KR20150006406A - Control valve for variable displacement compressor and control valve - Google Patents

Abstract

The present invention relates to a control valve capable of operating a main valve and a sub-valve by a single solenoid, and obtaining large flow when the sub-valve is opened. A control valve (1) comprises: a body (5) having a main path to connect a discharge chamber with a crank chamber, and a sub-path to connect the crank chamber with a suction chamber; a power element (6) to receive the suction pressure of a main valve prepared in the main path, a sub-valve prepared in the sub-path, and the suction chamber, and to generate a driving force in the valve opening direction of the main valve corresponding to the size of the suction pressure; and a solenoid (3) to generate a driving force in the valve closing direction of the main valve corresponding to the amount of the supplied current. Moreover, the power element (6), the main valve, the sub-valve, and the solenoid (3) are arranged in order in one end of the body (5), and a forced valve opening device to forcibly open a valve of the sub-valve by using a driving force of the solenoid (3) is provided additionally.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a control valve for a variable capacity compressor,

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.

BACKGROUND ART An automotive air conditioner generally includes a compressor for compressing a refrigerant flowing through a refrigeration cycle and discharging it as gas refrigerant at a high temperature and a high pressure, a condenser for condensing the gas refrigerant, and a condenser for expanding the condensed liquid refrigerant adiabatically, And an evaporator that performs heat exchange with air in the vehicle by evaporating the refrigerant. The refrigerant evaporated in the evaporator returns to the compressor again and circulates in the refrigeration cycle.

As this compressor, a variable displacement compressor (hereinafter also referred to as "compressor") capable of varying the discharge capacity of the refrigerant is used so that a constant refrigerating capacity is maintained regardless of the number of revolutions of the engine. In this compressor, a piston for compression is connected to a swing plate mounted on a rotary shaft driven to rotate by an engine, and the stroke of the piston is changed by changing the angle of the swing plate to adjust the discharge amount of the refrigerant. The angle of the swing plate changes continuously by introducing a part of the discharge refrigerant into the closed crank chamber and changing the balance of the 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 control valve for a variable capacity compressor (hereinafter also referred to as "control valve") provided between the discharge chamber of the compressor and the crank chamber.

Such a control valve adjusts the degree of opening of the valve by supplying a current from the outside to the solenoid as the driving portion. When it is necessary to quickly perform the air conditioning function, for example, at the time of starting the air conditioner, the maximum current is supplied to the solenoid, for example, to bring the valve into a valve closed state, lower the crank pressure Pc, The compressor can be operated at the maximum capacity. When the engine load of the vehicle is large, the solenoid is turned off to bring the valve into a fully open state, and the crank pressure Pc is increased to make the swing plate approximately perpendicular to the rotation axis, thereby enabling the compressor to operate at the minimum capacity.

In such a control valve, a main valve is provided in a main passage for communicating the discharge chamber and the crank chamber, and a sub-valve is provided in a sub passage for communicating the crank chamber and the suction chamber, and the valve is driven by a single solenoid (See, for example, Patent Document 1). According to this control valve, at the time of normal operation of the air conditioner, the opening degree of the main valve is adjusted while the sub valve is closed. Thereby, the crank pressure Pc can be controlled as described above, and the discharge capacity of the compressor can be controlled. Further, at the time of starting the air conditioner, the sub-valve is opened in a state where the main valve is closed, whereby the crank pressure Pc is quickly lowered, so that the compressor can be moved relatively quickly to the maximum capacity operating state. Further, since the plurality of valves are opened and closed by a single solenoid, the entire control valve can be constructed compactly.

In this control valve, the main valve body and the sub valve body are provided on the same axis in relation to driving the main valve and the sub valve by a single solenoid, and the solenoid is provided to each valve body through the operating rod arranged along the axis thereof. And a mechanism for transmitting the force. 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 sub passage is provided so as to pass through the main valve body. The main valve body is attached to and detached from the main valve seat provided at the opening end of the main valve hole to open and close the main valve and the sub valve body is attached to and detached from the sub valve seat provided at the opening end of the sub valve hole, Is opened and closed. However, during normal operation of the compressor, the sub valve body is pushed against the sub valve seat, and the valve closed state of the sub valve is maintained. At the time of starting the compressor, the sub-valve can be opened by maximizing the solenoid power and further urging the sub-valve body in the valve-opening direction with the main valve body seated on the main valve seat.

Japanese Patent Application Laid-Open No. 2008-240580

[0004] Recently, there is a demand for a vehicle manufacturer to operate the compressor more quickly. The air conditioning performance is displayed more quickly, thereby pursuing further comfort, and linking to sales promotion of the vehicle. For this purpose, the refrigerant flow rate at the time of opening the sub-valve should be increased. However, since the above-described control valve forms the sub valve hole in the main valve body, the size of the sub 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 sub valve hole larger than the main valve hole. It is also conceivable to set the lift amount from the sub-valve seat of the sub-valve body to be large, but increasing the stroke of the sub-valve body makes the entire control valve large, which is costly. Further, even if the stroke is enlarged like this, it is impossible to significantly increase the flow rate unless the size of the sub valve hole is changed.

SUMMARY OF THE INVENTION The present invention has been made in view of such a problem, and it is an object of the present invention to provide a control valve which drives a main valve and a sub valve by a single solenoid, so that a large flow rate can be obtained when the sub valve is opened.

In order to solve the above problems, a control valve for a variable capacity compressor according to an embodiment of the present invention compresses a refrigerant introduced into a suction chamber and discharges the discharge capacity of the variable capacity compressor discharging from the discharge chamber to a refrigerant which introduces the discharge capacity from the discharge chamber to the crank chamber, A control valve for a variable capacity compressor, comprising: a main passage for communicating a discharge chamber and a crank chamber; and a sub passage for communicating the crank chamber and the suction chamber with each other, A main valve seat provided in the main passage, a main valve body 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 body, and a sub valve body, which pressurizes a predetermined sensed pressure, A depressurizing portion for generating a driving force in a valve opening direction of the valve and a solenoid for generating a driving force in a valve closing direction of the main valve corresponding to the amount of supplied current. A depressurizing portion is disposed on one side of the main valve body, and a solenoid is disposed on the other side of the main body. The sub valve body is provided integrally with the body, and the body diameter of the sub valve body is larger than the actual body diameter of the main valve of the main valve body.

In this embodiment, in the structure in which the main valve body is disposed between the pressure reducing portion and the solenoid in the body, the sub valve body is formed on the body rather than the main valve body, and the sub valve is not restricted by the size of the main valve Respectively. Accordingly, the sub-valve can be enlarged independently of the main valve. Therefore, it is possible to obtain a large flow rate when the sub valve is opened.

Another aspect of the invention is also a control valve. The control valve includes a body having an introduction lead-in port for introducing or drawing out a working fluid, an introduction port for introducing a working fluid, an extraction port for leading out a working fluid, and a main body provided in a main passage for communicating the introduction port and the introduction lead- A sub valve provided in a sub passage for communicating the introduction lead-out port and the lead-out port; a sub valve provided in the sub passage for communicating the introduction lead-out port and the lead- And a solenoid for generating a driving force in the valve closing direction of the main valve corresponding to the amount of supplied current. A depressurizing portion is disposed on one side of the main valve, and a solenoid is disposed on the other side of the main valve. The sub-valve is larger than the main valve.

In this aspect, in the configuration in which the main valve is disposed between the pressure-reducing portion and the solenoid in the body, the sub-valve is larger than the main valve. Therefore, it is possible to obtain a large flow rate when the sub valve is opened.

According to the present invention, in a control valve that drives the main valve and the sub valve by a single solenoid, it is possible to obtain a large flow rate when the sub valve is opened.

1 is a cross-sectional view showing a configuration of a control valve according to a first embodiment.
2 is a partially enlarged cross-sectional view corresponding to the upper half of Fig.
3 is a view showing the operation of the control valve.
4 is a view showing the operation of the control valve.
5 is a partially enlarged cross-sectional view corresponding to the upper half of the control valve according to the second embodiment.
6 is a partially enlarged cross-sectional view corresponding to the upper half of the control valve according to the third embodiment.
7 is a partially enlarged cross-sectional view corresponding to the upper half of the control valve according to the fourth embodiment.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following description, for convenience, the positional relationship of each structure may be expressed up and down with reference to the state of the drawings.

[First Embodiment]

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

The control valve 1 is constituted by an electromagnetic valve for controlling the discharge capacity of a variable capacity compressor (hereinafter referred to as "compressor"), not shown, provided in the refrigeration cycle of the automotive air conditioner. This compressor compresses a cold air stream flowing in a refrigeration cycle and discharges it by gas refrigerant of high temperature and high pressure. The gas refrigerant is condensed by a condenser (external heat exchanger), and is expanded adiabatically by the expansion device to become a low-temperature and low-pressure mist refrigerant. The low-temperature and low-pressure refrigerant evaporates by the evaporator, and the vehicle interior air is cooled by the latent heat of evaporation. The refrigerant evaporated in the evaporator returns to the compressor again and circulates the refrigeration cycle. The compressor has a rotary shaft that is rotationally driven by an engine of an automobile, and a compression piston is connected to a swing plate mounted on the rotary shaft. And the stroke of the piston is changed by changing the angle of the swing plate, whereby the discharge amount of the refrigerant is adjusted. The control valve 1 controls the flow rate of refrigerant introduced into the crank chamber from the discharge chamber of the compressor, thereby changing the angle of the swash plate and further the discharge capacity of the compressor.

The control valve 1 is configured as a so-called Ps sensing valve for controlling the refrigerant flow rate introduced into the crankcase from the discharge chamber so as to maintain the suction pressure Ps (corresponding to the "sensing pressure" . The control valve 1 is constituted by integrally assembling the valve body 2 and the solenoid 3 together. The valve body 2 has a main valve for opening and closing a refrigerant passage for introducing a part of discharged refrigerant into the crank chamber at the time of operation of the compressor and a so-called bleed valve for placing the refrigerant in the crank chamber in the suction chamber Valve. The solenoid 3 drives the main valve in the opening and closing direction to adjust its opening degree and controls the refrigerant flow rate introduced into the crank chamber. The valve body 2 includes a cylindrical body 5 having a stepped portion, a main valve and a subvalve provided in the body 5, a power element (not shown) for generating a force against the solenoidal force 6). The power element 6 functions as a "pressure reducing portion ".

The body 5 is provided with the ports 12, 14, 16, 18 at the upper end thereof. The port 12 is provided at the upper opening of the body 5 and the ports 14, 16 and 18 are provided at the side of the body 5. The port 14 functions as a "discharge chamber communication port " communicating with the discharge chamber, and the port 16 functions as a " suction chamber communication port " And serves as a "crank chamber communication port" An end member (13) is fixed to the upper opening of the body (5). On the outer peripheral surface of the end member 13, a plurality of communication grooves 15 for forming the port 12 are provided. The lower end of the body (5) is connected to the upper end of the solenoid (3).

A main passage for communicating the port 14 and the port 16 and a sub passage for communicating the port 16 and the port 18 are formed in the body 5. The main passage is provided with a main valve having a small diameter and the sub passage is provided with a sub valve having a large diameter. The sub-valve is arranged coaxially on the lower side of the main valve, that is, closer to the solenoid 3 than the main valve. That is, the control valve 1 has a configuration in which the power element 6, the main valve, the sub-valve, and the solenoid 3 are disposed in order from the first stage as shown in the figure. The main passage is provided with a main valve hole (20) and a main valve seat (22). The sub-passage is provided with a sub-valve hole 32 and a sub-valve seat 34.

The port 12 communicates the suction chamber with the pressure chamber 23 partitioned at the upper portion of the body 5 and introduces the refrigerant at the suction pressure Ps into the pressure chamber 23. The power element 6 is disposed in the pressure chamber 23. The port 14 introduces the refrigerant of the discharge pressure Pd in the discharge chamber. The port 16 draws the refrigerant of the crank pressure Pc passed through the main valve toward the crank chamber at the time of normal operation of the compressor and the refrigerant of the crank pressure Pc discharged from the crank chamber at the time of starting the compressor . At this time, the introduced refrigerant is guided to the sub-valve. The port 18 introduces the refrigerant of the suction pressure Ps during the normal operation of the compressor while drawing the refrigerant of the suction pressure Ps passing through the sub valve toward the suction chamber at the start of the compressor.

The main valve hole 20 and the sub valve hole 32 are formed in a coaxial shape and the pressure chamber 24 between the main valve hole 20 and the sub valve hole 32 communicates with the port 16 have. 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. In this guide hole, a cylindrical valve sub-valve body 36 having a stepped portion is slidably inserted. That is, the sub 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 sub valve body 36 is attached to and detached from the sub valve seat 34 to open and close the sub valve.

A main valve hole (20) is formed in the upper diameter portion of the upper portion of the sub valve body (36), and a main valve seat (22) is formed in the lower end opening portion. On the other hand, an elongated rod-like working rod 38 is provided along the axis of the body 5. The upper half of the operation rod 38 is inserted into the sub valve body 36 and the lower half thereof is inserted into the solenoid 3. The upper end of the operating rod 38 is slidably supported at the upper end of the sub valve body 36 and is operatively connected to the power element 6 by its tip end. The lower end of the operating rod 38 is connected to the plunger 50 of the solenoid 3, which will be described later. In addition, the intermediate portion of the operating rod 38 is enlarged to form the main valve body 30. The main valve body 30 opens and closes the main valve seat 22 by being attached to and detached from the main valve seat 22 by the pressure chamber 24 to adjust the flow rate of the refrigerant flowing from the discharge chamber to the crank chamber. The operating rod 38 directly transmits the solenoidal force to the main valve body 30 and the sub valve body 36.

The sub valve member 36 seats on the sub valve seat 34 and closes the sub valve so that the communication between the pressure chamber 24 and the port 18 is cut off and the relief of the refrigerant from the crank chamber to the suction chamber Lt; / RTI > The sub valve body 36 is separated from the sub valve seat 34 to open the sub valve so that the pressure chamber 24 and the port 18 communicate with each other and the relief of the refrigerant in the suction chamber in the crank chamber Is allowed. The upper and middle portions of the sub-valve body 36 are provided with communication holes 35 and 37 that communicate with each other. The communicating hole 35 communicates the port 14 and the main valve hole 20 and the communicating hole 37 communicates the port 16 and the pressure chamber 24.

A spring 44 (functioning as a "biasing member") for biasing the sub valve body 36 in the valve closing direction of the sub valve is provided between the sub valve body 36 and the body 5 . The power element 6 includes a bellows 45 (functioning as a "sensing member ") that senses and changes the suction pressure Ps and generates a force against the solenoid force by displacement of the bellows 45 . This counter force is also transmitted to the main valve body 30 through the operation rod 38.

On the other hand, the solenoid 3 includes a cylindrical core 46 having a stepped portion and a bottomed cylindrical sleeve 48 assembled to seal the lower end opening of the core 46 and a cylindrical sleeve 48 accommodated in the sleeve 48 A cylindrical plunger 50 axially opposed to the core 46 and a cylindrical bobbin 52 inserted into the core 46 and the sleeve 48 and the bobbin 52, An electromagnetic coil 54 for generating a magnetic circuit by energization and a cylindrical case 56 which covers the electromagnetic coil 54 from the outside to function as a yoke and a lower end opening of the case 56 And an end member 58 adapted to be sealed. 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 is provided a spring 47 (functioning as a "biasing member") for biasing the plunger 50 in a direction away from the core 46.

The valve body 2 and the solenoid 3 are fixed by pressing the lower end of the body 5 into the upper opening of the core 46. [ A pressure chamber (24) is formed between the core (46) and the sub valve body (36). On the other hand, an operation rod 38 is inserted so as to pass through the center of the core 46 in the axial direction. The lower end 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 in a coaxial manner.

The operating rod 38 is supported by the plunger 50 from below and is operatively connected to the main valve body 30, the sub valve body 36 and the power element 6. The operating rod 38 suitably transmits the solenoidal 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, a driving force (also referred to as a "reduced driving force") caused by the expansion and contraction of the power element 6 is loaded on the working rod 38 so as to oppose the solenoid force. That is, in the control state of the main valve, a force adjusted by the solenoid force and the reduced pressure driving force acts on the main valve body 30, and appropriately controls the opening of the main valve. When the main valve is closed, the operating rod 38 is displaced relative to the body 5 in accordance with the solenoid force, and the sub valve body 36 is pushed up to open the sub valve. Thereby exerting a bleed function.

A ring-shaped shaft member 60 is press-fitted into the upper end of the core 46 and the operating rod 38 is supported by the shaft member 60 so as to be slidable in the axial direction. A communication groove parallel to the axis is formed at a predetermined position on the outer circumferential surface of the shaft member 60. The crank pressure Pc of the pressure chamber 24 is attracted to the inside of the sleeve 48 through the communication passage 62 formed by the gap between the communication groove and the operating rod 38 and the core 46.

The communication passage (62) functions as an orifice for making the inside of the sleeve (48) into an oil damper chamber. That is, in the present embodiment, in the manufacturing process of the control valve 1, the same kind of oil as the oil contained in the refrigerant is preliminarily put in the sleeve 48 for lubrication of the compressor. In this embodiment, the communication groove provided in the shaft member 60 functions as a shrinkage passage which resists the entry and exit of the oil of the sleeve 48. With such a configuration, the sleeve 48 can function as an oil damper chamber, and the minute vibration of the plunger 50 disposed in the sleeve 48 can be suppressed. As a result, generation of noise due to such minute vibration is prevented or suppressed. Further, in the modified example, the communication passage 62 may function as a shrinkage passage for resisting the entry / exit of the oil of the sleeve 48. That is, at least one of the communication groove and the communication passage 62 provided in the shaft member 60 may function as a shrinkage passage. The spring 47 also functions as an off spring for biasing the core 46 and the plunger 50 in a direction in which they are separated from each other.

Sleeve 48 is made of a non-magnetic material. A plurality of communication grooves 66 are provided on the side surface of the plunger 50 parallel to the axis and a plurality of communication grooves 68 extending radially and communicating with the inside and outside are provided on the lower end surface of the plunger 50. The crank pressure Pc is attracted to the back pressure chamber 70 through the gap between the plunger 50 and the sleeve 48 even when the plunger 50 is positioned at the bottom dead center as shown in the figure.

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

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

The body 5 is constructed by assembling the first body 81 and the second body 82 together. The first body 81 has a cylindrical shape with a step that gradually decreases in outer diameter toward the upper side and a lower half of the sub valve body 36 is slidably supported by a guide hole 27 formed in the inner side thereof have. The second body 82 has a cylindrical shape with a step and is fixed so that the lower half of the second body 82 is internally inserted into the upper half of the first body 81. The body 5 is configured such that its outer diameter is reduced toward the power element 6 side from the side of the solenoid 3 by the connection of the first body 81 and the second body 82, The ease of insertion of the mounting hole is increased.

On the lower side of the second body 82, a communication hole 83 communicating with the inside and the outside is provided. A port 14 is formed at 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 inner diameter of the lower half of the second body 82 is slightly reduced in diameter to form the guide holes 25, 26. On the sliding surface of the guide hole 26, a practical O-ring 28 (functioning as a "seal member") is provided. This prevents the high-pressure refrigerant introduced from the port 14 from leaking to the port 16 through the gap between the sub valve member 36 and the guide hole 26. [

The upper surface 90 of the main valve body 30 functions as a "detachable portion" that is attached to the main valve seat 22 and opens and closes the main valve. 36 ") in the valve-opening direction of the sub-valve. On the other hand, the upper surface 92 of the middle portion of the sub-valve body 36 functions as a "lock-up portion" in which the upward displacement of the sub-valve body 36 is regulated by engaging with the lower surface of the second body 82. The upper end portion 94 of the operating rod 38 is slidably inserted into the upper end portion of the sub valve body 36 and also functions as a partition wall isolating the pressure chamber 23 from the other pressure chambers.

With this configuration, when the solenoid 3 is non-energized, the actuating rod 38 is suppressed by the urging force of the spring 47 (see Fig. 1). As a result, as shown in the drawing, the main valve body 30 is separated from the main valve seat 22, and the main valve is in the fully open state. The sub valve body 36 maintains the valve closed state of the sub valve by the biasing force of the spring 44. However, when the sub valve body 36 is seated on the sub valve seat 34, . The shape and size of the sub valve element 36 are set so that the upper surface 92 is spaced apart from the lower surface of the second body 82 by a predetermined distance L1 in the closed state of the sub valve .

The power element 6 is configured such that the upper end opening of the bellows 45 is closed by the first stopper 84 (corresponding to the "base member") and the lower end opening is closed by the second stopper 86 ). The first stopper 84 has a columnar shape with a stepped portion and extends in the axial direction by the inside of the bellows 45. The second stopper 86 has a circular plate shape, and a central portion of the upper surface thereof is opposed to a lower end surface of the first stopper 84. The inside of the bellows 45 is a sealed reference pressure chamber S and the bellows 45 is urged in the extension direction between the first stopper 84 and the second stopper 86 A spring 88 is provided. The reference pressure chamber S is in a vacuum state in this embodiment. The first stopper 84 is formed integrally with the end member 13. Therefore, the first stopper 84 is fixed with respect to the body 5. The bellows 45 expands or contracts in the axial direction (opening / closing direction of the main valve) corresponding 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, if the bellows 45 contracts by a predetermined amount even if the differential pressure increases, the second stopper 86 comes into contact with the first stopper 84, and the shrinkage thereof is restricted.

In this configuration, the main valve body 30 is constituted by the main valve body 30 and the main valve seat 22, and the flow rate of the refrigerant introduced into the crank chamber from the discharge chamber is adjusted by opening of the main valve. A sub-valve is formed by the sub-valve body 36 and the sub-valve seat 34, and the opening and closing of the sub-valve allows or prevents the refrigerant from being drawn from the crank chamber into the suction chamber. In other words. The control valve 1 also functions as a three-way valve for switching the flow of the refrigerant by opening one of the main valve and the sub valve.

The effective water pressure A (the diameter of the seal portion) in the sub-valve of the sub-valve body 36 and the effective water pressure of the sliding portion between the sub-valve body 36 and the guide hole 27 Diameter (B) (actual diameter) are set to be the same. For this reason, most of the influence of the crank pressure Pc acting on the sub-valve body 36 is canceled. The effective hydraulic diameter C of the sliding portion of the sub valve member 36 with the guide hole 25 and the effective hydraulic diameter of the sliding portion between the sub valve member 36 and the guide hole 26 D (actual diameter) are set to be the same. Therefore, the influence of the discharge pressure Pd acting on the sub-valve body 36 is canceled.

That is, the influence of the crank pressure Pc is canceled with respect to the portion where the sub valve body 36 is largely formed. On the other hand, the differential pressure Pc-Ps between the crank pressure Pc and the suction pressure Ps acts in the valve opening direction of the sub-valve in the upper half portion of the sub-valve body 36, The urging force of the spring 44 in the valve closing direction of the sub valve is not increased. As a result, the valve closing state of the sub-valve can be stably maintained at the time of controlling the pressure regulator, although the sub-valve body 36 is largely constituted. When the compressor is started, The valve can be quickly opened. In other words, since the influence of the crank pressure Pc is canceled on the portion where the sub-valve body 36 is largely formed, even if the size of the portion is changed, the sub-valve body 36 The receiving load does not increase. Therefore, the size of the sub valve body 36 can be freely set. The effective hydraulic diameter E (actual diameter) of the main valve of the main valve body 30 and the effective hydraulic diameter F (actual diameter) of the sliding portion of the main valve body 30 are set to be equal to each other. Thus, 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 stably maintained during the control of the main valve.

In such a configuration, the main valve operates autonomously so that the suction pressure Ps of the pressure chamber 23 becomes a predetermined set pressure Pset under the stable control state of the control valve 1. [ This set pressure Pset is basically adjusted in advance by the spring load of the springs 44, 47 and 88 and the load of the bellows 45, and in relation to the temperature in the evaporator and the suction pressure Ps, Is set to a pressure value capable of preventing freezing of the refrigerant. The set pressure Pset can be changed by changing the supply current (set current) of the solenoid 3. In the present embodiment, the adjustment load of the spring can be finely adjusted and the set pressure Pset can be accurately adjusted by resetting the press-in amount of the end member 13 in a state where the assembly of the control valve 1 is substantially completed .

On the other hand, at the time of starting the control valve 1, the operation rod 38 is relatively displaced with respect to the sub valve body 36 by energization of the solenoid 3, The sub valve body 36 can be given a driving force in the valve opening direction through the main valve body 30 by closing the main valve by seating the valve body 22 on the valve body 22. Thereby, the sub-valve body 36 can be lifted from the sub-valve seat 34 to open the sub-valve. That is, the control valve 1 has a "forced valve opening mechanism" for forcibly opening the sub valve by using the driving force of the solenoid 3. When the sub valve body 36 is locked by the inclusion of the foreign object into the sliding portion between the sub valve body 36 and the guide holes 25, 26 and 27, this configuration is advantageous in that when the sub valve body 36 is locked, Mechanism, pressing mechanism).

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

Fig. 3 and Fig. 4 are views showing the operation of the control valve, and correspond to Fig. FIG. 2 already 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. Hereinafter, description will be made with reference to Fig. 1 and with reference to Figs. 2 to 4 as appropriate.

When the solenoid 3 is not energized in the control valve 1, that is, when the automotive air conditioner does not operate, no attraction force acts between the core 46 and the plunger 50. [ On the other hand, the suction pressure Ps is in a relatively high state. Therefore, as shown in Fig. 2, the bellows 45 is contracted, and the power element 6 does not substantially function. The operating rod 38 is pushed by the urging force of the spring 47 so that the main valve body 30 is separated from the main valve seat 22 and the main valve is fully opened. Further, the sub valve body 36 is seated on the sub valve seat 34 by the biasing force of the spring 44, and the sub valve maintains the valve 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 automotive air conditioner is started, the solenoid force causes the actuating rod 38 to be driven upward, The valve is closed, and the sub-valve is opened. That is, the main valve body 30 seats on the main valve seat 22 and closes the main valve by first displacing the operating rod 38 relative to the sub valve body 36. Subsequently, while the main valve body 30 is seated on the main valve seat 22 and the operating rod 38 is further displaced relative to the body 5, the sub valve body 36 is brought into contact with the sub valve seat 34) to open the valve of the sub-valve. However, the lift amount of the sub valve body 36 (that is, the opening degree of the sub valve) is restricted by the top surface 92 of the sub valve body 36 being engaged with the body 5. Since the suction pressure Ps is relatively high at the time of starting, the bellows 45 is kept in a contracted state and the open valve state of the sub valve is maintained.

That is, when the starting current is supplied to the solenoid 3, the main valve is closed, the sub valve is opened while the introduction of the discharge refrigerant into the crank chamber is regulated, and the refrigerant in the crank chamber is rapidly relieved to the suction chamber. As a result, the compressor can be started quickly. Further, even when the suction pressure Ps is low and the bellows 45 is stretched, for example, as in the case where the vehicle is placed in a low temperature environment, the sub valve can be opened by supplying a large current to the solenoid 3, The compressor can be started quickly.

Even when the sub valve body 36 is locked in the valve-opening direction by the inclusion of foreign matter into the sliding portion of the sub valve body 36 at the time of starting the control valve 1, the solenoid force causes the sub- The lock can be released by pressing the valve body 36. Even if the sub valve body 36 locks in the valve closing direction due to foreign matter mixed into the sliding portion of the sub valve body 36, for example, the suction pressure Ps decreases due to the start of the control valve 1 , When 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 to release the lock.

When the current value supplied to the solenoid 3 is in the control state set to the predetermined value, the bellows 45 expands because the suction pressure Ps is relatively low as shown in Fig. 4, The operation is connected. As a result, the main valve body 30 operates to adjust the opening degree of the main valve. At this time, the main valve body 30 is connected to the power element 6 operating in accordance with the force in the valve opening direction by the spring 47, the solenoid force in the valve closing direction by the solenoid 3, and the suction pressure Ps, The force against the solenoid force by the valve is stopped by the balanced valve lift position. In the control state of the main valve, the valve closed state of the sub-valve is maintained because the sub-valve body 36 is held in the sub-valve seat 34 by the urging force of the spring 44 .

For example, if the freezing load becomes larger and the suction pressure Ps becomes higher than the set pressure Pset, the bellows 45 is contracted, and therefore the main valve body 30 is displaced upward (valve closing direction) relatively. As a result, the valve opening of the main valve becomes small, and the compressor operates to increase the discharge capacity. As a result, the suction pressure Ps changes in the direction of lowering. On the other hand, when the refrigerating load becomes small and the suction pressure Ps becomes lower than the set pressure Pset, the bellows 45 expands. As a result, the urging force of the power element 6 acts in the direction against the solenoidal force. As a result, the force of the main valve body 30 in the closing direction of the valve is reduced so that the opening degree of the main valve is increased, and the compressor operates to decrease the discharge capacity. As a result, the suction pressure Ps is maintained at the set pressure Pset.

When the load on the engine increases during the execution of the normal control and the load on the air conditioner is reduced, the solenoid 3 is switched from ON to OFF by the control valve 1. [ The suction force does not act between the core 46 and the plunger 50 and the main valve body 30 is separated from the main valve seat 22 by the urging force of the spring 47, All are in the open state. At this time, since the sub valve body 36 is seated on the sub valve seat 34, the sub valve is closed. The refrigerant of the discharge pressure Pd introduced into the port 16 in the discharge chamber of the compressor passes through the main valve in the fully open state and flows from the port 14 to the crank chamber. Therefore, the crank chamber pressure Pc is increased, and the compressor performs the mini-capacity operation.

As described above, in the present embodiment, the sub valve seat 34 is not formed in the main valve body 30 but is formed in a part of the body 5. Therefore, the sizes of the sub-valve hole 32 and the sub-valve body 36 can be set independently of the size of the main valve body 30. That is, the size of the sub-valve can be set regardless of the size of the main valve. Particularly, by providing the sub 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 becomes larger, the sub valve body 36 can be made sufficiently large A large flow rate can be obtained at the time of opening the sub-valve, and the bleed function can be enhanced. In addition, by providing the main valve seat 22 integrally with the sub valve body 36, the number of parts can be reduced. The main valve seat 22 and the sub valve body 36 are integrally formed so that the main valve seat 22 is moved after the main valve is closed, It is not necessary to individually adjust the timing at which the main valve is closed and the timing at which the sub valve is opened, so that it is possible to reduce the number of parts to be selected and adjusted parts , The assemblability improves dramatically.

[Second Embodiment]

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. Therefore, the following description focuses on differences from the first embodiment. In the same drawing, substantially the same components as those in the first embodiment are denoted by the same reference numerals.

The control valve 201 has a structure in which the body 205 and the sub valve body 236 in the valve body 202 are different from those in the first embodiment. Also 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. The body 205 is composed of a first body 81 and a second body 282. The guide hole 25 of the second body 282 slidably supports the upper end 94 of the operating rod 38. A spring support member 240 is provided below the main valve body 30 in the operation rod 38. [ A spring 242 (functioning as a "biasing member") for biasing the sub valve body 236 in the valve opening direction of the sub valve is provided between the sub valve body 236 and the spring support member 240 Lt; / RTI > In the present embodiment, the spring 47 shown in Fig. 1 is not provided.

The sub valve body 236 is supported at two points by the guide hole 26 and the guide hole 27. Ring 228 (functioning as a "sealing member") is provided on the surface of the sub-valve 236 opposed to the guide hole 27. [ This prevents the refrigerant introduced from the port 16 from leaking to the port 18 through the gap between the sub valve body 236 and the guide hole 27. [

The effective hydraulic diameter E (actual diameter) of the main valve of the main valve body 30 and the effective hydraulic diameter F (actual diameter) of the sliding portion of the operating rod 38 are set to be the same have. Therefore, 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. Although the operation rod 38 and the plunger 50 are not fixed as in the first embodiment in the present embodiment, the operation rod 38 is urged against the plunger 50 by the reaction force of the spring 242 The operating rod 38 and the plunger 50 can always be held in contact with each other. In other words, the working rod 38 is not required to be press-fitted into the plunger 50.

[Third embodiment]

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 the present embodiment is different from the first embodiment in that a main valve sheet is formed in a valve seat forming member provided separately. Therefore, the following description focuses on differences from the first embodiment. In the same drawing, substantially the same components as those in the first embodiment are denoted by the same reference numerals.

The control valve 301 includes the valve body 305 of the valve body 302 formed of the first body 81 and the 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 control valve 301 as a whole. On the upper portion of the second body 382, a disk-shaped partition member 380 for partitioning the pressure chamber 23 is press-fitted. A guide hole 25 is formed so as to pass through the partition member 380. The guide hole 25 slidably supports the upper end 94 of the operating rod 38. [ On the lower side of the main valve body 330 in the operation rod 38, a pair of ring-shaped locking members 340 and 342 are inserted in the axial direction at predetermined intervals

In the guide hole 26, a cylindrical valve seat forming member 350 is slidably inserted. The valve seat forming member 350 is provided with an engagement portion 352 projecting radially outwardly from the upper end thereof. A spring 344 (functioning as a "biasing member") for biasing the valve seat forming member 350 downward is provided between the lock portion 352 and the partition member 380. [ A main valve hole 20 is formed in the inside of the valve seat forming member 350, and a main valve seat 22 is formed at the lower end opening.

The sub valve body 336 has a bottomed cylindrical shape and is configured so that its bottom portion is supported between the locking member 340 and the locking member 342. At the bottom of the sub valve body 336, a plurality of communication holes 337 for circulating the refrigerant is provided. The effective hydraulic diameter E (sealing member diameter) and the effective hydraulic diameter F (sealing member diameter) of the sliding portion of the operating rod 38 in the main valve of the main valve body 330 are set to be the same . 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 this arrangement, when the solenoid 3 is not energized, the sub valve body 336 maintains the closed valve state of the sub valve by the biasing force of the spring 44 as shown in the figure. The valve seat forming member 350 maintains the state in which the engagement portion 352 is engaged with the second body 382. [ 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 brought into the fully open state . The amount of lift L2 from the main valve seat 22 of the main valve body 330 and the distance between the bottom surface of the sub valve body 336 and the locking member 342 (L3) are set to be the same.

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 in which the main valve body 330 is lifted, since the locking member 342 does not engage with the sub valve body 336, the sub valve is not opened. The main valve body 330 autonomously operates so that the suction pressure Ps of the pressure chamber 23 becomes a predetermined set pressure Pset.

On the other hand, at the time of starting the control valve 1, the operation rod 38 is relatively displaced with respect to the sub valve body 336 by energization of the solenoid 3, The sub valve body 336 can be provided with a driving force in the valve opening direction through the main valve body 330 by closing the main valve. Thereby, the sub valve body 336 can be lifted from the sub valve seat 34 to open the sub valve. That is, the control valve 301 also has a "forced valve opening mechanism" for forcibly opening the sub valve by using the driving force of the solenoid 3. When the sub valve member 36 is locked by the foreign substance mixed into the sliding portion between the sub valve member 336 and the guide holes 26 and 27, this configuration is advantageous in that when the sub valve member 36 is locked, , A pushing mechanism).

[Fourth Embodiment]

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 that of the first embodiment in the configuration of the valve body. Therefore, the following description will focus on differences from the first embodiment. In the same drawing, substantially the same components as those in the first embodiment are denoted by the same reference numerals.

The control valve 401 is configured such that the body 405 of the valve body 402 is assembled with the first body 481 and the second body 482. Also in the present embodiment, the body 405, the core 46, the case 56, and the end member 58 form the body of the control valve 401 as a whole. A main valve is provided on the inside 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 the lower half of the second body 482 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 of the first body 481 and the second body 482. A port 16 is formed on the lower half side of the overlapped portion of the first body 481 and the second body 482.

The main valve body 430 has a cylindrical shape with a stepped portion and is slidable in the axial direction by a guide hole 25 provided at the center portion of the second body 482 and a guide hole 426 provided at the lower end portion . 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 of the main valve body 430 in the axial direction is reduced in diameter and the lower base portion of the reduced diameter portion is attached to and detached from the main valve seat 22 to constitute a detachable portion for opening and closing the main valve. On the surface of the main valve body 430 opposed to the guide hole 25, a labyrinth seal 495 having a plurality of annular grooves for suppressing the flow of refrigerant is provided. The pressure chamber 23 is formed above the main valve body 430.

On the other hand, in the first body 481, the sub valve hole 32 is formed below the second body 482, and the sub valve seat 34 is formed at the top opening. The sub valve body 436 has a cylindrical shape with a bottom and is inserted into the outside so as to be slidable on the lower end of the second body 482. A through hole 441 is provided at the bottom center of the sub valve body 436 and an operating rod 38 is provided through the sub valve body 436 and the main valve body 430. An engaging member 498 is fixed to an intermediate portion of the operating rod 38, and an upper surface thereof forms a coupling portion 496. [ When the operating rod 38 is operated upward and the locking member 498 is engaged with the lower surface of the sub valve body 436, upward force (valve opening direction of the sub valve) is transmitted to the sub valve body 436 . An engaging member 499 is fixed to the upper end of the operating rod 38 as well. When the operating rod 38 is operated downward and the engaging member 499 engages with the upper surface of the main valve body 430, a downward force (valve opening direction of the main valve) is transmitted to the main valve body 430 .

The sub valve body 436 is disposed to be sandwiched between the lower surface of the main valve body 430 and the engaging portion 496. A spring 444 (functioning as a "biasing member") is provided between the main valve body 430 and the sub-valve body 436 so as to urge the main valve body 430 and the sub- A pressure chamber 428 is formed between the sub valve body 436 and the core 46 so that the suction pressure Ps is satisfied. 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 of the sub valve body 436. The space enclosed 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. [

The engagement portion 496 of the actuating rod 38 and the sub-valve body 436 are spaced apart from each other by a predetermined distance L1 at the time of full opening of the main valve (valve closing of the sub-valve) The position of the engaging portion 496 is set. In the present embodiment, the predetermined interval L1 is made equal to the lift amount of the main valve body 430 from the main valve seat 22 when the main valve is fully opened. This prevents the sub valve from being opened in the control state of the main valve. In addition, the distance between the sub valve body 436 and the main valve body 430 at the time of closing the main valve becomes the total open stroke of the sub valve.

(E) actual part diameter in the main valve of the main valve body 430) and the effective hydraulic diameter F (actual part diameter) of the upper sliding part of the main valve body 430 are the same . Therefore, the influence of the discharge pressure Pd acting on the main valve body 430 is canceled. On the other hand, since the effective hydraulic pressure G (actual part diameter) of the lower sliding part of the main valve body 430 is set larger than the effective hydraulic pressure F (actual part diameter) of the upper sliding part, The differential pressure Pc-Ps in the valve opening direction corresponding to the difference GF between the diameters is applied. The effective pressure-receiving diameter A (actual diameter) of the sub-valve of the sub-valve body 436 and the effective pressure-receiving diameter B (actual diameter) of the sliding portion of the sub-valve body 436 are set in the sub- The differential pressure Pc-Ps in the valve closing direction corresponding to the difference AB between the diameter and the diameter acts.

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

On the other hand, when the control valve 401 is started, the actuating rod 38 is relatively displaced with respect to the sub valve body 436 by energization of the solenoid 3, 436 to push it up. Thereby, the sub valve body 436 can be lifted from the sub valve seat 34 to open the sub valve. That is, the control valve 401 also has a "forced valve opening mechanism" for forcibly opening the sub valve by using the driving force of the solenoid 3. This configuration also functions as a lock releasing mechanism (interlocking mechanism, pressing mechanism) for releasing the valve body when each valve body is locked by the inclusion of foreign matter into the sliding portions of the main valve body 430 and the sub valve body 436 do.

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

In the above-described embodiments, a so-called Ps sensing valve that operates by detecting the suction pressure Ps as the sensing pressure is shown as the control valve, but may be constructed as a so-called Pc sensing valve that operates by sensing the crank pressure Pc . In this case, the port 12 is made to communicate with the crank chamber.

In the above embodiment, the example in which the bellows 45 is employed as the pressure-reducing member constituting the power element 6 is shown, but a diaphragm may be employed. In this case, a plurality of diaphragms may be connected in the axial direction in order to secure a required operation stroke as the pressure-reducing member.

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

Although the spring (coil spring) is exemplified as the urging member with respect to the springs 44, 47, 242, 344, and 444 in the above embodiment, an elastic member such as rubber or resin or a resilient mechanism such as a leaf spring may be employed It is natural.

In the above-described embodiment, the so-called introduction control valve for controlling the flow rate or pressure of the refrigerant introduced into the crankcase from the discharge chamber of the variable displacement compressor is shown. However, in the modified example, the flow rate of the refrigerant led out from the crankcase to the suction chamber It may be configured as a so-called derivation control valve for adjusting the pressure. Further, the configuration of the above-described embodiment can be applied to a complex valve which is provided with a main valve and a sub valve in a common body such as another type of three-way valve and driven by a single solenoid.

In the above embodiment, the reference pressure chamber S in the bellows 45 is in the vacuum state. However, the atmosphere may be satisfied or the reference gas may be satisfied. Alternatively, any one of the discharge pressure Pd, the crank pressure Pc, and the suction pressure Ps may be satisfied. And the power element 6 appropriately operates by detecting the pressure difference between the inside and the outside of the bellows. In the above embodiment, the discharge pressure Pd is canceled with respect to the main valve body, but the pressure applied to the main valve body may not be canceled.

In the above embodiment, the power element 6 can be brought into contact with the sub valve body 36, and even if the sub valve body 36 is locked, the power element 6 can be released by the driving force of the power element 6 . 6, the power element 6 can be brought into contact with the valve-sheet-forming member when the valve-sheet-forming member is a separate member from the sub-valve member, and the valve- It may be configured such that it can be released by the driving force of the power element 6 even if it is locked.

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

1: Control valve
2:
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: 0 ring
30: Main valve body
32: Sub valve hole
34: Sub-valve seat
36: Sub valve body
38: Operation rod
45: bellows
201: Control valve
202: valve body
205: Body
228: 0 ring
236:
301: Control valve
302: valve body
305: Body
330: main valve body
336:
340, 342:
350: valve seat forming member
401: Control valve
402: valve body
405: Body
426: Guide hole
430: main valve body
436:
496:

Claims (4)

Adjusting a flow rate or pressure of at least one of a refrigerant introducing the refrigerant introduced into the suction chamber into the crank chamber and a refrigerant leading from the crank chamber to the suction chamber, the discharge capacity of the variable capacity compressor discharging in the discharge chamber by compressing the refrigerant introduced into the suction chamber The control valve for a variable capacity compressor,
A main passage for communicating the discharge chamber and the crank chamber, a body having 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 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 body which is attached to and detached from the sub valve seat to open and close the sub valve,
A depressurizing portion for depressurizing a predetermined sensed pressure and generating a driving force in a valve opening direction of the main valve corresponding to the magnitude of the sensed pressure;
And a solenoid for generating a driving force in a valve closing direction of the main valve corresponding to a supplied current amount.
The depressurizing portion is disposed on one side of the main valve body, the solenoid is disposed on the other side of the main valve body,
The sub valve seat is provided integrally with the body,
Wherein the actual diameter of the sub-valve of the sub-valve body is larger than the actual diameter of the main valve of the main valve body. The method according to claim 1,
Wherein the body includes a discharge chamber communication port communicating with the discharge chamber, a crank chamber communication port communicating with the crank chamber, and a suction chamber communication port communicating with the suction chamber,
And the crank chamber communication port is disposed between the discharge chamber communication port and the suction chamber communication port. 3. The method according to claim 1 or 2,
And the sub-valve body is slidably supported by the body. The method of claim 3,
The sub valve body of the sub valve body is set equal to the actual part diameter of the sliding portion of the sub valve body so that the crank pressure of the crank chamber acting on the sub valve body, Wherein at least a part of the influence of the suction pressure of the suction chamber is canceled.

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