KR20170120023A - Control valve for variable displacement compressor - Google Patents

Abstract

The control precision of the variable displacement compressor can be improved with a simple structure. The control valve 1 includes a solenoid 4 assembled to the body 5 and a pressure sensor 8 for detecting a predetermined refrigerant pressure referred to the energization control of the solenoid 4. The solenoid (4) has a solenoid body integrally assembled with the body (5) in the axial direction; An electromagnetic coil 54 held by the solenoid body and having a working space formed therein; A core 46 fixed to the solenoid body coaxially with the electromagnetic coil 54; A plunger (50) displaceably supported in the working space in an axial direction; And a power supply line connected to the electromagnetic coil 54 and drawn out from the side opposite to the body 5 of the solenoid body. The pressure sensor 8 includes a decompression section for detecting and displacing the refrigerant pressure and an output line for outputting a detection signal according to the displacement of the decompression section and is disposed on the side opposite to the body 5 with respect to the electromagnetic coil 54 have.

Description

[0001] CONTROL VALVE FOR VARIABLE DISPLACEMENT COMPRESSOR [0002]

The present invention relates to a control valve for controlling a discharge capacity of a variable capacity compressor.

BACKGROUND ART An automotive air conditioner is generally constituted by arranging a compressor, a condenser, an expansion device, an evaporator, and the like in a refrigeration cycle. As the compressor, a variable displacement compressor (sometimes abbreviated as "compressor") capable of varying the discharge capacity of the refrigerant is used so that a constant cooling capacity is maintained irrespective of the number of revolutions of the engine. In this compressor, a compression piston is connected to a swing plate mounted on a rotary shaft driven 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 swinging plate is continuously changed by introducing a part of the discharge refrigerant into the closed control chamber and changing the balance of the pressure applied to both surfaces of the piston. The pressure in the control chamber (hereinafter referred to as "control pressure") Pc is adjusted by a control valve provided between the discharge chamber and the control chamber of the compressor or between the control chamber and the suction chamber.

Such a control valve has various control methods, for example, to control the differential pressure between predetermined two points in the compressor to be the set differential pressure, to control the predetermined pressure to be the set pressure, and the solenoid . Any of the control valves includes a mechanism for transmitting the driving force of the solenoid to the valve body, a spring for generating a counterforce against the driving force, and the like. Although the set differential pressure or the set pressure is mechanically set by the load of the spring, it can be electrically changed by changing the supply current value to the solenoid.

Such a control valve operates according to a control command of the external control device. The control device determines the set differential pressure or the set pressure based on predetermined external information detected by various sensors such as the engine speed of the vehicle, the temperature of the vehicle interior and exterior, and the temperature of the air blown by the evaporator. Then, energization control is performed on the control valve so as to obtain a driving force for maintaining them (see, for example, Patent Document 1). At this time, even if the refrigerant pressure fluctuates, the valve mechanism operates autonomously so that the set differential pressure or set pressure corresponding to the supply current value is maintained.

Japanese Patent Application Laid-Open No. 2001-107854

In order to improve the precision of such control, for example, there is a feedback control in which the set differential pressure or the set pressure is set as a target value. The compressor is provided with a pressure sensor for detecting a pressure subject to feedback control. However, if the pressure sensor is additionally provided as described above, the number of mounting holes for mounting the pressure sensor in the compressor increases, thereby increasing the leakage area of the refrigerant, and increasing the sealing structure for sealing the leakage area . As a result, there has been a problem of causing the compressor to be large-sized and manufacturing costs to be increased.

It is an object of the present invention to realize improvement of the control precision of the variable displacement compressor with a simple structure.

One embodiment of the present invention is a control valve assembled to be inserted into a mounting hole provided in a variable displacement compressor and controlling a discharge capacity of a refrigerant discharged from the compressor. The control valve includes a valve body having a refrigerant flow path and a valve hole provided in the flow path; A valve body that opens and closes the valve portion by being in contact with the valve hole; A solenoid mounted on the valve body for applying a driving force in the axial direction corresponding to the supply current to the valve body; And a pressure sensor for detecting a predetermined refrigerant pressure referred to in energization control of the solenoid.

The solenoid includes a solenoid body integrally assembled with the valve body in the axial direction; An electromagnetic coil held by the solenoid body and having a working space formed therein; A core secured to the solenoid body in a coaxial fashion with the electromagnetic coil; A plunger displaceably supported in the axial direction in the working space; And a power supply line connected to the electromagnetic coil and drawn out from the side opposite to the valve body of the solenoid body. The pressure sensor includes a depressurizing portion for detecting and displacing the refrigerant pressure and an output line for outputting a detection signal according to the displacement of the depressurizing portion, and is arranged on the opposite side of the electromagnetic coil from the valve body.

Since the control valve according to this embodiment is inserted into the mounting hole of the compressor from the front end side (i.e., the front end side of the valve body), a pressure sensor is integrally provided on the rear end side (i.e., the rear end side of the solenoid body) . Further, the power line of the solenoid and the output line of the pressure sensor are gathered on the solenoid body side. Therefore, a common mounting hole may be provided in the compressor for mounting the control valve and the pressure sensor. That is, the control accuracy of the compressor can be improved with a simple structure.

According to the present invention, the control precision of the variable displacement compressor can be improved with a simple structure.

1 is a view showing a system to which a control valve according to the first embodiment is applied.
2 is a schematic diagram showing the electrical configuration of the control valve and its periphery.
3 is a view schematically showing a refrigeration cycle with the compressor as a center.
4 is a cross-sectional view showing the configuration of a control valve according to the first embodiment.
5 is an enlarged view of part A of Fig.
6 is a cross-sectional view showing the configuration of a control valve according to the second embodiment.
7 is a cross-sectional view showing the configuration of a control valve according to the third embodiment.
8 is a sectional view showing the configuration of a control valve according to the fourth embodiment.
9 is a sectional view showing the configuration of a control valve according to the fifth embodiment.
10 is a schematic diagram showing an electrical configuration of a control valve and a periphery thereof according to a modification.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. On the other hand, in the following description, for convenience, the positional relationship of each structure may be expressed on the basis of the illustrated state.

 [First Embodiment]

1 is a view showing a system to which a control valve according to the first embodiment is applied.

The control valve 1 is applied to an air conditioning system which is part of a vehicle control system. In this vehicle control system, a plurality of electronic control devices (hereinafter referred to as "ECU") for controlling each system system are connected via a network mounted on the vehicle. As shown in the figure, an engine ECU 101 for controlling the engine, a brake ECU 103 for controlling the brake device, and an air conditioner ECU 105 for controlling the air conditioner are connected via a communication line L1. The air conditioner ECU 105 is connected to the control unit of each device constituting the air conditioning system through the communication line L2.

In this embodiment, the communication line L1 of the main network is the CAN bus, and the communication line L2 of the subnetwork is the LIN bus. That is, CAN (Controller Area Network) is adopted as a communication protocol of the main network, and LIN (Local Interconnect Network) is adopted as a communication protocol of the subnetwork. The air conditioner ECU 105 operates as a master node connected to the LIN bus. On the other hand, the control valve 1 operates as a slave node connected to the LIN bus. On the other hand, in the modified example, CAN may be employed for both the main network and the subnetwork. Alternatively, at least one of the main network and the subnetwork may employ a communication protocol other than CAN or LIN.

The refrigeration cycle of the air conditioning system includes a compressor 100 for compressing a circulating refrigerant, a condenser 111 for condensing the compressed refrigerant, an expansion valve 113 for diverging the condensed refrigerant to send it in a mist state, An evaporator 115 for evaporating the refrigerant in the state of the evaporator and cooling the air in the inside of the vehicle by the latent heat of evaporation, and the like. The compressor 100 is a variable displacement compressor. The control valve 1 is a solenoid-driven solenoid valve, and controls the discharge capacity of the compressor 100 in accordance with a command from the air conditioner ECU 105. [

The air conditioner ECU 105 calculates the target suction pressure Ps of the compressor 100 based on predetermined external information detected by various sensors such as the engine speed, the indoor / outdoor temperature of the vehicle, and the discharged air temperature of the evaporator 115 (The set pressure Pset). Then, information indicating the set pressure Pset is outputted to the control valve 1 as a command signal. The control valve 1, when receiving the command signal, executes energization control of the solenoid so that the suction pressure Ps is maintained at the set pressure Pset. This energization control is performed by feedback control, which will be described later. The air conditioner ECU 105 also outputs a command signal indicative of the request to reduce the load torque of the compressor 100 from the engine ECU 101 in a high load state of the engine such as when the vehicle is accelerating, (1). When receiving the command signal, the control valve 1 cuts off the energization to the solenoid or suppresses the solenoid to a predetermined lower limit value, and causes the compressor 100 to transition to the minimum capacity operation.

Fig. 2 is a schematic view showing an electrical configuration of the control valve 1 and the periphery thereof.

The control device of the control valve 1 is constituted by mounting various circuits functioning as a control unit or a communication unit on the circuit board 121. [ This control device is constructed around a microcomputer 123 and includes a power supply circuit 125, a communication circuit 127 (transceiver), and a drive circuit 129. [ The microcomputer 123 functions as a "control unit " and the communication circuit 127 functions as a" communication unit ". The circuit board 121 is also provided with a pressure sensor 8 for detecting the suction pressure Ps.

The power supply circuit 125 supplies the power supply voltage supplied through the air conditioner ECU 105 to the microcomputer 123, the communication circuit 127, the drive circuit 129 and the pressure sensor 8. [ Power supply to the solenoid 4 is also performed through the power supply circuit 125. [ That is, the power supply line 55 and the ground line 57 of the solenoid 4 are connected to the microcomputer 123 through the drive circuit 129. The power from the power supply circuit 125 is supplied to the drive circuit 129 and further to the solenoid 4 through the microcomputer 123. The detection signal of the pressure sensor 8 is input to the microcomputer 123 via the output line 59. [

The microcomputer 123 includes a CPU for executing various arithmetic processing, a ROM for storing control programs and the like, a RAM used as a work area for data storage and program execution, and a nonvolatile memory (EEPROM Etc.), an input / output interface, and the like.

The communication circuit 127 is configured as a LIN transceiver and receives a command signal from the air conditioner ECU 105 and transmits it to the microcomputer 123. [ Further, the microcomputer 123 transmits an output signal from the microcomputer 123 to the air conditioner ECU 105. The drive circuit 129 outputs a duty-controlled drive signal to the electromagnetic coil of the solenoid 4 in response to a command from the microcomputer 123. [

The microcomputer 123 sets the control amount (the duty ratio of the supply current to the solenoid 4) for bringing the suction pressure Ps close to the set pressure Pset in accordance with the control command received via the communication circuit 127 And outputs a drive command (drive pulse) to the drive circuit 129 for realizing the operation. The drive circuit 129 supplies a duty-controlled drive current (current pulse) to the solenoid 4 in accordance with the drive command.

In the present embodiment, feedback control is performed to bring the suction pressure Ps close to the set pressure Pset. That is, information indicating the optimum set pressure Pset according to the vehicle control state is transmitted from the air conditioner ECU 105 as a control command. The microcomputer 123 receives this control command while acquiring the information of the actual suction pressure Ps detected by the pressure sensor 8. [ Then, the duty ratio is calculated based on the deviation between the detected suction pressure Ps and the set pressure Pset, and the duty-controlled drive signal is output.

The power line VCC, the ground line GND and the communication line L2 extend from the air conditioner ECU 105 and the power terminal 72a of the circuit board 121, The terminal 72b, and the communication terminal 72c, respectively. The ground line (GND) of each circuit on the circuit board 121 is connected to the ground terminal 72b.

3 schematically shows a refrigeration cycle around the compressor 100. As shown in Fig.

The compressor 100 includes a control valve 1 for controlling the discharge capacity of the refrigerant, and a discharge valve 160 for preventing backflow of the discharge refrigerant, in addition to the mechanism for compressing the refrigerant in the housing.

The housing of the compressor 100 includes a cylinder block 102, a front housing 104 joined to the front end side of the cylinder block 102, and a rear housing 106 joined to the rear end side of the cylinder block 102 And assembled. A valve plate 108 is interposed between the cylinder block 102 and the rear housing 106. The cylinder block 102 has a plurality of cylinders 110 around its axis. A crank chamber 112 is formed in a space surrounded by the cylinder block 102 and the front housing 104. In the present embodiment, the crank chamber 112 corresponds to the "control chamber ", but in the modified example, the pressure chamber separately provided in the crank chamber or the crank chamber may be a" control chamber ".

A suction chamber 114, a discharge chamber 116, and a mounting hole 118 are formed in the rear housing 106 in an area. The rear housing 106 also has a refrigerant inlet 120 for introducing refrigerant from the evaporator 115 side into the suction chamber 114 and a refrigerant outlet for discharging the refrigerant discharged from the discharge chamber 116 to the condenser 111 side A communication passage 124 for communicating the crank chamber 112 with the mounting hole 118, a communication passage 126 for communicating the crank chamber 112 with the mounting hole 118, a discharge chamber 116, And a communication path 128 for communicating the hole 118 is provided.

In the crank chamber 112, a rotation shaft 130 is disposed so as to pass through the center thereof. The rotary shaft 130 is rotatably supported by a bearing 132 provided in the cylinder block 102 and a bearing 134 provided in the front housing 104. [ A lag plate 136 is fixed to the rotary shaft 130 and the swash plate 140 (corresponding to the "swing plate") is supported via a support arm 138 projected from the lag plate 136.

The swash plate 140 is capable of tilting with respect to the axis of the rotating shaft 130 and is connected to the pistons 142 slidably disposed in the plurality of cylinders 110 through the shoes 144. The front end portion of the rotating shaft 130 extends through the front housing 104 to the outside and a bracket 146 is screwed to the front end portion. A lip seal 148 is provided to seal the gap between the rotary shaft 130 and the front end portion of the front housing 104 from the outside. The lip seal 148 is in sliding contact with the circumferential surface of the rotating shaft 130 to prevent the refrigerant gas from leaking along the circumferential surface thereof.

A bearing 150 is provided at a front end portion of the front housing 104, and a pulley 152 is rotatably supported. The pulley 152 transmits the driving force of the engine to the rotating shaft 130 through the bracket 146. [

The suction chamber 114 communicates with the cylinder 110 through a suction relief valve 154 provided in the valve plate 108 and also through the refrigerant inlet 120 to the outlet of the evaporator 115. The discharge chamber 116 communicates with the cylinder 110 via a discharge relief valve 156 provided in the valve plate 108 and also communicates with the inlet of the condenser 111 through the refrigerant outlet 122. On the other hand, an orifice having a fixed cross-sectional area is disposed in a refrigerant passage (not shown) which communicates with the crank chamber 112 and the suction chamber 114. The orifice having a small cross-sectional area is disposed from the crank chamber 112 to the suction chamber 114 And the internal circulation of the refrigerant in the compressor 100 is ensured.

The angle of the swash plate 140 is determined by the load of the springs 157 and 158 biasing the swash plate 140 in the crank chamber 112 or the load applied to both surfaces of the piston 142 connected to the swash plate 140 The load due to pressure and the like are maintained in a balanced position. The angle of the swash plate 140 is controlled by changing the control pressure Pc by introducing a part of the discharged refrigerant into the crank chamber 112 and changing the balance of the pressure applied to both surfaces of the piston 142, Can be changed. By changing the stroke of the piston 142 by the angle change of the swash plate 140, the discharge capacity of the refrigerant is adjusted. The pressure in the crank chamber (112) is controlled by the control valve (1).

The discharge valve 160 is disposed between the discharge chamber 116 and the refrigerant outlet 122 in the rear housing 106. The discharge valve 160 functions as a "check valve " which allows the forward flow of the refrigerant discharged from the compressor 100 and blocks the flow in the reverse direction. On the upstream side of the discharge valve 160, a fixed orifice 117 is provided. A differential pressure Pd1-Pd2 between the first discharge pressure Pd1 as the upstream pressure and the second discharge pressure Pd2 as the downstream pressure is generated before and after the fixed orifice 117. [ The first discharge pressure Pd1 is equal to the pressure in the discharge chamber 116. [ The control valve 1 may detect the differential pressure Pd1-Pd2 when the flow rate control for controlling the discharge flow rate of the compressor 100 to be constant is performed. However, the pressure loss due to the fixed orifice 117 is practically negligible in the entire refrigeration cycle, and there is no large difference between the first discharge pressure Pd1 and the second discharge pressure Pd2. Therefore, in the following description, they are generically referred to as "discharge pressure Pd"

The compressor 100 constructed as described above introduces the refrigerant gas introduced into the suction chamber 114 from the evaporator 115 side into the cylinder 110 and compresses the refrigerant gas from the discharge chamber 116 to the condenser 111 side, Of the refrigerant. A part of the discharged refrigerant is introduced into the crank chamber 112 through the control valve 1 and is provided for capacity control of the compressor 100. [

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

The control valve 1 is configured as a Ps control valve for controlling the flow rate of the refrigerant introduced into the crank chamber 112 from the discharge chamber 116 so as to maintain the suction pressure Ps of the compressor 100 at the set pressure . The control valve 1 is constructed by assembling the valve unit 2, the solenoid 4, and the control unit 6. The control unit 6 includes a pressure sensor 8 and is provided integrally with the solenoid 4.

The valve unit 2 includes a main valve for introducing a part of the discharge refrigerant into the crank chamber 112 during operation of the compressor 100 and a main valve for introducing the refrigerant in the crank chamber 112 into the suction chamber (So-called bleed valve) for relieving the refrigerant to be discharged into the discharge chamber 114. The solenoid 4 drives the main valve in the opening and closing direction to adjust its opening degree to control the refrigerant flow rate introduced into the crank chamber 112. The valve unit 2 has a cylindrical body 5 (functioning as a "valve body") having a step, a main valve and a sub valve provided inside the body 5, and the like.

The body 5 is provided with ports 12, 14, 16 from the upper end thereof. The port 12 functions as a "suction chamber communication port" and communicates with the suction chamber 114. The port 14 functions as a "control chamber communication port " and communicates with the crank chamber 112. The port 16 functions as a "discharge chamber communication port" and communicates with the discharge chamber 116.

A main passage for communicating the port 16 and the port 14 and a sub passage for communicating the port 14 and the port 12 are formed in the body 5. A main valve is provided in the main passage, and a sub valve is provided in the sub passage. That is, the control valve 1 has a configuration in which a sub valve, a main valve, a solenoid 4, and a control unit 6 are arranged in order from one end side. 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 114 with the operation chamber 23 partitioned at the upper portion of the body 5. [ The port 16 introduces the refrigerant of the discharge pressure Pd from the discharge chamber 116. A main valve chamber (24) is provided between the port (16) and the main valve hole (20), and a main valve is disposed. The port 14 draws the refrigerant having the control pressure Pc toward the crank chamber 112 via the main valve at the time of normal operation of the compressor 100, (Pc) discharged from the compressor (112). A sub valve chamber (26) is provided between the port (14) and the main valve hole (20), and a sub valve is disposed. The port 12 introduces the refrigerant at the suction pressure Ps during the normal operation of the compressor 100 and the refrigerant at the suction pressure Ps through the sub valve at the time of starting the compressor 100 And is directed toward the chamber 114.

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

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

The upper half of the valve drive body 29 is reduced in diameter and is divided into a partitioning portion 33 for partitioning inside and outside while passing through the main valve hole 20. [ The stepped portion formed in the middle portion of the valve driving body 29 is a main valve body 30 which is detachably attached to the main valve seat 22 to open and close the main valve. The main valve body 30 is attached to and detached from the main valve seat 22 at the side of the main valve chamber 24 to open and close the main valve so as to adjust the flow rate of the refrigerant flowing from the discharge chamber 116 to the crank chamber 112 . An upper portion of the partition portion 33 is enlarged in a tapered shape with its upper portion directed upward, and a sub valve seat 34 is formed at an upper end opening portion thereof. The sub valve seat 34 functions as a movable valve seat which is displaced together with the valve actuator 29. In this embodiment, the valve actuating member 29 and the main valve member 30 are distinguished from each other. However, the valve actuating member 29 may be regarded as the "main valve member ".

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

In addition, an operating rod 38 is formed along the axis of the body 5. The upper end of the operating rod 38 is connected to the sub-valve body 36. The lower end of the operating rod 38 is connected to the plunger 50 of the solenoid 4, which will be described later. The upper half of the operating rod 38 passes through the valve driving body 29, and its upper portion is reduced in diameter. And a sub-valve body 36 is fixed to the reduced-diameter portion.

A ring-shaped spring bearing 40 is fitted in and supported by the intermediate portion of the operating rod 38 in the axial direction. A spring 42 for biasing the valve actuator 29 in the closing direction of the main valve and the sub valve is interposed between the valve actuator 29 and the spring bearing 40. The main valve body 30 and the actuating rod 38 are integrally joined to each other in a state in which the valve actuating member 29 and the spring bearing 40 are in tight contact with each other by the elastic force of the spring 42. [ .

The relief of the refrigerant from the crank chamber 112 to the suction chamber 114 is blocked by the sub valve member 36 being seated on the sub valve seat 34 and closing the sub valve. The relief of the refrigerant from the crank chamber 112 to the suction chamber 114 is allowed by opening the sub valve away from the sub valve seat 34 of the sub valve body 36.

The solenoid 4 includes a cylindrical core 46 having a stepped portion and a cylindrical sleeve 48 having a bottom portion incorporated at the lower end of the core 46. The sleeve 48 is accommodated in the sleeve 48, Shaped bobbin 52 which is inserted into the core 46 and the sleeve 48 and which is wound around the bobbin 52. The cylindrical bobbin 52 is wound around the bobbin 52, An electromagnetic coil 54 for generating a magnetic circuit by energization and a cylindrical case 56 for covering the electromagnetic coil 54 from the outside and an end 56 for sealing the lower end opening of the case 56 (58) and a collar (60) embedded in the end member (58) below the bobbin (52). The collar 60 is made of a magnetic material and constitutes a yoke together with the core 46 and the case 56. Further, the case 56 and the end member 58 constitute a "solenoid body ".

The valve unit 2 and the solenoid 4 are fixed by pressing the lower end of the body 5 into the upper opening of the core 46. [ A pressure chamber 28 is formed between the core 46 and the valve actuator 29. 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 pressure chamber 28 communicates with the operating chamber 23 through the respective internal passages of the valve actuator 29 and the subvalve body 36. Therefore, the suction pressure Ps of the operating chamber 23 is introduced into the pressure chamber 28. The suction pressure Ps is also guided to the inside of the sleeve 48 through the communication passage 62 formed by the gap between the operation rod 38 and the core 46. [

Between the core 46 and the plunger 50, a spring 44 (which functions as a "biasing member") for biasing the both in a direction to separate them from each other is interposed. The spring 44 functions as a so-called off spring that opens the main valve when the solenoid 4 is turned off. The operation rod 38 is connected to the sub valve body 36 and the plunger 50 in a coaxial manner. The upper portion of the operation rod 38 is press-fitted into the sub valve body 36 and the lower end portion thereof is press-fitted into the upper portion of the plunger 50. The actuating rod 38, the sub-valve body 36 and the plunger 50 constitute a "movable member " which is displaced integrally with the valve actuator 29 in the control of the main valve.

The operating rod 38 suitably transmits the solenoidal force which is the suction force of the core 46 and the plunger 50 to the main valve body 30 and the sub valve body 36. [ On the other hand, a load by the spring 44 is loaded on the operation rod 38 so as to oppose the solenoidal force. That is, in the control state of the main valve, a force adjusted by the solenoid force acts on the main valve body 30, thereby appropriately controlling the opening of the main valve. At the time of starting the compressor 100, the operating rod 38 is displaced relative to the body 5 against the biasing force of the spring 44 in accordance with the magnitude of the solenoid force so as to close the main valve, (36) is pushed up to open the sub valve. Thereby exerting the bleed function.

The sleeve 48 is made of a non-magnetic material and has a cylindrical shape with a step. The upper end of the sleeve 48 is inserted into the lower end of the core 46 outwardly and is press-fitted. The lower portion of the sleeve 48 is reduced in diameter and is open to the pressure sensor 8. [

On the side surface of the plunger 50, there is provided a communication groove 66 parallel to the axis, and a communication hole 68 communicating with the inside and the outside is provided at the lower portion of the plunger 50. With this configuration, even when the plunger 50 is positioned at the bottom dead center as shown in the drawing, the suction pressure Ps is guided to the back pressure chamber 70 through the gap between the plunger 50 and the sleeve 48, And is also delivered to the pressure sensor 8.

A power supply line 55 and a ground line 57 connected to the electromagnetic coil 54 extend from the bobbin 52 to extend to the circuit board 121 of the control unit 6 . The power supply terminal 72a, the ground terminal 72b and the communication terminal 72c (collectively referred to as "connection terminal 72") described above are extended from the circuit board 121 to form end members 58 And is drawn out to the outside.

The end member 58 has a cylindrical shape with a step and is mounted so as to cover the entire structure in the solenoid 4 contained in the case 56 from below. The end member 58 is made of a resin material having corrosion resistance and is provided such that the resin material is also interposed between the case 56 and the electromagnetic coil 54. [ A connector portion 74 is integrally provided on the side of the end member 58 and a connection terminal 72 is disposed on the inside of the connector portion 74. [ On the inside of the end member 58, a storage chamber 76 is formed, and the control unit 6 is accommodated. And a cover member 78 is mounted so as to close the lower end opening of the end member 58. [

5 is an enlarged view of part A in Fig.

The control unit 6 is constituted by mounting a pressure sensor 8 and each of the circuits described above on a circuit board 121. [ The pressure sensor 8 includes a cylindrical sensor body 131 having a step and a sensor module 133 supported at the center of the sensor body 131. The sensor body 131 is composed of an upper body 135 and a lower body 137 and is assembled so as to sandwich the circuit board 121 (printed wiring board) therebetween. The sensor module 133 is provided inside the upper body 135. The sensor body 131 and the circuit board 121 are provided with a through passage 139 along the axis of the sensor body 131 and the sensor module 133 is disposed so as to traverse the through passage 139.

A pressure space is formed in the inside of the through passage 139 and is partitioned into a first pressure chamber 143 and a second pressure chamber 145 by a sensor module 133. The sensor module 133 includes a pressure sensitive element 161 (functioning as a "pressure reducing portion") formed by filling a protective material 155 between the sensor element 151 and the diaphragm 153. The diaphragm 153 is supported by a housing 163 provided inside the upper body 135. The housing 163 is composed of a cylindrical upper housing 165 having a step and a ring-shaped lower housing 167. The diaphragm 153 is supported between the upper housing 165 and the lower housing 167 such that the outer periphery thereof is fitted.

The sensor element 151 is provided with a pressure receiving portion 171 having a small thickness to be displaced by sensing the pressure and a supporting portion 173 having a thick thickness for supporting the pressure receiving portion 171 from the outside in the radial direction. The support portion 173 is mounted on the circuit board 121. [ The sensor element 151 is configured as a piezoresistive sensor, and a plurality of resistive elements such as strain gages are provided on the pressure receiving portion 171, and a bridge circuit is constituted by the plurality of resistive elements.

The protection material 155 is made of a fluorine-based, silicon-based rubber material or gel material and has electrical insulation properties. The protection member 155 is filled so as to cover the pressure receiving portion 171 of the sensor element 151 from above and protects the sensor circuit exposed on the upper surface of the pressure receiving portion 171. The pressure at which the diaphragm 153 is pressurized is also transmitted to the sensor element 151 through the protection material 155. [ That is, the protection material 155 also functions as a transfer material for transferring the pressure. The sensor element 151 outputs a detection signal in accordance with the differential pressure between the first pressure chamber 143 and the second pressure chamber 145. The detection signal by the sensor module 133 is outputted to the microcomputer 123 via the output line 59. [ On the other hand, in the modified example, an incompressible fluid such as oil may be used as the protective material 155 (transmitting material).

The pressure sensor 8 is supported so as to be axially fitted between the sleeve 48 and the cover member 78 and fixed to the end member 58 (solenoid body). An O-ring 175 is interposed between the small diameter portion of the sleeve 48 and the upper housing 165 and an O-ring 177 is interposed between the upper housing 165 and the upper body 135. Thereby, leakage of the refrigerant introduced into the back pressure chamber 70 is prevented.

The space surrounded by the sensor module 133 and the sleeve 48 becomes the first pressure chamber 143 and the suction pressure Ps of the back pressure chamber 70 is applied to the upper surface of the pressure- On the other hand, the second pressure chamber 145 communicates with the inside of the lower body 137. The second pressure chamber 145 is communicated with the communication hole 179, the containing chamber 76, and the internal passageway (not shown) of the connector portion 74 because the lower body 137 is provided with the communication hole 179 for communicating the inside and the outside 181 to the atmosphere. That is, atmospheric pressure is introduced into the second pressure chamber 145. Therefore, the pressure sensor 8 senses the differential pressure between the suction pressure Ps and the atmospheric pressure, that is, the gauge pressure of the suction pressure Ps. On the other hand, in the modified example, the second pressure chamber 145 may be closed to be in a vacuum state. Thereby, the pressure sensor 8 can sense the absolute pressure of the suction pressure Ps.

Next, the operation of the control valve will be described with reference to Fig.

In the present embodiment, a pulse width modulation (PWM) method is employed for energization control of the solenoid 4. The PWM control is performed by supplying a pulse current of about 400 Hz set at a predetermined duty ratio and is executed by the microcomputer 123 driving the drive circuit 129. [ The driving circuit 129 has a PWM output section for outputting a pulse signal (pulse current) having a specified duty ratio.

The suction force does not act between the core 46 and the plunger 50 when the solenoid 4 is turned off in the control valve 1, that is, when the air conditioning system is not operating. On the other hand, the biasing force of the spring 44 is transmitted to the valve actuator 29 through the plunger 50, the actuating rod 38 and the subvalve body 36. As a result, the main valve body 30 is separated from the main valve seat 22, and the main valve is opened. At this time, the sub-valve maintains the closed state.

On the other hand, when the starting current is supplied to the electromagnetic coil 54 of the solenoid 4 at the start of the air conditioning system, the sub valve is opened. This starting current is higher than the current (also referred to as "holding current") during normal control of the solenoid 4. That is, first, the main valve body 30 is pushed up by the biasing force of the spring 42 to sit on the main valve seat 22. Thereby, the main valve is closed and the introduction of the discharge refrigerant into the crank chamber 112 is regulated. At this time, since the solenoid force is applied to the biasing force of the spring 42, the sub valve body 36 is pushed up integrally with the operation rod 38 even after the main valve is closed. As a result, the sub valve body 36 is separated from the sub valve seat 34 and the sub valve is opened, and the bleed function is efficiently exhibited. That is, after the main valve is closed to regulate introduction of the discharge refrigerant into the crank chamber 112, the sub valve is opened to quickly relieve the refrigerant in the crank chamber 112 into the suction chamber 114. As a result, the compressor can be started quickly.

At the time of normal control of the solenoid 4, the feedback control described above is executed. That is, the microcomputer 123 acquires the control command information (information indicating the set pressure Pset) received from the air conditioner ECU 105, and acquires the actual suction pressure Ps detected by the pressure sensor 8 ) Of the user. Then, the duty ratio is calculated based on the deviation between the detected suction pressure Ps and the set pressure Pset, and the drive command is outputted to the drive circuit 129. The drive circuit 129 supplies a duty-controlled drive current to the solenoid 4 in accordance with the drive command. The main valve body 30 stops at the valve lift position where the force in the valve opening direction by the spring 44 and the solenoid force in the valve closing direction are balanced. Thereby, control for approaching or holding the suction pressure Ps to the set pressure Pset can be realized with high accuracy. On the other hand, the air conditioner ECU 105 may sequentially receive information indicating the set pressure Pset from the air conditioner ECU 105, and may receive the set pressure Pset previously received, May be used. The microcomputer 123 may transmit the detection information by the pressure sensor 8 to the air conditioner ECU 105. [

When there is an instruction to reduce the load on the compressor 100 from the air conditioner ECU 105 while the load of the engine becomes large while the normal control is being executed, the microcomputer 123 controls the solenoid 4 The energization for the energization is cut off or suppressed to a predetermined lower limit value. The suction force is not applied between the core 46 and the plunger 50 when the energization to the solenoid 4 is interrupted so that the main valve body 30 is closed by the biasing force of the spring 44, 22, so that the main valve is in a deployed state. At this time, since the sub valve body 36 basically sits on the sub valve seat 34, the sub valve is closed. The refrigerant of the discharge pressure Pd introduced from the discharge chamber 116 into the port 16 passes through the main valve in the expanded state and flows from the port 14 to the crank chamber 112. Therefore, the control pressure Pc is increased, and the compressor 100 is operated at the minimum capacity.

As described above, in this embodiment, since the control valve 1 is inserted into the mounting hole 118 of the compressor 100 from the front end side, the control unit 6 is integrally provided at the rear end side. The circuit of the control unit 6 and the circuit of the solenoid 4 are collected on the circuit board 121 and the common connection terminal 72 is provided in the connector section 74 on the rear end side. Therefore, it is not necessary to separately provide a dedicated mounting hole for mounting the control unit 6 in the compressor 100. [ Thereby, the external leakage portion of the refrigerant in the compressor 100 can be reduced. Since the control unit 6 and the connector portion of the solenoid 4 are made common, the control valve 1 can be made more compact, and the number of mounting of the connector when the compressor is mounted on the compressor 100 can be reduced. Since the communication circuit 127 is provided in the control unit 6, the number of terminals drawn out to the outside of the control valve 1 can be suppressed. As a result, the manufacturing cost of the compressor 100 can be reduced.

Further, by performing the feedback control using the output of the pressure sensor 8 by the control unit 6, the accuracy of the Ps control can be improved. The electrical disturbance between the air conditioner ECU 105 and the control valve 1 is controlled by the control of the control unit 6 because the control unit 6 is provided in the control valve 1 independently of the air conditioner ECU 105. [ . That is, according to the present embodiment, a configuration for controlling the compressor 100 with high precision can be realized with a simple and low cost.

[Second Embodiment]

6 is a cross-sectional view showing the configuration of a control valve according to the second embodiment. Hereinafter, differences from the first embodiment will be mainly described. In Fig. 6, the same components as those in the first embodiment are denoted by the same reference numerals.

The control valve 201 of the present embodiment is provided with the power element for adjusting the suction pressure Ps (corresponding to the "target pressure") autonomously (mechanically) in addition to the configuration of the control valve 1 of the first embodiment 210). The control valve 201 is configured as a so-called Ps sensing valve for controlling the flow rate of the refrigerant introduced into the crank chamber 112 from the discharge chamber 116 so as to maintain the suction pressure Ps of the compressor 100 at the set pressure have. The control valve 201 is constituted by integrally assembling a solenoid 4 and a cylindrical body 205 having a stepped portion integrally in the axial direction. An end member 213 is fixed to close the upper opening of the body 205. The control valve 201 has a configuration in which the power element 210, the sub valve, the main valve, the solenoid 4, and the control unit 6 are disposed in order from one end.

The power element 210 is disposed in the operation chamber 23. The power element 210 includes a bellows 245 that senses the suction pressure Ps and is displaced. A spring 246 for biasing the bellows 245 in the extension direction (the opening direction of the main valve) is disposed on the inside of the power element 210. The power element 210 generates a force against the solenoid force due to the displacement of the bellows 245. This counter force is also transmitted to the main valve body 30 through the operation rod 38 and the sub-valve body 36.

The actuating rod 38 passes through the sub-valve body 36 and its tip is operatively connectable to the power element 210. A driving force (also referred to as a "reduced driving force") caused by the expansion and contraction of the power element 210 is loaded on the working rod 38 so as to oppose the solenoid force. That is, in the control state of the main valve, a force adjusted by the solenoid force and the reduced pressure driving force acts on the main valve body 30 to properly control the opening of the main valve. Even when the main valve is being controlled, if the suction pressure Ps becomes considerably high, the operating rod 38 is displaced relative to the body 205 against the biasing force of the bellows 245 to close the main valve The sub valve body 36 is pushed up to open the sub valve. Thereby exerting the bleed function.

In the above configuration, when the starting current is supplied to the solenoid 4, if the suction pressure Ps is higher than the valve opening pressure (also referred to as "sub-valve opening pressure") determined by the supply current value, do. That is, the solenoidal force is against the biasing force of the spring 42, and the sub-valve body 36 is pushed up integrally. As a result, the sub valve body 36 is separated from the sub valve seat 34 and the sub valve is opened. On the other hand, the "sub-valve opening pressure" changes correspondingly as the set pressure Pset is changed according to the environment in which the vehicle is placed.

When the current value supplied to the solenoid 4 is within the control current value range of the main valve, the opening degree of the main valve is autonomously adjusted so that the suction pressure Ps becomes the set pressure Pset. This set pressure Pset is changed according to the supply current value to the solenoid 4. In this control state of the main valve, the sub valve body 36 is seated on the sub valve seat 34, and the sub valve remains closed. On the other hand, since the suction pressure Ps is relatively low, the bellows 245 extends and the main valve body 30 operates to adjust the opening degree of the main valve. At this time, the main valve body 30 is moved in the valve opening direction by the power element 210 in accordance with the force in the valve opening direction by the spring 44, the solenoid force in the valve closing direction, Stops at a balanced valve lift position.

Then, for example, when the refrigerant load becomes large and the suction pressure Ps becomes higher than the set pressure Pset, the bellows 245 contracts and the main valve body 30 relatively displaces upward (valve closing direction) . As a result, the valve opening of the main valve becomes small, and the compressor operates to increase the discharge capacity. As a result, the suction pressure Ps is lowered. On the other hand, when the refrigerating load becomes small and the suction pressure Ps becomes lower than the set pressure Pset, the bellows 245 expands. As a result, the power element 210 biases the main valve body 30 in the valve opening direction to increase the valve opening degree of the main valve, and the compressor operates so as to reduce the discharge capacity. As a result, the suction pressure Ps is maintained at the set pressure Pset.

When such normal control is being executed, the microcomputer 123 executes feedback control to correct autonomous control of the main valve. That is, the microcomputer 123 calculates the duty ratio based on the deviation between the detected suction pressure Ps and the set pressure Pset (so that the deviation approaches zero) Correct the drive command.

According to the present embodiment, the same effect as that of the first embodiment can be obtained for the Ps sensing valve. In addition, by autonomous control by the operation of the power element 210, it is possible to improve the responsiveness of the control of approaching the suction pressure Ps to the set pressure Pset. In the case where the time constant of the pressure sensor 8 is large, the control delay can be suppressed by autonomous operation. On the contrary, when the control response delay due to the pressure sensing occurs in this autonomous control, the response delay can be suppressed by the feedback control. It is also possible to prevent or suppress control hunting due to response delay. That is, by providing the pressure reducing portion and the control portion in the control valve 201, it is possible to realize both the improvement of the responsiveness as the Ps sensing valve and the improvement of the accuracy of the Ps control.

[Third Embodiment]

7 is a cross-sectional view showing the configuration of a control valve according to the third embodiment. Hereinafter, differences from the first embodiment will be mainly described. In Fig. 7, the same components as those in the first embodiment are denoted by the same reference numerals.

The control valve 301 of the present embodiment is not provided with a bleed valve and the arrangement of the valve body and the solenoid is also different from that of the first embodiment. The control valve 1 has a cylindrical body 305 (functioning as a "valve body") having a step, and a solenoid 304 assembled in the axial direction with the body 305.

A port 16 (discharge chamber communication port) is provided at the upper opening of the body 305 and a port 14 (control chamber communication port) and a port 12 (suction chamber communication port) are provided at the side portion from above. The body 305 is formed with a fluid passage 318 for communicating the port 14 and the port 16 and a pressure chamber 28 communicating with the port 12. A valve hole 20 is provided in the middle of the flow path 318 and a valve seat 22 is provided at an upstream end of the valve hole 20. In the port 16, a cylindrical filter member 315 having a bottom portion is mounted.

A guide hole 327 is provided in the body 305 so as to pass through the partition wall between the flow path 318 and the pressure chamber 28. The valve hole 20 and the guide hole 327 are formed coaxially along the axis of the body 305. The pressure chamber (28) opens wide toward the lower side of the body (305). A communication passage 332 is provided outside the guide hole 327. The communication passage 332 extends in parallel with the guide hole 327 to communicate the port 12 and the pressure chamber 28 with each other.

A valve chamber 24 is formed between the port 16 and the valve hole 20 and a ball-shaped valve body 330 is disposed in the valve chamber 24. The valve seat 22 is formed in a concave spherical shape having a slightly larger radius of curvature than that of the valve element 330 so that the valve body 330 can be easily attached and detached. The valve body 330 is opened and closed by removing the valve seat 22 from the upstream side. A spring bearing 340 is fixed to the upper end of the body 305 and a spring 342 is interposed between the valve body 330 and the spring bearing 340. The spring 342 biases the valve body 330 in the valve closing direction. The load of the spring 342 is adjusted by the fixing position of the spring bearing 340 in the body 305. [

A shaft 338 is provided so as to pass through the valve hole 20 and the guide hole 327 in the axial direction. The shaft 338 is slidably supported by the guide hole 327. The upper end of the shaft 338 is reduced in diameter and passes through the valve hole 20 to support the valve body 330 on the downstream side. The lower end of the shaft 338 is connected to the plunger 350 of the solenoid 304 across the pressure chamber 28.

On the other hand, the solenoid 304 includes a cylindrical case 356, a bobbin 52 housed in the case 356, an electromagnetic coil 54 wound around the bobbin 52, and a bobbin 52 An end member 358 provided to cover the lower end opening of the case 356 and a collar 362 embedded in the end member 358 below the bobbin 52 do. The case 356 and the end member 358 constitute a "solenoid body ". It goes without saying that members (sleeves 48 and the like) fixed to the case 356 and the end member 358 may be included as components of the "solenoid body ". In any case, the sensor body 131 is fixed with respect to the solenoid body.

A plunger 350 and a core 346 are disposed in an operating space 360 formed in the inside of the electromagnetic coil 54. The sleeve 348 is made of a non-magnetic material and holds the electromagnetic coil 54 between the case 348 and the case 356. The sleeve 348 is provided with a flange portion 357 extending radially outward from its top opening and the flange portion 357 is held between the body 305 and the case 356. The core 346 has a cylindrical shape with a step and is fixed by inserting the upper half of the core 346 into the lower end of the sleeve 348. The core 346 has an axial through hole 366. The through hole 366 is formed by a hole having a stepped portion whose upper half is slightly enlarged in diameter, and a spring 44 is accommodated in the large diameter portion.

The plunger 350 has a columnar shape with a step, and is slidably supported by the sleeve 348. The lower end of the shaft 338 is press-fitted in the upper half of the plunger 350 in a coaxial manner. The plunger 350 is disposed on the opposite side of the control unit 6 with respect to the core 346 and axially opposes the core 346. Between the core 346 and the plunger 350, a disk-shaped spacer 370 made of a non-magnetic material is disposed. The spring 44 is a coil spring having a larger load than the spring 342 and interposed between the stepped portion provided in the through hole 366 and the spacer 370. The spring 44 axially supports the plunger 350 through the spacer 370 and biases the plunger 350 in a direction away from the core 346. A sealing O-ring 372 is attached to the lower end surface of the body 305. [

The inside of the core 346 is open to the pressure sensor 8. A communication groove 66 parallel to the axial line is provided on the side surface of the plunger 350 and communicated with the through hole 366 of the core 346. With this configuration, the suction pressure Ps of the pressure chamber 28 is also delivered to the pressure sensor 8. [ The pressure sensor 8 is supported so as to be axially fitted between the core 346 and the cover member 78 and fixed to the end member 358 (solenoid body). The space surrounded by the sensor module 133 and the core 346 becomes the first pressure chamber 143 and the suction pressure Ps is applied to the upper surface of the pressure-

In the above configuration, when the solenoid 304 is non-energized, no attraction force acts between the core 346 and the plunger 350. On the other hand, since the load of the spring 44 is set to be considerably larger than the load of the spring 342, the plunger 350 is displaced upward to be integrated with the shaft 338 and operated to open the valve body 330 . As a result, the valve portion is in an expanded state, the control pressure Pc rises, and the compressor performs the minimum capacity operation.

On the other hand, when a starting current is supplied to the solenoid 304, the core 346 sucks the plunger 350 against the biasing force of the spring 44. As a result, the valve body 330 is pushed down by the spring 342 and seated on the valve seat 22, so that the control valve 301 is closed.

When the holding current is supplied to the solenoid 304, the force due to the differential pressure between the discharge pressure Pd and the control pressure Pc (i.e., the force due to the differential pressure acting on the valve element 330) The force of the differential pressure between the pressure Pc and the suction pressure Ps (i.e., the force due to the differential pressure acting on the shaft 338), the combined force of the springs 342 and 44 and the suction force of the solenoid 304 are balanced do. Thereby, the valve body 330 is pushed up and set to a predetermined opening spaced from the valve seat 22. As a result, the refrigerant of the discharge pressure Pd is controlled at a flow rate corresponding to the opening degree and introduced into the crank chamber 112, and the compressor 100 shifts to the operation of the capacity corresponding to the control current. The microcomputer 123 executes the aforementioned feedback control based on the deviation between the suction pressure Ps detected by the pressure sensor 8 and the set pressure Pset received from the air conditioner ECU 105. [

According to the present embodiment, the same operational effect as that of the first embodiment can be obtained even in the structure not including the sub-valve (bleed valve).

[Fourth Embodiment]

8 is a cross-sectional view showing a configuration of a control valve according to the fourth embodiment. Hereinafter, differences from the first embodiment will be mainly described. In Fig. 8, the same reference numerals are given to constituent parts which are substantially the same as those in the first embodiment.

The control valve 401 of the present embodiment is configured such that the pressure difference Pd-Ps between the discharge pressure Pd of the compressor 100 and the suction pressure Ps is close to the set differential pressure DELTA Pset, Quot; Pd-Ps < / RTI > differential pressure valve for controlling the flow rate of the refrigerant introduced into the crank chamber 112 from the "

The control valve 1 is constituted by integrally assembling the body 405 and the solenoid 404. The port 14 (control chamber communication port) and the port 12 (suction chamber communication port) are provided on the side of the body 405, and the port 16 (discharge chamber communication port) is provided at the upper end of the body 405 have.

A cylindrical valve-seat forming member 416 having a step is disposed in the passage for communicating the port 16 and the port 14 in the body 405. The valve seat forming member 416 has a hardness higher than that of the body 405. The valve seat forming member 416 is inserted into the upper portion of the body 405 in a coaxial manner and fixed. The valve seat forming member 416 is provided with a through hole 495 along the axial line, and the valve hole 20 is formed by the lower half thereof. A valve chamber 24 communicating with the port 14 is formed below the valve seat forming member 416 in the body 405. [ The lower half of the valve seat forming member 416 is tapered so that its outer diameter decreases downward and extends into the valve chamber 24. And a valve seat 22 is formed on the lower end surface of the valve seat forming member 416. The valve chamber (24) is provided with a valve body (430) facing the valve seat (22) from below. The opening degree of the valve portion is adjusted by the valve element 430 being brought into contact with the valve seat 22.

A bleed hole 496 parallel to the through hole 495 is provided on the radially outer side of the through hole 495 in the valve seat forming member 416. The bleed hole 496 is for ensuring oil circulation in the compressor by introducing the minimum amount of refrigerant into the control chamber even when the valve is closed.

A partition wall 426 is provided to divide the inner space of the body 405 vertically. A valve chamber (24) is formed above the partition (426), and a pressure chamber (28) is formed below the partition wall (426). The valve chamber (24) communicates with the control chamber through the port (14). The pressure chamber (28) communicates with the suction chamber (114) through the port (12). A guide portion 432 extending in the axial direction is provided at the center of the partition wall 426. A guide hole 427 is formed to penetrate the guide portion 432 along the axial line and an elongated working rod 434 is inserted into the guide hole 427 so as to be slidable in the axial direction. The valve body 430 is provided coaxially on the upper end of the operation rod 434. [ The valve body 430 and the operation rod 434 are integrally formed by cutting stainless steel.

The guide portion 432 protrudes slightly toward the upper surface side of the partition wall 426 and greatly protrudes toward the lower surface side. The guide portion has a tapered shape with its outer diameter decreasing downward and extends into the pressure chamber 28. Thereby, the length of the guide hole 427 is sufficiently secured, and the operation rod 434 is stably supported. The valve body 430 operates integrally with the operation rod 434 and is detachably attached to the valve seat 22 by its upper end surface to open and close the valve portion. Since the hardness of the valve seat forming member 416 is sufficiently high, even if the valve body 430 is repeatedly seated, the valve seat 22 is not easily deformed and the durability of the valve portion is secured.

A disk spring bearing 437 is provided on the lower portion of the operation rod 434 to engage with a snap ring 436 (E ring) and restrict the downward movement of the snap ring 436 by the snap ring 436. A spring 444 for biasing the operating rod 434 downward (valve opening direction) is interposed between the spring bearing 437 and the body 405 (partition wall 426). The spring 444 is a tapered spring whose diameter is reduced toward the lower spring bearing 437 from the lower surface of the partition wall 426. As described above, the tapered shape of the guide portion 432 allows the tapered spring 444 to be disposed. The lower portion of the body 405 constitutes a connection portion with the solenoid 404.

At the upper opening of the body 405, there is provided a filter member 445 for suppressing entry of foreign matter into the port 16. [

The solenoid 404 includes a cylindrical core 446, a cylindrical sleeve 448 having a stepped portion inserted into the core 446 outwardly, a sleeve 448 accommodated in the sleeve 448, A bobbin 52 inserted outwardly into the sleeve 448, an electromagnetic coil 54 wound around the bobbin 52, and an electromagnetic coil 54 from the outside in the axial direction A cylindrical connecting member 462 having a stepped portion assembled between the core 446 and the case 456 at an upper portion of the bobbin 52 and a cylindrical connecting member 462 having a stepped portion formed between the core 446 and the case 456, And an end member 458 mounted to the bottom opening. The sleeve 448 is made of a non-magnetic material and accommodates the core 446 in the upper half thereof and the plunger 450 in the lower half thereof. The lower portion of the sleeve 448 is reduced in diameter and is open to the pressure sensor 8.

A through hole 467 is formed so as to penetrate the center of the core 446 in the axial direction and a shaft 438 is inserted to penetrate the through hole 467. The shaft 438 is provided coaxially with the operating rod 434 and supports the operating rod 434 from below. The diameter of the shaft 438 is larger than the diameter of the operation rod 434. [ And a plunger 450 is assembled to the lower half of the shaft 438. In this embodiment, the shaft 438 and the actuating rod 434 constitute a "transmission rod" which transmits the solenoid force to the valve body 430. [

The plunger 450 is supported coaxially on the shaft 438 at its upper portion. A snap ring 470 (E-ring) is fitted to the transmission position in the axial middle portion of the shaft 438, and the upward movement of the plunger 450 is restricted by the snap ring 470. A communicating groove 626 is formed between the plunger 450 and the sleeve 448 so as to allow the refrigerant to pass therethrough.

A ring-shaped shaft support member 472 is press-fitted into the upper end of the core 446 and an upper end of the shaft 438 is supported by the shaft support member 472 so as to be slidable in the axial direction. A part of the outer periphery of the shaft supporting member 472 is notched so that a communication path is formed between the core 446 and the shaft supporting member 472. [ The suction pressure Ps is also delivered to the inside of the solenoid 404 through this communication path.

Further, the lower end of the sleeve 448 is slightly reduced in diameter, and the ring-shaped shaft supporting member 476 is press-fitted. The shaft support member 476 slidably supports the lower end of the shaft 438. That is, the shaft 438 is supported at two points by the upper shaft supporting member 472 and the lower shaft supporting member 476, so that the plunger 450 can be stably operated in the axial direction. A communicating path is formed between the sleeve 448 and the shaft supporting member 476 by providing a communication groove 478 in the outer peripheral portion of the shaft supporting member 476. [ The suction pressure Ps introduced into the solenoid 404 is a communication path between the core 446 and the shaft 438 and a communication path between the plunger 450 and the sleeve 448. The suction pressure Ps is introduced into the solenoid 404 through the shaft support member 476, (448) to the back pressure chamber (70). The back pressure chamber (70) communicates with the first pressure chamber (143).

A spring 442 for biasing the plunger 450 upwardly, that is, in the valve closing direction, is interposed between the shaft support member 476 and the plunger 450. That is, the valve body 430 receives, as a spring load, the resultant force of the force in the valve opening direction by the spring 444 and the force in the valve closing direction by the spring 442. However, since the load of the spring 444 is larger than the load of the spring 442, the spring load by the springs 444 and 442 acts in the valve opening direction.

With the above-described configuration, the suction pressure Ps of the pressure chamber 28 is also delivered to the pressure sensor 8. The pressure sensor 8 is supported so as to be axially fitted between the sleeve 448 and the cover member 78 and fixed to the end member 458 (solenoid body). The space surrounded by the sensor module 133 and the sleeve 448 becomes the first pressure chamber 143 and the suction pressure Ps is applied to the upper surface of the pressure-

The control pressure Pc acting on the valve body 430 in the valve chamber 24 is substantially equal to the control pressure Pc acting on the valve body 430 because the diameter of the operation rod 434 is slightly smaller than the inner diameter of the valve hole 20, ) Is almost canceled (canceled). The differential pressure Pd-Ps between the discharge pressure Pd and the suction pressure Ps substantially acts on the valve body 430 substantially in the hydraulic pressure area of the valve hole 20. The valve body 430 is operated so that the differential pressure Pd-Ps is maintained at the set differential pressure DELTA Pset set by the control current supplied to the solenoid 404.

When the solenoid 404 is not energized, the valve body 430 is separated from the valve seat 22 by the load in the valve opening direction by the resultant force of the springs 444 and 442, and the valve is kept in the deployed state. As a result, the compressor 100 is operated at the minimum capacity.

On the other hand, when a starting current is supplied to the solenoid 404, the plunger 450 is sucked to the core 446 with the maximum suction force. At this time, the valve body 430, the operation rod 434, the shaft 438 and the plunger 450 integrally operate in the valve closing direction, and the valve body 430 is seated on the valve seat 22 . Thereby, the compressor 100 is operated at the maximum capacity.

The valve body 430, the actuating rod 434, the shaft 438 and the plunger 450 operate integrally when the solenoid 404 is supplied with the holding current. At this time, the valve body 430 has a spring load of the spring 444 biasing the operation rod 434 in the valve opening direction and a spring force of the spring 442 biasing the plunger 450 in the valve closing direction. The load and the force of the solenoid 404 biasing the plunger 450 in the valve closing direction and the discharge pressure Pd that the valve body 430 presses in the valve opening direction, ) Is stopped at a balanced valve lift position by the suction pressure Ps which is pushed in the valve closing direction.

When the discharge capacity increases, the differential pressure Pd-Ps becomes large and a force in the valve opening direction acts on the valve body 430. As a result, (430) further increases the flow rate of the refrigerant flowing from the discharge chamber (116) to the crank chamber (112). Thereby, the control pressure Pc rises, and the compressor 100 operates in a direction to decrease the discharge capacity, and the differential pressure Pd-Ps is controlled to become the set differential pressure DELTA Pset. When the number of revolutions of the engine is lowered, the opposite operation is performed so that the differential pressure Pd-Ps is controlled to become the set differential pressure DELTA Pset.

When such normal control is being executed, the control valve 401 is controlled such that the differential pressure Pd-Ps is maintained at the set differential pressure DELTA Pset in the normal state where the suction pressure Ps is equal to or higher than the set pressure Pset , And controls the suction pressure Ps to be close to the set pressure Pset when the suction pressure Ps becomes lower than the set pressure Pset. That is, the control valve 401 basically functions as a Pd-Ps differential pressure valve for controlling the differential pressure Pd-Ps, while functioning as a Ps control valve when the suction pressure Ps is too low, do.

The microcomputer 123 executes a feedback control for approaching the suction pressure Ps to the set pressure Pset when the detected suction pressure Ps is lower than the set pressure Pset. That is, the duty ratio is calculated based on the deviation between the suction pressure Ps and the set pressure Pset, and a drive command to the drive circuit 129 is output.

According to the present embodiment, the same operational effect as that of the first embodiment can be obtained also in a control valve that controls the differential pressure between predetermined two points of the compressor 100 to be constant. Further, the differential pressure Pd-Ps can be estimated from the control set value, while the suction pressure Ps can be obtained based on the detection value of the pressure sensor 8. [ From these values, the value of the discharge pressure Pd can be estimated. Therefore, it is not necessary to separately provide a sensor for detecting the discharge pressure Pd. On the other hand, in the present embodiment, the control of the differential pressure Pd-Ps is set as the main control, and the control of the suction pressure Ps is designated as the auxiliary control. In the modified example, the latter pressure control may be the main control. That is, the microcomputer 123 may perform the feedback control so that the suction pressure Ps approaches the set pressure Pset at the time of normal control. In this case, the control valve 401 autonomously operates so as to bring the differential pressure Pd-Ps close to the optimum set differential pressure Pset with respect to the suction pressure Ps, while maintaining the suction pressure Ps constant. do.

[Fifth Embodiment]

9 is a cross-sectional view showing a configuration of a control valve according to a fifth embodiment. Hereinafter, differences from the first embodiment will be mainly described. 9, components substantially the same as those in the first embodiment are denoted by the same reference numerals.

The control valve 501 of this embodiment is a flow control valve that controls the discharge flow rate of the compressor 100 to be a set flow rate. The control valve 501 is constituted by integrally assembling the body 505 and the solenoid 504 in the axial direction. An end member 513 is fixed to the upper opening of the body 505 and a power element 510 is provided integrally with the end member 513. [

The body 505 has a cylindrical shape with a step and has a port 517 (communication port on the downstream side of the discharge chamber), a port 16 (discharge chamber communication port), a port 14 Port) and a port 12 (suction chamber communication port) are provided. A communication hole 520 is provided so as to pass through the end member 513 in the axial direction, and a port 516 (a discharge chamber communication port) is provided at the top opening. That is, the port 516 introduces the first discharge pressure Pd1 of the discharge chamber 116 into the interior of the power element 510.

The port 517 communicates with the pressure chamber 523 partitioned by the upper portion of the body 505 and the downstream side of the fixed orifice 117 (the upstream side of the discharge valve 160) The second discharge pressure Pd2 is introduced. The power element 510 is disposed in the pressure chamber 523. A guide hole 525 (first guide hole) is provided between the port 16 and the pressure chamber 523. A guide hole 527 (second guide hole) is provided between the port 12 and the port 14. In these guide holes, an operation rod 538 is inserted. A valve chamber (24) and a valve hole (20) are provided between the port (14) and the port (16). The operation rod 538 is slidably supported by the guide holes 525 and 527 and the upper end side thereof is connected to the power element 510 and the lower end side thereof is connected to the plunger 550 of the solenoid 504 . A valve body 530 is integrally provided at an intermediate portion of the operating rod 538.

The power element 510 includes a bellows 545 that senses the differential pressure Pd1-Pd2 between the first discharge pressure Pd1 and the second discharge pressure Pd2 to be displaced. On the inside of the power element 510, there is disposed a spring 542 for biasing the bellows 545 in the extension direction (valve opening direction). The power element 510 generates a force against the solenoid force due to the displacement of the bellows 545. This counter force is also transmitted to the valve body 530 through the operation rod 538. [ On the other hand, in consideration of the stability of the differential pressure Pd1-Pd2 to be sensed, it is preferable that the second discharge pressure Pd2 is introduced from a position away from the discharge valve 160 (check valve).

The solenoid 504 includes a core 546, a sleeve 548, a plunger 550, a bobbin 52, an electromagnetic coil 54, a case 556, and an end member 558. The lower end of the operating rod 538 is inserted into and supported by the plunger 550.

The outer diameter of the valve body 530 (the inner diameter of the guide hole 527) is slightly larger than the inner diameter of the valve hole 20 but has almost the same size. Therefore, The influence of the pressure Pc is substantially canceled.

When the solenoid 504 is not energized, the valve body 530 is separated from the valve seat 22 by the biasing force of the spring 44, and the valve portion is maintained in the deployed state. As a result, the compressor 100 is operated at the minimum capacity.

On the other hand, when a starting current is supplied to the solenoid 504, the plunger 550 is attracted to the core 546 with the maximum suction force. At this time, the valve body 530, the operation rod 538 and the plunger 550 are integrally operated in the valve closing direction, and the valve body 530 is seated on the valve seat 22. Thereby, the compressor 100 is operated at the maximum capacity.

The valve body 530, the actuating rod 538 and the plunger 550 operate as a single body when the solenoid 504 is supplied with the holding current. At this time, the valve body 530 is in contact with the spring load of the spring 44 biasing the operation rod 538 in the valve opening direction and the spring load of the solenoid 504 biasing the plunger 550 in the valve closing direction The load and the force due to the discharge pressure Pd in which the valve body 530 is pushed in the valve opening direction and the suction pressure Ps in which the valve body 430 is pressed in the valve closing direction, Stop at position.

When the rotation speed of the compressor increases with the number of revolutions of the engine and the discharge flow rate increases in this balanced state, the differential pressure Pd1-Pd2 increases and the bellows 545 expands. As a result, the valve body 530 further lifts and increases the flow rate of the refrigerant flowing from the discharge chamber 116 to the crank chamber 112. Thereby, the control pressure Pc rises, the discharge flow rate of the compressor 100 decreases, and the differential pressure Pd1-Pd2 is controlled to become the set differential pressure APdset. On the other hand, when the number of revolutions of the engine is decreased, the reverse operation is performed, and the differential pressure Pd1-Pd2 is controlled to be the set differential pressure DELTA Pdset. When the differential pressure Pd1-Pd2 is maintained constant, the discharge flow rate becomes constant. As a result, the discharge flow rate is maintained at the set flow rate.

When such normal control is being executed, the control valve 501 is controlled such that the differential pressure Pd1-Pd2 is maintained at the set differential pressure DELTA Pdset in the normal state where the suction pressure Ps is equal to or higher than the set pressure Pset , And controls the suction pressure Ps to be close to the set pressure Pset when the suction pressure Ps becomes lower than the set pressure Pset. That is, the control valve 501 basically functions as a flow rate control valve for keeping the discharge flow rate at the set flow rate, and functions as a Ps control valve when the suction pressure Ps is too low to prevent excessive cooling.

The microcomputer 123 executes a feedback control for approaching the suction pressure Ps to the set pressure Pset when the detected suction pressure Ps is lower than the set pressure Pset. That is, the duty ratio is calculated based on the deviation between the suction pressure Ps and the set pressure Pset, and a drive command to the drive circuit 129 is output.

According to the present embodiment, the same operational effect as that of the first embodiment can be obtained also in a control valve that controls the discharge flow rate of the compressor 100 to be constant. On the other hand, in the present embodiment, the flow rate control is set as the main control and the suction pressure Ps is set as the auxiliary control. In the modified example, the latter flow rate control may be the main control. That is, the microcomputer 123 may perform the feedback control so that the suction pressure Ps approaches the set pressure Pset at the time of normal control. In this case, the control valve 501 is controlled so as to autonomously adjust the differential pressure Pd1-Pd2 to be close to the optimum set differential pressure APdset with respect to the suction pressure Ps while maintaining the suction pressure Ps constant .

On the other hand, if the value of the suction pressure Ps can be detected by the pressure sensor 8, the torque of the compressor 100 can be calculated based on the suction pressure Ps and the set flow rate. Therefore, such calculation of the torque may be performed by the microcomputer 123 or the air conditioner ECU 105. [ In the former case, the microcomputer 123 can transmit the torque information to the air conditioner ECU 105. [ In the latter case, information on the flow rate information and the suction pressure Ps can be transmitted from the microcomputer 123 to the air conditioner ECU 105, and the torque can be calculated by the air conditioner ECU 105. [ According to the present embodiment, it is possible to perform torque control by controlling the flow rate of the refrigerant, control of the discharge air temperature by the suction pressure control, torque estimation based on the output of the pressure sensor 8, and the like. Therefore, both of the power saving by the torque control and the comfort by the air temperature control become compatible.

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

In the above embodiment, as shown in Fig. 2, the circuit board 121 has a configuration in which a communication circuit 127 (transceiver) is provided as a communication unit. In the modified example, the microcomputer 123 and the air conditioner ECU 105 may communicate with each other without providing the communication circuit 127.

10 is a schematic diagram showing an electrical configuration of the control valve 701 and the periphery thereof according to a modified example. In this modified example, serial communication is performed between the microcomputer 123 and the air conditioner ECU 105. Between the microcomputer 123 and the air conditioner ECU 105, an MOSI line 172c, an MISO line 172d and an SCK line 172e are provided. The MOSI line 172c is a communication line for connecting the input port of the microcomputer 123 and the output port of the air conditioner ECU 105. [ The MISO line 172d is a communication line for connecting the output port of the microcomputer 123 and the input port of the air conditioner ECU 105. [ The SCK line 172e is a communication line for transferring the synchronization clock from the air conditioner ECU 105 to the microcomputer 123. [

The power terminal 72a, the ground terminal 72b and the three communication terminals 172c, 172d and 172e (collectively referred to as "connection terminal 172 ") from the circuit board 721, Quot;) is prolonged and protruded, and is arranged in the inside of the connector portion 74.

In the above embodiment, an example of the structure of the pressure sensor 8 is shown, but it goes without saying that a different structure may be employed. In the above embodiment, a pressure sensor using a strain gauge is exemplified, but a pressure sensor using a magnetic sensor may be employed. For example, a magnetic sensor may be employed in which a magnet is provided integrally with the pressure-reduction element, and a detection signal corresponding to the displacement of the magnet in accordance with the displacement of the pressure-reduction element is output. The microcomputer 123 may calculate the suction pressure Ps or the like based on the detection value of the magnetic sensor.

In the embodiment described above, as shown in Fig. 4, a configuration in which the pressure sensor 8 is integrally provided in the control unit 6 is exemplified. In the modified example, they may be separately formed and assembled in the housing chamber 76 of the solenoid body.

2, the driving circuit 129 and the power supply circuit 125 are arranged outside the microcomputer 123, but any one or both of them may be connected to the microcomputer 123 As shown in Fig. This also applies to the modification of Fig.

In the above embodiment, a configuration is described in which a control unit is provided on the solenoid body. In a modified example, a pressure sensor may be provided in the solenoid body, and other circuits or the like may be disposed outside the control valve. Other circuits may be provided in the air conditioner ECU. The solenoid body may include a common connector unit including a connection terminal connected to the power line and the ground line of the solenoid, and a connection terminal connected to the power line, the ground line and the output line of the pressure sensor. The detection signal of the pressure sensor may be output to the air conditioner ECU via the output line. The control valve may perform only the input / output of the power source and the output of the pressure sensor. Then, the air conditioner ECU may calculate the pressure based on the output of the pressure sensor, and supply the necessary control current to the control valve.

In the above embodiment, an example of sensing the suction pressure Ps in the pressure sensor is presented. In a modified example, the pressure sensor may be configured to detect the control pressure Pc. In this case, the control pressure Pc may be a gauge pressure or an absolute pressure. At least one of the valve body and the solenoid body forms a passage for introducing the control pressure (Pc) to the pressure sensor. Alternatively, the differential pressure Pd-Ps between the discharge pressure Pd and the suction pressure Ps may be sensed by the pressure sensor. Alternatively, the differential pressure Pd1-Pd2 between the first discharge pressure Pd1 and the second discharge pressure Pd2 may be sensed by the pressure sensor. In this case, at least one of the valve body and the solenoid body forms a passage for introducing the discharge pressure Pd (the first discharge pressure Pd1, the second discharge pressure Pd2) to the pressure sensor. On the other hand, in the above embodiment, as shown in Fig. 3, an example of providing the fixed orifice 117 on the upstream side of the discharge valve 160 is shown. In the modified example, the fixed orifice 117 may be provided on the downstream side of the discharge valve 160. The flow rate may be controlled by detecting the pressure difference between the upstream side pressure and the downstream side pressure of the fixed orifice 117.

In the above embodiment, the control valve is controlled by adjusting the valve opening degree by PWM control. In a modified example, the valve may be opened or closed during normal control, and the control valve may be controlled by changing the opening / closing timing (opening / closing time). For example, the valve may be opened and closed at about 10 Hz, and the valve opening time may be adjusted.

In the above embodiment, as shown in Fig. 5, there has been shown an example of constituting a pressure-sensitive element (pressure-sensitive portion) by filling a protective material (transfer material) between the sensor element and the diaphragm with respect to the pressure sensor. In the modification, the diaphragm may be omitted, and the pressure-sensitive element may be constituted by the sensor element and the protection material. Alternatively, the pressure-sensitive element may be constituted by only the sensor element without the diaphragm and the protective material. In such a configuration, the working space inside the electromagnetic coil may be opened to the pressure-sensitive element. That is, a portion of the pressure sensor which is deformed under the differential pressure and whose deformation is electrically detected and converted into a pressure value may be referred to as a "reduced pressure portion ".

In the above embodiment, a so-called "introduction control" control valve in which the discharge capacity of the compressor is changed by adjusting the flow rate of the refrigerant introduced into the control chamber from the discharge chamber is illustrated. In the modified example, the so-called "derivation control" control valve in which the discharge capacity of the compressor is changed by adjusting the flow rate of the refrigerant led out from the control chamber to the suction chamber may be used. The pressure sensor 8 may be integrally provided in the control valve of the derivation control so that the feedback control for approaching the suction pressure Ps to the set pressure Pset may be performed.

In the above embodiment, the configuration in which the working space inside the electromagnetic coil is opened to the pressure-reducing member of the pressure sensor is exemplified. In the modified example, the operating space and the pressure-reducing member may be isolated from each other. The pressure to be sensed (sensing pressure) may be introduced from a port separately provided in the solenoid body, and may be introduced into the pressure reduction body.

In the above embodiment, a configuration is described in which a control section is provided on the side opposite to the valve body with respect to the electromagnetic coil. In a modification, the control unit may be provided between the valve body and the solenoid body or inside the valve body. With such a configuration, it is possible to cope with the problem of realizing the improvement of the control precision only by the control valve.

Although not mentioned in the above embodiment, a logic IC having a function of a drive circuit may be mounted on the circuit board of the control valve. The logic IC may be operated based on the command signal from the air conditioner ECU to control the solenoid.

In the above embodiment, an example is shown in which information indicating the set pressure Pset is transmitted from the air conditioner ECU to the microcomputer 123 as a control command. The information indicating the set pressure Pset may be a value indicating the set pressure Pset itself or temperature information associated with the set pressure Pset.

On the other hand, the present invention is not limited to the above-described embodiments and modifications, and can be embodied by modifying the constituent elements within the scope not departing from the gist of the invention. Various inventions may be formed by appropriately combining a plurality of constituent elements disclosed in the above embodiments or modifications. In addition, a few components may be deleted from all the components disclosed in the above embodiments and modifications.

1: Control valve
4: Solenoid
5: Body
6: Control unit
8: Pressure sensor
20: Valve hole
30: Main valve body
46: Core
50: plunger
54: electromagnetic coil
59: Output line
72: connection terminal
74:
100: Compressor
118: Mounting hole
121: circuit board
133: Sensor module
143: first pressure chamber
145: Second pressure chamber
151: Sensor element
161:
201: Control valve
205: Body
210: Power element
301: Control valve
304: Solenoid
305: Body
330: valve body
346: core
350: plunger
360: working space
366: Through hole
401: Control valve
404: Solenoid
405: Body
430: valve body
446: core
450: plunger
501: Control valve
504: Solenoid
505: Body
510: Power element
530:
546: core
550: plunger

Claims (7)

The control valve being assembled to be inserted into a mounting hole provided in the variable displacement compressor and controlling the discharge capacity of the refrigerant discharged from the compressor,
A valve body having a refrigerant flow path and a valve hole provided in the flow path;
A valve body that opens and closes the valve portion by being in contact with the valve hole;
A solenoid mounted on the valve body for applying an axial driving force corresponding to a supply current to the valve body; And
And a pressure sensor for detecting a predetermined refrigerant pressure referred to in energization control of the solenoid,
The solenoid includes:
A solenoid body integrally assembled with the valve body in the axial direction;
An electromagnetic coil held by the solenoid body and having a working space formed therein;
A core fixed to the solenoid body in a coaxial shape with the electromagnetic coil;
A plunger supported so as to be axially displaceable in the working space; And
And a power supply line connected to the electromagnetic coil and drawn out from a side opposite to the valve body of the solenoid body,
Wherein the pressure sensor includes a pressure-reducing section for sensing and displacing the refrigerant pressure and an output line for outputting a detection signal according to the displacement of the pressure-reducing section, wherein the pressure sensor is disposed on the side opposite to the valve body with respect to the electromagnetic coil Control valve for variable capacity compressors. The method according to claim 1,
Wherein the pressure sensor is housed in a space on the opposite side of the valve body in the solenoid body. 3. The method according to claim 1 or 2,
Wherein the pressure sensor includes a sensor body formed to surround the pressure-sensitive portion,
The sensor body is fixed with respect to the solenoid body,
The refrigerant pressure is introduced into the working space,
And the operating space is opened with respect to the depressurizing portion. 4. The method according to any one of claims 1 to 3,
Further comprising a control section for inputting a detection signal of the pressure sensor through the output line and executing energization control for the solenoid in response to a command from an external control device,
Wherein,
A valve body disposed on the side opposite to the valve body with respect to the electromagnetic coil,
And a feedback control for bringing the control amount determined for the refrigerant pressure to a target value based on command information from the external control device and detection information by the pressure sensor . 5. The method of claim 4,
Wherein the solenoid body integrally includes a common connector portion including a connection terminal connected to a communication line with the external control device and a connection terminal connected to the power line. 6. The method of claim 5,
A communication circuit for communicating with the external control device; and a circuit board on which the pressure sensor is mounted,
Wherein the circuit board is disposed on the side opposite to the valve body with respect to the electromagnetic coil. 4. The method according to any one of claims 1 to 3,
Wherein the solenoid body integrally includes a common connector unit including a connection terminal connected to the power supply line and a connection terminal connected to the output line.

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