KR100986939B1 - Displacement control valve of variable displacement compressor - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a capacity control valve of a variable displacement compressor. Since it is characterized in that the adjustment, the magnitude of the current acting on the electromagnetic solenoid is proportional to the difference between the discharge pressure and the suction pressure has the advantage that it is easy to adjust the discharge capacity and torque.

Compressor, variable capacity, capacity control valve, solenoid, valve body, electromagnetic coil, bellows

Description

Capacity control valve of variable displacement compressor {DISPLACEMENT CONTROL VALVE OF VARIABLE DISPLACEMENT COMPRESSOR}

The present invention relates to a capacity control valve of a variable displacement compressor, and more particularly, a capacity of a variable displacement compressor for adjusting a discharge capacity by a balance relationship between a discharge pressure and a suction pressure, a bellows force, and an electromagnetic force of an electromagnetic solenoid. It relates to a control valve.

Since the compressor included in the cooling system of the automotive air conditioner is directly connected to the engine through the belt, the rotation speed cannot be controlled.

Therefore, in recent years, a variable capacity compressor that can change the discharge amount of the refrigerant to obtain a cooling capacity without being regulated by the rotational speed of the engine has been used a lot.

Various types of variable displacement compressors are disclosed, such as swash plate type, rotary type and scroll type.

In the swash plate type compressor, the swash plate provided so that the inclination angle is variable in the crank chamber rotates according to the rotational motion of the rotating shaft, and the piston reciprocates by the rotational motion of the swash plate. In this case, the refrigerant in the suction chamber is sucked into the cylinder by the reciprocating motion of the piston, compressed and discharged into the discharge chamber. The inclination angle of the swash plate is changed according to the pressure difference in the crank chamber and the pressure in the suction chamber, and the discharge amount of the refrigerant is Will be controlled.

In particular, by adopting an electromagnetic solenoid type capacity control valve to open and close the valve by energization to adjust the pressure of the crank chamber, through this to adjust the inclination angle of the swash plate to adjust the discharge capacity.

At this time, the operation of the capacity control valve is calculated by a control unit in which a signal such as the detected engine speed, the temperature inside or outside the vehicle, the evaporator temperature, etc. is built in the CPU, and based on the calculation result, the current By sending it to an electromagnetic coil.

However, according to the conventional capacity control valve, there is no disclosure of a capacity control valve for adjusting the discharge capacity by using the equilibrium relationship between the pressure difference between the discharge chamber and the suction chamber, the bellows and the electromagnetic solenoid, which have a great influence on the torque of the compressor.

In addition, in the related art, a connection hole should be formed in the compressor and the capacity control valve in order to actuate the suction pressure in the capacity control valve.

In addition, conventionally, there is no means for preventing leakage of discharge pressure between the valve body operating inside the capacity control valve and the valve housing, and thus it is difficult to obtain a function of the capacity control valve.

In addition, according to the conventional capacity control valve, the valve seat is deformed due to frequent contact with the valve body, so that it is difficult to obtain an accurate opening degree, which has a disadvantage in that its performance is lowered.

In addition, since the valve must be operated against the high pressure formed in the discharge chamber communication path at the time of closing the valve, a large current must be supplied to the electromagnetic coil. As a result, the electromagnetic coil generates a large heat and damages the O-ring for sealing. This caused the refrigerant to leak.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a capacity control valve of a variable displacement compressor for adjusting the discharge capacity by using a balance between the pressure difference between the discharge chamber and the suction chamber, the bellows and the force of the electromagnetic solenoid. To provide.

It is also an object of the present invention to provide a capacity control valve of a variable displacement compressor that can simplify the manufacturing process of the compressor by forming a communication hole in which the suction pressure acts inside the capacity control valve.

It is also an object of the present invention to provide a capacity control valve of a variable displacement compressor capable of reliably preventing leakage of discharge pressure between a valve body operating inside the capacity control valve and a valve housing.

It is also an object of the present invention to provide a displacement control valve of a variable displacement compressor for preliminarily applying a deformation to a valve seat in contact with the valve body so as to accurately maintain the opening degree of the valve.

It is also an object of the present invention to provide a capacity control valve of a variable displacement compressor capable of preventing heat generation of an electromagnetic coil, preventing damage to peripheral parts such as an O-ring for sealing, and extending its life.

In order to achieve the above object, the capacity control valve of the variable displacement compressor according to the present invention, the difference between the discharge pressure (Pd) and the suction pressure (Ps), the force of the bellows installed in the capacity control valve and the electromagnetic force of the electromagnetic solenoid The discharge capacity is controlled by the equilibrium relationship.

In addition, a crank chamber connecting hole and a discharge chamber connecting hole respectively receiving the crank chamber pressure and the discharge chamber pressure of the compressor are respectively formed therein, and the valve formed so that the first guide hole passing through the discharge chamber connecting hole and the crank chamber connecting hole is passed through. Housings,

A valve body arranged to open and close a first guide hole inlet between the crank chamber connecting hole and the discharge chamber connecting hole while reciprocating;

An electromagnetic solenoid for reciprocating the valve body by energization;

And a bellows fixed to the opposite side of the solenoid of the valve body.

In this case, an off spring is disposed between the valve body and the electromagnetic solenoid.

In addition, the suction pressure of the compressor is applied to both ends of the valve body.

In addition, the electromagnetic solenoid is formed with a spring receiving portion for receiving the off spring, the valve housing is formed with a bellows receiving portion for receiving the bellows, the connection between the bellows receiving portion and the spring receiving portion by a connecting passage It is characterized by that.

The connecting passage may include a communication hole formed through the valve housing, and a communication path formed between the second guide hole formed inside the solenoid and the outer circumference of the valve body to move the valve body.

In addition, the valve body has a large diameter portion and a small diameter portion is formed, the portion divided into the suction chamber pressure and the discharge chamber pressure is characterized in that the portion divided into the small diameter portion, the crank chamber pressure and the suction chamber pressure is composed of a large diameter portion. .

In addition, the sealing body is interposed between the first guide hole and the small diameter portion of the valve body.

In addition, the sealing member is characterized in that the PTFE.

In addition, the first guide hole is formed with an inclined surface, characterized in that the valve body in contact with the inclined surface to open and close the first guide hole.

The inclined surface of the inclined portion is formed in the inlet portion of the variable displacement compressor of the displacement variable compressor, characterized in that.

In addition, the spring receiving portion is characterized in that it is formed by a container-shaped closed cylinder fitted to the electromagnetic solenoid.

In addition, a bellows stopper is fixedly installed around the valve body, and an end of the bellows is fixed to the bellows stopper.

In addition, the support spring is connected between the bellows and the valve housing.

According to the present invention, it is possible to provide the capacity control valve of the variable displacement compressor according to the present invention by adjusting the discharge capacity by using the equilibrium relationship between the pressure difference between the discharge chamber and the suction chamber, the bellows and the force of the electromagnetic solenoid.

That is, according to the present invention, the magnitude of the current acting on the electromagnetic solenoid is proportional to the difference between the discharge pressure and the suction pressure, so that the discharge capacity and the torque can be easily adjusted.

In addition, according to the present invention, a part of the capacity control valve is directly connected to the suction chamber, and the inside of the capacity control valve is formed so as to form a communication hole through which the suction pressure acts. Since there is no need for connecting holes, the manufacturing process of the compressor can be greatly simplified.

Further, according to the present invention, it is possible to reliably prevent leakage of the discharge pressure between the valve body and the valve housing operating inside the capacity control valve by the sealing body, thereby maintaining the reliability of the capacity control valve.

In addition, according to the present invention, by forming the intaglio portion by the load larger than the operating load of the valve body on the surface of the valve seat in contact with the valve body in advance to prevent the further deformation caused by the contact of the valve body and improve the opening degree of the valve It can be maintained accurately, so that the reliability of the capacity control valve can be maintained.

In addition, according to the present invention, the cooling of the electromagnetic solenoid is made by the connection hole, and since the bellows force assists the electromagnetic force of the electromagnetic coil, it prevents heat generation from the electromagnetic solenoid and damages peripheral parts such as an O-ring for sealing. It also has the advantage that it can prevent and prolong its life.

Hereinafter, with reference to the accompanying Figures 1 to 6 will be described in detail a preferred embodiment of the present invention.

First, the structure of the variable displacement swash plate type compressor provided with a capacity control valve according to the present invention will be described schematically.

As shown, the variable displacement swash plate type compressor C includes a cylinder block 10 having a plurality of cylinder bores 12 formed in parallel in the longitudinal direction on an inner circumferential surface thereof, and sealed in front of the cylinder block 10. The front housing 16 is coupled, and the rear housing 18 is hermetically coupled to the rear of the cylinder block 10 via a valve plate 20.

The crank chamber 86 is provided inside the front housing 16, and one end of the drive shaft 44 is rotatably supported near the center of the front housing 16, while the other end of the drive shaft 44 is Passed through the crank chamber 86 is supported via a bearing provided in the cylinder block 10.

In the crank chamber 86, the lug plate 54 and the swash plate 50 are provided around the drive shaft 44.

In the lug plate 54, a pair of power transmission support arms 62 each having a linearly perforated guide hole 64 formed at the center thereof are formed to protrude integrally on one surface, and one surface of the swash plate 50 has a ball. As the lug plate 54 rotates, the ball 66 of the swash plate 50 slides in the guide hole 64 of the lug plate 54 so that the swash plate 50 can be rotated. The inclination angle is variable.

In addition, the outer circumferential surface of the swash plate 50 is fitted to the piston 14 so as to be able to slide through the shoe 76.

Accordingly, as the swash plate 50 rotates in an inclined state, the pistons 14 fitted through the shoe 76 on the outer circumferential surface thereof are reciprocated in each cylinder bore 12 of the cylinder block 10. do.

In addition, a suction chamber 22 and a discharge chamber 24 are formed in the rear housing 18, and each cylinder bore is provided in the valve plate 20 interposed between the rear housing 18 and the cylinder block 10. A suction port 32 and a discharge port 36 are respectively formed in a position corresponding to (12).

By the reciprocating motion of the piston 14, the refrigerant in the suction chamber 22 is sucked into the cylinder bore 12, compressed, and discharged to the discharge chamber 24. The pressure in the crank chamber 86 and the suction chamber ( The inclination angle of the swash plate 50 is changed according to the pressure difference in the 22 to adjust the discharge amount of the refrigerant.

Specifically, the variable displacement compressor adopted in the embodiment of the present invention adopts the electromagnetic solenoid type capacity control valve 100 to adjust the pressure of the crank chamber 86 by opening and closing the valve by energization, through which the swash plate 50 ) To adjust the discharge capacity.

As shown in FIG. 2, the capacity control valve 100 according to the present invention is installed to be movable in the valve housing 110, the electromagnetic solenoid 130, and the valve housing 110 in which some connection holes are formed. The valve body 120 is included.

In addition, a first guide hole 117 is formed in the valve housing 110 to guide the movement of the valve body 120. The electromagnetic solenoid 130 has a movable iron core 131 and a valve body (to be described later). The second guide hole 137 for guiding the movement of the 120 is formed.

In particular, as the electromagnetic solenoid 130 is energized, the valve body 120 is configured to open and close the first guide hole 117 formed in the valve housing 110 while reciprocating.

The valve housing 110 is formed with a crank chamber connecting hole 112 and a discharge chamber connecting hole 113 in which the pressure Pc of the crank chamber 86 and the pressure Pd of the discharge chamber 24 respectively work. have. The discharge chamber connecting hole 113 and the crank chamber connecting hole 112 have a structure in communication with each other through the first guide hole 117.

In the drawing, the discharge chamber connecting hole 113 is formed in a direction orthogonal to the crank chamber connecting hole 112 and the suction chamber connecting hole 111, respectively, but the direction may be arbitrarily determined.

In addition, the bellows receiving portion 170 is formed at the opposite end of the solenoid of the valve housing 110. A portion of the tip of the valve body 120 protrudes through the first guide hole 117 of the valve housing 110, and a bellows 160 is installed at the tip of the bellows accommodating part 170.

The bellows 160 is a corrugated structure in which a certain amount of air is filled so that a predetermined pressure is applied when no external load is applied, and the bellows 160 exerts a force on a component connected thereto while performing expansion / contraction by external pressure. Component.

In the embodiment of the present invention, a bellows stopper 161 is fixedly installed around the valve body 120, and an end of the bellows 160 is fixed to the bellows stopper 161. The bellows stopper 161 regulates the opening degree of the valve to be described later and the expansion amount of the bellows.

In addition, the support spring 167 is connected between the bellows 160 and the valve housing 110, so that the bottom of the bellows 160 is always urged outward.

The bellows receiving portion 170 is directly connected to the suction chamber 22, the suction chamber pressure (Ps) is applied. However, the suction chamber 22 and the bellows receiving unit 170 may be connected through a separate inlet (not shown) formed in the compressor housing.

In the figure, reference numeral 162, which is not described, serves to block foreign matter from passing through the control valve as a filter.

In addition, the valve body 120 is divided into a large diameter portion 122 and a small diameter portion 123 with the jaw portion 121 as a boundary. The solenoid side of the electronic part solenoid part 122, the bellows 160 side of the jaw part 121 form a small diameter part 123. The jaw portion 121 is capable of opening and closing the inlet of the first guide hole 117 connecting the discharge chamber connecting hole 113 and the crank chamber connecting hole 112.

As shown in FIG. 2, when the pressure is used as a reference, the portion divided into the suction chamber pressure Ps and the discharge chamber pressure Pd is the small diameter portion 123, the crank chamber pressure Pc, and the suction chamber pressure. The portion divided by Ps is composed of a large diameter portion 122.

In particular, the inlet of the first guide hole 117 is formed with an inclined surface 117a which is a valve seat surface, and the jaw portion 121 of the valve body 120 contacts the inclined surface 117a with the first guide hole ( 117 may be configured to open and close.

In this case, the valve housing 110 is made of a material such as brass so as not to be magnetized, and the valve body 120 is made of steel. Therefore, the surface of the valve seat may be deformed by repeated contact with the jaw portion 121 of the valve body 120 and the valve seat (inclined surface 117a) of the valve housing 110, which is relatively sharp. Opening degree was not formed by the intended amount, and the reliability of the compressor may fall.

In order to prevent this, in the embodiment of the present invention, the valve seat surface (inclined surface) of the valve housing 110 in advance a load larger than the maximum load acting between the jaw portion 121 and the valve housing 110 of the valve body 120. , 117a) to form a concave recessed portion 118 to prevent deformation during operation.

On the other hand, the solenoid 130 is a movable iron core 131 connected to the valve body 120, the electromagnetic coil 132 disposed around the movable iron core 131, the electromagnetic coil 132 and the like The solenoid housing 134 is wrapped, and the fixed core 133 is disposed inside the electromagnetic coil 132 while surrounding the circumference of the valve body 120.

The solenoid housing 134 corresponds to an injection molded product or an insulating case surrounding the electronic coil 132.

Accordingly, the movable iron core 131 and the valve body 120 reciprocate by energizing the electromagnetic solenoid 130, and the discharge chamber connecting hole 113 is formed by the jaw portion 121 of the valve body 120. And the inlet of the first guide hole 117 connecting between the crank chamber connecting hole 112 is opened and closed.

An off-spring 125 is installed between the fixed iron core 133 and the movable iron core 131 or between the fixed iron core 133 and the valve body 120, so that the valve body 120 is normally used without an external force. Ascends to maintain the inlet of the first guide hole 117 is open.

2 and 3, a ring-shaped gap 138 is formed between the movable iron core 131 and the valve body 120, and between the bottom of the gap 138 and the central end of the solenoid housing 134. The off spring 125 is interposed.

2 and 3, the movable iron core 131 and the off spring 125 are accommodated by a container-shaped sealing tube 139 fitted to the solenoid housing 134 and the solenoid housing 134. It is. That is, the spring receiving portion 136 is formed between the fixed iron core 133 and the sealing tube 139.

In addition, as shown in FIG. 3, a communication hole 128 penetrating the valve housing 110 in the valve body moving direction between the bellows receiving portion 170 and the spring receiving portion 136, and a valve body ( It is communicated by the communication path 135 between the periphery of the 120 and the second guide hole 137 formed in the solenoid housing 134.

Accordingly, when the suction pressure Ps acts on the bellows accommodating part 170, the suction pressure also acts on the solenoid housing 134. With this structure, the external control hole for applying the suction pressure Ps to the spring receiving portion 170 can be omitted in the capacity control valve and the compressor.

Furthermore, the suction solenoid gas having the suction pressure Ps passes through the communication path 135, whereby the electronic solenoid 130 portion can be effectively cooled. Accordingly, the reliability of the electronic solenoid 130 is increased, and the electronic solenoid 130 can accurately generate electromagnetic force proportional to the current without being affected by the generated heat.

On the other hand, a sealing body 129 is interposed between the circumference of the valve body 120 and the first guide hole 117 of the valve housing 110, so that a high pressure difference between the discharge pressure Pd and the suction pressure Ps is achieved. It is possible to reliably prevent leakage caused.

The sealing body 129 may be a material such as PTFE.

4 and 5, the operation of the capacity control valve according to the present invention will be described.

In the operation description, the initial state is a state in which power supply to the capacity control valve 100 is cut off, as shown in FIG. 4, and the valve body 120 is lowered by the off-spring 125 so that the valve body ( The jaw portion 121 of the 120 is separated from the inlet of the first guide hole 117 connecting between the discharge chamber connecting hole 113 and the crank chamber connecting hole 112 to maintain an open state.

Accordingly, since the discharge pressure Pd acts on the crank chamber 86 through the crank chamber connecting hole 112 via the first guide hole 117 through the discharge chamber connecting hole 113, the crank chamber 86 ), The pressure increases and the inclination angle of the swash plate 50 rapidly decreases, thereby reducing the amount of refrigerant discharged.

Next, when the engine speed, the indoor and outdoor temperature difference, the evaporator downstream temperature and pressure is detected and the signal is sent to the MCU, the calculation is performed with the thermal load set in the MCU, and the detected thermal load exceeds the set value. The current signal for increasing the refrigerant discharge amount is sent to the power source.

Accordingly, an increased current flows through the electromagnetic solenoid 130, and as shown in FIG. 5, the movable iron core 131 and the valve body 120 resist the resistance of the off-spring 125 and the discharge chamber connecting hole 113. The discharge chamber connecting hole 113 is closed by moving upwardly after discharging the discharge pressure Pd.

As a result, the pressure inside the crank chamber 86 decreases and the inclination angle of the swash plate 50 increases, so that the discharge amount and the discharge pressure of the compressor increase rapidly.

At this time, the suction pressure Ps is increased due to the external thermal load, that is, the indoor temperature is high, and the suction pressure Ps thus raised is applied to the bellows receiving unit 170 through the filter 162. do.

The bellows 160 is reduced by the increased suction pressure Ps, and the valve body 120 fixed to the bellows 160 receives a rising force. In such a relationship, the valve body 120 can be easily moved up and down even if the electric current acting on the electromagnetic solenoid 130 is small. When the amount of current acting on the electronic solenoid 130 decreases, the amount of heat generated from the electronic coil 132 also decreases, thereby minimizing the thermal effect of the electronic solenoid 130 and maintaining reliability.

On the contrary, when the thermal load is reduced, a signal for the reduced current from the MCU is transmitted to the electronic solenoid 130, and in this case, the electromagnetic force is also reduced, so that the valve body (B) is discharged by the force of the discharge pressure Pd and the off spring 125. 120) receives a descending force.

Accordingly, the jaw portion 121 of the valve body 120 starts to be separated from the inlet of the first guide hole 117 connecting between the discharge chamber connecting hole 113 and the crank chamber connecting hole 112, and then Since the discharge pressure Pd acts on the crank chamber 86, the pressure of the crank chamber 86 is increased, and the inclination angle of the swash plate 50 and the discharge amount of the refrigerant are also drastically reduced.

In this state, since the cooling of the room temperature has already been sufficiently achieved, since the suction pressure Ps is naturally reduced, the bellows 160 expands again to assist the lowering of the valve body 120.

As shown in Fig. 5, in the displacement control valve of the present invention described above, the equilibrium relationship of the force between the components is as follows.

Fsol + Fbel-Fspr = (Pd-Ps) × (As1-As2)

Here, As1 is a cross section of the large diameter portion 122, As2 is a cross section of the small diameter portion 123, Fsol is an electromagnetic force of the electromagnetic solenoid, Fbel is a force acting on the valve body 120 by the bellows 160 , Fspr means the elastic force of the off spring (125).

As described above, the electromagnetic force from the electromagnetic solenoid 130 and the force from the bellows 160 are proportional to the difference between the discharge pressure Pd and the suction pressure Ps or the cross-sectional area difference between the large diameter portion and the small diameter portion. That is, the discharge pressure-suction pressure (Pd-Ps), torque, and discharge capacity may be easily adjusted according to the magnitude of the current acting on the electronic solenoid 130.

In the above-described action of the present invention, the jaw portion 121 of the valve body 120 only shows the configuration of opening and closing the inlet, but the opening degree of the inlet of the first guide hole 117 can be adjusted according to the amount of energization. Of course it can.

1 is a longitudinal sectional view showing a structure of a variable displacement compressor according to the present invention.

Figure 2 is a front longitudinal cross-sectional view showing the structure of the capacity control valve in FIG.

Figure 3 is a side longitudinal cross-sectional view showing the structure of the capacity control valve in FIG.

4 is a view showing a state in which the valve is open in FIG.

5 is a view showing a state in which the valve is closed in FIG.

Figure 6 is a perspective view showing the structure of a capacity control valve according to the present invention.

※ Explanation of Major Components

100 ... Capacity control valve

110 ... valve housing

112. Crankcase connector

113.Discharge chamber connection

117 ... The first guide

118 ... engraved

120 ... valve body

121 ... Chin

122 ... Dae Kyung

123 ... small neck

130 ... electronic solenoid

131. Iron core

132 ... electromagnetic coil

134 ... solenoid housing

137 ... The Second Guide

135.Communication path

136 ... spring receptacle

160 ... bellows

170 ... bellows receptacle

C ... variable displacement compressor

Claims (14)

In the displacement control valve of the variable displacement compressor, The discharge capacity is adjusted by the balance between the discharge pressure Pd and the suction pressure Ps, the balance of the bellows force and the electromagnetic force of the electromagnetic solenoid installed in the displacement control valve, A valve housing formed with a crank chamber connecting hole and a discharge chamber connecting hole respectively receiving the crank chamber pressure and the discharge chamber pressure of the compressor, and having a first guide hole passing through the discharge chamber connecting hole and the crank chamber connecting hole respectively; , A valve body arranged to open and close a first guide hole inlet between the crank chamber connecting hole and the discharge chamber connecting hole while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; A bellows fixed to the opposite side of the solenoid of the valve body, An inclined surface is formed in the first guide hole, and the capacity control valve of the variable displacement compressor, characterized in that for opening and closing the first guide hole while the valve body is in contact with the inclined surface. In the displacement control valve of the variable displacement compressor, The discharge capacity is adjusted by the balance between the discharge pressure Pd and the suction pressure Ps, the balance of the bellows force and the electromagnetic force of the electromagnetic solenoid installed in the displacement control valve, A valve housing formed with a crank chamber connecting hole and a discharge chamber connecting hole respectively receiving the crank chamber pressure and the discharge chamber pressure of the compressor, and having a first guide hole passing through the discharge chamber connecting hole and the crank chamber connecting hole respectively; , A valve body which is arranged to open and close a first guide hole inlet between the crank chamber connecting hole and the discharge chamber connecting hole while reciprocating, and the suction pressure of the compressor is applied to both ends; An electromagnetic solenoid for reciprocating the valve body by energization; A bellows fixed to the opposite side of the solenoid of the valve body, The valve body has a large diameter portion and a small diameter portion is formed, the portion divided into the suction chamber pressure and the discharge chamber pressure is a small diameter portion, the portion divided into the crank chamber pressure and the suction chamber pressure is composed of a large diameter portion, A capacity control valve of a variable displacement compressor, characterized in that a sealing body is interposed between the first guide hole and the small diameter portion of the valve body. The method of claim 1, A capacity control valve of a variable displacement compressor, characterized in that the off spring is disposed between the valve body and the solenoid. The method of claim 1, A capacity control valve of a variable displacement compressor, characterized in that the suction pressure of the compressor acts on both ends of the valve body. The method of claim 3, The electronic solenoid is formed with a spring receiving portion for receiving the off spring, the valve housing is formed with a bellows receiving portion for receiving the bellows, the bellows receiving portion and the spring receiving portion is connected by a connecting passage A capacity control valve of a variable displacement compressor. The method of claim 5, The connecting passage, the communication hole formed through the valve housing, the communication path formed between the second guide hole formed in the solenoid and the outer periphery of the valve body to move the valve body is configured to the capacity control valve of the variable displacement compressor . The method of claim 4, wherein The valve body has a large diameter portion and a small diameter portion is formed, the portion divided into the suction chamber pressure and the discharge chamber pressure is a small diameter portion, the portion divided into the crank chamber pressure and the suction chamber pressure is variable capacity, characterized in that consisting of a large diameter portion Capacity control valve of the compressor. The method of claim 7, wherein A capacity control valve of a variable displacement compressor, characterized in that a sealing body is interposed between the first guide hole and the small diameter portion of the valve body. The method of claim 8, The sealing body is a capacity control valve of a variable displacement compressor, characterized in that the PTFE. delete The method of claim 1, The inclined surface of the inclined portion is formed in the inlet portion of the variable displacement compressor of the displacement variable compressor, characterized in that. The method of claim 5, The spring receiving portion is a capacity control valve of a variable displacement compressor, characterized in that formed by a container-shaped closed cylinder fitted to the electromagnetic solenoid. The method of claim 1, A bellows stopper is fixedly installed around the valve body, and an end portion of the bellows is fixed to the bellows stopper. The method of claim 13, A capacity control valve of a variable displacement compressor, characterized in that the support spring is connected between the bellows and the valve housing.

Images