KR101058586B1 - Capacity control valve of variable displacement compressor - Google Patents

Abstract

 In the displacement control valve of the variable displacement compressor of the present invention, the crank chamber connection hole, the discharge chamber connection hole and the first suction chamber connection hole which receive the crank chamber pressure, the discharge chamber pressure and the suction chamber pressure of the compressor are respectively formed therein, A valve housing formed so that a first guide hole intersecting the discharge chamber connection hole and a crank chamber connection hole and a second guide hole receiving the suction chamber pressure through an end thereof; A valve body having first and second valves interlocked to reciprocate to open and close the inlets of the first and second guide holes, respectively; And an electromagnetic solenoid for reciprocating the valve body by energization.

Accordingly, since the first guide hole connecting the discharge chamber and the crank chamber and the second guide hole connecting the crank chamber and the suction chamber are opened and closed interlocked by the valve body having the first and second valves, it is possible to prevent the compression loss of the compressor. It works.

Capacity variable compressors, capacity control valves

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 variable displacement compressor capable of preventing compression loss of the compressor because it controls the connection passage of the discharge chamber and the crank chamber and the connection passage of the crank chamber and the suction chamber. Relates to a capacity 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 bore and compressed by the reciprocating motion of the piston, and then discharged into the discharge chamber. The inclination angle of the swash plate changes according to the pressure difference in the crank chamber and the pressure in the cylinder bore, and the amount of refrigerant discharged. Will be controlled.

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

In addition, the conventional capacity control valve generally controls the passage of the discharge chamber and the crank chamber or the passage of the crank chamber and the compression chamber.

However, in the case of the conventional capacity control valve which opens the connection passage between the discharge chamber and the crank chamber, the connection passage between the crank chamber and the suction chamber is always opened to a constant area, so compression loss occurs.

In particular, when the conventional capacity control valve is in the open (PD-> PC) state, the connection path between the crank chamber and the suction chamber is also always open, so that the refrigerant in the discharge chamber flowing into the crank chamber should be larger, thus compressing already. Since the discharged refrigerant is discharged to the suction chamber through the crank chamber, recompression loss occurs.

The present invention has been made to solve the above-mentioned conventional problems, an object of the present invention is to control the connection passage of the discharge chamber and the crank chamber and the connection passage of the crank chamber and the suction chamber to prevent the compression loss of the compressor. To provide a capacity control valve of a variable displacement compressor.

In the capacity control valve of the variable displacement compressor of the present invention for achieving the above object, the crank chamber connection hole and the discharge chamber connecting hole and the first suction chamber connected to the crank chamber pressure, the discharge chamber pressure and the suction chamber pressure of the compressor A valve housing having a ball formed therein and having a first guide hole crossing the discharge chamber connection hole and a crank chamber connection hole and a second guide hole receiving the suction chamber pressure at an end thereof; A valve body having first and second valves interlocked to reciprocate to open and close the inlets of the first and second guide holes, respectively; And an electromagnetic solenoid for reciprocating the valve body by energization.

In addition, the first guide hole and the second guide hole is in a straight line, the first valve and the second valve is preferably arranged in a straight line.

The first and second valves may include a large diameter portion and a small diameter portion for opening and closing the first and second guide holes, respectively, and the diameter of the first valve small diameter portion may be smaller than the inner diameter of the first guide hole. The diameter of the second valve small diameter portion is preferably formed to be smaller than the inner diameter of the second guide hole.

On the other hand, the first valve and the second valve is formed on the opposite side around the jaw portion, it is preferable that the large diameter portion and the small diameter portion is formed in succession from the jaw portion.

In addition, the second guide hole is preferably formed in a cap provided at the end of the valve housing.

In addition, the sleeve having a larger diameter than the small diameter portion of the first valve is formed and preferably comprises a sleeve member for connecting between the small diameter portion and the solenoid of the valve body.

On the other hand, the sleeve member is provided with a receiving portion, it is preferable that the receiving portion is provided with a bellows.

According to the variable displacement compressor according to the present invention, the first guide hole connecting the discharge chamber and the crank chamber and the second guide hole connecting the crank chamber and the suction chamber are opened and closed by interlocking by a valve body having the first and second valves. There is an effect that can prevent the loss of compression.

In addition, when the first guide hole connecting the discharge chamber and the crank chamber is opened, the second guide hole connecting the crank chamber and the suction chamber is closed so that the refrigerant in the crank chamber is not discharged to the suction chamber, so that the pressure in the crank chamber is quickly increased. As a result, the movement to the minimum inclination angle of the swash plate is quick.

On the contrary, when the first guide hole connecting the discharge chamber and the crank chamber is closed, the second guide hole connecting the crank chamber and the suction chamber is opened so that the refrigerant in the crank chamber is discharged into the suction chamber so that the pressure in the crank chamber is rapidly lowered. The swash plate moves quickly to the maximum inclination angle.

As a result, the inclination angle of the swash plate is generated quickly, there is a side effect of preventing the operation delay of the compressor.

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

1 is a longitudinal sectional view showing a structure of a variable displacement compressor according to the present invention, Figure 2 is a longitudinal sectional view showing a displacement control valve 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 installed 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 to the outer peripheral surface of the swash plate 50 via the shoe 76 reciprocate in the respective cylinder bores 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, the capacity control valve 100 according to the present invention, the valve housing 110, the solenoid 130, the valve body is provided to be movable in the interior of the valve housing 110, a few connection holes are formed. It includes 120.

In addition, a first guide hole 117 is formed in the valve housing 110 to guide the movement of the lower end of the valve body 120.

In addition, the valve housing 110 has 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. Formed. 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.

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

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, the cap 165 to guide the movement of the upper end of the valve body 120 The second guide hole 165a is formed.

The pressure guide PS of the suction chamber 22 acts on the second guide hole 165a and communicates with the crank chamber connecting hole 112. Accordingly, the second guide hole 165a acts to actuate the crankcase 86 pressure Pc and the suction chamber pressure Ps of the compressor.

In particular, as the electromagnetic solenoid 130 is energized, the valve body 120 reciprocates and opens and closes the first and second guide holes 117 and 165a formed in the valve housing 110 and the cap 165. .

The valve body 120 is divided into a first valve 120a and a second valve 120b with the jaw portion 123 as a boundary. The first guide hole 117 is formed as a first valve 120a and the second guide hole 165a is formed as a second valve 120b around the jaw portion 123.

In addition, the first valve 120a is formed of a large diameter portion 121a and a small diameter portion 122a, and the large diameter portion 121a is formed between the discharge chamber connecting hole 113 and the crank chamber connecting hole 112. It is possible to open and close the entrance of the first guide hole 117 to be connected.

On the other hand, the diameter of the small diameter portion (122a) formed in the first valve (120a) is formed smaller than the inner diameter of the first guide hole 117 to form a passage of the refrigerant.

In addition, the second valve 120b is also formed of a large diameter portion 121b and a small diameter portion 122b, and the large diameter portion 121b is capable of opening and closing the inlet of the second guide hole 165a.

In addition, the diameter of the small diameter portion 122b formed in the second valve 120b is smaller than the inner diameter of the second guide hole 165b to form a passage of the refrigerant.

Accordingly, the first guide hole 117 connecting the discharge chamber 24 and the crank chamber 86 of the compressor, and the second guide hole 165b connecting the crank chamber 86 and the suction chamber 22 are prepared. Since the first and second valves 120a and 120b are opened and closed in conjunction with the valve body 120 formed therein, the compression loss of the compressor is prevented.

More specifically, when the first guide hole 117 connecting the discharge chamber 24 and the crank chamber 86 is opened by the first valve 120a of the valve body 120, the crank chamber 86 Since the second guide hole 165a connecting the suction chamber 22 to the suction chamber 22 is closed by the second valve 120b of the valve body 120, the refrigerant in the crank chamber 86 is not discharged to the suction chamber 22. The pressure in the crank chamber 86 is rapidly increased.

At this time, the inclination angle of the swash plate 50 is rapidly reduced to reduce the discharge amount and the discharge pressure of the compressor.

On the contrary, when the first guide hole 117 connecting the discharge chamber 24 and the crank chamber 86 is closed by the first valve 120a of the valve body 120, the crank chamber 86 and suction The second guide hole 165a connecting the chamber 22 is opened by the second valve 120b of the valve body 120 so that the coolant in the crank chamber 86 is discharged into the suction chamber 22 so that the crank chamber ( The pressure in 86 drops quickly.

At this time, the inclination angle of the swash plate 50 is rapidly increased, the discharge amount and the discharge pressure of the compressor is rapidly increased.

As a result, the first guide hole 117 and the second guide hole 165a are opened and closed on the contrary by the valve body 120 in which the first and second valves 120a and 120b are formed, so that the inclination angle movement of the swash plate 50 is performed. It is generated quickly to prevent the delay of operation of the compressor.

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 122a.

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 (122a) 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 third 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 solenoid 130, and at the same time, the first and second valves 120a of the valve body 120 are provided. 120b opens and closes the entrances of the first and second guide holes 117 and 165a.

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. While maintaining the inlet of the open state and at the same time the second guide hole (165a) to maintain the closed state.

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, a second support spring 163 is provided between the valve body 120 and the cap 165 to balance the expansion force of the bellows 160 and the expansion force of the first spring 162 installed therein. The shock of the valve body 120 is alleviated.

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

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 the above-described operation of the present invention, the first and second valves 120a and 120b of the valve body 120 only show the configuration of opening and closing the inlets of the first and second guide holes 117 and 165a. Of course, the openings of the inlets of the first and second guide holes 117 and 165a can be adjusted.

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. It will be understood by those skilled in the art that many modifications and variations are possible without departing from the scope of the present invention.

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

FIG. 2 is a longitudinal sectional view showing the capacity control valve of FIG. 1. FIG.

* 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

130 ... electronic solenoid

131. Iron core

132 ... electromagnetic coil

134 ... solenoid housing

137 ... The Second Guide

140 ... sleeve

160 ... bellows

165 ... cap

165a .. 2nd guide

170 ... bellows receptacle

C ... variable displacement compressor

Claims (7)

In the displacement control valve of the variable displacement compressor, A crank chamber connecting hole, a discharge chamber connecting hole, and a first suction chamber connecting hole which receive the crank chamber pressure, the discharge chamber pressure, and the suction chamber pressure of the compressor, respectively, and are formed to cross the discharge chamber connecting hole and the crank chamber connecting hole. A valve housing having a first guide hole and a second guide hole receiving the suction chamber pressure through the guide hole; A valve body having first and second valves interlocked to reciprocate to open and close the inlets of the first and second guide holes, respectively; And An electromagnetic solenoid for reciprocating the valve body by energization; Capacity control valve of a variable displacement compressor comprising a. The method of claim 1, The first guide hole and the second guide hole is in a straight line, the first valve and the second valve capacity control valve of the variable displacement compressor, characterized in that arranged in a straight line. 3. The method of claim 2, The first and second valves are composed of a large diameter portion and a small diameter portion to open and close the first and second guide holes, respectively, The diameter of the first valve small diameter portion is formed to be smaller than the inner diameter of the first guide hole, A diameter control valve of the variable displacement compressor, characterized in that the diameter of the second valve small diameter portion is formed to be smaller than the inner diameter of the second guide hole. The method of claim 3, The first valve and the second valve is formed on the opposite side with respect to the jaw portion, and the large diameter portion and the small diameter portion formed in succession from the jaw portion capacity control valve of the variable displacement compressor. 5. The method according to any one of claims 1 to 4, The second guide hole is a capacity control valve of a variable displacement compressor, characterized in that formed in the cap installed at the end of the valve housing. The method of claim 5, And a sleeve member having a diameter larger than that of the small diameter portion of the first valve and including a sleeve member connecting the small diameter portion of the valve body to the solenoid of the valve body. The method of claim 6, An accommodation portion is formed in the sleeve member, and the accommodation portion has a capacity control valve of a variable displacement compressor, characterized in that a bellows is provided.

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