.

  For this reason, the valve body 352 of the switching valve 350 has a dynamic pressure generated by the force due to the difference (static pressure difference) between the pressure on the second port 353b side and the pressure on the first port 305c32 side, and the refrigerant flowing backward in the internal passage 352d. The first valve seat 305c31 moves toward the first valve seat 305c31 side, the one end surface 352a1 of the first valve portion 352a contacts the first valve seat 305c31, closes the first port 305c32, and the second port 353b The 3 port 351a2 is connected. That is, the switching valve 350 switches the pressure supply passage 145 a between the switching valve 350 and the crank chamber 140 to the first pressure release passage 146 a between the switching valve 350 and the crank chamber 140. 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 (backflows) in the internal passage 352d. In this case, the density of the refrigerant becomes significantly larger than that in the gas state, the dynamic pressure increases, and the valve body 352 can be reliably moved in the direction toward the first valve seat 305c31.

  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, and the compressed and discharged refrigerant is transferred to the first pressure sensing chamber. 302 is supplied. Thereby, in the switching valve 350, the pressure on the first port 305c32 side increases, the pressure on the first port 305c32 acting on the valve body 352 exceeds the pressure on the suction chamber 141 acting on the opposite side, and the first One end surface 352a1 of the valve portion 352a is separated from the first valve seat 305c31, and one end surface 352b1 of the second valve portion 352b is in contact with the second valve seat 353a. That is, the switching valve 350 switches the first pressure release passage 146 a between the switching valve 350 and the crank chamber 140 to the pressure supply passage 145 a between the switching valve 350 and the crank chamber 140. Therefore, 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 between the crank chamber 140 and the suction chamber 141 is minimized. (See FIG. 10).

  Therefore, the pressure in the crank chamber 140 increases according to 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 (discharge capacity) of the piston 136 decreases. To do. That is, the variable capacity compressor 100 is in the discharge capacity control state.

  As described above, in the present embodiment, the switching valve 35 includes the pressure supply passage between the valve hole 301c of the control valve 300 and the switching valve 350 when the control valve 300 closes the pressure supply passage 145. The communication with the pressure supply passage 145a between the switching valve 350 and the crank chamber 140 is shut off, and the communication portion (third port) connects the pressure supply passage 145a between the switching valve 350 and the crank chamber 140 and the suction chamber 141. 351a2). 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 is larger than when the pressure supply passage 145 is open. Become (becomes the 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 a reverse flow of the refrigerant from the crank chamber 140 toward the control valve 300. Furthermore, in this embodiment, the switching valve 350 is integrated with the control valve 300 having a function of controlling the supply of the refrigerant to the crank chamber 140 and configured as one valve device 200. For this reason, the structure of the variable capacity compressor 100 is simplified, and the layout of the valve device in the variable capacity compressor 100 is facilitated.

  In addition, when the control valve 300 closes the pressure supply passage, the switching valve 350 is connected to the second port in addition to the force due to the difference (static pressure difference) between the pressure on the second port 353b side and the pressure on the first port 305c32 side. The valve body 352 is moved using the force of dynamic pressure caused by the flow of refrigerant (reverse flow) toward the first valve chamber 351c from the 353b side 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 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 sucked into the suction chamber 141. Can be discharged quickly.

[Second Embodiment]
FIG. 11 is a cross-sectional view of the main part showing the configuration of the valve device 200B according to the second embodiment. In the above-described embodiment, the cylindrical portion 305c3 formed in the second end member 305c of the bellows 305 is press-fitted into the fitting hole 351a1 of the valve housing 351 of the switching valve 350. However, the present invention is not limited to this, and a slight gap may be formed between the cylindrical portion 305c3 and the fitting hole 351a1. In this case, as shown in FIG. 11, the bellows 305 is connected to the switching valve 350 so that the front end surface of the cylindrical portion 305c3 (periphery of the first valve seat 305c31) comes into contact with the bottom wall 351a3 of the fitting hole 351a1. It is preferable that a biasing member (compression coil spring or the like) 315 that biases toward the side is provided between the first end member 305 b of the bellows 305 and the wall portion of the first pressure sensing chamber 302. The biasing member 315 is attached to the valve housing 301 of the control valve 300, for example. In this way, it is not necessary to press-fit the cylindrical portion 305c3 into the fitting hole 351a1, and it is easy to connect the bellows 305 and the cylindrical portion 305c3, that is, to form the assembly 350B of the small assembly 350A and the bellows 305.

[Third Embodiment]
FIG. 12 is a cross-sectional view of a main part showing a configuration of a valve device 200C according to the third embodiment. In the above-described embodiment, the first valve seat 305c31 and the first port 305c32 of the switching valve 350 are formed on the second end member 305c of the bellows 305 that is a component of the control valve 300. However, the present invention is not limited to this, and the switching valve 350 itself may have the first valve seat and the first port. In this case, as shown in FIG. 12, for example, the switching valve 350 is formed with a first valve seat 354 a, a first port 354 b, and a communication hole 354 c that communicates the first port 354 b with the first pressure sensing chamber 302. The valve seat forming portion 354 is configured to be press-fitted into the fitting hole 351a1.

  The bellows 305 is connected to the switching valve 350 in a state where the second end member 305c is in contact with a contact portion 354d provided on the opposite side of the valve seat forming portion 354 from the first valve seat 354a. Preferably, a biasing member that biases the bellows 305 toward the switching valve 350 in order to ensure that the second end member 305c of the bellows 305 contacts the contact portion 354d of the valve seat forming portion 354 of the switching valve 350. (Compression coil spring or the like) 315 is provided. The biasing member 315 is attached to the valve housing 301 of the control valve 300, for example. In this way, the bellows 305 and the switching valve 350 can be easily connected as in the second embodiment, and a conventional bellows can be used as the bellows 305. Further, since the switching valve 350 constitutes an independent assembly, it is possible to check the operation of the switching valve 350 alone.

  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.

  The cylindrical portion 305c3 may be formed integrally with the peripheral wall 351a of the valve housing 351 of the switching valve 350. Alternatively, the entire second end member 305 c of the bellows 305 may be integrally formed with the peripheral wall 351 a of the valve housing 351 of the switching valve 350.

  In the switching valve 350, the peripheral wall 351a and the partition wall 351b of the valve housing 351 may be configured as separate members. In addition, a groove or a throttle passage is formed on one end surface 352b1 of the second valve portion 352b, and when the one end surface 352b1 of the second valve portion 352b contacts the second valve seat 353a, the second port 353b and the third port The communication with the port 351a2 may be configured not to be completely blocked. Moreover, it is good also as a structure to which slight leak is accept | permitted when the one end surface 352a1 of the 1st valve part 352a contact | abuts to the 1st valve seat 305c31. Further, when the other end surface 352a2 of the first valve portion 352a comes into contact with one end surface 351b2 of the partition wall 351b of the valve housing 351, a slight flow from the first valve chamber 351c to the second valve chamber 351d is allowed. May be configured.

  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, 104b ... Accommodating hole, 110 ... Drive shaft, 140 ... Crank chamber, 141 ... Suction chamber, 142 ... Discharge chamber, 145 (145a) ) ... pressure supply passage, 146a, 146b ... pressure release passage, 300 ... control valve, 301 ... valve housing (control valve housing), 301c ... valve hole, 304 ... valve body (control valve valve body), 305 ... bellows (feel) Pressure displacement member), 305c3 ... cylindrical portion, 305c31 ... first valve seat, 305c32 ... first port, 350 ... switching valve, 351 ... valve housing (switching valve housing), 351a ... peripheral wall, 351a2 ... third port, 351b ... Partition wall, 351b1 ... insertion hole, 351c ... first valve chamber, 351d ... second valve chamber, 352 ... valve body (switching valve valve body), 35 a ... first valve portion, 352b ... second valve portion, 352c ... shank, 352d ... internal passage, 353 ... valve seat forming portion, 353a ... second valve seat, 353b ... second port

Claims (9)

A variable capacity compressor whose discharge capacity is controlled by pressure regulation in the crank chamber,
A control valve configured to open and close the pressure supply passage by opening and closing a valve hole disposed in the pressure supply passage communicating the discharge chamber and the crank chamber;
A switching valve provided on the crank chamber side with respect to the valve hole of the control valve in the pressure supply passage, having a communication portion communicating with a suction chamber, and the control valve closed the pressure supply passage The communication between the pressure supply passage between the valve hole of the control valve and the switching valve and the pressure supply passage between the switching valve and the crank chamber is interrupted, and the switching valve and the crank The switching valve configured to communicate the pressure supply passage between the chamber and the suction chamber via the communication portion;
Including
The control valve and the switching valve are configured as one valve device,
Variable capacity compressor.   2. The variable displacement compression according to claim 1, comprising a pressure supply passage between the valve hole of the control valve and the switching valve, and a throttle passage communicating the suction chamber via the inside of the control valve. Machine.   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 3. 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 with a case where a supply passage is opened. The switching valve is
A first port communicating with the pressure supply passage between the valve hole of the control valve and the switching valve and a first valve chamber having 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 contacting / disconnecting with the first valve seat; a second valve portion disposed in the second valve chamber and contacting / disconnecting with the second valve seat; and the second valve portion. A valve body having an internal passage for communicating the second port and the first valve chamber when in contact with the second valve seat;
Including
When the control valve closes the pressure supply passage, the first valve is brought into contact with the first valve seat by utilizing the pressure drop on the first port side to close the first port and The second valve portion is separated from the second valve seat to communicate the second port and the third port, whereby a pressure supply passage between the valve hole of the control valve and the switching valve, Shutting off the communication with the pressure supply passage between the switching valve and the crank chamber, and communicating the pressure supply passage between the switching valve and the crank chamber with the suction chamber, Maximize the cross-sectional area of the pressure relief passage that communicates 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 using the pressure increase on the first port side to open the first port and the first port. Two valve seat portions are brought into contact with the second valve seat so that the communication between the second port and the third port is blocked or nearly closed, and the first port and the second port are connected to the internal passage. Thereby communicating the pressure supply passage between the valve hole of the control valve and the switching valve and the pressure supply passage between the switching valve and the crank chamber, and Configured to minimize the cross-sectional area of the pressure relief passage,
The variable capacity compressor as described in any one of Claims 1-3.   When the control valve closes the pressure supply passage, the switching valve reduces the pressure on the first port side and the refrigerant flowing from the second port side to the first valve chamber via the internal passage. The first port is brought into contact with the first valve seat by utilizing dynamic pressure due to the flow to close the first port, and the second valve portion is separated from the second valve seat to the second port. The variable capacity compressor according to claim 4, wherein the variable capacity compressor is configured to communicate with the third port. 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 4 or 5. A part of the first valve chamber of the switching valve is formed by components of the control valve,
The first port and the first valve seat are formed in the component of the control valve;
The variable capacity compressor according to any one of claims 4 to 6. The control valve is
One end opens and closes the valve hole, and the other end is a control valve valve body on which the pressure of the suction chamber acts,
A drive unit that is disposed on the other end side of the control valve valve body, and causes a biasing force in the direction of closing the valve hole to act on the control valve valve body when a current flows through a coil;
When the pressure in the suction chamber is higher than a set pressure that is connected to the one end of the control valve body through a connecting portion and is set by the current flowing in the coil, the opening of the valve hole is reduced, and the setting is performed. A pressure-sensitive displacement member that operates to increase the opening of the valve hole when the pressure in the suction chamber is lower than the pressure; and
Have
The component of the control valve is the pressure-sensitive displacement member;
The variable capacity compressor according to claim 7.   The control valve has a control valve housing that houses the control valve valve body and the pressure-sensitive displacement member, and the switching valve has a switching valve housing that houses the valve body, and the control valve housing and the control valve housing The variable capacity compressor according to claim 8, wherein the valve device is configured by being connected to a switching valve housing.