JP2018040385A - solenoid valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a solenoid valve that can achieve smooth operation of a valve element while preventing biting of foreign matters in a sliding part.SOLUTION: A solenoid valve of one embodiment comprises: a valve driving body 29 integrally provided with a valve element 30 and slidably supported in a guide hole 27; a solenoid 3 capable of imparting driving force in a valve closing direction to the valve driving body 29; an annular seal accommodating portion 100 formed in the valve driving body 29; and a seal ring 102 that is fitted in the seal accommodating portion 100 and abuts against a seal surface 104 formed on a body 5 to regulate a flow of fluid through a gap between the guide hole 27 and the valve driving body 29. The seal surface 104 has a shape or an arrangement in which, while the valve driving body 29 is displaced in the drive direction of the solenoid 3 within a predetermined control range including steady control, the seal ring 102 applies elastic reaction force in the counter drive direction of the solenoid 3 to the valve driving body 29.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a solenoid valve, and more particularly to a seal structure for a sliding portion.

  An automobile air conditioner is generally configured by arranging a compressor, a condenser, an evaporator, and the like in a refrigerant circulation passage. Various control valves are provided for switching the refrigerant circulation passage and adjusting the refrigerant flow rate. As such a control valve, an electromagnetic valve using a solenoid as an actuator is widely employed (see, for example, Patent Document 1).

  Such an electromagnetic valve is provided with a plurality of ports for introducing or deriving the refrigerant into the body. A valve hole is provided to communicate the introduction port and the outlet port, and the movable member is slidably supported by a guide hole coaxial with the valve hole. A valve body is provided integrally with the movable member. The movable member is driven in the axial direction by a solenoid, and the valve body contacts and separates from the valve hole to open and close the valve portion. The refrigerant introduced from the introduction port is guided in one direction along the outer periphery of the movable member and passes through the valve hole.

  On the other hand, since the introduction port has a relatively high pressure, a differential pressure is also generated before and after the guide hole. For this reason, a seal ring such as an O-ring is interposed between the two so that the refrigerant does not flow through the gap between the movable member and the guide hole due to the differential pressure. This prevents or suppresses foreign matter contained in the refrigerant from entering and interposing the gap and preventing the sliding of the movable member and the smooth operation of the valve element.

JP 2011-43102 A

  By the way, the sealing performance of the seal ring is ensured by deformation utilizing its flexibility. That is, the seal is ensured by compressing the seal ring in the radial direction and contacting both the movable member and the guide hole with sufficient pressure. However, since the contact force in the radial direction between the seal ring and the seal surface (the surface on which the seal ring abuts) is linked to the sliding resistance of the movable member, it may be a factor that hinders smooth operation of the valve element. In particular, there is a possibility of causing a delay in the operation of the valve body when no forcing force is applied, such as when the solenoid is turned off. Such a problem may occur not only in an air conditioner but also in electromagnetic valves for various purposes.

  The present invention has been made in view of such problems, and an object of the present invention is to provide an electromagnetic valve capable of realizing smooth operation of the valve body while preventing foreign matter from getting caught in the sliding portion. It is in.

  One embodiment of the present invention is a solenoid valve. This solenoid valve is provided coaxially with the introduction port for introducing the fluid, the extraction port for extracting the fluid, the valve hole provided in the passage connecting the introduction port and the extraction port, and the valve hole. A valve body that is open and close to the valve hole and opens and closes the valve portion, a valve drive body that is integrally provided and slidably supported in the guide hole, and a valve drive A solenoid capable of applying a driving force in a valve opening direction or a valve closing direction to the body, an annular seal housing portion formed on one of the body and the valve drive body, and a body and a valve fitted into the seal housing portion A seal ring that regulates the flow of fluid through the gap between the guide hole and the valve drive body by contacting the seal surface formed on the other side of the drive body. The seal surface has a shape or an arrangement in which the seal ring acts on the valve drive body in the predetermined control range including the steady control while the valve drive body is displaced in the solenoid drive direction. Have.

  According to this aspect, the seal ring disposed between the seal housing portion and the seal surface can regulate the flow of fluid through the gap between the valve drive body and the guide hole, and prevent foreign matter from being caught in the gap. Or it can be suppressed. As a result, a stable operation of the valve drive body and thus the valve body can be ensured. Further, due to the shape or arrangement of the seal surface, the elastic reaction force in the counter drive direction by the seal ring acts on the valve drive body while the valve drive body is displaced in the solenoid drive direction within a predetermined control range including steady control. To do. For this reason, when the solenoid is turned off, the valve body can be quickly moved to the off position.

  According to the control valve of the present invention, the smooth operation of the valve body can be realized while preventing the foreign matter from getting into the sliding portion.

It is sectional drawing which shows the structure of the control valve which concerns on 1st Embodiment. It is a partial expanded sectional view corresponding to the upper half part of FIG. It is a figure showing operation | movement of a control valve. It is a partial expanded sectional view showing the structure of a seal | sticker accommodating part and its periphery. It is sectional drawing which shows the structure of the principal part of the control valve which concerns on 2nd Embodiment. It is sectional drawing which shows the structure of the principal part of the control valve which concerns on 3rd Embodiment. It is sectional drawing which shows the structure of the principal part of the control valve which concerns on 4th Embodiment. It is sectional drawing which shows the structure of the principal part of the control valve which concerns on 5th Embodiment. It is sectional drawing which shows the structure of the principal part of the control valve which concerns on 6th Embodiment.

  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 based on the illustrated state. In the following embodiments and modifications thereof, substantially the same components are denoted by the same reference numerals, and the description thereof may be omitted as appropriate.

[First Embodiment]
FIG. 1 is a cross-sectional view illustrating a configuration of a control valve according to the first embodiment.
The control valve 1 controls the discharge capacity of a variable capacity compressor (simply referred to as “compressor”) installed in the refrigeration cycle of the automotive air conditioner. This compressor compresses the refrigerant flowing through the refrigeration cycle and discharges it as a high-temperature and high-pressure gas refrigerant. The gas refrigerant is condensed in a condenser (external heat exchanger) and further adiabatically expanded by an expansion device to become a low temperature / low pressure mist refrigerant. The low-temperature and low-pressure refrigerant evaporates in the evaporator, and the passenger compartment air is cooled by the latent heat of vaporization. The refrigerant evaporated in the evaporator is returned again to the compressor and circulates in the refrigeration cycle. The compressor has a rotating shaft that is rotationally driven by an automobile engine, and a compression piston is connected to a swing plate attached to the rotating shaft. The refrigerant discharge amount is adjusted by changing the stroke of the piston by changing the angle of the swing plate. The control valve 1 controls the angle of the swing plate, and thus the discharge capacity of the compressor, by controlling the flow rate of refrigerant introduced from the discharge chamber of the compressor into the control chamber and the flow rate of refrigerant introduced from the control chamber to the suction chamber. Change. In addition, although the control chamber of this embodiment consists of a crank chamber, in the modification, the pressure chamber separately provided in the crank chamber or the crank chamber may be sufficient.

  The control valve 1 is configured so that the suction pressure Ps (corresponding to “sensed pressure”) of the compressor is maintained at a set pressure, the refrigerant flow rate introduced from the discharge chamber into the control chamber, and the refrigerant led out from the control chamber to the suction chamber. It is configured as a so-called Ps sensing valve that controls the flow rate. The control valve 1 is an “electromagnetic valve” configured by assembling a valve body 2 and a solenoid 3 in the axial direction. The valve body 2 includes a main valve 7 that controls the flow rate of refrigerant flowing from the discharge chamber to the control chamber, and a sub-valve 8 that controls the flow rate of refrigerant flowing from the control chamber to the suction chamber. The main valve 7 functions as a “first valve”, and the auxiliary valve 8 functions as a “second valve”. The opening of the main valve 7 is adjusted during operation of the compressor, and a part of the discharged refrigerant is introduced into the control chamber. The auxiliary valve 8 is fully opened when the compressor is started, and functions as a so-called bleed valve that allows the refrigerant in the control chamber to escape to the suction chamber. The solenoid 3 generates a driving force in the valve closing direction of the main valve 7 and the valve opening direction of the sub valve 8 according to the supply current value. The valve body 2 has a stepped cylindrical body 5, and the main valve 7, the subvalve 8, and the power element 6 are accommodated in the body 5. The power element 6 functions as a “pressure sensing part” and generates a counter force to the solenoid 3 according to the magnitude of the suction pressure Ps.

  The body 5 is provided with ports 12, 14, and 16 from the upper end side. The port 12 functions as a “suction chamber communication port” and communicates with the suction chamber of the compressor. The port 14 functions as a “control room communication port” and communicates with the control room of the compressor. The port 16 functions as a “discharge chamber communication port” and communicates with the discharge chamber of the compressor. An end member 13 is fixed so as to close the upper end opening of the body 5.

  In the body 5, a main passage that communicates the port 16 and the port 14 and a sub passage that communicates the port 14 and the port 12 are formed. The main passage functions as a “first passage”, and the sub-passage functions as a “second passage”. A main valve 7 is provided in the main passage, and a sub valve 8 is provided in the sub passage. That is, the control valve 1 has a configuration in which the power element 6, the auxiliary valve 8, the main valve 7, and the solenoid 3 are sequentially arranged from one end side. A main valve hole 20 and a main valve seat 22 are provided in the main passage. A sub valve hole 32 and a sub valve seat 34 are provided in the sub passage. The main valve hole 20 functions as a “first valve hole”, and the sub valve hole 32 functions as a “second valve hole”.

  The port 12 allows the working chamber 23 defined in the upper part of the body 5 to communicate with the suction chamber. The power element 6 is disposed in the working chamber 23. The port 16 introduces a refrigerant having a discharge pressure Pd from the discharge chamber. A main valve chamber 24 is provided between the port 16 and the main valve hole 20, and the main valve 7 is disposed. The main valve chamber 24 functions as an “intermediate pressure chamber”. A main valve seat 22 is formed at the lower end opening of the main valve hole 20. The port 14 guides the refrigerant having the control pressure Pc through the main valve 7 to the control chamber during the steady operation of the compressor, while the refrigerant having the control pressure Pc discharged from the control chamber at the start of the compressor. Is introduced. A sub valve chamber 26 is provided between the port 14 and the main valve hole 20, and the sub valve 8 is disposed. The port 12 guides the refrigerant having the suction pressure Ps through the auxiliary valve 8 to the suction chamber when the compressor is started.

  Cylindrical filter members 15 and 17 are attached to the ports 14 and 16, respectively. The filter members 15 and 17 include a mesh for suppressing entry of foreign matter into the body 5. When the main valve 7 is opened, the filter member 17 suppresses entry of foreign matter into the port 16, and when the auxiliary valve 8 is opened, the filter member 15 suppresses entry of foreign matter into the port 14.

  A guide hole 25 is provided between the sub valve chamber 26 and the working chamber 23. A guide hole 27 is provided in the lower part of the body 5 (on the side opposite to the main valve hole 20 of the main valve chamber 24). A stepped cylindrical valve driver 29 (movable member) is slidably inserted into the guide hole 27.

  The upper part of the valve drive body 29 is reduced in diameter to form a partition portion 33 that partitions the inside and the outside while penetrating the main valve hole 20. A step formed in the valve driver 29 is a main valve body 30 that opens and closes the main valve 7 by being attached to and detached from the main valve seat 22. The main valve body 30 is opened / closed by attaching / detaching the main valve body 30 to / from the main valve seat 22 from the main valve chamber 24 side. The upper portion of the partition portion 33 is increased in a tapered shape toward the upper side, and a sub-valve seat 34 is formed at the upper end opening. The auxiliary valve seat 34 functions as a movable valve seat that is displaced together with the valve driver 29. In the present embodiment, the valve driver 29 and the main valve element 30 are distinguished from each other, but the valve driver 29 may be regarded as a “main valve element”.

  On the other hand, a cylindrical sub-valve element 36 is slidably inserted into the guide hole 25. An internal passage of the auxiliary valve body 36 is an auxiliary valve hole 32. This internal passage allows the auxiliary valve chamber 26 and the working chamber 23 to communicate with each other by opening the auxiliary valve 8. The auxiliary valve body 36 and the auxiliary valve seat 34 are disposed to face each other in the axial direction. The auxiliary valve body 36 opens and closes the auxiliary valve 8 by being attached to and detached from the auxiliary valve seat 34 in the auxiliary valve chamber 26.

  Further, an elongated operating rod 38 is provided along the axis of the body 5. The upper end portion of the operating rod 38 passes through the sub valve body 36 and is connected to the power element 6 so as to be operatively connectable. The lower end portion of the operating rod 38 is connected to a plunger 50 (described later) of the solenoid 3. The upper half of the actuating rod 38 passes through the valve driver 29 and the upper part thereof is reduced in diameter. The auxiliary valve body 36 is extrapolated and fixed to the reduced diameter portion. The tip of the reduced diameter portion is connected to the power element 6.

  A ring-shaped spring receiver 40 is fitted and supported at an intermediate portion in the axial direction of the operating rod 38. A spring 42 (functioning as an “urging member”) that urges the valve driver 29 in the valve closing direction of the main valve 7 and the subvalve 8 is interposed between the valve driver 29 and the spring receiver 40. ing. When the main valve 7 is controlled, the valve driver 29 and the spring receiver 40 are stretched by the elastic force of the spring 42, and the main valve body 30 and the operating rod 38 operate integrally.

  The power element 6 includes a bellows 45 that is displaced by sensing the suction pressure Ps, and generates a force that opposes the solenoid force by the displacement of the bellows 45. This counter force is also transmitted to the main valve body 30 via the actuating rod 38 and the auxiliary valve body 36. When the auxiliary valve body 36 is seated on the auxiliary valve seat 34 and the auxiliary valve 8 is closed, the relief of the refrigerant from the control chamber to the suction chamber is shut off. Further, when the auxiliary valve body 36 is separated from the auxiliary valve seat 34 and opens the auxiliary valve 8, the relief of the refrigerant from the control chamber to the suction chamber is allowed.

  On the other hand, the solenoid 3 includes a stepped cylindrical core 46, a bottomed cylindrical sleeve 48 assembled so as to seal the lower end opening of the core 46, and the sleeve 46 accommodated in the axial direction of the core 46. A stepped cylindrical plunger 50 disposed opposite to the core 46, a cylindrical bobbin 52 extrapolated to the core 46 and the sleeve 48, an electromagnetic coil 54 wound around the bobbin 52 and generating a magnetic circuit by energization, A cylindrical case 56 provided to cover the electromagnetic coil 54 from the outside, an end member 58 provided to seal the lower end opening of the case 56, and embedded in the end member 58 below the bobbin 52. A collar 60 made of a magnetic material is provided.

  The valve body 2 and the solenoid 3 are fixed by press-fitting the lower end of the body 5 into the upper end opening of the core 46. A working chamber 28 is formed between the body 5 and the core 46. On the other hand, the operating rod 38 is inserted so as to penetrate the center of the core 46 in the axial direction. The working chamber 28 communicates with the working chamber 23 through the internal passages of the valve drive body 29 and the sub-valve body 36. For this reason, the suction pressure Ps of the working chamber 23 is introduced into the working chamber 28. The suction pressure Ps is also guided to the inside of the sleeve 48 through the communication passage 62 formed by the gap between the operating rod 38 and the core 46.

  Between the core 46 and the plunger 50, a spring 44 (functioning as a “biasing member”) that biases them in a direction to separate them from each other is interposed. The spring 44 functions as a so-called off spring that fully opens the main valve 7 when the solenoid 3 is off. The operating rod 38 is coaxially connected to each of the auxiliary valve body 36 and the plunger 50. The upper part of the operating rod 38 is press-fitted into the sub-valve body 36, and the lower end part is press-fitted into the upper part of the plunger 50. The actuating rod 38, the auxiliary valve body 36 and the plunger 50 constitute a “movable body” that is displaced integrally with the valve drive body 29 when the main valve 7 is controlled.

  The operating rod 38 appropriately transmits a solenoid force, which is a suction force between the core 46 and the plunger 50, to the main valve body 30 and the sub valve body 36. On the other hand, the actuating rod 38 is loaded with a driving force (also referred to as “pressure-sensitive driving force”) due to the expansion / contraction operation of the power element 6 so as to oppose the solenoid force. That is, in the control state of the main valve 7, the force adjusted by the solenoid force and the pressure-sensitive driving force acts on the main valve body 30 to appropriately control the opening degree of the main valve 7. When the compressor is started, the operating rod 38 is displaced relative to the body 5 against the biasing force of the spring 44 according to the magnitude of the solenoid force, and after closing the main valve 7, the sub-valve body 36 is pushed up. The auxiliary valve 8 is opened. Even during the control of the main valve 7, when the suction pressure Ps is considerably increased, the operating rod 38 is displaced relative to the body 5 against the urging force of the bellows 45 and the main valve 7 is closed. The auxiliary valve body 36 is pushed up to open the auxiliary valve 8. As a result, the bleed function is exhibited.

  The sleeve 48 is made of a nonmagnetic material. A side surface of the plunger 50 is provided with a communication groove 66 parallel to the axis, and a lower portion of the plunger 50 is provided with a communication hole 68 for communication between the inside and the outside. With such a configuration, the suction pressure Ps is guided to the back pressure chamber 70 through the gap between the plunger 50 and the sleeve 48 even when the plunger 50 is located at the bottom dead center as shown in the figure.

  A pair of connection terminals 72 connected to the electromagnetic coil 54 extend from the bobbin 52, and extend through the end members 58 to the outside. For convenience of explanation, only one of the pair is displayed in the figure. The end member 58 is attached so as to seal the entire structure in the solenoid 3 included in the case 56 from below. The end member 58 is formed by molding (injection molding) of a resin material having corrosion resistance, and the resin material is also interposed in the gap between the case 56 and the electromagnetic coil 54. In this way, the resin material interposes the resin material in the gap between the case 56 and the electromagnetic coil 54, so that heat generated in the electromagnetic coil 54 can be easily transferred to the case 56, and the heat dissipation performance is enhanced. The end portion of the connection terminal 72 is drawn out from the end member 58 and connected to an external power source (not shown).

FIG. 2 is a partially enlarged cross-sectional view corresponding to the upper half of FIG.
A labyrinth seal 74 composed of a plurality of annular grooves for suppressing the flow of the refrigerant is provided on the sliding surface of the valve driver 29 with the guide hole 27. The labyrinth seal 74 is located in the vicinity of the main valve chamber 24 on the relatively high pressure side.

  A seal housing portion 100 is provided on a sliding surface with the guide hole 27 in the lower part of the valve driver 29, and an O-ring 102 (functioning as a “seal ring”) is fitted therein. The seal housing portion 100 is located in the vicinity of the working chamber 28 that is relatively on the low pressure side. The seal housing portion 100 is formed of an annular concave groove formed on the outer peripheral surface of the valve driver 29. A surface of the guide hole 27 facing the seal housing portion 100 is a seal surface 104 with which the seal housing portion 100 abuts. That is, the seal surface 104 has an inclined shape that is inclined with respect to the axis of the guide hole 27, and specifically has a tapered shape that increases in diameter downward. The O-ring 102 is made of an elastic body (for example, rubber), seals the gap between the valve drive body 29 and the guide hole 27, and regulates refrigerant leakage from the main valve chamber 24 to the working chamber 28. Details of the sealing structure by the O-ring 102 will be described later.

  A stepped portion 106 (a recessed portion having a predetermined depth) is provided around the outer peripheral surface of the portion of the valve drive body 29 located in the main valve chamber 24 for receiving foreign matter that has entered from the port 16. As a result, even if foreign matter is contained in the refrigerant introduced through the port 16, the foreign matter can be once received by the stepped portion 106 of the valve driver 29 and then guided to the main valve hole 20. Thereby, the foreign matter flowing along the wall surface of the valve driver 29 is less likely to directly collide with the main valve seat 22, and the occurrence of erosion in the main valve seat 22 can be prevented or suppressed.

  The lower half portion of the valve drive body 29 has an enlarged inner diameter, and the spring 42 is disposed so as to be accommodated in the enlarged diameter portion. With such a configuration, the contact point between the spring 42 and the valve drive body 29 is located near the center of the sliding portion in the guide hole 27, so that the valve drive body 29 is spring-loaded in a so-called manner. 42 is stably supported. As a result, it is possible to prevent or suppress the occurrence of hysteresis due to wobbling when the main valve body 30 is driven to open and close.

  The sub-valve element 36 has an insertion hole 43 that passes through the center in the axial direction. The upper part of the operating rod 38 extends through the insertion hole 43 to the power element 6. The sub-valve body 36 is positioned with respect to the operating rod 38 by being locked to a stepped portion 79 that is the base end of the reduced diameter portion of the operating rod 38. A plurality of internal passages 39 for communicating the internal passage 37 of the valve driver 29 and the working chamber 23 are formed around the insertion hole 43 in the sub valve body 36. The internal passage 39 extends in parallel with the insertion hole 43 and penetrates the auxiliary valve body 36. A labyrinth seal 75 is provided on a sliding surface of the auxiliary valve body 36 with the guide hole 25. In the illustrated state in which the sub-valve body 36 is seated on the sub-valve seat 34, the actuating rod 38 is arranged such that the upper surface of the spring receiver 40 is separated from the lower surface of the valve driver 29 by at least a predetermined interval L. The position of the stepped portion 79 is set. The predetermined interval L functions as so-called “play”.

  When the solenoid force is increased, the operation rod 38 can be displaced relative to the main valve body 30 (valve drive body 29) to push up the sub valve body 36. Thereby, the auxiliary valve body 36 and the auxiliary valve seat 34 can be separated and the auxiliary valve 8 can be opened. Further, the solenoid force can be directly transmitted to the main valve body 30 in a state where the spring receiver 40 and the valve drive body 29 are engaged (contacted), and the main valve body 30 is closed by the main valve 7. It can be pressed with great force in the direction. This configuration functions as an unlocking mechanism for releasing the operation of the main valve element 30 when the operation of the main valve element 30 is locked due to the foreign matter biting into the sliding portion between the valve driver 29 and the guide hole 27.

  The main valve chamber 24 is provided coaxially with the body 5 and is configured as a pressure chamber having a larger diameter than the main valve hole 20. For this reason, a relatively large space is formed between the main valve 7 and the port 16, and a sufficient flow rate of the refrigerant flowing through the main passage can be ensured when the main valve 7 is opened. Similarly, the auxiliary valve chamber 26 is also provided coaxially with the body 5 and is configured as a pressure chamber having a larger diameter than the main valve hole 20. For this reason, a relatively large space is also formed between the auxiliary valve 8 and the port 14. As shown in the figure, the attachment / detachment portion between the upper end of the valve drive body 29 and the lower end of the sub-valve body 36 is set to be located at the center of the sub-valve chamber 26. That is, the movable range of the main valve body 30 is set so that the sub valve seat 34 is always located in the sub valve chamber 26, and the sub valve 8 is opened and closed in the sub valve chamber 26. For this reason, when the auxiliary valve 8 is opened, a sufficient flow rate of the refrigerant flowing through the auxiliary passage can be secured. That is, the bleed function can be effectively exhibited.

  The power element 6 is configured such that the upper end opening of the bellows 45 is closed by a first stopper 82 and the lower end opening is closed by a second stopper 84. The bellows 45 functions as a “pressure sensitive member”. The first stopper 82 is integrally formed with the end member 13. The second stopper 84 is formed by pressing a metal material into a bottomed cylindrical shape, and has a flange portion 86 extending outward in the radial direction at the lower end opening. In the bellows 45, the upper end portion of the bellows-like main body is air-tightly welded to the lower surface of the end member 13, and the lower end opening of the main body is air-tightly welded to the upper surface of the flange portion 86. The inside of the bellows 45 is a sealed reference pressure chamber S. A spring 88 that urges the bellows 45 in the extending direction is interposed between the end member 13 and the flange portion 86 inside the bellows 45. The reference pressure chamber S is in a vacuum state in this embodiment.

  The end member 13 is a fixed end of the power element 6. By adjusting the amount of press-fitting of the end member 13 into the body 5, the set load of the power element 6 (set load of the spring 88) can be adjusted. The central portion of the first stopper 82 extends downward toward the inside of the bellows 45, the central portion of the second stopper 84 extends upward toward the inside of the bellows 45, and these are the bellows 45. The shaft core is formed. The bellows 45 expands or contracts in the axial direction (the opening and closing directions of the main valve and the subvalve) according to the differential pressure between the suction pressure Ps of the working chamber 23 and the reference pressure of the reference pressure chamber S. As the differential pressure decreases and the bellows 45 extends, a driving force in the valve opening direction of the main valve 7 and the valve closing direction of the auxiliary valve 8 is applied to the valve driver 29. Even if the differential pressure increases, if the bellows 45 contracts by a predetermined amount, the second stopper 84 comes into contact with the first stopper 82 and is locked, so that the contraction is restricted.

  In the present embodiment, the effective pressure receiving diameter A of the bellows 45, the effective pressure receiving diameter B (seal part diameter) of the main valve body 30 in the main valve 7, and the sliding part diameter C (seal part diameter) of the valve drive body 29. And the sliding part diameter D (seal part diameter) of the sub-valve element 36 are set equal. The term “equal” as used herein may be considered to include not only completely equal concepts but also almost equal (substantially equal) concepts. Therefore, in a state where the valve drive body 29 and the power element 6 are operatively connected, the influence of the discharge pressure Pd, the control pressure Pc, and the suction pressure Ps acting on the combined body of the main valve body 30 and the sub-valve body 36 is affected. Canceled. As a result, in the control state of the main valve 7, the main valve body 30 opens and closes based on the suction pressure Ps that the power element 6 receives in the working chamber 23. That is, the control valve 1 functions as a so-called Ps sensing valve.

  In this embodiment, in this way, the diameters B, C, and D are made equal, and the internal passage of the valve body (the main valve body 30 and the sub-valve body 36) is vertically penetrated, thereby acting on the valve body ( The influence of Pd, Pc, Ps) can be canceled. That is, the pressure before and after (up and down in the drawing) of the combined body of the auxiliary valve body 36, the valve driving body 29, the operating rod 38 and the plunger 50 can be made the same pressure (suction pressure Ps), thereby realizing the pressure cancellation. Is done. Thereby, the diameter of each valve body can also be set, without depending on the diameter of the bellows 45, and a design freedom is high. In the modification, the diameters B, C, and D may be made equal while the effective pressure receiving diameter A may be different from these. That is, the effective pressure receiving diameter A of the bellows 45 may be smaller than the diameters B, C, and D, or larger than the diameters B, C, and D.

  On the other hand, in the present embodiment, the seal portion diameter E in the sub valve 8 of the sub valve body 36 is made smaller than the effective pressure receiving diameter B in the main valve 7 of the main valve body 30, and the difference between the control pressure Pc and the suction pressure Ps. The pressure (Pc−Ps) acts on the valve driver 29 in the valve opening direction of the auxiliary valve 8. Such a pressure receiving structure and the biasing structure by the spring 42 realize a “differential pressure valve opening mechanism” that opens the auxiliary valve 8 when the differential pressure (Pc−Ps) becomes equal to or larger than the set differential pressure ΔPset. ing.

Next, the operation of the control valve will be described.
In the present embodiment, a PWM (Pulse Width Modulation) system is adopted for energization control to the solenoid 3. This PWM control is performed by supplying a pulse current of about 400 Hz set to a predetermined duty ratio, and is executed by a control unit (not shown). The control unit includes a PWM output unit that outputs a pulse signal having a designated duty ratio. However, since the configuration itself is employed, detailed description thereof is omitted.

  FIG. 3 is a diagram illustrating the operation of the control valve. FIG. 2 which has already been described shows the minimum capacity operation state of the control valve. FIG. 3 shows a state when the bleed function is operated when the control valve is started. The following description is based on FIG. 1 and with reference to FIGS. 2 and 3 as appropriate.

  When the solenoid 3 is not energized (off) in the control valve 1, that is, when the automobile air conditioner is not operating, no suction force acts between the core 46 and the plunger 50. On the other hand, the urging force of the spring 44 is transmitted to the valve driving body 29 via the plunger 50, the operating rod 38 and the auxiliary valve body 36. As a result, as shown in FIG. 2, the main valve body 30 is separated from the main valve seat 22 and the main valve 7 is fully opened. At this time, the sub-valve 8 maintains the closed state.

  On the other hand, when an activation current is supplied to the electromagnetic coil 54 of the solenoid 3 at the time of activation of the automotive air conditioner, as shown in FIG. 3, the valve opening pressure (“sub-valve opening” is determined by the supply current value. If it is higher than the pressure, the auxiliary valve 8 is opened. That is, the solenoid force overcomes the urging force of the spring 42, and the auxiliary valve body 36 is pushed up integrally. As a result, the auxiliary valve body 36 is separated from the auxiliary valve seat 34, the auxiliary valve 8 is opened, and the bleed function is effectively exhibited. During this operation, the main valve body 30 is pushed up by the urging force of the spring 42 and is seated on the main valve seat 22. As a result, the main valve 7 is closed. That is, after the main valve 7 is closed and the introduction of the refrigerant discharged into the control chamber is restricted, the sub valve 8 is opened to quickly relieve the refrigerant in the control chamber to the suction chamber. As a result, the compressor can be started quickly. Note that the “sub-valve opening pressure” changes accordingly when a set pressure Pset, which will be described later, is changed according to the environment in which the vehicle is placed.

  When the current value supplied to the solenoid 3 is within the control current value range of the main valve 7, the opening of the main valve 7 is autonomously adjusted so that the suction pressure Ps becomes the set pressure Pset set by the supply current value. The In the control state of the main valve 7, the sub valve body 36 is seated on the sub valve seat 34, and the sub valve 8 is maintained in the closed state. On the other hand, since the suction pressure Ps is relatively low, the bellows 45 extends, and the main valve body 30 operates to adjust the opening degree of the main valve 7. At this time, the main valve body 30 is in a valve lift position in which the force in the valve opening direction by the spring 44, the solenoid force in the valve closing direction, and the force in the valve opening direction by the power element 6 according to the suction pressure Ps are balanced. Stop.

  For example, when the refrigeration load increases and the suction pressure Ps becomes higher than the set pressure Pset, the bellows 45 is reduced, so that the main valve body 30 is displaced relatively upward (in the valve closing direction). As a result, the valve opening of the main valve 7 is reduced, and the compressor operates to increase the discharge capacity. As a result, the suction pressure Ps changes in a decreasing direction. Conversely, when the refrigeration load is reduced and the suction pressure Ps is lower than the set pressure Pset, the bellows 45 extends. As a result, the power element 6 urges the main valve body 30 in the valve opening direction to increase the valve opening of the main valve 7, and the compressor operates to reduce the discharge capacity. As a result, the suction pressure Ps is maintained at the set pressure Pset. When the suction pressure Ps is considerably higher than the set pressure Pset, it is assumed that the main valve 7 is closed and the sub-valve 8 is opened depending on the height of the suction pressure Ps. However, since there is a pressure range (dead zone) from when the main valve 7 is closed to when the sub valve 8 is opened, a situation such as the main valve 7 and the sub valve 8 being opened and closed unstable is prevented.

  When such steady control is being performed, the load on the engine increases, and when it is desired to reduce the load on the air conditioner, the solenoid 3 in the control valve 1 is switched from on to off. As a result, no suction force acts between the core 46 and the plunger 50, so that the main valve body 30 is separated from the main valve seat 22 by the biasing force of the spring 44, and the main valve 7 is fully opened. At this time, the auxiliary valve body 36 is basically seated on the auxiliary valve seat 34, so that the auxiliary valve 8 is closed. As a result, the refrigerant having the discharge pressure Pd introduced from the discharge chamber of the compressor into the port 16 passes through the fully opened main valve 7 and flows from the port 14 to the control chamber. Therefore, the control pressure Pc is increased and the compressor is operated at the minimum capacity.

  However, when the differential pressure (Pc−Ps) becomes equal to or higher than the set differential pressure ΔPset when switching to the minimum capacity operation, the differential pressure valve opening mechanism is activated (not shown). That is, the force due to the differential pressure (Pc−Ps) overcomes the urging force of the spring 42 and pushes down the valve driver 29 to open the auxiliary valve 8. For this reason, the rapid increase of the control pressure Pc can be prevented or suppressed. As the set differential pressure ΔPset, a value exceeding the maximum value of the differential pressure (Pc−Ps) that can act on the valve driver 29 during stable control of the main valve 7 is set. For this reason, the sub-valve 8 is basically not opened during the control of the main valve 7. The opening of the auxiliary valve 8 by the differential pressure opening mechanism is realized when the main valve 7 is in the opened state. This is different from the forced opening mechanism of the auxiliary valve 8 by the solenoid 3 shown in FIG. Different.

Next, the detail of the seal structure in a sliding part is demonstrated.
FIG. 4 is a partially enlarged cross-sectional view showing the seal housing portion and the surrounding structure. FIG. 4A is an enlarged view of a portion b in FIG. 2 and shows a non-excitation state in which the solenoid 3 is turned off. FIG. 4B is an enlarged view of part b of FIG. 3 and shows an excited state (bleed state) in which the solenoid 3 is turned on.

  As shown in FIG. 4A, the seal housing portion 100 includes a front side wall 100a located on the front side (upper side) in the driving direction by the solenoid 3 and a rear side wall 100b located on the rear side (lower side) in the driving direction. It has an opposing concave cross section. The seal accommodating portion 100 is configured such that the width in the axial direction (the interval between the front side wall 100a and the rear side wall 100b) is slightly larger than the width (diameter of the cross section) of the O ring 102 in consideration of the assembly of the O ring 102 and the like. Has been. Further, a gap S <b> 2 is formed between the bottom surface 100 c of the seal housing part 100 and the O-ring 102. With such a configuration, even if the O-ring 102 is compressed in the axial direction due to the differential pressure across the front and the width in the radial direction is increased, is the O-ring 102 subject to reaction force from the bottom surface 100c of the seal housing portion 100? , At least it is difficult to accept.

  On the other hand, the seal surface 104 in the guide hole 27 is a tapered surface that increases its inner diameter toward the lower side (counter-drive direction of the solenoid 3) and decreases the inner diameter toward the upper side (the driving direction of the solenoid 3). 4A and 4B, the O-ring 102 always has a size and shape that protrudes from the seal housing portion 100 toward the seal surface 104 in the driving range of the valve driver 29. . That is, the seal surface 104 increases the tightening allowance 102a of the O-ring 102 as the valve drive body 29 is displaced in the drive direction of the solenoid 3 (FIG. 4B), and the valve drive body 29 in the counter drive direction of the solenoid 3. 4 has a shape in which the tightening allowance 102a of the O-ring 102 is made smaller as the displacement of the O-ring 102 becomes larger (FIG. 4A). The O-ring 102 abuts on the seal surface 104 so as to be slidable. With such a configuration, the elastic reaction force in the counter-drive direction by the O-ring 102 acts on the valve driver 29 while the valve driver 29 is displaced in the driving direction of the solenoid 3. The elastic reaction force is set to be equal to or less than the maximum suction force of the solenoid force, and the driving of the main valve body 30 by the solenoid 3 is ensured.

  As described above, in the present embodiment, the O-ring 102 disposed between the seal housing portion 100 and the seal surface 104 can ensure the sealing performance in the gap between the valve driver 29 and the guide hole 27. Biting of foreign matter can be prevented or suppressed. As a result, stable operation of the valve drive body 29 and the main valve body 30 can be ensured. Further, due to the shape of the seal surface 104, the elastic reaction force in the counter drive direction by the O-ring 102 acts on the valve driver 29 while the valve driver 29 is displaced in the driving direction of the solenoid 3 in the steady control range. For this reason, when the solenoid 3 is turned off, the main valve body 30 can be quickly moved to the off position (the fully opened position of the main valve 7).

  In the present embodiment, the shape and size of the seal surface 104, the seal housing portion 100, and the O-ring 102 are increased so that the elastic reaction force by the O-ring 102 increases as the valve driver 29 is displaced in the driving direction of the solenoid 3. Well, the arrangement is adjusted. In the modified example, even when the valve driving body 29 is displaced in the driving direction or the counter driving direction of the solenoid 3, the elastic reaction force by the O-ring 102 is substantially constant, and the hysteresis accompanying the operation of the valve driving body 29 is constant. You may adjust them as you like.

[Second Embodiment]
FIG. 5 is a cross-sectional view showing the configuration of the main part of the control valve according to the second embodiment. FIG. 5A shows a non-excitation state in which the solenoid 3 is off, and FIG. 5B shows an excitation state (bleed state) in which the solenoid 3 is on. The upper part of each figure is a partially enlarged cross-sectional view corresponding to part a of FIG. 2, and the lower part is an enlarged view of part b. Below, it demonstrates centering on difference with 1st Embodiment.

  As shown in FIG. 5A, in the present embodiment, the seal surface 104 is formed in the middle portion of the guide hole 227 in the axial direction. That is, a concave step 204 is provided at the center in the axial direction of the guide hole 227, and a tapered surface is formed so as to be inclined downward from the step 204 so as to decrease the inner diameter. On the other hand, a seal housing portion 100 is formed on the surface of the valve driver 229 that faces the seal surface 104.

  5A and 5B, the O-ring 102 always has a size and shape that protrudes from the seal housing portion 100 toward the seal surface 104 in the driving range of the valve driver 229. . The seal surface 104 increases the tightening allowance 102a of the O-ring 102 as the valve driving body 229 is displaced in the driving direction of the solenoid 3 (FIG. 5B), and the valve driving body 229 is displaced in the counter driving direction of the solenoid 3. The smaller the tightening allowance 102a of the O-ring 102 is, the more the shape becomes (FIG. 5A). With such a configuration, the elastic reaction force in the counter driving direction by the O-ring 102 acts on the valve driving body 229 while the valve driving body 229 is displaced in the driving direction in the steady control range.

  With the configuration as described above, the present embodiment can provide the same effects as those of the first embodiment. Further, since the O-ring 102 is arranged on the high pressure side close to the main valve chamber 24, it becomes easier to prevent foreign matter from entering the gap between the valve driver 229 and the guide hole 227.

[Third Embodiment]
FIG. 6 is a cross-sectional view showing the configuration of the main part of the control valve according to the third embodiment. 6A shows a non-excited state in which the solenoid 3 is off, and FIG. 6B shows an excited state (bleed state) in which the solenoid 3 is turned on. The upper part of each figure is a partially enlarged cross-sectional view corresponding to part a of FIG. 2, and the lower part is an enlarged view of part b. Below, it demonstrates centering on the difference with 1st, 2nd embodiment.

  As shown in FIG. 6A, in this embodiment, the seal housing portion 100 is formed in the guide hole 327, and the seal surface 104 is formed in the valve driver 329. That is, the seal accommodating portion 100 is formed along the inner peripheral surface of the lower portion of the guide hole 327. On the other hand, a seal surface 104 is formed on a surface of the valve driver 329 facing the seal housing portion 100. A step 204 is provided on the outer peripheral surface of the lower portion of the valve driver 329, and a tapered surface that is inclined so as to increase the outer diameter downward from the step 204 is formed.

  6A and 6B, the O-ring 102 always has a size and shape that protrudes from the seal housing portion 100 toward the seal surface 104 within the driving range of the valve driver 329. . The seal surface 104 increases the tightening allowance 102a of the O-ring 102 as the valve drive body 329 is displaced in the drive direction of the solenoid 3 (FIG. 6B), and the valve drive body 329 is displaced in the reverse drive direction of the solenoid 3. The smaller the tightening margin 102a of the O-ring 102 is, the more the shape becomes (FIG. 6A). With such a configuration, the elastic reaction force in the counter driving direction by the O-ring 102 acts on the valve driving body 329 while the valve driving body 329 is displaced in the driving direction in the steady control range.

  With the configuration as described above, the present embodiment can provide the same effects as those of the first embodiment.

[Fourth Embodiment]
FIG. 7 is a cross-sectional view showing the configuration of the main part of the control valve according to the fourth embodiment. FIG. 7A shows a non-excitation state in which the solenoid 3 is off, and FIG. 7B shows an excitation state (bleed state) in which the solenoid 3 is on. The upper part of each figure is a partially enlarged cross-sectional view corresponding to part a of FIG. 2, and the lower part is an enlarged view of part b. Below, it demonstrates centering on difference with 1st Embodiment.

  As shown in FIG. 7A, in this embodiment, the shape of the seal housing portion 400 is slightly different from that of the seal housing portion 100 of the first embodiment. That is, in the first embodiment, the height of the front side wall 100a (the height from the bottom surface 100c) and the height of the rear side wall 100b are made equal, but in this embodiment, the height of the rear side wall 400b is higher. It is larger by Δr than the height of the side wall 100a.

  7A and 7B, the O-ring 102 always has a size and shape that protrudes from the seal housing portion 400 toward the seal surface 104 in the driving range of the valve driver 429. . The seal surface 104 increases the tightening allowance 102a of the O-ring 102 as the valve drive body 429 is displaced in the drive direction of the solenoid 3 (FIG. 7B), and the valve drive body 429 is displaced in the reverse drive direction of the solenoid 3. The smaller the tightening margin 102a of the O-ring 102 is, the more the shape becomes (FIG. 7A). With such a configuration, the elastic reaction force in the counter driving direction by the O-ring 102 acts on the valve driving body 429 while the valve driving body 429 is displaced in the driving direction in the steady control range.

  With the configuration as described above, the present embodiment can provide the same effects as those of the first embodiment. Further, by increasing the height of the rear side wall 400b, the gap S3 between the valve driver 429 and the guide hole 27 formed below (rearward) the O-ring 102 can be reduced. For this reason, it is possible to avoid a situation in which a part of the O-ring 102 that has received the elastic reaction force bites into the rear gap.

[Fifth Embodiment]
FIG. 8 is a cross-sectional view showing the configuration of the main part of the control valve according to the fifth embodiment. FIG. 8A shows a non-excitation state in which the solenoid 3 is turned off, and FIG. 8B shows an excitation state (bleed state) in which the solenoid 3 is turned on. The upper part of each figure is a partially enlarged cross-sectional view corresponding to part a of FIG. 2, and the lower part is an enlarged view of part b. Below, it demonstrates centering on difference with 1st Embodiment.

  As shown in FIG. 8A, in the present embodiment, the seal ring 502 is made of an elastic body (for example, rubber) having a shape such that a sheet-like ring bulges to one side. The seal ring 502 has a shape in which the first flat portion 510 and the second flat portion 512 are connected via a tapered portion 514. The taper portion 514 has a tapered cross section that increases in diameter upward. A lower end portion of the valve driving body 529 extends below the guide hole 527, and an annular seal housing portion 500 including a concave groove is formed along the outer peripheral surface of the extending portion.

  A radially inner half portion of the first flat portion 510 is fitted in the seal accommodating portion 500 in an airtight manner. On the other hand, a seal surface 504 is formed on the bottom surface of the body 505, and the upper surface of the second flat portion 512 is in contact therewith. As shown in FIGS. 8A and 8B, the seal ring 502 is crushed in the axial direction as the valve drive body 529 is displaced in the drive direction of the solenoid 3 in the drive range of the valve drive body 529. The elastic reaction force in the counter driving direction increases. During this time, since the seal ring 502 is in close contact with the seal surface 504, the sealing performance in the guide hole 527 is ensured. When the solenoid 3 is turned off, the main valve body 30 can be quickly moved to the off position (the fully opened position of the main valve 7) by the elastic reaction force.

[Sixth Embodiment]
FIG. 9 is a cross-sectional view showing the configuration of the main part of the control valve according to the sixth embodiment. FIG. 9A shows a non-excitation state in which the solenoid 3 is off, and FIG. 9B shows an excitation state (bleed state) in which the solenoid 3 is on. The upper part of each figure is a partially enlarged cross-sectional view corresponding to part a of FIG. 2, and the lower part is an enlarged view of part b. Below, it demonstrates centering on difference with 1st Embodiment.

  As shown in FIG. 9A, in this embodiment, the seal ring 602 is made of an elastic body (for example, rubber) having a V-shaped cross section. The seal ring 602 has a shape in which the concave side of the V-shaped cross section (or U-shaped cross section) is radially inward. The seal ring 602 includes a base portion 610 parallel to the axis, a first elastic portion 612 extending obliquely upward from the upper end of the base portion 610, and obliquely downward from the lower end of the base portion 610 toward the inside. And a second elastic portion 614 extending.

  On the other hand, an annular seal housing portion 600 is formed on the bottom surface of the body 605 and houses the first elastic portion 612. The valve driver 629 extends to the lower side of the guide hole 627, and a flange portion 630 extending outward in the radial direction is provided at a lower end portion thereof. A seal surface 604 is formed on the upper surface of the flange portion 630, and the second elastic portion 614 is in contact therewith. That is, the seal ring 602 is interposed between the seal housing portion 600 and the seal surface 604.

  As shown in FIGS. 9A and 9B, the seal ring 602 has an axial direction (first elastic portion 612) as the valve drive body 629 is displaced in the drive direction of the solenoid 3 in the drive range of the valve drive body 629. And a direction in which the second elastic portion 614 approaches), and an elastic reaction force in the opposite driving direction increases. During this time, since the seal ring 602 is in close contact with the seal surface 604, the sealing performance in the guide hole 627 is ensured. When the solenoid 3 is turned off, the main valve body 30 can be quickly moved to the off position (the fully opened position of the main valve 7) by the elastic reaction force.

  In this embodiment, since the concave side of the V-shaped cross section of the seal ring 602 is inward in the radial direction, the differential pressure across the guide hole 627 acts in the direction in which the seal ring 602 extends. For this reason, when the solenoid 3 is turned off, the differential pressure before and after promotes the valve opening operation of the main valve body 30 and makes it easy to fully open the main valve 7. Conversely, when the main valve body 30 is operated in the valve closing direction, the differential pressure before and after becomes a resistance force.

  In a modification, the concave side of the V-shaped cross section of the seal ring 602 may be outward in the radial direction. In that case, the differential pressure across the guide hole 627 acts in a direction to reduce the seal ring 602. For this reason, operation | movement to the valve closing direction of the main valve body 30 becomes easy compared with this embodiment. That is, since the valve opening characteristic of the main valve 7 can be changed depending on which side in the radial direction the concave side of the V-shaped cross section is directed, either one may be selected according to the control characteristic required for the control valve 1. .

  The preferred embodiments of the present invention have been described above. However, the present invention is not limited to the specific embodiments, and various modifications can be made within the scope of the technical idea of the present invention. Absent.

  In the said 1st-4th embodiment, the example which makes the sealing surface 104 taper shape was shown. In the modification, the seal surface may include a curved surface (R shape). In addition, other inclined shapes such as a shape that is inclined as a whole by providing a step having a continuous seal surface can also be adopted.

  Moreover, in the said 1st-4th embodiment, the cross-sectional circular O-ring was illustrated as a seal ring. In a modified example, a seal ring having a polygonal cross section or other shapes may be employed.

  In the above embodiment, the normally open type electromagnetic valve in which the main valve 7 is fully opened when the solenoid 3 is off is illustrated. In the modified example, the above-described seal structure may be applied to a normally closed electromagnetic valve in which the valve portion (main valve) is closed when the solenoid is off. In this case, the solenoid gives a driving force in the valve opening direction to the valve driver.

  In the above embodiment, the shape or arrangement of the seal surface is set so that the seal ring always applies an elastic reaction force to the valve drive body in the counter-drive direction of the solenoid while the valve drive body is displaced in the solenoid drive direction. did. In a modification, it is good also as a structure from which the elastic reaction force to the counter drive direction of the solenoid by a seal ring does not act on a valve drive body substantially in the state where a solenoid is OFF. In the case of a normally open type electromagnetic valve, the elastic reaction force may not act on the valve drive body in the fully open state where the solenoid is off or in the vicinity thereof. For example, the sealing surface may be parallel to the axis of the guide hole at the fully open position of the valve portion or in the vicinity thereof, and the elastic reaction force may not act on the valve driver in the valve opening direction. Further, in the case of a normally closed electromagnetic valve, the elastic reaction force may not act on the valve drive body in the closed state where the solenoid is off or in the vicinity thereof. For example, the seal surface may be parallel to the axis of the guide hole at the valve closing position of the valve portion or in the vicinity thereof, and the elastic reaction force may not act on the valve driver in the valve closing direction. In other words, the seal surface exerts an elastic reaction force in the anti-driving direction of the solenoid on the valve driving body while the valve driving body is displaced in the driving direction of the solenoid in a predetermined control range including at least steady control. What is necessary is just to have the shape or arrangement | positioning to act.

  In the said embodiment, the control valve for variable capacity compressors which makes a working fluid a refrigerant | coolant was illustrated. In the modification, the above-described seal structure may be applied to a solenoid valve for other uses.

  In the above embodiment, the main control is the so-called inlet control that controls the flow rate of the refrigerant flowing from the discharge chamber to the control chamber. However, the main control is the so-called vent control that controls the flow rate of the refrigerant flowing from the control chamber to the suction chamber. It is good also as a structure. Or it is good also as a structure which controls both insertion control and extraction control appropriately.

  In the above embodiment, a so-called Ps sensing valve that operates by directly sensing the suction pressure Ps is exemplified as the control valve. In a modified example, a so-called Pc sensing valve that operates by sensing the control pressure Pc as the sensed pressure may be used.

  In the above-described embodiment, the spring is exemplified as the biasing member (elastic body) with respect to the springs 42, 44 and the like, but it goes without saying that an elastic material such as rubber or resin may be adopted.

  In addition, this invention is not limited to the said embodiment and modification, A component can be deform | transformed and embodied in the range which does not deviate from a summary. Various inventions may be formed by appropriately combining a plurality of constituent elements disclosed in the above embodiments and modifications. Moreover, you may delete some components from all the components shown by the said embodiment and modification.

1 Control valve, 3 Solenoid, 5 Body, 6 Power element, 7 Main valve, 8 Sub valve, 12 port, 14 port, 16 port, 20 Main valve hole, 24 Main valve chamber, 27 Guide hole, 28 Working chamber, 29 Valve drive body, 30 Main valve body, 32 Sub valve hole, 36 Sub valve body, 38 Acting rod, 44 Spring, 74 Labyrinth seal, 100 Seal housing part, 100a Front side wall, 100b Rear side wall, 100c Bottom surface, 102 O-ring, 102a Tightening margin, 104 seal surface, 204 step, 227 guide hole, 229 valve drive body, 327 guide hole, 329 valve drive body, 400 seal housing portion, 400b rear side wall, 429 valve drive body, 500 seal housing portion, 502 seal Ring, 504 Sealing surface, 505 Body, 527 Guide hole, 529 Valve driver, 600 Lumpur accommodation unit, 602 seal ring 604 sealing surface, 605 body, 627 guide hole, 629 valve driving body, 630 flanges.

Claims (8)

An introduction port for introducing a fluid; a derivation port for deriving a fluid; a valve hole provided in a passage connecting the introduction port and the derivation port; and a guide provided coaxially with the valve hole A body having a hole;
A valve body that opens and closes the valve portion in contact with and away from the valve hole;
A valve drive body provided integrally with the valve body and slidably supported in the guide hole;
A solenoid capable of applying a driving force in a valve opening direction or a valve closing direction to the valve driver;
An annular seal housing portion formed on one of the body and the valve driver;
The fluid flow through the gap between the guide hole and the valve drive body is regulated by fitting into the seal housing portion and contacting the seal surface formed on the other of the body and the valve drive body. A seal ring;
With
The seal surface applies an elastic reaction force to the valve drive body in the anti-drive direction of the solenoid while the valve drive body is displaced in the drive direction of the solenoid in a predetermined control range including steady control. A solenoid valve having a shape or an arrangement to be acted upon. The seal housing portion is formed on one of an inner peripheral surface of the guide hole through which the valve driver is inserted and an outer peripheral surface of the valve driver through which the guide hole is inserted,
The electromagnetic valve according to claim 1, wherein the seal surface is formed on the other of the inner peripheral surface of the guide hole and the outer peripheral surface of the valve driving body. The sealing surface increases the tightening margin of the seal ring as the valve driving body is displaced in the driving direction of the solenoid, and tightens the sealing ring as the valve driving body is displaced in the non-driving direction of the solenoid. Has a shape to reduce,
The solenoid valve according to claim 2, wherein the seal ring is slidably contacted with the seal surface.   The electromagnetic valve according to claim 2 or 3, wherein the sealing surface has an inclined shape inclined with respect to an axis of the guide hole.   The said seal ring has a magnitude | size and a shape which protrude toward the said seal surface from the said seal accommodating part always in the drive range of the said valve drive body, The Claim 2 characterized by the above-mentioned. solenoid valve. The seal housing portion is provided on an outer peripheral surface of the valve driver, and has a concave cross section in which a front side wall and a rear side wall in a driving direction of the solenoid face each other.
The solenoid valve according to claim 2, wherein a height of the rear side wall is larger than a height of the front side wall. The valve hole and the guide hole communicate with each other in an axial direction through an intermediate pressure chamber;
The solenoid valve according to claim 1, wherein the introduction port communicates with the intermediate pressure chamber. It is configured as a control valve that changes the discharge capacity of the variable capacity compressor that compresses the refrigerant introduced into the suction chamber and discharges it from the discharge chamber by adjusting the flow rate of the refrigerant introduced from the discharge chamber into the control chamber,
The body has a discharge chamber communication port that communicates with the discharge chamber as the introduction port, a control chamber communication port that communicates with the control chamber as the lead-out port, and a suction chamber communication port that communicates with the suction chamber. The electromagnetic valve according to claim 7.

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