JP2009133237A - Control valve for variable displacement compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a control valve for variable displacement compressor capable of enhancing responsiveness of the control of a crank chamber pressure Pc, while simplifying its structure to suppress cost increase, and capable of reducing unnecessary flow of coolant to increase control efficiency. <P>SOLUTION: On a valve rod 15, an air supply valve body section 15a, a small bore section 15b, an intermediate large diameter section 15c, and a bleed valve body section 15g are provided in this order from the bottom. On a valve body section 20, a crank chamber pressure port 26, an air supply valve sheet section 22A, an air supply valve chamber 21A, a guide hole 19 into which the intermediate large diameter section 15c is inserted fittingly, a bleed valve chamber 21B having a bleed valve sheet section 22B, and an inlet pressure chamber 23 having an inlet pressure port 27 are provided in this order from the bottom. Further, on the valve rod 15, a crank chamber pressure passage 70 which communicates the crank chamber pressure port 26 and the bleed valve chamber 21B is provided, and when the valve rod 15 moves vertically, opening degree of the air supply valve body section 15a and opening degree of the bleed valve body section 15g are changed in reverse direction. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a control valve for a refrigeration cycle applied to a variable capacity compressor, and in particular, supply of refrigerant in a crank chamber from a discharge pressure region and discharge of refrigerant to a suction side region in the crank chamber as required. The present invention relates to a control valve for a variable displacement compressor that controls the compressor.

  The compressor used in the refrigeration cycle of the automotive air conditioner cannot directly control the rotational speed because it is directly connected to the engine with a belt or the like. In view of this, a variable capacity compressor capable of changing the compression capacity (discharge amount) is used in order to obtain an appropriate cooling capacity without being restricted by the rotational speed of the engine.

  In general, the variable capacity compressor compresses refrigerant sucked from a suction chamber that leads to a suction pipe, discharges the refrigerant into a discharge chamber that leads to a discharge pipe, and controls the pressure of the refrigerant by a control valve ( The refrigerant discharge amount is changed by changing the refrigerant pressure in the crank chamber).

  In Patent Document 1 below, a valve body disposed on the intake side is opened and closed by a pressure balance between the suction pressure Ps of the variable capacity compressor and the reaction force of a pressure-sensitive response member such as a bellows, and a discharge passage (discharge There is disclosed a control valve for a refrigeration cycle that controls the crank chamber pressure Pc by causing the discharged refrigerant to flow (intake air) from the pressure Pd) to the crank chamber (crank chamber pressure Pc). According to this control valve, the crank chamber pressure Pc of the variable displacement compressor can be controlled.

  However, in the above control valve, there is a problem in responsiveness and the like, such as control of the crank chamber pressure Pc of the variable displacement compressor takes a considerable time from the fluctuation of the suction pressure Ps to the end of the control.

  Therefore, the applicant of the present application has previously proposed a control valve having the following configuration in order to improve responsiveness and the like (see Patent Document 2 and the like).

  The proposed control valve basically includes a valve stem, a valve body, an electromagnetic actuator for driving the valve stem in the valve opening / closing direction, and the valve stem in response to the suction pressure Ps of the compressor. And a pressure sensitive response member such as a bellows that drives in the opening and closing direction.

  As shown in FIG. 3, the lower half of the control valve is, in order from the bottom, the valve rod 15, the supply valve body portion 15 a, the lower small diameter portion 15 b, the intermediate large diameter portion 15 c, and the intermediate small diameter. A portion 15d and an upper large diameter portion 15e are provided, and a lower end portion (lower end terrace surface) of the upper large diameter portion 15 is an extraction valve body portion 15g. Further, the lower small diameter portion 14c of the operating rod 14 driven in the vertical direction by the pressure sensitive member is connected and fixed to the upper end portion (vertical hole 15f) of the valve rod 15 by press-fitting or the like. The plunger 37 of the electromagnetic actuator is sandwiched by a large diameter portion (not shown) of the actuating rod 14 so that the valve rod 15 and the plunger 37 are moved up and down integrally.

  On the other hand, the valve body 20 includes, in order from the bottom, a crank chamber pressure port 26A communicating with the crank chamber of the compressor, an air supply valve seat portion 22A in which the air supply valve body portion 15a contacts and separates from its lower surface side, and a discharge pressure Pd. In order to introduce the crank chamber pressure Pc from the outside, the air supply valve chamber 21A having a discharge pressure port 25 for introducing gas, the guide hole 19 into which the intermediate large diameter portion 15c of the valve rod 15 is slidably fitted. In order to derive the suction pressure Ps, the bleed valve chamber 21B having a bleed valve seat portion 22B having a larger diameter than the crank chamber pressure introduction port 26B and the intermediate small diameter portion 15d of the valve rod 15 and contacting and separating the bleed valve body 15g. A suction pressure chamber 23 having a suction pressure port 27 is provided.

  In the control valve having such a configuration, when the variable displacement compressor is in an operating state, when the energization to the electromagnetic actuator (the solenoid) is off, the supply valve body 15a is fully opened and the extraction valve body is illustrated as shown in the figure. The part 15g is in a fully closed state. In this state, the crank chamber pressure Pc accompanying the fluctuations in the discharge pressure Pd and the suction pressure Ps is not controlled.

  When the solenoid is energized and the electromagnetic force is constant (control state), the air supply valve body 15a is adjusted (opened / closed) in accordance with the fluctuation of the suction pressure Ps, and at the same time, the extraction valve body 15g. The opening adjustment (closing / opening) is performed through the valve rod 15 by the same vertical movement as that of the air supply valve body 15a. During this time, when the suction pressure Ps rises, the supply valve body 15a moves upward (close direction), and at the same time, the extraction valve body 15g also moves upward (open direction). As a result of the cooperative action with the bleed valve body 15g, the crank chamber pressure Pc quickly decreases as compared with a conventional valve body having only one valve body.

  Conversely, when the suction pressure Ps decreases, the supply valve body 15a moves downward (in the opening direction) and at the same time the extraction valve body 15g also moves down (in the closing direction). As a result of the cooperative action of 15a and the bleed valve body 15g, the crank chamber pressure Pc is quickly increased as compared with a conventional valve body having only one valve body.

  When the electromagnetic force of the solenoid is changed, the crank chamber pressure Pc changes correspondingly, thereby changing the compression capacity (discharge amount), and the suction pressure Ps is kept constant at different levels. .

  That is, when the electromagnetic force of the solenoid is reduced, the upward suction force with respect to the plunger 37 is weakened. Therefore, the plunger 37 is moved downward, and the valve rod 15, the supply valve body 15a, and the extraction valve body 15g are also moved together. The valve opening of the supply valve body 15a increases, but the valve opening of the extraction valve body 15g decreases. As a result, the refrigerant flow rate from the discharge pressure port 25 to the crank chamber pressure port 26A increases. At the same time, the refrigerant flow rate from the crank chamber pressure introduction port 26B to the suction pressure port 27 is reduced, and by the cooperative action of the supply valve body portion 15a and the extraction valve body portion 15g, there is only one conventional valve body portion. The crank chamber pressure Pc is quickly increased and the discharge amount of the compressor is rapidly decreased as compared with the above.

  On the other hand, when the electromagnetic force of the solenoid increases, the upward suction force with respect to the plunger 37 increases, so that the plunger 37 moves upward, and the valve rod 15, the supply valve body 15a, and the extraction valve body 15g together with it. As a result, the valve opening of the supply valve body 15a is reduced, but the valve opening of the extraction valve body 15g is increased, resulting in a decrease in the refrigerant flow rate from the discharge pressure port 25 to the crank chamber pressure port 26A. At the same time, the refrigerant flow rate from the crank chamber pressure introduction port 26B to the suction pressure port 27 increases, and due to the cooperative action of the supply valve body portion 15a and the extraction valve body portion 15g, there is only one conventional valve body portion. The crank chamber pressure Pc is quickly lowered and the discharge amount of the compressor is quickly increased as compared with the above.

  As described above, in the proposed control valve, the valve rod 15 is provided with the supply valve body 15a and the extraction valve body 15g, and when the opening of the supply valve body 15a increases, the extraction valve body 15g When the opening degree decreases, and conversely, when the opening degree of the supply valve body part 15a decreases, the opening degree of the extraction valve body part 15g increases so that the supply valve body part 15a and the extraction valve body part 15g. And the crank chamber pressure Pc are controlled in cooperation with each other, so that the crank chamber pressure (control pressure) Pc is set to a target value (desired value) as compared with a conventional valve body having only one valve body portion. It becomes possible to approach quickly, and responsiveness and control efficiency are improved.

JP 2002-303262 A JP 2004-316429 A

  However, in the proposed variable displacement compressor control valve, the crank chamber pressure Pc is introduced into the crank chamber pressure introduction port 26B from the outside of the control valve, and this is introduced into the intake pressure port via the extraction valve body portion 15g. 27, it is necessary to provide a separate crank chamber pressure introduction port 26B in the valve body 20, and the crank chamber pressure Pc is applied to the compressor in which the control valve is used. Since a passage or the like for leading to the introduction port 26B is necessary, there are problems to be improved in terms of structure, cost, and flow (path) of the refrigerant.

  The present invention has been made in view of the above circumstances, and its object is to improve the control response of the crank chamber pressure Pc while simplifying the structure and suppressing an increase in cost. It is an object of the present invention to provide a control valve for a variable displacement compressor that can reduce wasteful flow of refrigerant and can improve control efficiency.

  In order to achieve the above object, a control valve for a variable displacement compressor according to the present invention basically includes a valve stem, a valve body, and an electromagnetic actuator for driving the valve stem in a valve opening / closing direction. And a pressure-sensitive responsive member that drives the valve stem in the valve opening / closing direction in response to a suction pressure of the compressor, and the valve stem includes, in order from the bottom, an air supply valve body portion, the air supply valve body A small-diameter portion having a smaller diameter than the small-diameter portion, an intermediate large-diameter portion having a larger diameter than the small-diameter portion, and a bleed valve body portion. , An air supply valve seat part to which the air supply valve body part contacts and separates, an air supply valve chamber having a discharge pressure port for introducing the discharge pressure of the compressor, and an intermediate large diameter part of the valve rod are slidable A guide hole to be inserted, a bleed valve chamber having a bleed valve seat part to which the bleed valve body part comes into contact with and separated from, and a suction pressure port for deriving suction pressure When the valve rod is moved up and down, a suction chamber having a suction port is provided, and a crank chamber pressure passage communicating the crank chamber pressure port and the extraction valve chamber is provided in the valve rod. The opening degree of the air valve body part and the opening degree of the extraction valve body part are changed in the opposite directions.

  In a preferred embodiment, the supply valve body is positioned below the supply valve seat, and the extraction valve body is positioned above the extraction valve seat.

  In the control valve for a variable displacement compressor according to the present invention, when the valve rod moves up and down, the opening degree of the supply valve body part and the opening degree of the extraction valve body part are changed in opposite directions, Since the valve body portion and the extraction valve body portion cooperate to control the crank chamber pressure, the crank chamber pressure (control pressure) Pc can be quickly brought close to the target value (desired value).

  In addition, since the crankshaft pressure passage that communicates the crank chamber pressure port and the bleed valve chamber is provided in the valve rod, the crank chamber pressure Pc can be reduced within the control valve without bypassing the crank chamber pressure port. Are introduced to the suction pressure port through the crank chamber pressure passage and the extraction valve body.

  Therefore, the crank chamber pressure introduction port (26B) provided in the conventional control valve shown in FIG. 3 is not necessary, and the crank chamber pressure Pc is guided to the compressor to the crank chamber pressure introduction port (26B). For this reason, there is no need for a passage.

  As a result, the structure becomes simple, the cost can be reduced, the responsiveness of the control of the crank chamber pressure Pc can be improved, the wasteful flow of the refrigerant can be reduced, and the control efficiency can be improved. be able to.

Hereinafter, embodiments of a control valve for a variable displacement compressor of the present invention will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing an embodiment of a control valve for a variable displacement compressor according to the present invention, and FIG. 2 is an enlarged view of a main part of FIG. In the variable displacement compressor control valve 1 shown in FIGS. 1 and 2, the same reference numerals are given to the portions corresponding to the respective parts of the conventional example shown in FIG.

  The control valve 1 in the illustrated embodiment includes a valve stem 15, a valve body 20, an electromagnetic actuator 30 for driving the valve stem 15 in the valve opening / closing direction, and the valve stem 15 in response to the suction pressure of the compressor. And a bellows body 40 as a pressure-sensitive response member that is driven in a valve opening / closing direction (vertical direction).

  The electromagnetic actuator 30 includes a coil 32 having a connector portion 31 for energization excitation, a cylindrical stator 33 disposed on the inner peripheral side of the coil 32, and a cross-section that is press-fitted and fixed to the inner periphery of the lower end portion of the stator 33. A pipe 35 with a flange 35a whose upper end is joined by TIG welding to the outer periphery (step portion) of the lower end of the stator 33, which is a concave shape, and on the inner peripheral side of the pipe 35 below the attractor 34 A plunger 37 slidably disposed in the vertical direction and a cylindrical housing 60 with a bottomed hole disposed so as to cover the outer periphery of the coil 32 are provided.

  Further, an adjustment screw 65 having a hexagonal hole is screwed onto the upper portion of the stator 33, and a suction pressure Ps of the compressor is interposed between the adjustment screw 65 and the suction element 34 on the inner peripheral side of the stator 33. Is formed in the pressure sensing chamber 45. The pressure sensing chamber 45 includes a bellows 41, a reverse convex upper stopper 42, a reverse concave lower stopper 43, and a compression coil. A bellows body 40 comprising a spring 44 is disposed, and further, a compression coil that urges the bellows body 40 and the suction element 34 in a direction in which the bellows body 40 contracts (a direction in which the bellows body 40 is compressed toward the adjustment screw 65). A spring 46 is disposed. Also, a stepped operating rod 14 that penetrates the suction element 34 is disposed between the lower stopper 43 (reverse recess) of the bellows body 40 and the plunger 37 (recess 37b), and further, the suction element 34 and a valve opening spring 47 made of a compression coil spring that urges the plunger 37 downward (in the valve opening direction) is disposed between the intermediate large diameter portion 14b of the operating rod 14 located in the concave portion 37b of the plunger 37. Be present.

  A lower end flange 35a of the pipe 35 is placed on the upper end of the valve body 20 via an O-ring 57, and a short cylindrical shape with a flange 56a is provided between the flange 35a and the coil 32. The pipe holder 56 is interposed, and the hook-like portions 35 a and 56 a are fastened and fixed together by the upper end outer periphery caulking portion 29 of the valve body 20. Further, the bottom portion 61 with a hole of the housing 60 is press-fitted and fixed to the upper end portion of the pipe holder 56, and the upper end portion 62 of the housing 60 is caulked and fixed on the flange-shaped portion 31 c of the connector portion 31. An O-ring 66 is interposed between the connector part 31 and the coil 32. A concave portion 31a is formed at the lower center of the connector portion 31. The concave portion 31a is formed with a convex portion 31b fitted into the hexagonal hole of the adjusting screw 65. The stator 33 and the adjusting screw are formed in the concave portion 31a. The upper part of 65 is inserted.

  In addition to FIG. 1, as can be understood by referring to FIG. 2 that shows an enlarged view of the lower half of the present control valve 1, the valve rod 15 has an air supply valve body portion 15 a, An annular recess 15h for defining a bleed valve chamber 21B between a small diameter portion 15b having a smaller diameter than the air supply valve body portion 15a, an intermediate large diameter portion 15c having a diameter larger than the small diameter portion 15b, and a guide hole 19 to be described later. An extraction valve body portion 15g and an upper large diameter portion 15e are provided.

  On the other hand, the valve body 20 includes, in order from the bottom, a crank chamber pressure port 26A communicating with the crank chamber of the compressor, an air supply valve seat portion 22A in which the air supply valve body portion 15a is in contact with and away from the lower surface side, a compression A supply valve chamber 21A having a discharge pressure port 25 for introducing the discharge pressure of the machine, a guide hole 19 into which the intermediate large diameter portion 15c of the valve rod 15 is slidably fitted, and the extraction valve body portion are in contact with each other. A bleed valve chamber 21B having a bleed valve seat portion 22B to be separated and a suction pressure chamber 23 having a suction pressure port 27 for deriving the suction pressure Ps are provided.

  The valve rod 15 is provided with a crank chamber pressure passage 70 including a plurality of lateral holes 72 and longitudinal through holes 71 for communicating the crank chamber pressure port 26 and the extraction valve chamber 21B.

  The lower small diameter portion 14c of the actuating rod 14 driven in the vertical direction by the bellows body 40 or the like is connected and fixed to the upper end portion of the valve rod 15 (the upper end portion of the vertical through hole 71) by press fitting or the like. The plunger 37 of the electromagnetic actuator 30 is sandwiched between the upper end surface of the actuator and the intermediate large-diameter portion 14b of the operating rod 14, so that the valve rod 15 and the plunger 37 are moved up and down integrally.

  On the other hand, a convex stopper portion 28 for restricting the lowest position of the plunger 37 protrudes from the upper center of the valve body 20, and the central portion above the valve chamber including the convex stopper portion 28 includes: The upper large diameter portion 15e of the valve stem 15 is loosely inserted. In addition, a suction pressure refrigerant introduction chamber 23 into which a refrigerant having a suction pressure Ps of the compressor is introduced is formed between the plunger 37 and the upper outer periphery (outer periphery of the convex stopper portion 28) of the valve body 20. A plurality of suction pressure ports 27 are formed on the outer peripheral side, and the refrigerant having the suction pressure Ps introduced from the suction pressure ports 27 into the suction pressure refrigerant introduction chamber 23 is formed by vertical grooves 37 a formed on the outer periphery of the plunger 37, 37a,... And the gap 39 formed between the suction element 34 and the actuating rod 14 are introduced into the pressure sensitive chamber 45.

  In the control valve 1 of the present embodiment configured as described above, when the variable displacement compressor is in an operating state, when the energization of the electromagnetic actuator (solenoid thereof) is off, the air supply valve is illustrated as shown in the figure. The body portion 15a is fully open and the extraction valve body portion 15g is fully closed. In this state, the crank chamber pressure Pc accompanying the fluctuations in the discharge pressure Pd and the suction pressure Ps is not controlled.

  On the other hand, when the energization to the solenoid is turned on, the plunger 37 is attracted to the attractor 34 side (upward) by the electromagnetic force of the solenoid, and the valve rod 15 moves the supply valve body portion 15a and the extraction valve body portion 15g. Accordingly, the air supply valve body portion 15a approaches the air supply valve seat portion 22A (the opening degree decreases), and the air extraction valve body portion 15g moves away (opens) from the air extraction valve seat portion 22B, and the crank chamber pressure is increased. Pc is led out from the crank chamber pressure passage 70 provided in the valve rod 15 to the suction pressure chamber 23 and the suction pressure port 27 through the extraction valve chamber 21B and the extraction valve body portion 15g.

  More specifically, when the solenoid is energized and the electromagnetic force is constant (control state), the supply valve body 15a is adjusted (opened / closed) according to the fluctuation of the suction pressure Ps, and at the same time, The bleed valve body 15g is also adjusted for opening (closed and opened) by the same vertical movement as the air supply valve body 15a through the valve rod 15. During this time, when the suction pressure Ps rises, the supply valve body 15a moves upward (close direction), and at the same time, the extraction valve body 15g also moves upward (open direction). As a result of the cooperative action with the bleed valve body 15g, the crank chamber pressure Pc quickly decreases as compared with a conventional valve body having only one valve body.

  Conversely, when the suction pressure Ps decreases, the supply valve body 15a moves downward (in the opening direction) and at the same time the extraction valve body 15g also moves down (in the closing direction). As a result of the cooperative action of 15a and the bleed valve body 15g, the crank chamber pressure Pc is quickly increased as compared with a conventional valve body having only one valve body.

  When the electromagnetic force of the solenoid is changed, the crank chamber pressure Pc changes correspondingly, thereby changing the compression capacity (discharge amount), and the suction pressure Ps is kept constant at different levels. .

  That is, when the electromagnetic force of the solenoid is reduced, the upward suction force with respect to the plunger 37 is weakened. Therefore, the plunger 37 is moved downward, and the valve rod 15, the supply valve body 15a, and the extraction valve body 15g are also moved together. The valve opening of the supply valve body 15a increases, but the valve opening of the extraction valve body 15g decreases. As a result, the refrigerant flow rate from the discharge pressure port 25 to the crank chamber pressure port 26A increases. At the same time, the refrigerant flow rate from the crank chamber pressure introduction port 26B to the suction pressure port 27 is reduced, and by the cooperative action of the supply valve body portion 15a and the extraction valve body portion 15g, there is only one conventional valve body portion. The crank chamber pressure Pc is quickly increased and the discharge amount of the compressor is rapidly decreased as compared with the above.

  On the other hand, when the electromagnetic force of the solenoid increases, the upward suction force with respect to the plunger 37 increases, so that the plunger 37 moves upward, and the valve rod 15, the supply valve body 15a, and the extraction valve body 15g together with it. As a result, the valve opening of the supply valve body 15a is reduced, but the valve opening of the extraction valve body 15g is increased, resulting in a decrease in the refrigerant flow rate from the discharge pressure port 25 to the crank chamber pressure port 26A. At the same time, the refrigerant flow rate from the crank chamber pressure introduction port 26B to the suction pressure port 27 increases, and due to the cooperative action of the supply valve body portion 15a and the extraction valve body portion 15g, there is only one conventional valve body portion. The crank chamber pressure Pc is quickly lowered and the discharge amount of the compressor is quickly increased as compared with the above.

  Thus, in the control valve 1 of the present embodiment, the supply valve body portion 15a and the extraction valve body portion 15g are provided on the valve rod 15, and when the opening degree of the supply valve body portion 15a increases, the extraction valve body portion When the opening degree of 15g becomes small and conversely, when the opening degree of the air supply valve body part 15a becomes small, the opening degree of the extraction valve body part 15g becomes large, and the air supply valve body part 15a and the extraction valve body Since the crank chamber pressure Pc is controlled in cooperation with the portion 15g, the crank chamber pressure (control pressure) Pc is set to a target value (desired value) as compared with a conventional valve body portion having only one valve body portion. ) Quickly.

  In addition, since the crank chamber pressure passage 70 is provided in the valve rod 15 so as to communicate the crank chamber pressure port 26 and the extraction valve chamber 21B, the crank chamber pressure Pc bypasses the crank chamber pressure port 26 to the outside. Instead, it is led to the suction pressure chamber 23 and the suction pressure port 27 through the crank chamber pressure passage 70 and the extraction valve body 15g in the control valve 1.

  Therefore, the crank chamber pressure introduction port (26B) provided in the conventional control valve shown in FIG. 3 is not necessary, and the crank chamber pressure Pc is guided to the compressor to the crank chamber pressure introduction port (26B). For this reason, there is no need for a passage.

  As a result, the structure becomes simple, the cost can be reduced, the responsiveness of the control of the crank chamber pressure Pc can be improved, the wasteful flow of the refrigerant can be reduced, and the control efficiency can be improved. be able to.

The longitudinal section showing one embodiment of the control valve for variable capacity type compressors concerning the present invention. FIG. 2 is an enlarged longitudinal sectional view of a main part of the control valve shown in FIG. 1. The expanded longitudinal cross-sectional view of the principal part of an example of the conventional control valve for variable displacement compressors.

Explanation of symbols

1 Control Valve 15 for Variable Capacity Compressor 15 Valve Rod 15a Supply Valve Body Part 15g Extraction Valve Body Part 19 Guide Hole 20 Valve Body 21A Supply Valve Chamber 21A Extraction Valve Chamber 22A Supply Valve Seat Part 22B Extraction Valve Seat Part 23 Suction pressure chamber 25 Discharge pressure port 26 Crank chamber pressure port 27 Suction pressure port 30 Electromagnetic actuator 37 Plunger 40 Bellows body 45 Pressure sensing chamber 47 Valve opening spring 70 Crank chamber pressure passage

Claims (2)

A valve stem, a valve body, an electromagnetic actuator for driving the valve stem in the valve opening / closing direction, and a pressure-sensitive responsive member for driving the valve stem in the valve opening / closing direction in response to a suction pressure of a compressor. A control valve for a variable displacement compressor,
In order from the bottom, the valve rod is provided with an air supply valve body portion, a small diameter portion having a smaller diameter than the air supply valve body portion, an intermediate large diameter portion having a larger diameter than the small diameter portion, and an extraction valve body portion, In order from the bottom to the valve body, a crank chamber pressure port communicating with the crank chamber of the compressor, an air supply valve seat portion where the air supply valve body portion contacts and separates, and a discharge for introducing the discharge pressure of the compressor An air supply valve chamber having a pressure port, a guide hole into which an intermediate large-diameter portion of the valve rod is slidably inserted, a bleed valve chamber having a bleed valve seat portion to which the bleed valve body portion contacts and separates, and an intake A suction pressure chamber having a suction pressure port for deriving pressure is provided;
The valve rod is provided with a crank chamber pressure passage communicating the crank chamber pressure port and the extraction valve chamber, and when the valve rod moves up and down, the opening degree of the intake valve body and the extraction A control valve for a variable displacement compressor, wherein the opening of the valve body portion is changed in the reverse direction.   2. The intake valve body portion is positioned below the supply valve seat portion, and the extraction valve body portion is positioned above the extraction valve seat portion. The control valve for a variable displacement compressor as described.

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