JP2014114890A - Control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a flow rate at the time of opening an auxiliary valve regardless of the size of a main valve, in a control valve in which the main valve and the auxiliary valve are driven by a single solenoid.SOLUTION: In a control valve 1, an auxiliary valve seat 34 is formed in a part of a body 5. The control valve 1 includes an actuation switch mechanism in which in the control state of a main valve, an actuation rod 38 is displaced integrally with a main valve body 30 while maintaining the valve closing state of an auxiliary valve, and after the valve closing state of the main valve, by relatively displacing the actuation rod 38 to the main valve body 30, an auxiliary valve body 36 is displaced in a valve opening direction.

Description

  The present invention relates to a control valve, and more particularly to a control valve that is provided with a main valve and a sub valve in a common body and is driven by a single solenoid.

  In general, an air conditioner for an automobile compresses the refrigerant flowing through the refrigeration cycle and discharges it as a high-temperature / high-pressure gas refrigerant, a condenser that condenses the gas refrigerant, and adiabatic expansion of the condensed liquid refrigerant. And an expansion device that converts the refrigerant into a low-temperature and low-pressure refrigerant, an evaporator that exchanges heat with the air in the vehicle interior by evaporating the refrigerant, and the like. The refrigerant evaporated in the evaporator is returned to the compressor and circulates in the refrigeration cycle.

  As this compressor, a variable capacity compressor (also simply referred to as “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 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 discharge amount of the refrigerant is changed by changing the stroke of the piston by changing the angle of the swing plate. adjust. 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 (hereinafter referred to as “crank pressure”) Pc is controlled by a variable displacement compressor control valve (also simply referred to as “control valve”) provided between the discharge chamber and the crank chamber of the compressor. The

  Such a control valve adjusts the valve opening degree by supplying current from the outside to a solenoid as a drive unit. When it is necessary to quickly exhibit the air conditioning function, such as when the air conditioner is started, the valve portion is closed by supplying a maximum current to the solenoid, for example, the crank pressure Pc is lowered and the swing plate is used as the rotating shaft. In contrast, the compressor can be operated at the maximum capacity by being tilted greatly. When the engine load on the vehicle is large, the solenoid is turned off to fully open the valve, and the crank pressure Pc is increased to make the swing plate substantially perpendicular to the rotating shaft, thereby reducing the compressor with the minimum capacity. Can be driven.

  In such a control valve, a main valve is provided in a main passage communicating the discharge chamber and the crank chamber, while a sub valve is provided in a sub passage communicating the crank chamber and the suction chamber. Some are driven by a solenoid (see, for example, Patent Document 1). According to this control valve, the opening degree of the main valve is adjusted with the sub valve closed during the steady operation of the air conditioner. Thereby, the crank pressure Pc can be controlled as described above, and the discharge capacity of the compressor can be controlled. On the other hand, when the air conditioner is started, the auxiliary valve is opened with the main valve closed, thereby quickly reducing the crank pressure Pc, so that the compressor can be shifted to the maximum capacity operation state relatively quickly. . Moreover, since it was set as the structure which opens and closes a some valve with a single solenoid, the whole control valve can be comprised compactly.

  Such a control valve is provided with a main valve body and a sub-valve body on the same axis for driving the main valve and the sub-valve by a single solenoid, and an operating rod disposed along the axis. And a mechanism for transmitting a solenoid force to each valve body via the. A main valve hole is provided in the body of the control valve, and a sub valve hole is provided in the main valve body. That is, the auxiliary passage is provided so as to penetrate the main valve body. And the main valve is opened and closed by attaching and detaching the main valve body to the main valve seat provided at the opening end of the main valve hole, and with respect to the sub valve seat provided at the opening end of the sub valve hole. The auxiliary valve is opened and closed by attaching and detaching the auxiliary valve body. However, during the steady operation of the compressor, the auxiliary valve body is pressed against the auxiliary valve seat, and the closed state of the auxiliary valve is maintained. When the compressor is started, the solenoid force is maximized, and the auxiliary valve can be opened by further energizing the auxiliary valve body in the valve opening direction with the main valve element seated on the main valve seat.

JP 2008-240580 A

  By the way, in recent years, there is a demand for a vehicle manufacturer to start the compressor more quickly. Pursuing further comfort by demonstrating air-conditioning performance more quickly will lead to vehicle sales promotion. For this purpose, the refrigerant flow rate when the auxiliary valve is open must be increased. However, since the above-mentioned control valve forms the auxiliary valve hole in the main valve body, the size of the auxiliary valve is restricted by the size of the main valve, and it is not easy to obtain a desired flow rate. That is, it is physically impossible to make the auxiliary valve hole larger than the main valve hole. Therefore, it is conceivable to increase the lift amount of the auxiliary valve body from the auxiliary valve seat. However, increasing the stroke of the auxiliary valve body enlarges the entire control valve, which is disadvantageous in terms of cost. Even if the stroke is increased, the flow rate cannot be significantly increased unless the size of the auxiliary valve hole is changed.

  The present invention has been made in view of such problems. In a control valve in which a main valve and a sub valve are driven by a single solenoid, a flow rate can be obtained regardless of the size of the main valve when the sub valve is opened. The purpose is to do so.

  In order to solve the above problems, a control valve according to an aspect of the present invention includes an introduction / exit port for introducing or deriving a working fluid, an introduction port for introducing the working fluid, and a body provided with a deriving port for deriving the working fluid. , A main valve provided in a main passage communicating the introduction port and the introduction port, a sub valve provided in a sub passage communicating the introduction / exit port and the outlet port, and a slidably supported by the body, A main valve body that opens and closes the main valve by opening and closing the main valve seat provided in the main passage, a sub valve body that opens and closes the sub valve by opening and closing the sub valve seat provided in the sub passage, and a current supplied A solenoid that generates a solenoid force having a magnitude corresponding to the amount; and an actuating rod that is coupled to the solenoid and can transmit the solenoid force directly or indirectly to the main valve body and the subvalve body. And a sub valve seat is formed in a part of body. In the control state of the main valve, the operating rod is integrally displaced with the main valve body while maintaining the closed state of the auxiliary valve, and the operating rod is displaced relative to the main valve body even after the main valve is closed. An operation switching mechanism for displacing the auxiliary valve body in the valve opening direction is further provided.

  According to this aspect, the auxiliary valve seat is formed not on the main valve body but on a part of the body. For this reason, the magnitude | size of a subvalve can be set independently of a main valve. In the control state of the main valve, the opening degree of the main valve is adjusted by displacing the operating rod integrally with the main valve body while maintaining the closed state of the auxiliary valve. Even after the main valve is closed, the sub-valve can be opened by displacing the operating rod relative to the main valve body. In other words, the operation of the operation switching mechanism accompanying the drive of the solenoid can control the main valve and the subvalve independently, and can sufficiently secure the flow rate when the subvalve is opened.

  According to the present invention, in a control valve in which a main valve and a sub valve are driven by a single solenoid, a flow rate can be obtained regardless of the size of the main valve when the sub valve is opened.

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

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

[First Embodiment]
FIG. 1 is a cross-sectional view illustrating a configuration of a control valve according to the first embodiment.
The control valve 1 is configured as an electromagnetic valve that controls the discharge capacity of a variable capacity compressor (not shown) (simply referred to as “compressor”) installed in the refrigeration cycle of the automotive air conditioner. This compressor compresses the refrigerant flowing through the refrigeration cycle and discharges it as a high-temperature and high-pressure gas refrigerant. The gas refrigerant is condensed in a condenser (external heat exchanger) and further adiabatically expanded by an expansion device to become a low temperature / low pressure mist refrigerant. The low-temperature and low-pressure refrigerant evaporates in the evaporator, and the passenger compartment air is cooled by the latent heat of evaporation. The refrigerant evaporated in the evaporator is returned again to the compressor and circulates in the refrigeration cycle. The compressor has a rotating shaft that is rotationally driven by an automobile engine, and a compression piston is connected to a swing plate attached to the rotating shaft. The refrigerant discharge amount is adjusted by changing the stroke of the piston by changing the angle of the swing plate. The control valve 1 controls the flow rate of the refrigerant introduced from the discharge chamber of the compressor into the crank chamber, thereby changing the angle of the swing plate, and thus the discharge capacity of the compressor.

  The control valve 1 is configured as a so-called Ps sensing valve that controls the flow rate of the refrigerant introduced from the discharge chamber into the crank chamber so as to keep the suction pressure Ps (corresponding to “sensed pressure”) of the compressor at a set pressure. Yes. The control valve 1 is configured by integrally assembling a valve body 2 and a solenoid 3. The valve body 2 is a main valve that opens and closes a refrigerant passage for introducing a part of the discharged refrigerant into the crank chamber when the compressor is in operation, and a so-called bleed valve that releases the refrigerant in the crank chamber to the suction chamber when the compressor is started. Including a functioning secondary valve. The solenoid 3 controls the flow rate of the refrigerant introduced into the crank chamber by driving the main valve in the opening / closing direction to adjust the opening degree. The valve body 2 includes a stepped cylindrical body 5, a main valve and a sub valve provided in the body 5, a power element 6 that generates a force that opposes the solenoid force to adjust the opening of the main valve, and the like. I have. The power element 6 functions as a “pressure sensitive part”.

  The body 5 is provided with ports 12, 14, and 16 from the upper end side. Among these, the port 12 is provided in the upper end opening of the body 5, and the ports 14 and 16 are provided in the side of the body 5. The port 12 functions as a “suction chamber communication port” communicating with the suction chamber, the port 14 functions as a “crank chamber communication port” communicating with the crank chamber, and the port 16 is a “discharge chamber communication port” communicating with the discharge chamber. Function as. An end member 13 is fixed to the upper end opening of the body 5. A plurality of communication grooves 15 for forming the port 12 are provided on the outer peripheral surface of the end member 13. The lower end of the body 5 is connected to the upper end of the solenoid 3.

  In the body 5, a main passage that communicates the port 16 and the port 14 and a sub passage that communicates the port 14 and the port 12 are formed. A main valve is provided in the main passage, and a sub valve is provided in the sub passage. The main valve and the sub valve are provided coaxially, and the sub valve is disposed above the main valve. That is, as shown in the figure, the control valve 1 has a configuration in which a power element 6, a sub valve, a main valve, and a solenoid 3 are arranged from one end side. A main valve hole 18 is provided in the main passage, and a main valve seat 20 is formed at the lower end opening edge. A sub valve hole 32 is provided in the sub passage, and a sub valve seat 34 is formed at the upper end opening edge.

  The port 16 introduces a refrigerant having a discharge pressure Pd from the discharge chamber. The port 14 guides the refrigerant having the crank pressure Pc via the main valve toward the crank chamber during steady operation of the compressor, and introduces the refrigerant having the crank pressure Pc discharged from the crank chamber when the compressor is started. The refrigerant introduced at this time is guided to the auxiliary valve. The port 12 introduces the refrigerant having the suction pressure Ps during the steady operation of the compressor, and guides the refrigerant having the suction pressure Ps via the auxiliary valve toward the suction chamber when the compressor is started. A pressure chamber 22 that is filled with the suction pressure Ps is formed between the port 12 and the auxiliary valve hole 32. The power element 6 is disposed in the pressure chamber 22.

  The main valve hole 18 and the sub valve hole 32 are formed coaxially, and a pressure chamber 27 between the main valve hole 18 and the sub valve hole 32 communicates with the port 14. A valve chamber 26 is formed between the port 16 and the main valve hole 18. On the opposite side of the valve chamber 26 from the main valve hole 18, a guide hole 24 is formed coaxially with the main valve hole 18. A bottomed cylindrical main valve body 30 is slidably inserted into the guide hole 24. A pressure chamber 28 is formed on the opposite side of the guide hole 24 from the valve chamber 26. The main valve body 30 opens and closes the main valve by being attached to and detached from the main valve seat 20 from the valve chamber 26 side, and adjusts the flow rate of refrigerant flowing from the discharge chamber to the crank chamber.

  On the other hand, a sub valve body 36 is provided so as to penetrate the sub valve hole 32. The auxiliary valve body 36 is disposed opposite to the main valve body 30 in the axial direction, and opens and closes the auxiliary valve by being attached to and detached from the auxiliary valve seat 34 from the pressure chamber 22 side. When the auxiliary valve body 36 is seated on the auxiliary valve seat 34 and closes the auxiliary valve, the relief of the refrigerant from the crank chamber to the suction chamber is blocked. Further, when the auxiliary valve body 36 is separated from the auxiliary valve seat 34 and opens the auxiliary valve, the refrigerant is allowed to be relieved from the crank chamber to the suction chamber. A communication hole 35 that communicates the inside and the outside is provided in the upper bottom portion of the main valve body 30, and an internal passage 37 communicates the pressure chamber 27 and the pressure chamber 28. That is, the upper and lower pressure chambers of the main valve body 30 and the internal passage 37 form a capacity chamber that is filled with the crank pressure.

  Further, an elongated operating rod 38 is provided along the axis of the body 5. The upper half of the operating rod 38 passes through the main valve body 30 and the sub-valve body 36 and is connected to the power element 6 so as to be operatively connectable. The lower end of the operating rod 38 is connected to a plunger 50 described later of the solenoid 3. The actuating rod 38 transmits a solenoid force directly or indirectly to the main valve body 30 and the sub valve body 36. A spring receiving member 40 is provided at an intermediate portion of the operating rod 38. Between the main valve body 30 and the spring receiving member 40, a spring 42 (functioning as a “first urging member”) that urges the main valve body 30 in the valve closing direction of the main valve is interposed. . On the other hand, a spring 44 (which functions as a “second urging member”) that urges the sub-valve body 36 in the valve closing direction of the sub-valve is interposed between the power element 6 and the sub-valve body 36. Yes. The power element 6 includes a bellows 45 (which functions as a “pressure-sensitive member”) that senses and displaces the suction pressure Ps, and generates a force that opposes the solenoid force by the displacement of the bellows 45. This counter force is also transmitted to the main valve body 30 via the operating rod 38.

  On the other hand, the solenoid 3 includes a stepped cylindrical core 46, a bottomed cylindrical sleeve 48 assembled so as to seal the lower end opening of the core 46, and the sleeve 46 accommodated in the axial direction of the core 46. A cylindrical plunger 50 disposed opposite to the core 46, a cylindrical bobbin 52 extrapolated to the core 46 and the sleeve 48, an electromagnetic coil 54 wound around the bobbin 52 and generating a magnetic circuit by energization, and an electromagnetic coil A cylindrical case 56 provided so as to cover 54 from the outside and also functioning as a yoke, and an end member 58 provided so as to seal the lower end opening of the case 56 are provided. In the present embodiment, the body 5, the core 46, the case 56, and the end member 58 form the body of the entire control valve 1. Between the plunger 50 and the core 46, a spring 47 (functioning as an “urging member”) that biases the plunger 50 in a direction away from the core 46 is interposed.

  The valve body 2 and the solenoid 3 are fixed by press-fitting the lower end of the body 5 into the upper end opening of the core 46. A pressure chamber 28 is formed between the core 46 and the body 5. On the other hand, the operating rod 38 is inserted so as to penetrate the center of the core 46 in the axial direction. The lower end portion of the operating rod 38 is press-fitted into the upper half of the plunger 50, and the operating rod 38 and the plunger 50 are connected coaxially.

  The operating rod 38 is supported from below by the plunger 50 and is configured to be operatively connected to the main valve body 30, the sub-valve body 36 and the power element 6. The operating rod 38 appropriately transmits a solenoid force, which is a suction force between the core 46 and the plunger 50, to the main valve body 30 or the sub valve body 36. On the other hand, the actuating rod 38 is loaded with a driving force (also referred to as “pressure-sensitive driving force”) due to the expansion / contraction operation of the power element 6 so as to oppose the solenoid force. That is, in the control state of the main valve, the force adjusted by the solenoid force and the pressure-sensitive driving force acts on the main valve body 30 to appropriately control the opening degree of the main valve. When the main valve is closed, the operating rod 38 is displaced relative to the main valve body 30 according to the magnitude of the solenoid force, and the sub valve body 36 is pushed up to open the sub valve. As a result, the bleed function is exhibited.

  A ring-shaped shaft support member 60 is press-fitted into the upper end portion of the core 46, and the operating rod 38 is supported by the shaft support member 60 so as to be slidable in the axial direction. A communication groove (not shown) parallel to the axis is formed at a predetermined location on the outer peripheral surface of the shaft support member 60. The crank pressure Pc in the pressure chamber 28 is also guided to the inside of the sleeve 48 through the communication groove 62 and the communication passage 62 formed by the gap between the operating rod 38 and the core 46.

  The communication path 62 functions as an orifice for making the inside of the sleeve 48 an oil damper chamber. That is, in the present embodiment, in the manufacturing process of the control valve 1, oil of the same type as that contained in the refrigerant is lubricated in the sleeve 48 in advance for lubricating the compressor. In the present embodiment, the communication groove provided in the shaft support member 60 functions as a throttle passage that resists oil entering and exiting the sleeve 48. With such a configuration, the sleeve 48 can function as an oil damper chamber, and minute vibrations of the plunger 50 disposed in the sleeve 48 are suppressed. As a result, the generation of noise due to such minute vibration is prevented or suppressed. In the modified example, the communication path 62 may function as a throttle path that resists oil entering and exiting the sleeve 48. That is, at least one of the communication groove and the communication path 62 provided in the shaft support member 60 may function as a throttle path. Note that the spring 47 functions as an off-spring that urges the core 46 and the plunger 50 in a direction to separate them from each other.

  The sleeve 48 is made of a nonmagnetic material. Plural communicating grooves 66 parallel to the axis are provided on the side surface of the plunger 50, and plural communicating grooves 68 extending in the radial direction and communicating between the inside and the outside are provided on the lower end surface of the plunger 50. With such a configuration, the crank pressure Pc is guided to the back pressure chamber 70 through the gap between the plunger 50 and the sleeve 48 even when the plunger 50 is located at the bottom dead center as shown in the figure.

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

FIG. 2 is a partially enlarged cross-sectional view corresponding to the upper half of FIG.
The body 5 is configured by assembling a first body 81 and a second body 82. A main valve is provided inside the first body 81, and a sub valve is provided inside the second body 82. The first body 81 has a stepped cylindrical shape, and supports the main valve body 30 in a slidable manner through a guide hole 24 formed in the inside thereof. The second body 82 has a stepped cylindrical shape, and is fixed so that its lower half is inserted into the upper half of the first body 81. A communication hole 83 that communicates the inside and the outside is provided on the lower side portion of the second body 82. A port 14 is formed in an overlap portion between the first body 81 and the second body 82. The power element 6 is provided so as to be accommodated in the second body 82. The sub valve hole 32 is formed by slightly reducing the inner diameter of the lower end opening of the second body 82.

  A labyrinth seal 90 composed of a plurality of annular grooves for suppressing refrigerant flow is provided on the sliding surface of the main valve body 30 with the guide hole 24. The upper bottom portion of the main valve body 30 forms a partition wall 92, and its lower surface functions as an “engaged portion” that can be appropriately engaged and connected to the operating rod 38. The actuating rod 38 has a stepped columnar shape whose diameter gradually decreases upward, and the first engagement portion 94 is formed by the first step, and the second engagement portion 96 is formed by the second step. It is formed. An intermediate portion between the first engaging portion 94 and the second engaging portion 96 in the operating rod 38 passes through an insertion hole provided in the center of the partition wall 92. Further, a cylindrical locking member 98 is press-fitted into the intermediate portion. For this reason, the relative movement range of the partition wall 92 is restricted by the first engaging portion 94 and the locking member 98. That is, the first engaging portion 94 and the locking member 98 provided on the operating rod 38 function as a “regulating portion” that restricts the relative movement range of the main valve body 30. In the drawing, the state in which the partition wall 92 abuts on the locking member 98 and the main valve body 30 is positioned at the top dead center relative to the operating rod 38 is shown.

  With such a configuration, when the solenoid 3 is not energized, the operating rod 38 is pushed down by the urging force of the spring 47 (see FIG. 1). At this time, the locking member 98 abuts against the partition wall 92 and the main valve body. 30 is urged in the valve opening direction. As a result, the main valve is fully opened as shown in the figure. Even in the control state of the main valve, the main valve body 30 is basically integrated with the operating rod 38 via the locking member 98 by the biasing force of the spring 42 and is operatively connected. In the state where the partition wall 92 is in contact with the locking member 98 as shown in the drawing, the operating rod 38 is positioned at the first step so that the first engagement portion 94 is separated from the partition wall 92 with a predetermined interval L1. Is set. The predetermined interval L1 functions as a so-called “play”.

  On the other hand, the diameter of the lower part of the second body 82 is reduced, and the auxiliary valve hole 32 is formed inside thereof. A sub valve seat 34 is formed at the upper end opening of the sub valve hole 32. The sub-valve element 36 has a stepped columnar shape, and a through hole 41 is provided along the axis. The upper end portion of the operating rod 38 passes through the through hole 41 and is connected to the power element 6. When the auxiliary valve is closed, the operating rod 38 can be displaced relative to the auxiliary valve body 36. The auxiliary valve body 36 is disposed so that its main body penetrates the auxiliary valve hole 32, and the upper end portion extends outward in the radial direction to constitute an attaching / detaching portion 43. The attachment / detachment portion 43 attaches / detaches to / from the auxiliary valve seat 34 from the pressure chamber 22 side to open / close the auxiliary valve. The second engaging portion 96 provided on the upper portion of the operating rod 38 functions as a pressing portion. That is, the second engaging portion 96 is separated from the sub-valve element 36 in the illustrated state, but the operating rod 38 is engaged with the bottom surface of the sub-valve element 36 by relative displacement with respect to the body 5. The solenoid force in the valve opening direction of the auxiliary valve can be directly transmitted to the auxiliary valve body 36.

  In the present embodiment, the distance L2 between the second engagement portion 96 of the actuating rod 38 and the sub valve body 36 when the main valve is fully opened is equal to the lift amount of the main valve body 30 from the main valve seat 20. The position of the second step is set. This prevents the auxiliary valve from opening until the main valve is closed, and promptly opens the auxiliary valve after the main valve is closed. That is, according to this configuration, the main valve body 30 is seated on the main valve seat 20 and the main valve is closed, and at the same time, the second engagement portion 96 is engaged with the sub valve body 36. For this reason, after closing the main valve, the sub rod body 36 can be pushed up by opening the sub valve by moving the operating rod 38 relative to the main valve body 30. However, the lift amount of the auxiliary valve body 36 from the auxiliary valve seat 34 is up to a height equal to the predetermined interval L1. The setting of the predetermined intervals L1 and L2 in the present embodiment, the structures of the main valve body 30, the sub-valve body 36, and the operating rod 38 for realizing them and their arrangement configuration constitute an “operation switching mechanism”. .

  In the modification, the interval L2 may be slightly larger than the lift amount of the main valve body 30 when the main valve is fully opened, and may be smaller than a value obtained by combining the lift amount and the predetermined interval L1. Thereby, an appropriate margin can be provided from when the main valve is closed to when the sub valve is opened. That is, even in the control state of the main valve, in some cases, the main valve may be temporarily moved to the maximum capacity operation by closing the main valve. Can be maintained stably.

  The power element 6 has an upper end opening of the bellows 45 closed by a first stopper 84 (corresponding to a “base member”) and a lower end opening closed by a second stopper 86 (corresponding to a “base member”). It is configured. The first stopper 84 has a stepped columnar shape and extends in the axial direction inside the bellows 45. The second stopper 86 has a disc shape, and the center portion of the upper surface thereof is disposed opposite to the lower end surface of the first stopper 84. The inside of the bellows 45 is a sealed reference pressure chamber S, and a spring 88 that biases the bellows 45 in the extending direction is interposed between the first stopper 84 and the second stopper 86. The reference pressure chamber S is in a vacuum state in this embodiment. The first stopper 84 is integrally formed with the end member 13. Therefore, the first stopper 84 is fixed to the body 5. The bellows 45 extends or contracts in the axial direction (opening / closing direction of the main valve) according to the differential pressure between the suction pressure Ps of the pressure chamber 22 and the reference pressure of the reference pressure chamber S. However, even if the differential pressure increases, if the bellows 45 contracts by a predetermined amount, the second stopper 86 comes into contact with the first stopper 84 and is locked, so that the contraction is restricted.

  In the present embodiment, the bottom surface of the second stopper 86 is a flat surface, but the upper end surface of the operating rod 38 has an R shape. For this reason, when the operating rod 38 is operatively connected to the power element 6, the operating rod 38 and the second stopper 86 are substantially in point contact. For this reason, even if a lateral load is generated in one of the actuating rod 38 and the power element 6, the lateral load is unlikely to act on the other, and the behavior of each valve body that is operatively connected is stably maintained. A spring 44 is interposed between the sub valve body 36 and the second stopper 86.

  In the above configuration, the main valve body 30 and the main valve seat 20 constitute a main valve, and the flow rate of the refrigerant introduced from the discharge chamber to the crank chamber is adjusted by the opening of the main valve. Further, the auxiliary valve body 36 and the auxiliary valve seat 34 constitute an auxiliary valve, and the opening and closing of the auxiliary valve permits or blocks the refrigerant from the crank chamber to the suction chamber. That is, the control valve 1 also functions as a three-way valve that switches the flow of the refrigerant by opening one of the main valve and the sub valve.

  In the present embodiment, the effective pressure receiving diameter B (seal part diameter) of the main valve body 30 in the main valve is set equal to the effective pressure receiving diameter C (seal part diameter) of the sliding part of the main valve body 30. . For this reason, the influence of the discharge pressure Pd, the crank pressure Pc and the suction pressure Ps acting on the main valve body 30 is cancelled. As a result, the main valve body 30 opens and closes based on the suction pressure Ps of the pressure chamber 22 in the control state of the main valve. That is, the control valve 1 functions as a so-called Ps sensing valve. In the present embodiment, the effective pressure receiving diameter A (seal portion diameter) of the auxiliary valve body 36 in the auxiliary valve is larger than the effective pressure receiving diameter B of the main valve element 30 in the main valve. The magnitude relationship (that is, the magnitude relationship between the main valve and the subvalve) can be set as appropriate according to the specifications of the control valve 1.

  In such a configuration, when the control valve 1 is in a stable control state, the main valve operates autonomously so that the suction pressure Ps of the pressure chamber 22 becomes the predetermined set pressure Pset. This set pressure Pset is basically adjusted in advance by the spring load of the springs 42, 44, 47, 88 and the load of the bellows 45, and the evaporator is frozen from the relationship between the temperature in the evaporator and the suction pressure Ps. It is set as a pressure value that can be prevented. The set pressure Pset can be changed by changing the supply current (set current) to the solenoid 3. In this embodiment, the set load of the spring can be finely adjusted by readjusting the press-fitting amount of the end member 13 with the assembly of the control valve 1 substantially completed, and the set pressure Pset is accurately adjusted. be able to.

  On the other hand, when the solenoid force is increased, the actuating rod 38 is relatively displaced with respect to the body 5 even after the main valve is closed, whereby the sub valve body 36 is lifted from the sub valve seat 34 to open the sub valve. it can. Further, the solenoid force can be directly transmitted to the main valve body 30 in a state where the first engagement portion 94 is engaged (contacted) with the partition wall 92, and the main valve body with a force larger than the urging force of the spring 42. 30 can be pressed in the valve closing direction of the main valve. This configuration can also be used as an unlocking mechanism (an interlocking mechanism, a pressing mechanism) for releasing the main valve body 30 when the main valve body 30 is locked by the foreign matter biting into the sliding portion between the main valve body 30 and the guide hole 24. Function.

Next, the operation of the control valve will be described.
3 and 4 are diagrams showing the operation of the control valve, and correspond to FIG. FIG. 2 which has already been described shows the minimum capacity operation state of the control valve. FIG. 3 shows a state when the bleed function of the control valve is operated. FIG. 4 shows a relatively stable control state. In the following, description will be given based on FIG. 1 and with reference to FIGS.

  When the solenoid 3 is not energized in the control valve 1, that is, when the automotive air conditioner is not operating, no suction force acts between the core 46 and the plunger 50. On the other hand, the suction pressure Ps is relatively high. For this reason, as shown in FIG. 2, the bellows 45 shrinks and the power element 6 does not function substantially. Further, the urging force of the spring 47 is transmitted to the main valve body 30 via the locking member 98, the main valve body 30 is separated from the main valve seat 20, and the main valve is fully opened. On the other hand, the sub-valve element 36 is kept seated on the sub-valve seat 34 by the biasing force of the spring 44, and the sub-valve maintains the closed state.

  On the other hand, when a control current is supplied to the electromagnetic coil 54 of the solenoid 3 such as when the automobile air conditioner is activated, the operating rod 38 is driven upward by the solenoid force. As a result, as shown in FIG. 3, the main valve body 30 is seated on the main valve seat 20 and closes the main valve. Further, when the operating rod 38 is displaced relative to the main valve body 30 against the urging force of the spring 42, the second engaging portion 96 engages with the sub-valve body 36 and pushes it up. 36 separates from the auxiliary valve seat 34 and opens the auxiliary valve. However, since the displacement of the actuating rod 38 is restricted when the first engaging portion 94 is locked to the partition wall 92, the lift amount of the sub valve body 36 (that is, the opening degree of the sub valve) is also regulated. In addition, since the suction pressure Ps is usually relatively high at the time of startup, the bellows 45 maintains the contracted state and the auxiliary valve is maintained open.

  That is, when a starting current is supplied to the solenoid 3, the main valve is closed to restrict the introduction of the refrigerant discharged into the crank chamber, and the sub valve is opened to quickly relieve the refrigerant in the crank chamber to the suction chamber. As a result, the compressor can be started quickly. Even when the suction pressure Ps is low and the bellows 45 is extended, for example, when the vehicle is placed in a low temperature environment, the auxiliary valve can be opened by supplying a large current to the solenoid 3. And the compressor can be started quickly.

  When the current value supplied to the solenoid 3 is in a control state set to a predetermined value, as shown in FIG. 4, since the suction pressure Ps is relatively low, the bellows 45 is extended, and the main valve body 30 is Operates to adjust the opening of the main valve. At this time, the main valve body 30 operates in accordance with the force in the valve opening direction by the spring 47, the force in the valve closing direction by the spring 42, the solenoid force in the valve closing direction by the solenoid 3, and the suction pressure Ps. Stops at the valve lift position where the force against the solenoid force due to 6 is balanced. In the control state of the main valve, the auxiliary valve body 36 is kept seated on the auxiliary valve seat 34 by the urging force of the spring 44, so the closed state of the auxiliary valve is maintained.

  For example, when the refrigeration load increases and the suction pressure Ps becomes higher than the set pressure Pset, the bellows 45 is reduced, so that the main valve body 30 is displaced relatively upward (in the valve closing direction). As a result, the valve opening of the main valve decreases, and the compressor operates to increase the discharge capacity. As a result, the suction pressure Ps changes in a decreasing direction. Conversely, when the refrigeration load is reduced and the suction pressure Ps is lower than the set pressure Pset, the bellows 45 extends. As a result, the urging force by the power element 6 acts in a direction opposite to the solenoid force. As a result, the force in the valve closing direction on the main valve body 30 is reduced, the valve opening of the main valve is increased, and the compressor operates to reduce the discharge capacity. As a result, the suction pressure Ps is maintained at the set pressure Pset.

  When such steady control is being performed, the load on the engine increases, and when it is desired to reduce the load on the air conditioner, the solenoid 3 in the control valve 1 is switched from on to off. As a result, no suction force acts between the core 46 and the plunger 50, so that the main valve body 30 is separated from the main valve seat 20 by the biasing force of the spring 47, and the main valve is fully opened. At this time, since the auxiliary valve body 36 is seated on the auxiliary valve seat 34, the auxiliary valve is closed. At this time, the refrigerant having the discharge pressure Pd introduced from the compressor discharge chamber to the port 16 passes through the fully opened main valve and flows from the port 14 to the crank chamber. Therefore, the crank pressure Pc is increased and the compressor is operated at the minimum capacity.

  As described above, in the present embodiment, the auxiliary valve hole 32 and the auxiliary valve seat 34 are not formed in the main valve body 30 but are formed in a part of the body 5. For this reason, regardless of the size of the main valve body 30, the sizes of the auxiliary valve hole 32 and the auxiliary valve body 36 can be set. That is, the size of the sub valve can be set regardless of the size of the main valve. Then, in the control state of the main valve, the opening degree of the main valve is adjusted by displacing the operating rod 38 integrally with the main valve body 30 while maintaining the closed state of the auxiliary valve. Even after the main valve is closed, the sub-valve can be opened by the solenoid force by displacing the operating rod 38 relative to the main valve body 30. In other words, the operation of the operation switching mechanism accompanying the driving of the solenoid 3 can control the opening and closing of the main valve and the sub valve independently, and can sufficiently secure the flow rate when the sub valve is opened. For this reason, it is possible to increase the refrigerant flow rate by increasing the sub-valve, thereby enhancing the bleed function.

[Second Embodiment]
FIG. 5 is a partially enlarged cross-sectional view corresponding to the upper half of the control valve according to the second embodiment. The control valve of the present embodiment is slightly different from the first embodiment in the configuration of the valve body. For this reason, below, it demonstrates centering on difference with 1st Embodiment. In the figure, the same components as those in the first embodiment are denoted by the same reference numerals.

  In the control valve 201, in addition to the port 12, a port 212 (functioning as “another suction chamber communication port”) connected to the suction chamber is provided in the body 205 of the valve body 202. That is, the port 212 is provided in the intermediate portion in the axial direction of the guide hole 224 in the first body 281. On the other hand, a concave groove 232 is provided around the outer peripheral surface of the main valve body 230 facing the port 212. As a result, a pressure chamber 222 communicating with the port 212 is formed between the main valve body 230 and the guide hole 224. In the present embodiment, the body 205, the core 46, the case 56, and the end member 58 form the body of the entire control valve 201. In this embodiment, the concave groove 232 is provided on the guide hole 224 side, but may be provided on the main valve body 230 side. Alternatively, the concave groove 232 can be omitted by using the port 212 itself as the pressure chamber 222.

  With such a configuration, even if the high-pressure discharged refrigerant introduced from the port 16 attempts to leak into the guide hole 224, it can be guided to the pressure chamber 222 and led out from the port 212. That is, the leaked refrigerant can be prevented from entering the pressure chamber 28 and affecting the crank pressure Pc. Further, since the leakage portion from the discharge chamber to the crank chamber can be only the valve portion of the main valve, the maximum displacement operation can be maintained and the deviation of the suction pressure Ps from the set pressure Pset in the control state can be reduced. . As a result, a stable control state of the main valve can be maintained.

  In order to realize such a configuration, the main valve body 230 is longer in the axial direction than the main valve body 30 of the first embodiment. In addition, a partition wall 92 is provided at an intermediate portion in the axial direction of the main valve body 230. On the other hand, the auxiliary valve hole 32 formed in the second body 282 is made smaller than that of the first embodiment. The effective pressure receiving diameter A (seal part diameter) of the sub valve of the sub valve body 236 is made equal to the effective pressure receiving diameter B (seal part diameter) of the main valve of the main valve body 330. In the modification, the effective pressure receiving diameter A may be larger than the effective pressure receiving diameter B.

[Third Embodiment]
FIG. 6 is a partially enlarged cross-sectional view corresponding to the upper half of the control valve according to the third embodiment. The control valve of this embodiment is different from the second embodiment in the configuration of the valve body. For this reason, below, it demonstrates centering on difference with 2nd Embodiment. In the figure, the same components as those in the second embodiment are denoted by the same reference numerals.

  In the control valve 301, the suction pressure Ps is introduced into the pressure chamber 28 in the valve body 302. This suction pressure Ps is also introduced into the solenoid 3. That is, a communication hole 335 is formed in the concave groove 232 of the main valve body 330 to communicate the inside and outside. The communication hole 335 also communicates with the front and rear of the partition wall 92. On the other hand, the auxiliary valve body 336 extends downward, and the lower part thereof is inserted into the upper end opening of the main valve body 330. The sub-valve body 336 is formed with an internal passage 340 that allows the pressure chamber 22 and the internal passage 37 of the main valve body 330 to communicate with each other.

  With such a configuration, the pressure chamber 22 and the pressure chamber 28 are communicated with each other through the internal passages of the auxiliary valve body 336 and the main valve body 330. As a result, the suction pressure Ps introduced through the port 12 or the port 212 is also introduced into the solenoid 3. On the other hand, the differential pressure (Pc−Ps) between the crank pressure Pc and the suction pressure Ps acts on the main valve body 330 and the sub-valve body 336, respectively, but the loads of the springs 42, 44, etc. are appropriately set. It is considered that there is no problem in practical use.

[Fourth Embodiment]
FIG. 7 is a partially enlarged cross-sectional view corresponding to the upper half of the control valve according to the fourth embodiment. The control valve of this embodiment differs from the third embodiment in the configuration of the valve body. For this reason, below, it demonstrates centering on difference with 3rd Embodiment. In the figure, the same components as those in the third embodiment are denoted by the same reference numerals.

  The control valve 401 uses the port 212 of the third embodiment as the port 14 and communicates with the crank chamber instead of the suction chamber. As a result, the arrangement of the ports connected to the compressor is different from that of the third embodiment. An annular strainer 417 is attached to the port 16. The strainer 417 includes a filter for suppressing entry of foreign matter into the body 405. The body 405 is composed of a single body, and the main valve hole 18 and the sub valve hole 32 are integrally formed in the body 405 as a common valve hole. The internal passage 37 of the main valve body 330 constitutes both a main passage and a sub passage. With such a configuration, the entire control valve 401 can be configured compactly.

  The spring receiving member 25 is press-fitted into the body 405, and the spring 44 is interposed between the spring receiving member 25 and the sub valve body 436. With such a configuration, the load adjustment of the spring 44 alone can be easily performed by adjusting the press-fitting amount of the spring receiving member 25.

[Fifth Embodiment]
FIG. 8 is a partially enlarged cross-sectional view corresponding to the upper half of the control valve according to the fifth embodiment. The control valve of this embodiment is slightly different from the fourth embodiment in the configuration of the valve body. For this reason, below, it demonstrates centering on difference with 4th Embodiment. In the figure, the same components as those in the fourth embodiment are denoted by the same reference numerals.

  The control valve 501 is provided with a seal structure for preventing leakage of the refrigerant from the port 16 to the port 14 in the body 505 of the valve body 502. That is, a seal accommodating portion 510 formed of an annular concave groove is provided at the upper end portion of the guide hole 224, and an O-ring 520 as a seal member is fitted. The O-ring 520 seals the gap between the main valve body 330 and the guide hole 224, and regulates refrigerant leakage from the valve chamber 26 to the pressure chamber 222 and thus to the pressure chamber 28. On the other hand, a gap is formed between the main valve body 330 and the guide hole 224 in the front and rear of the seal housing portion 510. The high-pressure side clearance CL1 on the valve chamber 26 side of the seal housing portion 510 is on the pressure chamber 222 side. It is comprised so that it may become larger than the low voltage | pressure side clearance CL2. In the present embodiment, the high-pressure side clearance CL1 is set larger than the width of the filter mesh of the strainer 417. On the other hand, the low pressure side clearance CL2 is set smaller than the width of the mesh of the filter.

  With such a configuration, when a differential pressure acts on the O-ring 520, the O-ring 520 is pressed against the seal housing 510 so as to close the low-pressure side clearance CL2. As a result, the sealing performance of the sliding portion of the main valve body 330 can be maintained satisfactorily. Further, since the low pressure side clearance CL2 is relatively small, even if the O-ring 520 is deformed, there is no problem of increasing the sliding resistance by being sandwiched by the low pressure side clearance CL2. On the other hand, since the high-pressure-side clearance CL1 is relatively large, even if a foreign object enters from the high-pressure side, the occurrence of the foreign object can be prevented or suppressed. As a result, the smooth operation of the main valve body 330 can be maintained. By providing the strainer 417, foreign matter that enters the body 405 in the first place is restricted to a sufficiently small amount with respect to the high-pressure side clearance CL1. Further, the amount of foreign matter introduced between the main valve body 330 and the guide hole 224 is suppressed. As a result, it is difficult for foreign matter to be caught.

  In addition, a gap is formed between the bottom surface of the seal housing portion 510 and the O-ring 520. With such a configuration, even if the O-ring 520 is compressed in the axial direction due to the differential pressure across the front and rear, and as a result, the O-ring 520 receives a reaction force from the bottom surface of the seal housing portion 510 even if the O-ring 520 increases outward in the radial direction. It has a difficult structure. Thereby, the sliding resistance between the O-ring 520 and the main valve body 330 is prevented from becoming excessive, and the smooth operation of the main valve body 330 is maintained.

  In the present embodiment, an example in which the O-ring 520 is provided on the guide hole 224 side is shown, but it may be provided on the main valve body 330 side. Further, a seal ring other than an O-ring or a seal washer may be used as the seal member, or a seal member made of polytetrafluoroethylene (PTFE) or the like may be employed. In the present embodiment, a gap is formed between the bottom surface of the seal housing portion 510 and the O-ring 520. However, such a gap may not be provided.

[Sixth Embodiment]
FIG. 9 is a partial enlarged cross-sectional view corresponding to the upper half of the control valve according to the sixth embodiment. The control valve of the present embodiment is slightly different from the first embodiment in the arrangement configuration of the auxiliary valves. For this reason, below, it demonstrates centering on difference with 1st Embodiment. In the figure, the same components as those in the first embodiment are denoted by the same reference numerals.

  The control valve 601 is configured by assembling a first body 681 and a second body 682 on a body 605 of a valve body 602. A main valve is provided inside the second body 682, and a sub-valve is provided between the first body 681 and the second body 682. That is, the positional relationship between the main valve and the sub valve is different from that of the first embodiment.

  The second body 682 is fixed so that its lower half is inserted into the upper half of the first body 681. A sub valve hole 32 is formed below the second body 682 in the first body 681. The sub valve body 636 has a bottomed cylindrical shape, and is slidably inserted at the lower end portion of the second body 682. A port 16 is formed on the upper half side of the overlap portion between the first body 681 and the second body 682. On the other hand, a pressure chamber 27 is formed on the lower half side of the overlap portion between the first body 681 and the second body 682. The first body 681 is provided with a port 14 so that the inside and outside of the pressure chamber 27 communicate with each other. The sub valve body 636 is disposed in the pressure chamber 27. The first body 681 is also provided with a port 17 so that the inside and outside of the pressure chamber 28 communicate with each other. The port 17 communicates with the suction chamber and introduces the suction pressure Ps.

  On the other hand, the main valve body 630 has a stepped cylindrical shape, and functions as a guide hole 24 provided in the center portion of the second body 682 and a guide hole 624 provided in the lower end portion (a “second guide hole”). ) And is slidably supported in the axial direction. The outer diameter of the intermediate portion in the axial direction of the main valve body 630 is reduced, and an attachment / detachment portion that opens and closes the main valve seat 20 to open and close the main valve is configured by the lower base end portion of the reduced diameter portion. Yes. A labyrinth seal 90 is provided on the surface of the main valve body 630 facing the guide hole 24. The pressure chamber 22 is formed above the main valve body 630.

  A through hole 41 is provided in the center of the bottom of the sub valve body 636, and an operating rod 38 is provided so as to penetrate the sub valve body 636 and the main valve body 630. A locking member 698 is fixed to an intermediate portion of the operating rod 38, and an upper surface thereof forms an engaging portion 696. When the actuating rod 38 moves upward and the locking member 698 engages the lower surface of the sub-valve element 636, an upward force (the valve opening direction of the sub-valve) is transmitted to the sub-valve element 636. A locking member 699 is also fixed to the upper end portion of the operating rod 38. When the operation rod 38 moves downward and the locking member 699 engages with the upper surface of the main valve body 630, a downward force (the valve opening direction of the main valve) is transmitted to the main valve body 630.

  The sub valve body 636 is disposed so as to be sandwiched between the lower surface of the main valve body 630 and the engaging portion 696. A spring 44 is provided between the main valve body 630 and the sub-valve body 636 to urge them in a direction away from each other. A plurality of communication holes 635 are provided in the vicinity of the periphery of the bottom portion of the sub valve body 636. A space surrounded by the second body 682, the main valve body 630, and the sub valve body 636 forms a pressure chamber 690. The suction pressure Ps of the pressure chamber 28 is also introduced into the pressure chamber 690 via the communication hole 635.

  In the present embodiment, when the main valve is fully opened (when the subvalve is closed), the engaging portion 696 is arranged such that the engaging portion 696 of the actuating rod 38 and the subvalve body 636 are separated by a predetermined interval L1. The position of is set. In the present embodiment, the predetermined interval L1 is made to coincide with the lift amount from the main valve seat 20 of the main valve body 630 when the main valve is fully opened. This prevents the auxiliary valve from being opened in the control state of the main valve. Further, the distance between the sub valve body 636 and the main valve body 630 when the main valve is closed is the fully open stroke of the sub valve.

  In this embodiment, the effective pressure receiving diameter B (seal part diameter) of the main valve body 630 in the main valve is set equal to the effective pressure receiving diameter C (seal part diameter) of the upper sliding part of the main valve body 630. ing. For this reason, the influence of the discharge pressure Pd acting on the main valve body 630 is cancelled. On the other hand, the effective pressure receiving diameter D (seal portion diameter) of the lower sliding portion of the main valve body 630 is set larger than the effective pressure receiving diameter C (sealing portion diameter) of the upper sliding portion. A differential pressure (Pc−Ps) in the valve opening direction corresponding to the difference in diameter (C−D) acts on the body 630. Further, the auxiliary valve body 636 has an effective pressure receiving diameter A (seal part diameter) in the auxiliary valve of the auxiliary valve body 636 and an effective pressure receiving diameter E (seal part diameter) of the sliding part of the auxiliary valve body 636. The differential pressure (Pc−Ps) in the valve closing direction corresponding to the difference (A−E) is applied.

  In such a configuration, when the main valve body 630 is locked due to foreign matter being caught in the sliding portion between the main valve body 630 and the guide hole, the engaging portion 696 presses the sub-valve body 636 by the solenoid force. Then, by opening the valve, and further pressing the main valve body 630 in the valve closing direction via the sub-valve body 636, the lock can be released. According to this embodiment, since the auxiliary valve hole 32 is provided in the first body 681 having a larger diameter than the second body 682, the auxiliary valve can be enlarged.

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

  In each of the above embodiments, the first engagement portion 94 is configured using the step provided on the operating rod 38, and the main valve body 30, 230, 330 can be directly pressed by the first engagement portion 94. In the modified example, for example, by sufficiently increasing the spring load or the spring constant of the spring 42, the solenoid force may be largely transmitted to the main valve body through the spring 42 (elastic body). In other words, it is desirable to directly apply the solenoid force to the main valve body, but it is possible to release the lock even in such a configuration that it is indirectly applied through the elastic body.

  In each of the above embodiments, a so-called Ps sensing valve that operates by sensing the suction pressure Ps is shown as the control valve. However, it may be configured as a so-called Pc sensing valve that operates by sensing the crank pressure Pc. In that case, the port 12 is communicated with the crank chamber.

  In the said embodiment, although the example which employ | adopts the bellows 45 as a pressure-sensitive member which comprises the power element 6 was shown, you may employ | adopt a diaphragm. In this case, a plurality of diaphragms may be connected in the axial direction in order to ensure an operation stroke necessary for the pressure sensitive member.

  In each of the above embodiments, an example in which a single port 14 is provided as a crank chamber communication port (introduction / exit port) communicating with the crank chamber has been described. In the modification, the crank chamber communication port is divided into a first port (outlet port) for leading the refrigerant that has passed through the main valve to the crank chamber, and a second port (inlet port) for introducing the refrigerant in the crank chamber. It may be configured.

  In the above-described embodiment, the spring (coil spring) is exemplified as the biasing member with respect to the springs 42, 44, 47, 78 and the like. However, an elastic material such as rubber or resin, or an elastic mechanism such as a leaf spring may be employed. Needless to say, it is good.

  In the above embodiment, a control valve for so-called closing control that adjusts the flow rate or pressure of the refrigerant introduced from the discharge chamber of the variable capacity compressor to the crank chamber has been shown. However, in a modified example, the control valve is led out from the crank chamber to the suction chamber. You may comprise as a control valve of what is called extraction control which adjusts the flow volume or pressure of the refrigerant | coolant to perform. Further, for example, the configuration of the above embodiment can be applied as long as it is a compound valve in which a main valve and a subvalve are provided in a common body, such as a three-way valve of another form, and is driven by a single solenoid. .

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

  1 control valve, 2 valve body, 3 solenoid, 5 body, 6 power element, 12, 14, 16 port, 18 main valve hole, 20 main valve seat, 22 pressure chamber, 24 guide hole, 26 valve chamber, 27, 28 Pressure chamber, 30 main valve body, 32 sub valve hole, 34 sub valve seat, 35 communication hole, 36 sub valve body, 38 operating rod, 42, 44 spring, 92 partition, 94 first engaging portion, 96 second engagement Joint, 98 Locking member, 201 Control valve, 202 Valve body, 205 Body, 212 port, 222 Pressure chamber, 224 Guide hole, 230 Main valve body, 236 Sub valve body, 301 Control valve, 302 Valve body, 330 Main Valve body, 336 sub-valve body, 401 control valve, 405 body, 436 sub-valve body, 501 control valve, 502 valve body, 505 body, 510 seal housing portion, 520 O-ring, 601 control valve, 602 valve body, 605 body, 630 main valve body, 636 sub-valve body, 696 engaging portion.

Claims (10)

A body provided with an introduction port for introducing or deriving the working fluid, an introduction port for introducing the working fluid, and a deriving port for deriving the working fluid;
A main valve provided in a main passage communicating the introduction port and the introduction / exit port;
A sub-valve provided in a sub-passage for communicating the introduction / exit port and the outlet port;
A main valve body that is slidably supported by the body and opens and closes the main valve seat attached to and detached from a main valve seat provided in the main passage;
A sub-valve element that opens and closes the sub-valve by attaching to and detaching from a sub-valve seat provided in the sub-passage;
A solenoid that generates a solenoid force having a magnitude corresponding to the amount of current supplied;
An operating rod connected to the solenoid and capable of transmitting a solenoid force directly or indirectly to the main valve body and the sub-valve body;
With
The auxiliary valve seat is formed on a part of the body;
In the control state of the main valve, the operating rod is integrally displaced with the main valve body while maintaining the closed state of the sub-valve, and the operating rod remains in the main valve body even after the main valve is closed. A control valve further comprising an operation switching mechanism for displacing the sub-valve element in the valve opening direction by relative displacement. The actuating rod and the auxiliary valve body are relatively displaceable in a control state of the main valve;
The actuating rod has an engaging portion capable of engaging with the sub-valve body by being relatively displaced with respect to the body, and capable of directly transmitting a solenoid force in the valve opening direction of the sub-valve to the sub-valve body. The control valve according to claim 1.   The operation switching mechanism is configured such that the interval between the engaging portion of the operating rod and the sub valve body is equal to or greater than the lift amount of the main valve body from the main valve seat, regardless of the open / closed state of the main valve. The control valve according to claim 2, wherein the control valve is held by the valve.   The control valve according to claim 3, wherein a restriction portion for restricting a relative movement range of the main valve body is provided on the operating rod.   The control valve according to any one of claims 1 to 4, wherein a seal portion diameter of the sub valve body is set larger than a seal portion diameter of the main valve body.   The pressure mechanism which increases the load which presses the said main valve body in the valve closing direction of the said main valve by displacing the said operating rod with respect to the said main valve body is provided. The control valve according to any one of the above. At least of the refrigerant introduced into the crank chamber from the discharge chamber and the refrigerant led out from the crank chamber to the suction chamber, the discharge capacity of the variable capacity compressor that compresses the refrigerant introduced into the suction chamber and discharges it from the discharge chamber It is configured as a control valve for a variable capacity compressor that is changed by adjusting one flow rate or pressure,
A crank chamber communication port communicating with the crank chamber as the introduction / exit port, a discharge chamber communication port communicating with the discharge chamber as the introduction port, and a suction chamber communication port communicating with the suction chamber as the lead-out port are provided. Said body,
The suction pressure of the suction chamber or the crank pressure of the crank chamber is sensed as a sensed pressure, and when the sensed pressure becomes lower than a set pressure, a force in the valve opening direction acts on the main valve body via the actuating rod. A pressure sensitive part,
The control valve according to claim 1, comprising: A capacity chamber that is filled with crank pressure by communicating with the discharge chamber communication port is formed in a space defined by the sub valve body in the body,
The influence of the pressure of the refrigerant acting on the main valve body is canceled by arranging the main valve body so as to receive the pressure of the capacity chamber in the opening / closing direction of the main valve. Item 8. The control valve according to Item 7. A guide portion is formed between the discharge chamber communication port and the crank chamber communication port of the body so as to slidably support the main valve body,
The seal member for restricting leakage of the refrigerant from the discharge chamber communication port to the crank chamber communication port is provided between the guide portion and the main valve body. The control valve described. A guide portion is formed between the discharge chamber communication port and the crank chamber communication port of the body so as to slidably support the main valve body,
The control valve according to claim 7, wherein another suction chamber communication port communicating with the suction chamber is provided in the middle of the guide portion.

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