JP2005264907A - Control valve for variable displacement swash plate type compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a control valve for a variable displacement swash plate type compressor capable of performing feedback control of discharge displacement of the compressor with simple constitution. <P>SOLUTION: The control valve for the variable displacement swash plate type compressor used for an air conditioner for cooling and heating is provided with a pressure receiving piece disposed in refrigerant gas flowing in a refrigerant circuit; a solenoid valve; a fluid force transmission mechanism for transmitting fluid force of refrigerant gas applied to the pressure receiving piece, to a rod of the solenoid valve; an external information detecting means for detecting air-conditioning load, the traveling state of a vehicle, and the like; and a control means for controlling an electric power value supplied to the solenoid valve based on external information. The solenoid valve turns on/off introduction of compressor discharge gas into a crank chamber according to the magnitude relation between the fluid force of refrigerant gas flowing in the refrigerant circuit and transmitted to the rod from the pressure receiving piece, and electromagnetic force applied to the rod. The fluid force of refrigerant gas applied to the pressure receiving piece is bent at a right angle through the fluid force transmission mechanism and transmitted to the rod of the solenoid valve. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a control valve for a variable capacity swash plate compressor used in an air conditioner for air conditioning.

  In the variable capacity swash plate compressor, the discharge capacity is controlled by adjusting the crank chamber pressure. In a variable capacity swash plate compressor used in an air conditioner for air conditioning, for example, a target difference in which a differential pressure between two predetermined points on a refrigerant circuit is determined based on external information provided from external information detection means The crank chamber pressure is autonomously adjusted so as to approach the pressure, the differential pressure between the two points is feedback-controlled, and consequently the discharge capacity is feedback-controlled.

Patent Document 1 is a control valve of a variable displacement swash plate compressor that autonomously adjusts the crank chamber pressure, and is a predetermined 2 on the refrigerant circuit determined based on external information provided from external information detection means. A valve that is pressed in one direction by an electromagnetic force corresponding to a target differential pressure between points, and that is pressed in a direction opposite to the one direction by receiving the differential pressure between the two predetermined points on the refrigerant circuit. By introducing the discharge gas into the crank chamber through a variable opening amount valve having a body, the crank chamber pressure is autonomously adjusted so that the differential pressure between the two points approaches the target differential pressure. A control valve configured to feedback control the differential pressure between the two points, and thus to control the discharge capacity, is disclosed.
In the control valve of Patent Document 1, in order to stably feedback control the differential pressure between two predetermined points on the refrigerant circuit, a throttle is provided between the two points to increase the differential pressure between the two points. ing.
JP 2001-107854 A

In the control valve of Patent Document 1, since the throttle and the valve that cuts in and out of the discharge gas into the crank chamber are separate mechanisms, it is necessary to provide a passage for guiding the differential pressure before and after the throttle to the valve. There is a problem that becomes complicated.
The present invention has been made in view of the above problems, and an object of the present invention is to provide a control valve for a variable displacement swash plate compressor that can feedback control the discharge capacity of the compressor with a simple configuration.

In order to solve the above-mentioned problem, in the present invention, a control valve of a variable capacity swash plate compressor used in an air conditioner for heating and cooling, a pressure receiving piece disposed in the refrigerant gas flowing through the refrigerant circuit, Based on external information, an electromagnetic valve, a fluid force transmission mechanism that transmits a fluid force of refrigerant gas applied to the pressure receiving piece to the rod of the electromagnetic valve, an external information detection means that detects a cooling load, a vehicle running state, and the like Control means for controlling the power value supplied to the solenoid valve, and the solenoid valve has a magnitude relationship between the fluid force of the refrigerant gas flowing through the refrigerant circuit transmitted from the pressure receiving piece to the rod and the electromagnetic force applied to the rod. Accordingly, the introduction of the compressor discharge gas into the crank chamber is turned on and the fluid force of the refrigerant gas applied to the pressure receiving piece is bent at a right angle via the fluid force transmission mechanism and transmitted to the rod of the solenoid valve. Variable capacity swash plate pressure To provide a control valve of the machine.
In the control valve according to the present invention, the pressure receiving piece disposed in the refrigerant gas flowing through the refrigerant circuit forms a throttle and also forms a part of the valve that cuts the introduction of the discharge gas into the crank chamber. Therefore, there is no need to provide a passage for guiding the differential pressure before and after the throttle to the valve. Therefore, the control valve according to the present invention can feedback control the discharge capacity of the compressor with a simple configuration.
In the control valve according to the present invention, the fluid force of the refrigerant gas applied to the pressure receiving piece is bent at a right angle via the fluid force transmission mechanism and transmitted to the rod of the solenoid valve, so that the fluid force of the refrigerant gas is linear. As compared with the case where the control valve is transmitted to the rod of the electromagnetic valve, the overall length of the control valve is shortened and the control valve is downsized.

In a preferred aspect of the present invention, the fluid force transmission mechanism is an L-shaped lever member in which one arm can abut against the pressure receiving piece and the other arm can abut against the rod of the electromagnetic valve.
In a preferred aspect of the present invention, the fluid force transmission mechanism includes a first rack attached to the pressure receiving piece, a second rack attached to the rod of the solenoid valve, and a gear meshing with the first rack and the second rack. And a rack and pinion mechanism.
The fluid force of the refrigerant gas applied to the pressure receiving piece can be bent at a right angle and transmitted to the rod of the electromagnetic valve via the lever member or the rack and pinion mechanism.

In the preferable aspect of this invention, the pressure receiving piece is arrange | positioned at the funnel-shaped enlarged diameter part of the refrigerant circuit.
By arranging the pressure receiving piece in the funnel-shaped enlarged portion of the refrigerant circuit, it is possible to prevent the control valve from reacting sensitively to the change in the flow rate of the refrigerant gas flowing through the refrigerant circuit, and the situation where the controllability deteriorates.

In a preferred aspect of the present invention, the control valve of the variable capacity swash plate compressor includes a rod length adjusting member.
By disposing the rod length adjusting member, the performance of the control valve can be enhanced. Moreover, the workability | operativity for the assembly | attachment precision improvement at the time of an assembly | attachment can be improved.

In the control valve according to the present invention, the pressure receiving piece disposed in the refrigerant gas flowing through the refrigerant circuit forms a throttle and also forms a part of the valve that cuts the introduction of the discharge gas into the crank chamber. Therefore, there is no need to provide a passage for guiding the differential pressure before and after the throttle to the valve. Therefore, the control valve according to the present invention can feedback control the discharge capacity of the compressor with a simple configuration.
In the control valve according to the present invention, the fluid force of the refrigerant gas applied to the pressure receiving piece is bent at a right angle through the fluid force transmission mechanism and transmitted to the rod of the solenoid valve, so that the refrigerant gas force is linear. Compared with the case of being transmitted to the rod of the solenoid valve, the total length of the control valve is shortened, and the control valve is miniaturized.

A control valve of a variable capacity swash plate compressor according to an embodiment of the present invention will be described.

As shown in FIG. 1, a variable capacity swash plate compressor 1, a condenser 2, an expansion valve 3, and an evaporator 4 constitute an in-vehicle air conditioner A. The air conditioner A includes a damper 5, a blower 6, and an air conditioning operation panel 7 that switch an air passage between the introduction of outside air and the circulation of inside air.
The air conditioning operation panel 7 is equipped with an ON / OFF switch for the air conditioner A operated by a vehicle occupant, a temperature setting device, and the like. In the vicinity of the evaporator 4, a temperature sensor for detecting the air temperature in the passenger compartment is disposed. A vehicle (not shown) is equipped with various sensors for detecting the vehicle running state, such as a vehicle speed sensor, an engine speed sensor, and a throttle opening sensor. The ON / OFF switch, temperature setter, temperature sensor, and various sensors that detect the vehicle running state constitute an external information detection device 8.

The variable capacity swash plate compressor 1 includes a main shaft (not shown) connected to a vehicle engine (not shown) without a clutch, a swash plate (not shown) attached to the main shaft so as not to rotate relative to the main shaft, and a shoe. A piston (not shown) that engages with the swash plate and linearly reciprocates in synchronization with the rotation of the swash plate, a cylinder bore 1a into which the piston is slidably inserted, and a discharge chamber 1b that communicates with the cylinder bore 1a through a discharge valve. A crank chamber 1c that accommodates the main shaft and the swash plate, and a suction chamber 1d that communicates with the cylinder bore 1a via a suction valve are provided. The crank chamber 1c and the suction chamber 1d communicate with each other through an orifice hole 1e.

  The discharge chamber 1b of the variable capacity swash plate compressor 1, the condenser 2, the expansion valve 3, the evaporator 4, and the suction chamber 1d of the variable capacity swash plate compressor 1 are sequentially connected by a refrigerant circuit 9. Yes.

A control valve 10 for controlling the discharge capacity of the variable capacity swash plate compressor 1 is provided. The control valve 10 controls the operation of the valve body 11, the aforementioned external information detection device 8, and the solenoid valve that forms a part of the valve body 11 based on the external information input from the external information detection device 8. The apparatus 12 and the drive circuit 13 of a solenoid valve are provided. The main body 11 of the control valve is disposed in the middle of the refrigerant circuit 9.

The configuration of the valve body 11 will be described in detail.
As shown in FIG. 2, the valve body 11 of the control valve includes a coil 11a, a fixed iron core 11b, a movable iron core 11c, a rod 11d fixed to the movable iron core 11c, and a direction in which the movable iron core 11c is moved away from the fixed iron core 11b. There is provided an electromagnetic valve 11h composed of a spring 11e urging the valve 11b, a valve body 11f formed at a substantially central portion in the length direction of the rod 11d, and a valve seat 11g with which the valve body 11f can come into contact. The coil 11a is connected to the drive circuit 13 through a conducting wire (not shown). When the valve body 11f abuts on the valve seat 11g, the communication passage 11i between the discharge chamber 1b and the crank chamber 1c of the variable capacity swash plate compressor 1 is closed, and the valve body 11f is separated from the valve seat 11g. The communication path 11i between the discharge chamber 1b and the crank chamber 1c of the variable capacity swash plate compressor 1 is opened.

The valve body 11 of the control valve includes a disk-shaped pressure receiving piece 11j disposed in the refrigerant gas flowing through the refrigerant circuit 9. The pressure receiving piece 11j is disposed orthogonal to the flow of the refrigerant gas. The pressure receiving piece 11j is disposed in a diameter expanding portion 9a of the refrigerant circuit 9 that expands in a funnel shape from upstream to downstream. The enlarged diameter portion 9a is orthogonal to the rod 11d of the electromagnetic valve 11h. A columnar protrusion 11j ′ extending from the downstream end face of the pressure receiving piece 11j is slidably inserted into a through hole formed in a support arm 11k extending from the surrounding wall of the refrigerant circuit 9. The pressure receiving piece 11j forms a throttle that generates a differential pressure between two points in the enlarged diameter portion 9a.

An L-shaped lever member 11m is swingably disposed downstream of the pressure receiving piece 11j. One arm of the lever member 11m can come into contact with the tip of the columnar protrusion 11j '. A nut 11n for adjusting the rod length is screwed to the tip of the rod 11d. The other arm of the lever member 11m can come into contact with the tip of the rod 11d through the nut 11n.

The operation of the control valve 10 according to this embodiment having the above configuration will be described.
A main shaft (not shown) of the variable capacity swash plate compressor 1 is driven by a vehicle engine (not shown) and is always rotating.
During the operation of the air conditioner A, the control device 12 is the target discharge capacity Q of the variable capacity swash plate compressor 1 and thus the refrigerant gas flowing through the refrigerant circuit 9 based on the external information input from the external information detection device 8. A target flow rate Q of the discharge gas of the variable capacity swash plate compressor 1 is determined, and an electromagnetic valve supply power value corresponding to the target flow rate Q is determined. The control device 12 duty-controls the power supplied to the coil 11a of the electromagnetic valve 11h via the drive circuit 13. The magnetized movable iron core 11c receives an electromagnetic force from the magnetized fixed iron core 11b and moves in a direction approaching the fixed iron core 11b against the biasing force of the spring 11e. The valve body 11f comes into contact with the valve seat 11g, and the communication path 11i between the discharge chamber 1b and the crank chamber 1c is closed.
The compressor discharge gas is prevented from flowing into the crank chamber 1c. Since the gas in the crank chamber 1c flows out to the suction chamber 1d through the orifice hole 1e, the internal pressure of the crank chamber 1c decreases, the inclination angle of a swash plate (not shown) increases, and the discharge capacity of the variable displacement swash plate compressor 1 Increases, the flow rate of the refrigerant gas flowing through the refrigerant circuit 9 increases, the differential pressure between the primary pressure P1 and the secondary pressure P2 of the pressure receiving piece 11j increases, and consequently the refrigerant gas applied to the pressure receiving piece 11j. The fluid force increases.

When the refrigerant gas flows through the refrigerant circuit 9, the pressure receiving piece 11j that receives the fluid force from the refrigerant gas flow moves to the downstream side with respect to the refrigerant gas flow, and the columnar protrusion 11j 'comes into contact with one arm of the lever member 11m. The member 11m swings, and the other arm of the lever member 11m comes into contact with the nut 11n. As a result, the pressure receiving piece 11j contacts the tip of the rod 11d via the lever member 11m and the nut 11n. The fluid force of the refrigerant gas applied to the pressure receiving piece 11j is bent at a right angle through the lever member 11m and transmitted to the rod 11d of the electromagnetic valve. With the valve body 11f in contact with the valve seat 11g, the pressure receiving piece 11j moves downstream with respect to the refrigerant gas flow and contacts the lever member 11m, and the lever member swings and contacts the tip of the rod 11d. The position of the pressure receiving piece 11j at the time is referred to as an initial position of the pressure receiving piece 11j in the following description.

The fluid force of the refrigerant gas that is transmitted from the pressure receiving piece 11j to the rod 11d through the lever member 11m and the nut 11n is supplied from the fixed core 11b through the movable core 11c under the supply power value that corresponds to the target flow rate Q. As long as it is smaller than the electromagnetic force applied to the rod 11d, the state in which the valve body 11f is in contact with the valve seat 11g is maintained, and the state in which the electromagnetic valve 11h closes the communication path 11i is maintained. As a result, the inclination angle of the swash plate increases, the discharge capacity of the variable capacity swash plate compressor 1 increases, and the flow rate of the refrigerant gas flowing through the refrigerant circuit 9 increases. The pressure receiving piece 11j is stopped at the initial position.

The flow rate of the refrigerant gas flowing through the refrigerant circuit 9 increases, and the fluid force of the refrigerant gas transmitted from the pressure receiving piece 11j to the rod 11d through the lever member 11m and the nut 11n has a supply power value corresponding to the target flow rate Q. When the electromagnetic force applied to the rod 11d from the fixed iron core 11b through the movable iron core 11c is exceeded, the pressure receiving piece 11j that receives the fluid force moves downstream from the initial position with respect to the refrigerant gas flow. The columnar protrusion 11j ′ swings the lever member 11m, the lever member 11m pushes the rod 11d, the rod 11d moves, and the valve body 11f moves away from the valve seat 11g. The communication path 11i between the discharge chamber 1b and the crank chamber 1c is opened.
The compressor discharge gas flows into the crank chamber 1c, the internal pressure of the crank chamber 1c increases, the inclination angle of a swash plate (not shown) decreases, the discharge capacity of the variable capacity swash plate compressor 1 decreases, and flows through the refrigerant circuit 9. As the flow rate of the refrigerant gas decreases, the differential pressure between the primary side pressure P1 and the secondary side pressure P2 of the pressure receiving piece 11j decreases, and as a result, the fluid force of the refrigerant gas applied to the pressure receiving piece 11j decreases.

The fluid force of the refrigerant gas marked on the rod 11d through the lever member 11m and the nut 11n from the pressure receiving piece 11j under the supply power value corresponding to the target flow rate Q from the fixed iron core 11b through the movable iron core 11c. When it becomes smaller than the electromagnetic force applied to the rod 11d, the rod 11d moves, the valve body 11f contacts the valve seat 11g, and the communication path 11i between the discharge chamber 1b and the crank chamber 1c is closed.
As the compressor discharge gas is prevented from flowing into the crank chamber 1c and the gas in the crank chamber 1c flows out into the suction chamber 1d through the orifice hole 1e, the internal pressure of the crank chamber 1c decreases, not shown. The inclination angle of the swash plate increases, the discharge capacity of the variable capacity swash plate compressor 1 increases, the flow rate of the refrigerant gas flowing through the refrigerant circuit 9 increases, and the primary pressure P1 and the secondary pressure P2 of the pressure receiving piece 11j. And the fluid force of the refrigerant gas applied to the pressure receiving piece 11j increases.

Opening and closing of the communication passage 11i by the valve body 11 is autonomously repeated, and introduction and stoppage of the compressor discharge gas into the crank chamber 1c are autonomously repeated to adjust the internal pressure of the crank chamber 1c autonomously, Feedback control is performed so that the flow rate of the compressor discharge gas that passes through the pressure receiving piece 11j approaches the target flow rate Q, and consequently feedback control is performed so that the discharge capacity of the variable displacement swash plate compressor 1 approaches the target value Q.

When the ON / OFF switch of the air conditioner A is turned OFF and the air conditioner A is stopped, the control device 12 stops the power supply to the coil 11 a via the drive circuit 13.
The application of electromagnetic force from the fixed iron core 11b to the movable iron core 11c stops, the movable iron core 11c moves in a direction away from the fixed iron pipe 11b under the urging force of the spring 11e, and the valve body 11f moves away from the valve seat 11g. As a result, the communication passage 11i is opened, and the compressor discharge gas flows into the crank chamber 1c via the communication passage 11i, the internal pressure of the crank chamber 1c increases, the inclination angle of the swash plate decreases, and the variable displacement swash plate compression The discharge capacity of the machine 1 decreases to a minimum value. As a result, waste of energy generated by the vehicle engine is suppressed.
The discharge gas that has flowed into the crank chamber 1c through the control valve 10 flows into the suction chamber 1d through the orifice hole 1e and continues to operate from the suction chamber 1d as indicated by a thick double arrow in FIG. The air is sucked into the cylinder bore 1 a of the swash plate compressor 1, discharged from the cylinder bore 1 a to the discharge chamber 1 b, and returned to the control valve 10.

In the control valve 10, the pressure receiving piece 11 j disposed in the refrigerant gas flowing through the refrigerant circuit 9 forms a throttle, and a part of the valve body 11 that cuts in the introduction of the compressor discharge gas into the crank chamber 1 c. Therefore, there is no need to provide a passage for guiding the differential pressure before and after the throttle to the valve body 11. Therefore, the control valve 10 can feedback control the discharge capacity of the compressor 1 with a simple configuration.
In the control valve 10, the fluid force of the refrigerant gas applied to the pressure receiving piece 11j is bent at a right angle through the lever member 11m and transmitted to the rod 11d of the solenoid valve, so that the fluid force is linearly changed to the solenoid valve. The total length of the control valve 10 is shortened and the control valve 10 is downsized as compared with the case where the control valve 10 is transmitted to the rod 11d.

In the control valve 10, by disposing the pressure receiving piece 11j in the funnel-shaped enlarged portion 9a of the refrigerant circuit, it is possible to suppress the valve body 11 from reacting sensitively to changes in the flow rate of the refrigerant gas flowing through the refrigerant circuit 9. Yes.
After the pressure receiving piece 11j starts moving from the initial position to the downstream side, the pressure receiving piece 11j moves to the downstream side or the upstream side according to the magnitude relationship between the applied fluid force and the electromagnetic force. When the flow rate of the refrigerant gas increases and the pressure receiving piece 11j moves to the downstream side, the clearance S between the surrounding wall of the funnel-shaped enlarged diameter portion 9a of the refrigerant circuit and the pressure receiving piece 11j widens, and the pressure loss of the throttle formed by the pressure receiving piece 11j. Decrease. As a result, an increase in the fluid force applied to the pressure receiving piece 11j is suppressed. When the refrigerant gas flow rate decreases and the pressure receiving piece 11j moves to the upstream side, the gap S between the surrounding wall of the funnel-shaped enlarged diameter portion 9a of the refrigerant circuit and the pressure receiving piece 11j is narrowed, and the pressure loss of the throttle formed by the pressure receiving piece 11j is reduced. Will increase. As a result, a decrease in fluid force applied to the pressure receiving piece 11j is suppressed. By suppressing the increase or decrease of the fluid force applied to the pressure receiving piece 11j caused by the increase or decrease of the refrigerant flow rate in the refrigerant circuit 9, the valve body 11f reacts to the increase or decrease of the refrigerant flow rate and the valve seat 11g. Is repeated, and the occurrence of a situation in which the controllability of the valve body 11 and thus the control valve 10 deteriorates is prevented.

When the refrigerant gas flow rate reaches the target flow rate Q, the fluid force applied to the pressure receiving piece 11j needs to be equal to the electromagnetic force commensurate with the target flow rate Q applied to the rod 11d of the solenoid valve. The fluid force applied to the pressure receiving piece 11j is caused by a pressure loss when the refrigerant gas flows through the gap S between the pressure receiving piece 11j and the funnel-shaped enlarged diameter portion 9a of the refrigerant circuit, so It is necessary to accurately manage the clearance S between the pressure receiving piece 11j and the surrounding wall of the funnel-shaped enlarged portion 9a of the refrigerant circuit. In the control valve 10, by adjusting the screwing amount of the nut 11n to adjust the length of the rod 11d including the nut 11n, the pressure receiving piece 11j in the initial position and the funnel-shaped enlarged portion 9a surrounding wall of the refrigerant circuit The gap S between the two is accurately managed, and as a result, the performance of the control valve 10 is enhanced. In order to assemble the members of the control valve 10 while accurately managing the gap S between the pressure receiving piece 11j and the funnel-shaped enlarged portion 9a of the refrigerant circuit, it is necessary to improve the assembling accuracy. The workability for improving the assembly accuracy is enhanced by the arrangement of the nut 11n.

Instead of operatively engaging the pressure receiving piece 11j with the rod 11d via the lever member 11m, as shown in FIG. 3, a rack 11p fixed to the columnar protrusion 11j 'of the pressure receiving piece 11j meshes with the rack 11p. The pressure receiving piece 11j is actuated on the rod 11d via a rack and pinion mechanism 11s composed of a gear 11q and a rack 11r which is disposed perpendicular to the rack 11p and press-fitted into the tip of the rod 11d and meshes with the gear 11q. A shim 11t that engages and adjusts the length of the rod 11d including the rack 11r may be inserted into the press-fit portion.
The fluid force applied to the pressure receiving piece 11j is bent at a right angle via the rack and pinion mechanism 11s and transmitted to the rod 11d of the solenoid valve, so that the fluid force is transmitted linearly to the rod 11d of the solenoid valve. Compared to the case, the overall length of the control valve 10 is shortened, and the control valve 10 is downsized.

By adjusting the thickness of the shim 11t, finely adjusting the length of the rod 11d including the rack 11r, and finely adjusting the meshing state of the rack 11r and the gear 11q, the valve body 11f comes into contact with the valve seat 11g. The clearance S between the pressure receiving piece 11j and the surrounding wall of the funnel-shaped enlarged portion 9a of the refrigerant circuit in a state where the valve body 11 closes the communication passage 11i is accurately managed.

The present invention can be widely used as a control valve for a variable capacity swash plate compressor used in an air conditioner for air conditioning.

It is a block diagram of a variable capacity swash plate type compressor provided with a control valve concerning an example of the present invention, and a block diagram of a vehicle-mounted air conditioner provided with the compressor concerned. It is sectional drawing of the control valve which concerns on 1st Example of this invention. It is sectional drawing of the control valve which concerns on 2nd Example of this invention.

Explanation of symbols

A In-vehicle air conditioner 1 Variable capacity swash plate compressor 2 Condenser 3 Expansion valve 4 Evaporator 8 External information detection device 9 Refrigerant circuit 9a Funnel-shaped enlarged portion 10 Control valve 11 Valve body 11h Electromagnetic valve 11j Pressure receiving piece 11m Insulator member 11n Nut 11s Rack and pinion mechanism 12 Controller 13 Drive circuit

Claims (5)

A control valve for a variable capacity swash plate compressor used in an air conditioner for heating and cooling, comprising a pressure receiving piece disposed in the refrigerant gas flowing through the refrigerant circuit, an electromagnetic valve, and a refrigerant gas applied to the pressure receiving piece. A fluid force transmission mechanism for transmitting a fluid force to the rod of the solenoid valve; an external information detection means for detecting a cooling load, a vehicle running state, etc .; and a control means for controlling a power value supplied to the solenoid valve based on the external information; The solenoid valve is configured to introduce the compressor discharge gas into the crank chamber according to the magnitude relationship between the fluid force of the refrigerant gas flowing through the refrigerant circuit transmitted from the pressure receiving piece to the rod and the electromagnetic force applied to the rod. And the fluid force of the refrigerant gas applied to the pressure receiving piece is bent at a right angle through the fluid force transmission mechanism and transmitted to the rod of the solenoid valve. valve. 2. The variable force transmission mechanism according to claim 1, wherein the fluid force transmission mechanism is an L-shaped lever member in which one arm can abut against the pressure receiving piece and the other arm can abut against the rod of the electromagnetic valve. Control valve for capacity swash plate compressor. The fluid force transmission mechanism is a rack and pinion mechanism having a first rack attached to the pressure receiving piece, a second rack attached to the rod of the solenoid valve, and a gear meshing with the first rack and the second rack. The control valve for a variable capacity swash plate compressor according to claim 1. The control valve for a variable capacity swash plate compressor according to any one of claims 1 to 3, wherein the pressure receiving piece is disposed in a funnel-shaped enlarged portion of the refrigerant circuit. The control valve for a variable capacity swash plate compressor according to any one of claims 1 to 4, further comprising a rod length adjusting member.

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