JP2007154718A - Control valve for variable displacement compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To damp the impact of a valve element by a solenoid force when it is seated and, more preferably, simplify the structure of a drive force transmission portion for transmitting a drive force to the valve element in a control valve for a variable displacement compressor. <P>SOLUTION: In this control valve 1 for the variable displacement compressor, a support structure composed of spring retainers 43, 44 and a spring 45 is formed in a plunger 33. The support structure supports a shaft 17 on the plunger 33 displaceably relative to each other when the valve element 18 is seated on a valve seat 16. Therefore, the impact force of the valve element 18 by the solenoid force when the valve element 18 is seated can be damped. Also, since the valve element 18 is formed integrally with the shaft 17, the structure of the drive force transmission portion transmitting the drive force to the valve element 18 can be simplified. In addition, since the number of parts can be reduced, the manufacturing cost can be reduced. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a control valve for a variable capacity compressor, and more particularly to a control valve for a variable capacity compressor that is suitable for controlling the discharge capacity of a variable capacity compressor that constitutes the refrigeration cycle of an automotive air conditioner.

  Since the compressor used for compressing the refrigerant in the refrigeration cycle of the air conditioner for automobiles uses the engine as a drive source, the rotational speed control cannot be performed. Therefore, in order to obtain an appropriate cooling capacity without being restricted by the engine speed, a variable capacity compressor capable of changing the compression capacity of the refrigerant is used.

  In such a variable capacity compressor, a compression piston is connected to a swing plate attached to a shaft that is rotationally driven by an engine, and the stroke of the compression piston is changed by changing the angle of the swing plate. The amount of refrigerant discharged is changed.

  The angle of the swing plate is continuously increased by introducing a part of the compressed refrigerant into the sealed crank chamber, changing the pressure of the introduced refrigerant, and changing the balance of pressure applied to both sides of the compression piston. Is changing.

  The pressure in the crank chamber is adjusted by, for example, providing a control valve between the discharge chamber and the crank chamber of the variable capacity compressor and changing the flow rate of the refrigerant introduced from the discharge chamber into the crank chamber. At this time, an orifice is provided between the crank chamber and the suction chamber, and a path through which the refrigerant flows from the discharge chamber to the suction chamber is formed. The control valve includes, for example, a valve body capable of opening and closing a valve hole that is in contact with and separated from a valve hole that forms a refrigerant passage that communicates the discharge chamber and the crank chamber. And the flow rate of the refrigerant | coolant which flows from the discharge chamber side to the suction chamber side is adjusted by controlling the lift amount from the valve hole of this valve body (for example, refer patent document 1).

  More specifically, this control valve has a valve body disposed downstream of the valve hole (that is, the crank chamber side), and is sequentially provided with a piston rod and a shaft on the opposite side of the valve hole of the valve body. The valve body has a guide portion that slides along a guide hole provided in the body so as to operate along the same axis as the piston rod. The shaft is integrated with the plunger of the solenoid, and when the solenoid is energized, transmits the solenoid force in the valve closing direction to the valve body via the piston rod. The suction surface (Ps) acting in the valve closing direction and the solenoid force thereof are loaded on the end surface of the piston rod opposite to the valve body.

The control valve also communicates a space provided around the connecting portion between the valve body and the piston rod to the crank chamber of the variable capacity compressor. As a result, the control valve communicates or closes the passage between the discharge chamber and the crank chamber so that the pressure difference (Pd−Ps) between the discharge pressure (Pd) and the suction pressure (Ps) is maintained at a predetermined value. By controlling, the predetermined value of the differential pressure can be set from the outside by the value of the current supplied to the solenoid. As a result, when the engine speed increases, the pressure (Pc) introduced into the crank chamber is increased to reduce the discharge capacity, and when the engine speed decreases, the orifice is made larger than the refrigerant flow rate introduced into the crank chamber. The flow rate released to the suction chamber is increased and the pressure (Pc) in the crank chamber is decreased to increase the discharge capacity, thereby keeping the discharge capacity of the variable capacity compressor constant.
JP2003-328936A (FIG. 2 etc.)

  By the way, in such a control valve for a variable capacity compressor, since the valve body, the piston rod and the shaft are each configured independently, the number of parts is large, the assembling work becomes complicated, and the manufacturing cost increases. was there.

  Further, during the operation of the control valve for the variable capacity compressor, the valve body, the piston rod and the shaft are integrated, and the solenoid force is directly transmitted to the valve body via the shaft and the piston rod. For this reason, the impact force when the valve body is seated on the valve seat provided at the opening end of the valve hole is increased due to the steep solenoid force particularly at the start of energization, and the impact sound is generated. In general, since the solenoid is energized and controlled at a predetermined frequency (for example, 400 Hz) even when the valve is closed, the plunger slightly vibrates at that frequency. For this reason, there has been a problem that the valve body bounces against the valve seat due to the vibration of the plunger, and an impact sound is generated by the impact force at the time of the bound.

  The present invention has been made in view of the above points, and can reduce the impact force when the valve body is seated by the solenoid force, and more preferably a variable that can simplify the configuration of the driving force transmission portion to the valve body. An object of the present invention is to provide a control valve for a capacity compressor.

  In the present invention, in order to solve the above problem, the flow rate of the refrigerant introduced from the discharge chamber to the crank chamber is controlled and variable so that the differential pressure between the discharge pressure of the discharge chamber and the suction pressure of the suction chamber is maintained at a predetermined value. In a control valve for a variable capacity compressor that changes a refrigerant discharge capacity from a capacity compressor, a valve hole that forms a refrigerant passage that communicates the body with a refrigerant passage formed therein, and the discharge chamber and the crank chamber A valve body that is arranged so as to be in contact with and away from the crank chamber side, opens and closes the valve hole, a shaft that transmits axial force to the valve body, a core that is fixed to the body, and the shaft A plunger that is inserted in the axial direction, a support structure that supports the shaft so as to be relatively displaceable with respect to the plunger, and a suction that acts in the valve closing direction of the valve body between the core and the plunger when energized. Control valve is provided, characterized in that it comprises a solenoid having an electromagnetic coil, a for generating.

  In such a control valve for a variable capacity compressor, even if the shaft moves in the valve closing direction by the operation of the plunger, the shaft can be displaced relative to the plunger at the same time as the valve body is seated. For this reason, the impact force at the time of seating of the valve body by a solenoid force can be relieved.

  In this case, by providing the support structure inside the plunger so as to be displaced together with the plunger, it is possible to ensure a normal control state in which the shaft and the plunger are integrated except when the valve is closed.

  Further, in the present invention, the flow rate of the refrigerant introduced from the discharge chamber to the crank chamber is controlled so that the differential pressure between the discharge pressure of the discharge chamber and the suction pressure of the suction chamber is maintained at a predetermined value. In the control valve for a variable capacity compressor that changes the discharge capacity of the refrigerant, the crank chamber is formed in a valve hole that forms a refrigerant passage that connects the discharge chamber and the crank chamber to a body in which a refrigerant passage is formed. A valve body that is arranged so as to be in contact with or separated from the side and opens and closes the valve hole, a shaft in which the valve body is integrally provided, and a solenoid force corresponding to the differential pressure of the predetermined value is applied to the shaft. And a solenoid for operating the valve element in the axial direction of the shaft. A control valve for a variable capacity compressor is provided.

  In such a control valve for a variable capacity compressor, the valve body is provided integrally with the shaft, and the operation of the shaft directly becomes the operation of the valve body.

  According to the control valve for a variable capacity compressor of the present invention, the shaft is configured to be relatively displaceable with respect to the plunger, and even when a solenoid force is applied, the shaft operates more slowly than the plunger when the valve is closed. Can reduce the impact force when closing the valve hole.

  Further, according to another control valve for a variable capacity compressor of the present invention, since the valve body is provided integrally with the shaft, the configuration of the driving force transmission portion to the valve body is simplified. In addition, since the number of parts is reduced, the manufacturing cost can be reduced.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following description, for the sake of convenience, the positional relationship between the structures may be expressed as upper and lower with reference to the illustrated state.
[First Embodiment]
FIG. 1 is a cross-sectional view illustrating a configuration of a variable displacement compressor control valve according to a first embodiment.

  The variable displacement compressor control valve 1 includes a valve component 2 that opens and closes a refrigerant passage for allowing a part of refrigerant discharged from a variable displacement compressor (not shown) to flow into the crank chamber, and a valve portion of the valve component 2. And a solenoid 3 for controlling the flow rate of the refrigerant passing therethrough by adjusting the degree of opening thereof.

  The valve component 2 is provided with a port 11 at the top of the body 10 for receiving the discharge pressure Pd in communication with the discharge chamber of the variable capacity compressor. A strainer 12 is fitted to the upper end portion of the body 10 so as to cover the port 11. The port 11 communicates internally with a port 13 provided on the side of the body 10. The port 13 communicates with a crank chamber of the variable capacity compressor and derives a controlled pressure (referred to as “crank pressure”) Pc in the crank chamber.

  A cylindrical valve seat forming member 14 is press-fitted into the refrigerant passage communicating the port 11 and the port 13, and a valve hole 15 is formed by the internal passage, and the valve is formed by the inner peripheral edge of the end face on the crank chamber side. A seat 16 is formed.

  Further, a valve body 18 composed of one end of a long shaft 17 is disposed so as to be able to contact and separate from the valve seat 16 from the side from which the discharge pressure Pd is derived. The valve body 18 is slidably supported by a guide hole 19 provided in the center of the body 10. The valve body 18 is disposed in a pressure chamber 21 having a distal end thereof communicating with the crank chamber on the downstream side of the valve hole 15, and an outer peripheral edge of the distal end surface is attached to and detached from the valve seat 16 to open and close the valve hole 15.

  In addition, a port 22 that communicates with the suction chamber of the variable capacity compressor and receives the suction pressure Ps is formed in a side portion near the lower end portion of the body 10, and an opening having a predetermined depth provided at the lower end center of the body 10. It communicates with the hole 24. The opening hole 24 forms a pressure chamber 25 into which the suction pressure Ps is introduced. The pressure chamber 25 communicates with the inside of the solenoid 3. The body 10 is connected to the solenoid 3 via a stepped cylindrical connecting member 26, and the upper end portion of the connecting member 26 is press-fitted into the opening hole 24 of the body.

  On the other hand, the solenoid 3 generates a magnetic circuit including a core 32 fixed in the case 31, a plunger 33 inserted through the shaft 17 and supported in the axial direction, and a core 32 and the plunger 33 by an externally supplied current. The electromagnetic coil 34 is provided. The upper end portion of the case 31 is crimped and joined to the outer peripheral portion of the lower end of the connection member 26.

  The upper end of the core 32 is press-fitted into the inner peripheral surface of the connection member 26. The core 32 is provided with an insertion hole that penetrates the center thereof in the axial direction and inserts the shaft 17, and an upper end opening thereof is opened to the pressure chamber 25.

  A bottomed sleeve 36 having a closed lower end is externally inserted into the core 32. In the bottomed sleeve 36, the plunger 33 is supported below the core 32 so as to be able to advance and retract in the axial direction. The bottomed sleeve 36 is press-fitted into the lower half of the connecting member 26 at its upper end. A bearing member 37 is fixedly disposed at the lower end of the bottomed sleeve 36, and supports the lower end of the shaft 17 so as to be slidable.

  The shaft 17 is provided with a small-diameter portion 38 having a smaller diameter at the lower part thereof, and a plunger 33 is inserted downward from the vicinity of the base end portion of the small-diameter portion 38. The tip of the small diameter portion 38 is slidably inserted into the bearing member 37.

  The plunger 33 has a bottomed cylindrical main body 41, and the shaft 17 is inserted through a circular hole 42 formed at the center of the upper bottom thereof. A stepped annular spring receiver 43 is press-fitted in the vicinity of the lower end opening of the main body 41. A stepped annular spring receiver 44 is slidably disposed in the plunger 33 so as to face the spring receiver 43. The spring receiver 44 is configured such that the upper end surface thereof is in contact with the base end portion of the small diameter portion 38 so as to be able to operate integrally with the shaft 17, and the upper end surface corresponds to the upper bottom surface of the plunger 33 (“locking portion”). The displacement in the axial direction is regulated.

  A spring 45 (corresponding to “biasing means”) is interposed between the spring receiver 43 and the spring receiver 44, and the movement of the plunger 33 is transmitted to the shaft 17 via the spring 45 and the spring receiver 44. It has come to be. However, the plunger 33 and the shaft 17 are not fixed to each other and are connected via a spring 45 serving as an axial cushioning material. For this reason, when a large force is applied to the shaft 17 in the axial direction, the spring 45 is deformed, and the shaft 17 is displaced relative to the plunger 33. The spring load applied to the shaft 17 by the spring 45 via the spring receiver 44 can be adjusted by changing the amount of press-fitting of the spring receiver 43 into the plunger 33.

  A spring 46 that biases the plunger 33 away from the core 32 is interposed between the core 32 and the plunger 33, and the plunger 33 is interposed between the spring receiver 43 and the bearing member 37. A spring 47 is disposed so as to be biased in a direction to be close to 32. The spring load of the springs 46 and 47 can be adjusted by pressing the bottom surface of the bottomed sleeve 36 from the outside to deform it and displacing the bearing member 37.

  Next, the operation of the control valve for the variable capacity compressor will be described. FIG. 2 is an enlarged view of part A in FIG. (A) shows a state where the shaft 17 is operating integrally with the plunger 33, and (B) shows a state where the shaft 17 is relatively displaced with respect to the plunger 33.

  In the variable displacement compressor control valve 1 shown in FIG. 1, the spring load of the spring 46 that applies the biasing force in the valve opening direction to the plunger 33 is the spring load of the spring 47 that applies the biasing force in the valve closing direction. Is set larger than. For this reason, when the solenoid 3 is not energized, the valve element 18 is separated from the valve seat 16 and the valve portion is held in a fully opened state. At this time, the high-pressure refrigerant having the discharge pressure Pd introduced from the discharge chamber of the variable capacity compressor to the port 11 passes through the valve portion in the fully open state and flows from the port 13 to the crank chamber. Therefore, the variable displacement compressor performs an operation with the minimum discharge capacity because the crank pressure Pc is close to the discharge pressure Pd.

  On the other hand, when the automotive air conditioner is activated or when the cooling load is maximum, the current value supplied to the solenoid 3 is maximum, and the plunger 33 is attracted to the core 32 with the maximum suction force. At this time, since the spring load of the spring 45 is set so large that it is not contracted by the inertial force accompanying the suction force, the shaft 17 is integrated with the plunger 33 until the valve body 18 is seated on the valve seat 16. It operates in the valve closing direction. In this process, as shown in FIG. 2A, the spring receiver 44 is in contact with the lower surface of the upper bottom portion of the plunger 33, and there is no relative displacement between the shaft 17 and the plunger 33.

  When the valve element 18 is seated on the valve seat 16, the plunger 33 operates in the valve closing direction as it is due to the inertial force, but the shaft 17 is moved in the axial direction by the valve element 18 being seated on the valve seat 16. Displacement is regulated. At this time, as shown in FIG. 2B, the spring receiver 44 is separated from the lower surface of the upper bottom portion of the plunger 33, and the shaft 17 is relatively displaced with respect to the plunger 33. As a result, the suction force applied to the plunger 33 is not directly transmitted to the shaft 17, and only the spring load by the spring 45 is applied. That is, the impact force when the valve body 18 is seated is relaxed by the spring 45 and becomes small.

  Even when the valve is closed, the solenoid is energized and controlled at a predetermined frequency (for example, 400 Hz), so that the plunger 33 microscopically vibrates at that frequency. For this reason, the relationship between the shaft 17 and the plunger 33 repeats the integral operation of FIG. 2A and the relative displacement of FIG. 2B, and the valve element 18 bounces against the valve seat 16. become. However, since the shaft 17 is relatively displaced with respect to the plunger 33 every time the valve body 18 is seated on the valve seat 16, the impact force when the valve body 18 is seated is relaxed and becomes small.

  When the valve is closed, the high-pressure refrigerant with the discharge pressure Pd introduced into the port 11 is blocked by the fully-closed valve portion, so that the variable capacity compressor has the crank pressure Pc close to the suction pressure Ps. Therefore, the operation with the maximum discharge capacity is performed.

  Here, when the current value supplied to the solenoid 3 is set to a predetermined value, as shown in FIG. 2A, the spring receiver 44 and the plunger 33 come into contact with each other, and the shaft 17 and the plunger 33 are integrated. Operate. At this time, the valve body 18 applies the spring load of the spring 46 that urges the plunger 33 in the valve opening direction, the spring load of the spring 47 that urges the plunger 33 in the valve closing direction, and the plunger 33 in the valve closing direction. The valve lift position balances the load of the energizing solenoid 3, the force due to the discharge pressure Pd received by the valve body 18 in the valve opening direction, and the force due to the suction pressure Ps received by the valve body 18 in the valve closing direction. And stop.

  In this balanced state, if the rotational speed of the variable capacity compressor is increased by increasing the rotational speed of the engine and the discharge capacity is increased, the discharge pressure Pd is increased and the suction pressure Ps is decreased. (Pd−Ps) increases, and a force in the valve opening direction acts on the valve body 18, and the valve body 18 is further lifted to increase the flow rate of the refrigerant flowing from the discharge chamber to the crank chamber. As a result, the crank pressure Pc increases, and the variable displacement compressor operates in a direction to decrease the discharge capacity, and is controlled so that the differential pressure (Pd−Ps) becomes a predetermined value set by the solenoid 3. . When the engine speed decreases, the reverse operation is performed, and the variable capacity compressor is controlled so that the differential pressure (Pd−Ps) becomes a predetermined value set by the solenoid 3.

  As described above, the variable displacement compressor control valve 1 according to the present embodiment is provided with the support structure including the spring receivers 43 and 44 and the spring 45 in the plunger 33. This support structure supports the shaft 17 so that it can be displaced relative to the plunger 33 when the valve body 18 is seated on the valve seat 16. For this reason, the impact force at the time of seating of the valve body 18 by a solenoid force can be relieved.

  Further, since the valve body 18 is provided integrally with the shaft 17, the configuration of the driving force transmission portion to the valve body 18 is simplified. In addition, since the number of parts is reduced, the manufacturing cost can be reduced.

  In this embodiment, the force in the valve opening direction on the shaft 17 (including the valve body 18) is generated only by the differential pressure (Pd−Ps) applied to the shaft 17, A configuration in which the valve is opened automatically may be employed. FIG. 3 is a cross-sectional view showing a configuration of a control valve for a variable capacity compressor according to a modification of the present embodiment. In the figure, the same components as those in FIG. 1 are denoted by the same reference numerals.

  As shown in FIG. 3, a retaining ring 111 is fitted into a portion of the shaft 117 in the pressure chamber 25, and a spring receiver 112 is provided so that upward movement is restricted by the retaining ring 111. A conical spring 113 that urges the shaft 117 in the valve opening direction may be interposed between the body 10 and the body 10. As a result, the valve portion can be quickly opened when the solenoid 3 is not energized.

  Further, in the present embodiment, the configuration in which the spring receiver 44 is provided so as to be operable independently of the shaft 17 is shown, but the spring receiver 44 may be fixed to the shaft 17. As a result, the shaft 17 operates in the valve opening direction together with the spring receiver 44 that operates integrally with the plunger 33 when the solenoid 3 is not energized, and the valve portion can be quickly opened.

Alternatively, the same action can be obtained by integrally forming a spring receiving portion having the same function as the spring receiving 44 on the shaft 17.
[Second Embodiment]
Next, a second embodiment of the present invention will be described. The control valve for a variable capacity compressor according to the present embodiment is substantially the same as the configuration shown in the first embodiment, except that the structure of the shaft including the valve body and the support portion thereof are different. For this reason, about the component similar to the said 1st Embodiment, the same code | symbol is attached | subjected etc., and the description is abbreviate | omitted suitably. FIG. 4 is a cross-sectional view showing a configuration of a control valve for a variable capacity compressor according to the second embodiment. In the figure, the strainer 12 shown in FIG. 1 is omitted.

In the variable displacement compressor control valve 201, shaft support portions of the shaft 217 are provided at both ends of the valve body 218.
That is, in the valve component 202, the shaft end 222 is connected to the valve body 218 of the shaft 217 via the constricted portion 221 having a smaller diameter. The shaft end portion 222 is pivotally supported on an upper portion of the valve seat forming member 214 (corresponding to a “shaft support portion” and a “guide portion”), and a spring receiver 223 is fitted to the upper end portion thereof. An adjustment member 224 is press-fitted into the upper end opening of the body 210, and a spring 225 that biases the shaft 217 in the valve opening direction is interposed between the adjustment member 224 and the spring receiver 223.

  A communication hole 226 that allows the port 11 and the internal valve hole 215 to communicate with each other is formed on a side portion of the valve seat forming member 214. The communication hole 226 and the refrigerant passage provided around the constricted portion 221 of the valve hole 215 constitute a communication passage that connects the discharge chamber and the crank chamber. The refrigerant having the discharge pressure Pd introduced from the port 11 is decompressed by the valve portion through this communication path, and is led to the port 13 as the refrigerant having the crank pressure Pc.

  On the other hand, the plunger 233 of the solenoid 203 constitutes a guide portion 231 in which the lower end of the main body 241 slightly expands in diameter and slides on the inner peripheral surface of the bottomed sleeve 236. The spring receiver 243 press-fitted in the vicinity of the lower end opening of the plunger 233 also constitutes a shaft support portion that supports the small diameter portion 238 of the shaft 217. For this reason, the bottomed sleeve 236 is not provided with the bearing member 37 shown in FIG. Therefore, the bottomed sleeve 236 is more compact than the bottomed sleeve 36 shown in FIG. 1, and the entire variable displacement compressor control valve 201 is downsized.

Note that the operation of the variable displacement compressor control valve of the present embodiment is the same as that of the first embodiment, and a description thereof will be omitted.
Also in the variable displacement compressor control valve 201 of the present embodiment, a support structure including spring receivers 243 and 44 and a spring 45 is provided in the plunger 233. For this reason, the impact force at the time of seating of the valve body 218 by a solenoid force can be relieved.

[Third Embodiment]
Next, a third embodiment of the present invention will be described. The control valve for a variable capacity compressor according to the present embodiment is the same as the configuration shown in the second embodiment, except that the structure of the shaft support is slightly different. For this reason, the same components as those in the second embodiment are denoted by the same reference numerals, and the description thereof is omitted as appropriate. FIG. 5 is a cross-sectional view illustrating a configuration of a control valve for a variable capacity compressor according to a third embodiment.

In the variable displacement compressor control valve 301, one of the shaft support portions of the shaft 317 is constituted by the end portion of the bottomed sleeve 336.
That is, the bottomed sleeve 336 constituting the solenoid 303 protrudes downward from the center of the lower end portion thereof, and the tip of the small diameter portion 338 of the shaft 317 is slidably supported by the protruding portion 331. For this reason, the inner diameter of the spring receiver 343 press-fitted in the vicinity of the lower end opening of the plunger 333 is slightly larger than the small diameter portion 338. Even in such a configuration, since the bearing member 37 shown in FIG. 1 can be omitted, the cost can be reduced by reducing the number of parts.

  Also in the variable displacement compressor control valve 301 of the present embodiment, a support structure including spring receivers 343 and 44 and a spring 45 is provided in the plunger 333. For this reason, the impact force at the time of seating of the valve body 218 by a solenoid force can be relieved.

[Fourth Embodiment]
Next, a fourth embodiment of the present invention will be described. The control valve for a variable capacity compressor according to the present embodiment is the same as the configuration shown in the first embodiment except that a support structure for supporting the shaft so as to be relatively displaceable with respect to the plunger is not provided. It is. For this reason, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted as appropriate. FIG. 6 is a cross-sectional view showing a configuration of a control valve for a variable capacity compressor according to a fourth embodiment.

  That is, in the variable displacement compressor control valve 401, the plunger 433 constituting the solenoid 403 is not provided with the spring receivers 43 and 44 and the spring 45 shown in FIG. Plunger 433 is press-fitted and fixed. An opening 442 whose diameter is increased downward is provided at the center of the lower end of the plunger 433, and a spring 447 is interposed between the plunger 433 and the bearing member 37 so as to be inserted into the opening 442. ing.

  According to the variable displacement compressor control valve 401 of the present embodiment, since the valve body 18 is provided integrally with the shaft 17, the configuration of the driving force transmission portion to the valve body 18 is simplified. In addition, since the number of parts is reduced, the manufacturing cost can be reduced.

It is sectional drawing which shows the structure of the control valve for variable capacity compressors which concerns on 1st Embodiment. It is the A section enlarged view of FIG. It is sectional drawing which shows the structure of the control valve for variable capacity compressors which concerns on a modification. It is sectional drawing which shows the structure of the control valve for variable capacity compressors which concerns on 2nd Embodiment. It is sectional drawing which shows the structure of the control valve for variable capacity compressors which concerns on 3rd Embodiment. It is sectional drawing which shows the structure of the control valve for variable capacity compressors which concerns on 4th Embodiment.

Explanation of symbols

1,201,301,401 Control valve for variable capacity compressor 2,202 Valve component 3,203,303,403 Solenoid 10,210 Body 11,13,22 Port 14,214 Valve seat forming member 15 Valve hole 16 Valve Seat 17, 117, 217, 317 Shaft 18, 218 Valve 19 Guide hole 32 Core 33, 233, 333, 433 Plunger 34 Electromagnetic coil 36, 236, 336 Bottomed sleeve 37 Bearing member 45, 46, 47, 113, 225 , 447 Spring 221 Constriction 331 Projection

Claims (14)

The refrigerant discharge capacity from the variable capacity compressor is changed by controlling the flow rate of refrigerant introduced from the discharge chamber into the crank chamber so that the differential pressure between the discharge pressure in the discharge chamber and the suction pressure in the suction chamber is maintained at a predetermined value. In a control valve for a variable capacity compressor,
A body having a refrigerant passage formed therein;
A valve body that opens and closes the valve hole, arranged so as to be in contact with and away from the crank chamber side, in a valve hole that forms a refrigerant passage for communicating the discharge chamber and the crank chamber;
A shaft that transmits axial force to the valve body;
A core fixed to the body; a plunger for inserting the shaft in an axial direction; a support structure for supporting the shaft so as to be relatively displaceable with respect to the plunger; and the energization between the core and the plunger. A solenoid having an electromagnetic coil that generates an attractive force acting in the valve closing direction of the valve body;
A control valve for a variable capacity compressor.   The control valve for a variable capacity compressor according to claim 1, wherein the support structure is provided inside the plunger and is configured to be displaced together with the plunger. The support structure is
Urging means for urging the shaft in the valve closing direction with respect to the plunger;
Restriction means for restricting the operating range of the biasing means;
The control valve for a variable capacity compressor according to claim 2, further comprising: The biasing means is arranged in the plunger, and one end thereof is fixed to the plunger, and comprises a spring that biases the shaft directly or indirectly on the other end side,
The restricting means comprises a locking portion provided on the plunger and locking the extension of the spring directly or indirectly;
The control valve for a variable capacity compressor according to claim 3.   Between the spring and the locking part, it is extrapolated to the shaft, one end side in the axial direction forms a contact surface that can contact and separate from the locking part, and the other end side is the other end side of the spring. 5. The control valve for a variable capacity compressor according to claim 4, further comprising a spring receiver supported by the valve.   6. The variable capacity according to claim 5, wherein a shaft support portion is provided in the plunger so as to be opposed to the spring receiver and to slidably support an end portion of the shaft opposite to the valve body. Control valve for compressor.   The control valve for a variable capacity compressor according to claim 6, wherein the spring is interposed between the shaft support portion and the spring support.   2. The control valve for a variable capacity compressor according to claim 1, wherein the valve body is integrally formed at a tip portion of the shaft.   9. The control valve for a variable capacity compressor according to claim 8, wherein the valve body is constituted by a tip portion of the shaft.   One end of the shaft is slidably supported by a guide portion provided on the body, and the other end is slidably supported by a shaft support provided on the opposite side of the solenoid from the valve body. The control valve for a variable capacity compressor according to claim 1, wherein the control valve is provided.   11. The control for a variable capacity compressor according to claim 10, wherein the shaft support portion is configured by an end portion of a sleeve arranged so as to be inserted between the core of the solenoid and the electromagnetic coil. valve. The shaft has a constricted portion in the vicinity of one end side that is pivotally supported by the guide portion, and constitutes a communication path that communicates the discharge chamber and the crank chamber between the constricted portion and the body,
The valve body is constituted by a downstream end portion of the constricted portion of the shaft;
The control valve for a variable capacity compressor according to claim 10. The refrigerant discharge capacity from the variable capacity compressor is changed by controlling the flow rate of refrigerant introduced from the discharge chamber into the crank chamber so that the differential pressure between the discharge pressure in the discharge chamber and the suction pressure in the suction chamber is maintained at a predetermined value. In a control valve for a variable capacity compressor,
A body having a refrigerant passage formed therein;
A valve body that opens and closes the valve hole, arranged so as to be in contact with and away from the crank chamber side, in a valve hole that forms a refrigerant passage for communicating the discharge chamber and the crank chamber;
A shaft integrally provided with the valve body;
A solenoid that applies a solenoid force corresponding to the differential pressure of the predetermined value to the shaft, and operates the valve body in an axial direction of the shaft;
A control valve for a variable capacity compressor. 14. The control valve for a variable capacity compressor according to claim 13, wherein the valve body is constituted by a tip portion of the shaft.

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