KR20170056447A - Solenoid valve - Google Patents

Abstract

The present invention relates to a solenoid-operated valve obtained by press-fitting a body into a solenoid enabling the miniaturization of the body with a simple method and securing the fine operation of the valve body. A control valve (1) is formed by assembling the valve body (2) and the solenoid (3) in a direction of an axial line. The solenoid (3) includes a ring-shaped connection unit (100) capable of receiving an end of the valve body (2). The valve body (2) includes a cylindrical body (5) having a valve hole (20) and a guide hole (27) coaxially formed and a valve driving body (29) supported by a guide unit (106) demarcating the guide hole (27) to be able to slide. A press-fitting unit (104) formed in an end of the body (5) is press-fitted into the ring-shaped connection unit (100). The body (5) includes a part where the press-fitting unit (104) and the guide unit (106) are overlapped in a radial direction at least in a part in the direction of the axial line and a groove (102) for forming a space in a radial direction between the press-fitting unit (104) and the guide unit (106). The shape of the press-fitting unit (104) is symmetrical about the axial line of the body (5).

Description

SOLENOID VALVE

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a solenoid valve, and more particularly to a solenoid valve constituted by assembling a valve body and a solenoid by press fitting.

A control valve for controlling the flow of the working fluid is used for a device that performs control using a working fluid. For example, a variable capacity compressor (simply referred to as "compressor") capable of varying the discharge capacity of a refrigerant is used in an air conditioner for an automotive vehicle so that a constant cooling capacity is maintained regardless of the number of revolutions of the engine. In order to control the capacity of the compressor, a solenoid-operated solenoid valve is generally used.

Such a solenoid valve is constituted by assembling a valve body for accommodating a valve mechanism and a solenoid for driving the valve mechanism in the axial direction. The valve body includes a body having a valve hole along the axial line, and a valve body that opens and closes the valve portion in contact with the valve hole. The driving force of the solenoid is transmitted to the valve body through the transmitting member supported by the body so as to be slidable in the axial direction.

Although such a solenoid valve is constructed by assembling the body of the valve body and the solenoid in the axial direction, a simple press-fitting is often employed as a method of assembling the solenoid (see, for example, Patent Document 1). That is, by press-fitting the end portion of the body with respect to the ring-shaped connecting portion provided at the end portion of the solenoid, they are assembled into a coaxial shape.

Japanese Patent Application Laid-Open No. 2015-21605

However, it has been found by the inventor's examination that the following problems arise when the press-fitting is employed. That is, a slight deformation in the radial direction occurs at the end portion of the body along with the press-fitting. Therefore, when the press-in portion (press-fitted portion into the ring-shaped connection portion) of the body and the guide portion (the portion guiding the sliding of the transmission member) overlap in the radial direction, The sliding property of the transmitting member is deteriorated. As a result, the operability of the valve body is deteriorated. In order to avoid this, it is possible to consider a design in which the press-fitting portion and the guide portion are displaced in the axial direction (that is, a design in which they do not overlap in the radial direction), but the dimension in the axial direction of the body becomes large. It is also possible to consider a design in which a change in the inner diameter of the guide portion is predicted. However, considering the dimensional error and the like is also very troublesome.

An object of the present invention is to solve the above problems and to provide a solenoid valve in which a valve body is press-fitted into a solenoid, a valve body can be miniaturized by a simple method, do.

One embodiment of the present invention is a solenoid valve constituted by assembling a valve body and a solenoid in the axial direction. The solenoid includes a core fixed to the valve body; A plunger provided coaxially with the core; And a ring-shaped connection portion provided integrally with the core and capable of receiving an end portion of the valve body. The valve body includes: a tubular body having a valve hole and a guide hole coaxially formed; A valve body that opens and closes the valve portion by being in contact with the valve hole; And a valve driving body slidably supported by a guide portion defining a guide hole and capable of transmitting the driving force of the solenoid by the operation of the plunger to the valve body. The valve body and the solenoid are assembled by press-fitting the press-fitting portion provided at the end of the body into the ring-shaped connecting portion. The body is provided at least partially in the axial direction with a portion where the press-fitting portion and the guide portion overlap in the radial direction, and has a groove for forming a radial space between the press-fitting portion and the guide portion. The press-in portion has a shape symmetrical with respect to the axis of the body.

According to this configuration, since the press-fit portion and the guide portion have a portion overlapping in the radial direction, the solenoid valve can be made as small as possible. On the other hand, since the groove is formed between the press-in portion and the guide portion, even if the press-in portion is deformed radially inwardly when the end portion of the body is press-fitted into the ring-shaped connection portion, the space by the groove can absorb the deformation . Further, since the press-fitting portion has a shape symmetrical with respect to the axial line of the body, when the press-fitting portion is deformed in the radial direction, it is deformed almost uniformly around the axial line. As a result, the influence of the deformation of the press-in portion on the guide portion can be eliminated or at least suppressed. In other words, the diameter of the guide portion can be kept substantially equal to that before the press-fitting by a simple method of forming a groove in the body, and the sliding property of the valve body and the operability of the valve body can be satisfactorily maintained.

According to the present invention, in the solenoid valve obtained by press-fitting the valve body into the solenoid, it is possible to realize the miniaturization of the body by a simple method and secure the good operation of the valve body.

1 is a sectional view showing a configuration of a control valve according to an embodiment.
2 is a partially enlarged cross-sectional view corresponding to the upper half of Fig.
3 is a view showing the operation of the control valve.
4 is a view schematically showing a process of assembling the valve body and the solenoid.
5 is a partially enlarged view showing a main part of the assembly structure.

DESCRIPTION OF THE PREFERRED EMBODIMENTS 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, there is a case where the positional relationship of each structure is expressed up and down based on the illustrated state.

1 is a cross-sectional view showing a configuration of a control valve according to an embodiment.

The control valve 1 is configured as an electromagnetic valve for controlling a discharge capacity of a variable displacement compressor (simply referred to as "compressor") installed in a refrigeration cycle of an automotive air conditioner. This compressor compresses the refrigerant flowing in the refrigeration cycle and discharges it as gas refrigerant of high temperature and high pressure. The gas refrigerant is condensed by a condenser (external heat exchanger), and is expanded adiabatically by the expansion device to become a low-temperature and low-pressure mist refrigerant. The low-temperature and low-pressure refrigerant is evaporated by the evaporator, and the room air is cooled by the latent heat of evaporation. The refrigerant evaporated in the evaporator returns to the compressor again and circulates in the refrigeration cycle. The compressor includes a rotary shaft that is rotationally driven by an engine of an automobile, and a compression piston is connected to a swing plate mounted on the rotary shaft. By changing the angle of the swing plate to change the stroke of the piston, the discharge amount of the refrigerant is adjusted. The control valve 1 controls the flow rate of the refrigerant introduced into the control chamber from the discharge chamber of the compressor, thereby changing the angle of the swing plate, and thus the discharge capacity of the compressor. The control chamber of the present embodiment is formed of a crank chamber, but in the modified example, it may be a pressure chamber separately provided in the crank chamber or the crank chamber.

The control valve 1 is configured as a so-called Ps sensing valve for controlling the refrigerant flow rate introduced into the control chamber from the discharge chamber so as to maintain the suction pressure Ps (corresponding to the "sensing pressure" have. The control valve 1 is constituted by assembling the valve body 2 and the solenoid 3 in the axial direction. The valve body 2 includes a main valve for opening and closing a refrigerant passage for introducing a part of the discharge refrigerant into the control chamber during operation of the compressor and a sub valve serving as a so-called bleed valve for releasing the refrigerant in the control chamber into the suction chamber Valve. The solenoid (3) drives the main valve in the open / close direction to regulate the degree of opening thereof, thereby controlling the refrigerant flow rate introduced into the control chamber. The valve body 2 includes a cylindrical body 5 having a stepped portion, a main valve and a sub-valve provided in the body 5, and a power generating unit for generating a force against the solenoid force Element 6 and the like. The power element 6 functions as a "pressure reducing portion ".

The body 5 is provided with ports 12, 14, 16 from the upper end thereof. 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 chamber communication port " and communicates with the control chamber of the compressor. The port 16 functions as a "discharge chamber communication port " and communicates with the discharge chamber of the compressor. And an end member 13 is fixed so as to close the upper opening of the body 5. [ The valve body 2 and the solenoid 3 are fixed by pressing the lower end portion of the body 5 into the upper end portion of the solenoid 3.

A main passage which is an internal passage for communicating the port 16 and the port 14 and a sub passage which is an internal passage for communicating the port 14 and the port 12 are formed in the body 5. [ A main valve is provided in the main passage, and a sub valve is provided in the sub passage. That is, the control valve 1 has a configuration in which the power element 6, the sub-valve, the main valve, and the solenoid 3 are sequentially disposed from one end. The main passage is provided with a main valve hole (20) and a main valve seat (22). A sub-valve hole (32) and a sub-valve seat (34) are provided in the sub passage.

The port 12 communicates the suction chamber with the operation chamber 23 partitioned on the upper portion of the body 5. [ The power element 6 is disposed in the operation chamber 23. [ The port 16 introduces the refrigerant of the 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 a main valve is disposed. The port 14 draws the refrigerant having the control pressure Pc through the main valve toward the control chamber during the normal operation of the compressor toward the control room while discharging the refrigerant with the control pressure Pc discharged from the control room . A sub valve chamber (26) is provided between the port (14) and the main valve hole (20), and a sub valve is disposed. The port 12 introduces the refrigerant having the suction pressure Ps at the normal operation of the compressor while drawing the refrigerant having the suction pressure Ps through the sub valve toward the suction chamber at the start of the compressor.

That is, when the valve of the main valve is opened, the port 16 functions as an "introduction port" for introducing the refrigerant from the discharge chamber, while the "port 14" . On the other hand, when the valve of the sub-valve is opened, the port 14 functions as an "introduction port" for introducing the refrigerant from the control chamber, while the port 12 serves as the " . The port 14 functions as an "introduction / extraction port" for introducing or deriving the refrigerant in accordance with the opening and closing states of the main valve and the sub-valve.

In the ports 14 and 16, cylindrical filter members 15 and 17 are attached, respectively. The filter members (15, 17) include a mesh for suppressing intrusion of foreign matter into the interior of the body (5). When the valve of the main valve is opened, the filter member 17 regulates the entry of foreign matter into the port 16, and when the valve of the sub valve is opened, the filter member 15 regulates the entry of foreign matter into the port 14.

A main valve hole 20 is provided between the main valve chamber 24 and the sub valve chamber 26 and a main valve seat 22 is formed at the lower end opening end thereof. A guide hole (25) is provided between the port (14) and the operation chamber (23). A guide hole 27 is provided in a lower portion of the body 5 (opposite to the main valve hole 20 of the main valve chamber 24). A cylindrical valve drive body 29 having a stepped portion is slidably inserted into the guide hole 27 (a guide portion 106 described later for defining the guide hole 27).

The upper half of the valve driving body 29 is reduced in diameter and is formed into a dividing portion 33 for dividing the inside and outside while passing through the main valve hole 20. [ The stepped portion formed in the middle portion of the valve driving body 29 is a main valve body 30 which is detachably attached to the main valve seat 22 to open and close the main valve. The main valve body 30 is detachably attached to the main valve seat 22 on the side of the main valve chamber 24 to open and close the main valve so as to adjust the flow rate of the refrigerant flowing from the discharge chamber to the control chamber. The upper portion of the partition portion 33 is tapered upward and the sub valve seat 34 is formed at the upper end opening. The sub valve seat 34 functions as a movable valve seat which is displaced together with the valve actuator 29. In this embodiment, the valve actuating member 29 and the main valve member 30 are distinguished from each other, but the valve actuating member 29 may be regarded as the "main valve member ".

On the other hand, in the guide hole 25, a cylindrical sub valve body 36 is slidably inserted. And an internal passage of the sub valve body 36 serves as a sub valve hole 32. [ This internal passage allows the sub valve chamber 26 and the operation chamber 23 to communicate with each other by the valve opening of the sub valve. The sub valve body (36) and the sub valve seat (34) are arranged to face each other in the axial direction. And the sub valve is opened and closed by the sub valve body (36) being detached from the sub valve chamber (26) to the sub valve seat (34).

In addition, a long rod-like working rod 38 is provided along the axis of the body 5. [ The upper end of the operating rod 38 is operatively connected to the power element 6 through the sub-valve body 36. The lower end of the operating rod 38 is connected to the plunger 50 of the solenoid 3, which will be described later. The upper half of the operating rod 38 passes through the valve driving body 29, and the upper portion thereof is reduced in diameter. And the sub-valve body 36 is inserted outside and fixed by press fitting. And the distal end of the shaft portion is connected to the power element 6.

A ring-shaped spring bearing 40 is fitted and supported in the axial middle portion of the operating rod 38. A spring 42 (functioning as a "biasing member") for biasing the valve actuator 29 in the valve closing direction of the main valve and the sub valve is interposed between the valve actuator 29 and the spring bearing 40 have. The valve actuator 29 and the spring bearing 40 are pulled by the elastic force of the spring 42 so that the main valve body 30 and the operating rod 38 operate in unison .

The power element 6 includes a bellows 45 which senses a suction pressure Ps to be displaced and generates a force against the solenoid force due to the displacement of the bellows 45. [ This counter force is also transmitted to the main valve body 30 through the operation rod 38 and the sub-valve body 36. The relief of the refrigerant from the control chamber to the suction chamber is blocked by the sub valve member 36 being seated on the sub valve seat 34 and closing the sub valve. In addition, relief of the refrigerant from the control chamber to the suction chamber is allowed by opening the sub valve away from the sub valve seat 34 of the sub valve body 36. [

The solenoid 3 includes a cylindrical core 46 having a stepped portion and a cylindrical sleeve 48 having a bottom portion assembled to seal the lower end opening of the core 46. The solenoid 3 is accommodated in the sleeve 48, A cylindrical bobbin 52 inserted into the core 46 and the sleeve 48 and a bobbin 52 wound around the bobbin 52. The cylindrical bobbin 52 is wound around the bobbin 52, An electromagnetic coil 54 for generating a magnetic circuit by energization, a cylindrical case 56 for covering the electromagnetic coil 54 from the outside, an end member 58 for sealing the lower end opening of the case 56 And a collar 60 made of a magnetic material embedded in the end member 58 below the bobbin 52. [ Further, the core 46, the case 56 and the collar 60 constitute a yoke. The body 5, the end member 13, the core 46, the case 56, and the end member 58 form the body of the entire control valve 1. [

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

Between the core 46 and the plunger 50, there is interposed a spring 44 (functioning as a "biasing member") which biases the both in the direction of separating them from each other. The spring 44 functions as a so-called off spring for opening the valve of the main valve when the solenoid 3 is off. The operation rod 38 is connected to the sub valve body 36 and the plunger 50 in a coaxial manner. The upper portion of the operation rod 38 is press-fitted into the sub valve body 36 and the lower end portion thereof is press-fitted into the upper portion of the plunger 50. The actuating rod 38, the sub-valve body 36 and the plunger 50 constitute a "movable member " which is displaced integrally with the valve actuator 29 in the control of the main valve.

The operating rod 38 suitably transmits the solenoidal force which is the suction force of the core 46 and the plunger 50 to the main valve body 30 and the sub valve body 36. [ On the other hand, a driving force (also referred to as a "reduced driving force") caused by the expansion and contraction of the power element 6 is loaded on the working rod 38 so as to oppose the solenoid force. That is, in the control state of the main valve, a force adjusted by the solenoid force and the reduced pressure driving force acts on the main valve body 30 to properly control the opening of the main valve. When the compressor is started, the operation rod 38 is displaced relative to the body 5 against the urging force of the spring 44 in accordance with the magnitude of the solenoid force, and after the main valve is closed, So that the sub valve is opened. Even when the main valve is being controlled, when the suction pressure Ps becomes significantly high, the operating rod 38 is relatively displaced with respect to the body 5 against the biasing force of the bellows 45, The valve body 36 is pushed up to open the valve of the sub valve. Thereby exerting the bleed function.

Sleeve 48 is made of a non-magnetic material. On the side surface of the plunger 50, there is provided a communication groove 66 parallel to the axis, and a communication hole 68 communicating with the inside and the outside is provided at the lower portion of the plunger 50. With this arrangement, even when the plunger 50 is positioned at the bottom dead center as shown in the figure, the suction pressure Ps is delivered to the back pressure chamber 70 through the gap between the plunger 50 and the sleeve 48.

A pair of connection terminals 72 connected to the electromagnetic coil 54 extend from the bobbin 52 and protrude from the bobbin 52 and pass through the end member 58 and are drawn out to the outside. For convenience of explanation, only one of the pair is shown in Fig. The end member 58 is mounted so as to seal the entire structure in the solenoid 3 contained in the case 56 from below. The end member 58 is formed by molding (injection molding) a resin material having corrosion resistance, and the resin material is also filled in the gap between the case 56 and the electromagnetic coil 54. As described above, the resin material fills the gap between the case 56 and the electromagnetic coil 54 to easily transfer heat generated in the electromagnetic coil 54 to the case 56, thereby enhancing the heat radiation performance. The distal end portion of the connection terminal 72 is drawn out from the end member 58 and connected to an external power source (not shown).

2 is a partially enlarged cross-sectional view corresponding to the upper half of Fig.

A labyrinth seal 74 having a plurality of ring-shaped grooves for restricting the flow of refrigerant is provided on the sliding surface of the valve driving body 29 with the guide hole 27. The spring bearing 40 is a so-called E-ring, and is supported so as to fit into a ring-shaped groove formed in the intermediate portion of the operating rod 38, and is disposed in the operating chamber 28.

The lower half of the valve drive body 29 has an inner diameter enlarged, and a spring 42 is disposed so as to be accommodated in the enlarged diameter portion. With this configuration, the point of contact between the spring 42 and the valve driving body 29 is located closer to the main valve chamber 24 side than the center of the sliding portion in the guide hole 27, 29 are stably supported on the spring 42 in the form of a so-called balance toy. As a result, it is possible to prevent or suppress the occurrence of hysteresis due to vibration when the main valve body 30 is opened and closed.

The sub-valve body (36) has a through hole (43) that passes through the center in the axial direction. The upper portion of the operating rod 38 extends through the through hole 43 to the power element 6. [ The sub valve body 36 is engaged with the stepped portion 79, which is the base end of the reduced diameter portion of the operating rod 38, so that the sub valve body 36 is positioned with respect to the operating rod 38. A plurality of internal passages 39 for communicating the internal passageway 37 of the valve driving body 29 with the operation chamber 23 are formed around the insertion hole 43 in the sub valve body 36 have. The inner passage 39 extends parallel to the insertion hole 43 and penetrates the sub valve body 36. A labyrinth seal 75 is provided on the sliding surface of the sub valve body 36 and the guide hole 25. When the subordinate valve body 36 is seated on the sub valve seat 34, the upper surface of the spring bearing 40 is supported on the lower surface of the valve driving body 29 at least at a predetermined The position of the stepped portion 79 is set so as to be spaced apart from the gap L. The predetermined interval L functions as a so-called "clearance ".

When the solenoid force is increased, the operation rod 38 may be displaced relative to the main valve body 30 (the valve driving body 29) to push up the sub valve body 36. Thereby, the sub valve can be opened by separating the sub valve member 36 and the sub valve seat 34 from each other. The solenoid force can be directly transmitted to the main valve body 30 in a state in which the spring bearing 40 and the valve driving body 29 are engaged with each other and the main valve body 30 can be closed It is possible to pressurize it with a large force in the direction. This configuration functions as a lock release mechanism for releasing the operation of the main valve body 30 when the operation of the main valve body 30 is locked by the entry of foreign matter into the sliding portions of the valve driving body 29 and the guide hole 27. [

The main valve chamber 24 is formed as a pressure chamber which is coaxial with the body 5 and has a larger diameter than the main valve hole 20. [ Therefore, a relatively large space is formed between the main valve and the port 16, so that the flow rate of the refrigerant flowing through the main passage when the main valve is opened can be sufficiently secured. Similarly, the sub valve chamber 26 is also formed as a pressure chamber which is coaxial with the body 5 and has a diameter larger than that of the main valve hole 20. Therefore, a relatively large space is also formed between the sub valve and the port 14. As shown in the figure, the upper end of the valve driving body 29 and the lower end of the sub valve body 36 are set to be positioned at the middle portion 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 positioned in the sub valve chamber 26, and the sub valve is opened and closed in the sub valve chamber 26. Therefore, when the sub valve is opened, the flow rate of the refrigerant flowing through the sub passage can be sufficiently secured. That is, the bleed function can be effectively exerted.

The power element 6 is constituted such that the upper end opening of the bellows 45 is closed by the first stopper 82 and the lower end opening is closed by the second stopper 84. [ The bellows 45 functions as a " pressure reducing member ", and the first stopper 82 and the second stopper 84 each function as a "base member ". The first stopper 82 is supported coaxially by the end member 13. The stoppers 82 and 84 are formed into a cylindrical shape having a bottom by press-forming a metal material, and have flange portions 86 extending radially outwardly from the opening end portions thereof. The bellows 45 has a bellows-like main body and the upper end opening of the bellows 45 is hermetically welded to the flange portion 86 of the first stopper 82. The lower end opening of the bellows 45 is connected to the second stopper 84 Tightly welded to the flange portion 86 of the flange portion 86. The inside of the bellows 45 is a sealed reference pressure chamber S and a bellows 45 is provided between the first stopper 82 and the second stopper 84 on the inside of the bellows 45 in the extension direction And a spring 88 biased to the left. The reference pressure chamber S is in a vacuum state in the present embodiment.

The end member (13) is a fixed end of the power element (6). At the lower center of the end member 13, a support 89 protrudes downward. The supporting portion 89 is coaxially fitted to the first stopper 82 and supports the first stopper 82 from above. The upward displacement of the power element 6 is restricted by the engagement of the bottom of the first stopper 82 with the tip of the support 89. The set load of the power element 6 (the set load of the spring 88) can be adjusted by adjusting the amount of press fitting with respect to the body 5.

The central portion of the first stopper 82 extends downward toward the inside of the bellows 45 and the central portion of the second stopper 84 extends upward toward the inside of the bellows 45, . And the upper end of the operating rod 38 is engaged with the second stopper 84. [ The bellows 45 elongates or contracts in the axial direction (opening and closing directions of the main valve and the sub valve) in accordance with the differential pressure between the suction pressure Ps of the operating chamber 23 and the reference pressure of the reference pressure chamber S. [ The driving force in the valve opening direction is given to the main valve body 30 in accordance with the displacement of the bellows 45. [ If the bellows 45 is contracted by a predetermined amount, the second stopper 84 comes into contact with the first stopper 82 and is locked, so that the shrinkage is restricted.

In the present embodiment, the effective hydraulic diameter A of the bellows 45, the effective hydraulic pressure B (sealing portion diameter) in the main valve of the main valve body 30, and the sliding portion diameter C (the diameter of the sealing portion) and the sliding portion diameter D (the diameter of the sealing portion) of the sub-valve body 36 are set equal to each other. Here, "the same" as used herein may include almost the same concept as well as substantially the same (substantially the same) concept. The discharge pressure Pd acting on the combined body of the main valve body 30 and the sub valve body 36 and the control pressure Pc acting on the combined body of the main valve body 30 and the sub valve body 36 Pc and the suction pressure Ps are canceled. As a result, in the control state of the main valve, the main valve body 30 is opened and closed based on the suction pressure Ps received by the power element 6 in the operating chamber 23. As a result, That is, the control valve 1 functions as a so-called Ps sensing valve.

In this embodiment, the diameters B, C, and D are made the same, and the inner passages of the valve body (the main valve body 30 and the sub-valve body 36) The influence of the pressures (Pd, Pc, Ps) can be canceled. That is, the pressures in the front and rear (upper and lower in the figure) of the combined body of the sub valve body 36, the valve actuator 29, the operating rod 38 and the plunger 50 can be set to the same pressure (suction pressure Ps) Whereby the pressure cancellation is realized. Thereby, the diameter of each valve body can be set independently of the diameter of the bellows 45, and the degree of design freedom is high. Therefore, in the modified example, the diameters B, C, and D may be the same, and the effective hydraulic pressure diameter A may be different from these diameters. That is, the effective pressure-receiving diameter A of the bellows 45 may be smaller than the diameters B, C, and D, or may be larger than the diameters B, C,

On the other hand, in the present embodiment, the sealing portion diameter E in the sub-valve of the sub-valve body 36 becomes smaller than the sealing portion diameter effective hydraulic pressure B in the main valve of the main valve body 30, The differential pressure Pc-Ps between the suction pressure Pc and the suction pressure Ps acts on the valve actuator 29 in the valve opening direction of the sub valve. This hydraulic structure and the biased structure by the spring 42 realize a "differential pressure valve opening mechanism" for opening the sub-valve when the differential pressure Pc-Ps becomes equal to or greater than the set differential pressure DELTA Pset.

An O-ring 92 is fitted between the port 12 and the port 14 on the outer peripheral surface of the body 5 and an O-ring 94 is inserted between the port 14 and the port 16. [ An O-ring 96 is also fitted to the outer circumferential surface near the upper end of the core 46. The O-rings 92, 94 and 96 have a sealing function and regulate the leakage of the refrigerant when the control valve 1 is mounted in the mounting hole of the compressor.

Next, the operation of the control valve will be described.

In the present embodiment, PWM (Pulse Width Modulation) is employed for energizing control of the solenoid 3. The PWM control is performed by supplying a pulse current of about 400 Hz set at a predetermined duty ratio, and is performed by a control unit (not shown). This control unit has a PWM output unit for outputting a pulse signal of a specified duty ratio, but a known one is employed in the configuration itself, and thus a detailed description thereof will be omitted.

3 is a view showing the operation of the control valve. FIG. 2 already described shows the minimum capacity operation state of the control valve. Fig. 3 shows a state when the bleed function is operated at the time of starting the control valve. Hereinafter, a description will be made with reference to Fig. 1 and with reference to Figs. 2 and 3 as appropriate.

The suction force does not act between the core 46 and the plunger 50 when the solenoid 3 is turned off in the control valve 1, that is, when the automotive air conditioner is not operating. On the other hand, the urging force of the spring 44 is transmitted to the valve actuator 29 through the plunger 50, the actuating rod 38 and the subvalve 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 is in a deployed state. At this time, the sub-valve maintains the valve closed state.

On the other hand, when a starting current is supplied to the electromagnetic coil 54 of the solenoid 3 at the start of the automotive air conditioner, as shown in Fig. 3, the suction pressure Ps becomes equal to the valve opening pressure (Also referred to as "sub-valve opening pressure"), the sub-valve is opened. That is, the solenoid force overcomes the urging force of the spring 42, and the sub-valve body 36 is pushed up integrally. As a result, the sub valve body 36 is separated from the sub valve seat 34 and the sub valve is opened, and the bleed function is effectively exhibited. In this operation process, the main valve body 30 is pushed up by the biasing force of the spring 42 to seat on the main valve seat 22. As a result, the main valve is closed. That is, after the main valve is closed to regulate the introduction of the discharge refrigerant into the control chamber, the sub valve is opened to quickly relieve the refrigerant in the control chamber into the suction chamber. As a result, the compressor can be started quickly. The "sub-valve opening pressure" is changed as the set pressure Pset to 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, the opening degree of the main valve is autonomously adjusted such that the suction pressure Ps becomes the set pressure Pset set by the supply current value. In this control state of the main valve, the sub valve body 36 is seated on the sub valve seat 34, and the sub valve remains in the valve closed state. On the other hand, since the suction pressure Ps is relatively low, the bellows 45 is elongated and the main valve body 30 is operated to adjust the opening degree of the main valve. At this time, the main valve body 30 is moved in the valve opening direction by the power element 6 in accordance with the force in the valve opening direction by the spring 44, the solenoid force in the valve closing direction, Stops at a balanced valve lift position.

When the refrigerant load becomes large and the suction pressure Ps becomes higher than the set pressure Pset, for example, the bellows 45 is contracted, so that the main valve body 30 is displaced relatively upward (valve closing direction). As a result, the valve opening of the main valve becomes small, and the compressor operates to increase the discharge capacity. As a result, the suction pressure Ps is lowered. On the other hand, when the refrigerating load becomes small and the suction pressure Ps becomes lower than the set pressure Pset, the bellows 45 expands. As a result, the power element 6 bucks the main valve body 30 in the valve opening direction to increase the valve opening degree of the main valve, and the compressor operates so as to reduce the discharge capacity. As a result, the suction pressure Ps is maintained at the set pressure Pset.

When the load on the engine becomes large while the normal control is being performed and the load on the air conditioner is to be reduced, the solenoid 3 of the control valve 1 is switched off. The main valve body 30 is separated from the main valve seat 22 by the urging force of the spring 44 so that the main valve body 30 is separated from the main valve seat 22 by the urging force of the spring 44, It becomes an expanded state. At this time, since the sub valve body 36 basically sits on the sub valve seat 34, the sub valve is closed. Thereby, the refrigerant of the discharge pressure Pd introduced into the port 16 from the discharge chamber of the compressor passes through the main valve in the expanded state, and flows from the port 14 to the control chamber. Therefore, the control pressure Pc is increased, and the compressor can perform the minimum capacity operation.

Next, the main part of the assembly structure and method of the control valve 1 will be described in detail.

4 is a view schematically showing a process of assembling the valve body and the solenoid. 5 is a partially enlarged view showing a main part of the assembling structure. Fig. 5A shows an assembling structure of the present embodiment, and corresponds to an enlarged view of part A in Fig. Fig. 5 (B) is a partially enlarged view of an assembled structure according to a comparative example. Although Fig. 5 shows one structural part with respect to the axis of the control valve 1 for the sake of convenience, the same constitution appears symmetrically with respect to the axis as shown in Fig.

As shown in Fig. 4, in the process of assembling the control valve 1, the valve body 2 and the solenoid 3 are individually assembled, and then both are assembled in the axial direction. The filter element 17 is provided with the power element 6, the valve element 36, the valve actuator 29, the O-rings 92 and 94, (On the side of the connection portion of the body 5 with the solenoid 3), and the filter member 15 is assembled on the upper side (the tip side of the body 5). A partition wall 90 protrudes from the outer peripheral surface of the body 5 so as to separate the port 14 and the port 16 so that the filter member 15 and the filter member 17 are engaged with the partition wall 90 And is assembled to the body 5. The control valve 1 is obtained by press-fitting the lower end portion (the lower end portion of the body 5) of the valve body 2 in which each filter member is assembled into the upper end opening portion of the core 46 as described above. The upper end opening of the core 46 is a ring-shaped connecting portion 100 capable of receiving the lower end portion 98 of the body 5.

A predetermined indentation margin is provided between the lower end portion 98 of the body 5 and the ring-shaped connection portion 100 because the indentation is adopted in the assembly of the valve body 2 and the solenoid 3. [ That is, the outer diameter of the body 5 is slightly larger than the inner diameter of the ring-shaped connecting portion 100 in the press-fitting portions of both. Therefore, in the press-fitting step, the lower end portion 98 of the body 5 receives compressive stress inward in the radial direction. When the inner diameter of the guide hole 27 is changed by this compressive stress, the smooth sliding property of the valve driving body 29 is lowered, which may affect the stable operation of the main valve body 30 .

In this embodiment, the annular ring-shaped groove 102 is provided at the lower end of the body 5, the press-in portion 104 press-fitted into the ring-shaped connecting portion 100, and the valve- So as to radially separate the guide portion 106 that supports the guide portion 106 as much as possible. Although not shown, the ring-shaped groove 102 has a shape in which the concave groove is connected in a circular ring shape on the lower surface of the body 5. The thickness on the side of the press-in portion 104 is smaller than the thickness on the side of the guide portion 106 with the ring-shaped groove 102 as a boundary with respect to the radial thickness at the lower end of the body 5. [ In addition, the port 16 is provided at a position to avoid the press-in portion 104, and the press-in portion 104 has a shape symmetrical with respect to the axis of the body 5. In this embodiment, no holes or grooves are formed along the inner circumferential surface of the press-fit portion 104. Therefore, when the press-fit portion 104 is deformed in the radial direction, it is deformed almost uniformly around its axis. As a result, the influence of the press-fitting of the press-in portion 104 is less likely to be applied to the guide portion 106, thereby substantially preventing the inner diameter change of the guide hole 27 at the time of assembly. In addition, even if the guide hole 27 slightly accompanies the inner diameter change, it is possible to prevent partial contact between the guide portion 106 and the valve driving member 29, The smooth sliding property of the driving body 29 can be maintained.

More specifically, as shown in Fig. 5 (A), the ring-shaped connecting portion 100 is provided with a circular concave hole when viewed from the plane for inserting the lower end portion of the body 5, The press-fit portion 104 is received. The inner diameter of the upper half portion of the ring-shaped connecting portion 100 is slightly enlarged to be the insertion guide portion 108 while the outer diameter of the vicinity of the lower end of the body 5 is slightly reduced in diameter to form the insertion distal end portion 110. This facilitates insertion of the lower end of the body 5 into the ring-shaped connecting portion 100, and further, press-fitting of the press-fitting portion 104.

On the other hand, the guide portion 106 is located inwardly of the axial direction of the body 5 with respect to the press-fit portion 104, and secures the size of the operation chamber 28 in addition to the formation of the ring- The lower inner peripheral portion of the guide portion 106 has a tapered shape that is downwardly directed and facilitates insertion of the valve driving body 29 into the body 5.

In this embodiment, the length L1 of the press-in portion 104 and the length L2 of the guide portion 106 are sufficiently large in relation to the dimension in the axial direction. Thereby, the body 5 is firmly fixed to the solenoid 3, and the valve driving body 29 is stably supported. In the present embodiment, the length G2 of the insertion guide portion 108 is significantly larger than the length G1 of the insertion tip portion 110. [ This is for securing a region for inserting the O-ring 96 in the radial direction outside of the insertion guide portion 108 in the ring-shaped connecting portion 100. When the O-ring 96 is not placed in the ring-shaped connecting portion 100, the length of the insertion guide portion 108 can be made smaller than that shown in the drawing.

In addition, by configuring the portion where the press-in portion 104 and the guide portion 106 overlap each other in the radial direction (the overlap portion in which the projections in the radial direction of the both overlap each other) by the length h in the axial direction, Thereby achieving compactness in the direction of the axis. On the other hand, a ring-shaped groove 102 is formed between the press-fit portion 104 and the guide portion 106. The depth D1 of the ring shaped groove 102 based on the lower end of the body 5 is set to be sufficiently large and the bottom portion of the ring shaped groove 102 is located inside the axial direction of the body 5 Located. That is, with respect to the position in the axial direction with respect to the opening end of the body 5 on the side of the solenoid 3, the ring shaped groove 102 is formed at a position where the bottom of the ring shaped groove 102 is separated from the open end of the press- The depth of the light guide plate 102 is set to be large. With this configuration, even when the press-in portion 104 is deformed radially inward when the body 5 is press-fitted into the ring-shaped connecting portion 100, the space Sr formed by the ring- The deformation can be absorbed. As a result, the influence of the deformation of the press-in portion 104 on the guide portion 106 can be substantially eliminated. The height D2 of the guide portion 106 is smaller than the height D1 of the opening end of the body 5 when the bottom of the ring shaped groove 102 is taken as a reference. The height D3 of the sliding surface of the guide portion 106 is smaller than the height D2 of the guide portion 106. [

On the other hand, in the comparative example shown in Fig. 5 (B), a radial overlap portion is formed between the press-in portion 104 and the guide portion 106, but no space is formed between the both portions. In such a configuration, when the body 105 is press-fitted into the ring-shaped connecting portion 100, when the press-in portion 104 is deformed radially inward, the deformation thereof is connected to the deformation of the guide portion 106, The inner diameter of the hole 27 is reduced. As a result, the sliding resistance applied to the valve driving body 29 becomes larger than the designed value, which may cause sliding of the valve driving body 29 and further deterioration of the operability of the main valve body 30. That is, according to the present embodiment, such a problem can be prevented.

The overlapped portion is biased to one side (lower side) in the axial direction of the guide portion 106 although a radial overlap portion is formed between the press-fit portion 104 and the guide portion 106. [ Therefore, according to the comparative example, the clearance between the valve actuator 29 and the guide portion 106 becomes smaller toward the axial direction side. A differential pressure Pd-Ps between the discharge pressure Pd and the suction pressure Ps acts between the port 16 and the operation chamber 28 and the clearance becomes smaller toward the low pressure side. Therefore, when minute foreign matter enters the main valve chamber 24 through the filter member 17, the foreign matter tends to stay in a place where the foreign matter becomes smaller at the clearance. As a result, there is a possibility that the sliding property of the valve driving body 29 is lowered. In this respect, according to the present embodiment, since the clearance between the valve driving body 29 and the guide portion 106 can be kept almost constant from the high pressure side toward the low pressure side, such a problem can be avoided .

As described above, in this embodiment, the inner diameter of the guide portion 106 (that is, the diameter of the guide hole 27) is pressed and inserted by a simple method of forming the annular groove 102 in the body 5 It can be kept almost equal to before. As a result, the slidability of the valve actuator 29 and the operability of the main valve body 30 can be stably maintained as designed values.

Although the preferred embodiments of the present invention have been described above, it is needless to say that the present invention is not limited to the specific embodiments, and various modifications are possible within the scope of the technical idea of the present invention.

In the above embodiment, an example of the positional relationship between the press-fit portion 104 and the guide portion 106 is shown, as shown in Fig. 5 (A). In the modified example, the overlap portion in the radial direction of the guide portion 106 may be enlarged by extending the guide portion 106 downward. Thereby, the position of the guide portion 106 can be brought close to the solenoid 3, and can be connected to the compactness of the single-layered body 5. In this case, the depth of the ring-shaped groove 102 is sufficiently secured. That is, the radial space Sr is formed between the press-fit portion 104 and the guide portion 106 at least in the axial direction region corresponding to the overlapped portion.

The shape of the ring shaped groove 102 is such that the outer wall portion thereof is parallel to the outer peripheral surface of the press-in portion 104 and the inner wall portion is inclined with respect to the guide portion 106 (the guide hole 27) Shape (tapered shape). In the modified example, other shapes may be used. For example, the inner wall portion of the ring-shaped groove may be parallel to the guide portion 106. The outer wall portion of the ring-shaped groove may be tapered (inclined) relative to the outer peripheral surface of the press-fit portion 104. [

In the above embodiment, the thickness of the press-in portion 104 side is made smaller than the thickness of the guide portion 106 side with the ring-shaped groove 102 as a boundary. In the modified example, the thicknesses of both may be equal. Alternatively, the thickness of the press-in portion 104 side may be larger than the thickness of the guide portion 106 side. However, considering the absorption of the compressive stress by the press-fit portion 104 and the securing of the support rigidity by the guide portion 106, it is preferable to adopt the configuration of the above-described embodiment.

In the above embodiment, an example in which the main valve body 30 and the sub valve seat 34 are integrally provided is shown. In a modified example, they may be formed separately from each other. Specifically, a valve seat member may be provided separately from the main valve body 30, and the sub valve seat 34 may be formed on the valve seat member.

In the above embodiment, the sub valve body 36 is fixed to the operation rod 38. [ In the modified example, both of them may be configured to be relatively displaceable. Concretely, the sub-valve body 36 shown in Fig. 2 is slidably inserted into the operating rod 38, and functions as a spring (a "biasing member") for biasing the sub-valve body 36 in the valve closing direction ) May be interposed. For example, a spring may be interposed between the sub-valve body 36 and the power element 6. However, the displacement of the sub valve body 36 in the valve closing direction is regulated by the stepped portion 79 of the operating rod 38.

In the above embodiment, as shown in Fig. 2, an example in which the spring 42 is interposed between the valve actuator 29 and the actuating rod 38 is shown. The spring 42 may be interposed between the valve actuator 29 and the core 46 (the body of the control valve 1).

In the above-described embodiment, the configuration in which the ring-shaped connecting portion 100 is formed integrally with the core 46 is exemplified. In the modified example, the ring-shaped connecting portion and the core may be separately formed and fixed in a coaxial shape. That is, the valve body and the solenoid may be fixed through the ring-shaped connecting portion, and the ring-shaped connecting portion may be regarded substantially as a component of the solenoid.

In the above-described embodiment, the valve actuating member 29 and the actuating rod 38 are configured to be relatively displaceable separately from each other. The valve actuating member 29 and the actuating rod 38 may be integrally fixed by separate members or the valve actuating member 29 and the actuating rod 38 may be formed integrally with the same member . In the latter case, it may be configured as a shaft that does not distinguish between the two, and may function as a "valve drive body ".

Although not described in the above embodiment, the thickness in the radial direction of the ring-shaped connecting portion may be made smaller than the thickness in the radial direction of the press-in portion of the body, so that deformation in the radial direction of the press- good. That is, the ring-shaped connecting portion can be easily bent outward in the radial direction, thereby suppressing deformation of the press-fit portion.

The above embodiment exemplifies a so-called Ps sensing valve in which the power element 6 is disposed in the operating chamber 23 filled with the suction pressure Ps and the suction pressure Ps is directly sensed . In the modified example, a so-called Pc sensing valve may be used, which operates by sensing the control pressure Pc as the detected pressure instead of the suction pressure Ps. Alternatively, the movable element including the valve element may be configured as a differential pressure valve operated by sensing the differential pressure without providing a power element. For example, the differential pressure Pd-Ps between the discharge pressure Pd and the suction pressure Ps may be a Pd-Ps differential pressure valve operated to be a set differential pressure. Or a Pd-Pc differential pressure valve that operates so that the differential pressure Pd-Pc between the discharge pressure Pd and the control pressure Pc becomes a set differential pressure.

In the above embodiment, the springs 42, 44 and the like are exemplified by the spring as the biasing member (elastic body), but it goes without saying that an elastic material such as rubber or resin may be employed.

In the above embodiment, the reference pressure chamber S in the bellows 45 is in a vacuum state. However, the atmosphere may be filled in, or a predetermined gas to be a reference may be filled. Alternatively, either one of the discharge pressure Pd, the control pressure Pc, and the suction pressure Ps may be filled. The power element may be configured to operate by detecting the pressure difference between the inside and the outside of the bellows. Further, in the above embodiment, the pressure Pd, Pc, Ps directly received by the main valve body is canceled, but the pressure of at least one of them may not be canceled.

The present invention is not limited to the above-described embodiment and modifications, and can be embodied by modifying constituent elements without departing from the gist of the invention. Various inventions may be formed by suitably combining a plurality of constituent elements disclosed in the above-described embodiment or modified examples. In addition, some of the constituent elements may be deleted from all the constituent elements disclosed in the above-mentioned embodiment or modified examples.

1: Control valve
2:
3: Solenoid
5: Body
6: Power element
12: Port
14: Port
16: Port
20: Main valve hole
20: Valve hole
22: Main valve seat
23: working room
27: Guide hole
28: working room
29:
30: Main valve body
32: Sub valve hole
34: Sub-valve seat
36: Sub valve body
38: Operation rod
46: Core
50: plunger
100: ring-
102: ring shaped groove
102: Home
104:
106: guide portion
108: insertion guide portion
110: insertion tip
Sr: Space

Claims (7)

A solenoid valve comprising a valve body and a solenoid assembled in an axial direction,
The solenoid includes:
A core secured to the valve body;
A plunger provided coaxially with the core; And
And a ring-shaped connection portion provided integrally with the core and capable of receiving an end portion of the valve body,
Wherein the valve body comprises:
A tubular body having a valve hole and a guide hole in a coaxial shape;
A valve body that opens and closes the valve portion by being in contact with the valve hole; And
And a valve actuator which is slidably supported on a guide portion defining the guide hole and is capable of transmitting a driving force of the solenoid by the operation of the plunger to the valve body,
The valve body and the solenoid are assembled by press-fitting the press-fitting portion provided at the end of the body into the ring-shaped connecting portion,
The body,
Wherein the press-fit portion and the guide portion at least partially overlap each other in a radial direction,
And a groove for forming a radial space between the press-fit portion and the guide portion,
And the press-fit portion has a shape symmetrical with respect to the axis of the body. The method according to claim 1,
Wherein a thickness of the press-in portion side of the body is smaller than a thickness of the guide portion side with the groove as a boundary. 3. The method according to claim 1 or 2,
Wherein a depth of the groove is set to a large extent so that a bottom portion of the groove is separated from the opening end of the press-in portion with respect to a position in the axial direction with respect to an opening end of the body on the solenoid side, . 3. The method according to claim 1 or 2,
Wherein the pressure of the solenoid with the guide portion as a boundary with respect to the fluid pressure in the body is made smaller than the pressure on the side opposite to the solenoid. 5. The method of claim 4,
And a discharge capacity of a variable capacity compressor for compressing a refrigerant introduced into the suction chamber and discharging the refrigerant from the discharge chamber is adjusted by adjusting a flow rate of a refrigerant introduced into the control chamber from the discharge chamber,
The body includes a discharge chamber communication port communicating with the discharge chamber, a control chamber communication port communicating with the control chamber, a suction chamber communication port communicating with the suction chamber, and an operating chamber communicating with the suction chamber communication port ,
The valve hole is provided in the fluid passage communicating the discharge chamber communication port and the control chamber communication port,
And the guide hole is formed between the discharge chamber communication port and the operation chamber. 6. The method of claim 5,
A main passage as the fluid passage, and a sub passage communicating the control chamber communication port and the suction chamber communication port;
A main valve seat provided in the main passage;
A main valve body detachably attached to the main valve seat to open and close the main valve;
A sub valve seat provided in the sub passage;
A sub valve body that is detachably attached to the sub valve seat to open and close the sub valve; And
And an actuating rod connected to the plunger in a coaxial manner and for transmitting the driving force of the solenoid to the valve actuator,
Wherein the main valve body is formed integrally with the valve driving body as the valve body and is capable of relative displacement with respect to the operating rod,
Wherein the actuating rod passes through the valve actuator,
Wherein the sub-valve body is provided integrally with the operation rod,
The sub valve seat is provided integrally with the valve driving body,
And the suction chamber communication port and the operation chamber communicate with each other through the inside of the valve drive body. The method according to claim 6,
And a depressurizing portion for sensing a predetermined sensed pressure and generating a driving force in a valve opening direction of the main valve according to a magnitude of the sensed pressure,
Wherein the operating rod is disposed between the pressure-reducing portion and the plunger,
Wherein an opening degree of the main valve is controlled such that the detected pressure becomes a set pressure corresponding to a supply current value to the solenoid.

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