KR20100116737A - Displacement control valve of variable displacement compressor - Google Patents

Abstract

PURPOSE: A valve for controlling the capacity of a variable capacity compressor is provided to facilitate control since a nonmagnetic ring is installed between a fixed metal pin and a movable metal pin. CONSTITUTION: A valve(100) for controlling the capacity of a variable capacity compressor comprises a solenoid(130). The solenoid is composed of a fixed metal pin(133) and a movable pin(131). A non-magnetic ring is tightly inserted between the fixed metal pin and the movable metal pin and the thickness of the non-magnetic ring is the same as the minimum gap between the movable metal pin and the fixed metal pin. The shape of the non-magnetic ring is the same as that of a contact part at which the fixed metal pin and the movable metal pin face. The non-magnetic ring is formed as a disc on which a hole is formed.

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 to a capacity control valve of a variable displacement compressor capable of maintaining a fixed interval between the fixed iron core and the movable iron core.

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 installed so that the inclination angle is variable in the crank chamber rotates according to the rotational motion of the rotary 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.

A representative example of a capacity control valve of such a variable displacement compressor is disclosed in the following Patent Document 1 (hereinafter referred to as 'prior art'), and a schematic configuration thereof will be described with reference to FIG.

As shown, the capacity control valve 5 according to the prior art has a shaft portion 15c, a valve body having a diameter smaller than the middle small diameter portion 15b and a diameter larger than the shaft portion 15c than the shaft portion 15c. A valve rod 15 having a portion 15a, a guide hole 19 into which the shaft portion 15c of the valve rod 15 is inserted so as to be free to slide, and a valve body portion 15a are provided at their lower ends (valve). The discharge pressure Pd from the compressor to the valve chamber 21 provided with the valve opening 22 separated from the seat 22a, and the outer peripheral part (upstream of the valve opening 22) of the valve chamber 21. A discharge pressure refrigerant inlet port 25 with a plurality of filters 25A for introducing a refrigerant of refrigerant is provided, and the refrigerant continuously passes through the crank chamber of the compressor at the lower side (downstream side) of the valve port 22. The valve body 20 and the electronic actuator 30 provided with the outlet 26 are provided.

The electromagnetic actuator 30 includes a coil 32 having a connector portion 31 for power transmission, a cylindrical stator 33 disposed on an inner circumferential side of the coil 32, and a stator 33. A pipe having a fixed iron core 34 having a concave shape in which a cross section is press-fitted to the lower end inner circumference and a flange-shaped portion 35a whose upper end is joined to the outer circumference (step portion) of the stator 33 by TIG welding ( 35 and a bottom disposed to cover the outer circumference of the movable core 37 and the coil 32 which are arranged to be freely slidable in the vertical direction on the inner circumferential side of the pipe 35 from below the fixed iron core 34. The cylindrical housing 60 which has a hole with this is provided.

In addition, an adjustment screw 65 having a hexagonal hole is screwed to the upper portion of the stator 33, and between the adjustment screw 65 and the fixed core 34 on the inner circumferential side of the stator 33. The decompression chamber 45 is formed in which the suction pressure Ps of the compressor is introduced, and the decompression chamber 45 is provided with a bellows 41 as a member moving in accordance with the decompression, and has an inverted convex upper stopper 42. ), A bellows main body 40 composed of an inverted lower stopper 43 and a compression coil spring 44 is disposed.

A compression coil spring 46 is disposed between the bellows main body 40 and the fixed iron core 34 to compress the bellows main body 40 in a direction in which the bellows main body 40 is contracted (compression direction on the adjustment screw 65 side). It is. Further, an operating rod 14 penetrating the fixed iron core 34 is provided between the lower stopper 43 (reverse concave portion) of the bellows body 40 and the concave portion 37c of the movable iron core 37. The compression coil spring which is arrange | positioned and presses the valve rod 15 downward (valve opening direction) via the movable iron core 37 between the said fixed iron core 34 and the movable iron core 37 (concave part 37b). The valve opening spring 47 which consists of this is arrange | positioned.

On the other hand, a convex stopper portion 28 protruding from the upper center of the valve body 20 for regulating the lowest position of the movable iron core 37 is provided, and includes the convex stopper portion 28. In the central portion above the valve chamber, a guide hole 19 into which the valve rod 15 is inserted so as to slide freely is formed. In addition, between the movable iron core 37 and the upper outer circumference of the valve body 20 (the outer circumference of the convex stopper portion 28), a suction pressure refrigerant introduction chamber 23 through which a refrigerant at the suction pressure of the compressor is introduced is formed. At the same time, a plurality of suction pressure refrigerant inlets 27 are formed on the outer circumferential side thereof, and the refrigerant at the suction pressure Ps introduced into the suction pressure refrigerant introduction chamber 23 from the suction pressure refrigerant inlet 27 is: The decompression chamber through the vertical grooves 37a, 37a, ... formed in the outer circumference of the movable iron core 37 and the continuous passage hole 37d protruding from the center portion, the continuous passage hole 39 formed in the fixed core 34, and the like. Introduced at 45.

The valve closing spring 48 which consists of a conical compression coil spring which presses the said valve rod 15 upward is arrange | positioned in the lower part (refrigerant outlet 26) of the said valve main body 20, The said valve closing spring By the pressing force of 48, the upper end part of the valve rod 15 always contacts with the movable core 37 (continuous passage hole 37d part).

In addition, a lower flange portion 35a of the pipe 35 is placed on the upper end portion of the valve body 20 through an O-ring 57, and between the flange portion 35a and the coil 32. A short cylindrical pipe holder 56 with a flanged portion 56a is fitted therein, and the flanged portions 35a and 56a are all fastened by the upper outer circumferential caulking portion 29 of the valve body 20. It is fixed.

In addition, the upper end portion of the pipe holder 56 is press-fitted and fixed with a bottom portion 61 having a hole in the housing 60, and the upper end portion 62 of the housing 60 has a flange shape of the connector portion 31. A caulking is fixed on the portion 31c, and a zero ring 66 is fitted between the housing 60 and the connector portion 31 and the coil 32. Moreover, the recessed part 31a in which the convex part 31b which fits in the hexagonal hole of the said adjustment screw 65 protrudes is formed in the center lower part of the connector part 31, and this recessed part 31a is provided. The upper part of the stator 33 and the adjustment screw 65 is inserted into the.

In the control valve 5 comprised in this way, when the solenoid part which consists of the coil 32, the stator 33, and the fixed iron core 34 was energized, the movable iron core 37 will be attracted to the fixed iron core 34. FIG. . As a result, the valve rod 15 can move upward (valve closing direction) by the pressing force of the valve closing spring 48.

On the other hand, the refrigerant of the suction pressure Ps introduced from the compressor to the suction pressure inlet 27 is fixed to the vertical grooves 37a, 37a, ... formed on the outer circumference of the movable iron core 37 from the introduction chamber 23. The bellows main body 40 (internal vacuum pressure) is introduced into the decompression chamber 45 through the continuous through hole 39 formed in the iron core 39, and the like (suction pressure Ps). Expansion and contraction (shrinkage when the suction pressure Ps is high and elongate when the suction pressure Ps is high), the displacement is transmitted to the valve rod 15 through the operating rod 14 and the movable core 37, and thus the valve. The opening degree (the lift amount of the valve body part 15a from the valve seat part 22a of the valve opening 22) is adjusted.

That is, the valve opening degree is the suction force of the movable core 37 by the solenoid part which consists of the coil 32, the stator 33, and the fixed iron core 34, the pressing force of the bellows main body 40, and the valve opening spring. It is determined by the pressing force by the 47 and the valve closing spring 48, the valve opening direction load by the discharge pressure Pd with respect to the valve shaft 15, and the valve closing direction load, and according to the valve opening degree, The amount of condensation of the refrigerant of the discharge pressure Pd introduced into the valve chamber 21 from the discharge pressure refrigerant inlet 25, that is, the amount of condensation (condensation amount) into the crank chamber is adjusted. In other words, the pressure Pc on the refrigerant outlet 26 side, that is, the pressure in the crank chamber, is controlled in accordance with the valve opening degree, thereby adjusting the inclination angle of the inclined plate of the compressor and the stroke of the piston, thereby increasing and decreasing the discharge amount. .

However, the capacity control valve 5 for a variable displacement compressor according to the prior art has a problem that it is difficult to maintain a proper installation interval between each other when assembling the fixed iron core 34 and the movable iron core 35.

As a result, since it is difficult to maintain the proper installation interval between the fixed iron core 34 and the movable iron core 35, the control of the solenoid portion becomes difficult, and thus the operation reliability of the capacity control valve 5 is lowered.

More specifically, if the distance between the fixed iron core 34 and the movable iron core 35 is too small, the electromagnetic force increases sharply so that there is no linear relationship between the current and the gap. The solenoid control becomes difficult.

[Patent Document 1] Japanese Unexamined Patent Publication No. 2006-291867

The present invention has been made to solve the above-mentioned conventional problems, the object of the present invention is to maintain a fixed interval between the installation of the fixed iron core and the movable core at the time of assembly capacity control valve of the variable displacement compressor easy to control To provide.

In the capacity control valve of the variable displacement compressor of the present invention for achieving the above object, in the capacity control valve of a variable displacement compressor including a solenoid consisting of a fixed iron core and a movable iron core, a nonmagnetic material between the fixed iron core and the movable iron core; The ring formed by the contact is inserted closely, the thickness of the ring is characterized in that the minimum spacing between the fixed core and the movable core.

In addition, the ring is preferably formed in the same shape as the contact portion in which the fixed iron core and the movable iron core face each other.

And, the capacity control valve of the variable displacement compressor, characterized in that the ring is formed by coupling a partial conical plate to the end of the disc formed hole.

On the other hand, the ring is preferably formed of a disc formed with a hole.

In addition, the ring is preferably formed of a partial conical plate.

And, the ring is preferably formed of brass.

In the displacement control valve of the variable displacement compressor of the present invention, the capacity control valve of the variable displacement compressor, the crank chamber connection hole, the discharge chamber connection hole and the suction chamber connection hole which receives the crank chamber pressure, the discharge chamber pressure and the suction chamber pressure of the compressor A valve housing formed in each of the plurality of valve housings to allow the first guide hole to communicate with the discharge chamber connecting hole and the crank chamber connecting hole; A valve body composed of a large diameter portion and a small diameter portion to open and close the first guide hole entrance while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; And a sleeve member having a diameter larger than that of the small diameter portion, the sleeve member connecting between the small diameter portion of the valve body and the electromagnetic solenoid, wherein the electromagnetic solenoid includes a fixed iron core and a movable iron core. A ring formed of a nonmagnetic material is tightly inserted between the movable iron cores, and the thickness of the ring is the minimum distance between the fixed iron core and the movable iron cores.

According to the capacity control valve of the variable displacement compressor according to the present invention, by installing a nonmagnetic ring between the fixed iron core and the movable iron core at the time of assembly, the installation interval can be kept constant, thereby controlling the effect easily.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings.

Figure 2 is a longitudinal sectional view showing a structure of a variable displacement compressor according to the present invention, Figure 3 is a longitudinal sectional view showing the capacity control valve of Figure 2, Figure 4 is a cross-sectional view showing the ring of FIG.

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 has a cylinder block 10 having a plurality of cylinder bores 12 formed parallel to the inner circumferential surface in the longitudinal direction, 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 It is designed to adjust the discharge capacity by adjusting the inclination angle of), and can be applied to all compressors of this characteristic.

Hereinafter, the capacity control valve 100 according to the present invention will be described in detail.

As shown in FIG. 5, the capacity control valve 100 according to the present invention is 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 to be installed 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.

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 addition, the valve housing 110 has a suction chamber connecting hole 111 formed at a lower end of the discharge chamber connecting hole 113.

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

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 crankcase connecting hole 112 is formed around the jaw portion 121 as the large diameter portion 122 and the suction chamber connecting hole 111 is formed as the small diameter portion 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.

On the other hand, although not shown, it is preferable that the suction pressure Ps of the compressor C or the pressure Pc of the crank chamber 86 act on both ends of the valve body 120.

In addition, a sleeve member 140 is provided at an end of the small diameter portion 123 of the valve body 120 to connect the small diameter portion 123 of the valve body 120 to the solenoid 130.

Meanwhile, a sleeve bore 119 is formed in the valve housing 110 in which the sleeve member 140 is installed, and a sleeve 141 corresponding to the sleeve bore 119 is formed in the sleeve member 140. . The sleeve 141 is preferably larger in diameter than the small diameter portion 123.

Here, the cross sectional area with respect to the diameter of the sleeve 141 is greater than or equal to the sum of the cross sectional area with respect to the diameter of the first guide hole 117 and the cross sectional area with respect to the diameter of the large diameter portion 122 divided by two. It is preferable to form so that a detailed description thereof will be described later.

On the other hand, the sleeve member 140 is preferably configured to be pressed against each other and the small diameter portion 123 to prevent relative movement.

In addition, the electromagnetic solenoid 130 may include a movable iron core 131 connected to the sleeve member 140, an electromagnetic coil 132 disposed around the movable iron core 131, the electronic coil 132, and the like. Wrapping is composed of a solenoid housing 134, a fixed iron core 133 disposed inside the electromagnetic coil 132 and a rod 135 coupled to the fixed iron core 133 and fixed to the bellows 160 to be described later. .

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

In addition, a second guide hole 131a for guiding the movement of the rod 135 is formed in the movable iron core 131.

Accordingly, the movable iron core 131, the sleeve member 140, and the valve body 120 reciprocate by energizing the electromagnetic solenoid 130, and are discharged by the jaw portion 121 of the valve body 120. The inlet of the first guide hole 117 connecting between the thread connection hole 113 and the crankcase connection hole 112 is opened and closed.

In addition, an off-spring 125 is installed between the fixed iron core 133 and the movable iron core 131. In the absence of external force, the valve body 120 is raised to raise the first guide hole 117. Keep the inlet open.

On the other hand, the fixed iron core 133 and the movable iron core 131 should be assembled at a predetermined interval. This is because, when the distance between the fixed iron core 133 and the movable iron core 131 is too small, the electromagnetic force increases sharply, and when the distance is too large, the electromagnetic force decreases rapidly, making it difficult to control the solenoid 130.

In order to solve this problem, a ring 139 formed of a non-magnetic material is closely inserted between the fixed iron core 133 and the movable iron core 131, and the thickness of the ring 139 is fixed iron core 133 and the movable iron core. It is formed at the minimum interval between 131. At this time, the minimum spacing between the fixed iron core 133 and the movable iron core 131 is determined through an operation experiment for finding an optimal state of the control of the solenoid 130.

In addition, the ring 139 is formed in the same shape as the contact portion 138 where the fixed iron core 133 and the movable iron core 131 face each other.

More specifically, as shown in (a) of FIG. 4, the ring 139 has a shape in which a partial conical plate is coupled to an end edge of a disc in which holes are formed to contact both upper and lower bent portions of the contact portion 138. 4, the ring 139 may be formed of a disc formed with a hole formed to contact the lower bent portion of the contact portion 138, or the ring 139 as shown in FIG. 4C. May be formed as a partial conical plate to abut the upper bent portion of the contact portion 138.

On the other hand, it is not limited to the shape of the ring 139 as described above, it is noted that it can be variously changed to correspond to the shape of the contact portion 138.

In addition, the ring 139 is preferably formed of a non-magnetic brass.

Accordingly, the operation reliability of the solenoid 130 is improved by keeping the installation intervals of the fixed iron core 133 and the movable iron core 131 constant by the ring 139.

In addition, the rod 135 may be screwed with the fixed iron core 133 to adjust an initial set value of the bellows 160 to be described later by the rotation of the rod 135.

In addition, the maximum opening amount of the valve body 120 is limited by the inner surface of the valve housing 110 in which one surface of the sleeve member 140 and the first guide hole 117 are formed.

In addition, the sleeve member 140 has an accommodating part 170 formed therein, and the accommodating part 170 is provided with a bellows 160.

On the other hand, the receiving portion 170 is directly connected to the suction chamber 22, the suction chamber pressure (Ps) is applied.

In addition, an insertion groove 161 is formed in the bellows 160, and an insertion hole 135a corresponding to the insertion groove 161 is formed in the rod 135 to be fixedly coupled to prevent relative movement.

On the other hand, the opposite end is not formed the insertion groove 161 of the bellows 160 is preferably fixed to the inside of the sleeve member (140).

In addition, the first support spring 162 may be built in the bellows 160 to maintain the expanded state.

In addition, the valve housing 110 is provided with a cap 165 that is screwed in a direction facing the end of the valve body 120, a second support spring between the valve body 120 and the cap 165. The expansion force of the bellows 160 and the expansion force of the first spring 162 installed therein are regulated.

In this case, the initial setting value of the second support spring 163 may be adjusted by the rotation of the cap 165.

 On the other hand, the cap 165 is formed so that a part is open so that the pressure (Pc) of the crank chamber 86 acts.

In addition, the movable iron core 131 is formed with a guide groove 131b to communicate with the suction chamber connecting hole 111.

Accordingly, the pressure Ps of the suction chamber 22 also acts on the solenoid housing 134. With this structure, the pressure Ps of the suction chamber 22 can also be applied to the movable iron core 131 and the sleeve member 140.

Furthermore, the suction solenoid gas having the pressure Ps of the suction chamber 22 passes through the solenoid housing 134 so that 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 an electromagnetic force proportional to the current without being affected by the generated heat.

Meanwhile, a ring groove 136 is formed in the rod 135, and an O-ring 137 is inserted into the ring groove 136 to prevent the leakage of the refrigerant introduced through the guide groove 131b.

In addition, a filter 180 is installed in the discharge chamber connecting hole 113 to serve to block foreign substances from entering the control valve.

As mentioned above, although preferred embodiment of this invention was described in detail, the technical scope of this invention is not limited to the above-mentioned embodiment, It should be interpreted by the claim. At this time, those of ordinary skill in the art should consider that many modifications and variations are possible without departing from the scope of the present invention.

For example, the filter 180 is installed in the discharge chamber connecting hole 113, but the foreign matter is applied to the control valve by applying to both the suction chamber connecting hole 111 and the crank chamber connecting hole 112 into which the refrigerant is introduced. It can be configured to block the input.

In addition, although the material of the ring 139 has been described as brass, the material of the ring 139 is not limited thereto, and may be used by changing to any material having a nonmagnetic material such as synthetic resin and nonferrous metal.

In addition, it is possible to apply to all the solenoid control valve applied to the variable displacement compressor.

1 is a longitudinal sectional view showing a capacity control valve of a variable displacement compressor according to the prior art.

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

3 is a longitudinal sectional view showing the capacity control valve of FIG.

4 is a cross-sectional view of the ring of FIG. 3.

* Description of symbols on main parts of the drawings *

100 ... Capacity control valve

110 ... valve housing

111 ... Suction Room Connector

112. Crankcase connector

113.Discharge chamber connection

117 ... The first guide

119 ... Sleeve Bore

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

138 ... contacts

139 ... Ring

140 ... sleeve

160 ... bellows

170 ... bellows receptacle

C ... variable displacement compressor

Claims (7)

In the capacity control valve of a variable displacement compressor including a solenoid consisting of a fixed iron core and a movable iron core, A ring formed of a nonmagnetic material is tightly inserted between the fixed iron core and the movable iron core, and the thickness of the ring is the minimum distance between the fixed iron core and the movable iron core. The method of claim 1, The ring is a capacity control valve of a variable displacement compressor, characterized in that the fixed iron core and the movable core is formed in the same shape as the contact portion facing each other. 3. The method of claim 2, The ring is a capacity control valve of a variable displacement compressor, characterized in that the partial conical plate is coupled to the end of the disc formed with holes. 3. The method of claim 2, The ring is a capacity control valve of a variable displacement compressor, characterized in that formed by a disc formed with a hole. 3. The method of claim 2, The ring capacity control valve of the variable displacement compressor, characterized in that formed by a partial conical plate. The method according to any one of claims 1 to 5, The capacity control valve of the variable displacement compressor, characterized in that the ring is formed of brass. In the displacement control valve of the variable displacement compressor, The first guide is provided with a crank chamber connecting hole, a discharge chamber connecting hole, and a suction chamber connecting hole which receive the crank chamber pressure, the discharge chamber pressure, and the suction chamber pressure of the compressor, respectively, and communicate with the discharge chamber connecting hole and the crank chamber connecting hole. A valve housing formed so that the ball penetrates; A valve body composed of a large diameter portion and a small diameter portion to open and close the first guide hole entrance while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; And A sleeve member having a diameter larger than that of the small diameter portion is formed and connects the small diameter portion of the valve body to the solenoid of the valve body. The electromagnetic solenoid is composed of a fixed iron core and a movable iron core, a ring formed of a non-magnetic material between the fixed iron core and the movable core is tightly inserted, the thickness of the ring is characterized in that the minimum interval between the fixed iron core and the movable iron core Capacity control valve of variable compressor.

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