JP2008280920A - Control valve for variable displacement compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a control valve for duty control inhibiting resonant acceleration added to valve bodies by resonance during vibration and also inhibiting increase in hysteresis of control characteristics. <P>SOLUTION: When vibration amplitude of each valve body exceeds a predetermined minute amplitude range due to resonance of the control valve 1 for a variable displacement compressor, a resonance inhibition member 50 gives slide resistance to each valve body and therefore the resonant acceleration added to each valve body can be inhibited. On the other hand, the duty control is performed on pulsed current supplied to a solenoid 3 and each valve body can be minutely vibrated at a smaller amplitude than the minute amplitude range in a normal control condition of the control valve 1 for the variable displacement compressor. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

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

  In a refrigeration cycle of an automotive air conditioner, a variable capacity compressor capable of varying the refrigerant discharge capacity is used so that a constant cooling capacity is maintained regardless of the engine speed. In this variable capacity compressor, a piston for compression is connected to a swing plate attached to a rotary shaft that is driven to rotate by an engine, and the refrigerant is discharged by changing the stroke of the piston by changing the angle of the swing plate. Adjust the amount. The angle of the swing plate can be continuously changed by introducing a part of the discharged refrigerant into the sealed crank chamber and changing the balance of pressure applied to both surfaces of the piston. The pressure in the crank chamber is controlled by a solenoid-controlled variable displacement compressor control valve (hereinafter simply referred to as “control”) provided between the discharge chamber and the crank chamber of the variable displacement compressor or between the crank chamber and the suction chamber. It is also controlled by “valve”.

  In such a control valve, a current having a value corresponding to the set capacity is supplied to the solenoid coil of the solenoid, and the valve body is operated by the solenoid force generated at that time, thereby adjusting the opening of the valve portion. In order to reduce the hysteresis of the valve opening characteristic, a pulse current of about 400 Hz is supplied, and there is also a type that performs capacity control by making the natural frequency of the movable part close to this in the control state of the control valve (for example, patent) Reference 1).

In such a control valve, a set load acting on the valve body is set by an average current value to the solenoid according to the duty ratio, and the capacity of the refrigerant discharged from the variable capacity compressor is controlled. For example, when using a normally open control valve that opens when the solenoid is not energized, if you want to operate the variable capacity compressor with the minimum capacity, minimize the duty ratio and maximize the valve lift, The flow rate of the refrigerant flowing from the engine to the crank chamber is controlled to the maximum. Conversely, when operating the variable capacity compressor at the maximum capacity, the duty ratio is maximized to minimize the lift amount (valve closed state), and the flow rate of the refrigerant flowing from the discharge chamber to the crank chamber is made zero.
JP 2005-171908 [paragraph [0026] etc.]

  However, when the natural frequency of the movable part of such a control valve matches the frequency at the time of vehicle vibration in the driving state of the engine, the movable part including the valve body resonates, and the resonance acceleration increases, thereby controlling the capacity. There was a problem that the reliability of the system deteriorated. That is, since the rigidity of the spring that biases them can change depending on the position of the movable part such as the valve body and the plunger, resonance may occur at a frequency lower than the natural frequency in the above-described control state.

  The present invention has been made in view of such a problem, and in a control valve for duty control, the resonance acceleration applied to the valve body due to resonance during vibration is suppressed, and an increase in the hysteresis of the control characteristic is also suppressed. With the goal.

  In order to solve the above problems, a control valve for a variable displacement compressor according to an aspect of the present invention is configured to drive a solenoid with a pulse current to operate a valve body and introduce a refrigerant flow rate introduced from a discharge chamber into a crank chamber; The discharge capacity of the variable capacity compressor is changed by controlling at least one of the refrigerant flow rates led out from the crank chamber to the suction chamber. This control valve for a variable capacity compressor includes a resonance suppression member capable of transmitting the sliding resistance obtained in the solenoid to the valve body that vibrates in the opening and closing direction of the valve portion, and the sliding resistance obtained by the resonance suppression member. Regardless of the above, there is provided a suppression release structure that allows vibration of the valve body within a predetermined minute amplitude range.

  The “predetermined minute amplitude range” here may be set as a range in which the amplitude of the minute vibration of the valve body for suppressing hysteresis is allowed at least when the control valve for the variable capacity compressor is not resonant.

  According to this aspect, when the amplitude of the vibration of the valve body exceeds a predetermined minute amplitude range due to resonance with the installation target of the control valve for the variable capacity compressor, the resonance suppression member provides sliding resistance to the valve body. Since it transmits, the resonant acceleration added to a valve body can be suppressed. On the other hand, since the duty control of the pulse current supplied to the solenoid is performed, in the normal control state of the control valve for the variable capacity compressor, the valve body is substantially subjected to the sliding resistance within the minute amplitude range. It can be made to vibrate slightly. Thereby, an increase in the hysteresis of the control characteristic can also be suppressed.

  According to the present invention, in the control valve for duty control, it is possible to suppress an increase in hysteresis of the control characteristics while suppressing the resonance acceleration applied to the valve body due to the resonance during vibration.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following description, for the sake of convenience, the positional relationship between the structures may be expressed as upper and lower with reference to the illustrated state.

[First Embodiment]
FIG. 1 is a cross-sectional view illustrating a configuration of a variable displacement compressor control valve according to a first embodiment. The variable displacement compressor control valve 1 is incorporated in a variable displacement compressor constituting a refrigeration cycle of an automotive air conditioner (not shown). This refrigeration cycle consists of a variable capacity compressor that compresses refrigerant and discharges it as high-temperature and high-pressure gas refrigerant, a condenser that condenses the gas refrigerant, and low-temperature and low-pressure refrigerant by adiabatically expanding the condensed liquid refrigerant And an evaporator for exchanging heat with the passenger compartment air by evaporating the refrigerant. For example, alternative chlorofluorocarbon (HFC-134a) is used as the refrigerant, but a refrigerant having a high operating pressure such as carbon dioxide may be used. In that case, an external heat exchanger such as a gas cooler may be arranged in place of the condenser.

  The variable displacement compressor control valve 1 is a three-way valve that controls the flow rate of refrigerant introduced from the discharge chamber of the variable displacement compressor into the crank chamber and the flow rate of refrigerant injected from the crank chamber into the suction chamber. It has a structure and is configured as a so-called Ps sensing valve that performs capacity control so as to keep the suction pressure Ps at a set pressure. The control valve 1 for a variable capacity compressor includes a valve body 2 having a valve portion therein and a solenoid 3 that is integrally assembled with the valve body 2 to open and close the valve portion. The valve body 2 includes a stepped cylindrical body 5 having a refrigerant passage formed therein. The upper end opening of the body 5 is provided with a port 6 that communicates with a discharge chamber of a variable capacity compressor (not shown) and introduces a discharge pressure Pd. Further, the side of the body 5 is connected in order from the top to the ports 7 and 8 through which the controlled pressure (referred to as “crank pressure”) Pc communicates with the crank chamber of the variable capacity compressor, and the suction chamber. Thus, a port 9 for introducing the suction pressure Ps is formed.

  The port 6 and the port 7 communicate with each other inside the body 5, and a first valve portion is provided in a refrigerant passage that connects the two ports. The refrigerant introduced from the discharge chamber through the port 6 is led out to the crank chamber through the first valve portion and the port 7. On the other hand, the port 8 and the port 9 communicate with each other inside the body 5, and a second valve portion is provided in a refrigerant passage that connects both the ports. The refrigerant introduced from the crank chamber through the port 8 is led out to the suction chamber through the second valve portion and the port 9. That is, in the variable capacity compressor, the refrigerant passage for introducing the crank pressure Pc1 into the crank chamber and the refrigerant passage for deriving the crank pressure Pc2 from the crank chamber are separated, so that the circulation of oil introduced into and discharged from the crank chamber is performed. Keeps good.

  A valve hole 11 is provided in the refrigerant passage communicating the port 6 and the port 7. A valve seat 12 is formed integrally with the body 5 at the opening end of the valve hole 11 on the port 6 side. A ball-shaped valve body 13 (first valve body) is disposed so as to face the valve seat 12 from the discharge chamber side. The valve body 13 constitutes a first valve portion together with the valve seat 12. Furthermore, a guide hole 15 is formed so as to face the valve hole 11 along the axis of the body 5, and a long operating rod 16 is slidably inserted into the guide hole 15. The valve element 13 is supported by the tip of the reduced diameter portion provided at the upper end of the operating rod 16. The valve body 13 can move in contact with and away from the valve seat 12 along the axial direction in conjunction with the operating rod 16.

  A spring receiving member 17 is screwed into the upper end opening of the body 5. Between the spring receiving member 17 and the valve body 13, as a biasing means for biasing the valve body 13 in the valve closing direction. A spring 18 is interposed. The load of the spring 18 can be adjusted by the screwing amount of the spring receiving member 17 into the body 5. A strainer 19 is fitted to the upper end portion of the body 5 so as to cover the upper end opening, thereby preventing inflow of dust and the like from the outside.

  Further, a valve hole 21 is provided in the refrigerant passage that communicates the port 8 and the port 9. A valve seat 22 is formed integrally with the body 5 at the opening end of the valve hole 21 on the port 9 side. The lower end portion of the actuating rod 16 penetrates the valve hole 21, and the position near the valve hole 21 is slightly enlarged to form a stepped cylindrical valve body 23 (second valve body). The valve body 23 is disposed so as to face the valve seat 22 from the suction chamber side, and constitutes a second valve portion together with the valve seat 22. A spring 24 that biases the actuation rod 16 downward (in the valve opening direction of the second valve portion) is interposed between the enlarged diameter portion provided at the lower end portion of the actuation rod 16 and the body 5. . The lower end opening of the body 5 is formed with a pressure chamber that communicates with the port 9 and into which the suction pressure Ps is introduced.

  The solenoid 3 is inserted into a case 30 that also functions as a yoke, a stepped cylindrical bobbin 31 disposed in the case 30, an electromagnetic coil 32 wound around the bobbin 31, and the upper half of the bobbin 31. A cylindrical sleeve 33, a core 34 inserted and fixed in the lower half of the bobbin 31, and a plunger 35 inserted through the sleeve 33 and disposed opposite to the core 34 in the axial direction. It is configured.

  The upper end of the case 30 is crimped and fixed to the body 5, and a resin handle 36 is provided at the lower end so as to seal the inside of the solenoid 3 from below. A ring-shaped plate 37 made of a magnetic material is molded on the handle 36. This plate 37 forms a magnetic circuit together with the case 30. Further, a harness 39 is inserted through a hole provided to penetrate the handle 36 through a rubber bush 38 for sealing. The harness 39 is connected to the electromagnetic coil 32 on the one hand and to an external power source (not shown) on the other hand. A pulse current of about 400 Hz is output from the external power source at a predetermined duty ratio, and is supplied to the electromagnetic coil 32 via the harness 39.

  The sleeve 33 is made of a nonmagnetic material, and an inner surface thereof forms a sliding surface (corresponding to an “internal sliding surface”) of the plunger 35. A diaphragm 40 is interposed between the body 5 and the case 30 so as to partition the inside of both. The diaphragm 40 is a pressure-sensitive member having flexibility, and is configured by stacking a plurality of polyimide films. Due to the presence of the diaphragm 40, the suction pressure Ps is not introduced into the solenoid 3. In addition, the diaphragm 40 may be comprised with metal thin plates, such as beryllium copper and stainless steel, for example.

  The plunger 35 is press-fitted into one end of a shaft 43 that extends in the axial direction around the center of the core 34. The other end of the shaft 43 is supported by a bearing member 44 that is inserted into the handle 36. A retaining ring 45 is fitted in the middle of the shaft 43, and a spring receiver 46 is provided so that upward movement is regulated by the retaining ring 45. A spring 48 that urges the plunger 35 in a direction away from the core 34 via the shaft 43 is interposed between the spring receiver 46 and the bearing member 44. The load of the spring 48 can be adjusted by changing the screwing amount of the bearing member 44 into the handle 36. The plunger 35 is integrally connected to the operating rod 16 through the diaphragm 40.

  A concave portion 55 is provided in the outer peripheral portion of the plunger 35 at substantially the center in the axial direction, and the ring-shaped resonance suppression member 50 is disposed in the concave portion 55. The resonance suppression member 50 includes a sliding member 51 and a spring 52 (corresponding to an “urging member”) arranged concentrically and pressing the inner sliding surface of the sleeve 33 from the inside. The sliding resistance is obtained by the reaction force, and details thereof will be described later.

  FIG. 2 is a diagram illustrating the configuration of the sliding member that configures the resonance suppression member. (A) represents the plan view, and (B) represents the front view. FIG. 3 is a diagram illustrating a configuration of a spring constituting the resonance suppressing member. (A) represents the plan view, and (B) represents the front view. FIG. 4 is a cross-sectional view showing the plunger after the resonance suppressing member is attached. The figure shows a state before the plunger 35 is assembled in the solenoid 3.

  As shown in FIG. 2, the sliding member 51 has a so-called C-ring configuration in which one circumferential position is opened in a substantially circular ring having a predetermined height (length in the axial direction). The opening 53 extends slightly outward, but can be bent inward in the radial direction. The sliding member 51 is made of a resin member having a friction coefficient smaller than that of a metal member such as stainless steel, and moderately reduces sliding resistance when contacting the inner sliding surface of the sleeve 33. As this resin member, for example, a fluororesin such as Teflon (registered trademark) can be adopted, but it may be subjected to a surface treatment such as coating with such a resin.

  As shown in FIG. 3, the spring 52 has a configuration of a C-ring formed by bending a thin metal plate such as stainless steel into a circular shape. The spring 52 extends slightly outward in the opening 54, but can be bent inward in the radial direction. The resonance suppression member 50 is configured as a double ring by fitting the spring 52 inside the sliding member 51. The spring 52 has substantially the same height as the sliding member 51 and biases the sliding member 51 outward from the inside. That is, the spring 52 functions to compensate for the elastic return force of the sliding member 51 outward. In the present embodiment, the sliding member 51 and the spring 52 function as elastic members.

  As shown in FIG. 4, the resonance suppression member 50 in which the sliding member 51 and the spring 52 are superimposed is fitted into a recess 55 formed on the outer peripheral surface of the plunger 35. The recess 55 is formed around the periphery of the plunger 35 and has a depth that is the sum of the radial thicknesses of the sliding member 51 and the spring 52. As illustrated, the outer peripheral surface (that is, the outer peripheral surface of the sliding member 51) protrudes from the side surface of the plunger 35 by a predetermined amount due to the elastic force of the resonance suppression member 50. When the resonance suppressing member 50 is incorporated in the solenoid 3 in a state of being elastically deformed inward, the outer peripheral surface of the sliding member 51 comes into contact with the inner sliding surface of the sleeve 33 by the action of the reaction force. . On the other hand, since the friction coefficient of the outer peripheral surface of the sliding member 51 is relatively small, the resonance suppressing member 50 can obtain an appropriate sliding resistance.

  Further, the height h of the resonance suppressing member 50 is formed to be smaller than the width w of the recess 55 by a predetermined amount, and a clearance cl having a predetermined size is formed between the two in the axial direction. ing. The plunger 35 can be displaced relatively to the resonance suppression member 50 within the range of the clearance cl. That is, minute vibrations of the plunger 35 and the respective valve bodies are allowed without being substantially affected by the sliding resistance obtained by the resonance suppressing member 50. In this manner, a suppression release structure that allows vibration of each valve body within a predetermined minute amplitude range is formed by the clearance cl. Since the clearance cl is set larger than the amplitude of vibration of each valve body when the variable displacement compressor control valve 1 is not resonating, the movement of each valve body is not hindered during the non-resonance. . On the other hand, if the amplitude of the vibration of each valve element exceeds the size of the clearance cl due to the resonance with the vibration of the installation target of the control valve 1 for the variable capacity compressor (in this case, the variable capacity compressor and thus the vehicle), the resonance is suppressed. Since the vibration suppression force based on the sliding resistance acts on each valve body via the member 50, the resonance acceleration applied to each valve body can be suppressed.

  In the variable displacement compressor control valve 1 configured as described above, when the solenoid 3 is turned on and the maximum current is supplied to the electromagnetic coil 32, the plunger 35 is attracted to the core 34, and the valve body 13 is moved. The valve seat 12 is seated by the urging force of the spring 18 or the like. For this reason, the first valve portion is fully closed. On the other hand, since the operating rod 16 is displaced downward together with the valve body 13, the valve body 23 is separated from the valve seat 22, and the second valve portion is fully opened. As a result, inhalation of air from the crank chamber side to the suction chamber side is promoted, and the variable capacity compressor promptly shifts to the maximum capacity operation.

  In a control state in which the current value supplied to the solenoid 3 is set to a predetermined value, the valve body 13 is lifted from the valve seat 12 by the urging force of the spring 48 to open the first valve portion by a predetermined amount. The lift amount of the valve body 13 is set by the solenoid force of the solenoid 3, and the solenoid force can be set and changed from the outside by duty-controlling the pulse current supplied to the electromagnetic coil 32. That is, when the duty ratio of the pulse current is increased and the average current value is increased, the attractive force between the plunger 35 and the core 34 is increased and the lift amount is decreased. Decreasing the current value increases the lift amount.

  Here, when the suction pressure Ps is lowered, the diaphragm 40 is displaced upward to operate the valve body 13 in the valve opening direction. As a result, the flow rate of the refrigerant supplied to the crank chamber is increased, the crank pressure Pc is increased, the discharge capacity is reduced, and the suction pressure Ps is increased. Conversely, when the suction pressure Ps increases, the diaphragm 40 is displaced downward to operate the valve body 13 in the valve closing direction. As a result, the flow rate of the refrigerant supplied to the crank chamber decreases, the crank pressure Pc decreases, the discharge capacity increases, and the suction pressure Ps decreases. That is, the valve body 13 operates autonomously so that the suction pressure Ps becomes the set pressure.

  In this variable displacement compressor control valve 1, regardless of whether the solenoid 3 is on or off, when the amplitude of vibration of each valve element exceeds the size of the clearance cl due to resonance of the movable part, the resonance suppression member 50 The sliding resistance received suppresses the vibration of the plunger 35 and thus each valve body.

  As described above, in the present embodiment, when the amplitude of the vibration of each valve body exceeds a predetermined minute amplitude range due to the resonance of the control valve 1 for the variable capacity compressor, the resonance suppression member 50 is moved to each valve body. Since the sliding resistance is transmitted to the valve body, the resonance acceleration applied to each valve body can be suppressed. Thereby, for example, when the valve body is controlled at a position in the vicinity of the valve seat, it is possible to avoid a phenomenon in which the valve body collides with the valve seat and jumps up to make its control characteristics unstable. On the other hand, since the duty control of the pulse current supplied to the solenoid 3 is performed, in the normal control state of the control valve 1 for the variable capacity compressor, each valve body can be slightly vibrated within the above minute amplitude range. Thereby, an increase in the hysteresis of the control characteristic can also be suppressed.

[Second Embodiment]
Next, a second embodiment of the present invention will be described. The variable displacement compressor control valve according to the present embodiment is common in that it has the same resonance suppression member, although the capacity control method is different from that of the first embodiment. In the following description, components that are substantially the same as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted as appropriate.

  FIG. 5 is a cross-sectional view showing a configuration of a control valve for a variable capacity compressor according to a second embodiment. The control valve 201 for the variable displacement compressor introduces a flow rate of refrigerant introduced from the discharge chamber into the crank chamber so that the differential pressure (Pd−Ps) between the discharge pressure Pd and the suction pressure Ps of the variable displacement compressor is maintained at the set differential pressure. It is configured as a so-called Pd-Ps differential pressure valve for controlling the pressure. A port 7 for deriving the crank pressure Pc controlled by the valve portion is provided on a side portion of the body 205 of the valve body 202, but a port for introducing the crank pressure Pc is not provided.

  A stepped cylindrical valve seat forming member 210 is press-fitted into a refrigerant passage communicating the port 6 and the port 7 in the upper part of the body 205, and the valve hole 11 is formed by the internal passage. The valve seat 12 is formed by the end face of the valve seat forming member 210 on the crank chamber side. A valve element 13 made of one end of a long operating rod 216 is disposed so as to be able to contact and separate from the valve seat 12 from the crank chamber side.

  A guide hole 20 is formed at the center of the body 205, and the operating rod 216 is pivotally supported by the guide hole 20 so as to be slidable. The valve body 13 is disposed in a pressure chamber communicating with the crank chamber on the downstream side of the valve hole 11, and opens and closes the valve hole 11 by attaching and detaching the outer peripheral edge of the distal end surface to the valve seat 12. Between the retaining ring 217 fixed to the lower end portion of the operating rod 216 and the lower end surface of the body 205, a spring 24 for biasing the operating rod 216 toward the solenoid 203, that is, in the valve opening direction is interposed.

  An internal space surrounded by the body 205 and the solenoid 203 forms a pressure chamber that communicates with the port 9 and into which the suction pressure Ps is introduced. The suction pressure Ps is also introduced into the solenoid 203.

  On the other hand, in the solenoid 203, the positional relationship between the core 234 and the plunger 235 arranged in parallel in the axial direction is opposite to that of the first embodiment, and the plunger 235 is disposed below the core 234.

  A shaft 243 passes through the center of the core 234 in the axial direction. A ring-shaped bearing member 244 is press-fitted into the upper end opening of the core 234, and the upper end of the shaft 243 is slidably supported. The bearing member 244 is provided with a communication hole (not shown) that guides the suction pressure Ps introduced through the port 9 to the inside of the solenoid 203.

  A sleeve 233 is extrapolated to the core 234. In the sleeve 233, the plunger 235 is disposed below the core 234 so as to be able to advance and retract in the axial direction. The sleeve 233 is made of a nonmagnetic material, and its inner surface forms a sliding surface (internal sliding surface) of the plunger 235.

  The upper portion of the plunger 235 is press-fitted into the lower half of the shaft 243. Between the plunger 235 and the core 234, a spring 245 that urges the plunger 235 in a direction to separate the plunger 235 from the core 234 is interposed. A spring 48 that biases the plunger 235 in the valve closing direction is interposed between the plunger 235 and the bearing member 44.

  In the above configuration, although the diameter of the operating rod 216 is slightly larger than the inner diameter of the valve hole 11, it has substantially the same size, so that the crank pressure Pc introduced from the port 7 is almost canceled when the valve is opened. Therefore, a differential pressure (Pd−Ps) between the discharge pressure Pd and the suction pressure Ps substantially acts on the valve body 13 with respect to the pressure receiving area approximately the size of the valve hole 11. The valve body 13 operates so that the differential pressure (Pd−Ps) is maintained at the set differential pressure set by the control current supplied to the solenoid 203. This control current is supplied as a pulse current from the outside as in the first embodiment.

  In the present embodiment, the same resonance suppression member 50 as that in the first embodiment is provided on the outer peripheral surface near the lower end of the plunger 235. That is, the plunger 235 is also formed with the recess 55 as shown in FIG. 4, and the resonance suppressing member 50 is fitted while forming a predetermined clearance in the axial direction. Therefore, although the control method is different, the same effect as the first embodiment can be obtained.

  The preferred embodiments of the present invention have been described above, but 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. Needless to say.

  In each of the above-described embodiments, the resonance suppressing member 50 is configured by overlapping the sliding member 51 and the spring 52. In the modified example, as long as an appropriate sliding resistance is obtained, the resonance suppression member may be configured by either the sliding member 51 or the spring 52.

  In each of the above embodiments, an example in which the ring-shaped resonance suppression member 50 is provided on the outer peripheral portion of the solenoid plunger has been described. In a modified example, a similar resonance suppressing member may be provided in at least one of movable members other than the plunger, that is, a member that operates integrally with the valve body. Moreover, the resonance suppression member does not need to be formed in a ring shape, and may be any member that can transmit the sliding resistance in the axial direction directly or indirectly to the valve body.

  In the above embodiments, the sliding member 51 and the spring 52 have the same height, but may be configured to have different heights. In that case, a clearance cl in the axial direction may be ensured between the higher member and the recess 55.

It is sectional drawing which shows the structure of the control valve for variable capacity compressors which concerns on 1st Embodiment. It is a figure showing the structure of the sliding member which comprises a resonance suppression member. It is a figure showing the structure of the spring which comprises a resonance suppression member. It is sectional drawing showing the plunger after the attachment of the resonance suppression member. It is sectional drawing which shows the structure of the control valve for variable capacity compressors which concerns on 2nd Embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Control valve for variable capacity compressors, 2 Valve body, 3 Solenoid, 5 Body, 11 Valve hole, 12 Valve seat, 13 Valve body, 16 Actuating rod, 21 Valve hole, 22 Valve seat, 23 Valve body, 32 Electromagnetic coil , 33 sleeve, 34 core, 35 plunger, 40 diaphragm, 43 shaft, 50 resonance suppression member, 51 sliding member, 52 spring, 53 open part, 54 open part, 55 recessed part, 201 control valve for variable capacity compressor, 202 valve Main body, 203 solenoid, 205 body, 210 valve seat forming member, 216 actuating rod, 233 sleeve, 234 core, 235 plunger, 243 shaft.

Claims (7)

The solenoid is driven by a pulse current to operate the valve body, and at least one of the refrigerant flow rate introduced from the discharge chamber into the crank chamber and the refrigerant flow rate led out from the crank chamber to the suction chamber is controlled to control the variable capacity compressor. In the control valve for variable capacity compressor that changes the discharge capacity,
A resonance suppression member capable of transmitting the sliding resistance obtained in the solenoid to the valve body that vibrates in the opening and closing direction of the valve portion;
Regardless of the sliding resistance obtained by the resonance suppression member, a suppression release structure that allows vibration of the valve body within a predetermined minute amplitude range;
A control valve for a variable capacity compressor.   The solenoid includes a core that is fixed inside, a plunger that is disposed opposite to the core in the axial direction and is displaced, and that transmits a solenoid force to the valve body, and the core and the plunger that are supplied with the pulse current. 2. The control valve for a variable capacity compressor according to claim 1, further comprising an electromagnetic coil that generates the solenoid force between the control valve and the valve.   The resonance suppression member is provided on an outer peripheral portion of the plunger, and is configured to press the internal sliding surface of the solenoid from the inside and obtain the sliding resistance by a reaction force thereof. The control valve for a variable capacity compressor according to claim 2.   The resonance suppression member is configured to include an elastic member that presses the internal sliding surface by a reaction force by being incorporated in the solenoid while being elastically deformed inward. The control valve for a variable displacement compressor according to claim 3.   The resonance suppression member, as the elastic member, slidably slides while reducing sliding resistance with the internal sliding surface, and biases the sliding member from the inside of the sliding member toward the internal sliding surface. The control valve for a variable capacity compressor according to claim 4, comprising an urging member. The elastic member is fitted into a recess formed on the outer peripheral surface of the plunger,
The suppression release structure is formed by an axial clearance between the elastic member and the recess;
The control valve for a variable displacement compressor according to claim 4.   The control valve for a variable capacity compressor according to claim 6, wherein the clearance is set larger than an amplitude of vibration of the valve body when the control valve for the variable capacity compressor is not resonant.

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