KR101069633B1 - Displacement control valve of variable displacement compressor and assembly method thereof - Google Patents

Abstract

In the displacement control valve of the variable displacement compressor of the present invention, in the displacement control valve of the variable displacement compressor, a crank chamber connection hole and a discharge chamber connection hole respectively receiving the crank chamber pressure and the discharge chamber pressure of the compressor are respectively formed therein. A valve housing formed through the discharge chamber connecting hole and the first guide hole crossing the crank chamber connecting hole, a valve body composed of a large diameter portion and a small diameter portion at the periphery of the jaw to open and close the opening of the first guide hole while reciprocating, It characterized in that it comprises an electromagnetic solenoid for reciprocating the valve body, a sleeve which is provided in the small diameter portion of the valve body, the diameter is larger than the small diameter portion and the bellows is provided at the end of the sleeve and the coupling hole is formed.

Thereby, since the opening amount of the valve body is limited by the sleeve, even if the discharge pressure Pd increases, the suction pressure Ps maintains a constant value, thereby improving control accuracy.

Variable displacement compressor, displacement control valve, discharge pressure, suction pressure, sleeve

Description

Capacity control valve and assembling method of variable displacement compressor {DISPLACEMENT CONTROL VALVE OF VARIABLE DISPLACEMENT COMPRESSOR AND ASSEMBLY METHOD THEREOF}

The present invention relates to a capacity control valve and a method for assembling a variable displacement compressor, and more particularly, a variable displacement compressor configured to maintain a constant value of the suction pressure Ps even when the discharge pressure Pd is increased. It relates to a capacity control valve and an assembly method.

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.

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

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 refrigerant of the refrigerant is provided, and is continuously connected to 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 refrigerant | coolant 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 concave aspirator 34 having a concave end face press-fitted to the lower end inner circumference and a flange-shaped portion 35a whose upper end is joined to the outer circumference (step difference) of the stator 33 by TIG welding ( 35 and the plunger 37 and the bottom disposed to cover the outer circumference of the coil 32 are arranged on the inner circumferential side of the pipe 35 so as to be free to slide up and down on the inner circumferential side of the suction 34. A cylindrical housing 60 having a hole therein is provided.

Moreover, the adjustment screw 65 which has a hexagonal hole is screwed on the upper part of the said stator 33, and is between the said adjustment screw 65 and the aspirator 34 in the inner peripheral side of the stator 33. Moreover, as shown in FIG. 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.

And between the bellows main body 40 and the aspirator 34, the compression coil spring 46 which presses in the direction which contracts the bellows main body 40 (the direction compressed to the adjustment screw 65 side) is arrange | positioned. It is. In addition, between the lower stopper 43 (recess recess) of the bellows body 40 and the recess 37c of the plunger 37, an operating rod 14 penetrating the suction 34 is disposed. Between the suction 34 and the plunger 37 (concave portion 37b), a valve comprising a compression coil spring for pressing the valve rod 15 downward (valve opening direction) through the plunger 37. An opening spring 47 is arranged.

On the other hand, in the upper center of the valve body 20, a convex stopper portion 28 protruding from the lowermost position of the plunger 37 protrudes and is installed, and includes a valve including the convex stopper portion 28. In the center portion of the upper thread, a guide hole 19 into which the valve rod 15 is inserted so as to slide freely is formed. Further, between the plunger 37 and the upper outer circumference (the outer circumference of the convex stopper portion 28) of the valve body 20, a suction pressure refrigerant introduction chamber 23 through which the refrigerant at the suction pressure of the compressor is introduced is formed. 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 a plunger. The decompression chamber 45 through the vertical grooves 37a, 37a, ... formed on the outer circumference of the 37 and the continuous passage hole 37d protruding from the center portion, the continuous passage hole 39 formed in the aspirator 34, and the like. Is introduced.

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 is always pressed against the plunger 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 suction 34 is energized, the plunger 37 will be attracted to the suction 34. As shown in 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 formed in the longitudinal grooves 37a, 37a, ... and suction formed on the outer circumference of the plunger 37 from the introduction chamber 23. The bellows main body 40 (internal vacuum pressure) is introduced into the decompression chamber 45 through the continuous passage hole 39 formed in the 39, and the pressure (suction pressure Ps) of the decompression chamber 45. 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 plunger 37, thereby opening the valve. (The lift amount of the valve body part 15a from the valve seat part 22a of the valve port 22) is adjusted.

That is, the valve opening degree is the suction force of the plunger 37 by the solenoid part which consists of the coil 32, the stator 33, and the suction 34, the pressing force of the bellows main body 40, and the valve opening spring ( 47) and the pressing force by 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 are discharged 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 pressurized refrigerant introduction port 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 the variable displacement compressor according to the prior art has a problem to be improved as follows.

That is, in the control valve 5, the discharge pressure refrigerant inlet 21 is provided upstream of the valve port 22, and the refrigerant outlet 26 is provided downstream of the valve port 22, and the valve main body is provided. The portion 15a is provided at the lower end of the shaft portion 15c of the valve rod 15 to open and close the valve opening 22 from the lower side thereof, and the discharge pressure Pd acts on the valve rod 15. have.

In this case, in order to facilitate valve assembly, as shown schematically in Figs. 2A and 2B, the valve port 22 moves the shaft portion 15c of the valve rod 15 to its lower portion. The aperture Da is made slightly larger than the outer diameter Db of the shaft portion 15c so as to pass through from the lower side, and also to open and close the valve opening 22 from the lower side in the valve body portion 15a. The outer diameter Dc of the valve main body 15a is the diameter Da of the valve port 22 (so that the valve main body 15a is in contact with and separated from the valve seat 22a provided at the lower end of the valve port 22). It becomes larger (Db <Da <Dc).

In this case, the valve closing direction load (pushing force) A by the discharge pressure Pd acting on the valve rod 15 depends on the hydraulic pressure area (outer diameter Db) of the shaft portion 15c. The opening direction load (pushing force) B is applied to the load Ba along the diameter Da of the valve port 22 (valve seat portion 22a) to the outer diameter Dc (Dc-Da) of the valve body portion 15a. The load Bb according to this is added magnitude.

Here, since Da and Db may be assumed to be approximately equal, the valve opening direction load (pushing force) due to the discharge pressure Pd to the valve rod 15 is greater than the valve closing direction load (pushing force). Bb is large. Therefore, if the current value I supplied to the coil 32 of the electronic actuator 30 is made constant, the discharge pressure Pd is increased by the (Pd)-(Ps) characteristics shown in FIG. Pc) Furthermore, the suction pressure Ps (on the use of the compressor, the outlet pressure Pc and the suction pressure Ps are approximately equal) also tends to be high (upper right), which adversely affects the control (control There is a problem).

[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 configured to maintain a constant value of the suction pressure (Ps) even if the discharge pressure (Pd) is increased capacity variable deformation improved control accuracy To provide a capacity control valve and an assembly method of the compressor.

Another object of the present invention is to provide a capacity control valve and a method for assembling a variable displacement compressor that adjusts the discharge capacity by using a balance between the pressure difference between the discharge chamber and the suction chamber, and the force of the bellows and the solenoid.

In addition, another object of the present invention is to provide a variable displacement compressor that maintains the gap between the suction pressure Ps and the discharge pressure Pd passage and the sleeve by firmly fixing the coupling between the valve body and the sleeve by screwing and sliding tolerances. To provide a capacity control valve and an assembly method.

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 connecting hole and the discharge chamber connecting hole which receives the crank chamber pressure and the discharge chamber pressure of the compressor, respectively And a valve housing formed therein, through which the first guide hole crossing the discharge chamber connecting hole and the crank chamber connecting hole penetrates, and to the large diameter part and the small diameter part to open and close the opening of the first guide hole while reciprocating. A valve body configured to be provided, an electromagnetic solenoid for reciprocating the valve body by energization, a sleeve provided at a small diameter portion of the valve body and having a diameter larger than that of the small diameter portion, and a bellows formed at an end of the sleeve. Characterized in that it comprises a.

In addition, it is preferable to include a coupling means for fixing the small diameter portion and the sleeve.

The coupling means may include a male screw formed at an end of the small diameter portion, an insertion hole formed in the sleeve to be inserted into an outer circumferential surface of the small diameter portion, and a fixing member having a pressure screw coupled to the male screw. .

On the other hand, the end of the small diameter portion penetrating the fixing member is formed with a corresponding coupling hole corresponding to the coupling hole, the coupling hole and the coupling sphere is preferably pressed or sliding coupled to each other.

In addition, the fixing member is formed with a coupler corresponding to the coupling hole, it is preferable that the coupling hole and the coupler is pressed or slidingly coupled to each other.

And, it is preferable that a washer is installed between the sleeve and the fixing member.

On the other hand, the coupling means, the male screw formed on one side of the small diameter portion, the insertion port is formed to extend to the male screw on the other side of the small diameter portion, the female screw formed on the sleeve to correspond to the male screw and the insertion port corresponding to It is preferable that the insertion hole is formed in the sleeve as much as possible.

In addition, the coupling hole corresponding to the coupling hole is formed in the sleeve, it is preferable that the coupling hole and the coupling hole is pressed or slidingly coupled to each other.

The electromagnetic solenoid is provided with a core, and the core preferably has a stopper facing the end of the valve body.

On the other hand, the cap is preferably provided with a cap coupled to the valve housing to surround the bellows.

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

The sleeve is preferably formed integrally with the valve body.

On the other hand, the sleeve is preferably formed of a separate part from the valve body.

In addition, it is preferable that the sleeve and the valve body are press-fitted to each other.

The cross-sectional area with respect to the diameter of the sleeve is preferably greater than or equal to the sum of the cross-sectional area with respect to the diameter of the first guide hole and the cross-sectional area with respect to the diameter of the large diameter portion divided by two.

In addition, the coupling hole corresponding to the coupling hole is formed in the sleeve, it is preferable that the coupling hole and the coupling hole is pressed or slidingly coupled to each other.

In the method of assembling the capacity control valve of the variable displacement compressor of the present invention, in the above-described capacity control valve of the variable displacement compressor, the solenoid in which the valve body is inserted is combined with the valve housing, and the valve is exposed to one side of the valve housing. Coupling the sleeve to the small diameter portion of the sieve, coupling the bellows to the sleeve, and fixing the valve housing and the cap to cover the bellows.

According to the capacity control valve and the assembly method of the variable displacement compressor according to the present invention, since the opening amount of the valve body is limited by the sleeve, even if the discharge pressure (Pd) is increased, the suction pressure (Ps) maintains a constant value to improve the control precision It is effective.

In addition, there is an effect of adjusting the discharge capacity by using the equilibrium relationship between the differential pressure of the discharge chamber and the suction chamber, the force of the bellows and 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, it is firmly fixed by the coupling means of the valve body and the sleeve provides an effect of maintaining a constant distance between the sleeve bore and the sleeve through which the suction pressure Ps and the discharge pressure Pd flow.

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

4 is a longitudinal sectional view showing the structure of a variable displacement compressor according to the present invention, Figure 5 is a longitudinal sectional view showing the structure of a capacity control valve according to a first embodiment of the present invention, Figure 6 is a capacity control valve of Figure 5 In FIG. 7 is a longitudinal sectional view showing a balance of force between components, FIG. 7 is a vertical sectional view showing a structure of a capacity control valve according to a second embodiment of the present invention, and FIG. It is a longitudinal cross-sectional view which shows the structure of the capacity control valve which concerns.

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 having linearly perforated guide holes 64 are formed to protrude integrally on one surface, and on one surface of the swash plate 50. A ball 66 is formed so that the ball 66 of the swash plate 50 slides in the guide hole 64 of the lug plate 54 as the lug plate 54 rotates. The inclination angle of the 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 ) To adjust the discharge capacity.

First embodiment

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

5 to 6, the capacity control valve 100 according to the first embodiment of the present invention, the valve housing 110, the electromagnetic solenoid 130, the valve housing 110 is formed with a plurality of connection holes It includes a valve body 120 that is installed to be movable in the interior.

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.

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.

Although not shown, it is preferable that the suction pressure Ps of the compressor C and 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 the end of the small diameter portion 123 of the valve body 120, and a sleeve bore 119 is formed in the valve housing 110 in which the sleeve 140 is installed.

In addition, the portion where the sleeve 140 of the small diameter portion 123 is coupled is formed to have an outer diameter smaller than the portion that is not coupled with the sleeve 140 of the small diameter portion 123, and this portion is described as a step 124. In addition, the step 124 limits the movement of the sleeve 140.

Here, the coupling means 180 for fixing the small diameter portion 123 and the sleeve 140 of the valve body 120.

The coupling means 180, the male screw 181 formed at the end of the small diameter portion 123, the insertion hole 182 formed in the sleeve 140 to be inserted into the outer peripheral surface of the small diameter portion 123, It is composed of a fixing member 183 formed with a female screw 183a coupled to the male screw 181.

In addition, the outer circumferential surface of the small diameter portion 123 and the insertion hole 182 are preferably formed to have a sliding tolerance, and the small diameter portion 123 and the sleeve 140 of the valve body 120 are fixed members 183. It is firmly fixed by).

On the other hand, the end of the sleeve 140 is provided with a bellows 160, the coupling hole 161 is formed.

In addition, a coupling hole 184 corresponding to the coupling hole 161 is formed at an end portion of the small diameter portion 123 penetrating the fixing member 183, and the coupling hole 161 and the coupling hole 184 are formed. Are press-fitted or slidingly coupled to each other.

A washer 185 is installed between the sleeve 140 and the fixing member 183 to prevent loosening and prevent gaps therebetween.

On the other hand, the cross-sectional area (Ac) with respect to the diameter of the sleeve 140 is the sum of the cross-sectional area (Ad) for the diameter of the first guide hole 117 and the cross-sectional area (Aa) for the diameter of the large diameter portion (122). It is preferably configured to be greater than or equal to a value divided by two, which will be described later.

In addition, the solenoid 130 is a movable iron core 131 connected to the valve body 120, an electromagnetic coil 132 disposed around the movable iron core 131, the electromagnetic coil 132, and the like. Wrapping is composed of a solenoid housing 134 and a fixing iron core 133 wrapped around the valve body 120 and disposed inside the electromagnetic coil 132.

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.

In addition, an off-spring 125 is provided 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 there is no external force in a normal valve body ( 120 rises to maintain the inlet of the first guide hole 117 is open.

In addition, the solenoid 130 is provided with a core 135, and at the lower end of the core 135, a protrusion stopper 136 corresponding to an end of the movable iron core 131 is formed to form a valve body 120. Limit the maximum amount of opening.

A bellows accommodating portion 170 is formed at an end of the valve housing 110 opposite to the solenoid 130 of the valve housing 110. The bellows receiving portion 170 protrudes a portion of the front end of the coupling bore 184 past the insertion hole 182 formed in the sleeve bore 119 of the valve housing 110 and the sleeve 140, and the bellows ( 160 is installed.

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 addition, a spring 162 may be built in the bellows 160 to maintain an expanded state.

In addition, the support spring 163 is connected between the bellows 160 and the valve housing 110, so that the bottom of the bellows 160 is always supported outward. As a result, the expansion force of the bellows 160 and the expansion force of the spring 162 installed therein are regulated.

On the other hand, 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 portion 170 may communicate with each other through a separate inlet (not shown) formed in the compressor housing.

In addition, a cap 165 is further provided to surround the bellows 160, and the cap 165 is screwed with the valve housing 110 to rotate the bellows 160 by the rotation of the cap 165. The initial set value of the spring 162 can be adjusted.

 On the other hand, the cap 165 is formed so that a part is open so that the pressure (Ps) of the suction chamber 22 acts, the opening of the cap 165 is provided with a filter (not shown) to the control valve It is desirable to play a role to block the introduction of foreign matter.

In addition, although not shown, the lower end of the solenoid housing 134 in which the movable iron core 131 is installed is preferably configured to communicate the pressure Pc of the crank chamber 86.

Accordingly, the pressure Pc of the crank chamber 86 also acts on the solenoid housing 134. With this structure, the pressure Pc of the crank chamber 86 can be applied to the end portion of the large diameter portion 122 of the valve body 120.

Furthermore, the suction solenoid gas having the pressure Pc of the crank chamber 86 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 electromagnetic force proportional to the current without being affected by the generated heat.

Hereinafter, the operation of the capacity control valve according to the first embodiment of the present invention with reference to the drawings.

In the operation description, the initial state is a state in which power supply to the capacity control valve 100 is cut off, and the valve body 120 is lowered by the off-spring 125 so that the jaw portion 121 of the valve body 120 is discharged. It is assumed that it is separated from the inlet of the first guide hole 117 connecting between the thread connection hole 113 and the crank chamber connection 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 so that the movable core 131 and the valve body 120 may discharge the resistance of the off-spring 125 and the discharge pressure Pd of the discharge chamber connecting hole 113. By winning and moving upward, the discharge chamber connecting hole 113 is closed.

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.

On the other hand, the displacement control valve 100 of the present invention described above is formed so that the discharge pressure (Pd) acts on the jaw portion 121 of the valve body 120.

For example, the cross-sectional area Ab for the diameter of the small-diameter portion 123 is a cross-sectional area for the diameter of the first guide hole 117 to facilitate the valve assembly and the discharge pressure Pd to move to the crank chamber 86 ( It is formed smaller than Ad), the cross-sectional area (Aa) with respect to the diameter of the large diameter portion 122 is formed larger than the cross-sectional area (Ad) of the first guide hole 117 to open and close the first guide hole (117). (Ab <Ad <Aa).

Here, the valve body 120 may be assumed to have an equilibrium of force (valve closing direction = valve opening direction). Therefore, the valve body 120 is caused by the discharge pressure Pd acting on the large diameter part 122. ) Moves in the open direction.

Therefore, if the current value supplied to the electromagnetic solenoid 130 is made constant, as the discharge pressure Pd increases, the crank chamber outlet pressure Pc and the suction pressure Ps (in use of the compressor, the crank chamber 86). Pressure (Pc) and suction pressure (Ps) are approximately equal), and the sleeve 140 of the present invention has been proposed to improve this.

Specifically, the cross-sectional area Ac of the sleeve 140 is greater than or equal to the sum of the cross-sectional area Ad of the first guide hole 117 and the cross-sectional area Aa of the large diameter part 122 divided by two. The discharge pressure Pd applied to the large diameter portion 122 and the jaw portion 121 acts the same on the sleeve 140 so that the valve body 120 is stopped without moving due to the force balance. do.

As a result, since the valve body 120 is not opened by the discharge pressure Pd, the suction pressure Ps is maintained at a constant value so that the control precision of the capacity control valve 100 according to the present invention is improved.

As shown in Fig. 6, in the displacement control valve according to the first embodiment of the present invention described above, the force equilibrium relationship between the components is as follows.

ΣF = Pc * Aa - Pd * ( Ad - Ab ) - ( Pc + Pd ) * ( Aa - Ad ) / 2 + Pd *

        ① ② ③

( Ac - Ab ) -Ps * Ac + F_ bellows - Fs _1 + Fs _2 - Fs _3 + F_ solenoid

    ④ ⑤ ⑥ ⑦ ⑧ ⑨ ⑩

That is, ΣF = ½Pc * (Aa + Ad) + ½Pd * (2Ac-Ad-Aa)-Ps * Ac + (⑥, ⑦, ⑧, ⑨, ⑩)

Here, Aa: (π / 4) * a ² , that is, the cross-sectional area for the diameter a, so Ab, Ac, Ad are the cross-sections for the respective diameters b, c, d, and Fs: Spring Force of ⑦, ⑧, ⑨ , ⑥'s F_bellows: Bellows Force (function of Ps), ⑩'s F_solenoid: meaning electromagnetic force.

As a result, in order to avoid a phenomenon in which the suction pressure Ps increases as the discharge pressure Pd increases, the force should not be applied in the direction in which the valve body 120 opens when the discharge pressure Pd increases.

As described above, since (2Ac-Ad-Aa) ≥ 0, that is, Ac ≥ (Ad + Aa) / 2 is satisfied, the discharge pressure Pd does not act in the opening direction (-direction of F) of the valve body 120. Since the discharge pressure Pd is increased, the suction pressure Ps is maintained at a constant value so that control can be easily performed.

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.

Hereinafter, in describing another embodiment of the capacity control valve according to the present invention, the same reference numerals are used for the same components and functions as those of the capacity control valve of the first embodiment of the present invention. Only describe the differences.

Second embodiment

As shown in FIG. 7, the capacity control valve 100 according to the second embodiment of the present invention includes a valve housing 110 in which some connection holes are formed, an electronic solenoid 130, and an interior of the valve housing 110. The valve body 120 is installed to be movable in the.

In addition, a sleeve 140 is provided at the end of the small diameter portion 123 of the valve body 120, and a sleeve bore 119 is formed in the valve housing 110 in which the sleeve 140 is installed. .

Here, the coupling means 180 'for fixing the small diameter portion 123 and the sleeve 140 of the valve body 120 is included.

The coupling means 180 'may include a male screw 181' formed at an end of the small diameter portion 123 and an insertion hole 182 formed in the sleeve 140 to be inserted into an outer circumferential surface of the small diameter portion 123 '. And a fixing member 183 'having a female screw 183a' coupled to the male screw 181 '.

The outer circumferential surface of the small diameter portion 123 and the insertion hole 182 ′ are preferably formed to have a sliding tolerance, and the small diameter portion 123 and the sleeve 140 of the valve body 120 may be fixed members ( 183 ').

On the other hand, the end of the sleeve 140 is provided with a bellows 160, the coupling hole 161 is formed.

In addition, the coupling member 184 'corresponding to the coupling hole 161 is formed in the fixing member 183', and the coupling hole 161 and the coupling hole 184 'are press-fitted or slidingly coupled to each other.

As a result, unlike the coupling of the sleeve 140 and the bellows 160 of the first embodiment, the displacement control valve 100 according to the second embodiment is coupled to each other by the fixing member 183 ′ and the bellows 160.

A washer 185 'is installed between the sleeve 140 and the fixing member 183' to prevent loosening and prevent gaps therebetween.

Third embodiment

As shown in FIG. 8, the capacity control valve 100 according to the third embodiment of the present invention includes a valve housing 110, an electronic solenoid 130, and an interior of the valve housing 110 in which a plurality of connection holes are formed. The valve body 120 is installed to be movable in the.

In addition, a sleeve 140 is provided at the end of the small diameter portion 123 of the valve body 120, and a sleeve bore 119 is formed in the valve housing 110 in which the sleeve 140 is installed.

Here, the coupling means 180 "for fixing the small diameter portion 123 and the sleeve 140 of the valve body 120 is included.

The coupling means 180 " includes a male screw 181 " formed at one side of the small diameter portion 123 and an insertion hole 182 extending at the other side of the small diameter portion 123 and the male screw 181 ". &Quot;) and an insertion hole 184 " formed in the sleeve 140 to correspond to the female thread 183 " and the insertion hole 182 ", which are formed in the sleeve 140 so as to correspond to the male screw 181 ". It consists of.

As a result, the male screw 181 ″ and the female screw 183 ″ are engaged with each other, and the insertion hole 182 ″ and the insertion hole 184 ″ have a sliding tolerance so that the valve body 120 and the sleeve 140 are inserted. It is firmly fixed to each other.

On the other hand, the end of the sleeve 140 is provided with a bellows 160, the coupling hole 161 is formed.

In addition, the sleeve 140 is formed with a coupling hole 185 ″ corresponding to the coupling hole 161, and the coupling hole 161 and the coupling hole 185 ″ are press-fitted or slidably coupled to each other and the sleeve 140 is formed. ) And the bellows 160 are firmly fixed to each other.

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 sleeve 140 and the valve body 120 may be fixed to each other without the configuration of the restricting means 180 ″ of the third embodiment.

For example, the sleeve 140 may be formed integrally with the small diameter portion 123 of the valve body 120 or may be formed as separate components.

In this case, when the sleeve 140 and the small diameter portion 123 are formed as separate components, the sleeve 140 and the small diameter portion 123 may be press-fitted to each other so as not to move relative to each other, thereby implementing the same operation as the capacity control valve of the third embodiment.

On the other hand, the sleeve 140 is preferably formed with a coupler 185 "corresponding to the coupling hole 161 of the bellows 160.

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

2 is an enlarged longitudinal sectional view (a) and an operation explanatory view (b) of an essential part of a capacity control valve according to the prior art.

3 is a graph showing Pd-Ps characteristics of the displacement control valve of FIG.

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

5 is a longitudinal sectional view showing a structure of a capacity control valve according to a first embodiment of the present invention.

FIG. 6 is a vertical cross-sectional view illustrating a balance of forces between components in the displacement control valve of FIG. 5.

7 is a longitudinal sectional view showing a structure of a capacity control valve according to a second embodiment of the present invention.

8 is a longitudinal sectional view showing a structure of a capacity control valve according to a third embodiment of the present invention.

* Description of symbols on main parts of the drawings *

100 ... Capacity control valve

110 ... valve housing

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

140 ... sleeve

160 ... bellows

170 ... bellows receptacle

180 ... Joining means

C ... variable displacement compressor

Claims (17)

In the displacement control valve of the variable displacement compressor, A valve housing formed with a crank chamber connecting hole and a discharge chamber connecting hole respectively receiving a crank chamber pressure and a discharge chamber pressure of the compressor, and a first guide hole passing through the discharge chamber connecting hole and the crank chamber connecting hole respectively; A valve body composed of a large diameter portion and a small diameter portion at the boundary of the jaw portion to open and close the first guide hole entrance while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; A sleeve provided in the small diameter portion of the valve body and having a larger diameter than the small diameter portion; And It includes bellows is provided at the end of the sleeve and the coupling hole is formed, A capacity control valve of a variable displacement compressor comprising a coupling means for fixing the small diameter portion and the sleeve. In the displacement control valve of the variable displacement compressor, A valve housing formed with a crank chamber connecting hole and a discharge chamber connecting hole respectively receiving a crank chamber pressure and a discharge chamber pressure of the compressor, and a first guide hole passing through the discharge chamber connecting hole and the crank chamber connecting hole respectively; A valve body composed of a large diameter portion and a small diameter portion at the boundary of the jaw portion to open and close the first guide hole entrance while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; A sleeve provided in the small diameter portion of the valve body and having a larger diameter than the small diameter portion; And It includes bellows is provided at the end of the sleeve and the coupling hole is formed, The cross-sectional area with respect to the diameter of the sleeve, The sum of the cross-sectional area of the diameter of the first guide hole and the cross-sectional area of the diameter of the large diameter portion is greater than or equal to the value divided by two, the capacity control valve of the variable displacement compressor. 3. The method of claim 2, A capacity control valve of a variable displacement compressor comprising a coupling means for fixing the small diameter portion and the sleeve. The method according to claim 1 or 3, The coupling means, A male screw formed at an end of the small diameter portion; An insertion hole formed in the sleeve to be inserted into an outer circumferential surface of the small diameter portion; Capacity control valve of a variable displacement compressor characterized in that it consists of a fixed member formed with a pressure screw coupled to the male screw. The method of claim 4, wherein A coupling hole corresponding to the coupling hole is formed at an end portion of the small diameter portion penetrating the fixing member, and the coupling hole and the coupling hole are press-fitted or slidably coupled to each other. The method of claim 4, wherein The fixing member is provided with a coupling sphere corresponding to the coupling hole, the coupling hole and the coupling sphere is a capacity control valve of a variable displacement compressor, characterized in that the press-fit or sliding coupling with each other. The method of claim 4, wherein A capacity control valve of a variable displacement compressor, characterized in that a washer is installed between the sleeve and the fixing member. The method according to claim 1 or 3, The coupling means, A male screw formed on one side of the small diameter portion; An insertion hole formed to extend with the male screw to the other side of the small diameter portion; A female thread formed in the sleeve to correspond to the male thread and A capacity control valve of a variable displacement compressor, characterized in that consisting of an insertion hole formed in the sleeve so as to correspond to the insertion port. The method of claim 8, A coupling hole corresponding to the coupling hole is formed in the sleeve, and the coupling hole and the coupling hole are press-fitted or slidingly coupled to each other. The method according to claim 1 or 2, The electromagnetic solenoid is provided with a core, the core is a capacity control valve of the variable displacement compressor, characterized in that the stopper facing the end of the valve body protrudes. The method according to claim 1 or 2, Capacitance control valve of the variable displacement compressor, characterized in that the cap is coupled to the valve housing so as to surround the bellows. The method of claim 11, A capacity control valve of a variable displacement compressor, characterized in that a support spring is provided between the bellows and the valve housing. The method according to claim 1 or 2, The sleeve is a capacity control valve of a variable displacement compressor, characterized in that formed integrally with the valve body. The method according to claim 1 or 2, The sleeve is a capacity control valve of a variable displacement compressor, characterized in that formed by a separate component from the valve body. 15. The method of claim 14, And the sleeve and the valve body are press-fit fixed to each other. The method according to claim 1 or 2, A coupling hole corresponding to the coupling hole is formed in the sleeve, and the coupling hole and the coupling hole are press-fitted or slidingly coupled to each other. In the method of assembling the capacity control valve of the variable displacement compressor according to any one of claims 1 to 3, The valve housing and the cap are coupled to the solenoid with the valve body inserted into the valve housing, the sleeve is coupled to the small diameter portion of the valve body exposed to one side of the valve housing, the bellows is coupled to the sleeve, and the valve housing is covered to cover the bellows. A capacity control valve assembly method of a variable displacement compressor characterized in that the fixing.

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