KR20110048108A - Displacement control valve of variable displacement compressor - Google Patents

Abstract

PURPOSE: A capacity control valve of a capacity-variable compressor is provided to prevent the operation delay of the compressor by smoothly discharging liquid refrigerant evaporated from a crank chamber to a suction chamber at the initial operation of the compressor. CONSTITUTION: A capacity control valve of a capacity-variable compressor comprises a valve housing(110), a valve body(120), an electronic solenoid(130), a sleeve(140) and a relief valve(150). The valve housing a crank-chamber connecting hole(112), a discharge-chamber connecting hole(113), and a suction-chamber connecting hole(111), which undergoes the pressures of the crank chamber, the discharge chamber and the suction chamber of the compressor. A first guide hole(117), which crosses the discharge-chamber connecting hole and the crank-chamber connecting hole, passes through the valve housing. The valve body opens/closes the inlet of the first guide hole while reciprocating.

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 that can be quickly discharged when the crankcase pressure of the compressor rapidly increases.

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.

Hereinafter, the capacity control valve of the prior art will be schematically described with reference to the drawings.

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

As shown in FIG. 1, the capacity control valve 10 according to the related art is installed to be movable in the valve housing 11, the electromagnetic solenoid 13, and the valve housing 11 in which some connection holes are formed. The valve body 12 is included.

The valve housing 11 is formed with a first guide hole 14 for guiding the movement of the valve body 12.

In particular, as the electromagnetic solenoid 13 is energized, the valve body 12 is reciprocated to open and close the first guide hole 14 formed in the valve housing 11.

The valve housing 11 has a crank chamber connecting hole 15 and a discharge chamber connecting hole 16 in which the pressure Pc of the crank chamber and the pressure Pd of the discharge chamber respectively act. The discharge chamber connecting hole 16 and the crank chamber connecting hole 15 are configured to communicate with each other through the first guide hole 14.

In addition, the valve housing 11 has a suction chamber connecting hole 17 formed at a lower end of the discharge chamber connecting hole 16.

In addition, a sleeve member 18 is provided at the end of the valve body 12 to be configured to connect between the valve body 12 and the solenoid 13.

Meanwhile, a sleeve bore 19 is formed in the valve housing 11 in which the sleeve member 18 is installed, and a sleeve 20 corresponding to the sleeve bore 19 is formed in the sleeve member 18. .

In addition, the sleeve member 18 is provided with an accommodating portion 21 therein, and the accommodating portion 21 is provided with a bellows 22.

The valve housing 11 is provided with a cap 23 which is screwed in a direction facing the end of the valve body 12, and a support spring 24 between the valve body 12 and the cap 23. ) Is provided to regulate the expansion force of the bellows 22 and the expansion force of the first spring 25 installed therein.

On the other hand, the cap 23 is formed so that a part is open is configured to act on the pressure (Pc) of the crank chamber.

However, the capacity control valve according to the prior art has not been disclosed to discharge the crankcase liquid refrigerant when the crankcase liquid refrigerant suddenly increases due to vaporization of the crankcase liquid refrigerant during the initial operation of the compressor or abnormal operation of the compressor. .

The present invention has been made to solve the above-mentioned conventional problems, and an object of the present invention is to provide a capacity control valve of a variable displacement compressor capable of quickly discharging when the pressure of the crankcase rapidly increases. .

The capacity control valve of the variable displacement compressor of the present invention for achieving the above object is, in the capacity control valve of the variable displacement compressor, the crank chamber connection hole and the discharged crank chamber pressure and discharge chamber pressure and suction chamber pressure of the compressor A valve housing having a seal connecting hole and a suction chamber connecting hole respectively formed therein and having a first guide hole passing through the discharge chamber connecting hole and the crank chamber connecting hole; A valve body which opens and closes the first guide hole inlet while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; A sleeve for connecting between the solenoid and the valve body; And a relief valve which opens when the pressure of the crank chamber is equal to or higher than a set pressure and connects the crank chamber and the suction chamber.

The relief valve may further include: a second guide hole formed in the sleeve, an auxiliary valve body for opening and closing the second guide hole inlet and reciprocating motion, an elastic body elastically supporting the auxiliary valve body in the direction of the second guide hole; It is preferable to include a discharge groove formed in the sleeve.

In addition, an inflow passage connecting the crank chamber and the second guide hole is formed in the sleeve, and a discharge passage connected to the discharge groove is formed between the valve housing and the sleeve.

On the other hand, the sleeve is preferably provided with an elastic support wall.

In addition, the auxiliary valve body is preferably formed in a spherical shape.

In addition, the elastic body is preferably one of a coil spring, a leaf spring, rubber and resin series.

According to the displacement control valve of the variable displacement compressor according to the present invention, when the crankcase pressure of the compressor rapidly increases by the relief valve, it can be quickly discharged to the suction chamber.

That is, the liquid refrigerant evaporated from the crank chamber during the initial operation of the compressor smoothly discharged to the suction chamber to prevent the operation delay of the compressor and at the same time easy to move to the maximum inclination angle of the swash plate.

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

2 is a longitudinal sectional view showing the structure of a variable displacement compressor according to the present invention, Figure 3 is a longitudinal sectional view showing the structure of the capacity control valve in Figure 2, Figure 4 is an enlarged longitudinal sectional view of a part 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 in FIG. 2, the variable displacement swash plate type compressor C includes a cylinder block 10 having a plurality of cylinder bores 12 formed on an inner circumferential surface in parallel in a longitudinal direction thereof, and a cylinder block 10 of the cylinder block 10. The front housing 16 is hermetically coupled to the front, and the rear housing 18 hermetically coupled via a valve plate 20 to the rear of the cylinder block 10.

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. 3, 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.

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 140 is provided at an end of the valve body 120 to be configured to connect between the valve body 120 and the solenoid 130.

Meanwhile, a sleeve bore 119 is formed in the valve housing 110 in which the sleeve 140 is installed, and a needle 141 corresponding to the sleeve bore 119 is formed in the sleeve 140. The needle 141 is preferably formed larger than the diameter of the valve body 120.

In addition, the needle 141 penetrates through the valve body 120 and is preferably fixed to prevent relative movement.

In addition, a relief valve 150 is further provided to open when the pressure Pc of the crank chamber 86 is greater than or equal to a set pressure to connect the crank chamber 86 and the suction chamber 32.

The relief valve 150 has a second guide hole 151 formed in the sleeve 140, an auxiliary valve body 152 for opening and closing the inlet of the second guide hole 151 while reciprocating, and the auxiliary valve. It includes an elastic body 153 for elastically supporting the sieve 152 in the direction of the second guide hole 151 and a discharge groove 154 formed in the sleeve 140.

In addition, the inlet flow passage 155 connecting the crank chamber 86 and the second guide hole 151 is formed in the sleeve 140, and the discharge groove is formed between the valve housing 110 and the sleeve 140. A discharge passage 156 is formed that is connected to the 154. At this time, the discharge passage 156 is preferably connected to the suction chamber (22).

When the crank chamber 86 pressure Pc of the compressor is rapidly increased by the relief valve 150 configured as described above, the auxiliary valve body 152 opens the second guide hole 151 to press the crank chamber 86 pressure. Pc is quickly discharged to the suction chamber 22.

That is, during initial operation of the compressor, the liquid refrigerant evaporated from the crank chamber 86 is smoothly discharged to the suction chamber 22 to prevent the operation delay of the compressor and to easily move to the maximum inclination angle of the swash plate 50. do.

In addition, the sleeve 140 is provided with an elastic support wall 157 is configured so that the crank chamber 86 pressure (Pc) does not affect the bellows 160 to be described later.

On the other hand, the set pressure of the relief valve 150 is adjusted by the elastic force of the elastic body 153.

In addition, the electromagnetic solenoid 130 surrounds the movable iron core 131 connected to the sleeve 140, the electromagnetic coil 132 disposed around the movable iron core 131, the electronic coil 132, and the like. It 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 140, and the valve body 120 reciprocate by energizing the electromagnetic solenoid 130, and the discharge chamber connecting hole 113 by 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.

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.

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 140 and the first guide hole 117 are formed.

In addition, an accommodating part 170 is formed inside the sleeve 140, and a bellows 160 is installed in the accommodating part 170.

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 (140).

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

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. 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.

For example, the auxiliary valve body 152 may be a spherical ball valve is applied.

In addition, the elastic body 153 is shown as a coil spring, but is not particularly limited thereto, and may include plate springs, rubber, and resin series.

In addition, in the above description, the relief valve 150 is illustrated and described as being formed in the sleeve 140, but the relief valve 150 of the present invention may be formed in the valve body of the capacity control valve.

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 cross-sectional view showing the structure of the displacement control valve in FIG.

4 is an enlarged vertical cross-sectional view of a portion 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 Third Guide

140 ... sleeve

150 ... relief valve

160 ... bellows

170 ... bellows receptacle

C ... variable displacement compressor

Claims (6)

In the displacement control valve of the variable displacement compressor, A crank chamber connection hole, a discharge chamber connection hole, and a suction chamber connection hole, respectively, which receive the crank chamber pressure, the discharge chamber pressure, and the suction chamber pressure of the compressor, are respectively formed therein, and the first guide crosses the discharge chamber connection hole and the crank chamber connection hole. A valve housing formed so that the ball penetrates; A valve body which opens and closes the first guide hole inlet while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; A sleeve for connecting between the solenoid and the valve body; And A relief valve which opens when the crank chamber pressure is equal to or higher than a set pressure and connects the crank chamber and the suction chamber; Capacity control valve of a variable displacement compressor comprising a. The method of claim 1, The relief valve, A second guide hole formed in the sleeve, an auxiliary valve body for opening and closing the second guide hole inlet and reciprocating motion, an elastic body elastically supporting the auxiliary valve body in the direction of the second guide hole, and a discharge groove formed in the sleeve Capacity control valve of the capacity of the deformation compressor comprising a. 3. The method of claim 2, An inlet flow passage is formed in the sleeve to connect the crank chamber and the second guide hole, and a discharge flow passage connected to the discharge groove is formed between the valve housing and the sleeve. The method of claim 2 or 3, Capacity control valve of the variable displacement compressor, characterized in that the sleeve is provided with an elastic support wall. 3. The method of claim 2, The auxiliary valve body is a capacity control valve of a variable displacement compressor, characterized in that formed in a spherical shape. 3. The method of claim 2, The elastic body is a capacity control valve of a variable displacement compressor, characterized in that one of the coil spring, leaf spring, rubber and resin series.

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