KR101988572B1

KR101988572B1 - Exhaust control valve for variable displacement compressor

Info

Publication number: KR101988572B1
Application number: KR1020170155052A
Authority: KR
Inventors: 박장식; 강동수; 홍태호; 황성환; 국무성; 박지영; 김준태
Original assignee: 동일기계공업 주식회사
Priority date: 2017-11-20
Filing date: 2017-11-20
Publication date: 2019-06-12
Also published as: WO2019098804A1; KR20190057742A

Abstract

More particularly, the present invention relates to a control valve for a variable capacity compressor, in which a two-stage coil for accommodating and driving a part of a plunger in a control valve for a variable displacement compressor is applied to increase concentricity between parts and increase driving force, The present invention relates to an apparatus for smoothly performing operation by adding a sleeve to a crank chamber, a crank chamber, a discharge chamber, and a suction chamber. The crank chamber is connected to a variable capacity compressor having a swash plate, A control valve for controlling an inclination angle of the swash plate; A hollow body portion 100 in which a first port 101, a second port 102, and a third port 103 communicating with the crank chamber, the discharge chamber, and the suction chamber are formed; And a main valve (210) positioned to be movable along the longitudinal direction in the body part (100) and capable of adjusting the opening degree of a flow path formed between the first port (101) and the second port (102) (200); A pressure sensitive part 300 including a pressure sensitive member 310 which is expandable and contractible according to a pressure change of the third port 103 to correct the position of the valve part 200; Stage coil 410 formed of a stepped large-diameter portion 411 and a small-diameter portion 412 having different inner diameters and forming a magnetic force corresponding to the amount of supplied current, and a two-stage coil 410 having one end connected to the valve portion 200 And a plunger (420) inserted into the large diameter portion (411) of the two-stage coil (410) and movable forward and backward; And a sleeve (500) of non-magnetic material interposed to reduce frictional resistance by reducing the influence of the magnetic force by maintaining a state where the inner circumferential surface of the body part (100) and the outer circumferential surface of the plunger (420) , It is possible to prevent interference that may occur due to the centering of the valve, to perform valve control with high accuracy, and to maximize the market competitiveness while increasing the reliability and merchantability of the product.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a control valve for a variable-

[0001] The present invention relates to a control valve for a variable capacity compressor, and particularly to a control valve for a variable capacity compressor, in which a two-stage coil for accommodating and driving a part of a plunger is applied to increase concentricity between parts and increase driving force, So as to prevent the interference which may occur due to the turning of the center and to perform the valve control with high accuracy and to maximize the market competitiveness while increasing the reliability and merchability of the product It's about what you can do.

Generally, since a compressor for a refrigerant applied to a vehicle air conditioner is driven by receiving the rotational force of the engine, the driving of the compressor depends on the rotational speed of the engine, that is, the rotational speed per minute, The rotation speed is greatly influenced.

As a result, since the cooling performance of the vehicle is determined by the number of revolutions per minute of the engine, the cooling control is not free, and the variable capacity compressor which performs the proper cooling by varying the discharge capacity of the refrigerant irrespective of the revolution speed per minute of the engine is widely It has been applied.

In a general variable capacity compressor, a swash plate is provided on a crankshaft that is rotated by receiving the rotational force of the engine, and the variable displacement compressor varies the discharge capacity of the refrigerant by appropriately adjusting the inclination angle of the swash plate.

In order to control the inclination angle of the swash plate, a control valve is provided in the variable displacement compressor. One of the conventional control valves for the variable displacement compressor is disclosed in Korean Patent Registration No. 10-933830.

However, such conventional control valves for variable capacity compressors have some technical problems as follows.

First, since the valve body for controlling the opening and closing of the valve is provided on the opposite side of the plunger, while the plunger driven by the coil is located in the coil, the length from the plunger to the valve body is long, It is difficult to accurately maintain the concentricity and coaxiality, and vibration and noise are frequently generated as well as interference and malfunction between components.

Secondly, since the plunger is located inside the coil, it is necessary to design the outer diameter of the plunger to be smaller than the inner diameter of the coil, so that it is difficult to obtain a high driving force at a desired level.

Third, the friction between the moving plunger itself or the plunger and other fixed parts causes friction resistance. This resistance is increased due to the magnetic force, which causes the driving force of the control valve to be lowered. .

Korean Patent Publication No. 10-933830

SUMMARY OF THE INVENTION The present invention has been made in order to solve the above-mentioned problems, and it is an object of the present invention to provide a control valve for a variable capacity compressor, in which a part of a plunger is accommodated and a two- The valve control can be performed with high accuracy by increasing the driving force. In particular, the non-magnetic material sleeve is added to the sliding portion to reduce the influence by the magnetic force and reduce the sliding resistance, The present invention provides a control valve for a variable displacement compressor that maximizes market competitiveness while increasing reliability and merchantability of the product.

The control valve is connected to a variable capacity compressor having a crank chamber, a discharge chamber, and a suction chamber and having a swash plate in the crank chamber, and controls the inclination angle of the swash plate through the passage switching of the refrigerant. A hollow body portion having a first port, a second port, and a third port communicating with the crank chamber, the discharge chamber, and the suction chamber, respectively; And a main valve positioned to be movable along the longitudinal direction in the body portion and capable of adjusting an opening degree of a flow path formed between the first port and the second port; A pressure sensitive part including a pressure sensitive member that is expandable and contractible in accordance with a pressure change of the third port to correct a position of the valve part; Stage coil having a large-diameter portion and a small-diameter portion with different inner diameters and forming a magnetic force corresponding to the amount of supplied current, and a two-stage coil having one end connected to the valve portion and the other portion connected to the large- A driving unit including a plunger that is inserted and retractable; And a sleeve of a non-magnetic material interposed between the inner circumferential surface of the body portion and the outer circumferential surface of the plunger so as to reduce the influence of the magnetic force and reduce the frictional resistance by maintaining a state in which mutual gaps are spaced from each other.

Here, the body portion may include a main body having the first port and the second port formed therein, and a yoke having the third port and made of a paramagnetic material; The sleeve may be interposed between the inner circumferential surface of the yoke and the outer circumferential surface of the plunger.

In addition, the pressure responsive portion includes a bellows, which is a pressure sensitive member having an elastic body therein, and is located in the plunger. One side of the bellows is fixed to a core located inside the two-stage coil, It may be preferable to selectively contact the valve portion according to the position of the valve body.

At this time, it is preferable that the sleeve is supported on the core and fixed in position.

Finally, the valve portion may further include a bypass passage for communicating the first port and the third port, so that the gap between the valve portion and the valve seat may be changed while the valve portion is advanced or retracted, thereby performing a variable orifice function .

As described above, the present invention can prevent the interference that may occur due to the turning of the center by increasing the concentricity and the coaxiality between the components by applying a two-stage coil for receiving and driving a part of the plunger in the control valve for the variable capacity compressor, By increasing the driving force, the valve control is performed with high accuracy. Particularly, by adding the non-magnetic material sleeve to the sliding portion, the influence by the magnetic force is reduced and the sliding resistance is reduced. And to maximize market competitiveness while increasing commerciality.

1 is a perspective view showing a control valve for a variable capacity compressor according to the present invention,
FIG. 2 is an exploded perspective view of a control valve for a variable capacity compressor according to the present invention,
FIG. 3 is an exploded perspective view of a control valve for a variable capacity compressor according to the present invention,
FIG. 4 is an exploded perspective view of a control valve for a variable capacity compressor according to the present invention,
FIG. 5 is an exploded perspective view of a control valve for a variable capacity compressor according to the present invention,
6 is a sectional view showing a control valve for a variable capacity compressor according to the present invention,
FIG. 7 is an enlarged view of a portion A of FIG. 6 showing a case where power is not applied to a driving portion in a control valve for a variable capacity compressor according to the present invention,
FIG. 8 is an enlarged view of a portion A of FIG. 6 showing a case where a current amount is applied to a driving portion in a control valve for a variable capacity compressor according to the present invention,
FIG. 9 is an enlarged view of a portion A of FIG. 6 showing a case where a current amount is appropriately adjusted and applied to a drive portion in a control valve for a variable capacity compressor according to the present invention,
Fig. 10 is an enlarged view of a portion B in Fig. 6; Fig.

FIG. 1 is a perspective view showing a control valve for a variable capacity compressor according to the present invention, FIG. 2 is an exploded perspective view of a part of a body portion of a control valve for a variable capacity compressor according to the present invention, Fig. 2 is an exploded perspective view of a control valve for a variable capacity compressor according to the present invention.

4 is an exploded perspective view of a control valve for a variable capacity compressor according to the present invention in which a valve portion is disassembled; FIG. 5 is an exploded perspective view of a control valve for a variable capacity compressor according to the present invention, 6 is a sectional view showing a control valve for a variable capacity compressor according to the present invention.

FIG. 7 is an enlarged view of a portion A of FIG. 6 showing the case where power is not applied to the driving portion in the control valve for the variable capacity compressor according to the present invention. FIG. FIG. 9 is an enlarged view of a portion A in FIG. 6 showing a case where a current amount is applied to a driving portion of the valve in FIG. 6; FIG. 9 is a cross- Fig. 6 is an enlarged view of a portion A in Fig.

Finally, FIG. 10 is an enlarged view of the portion B in FIG.

The specific structure or functional description presented in the embodiment of the present invention is merely illustrative for the purpose of illustrating an embodiment according to the concept of the present invention, and embodiments according to the concept of the present invention can be implemented in various forms. And should not be construed as limited to the embodiments described herein, but should be understood to include all modifications, equivalents, and alternatives falling within the spirit and scope of the invention.

Meanwhile, in the present invention, the terms first and / or second etc. may be used to describe various components, but the components are not limited to the terms. The terms may be referred to as a second element only for the purpose of distinguishing one element from another, for example, to the extent that it does not depart from the scope of the invention in accordance with the concept of the present invention, Similarly, the second component may also be referred to as the first component.

It is to be understood that when an element is referred to as being "connected" or "connected" to another element, it may be directly connected or connected to the other element, but it should be understood that there may be other elements in between something to do. On the other hand, when it is mentioned that an element is "directly connected" or "directly contacted" to another element, it should be understood that there are no other elements in between. Other expressions for describing the relationship between components, such as "between" and "between" or "adjacent to" and "directly adjacent to" should also be interpreted.

The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The singular expressions include plural expressions unless the context clearly dictates otherwise. It will be further understood that the terms " comprises ", or "having ", and the like in the specification are intended to specify the presence of stated features, integers, But do not preclude the presence or addition of steps, operations, elements, parts, or combinations thereof.

The control valve for a variable capacity compressor according to the present invention can prevent interference that may occur due to the center turning by increasing the concentricity and coaxiality between parts by applying a two stage coil 410 which receives and drives a part of the plunger, By performing the valve control with high accuracy by increasing the driving force, the sleeve 500 of the non-magnetic material can be added to the sliding portion in particular to reduce the influence by the magnetic force and reduce the sliding resistance, The basic feature of the technology is that it maximizes market competitiveness while increasing the reliability and merchability of the product.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

1 to 5, a control valve for a variable capacity compressor according to the present invention is connected to a variable displacement compressor provided with a crank chamber, a discharge chamber, and a suction chamber, and having a swash plate in the crank chamber, 1. A control valve for controlling an inclination angle of a swash plate by switching a flow path, comprising: A hollow body portion 100 in which a first port 101, a second port 102, and a third port 103 communicating with the crank chamber, the discharge chamber, and the suction chamber are formed; And a main valve (210) positioned to be movable along the longitudinal direction in the body part (100) and capable of adjusting the opening degree of a flow path formed between the first port (101) and the second port (102) (200); A pressure sensitive part 300 including a pressure sensitive member 310 which is expandable and contractible according to a pressure change of the third port 103 to correct the position of the valve part 200; Stage coil 410 formed of a stepped large-diameter portion 411 and a small-diameter portion 412 having different inner diameters and forming a magnetic force corresponding to the amount of supplied current, and a two-stage coil 410 having one end connected to the valve portion 200 And a plunger (420) inserted into the large diameter portion (411) of the two-stage coil (410) and movable forward and backward; And a sleeve (500) of a nonmagnetic material interposed to reduce frictional resistance by reducing the influence of the magnetic force by maintaining a state in which mutual gaps are maintained between the inner circumferential surface of the body part (100) and the outer circumferential surface of the plunger Lt; / RTI >

That is, the control valve for a variable capacity compressor according to the present invention includes a body 100, a valve 200, a pressure sensitive part 300, a driving part 400, and a sleeve 500.

Basically, the control valve for a variable capacity compressor according to the present invention is suitable for application to a known variable capacity compressor which is a key element constituting an air conditioner of a vehicle. The known variable capacity compressor has a crank chamber, a discharge chamber, A suction chamber is formed.

Such a variable capacity compressor corresponds to a compressor in a cooling cycle in which a compressor, a condenser, an expansion valve, and an evaporator are provided and perform cooling according to the refrigerant circulation.

At this time, a swash plate is provided in the crank chamber of the variable capacity compressor, and the control valve for the variable capacity compressor of the present invention is connected to the variable capacity compressor to control the inclination angle of the swash plate by switching the flow path of the refrigerant.

Here, when the pressure of the refrigerant supplied to the crank chamber is decreased to control the inclination angle of the swash plate, the amount of the refrigerant discharged from the variable capacity compressor increases, thereby increasing the cooling effect.

On the other hand, when the pressure of the refrigerant supplied to the crank chamber is increased to control the inclination angle of the swash plate to be small, the amount of refrigerant discharged from the variable capacity compressor decreases, thereby lowering the cooling effect.

As shown in FIGS. 2 and 6, the body part 100 has a substantially hollow pipe shape. The body part 100 has a basic skeleton in the control valve for a variable capacity compressor of the present invention. Or may be provided movably.

Here, the body 100 may be a single body composed of only one component, or an assembly of two or more components assembled together.

However, it is preferable that the body part 100 is made of a single body as much as possible in consideration of ease of assembly and the like. However, if the internal shape of the body part 100 is desired to be processed easily or partially in terms of physical properties of a specific material, Will be good.

The body portion 100 includes a first port 101, a second port 102, and a third port (not shown) communicating with the crank chamber, the discharge chamber, and the suction chamber formed in the variable capacity compressor, 103 are formed.

At this time, the first port 101, the second port 102, and the third port 103 are sequentially formed on the body portion 100 from left to right in the drawing, The second port 102 and the third port 103 are formed on the circumferential surface of the body part 100 in such a manner that one or more than one As shown in FIG.

Of course, there will be no limit to the direction in which each of these ports is directed.

A plurality of through holes 131 are radially formed along the rim of the valve seat 130 to allow the refrigerant to flow through the valve seat 130, And may be distributed to the first port 101. [

The valve seat 130 may be press-fitted to the inner circumferential surface of the first port 101 in a non-adjustable position or may be screwed to adjust the fixing position of the valve seat 130, A separate filter 132 may be additionally installed at the end of the first port 101 to filter the foreign substances from the refrigerant passing through the first port 101. [

The valve seat 130 will be controlled by a gap between the valve seat 200 and the valve seat 200 to function as a variable orifice, which will be described later.

A generally rectangular filter frame 140 may be provided around the second port 102. A porous filter not shown in the drawing may be attached to the filter frame 140, It is possible to filter out the foreign substances contained in the refrigerant flowing through the refrigerant circulation pipe 102.

In the figure, reference numeral 105 denotes a sealing ring made of an elastic sealing material provided on the outer circumferential surface of the body part 100 to maintain airtightness. In the figure, a sealing ring 105 is positioned between the respective ports, 100 have been illustrated with three seals 105 applied thereto.

4 and 6, the valve unit 200 may be disposed within the body 100 and be movable along the longitudinal direction. The valve unit 200 may also be formed of a unitary body or an assembly .

The main valve 210 and the valve shaft 220 are connected to each other by screws 211. The main valve 210 and the valve shaft 220 are connected to each other by a screw Or they can be integrated with each other.

Particularly, the main valve 210 and the valve shaft 220 of the valve unit 200 are both formed of hollow bodies, and a flow path is formed therein, so that the refrigerant can be selectively circulated.

At this time, the main valve 210 functions to regulate the opening of the flow path formed between the first port 101 and the second port 102 in the body 100 described above.

For example, when the main valve 210 is advanced to the left in FIG. 7, the flow path formed between the first port 101 and the second port 102 is opened, If you retreat, you will close this channel.

Of course, the main valve 210 is not only switched between a fully opened state and a fully closed state, but serves to precisely control the opening of the flow path between the opened state and the closed state as illustrated in FIG. 9 And precise control of this opening degree can be performed by the pressure-sensitive portion 300 to be described later.

4 to 6, the pressure sensing unit 300 includes a pressure sensitive member 310 that is stretchable and contractible in response to a change in peripheral pressure. The pressure sensing unit 300 includes a pressure sensing member 310, (100).

Accordingly, the pressure sensitive member 310 is affected by the refrigerant pressure of the third port 103, that is, the refrigerant pressure in the suction chamber of the variable capacity compressor, So that precise control can be performed.

For example, when the pressure of the refrigerant applied to the pressure sensitive member 310 is high, the pressure sensitive member 310 is contracted, and when the pressure of the refrigerant is low, the pressure sensitive member 310 is extended .

In the pressure sensitive part 300, the expansion and contraction of the pressure sensitive member 310 affects the position control of the valve part 200.

1 to 3 and 6, the driving unit 400 corresponds to a well-known solenoid driving mechanism including a coil and a plunger. Particularly, in the present invention, And a two-stage coil 410 made up of a small-diameter portion 411 and a small-diameter portion 412.

At this time, the two-stage coil 410 may be provided in a cylindrical casing 440, and reference numeral 401 denotes a seal provided on an outer circumferential surface of the driving unit 400.

The large-diameter portion 411 having an inner diameter larger than that of the small-diameter portion 412 is formed on the inner circumferential surface of the outer circumferential surface of the two-stage coil 410 about the entire length of the two- And is formed to have a length corresponding to 1/3 to 1/2.

The two-stage coil 410 can be formed by making the numbers of turns of the small-diameter portion 412 and the large-diameter portion 411 different from each other.

For example, when a high current amount is applied, a relatively large magnetic force is formed. When a low amount of current is applied, a relatively small amount of magnetic force .

Of course, if no current is applied, no magnetic force will be formed, and the amount of current supplied to the two-stage coil 410 may be actively controlled by the air conditioning controller of the vehicle.

In the present invention, only a part of the plunger 420 is positioned so as to be inserted into the two-stage coil 410. The plunger 420 is moved in accordance with the magnetic force of the two- will be.

That is, the plunger 420 is positioned so as to be completely accommodated in the two-stage coil 410 described above, or is not located completely out of the two-stage coil 410 described above.

The reason that the plunger 420 is completely accommodated in the two-stage coil 410 is that the entire length of the two-stage coil 410 is overlapped to accommodate the entire length of the plunger 420 It means.

In such a case, since the distance between the valve unit 200 and the plunger 420 is relatively long, it is difficult to accurately maintain the concentricity and the coaxiality between the components, and vibration and noise are frequently generated It causes.

The fact that the plunger 420 is located completely out of the two-stage coil 410 means that the entire length of the two-stage coil 410 is positioned so that no part of the entire length of the plunger 420 overlaps .

In this case, the distance between the valve portion 200 and the plunger 420 is relatively close, which is good for accurately maintaining the concentricity or coaxiality between the components. However, the plunger 420 is too far away from the coil, It is difficult to obtain a high driving force at a desired level.

That is, according to the present invention, only a part of the plunger 420 is positioned in the two-stage coil 410, so that the desired driving force of the plunger 420 can be obtained while maintaining the concentricity and coaxiality between the components accurately.

The left end of the plunger 420 is connected to the outer circumferential surface of the valve shaft 220 of the valve unit 200 and the right part of the plunger 420 is connected to the large diameter portion 411 of the two- As shown in FIG.

6, the position where the plunger 420 can be fully inserted to the right in the drawing is a position where the entirety of the two-stage coil 410, which is the large-diameter portion 411 formed in the two-stage coil 410, About 1/3 to 1/2 of the length.

4 and 6, a coil spring 450 is provided between the two-stage coil 410 and the plunger 420 so that the plunger 420 moves from the two-stage coil 410 to the left side in the drawing And is elastically supported to be spaced apart.

To this end, a separate step 421 for contacting the coil spring 450 may be formed on the outer circumferential surface of the plunger 420.

6, when the amount of current is not applied to the two-stage coil 410, the plunger 420 is advanced to the left side in FIG. 6 by the coil spring 450, The plunger 420 is retracted to the right side in Fig. 6 by the magnetic force formed in the two-stage coil 410. [

The valve shaft 220 is connected to the left end of the plunger 420 such that the valve shaft 220 is integrally movable with respect to the valve shaft 220. As the plunger 420 moves, The entire body 200 can be moved together.

6 and 10, the inner circumferential surface of the body 100 and the outer circumferential surface of the plunger 420 are spaced apart from each other to reduce the influence of the magnetic force, thereby reducing the frictional resistance And a sleeve 500 of a non-magnetic material interposed therebetween.

Here, the sleeve 500 is made of a non-magnetic material in the form of a hollow pipe having a thickness of about 1 mm or less, more preferably 0.5 mm or less.

The gap between the inner circumferential surface of the body 100 and the outer circumferential surface of the plunger 420 can be maintained constant by the sleeve 500. [

In addition, when the yoke 120 made of a paramagnetic material is further added to the body portion 100 to extend the magnetic force formed in the driving portion 400 toward the left side in the drawing where the plunger 420 is located, The sleeve 500 made of a nonmagnetic material is positioned between the yoke 120 made of a paramagnetic material and the plunger 420 made of a paramagnetic material in the driving part 400. [

The sliding resistance between the plunger 420 and the yoke 120 is reduced by locating the sleeve 500 made of non-magnetic material between the plunger 420 and the yoke 120, The role is to be effective.

As a result, by reducing the influence of the magnetic force acting between the plunger 420 and the yoke 120 by the sleeve 500, the sliding portion formed between the outer peripheral surface of the plunger 420 and the inner peripheral surface of the yoke 120 The frictional resistance can be greatly reduced and the driving force of the plunger 420 can be effectively prevented from being lowered.

The present applicant has measured the sliding resistance generated between the plunger 420 and the yoke 120 while increasing or decreasing the thickness of the sleeve 500. As a result, even when the thickness of the sleeve 500 is 0.1 mm, Respectively.

According to the test results, the sliding resistance between the plunger 420 and the yoke 120 can be improved by appropriately changing the thickness of the sleeve 500 without reducing the driving force of the plunger 420 It is possible to appropriately reduce it.

In order to extend the magnetic force of the driving unit 400 as described above, the body 100 of the present invention includes a main body 110 having the first port 101 and the second port 102 formed therein, And a yoke (120) having the third port (103) and made of a paramagnetic material; Preferably, the sleeve 500 is interposed between the inner circumferential surface of the yoke 120 and the outer circumferential surface of the plunger 420.

This is because only the yoke 120 is locally applied to the body portion 100 as a box material having a material different from that of the body portion 100. Accordingly, A second port 102 may be formed, and the third port 103 may be formed in the yoke 120.

5 and 6, the pressure sensitive part 300 includes a bellows which is a pressure sensitive member 310 having an elastic body 311 therein, and is disposed in the plunger 420 Stage coil 410. The other side of the core 430 may be selectively in contact with the valve 200 according to the elongation and contraction of the bellows.

That is, the first and second support members 312 and 313 are provided at both ends of the bellows, which is the pressure sensitive member 310 of the pressure sensitive part 300, and an elastic body 311 is provided so as to be elastically stretched in the bellows. .

Accordingly, when the pressure of the refrigerant acting on the pressure sensitive member 310 is low, the elastic body 311 elastically extends the pressure of the refrigerant. When the pressure of the refrigerant acting on the pressure sensitive member 310 is high, .

The pressure sensing part 300 may be disposed within the plunger 420 so that the plunger 420 may be formed in a housing shape to accommodate the pressure sensing part 300 .

A through hole 422 is formed in the circumferential surface of the plunger 420 so that the refrigerant pressure of the third port 103 is smoothly applied to the pressure sensing part 300 through the plunger 420 Will be good.

An adjustment screw 320 is connected to the second support member 313 on the right side of the pressure sensitive part 300. The adjustment screw 320 is positioned inside the above- Lt; RTI ID = 0.0 > 430 < / RTI >

Here, reference numeral 301 denotes a sealing ring 301 provided on the outer peripheral surface of the adjusting screw 320.

6, the adjusting screw 320 is fixed to the inner circumferential surface of the core 430, and the adjusting screw 320 is rotated to change the engaging position. As a result, It is also possible to finely adjust the support position of the pressure sensitive member 310. [

The first support member 312 provided on the left side of the pressure sensitive portion 300 may be selectively brought into contact with the valve portion 200 according to the expansion and contraction of the bellows as the pressure sensitive member 310 .

Accordingly, the valve unit 200 basically acts on the elastic body 311, the plunger 420, and the pressure sensitive part 300 in a complex manner, It becomes possible to appropriately control it.

In the present invention, it is preferable that the sleeve 500 is supported by the core 430 and fixed in position.

4, the sleeve 500 is positioned between the outer circumferential surface of the plunger 420 and the inner circumferential surface of the yoke 120 of the body 100, and the sleeve 500 is integrally formed with the core 430 And the yoke 120 is integrally connected to the sleeve 500, it is possible to reduce the number of assembled parts.

In addition, it is possible to prevent the sleeve 500 from flowing finely due to an assembly tolerance or the like by simply fixing the position of the sleeve 500 not to interpose the sleeve 500 at a predetermined position.

A bypass passage 221 for connecting the first port 101 and the third port 103 is additionally formed in the valve portion 200 of the valve 200, It is preferable to perform the variable orifice function while the clearance with the valve seat 130 changes during forward and backward movement.

In a conventional conventional variable capacity compressor, a separate orifice is provided inside or outside the body of the variable capacity compressor in order to directly discharge the refrigerant in the crankcase into the suction chamber for the purpose of effective control of the compressor.

However, since the opening orifice is not provided separately and has a fixed orifice shape having a constant diameter, the compression efficiency of the variable capacity compressor is greatly reduced due to the discharge of the refrigerant in the crankcase to the suction chamber even when the fixed orifice is not required. .

Correspondingly, in the present invention, both the main valve 210 and the valve shaft 220 are formed as a hollow body in the valve unit 200, and the first port 101 and the third port 103 can communicate with each other The bypass passage 221 is formed in the valve portion 200 so that the bypass passage 221 is formed.

6, the bypass passage 221 is further formed in the valve shaft 220 as shown in FIG. 6 so that the inside of the valve portion 200 and the third port 103 are communicated with each other It would be desirable to be able to do so.

Thus, in the present invention, the variable orifice composed of the first port 101, the valve seat 130 and the main valve 210, the bypass passage 221 of the valve shaft 220, and the third port 103 As shown in FIG.

The variable orifice configured as described above is adapted to automatically discharge the refrigerant in the crank chamber to the suction chamber by adjusting the clearance between the valve portion 200 and the valve seat 130 when the valve portion 200 moves back and forth .

7, when the main valve 210 of the valve unit 200 is completely in close contact with the valve seat 130, the variable orifice is closed, and the main valve 210 is closed by the valve seat 130 , The variable orifice is opened.

9, the opening degree between the main valve 210 and the valve seat 130 is appropriately adjusted even when the valve portion 200 moves forward and backward by the pressure sensitive portion 300 .

As a result, in the present invention, by applying the variable orifice to the control valve for the variable displacement compressor, it is possible to greatly improve the compression efficiency of the variable displacement compressor while eliminating the existing fixed orifice.

Hereinafter, the operation of the present invention will be described with reference to the drawings.

In the control valve for a variable capacity compressor of the present invention having the above-described structure, when no power is applied to the driving unit 400, when the amount of current is 100% applied to the driving unit 400, , And each case will be separately described below.

&Lt; No power is applied to the driving unit 400 >

When the power is not applied to the control valve for the variable capacity compressor of the present invention, the driving unit 400 does not operate, and the plunger 420 moves to the left side in the drawing by the elastic force of the coil spring 450 only.

Accordingly, the entire valve unit 200 including the main valve 210 moves to the left through the valve shaft 220 connected to the plunger 420.

As a result, the main valve 210 opens the flow path between the first port 101 and the second port 102 formed in the body portion 100 as shown in Fig. 7, thereby opening the flow path from the discharge chamber of the variable capacity compressor to the crank chamber, The refrigerant flows as indicated by arrows in Fig. 4A. In this case, the variable orifice is closed.

As a result, the amount of refrigerant discharged from the variable displacement compressor is minimized by controlling the inclination angle of the swash plate to be as small as possible as the refrigerant pressure in the crank chamber rises in the variable displacement compressor, and the variable orifice is closed, The refrigerant is not discharged.

&Lt; Case in which the amount of current is applied to the driving part 400 by 100%

When 100% power is applied to the control valve for the variable capacity compressor according to the present invention, a driving current of 100% is supplied to the driving unit 400. At this time, the driving force of the plunger 420 is transmitted to the driving unit 400, The plunger 420 is maximally moved to the right side in the drawing.

Accordingly, the entire valve unit 200 including the main valve 210 moves to the right through the valve shaft 220 connected to the plunger 420.

As a result, the main valve 210 closes the flow path between the first port 101 and the second port 102 formed in the body portion 100 as shown in FIG. 8, There is no flow of coolant through the crankcase, and in this case, the variable orifice is opened to the maximum.

As a result, the amount of refrigerant discharged from the variable displacement compressor is maximized by controlling the inclination angle of the swash plate as large as possible as the refrigerant pressure in the crank chamber decreases in the variable displacement compressor. In particular, The refrigerant is quickly discharged to the suction chamber, effectively increasing the compression efficiency.

&Lt; Case where the amount of current is appropriately adjusted and applied to the driving unit 400 >

In the case where the control valve for the variable capacity compressor of the present invention is appropriately regulated and supplied with power, a proper amount of current is supplied to the driving unit 400. In this case, The pressure of the refrigerant in the crankcase is applied to the pressure sensing part 300.

At this time, along with the driving force of the plunger 420 and the elastic extension force of the coil spring 450, a force to expand and contract according to the refrigerant pressure acting on the pressure sensitive member 310 in the pressure sensitive portion 300 is added The plunger 420 moves alternately from left to right in the drawing.

The entire valve portion 200 including the main valve 210 moves through the valve shaft 220 connected to the plunger 420 in accordance with the refrigerant pressure change in the suction chamber to the left or right in the drawing will be.

As a result, the main valve 210 appropriately adjusts the opening degree of the flow path between the first port 101 and the second port 102 formed in the body portion 100 as shown in FIG. 9, So that the amount of refrigerant discharged from the variable displacement compressor is optimized by controlling the slope angle of the swash plate to be suitably large or small while repeatedly raising or lowering the refrigerant pressure in the crank chamber.

At the same time, the variable orifice also appropriately adjusts the opening degree between the main valve 210 and the valve seat 130 in accordance with the movement of the valve unit 200, thereby improving the compression efficiency of the variable capacity compressor It will help.

Accordingly, in the present invention, in the control valve for variable capacity compressors performing the basic operation as described above, since only a part of the plunger 420 is located in the two-stage coil 410 as shown in FIG. 6, The distance between the valve portions 200 is relatively short so that the desired driving force of the plunger 420 can be obtained while maintaining the concentricity and the coaxiality between the components accurately.

In addition, in the present invention, it is possible to obtain a high driving force even if only a part of the plunger 420 is placed in the two-stage coil 410 by adding the yoke 120 made of the paramagnetic material, The sleeve 500 made of a non-magnetic material is positioned between the yoke 120 made of a box-like material and the plunger 420 made of a box-like material in the driving unit 400, so that the plunger 420 and the yoke 120 Thereby effectively reducing the sliding resistance acting on each other.

The sliding portion 500 reduces the influence of the magnetic force acting between the plunger 420 and the yoke 120 and reduces the influence of the magnetic force acting between the plunger 420 and the inner peripheral surface of the yoke 120, It is possible to effectively prevent the driving force of the plunger 420 from being reduced by effectively reducing the frictional resistance of the plunger 420. [

In addition, the variable orifice is integrally formed in the control valve for the variable displacement compressor, so that the refrigerant in the crank chamber can be quickly discharged to the suction chamber as required, thereby effectively increasing the compression efficiency.

The above embodiment is an example for explaining the technical idea of the present invention specifically, and the scope of the present invention is not limited to the above-mentioned drawings or embodiments.

100: body part 101: first port
102: second port 103: third port
105: Sealing 106: Valve mechanism
110: main body 120: yoke
130: valve seat 131: through hole
132: filter 140: filter frame
200: valve part 210: main valve
220: valve shaft 221: bypass passage
300: Pressure sensitive part 301: Sealing
310: Pressure sensitive member 311: Elastic body
312: first support member 313: second support member
320: adjusting screw 400:
401: sealing 410: two-stage coil
411: large diameter portion 412: small diameter portion
420: plunger 421: step
422: through hole 430: core
440: casing 450: coil spring
500: Sleeve

Claims

A control valve connected to a variable capacity compressor having a crank chamber, a discharge chamber, and a suction chamber and having a swash plate in the crank chamber, for controlling the inclination angle of the swash plate through switching of a flow path of the refrigerant;
A hollow body portion having a first port, a second port, and a third port communicating with the crank chamber, the discharge chamber, and the suction chamber, respectively;
And a main valve positioned to be movable along the longitudinal direction in the body portion and capable of adjusting an opening degree of a flow path formed between the first port and the second port;
A pressure sensitive part including a pressure sensitive member that is expandable and contractible in accordance with a pressure change of the third port to correct a position of the valve part;
A two-stage coil formed of a large-diameter portion and a small-diameter portion in the form of steps having different inner diameters, the large-diameter portion being positioned adjacent to the valve portion and forming a magnetic force corresponding to an amount of supplied current, And a plunger disposed in the body and directly connected to the valve without any other configuration and having a portion of the other end inserted into the large diameter portion of the two-stage coil and capable of advancing and retracting between the body and the large diameter portion of the two- ;
And a sleeve of a non-magnetic material which is interposed between the inner circumferential surface of the body portion and the outer circumferential surface of the plunger so as to reduce the influence of the magnetic force to reduce frictional resistance by maintaining a state in which mutually- .

[3] The apparatus of claim 1, wherein the body includes a main body having the first port and the second port formed therein, and a yoke made of a paramagnetic material in which the third port is formed;
Wherein the sleeve is interposed between an inner peripheral surface of the yoke and an outer peripheral surface of the plunger.

The pressure sensor according to claim 2, wherein the pressure sensitive part includes a bellows, which is a pressure sensitive member having an elastic body therein, and is located in the plunger, one side of which is fixed to a core located on the inner side of the two- And selectively contacts the valve portion according to expansion and contraction of the bellows.

The control valve for a variable capacity compressor according to claim 3, wherein the sleeve is supported and fixed in the core.

[5] The apparatus of claim 4, wherein the valve unit further includes a bypass passage communicating the first port and the third port to perform a variable orifice function while changing a clearance between the valve seat and the valve seat when the valve unit moves back and forth And a control valve for a variable capacity compressor.