JP2007218168A - Control valve for variable capacity compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve vibration resistance by inhibiting wear of a plunger due to roll in a control valve for a variable capacity compressor. <P>SOLUTION: In the control valve for the variable capacity compressor, a second plunger 32 butts on a part of a body 11 via a taper surface to regulate movement thereof in a direction perpendicular to an axial direction when electricity carry to a solenoid 2 is turned off. Consequently, wear between the second plunger 32 and the body 11 can be prevented even if roll is applied to the control valve for the variable capacity compressor. As a result, vibration resistance of the control valve for the variable capacity compressor can be improved. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a control valve for a variable capacity compressor, and more particularly to a control valve for a variable capacity compressor suitable for controlling a refrigerant discharge capacity in a variable capacity compressor of an automotive air conditioner.

  The compressor used in the refrigeration cycle of the air conditioner for automobiles cannot control the rotational speed because it uses an engine whose rotational speed varies depending on the running state as a drive source. Therefore, in order to obtain an appropriate cooling capacity without being restricted by the engine speed, a variable capacity compressor capable of varying the refrigerant discharge capacity is used.

  In a variable capacity compressor, generally, an oscillating plate provided with a variable inclination angle is driven by an oscillating motion of a rotating shaft in an airtight crank chamber to perform an oscillating motion. The piston that reciprocates in the direction parallel to the rotation axis by the swinging motion of the swinging plate sucks the refrigerant in the suction chamber into the cylinder and compresses it, and then discharges it to the discharge chamber. At this time, by changing the pressure in the crank chamber, the inclination angle of the swing plate can be changed, whereby the stroke of the piston is changed and the discharge amount of the refrigerant is changed. The control valve for the variable capacity compressor controls to change the pressure in the crank chamber.

  In general, the variable displacement compressor control valve introduces a part of the refrigerant having the discharge pressure Pd discharged from the discharge chamber into an airtight crank chamber. Then, for example, the crank pressure Pc is controlled by controlling the introduction amount according to the suction pressure Ps of the suction chamber. That is, such a control valve for a variable capacity compressor senses the suction pressure Ps and controls the flow rate of the refrigerant introduced from the discharge chamber into the crank chamber so that the suction pressure Ps is kept constant.

  For this reason, the control valve for the variable capacity compressor has a pressure sensing part that senses the suction pressure Ps and a valve part that controls the opening and closing of the passage leading from the discharge chamber to the crank chamber according to the suction pressure Ps sensed by the pressure sensing part. And. Furthermore, the control valve for the variable displacement compressor is provided with a solenoid that can vary the set value of the pressure sensing unit by an external current so that the value of the suction pressure Ps when entering the variable displacement operation can be freely set from the outside. I have.

  By the way, among the conventional control valves for variable capacity compressors that can be controlled externally, an electromagnetic clutch that transmits or interrupts the driving force to the engine between the engine and a rotary shaft provided with a swing plate. There is a type that controls a so-called clutchless variable capacity compressor in which the engine and the rotary shaft are directly connected without using the compressor.

  This control valve for a variable capacity compressor is compared with the atmospheric pressure and a valve portion that controls opening and closing of a passage from the discharge chamber to the crank chamber, a solenoid that generates electromagnetic force that causes the valve portion to act in the closing direction, and And a pressure-sensitive portion that causes the valve portion to act in the opening direction as the suction pressure Ps decreases. For this reason, when the solenoid is not energized, the valve portion is fully open, and the crank pressure Pc can be maintained at a pressure close to the discharge pressure Pd. At right angles, the variable capacity compressor can be operated at the minimum capacity. Even if the engine and the rotary shaft are directly connected, the discharge capacity can be substantially reduced to zero, so that the electromagnetic clutch can be eliminated.

  In recent years, as a control valve for such a variable capacity compressor, there has been proposed a valve that does not need to consider the pressure resistance of the solenoid portion by disposing the solenoid outside the pressure chamber. This is because the solenoid plunger is divided into two parts, a first plunger and a second plunger, and a pressure-sensitive member for sensing the suction pressure is arranged between them, and the pressure in the crank chamber is controlled by the divided second plunger. The opening degree control of the valve part to perform is performed (for example, refer patent document 1).

FIG. 3 is a partial cross-sectional view illustrating a configuration example of a conventional control valve for a variable capacity compressor.
This control valve for a variable capacity compressor is composed of a valve body and a solenoid connected to the valve body via a pressure sensitive part. A port 102 that communicates with the crank chamber is provided at one end of the body 101 of the valve body, and a port 103 that communicates with the discharge chamber from a side close to the port 102 and a port 104 that communicates with the suction chamber on the side of the body 101. Is provided. The port 102 and the port 103 are communicated with each other via a valve hole 105 provided along the axis of the body 101. A valve seat 106 is formed integrally with the body 101 at the end of the valve hole 105 on the port 102 side. The body 101 is provided with a guide hole 107 along the axial direction so as to face the valve hole 105, and a shaft 109 provided with a valve body 108 at one end is slidably inserted. The other end of the shaft 109 is supported by one plunger of the solenoid.

  That is, the solenoid plunger is divided into a plunger 111 disposed in a pressure chamber into which the suction pressure Ps is introduced with the diaphragm 110 as a boundary, and a plunger 112 disposed outside the pressure chamber. The plunger 111 and the plunger 112 are arranged in series in the axial direction. The plunger 111 is fitted to the end of the shaft 109 opposite to the valve body 108 and is urged by the spring 113 in the valve opening direction. On the other hand, the plunger 112 is disposed facing the core 114 while being urged in the valve opening direction by a spring (not shown).

  When the solenoid is not energized, the plunger 111 and the plunger 112 are separated from each other by the urging force of the spring 113 as shown in the figure, and the valve portion is kept fully open. When the solenoid is energized, the plunger 111 and the plunger 112 are sucked together and operate integrally.

That is, the integrated plunger is driven according to the suction pressure Ps sensed by the pressure sensing unit, and the driving force is transmitted to the valve body 108 via the shaft 109. The valve body 108 contacts and separates from the valve seat 106 from the port 102 side to open and close the valve portion. The discharge pressure Pd introduced from the port 103 is controlled to be reduced by passing through the valve portion to become the crank pressure Pc, and is led out to the crank chamber via the port 102. That is, the control valve for the variable capacity compressor senses the suction pressure Ps and controls the flow rate of the refrigerant at the discharge pressure Pd introduced from the discharge chamber into the crank chamber so that the suction pressure Ps is kept constant.
Japanese Patent Laying-Open No. 2005-214059 (FIG. 1)

  However, in such a control valve for a variable capacity compressor, since the coupling between the plunger 111 and the plunger 112 is released when the solenoid is not energized, the support of the plunger 111 on the pressure chamber side is substantially the biasing force of the spring 113. It will depend only on. At this time, the plunger 111 is pressed against the body 101 by the spring 113. However, if the plunger 111 rolls due to vibration of the vehicle body or the like, wear may occur between the plunger 111 and the body 101.

  In this case, it is conceivable to prevent displacement of the plunger 111 in the lateral direction by fixing the plunger 111 to the shaft 109 by press-fitting. However, in such a configuration, the displacement of the plunger 111 is transmitted to the shaft 109 as it is. Therefore, when the plunger vibrates laterally when the solenoid is energized, the vibration is directly transmitted to the shaft 109. As a result, a couple of forces is applied to the shaft 109 due to the vibration, and wear may occur between the shaft 109 and the guide hole 107 when the shaft 109 slides. In any case, there is a problem that the vibration resistance of the control valve for the variable capacity compressor is not good.

  This invention is made | formed in view of such a point, and it aims at providing the control valve for variable capacity compressors which can suppress the abrasion by rolling and can improve vibration resistance.

  In the present invention, in order to solve the above problem, in a control valve for a variable capacity compressor that changes the discharge capacity of the refrigerant by the variable capacity compressor by controlling the pressure in the crank chamber of the variable capacity compressor, A body in which a refrigerant passage is formed, and a valve that contacts and separates from a valve seat formed in the body in order to adjust a refrigerant flow rate when a part of refrigerant discharged from the variable capacity compressor flows into the crank chamber A body, a shaft that is slidably inserted in a guide hole provided in the body, and is supported by one end thereof, a shaft that supports the valve body, a core fixed to the body, A plunger that transmits a driving force to the valve body while supporting the other end side of the shaft, and an electromagnetic coil that generates a magnetic circuit including the plunger and the core by energization. And a solenoid configured to restrict movement in a direction perpendicular to the axial direction by contacting a part of the body when the body is fully open, and a control valve for a variable capacity compressor Is provided.

  According to such a control valve for a variable capacity compressor, when the solenoid is de-energized, the plunger comes into contact with a part of the body, and movement in a direction perpendicular to the axial direction is restricted. For this reason, even if rolling is added to the control valve for a variable capacity compressor, it is possible to prevent wear between the plunger and the body. As a result, the vibration resistance of the control valve for the variable capacity compressor can be improved.

  According to the control valve for a variable capacity compressor of the present invention, it is possible to suppress wear due to rolling and improve vibration resistance.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a cross-sectional view showing a configuration of a control valve for a variable capacity compressor according to an embodiment. In the following description, for convenience, it may be expressed as upper and lower with reference to the illustrated state.

  The control valve for a variable capacity compressor includes a valve body 1 that opens and closes a refrigerant flow path for allowing a part of refrigerant discharged from a variable capacity compressor (not shown) to flow into the crank chamber, and a valve opening amount of the valve body 1. And a solenoid 2 for controlling the flow rate of the refrigerant passing through the valve unit is integrally assembled. At the lower end of the solenoid 2, there is provided a handle 3 in which a connection terminal for energization is arranged.

  The valve body 1 is provided with a port 12 that is connected to a discharge chamber of a variable capacity compressor and receives a discharge pressure Pd on a side portion of the body 11, and a strainer 13 is provided around the port 12. The port 12 communicates internally with a port 14 opened at the top of the body 11. The port 14 communicates with the crank chamber of the variable capacity compressor and derives a pressure (crank pressure) Pc controlled in the crank chamber.

  A valve seat 15 is formed integrally with the body 11 in the refrigerant passage communicating the port 12 and the port 14. The valve body 16 is disposed so as to be able to contact and separate in the axial direction facing the side from which the crank pressure Pc of the valve seat 15 is derived. The valve body 16 is formed integrally with the shaft 19 through a small diameter portion 18 inserted through the valve hole 17. The shaft 19 is inserted through a guide hole 20 formed so as to face the valve hole 17 along the axis of the body 11, and is held so as to be movable forward and backward in the axial direction. A discharge pressure Pd from the discharge chamber is introduced into the refrigerant passage in which the small diameter portion 18 is disposed. The outer diameter of the shaft 19 is substantially the same as the inner diameter of the valve hole 17 so that the pressure receiving area of the valve body 16 and the pressure receiving area of the shaft 19 are the same. Thereby, the force that the discharge pressure Pd acts on the valve body 16 is almost canceled by the force that acts on the shaft 19 downward, and the control of the valve portion is less affected by the high discharge pressure Pd.

  In addition, a step portion for forming a gap larger than the clearance of the sliding portion between the guide hole 20 and the guide hole 20 is formed at an intermediate portion in the axial direction of the shaft 19. The configuration of this step portion will be described in detail later.

The valve body 16 is biased in the valve closing direction by a spring 24, and the load of the spring 24 is adjusted by an adjustment screw 25 screwed into the port 14.
Further, a port 26 that communicates with the suction chamber of the variable capacity compressor and receives the suction pressure Ps is formed below the body 11.

  The lower end portion of the body 11 is fixed by press-fitting to a body 30 made of a cylindrical magnetic member constituting a part of the solenoid 2. The body 30 is provided with a second plunger 32 that is one of the divided plungers 31 of the solenoid 2. The second plunger 32 is further urged upward by a spring 36 disposed between the step portion formed in the body 30. The spring 36 has a larger spring force than the spring 24 that urges the valve body 16 in the valve closing direction.

  Below the second plunger 32, a diaphragm 37 formed by stacking one or more polyimide films and the remaining components of the solenoid 2 are arranged. That is, below the second plunger 32, the first plunger 39, the core 40, and the spring 50, which is the other plunger divided by the solenoid 2, are accommodated in the bottomed sleeve 38 that forms a vacuum container. An assembly in which the opening is sealed with a diaphragm 37 is arranged. Outside the bottomed sleeve 38, an electromagnetic coil 42 and a case 43 made of a magnetic material forming a yoke for forming a magnetic circuit are arranged.

  The bottomed sleeve 38 has a bottomed cylindrical shape having a flange portion extending radially outward at the upper end, and welds an upper half 44 made of a non-magnetic material and a lower half 45 made of a magnetic material. It is comprised by. In the bottomed sleeve 38, the core 40 is fixed by press-fitting to the lower half portion 45 side, and the first plunger 39 is disposed on the upper half portion 44 side so as to be able to advance and retreat in the axial direction.

  The first plunger 39 is fixed by press-fitting to one end of a shaft 46 extending in the axial direction at the center of the core 40, and the other end of the shaft 46 is slidably disposed in the core 40. It is supported. A retaining ring 48 is fitted in the middle of the shaft 46, and a spring receiver 49 is provided so that the upward movement of the figure is restricted by the retaining ring 48. A spring 50 is disposed between the two. The first plunger 39 is urged by the spring 50 through the shaft 46 in a direction away from the core 40.

  In addition, the spring 50 can change a load by adjusting the position of the axial direction of the bearing part 47 from the outside. Specifically, when the control valve for the variable capacity compressor is assembled and final adjustment is performed, the bottom portion of the bottomed sleeve 38 is pushed and deformed inwardly, whereby the bearing is in contact with the bottom portion. The load of the spring 50 is adjusted by changing the position of the portion 47 in the axial direction, thereby adjusting the set value of the control valve for the variable capacity compressor.

Next, the detail of the drive part of the valve part in this Embodiment is demonstrated. FIG. 2 is an enlarged view of the upper half of the control valve for the variable displacement compressor shown in FIG.
The control valve for the variable capacity compressor includes a foreign matter countermeasure structure for preventing foreign matter contained in the refrigerant from being caught in the sliding portion of the shaft 19 and hindering the operation of the valve portion, and the shaft 19 or It has a vibration-proof structure that prevents the second plunger 32 from being worn.

  That is, as a foreign matter countermeasure structure, the shaft 19 includes a first sliding portion 21 and a second sliding portion 22 that slide near the opening portions at both ends of the guide hole 20, and the first sliding portion 21 and the second sliding portion. A diameter-reducing portion 23 having a predetermined depth is formed by reducing the diameter at an intermediate portion with the moving portion 22 to form a stepped portion. Moreover, the upper end part of the 1st sliding part 21 is comprised so that it may protrude a little from the opening edge part of the guide hole 20 in a valve closing state.

  In such a configuration, when foreign matter such as aluminum powder circulating in the refrigeration cycle passes through the strainer 13 and is introduced from the port 12, the foreign matter is discharged by the pressure difference between the discharge pressure Pd and the suction pressure Ps. At the same time, it tends to flow into the first sliding portion 21 side. At this time, foreign matter having a size larger than the clearance between the first sliding portion 21 and the guide hole 20 is collected near the opening end portion of the guide hole 20. When the valve portion is opened, the first sliding portion 21 strokes upward, so that the foreign matter near the opening is pushed out of the guide hole 20, and the valve hole 17 is discharged together with the discharged refrigerant introduced from the port 12. And sent downstream.

  On the other hand, a foreign substance smaller than the clearance between the first sliding portion 21 and the guide hole 20 may flow from the first sliding portion 21 side. However, the foreign matter is retained in the stepped portion formed by the reduced diameter portion 23 or passes through the second sliding portion 22 on the downstream side and is discharged to the outside of the guide hole 20. For this reason, a situation in which foreign matter is caught between the shaft 19 and the guide hole 20 and the shaft 19 is locked does not occur.

  Further, as the vibration-proof structure, the second plunger 32 is formed in a T-shaped cross section, and a circular recess 33 having a predetermined width and depth is provided in the center of the upper surface. And the lower end part of the shaft 19 is accommodated in this recessed part 33, forming predetermined play (gap). Thus, even if the second plunger 32 rolls in a direction perpendicular to the axis, the vibration is prevented from being directly transmitted to the shaft 19. That is, the shaft 19 is prevented from receiving a couple of forces due to the rolling of the second plunger 32, and the shaft 19 is pressed against the guide hole 20 during sliding so that the shaft 19 is not worn.

  Moreover, the contact part of the 2nd plunger 32 and the body 11 is formed in a complementary shape, and the horizontal vibration of the 2nd plunger 32 at the time of full opening of a valve part is prevented. That is, the center part of the lower end of the body 11 protrudes downward, and a tapered surface 51 that decreases in diameter toward the tip is formed at the lower end part. The second sliding portion 22 of the shaft 19 protrudes downward from the center of the lower end portion.

  On the other hand, the second plunger 32 has a flange-shaped large-diameter portion 35 that is connected to the upper end of the small-diameter portion inserted through the body 30 and extends outward in the radial direction. A tapered surface 52 is formed which increases in diameter upward from 33 to the large diameter portion 35. The taper surfaces 51 and 52 have substantially the same taper inclination when in contact with each other, thereby realizing a complementary shape. Thus, when the second plunger 32 is displaced to the top dead center position when the valve portion is fully opened, the second plunger 32 is brought into contact with the body 11 in the axial direction and locked. At this time, since the tapered surface as the contact portion is inclined with respect to the axis of the second plunger 32, when the second plunger 32 contacts the body 11, the operation is in a lateral direction perpendicular to the axis. Are also regulated. For this reason, it is possible to prevent the second plunger 32 from operating and wearing in the lateral direction with respect to the body 11 when rolling occurs in the control valve for the variable capacity compressor. On the other hand, during the opening / closing control of the valve portion, the engagement state between the second plunger 32 and the body 11 is released, so that the movement of the second plunger 32 is not restricted by the body 11.

  A communication hole 34 is formed in the side portion of the second plunger 32 so as to allow the inside and outside of the recess 33 to communicate with each other, so that the suction pressure Ps introduced from the port 26 can be transmitted to the diaphragm 37 satisfactorily. Yes. The lower surface of the large-diameter portion 35 of the second plunger 32 faces the upper surface of the body 30. Accordingly, when energization of the solenoid 2 is started, an axial suction force is generated between the opposed surfaces of the large diameter portion 35 and the body 30 to help the valve body 16 to move quickly in the valve closing direction. Yes.

Next, the operation of the control valve for the variable capacity compressor of the present embodiment will be described.
The control valve for the variable displacement compressor is operated in a state where the discharge capacity is minimum when the solenoid 2 is not energized and the suction pressure Ps is high, that is, when the automotive air conditioner is not operating.

  That is, in this case, since the suction pressure Ps is high, the first plunger 39 in contact with the diaphragm 37 is displaced downward against the load of the spring 50. On the other hand, the second plunger 32 is biased upward by the spring 36 so as to be separated from the first plunger 39, and biases the valve body 16 to its fully open position via the shaft 19. Therefore, even if the rotary shaft of the variable capacity compressor is rotationally driven by the engine, the variable capacity compressor is operated with a minimum discharge capacity. At this time, since the second plunger 32 is engaged with the body 11, vibration in the lateral direction is prevented.

  Here, when the maximum control current is supplied to the electromagnetic coil 42 of the solenoid 2 as in the case where the automobile air conditioner is activated, the first plunger 39 passes through the diaphragm 37 as shown in FIG. Thus, the second plunger 32 is sucked against the urging force of the spring 36. The second plunger 32 is moved downward by being sucked and brought into contact with the diaphragm 37. Accordingly, the valve body 16 is pushed down by the spring 24 and is seated on the valve seat 15, and the valve portion is fully closed. It becomes a state. As a result, the passage from the discharge chamber to the crank chamber is blocked, so that the variable capacity compressor quickly shifts to the maximum capacity operation.

  When the variable capacity compressor continues to operate at the maximum capacity and the suction pressure Ps in the suction chamber becomes sufficiently low, the diaphragm 37 detects the suction pressure Ps and tries to move upward. At this time, if the control current supplied to the electromagnetic coil 42 of the solenoid 2 is reduced in accordance with the set temperature of the air conditioning, the second plunger 32 and the first plunger 39 are integrated in the adsorbed state, and the suction pressure Ps and the spring are integrated. It moves upward to a position where the load of 24, 36, 50 and the suction force of the solenoid 2 are balanced. As a result, the valve body 16 is pushed up by the second plunger 32 and is separated from the valve seat 15 and set to a predetermined opening degree. Therefore, the refrigerant having the discharge pressure Pd is controlled to a flow rate corresponding to the opening degree and is introduced into the crank chamber, and the variable capacity compressor shifts to an operation with a capacity corresponding to the control current. At this time, since the contact state between the second plunger 32 and the body 11 is released, the second plunger 32 is not rubbed against the body 11 and worn. Further, since there is a predetermined gap in the lateral direction between the second plunger 32 and the shaft 19, even if the plunger 31 laterally vibrates, the vibration can be prevented from being directly transmitted to the shaft 19. For this reason, the shaft 19 is not rubbed against the guide hole 20 and worn.

  When the control current supplied to the electromagnetic coil 42 of the solenoid 2 is constant, the diaphragm 37 senses the suction pressure Ps and controls the valve opening. For example, when the refrigeration load is increased and the suction pressure Ps is increased, the valve body 16 is displaced downward together with the shaft 19, the second plunger 32, the diaphragm 37, and the first plunger 39. The variable capacity compressor operates to increase the discharge capacity. Conversely, when the refrigeration load decreases and the suction pressure Ps decreases, the valve body 16 is displaced upward to increase the valve opening, so that the variable capacity compressor operates to reduce the discharge capacity. In this way, the control valve for the variable capacity compressor controls the discharge capacity of the variable capacity compressor so that the suction pressure Ps becomes a value set by the solenoid 2.

  As described above, in the variable displacement compressor control valve of the present embodiment, when the solenoid 2 is de-energized, the second plunger 32 contacts a part of the body 11 via the tapered surface. The movement in the direction perpendicular to the axial direction is restricted. For this reason, even if a roll is applied to the control valve for the variable capacity compressor, it is possible to prevent wear between the second plunger 32 and the body 11. As a result, the vibration resistance of the control valve for the variable capacity compressor can be improved.

  The preferred embodiment of the present invention has been described above, but the present invention is not limited to the specific embodiment, and it can be changed and modified within the spirit of the present invention. Not too long.

  For example, in the above-described embodiment, an example in which the contact surface between the second plunger 32 and the body 11 is tapered has been shown. However, when the second plunger 32 contacts a part of the body 11, As long as the movement in the perpendicular direction is restricted, the contact surface can take various shapes.

Moreover, although the example which provided the level | step-difference part in the shaft 19 side was shown in the said embodiment, a level | step-difference part may be provided in the guide hole 20 side, or you may make it provide a level | step-difference part in both.
Moreover, in the said embodiment, although the structure which employ | adopted the diaphragm as a pressure sensitive member was shown, you may employ | adopt a bellows other pressure sensitive members.

It is sectional drawing which shows the structure of the control valve for variable capacity compressors which concerns on embodiment. It is an enlarged view of the upper half part of the control valve for variable capacity compressors shown in FIG. It is a fragmentary sectional view showing the example of composition of the conventional control valve for variable capacity compressors.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Valve main body 2 Solenoid 11 Body 15 Valve seat 16 Valve body 17 Valve hole 19 Shaft 20 Guide hole 31 Plunger 33 Concave part 40 Core 51, 52 Tapered surface

Claims (5)

In a control valve for a variable capacity compressor that changes the discharge capacity of the refrigerant by the variable capacity compressor by controlling the pressure in the crank chamber of the variable capacity compressor,
A body having a refrigerant passage formed therein;
A valve body that contacts and separates a valve seat formed in the body in order to adjust a refrigerant flow rate when a part of refrigerant discharged from the variable capacity compressor flows into the crank chamber;
While being slidably inserted into a guide hole provided in the body and pivotally supported, a shaft supporting the valve body on one end side thereof,
A core fixed to the body; a plunger that transmits a driving force to the valve body while supporting the other end of the shaft; and an electromagnetic coil that generates a magnetic circuit including the plunger and the core when energized. A solenoid configured to restrict movement in a direction perpendicular to an axial direction thereof by contacting the part of the body when the valve body is fully opened;
A control valve for a variable capacity compressor.   2. The variable according to claim 1, wherein the plunger and a part of the body are configured to contact each other in the axial direction, and the contact surfaces thereof are formed in complementary tapered shapes, respectively. Control valve for capacity compressor.   The control valve for a variable capacity compressor according to claim 1, wherein the plunger is formed with a recess for loosely fitting and supporting the other end of the shaft. The plunger is configured by arranging a first plunger facing the core and a second plunger supporting the other end of the shaft in series in the axial direction,
Between the first plunger and the second plunger, a pressure sensitive member for sensing the suction pressure of the suction chamber, and a biasing means for biasing the second plunger in the valve opening direction are arranged,
When the solenoid is energized, the first plunger and the second plunger operate integrally through the pressure-sensitive member, and when the solenoid is not energized, the second plunger is the biasing means. Acting away from the first plunger by an urging force;
The control valve for a variable capacity compressor according to claim 1. A cylindrical magnetic member for fixing the pressure sensitive member to the solenoid is disposed between the first plunger and the second plunger,
The second plunger extends in a radially outward direction from the small-diameter portion that is inserted in the magnetic member with a predetermined space and is opposed to the magnetic member in the axial direction. A large diameter portion that forms a facing surface, and when energizing the solenoid, the magnetic circuit is formed through the facing surface,
The control valve for a variable capacity compressor according to claim 4.

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