JP6064181B2 - Control valve for variable capacity compressor - Google Patents

Description

  The present invention relates to a control valve, and more particularly to a control valve suitable for controlling the discharge capacity of a variable capacity compressor.

  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 large flow rate can be obtained when the sub valve is opened. Objective.

  In order to solve the above problems, a control valve for a variable capacity compressor according to an aspect of the present invention provides a discharge capacity of a variable capacity compressor that compresses a refrigerant introduced into a suction chamber and discharges the refrigerant from the discharge chamber. The discharge chamber and the crank chamber communicate with each other in a control valve for a variable capacity compressor that is changed by adjusting the flow rate or pressure of at least one of the refrigerant introduced into the crank chamber and the refrigerant introduced from the crank chamber into the suction chamber A body formed with a main passage, a sub-passage communicating the crank chamber and the suction chamber, a main valve seat provided in the main passage, and a main valve body that is attached to and detached from the main valve seat to open and close the main valve; A sub-valve seat provided in the sub-passage, a sub-valve element that opens and closes the sub-valve by attaching to and detaching from the sub-valve seat, and a main valve that receives a predetermined sensed pressure and that corresponds to the magnitude of the sensed pressure A pressure sensing unit that generates a driving force in the valve opening direction, and Comprising a solenoid for generating the closing direction of the driving force of the main valve in accordance with the amount, the. A pressure sensitive part is disposed on one side with respect to the main valve body, and a solenoid is disposed on the other side with respect to the main valve body. The sub valve seat is provided integrally with the body, and the seal portion diameter of the sub valve of the sub valve body is larger than the seal portion diameter of the main valve of the main valve body.

  In this aspect, in the configuration in which the main valve body is disposed between the pressure sensing portion and the solenoid in the body, the sub valve seat is formed in the body instead of the main valve body, and the size of the sub valve is the size of the main valve. It is configured not to be restricted by this. And the subvalve is enlarged independently of the main valve. For this reason, a large flow rate can be obtained when the auxiliary valve is opened.

  Another aspect of the present invention is also a control valve. The control valve includes an introduction / exit port for introducing or deriving a working fluid, an introduction port for introducing the working fluid, a body provided with a deriving port for deriving the working fluid, and a main passage that communicates the introduction port and the introduction / extraction port. A main valve provided in the main passage, a sub-valve provided in a sub-passage for communicating the introduction / exit port and the lead-out port, a predetermined sensed pressure, and a main valve according to the magnitude of the sensed pressure. A pressure sensing unit that generates driving force in the valve opening direction; and a solenoid that generates driving force in the valve closing direction of the main valve in accordance with the amount of current supplied. A pressure sensitive part is disposed on one side of the main valve, and a solenoid is disposed on the other side of the main valve. The secondary valve is larger than the main valve.

  In this aspect, in the configuration in which the main valve is disposed between the pressure-sensitive part and the solenoid in the body, the sub valve is made larger than the main valve. For this reason, a large flow rate can be obtained when the auxiliary valve 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 large flow rate can be obtained 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.

  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 vaporization. The refrigerant evaporated in the evaporator is returned again to the compressor and circulates in the refrigeration cycle. The compressor has a rotating shaft that is rotationally driven by an automobile engine, and a compression piston is connected to a swing plate attached to the rotating shaft. The refrigerant discharge amount is adjusted by changing the stroke of the piston by changing the angle of the swing plate. The control valve 1 controls the 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, 16, and 18 from its upper end side. Among these, the port 12 is provided in the upper end opening of the body 5, and the ports 14, 16, and 18 are provided in the side of the body 5. Ports 12 and 18 function as “suction chamber communication ports” that communicate with the suction chamber, port 14 functions as “discharge chamber communication port” that communicates with the discharge chamber, and port 16 communicates with “crank chamber communication” that communicates with the crank chamber. Functions as a "port". 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 14 and the port 16 and a sub passage that communicates the port 16 and the port 18 are formed. The main passage is provided with a small-diameter main valve, and the sub-passage is provided with a large-diameter sub-valve. The auxiliary valve is arranged coaxially below the main valve, that is, on the side closer to the solenoid 3 than the main valve. That is, as shown in the figure, the control valve 1 has a configuration in which a power element 6, a main valve, a sub valve, and a solenoid 3 are sequentially arranged from one end side. A main valve hole 20 and a main valve seat 22 are provided in the main passage. A sub valve hole 32 and a sub valve seat 34 are provided in the sub passage.

  The port 12 communicates the pressure chamber 23 defined in the upper part of the body 5 with the suction chamber, and introduces the refrigerant having the suction pressure Ps into the pressure chamber 23. The power element 6 is disposed in the pressure chamber 23. The port 14 introduces a refrigerant having a discharge pressure Pd from the discharge chamber. The port 16 guides the refrigerant having the crank pressure Pc via the main valve toward the crank chamber during the 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 18 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 sub valve toward the suction chamber when the compressor is started.

  The main valve hole 20 and the sub valve hole 32 are formed coaxially, and the pressure chamber 24 between the main valve hole 20 and the sub valve hole 32 communicates with the port 16. A guide hole 25 (functioning as a “first guide hole”) is provided between the port 14 and the pressure chamber 23. A guide hole 26 (functioning as a “second guide hole”) is provided between the port 14 and the port 16. A guide hole 27 (functioning as a “third guide hole”) is provided between the port 16 and the port 18. A stepped cylindrical sub-valve element 36 is slidably inserted into these guide holes. That is, the auxiliary valve body 36 is supported at three points by the body. A sub valve seat 34 is formed on the upper surface of the solenoid 3. The auxiliary valve body 36 is attached to and detached from the auxiliary valve seat 34 to open and close the auxiliary valve.

  The main valve hole 20 is provided in the reduced diameter part of the upper part of the subvalve body 36, and the main valve seat 22 is formed in the lower end opening part. On the other hand, a long operating rod 38 is provided along the axis of the body 5. The operating rod 38 has an upper half inserted through the sub-valve element 36 and a lower half inserted through the solenoid 3. The upper end portion of the operating rod 38 is slidably supported on the upper end portion of the sub-valve body 36, and is connected to the power element 6 at the distal end portion so as to be operatively connectable. The lower end portion of the operating rod 38 is connected to a plunger 50 (described later) of the solenoid 3. Further, the intermediate portion of the operating rod 38 is expanded in diameter to form the main valve body 30. The main valve body 30 opens and closes the main valve by being attached to and detached from the main valve seat 22 in the pressure chamber 24, and adjusts the flow rate of refrigerant flowing from the discharge chamber to the crank chamber. The operating rod 38 directly transmits a solenoid force to the main valve body 30 and the sub valve body 36.

  When the auxiliary valve body 36 is seated on the auxiliary valve seat 34 and closes the auxiliary valve, the communication state between the pressure chamber 24 and the port 18 is interrupted, and the relief of the refrigerant from the crank chamber to the suction chamber is interrupted. Further, when the auxiliary valve body 36 is separated from the auxiliary valve seat 34 and opens the auxiliary valve, the pressure chamber 24 and the port 18 communicate with each other, and the relief of the refrigerant from the crank chamber to the suction chamber is allowed. In the upper part and the middle part of the sub-valve body 36, communication holes 35 and 37 that communicate with the inside and the outside are provided. The communication hole 35 communicates the port 14 and the main valve hole 20, and the communication hole 37 communicates the port 16 and the pressure chamber 24.

  A spring 44 (which functions as an “urging member”) for biasing the sub valve body 36 in the valve closing direction of the sub valve is interposed between the sub valve body 36 and the body 5. 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 24 is formed between the core 46 and the auxiliary valve body 36. 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 body 5 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 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 of the pressure chamber 24 is also guided to the inside of the sleeve 48 through the communication groove, the communication path 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. The first body 81 has a stepped cylindrical shape whose outer diameter gradually decreases upward, and can slide on the lower half of the sub-valve body 36 through a guide hole 27 formed on the inside thereof. I support it. 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. The body 5 is configured such that the outer diameter decreases from the solenoid 3 side toward the power element 6 side by connecting the first body 81 and the second body 82, and the body 5 is connected to a mounting hole of a compressor (not shown). The ease of insertion is enhanced.

  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 upper half of the second body 82. The guide holes 25 and 26 are formed by slightly reducing the inner diameter of the lower half of the second body 82. The sliding surface of the guide hole 26 is provided with a sealing O-ring 28 (functioning as a “seal member”). As a result, the high-pressure refrigerant introduced from the port 14 is prevented from leaking to the port 16 through the gap between the sub valve body 36 and the guide hole 26.

  The upper surface 90 of the main valve body 30 functions as an “attachment / detachment portion” that opens and closes the main valve seat 22 and opens and closes the main valve, and the subvalve body 36 is moved upward (the subvalve of the subvalve is seated on the main valve seat 22). It also functions as an “engaging part” that presses in the valve opening direction). On the other hand, the upper surface 92 of the intermediate portion of the sub valve body 36 functions as a “locking portion” in which the upward displacement of the sub valve body 36 is restricted by being locked to the lower surface of the second body 82. The upper end portion 94 of the actuating rod 38 is slidably inserted into the upper end portion of the sub-valve element 36, and also functions as a partition wall that isolates the pressure chamber 23 from other pressure chambers.

  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). As a result, as shown in the figure, the main valve body 30 is separated from the main valve seat 22, and the main valve is fully opened. The auxiliary valve body 36 maintains the closed state of the auxiliary valve by the urging force of the spring 44, but the downward displacement thereof is restricted by the auxiliary valve body 36 seated on the auxiliary valve seat 34. In the present embodiment, the shape and size of the auxiliary valve body 36 are set so that the upper surface 92 is spaced from the lower surface of the second body 82 with a predetermined interval L1 when the auxiliary valve is closed.

  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 expands 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 23 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 above configuration, the main valve body 30 and the main valve seat 22 constitute a main valve, and the flow rate of the refrigerant introduced from the discharge chamber into 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 A (seal part diameter) of the sub valve of the sub valve body 36 and the effective pressure receiving diameter B (seal part diameter) of the sliding portion with the guide hole 27 of the sub valve body 36 are as follows. Are set equal. For this reason, most of the influence of the crank pressure Pc acting on the auxiliary valve body 36 is cancelled. Further, the effective pressure receiving diameter C (seal portion diameter) of the sliding portion with the guide hole 25 of the sub-valve body 36 and the effective pressure receiving diameter D (sealing portion diameter) of the sliding portion with the guide hole 26 of the sub-valve body 36 are also shown. And are set equal. For this reason, the influence of the discharge pressure Pd acting on the auxiliary valve body 36 is cancelled.

  That is, the influence of the crank pressure Pc is canceled for the portion where the auxiliary valve body 36 is formed larger. On the other hand, a differential pressure (Pc−Ps) between the crank pressure Pc and the suction pressure Ps acts in the opening direction of the auxiliary valve on the small diameter portion which is the upper half of the auxiliary valve body 36. Therefore, it cannot be larger than the urging force of the sub valve by the spring 44 in the valve closing direction. As a result, the closed state of the auxiliary valve can be stably maintained during the control of the compressor even when the auxiliary valve body 36 is configured to be large. Can be opened. In other words, in order to cancel the influence of the crank pressure Pc on the portion where the auxiliary valve body 36 is formed to be large, even if the size of this portion is changed, the load received by the auxiliary valve body 36 due to the differential pressure (Pc−Ps) Does not grow. For this reason, it becomes possible to set the magnitude | size of the subvalve body 36 freely. Further, the effective pressure receiving diameter E (seal part diameter) of the main valve body 30 in the main valve and the effective pressure receiving diameter F (seal part diameter) of the sliding part of the main valve body 30 are set equal. Thereby, the influence of the discharge pressure Pd acting on the main valve body 30 is canceled, and the behavior of the main valve body 30 can be kept stable during the control of the main valve.

  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 23 becomes the predetermined set pressure Pset. The set pressure Pset is basically adjusted in advance by the spring load of the springs 44, 47, 88 and the load of the bellows 45, and the evaporator can be prevented from freezing from the relationship between the temperature in the evaporator and the suction pressure Ps. Set as pressure value. 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 control valve 1 is started, the main valve body 30 is seated on the main valve seat 22 by displacing the operating rod 38 relative to the sub-valve body 36 by energizing the solenoid 3. It closes and the driving force of the valve opening direction can be given to the subvalve body 36 through the main valve body 30. Thereby, the auxiliary valve body 36 can be lifted from the auxiliary valve seat 34 to open the auxiliary valve. That is, the control valve 1 has a “forced valve opening mechanism” for forcibly opening the auxiliary valve using the driving force of the solenoid 3. In this configuration, when the sub-valve body 36 is locked due to a foreign object biting into the sliding portion between the sub-valve body 36 and the guide holes 25, 26, 27, an unlocking mechanism (interlocking mechanism) is released. , Also functions as a pressing mechanism).

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 operating rod 38 is pushed down by the urging force of the spring 47, the main valve body 30 is separated from the main valve seat 22, 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 air conditioner for automobiles is started, the operating rod 38 is driven upward by the solenoid force and the main valve is closed as shown in FIG. , The vice valve is opened. That is, first, the operating rod 38 is relatively displaced with respect to the sub valve body 36, whereby the main valve body 30 is seated on the main valve seat 22 and the main valve is closed. Subsequently, while the main valve body 30 is seated on the main valve seat 22, the operating rod 38 is further displaced relative to the body 5, so that the sub valve body 36 is separated from the sub valve seat 34 and the sub valve is operated. Open the valve. However, when the upper surface 92 of the sub-valve element 36 is locked to the body 5, the lift amount of the sub-valve element 36 (that is, the opening degree of the sub-valve) is 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.

  Even when the sub-valve body 36 is locked in the valve opening direction due to foreign matter being caught in the sliding portion of the sub-valve element 36 when the control valve 1 is activated, the sub-valve element is driven by the solenoid force. The lock can be released by pressing 36. Even if the sub-valve element 36 is locked in the valve closing direction due to the foreign matter biting into the sliding portion of the sub-valve element 36, the suction pressure Ps is reduced by the activation of the control valve 1 and the bellows 45 is extended. The second stopper 86 comes into contact with the upper end surface of the sub-valve body 36 and presses it downward, so that the lock can be released.

  When the current value supplied to the solenoid 3 is in the control state set to a predetermined value, as shown in FIG. 4, the suction pressure Ps is relatively low, so that the bellows 45 extends, and the operation rod 38 operates. Connected. Thereby, the main valve body 30 operates and adjusts the opening degree of the main valve. At this time, the main valve body 30 has a force in the valve opening direction by the spring 47, a solenoid force in the valve closing direction by the solenoid 3, and a force that opposes the solenoid force by the power element 6 that operates according to the suction pressure Ps. Stop at the balanced valve lift position. 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. Then, the suction force does not act between the core 46 and the plunger 50, so that the main valve body 30 is separated from the main valve seat 22 by the biasing force of the spring 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. The refrigerant having the discharge pressure Pd introduced from the discharge chamber of the compressor 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 seat 34 is not formed on the main valve body 30 but is formed on 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. In particular, by providing the auxiliary valve body 36 closer to the solenoid 3 than the power element 6, that is, on the side where the outer diameter of the body 5 is increased, the auxiliary valve body 36 can be made sufficiently large. Sometimes a large flow rate is obtained and the bleed function can be enhanced. Further, the main valve seat 22 is provided integrally with the auxiliary valve body 36, so that the number of parts can be reduced. Further, the main valve seat 22 (valve seat forming portion) and the sub valve body 36 are integrated, so that the main valve seat 22 moves after the main valve is closed, and at the same time, the sub valve is integrated with the main valve seat 22. Since the auxiliary valve is opened by the movement of the body 36, there is no need to individually adjust the closing timing of the main valve and the opening timing of the auxiliary valve, the selection of parts and adjustment parts can be reduced, and the assemblability is greatly improved. .

[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.

  The control valve 201 is different from the first embodiment in the configuration of the body 205 and the auxiliary valve body 236 in the valve main body 202. Also in this embodiment, the body 205, the core 46, the case 56, and the end member 58 form the body of the entire control valve 201. The body 205 includes a first body 81 and a second body 282. The guide hole 25 of the second body 282 supports the upper end portion 94 of the operating rod 38 so as to be slidable. A spring receiving member 240 is provided below the main valve body 30 in the operating rod 38. Between the sub valve body 236 and the spring receiving member 240, a spring 242 (functioning as an “urging member”) that biases the sub valve body 236 in the valve opening direction of the sub valve is interposed. In this embodiment, the spring 47 shown in FIG. 1 is not provided.

  The auxiliary valve body 236 is supported at two points by the guide hole 26 and the guide hole 27. A sealing O-ring 228 (functioning as a “seal member”) is provided on the surface of the sub-valve body 236 facing the guide hole 27. Thereby, the refrigerant introduced from the port 16 is prevented from leaking to the port 18 through the gap between the sub valve body 236 and the guide hole 27.

  Also in the present embodiment, the effective pressure receiving diameter E (seal part diameter) of the main valve of the main valve body 30 is set equal to the effective pressure receiving diameter F (seal part diameter) of the sliding part of the operating rod 38. Thereby, the influence of the discharge pressure Pd acting on the main valve body 30 is canceled, and the control of the main valve is stabilized. In this embodiment, the operating rod 38 and the plunger 50 are not fixed as in the first embodiment, but the operating rod 38 is urged toward the plunger 50 by the reaction force of the spring 242, so that the operation rod 38 is operated. The contact state between the rod 38 and the plunger 50 can always be maintained. In other words, the operation rod 38 does not need to be press-fitted into the plunger 50.

[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 first embodiment in that the main valve seat is formed on a valve seat forming member provided separately. 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 301, the body 305 of the valve main body 302 includes a first body 81 and a second body 382. Also in this embodiment, the body 305, the core 46, the case 56, and the end member 58 form the body of the entire control valve 301. A disc-shaped partition member 380 for partitioning the pressure chamber 23 is press-fitted into the upper portion of the second body 382. And the guide hole 25 is formed so that the partition member 380 may be penetrated. The guide hole 25 slidably supports the upper end portion 94 of the operating rod 38. A pair of ring-shaped locking members 340 and 342 are fitted to the operating rod 38 below the main valve body 330 at a predetermined interval in the axial direction.

  A cylindrical valve seat forming member 350 is slidably inserted into the guide hole 26. The valve seat forming member 350 has a locking portion 352 extending outward in the radial direction at an upper end portion thereof. A spring 344 (which functions as a “biasing member”) that biases the valve seat forming member 350 downward is interposed between the locking portion 352 and the partition member 380. And the main valve hole 20 is formed in the inside of the valve seat formation member 350, and the main valve seat 22 is formed in the lower end opening part.

  The auxiliary valve body 336 has a bottomed cylindrical shape, and is configured such that the bottom portion thereof is supported between the locking member 340 and the locking member 342. A plurality of communication holes 337 for circulating the refrigerant are provided at the bottom of the sub valve body 336. Also in the present embodiment, the effective pressure receiving diameter E (seal portion diameter) of the main valve of the main valve body 330 is set equal to the effective pressure receiving diameter F (seal portion diameter) of the sliding portion of the operating rod 38. Thereby, the influence of the discharge pressure Pd acting on the main valve body 330 is canceled, and the control of the main valve is stabilized.

  With such a configuration, when the solenoid 3 is not energized, the auxiliary valve body 336 maintains the closed state of the auxiliary valve by the urging force of the spring 44 as shown in the figure. The valve seat forming member 350 maintains the state in which the locking portion 352 is locked to the second body 382. Further, since the operating rod 38 is pushed downward by the spring 47 (see FIG. 1), the main valve body 330 is separated from the main valve seat 22, and the main valve is fully opened. In the present embodiment, in such a state, the lift amount L2 of the main valve body 330 from the main valve seat 22 and the distance L3 between the bottom bottom surface of the sub valve body 336 and the locking member 342 are set to be equal. Has been.

  In the stable control state of the control valve 301, the main valve body 330 is pushed up by the solenoid force, and the lift amount from the main valve seat 22 is basically smaller than L2. In the state where the main valve body 330 is lifted, the locking member 342 is not engaged with the sub valve body 336, so that the sub valve is not opened. The main valve body 330 operates autonomously so that the suction pressure Ps of the pressure chamber 23 becomes a predetermined set pressure Pset.

  On the other hand, when the control valve 1 is started, the main valve body 330 is seated on the main valve seat 22 by displacing the actuating rod 38 relative to the sub-valve body 336 by energizing the solenoid 3 so that the main valve is moved. It closes and the driving force of the valve opening direction can be given to the subvalve body 336 through the main valve body 330. Thereby, the auxiliary valve body 336 can be lifted from the auxiliary valve seat 34 to open the auxiliary valve. That is, the control valve 301 also has a “forced valve opening mechanism” for forcibly opening the auxiliary valve using the driving force of the solenoid 3. In this configuration, when the sub-valve body 36 is locked due to foreign matter biting into the sliding portion between the sub-valve body 336 and the guide holes 26 and 27, the lock release mechanism (interlocking mechanism, pressing force) is released. It also functions as a mechanism.

[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 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.

  The control valve 401 is configured by assembling a first body 481 and a second body 482 in a body 405 of the valve main body 402. Also in this embodiment, the body 405, the core 46, the case 56, and the end member 58 form the entire body of the control valve 401. A main valve is provided inward of the second body 482, and a sub valve is provided between the first body 481 and the second body 482. The second body 482 is fixed so that its lower half is inserted into the upper half of the first body 481. A port 14 is formed on the upper half side of the overlap portion between the first body 481 and the second body 482. On the other hand, a port 16 is formed on the lower half side of the overlap portion between the first body 481 and the second body 482.

  The main valve body 430 has a stepped cylindrical shape, and is supported by a guide hole 25 provided at the center of the second body 482 and a guide hole 426 provided at the lower end so as to be slidable in the axial direction. ing. The main valve hole 20 is formed between the guide hole 25 and the guide hole 426 in the second body 482, and the main valve seat 22 is formed at the lower end opening thereof. The outer diameter of the intermediate portion in the axial direction of the main valve body 430 is reduced, and an attachment / detachment portion that opens and closes the main valve seat 22 to open and close the main valve is configured by the lower base end portion of the reduced diameter portion. Yes. A labyrinth seal 495 including a plurality of annular grooves for suppressing the circulation of the refrigerant is provided on the surface of the main valve body 430 facing the guide hole 25. The pressure chamber 23 is formed above the main valve body 430.

  On the other hand, the auxiliary valve hole 32 is formed below the second body 482 in the first body 481, and the auxiliary valve seat 34 is formed at the upper end opening thereof. The sub valve body 436 has a bottomed cylindrical shape, and is slidably inserted at the lower end of the second body 482. A through hole 441 is provided in the center of the bottom of the sub-valve element 436, and an operating rod 38 is provided so as to penetrate the sub-valve element 436 and the main valve element 430. A locking member 498 is fixed to an intermediate portion of the operating rod 38, and an upper surface thereof forms an engaging portion 496. When the actuating rod 38 moves upward and the locking member 498 engages with the lower surface of the auxiliary valve body 436, an upward force (the opening direction of the auxiliary valve) is transmitted to the auxiliary valve body 436. A locking member 499 is also fixed to the upper end portion of the operating rod 38. When the operation rod 38 moves downward and the locking member 499 engages with the upper surface of the main valve body 430, a downward force (the valve opening direction of the main valve) is transmitted to the main valve body 430.

  The sub valve body 436 is disposed so as to be sandwiched between the lower surface of the main valve body 430 and the engaging portion 496. Between the main valve body 430 and the sub-valve body 436, a spring 444 (functioning as an “urging member”) that biases the main valve body 430 and the sub-valve body 436 away from each other is provided. A pressure chamber 428 that is filled with the suction pressure Ps is formed between the sub valve body 436 and the core 46. The pressure chamber 428 communicates with the port 18. A plurality of communication holes 435 are provided in the vicinity of the periphery of the bottom portion of the sub valve body 436. A space surrounded by the second body 482, the main valve body 430, and the sub valve body 436 forms a pressure chamber 490. The suction pressure Ps of the pressure chamber 428 is also introduced into the pressure chamber 490 through the communication hole 435.

  In the present embodiment, when the main valve is fully opened (when the sub valve is closed), the engaging portion 496 of the actuating rod 38 and the sub valve body 436 are spaced apart by a predetermined distance 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 22 of the main valve body 430 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 element 436 and the main valve element 430 when the main valve is closed is the full-open stroke of the sub-valve.

  Further, in this embodiment, the effective pressure receiving diameter E (seal portion diameter) of the main valve body 430 in the main valve is set equal to the effective pressure receiving diameter F (seal portion diameter) of the upper sliding portion of the main valve body 430. ing. For this reason, the influence of the discharge pressure Pd acting on the main valve body 430 is cancelled. On the other hand, the effective pressure receiving diameter G (seal portion diameter) of the lower sliding portion of the main valve body 430 is set larger than the effective pressure receiving diameter F (sealing portion diameter) of the upper sliding portion. A differential pressure (Pc−Ps) in the valve opening direction corresponding to the difference in diameter (G−F) acts on the body 430. The sub-valve element 436 has an effective pressure receiving diameter A (seal part diameter) at the sub-valve of the sub-valve element 436 and an effective pressure receiving diameter B (seal part diameter) of the sliding part of the sub-valve element 436. A differential pressure (Pc−Ps) in the valve closing direction corresponding to the difference (A−B) is applied.

  In the stable control state of the control valve 401, the main valve body 430 includes a force in the valve closing direction by the spring 444, a force in the valve closing direction by the solenoid 3, a force in the valve opening direction by the power element 6, and the spring 47. The valve lift position is controlled so that the force in the valve opening direction is balanced. The main valve body 430 operates autonomously so that the suction pressure Ps of the pressure chamber 23 becomes a predetermined set pressure Pset. At this time, the secondary valve body 436 is biased in the valve closing direction by the reaction force of the spring 444, so that the secondary valve is not opened.

  On the other hand, when the control valve 401 is activated, the locking rod 436 is engaged with the sub valve body 436 by displacing the operating rod 38 relative to the sub valve body 436 by energizing the solenoid 3. Push up. Thereby, the auxiliary valve body 436 can be lifted from the auxiliary valve seat 34 to open the auxiliary valve. That is, the control valve 401 also has a “forced valve opening mechanism” for forcibly opening the auxiliary valve using the driving force of the solenoid 3. This configuration is used as an unlocking mechanism (an interlocking mechanism, a pressing mechanism) for releasing each valve body when a foreign object is caught in the sliding portions of the main valve body 430 and the sub-valve body 436. Also works.

  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 control valve is a so-called Ps sensing valve that operates by sensing the suction pressure Ps as the sensed pressure. However, the control valve may be configured as a so-called Pc sensing valve that operates by sensing the crank pressure Pc. Good. 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 embodiment, the spring (coil spring) is exemplified as the biasing member for the springs 44, 47, 242, 344, 444, etc., but an elastic material such as rubber or resin or an elastic mechanism such as a leaf spring is adopted. Needless to say.

  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 the above embodiment, the reference pressure chamber S inside the bellows 45 is in a vacuum state, but it may be filled with the atmosphere or a predetermined gas as a reference. Alternatively, any one of the discharge pressure Pd, the crank pressure Pc, and the suction pressure Ps may be satisfied. And it is good also as a structure which the power element 6 detects suitably the pressure difference inside and outside of a bellows, and act | operates. Moreover, in the said embodiment, although it was set as the structure which cancels the discharge pressure Pd about a main valve body, it is good also as a structure which has not canceled the pressure which a main valve body receives.

  In the above embodiment, the power element 6 can be brought into contact with the sub-valve element 36, and even if the sub-valve element 36 is locked, the power element 6 can be released by the driving force of the power element 6. In the modification, for example, as shown in FIG. 6, when the valve seat forming member is configured separately from the sub valve body, the power element 6 can be brought into contact with the valve seat forming member. Even if is locked, it may be configured such that it can be released by the driving force of the power element 6.

  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, 18 port, 20 main valve hole, 22 main valve seat, 25, 26, 27 guide hole, 28 O-ring, 30 Main valve body, 32 Sub valve hole, 34 Sub valve seat, 36 Sub valve body, 38 Operating rod, 45 Bellows, 201 Control valve, 202 Valve body, 205 Body, 228 O-ring, 236 Sub valve body, 301 Control valve, 302 valve body, 305 body, 330 main valve body, 336 sub valve body, 340, 342 locking member, 350 valve seat forming member, 401 control valve, 402 valve body, 405 body, 426 guide hole, 430 main valve body, 436 Sub valve body, 496 Engagement part.

Claims (3)

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 In a control valve for a variable capacity compressor that is changed by adjusting one flow rate or pressure,
A body formed with a main passage for communicating the discharge chamber and the crank chamber, and a sub-passage for communicating the crank chamber and the suction chamber;
A main valve seat provided in the main passage;
A main valve body that opens and closes the main valve by attaching to and detaching from the main valve seat;
An auxiliary valve seat provided in the auxiliary passage;
A sub-valve element that opens and closes the sub-valve by attaching to and detaching from the sub-valve seat;
A pressure sensing unit that receives a predetermined sensed pressure and generates a driving force in the valve opening direction of the main valve in accordance with the magnitude of the sensed pressure;
A solenoid that generates a driving force in the valve closing direction of the main valve in accordance with the amount of current supplied;
With
The pressure sensing portion is disposed on one side of the main valve body, and the solenoid is disposed on the other side of the main valve body;
The sub valve seat is provided integrally with the body;
Sealing portion diameter in the sub valve of the sub-valve body is much larger than the sealing portion diameter of said main valve of said main valve body,
The body includes a discharge chamber communication port that communicates with the discharge chamber, a crank chamber communication port that communicates with the crank chamber, and a suction chamber communication port that communicates with the suction chamber,
The control valve for a variable capacity compressor , wherein the crank chamber communication port is disposed between the discharge chamber communication port and the suction chamber communication port . The control valve for a variable capacity compressor according to claim 1 , wherein the sub valve body is slidably supported by the body. By setting the seal portion diameter of the subvalve of the subvalve body substantially equal to the seal portion diameter of the sliding portion of the subvalve body with the body, the crank chamber acting on the subvalve body The control valve for a variable capacity compressor according to claim 2 , wherein at least part of the influence of the crank pressure or the suction pressure of the suction chamber is canceled.

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