JP4365691B2 - Control valve for variable capacity compressor - Google Patents

Description

  The present invention relates to a control valve for a variable capacity compressor used in a refrigeration cycle of an air conditioner for an automobile, and more particularly, to control the intake pressure of the variable capacity compressor to a value set by a duty ratio control solenoid. The present invention relates to a control valve for a variable capacity compressor that controls pressure.

  Since the compressor used for compressing the refrigerant in the refrigeration cycle of the air conditioner for automobiles uses the engine as a drive source, the rotational speed control cannot be performed. Therefore, in order to obtain an appropriate cooling capacity without being restricted by the engine speed, a variable capacity compressor capable of changing the compression capacity of the refrigerant is used.

  In such a variable capacity compressor, a compression piston is connected to a rocking plate attached to a shaft that is rotationally driven by an engine, and the stroke of the piston is changed by changing the angle of the rocking plate. The discharge amount, that is, the capacity of the compressor is changed.

  The angle of the oscillating plate is continuously changed by introducing a part of the compressed refrigerant into the sealed crank chamber, changing the pressure Pc in the crank chamber, and changing the balance of pressure applied to both surfaces of the piston. It is changing.

  The pressure Pc in the crank chamber of the variable capacity compressor forms a refrigerant passage between the discharge chamber and the crank chamber of the variable capacity compressor and between the crank chamber and the suction chamber, and passes through the crank chamber from the discharge chamber. It can be changed by controlling the flow rate of the refrigerant flowing into the suction chamber. Specifically, a control valve is provided in one of the refrigerant passages between the discharge chamber and the crank chamber and between the crank chamber and the suction chamber, an orifice is provided in the other refrigerant passage, and the control valve passes through the refrigerant passage. The pressure Pc in the crank chamber is controlled by opening / closing control so as to communicate or block. In addition, two valves are arranged in the refrigerant passages between the discharge chamber and the crank chamber and between the crank chamber and the suction chamber and interlocked with each other, and the refrigerant passages before and after the crank chamber are controlled to open and close simultaneously. A control valve for controlling the pressure Pc in the crank chamber is also known.

  The control valve includes a pressure sensing part that senses the suction pressure Ps. The pressure sensing part senses the suction pressure Ps that fluctuates, and the pressure in the crank chamber is set so that the suction pressure Ps becomes a predetermined pressure. A type of control valve that controls Pc is known. The predetermined pressure can be freely set from the outside by changing the value of the current supplied to the solenoid, whereby the variable capacity compressor is controlled to a desired capacity regardless of the engine speed. Will be.

  Capacitance control is performed by supplying a current corresponding to the set capacity to the solenoid of the control valve. However, there is a case where capacity control is performed by supplying a pulse current of about 400 Hz and changing its duty ratio. is there. By supplying pulsed current, the valve element driven by it always vibrates slightly in its opening and closing direction, so that the hysteresis of the valve characteristic can be minimized, thereby providing a stable valve characteristic be able to. The control valve of this duty ratio control is controlled so that the set load is set by the average current value to the solenoid according to the duty ratio, and the discharge capacity of the refrigerant from the variable capacity compressor becomes the set capacity. (For example, refer to Patent Document 1).

In such a control valve, a ball-shaped ball valve, a tapered needle valve or tapered valve, a flat flat valve, or the like is employed. The flow rate control of the refrigerant from the discharge chamber to the crank chamber is performed by changing the lift amount of the valve body.When the variable capacity compressor is operated with the minimum capacity, the lift amount is maximum, and when the maximum capacity is operated, The lift amount is minimized, that is, the valve is closed.
JP 2001-342946 A (paragraph [0019])

  However, in a duty ratio control valve, the valve body and the shaft that drives the valve body vibrate slightly in the longitudinal direction thereof, so that the valve body is not closed during the valve closing operation or when the valve body is in the vicinity of the valve closing position. When driven in the valve closing direction from the desired lift position, the valve element hits the valve seat and rebounds, and the valve element moves in the valve opening direction, resulting in a problem that the valve lift characteristic becomes non-linear.

In addition, when the valve is closed, the slightly vibrating valve body directly and repeatedly collides with the valve seat, which causes a problem that durability of the valve body and the valve seat is lowered.
The present invention has been made in view of these points, and an object thereof is to provide a control valve for duty ratio control for a variable capacity compressor having improved characteristics in the vicinity of the valve closing position.

  In the present invention, in order to solve the above problem, in the control valve of the variable capacity compressor that controls the pressure in the crank chamber so that the suction pressure of the variable capacity compressor becomes a value set by the duty ratio control solenoid, the refrigerant is A valve portion for controlling opening and closing of a passage between the first port to be introduced and the second port from which the refrigerant is led out is configured by a spool valve, and the solenoid force of the valve body of the spool valve and the solenoid is applied to the valve body. Control of a variable capacity compressor characterized in that a transmission shaft is integrally formed with the same outer diameter, and a valve hole into which the valve body is inserted and removed and a holding hole of the shaft are formed with the same inner diameter. A valve is provided.

  According to the control valve of such a variable capacity compressor, the valve portion is constituted by a spool valve, so that the valve body of the spool valve is slightly vibrated in the valve opening / closing direction by the duty ratio being controlled by the solenoid. Even so, there is no collision of the valve body with the valve seat due to vibration in the vicinity of the valve closing position, so there is no valve opening phenomenon due to collision with the valve seat immediately before valve closing, not only the lift characteristics are improved, The durability of the parts is improved. Also, by integrating the valve body and the shaft and forming the same outer diameter, the tolerance of the outer diameter and the surface roughness accuracy of the integrated parts can be easily increased, and the valve formed on the body Since the hole and the shaft holding hole have the same inner diameter, the tolerance of the inner diameter and the accuracy of the surface roughness can be easily increased, so that the internal leakage of the refrigerant when the spool valve is closed can be suppressed. .

  In the control valve of the variable capacity compressor of the present invention, since the valve body and the shaft are integrated and the outer diameter is the same, the integrated parts can be centerless polished. There is an advantage that the accuracy can be increased. Further, since the valve hole formed in the body and the holding hole of the shaft have the same inner diameter, burnishing can be performed, so that the tolerance of the inner diameter and the accuracy of the surface roughness can be increased. By increasing these precisions, the internal leakage of the refrigerant when the spool valve is essentially closed can be reduced. Furthermore, by integrating the valve body and the shaft, the number of parts can be reduced and the cost can be reduced.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a cross-sectional view showing the control valve according to the first embodiment when the valve is open, and FIG. 2 is a cross-sectional view showing the control valve according to the first embodiment when the valve is closed.

  This control valve includes a valve portion 10, a pressure sensitive portion 11, and a solenoid portion 12, and constitutes an external variable control type control valve that can control a set value by an electric signal from the outside. The body 13 of the valve portion 10 has a port 14 opened at one end portion in the longitudinal direction, and a port 15 and a port 16 formed so as to penetrate in the radial direction. When these control valves are incorporated in a variable capacity compressor (not shown), the ports 14, 15, and 16 are connected to the discharge chamber to introduce the refrigerant having the discharge pressure Pd, and the port 15 is connected to the crank chamber. The refrigerant of the controlled pressure Pc is led out in communication with the port 16 and the port 16 is in communication with the suction chamber so that the pressure sensing part 11 senses the suction pressure Ps.

  A valve hole 17 is provided between the port 14 and the port 15 in the axial direction of the body 13, and a valve body 18 is disposed on the port 14 side so as to be detachable from the valve hole 17. Yes. The valve body 18 is urged in the valve closing direction by a spring 20 via a spring receiving portion 19. The upper end of the spring 20 is received by an adjustment screw 21, and the spring load is adjusted by the screwing amount of the adjustment screw 21 into the port 14. A strainer 22 is provided at the end of the body 13 where the port 14 is opened so as to cover the port 14 into which the refrigerant having the discharge pressure Pd is introduced.

  The valve body 18 is formed integrally with a shaft 23 that penetrates the valve hole 17 and extends in the axial direction, and the shaft 23 is held by the body 13 so as to be movable forward and backward in the axial direction. One end of the shaft 23 connected to the valve body 18 is reduced in diameter to form a spool, whereby the valve portion 10 of this control valve constitutes a spool valve.

  The outer diameters of the valve body 18 and the shaft 23 are formed to have the same dimension, and the inner diameters of the valve hole 17 and the holding hole of the shaft 23 in which the valve body 18 and the shaft 23 slide correspond to the same dimension. Is formed. Since these dimensions are directly related to the internal leakage amount of the refrigerant in the valve section 10, it is necessary to manage the diameter and surface roughness with as high accuracy as possible to eliminate radial clearance.

  The integrally formed valve body 18 and shaft 23 are processed by centerless polishing, in which their surfaces are scraped with high precision by a grindstone that rotates at high speed. In particular, since the outer diameter dimensions thereof are the same and the valve body 18 and the shaft 23 can be processed simultaneously by passing polishing, the valve body 18 and the shaft 23 are individually polished in a separate process by stop polishing. Compared to the above, the manufacturing cost can be reduced, and the tolerance of the outer diameter and the surface roughness can be managed with high accuracy.

  Further, since the valve hole 17 and the holding hole of the shaft 23 are also concentrically arranged and have the same inner diameter, their inner wall surfaces can be mirror-finished simultaneously. That is, by drilling a hole smaller than the desired inner diameter in the center of the body 13 in the axial direction and forcibly passing a hard steel ball having a high sphericity with an outer diameter equal to the desired inner diameter into the hole. It is possible to use a burnishing method in which a smooth mirror surface is finished by a burnishing action that crushes unevenness of the surface roughness on the sliding surface, and thereby it is possible to manage the tolerance of the inner diameter and the surface roughness with high accuracy. .

  The pressure sensing unit 11 disposed between the valve unit 10 and the solenoid unit 12 and sensing the suction pressure Ps uses the diaphragm 24 as a pressure sensing member. The outer peripheral edge of the diaphragm 24 is held in an airtight state by the body 13 and the solenoid part 12, and the center disk 25 is disposed in contact with the central part on the valve part 10 side. The center disk 25 is fitted with the other end of a shaft 23 having one end formed integrally with the valve body 18.

  The space in which the center disk 25 is disposed communicates with the port 16 and is configured such that the diaphragm 24 receives the suction pressure Ps of the suction chamber of the variable capacity compressor. Thus, the diaphragm 24 receives the introduced suction pressure Ps and is displaced in the vertical direction in the figure, and can control the lift amount of the valve body 18 via the center disk 25 and the shaft 23.

  The solenoid part 12 has a sleeve 27 around which a coil 26 is provided, and a core 28 forming a fixed iron core is fixed to the lower end part of the figure. A plunger 29 forming a movable iron core is slidably disposed in the sleeve 27 in a state in which the plunger 29 is urged toward the diaphragm 24 by a spring 30. The shaft 31 is disposed at the axial position of the core 28 and the plunger 29, one end thereof is supported by a bearing portion 33 disposed in the connector housing 32, and the other end is fixed by being press-fitted into the plunger 29. Yes. The coil 26 is surrounded by a case 34 that forms a yoke of the magnetic circuit.

  Here, when the coil 26 is energized, the plunger 29 is attracted by the core 28, so that the valve element 18 is inserted into the valve hole 17 by the spring 20 and is closed. On the other hand, if the coil 26 is in a non-energized state, the urging force of the spring 30 acts on the plunger 29, and the shaft 23 is pushed upward from the diaphragm 24 in contact with the plunger 29 via the center disk 25 in the figure. Therefore, the valve body 18 is lifted in the valve opening direction by a predetermined distance.

  Thus, in this control valve, since the valve opening degree of the valve unit 10 is set by the solenoid force by the solenoid unit 12 and is changed by sensing the suction pressure Ps, the suction pressure Ps of the variable capacity compressor is changed to the solenoid. A valve for controlling the pressure Pc in the crank chamber is configured so as to have a value set by the section 12.

Next, the operation of the control valve of the present invention will be described.
First, when the automobile air conditioner is stopped, the solenoid unit 12 is in a non-energized state. At this time, as shown in FIG. 1, the spring 30 of the solenoid portion 12 having a larger spring force than the spring 20 that biases the valve element 18 in the valve closing direction biases the plunger 29 in the valve opening direction. As a result, the integrated valve body 18 and shaft 23 are pushed upward in the figure, and the valve portion 10 is maintained in a fully open state. As a result, the pressure Pc in the crank chamber of the variable displacement compressor becomes a pressure close to the discharge pressure Pd, so that the inclination angle of the swash plate is minimized and the piston stroke is minimized. It will be operated at the minimum capacity.

  When the automobile air conditioner is started, the maximum current is supplied to the coil 26 of the solenoid unit 12. As a result, the plunger 29 is sucked and adsorbed by the core 28, so that the plunger 29 moves to a position farthest from the valve portion 10 as shown in FIG. As a result, the valve body 18 is moved into the valve hole 17 by the urging force of the spring 20, and the valve unit 10 is fully closed. Therefore, the pressure Pc in the crank chamber of the variable capacity compressor becomes a pressure close to the suction pressure Ps, and the variable capacity compressor is operated at the maximum capacity.

  When the variable capacity compressor is operated at its maximum capacity and eventually the temperature of the air blown from the air conditioner approaches the set temperature, the current supplied to the coil 26 of the solenoid unit 12 is changed to change the control valve. Change the set value. In the solenoid unit 12, the set value of the control valve is changed by controlling the duty ratio of the pulse current flowing through the coil 26. That is, by reducing the duty ratio and reducing the average current value, the urging force of the spring 30 can be increased, thereby increasing the lift amount of the valve body 18 and setting the valve opening degree large.

  Here, when a pulse current having a duty ratio in the coil 26 is supplied and the valve unit 10 is set to a predetermined valve opening, for example, when the suction pressure Ps is lowered, the diaphragm 24 is moved upward in the figure. And the valve body 18 is driven in the valve opening direction to increase the valve opening. As a result, the flow rate of refrigerant supplied to the crank chamber increases and the internal pressure Pc increases, the discharge capacity of the variable capacity compressor decreases, and the suction pressure Ps increases.

  On the contrary, when the suction pressure Ps increases, the diaphragm 24 is displaced downward in the drawing to drive the valve body 18 in the valve closing direction, thereby reducing the valve opening degree. As a result, the flow rate of the refrigerant supplied to the crank chamber decreases, the pressure Pc in the crank chamber decreases, the discharge capacity of the variable capacity compressor increases, and the suction pressure Ps attempts to decrease.

  When the duty ratio of the pulse current flowing through the coil 26 is increased while the valve unit 10 is controlled to a predetermined valve opening, the plunger 29 is attracted to the core 28 and the valve body 18 is closed. Move in the direction. At this time, the valve body 18 moves downward in the figure while slightly vibrating in the axial direction. Alternatively, even when the suction pressure Ps is increased when the valve body 18 is controlled to have a valve opening in the vicinity of the valve closing position, the valve body 18 moves downward in the figure while slightly vibrating in the valve opening / closing direction. Go to.

  However, in the valve portion 10 having the spool valve structure, even when the valve body 18 reaches the opening end surface of the valve hole 17 and passes through the opening end surface and is inserted into the valve hole 17, the valve body 18 is not connected to the valve hole 17. 17 does not collide with the body 13 constituting 17.

  Accordingly, not only can the lift characteristic of the control valve in the vicinity of the valve closing position be made substantially linear, but also the valve element 18 does not collide directly and repeatedly with the body 13, so that the durability of the valve unit 10 is improved. Can maintain its initial characteristics.

  FIG. 3 is a cross-sectional view showing a control valve according to the second embodiment. In FIG. 3, the same or equivalent elements as those of the control valve shown in FIGS. 1 and 2 are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the control valve according to the second embodiment, the positions of the port 14 for introducing the discharge pressure Pd and the port 15 for deriving the controlled pressure Pc are compared with the control valve according to the first embodiment. Is reversed. Since the port 14 for introducing the discharge pressure Pd is formed on the side surface of the body 13, the strainer 22 for removing foreign matter in the refrigerant introduced into the control valve covers the body 13 so as to cover the port 14. Is installed around.

  This control valve is configured such that the integrally formed valve body 18 and the shaft 23 have the same outer shape, and the discharge pressure Pd is introduced into the reduced diameter spool. Therefore, in this spool, the force that the discharge pressure Pd acts on the valve element 18 in the valve opening direction is the same as the force that the discharge pressure Pd acts on the shaft 23 in the valve closing direction. However, the discharge pressure canceling structure does not contribute to the opening / closing operation of the valve unit 10. With this structure, the solenoid unit 12 does not need to generate a solenoid force that opposes the discharge pressure Pd having a large pressure, and therefore can be controlled with a small solenoid force regardless of the magnitude of the discharge pressure Pd. Moreover, even if the discharge pressure Pd introduced into the control valve fluctuates greatly, the pressure fluctuation does not affect the control of the valve opening.

  The pressure sensitive part 11 and the solenoid part 12 other than the valve part 10 have exactly the same configuration as the control valve according to the first embodiment. Therefore, since the operation and effect of the control valve according to the second embodiment are the same as those of the control valve according to the first embodiment, the description thereof is omitted here.

  FIG. 4 is a cross-sectional view showing a control valve according to the third embodiment. 4, the same or equivalent elements as those of the control valve shown in FIG. 3 are denoted by the same reference numerals, and detailed description thereof is omitted.

  The control valve according to the third embodiment is different from the control valve according to the second embodiment in that a set value adjusting mechanism is provided on the atmospheric pressure side. In other words, the spring receiving portion 19, the spring 20, and the adjusting screw 21 that the control valve shown in FIG. 3 has are excluded from the valve portion 10, and the adjusting screw 35 is provided in the connector housing 32. The adjustment screw 35 is screwed into the connector housing 32, and the spring load of the spring 30 urging the plunger 29 of the solenoid portion 12 in the direction of the pressure-sensitive portion 11 can be adjusted by the amount of screwing into the connector housing 32. I am doing so.

  The adjustment screw 35 has a recessed bearing portion that receives the shaft 31 of the solenoid portion 12 at the axial position. Thus, both ends of the shaft 31 are supported by the plunger 29 and the adjusting screw 35 so as to be movable back and forth in the axial direction.

  Further, the shaft 23 integrated with the valve body 18 is fitted with the center disk 25 at the lower end portion in the drawing so that the shaft 23 can move forward and backward in the axial direction. The center disk 25 is urged in the direction of the diaphragm 24 by a spring 36, and ensures the urging force in the valve closing direction of the valve body 18 that is lost by eliminating the spring 20 of the valve portion 10.

  FIG. 5 is a cross-sectional view showing a control valve according to the fourth embodiment. In FIG. 5, the same or equivalent elements as those of the control valve shown in FIG. 4 are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the control valve according to the fourth embodiment, the valve body 18, the shaft 23, and the center disk 25 are integrally formed as compared with the control valve according to the third embodiment. Is different. Thus, by integrally forming the valve body 18, the shaft 23, and the center disk 25, the number of parts can be reduced and the assemblability can be further improved.

  FIG. 6 is a cross-sectional view showing a control valve according to the fifth embodiment. In FIG. 6, the same or equivalent elements as those of the control valve shown in FIGS. 1 to 4 are denoted by the same reference numerals, and detailed description thereof is omitted.

  The control valve according to the fifth embodiment controls the flow rate of the refrigerant supplied from the discharge chamber of the variable capacity compressor to the crank chamber by the control valve according to the first to fourth embodiments. On the other hand, the difference is that the flow rate of the refrigerant fed from the discharge chamber to the crank chamber and the flow rate of the refrigerant extracted from the crank chamber to the suction chamber are controlled simultaneously.

  For this reason, the valve section 10 includes a first valve that supplies the crank chamber with a pressure Pc1 that is controlled by receiving the discharge pressure Pd from the discharge chamber, and a suction pressure that is controlled by receiving the pressure Pc2 (= Pc1) from the crank chamber. And a second valve for supplying Ps to the suction chamber.

  The first valve has the same configuration as the valve portion 10 of the control valve according to the third and fourth embodiments. Between the port 14 communicated with the discharge chamber and the port 16 communicated with the suction chamber, there is a port 15 a formed penetrating in the radial direction of the body 13. A valve hole 37 is provided between the port 15 a and the port 16 in the axial direction of the body 13, and a valve body 38 is disposed in the space communicating with the port 16 so as to be detachable from the valve hole 37. Has been. The valve body 38 is formed integrally with a shaft 39 that is reduced in diameter to form a spool, and constitutes a second valve having a spool valve structure.

  In this second valve, the valve body 38 has an outer diameter that is smaller than the inner diameter of the valve hole 37, and the valve body 38 is in a position where it is inserted into the valve hole 37. It has a predetermined clearance between the inner wall surface of the hole 37 and functions as a fixed orifice whose opening area does not change.

  The valve body 38 of the second valve is formed integrally with the valve body 18 of the first valve together with the shaft 23 and the shaft 39 so as to operate in conjunction with the valve body 18 of the first valve. Yes. The shaft 39 is formed to have a diameter larger than that of the shaft 23, and the figure of the valve body 18 of the first valve and the valve body 38 of the second valve so that the stepped portion at the boundary between the shafts 39 abuts on the body 13. It is a stopper that restricts the upward movement of the.

  The valve body 38 of the second valve is also formed integrally with the center disk 25. By integrally forming the valve body 18, the shafts 23 and 39, the valve body 38, and the center disk 25, the number of parts can be reduced.

  In the control valve having the above configuration, when the first valve is controlled in the closing direction, the second valve is controlled in the opening direction, and when the first valve is controlled in the opening direction, the second valve is controlled. The valve is controlled in the closing direction. Therefore, when it is desired to switch the variable capacity compressor to the minimum capacity or the maximum capacity, the first valve and the second valve operate in the opposite directions in conjunction with each other, and the pressure Pc in the crank chamber (= Pc1 = Pc2) Since the variable capacity compressor can be changed in a short time, the variable capacity compressor can be promptly shifted to the operation state of the minimum capacity or the maximum capacity.

It is sectional drawing which shows the control valve which concerns on 1st Embodiment in the state at the time of valve opening. It is sectional drawing which shows the control valve which concerns on 1st Embodiment in the state at the time of valve closing. It is sectional drawing which shows the control valve which concerns on 2nd Embodiment. It is sectional drawing which shows the control valve which concerns on 3rd Embodiment. It is sectional drawing which shows the control valve which concerns on 4th Embodiment. It is sectional drawing which shows the control valve which concerns on 5th Embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Valve part 11 Pressure sensing part 12 Solenoid part 13 Body 14, 15, 15a, 16 Port 17 Valve hole 18 Valve body 19 Spring receiving part 20 Spring 21 Adjustment screw 22 Strainer 23 Shaft 24 Diaphragm 25 Center disk 26 Coil 27 Sleeve 28 Core 29 Plunger 30 Spring 31 Shaft 32 Connector housing 33 Bearing part 34 Case 35 Adjustment screw 36 Spring 37 Valve hole 38 Valve element 39 Shaft Pc, Pc1, Pc2 Crank chamber pressure Pd Discharge pressure Ps Suction pressure

Claims (7)

In the control valve of the variable capacity compressor for controlling the pressure in the crank chamber so that the suction pressure of the variable capacity compressor becomes a value set by the solenoid for duty ratio control,
A valve portion for controlling opening and closing of a passage between the first port into which the refrigerant is introduced and the second port from which the refrigerant is led out is configured by a spool valve, and the solenoid force of the valve body of the spool valve and the solenoid is used as the valve A variable capacity compressor characterized in that a shaft transmitting to a body is integrally formed with the same outer diameter, and a valve hole into which the valve body is inserted and removed and a holding hole of the shaft are formed with the same inner diameter. Control valve.   A center disk that is disposed in contact with a pressure-sensitive member that senses the suction pressure and transmits an axial displacement of the pressure-sensitive member to the shaft is formed integrally with the shaft. Item 8. A control valve for a variable displacement compressor according to Item 1.   A second spool valve for controlling opening and closing of a passage between the third port into which the refrigerant is introduced and the fourth port from which the refrigerant is led in conjunction with the spool valve; and a second valve of the second spool valve 2. A control valve for a variable capacity compressor according to claim 1, wherein a body is formed integrally with said shaft.   A center disk that is disposed in contact with the pressure-sensitive member that senses the suction pressure and transmits the axial displacement of the pressure-sensitive member to the shaft is formed integrally with the second valve body. The control valve for a variable capacity compressor according to claim 3.   The valve portion includes a first spring that urges the valve body in a valve closing direction, and an adjustment mechanism that adjusts a load of the first spring, and the solenoid is a pressure-sensitive member that senses the suction pressure. 2. The control valve for a variable capacity compressor according to claim 1, further comprising a second spring that urges the shaft in the valve opening direction via a valve.   The valve portion includes a first spring that biases the shaft in the valve closing direction, and the solenoid biases the shaft in the valve opening direction via a pressure-sensitive member that senses the suction pressure. The control valve for a variable capacity compressor according to claim 1, further comprising a second spring and an adjusting mechanism for adjusting a load of the second spring. 2. The control valve for a variable capacity compressor according to claim 1, wherein the valve portion is configured to introduce refrigerant from the first port into a spool of the spool valve.

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