JP2017194113A - Control valve for variable displacement compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize accuracy improvement of control of a variable displacement compressor with a simple structure.SOLUTION: A control valve 1 comprises a solenoid 4 attached to a body 5, and a pressure sensor 8 that detects a predetermined refrigerant pressure to be referenced for energization control of the solenoid 4. The solenoid 4 comprises a solenoid body attached integrally with the body 5 in an axial direction, an electromagnetic coil 54 retained by the solenoid body and inside which a working space is formed, a core 46 fixed to the solenoid body coaxially with the electromagnetic coil 54, a plunger 50 supported so as to be displaceable in the axial direction in the working space, and a power supply line connected to the electromagnetic coil 54 and drawn from the solenoid body on the side opposite to the body 5. The pressure sensor 8 includes a pressure sensing part that senses the refrigerant pressure and is displaced, and an output line that outputs a detection signal depending on a displacement of the pressure sensing part, and is arranged on the side opposite to the body 5 with respect to the electromagnetic coil 54.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a control valve that controls the discharge capacity of a variable capacity compressor.

  An automotive air conditioner is generally configured by arranging a compressor, a condenser, an expansion device, an evaporator, and the like in a refrigeration cycle. As the compressor, a variable capacity compressor (also simply referred to as “compressor”) capable of varying the refrigerant discharge capacity is used so that a constant cooling capacity is maintained regardless of the engine speed. In this compressor, a piston for compression is connected to a rocking plate attached to a rotating shaft driven by an engine, and the discharge amount of the refrigerant is adjusted by changing the stroke of the piston by changing the angle of the rocking plate. To do. The angle of the swinging plate can be continuously changed by introducing a part of the discharged refrigerant into the sealed control chamber and changing the balance of pressure applied to both surfaces of the piston. The pressure Pc 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 such as a control valve that controls a differential pressure between two predetermined points in a compressor to a set differential pressure, and a control valve that controls a predetermined pressure to be a set pressure. Many of them have a solenoid as a drive unit. Each type of control valve includes a mechanism that transmits the driving force of the solenoid to the valve body, a spring that generates a counter force against the driving force, and the like. The set differential pressure and set pressure are mechanically set by the load of the spring, but can be electrically changed by changing the supply current value to the solenoid.

  Such a control valve operates based on a control command of the external control device. The control device determines the set differential pressure and the set pressure based on predetermined external information detected by various sensors such as the engine speed of the vehicle, the temperature inside and outside the vehicle, and the temperature of air blown from the evaporator. . And energization control to a control valve is performed so that the driving force for maintaining them may be obtained (for example, refer to patent documents 1). At this time, the valve mechanism operates autonomously so that the set differential pressure and the set pressure corresponding to the supply current value are maintained even if the refrigerant pressure fluctuates.

JP 2001-107854 A

  In order to increase the accuracy of such control, for example, there is one that performs feedback control using a set differential pressure or a set pressure as a target value. The compressor is provided with a pressure sensor that detects a pressure to be subjected to feedback control. However, when a pressure sensor is additionally provided in this way, an increase in the number of mounting holes for mounting the pressure sensor in the compressor, an accompanying increase in the leakage site of the refrigerant, and an increase in the sealing structure for sealing the leakage site. Etc. As a result, there is a problem that the compressor is increased in size and the manufacturing cost is increased.

  One of the objects of the present invention is to realize an improvement in control accuracy of a variable capacity compressor with a simple structure.

  One aspect of the present invention is a control valve that is assembled so as to be inserted into an attachment hole provided in a variable capacity compressor, and controls the discharge capacity of refrigerant discharged from the compressor. The control valve is assembled and supplied to a valve body having a refrigerant flow passage and a valve hole provided in the flow passage, a valve body that opens and closes the valve hole to open and close the valve portion, and is supplied to the valve body. A solenoid for applying a driving force in the axial direction according to the current to the valve body, and a pressure sensor for detecting a predetermined refrigerant pressure referred to in energization control of the solenoid are provided.

  The solenoid is a solenoid body that is integrally assembled with the valve body in the axial direction, an electromagnetic coil that is held by the solenoid body and has an inner working space, and a core that is coaxially fixed to the solenoid body. And a plunger supported so as to be displaceable in the axial direction in the working space, and a power line connected to the electromagnetic coil and drawn from the opposite side of the solenoid body from the valve body. The pressure sensor includes a pressure sensing part that senses and displaces the refrigerant pressure, and an output line that outputs a detection signal corresponding to the displacement of the pressure sensing part, and is disposed on the opposite side of the valve body from the electromagnetic coil. Has been.

  The control valve of this aspect is inserted into the mounting hole of the compressor from the front end side (that is, the front end side of the valve body), and the pressure sensor is integrated with the rear end side (that is, the rear end side of the solenoid body). Provided. Moreover, the solenoid power supply line and the pressure sensor output line are combined on the solenoid body side. For this reason, it is sufficient if the compressor is provided with a common mounting hole for mounting the control valve and the pressure sensor. That is, it is possible to realize improvement in the control accuracy of the compressor with a simple structure.

  ADVANTAGE OF THE INVENTION According to this invention, the precision improvement of control of a variable capacity compressor is realizable with a simple structure.

1 is a diagram illustrating a system to which a control valve according to a first embodiment is applied. It is a schematic diagram showing the electrical structure of a control valve and its periphery. It is a figure which represents roughly the refrigerating cycle centering on a compressor. It is sectional drawing which shows the structure of the control valve which concerns on 1st Embodiment. It is the A section enlarged view of FIG. It is sectional drawing which shows the structure of the control valve which concerns on 2nd Embodiment. It is sectional drawing which shows the structure of the control valve which concerns on 3rd Embodiment. It is sectional drawing which shows the structure of the control valve which concerns on 4th Embodiment. It is sectional drawing which shows the structure of the control valve which concerns on 5th Embodiment. It is a schematic diagram showing the electrical structure of the control valve which concerns on a modification, and its periphery.

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

[First Embodiment]
FIG. 1 is a diagram illustrating a system to which a control valve according to the first embodiment is applied.
The control valve 1 is applied to an air conditioner system that is a part of a vehicle control system. A plurality of electronic control devices (hereinafter referred to as “ECU”) for controlling each system system are connected to the vehicle control system via an in-vehicle network. As illustrated, an engine ECU 101 that controls the engine, a brake ECU 103 that controls the brake device, an air conditioner ECU 105 that controls the air conditioner, and the like are connected via a communication line L1. The air conditioner ECU 105 is connected to the control unit of each device constituting the air conditioner system via the communication line L2.

  In this embodiment, the communication line L1 of the main network is a CAN bus, and the communication line L2 of the subnetwork is a LIN bus. That is, CAN (Controller Area Network) is adopted as the communication protocol of the main network, and LIN (Local Interconnect Network) is adopted as the communication protocol of the sub-network. 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. In the modification, CAN may be adopted for both the main network and the sub-network. Alternatively, a communication protocol other than CAN or LIN may be adopted for at least one of the main network and the sub-network.

  The refrigeration cycle of the air conditioner system includes a compressor 100 that compresses the circulating refrigerant, a condenser 111 that condenses the compressed refrigerant, an expansion valve 113 that squeezes and expands the condensed refrigerant and sends it in a mist, and the mist An evaporator 115 and the like for evaporating the refrigerant and cooling the air in the passenger compartment by the latent heat of evaporation are provided. The compressor 100 is a variable capacity compressor. The control valve 1 is a solenoid-driven electromagnetic 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 determines the target value (set pressure) of the suction pressure Ps of the compressor 100 based on predetermined external information detected by various sensors such as the engine speed, the temperature inside and outside the vehicle, and the temperature of air blown from the evaporator 115. Pset) is determined. Then, information indicating the set pressure Pset is output to the control valve 1 as a command signal. Upon receiving the command signal, the control valve 1 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 described later. The air conditioner ECU 105 also outputs a command signal indicating that to the control valve 1 when there is a request for reducing the load torque of the compressor 100 from the engine ECU 101 in a high engine load state such as when the vehicle is accelerating or running uphill. . When receiving the command signal, the control valve 1 cuts off the energization of the solenoid or suppresses it to a predetermined lower limit value, and shifts the compressor 100 to the minimum capacity operation.

FIG. 2 is a schematic diagram showing the electrical configuration of the control valve 1 and its surroundings.
The control device of the control valve 1 is configured by mounting various circuits functioning as a control unit and a communication unit on the circuit board 121. This control apparatus is configured 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 via 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 via 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 via the drive circuit 129. Electric power from the power supply circuit 125 is supplied to the drive circuit 129 and then to the solenoid 4 via the microcomputer 123. A detection signal from the pressure sensor 8 is input to the microcomputer 123 via the output line 59.

  The microcomputer 123 includes a CPU that executes various arithmetic processes, a ROM that stores control programs, a RAM that is used as a work area for data storage and program execution, and a non-volatile memory that retains stored contents even after power is turned off ( EEPROM, etc.), 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 sends it to the microcomputer 123. Further, an output signal from the microcomputer 123 is transmitted to the air conditioner ECU 105. The drive circuit 129 outputs a drive signal whose duty is controlled with respect to the electromagnetic coil of the solenoid 4 based on a command from the microcomputer 123.

  The microcomputer 123 calculates a control amount (duty ratio of the current supplied to the solenoid 4) for bringing the suction pressure Ps close to the set pressure Pset based on a control command received via the communication circuit 127, and realizes this. Drive command (drive pulse) for output to the drive circuit 129. The drive circuit 129 supplies a duty-controlled drive current (current pulse) to the solenoid 4 based on the drive command.

  In the present embodiment, feedback control is executed to bring the suction pressure Ps closer to the set pressure Pset. That is, the air conditioner ECU 105 sends information representing the optimum set pressure Pset according to the vehicle control state as a control command. The microcomputer 123 receives this control command, and acquires information on the actual suction pressure Ps detected by the pressure sensor 8. The duty ratio is calculated based on the detected deviation between the suction pressure Ps and the set pressure Pset, and a duty-controlled drive signal is output.

  In this embodiment, as shown in the figure, a power supply line (VCC), a ground line (GND), and a communication line L2 extend from the air conditioner ECU 105, and are connected to the power supply terminal 72a, the ground terminal 72b, and the communication terminal 72c of the circuit board 121, respectively. Has been. The ground line (GND) of each circuit on the circuit board 121 is connected to the ground terminal 72b.

FIG. 3 is a diagram schematically illustrating a refrigeration cycle centered on the compressor 100.
In addition to a mechanism for compressing the refrigerant in the housing, the compressor 100 includes a control valve 1 that controls the discharge capacity of the refrigerant and a discharge valve 160 that prevents the reverse flow of the discharged refrigerant.

  The housing of the compressor 100 is configured by assembling 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. 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 a modified example, a pressure chamber separately provided outside or outside the crank chamber may be used as the “control chamber”.

  A suction chamber 114, a discharge chamber 116 and a mounting hole 118 are defined in the rear housing 106. The rear housing 106 also includes a refrigerant inlet 120 for introducing refrigerant from the evaporator 115 side to the suction chamber 114, a refrigerant outlet 122 for discharging refrigerant discharged from the discharge chamber 116 to the condenser 111 side, a suction chamber 114 and a mounting hole 118. Are connected to each other, a communication passage 126 that connects the crank chamber 112 and the mounting hole 118, and a communication path 128 that connects the discharge chamber 116 and the mounting hole 118.

  A rotating shaft 130 is disposed in the crank chamber 112 so as to penetrate the center thereof. The rotating shaft 130 is rotatably supported by a bearing 132 provided on the cylinder block 102 and a bearing 134 provided on the front housing 104. A lug plate 136 is fixed to the rotary shaft 130, and a swash plate 140 (corresponding to a “swing plate”) is supported via a support arm 138 projecting from the lug plate 136.

  The swash plate 140 can be tilted with respect to the axis of the rotary shaft 130 and is connected to pistons 142 slidably disposed in the plurality of cylinders 110 via shoes 144. The front end portion of the rotating shaft 130 extends through the front housing 104, and a bracket 146 is screwed to the front end portion. Further, a lip seal 148 is provided so as to seal the gap between the front end portion of the rotating shaft 130 and the front housing 104 from the outside. The lip seal 148 is in sliding contact with the peripheral surface of the rotating shaft 130 and prevents leakage of refrigerant gas along the peripheral surface.

  A bearing 150 is provided at the 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 rotary shaft 130 via the bracket 146.

  The suction chamber 114 communicates with the cylinder 110 via a suction relief valve 154 provided on the valve plate 108, and also communicates with the outlet of the evaporator 115 via the refrigerant inlet 120. The discharge chamber 116 communicates with the cylinder 110 via a discharge relief valve 156 provided on the valve plate 108, and also communicates with the inlet of the condenser 111 via the refrigerant outlet 122. In addition, an orifice (not shown) that connects the crank chamber 112 and the suction chamber 114 is provided with an orifice having a fixed cross-sectional area so that the refrigerant having the lowest flow rate set in advance from the crank chamber 112 to the suction chamber 114 is disposed. The flow is allowed and internal circulation of the refrigerant in the compressor 100 is ensured.

  The angle of the swash plate 140 is held at a position where the loads of the springs 157 and 158 for urging the swash plate 140 in the crank chamber 112 and the load due to the pressure applied to both surfaces of the piston 142 connected to the swash plate 140 are balanced. The The angle of the swash plate 140 can be continuously changed by introducing a part of the refrigerant discharged into the crank chamber 112 to change the control pressure Pc and changing the balance of pressure applied to both surfaces of the piston 142. it can. The refrigerant discharge capacity is adjusted by changing the stroke of the piston 142 by changing the angle of the swash plate 140. 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” that allows a forward flow of refrigerant discharged from the compressor 100 and blocks a reverse flow. A fixed orifice 117 is provided on the upstream side of the discharge valve 160. Before and after the fixed orifice 117, a differential pressure (Pd1-Pd2) between the first discharge pressure Pd1 that is the upstream pressure and the second discharge pressure Pd2 that is the downstream pressure is generated. The first discharge pressure Pd1 is equal to the pressure in the discharge chamber 116. When the flow rate control for controlling the discharge flow rate of the compressor 100 to be constant is performed, the control valve 1 may sense this differential pressure (Pd1−Pd2). However, the pressure loss due to the fixed orifice 117 is practically negligible in the entire refrigeration cycle, and there is no significant difference between the first discharge pressure Pd1 and the second discharge pressure Pd2. Therefore, in the following description, these are collectively referred to as “discharge pressure Pd” unless otherwise distinguished.

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

FIG. 4 is a cross-sectional view showing the configuration of the control valve according to the first embodiment.
The control valve 1 is configured as a Ps control valve that controls the flow rate of the refrigerant introduced from the discharge chamber 116 to the crank chamber 112 so as to keep the suction pressure Ps of the compressor 100 at a set pressure. The control valve 1 is configured by assembling a valve unit 2, a solenoid 4, and a 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 refrigerant discharged into the crank chamber 112 during operation of the compressor 100 and a sub-valve for allowing the refrigerant in the crank chamber 112 to escape to the suction chamber 114 when the compressor 100 is started. (So-called bleed valve). The solenoid 4 controls the flow rate of the refrigerant introduced into the crank chamber 112 by driving the main valve in the opening / closing direction to adjust the opening degree. The valve unit 2 includes a stepped cylindrical body 5 (functioning as a “valve body”), a main valve, a subvalve, and the like provided inside the body 5.

  The body 5 is provided with ports 12, 14, and 16 from the upper end side. 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.

  In the body 5, a main passage that communicates the port 16 and the port 14 and a sub passage that communicates the port 14 and the port 12 are formed. A main valve is provided in the main passage, and a sub valve is provided in the sub passage. 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 sequentially arranged from one end side. A main valve hole 20 and a main valve seat 22 are provided in the main passage. A sub valve hole 32 and a sub valve seat 34 are provided in the sub passage.

  The port 12 communicates the working chamber 23 and the suction chamber 114 defined in the upper part of the body 5. The port 16 introduces a refrigerant having a 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 the main valve is disposed. The port 14 guides the refrigerant that has reached the control pressure Pc via the main valve to the crank chamber 112 during the steady operation of the compressor 100, while the control pressure discharged from the crank chamber 112 when the compressor 100 is started. Pc refrigerant is introduced. 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 having the suction pressure Ps during the steady operation of the compressor 100, and guides the refrigerant having the suction pressure Ps to the suction chamber 114 via the auxiliary valve when the compressor 100 is started.

  Cylindrical filter members 15 and 17 are attached to the ports 14 and 16, respectively. The filter members 15 and 17 include a mesh for suppressing entry of foreign matter into the body 5. When the main valve is opened, the filter member 17 restricts entry of foreign matter into the port 16, and when the auxiliary valve is opened, the filter member 15 restricts entry of foreign matter into the port 14.

  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 working chamber 23. A guide hole 27 is provided in the lower part of the body 5 (on the side opposite to the main valve hole 20 of the main valve chamber 24). A stepped cylindrical valve driver 29 is slidably inserted into the guide hole 27.

  The upper half part of the valve drive body 29 is reduced in diameter to form a partition part 33 that partitions the inside and the outside while penetrating the main valve hole 20. A step portion formed at an intermediate portion of the valve driver 29 is a main valve body 30 that is attached to and detached from 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 from the main valve chamber 24 side to open and close the main valve, and adjust the flow rate of refrigerant flowing from the discharge chamber 116 to the crank chamber 112. The upper portion of the partition portion 33 is increased in a tapered shape toward the upper side, and a sub-valve seat 34 is formed at the upper end opening. The auxiliary valve seat 34 functions as a movable valve seat that is displaced together with the valve driver 29. In the present embodiment, the valve driver 29 and the main valve element 30 are distinguished from each other, but the valve driver 29 may be regarded as a “main valve element”.

  On the other hand, a cylindrical sub-valve element 36 is slidably inserted into the guide hole 25. An internal passage of the auxiliary valve body 36 is an auxiliary valve hole 32. This internal passage allows the auxiliary valve chamber 26 and the working chamber 23 to communicate with each other by opening the auxiliary valve. The auxiliary valve body 36 and the auxiliary valve seat 34 are disposed to face each other in the axial direction. The auxiliary valve body 36 opens and closes the auxiliary valve by attaching and detaching to the auxiliary valve seat 34 in the auxiliary valve chamber 26.

  Further, an elongated operating rod 38 is provided along the axis of the body 5. The upper end portion of the operating rod 38 is connected to the auxiliary valve body 36. The lower end portion of the operating rod 38 is connected to a plunger 50 (described later) of the solenoid 4. The upper half of the actuating rod 38 passes through the valve driver 29 and the upper part thereof is reduced in diameter. The auxiliary valve body 36 is fixed to the reduced diameter portion.

  A ring-shaped spring receiver 40 is fitted and supported at an intermediate portion in the axial direction of the operating rod 38. Between the valve drive body 29 and the spring receiver 40, a spring 42 for biasing the valve drive body 29 in the valve closing direction of the main valve and the sub valve is interposed. When the main valve is controlled, the valve drive body 29 and the spring receiver 40 are stretched by the elastic force of the spring 42, and the main valve body 30 and the operating rod 38 operate integrally.

  When the auxiliary valve body 36 sits on the auxiliary valve seat 34 and closes the auxiliary valve, the relief of the refrigerant from the crank chamber 112 to the suction chamber 114 is blocked. Further, when the auxiliary valve body 36 is separated from the auxiliary valve seat 34 and opens the auxiliary valve, the relief of the refrigerant from the crank chamber 112 to the suction chamber 114 is allowed.

  On the other hand, the solenoid 4 includes a stepped cylindrical core 46, a bottomed cylindrical sleeve 48 assembled to the lower end of the core 46, and a step accommodated in the sleeve 48 and disposed opposite to the core 46 in the axial direction. A cylindrical plunger 50 with a cylindrical shape, a cylindrical bobbin 52 extrapolated to the core 46 and the sleeve 48, an electromagnetic coil 54 wound around the bobbin 52 to generate a magnetic circuit by energization, and the electromagnetic coil 54 to the outside A cylindrical case 56 provided to cover the lower end of the case 56, an end member 58 provided to seal the lower end opening of the case 56, 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 press-fitting the lower end of the body 5 into the upper end opening of the core 46. A pressure chamber 28 is formed between the core 46 and the valve driver 29. On the other hand, the operating rod 38 is inserted so as to penetrate the center of the core 46 in the axial direction. The pressure chamber 28 communicates with the working chamber 23 through the internal passages of the valve drive body 29 and the sub valve body 36. For this reason, the suction pressure Ps of the working 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 operating rod 38 and the core 46.

  Between the core 46 and the plunger 50, a spring 44 (functioning as a “biasing member”) that biases them 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 operating rod 38 is coaxially connected to each of the auxiliary valve body 36 and the plunger 50. The upper part of the operating rod 38 is press-fitted into the sub-valve body 36, and the lower end part is press-fitted into the upper part of the plunger 50. The actuating rod 38, the auxiliary valve body 36, and the plunger 50 constitute a “movable member” that is integrally displaced with the valve drive body 29 when the main valve is controlled.

  The operating rod 38 appropriately transmits a solenoid force, which is a suction force between the core 46 and the plunger 50, to the main valve body 30 and the sub valve body 36. On the other hand, the operating rod 38 is loaded so that the load by the spring 44 opposes the solenoid force. That is, in the control state of the main valve, the force adjusted by the solenoid force acts on the main valve body 30 to appropriately control the opening degree of the main valve. When the compressor 100 is started, the operating rod 38 is displaced relative to the body 5 against the biasing force of the spring 44 according to the magnitude of the solenoid force, and after closing the main valve, the sub-valve body 36 is pushed up. Open the secondary valve. As a result, the bleed function is exhibited.

  The sleeve 48 is made of a nonmagnetic material and has a stepped cylindrical shape. The upper end portion of the sleeve 48 is extrapolated and press-fitted into the lower end portion of the core 46. The lower portion of the sleeve 48 is reduced in diameter and opened to the pressure sensor 8.

  A side surface of the plunger 50 is provided with a communication groove 66 parallel to the axis, and a lower portion of the plunger 50 is provided with a communication hole 68 for communication between the inside and the outside. With such a configuration, even when the plunger 50 is located 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 further to the pressure sensor 8. Is also guided.

  A power line 55 and a ground line 57 connected to the electromagnetic coil 54 extend from the bobbin 52 and are connected to the circuit board 121 (specifically, the drive circuit 129) of the control unit 6. From the circuit board 121, the power supply terminal 72a, the ground terminal 72b, and the communication terminal 72c (collectively referred to as “connection terminal 72”) extend, and are respectively led out through the end member 58. .

  The end member 58 has a stepped cylindrical shape, and is attached so as to cover the entire structure in the solenoid 4 included in the case 56 from below. The end member 58 is made of a resin material having corrosion resistance, and is provided so that the resin material is also interposed in the gap between the case 56 and the electromagnetic coil 54. A connector portion 74 is integrally provided on a side portion of the end member 58, and the connection terminal 72 is disposed inside the connector portion 74. An accommodation chamber 76 is formed inside the end member 58 and accommodates the control unit 6. A lid member 78 is attached so as to close the lower end opening of the end member 58.

FIG. 5 is an enlarged view of a portion A in FIG.
The control unit 6 is configured by mounting the pressure sensor 8 and each circuit described above on a circuit board 121. The pressure sensor 8 includes a stepped cylindrical sensor body 131 and a sensor module 133 supported at the center of the sensor body 131. The sensor body 131 includes an upper body 135 and a lower body 137, and is assembled so as to sandwich a circuit board 121 (printed wiring board) between them. 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 path 139 along the axis of the sensor body 131, and the sensor module 133 is disposed so as to cross the through path 139.

  A pressure space is formed inside the through passage 139, and is partitioned into a first pressure chamber 143 and a second pressure chamber 145 by the sensor module 133. The sensor module 133 includes a pressure-sensitive body 161 (functioning as a “pressure-sensitive portion”) configured 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 includes a stepped cylindrical upper housing 165 and a ring-shaped lower housing 167. The diaphragm 153 is supported so that the outer peripheral edge portion is sandwiched between the upper housing 165 and the lower housing 167.

  The sensor element 151 includes a thin pressure receiving portion 171 that senses and displaces pressure, and a thick support portion 173 that supports the pressure receiving portion 171 from the outside in the radial direction. A support portion 173 is attached to the circuit board 121. The sensor element 151 is configured as a piezoresistive sensor, and a plurality of resistance elements such as strain gauges are provided in the pressure receiving portion 171, and a bridge circuit is configured by the plurality of resistance elements.

  The protective material 155 is made of a fluorine-based or silicon-based rubber material or gel material, and has electrical insulation. The protective material 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 received by the diaphragm 153 is also transmitted to the sensor element 151 through the protective material 155. That is, the protective material 155 also functions as a transmission material for transmitting pressure. The sensor element 151 outputs a detection signal corresponding to the differential pressure between the first pressure chamber 143 and the second pressure chamber 145. A detection signal from the sensor module 133 is output to the microcomputer 123 via the output line 59. In the modification, 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 sandwiched between the sleeve 48 and the lid member 78 in the axial direction, and is 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.

  A 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-sensitive body 161. On the other hand, the second pressure chamber 145 communicates with the inside of the lower body 137. Since the lower body 137 is provided with a communication hole 179 that communicates the inside and the outside, the second pressure chamber 145 communicates with the atmosphere via the communication hole 179, the accommodation chamber 76, and the internal passage 181 of the connector portion 74. That is, atmospheric pressure is introduced into the second pressure chamber 145. For this reason, 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. In the modification, the second pressure chamber 145 may be sealed 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 PWM (Pulse Width Modulation) system is adopted for energization control to the solenoid 4. The PWM control is performed by supplying a pulse current of about 400 Hz set to a predetermined duty ratio, and is executed when the microcomputer 123 drives the drive circuit 129. The drive circuit 129 has a PWM output unit that outputs a pulse signal (pulse current) having a designated duty ratio.

  When the solenoid 4 is not energized (off) in the control valve 1, that is, when the air conditioner system is not operating, no suction force acts between the core 46 and the plunger 50. On the other hand, the urging force of the spring 44 is transmitted to the valve driving body 29 via the plunger 50, the operating rod 38 and the auxiliary valve body 36. As a result, the main valve body 30 is separated from the main valve seat 22 and the main valve is fully opened. At this time, the auxiliary valve maintains the closed state.

  On the other hand, when an activation current is supplied to the electromagnetic coil 54 of the solenoid 4 at the time of activation of the air conditioner system, the auxiliary valve opens. This starting current is higher than the current during steady-state control of the solenoid 4 (also referred to as “holding current”). That is, first, the main valve body 30 is pushed up by the urging force of the spring 42 and is seated on the main valve seat 22. As a result, the main valve is closed and introduction of the refrigerant discharged into the crank chamber 112 is restricted. At this time, since the solenoid force overcomes the urging force of the spring 42, the auxiliary valve body 36 is pushed up integrally with the operating rod 38 even after the main valve is closed. As a result, the auxiliary valve body 36 is separated from the auxiliary valve seat 34, the auxiliary valve is opened, and the bleed function is effectively exhibited. That is, after the main valve is closed and the introduction of the refrigerant discharged into the crank chamber 112 is restricted, the sub valve is opened to quickly relieve the refrigerant in the crank chamber 112 to the suction chamber 114. As a result, the compressor can be started quickly.

  During the steady control of the solenoid 4, the above-described feedback control is executed. That is, the microcomputer 123 acquires control command information (information indicating the set pressure Pset) received from the air conditioner ECU 105, and acquires information on the actual suction pressure Ps detected by the pressure sensor 8. Then, the duty ratio is calculated based on the detected difference between the suction pressure Ps and the set pressure Pset, and a drive command is output to the drive circuit 129. The drive circuit 129 supplies a drive current that is duty controlled to the solenoid 4 based on the drive command. The main valve body 30 stops at a 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. As a result, the control for bringing the suction pressure Ps close to or maintaining the set pressure Pset can be realized with high accuracy. Note that the air conditioner ECU 105 may sequentially receive information indicating the set pressure Pset from the air conditioner ECU 105, or may use the previously received set pressure Pset unless it is transmitted from the air conditioner ECU 105. The microcomputer 123 may transmit information detected by the pressure sensor 8 to the air conditioner ECU 105.

  When such a steady control is being performed, the load on the engine increases, and when the air conditioner ECU 105 gives a command to reduce the load on the compressor 100, the microcomputer 123 cuts off the power to the solenoid 4. Alternatively, it is suppressed to a predetermined lower limit value. When the energization of the solenoid 4 is interrupted, the suction force does not act between the core 46 and the plunger 50, so that the main valve body 30 is separated from the main valve seat 22 by the urging force of the spring 44, and the main valve is Fully open. At this time, the auxiliary valve body 36 is basically seated on the auxiliary valve seat 34, so that the auxiliary valve is closed. As a result, the refrigerant having the discharge pressure Pd introduced from the discharge chamber 116 to the port 16 passes through the fully opened main valve and flows from the port 14 to the crank chamber 112. Therefore, the control pressure Pc is increased, and the compressor 100 performs the minimum capacity operation.

  As described above, in the present embodiment, the control valve 1 is inserted into the mounting hole 118 of the compressor 100 from the front end side, and the control unit 6 is integrally provided on the rear end side. In addition, the circuit of the control unit 6 and the circuit of the solenoid 4 are integrated on the circuit board 121, and a common connection terminal 72 is provided on the connector portion 74 on the rear end side. For this reason, it is not necessary to provide a dedicated mounting hole for mounting the control unit 6 in the compressor 100 separately. Thereby, the external leakage site | part of the refrigerant | coolant in the compressor 100 can be reduced. Since the connector portion of the control unit 6 and the solenoid 4 is shared, the control valve 1 can be made compact, and the number of man-hours for attaching the connector when attaching to 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, the control unit 6 performs feedback control using the output of the pressure sensor 8, whereby the accuracy of Ps control can be improved. Since the control unit 6 is provided in the control valve 1 independently of the air conditioner ECU 105, an electrical disturbance between the air conditioner ECU 105 and the control valve 1 has little influence on the control of the control unit 6. That is, according to the present embodiment, the configuration for controlling the compressor 100 with high accuracy can be realized easily and at low cost.

[Second Embodiment]
FIG. 6 is a cross-sectional view showing the configuration of the control valve according to the second embodiment. Below, it demonstrates centering on difference with 1st Embodiment. In the figure, the same components as those in the first embodiment are denoted by the same reference numerals.

  In addition to the configuration of the control valve 1 of the first embodiment, the control valve 201 of the present embodiment includes a power element 210 for autonomously (mechanically) adjusting the suction pressure Ps (corresponding to “sensed pressure”). Have The control valve 201 is configured as a so-called Ps sensing valve that controls the flow rate of the refrigerant introduced from the discharge chamber 116 to the crank chamber 112 so as to keep the suction pressure Ps of the compressor 100 at a set pressure. The control valve 201 is configured by integrally assembling a stepped cylindrical body 205 and a solenoid 4 in the axial direction. An end member 213 is fixed so as to close the upper end opening of the body 205. The control valve 201 has a configuration in which a power element 210, a sub valve, a main valve, a solenoid 4, and a control unit 6 are arranged in this order from one end side.

  The power element 210 is disposed in the working chamber 23. The power element 210 includes a bellows 245 that senses and displaces the suction pressure Ps. A spring 246 that urges the bellows 245 in the extending direction (opening direction of the main valve) is disposed inside the power element 210. The power element 210 generates a force that opposes the solenoid force due to the displacement of the bellows 245. This counter force is also transmitted to the main valve body 30 via the actuating rod 38 and the auxiliary valve body 36.

  The operating rod 38 passes through the sub-valve body 36, and the tip of the operating rod 38 can be operatively connected to the power element 210. The actuating rod 38 is loaded with a driving force (also referred to as “pressure-sensitive driving force”) due to the expansion / contraction operation of the power element 210 so as to oppose the solenoid force. That is, in the control state of the main valve, the force adjusted by the solenoid force and the pressure-sensitive driving force acts on the main valve body 30 to appropriately control the opening degree of the main valve. Even during the control of the main valve, when the suction pressure Ps increases considerably, the operating rod 38 is displaced relative to the body 205 against the urging force of the bellows 245, and after closing the main valve, the sub-valve body 36 is closed. Push up to open the secondary valve. As a result, the bleed function is exhibited.

  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 determined by the supplied current value (also referred to as “sub valve opening pressure”), the sub valve opens. To do. That is, the solenoid force overcomes the urging force of the spring 42, and the auxiliary valve body 36 is pushed up integrally. As a result, the auxiliary valve body 36 is separated from the auxiliary valve seat 34 and the auxiliary valve is opened. Note that the “sub-valve opening pressure” changes accordingly when 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 of the main valve is adjusted autonomously so that the suction pressure Ps becomes the set pressure Pset. This set pressure Pset changes according to the supply current value to the solenoid 4. In the control state of the main valve, the sub valve body 36 is seated on the sub valve seat 34, and the sub valve maintains the closed state. 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 of the main valve. At this time, the main valve body 30 is in a valve lift position in which the force in the valve opening direction by the spring 44, the solenoid force in the valve closing direction, and the force in the valve opening direction by the power element 210 corresponding to the suction pressure Ps are balanced. Stop.

  For example, when the refrigeration load increases and the suction pressure Ps becomes higher than the set pressure Pset, the bellows 245 is reduced, and the main valve element 30 is relatively displaced upward (in the valve closing direction). As a result, the valve opening of the main valve decreases, and the compressor operates to increase the discharge capacity. As a result, the suction pressure Ps changes in a decreasing direction. Conversely, when the refrigeration load decreases and the suction pressure Ps becomes lower than the set pressure Pset, the bellows 245 extends. As a result, the power element 210 urges the main valve body 30 in the valve opening direction to increase the valve opening of the main valve, and the compressor operates to reduce the discharge capacity. As a result, the suction pressure Ps is maintained at the set pressure Pset.

  When such steady control is performed, the microcomputer 123 executes feedback control so as to correct the autonomous control of the main valve. That is, the microcomputer 123 calculates a duty ratio based on the detected deviation between the suction pressure Ps and the set pressure Pset (to make the deviation close to zero), and corrects the drive command to the drive circuit 129.

  According to the present embodiment, the same effect as that of the first embodiment can be obtained for the Ps sensing valve. Furthermore, the responsiveness of the control for bringing the suction pressure Ps closer to the set pressure Pset can be improved by the autonomous control by the operation of the power element 210. When the time constant of the pressure sensor 8 is large, the control delay can be suppressed by an autonomous operation. Conversely, when a control response delay due to pressure sensing occurs in this autonomous control, the response delay can be suppressed by feedback control. Control hunting due to response delay can also be prevented or suppressed. In other words, by providing the control valve 201 with a pressure sensitive part and a control part, it is possible to achieve both improvement in responsiveness as a Ps sensing valve and improvement in accuracy of Ps control.

[Third Embodiment]
FIG. 7 is a cross-sectional view illustrating a configuration of a control valve according to the third embodiment. Below, it demonstrates centering on difference with 1st Embodiment. In the figure, the same components as those in the first embodiment are denoted by the same reference numerals.

  The control valve 301 of this embodiment does not include a bleed valve, and the arrangement configuration of the valve body and the solenoid is also different from that of the first embodiment. The control valve 1 includes a stepped cylindrical body 305 (functioning as a “valve body”) and a solenoid 304 assembled to the body 305 in the axial direction.

  A port 16 (discharge chamber communication port) is provided at the upper end opening of the body 305, and a port 14 (control chamber communication port) and a port 12 (suction chamber communication port) are provided from the upper side. The body 305 is formed with a flow passage 318 that connects the port 14 and the port 16 and a pressure chamber 28 that communicates with the port 12. A valve hole 20 is provided in the middle of the flow passage 318, and a valve seat 22 is provided at the upstream end of the valve hole 20. A filter member 315 having a bottomed cylindrical shape is attached to the port 16.

  A guide hole 327 is provided in the body 305 so as to penetrate the partition wall between the flow passage 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 is greatly open toward the lower side of the body 305. A communication path 332 is provided outside the guide hole 327. The communication path 332 extends in parallel with the guide hole 327 and connects the port 12 and the pressure chamber 28.

  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 the valve body 330 so that the valve body 330 can be easily attached and detached. When the valve body 330 is attached to and detached from the valve seat 22 from the upstream side, the valve portion is opened and closed. A spring receiver 340 is fixed to the upper end portion of the body 305, and a spring 342 is interposed between the valve body 330 and the spring receiver 340. The spring 342 biases the valve body 330 in the valve closing direction. The load of the spring 342 is adjusted by the fixed position of the spring receiver 340 in the body 305.

  A shaft 338 is provided so as to penetrate the valve hole 20 and the guide hole 327 in the axial direction. The shaft 338 is slidably supported in the guide hole 327. The upper end of the shaft 338 is reduced in diameter and penetrates the valve hole 20 to support the valve body 330 from 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 cylindrical sleeve 348 that supports the bobbin 52 from the inside. And 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. The case 356 and the end member 358 constitute a “solenoid body”. Needless to say, the components of the “solenoid body” may include a member (sleeve 48 or the like) fixed to the case 356 and the end member 358. In any case, the sensor body 131 is fixed to the solenoid body.

  A plunger 350 and a core 346 are disposed in a working space 360 formed inside the electromagnetic coil 54. The sleeve 348 is made of a nonmagnetic material, and holds the electromagnetic coil 54 between the case 356 and the sleeve 348. The sleeve 348 has a flange portion 357 extending radially outward from the upper end opening thereof, and the flange portion 357 is sandwiched between the body 305 and the case 356. The core 346 has a stepped cylindrical shape, and is fixed so that the upper half of the core 346 is inserted into the lower end of the sleeve 348. The core 346 has a through hole 366 in the axial direction. The through hole 366 is a stepped hole whose upper half is slightly enlarged in diameter, and the spring 44 is accommodated in the large diameter part.

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

  The interior of the core 346 is open to the pressure sensor 8. A communication groove 66 parallel to the axis is provided on the side surface of the plunger 350 and communicates with the through hole 366 of the core 346. With such a configuration, the suction pressure Ps of the pressure chamber 28 is also guided to the pressure sensor 8. The pressure sensor 8 is supported so as to be sandwiched between the core 346 and the lid member 78 in the axial direction, and is fixed to the end member 358 (solenoid body). A 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 sensitive body 161.

  In the above configuration, when the solenoid 304 is not energized, no attractive 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 that of the spring 342, the plunger 350 is displaced upward, and the valve body 330 is opened together with the shaft 338. As a result, the valve portion is fully opened, the control pressure Pc is increased, and the compressor performs the minimum capacity operation.

  On the other hand, when an activation current is supplied to the solenoid 304, the core 346 attracts the plunger 350 against the biasing force of the spring 44. Accordingly, the valve body 330 is pushed down by the spring 342 and is seated on the valve seat 22, and the control valve 301 is closed.

  When the holding current is supplied to the solenoid 304 by shifting to the steady control, the force due to the differential pressure between the discharge pressure Pd and the control pressure Pc (that is, the force due to the differential pressure acting on the valve body 330), the control pressure Pc and the suction pressure. The force due to the differential pressure with Ps (that is, the force due to the differential pressure acting on the shaft 338), the resultant force of the springs 342 and 44, and the attractive force of the solenoid 304 are balanced. As a result, the valve body 330 is pushed up, away from the valve seat 22, and set to a predetermined opening degree. As a result, the refrigerant having the discharge pressure Pd is controlled to a flow rate corresponding to the opening degree and introduced into the crank chamber 112, and the compressor 100 shifts to an operation with a capacity corresponding to the control current. The microcomputer 123 performs the above-described 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 this embodiment, even in a structure that does not have a sub-valve (bleed valve), the same effect as that of the first embodiment can be obtained.

[Fourth Embodiment]
FIG. 8 is a cross-sectional view showing the configuration of the control valve according to the fourth embodiment. Below, it demonstrates centering on difference with 1st Embodiment. In the figure, the same components as those in the first embodiment are denoted by the same reference numerals.

  The control valve 401 of the present embodiment is configured so that the differential pressure (Pd−Ps) between the discharge pressure Pd and the suction pressure Ps of the compressor 100 approaches the set differential pressure ΔPset, which is a control target value, from the discharge chamber 116 to the crank chamber 112. It is configured as a so-called Pd-Ps differential pressure valve that controls the flow rate of the refrigerant introduced into the.

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

  A stepped cylindrical valve seat forming member 416 is disposed in a passage in the body 405 that connects the port 16 and the port 14. The valve seat forming member 416 is harder than the body 405. The valve seat forming member 416 is inserted coaxially into the upper portion of the body 405 and fixed. The valve seat forming member 416 is provided with a through hole 495 along the axis, 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 portion of the valve seat forming member 416 has a tapered shape with an outer diameter that decreases downward and extends into the valve chamber 24. A valve seat 22 is formed on the lower end surface of the valve seat forming member 416. A valve body 430 is disposed in the valve chamber 24 so as to face the valve seat 22 from below. When the valve body 430 contacts and separates from the valve seat 22, the opening degree of the valve portion is adjusted.

  A bleed hole 496 parallel to the through hole 495 is provided outside the through hole 495 in the valve seat forming member 416 in the radial direction. The bleed hole 496 is for ensuring oil circulation in the compressor by allowing a minimum amount of refrigerant to flow into the control chamber even when the valve is closed.

  A partition wall 426 is provided so as to partition the internal space of the body 405 vertically. A valve chamber 24 is formed above the partition wall 426, and a pressure chamber 28 is formed below the partition wall 426. The valve chamber 24 communicates with the control chamber via the port 14. The pressure chamber 28 communicates with the suction chamber 114 via 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 so as to penetrate the guide portion 432 along the axis, and a long operating 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 at the upper end of the operating rod 434. The valve body 430 and the operating rod 434 are integrally formed by cutting stainless steel.

  The guide part 432 protrudes small on the upper surface side of the partition wall 426 and protrudes largely on the lower surface side. The guide portion has a tapered shape with an outer diameter that decreases 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 attaches and detaches the valve seat 22 at the upper end surface thereof to open and close the valve portion. Since the hardness of the valve seat forming member 416 is sufficiently high, the valve seat 22 is not easily deformed even when the valve body 430 is repeatedly seated, and the durability of the valve portion is ensured.

  A retaining ring 436 (E-ring) is fitted to the lower part of the operating rod 434, and a disk-shaped spring receiver 437 is provided so that the downward movement is restricted by the retaining ring 436. A spring 444 that biases the operating rod 434 downward (in the valve opening direction) is interposed between the spring receiver 437 and the body 405 (partition wall 426). The spring 444 is a tapered spring that decreases in diameter from the lower surface of the partition wall 426 toward the lower spring receiver 437. Since the guide part 432 is tapered as described above, the tapered spring 444 can be arranged. The lower part of the body 405 constitutes a connecting part with the solenoid 404.

  A filter member 445 that suppresses entry of foreign matter into the port 16 is provided at the upper end opening of the body 405.

  On the other hand, the solenoid 404 includes a cylindrical core 446, a stepped cylindrical sleeve 448 that is externally attached to the core 446, a plunger 450 that is accommodated in the sleeve 448 and is disposed to face the core 446 in the axial direction, and a sleeve. Bobbin 52 extrapolated to 448, electromagnetic coil 54 wound around bobbin 52, cylindrical case 456 provided to cover electromagnetic coil 54 from the outside, and core 446 above bobbin 52. A stepped cylindrical connecting member 462 assembled between the case 456 and an end member 458 attached to the lower end opening of the case 456. The sleeve 448 is made of a non-magnetic material, and the core 446 is accommodated in the upper half and the plunger 450 is accommodated in the lower half. The lower portion of the sleeve 448 is reduced in diameter and opened to the pressure sensor 8.

  An insertion hole 467 is formed so as to penetrate the center of the core 446 in the axial direction, and a shaft 438 is inserted so as to penetrate the insertion 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 that of the operating rod 434. A plunger 450 is assembled to the lower half of the shaft 438. In the present embodiment, the shaft 438 and the operating rod 434 constitute a “transmission rod” that transmits the solenoid force to the valve body 430.

  The plunger 450 is coaxially supported on the shaft 438 at the upper portion thereof. A retaining ring 470 (E-ring) is fitted at a predetermined position in the axial direction intermediate portion of the shaft 438, and the upward movement of the plunger 450 is restricted by the retaining ring 470. A communication groove 466 parallel to the axis is provided on the side surface of the plunger 450, and a communication passage 62 through which the refrigerant passes is formed between the plunger 450 and the sleeve 448.

  A ring-shaped shaft support member 472 is press-fitted into the upper end portion of the core 446, and the upper end portion 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 support member 472 is cut away, so that a communication path is formed between the core 446 and the shaft support member 472. The suction pressure Ps is also guided to the inside of the solenoid 404 through this communication path.

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

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

  With the above configuration, the suction pressure Ps of the pressure chamber 28 is also guided to the pressure sensor 8. The pressure sensor 8 is supported so as to be sandwiched between the sleeve 448 and the lid member 78 in the axial direction, and is fixed to the end member 458 (solenoid body). A 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 sensitive body 161.

  In the above configuration, the diameter of the operating rod 434 is slightly smaller than the inner diameter of the valve hole 20 but has almost the same size. Therefore, the influence of the control pressure Pc acting on the valve body 430 in the valve chamber 24 is substantially canceled (offset). Is done. Therefore, the differential pressure (Pd−Ps) between the discharge pressure Pd and the suction pressure Ps substantially acts on the valve body 430 with respect to the pressure receiving area approximately the size of the valve hole 20. The valve body 430 operates so that the differential pressure (Pd−Ps) is held at the set differential pressure ΔPset 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 due to the resultant force of the springs 444 and 442, and the valve portion is held in the fully opened state. As a result, the compressor 100 performs the minimum capacity operation.

  On the other hand, when an activation current is supplied to the solenoid 404, the plunger 450 is attracted to the core 446 with the maximum attraction force. At this time, the valve body 430, the operating rod 434, the shaft 438, and the plunger 450 are integrally operated in the valve closing direction, and the valve body 430 is seated on the valve seat 22. Thereby, the compressor 100 performs the maximum capacity operation.

  When the control is shifted to the steady control and the holding current is supplied to the solenoid 404, the valve body 430, the operating rod 434, the shaft 438, and the plunger 450 are integrally operated. At this time, the valve body 430 includes a spring load of the spring 444 that biases the operating rod 434 in the valve opening direction, a spring load of the spring 442 that biases the plunger 450 in the valve closing direction, and the plunger 450 in the valve closing direction. A valve lift position in which the load of the energizing solenoid 404, the force due to the discharge pressure Pd received by the valve body 430 in the valve opening direction, and the force due to the suction pressure Ps received by the valve body 430 in the valve closing direction are balanced. Stop at.

  In this balanced state, if the compressor speed increases with the engine speed and the discharge capacity increases, the differential pressure (Pd-Ps) increases and a force in the valve opening direction acts on the valve body 430. The valve body 430 further lifts and increases the flow rate of the refrigerant flowing from the discharge chamber 116 to the crank chamber 112. As a result, the control pressure Pc increases, the compressor 100 operates in a direction to decrease the discharge capacity, and is controlled so that the differential pressure (Pd−Ps) becomes the set differential pressure ΔPset. When the engine speed decreases, the reverse operation is performed and the differential pressure (Pd−Ps) is controlled to be the set differential pressure ΔPset.

  When such steady control is performed, the control valve 401 controls to maintain the differential pressure (Pd−Ps) at the set differential pressure ΔPset during normal times when the suction pressure Ps is equal to or higher than the set pressure Pset. When the suction pressure Ps becomes lower than the set pressure Pset, the suction pressure Ps is controlled to approach the set pressure Pset. That is, the control valve 401 basically functions as a Pd-Ps differential pressure valve that controls the differential pressure (Pd-Ps), while it functions as a Ps control valve when the suction pressure Ps is excessively reduced, thereby preventing excessive cooling.

  When the detected suction pressure Ps is lower than the set pressure Pset, the microcomputer 123 performs feedback control that brings the suction pressure Ps closer to 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 effect as that of the first embodiment can be obtained even in the control valve that controls the differential pressure between two predetermined 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 detected value of the pressure sensor 8. From these, the value of the discharge pressure Pd can be estimated. For this reason, it is not necessary to separately provide a sensor for detecting the discharge pressure Pd. In the present embodiment, the control of the differential pressure (Pd−Ps) is the main control, and the control of the suction pressure Ps is positioned as an auxiliary control. In the modification, the latter pressure control may be the main control. That is, the microcomputer 123 may perform feedback control so that the suction pressure Ps approaches the set pressure Pset during steady control. In this case, the control valve 401 operates autonomously so as to bring the differential pressure (Pd−Ps) closer to the optimum set differential pressure ΔPset with respect to the suction pressure Ps while maintaining the suction pressure Ps constant.

[Fifth Embodiment]
FIG. 9 is a cross-sectional view showing a configuration of a control valve according to the fifth embodiment. Below, it demonstrates centering on difference with 1st Embodiment. In the figure, the same components as those in the first embodiment are denoted by the same reference numerals.

  The control valve 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 configured by integrally assembling a body 505 and a solenoid 504 in the axial direction. An end member 513 is fixed to the upper end opening of the body 505, and a power element 510 is provided integrally with the end member 513.

  The body 505 has a stepped cylindrical shape. From the upper side, the body 505 has a port 517 (discharge chamber downstream communication port), a port 16 (discharge chamber communication port), a port 14 (control chamber communication port), and a port 12 (suction). Room communication port). In addition, a communication hole 520 is provided so as to penetrate the end member 513 in the axial direction, and a port 516 (discharge chamber communication port) is provided at the upper end opening. That is, the port 516 introduces the first discharge pressure Pd1 of the discharge chamber 116 into the power element 510.

  The port 517 communicates the pressure chamber 523 defined in the upper part of the body 505 with the downstream side of the fixed orifice 117 (upstream side of the discharge valve 160), and introduces the second discharge pressure Pd2 into the pressure chamber 523. 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. The operation rod 538 is inserted through these guide holes. A valve chamber 24 and a valve hole 20 are provided between the port 14 and the port 16. The operating rod 538 is slidably supported in the guide holes 525 and 527, and has an upper end connected to the power element 510 and a lower end 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 and displaces a pressure difference (Pd1−Pd2) between the first discharge pressure Pd1 and the second discharge pressure Pd2. A spring 542 that urges the bellows 545 in the extending direction (valve opening direction) is disposed inside the power element 510. The power element 510 generates a force that opposes the solenoid force by the displacement of the bellows 545. This counter force is also transmitted to the valve body 530 via the operating rod 538. In consideration of the stability of the differential pressure (Pd1-Pd2) that is a sensing target, it is preferable to introduce the second discharge pressure Pd2 from a position away from the discharge valve 160 (check valve).

  On the other hand, 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 portion of the operating rod 538 is inserted into and supported by the plunger 550.

  In the above configuration, 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 crank pressure Pc acting on the valve body 530 is Canceled substantially.

  When the solenoid 504 is not energized, the valve body 530 is separated from the valve seat 22 by the urging force of the spring 44 and the valve portion is held in the fully open state. As a result, the compressor 100 performs the minimum capacity operation.

  On the other hand, when an activation 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 operating 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 performs the maximum capacity operation.

  When the control is shifted to the steady control and the holding current is supplied to the solenoid 504, the valve body 530, the operating rod 538, and the plunger 550 are integrally operated. At this time, the valve body 530 includes a spring load of the spring 44 that biases the operating rod 538 in the valve opening direction, a load of the solenoid 504 that biases the plunger 550 in the valve closing direction, and the valve body 530 opens the valve. The valve stops at a valve lift position where the force by the discharge pressure Pd received in the direction and the force by the suction pressure Ps received by the valve body 430 in the valve closing direction are balanced.

  In this balanced state, when the rotational speed of the compressor increases with the rotational speed of the engine and the discharge flow rate increases, 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. As a result, the control pressure Pc increases, the discharge flow rate of the compressor 100 decreases, and the differential pressure (Pd1−Pd2) is controlled to the set differential pressure ΔPdset. On the other hand, when the engine speed decreases, the reverse operation is performed and the differential pressure (Pd1−Pd2) is controlled to be the set differential pressure ΔPdset. If the differential pressure (Pd1-Pd2) is kept constant, the discharge flow rate will also be constant. As a result, the discharge flow rate is maintained at the set flow rate.

  When such steady control is performed, the control valve 501 controls to maintain the differential pressure (Pd1−Pd2) at the set differential pressure ΔPdset during normal times when the suction pressure Ps is equal to or higher than the set pressure Pset. When the suction pressure Ps becomes lower than the set pressure Pset, the suction pressure Ps is controlled to approach the set pressure Pset. That is, the control valve 501 basically functions as a flow rate control valve that maintains the discharge flow rate at the set flow rate, but functions as a Ps control valve when the suction pressure Ps is excessively reduced to prevent excessive cooling.

  When the detected suction pressure Ps is lower than the set pressure Pset, the microcomputer 123 performs feedback control that brings the suction pressure Ps closer to 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 effect as that of the first embodiment can be obtained even in the control valve that controls the discharge flow rate of the compressor 100 to be constant. In this embodiment, the flow rate control is the main control, and the control of the suction pressure Ps is positioned as an auxiliary control. In the modification, the latter flow control may be the main control. That is, the microcomputer 123 may perform feedback control so that the suction pressure Ps approaches the set pressure Pset during steady control. In this case, the control valve 501 operates autonomously so as to bring the differential pressure (Pd1−Pd2) close to the optimum set differential pressure ΔPdset with respect to the suction pressure Ps while maintaining the suction pressure Ps constant.

  If the pressure sensor 8 can detect the value of the suction pressure Ps, the torque of the compressor 100 can be calculated based on the suction pressure Ps and the set flow rate. For this reason, such calculation of torque may be performed by the microcomputer 123 or the air conditioner ECU 105. In the former case, torque information can be transmitted from the microcomputer 123 to the air conditioner ECU 105. In the latter case, the microcomputer 123 can transmit flow rate information and suction pressure Ps information to the air conditioner ECU 105, and the air conditioner ECU 105 can calculate the torque. According to the present embodiment, torque control based on refrigerant flow rate control, control of blown air temperature based on suction pressure control, torque estimation based on the output of the pressure sensor 8, and the like can be performed. For this reason, both power saving by torque control and comfort by air temperature control can be achieved.

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

  In the above embodiment, as illustrated in FIG. 2, the configuration in which the circuit board 121 includes the communication circuit 127 (transceiver) as the communication unit is illustrated. In a modification, it is good also as a structure which communicates between the microcomputer 123 and air-conditioner ECU105, without providing such a communication circuit 127. FIG.

  FIG. 10 is a schematic diagram showing the electrical configuration of the control valve 701 and its surroundings according to a modification. In this modification, serial communication is performed between the microcomputer 123 and the air conditioner ECU 105. Between the microcomputer 123 and the air conditioner ECU 105, a MOSI line 172c, a MISO line 172d, and an SCK line 172e are provided. The MOSI line 172c is a communication line that connects 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 that connects 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 sending a synchronization clock from the air conditioner ECU 105 to the microcomputer 123.

  With this configuration, in this modification, the power supply terminal 72a, the ground terminal 72b, and the three communication terminals 172c, 172d, and 172e (these are also collectively referred to as “connection terminal 172”) extend from the circuit board 721. , And is disposed inside the connector portion 74.

  In the above embodiment, an example of the structure of the pressure sensor 8 has been shown, but it goes without saying that a structure different from this may be adopted. In the above embodiment, a pressure sensor using a strain gauge is exemplified, but a pressure sensor using a magnetic sensor may be adopted. For example, a magnetic sensor may be employed in which a magnet is provided integrally with the pressure sensitive body, and a detection signal corresponding to the displacement of the magnet accompanying the displacement of the pressure sensitive body is output. The microcomputer 123 may calculate the suction pressure Ps and the like based on the detected value of the magnetic sensor.

  In the above embodiment, as illustrated in FIG. 4, the configuration in which the pressure sensor 8 is integrally provided in the control unit 6 is illustrated. In a modification, these may be configured separately and assembled in the solenoid chamber housing chamber 76, respectively.

  In the above embodiment, as shown in FIG. 2, the configuration in which the drive circuit 129 and the power supply circuit 125 are arranged outside the microcomputer 123 is exemplified. Also good. The same applies to the modification of FIG.

  In the said embodiment, the structure which provides a control part in a solenoid body was illustrated. In a modification, a pressure sensor may be provided in the solenoid body, and other circuits and the like may be disposed outside the control valve. Another circuit or the like may be provided to the air conditioner ECU. The solenoid body may integrally include a common connector portion including connection terminals connected to the power supply line and the ground line of the solenoid and connection terminals connected to the power supply line, the ground line, and the output line of the pressure sensor. And you may output the detection signal of a pressure sensor to air-conditioner ECU via an output line. The control valve may execute only power input / output and pressure sensor output. Then, the air conditioner ECU may calculate the pressure based on the output of the pressure sensor and supply a necessary control current to the control valve.

  In the above-described embodiment, an example in which the suction pressure Ps is detected by the pressure sensor has been described. In a modification, the pressure sensor may be configured to sense the control pressure Pc. In that case, the control pressure Pc may be a gauge pressure or an absolute pressure. A passage for introducing the control pressure Pc to the pressure sensor is formed in at least one of the valve body and the solenoid body. Alternatively, a pressure sensor may sense a differential pressure (Pd−Ps) between the discharge pressure Pd and the suction pressure Ps. Alternatively, the pressure sensor may sense a differential pressure (Pd1−Pd2) between the first discharge pressure Pd1 and the second discharge pressure Pd2. In this case, a passage for introducing the discharge pressure Pd (first discharge pressure Pd1, second discharge pressure Pd2) to the pressure sensor is formed in at least one of the valve body and the solenoid body. In the above embodiment, as shown in FIG. 3, the example in which the fixed orifice 117 is provided on the upstream side of the discharge valve 160 is shown. In a modification, a fixed orifice 117 may be provided on the downstream side of the discharge valve 160. Then, the flow rate may be controlled by sensing the differential pressure between the upstream pressure and the downstream pressure of the fixed orifice 117.

  In the said embodiment, the control valve which controls by adjusting a valve opening degree by PWM control was shown. In a modification, it is good also as a control valve which controls by opening and closing a valve part also during steady control, and changing the opening-closing timing (opening-closing time). For example, the valve portion may be opened and closed at about 10 Hz, and a control valve that adjusts the valve opening time may be used.

  In the above embodiment, as shown in FIG. 5, the pressure sensor is configured such that a pressure sensitive body (pressure sensitive portion) is configured by filling a protective material (transmitting material) between the sensor element and the diaphragm. In the modification, the diaphragm may be omitted, and the pressure-sensitive body may be configured by the sensor element and the protective material. Alternatively, the diaphragm and the protective material may be omitted, and the sensor element alone may constitute the pressure sensitive body. In such a configuration, the inner working space of the electromagnetic coil may be opened to the pressure sensitive body. In other words, a portion that is deformed by receiving a differential pressure in the pressure sensor, and the deformation is electrically detected and converted into a pressure value may be referred to as a “pressure-sensitive portion”.

  In the above-described embodiment, a control valve for so-called “fill control” that changes the discharge capacity of the compressor by adjusting the flow rate of the refrigerant introduced from the discharge chamber to the control chamber has been exemplified. In a modified example, a control valve for so-called “extraction control” that changes the discharge capacity of the compressor 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 provided integrally with the control valve for the extraction control, and feedback control for bringing the suction pressure Ps closer to the set pressure Pset may be executed.

  In the said embodiment, the structure which open | releases the inner working space of an electromagnetic coil to the pressure sensitive body of the pressure sensor was illustrated. In a modified example, the working space and the pressure sensitive body may be isolated. Then, a pressure to be sensed (sensed pressure) may be introduced from a port separately provided in the solenoid body and guided to the pressure sensitive body.

  In the said embodiment, the structure which provides a control part on the opposite side to a valve body with respect to the electromagnetic coil was illustrated. In a modification, the control unit may be provided between the valve body and the solenoid body or inside the valve body. Even with such a configuration, it is possible to cope with the problem of improving the control accuracy with a single control valve.

  Although not described 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 operate based on a command signal from the air conditioner ECU to control the solenoid.

  In the above embodiment, an example in which information indicating the set pressure Pset is sent as a control command from the air conditioner ECU to the microcomputer 123 has been described. This “information indicating the set pressure Pset” may be a value indicating the set pressure Pset itself, or may be temperature information associated with the set pressure Pset.

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

DESCRIPTION OF SYMBOLS 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 Connector part, 100 Compressor, 118 mounting hole, 121 circuit board, 133 sensor module, 143 first pressure chamber, 145 second pressure chamber, 151 sensor element, 161 pressure sensitive body, 201 control valve, 205 body, 210 power element, 301 control valve , 304 Solenoid, 305 Body, 330 Valve body, 346 Core, 350 Plunger, 360 Operating 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 valve body, 546 core, 550 plunger.

Claims (7)

A control valve that is assembled so as to be inserted into a mounting hole provided in a variable capacity compressor, and that controls the discharge capacity of refrigerant discharged from the compressor,
A valve body having a refrigerant flow passage and a valve hole provided in the flow passage;
A valve body that opens and closes the valve portion in contact with and away from the valve hole;
A solenoid that is assembled to the valve body and applies a driving force in the axial direction to the valve body in accordance with a supply current;
A pressure sensor for detecting a predetermined refrigerant pressure referred to for energization control of the solenoid;
With
The solenoid is
A solenoid body assembled integrally with the valve body in the axial direction;
An electromagnetic coil that is held by the solenoid body and has an inner working space;
A core fixed to the solenoid body coaxially with the electromagnetic coil;
A plunger supported so as to be axially displaceable in the working space;
A power line connected to the electromagnetic coil and drawn from the opposite side of the valve body of the solenoid body;
Including
The pressure sensor is
A pressure sensing part that senses and displaces the refrigerant pressure;
An output line for outputting a detection signal corresponding to the displacement of the pressure-sensitive portion;
And a control valve for a variable capacity compressor, wherein the control valve is disposed on a side opposite to the valve body with respect to the electromagnetic coil.   2. The control valve for a variable capacity compressor according to claim 1, wherein the pressure sensor is housed in a space of the solenoid body opposite to the valve body. The pressure sensor includes a sensor body formed so as to surround the pressure-sensitive portion,
The sensor body is fixed to the solenoid body;
The refrigerant pressure is introduced into the working space;
The control valve for a variable capacity compressor according to claim 1 or 2, wherein the working space is open to the pressure-sensitive portion. A control unit that inputs a detection signal of the pressure sensor via the output line, and that controls energization of the solenoid based on a command from an external control device;
The controller is
Arranged on the opposite side of the valve body with respect to the electromagnetic coil,
The feedback control for executing a control amount determined for the refrigerant pressure close to a target value based on command information from the external control device and information detected by the pressure sensor is performed. 4. The control valve for a variable capacity compressor according to any one of 3 above.   5. The variable capacitor according to 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 supply line. Control valve for compressor. A control circuit that functions as the control unit, a communication circuit for communicating with the external control device, and a circuit board on which the pressure sensor is mounted,
6. The control valve for a variable capacity compressor according to claim 5, wherein the circuit board is disposed on the side opposite to the valve body with respect to the electromagnetic coil.   The variable capacity compression according to any one of claims 1 to 3, wherein the solenoid body integrally includes a common connector portion including a connection terminal connected to the power supply line and a connection terminal connected to the output line. Control valve for machine.

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