KR101099092B1 - Displacement control valve of variable displacement compressor - Google Patents

Abstract

The capacity control valve of the variable displacement compressor of the present invention is a capacity control valve of a variable displacement compressor, the suction chamber connection hole, the crank chamber connection hole and the discharge chamber connection hole which receives the suction chamber pressure, the crank chamber pressure and the discharge chamber pressure of the compressor. Valve housings each formed to pass through the first guide hole crossing the discharge chamber connecting hole and the crank chamber connecting hole; A valve body composed of a large diameter portion and a small diameter portion to open and close the first guide hole entrance while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; And a sleeve member having a diameter larger than that of the small diameter portion, the sleeve member connecting between the small diameter portion of the valve body and the solenoid of the valve body, wherein the sleeve member includes at least one of the suction chamber connecting hole, the crank chamber connecting hole, and the discharge chamber connecting hole. The connection hole is characterized in that it is formed inclined with respect to the plane perpendicular to the direction of movement of the valve body.

Accordingly, at least one of the connection holes of the suction chamber connecting hole, the crank chamber connecting hole, and the discharge chamber connecting hole is formed to be inclined with respect to a plane perpendicular to the direction of movement of the valve body, thereby reducing the overall length and improving the mounting property. .

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

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 reduces the overall length and improves the mounting.

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

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

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

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

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

A representative example of a capacity control valve of such a variable displacement compressor is disclosed in 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 a refrigerant of refrigerant is provided, and the refrigerant continuously passes through the crank chamber of the compressor at the lower side (downstream side) of the valve port 22. The valve body 20 and the electronic actuator 30 provided with the outlet 26 are provided.

The electromagnetic actuator 30 includes a coil 32 having a connector portion 31 for power transmission, a cylindrical stator 33 disposed on an inner circumferential side of the coil 32, and a stator 33. A pipe having a 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 member 34 is disposed. And a compression coil spring that presses the valve rod 15 downward (valve opening direction) through the plunger 37 between the suction 34 and the recess 37b of the plunger 37. The valve 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.

First, input ports such as the discharge pressure refrigerant inlet 25 and the suction pressure inlet 27 are sequentially formed to be orthogonal to the axial direction so that the order of the input ports viewed from the outside of the control valve 5 is the same. Are arranged.

In such a case, there is a problem in that the overall length of the control valve 5 is long and the mountability to the compressor is inferior.

In particular, when the bellows main body 40 is installed between the electronic actuator 30 and the valve rod 15, the length of the portion where the suction pressure Ps of the control valve acts due to the length of the bellows main body 40. It was hard to reduce.

In addition, the outlet pressure Pc through the refrigerant outlet 26 acted on the end of the valve rod 15, making it difficult to accurately control the control valve 5.

As a result, in the control of the control valve 5, the outlet pressure Pc is added, so that the control variable increases so that the precision of the control cannot be increased.

Further, 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 body portion 15a is provided with a valve rod ( It is provided in the lower end part of the shaft part 15c of 15, and it opens and closes the said valve opening 22 from the lower side, and the discharge pressure Pd acts on the valve rod 15.

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 to open and close the valve port 22 in the valve body portion 15a from the lower side thereof ( The outer diameter Dc of the valve main body 15a is larger than the diameter Da of the valve port 22 so that the valve main body 15a is in contact with the valve seat 22a provided at the lower end of the valve port 22. It becomes large (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, it is an object of the present invention to provide a capacity control valve of a variable displacement compressor to reduce the overall length is improved mounting.

In addition, another object of the present invention is that the discharge chamber pressure (Pd) and the crank chamber pressure (Pc) is configured so that the valve body does not affect the control variable is reduced capacity control valve of the variable displacement compressor that can reduce the control accuracy To provide.

Further, another object of the present invention is to provide a capacity control valve of a variable displacement compressor configured to maintain a constant value even if the discharge pressure Pd is increased, thereby improving control accuracy.

In addition, another object of the present invention is to provide a capacity control valve of a variable displacement compressor that adjusts the discharge capacity by using the balance of pressure of the suction chamber, the bellows and the force of the electromagnetic solenoid.

The capacity control valve of the variable displacement compressor of the present invention for achieving the above object, in the capacity control valve of the variable displacement compressor, the suction chamber connection hole and the crank receiving the suction chamber pressure and the crank chamber pressure and the discharge chamber pressure of the compressor A valve housing in which a seal connecting hole and a discharge chamber connecting hole are formed, respectively, and a first guide hole passing through the discharge chamber connecting hole and the crank chamber connecting hole is passed therethrough; A valve body composed of a large diameter portion and a small diameter portion to open and close the first guide hole entrance while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; And a sleeve member having a diameter larger than that of the small diameter portion, the sleeve member connecting between the small diameter portion of the valve body and the solenoid of the valve body, wherein the sleeve member includes at least one of the suction chamber connecting hole, the crank chamber connecting hole, and the discharge chamber connecting hole. The connection hole is characterized in that it is formed inclined with respect to the plane perpendicular to the direction of movement of the valve body.

In addition, the crank chamber connecting hole is formed to be inclined, the outer side of the crank chamber connecting hole is formed between the suction chamber connecting hole and the discharge chamber connecting hole, the inner side of the intermediate connection is disposed a large diameter across the discharge chamber connecting hole It is preferably formed to communicate with the space.

The discharge chamber connecting hole is preferably formed to be orthogonal to the first guide hole between the large diameter portion and the sleeve.

On the other hand, the valve body is preferably provided with a guide rod.

In addition, the valve housing is provided with a cap coupled in a direction facing the end of the valve body, the guide rod of the valve body is preferably coupled to pass through the cap.

The crankcase pressure is formed to act on the side of the valve body, and the suction chamber pressure is preferably formed at the end of the valve body.

On the other hand, the valve housing is preferably formed in the communication hole communicating with the suction chamber connection hole.

In addition, the valve housing is provided with a cap coupled in a direction facing the end of the valve body, it is preferable that the large diameter portion of the valve body is coupled to pass through the cap.

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.

On the other hand, the valve housing is preferably formed with a sleeve bore corresponding to the sleeve.

In addition, the sleeve member is formed with a receiving portion, the support is bisected in the receiving portion, the bellows is provided to surround the nutrient support, and the bellows includes a first spring installed between the nutrient support desirable.

The bellows is preferably disposed between the valve body and the electromagnetic solenoid.

On the other hand, the electromagnetic solenoid is preferably composed of a movable iron core connected to the sleeve member, an electromagnetic coil disposed around the movable iron core, a rod connected to the bellows and a fixed iron core fixing the rod.

In addition, the movable iron core is preferably formed with a second guide hole for guiding the movement of the rod.

In addition, the sleeve and the valve body is preferably fixed to prevent relative movement.

In the displacement control valve of the variable displacement compressor of the present invention, the suction chamber connection hole, the crank chamber connection hole, and the discharge chamber connection hole which receive the suction chamber pressure, the crank chamber pressure, and the discharge chamber pressure of the compressor are formed, respectively, A valve housing formed so that the first guide hole traversing the crank chamber connecting hole is penetrated; And a valve body for opening and closing the inlet of the first guide hole while reciprocating, wherein the arrangement order of the suction chamber connecting hole, the crank chamber connecting hole, and the discharge chamber connecting hole is viewed from the outside of the valve housing and the inside thereof. When viewed from the is characterized in that arranged differently.

Further, when viewed from the outside of the valve housing, the suction chamber connecting hole, the crank chamber connecting hole, and the discharge chamber connecting hole are arranged in the order, and when viewed from the inside of the valve housing, the suction chamber connecting hole, the discharge chamber connecting hole, and the crank chamber. It is preferably arranged in the order of connecting holes.

The displacement control valve may further include an electromagnetic solenoid for reciprocating the valve body by energization, and a bellows for detecting a pressure in the suction chamber of the compressor and transmitting the pressure to the valve body. It is preferable to be located in the opposite direction to the bellows.

According to the capacity control valve of the variable displacement compressor according to the present invention, at least one of the connection hole of the suction chamber connecting hole, the crank chamber connecting hole and the discharge chamber connecting hole is formed to be inclined with respect to the plane perpendicular to the direction of movement of the valve body. By reducing the length has the effect of improving the mounting.

In addition, since the crank chamber pressure Pc acts on the side of the valve body, the crank chamber pressure Pc does not affect the valve body, so that the control variable is reduced, thereby improving the control accuracy.

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

In addition, there is an effect of adjusting the discharge capacity by using a balance relationship between the pressure of the suction chamber, the bellows and the force of the electromagnetic solenoid.

In addition, the suction pressure Ps acts on both ends of the valve body by the communication hole.

In addition, the sealing is improved by preventing the outflow of the refrigerant by the O-ring.

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

Figure 4 is a longitudinal sectional view showing a 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 in Figure 4, Figure 6 is a cross-sectional view between each component in the capacity control valve of Figure 4 Figure 6 is a longitudinal cross-sectional view showing a balance of force, Figure 6 is a longitudinal cross-sectional view showing a balance of force between the components in the displacement control valve of Figure 5, Figure 7 is a displacement 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, and FIG. 9 is a balance of force between components in the capacity control valve of FIG. It is a longitudinal cross-sectional view which shows.

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

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

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

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

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

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

Accordingly, as the swash plate 50 rotates in an inclined state, the pistons 14 fitted 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.

First embodiment

As shown in FIG. 5, the capacity control valve 100 according to the first 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 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, an intermediate connection space 115 is formed above the first guide hole 117.

In addition, the valve housing 110 is formed with a suction chamber connecting hole 111 in which the suction pressure Ps of the compressor C acts at the lower end of the discharge chamber connecting hole 113.

In addition, the valve body 120 is divided into a large diameter portion 122 and a small diameter portion 123 with the jaw portion 121 as a boundary. The crankcase connecting hole 112 is formed around the jaw portion 121 as the large diameter portion 122 and the suction chamber connecting hole 111 is formed as the small diameter portion 123. The jaw portion 121 is capable of opening and closing the inlet of the first guide hole 117 connecting the discharge chamber connecting hole 113 and the crank chamber connecting hole 112.

Although not shown, the suction pressure Ps of the compressor C may be applied to both ends of the valve body 120.

In addition, at least one connection hole of the suction chamber connection hole 111, the crank chamber connection hole 112, and the discharge chamber connection hole 113 may be inclined with respect to a plane perpendicular to the direction of movement of the valve body 120. . This reduces the overall length of the capacity control valve 100 including the valve housing 110 and the valve housing 110.

More specifically, the discharge chamber connecting hole 113 is formed to be orthogonal to the first guide hole 117 between the large diameter portion 122 and the sleeve 141 to be described later, the crank chamber connecting hole 112 is It is formed to be inclined to cross the discharge chamber connecting hole 113.

In addition, an outer side (outer peripheral surface of the housing) of the crank chamber connecting hole 112 is formed between the suction chamber connecting hole 111 and the discharge chamber connecting hole 113, and an inner side (inner peripheral surface of the housing) is the discharge chamber. It is formed in the direction of the large diameter portion 122 across the connection hole 113 to reduce the length of the valve housing 110 and to reduce the overall length of the capacity control valve 100 to improve the mounting.

As a result, the one or more connecting holes are formed in the valve housing 110 so as to overlap with each other, unlike the sequential arrangement of the conventional connecting holes to reduce the length as long as the connecting holes overlap.

On the other hand, as the inclination angle (θ) of the crank chamber connecting hole 112 increases, the length of the valve housing 110 can be reduced.

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

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

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

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

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

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

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

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

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

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 support portion 172 is bisected in the receiving portion 170, and the bellows is provided to surround the bisected support 172.

In addition, a first support spring 162 is embedded between the divided supports 172 to maintain the expanded state of the bellows 160.

That is, the bellows 160 detects the suction chamber pressure Ps of the compressor and transmits the pressure to the valve body 120.

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 guide iron 131b is formed in the movable iron core 131 so as 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 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.

Hereinafter, the operation of the capacity control valve according to the first embodiment of the present invention will be described with reference to FIGS. 5 to 6.

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 lifted 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, the electric current flows through the solenoid 130 so that the movable core 131, the sleeve member 140, and the valve body 120 discharge the resistance of the off-spring 125 and the discharge chamber connecting hole 113. The discharge chamber connecting hole 113 is closed by lowering the pressure Pd.

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

At this time, the suction pressure Ps is increased due to the external thermal load, that is, the indoor temperature is high, and the suction pressure Ps thus raised acts on the receiving unit 170.

The bellows 160 is reduced by the increased suction pressure Ps, and the valve body 120 fixed to the bellows 160 receives a descending force. In such a relationship, the valve body 120 can easily move downward 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 (Pd) and the force of the off spring 125 are reduced. 120) is ascended.

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 is already sufficient, the suction pressure Ps is naturally reduced, so the bellows 160 expands again to help the valve body 120 to rise.

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, conventionally, 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 ( The pressure Pc and the suction pressure Ps of 86) tended to be high.

On the other hand, according to the present invention, a value obtained by dividing the cross-sectional area Ac of the sleeve 141 by 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. When formed to be greater than or equal to, 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 does not move due to the balance of force. Keep stopped.

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.

Hereinafter, in describing another embodiment of the displacement control valve according to the present invention, the same reference numerals are used for components having the same configuration and function as the first embodiment of the present invention, and detailed descriptions thereof are omitted and only differences are described. do.

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.

First, the valve body 120 is provided with a guide rod 124 in the cap 165 direction for stable movement.

In addition, the cap 165 is formed so as to penetrate the center is coupled so that the guide 124 of the valve 120 passes through the cap 165.

Accordingly, the longitudinal movement of the valve body 120 may be supported by the guide 124 penetrating the cap 165 to perform a stable operation.

Third embodiment

8 to 9, the capacity control valve 100 according to the second embodiment of the present invention includes a valve housing 110, an electronic solenoid 130, and the valve housing 110 in which a plurality of connection holes are formed. It includes a valve body 120 that is installed to be movable in the interior.

In the figure, the crankcase connecting hole 112 is formed to act on the side of the valve body 120 so that the crankcase pressure Pc does not affect the valve body 120, the capacity control valve 100 of the present invention Reduced control variables can improve the precision of the control, which will be described later.

In addition, the valve housing 110 has a communication hole 114 in communication with the suction chamber connecting hole 111 is formed, the communication hole 114, the suction pressure (Ps) is applied to the upper end of the valve body (120). It is formed to.

Meanwhile, a suction port (not shown) communicating with the suction chamber 22 may be separately formed in the compressor C so that the suction pressure Ps acts on the upper end of the valve body 120. It is also possible to have the same effect as).

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 is formed so that the center penetrates the valve 120 Large diameter portion of 122 is coupled to pass through the cap 165.

On the other hand, the cap 165 is formed so that a part is open so that the suction pressure (Ps) acts on the valve body 120.

With the above-described configuration, since the crankcase pressure Pc acts on the side surface of the valve body 120, the force acting on one end of the valve body 120 is only the suction pressure Ps.

Thereby, the item which the crankcase pressure Pc enters as a variable in control of the control valve 100 reduces some.

In other words, there is no influence of the crankcase pressure Pc in the control of the control valve 100, which means that the control variable is reduced by that, and the accuracy of the control can be improved.

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.

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 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.

FIG. 9 is a longitudinal cross-sectional view illustrating a balance of forces between components in the displacement control valve of FIG. 8.

* Description of symbols on main parts of the drawings *

100 ... Capacity control valve

110 ... valve housing

111 ... Suction Room Connector

112. Crankcase connector

113.Discharge chamber connection

117 ... The first guide

119 ... Sleeve Bore

120 ... valve body

121 ... Chin

122 ... Dae Kyung

123 ... small neck

130 ... electronic solenoid

131. Iron core

132 ... electromagnetic coil

134 ... solenoid housing

137 ... The Second Guide

140 ... sleeve

160 ... bellows

170 ... bellows receptacle

C ... variable displacement compressor

Claims (18)

In the displacement control valve of the variable displacement compressor, A suction chamber connecting hole, a crank chamber connecting hole, and a discharge chamber connecting hole are formed, respectively, which receive the suction chamber pressure, the crank chamber pressure, and the discharge chamber pressure of the compressor. A valve housing so formed; A valve body composed of a large diameter portion and a small diameter portion to open and close the first guide hole entrance while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; And A sleeve member having a diameter larger than that of the small diameter portion is formed and connects the small diameter portion of the valve body to the solenoid of the valve body. At least one connection hole of the suction chamber connection hole, the crank chamber connection hole, and the discharge chamber connection hole is formed to be inclined with respect to a plane perpendicular to the direction of movement of the valve body. The crank chamber connecting hole is formed to be inclined, and the outer side of the crank chamber connecting hole is formed between the suction chamber connecting hole and the discharge chamber connecting hole, and the inner side of the crank chamber connecting hole is disposed in the intermediate connecting space where the large diameter part is disposed across the discharge chamber connecting hole. A capacity control valve of a variable displacement compressor, characterized in that it is formed to communicate. In the displacement control valve of the variable displacement compressor, A suction chamber connecting hole, a crank chamber connecting hole, and a discharge chamber connecting hole are formed, respectively, which receive the suction chamber pressure, the crank chamber pressure, and the discharge chamber pressure of the compressor. A valve housing so formed; A valve body composed of a large diameter portion and a small diameter portion to open and close the first guide hole entrance while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; And A sleeve member having a diameter larger than that of the small diameter portion is formed and connects the small diameter portion of the valve body to the solenoid of the valve body. At least one connection hole of the suction chamber connection hole, the crank chamber connection hole, and the discharge chamber connection hole is formed to be inclined with respect to a plane perpendicular to the direction of movement of the valve body. 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. In the displacement control valve of the variable displacement compressor, A suction chamber connecting hole, a crank chamber connecting hole, and a discharge chamber connecting hole are formed, respectively, which receive the suction chamber pressure, the crank chamber pressure, and the discharge chamber pressure of the compressor. A valve housing so formed; A valve body composed of a large diameter portion and a small diameter portion to open and close the first guide hole entrance while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; And A sleeve member having a diameter larger than that of the small diameter portion is formed and connects the small diameter portion of the valve body to the solenoid of the valve body. At least one connection hole of the suction chamber connection hole, the crank chamber connection hole, and the discharge chamber connection hole is formed to be inclined with respect to a plane perpendicular to the direction of movement of the valve body. The valve housing is a capacity control valve of a variable displacement compressor, characterized in that the sleeve bore corresponding to the sleeve is formed. In the displacement control valve of the variable displacement compressor, A suction chamber connecting hole, a crank chamber connecting hole, and a discharge chamber connecting hole are formed, respectively, which receive the suction chamber pressure, the crank chamber pressure, and the discharge chamber pressure of the compressor. A valve housing so formed; A valve body composed of a large diameter portion and a small diameter portion to open and close the first guide hole entrance while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; And A sleeve member having a diameter larger than that of the small diameter portion is formed and connects the small diameter portion of the valve body to the solenoid of the valve body. At least one connection hole of the suction chamber connection hole, the crank chamber connection hole, and the discharge chamber connection hole is formed to be inclined with respect to a plane perpendicular to the direction of movement of the valve body. And the sleeve and the valve body are fixedly coupled to prevent relative movement. In the displacement control valve of the variable displacement compressor, A suction chamber connecting hole, a crank chamber connecting hole, and a discharge chamber connecting hole are formed, respectively, which receive the suction chamber pressure, the crank chamber pressure, and the discharge chamber pressure of the compressor. A valve housing so formed; A valve body composed of a large diameter portion and a small diameter portion to open and close the first guide hole entrance while reciprocating; An electromagnetic solenoid for reciprocating the valve body by energization; And A sleeve member having a diameter larger than that of the small diameter portion is formed and connects the small diameter portion of the valve body to the solenoid of the valve body. At least one connection hole of the suction chamber connection hole, the crank chamber connection hole, and the discharge chamber connection hole is formed to be inclined with respect to a plane perpendicular to the direction of movement of the valve body. The sleeve member is provided with a receiving portion, the support is bisected in the receiving portion, a bellows is provided to surround the bisected support, the bellows includes a first spring installed between the bisected support, The electromagnetic solenoid includes a movable iron core connected to the sleeve member, an electromagnetic coil disposed around the movable iron core, a rod connected to the bellows, and a fixed iron core fixing the rod. Capacity control valve of the compressor. 5. The method according to any one of claims 1 to 4, The discharge chamber connection hole is a capacity control valve of a variable displacement compressor, characterized in that formed to be orthogonal to the first guide hole between the large diameter portion and the sleeve. The method of claim 6, Capacity control valve of the variable displacement compressor, characterized in that the valve body is provided with a guide rod. The method of claim 7, wherein The valve housing is provided with a cap coupled in a direction facing the end of the valve body, the guide rod of the valve body capacity control valve of the variable displacement compressor, characterized in that coupled to pass through the cap. The method of claim 8, The crankcase pressure is formed to act on the side of the valve body, the capacity control valve of the variable displacement compressor, characterized in that the inlet chamber pressure is formed to act on the end of the valve body. The method of claim 8, The valve housing is a capacity control valve of a variable displacement compressor, characterized in that the communication hole is formed in communication with the suction chamber connecting hole. The method of claim 6, The valve housing is provided with a cap coupled in a direction facing the end of the valve body, the large-capacity control valve of the variable displacement compressor, characterized in that coupled to pass through the cap. The method of claim 5, The bellows is a displacement control valve of a variable displacement compressor, characterized in that disposed between the valve body and the solenoid. delete The method of claim 5, The capacity control valve of the variable displacement compressor, characterized in that the movable guide core is formed with a second guide hole for guiding the movement of the rod. delete In the displacement control valve of the variable displacement compressor, A suction chamber connection hole, a crank chamber connection hole, and a discharge chamber connection hole are formed, respectively, which receive the suction chamber pressure, the crank chamber pressure, and the discharge chamber pressure of the compressor. A valve housing so formed; Including; valve body for opening and closing the inlet of the first guide hole while reciprocating, And the arrangement order of the suction chamber connecting hole, the crank chamber connecting hole, and the discharge chamber connecting hole is arranged differently when viewed from the outside of the valve housing and when viewed from the inside. The method of claim 16, When viewed from the outside of the valve housing is arranged in the order of the suction chamber connecting hole, the crank chamber connecting hole, the discharge chamber connecting hole, When viewed from the inside of the valve housing capacity control valve of a variable displacement compressor, characterized in that arranged in the order of the suction chamber connection hole, the discharge chamber connection hole, the crank chamber connection hole. The method according to claim 16 or 17, The capacity control valve, An electromagnetic solenoid for reciprocating the valve body by energization; It further comprises a bellows for detecting the pressure of the suction chamber of the compressor to deliver to the valve body, And the valve body and the solenoid are located in opposite directions with respect to the bellows.

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