JP2017129042A - Capacity control valve of variable displacement compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the discharge performance of a liquid refrigerant from a control pressure chamber, such as a crank chamber.SOLUTION: A capacity control valve 300 includes: a first valve part 321b for adjusting an opening of a first valve hole 323b partially constituting pressure supply paths 145A, 145B connecting a discharge chamber 142 and a crank chamber 140; and a second valve part 321c for adjusting an opening of a second valve hole 311b partially constituting pressure release paths 147, 145B connecting the crank chamber 140 and a suction chamber 141. The first valve part 321b and the second valve part 321c are formed integrally with one valve body 321 to perform an opening/closing operation opposite to each other. Here, when the first valve part 321b is fully closed, the second valve part 321c is subjected to a maximum opening, and when the first valve part 321b adjusts an opening with a first minimum opening larger than zero or more, the second valve part 321c is maintained in a second minimum opening larger than zero.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a capacity control valve used in a variable capacity compressor.

A variable capacity compressor used in a vehicle air conditioner system reciprocates in a cylinder bore, sucks refrigerant from a suction chamber, compresses the sucked refrigerant, and discharges the refrigerant into a discharge chamber, in accordance with internal pressure. A control pressure chamber for changing a discharge capacity by changing a stroke amount of the piston; and a capacity control valve for adjusting a pressure of the control pressure chamber for capacity control.
As the control pressure chamber, a crank chamber behind the piston is generally used as in Patent Document 1, but, as in Patent Document 2, an actuator for capacity control is provided separately from the crank chamber. (Cylinder) may be provided, and the pressure chamber may be used as a control pressure chamber for capacity control.

  By the way, in a vehicle air conditioner system, if the compressor is stopped for a long time with the air conditioner OFF, a large amount of liquid refrigerant may accumulate in the compressor. In such a state, even if the compressor is started with the air conditioner turned on, the pressure in the control pressure chamber remains high, the discharge capacity does not increase, and the air conditioner does not function until the liquid refrigerant in the control pressure chamber is discharged. was there.

In view of such a problem, a displacement control valve shown in Patent Document 1 has been proposed.
The capacity control valve has therein a discharge side passage (31, 32, 33) communicating with the discharge chamber (11) and the control pressure chamber (12), a suction chamber (13), and a control pressure chamber (12). A suction side passage (34, 44, 33) communicating with each other, a first valve portion (41) for adjusting the opening degree of the discharge side passage, a second valve portion (42) for adjusting the opening degree of the suction side passage, and And a third valve portion (43). Here, the first valve portion (41) and the second valve portion (42) are integrally formed in one valve body and perform opening / closing operations in opposite directions. The third valve portion (43) is attached to a pressure sensitive body (50) such as a bellows that responds to a pressure change in the pressure sensitive chamber (38), and discharges liquid refrigerant to the suction chamber when the air conditioner is activated. Therefore, it will be open.

Republished publication WO2006 / 090760 JP-A-2015-90100

However, the technique described in Patent Document 1 has the following problems.
When the first valve portion (41) closes the discharge side passages (31, 32), it is desirable that the third valve portion (43) always opens the suction side passage (44). However, since the third valve portion (43) opens and closes in response to the pressure change in the pressure sensing chamber (38), the opening and closing of the suction side passage (44) is not interlocked with the first valve portion (41).
For example, in a season when the outside air temperature is not so high, the pressure in the pressure sensing chamber (38) is relatively low, and even when the air conditioner is activated, the pressure sensing body (50) expands and the third valve portion (43) closes, and inhalation occurs. The side passage (44) is closed and the liquid refrigerant cannot be discharged.

  The present invention provides a capacity control valve for a variable capacity compressor, which can solve the above-described problems.

The capacity control valve according to the present invention includes a pressure supply passage that connects the discharge chamber and the control pressure chamber, a first valve portion that adjusts an opening degree of a first valve hole that constitutes a part of the pressure supply passage, A solenoid unit that applies an electromagnetic force in the valve closing direction to one valve portion; and a pressure-sensitive pressure that responds to the pressure in the suction chamber and applies a biasing force to the first valve portion in the valve opening direction as the pressure decreases. A unit, a pressure relief passage that connects the control pressure chamber and the suction chamber, and a second valve portion that adjusts the opening of a second valve hole that constitutes a part of the pressure relief passage. The
Here, the first valve portion and the second valve portion are configured to perform opening / closing operations in opposite directions with one valve body. When the first valve portion is fully closed, the second valve portion is at the maximum opening, and when the first valve portion is adjusting the opening at the first minimum opening greater than zero. While the second valve portion is maintained at a second minimum opening greater than zero and the second valve portion changes from the maximum opening to the second minimum opening, the first valve portion is It is configured to be maintained at the first minimum opening.

  According to the present invention, when the first valve portion closes the first valve hole and closes the pressure supply passage, the second valve portion has the maximum opening, and the pressure relief passage functions at its maximum. Therefore, the refrigerant discharge performance of the control pressure chamber is improved. This speeds up the effectiveness of the air conditioner. Further, when the first valve part is adjusting the opening degree of the first valve hole, the opening degree of the second valve part is kept to a minimum, so that the internal leakage of the refrigerant through the pressure relief passage can be reduced.

Sectional drawing of the variable capacity compressor which shows 1st Embodiment of this invention. Sectional drawing of the capacity | capacitance control valve in 1st Embodiment same as the above Detailed view of the first valve part and the second valve part The figure which shows the lift characteristic of a 1st valve part and a 2nd valve part Diagram showing the relationship between the current flowing through the coil and the set pressure Sectional drawing of the capacity | capacitance control valve which shows 2nd Embodiment of this invention. Sectional drawing of the capacity | capacitance control valve which shows 3rd Embodiment of this invention. Main part enlarged view of 3rd Embodiment Sectional drawing of the capacity | capacitance control valve which shows 4th Embodiment of this invention. Detailed view of part X (second valve part) of FIG. System diagram of a variable capacity compressor showing a fifth embodiment of the present invention

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 shows a schematic configuration of a variable displacement compressor to which a displacement control valve according to the present invention is applied. The variable displacement compressor of this example is used in a vehicle air conditioner system, and can be operated in the vicinity of zero discharge capacity, and is therefore a clutchless variable displacement compressor.

A basic configuration of the variable capacity compressor 100 shown in FIG. 1 will be described.
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 drive shaft 110 is provided so as to traverse the crank chamber 140 defined by the cylinder block 101 and the front housing 102. A swash plate 111 is disposed around an intermediate portion in the axial direction of the drive shaft 110. The swash plate 111 is connected to a rotor 112 fixed to the drive shaft 110 via a link mechanism 120 and rotates as the drive shaft 110 rotates. The swash plate 11 is also supported so that the tilt angle can be changed with respect to the drive shaft 110.

  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. The link arm 121 is movably connected and the other end side is rotatably connected to the second arm 111a via the second connection pin 123.

  The through hole 111b of the swash plate 111 is formed so that the swash plate 111 can tilt within the range of the maximum inclination angle to the minimum inclination angle, and the minimum inclination angle restricting portion that contacts the drive shaft 110 is formed in the through hole 111b. ing. When the inclination angle of the swash plate 111 when the swash plate 111 is orthogonal to the drive shaft 110 is set to 0 °, the minimum inclination restriction portion of the through hole 111b is formed so that the inclination of the swash plate 111 can be displaced to almost 0 °. Has been. The maximum inclination angle of the swash plate 111 is regulated by the swash plate 111 coming into contact with the rotor 112.

  Between the rotor 112 and the swash plate 111, an inclination reduction spring 114 that urges the swash plate 111 toward the minimum inclination angle is mounted. Further, between the swash plate 111 and the spring support member 116 provided on the drive shaft 110, an inclination increasing spring 115 that urges the swash plate 111 toward the maximum inclination angle is mounted. Here, since the urging force of the inclination increasing spring 115 at the minimum inclination angle is set to be larger than the urging force of the inclination decreasing spring 114, when the drive shaft 110 is not rotating, the swash plate 111 and the inclination decreasing spring 114 are It is located at an inclination angle that balances the urging force of the inclination angle increasing spring 115.

  One end of the drive shaft 110 extends through the inside of the boss portion 102a of the front housing 102 to the outside of the front housing 102, and is connected to a power transmission device (not shown). A shaft seal device 130 is inserted between the drive shaft 110 and the boss portion 102a to block the inside and outside of the crank chamber 140 from each other.

The integral structure of the drive shaft 110 and the rotor 112 is supported by bearings 131 and 132 in the radial direction and supported by a bearing 133 and a thrust plate 134 in the thrust direction. The clearance between the thrust plate 134 contact portion of the drive shaft 110 and the thrust plate 134 is adjusted to a predetermined clearance by the adjustment screw 135.
Therefore, power from the external drive source (vehicle engine) is transmitted to the power transmission device, and the drive shaft 110 rotates in synchronization with the power transmission device.

  A piston 136 is disposed in the cylinder bore 101a. The inner space of the end of the piston 136 projecting toward the crank chamber 140 accommodates the outer periphery of the swash plate 111 via a pair of shoes 137, whereby the swash plate 111 is interlocked with the piston 136. Accordingly, the piston 136 reciprocates in the cylinder bore 101a by the rotation of the swash plate 111. The swash plate 111 can also change the stroke amount of the piston 136 by controlling the tilt angle.

In the cylinder head 104, a suction chamber 141 is formed on the radially inner side, and a discharge chamber 142 is formed on the radially outer side so as to surround the suction chamber 141 in an annular shape.
The suction chamber 141 communicates with the cylinder bore 101a via a suction hole 103a provided in the valve plate 103 and a suction valve (not shown) formed in the suction valve forming sheet. The discharge chamber 142 communicates with the cylinder bore 101a via a discharge hole 103b provided in the valve plate 103 and a discharge valve (not shown) formed in the discharge valve forming sheet.
Therefore, the piston 136 sucks the refrigerant gas from the suction chamber 141 into the cylinder bore 101a by the reciprocating motion, compresses the sucked refrigerant gas, and discharges it to the discharge chamber 142.

  Front housing 102, center gasket (not shown), cylinder block 101, cylinder gasket (not shown), suction valve forming sheet (not shown), valve plate 103, discharge valve forming sheet (not shown), head gasket (Not shown) and the cylinder head 104 are fastened by a plurality of through bolts 105 to form a compressor housing.

  The cylinder head 104 is formed with a suction passage 104b having a suction port 104a at one end. The suction port 104a is connected to a low pressure side refrigerant circuit (suction side refrigerant circuit) of the vehicle air conditioner system. The other end side of the suction passage 104 b extends from the outer peripheral side of the cylinder head 104 so as to cross a part of the discharge chamber 142 and communicates with the suction chamber 141. As a result, the refrigerant gas flows into the suction chamber 141 from the suction passage 104b.

  A muffler 160 is provided above the cylinder block 101 in order to reduce noise and vibration due to refrigerant pulsation. The muffler 160 is formed by fastening a lid member 106 with a bolt via a seal member (not shown) to a muffler forming wall 101b formed on the upper portion of the cylinder block 101. In the muffler space 143 in the muffler 160, a check valve 200 that suppresses the backflow of the refrigerant gas from the discharge side refrigerant circuit to the discharge chamber 142 is disposed.

  The check valve 200 is disposed at a connection portion between the communication path 144 formed across the cylinder head 104, the valve plate 103, and the cylinder block 101 and the muffler space 143. The 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 shuts off the communication path 144 when the pressure difference is smaller than a predetermined value. Is greater than a predetermined value, the communication path 144 is opened. Accordingly, the discharge chamber 142 is connected to the discharge-side refrigerant circuit of the vehicle air conditioner system via the discharge passage constituted by the communication passage 144, the check valve 200, the muffler space 143, and the discharge port 106a.

The cylinder head 104 is further provided with a capacity control valve 300.
The capacity control valve 300 is interposed in the pressure supply passages 145A and 145B so as to constitute a part of the pressure supply passages 145A and 145B communicating with the discharge chamber 142 and the crank chamber 140. The capacity control valve 300 basically responds to the pressure in the suction chamber 141 introduced through the pressure introduction passage 147 and the electromagnetic force generated by the current flowing through the solenoid, in the pressure supply passages 145A and 145B. The opening degree is adjusted, and the amount of refrigerant gas introduced into the crank chamber 140 is controlled.

Therefore, blow-by gas that leaks from the gap with the cylinder bore 101a when the piston 136 compresses the refrigerant gas and the discharge gas that passes through the capacity control valve 300 flow into the crank chamber 140.
The refrigerant in the crank chamber 140 flows to the suction chamber 141 through the pressure release passage 146 configured by the communication passage 101c, the space 101d, and the fixed throttle 103c.

The space portion 101 d is formed by denting the central portion of the cylinder block 101 between the cylinder block 101 and the valve plate 103. The communication passage 101c is formed in the cylinder block 101 so as to allow the crank chamber 140 and the space portion 101d to communicate with each other.
The fixed throttle 103c is formed in the valve plate 103 so as to allow the space 101d on the cylinder block 101 side and the suction chamber 141 on the cylinder head 104 side to communicate with each other, and defines the minimum channel cross-sectional area of the pressure release passage 146. Yes.

  Accordingly, the pressure supply passages 145A and 145B that connect the discharge chamber 142 and the crank chamber 140, the capacity control valve 300 disposed in the pressure supply passages 145A and 145B, and the release passage that connects the crank chamber 140 and the suction chamber 141 are communicated. By providing the pressure passage 146 and the fixed throttle 103c disposed in the pressure release passage 146, the pressure of the crank chamber 140 as the control pressure chamber is changed by the capacity control valve 300, and the inclination angle of the swash plate 111, that is, the piston The stroke amount of 136 can be changed.

That is, by changing the pressure of the crank chamber 140 as the control pressure chamber, the pressure difference between the front and rear of each piston 136, in other words, the pressure difference between the compression chamber in the cylinder bore 101a sandwiching the piston 15 and the crank chamber 140 is used. Thus, the tilt angle of the swash plate 111 can be arbitrarily controlled, and thereby the stroke amount of the piston 136 can be changed.
Specifically, when the pressure in the crank chamber 140 is decreased, the inclination angle of the swash plate 111 is increased, and thereby the stroke amount of the piston 136 can be increased. Thereby, the discharge capacity of the variable capacity compressor 100 can be variably controlled.

When the air conditioner is operating, that is, when the variable capacity compressor 100 is operating, the control device adjusts the energization amount of the solenoid of the capacity control valve 300 based on the external signal, and the discharge capacity so that the pressure of the suction chamber 141 becomes a predetermined value. Is variably controlled. Therefore, the capacity control valve 300 can optimally control the pressure in the suction chamber 141 according to the external environment.
Further, when the air conditioner is not operated, that is, when the variable capacity compressor 100 is not operated, the pressure supply passages 145A and 145B are fully opened and the pressure in the crank chamber 140 is controlled to the maximum by turning off the solenoid. The discharge capacity of the variable capacity compressor 100 is controlled to the minimum.

Next, a first embodiment of the capacity control valve 300 of this embodiment will be described in detail with reference to FIG.
The capacity control valve 300 includes a solenoid unit 310 and a valve unit 320.

  The solenoid unit 310 includes a fixed core 311 having a through-hole 311a penetrating both ends therein, a movable core 312 disposed opposite to one end face of the fixed core 311 with a predetermined gap therebetween, and a movable core 312 A solenoid rod 313 that is integrally connected and inserted through the through hole 311a with a gap, a compression coil spring 314 that applies a biasing force in a direction to separate the movable core 312 from the fixed core 311, and the fixed core 311 and the movable core A cylindrical housing member 315 formed of a non-magnetic material for housing 312; a coil 316 disposed around the housing member 315 and covered with resin; and a housing member for housing the coil 316. And a solenoid housing 317 for holding 315.

  The fixed core 311, the movable core 312, and the solenoid housing 317 are made of a magnetic material, and a magnetic circuit is formed when the coil 316 is energized. Attraction is directed to one end surface of the movable core 312 toward one end surface of the fixed core 311. A force (electromagnetic force) is applied, and an urging force in the valve closing direction is applied to the valve body 321 of the valve unit 320 via the solenoid rod 313.

  The valve unit 320 has one end connected to the solenoid rod 313 to open and close the pressure supply passages 145A and 145B, a pressure sensing rod 321a integrally extended from the other end of the valve 321, and one end A pressure-sensitive unit (bellows unit) 322 that contacts the tip of the pressure-sensitive rod 321a and expands and contracts in the axial direction according to the pressure of the suction chamber 141 to drive the valve body 321; the valve body 321; the pressure-sensitive rod 321a; And a valve housing 323 that accommodates the pressure unit 322.

The valve housing 323 is formed with a valve chamber 323a in which the valve body 321 is disposed, a first valve hole 323b, a communication hole 323c, and a communication hole 323d.
The valve chamber 323a communicates with the crank chamber 140 (the pressure supply passage 145B to the crank chamber 140) through the communication hole 323d.
The first valve hole 323b is formed on the same axis as the valve body 321. The first valve hole 323b communicates with the discharge chamber 142 (pressure supply passage 145A from the discharge chamber 142) via the communication hole 323c on one end side and the valve chamber on the other end side. Open to 323a.
Therefore, the first valve hole 323b forms part of the pressure supply passages 145A and 145B that connect the discharge chamber 142 and the crank chamber 140.

  The valve housing 323 further includes a pressure sensing chamber 323e that houses the pressure sensing unit 322, a communication hole 323f that communicates the suction chamber 141 and the pressure sensing chamber 323e via the pressure introduction passage 147, and a pressure sensing rod 321a. And an insertion hole 323g for inserting and supporting.

The other end of the fixed core 311 is press-fitted and fixed to one end of the valve housing 323, and the other end surface of the fixed core 311 faces the valve chamber 323a.
The other end of the fixed core 311 is formed with a second valve hole 311b that constitutes a part of the through hole 311a. The second valve hole 311b is provided on the same axis as the first valve hole 323b, and opens to the valve chamber 323a on one end side so as to face the opening of the first valve hole 323b.

  The valve body 321 has a first valve portion 321b for opening and closing the first valve hole 323b on one end side, and a second valve portion 321c for opening and closing the second valve hole 311b on the other end side. Here, the 1st valve part 321b and the 2nd valve part 321c are integrally formed in one valve body 321, and it is comprised so that it may open and close mutually oppositely so that it may mention later. However, the first valve portion 321b and the second valve portion 321c do not need to be integrally formed as long as they are configured to perform opening / closing operations in opposite directions with one valve body 321. Even if it is a body, what is necessary is just the structure interlock | cooperated integrally.

A solenoid rod 313 is press-fitted and fixed to an extension of the valve body 321 on the second valve portion 321c side. Therefore, the pressure-sensitive rod 321a, the valve body 321, the solenoid rod 313, and the movable core 312 are an integral component.
The integrated structure of the pressure-sensitive rod 321a, the valve body 321, the solenoid rod 313, and the movable core 312 is an accommodation member on one end side (pressure-sensitive rod 321a) in the insertion hole 323g and the other end side (outer peripheral surface of the movable core 312). 315 is slidably supported on the inner peripheral surface of 315, and other parts can move in the axial direction without contact.

A through hole 321d that penetrates the valve body 321 and the pressure sensing rod 321a is formed, and a communication hole 321e that communicates the through hole 321d and the pressure sensing chamber 323e is formed on the side of the pressure sensing rod 321a. Is formed. A communication hole 321f that connects the second valve hole 311b and the through hole 321d is formed on the side of the extension portion of the valve body 321 on the second valve portion 321c side.
Therefore, the valve chamber 323a is configured to communicate with the pressure sensitive chamber 323e via the second valve hole 311b, the communication hole 321f, the through hole 321d, and the communication hole 321e.

  Therefore, the capacity control valve 300 has its internal passages (communication hole 323d, valve chamber 323a, second valve hole 311b, communication hole 321f, through hole 321d, communication hole 321e, pressure sensing chamber 323e, communication hole 323f). The degree of communication can be controlled by the second valve portion 321c that connects the crank chamber 140 (passage 145B) and the suction chamber 141 (passage 147) and adjusts the opening of the second valve hole 311b.

  Further, the second valve hole 311b communicates with the space in the housing member 315 in which the movable core 312 is disposed via a gap between the through hole 311a and the solenoid rod 313. Therefore, the pressure in the pressure sensing chamber 323e, that is, the pressure in the suction chamber 141 is guided to the space in the housing member 315 in which the movable core 312 is disposed.

  The pressure-sensitive unit 322 includes a bellows-shaped bellows 322a, one end of the bellows 322a, a first end member 322b that receives the tip of the pressure-sensitive rod 321a, and the other end of the bellows 322a. The second end member 322c is positioned and fixed to the housing 323, and the compression coil spring 322d is disposed inside the bellows 322a and applies a biasing force in a direction in which the bellows 322a extends. Note that the inside of the bellows 322a has a negative pressure.

  The solenoid unit 310 and the valve unit 320 are integrated by being fitted and fixed to each other.

  Detailed structures of the first valve portion 321b and the first valve hole 323b, and the second valve portion 321c and the second valve hole 311b will be described with reference to FIG.

The first valve portion 321b enters a cylindrical first body portion 321b1, a first tip portion 321b2 that enters the first valve hole 323b and has a smaller diameter than the first body portion 321b1, and a first body portion 321b1. And a first tapered portion 321b3 that connects the first tip portion 321b2.
The first valve hole 323b opens to the valve chamber 323a, is adjacent to the first taper hole 323b1 serving as a flow rate adjusting portion, and the minimum diameter portion of the first taper hole 323b1, and the first tip portion 321b2 enters the first valve hole 323b. 1 cylindrical hole 323b2.

  The gap between the outer peripheral surface of the first tip 321b2 and the inner peripheral surface of the first cylindrical hole 323b2 is set to be a minimum, and the first cylindrical hole 323b2 is a flow rate restricting portion. The 1st taper part 321b3 contact | abuts to the opening periphery of the 1st taper hole 323b1, and the 1st valve hole 323b is closed.

Similarly, the second valve portion 321c enters the cylindrical second main body portion 321c1, the second tip portion 321c2 that enters the second valve hole 311b and has a smaller diameter than the second main body portion 321c1, and the second A second tapered portion 321c3 that connects the main body portion 321c1 and the second distal end portion 321c2.
The second valve hole 311b opens to the valve chamber 323a, is adjacent to the second tapered hole 311b1 serving as a flow rate adjusting portion, and the minimum diameter portion of the second tapered hole 311b1, and the second tip portion 321c2 enters. 2 cylindrical holes 311b2.

  The gap between the outer peripheral surface of the second tip 321c2 and the inner peripheral surface of the second cylindrical hole 311b2 is set to be minimum, and the second cylindrical hole 311b2 is a flow rate restricting portion. The 2nd taper part 321c3 contact | abuts to the opening periphery of 2nd taper hole 311b1, and the 2nd valve hole 311b is closed.

Next, the operation of the first valve part 321b and the second valve part 321c will be described.
Since the 1st valve part 321b and the 2nd valve part 321c are arrange | positioned at the both ends of one valve body 321, the operation | movement of both valve parts is as follows. FIG. 4 is a lift characteristic diagram of the first valve portion and the second valve portion, and corresponds to (a) to (c) of FIG.

  (A) As shown in FIG. 3A, when the first taper portion 321b3 abuts on the opening periphery of the first taper hole 323b1, the first valve hole 323b is closed, and at the same time, the second tip portion 321c2 is The second valve hole 311b is opened to the maximum by separating from the two valve holes 311b.

At this time, the crank chamber 140 includes a pressure release passage 146, a passage 145B, an internal passage of the capacity control valve 300 (communication hole 323d, valve chamber 323a, second valve hole 311b, communication hole 321f, through hole 321d, communication hole 321e. , The pressure chamber 323e, the communication hole 323f) and the pressure relief passage constituted by the passage 147 communicate with the suction chamber 141, so that the refrigerant in the crank chamber 140 can be quickly supplied to the suction chamber 141. Can be discharged. Therefore, the pressure in the crank chamber 140 is equivalent to the pressure in the suction chamber 141, the inclination angle of the swash plate 111 is maximized, and the stroke amount of the piston 136 is maximized.
When the first valve portion 321b closes the first valve hole 323b, the second valve portion 321c always opens the second valve hole 311b to the maximum. For example, such a state is continued from the start of the air conditioner until it approaches a predetermined state in which the air conditioning state in the passenger compartment is set.

(B) As shown in FIG. 3B, even if the first tapered portion 321b3 is slightly separated from the opening periphery of the first tapered hole 323b1, the distal end periphery of the first distal end portion 321b2 is the first cylindrical hole 323b2. When the valve is located at the position, the flow from the first valve hole 323b to the valve chamber 323a is a minimum flow, and the pressure in the crank chamber 140 cannot be increased.
When the leading edge of the first tip 321b2 is positioned at the boundary between the first cylindrical hole 323b2 and the first tapered hole 323b1, the leading edge of the second tip 321c2 is positioned in the second cylindrical hole 311b2. Therefore, at this time, the internal passage connecting the valve chamber 323a and the pressure sensitive chamber 323e has a minimum opening.

  Therefore, when the distal end periphery of the first distal end portion 321b2 is positioned in the first tapered hole 323b1 (flow rate adjusting portion) and the opening degree of the first valve hole 323b is adjusted, the crank chamber 140 is connected to the pressure release passage 146. The passage 145B, the internal passage (including the second valve hole 311b) of the capacity control valve 300, and the pressure relief passage constituted by the passage 147 communicate with the suction chamber 141 through two paths. At this time, the opening of the internal passage (the minimum opening of the second valve hole 311b by the second valve portion 321c) is set to a minimum opening smaller than the opening cross-sectional area of the fixed throttle 103c of the pressure release passage 146. ing. For this reason, by adjusting the opening degree of the first valve hole 323b, the pressure in the crank chamber 140 can be easily changed (increase or decrease in pressure), and the tilt angle of the swash plate 111 can be changed to reduce the stroke amount of the piston 136. Can be controlled. By controlling the stroke amount of the piston 136, the flow rate of the refrigerant flowing through the refrigerant circuit of the air conditioning system is adjusted, and the air conditioning state in the passenger compartment is maintained in a predetermined state.

  Since the outer diameter of the insertion portion of the pressure-sensitive rod 321a, the outer diameter of the first tip portion 321b2, and the outer diameter of the second tip portion 321c2 are set to be the same, the force acting on the valve body 321 is: The following formula (1) is obtained, from which the following formula (2) is derived.

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

F (I): Solenoid electromagnetic force f: Biasing force of compression coil spring 314 Ps: Suction chamber pressure Sb: Bellows effective pressure receiving area F: Bellows biasing force

  Therefore, the capacity control valve 300 senses the pressure of the suction chamber 141 by the pressure sensing unit 322, and autonomously controls the valve body 321 so that the pressure of the suction chamber 141 is determined by the current flowing through the coil 316. Then, the opening degree of the pressure supply passages 145A and 145B is adjusted. As shown in FIG. 5, the control characteristic is such that when the current flowing through the coil 316 is increased, the pressure in the suction chamber 141 is decreased.

(C) As shown in FIG. 3C, when the second taper portion 321c3 abuts on the opening peripheral edge of the second taper hole 311b1, the second valve hole 311b is closed and at the same time the first tip portion 321b2 is The first valve hole 323b is opened to the maximum by separating from the one valve hole 323b.
When the power supply to the coil 316 is turned off, such a state is brought about by the biasing force of the compression coil spring 314.

  At this time, the crank chamber 140 communicates with the suction chamber 141 only through the pressure release passage 146 having the fixed throttle 103c. For this reason, the pressure in the crank chamber 140 is rapidly increased, the inclination angle of the swash plate 111 is minimized, and the stroke amount of the piston 136 is minimized. For example, when the air conditioner is turned off, such a state is obtained.

In the present embodiment, the first valve portion 321b that adjusts the opening degree of the first valve hole 323b that constitutes part of the pressure supply passages 145A and 145B, and the second valve that constitutes part of the pressure relief passages 147 and 145B. The second valve portion 321c for adjusting the opening degree of the hole 311b is configured to perform opening / closing operations in opposite directions with one valve body 321, and the second valve portion 321b is fully closed when the first valve portion 321b is fully closed. When the valve portion 321c is at the maximum opening and the first valve portion 321b is adjusting the opening at the first minimum opening greater than zero, the second minimum opening at which the second valve portion 321c is greater than zero. Maintained at a time. Therefore, since the escape amount when the pressure supply is stopped can be maximized, the discharge performance of the refrigerant in the crank chamber 140 is improved. This speeds up the effectiveness of the air conditioner. On the other hand, when the opening degree of the first valve part 321b is adjusted for air-conditioner control, the opening degree of the second valve part 321c is kept to a minimum, so that the internal leakage of the refrigerant can be reduced.
In the present embodiment, the first valve portion 321b is maintained at the first minimum opening while the second valve portion 321c changes from the maximum opening to the second minimum opening. ing. As a result, both of them do not open at the same time even in a transient state.

  In this embodiment, when the 1st valve part 321b becomes the maximum opening degree, it is comprised so that the 2nd valve part 321c may be fully closed. Thereby, when the first valve portion 321b reaches the maximum opening, the internal leakage of the refrigerant from the valve chamber 323a to the pressure sensing chamber 323e can be shut off, and the pressure in the crank chamber 140 can be quickly increased. Thereby, when the power supply to the coil 316 is turned off, the discharge capacity can be promptly shifted to the minimum state.

  In the present embodiment, the first valve portion 321b is formed with a cylindrical first tip portion 321b2, the first valve hole 323b is provided with a first taper hole 323b1 for flow rate adjustment and a cylindrical shape for defining a minimum flow path cross-sectional area. The structure which forms the 1st cylindrical hole 323b2, and the cylindrical 2nd tip part 321c2 is formed in the 2nd valve part 321c, and the 2nd cylindrical shape for the minimum flow-path cross-sectional area regulation to the 2nd valve hole 311b. A desired opening characteristic is realized by the configuration in which the cylindrical hole 311b2 is formed. Therefore, it can be implemented by changing the shape of the valve portion and the valve hole.

  In the present embodiment, the integral component of the movable core 312, the solenoid rod 313, the valve body 321 and the pressure sensing rod 321 a is slidably supported by the insertion hole 323 g of the housing 323 at the outer periphery of the pressure sensing rod 321 a. And slidably supported between the outer periphery of the movable core 312 and the housing member 315. Thereby, it can support reliably at two points, and each outer peripheral surface of the 1st tip part 321b2 and the 2nd tip part 321c2 does not contact each inner peripheral surface of the 1st cylindrical hole 323b2 and the 2nd cylindrical hole 311b2. Can be. Therefore, the minimum channel cross-sectional area does not change due to wear.

  Next, a second embodiment of the capacity control valve according to the present invention will be described with reference to FIG. In addition, the same code | symbol is attached | subjected to the same element as 1st Embodiment, and a different element is demonstrated.

  A through hole 313a that penetrates the entire length of the solenoid rod 313 is formed, and the through hole 313a communicates with the valve body 321 and the through hole 321d inside the pressure sensitive rod 321a. Therefore, the pressure of the pressure sensing chamber 323e (pressure of the suction chamber 141) is introduced into the accommodation space (inside the accommodation member 315) of the movable core 312 via the through hole 313a.

The through-hole 311a of the fixed core 311 has a small-diameter portion 311c having a smaller diameter than other regions on one end surface side, and a solenoid rod 313 is inserted and supported by the small-diameter portion 311c.
The integrated structure of the movable core 312, the solenoid rod 313, the valve body 321 and the pressure sensing rod 321 a is supported at two points: an insertion hole 323 g of the pressure sensing rod 321 a and a small diameter portion 311 c of the fixed core 311. Therefore, the outer peripheral surface of the movable core 312 is not in contact with the inner peripheral surface of the housing member 315.

  The two support portions described above have a minute gap, and the integrated component of the movable core 312, the solenoid rod 313, the valve body 321, and the pressure sensitive rod 321 a is inclined within the gap, but the support portion Since the small diameter portion 311c of the fixed core 311 is used, the inclination is suppressed. Therefore, a gap between the outer peripheral surface of the first tip portion 321b2 and the inner peripheral surface of the first cylindrical hole 323b2, and between the outer peripheral surface of the second tip portion 321c2 and the inner peripheral surface of the second cylindrical hole 311b2. Can be set smaller. Accordingly, the opening degree of the first valve hole 323b can be adjusted to the minute flow rate range by the first valve part 321b, and the valve when the first valve part 321b is adjusting the opening degree of the first valve hole 323b. The internal leakage of the refrigerant from the chamber 323a to the pressure sensitive chamber 323e can be further suppressed.

  Next, a third embodiment of the capacity control valve according to the present invention will be described with reference to FIGS. In addition, the same code | symbol is attached | subjected to the same element as 1st Embodiment, and a different element is demonstrated.

  As in the second embodiment, a through hole 313a that penetrates the entire length of the solenoid rod 313 is formed, and the through hole 313a communicates with the valve body 321 and the through hole 321d inside the pressure sensitive rod 321a. . However, the communication hole 321f (FIGS. 2 and 6) that connects the second valve hole 311b and the through hole 321d is not formed in the valve body 321.

  Accordingly, the valve chamber 323a includes the second valve hole 311b, the gap between the through hole 311a of the fixed core 311 and the solenoid rod 313, the accommodation space of the movable core 312 (within the accommodation member 315), and the through hole 313a of the solenoid rod 313. The valve body 321 and the pressure sensitive rod 321a are configured to communicate with the pressure sensitive chamber 323e via an internal passage formed by a through hole 321d.

Further, the second valve portion 321c does not include the second tapered portion 321c3 (FIG. 3) that contacts the peripheral edge of the second tapered hole 311b1 when the first valve portion 321b has the maximum opening. Therefore, when the first valve portion 321b has the maximum opening, the second valve portion 321c has the minimum opening.
On the other hand, the solenoid rod 313 protrudes from the end surface of the movable core 312, and the protruding end 313 d faces the inner end wall 315 a of the housing member 315. Therefore, when the first valve portion 321b has the maximum opening, the protruding end portion 313d of the solenoid rod 313 contacts the end wall 315a inside the housing member 315, and the opening portion of the through hole 313a is closed.

  Therefore, when the first valve hole 323b is opened to the maximum, the end of the through hole 313a is closed, so that the second valve hole 311b is substantially closed, and the pressure chamber is moved from the valve chamber 323a. The internal leakage of the refrigerant to the H.323e can be cut off, and the pressure in the crank chamber 140 can be quickly increased. Thereby, when the power supply to the coil 316 is turned off, the discharge capacity can be promptly shifted to the minimum state.

  Next, a fourth embodiment of the capacity control valve according to the present invention will be described with reference to FIGS. In addition, the same code | symbol is attached | subjected to the same element as 1st Embodiment, and a different element is demonstrated.

  The solenoid rod 313, the valve body 321 and the pressure sensitive rod 321a are formed integrally and a through hole 321d is formed inside.

The second valve hole and the second valve portion are different from the first to third embodiments.
The second valve hole 323h in the present embodiment opens into the pressure sensitive chamber 323e on one end side. The second valve portion 321c is disposed in the pressure sensitive chamber 323e and faces the opening of the second valve hole 323h.

  As shown in the enlarged view of FIG. 10, the second valve hole 323h is formed in the valve housing 323, and is connected to the second tapered hole 323h1 that opens to the pressure sensing chamber 323e, and the minimum diameter portion of the second tapered hole 323h1. A second cylindrical hole 323h2.

  As shown in the enlarged view of FIG. 10, the second valve portion 321c has a cylindrical second tip portion 321c2 that is formed in the pressure-sensitive rod 321a and enters the second valve hole 323h. However, the second tapered portion 321c3 (FIG. 3) that contacts the peripheral edge of the second tapered hole 323h1 is not provided.

The pressure-sensitive rod 321a has a communication hole 321g that allows the through hole 321d and the second valve hole 323h to communicate with each other.
Therefore, the other end side of the second valve hole 323h communicates with the solenoid rod 313, the valve body 321 and the through hole 321d of the pressure-sensitive rod 321a via the communication hole 321g, and further, the space in the housing member 315, and The valve chamber 323a communicates with a gap between the outer periphery of the solenoid rod 313 and the through hole 311a of the fixed core 311.

Accordingly, the valve chamber 323a is configured by a gap between the outer peripheral portion of the solenoid rod 313 and the through hole 311a of the fixed core 311, a space in the housing member 315, the through hole 321d, the communication hole 321g, and the second valve hole 323h. The pressure sensing chamber 323e communicates with the internal passage.
The internal passage is closed when the protruding end 313 d of the solenoid rod 313 contacts the end wall 315 a of the housing member 315.

  Even if the second valve portion 321c is arranged on the pressure-sensitive rod 321a side as in the present embodiment, the same effects as those in the first to third embodiments can be obtained.

Next, a fifth embodiment of the present invention will be described.
In the variable capacity compressor shown in FIG. 1, the crank chamber 140 as the control pressure chamber changes the stroke amount of the piston 136 by changing the inclination angle of the swash plate 111 according to the internal pressure, thereby changing the discharge capacity. It is a configuration.
On the other hand, in the fifth embodiment, an actuator (cylinder) 500 for capacity control is provided separately from the crank chamber 140, and the pressure chamber is used as a control pressure chamber for capacity control. The capacity control actuator 500 acts directly on the swash plate 111 to change its tilt angle.

FIG. 11 is a system diagram of a variable capacity compressor showing a fifth embodiment of the present invention.
The capacity control actuator 500 includes a cylinder part (sliding hole) 501 formed in the rotor 112 fixed to the drive shaft 110, and is supported by the cylinder part 501 so as to be slidable in the axial direction. And a piston 502 in contact therewith.

The cylinder portion (sliding hole) 501 is formed as an annular recess surrounding the drive shaft 110 on the surface of the rotor 112 fixed to the drive shaft 110 on the swash plate 11 side.
One end of the piston 502 is slidably inserted into the cylinder portion 501, and a control pressure chamber 503 is formed between the bottom of the cylinder portion 501 and the piston 502.

  A compression coil spring (tilt angle reducing spring) 504 is interposed in the control pressure chamber 503, that is, between the bottom of the cylinder portion 501 and the piston 502. The compression coil spring 504 urges the piston 502 to bring the piston 502 into contact with the convex portion 505 of the swash plate 111. Here, when the piston 502 pushes the convex portion 505 of the swash plate 111, the inclination angle of the swash plate 111 can be reduced.

Therefore, when the pressure in the control pressure chamber 503 is increased, the inclination angle of the swash plate 11 is decreased, and thereby the stroke amount of the piston 136 can be decreased.
On the contrary, when the pressure in the control pressure chamber 503 is decreased, the inclination angle of the swash plate 111 is increased, whereby the stroke amount of the piston 136 can be increased.

In order to control the pressure in the control pressure chamber 503, a communication hole 506 is formed in the shaft center of the drive shaft 110, and one end of the communication hole 506 communicates with the control pressure chamber 503 through the communication hole 507. Then, the capacity control valve 300 is connected to the other end of the communication hole 506 through the passage 145B.
Accordingly, the pressure in the control pressure chamber 503 is controlled by the capacity control valve 300.

  The capacity control valve 300 is the same as that described in the first to fourth embodiments, and is connected to the discharge chamber 142 and the passage 145A, and is connected to the suction chamber 141 and the passage 147.

Therefore, the capacity control valve 300 has the first valve hole and the first valve portion between the passage 145A from the discharge chamber 142 and the passage 145B to the control pressure chamber 503, and is controlled by the first valve portion. The supply amount of the discharge pressure from the discharge chamber 142 to the control pressure chamber 503 can be controlled.
The capacity control valve 300 also has a second valve hole and a second valve portion between the passage 147 from the suction chamber 141 and the passage 145B to the control pressure chamber 503, and is controlled by the second valve portion. The amount of pressure relief from the control pressure chamber 503 to the suction chamber 141 can be controlled.

  In the first embodiment, the pressure release passage 146 having the fixed throttle 103c and the pressure release passages 145B and 147 exist in order to release the pressure in the crank chamber 140 as the control pressure chamber. On the other hand, in this embodiment, in order to release the pressure in the control pressure chamber 503, only the pressure relief passages 145B and 147 are used. Therefore, the fixed throttle 103c of the pressure release passage 146 is not necessary.

The operation in the fifth embodiment will be described.
(A) When the first valve portion is fully closed, the second valve portion has a maximum opening. At this time, the control pressure chamber 503 communicates with the suction chamber 141 through the pressure relief passages 145B and 147 that pass through the second valve portion in the capacity control valve 300, so that the refrigerant in the control pressure chamber 503 is quickly transferred to the suction chamber 141. The pressure in the control pressure chamber 503 is equivalent to the pressure in the suction chamber 141, the inclination angle of the swash plate 111 is maximized, and the stroke amount of the piston 136 is maximized. For example, such a state is continued from the start of the air conditioner until it approaches a predetermined state in which the air conditioning state in the passenger compartment is set.

(B) When the second valve portion operates in the closing direction, the first valve portion opens, but the minimum opening is maintained. Therefore, the pressure in the control pressure chamber 503 cannot be increased.
When the second valve portion reaches the minimum opening, the flow rate can be adjusted by the first valve portion. At this time, the second valve portion is maintained at the minimum opening. Therefore, the pressure of the control pressure chamber 503 can be easily changed (pressure increase or pressure reduction) by adjusting the opening degree of the first valve portion, and the stroke amount of the piston 136 can be controlled by changing the inclination angle of the swash plate 111. By controlling the stroke amount of the piston 136, the flow rate of the refrigerant flowing through the refrigerant circuit of the air conditioning system is adjusted, and the air conditioning state in the passenger compartment is maintained in a predetermined state.

(C) When the first valve portion reaches the maximum opening, the second valve portion is fully closed. When the power supply to the coil 316 is turned off, such a state is brought about by the urging force of the compression coil spring 314. At this time, since the control pressure chamber 503 communicates with the discharge chamber 142 via the passages 145A and 145B, the pressure in the control pressure chamber 503 is rapidly increased, and the inclination angle of the swash plate 111 is minimized and the piston 136 Stroke amount is minimized. For example, when the air conditioner is turned off, such a state is obtained.

  As described above, the present invention is applicable not only to the case where the crank chamber 140 is used as the control pressure chamber for capacity control, but also to the case where the pressure control actuator 500 is provided and the pressure chamber is used.

  The illustrated embodiments are merely examples of the present invention, and the present invention is not limited to those directly described by the described embodiments, and various improvements and modifications made by those skilled in the art within the scope of the claims. Needless to say, it encompasses changes.

DESCRIPTION OF SYMBOLS 100 Variable capacity compressor 101 Cylinder block 101a Cylinder bore 101b Muffler formation wall 101c Communication path 101d Space part 102 Front housing 102a Boss part 103 Valve plate 103a Suction hole 103b Discharge hole 103c Fixed throttle 104 Cylinder head 104a Suction port 104b Suction path 105 Through bolt 106 Lid member 106a Discharge port 110 Drive shaft 111 Swash plate 111a Second arm 111b Through hole 112 Rotor 112a First arm 114 Inclination decreasing spring 115 Inclination increasing spring 116 Spring support member 120 Link mechanism 121 Link arm 122 First connecting pin 123 First 2 connecting pin 130 shaft seal device 131, 132 bearing 133 bearing 134 thrust plate 135 adjustment screw 136 piston 137 shoe 140 crank chamber Control pressure chamber)
141 Suction chamber 142 Discharge chamber 143 Muffler space 144 Communication path 145A, 145B Pressure supply path 146 Pressure release path 147 Pressure introduction path 160 also serving as a pressure relief path Muffler 200 Check valve 300 Capacity control valve 310 Solenoid unit 311 Fixed core 311a Through hole (Through hole of fixed core)
311b 2nd valve hole 311b1 2nd taper hole 311b2 2nd cylindrical hole 311c Small diameter part 312 Movable core 313 Solenoid rod 313a Solenoid rod through-hole 313d Solenoid rod protruding end 314 Compression coil spring 315 Housing member 315a Housing member end wall 316 Coil 317 Solenoid housing 320 Valve unit 321 Valve body 321a Pressure sensing rod 321b First valve portion 321b1 First body portion 321b2 First tip portion 321b3 First taper portion 321c Second valve portion 321c1 Second body portion 321c2 Second tip portion 321c3 Second tapered portion 321d Valve body and pressure-sensitive rod through-hole 321e Communication hole 321f Communication hole 321g Communication hole 322 Pressure-sensitive unit 322a Bellows 322b First end member 322c Second end member 322d Compression coil spring 32 Valve housing 323a Valve chamber 323b First valve hole 323b1 First taper hole 323b2 First cylindrical hole 323c Communication hole 323d Communication hole 323e Pressure sensing chamber 323f Communication hole 323g Insertion hole 323h Second valve hole 323h1 Second taper hole 323h2 Second cylinder Hole 500 Capacity control actuator 501 Cylinder portion 502 Piston 503 Pressure chamber (control pressure chamber)
504 Compression coil spring (Inclination reduction spring)
505 Convex part 506, 507 Communication hole

Claims (15)

A capacity control valve (300) used in the variable capacity compressor (100),
The variable capacity compressor (100) reciprocates in the cylinder bore (101a), thereby sucking refrigerant from the suction chamber (141), compressing the sucked refrigerant, and discharging it to the discharge chamber (142) ( 136) and control pressure chambers (140, 503) for changing the discharge volume by changing the stroke amount of the piston (136) according to the internal pressure,
The capacity control valve (300)
Pressure supply passages (145A, 145B) connecting the discharge chamber (142) and the control pressure chambers (140, 503);
A first valve portion (321b) for adjusting an opening degree of a first valve hole (323b) constituting a part of the pressure supply passage (145A, 145B);
A solenoid unit (310) for applying an electromagnetic force to the first valve portion (321b) in the valve closing direction;
A pressure-sensitive unit (322) that responds to the pressure in the suction chamber (141) and applies a biasing force in the valve opening direction to the first valve portion (321b) as the pressure decreases;
Pressure relief passages (147, 145B) connecting the control pressure chambers (140, 503) and the suction chamber (141);
A second valve portion (321c) for adjusting the opening degree of the second valve hole (311b) constituting a part of the pressure relief passage (147, 145B);
Comprising
The first valve part (321b) and the second valve part (321c) are configured to perform opening / closing operations in opposite directions with one valve body (321),
When the first valve portion (321b) is fully closed, the second valve portion (321c) has a maximum opening, and the first valve portion (321b) has an opening that is greater than or equal to a first minimum opening that is greater than zero. The second valve portion (321c) is maintained at a second minimum opening greater than zero when adjusting
While the second valve portion (321c) changes from the maximum opening to the second minimum opening, the first valve portion (321b) is configured to be maintained at the first minimum opening. A capacity control valve characterized by comprising:   The capacity control according to claim 1, wherein the second valve portion (321c) is fully closed when the first valve portion (321b) reaches a maximum opening. valve. The first valve portion (321b) has a cylindrical first tip portion (321b2) that enters the first valve hole (323b) by an operation in the valve closing direction, and the first valve hole (323b). ) Expands in a tapered shape toward the first valve portion (321b) and is connected to the first tapered hole (323b1) serving as a flow rate adjusting portion and the minimum diameter portion of the first tapered hole (323b1). A cylindrical first cylindrical hole (323b2) defining a minimum flow path cross-sectional area with a gap between the first tip portion (321b2) and the outer peripheral surface;
The second valve portion (321c) has a cylindrical second tip portion (321c2) that enters the second valve hole (311b) by an operation in the valve closing direction, and the second valve hole (311b). ) Has a cylindrical second cylindrical hole (311b2) that defines a minimum flow path cross-sectional area with a gap between the second tip portion (321c2) and the outer peripheral surface,
When the first valve portion (321b) closes the first valve hole (323b), the second tip portion (321c2) is detached from the second cylindrical hole (311b2), and the second valve The opening of the hole (311b) is maximized,
The tip peripheral edge of the first tip part (321b2) is detached from the first cylindrical hole (323b2), and the gap between the tip peripheral edge of the first tip part (321b2) and the first taper hole (323b1) is obtained. When the opening degree of the first valve hole (323b) is being adjusted, the peripheral edge of the second tip part (321c2) enters the second cylindrical hole (311b2) and the second valve hole (311b). 3. The capacity control valve according to claim 1, wherein the opening is configured to be the second minimum opening. 4.   The second valve portion (321c) has an annular contact surface (321c3) that contacts the periphery of the second valve hole (311b) around the second tip portion (321c2). 4. The capacity control valve according to claim 3, wherein the valve is fully closed by contacting a peripheral edge of the second valve hole (311 b). 5. The first valve hole (323b) communicates with the discharge chamber (142) on one end side and opens to the valve chamber (323a) with the other end side communicating with the control pressure chamber (140, 503),
The valve body (321) having the first valve portion (321b) and the second valve portion (321c) passes through the first valve hole (323b), and the first valve portion (321b) is the valve. Adjusting the opening of the first valve hole (323b) relative to the opening of the first valve hole (323b) in the chamber (323a);
The solenoid unit (310) has a movable core (312) integrally connected to one end of the valve body (321) via a solenoid rod (313), and the solenoid rod (313) inserted therethrough. A fixed core (311) facing the movable core (312) via a predetermined gap, and provided on the outer peripheral side of the fixed core (311) and the movable core (312) to move the movable core (312) The valve body includes a nonmagnetic housing member (315) that can be housed and a coil (316) disposed on an outer peripheral side of the housing member (315), and energizes the coil (316). (321), a biasing force due to electromagnetic force is applied in a direction in which the first valve portion (321b) decreases the opening of the first valve hole (323b),
The pressure sensing unit (322) is disposed in the pressure sensing chamber (323e) communicating with the suction chamber (141) and the pressure sensing chamber (323e), and expands and contracts according to the pressure in the suction chamber (141). A bellows (322a), a pressure sensitive rod (321a) connecting the other end of the valve body (321) and the bellows (322a), and the pressure in the suction chamber (141) is controlled by the solenoid unit (310). ), The first valve portion (321b) is moved in the direction in which the opening degree of the first valve hole (323b) increases to reduce the suction. When the pressure in the chamber (141) becomes higher than the predetermined value, the first valve portion (321b) is moved in a direction in which the opening degree of the first valve hole (323b) decreases,
The second valve hole (311b) is provided on the same axis as the first valve hole (323b), and opens to one of the valve chamber (323a) and the pressure sensing chamber (323e) on one end side. The second valve portion (321c) communicates with the other at the other end side, and the second valve portion (321c) is relative to the opening of the second valve hole (311b) to the valve chamber (323a) or the pressure sensitive chamber (323e). And the opening degree of the said 2nd valve hole (311b) is adjusted, The capacity | capacitance control valve as described in any one of Claims 1-4 characterized by the above-mentioned. The second valve hole (311b) opens to the valve chamber (323a) on one end side so as to face the opening of the first valve hole (323b),
The second valve portion (321c) is disposed in the valve chamber (323a) in a direction opposite to the first valve portion (321b) and is opposed to the opening of the second valve hole (311b). The capacity control valve according to claim 5, wherein   The other end side of the second valve hole (311b) communicates with the pressure sensing chamber (323e) via the valve body (321) and the internal passage (321d) of the pressure sensing rod (321a). The capacity control valve according to claim 6, wherein   The other end side of the second valve hole (311b) is a gap between the solenoid rod (313) and the through hole (311a) of the fixed core (311), a space in the housing member (315), and The solenoid rod (313), the valve body (321), and the pressure sensitive rod (321a) are communicated with the pressure sensitive chamber (323e) via internal passages (313a, 321d). The capacity control valve according to claim 6.   The solenoid rod (313) penetrates the movable core (312) and protrudes from the other end surface of the movable core (312). When the opening degree of the first valve portion (321b) is maximum, the solenoid rod When the end surface of (313) contacts the end wall (315a) of the housing member (315), the internal passage of the solenoid rod (313) is closed, and the second valve portion (321c) is fully closed. The capacity control valve according to claim 8, wherein The second valve hole (311b) opens to the pressure sensitive chamber (323e) on one end side,
The capacity control valve according to claim 5, wherein the second valve portion (321c) is disposed in the pressure sensing chamber (323e) and faces the second valve hole (311b).   The other end side of the second valve hole (311b) is inside the pressure sensitive rod (321a), the valve body (321), the internal passage (321d) of the solenoid rod (313), and the accommodating member (315). 11. The valve chamber (323 a) communicates with the valve chamber (323 a) via a space, a gap between the solenoid rod (313) and the through hole (311 a) of the fixed core (311). Capacity control valve.   The integral structure of the movable core (312), the solenoid rod (313), the valve body (321) and the pressure sensing rod (321a) is an outer peripheral portion of the pressure sensing rod (321a) of the housing (323). It is slidably supported by the insertion hole (323g) and is slidably supported between the outer peripheral portion of the movable core (312) and the housing member (315). The capacity control valve according to any one of claims 5 to 11.   The integral structure of the movable core (312), the solenoid rod (313), the valve body (321) and the pressure sensing rod (321a) is an outer peripheral portion of the pressure sensing rod (321a) of the housing (323). It is slidably supported by the insertion hole (323g) and slidably supported between the outer peripheral portion of the solenoid rod (313) and the through hole (311a) of the fixed core (311). The capacity control valve according to any one of claims 5 to 11, wherein: A piston (136) that reciprocates in the cylinder bore (101a), sucks refrigerant from the suction chamber (141), compresses the sucked refrigerant, and discharges the refrigerant to the discharge chamber (142);
Control pressure chambers (140, 503) for changing the discharge capacity by changing the stroke amount of the piston (136) according to the internal pressure;
The capacity control valve (300) according to any one of claims 1 to 13,
A variable capacity compressor (100) including the compressor. A pressure relief passage (146) having a fixed throttle (103c) connecting the control pressure chamber (140) and the suction chamber (141);
15. The variable capacity according to claim 14, wherein the second minimum opening of the second valve portion (321c) is smaller than an opening cross-sectional area of the fixed throttle (103c) of the pressure release passage (146). Compressor (100).