WO1999006700A1

WO1999006700A1 - Control valve of variable capacity compressor

Info

Publication number: WO1999006700A1
Application number: PCT/JP1998/000574
Authority: WO
Inventors: Ken Suitou; Masahiro Kawaguchi; Hiroyuki Nagai; Tetsuhiko Fukanuma
Original assignee: Kabushiki Kaisha Toyoda Jidoshokki Seisakusho
Priority date: 1997-07-30
Filing date: 1998-02-12
Publication date: 1999-02-11
Also published as: KR20000064512A; KR100302993B1

Abstract

A control valve (62) for a variable capacity compressor which controls the capacity on the basis of regulation of the tilt angle of a swash plate (32) provided in a crank chamber (25) is disclosed. The compressor is equipped with an air supply passage (58) for the communication of a discharge chamber (48) with the crank chamber (25) and an air extraction passage (61) for the communication of the crank chamber (25) with an intake chamber (47). The control valve (62) is equipped with a first valve mechanism (81) for opening and closing the air supply passage (58) selectively, a second valve mechanism (82) for regulating the quantity of gas released from the crank chamber (25) into the intake chamber (47) through the air extraction passage (61) and a solenoid mechanism (83) for operating the first valve mechanism (81) and the second valve mechanism (82). The first valve mechanism (81) and the second valve mechanism (82) operate independently of each other. The first valve mechanism (81), the second valve mechanism (82) and the solenoid mechanism (83) are assembled in one housing (84).

Description

TECHNICAL FIELD The present invention relates to a displacement control valve of a variable displacement compressor used for a vehicle air conditioner, for example. In particular, the present invention relates to a control valve including a mechanism for controlling supply of refrigerant gas from a discharge chamber to a crank chamber and a mechanism for controlling release of refrigerant gas from a crank chamber to a suction chamber. BACKGROUND ART FIG. 12 is a model diagram schematically showing an example of a conventional variable displacement compressor. In this compressor, the discharge chamber 122 is connected to the crank chamber 122 via an air supply passage 123. The crank chamber 122 is connected to the suction chamber 124 via a bleed passage 125. Refrigerant gas is supplied from the external refrigerant circuit 129 to the suction chamber 124 through the suction passage 128 of the compressor. Although not shown, the swash plate is tiltably supported by the drive shaft in the crank chamber 122. A piston housed in the cylinder bore is operatively connected to the swash plate. The piston compresses the refrigerant gas supplied from the suction chamber 124 into the cylinder bore, and discharges the compressed refrigerant gas from the cylinder bore to the external refrigerant circuit 129 via the discharge chamber 121. A solenoid valve 1 26 is provided in the middle of the air supply passage 1 2 3. The solenoid valve 126 selectively opens and closes the intake passage 123 in order to control the supply of the refrigerant gas from the discharge chamber 122 to the crank chamber 122. An adjustment valve 127 is provided in the middle of the bleed passage 125. This regulating valve 1 27 adjusts the opening amount of the bleed passage 1 25 in accordance with the pressure P sc of the suction passage 1 28 內, and is discharged from the crank chamber 1 2 2 to the suction chamber 1 2 4 Control the amount of refrigerant gas. The operation of these solenoid valve 1 26 and regulating valve 1 27 The pressure Pc in the crankcase 1 2 2 is adjusted by the operation. By adjusting the pressure Pc in the crankcase 122, the difference between the pressure Pc in the crankcase 122 and the pressure in the cylinder bore changes, and the inclination of the swash plate changes accordingly. The piston reciprocates in the cylinder bore で with a stroke corresponding to the inclination of the swash plate. Accordingly, the displacement of the compressor changes according to the inclination angle of the swash plate. In the compressor described above, the solenoid valve 126 and the regulating valve 127 are configured independently of each other, and each of the valves 126 and 127 is separately incorporated in the compressor. For this reason, the structure for controlling the displacement of the compressor is complicated, and the manufacturing cost of the compressor is increased. In addition, there must be a large space in the compressor to accommodate the two valves. This leads to an increase in the size of the compressor. An object of the present invention is to provide a control valve for a variable displacement compressor which can simplify the configuration for controlling the displacement of the compressor and can reduce the size of the compressor. DISCLOSURE OF THE INVENTION In order to achieve the above object, the present invention discloses a control valve of a variable displacement compressor that controls a discharge displacement based on adjusting a tilt angle of a drive plate provided in a crank chamber. . The compressor includes a piston operatively connected to the drive plate and disposed within the cylinder bore. The piston compresses the gas supplied from the suction chamber into the cylinder bore, and discharges the compressed gas to the discharge chamber. The tilt angle of the drive plate changes according to the pressure in the crankcase. The compressor further includes an air supply passage connecting the discharge chamber to the crank chamber to supply gas from the discharge chamber to the crank chamber, and a crank chamber to discharge gas from the crank chamber to the suction chamber. And a bleed passage connected to the The control valve has a first valve mechanism for selectively opening and closing the air supply passage, and a second valve mechanism for adjusting the amount of gas released from the crank chamber through the bleed passage to the suction chamber. For assembling the first and second valve mechanisms And one housing. The first valve mechanism and the second valve mechanism are provided so as to operate independently of each other. Therefore, according to the present invention, the first valve mechanism for opening and closing the air supply passage and the second valve mechanism for adjusting the opening amount of the bleed passage are assembled in one housing. For this reason, the structure for controlling the displacement of the compressor is simplified compared to the conventional technology in which the two types of valves are individually configured and separately assembled in the compressor. Manufacturing cost is reduced. In addition, since it is only necessary to secure a space for incorporating one control valve in the compressor, the control valve can be easily incorporated in the compressor, and the compressor can be downsized. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a sectional view showing a control valve according to a first embodiment of the present invention.

FIG. 2 is a sectional view showing a variable displacement compressor provided with the control valve of FIG.

FIG. 3 is a partially enlarged sectional view showing the compressor when the inclination angle of the swash plate is at a maximum.

FIG. 4 is a partially enlarged sectional view showing the compressor when the inclination angle of the swash plate is at a minimum.

FIG. 5 is a model diagram schematically showing a refrigerant gas flow path in the compressor of FIG.

FIG. 6 is a cross-sectional view illustrating a state where the solenoid of the control valve according to the second embodiment is excited.

FIG. 7 is a cross-sectional view showing a state in which the solenoid of the control valve in FIG. 6 is demagnetized. FIG. 8 is a cross-sectional view showing a state where the solenoid of the control valve according to the third embodiment is excited.

FIG. 9J is a sectional view showing a state where the solenoid of the control valve in FIG. 8 is demagnetized. FIG. 10 is a cross-sectional view showing a state where the solenoid of the control valve according to the fourth embodiment is excited.

Figure 1 1 is a _c Figure 1 2 is a cross-sectional view showing a state where Sorenoi de of the control valve of Figure 1 0 is demagnetized, the model diagram schematically showing the flow path of the refrigerant gas in the conventional compressor It is. BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, a first embodiment of a displacement control valve of a variable displacement compressor embodying the present invention will be described with reference to FIGS. First, the configuration of the variable capacity compressor will be described. As shown in FIG. 2, a front housing 22 is joined to a front end of the cylinder block 21. The rear housing 23 is connected to the rear end of the cylinder block 21 via a valve plate 24. The crank chamber 25 is formed inside the front housing 22 on the front side of the cylinder block 21. The drive shaft 26 is rotatably supported by the front housing 22 and the cylinder block 21. The front end of the drive shaft 26 projects outside from the crank chamber 25, and a pulley 27 is fixed to this projection. The pulley 27 is directly connected to an external drive source (vehicle engine E in this embodiment) via a belt 28. That is, the compressor of this embodiment is a clutchless type variable displacement compressor in which no clutch exists between the drive shaft 26 and the external drive source. The pulley 27 is supported by the front housing 22 via an angular bearing 29. Front housing 2 2 both load in the thrust direction of the load及beauty radial direction acting on the pulley 2 7, the front end outer periphery and the front housing 2 2 _c drive shaft 2 6 for receiving via the Aringu 2 9 base Angiyura A lip seal 30 is interposed between them. Lip seal 30 prevents pressure leakage in crankcase 25 內. The substantially disk-shaped swash plate 32 is supported by the drive shaft 26 in the crank chamber 25 內 so as to be able to slide in the axial direction of the shaft 26 and to be tiltable. tip A pair of guide bins 33 each having a guide ball is fixed to a swash plate 32. The rotating body 31 is fixed to the drive shaft 26 so as to be integrally rotatable in the crank chamber 25. The rotating body 31 has a support arm 34 projecting toward the swash plate 32. The support arm 34 has a pair of guide holes 35 formed therein. The guide bins 33 are respectively slidably fitted into the guide holes 35. The engagement between the support arm 34 and the guide pin 33 causes the swash plate 32 to rotate integrally with the drive shaft 26. Further, the engagement between the support arm 34 and the guide bin 33 guides the movement of the swash plate 32 along the axial direction of the drive shaft 26 and the tilt of the swash plate 32. As the swash plate 32 moves toward the cylinder block 21 side (rearward), the inclination angle of the swash plate 32 decreases. A protrusion 31 a is formed on the rear surface of the rotating body 31. By contacting the swash plate 32 with the projection 31a, the swash plate 32 is regulated so as not to incline beyond a predetermined maximum inclination angle. The coil spring 36 is arranged between the rotating body 31 and the swash plate 32. The spring 26 biases the swash plate 32 rearward (in a direction in which the inclination angle of the swash plate 32 decreases). As shown in FIGS. 2 to 4, an accommodation hole 37 is provided in the center of the cylinder block 21 so as to extend along the axial direction of the drive shaft 26. In the accommodation hole 37, a cylindrical blocking body 38 whose one end is closed is accommodated so as to be able to slide along the axial direction of the drive shaft 26. The interrupter 38 has a large-diameter portion 38a and a small-diameter portion 38b. The rear end of the drive shaft 26 is inserted into the blocking body 38. A radial bearing 40 is fixed to an inner peripheral surface of the large-diameter portion 38 a by a snap ring 41. The radial bearing 40 can slide with respect to the drive shaft 26 _c The rear end of the drive shaft 26 is supported by the inner peripheral surface of the receiving hole 37 via the radial bearing 40 and the blocking member 38 Is done. The coil spring 39 is disposed between a step between the large-diameter portion 38a and the small-diameter portion 38b and a surface of the housing hole 37. The spring 39 biases the blocking body 38 toward the swash plate 32. The biasing force of the coil spring 39 is smaller than the biasing force of the coil spring 36. The suction passage 42 is formed at the center of the rear housing 23 and the valve plate 24 so as to extend along the axis of the drive shaft 26. The suction passage 42 forms a suction pressure region. The inner end of the suction passage 42 communicates with the accommodation hole 37. The positioning surface 43 is formed on the valve plate 24 around the opening at one end of the suction passage 42. The rear end face of the blocking member 38 can be in contact with the positioning surface 43. As shown in FIG. 4, when the rear end face of the blocking body 38 contacts the positioning surface 43, the movement of the blocking body 38 backward (in the direction away from the rotating body 31) is restricted. Then, the suction passage 42 is shut off from the accommodation hole 37. The thrust bearing 44 is supported on the drive shaft 26 so as to be movable in the axial direction between the swash plate 32 and the blocking body 38. The thrust bearing 44 is always sandwiched between the swash plate 32 and the interrupter 38 by the urging force of the coil spring 39. The thrust bearing 44 prevents the rotation of the swash plate 32 from being transmitted to the interrupter 38. The plurality of cylinder bores 21 a are formed through the cylinder block 21 so as to extend in parallel with the axis of the drive shaft 26. The cylinder bores 21 a are arranged at equal intervals around the axis of the drive shaft 26. A single-headed piston 45 is housed in each cylinder pore 21a. A hemispherical portion of a pair of shoes 46 is slidably fitted to each biston 45. The swash plate 32 is slidably sandwiched between the flat portions of the shoes 46. The rotation of the drive shaft 26 is transmitted to the swash plate 32 via the rotating body 31. The rotational motion of the swash plate 32 is converted into a reciprocating motion of the biston 45 in the cylinder bore 21 a 內 through the shoe 46. The suction chamber 4 7 are formed in the central portion in the Rya housing ² 3. The suction chamber 47 communicates with the accommodation hole 37 via the communication port 55. The discharge chamber 48 is formed in the housing 23 around the suction chamber 47. The suction port 49 and the discharge port 50 are formed on the valve plate 24 so as to correspond to the respective cylinder bores 21a. The suction valves 51 are formed on the valve plate 24 so as to correspond to the respective suction ports 49. The discharge valves 52 are formed on the valve ports 24 so as to correspond to the respective discharge ports 50. When each biston 45 moves the cylinder bore 21 a from the top dead center to the bottom dead center, the refrigerant gas in the suction chamber 47 pushes the suction valve 51 out of the suction port 49 and pushes each cylinder bore 2 Flow into 1a. When each piston 45 moves in the cylinder bore 21a from the bottom dead center toward the top dead center, the refrigerant gas compressed until reaching a predetermined pressure in each cylinder bore 21a is discharged to the discharge port 50. Then, the discharge valve 52 is pushed out and discharged to the discharge chamber 48. The opening of the discharge valve 52 is regulated by contacting the retainer 53 on the valve plate 24. A thrust bearing 54 is arranged between the rotating body 31 and the front housing 22. The thrust bearing 54 receives a compression reaction force acting on the rotating body 31 via the piston 45, the swash plate 32, and the like. The pressure release passage 56 is formed in the drive shaft 26. The pressure release passage 56 has an inlet 56 a that opens into the crank chamber 25 near the lip seal 30, and an outlet 56 b that opens inside the shutoff 38. The pressure release hole 57 is formed on the peripheral surface of the rear end of the blocking body 38. The pressure release hole 57 communicates the inside of the blocking body 38 with the accommodation hole 37. Refrigerant gas is discharged from the crank chamber 25 to the suction chamber 47 through the pressure release passage 56 and the pressure release hole 57. As shown in FIGS. 2 to 5, the air supply passage 58 connects the discharge housing 48 and the crank chamber 25 with the rear housing 23, the valve plate 24, and the cylinder block. It is formed in the 21st. In addition to the air supply passage 58, a communication passage 59 connecting the discharge chamber 48 and the crank chamber 25 is formed in the valve plate 24 and the cylinder block 21. The communication passage 59 has a fixed throttle 60 at an end opening to the crank chamber 25. The bleed passage 61 is formed in the rear housing 23, the valve plate 24, and the cylinder block 21 to connect the crank chamber 25 and the suction chamber 47. The capacity control valve 62 is mounted on the rear housing 23 so as to be located in the middle of the air supply passage 58 and the bleed passage 61. The supply passage 58 and the bleed passage 61 are shared between the crank chamber 25 and the control valve 62. The introduction passage 63 is provided between the suction passage 42 and the control valve 62 to guide the pressure in the suction passage 42 to the control valve 62 (hereinafter referred to as the primary suction pressure Pse). It is formed in a housing 23. As shown in FIG. 2, the discharge port 64 is formed in the cylinder block 21 so as to communicate with the discharge chamber 48. The external refrigerant circuit 65 connects the outlet 64 and the suction passage 42. On the external refrigerant circuit 65, a condenser 66, an expansion valve 67 and an evaporator 68 are provided. The expansion valve 67 adjusts the flow rate of the refrigerant according to a change in the temperature of the refrigerant gas on the outlet side of the evaporator 68. In the vicinity of the evaporator 68, a temperature sensor 69 is provided. Temperature sensor 69 detects the temperature of evaporator 68 and outputs a signal based on the detected temperature to control computer 70. Various devices including a room temperature setting device 71, a room temperature sensor 72, an air conditioner operating switch 73, an engine speed sensor 74, and the like are connected to the computer 70. The passenger sets the desired room temperature, that is, the target temperature by using the setting device 71. The computer 70 is, for example, a room temperature preset by the room temperature setting device 71, a detected temperature obtained from the temperature sensor 69, a detected temperature obtained from the room temperature sensor 72, and an ON / OFF state of the operation switch 73. A current value to be given to the control valve 62 is instructed to the drive circuit 75 based on various information such as the engine speed obtained from the engine speed sensor 74. The drive circuit 75 outputs the current of the commanded value to the coil 110 of the control valve 62 described later. Determine the current value to be given to control valve 62. The information for determining may include information other than the above information, such as the temperature outside the vehicle compartment. Next, the structure of the control valve 62 will be described in detail. As shown in FIGS. 1, 2 and 5, the control valve 62 adjusts the opening amount of the first valve mechanism 81 and the bleed passage 61 for selectively opening and closing the supply passage 58. And a solenoid mechanism 83 for operating the two valve mechanisms 81, 82. The first valve mechanism 81, the second valve mechanism 82, and the solenoid mechanism 83 are assembled in one housing 84. First, the first valve mechanism 81 will be described in detail. The first valve chamber 85 and the communication chamber 86 are formed in the housing 84 so as to communicate with each other. The first valve chamber 85 is connected to the discharge chamber 48 via the air supply port 87 and the air supply passage 58. Therefore, the pressure Pd of the discharge chamber 48 內 is guided into the first valve chamber 85. When the control valve 62 is mounted on the rear housing 23, the annular chamber 23a is located at the position S corresponding to the communication chamber 86, and the outer peripheral surface of the housing 84 of the control valve 62 and the rear housing 23 Formed between the inner wall of The communication chamber 86 is connected to the crank chamber 25 via a communication port 88, an annular chamber 23a, and an air supply passage 58 shared with the bleed passage 61. Therefore, the pressure P c of the crank chamber 25 內 is guided into the communication chamber 86. The communication chamber 86 has a first valve hole 89 opening to the first valve chamber 85. The first valve body 90 is movably disposed in the first valve chamber 85 so as to selectively open and close the first valve hole 89. A first plunger 92 is connected to a lower end of the first valve body 90 via a first rod 91. The opening panel 93 is arranged between the first valve body 90 and the inner end face of the first valve chamber 85. The opening spring 93 urges the first valve body 90 in a direction away from the first valve hole 89. The insertion hole 94 is formed through the center of the first valve body 90, the first rod 91, and the first plunger 92. The cross-sectional area S 1 of the first rod 91 is It is almost equal to the area S2. Next, the second valve mechanism 82 will be described in detail. The second valve chamber 95 is formed in the housing 84 so as to communicate with the communication chamber 86. The second valve chamber 95 is connected to the suction chamber 47 via the bleed port 97 and the bleed passage 61. Therefore, the pressure in the suction chamber 47 (hereinafter, referred to as the secondary suction pressure Psc) is guided to the second valve chamber 95 內. The pressure sensing chamber 96 is formed in the housing 84 above the second valve chamber 95. The pressure sensing chamber 96 is connected to the suction passage 42 via the pressure sensing port 98 and the introduction passage 63. Therefore, the primary suction pressure P se of the suction passage 42 is guided into the pressure-sensitive chamber 96. The communication chamber 86 has a second valve hole 99 opening to the second valve chamber 95. The second rod 100 is relatively movably inserted into the insertion hole 94 of the first rod 91 in the first valve mechanism 81. The second plunger 101 is fixed at the lower end of the second rod 100. The upper end of the second rod 100 extends through the communication chamber 86 toward the second valve chamber 95. The second valve body 102 is fixed to the upper end of the second port 100 in the second valve chamber 95 內 in order to adjust the opening amount of the second valve hole 99. The closing panel 103 is arranged between the second valve body 102 and the inner end face of the second valve chamber 95. The closing panel 103 urges the second valve body 102 in a direction approaching the second valve hole 99. The bellows 104 functioning as a pressure-sensitive member is disposed in the pressure-sensitive chamber 96. A connecting cylinder 105 whose upper end is closed is fixed to the lower end of the bellows 104. The pressure-sensitive rod 106 protrudes from the upper surface of the second valve body 102. The upper end of the pressure-sensitive rod 106 is inserted into the connecting cylinder 105 so as to be relatively movable. Therefore, the bellows 104 is connected to the second valve body 102 via the connecting cylinder 105 and the pressure-sensitive rod 106 so as to be able to approach and separate therefrom. The bellows 104 expands and contracts in response to the primary suction pressure P se guided from the suction passageway 42 to the pressure-sensitive chamber 96, and the expansion and contraction causes the second valve body 102 to open the second valve hole 99. Operate to adjust the amount. Next, the solenoid mechanism 83 will be described in detail. The solenoid chamber 107 is formed in the housing 84 so as to be located below the first valve chamber 85 described above. The communication hole 108 is formed in the housing 84 so as to connect the annular chamber 23a and the solenoid chamber 107. Therefore, the pressure in the annular chamber 23a (crank chamber pressure Pc) is guided to the solenoid chamber 107 via the force communication hole 108. The fixed iron core 109 is arranged between the solenoid chamber 107 and the first valve chamber 85. The first plunger 92 and the second plunger 101 are arranged in the solenoid chamber 107 so as to face the fixed iron core 1 9. The coil 110 is mounted on the fixed iron core 109 so as to be located around the plungers 92 and 101. The coil 110 is supplied with a current of a predetermined value from a drive circuit 75 based on a command from the computer 70. As shown in FIGS. 1 and 2, the solenoid mechanism 83 is disposed at a lower end of a housing 84. When the control valve 62 is installed in the rear housing 23 of the compressor, the solenoid mechanism 83 is exposed outside the rear housing 23. Therefore, the wiring extending from the drive circuit 75 can be easily connected to the coil 110 of the solenoid mechanism 83 outside the compressor. Next, the operation of the variable displacement compressor configured as described above will be described. If the temperature in the cabin detected by the room temperature sensor 72 is equal to or higher than the value set by the room temperature setting device 71 when the operation switch 73 is turned on, the computer 70 controls the control valve 6. The excitation of the solenoid mechanism 83 of 2 is instructed to the drive circuit 75. Then, a current of predetermined value is supplied to the coil 1 1 0 via the drive circuit 7 5, the _c attraction force is generated between the stationary core 1 0 9 and the first plunger 9 2 of the first valve mechanism 8 1 As shown in FIGS. 1 to 3, the suction force moves the first valve body 90 to a position where the first valve hole 89 is closed against the urging force of the opening spring 93. Therefore, the discharge chamber 48 and the The air supply passage 58 between the tank room 25 and the tank room 25 is closed. It should be noted that the first valve body 90 is always located at a position where the first valve hole 89 is closed when a current is supplied to the coil 110 irrespective of the current value. At this time, the first plunger 92 coming into contact with the fixed core 109 functions as a part of the fixed core 109. When a current of a predetermined value is supplied to the coil 110, an attraction force corresponding to the supplied current value is generated by the second plunger 101 of the first plunger 92 and the second valve mechanism 82. Occurs between This suction force is transmitted to the second valve body 102 via the second rod 100. Therefore, the second valve body 102 is urged in a direction to open the second valve hole 99 against the urging force of the closing panel 103. On the other hand, the bellows 104 is displaced in accordance with a change in the primary suction pressure P se introduced into the pressure-sensitive chamber 96 from the suction passage 42 through the introduction passage 63. The displacement of the bellows 104 is transmitted to the second valve body 102 via the pressure-sensitive rod 106. Therefore, the amount of opening of the second valve hole 99 by the second valve body 102 is determined by the balance of a plurality of forces acting on the second valve body 102, specifically, by the attachment from the solenoid mechanism 83. It is determined based on the balance between the power, the power from the bellows 104, and the power from the closing panel 103. As described above, with the first valve body 90 of the first valve mechanism 81 closing the first valve hole 89, the second valve body 102 of the second valve mechanism 82 is The opening amount of the second valve hole 99 is adjusted according to the balance of the plurality of forces acting on 102. That is, the first valve mechanism 81 and the second valve mechanism 82 operate independently. When the cooling load is large, for example, the difference between the temperature detected by the room temperature sensor 72 and the temperature set by the room temperature setting device 71 is large. The computer 70 instructs the drive circuit 75 to increase the value of the current supplied to the coil 110 of the control valve 62 as the difference between the detected temperature and the set temperature increases. Therefore, the suction force between the first plunger 92 and the second plunger 101 increases, and the force for urging the second valve body 102 in the opening direction of the second valve hole 99 increases. . Therefore, the second valve body 1 0 2 The primary suction pressure P se required to move the valve in the opening direction of the second valve hole 99 is set to a low value. Therefore, the second valve body 102 operates to adjust the opening amount of the second valve hole 99 according to the lower primary suction pressure P se. In other words, the second valve mechanism 82 operates so as to maintain a lower primary suction pressure Pse as the supplied current value increases. When the amount of opening of the second valve hole 99 by the second valve body 102 increases, the amount of refrigerant gas discharged from the crank chamber 25 to the suction chamber 47 via the bleed passage 61 increases. On the other hand, since the air supply passage 58 is closed by the first valve mechanism 81, refrigerant gas is not supplied from the discharge chamber 48 to the crank chamber 25 via the air supply passage 58. For this reason, the pressure P c in the crank chamber 25 decreases. In a state where the cooling load is large, the secondary suction pressure P sc in the suction chamber 47 is high, so that the pressure in the cylinder bore 21 a is also low. Therefore, the difference between the pressure Pc in the crank chamber 25 and the pressure in the cylinder bore 21a becomes small, and the inclination angle of the swash plate 32 becomes large, so that the compressor is operated with a large discharge capacity. When the second valve body 102 maximizes the opening amount of the second valve hole 99, the amount of refrigerant gas discharged from the crank chamber 25 to the suction chamber 47 via the bleed passage 61 is maximized. Become. Therefore, the pressure Pc in the crank chamber 25 becomes almost the same as the pressure Psc in the suction chamber 47. Therefore, as shown in FIGS. 2 and 3, the inclination angle of the swash plate 32 becomes maximum, and the compressor is operated at the maximum discharge capacity. By contacting the swash plate 32 with the protrusion 31 a of the rotating body 31, the swash plate 32 is regulated so as not to incline beyond a predetermined maximum inclination angle. When the compressor is operated at the maximum discharge capacity, the discharge pressure Pd in the discharge chamber 48 increases significantly due to the fluctuation of the condensation capacity of the condenser 66 on the external refrigerant circuit 65. There is. This high discharge pressure Pd is introduced into the first valve chamber 85 of the first valve mechanism 81 through the air supply passage 58, and acts on the first valve body 90. However, in the control valve 62 of this embodiment, the cross-sectional area S 1 of the first rod 91 connecting the first valve body 90 and the first plunger 92, and the cut-off of the first valve hole 89 are provided. It is almost equal to the area S2. In a state where the first valve body 90 closes the first valve hole 89, the discharge pressure F d in the portion except for the portion to which the first rod 91 is connected and the portion opposed to the first valve hole 89. Acts on the first valve body 90. Therefore, in a state where the first valve body 90 closes the first valve hole 89, a force based on the discharge pressure Pd for urging the first valve body 90 in the closing direction of the first valve hole 89 is generated. However, the force is substantially the same as the force based on the discharge pressure Pd for urging the first valve body 90 in the opening direction of the first valve hole 89. Therefore, the discharge pressure Pd acting on the first valve body 90 is canceled, and the first valve body 90 operates accurately without being affected by the discharge pressure Pd. Conversely, when the cooling load is small, for example, the difference between the temperature detected by the room temperature sensor 72 and the temperature set by the room temperature setting device 71 is small. Computer 7

0 instructs the drive circuit 75 to reduce the value of the current supplied to the coil 110 of the control valve 62 as the difference between the detected temperature and the set temperature is smaller. Therefore, the suction force between the first plunger 92 and the second plunger 101 is weakened, and the force for urging the second valve body 102 in the opening direction of the second valve hole 99 is reduced. Therefore, the second valve body

The primary suction pressure P se required to move 102 in the opening direction of the second valve hole 99 is set to a high value. For this reason, the second valve body 102 operates to adjust the opening amount of the second valve hole 99 in accordance with the higher primary suction pressure P se. In other words,

The two-valve mechanism 82 operates to maintain a higher primary suction pressure P se as the supplied current value decreases. When the opening amount of the second valve hole 99 by the second valve body 102 decreases, the amount of refrigerant gas discharged from the crank chamber 25 to the suction chamber 47 via the bleed passage 61 decreases. The pressure P c in the crank chamber 25 increases. Further, since the cooling load is small state lower secondary suction pressure P s in the suction chamber 4 in 7, thus _c becomes lower pressure in the cylinder bore 2 1 a, the pressure P c and the cylinder bore 2 1 of the crank chamber 2 5 The difference from the pressure in a becomes large, and the inclination of the swash plate 32 becomes small, and the compressor is operated with a small discharge capacity. You. '-As the cooling load is approached, the temperature of the evaporator 68 in the external refrigerant circuit 65 decreases so as to approach the temperature at which frost starts to be generated. When the temperature detected by the temperature sensor 69 becomes equal to or lower than the temperature at which frost starts to be generated, the combinator 70 commands the drive circuit 75 to demagnetize the solenoid mechanism 83. Then, the drive circuit 75 stops energizing the coil 110 in order to demagnetize the solenoid mechanism 83. As a result, no suction force is generated between the fixed iron core 109 and the first plunger 92, and no suction force is generated between the first plunger 92 and the second plunger 101. Therefore, as shown in FIG. 4, the first valve body 90 moves in a direction to open the first valve hole 89 by the urging force of the opening panel 93. As a result, the air supply passage 58 between the discharge chamber 48 and the crank chamber 25 is opened. On the other hand, the second valve body 102 is moved to a position where the second valve hole 99 is closed by the urging force of the closing spring 103. As a result, the bleed passage 61 between the crank chamber 25 and the suction chamber 47 is closed. Accordingly, a large amount of the high-pressure refrigerant gas in the discharge chamber 48 is supplied to the crank chamber 25 through the air supply passage 58, and the pressure P c in the crank chamber 25 內 further increases. Therefore, as shown in FIG. 4, the inclination angle of the swash plate 32 is minimized, and the compressor is operated with the minimum displacement. When the operation switch 73 is turned off, the computer 70 instructs the drive circuit 75 to demagnetize the solenoid mechanism 83. Therefore, the inclination angle of the swash plate 32 is minimized. If the primary suction pressure P se in the suction passage 42 is in a high state when the solenoid mechanism 83 is demagnetized, the high primary suction pressure P se is applied to the pressure-sensitive chamber 96 through the introduction passage 63. Introduced to shrink bellows 104. The direction in which the bellows 104 contracts is opposite to the direction in which the closing spring 103 biases the second valve body 102. However, in this embodiment, the tip of the pressure-sensitive rod 106 protruding from the second valve body 106 is inserted into the connecting cylinder 105 fixed to the bellows 104 so as to be relatively movable. I have. this Enables the second valve body 102 and the bellows 104 to approach and separate from each other. Accordingly, when the solenoid mechanism 83 is demagnetized and the primary suction pressure P se is high, the second valve body 102 and the bellows 104 are moved in a direction away from each other, and the bellows 104 Is not transmitted to the second valve body 102. For this reason, the second valve body 102 is securely located at a position where the second valve hole 99 is closed with the demagnetization of the solenoid mechanism 83 without being affected by the high primary suction pressure Pse. Is done. As described above, the first valve mechanism 81 of the control valve 62 selectively opens and closes the air supply passage 58 according to the supply and stop of the current to the coil 110 of the solenoid mechanism 83. Will be closed. In addition, the second valve mechanism 82 adjusts the opening amount of the bleed passage 61 according to the current value supplied to the coil 110. Specifically, the second valve element 102 of the second valve mechanism 82 has a second valve hole 9 9 according to the lower primary suction pressure P se as the current value supplied to the coil 110 is larger. It operates to adjust the opening amount of the second valve hole 99 according to the higher primary suction pressure Pse as the current value supplied to the coil 110 decreases. I do. Then, the compressor controls the inclination angle of the swash plate 32 to adjust the discharge capacity so as to maintain the primary suction pressure Pse at the target value. Therefore, the control valve 62 has a role of changing the target value of the primary suction pressure Pse according to the supplied current value, and a role of causing the compressor to perform the minimum capacity operation regardless of the primary suction pressure Pse. I am carrying it. The compressor provided with such a control valve 62 has a role of changing the cooling capacity of the air conditioner. When the inclination of the swash plate 32 is controlled in accordance with the adjustment of the opening amount of the bleed passage 61 by the second valve mechanism 82, the air supply passage 58 is closed by the first valve mechanism 81. For this reason, the refrigerant gas in the discharge chamber 48 is not supplied to the crank chamber 25 through the air supply passage 58. The crankcase 2 5, part of the refrigerant gas in the cylinder bore 2 1 a is, the blow-by gas in the bore 2 1 a and the piston 4 5 with clearance through the _c crankcase 2 5 supplied as blow-by gas in In a state in which only the refrigerant gas is supplied, the amount of the refrigerant gas in the crank chamber 25 decreases. In such a state, when the adjustment to reduce the opening amount of the bleed passage 61 is performed by the second valve mechanism 82, the crank chamber 2 The pressure in 5 may not rise sufficiently. This prevents a rapid change in the inclination of the swash plate 32. In this embodiment, a communication path 59 having a fixed throttle 60 is provided between the discharge chamber 48 and the crank chamber 25. Therefore, a predetermined amount of refrigerant gas is always supplied from the discharge chamber 48 to the crank chamber 25 through the communication path 59. Therefore, even if the air supply passage 58 is closed by the first valve mechanism 81 and the opening amount of the bleed passage 61 is adjusted by the second valve mechanism 82, the crank chamber 2 The pressure in (5) is always maintained at or above the specified value. Therefore, the inclination angle of the swash plate 32 changes quickly based on the adjustment of the opening amount of the bleed passage 61 by the second valve mechanism 82. This improves responsiveness when changing the discharge capacity of the compressor. The swash plate 32 moves rearward as its inclination decreases. As the swash plate 32 moves backward, the swash plate 32 pushes the blocking body 38 backward through the thrust bearing 44. Therefore, the blocking body 38 moves toward the positioning surface 43 against the urging force of the coil spring 39. The blocking body 38 gradually reduces the cross-sectional area of the gas flow path from the suction passage 42 to the suction chamber 47 as the inclination angle of the swash plate 32 decreases. This gradually reduces the amount of refrigerant gas flowing into the suction chamber 47 from the suction passage 42. Therefore, the amount of the refrigerant gas sucked from the suction chamber 47 into the cylinder bore 21 a 內 gradually decreases, and the discharge capacity gradually decreases. Accordingly, the discharge pressure Pd gradually decreases, and the torque required for driving the compressor also gradually decreases. Therefore, when the discharge capacity is reduced from the maximum to the minimum, the torque does not largely change in a short time, and the impact caused by the change in the torque is reduced. As shown in FIG. 4, when the inclination angle of the swash plate 32 is minimized, the blocking member 38 comes into contact with the positioning surface 43. When the blocking body 38 contacts the positioning surface 43, the swash plate 32 is positioned at the minimum tilt position, and the suction passage 42 is shut off from the suction chamber 47. Therefore, the refrigerant gas does not flow from the external refrigerant circuit 65 to the suction chamber 47, and the circulation of the refrigerant gas between the external refrigerant circuit 65 and the compressor is stopped. The minimum inclination angle of the swash plate 32 is slightly larger than 0 degree. The angle when the swash plate 32 is disposed on a plane orthogonal to the axis of the drive shaft 26 is 0 degree. For this reason, even if the inclination angle of the swash plate 32 becomes minimum, the refrigerant gas is discharged from the cylinder bore 21a to the discharge chamber 48, and the compressor is operated with the minimum discharge capacity. The refrigerant gas discharged from the cylinder bore 21 a into the discharge chamber 48 flows into the crank chamber 25 through the air supply passage 58. The refrigerant gas in the crank chamber 25 is sucked into the cylinder bore 21a again through the pressure release passage 56, the pressure release hole 57, the communication port 55, and the suction chamber 47. In other words, when the inclination angle of the swash plate 32 is minimum, the refrigerant gas flows into the discharge chamber 48, the air supply passage 58, the crank chamber 25, the pressure release passage 56, the pressure release hole 57, the communication port 5 5. Circulate through the circulation passage in the compressor around the suction chamber 47 and the cylinder bore 21a. With this circulation, the lubricating oil contained in the refrigerant gas lubricates each part of the compressor 內. When the cooling load increases as the temperature in the vehicle interior increases, with the operation switch 73 turned on and the swash plate 32 maintained at the minimum inclination, the room temperature sensor 72 detects this. Temperature becomes higher than the temperature set by the room temperature setting device 71. The computer 70 instructs the drive circuit 75 to excite the solenoid mechanism 83 based on the rise in the detected temperature. When the solenoid mechanism 83 is excited, the air supply passage 58 is closed by the first valve mechanism 81 and the bleed passage 61 is opened by the second valve mechanism 82. Therefore, the refrigerant gas in the crank chamber 25 flows out to the suction chamber 47 via the bleed passage 61. Therefore, the pressure Pc in the crank chamber 25 gradually decreases, and the swash plate 32 moves from the minimum tilt position to the maximum tilt position. As the inclination angle of the swash plate 32 increases, the blocking body 38 gradually moves away from the positioning surface 43 by the biasing force of the spring 39. Accordingly, the cross-sectional area of the gas flow path from the suction passage 42 to the suction chamber 47 gradually increases. This gradually increases the amount of the refrigerant gas flowing into the suction chamber 47 from the suction passage 42. Therefore, the amount of the refrigerant gas sucked from the suction chamber 47 into the cylinder bore 21 a 內 gradually increases, and the discharge capacity gradually increases. Therefore, the discharge pressure P d gradually increases, The required torque also gradually increases. Therefore, when the discharge capacity changes from the minimum to the maximum, the torque does not fluctuate greatly in a short time, and the shock accompanying the fluctuation of the torque is reduced. When the engine E stops, the operation of the compressor stops (in other words, the rotation of the swash plate 32 also stops), and the supply of current to the coil 110 of the solenoid mechanism 83 of the control valve 62 also stops. Stopped. As a result, the solenoid mechanism 83 is demagnetized and the first valve mechanism

8 1 opens the air supply passage 5 8 and the second valve mechanism 8 2

1 is closed. Therefore, the inclination angle of the swash plate 32 is minimized. If the operation of the compressor continues to be stopped, the pressure in the compressor becomes uniform, but the swash plate 32 is held at the minimum inclination angle by the biasing force of the spring 36. Therefore, when the operation of the compressor is started with the start of the engine E, the swash plate 32 starts to rotate from the state of the minimum inclination with the smallest load torque. This reduces shocks when starting the compressor. As described above, in the control valve 62 of the present embodiment, the first valve mechanism 81 for opening and closing the air supply passage 58 and the second valve mechanism 8 for adjusting the opening amount of the extraction passage 61 are provided. Two and one force are assembled in one housing 84. For this reason, the structure for controlling the discharge capacity of the compressor is simplified compared to the conventional technology in which the two types of valves are individually configured and separately assembled in the compressor. Machine manufacturing costs are reduced. Moreover, since it is only necessary to secure a space for incorporating one control valve 62 in the compressor, the control valve 62 can be easily incorporated in the compressor, and the compressor can be downsized. One coil 11 ◦ is provided for the first plunger 92 of the first valve mechanism 81 and the second plunger 101 of the second valve mechanism 82. In other words, one coil 110 is shared to control the operation of the valve bodies 90 and 102 of both valve mechanisms 81 and 82. Therefore, the structure of the control valve 62 is simplified. Also one coil With the supply of current to 11 ° and the stoppage, the valve bodies 9Ο and —102 of both valve mechanisms 81 and 82 can be simultaneously operated. In each of the valve mechanisms 81 and 82, the valve bodies 90 and 102 and the plungers 92 and 101 are connected to each other by mouths 91 and 100, respectively. Further, the first rod 91 is formed in a cylindrical shape with a force S, and the second rod 100 is passed through the first rod 91 so as to be relatively movable. Therefore, the two valve mechanisms 81 and 82 can be arranged on the same axis. In addition, both valve bodies 90 and 102 can be arranged close to each other, and both plungers 92 and 101 can be arranged close to each other. This is an effective configuration for reducing the size of the control valve 62 provided with the two valve mechanisms 81 and 82. When the supply of current to the coil 110 is stopped, the second valve 侔 102 of the second valve mechanism 82 is brought to a position where the second valve hole 99 is closed by the urging force of the closing spring 103. Be moved. For this reason, at the time of assembling the second valve mechanism 82, the second valve body 102 is disposed in a state of being in contact with the second valve hole 99 by the urging force of the closing spring 103. This facilitates the work of assembling the control valve 62. Next, a control valve 62 according to a second embodiment of the present invention will be described with reference to FIGS. 6 and 7, focusing on the differences from the first embodiment. In the control valve 62 of this embodiment, the first valve mechanism 81 and the second valve mechanism 82 are disposed on both sides of the solenoid mechanism 83. Specifically, the housing 84 includes a pressure-sensitive chamber 96, a second valve chamber 95 of the second valve mechanism 82, a communication chamber 86, a solenoid chamber 107, and a first valve mechanism 81. The first valve chamber 85 and the panel chamber 115 are formed in order from the top. The solenoid chamber 107 is connected to the annular chamber 23a via the communication hole 108. The panel room 1 15 is connected to the solenoid room 107 via the communication hole 1 16. A spherical first valve body 90 is provided at an intermediate portion of the first rod 91 of the first valve mechanism 81. Have been. A first plunger 92 and a spring receiver 1-7 are fixed to both ends of the first rod 91, respectively. The first rod 91 is arranged on the same axis as the second rod 100 of the second valve mechanism 82, and is movable along the axis. The first plunger 92 is disposed in the solenoid chamber 107 near the second plunger 101 of the second valve mechanism 82. The spring receiver 1 17 is disposed in the spring chamber 1 15. An open spring 93 is disposed between the spring receiver 117 and the inner end face of the spring chamber 115. The control valve 62 of the present embodiment configured as described above operates substantially the same as the control valve 62 of the first embodiment. Specifically, when the solenoid mechanism 83 is excited, as shown in FIG. 6, the first valve body 90 of the first valve mechanism 81 becomes the first valve hole 89

(That is, the air supply passage 5 8) is closed. Further, a second valve body 102 force of the second valve mechanism 82; an attraction force between the fixed iron core 109 and the second plunger 101 based on a supply current value to the coil 110; and The second valve hole 9 9 according to the primary suction pressure P se in the pressure sensing chamber 96

The opening amount of the bleed passage 61 is adjusted. On the other hand, when the solenoid mechanism 83 is demagnetized, the first valve body 90 of the first valve mechanism 81 is moved by the urging force of the opening spring 93, as shown in FIG. (That is, the air supply passage 58) is opened. Further, the second valve body 102 of the second valve mechanism 82 closes the second valve hole 99 (that is, the bleed passage 61) by the urging force of the closing panel 103. Therefore, in this embodiment, substantially the same operation and effect as those of the first embodiment can be obtained. In particular, in this embodiment, the rods 91, 100 of the two valve mechanisms 81, 82 are independently arranged on the same axis. This simplifies the support structure of each of the rods 91, 100 with respect to the housing 84, and facilitates the manufacture of the control valve 62. Next, a control valve 62 according to a third embodiment of the present invention will be described with reference to FIGS. 8 and 9, focusing on parts different from the first embodiment. In the control valve 62 of this embodiment, a pressure sensing chamber 96, a second valve chamber 95 of the second valve mechanism 82, a second communication chamber 1 19, and a first valve mechanism 8 are provided in the housing 84. 1, a first valve chamber 85, a communication chamber 86, and a solenoid chamber 10Ί are formed in this order from the top. The first valve chamber 85 is connected to the crank chamber 25 via an air supply port 87, an annular chamber 23a, and an air supply passage 58 formed separately from the bleed passage 61. . The solenoid chamber 107 is connected to the annular chamber 23a via a communication hole 108. Therefore, the pressure in the annular chamber 23a (crank chamber pressure Pc) is led to the solenoid chamber 107. The communication chamber 86 is connected to the discharge chamber 48 via a communication port 88 and an air supply passage 58. The second communication chamber 1 19 is partitioned from the first valve chamber 85 by a partition wall 84a. The second communication chamber 119 is connected to the second valve chamber 95 via the second valve hole 99. Further, the second communication chamber 1 19 is connected to the crank chamber 25 via a second communication port 120 and a bleed passage 61 formed separately from the air supply passage 58. . That is, in this embodiment, the air supply passage 58 and the bleed passage 61 provided between the crank chamber 25 and the control valve 62 are formed separately. The first plunger 92 of the first valve mechanism 81 is formed in a hollow shape, and the second plunger 101 of the second valve mechanism 82 is accommodated therein so as to be relatively movable. An open panel 93 is arranged between the first plunger 92 and the fixed iron core 109. The release panel 93 urges the first valve body 90 in a direction away from the first valve hole 89. A second opening panel 118 is arranged between the plungers 92,101. The second opening panel 118 urges the second valve body 102 in a direction away from the second valve hole 99. The control valve 62 of the present embodiment configured as described above performs almost the same operation as the control valve 62 of the first embodiment when the solenoid mechanism 83 is excited. More specifically, when the solenoid mechanism 83 is excited, as shown in FIG. 8, the first valve body 90 of the first valve mechanism 81 becomes the first valve hole 89 (that is, the air supply passage 5). 8) Close. Further, the second valve body 102 of the second valve mechanism 82 is controlled based on the current supplied to the coil 110. According to the suction force between the first plunger 92 and the second plunger 101, and the primary suction pressure P se in the pressure-sensitive chamber 96, the second valve hole 99 (that is, the bleed passage 61) Adjust the opening of. Note that, in this embodiment, unlike the first embodiment, as the suction force between the first plunger 92 and the second plunger 101 becomes stronger, the second valve body 102 is connected to the second valve hole. 9 The biasing force in the closing direction of 9 increases. That is, as the value of the current supplied to the coil 110 increases, the opening amount of the second valve hole 99 by the second valve body 102 decreases, and the discharge capacity of the compressor decreases. Therefore, in this embodiment, contrary to the above-described first embodiment, the computer 70 drives so that the smaller the cooling load is, the larger the current value supplied to the coil 110 of the control valve 62 is. Instruct circuit 75. When the temperature detected by the temperature sensor 69 becomes equal to or lower than the temperature at which frost starts to occur, or when the operation switch 73 is turned off, the computer 70 is connected to the solenoid mechanism 83 as in the first embodiment. Command to the drive circuit 75. When the solenoid mechanism 83 is demagnetized, as shown in FIG. 9, the first valve body 90 of the first valve mechanism 81 is moved by the urging force of the opening panel 93 to the first valve hole 89 (that is, the Open the air passage 5 8). Further, the second valve body 102 of the second valve mechanism 82 also opens the second valve hole 99 (that is, the bleed passage 61) by the urging force of the second opening panel 118. With the opening of the air supply passage 58, a large amount of high-pressure refrigerant gas in the discharge chamber 48 is supplied to the crank chamber 25 through the air supply passage 58. For this reason, the pressure Pc in the crank chamber 25 increases even though the bleed passage 61 is opened. Accordingly, the inclination angle of the swash plate 32 is minimized, and the compressor is operated with the minimum displacement. Also in this embodiment, substantially the same operation and effect as those of the first embodiment can be obtained. In particular, in this embodiment, when the current supply to the coil 110 of the solenoid mechanism 83 is stopped, the first valve mechanism 81 opens the air supply passage 58, and the second valve mechanism 8 2 opens the bleed passage 6 1. In other words, when the compressor operates at the minimum capacity, In addition to the passage 58, the bleed passage 61 between the crank chamber 25 and the suction chamber 47 is also opened. For this reason, when the compressor operates at the minimum capacity (in other words, when the inclination angle of the swash plate 32 is at a minimum), the bleed passage 61 forms a part of a refrigerant gas circulation passage in the compressor. In a clutchless variable displacement compressor in which the drive shaft 26 is directly connected to an external drive source such as the engine E, the compressor can be operated with the minimum discharge capacity even when cooling is not required. Therefore, in such a compressor, it is important to lubricate the inside of the compressor well during the minimum capacity operation. If the control valve 62 of the present embodiment is used for a compressor, the refrigerant gas in the crank chamber 25 flows through a passage including the pressure release passage 56 and the pressure release hole 57 when the compressor operates at the minimum capacity. Not only does it flow through the bleed passage 61 to the suction chamber 47. Therefore, at the time of the minimum capacity operation of the compressor, the lubricating oil contained in the refrigerant gas smoothly circulates in the compressor and lubricates the components in the compressor well. For this reason, the control valve 62 of the present embodiment can be suitably used for a clutchless variable displacement compressor. Next, a fourth embodiment of the present invention will be described based on FIG. 10 and FIG. 11, focusing on portions different from the first embodiment. In the control valve 62 of the fourth embodiment, the first valve mechanism 81 and the second valve mechanism 82 are arranged on both sides of the solenoid mechanism 83 in a manner similar to the second embodiment. Has been done. Specifically, the housing 84 includes a pressure sensing chamber 96, a second valve chamber 95 of the second valve mechanism 82, a communication chamber 86, a pair of solenoid chambers 107, and a first valve mechanism. The first valve chamber 85 of 81 and the spring chamber 115 are formed in order from the top. Both solenoid chambers 107 are separated from each other by a fixed iron core 109. The two solenoid chambers 107 are connected to the crank chamber 25 via a communication hole 108, an annular chamber 23a, and an air supply passage 58 formed separately from the bleed passage 61. I have. The spring chamber 115 is connected to the lower solenoid chamber 107 via the communication hole 116. The communication chamber 86 is connected to the crank chamber 25 via a communication port 88 and a bleed passage 61 formed separately from the air supply passage 58. That is, in this embodiment, the third embodiment is different from the third embodiment. Similarly, an air supply passage 58 and a bleed passage 61 provided between the crank chamber 25 and the control valve 62 are formed separately. A spherical first valve body 90 is provided at an intermediate portion of the first rod 91 of the first valve mechanism 81. A first plunger 92 and a panel receiver 117 are fixed to both ends of the first rod 91, respectively. The first rod 91 is arranged on the same axis as the second rod 100 of the second valve mechanism 82, and is movable along the axis. The first plunger 92 is disposed in the lower solenoid chamber 107. The second plunger 101 is arranged in the upper solenoid chamber 107. The plungers 92 and 101 oppose each other with the fixed iron core 109 interposed therebetween. The panel receiver 1 17 is arranged in the spring chamber 1 15. An open spring 93 is disposed between the spring receiver 1 17 and the inner end surface of the spring chamber 1 15. The opening panel 93 urges the first valve body 90 in a direction away from the first valve hole 89. A second open panel 118 is arranged between the second plunger 101 and the fixed core 109. The second opening panel 118 urges the second valve body 102 in a direction away from the second valve hole 99. The control valve 62 of this embodiment configured as described above operates substantially the same as the control valve 62 of the third embodiment described above. Specifically, when the solenoid mechanism 83 is excited, as shown in FIG. 10, the first valve body 90 of the first valve mechanism 81 is connected to the first valve hole 89 (that is, the air supply passage 58). ) Close. Further, the suction force between the fixed iron core 109 and the second plunger 101 based on the supply current value to the coil 110 of the second valve body 102 of the second valve mechanism 82, and the pressure sensitivity The opening amount of the second valve hole 99 (that is, the bleed passage 61) is adjusted according to the primary suction pressure Pse in the chamber 96. In this embodiment, as in the third embodiment, as the suction force between the fixed iron core 109 and the second plunger 101 increases, the second valve body 102 is connected to the second valve hole. 9 The biasing force in the closing direction of 9 increases. Therefore, in this embodiment, the third embodiment Similarly, the computer 70 instructs the drive circuit 75 to increase the value of the current supplied to the coil 110 of the control valve 62 as the cooling load decreases. Similarly to the third embodiment, when the temperature detected by the temperature sensor 69 becomes lower than the temperature at which frost begins to occur, or when the operation switch 73 is turned off, the computer 70 is connected to the solenoid mechanism 8. Command degaussing of 3 to drive circuit 75. When the solenoid mechanism 83 is demagnetized, the first valve body 90 of the first valve mechanism 81 is moved by the urging force of the opening panel 93, as shown in FIG. That is, the air supply passage 58) is opened. Further, the second valve body 102 of the second valve mechanism 82 also opens the second valve hole 99 (that is, the bleed passage 61) by the urging force of the second opening spring 118. Therefore, similarly to the third embodiment, the inclination angle of the swash plate 32 is minimized, and the compressor is operated with the minimum discharge capacity. Also in this embodiment, substantially the same operation and effect as in the third embodiment can be obtained. Moreover, since the rods 91, 100 of the two valve mechanisms 81, 82 are independently arranged on the same axis, the rods 91, 102 with respect to the housing 84, similarly to the second embodiment. , 100, the support structure is simplified, and the manufacture of the control valve 62 is facilitated. The present invention can be embodied with the following modifications. In the first embodiment and the third embodiment, the second rod 100 of the second valve mechanism 82 is formed in a cylindrical shape, and the second valve 100 is provided with the first valve mechanism 81 in the second opening 100. The first rod 91 must be inserted so that it can move relatively. In each of the above embodiments, the solenoid chamber 107 and the spring chamber 115 are connected to the crank chamber via the communication holes 108, 116, the ^ -shaped chamber 23a, and the air supply passage 58. It was connected to 25. However, the present invention is not limited to this.A port is provided on the peripheral surface of the housing 84 at a position corresponding to the solenoid chamber 107 and the spring chamber 115, and the port is connected to the air supply passage 58. May be. In this case, the pressure P c force in the crank chamber 25, The air is introduced into the solenoid chamber 107 and the spring chamber 115 through the air supply passage 58 and the port. The control valve 62 of the present invention is applied to a variable displacement compressor in which a drive shaft 26 is connected to an external drive source E via a clutch.

Claims

Claims +

1. A control valve for a variable displacement compressor that controls a discharge displacement based on adjusting a tilt angle of a drive plate (32) provided in a crank chamber (25), wherein the compressor is driven It has a piston (45) operatively connected to the plate (32) and arranged in the cylinder bore (21a), the piston (45) being moved from the suction chamber (47) to the cylinder bore (22). 1a) is compressed while the compressed gas is discharged from the cylinder bore (21a) into the discharge chamber (48), and the inclination of the drive plate (32) is changed to the crank chamber (2). 5) Varies according to the internal pressure, and the air supply passage (58) connects the discharge chamber (48) with the crank chamber to supply gas from the discharge chamber (48) to the crank chamber (25). (25), and the bleed passage (61) is used to discharge gas from the crank chamber (25) to the suction chamber (47). Crankcase (2 5) are connected to the suction chamber (4 7), said control valve,

A first valve mechanism (81) for selectively opening and closing the air supply passage (58);

A second valve mechanism (82) for adjusting an amount of gas released from the crank chamber (25) to the suction chamber (47) through the bleed passage (61); and the first valve mechanism. (8

1) The second valve mechanism (8 2) is provided so as to operate independently of each other,

One housing (84) for assembling the first valve mechanism (8 1) and the second valve mechanism (8 2);

It is characterized by having.

2. The control valve according to claim 1, further comprising: the first valve mechanism (8 1) and the second valve mechanism (8

In order to operate 2), there is provided one solenoid mechanism (83) assembled in the housing (84).

3. The control valve according to claim 2, wherein the solenoid valve (83) is exposed from the compressor when the control valve (62) is incorporated in the compressor. 3) is characterized in that it is arranged at the end of the housing (84) '. -

4. In the control valve of claim 2,

The first valve mechanism (81) is provided with a first valve hole (89) provided in the housing (84) so as to be located in the middle of the air supply passage (58), and the first valve hole (89). ) For selectively opening and closing the first valve body (90);

The second valve mechanism (82) includes a second valve hole (99) provided in the housing (84) so as to be located in the middle of the bleed passage (61), and a second valve hole (99). And a second valve body (102) for adjusting the opening amount of the valve.

The solenoid mechanism (83) is selectively energized and demagnetized based on the supply of current to operate the first valve body (90) and the second valve body (102). I do.

5. In the control valve of claim 4,

The first valve body (90) is movable in a first direction and a second direction opposite to the first direction, and the first valve body (90) opens a first valve hole (89). Moving in a first direction to close the first valve hole (89) in a second direction to close the first valve hole (89), wherein the second valve body (102) is moved in a third direction and its third direction. The second valve body (102) moves in the third direction to open the second valve hole (99), and moves through the second valve hole (99). The solenoid valve moves in a fourth direction to close, and when the solenoid mechanism (83) is excited by the supply of electric current, the solenoid mechanism (83) closes the first valve hole (89). The first valve body (90) is urged in the second direction, and the second valve body (102) is moved in the third and fourth directions by a force corresponding to the magnitude of the supplied current. To one of the

The second valve mechanism (82) has a pressure-sensitive member (104) for sensing a pressure of gas supplied to the compressor, and the pressure-sensitive member (104) is provided with a gas-sensitive member (104) supplied to the compressor. The second valve body (102) is moved in accordance with the pressure of the second valve body.

6. The control valve according to claim 5, wherein the first valve mechanism (81) is connected to the first valve body (9). 0), and the second valve mechanism (82) has a second plunger (101) connected to the second valve body (102). The solenoid mechanism (83) includes a fixed core (109) and a coil (110), and the first plunger (92) and the second plunger (101) include the core (109).

(1 09), the coil (1 110) and the plunger (9 2, 9) are connected to the coil (1 10) according to the value of the current. And a suction force for urging the first and second valve bodies (90, 102) between the first and second valve bodies.

7. The control valve according to claim 6, wherein the first valve mechanism (81) has a first rod (91) connecting the first valve body (90) and the first plunger (92), The second valve mechanism (82) has a second rod (100) connecting the second valve body (102) and the second plunger (101), and the first rod (91) One of the second rod (100) and the second rod (100) is connected to the other so as to be relatively movable.

8. The control valve according to claim 6, wherein the first valve mechanism (81) includes a first rod (91) connecting the first valve body (90) and the first plunger (92), A valve chamber (85) provided in the housing (84) for receiving the valve element (90) and connected to the first valve hole (89); and the solenoid mechanism (83) is provided with a valve. One of the discharge chamber (48) and the crank chamber (25) is disposed on the opposite side of the first valve hole (89) with the chamber (85) interposed therebetween, and the valve is connected to the valve via an air supply passage (58). The first rod (91) is connected to the first valve hole (89) through an air supply passage (58). The first rod (91) is connected to the first valve hole (89). It has a cross-sectional area (S 1) that is almost equal to the cross-sectional area (S 2).

9. The control valve according to any one of claims ⁵ to 8, wherein the first valve mechanism (81) opens the first valve hole (89) when the solenoid mechanism (83) is demagnetized. In order to urge the first valve body (90) in the first direction, the first valve means (93) is provided, and the second valve mechanism (82) is provided with the solenoid mechanism (83). When the second is demagnetized A second urging means (103) for urging the second valve body (102) in the fourth direction to close the valve hole (99) is provided.

10. The control valve according to claim 9, wherein when the solenoid mechanism (83) is excited by supply of electric current, the solenoid mechanism (83) connects the second valve body (102) to the third valve. The pressure-sensitive member (104) moves the second valve body (102) in the third direction as the pressure of the gas supplied to the compressor increases, The second valve mechanism (82) has a connecting body (105, 106) that connects the second valve body (102) and the pressure-sensitive member (104) so that they can approach and separate from each other, Its concatenation (105,

106) is at a position where the second valve body (102) closes the second valve hole (99) by the second biasing means (103) when the solenoid mechanism (83) is demagnetized. It is characterized by being allowed to be moved.

1 1. The control valve according to any of claims 5 to 7, wherein the first valve mechanism (81) opens the first valve hole (89) when the solenoid mechanism (83) is demagnetized. And a first urging means (93) for urging the first valve body (90) in the first direction. The second valve mechanism (82) is configured such that the solenoid mechanism (83) is demagnetized. The second valve body (102) is urged in the third direction so as to open the second valve hole (99).

(3) It has a biasing means (1 18).

1 2. The control valve according to any one of claims 1 to 8, wherein the compressor includes a discharge chamber (48) for continuously supplying gas from the discharge chamber (48) to the crank chamber (25). A communication path (59) connected to the communication path (25), the communication path (59) having a fixed throttle (60) for limiting the amount of gas flowing through the communication path (59) to a predetermined amount. And