JPH10318403A - Control valve for compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a control valve for a compressor whereby thermal stress acting on a fixed part of a terminal and an element fixed piece of an electric element can be reduced. SOLUTION: A power feed side terminal 94 and an earth side terminal 95 are fixed to a terminal base 93 formed of an insulating synthetic resin. In a coil 92 constituting a solenoid, a power feed side terminal 92a is connected to the power feed side terminal 94, an earth side terminal 92b is connected to the earth side terminal 95. A cathode fixed piece 97 is provided in the power feed side terminal 94, an anode fixed piece 98 is provided in the earth side terminal 95. Both the fixed pieces 97, 98 are buried in an insulation coating 102 applied to a coil unit 91. Both terminals 104, 105 of a diode 100 are fixed to the corresponding fixed pieces 97, 98. In the diode 100, by bending the halfway of both the terminals 104, 105, extension/contraction parts 104a, 105a are formed.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a control valve for controlling a compressor applied to, for example, a vehicle air conditioning system.

[0002]

2. Description of the Related Art As a compressor of this type, there is a variable displacement compressor capable of changing a discharge capacity. For example, the housing is fixedly joined to a cylinder block, and a crank chamber is defined and formed inside the housing so as to be surrounded by the two. The drive shaft is disposed in the crank chamber, and is rotatably supported by the housing and the cylinder block. The cylinder bore is formed through the cylinder block, and the piston is housed in the cylinder bore. The swash plate is integrally and rotatably mounted on the drive shaft in the crank chamber, and is swung back and forth in the axial direction by rotation of the drive shaft. The piston is connected to the swash plate, so that the piston is reciprocated by the rotation of the drive shaft to compress the refrigerant gas.

[0003] The crank chamber communicates with a suction pressure region through a bleed passage. The crank chamber is communicated with a discharge pressure region via an air supply passage. The capacity control valve formed of an electromagnetic valve is interposed in at least one of the bleed passage and the supply passage. Then, the drive circuit is operated under the control of the control computer based on the cooling load and the like, and the solenoid of the displacement control valve is excited and demagnetized. Therefore, the valve body of the same capacity control valve is operated, and at least one of the bleed passage and the supply passage is opened and closed, so that at least the amount of refrigerant gas discharged into the crank chamber and the amount of refrigerant gas discharged from the crank chamber are reduced. One is adjusted. As a result, the difference between the pressure in the crank chamber and the pressure in the cylinder bore via the piston is changed, the inclination angle of the swash plate is changed, and the discharge capacity is changed.

FIGS. 9 and 10 show a coil unit 112 of the solenoid. That is, the bobbin 113 made of insulating synthetic resin has a cylindrical shape,
A coil 114 is wound around the outer periphery of the. The terminal base 115 is integrally formed at the edge of the bobbin 113 so as to extend therefrom. Power supply terminal 116 which is a conductor
The ground terminal 117 is connected to the terminal base 11.
5 fixedly supported. Power supply terminal 1 of coil 114
The power supply terminal 14a is connected to a power supply side terminal 116, and is connected to a power supply line of a drive circuit (not shown) via the power supply side terminal 116. Ground side terminal 11 of coil 114
4b is connected to the ground terminal 117 and is grounded via the ground terminal 117. The cathode fixing piece 116a is provided on the power supply side terminal 116, and the anode fixing piece 117a is provided on the ground side terminal 117, respectively.

The diode 119 has a cathode terminal 119a fixed to the cathode fixing piece 116a and an anode terminal 119b fixed to the anode fixing piece 117a by soldering (solder part 121). Therefore, the diode 119 is connected to both terminals 116 and 11.
7, and is connected to the coil 114 to form a flywheel circuit with respect to the coil 114. That is, for example, the coil 114 generates a back electromotive force based on the self-inductance by demagnetizing the solenoid from the excited state (the ground side is stepped up). However, the excessive current based on the back electromotive force is consumed via the flywheel circuit. Therefore, the current does not flow to the drive circuit side, and it is possible to prevent an excessive electric load from being applied to the drive circuit.

The insulating coating 120 is formed by placing an insulating synthetic resin on the outer surface of the coil unit 112.
Coil 114, terminals 116 and 117, fixing piece 11
6a, 117a, diode 119, etc.
Buried in 20. The insulating coating 120 improves the weather resistance and insulation of these electric components buried therein.

[0007]

However, the terminal base 115 and the insulating coating 120 are made of a synthetic resin having a large expansion coefficient, and connect the cathode fixing piece 116a and the anode fixing piece 117a. The terminal base 115 and the insulating coating 120 tend to expand due to operating heat generated by the solenoid. Therefore, both fixing pieces 116a,
The interval of 117a is about to widen. In addition, the terminal base 115 and the insulating coating 120 tend to contract due to a decrease in outside air temperature or the like. Therefore, both fixing pieces 116a, 1
The interval of 17a is about to be reduced.

However, in the diode 119, both terminals 119a and 119b occupying most of the entire length direction are made of a metal having a lower expansion coefficient than synthetic resin, and the entire length is hardly changed by a temperature change. That is, both fixing pieces 116a and 117a are in a state of being restrained by the diode 119. As a result, thermal stress is generated in the terminal base 115 and the insulating coating 120, and both fixing pieces 1
16a and 117a, there is a possibility that the soldered portion 121, which is weak in strength, will eventually be fatigued and destroyed, resulting in poor conduction.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems in the prior art, and has as its object to reduce thermal stress applied to a fixed portion between an electric element terminal and an element fixing piece. It is to provide a possible compressor control valve.

[0010]

According to one aspect of the present invention, there is provided a control valve for controlling a compressor by operating a valve body by exciting and demagnetizing a solenoid, wherein the control valve comprises a pair of conductors. At least one of the terminals is connected to a terminal of a coil constituting a solenoid, and each terminal is provided with an element fixing piece for connecting an electric element to the coil. One terminal extending from the element main body of the electric element is connected to the element fixing piece of one terminal, and the other terminal extending from the element main body is also connected to the element fixing piece of the other terminal. It is fixed, and an elastic part is formed by bending at least one of the terminals in the middle, and the electric element changes the distance between the two element fixing pieces by the expansion and contraction of the elastic part. A configuration the control valve to allow contents.

According to the second aspect of the present invention, the two element fixing pieces are opposed to each other, and the element body is arranged in a space surrounded by the two element fixing pieces. In the invention according to claim 3, the spacer is a terminal base for fixedly supporting both terminals.

In the invention according to claim 4, the coil is wound around a bobbin made of an insulating synthetic resin, and the terminal base is formed integrally with the bobbin. According to the fifth aspect of the present invention, the spacer is an insulating coating that fills both element fixing pieces.

According to a sixth aspect of the present invention, the pair of terminals includes a power supply terminal to which a power supply terminal of the coil is connected, and a ground terminal to which a ground terminal of the coil is connected. Is a component of a flywheel circuit for the coil.

According to a seventh aspect of the present invention, in the compressor, a crank chamber and a control pressure chamber are formed inside the housing, the drive shaft is rotatably supported, and a cylinder bore is formed in a cylinder block constituting a part of the housing. A piston is reciprocally housed in the cylinder bore, a cam plate is inserted into the drive shaft so as to be able to rotate integrally and tiltably, and the pressure in the control chamber is changed to change the pressure in the crank chamber and the cylinder bore. The control according to any one of claims 1 to 6, wherein the displacement is controlled by changing a difference between the pressure and the pressure via the piston and changing the inclination angle of the cam plate according to the difference. The valve is interposed in at least one of a bleed passage that communicates the control pressure chamber with the suction pressure region and a supply passage that communicates the control pressure chamber with the discharge pressure region. A displacement control valve to change the pressure in the control chamber by adjusting the opening degree of the passage by operating the valve body.

(Function) In the first aspect of the present invention, the spacer made of a synthetic resin tends to expand or contract due to a change in temperature around the spacer, and the distance between the two element fixing pieces connected by the spacer changes. try to. However, the two element fixing pieces are also connected by an electric element that does not expand or contract as much as the spacer, so that thermal stress is generated in the spacer. However, the electric element has an elastic part in the middle of the terminal, and the elastic part expands and contracts when thermal stress acts on both element fixing pieces. Therefore, the total length of the electric element is changed, and a change in the distance between the two element fixing pieces is allowed. As a result, the thermal stress generated in the spacer is reduced, and the load applied to the fixed portion between the terminal of the electric element and the element fixing piece is reduced.

According to the second aspect of the present invention, the element body is housed in the housing space. Therefore, an effect of protecting the element body by the element fixing piece can be expected. For example, at the time of assembling the control valve, other members may interfere with the element body,
An operator or a tool can be prevented from touching the element body.

According to the third aspect of the present invention, when the terminal base tries to expand or contract due to a change in ambient temperature, the arrangement interval between the two terminals on the terminal base tends to change, and the two element fixing members provided on the terminal are fixed. The spacing between the pieces is about to change.

According to the fourth aspect of the present invention, the terminal base is formed integrally with the bobbin. Therefore, the coil,
The terminal, the element fixing piece, and the electric element are unitized, so that they can be easily handled, for example, when assembling the control valve.

In the fifth aspect of the present invention, the insulating coating tends to expand or contract due to a change in ambient temperature, and the distance between the two element fixing pieces connected by the insulating coating tends to change. In the invention according to claim 6, for example, when the solenoid in the excited state is demagnetized, a back electromotive force is generated in the coil of the solenoid based on the self inductance. However, since the electric element is connected to the coil to form a flywheel circuit, the current due to the back electromotive force is consumed via the flywheel circuit. Therefore, the current does not flow into the drive circuit that controls the energization of the coil.

In the seventh aspect of the present invention, the opening of at least one of the bleed passage and the supply passage is adjusted by operating the valve body by exciting and demagnetizing the solenoid, and the pressure of the control pressure chamber is changed. Therefore, the difference between the pressure in the crank chamber and the pressure in the cylinder bore via the piston is changed, and the inclination of the cam plate is changed in accordance with the difference to control the displacement.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the control valve of the present invention is embodied in a displacement control valve of a clutchless type variable displacement compressor will be described below.

As shown in FIG. 1, the front housing 1
1 is fixedly joined to the front end of the cylinder block 12. The rear housing 13 is fixedly joined to the rear end of the cylinder block 12 via a valve forming body 14. The crank chamber 15 as a control pressure chamber is
And a cylinder block 12. The drive shaft 16 is rotatably supported between the front housing 11 and the cylinder block 12 so as to pass through the crank chamber 15. The pulley 17 is supported on the front housing 11 via an angular bearing 18. The pulley 17 is connected to a protruding end of the drive shaft 16 from the front housing 11, and is connected to a vehicle engine 20 as an external drive source via a belt 19 wrapped around the outer periphery of the pulley 17. They are directly connected without going through the clutch mechanism.

The rotary support 22 is fixed to the drive shaft 16 in the crank chamber 15. The swash plate 23 as a cam plate is supported so as to be slidable and tiltable with respect to the drive shaft 16 in the direction of the axis L thereof. The support arm 24 protrudes from the rotary support 22, and has a guide hole 25 a provided on a swash plate 23.
Is engaged with the spherical portion 25a. And the swash plate 23
Is linked by the support arm 24 and the guide pin 25,
The drive shaft 16 can be tilted in the direction of the axis L of the drive shaft 16 and
And can be rotated integrally. The tilt of the swash plate 23 is guided by a slide guide relationship between the guide hole 24a and the spherical portion 25a and a slide support operation of the drive shaft 16. When the radial center of the swash plate 23 is moved toward the cylinder block 12, the inclination angle of the swash plate 23 is reduced. The inclination reduction spring 26 is interposed between the rotary support 22 and the swash plate 23. The tilt-angle reducing spring 26 urges the swash plate 23 in the direction of decreasing the tilt angle. The inclination restricting projection 22a is formed on the rear surface of the rotary support 22, and regulates the maximum inclination of the swash plate 23.

As shown in FIG. 2, the housing hole 27 is provided in the center of the cylinder block 12 in the direction of the axis L of the drive shaft 16. The blocking body 28 has a cylindrical shape and is slidably housed in the housing hole 27. The suction passage opening spring 29 is interposed between the end surface of the housing hole 27 and the blocking body 28 and urges the blocking body 28 toward the swash plate 23.

The drive shaft 16 is inserted into the inside of the blocking member 28 with its rear end. Radial bearing 3
Numeral 0 is interposed between the rear end of the drive shaft 16 and the inner peripheral surface of the blocking body 28, and is slidable with the blocking body 28 in the direction of the axis L with respect to the drive shaft 16. As described above, the rear end of the drive shaft 16 is rotatably supported on the inner peripheral surface of the housing hole 27 via the radial bearing 30 and the blocking body 28.

The suction passage 32 constituting the suction pressure region is formed at the center of the rear housing 13 and the valve forming body 14. The suction passage 32 communicates with the housing hole 27, and a positioning surface 33 is formed around an opening that appears on the front surface of the valve forming body 14. The blocking surface 34 is the blocking body 2
8 and is moved toward and away from the positioning surface 33 by the movement of the blocking body 28. The blocking surface 34 is the positioning surface 3
The contact between the suction passage 32 and the inner space of the housing hole 27 is interrupted by the sealing action between the two.

The thrust bearing 35 is interposed between the swash plate 23 and the blocking body 28 and is supported on the drive shaft 16 so as to be slidable. The thrust bearing 35 is
It is urged by the suction passage opening spring 29 and is always held between the swash plate 23 and the blocking body 28.

As the swash plate 23 tilts toward the blocking body 28, the tilt of the swash plate 23 causes the thrust bearing 3 to rotate.
5 to the interrupter 28. Accordingly, the blocking body 28 is moved toward the positioning surface 33 against the urging force of the suction passage opening spring 29, and the blocking body 28 contacts the positioning surface 33 with the blocking surface 34. In a state where the blocking surface 34 is in contact with the positioning surface 33, further tilting of the swash plate 23 is restricted, and in this restricted state, the swash plate 23
The minimum inclination angle is slightly larger than 0 °.

The cylinder bore 12a is the cylinder block 1.
2, a single-headed piston 36 is accommodated in the cylinder bore 12a. The piston 36 is moored to the outer peripheral portion of the swash plate 23 via a shoe 37,
The swash plate 23 is reciprocated back and forth within the cylinder bore 12a by the rotational movement of the swash plate 23.

The suction chamber 38 forming the suction pressure area and the discharge chamber 39 forming the discharge pressure area are formed in the rear housing 13 respectively. A suction port 40, a suction valve 41 for opening and closing the suction port 40, a discharge port 42, and a discharge valve 43 for opening and closing the discharge port 42 are formed in the valve body 14. Then, the refrigerant gas in the suction chamber 38 is supplied to the suction port 40 by the reciprocating operation of the piston 36.
And, it is sucked into the cylinder bore 12a via the suction valve 41. The refrigerant gas sucked into the cylinder bore 12 a is compressed to a predetermined pressure by the forward movement of the piston 36, and then is discharged through the discharge port 42 and the discharge valve 43.
9 is discharged.

The suction chamber 38 communicates with the accommodation hole 27 through the opening 45.
Is communicated to. Then, the blocking body 28 has its blocking surface 3
When the abutment 4 contacts the positioning surface 33, the opening 45 is shut off from the suction passage 32. The passage 46 is formed in the axis of the drive shaft 16 and communicates the crank chamber 15 with the inner space of the blocking body 28. The pressure release passage 47 penetrates through the peripheral surface of the blocking body 28, and the internal space of the blocker 28 and the internal space of the housing hole 27 are communicated via the pressure release port 47. The inner space of the housing hole 27, the passage 45, the passage 46, and the pressure release passage 47 constitute a bleed passage.

The supply passage 48 is provided between the discharge chamber 39 and the crank chamber 1.
5, and a capacity control valve 49 is interposed on the passage 48. The pressure detection passage 50 is formed between the suction passage 32 and the capacity control valve 49.

The displacement control valve 49 includes a valve housing 51
And the solenoid 52 are joined near the center. The valve chamber 53 includes the valve housing 51 and the solenoid 5.
2 is formed between them. The valve element 54 is housed in the valve chamber 53. The valve hole 55 is formed on the axis of the valve housing 51 in the valve chamber 53, and is opened to face the valve element 54. The forcible opening spring 56 is interposed between the valve body 54 and the inner wall of the valve chamber 53 and urges the valve body 54 in a direction to open the valve hole 55. The valve chamber 53 communicates with the discharge chamber 39 via a valve chamber port 57 and an air supply passage 48.

The pressure-sensitive chamber 58 is defined in the upper part of the valve housing 51. The pressure sensing chamber 58 communicates with the suction passage 32 via a suction pressure introduction port 59 and a pressure detection passage 50. Bellows 60 is housed in pressure-sensitive chamber 58. The pressure-sensitive rod insertion hole 61 is formed between the pressure-sensitive chamber 58 and the valve chamber 53 and is continuous with the valve hole 55. The pressure-sensitive rod 62 is slidably inserted into the pressure-sensitive rod insertion hole 61. The valve body 54 and the bellows 60 are operatively connected by a pressure-sensitive rod 62. The portion of the pressure-sensitive rod 62 on the valve element 54 side has a small diameter in order to secure a passage for the refrigerant gas in the valve hole 55.

The port 63 is formed between the valve chamber 53 and the pressure sensing chamber 58 in the valve housing 51 and has a valve hole 55.
And orthogonal. The port 63 communicates with the crank chamber 15 via an air supply passage 48. That is, the valve chamber port 57, the valve chamber 53, the valve hole 55, and the port 63 form a part of the air supply passage.

The solenoid 52 has a substantially closed cylindrical solenoid casing 71 and a substantially bottomed cylindrical housing cylinder 72. The fixed core 64 is fitted into the upper opening of the housing cylinder 72, and the fixed core 64 is
An accommodation chamber 65 is formed therein. The movable iron core 67 has a closed cylindrical shape, and is accommodated in the accommodation room 65 so as to be able to reciprocate. The follower spring 68 is interposed between the movable iron core 67 and the bottom surface of the housing cylinder 72. The follow-up spring 68
The spring having a smaller elastic coefficient than the forcible release spring 56 is used.

The solenoid rod insertion hole 69 is provided in the fixed iron core 6.
4 and communicates between the accommodation chamber 65 and the valve chamber 53. The solenoid rod 70 is formed integrally with the valve body 54 and is slidably inserted into the solenoid rod insertion hole 69. The end of the solenoid rod 70 on the movable iron core 67 side is brought into contact with the movable iron core 67 by the urging force of the forcible opening spring 56 and the follower spring 68. The movable iron core 67 and the valve element 54 are operatively connected via a solenoid rod 70.

FIG. 4 is an enlarged sectional view of a main part of the displacement control valve 49, and FIGS. 5 and 6 show a coil unit 90 of the solenoid 52. The cylindrical bobbin 91 made of insulating synthetic resin is accommodated in the housing cylinder 7 in the solenoid casing 71.
2 is fitted over the outer circumference of the fixed iron core 64 and the movable iron core 67. The coil 92 is wound around the outer periphery of the bobbin 91. A plate-like terminal base 93 as a spacer is integrally formed at the edge of the bobbin 91 so as to extend therefrom. Power supply terminal 9 made of metal as conductor
The terminal 4 and the ground terminal 95 have a plate shape and are fixedly supported by a terminal base 93, respectively. Coil 92
The power supply side terminal 92a is connected to the power supply side terminal 94 via the fusing 94a. The ground terminal 92b of the coil 92 is connected to the ground terminal 95 via the fusing 95a. Although not described in detail, the ground terminal 95 is connected to the rear housing 13 via the valve housing 51 and the bracket 66, and grounds the ground terminal 92b of the coil 92.

The connector pin fixing pieces 96 and the cathode fixing pieces 97 as element fixing pieces are formed by cutting and raising a part of the power supply terminal 94 into a rectangular shape. The anode fixing piece 98 as the element fixing piece is formed by cutting and raising a part of the ground terminal 95 into a rectangular shape. The cathode fixing piece 97 and the anode fixing piece 98 are arranged with the plate surfaces 97a, 98a facing each other. Therefore, the accommodation space 103 is formed so as to be surrounded by the plate surfaces 97a and 98a of the fixing pieces 97 and 98.

The base end of the connector pin 99 is fixed to the connector pin fixing piece 96 by known soldering. Diode 100 as an electric element
Includes a diode body 100a as an element body, and a metal cathode-side terminal 104 and an anode-side terminal 105 taken out of the diode body 100a. In the diode 100, the diode main body 100a is disposed in the accommodation space 103 described above, and the cathode terminal 104 is soldered to the tip of the cathode fixing piece 97, and the anode terminal 105 is soldered to the tip of the anode fixing piece 98, respectively. Fixed (soldering part 1
01). Therefore, the diode 100 is connected to both terminals 9.
4, 95, and is connected to the coil 92.
Constitute a flywheel circuit.

The insulating coating 102 as a spacer is formed of an insulating synthetic resin laid on the outer surface of the coil unit 90. Coil 92, terminals 94 and 95, fixing piece 9
6 to 98, the diode 100, and the like are buried in the insulating coating 102, and are in a so-called resin-buried state. The insulating coating 102 improves the insulation and weather resistance of these electric components. The socket 102a is integrally formed outside the insulating coating 102. The connector pin 99 has its tip protruding into the inner space of the socket 102a. Drive circuit 7
4 is connected to a vehicle battery or the like (not shown), and the power supply line 74a is connected to a power supply terminal 94 via a connector pin 99.

As shown in FIG. 7, the diode 100 has two terminals 104 and 105 which are wires.
The way from the diode body 100a to each of the fixing pieces 97 and 98 is bent in a crank shape, and the bent portions constitute the elastic portions 104a and 105a, respectively. Then, when a tensile force or a compressive force is applied to both terminals 104 and 105, the diode 100 expands and contracts the expandable portions 104a and 104a.
The overall length can be changed by actively deforming and expanding and contracting 5a.

Each of the elastic portions 104a and 105a has a linear shape from the side of the soldering portion 101 to the diode body 100.
Toward the side a, the fixing pieces 97 and 98 are bent toward the terminal base 93 along the extending direction of the fixing pieces 97 and 98. Therefore, the extension portions 104a, 105a are connected to both terminals 104, 1
05, the diode body 100a could be arranged in the housing space 103. In other words, based on the state of the prior art in FIGS. 9 and 10, how to prevent the diode main body 100 a from protruding from the housing space 103 while forming the expansion and contraction portions 104 a and 105 a on both terminals 104 and 105. In addition, it is necessary to bend the middle of both terminals 104 and 105 toward the terminal base 93 along the extending direction of the fixing pieces 97 and 98. By the way, another example shown in FIG. 8 (a), which will be described later, is an example in which the expansion and contraction portions 104a, 105a are formed on both terminals 104, 105, so that the diode main body 100a is shifted from the accommodation space 103 and protrudes.

The compressor having the above-described configuration includes the suction passage 32 serving as a passage for introducing the refrigerant gas into the suction chamber 38 and the discharge chamber 3.
An external refrigerant circuit 76 connects the discharge flange 75 for discharging the refrigerant gas from the refrigerant gas 9. The condenser 77, the expansion valve 78, and the evaporator 79 are interposed on the external refrigerant circuit 76. And, although not shown, the compressor having the above configuration,
The condenser 77, the expansion valve 78, and the evaporator 79 are mounted on a vehicle to construct a vehicle air conditioning system.

Evaporator temperature sensor 81, vehicle compartment temperature sensor 8
2, the air conditioner switch 83, the cabin temperature setting device 84 and the drive circuit 74 are connected to a control computer 85. Then, the control computer 85 controls each sensor 8
1, 82, the air conditioner switch 83
The duty ratio (the ratio of the excitation time of the solenoid 52 to the unit time) is determined based on the OFF signal, the input value of the set temperature signal from the vehicle interior temperature setting device 84, and the like, and the duty ratio is instructed to the drive circuit 74. The drive circuit 74 controls the energization amount of the coil 92 based on the commanded duty ratio to excite and demagnetize the solenoid 52. The larger the duty ratio is, the more the solenoid 52 has both iron cores 64 and 67.
Increase the suction force between them.

Next, the operation of the compressor having the above configuration will be described. The control computer 85 includes the air conditioner switch 8
If the detected value of the compartment temperature sensor 82 is equal to or higher than the set temperature of the compartment temperature setter 84 while the switch 3 is in the ON state, the solenoid 52 is excited (the duty ratio ≠
0%). Then, a current is supplied to the coil 92 of the solenoid 52 by the drive circuit 74, and as shown in FIG. 2, an attractive force corresponding to the duty ratio is generated between the two iron cores 64, 67. This suction force is applied to the forcible release spring 56.
Is transmitted to the valve body 54 via the solenoid rod 70 as a force in the direction in which the valve opening decreases. On the other hand, the bellows 60 is displaced in accordance with the fluctuation of the suction pressure introduced from the suction passage 32 into the pressure sensing chamber 58 via the pressure detection passage 50. The bellows 60 responds to the suction pressure when the solenoid 52 is excited, and its displacement is transmitted to the valve element 54 via the pressure-sensitive rod 62. The valve opening of the displacement control valve 49 is determined by the urging force from the solenoid 52 and the bellows 60.
And the biasing force of the forcible opening spring 56 are determined.

When the cooling load is large, for example, the difference between the compartment temperature detected by the compartment temperature sensor 82 and the temperature set by the compartment temperature setting device 84 is large. The control computer 85 changes the duty ratio so as to change the set suction pressure based on the vehicle interior temperature and the set temperature. The control computer 85 increases the duty ratio as the difference between the cabin temperature and the set temperature increases. Therefore, the attraction force between the fixed iron core 64 and the movable iron core 67 increases, and the urging force in the direction in which the valve opening of the valve body 54 decreases decreases. Then, the valve body 54 is opened and closed at a lower suction pressure. Therefore, the capacity control valve 49 is operated to maintain a lower suction pressure by increasing the duty ratio.

When the valve opening of the valve element 54 is reduced, the amount of refrigerant gas flowing from the discharge chamber 39 into the crank chamber 15 via the air supply passage 48 is reduced. On the other hand, the refrigerant gas in the crank chamber 15 flows out to the suction chamber 38 via the passage 46 and the pressure release port 47. For this reason, the crankcase 1
The pressure of 5 drops. Further, when the cooling load is large, the suction pressure of the cylinder bore 12a is high, and the crank chamber 1
5 and the suction pressure of the cylinder bore 12a are reduced. Therefore, the inclination angle of the swash plate 23 increases.

When the passage cross-sectional area in the air supply passage 48 is zero, that is, when the valve body 54 of the capacity control valve 49 completely closes the valve hole 55, the supply of the high-pressure refrigerant gas from the discharge chamber 39 to the crank chamber 15 is performed. Is not done. Then, the pressure in the crank chamber 15 becomes substantially the same as the pressure in the suction chamber 38, and the inclination angle of the swash plate 23 becomes maximum.

Conversely, when the cooling load is small, for example, the difference between the cabin temperature and the set temperature is small. The control computer 85 instructs the duty ratio to decrease as the vehicle interior temperature decreases. For this reason, the suction force between the fixed iron core 64 and the movable iron core 67 is weak, and the urging force in the direction in which the valve opening of the valve body 54 decreases is reduced. Then, the valve body 54 is opened and closed at a higher suction pressure. Therefore, the capacity control valve 49 operates to maintain a higher suction pressure by reducing the duty ratio.

When the valve opening of the valve body 54 increases, the amount of refrigerant gas flowing from the discharge chamber 39 into the crank chamber 15 increases, and the pressure in the crank chamber 15 increases. When the cooling load is small, the suction pressure of the cylinder bore 12a is low, and the difference between the pressure in the crank chamber 15 and the suction pressure of the cylinder bore 12a increases. Therefore, the inclination angle of the swash plate 23 becomes small.

As the cooling load is approached, the temperature in the evaporator 79 approaches the temperature at which frost occurs. When the evaporator temperature becomes equal to or lower than the frost determination temperature, the control computer 85 instructs the solenoid 52 to demagnetize (duty ratio = 0%). The frost determination temperature reflects a situation in which frost is likely to occur in the evaporator 79. Then, the solenoid 52 is connected to the drive circuit 74.
When the current supply to the coil 92 is stopped, the coil is demagnetized, and the attractive force between the fixed iron core 64 and the movable iron core 67 disappears. For this reason, as shown in FIG.
Due to the urging force of No. 6, it is moved downward against the urging force of the follower spring 68 acting via the movable iron core 67 and the solenoid rod 70. Then, the valve element 54 shifts to the valve opening position where the valve hole 55 is opened to the maximum. Therefore, a large amount of the high-pressure refrigerant gas in the discharge chamber 39 is supplied to the crank chamber 15 through the air supply passage 48, and the pressure in the crank chamber 15 increases.
The tilt angle of the swash plate 23 shifts to the minimum tilt angle due to the pressure increase in the crank chamber 15.

When the air conditioner switch 83 is turned off, the control computer 85 demagnetizes the solenoid 52, and accordingly the swash plate 23 is tilted to the minimum tilt angle.

As described above, the opening / closing operation of the capacity control valve 49 is changed according to the magnitude of the duty ratio for exciting and demagnetizing the solenoid 52. When the duty ratio increases, the opening and closing are performed at a low suction pressure, and when the duty ratio decreases, the opening and closing operation is performed at a high suction pressure. The compressor changes the inclination angle of the swash plate 23 to maintain the set suction pressure,
The discharge capacity is changed. That is, the capacity control valve 49 is
It has a role of changing the set suction pressure according to the duty ratio and a role of performing the minimum displacement operation regardless of the suction pressure. By providing such a capacity control valve 49,
The compressor is responsible for changing the refrigeration capacity of the refrigeration circuit.

When the inclination angle of the swash plate 23 is minimized, the blocking body 2
8 is in contact with the positioning surface 33 with its blocking surface 34,
The suction passage 32 is shut off. In this state, the suction passage 3
2, the passage cross-sectional area becomes zero, and the flow of the refrigerant gas from the external refrigerant circuit 76 into the suction chamber 38 is prevented. The minimum inclination angle of the swash plate 23 is set to be slightly larger than 0 °. This minimum inclination state is brought about when the blocking body 28 is arranged at the closed position where the communication between the suction passage 32 and the accommodation hole 27 is blocked. The blocking body 28 is switched between the closed position and the open position separated from the closed position in conjunction with the swash plate 23.

Since the minimum inclination angle of the swash plate 23 is not 0 °,
Even in the minimum inclination state, the refrigerant gas is discharged from the cylinder bore 12a to the discharge chamber 39. The refrigerant gas discharged from the cylinder bore 12 a into the discharge chamber 39 flows into the crank chamber 15 through the air supply passage 48. The refrigerant gas in the crank chamber 15 flows into the suction chamber 38 through the passage 46 and the pressure release passage 47. The refrigerant gas in the suction chamber 38 is sucked into the cylinder bore 12a and discharged again to the discharge chamber 39. That is, in the minimum inclination state, the discharge chamber 39, the air supply passage 48, the crank chamber 15,
6, a circulation passage passing through the pressure release port 47, the housing hole 27, the suction chamber 38 as a suction pressure area, and the cylinder bore 12a is formed in the compressor. A pressure difference occurs between the discharge chamber 39, the crank chamber 15, and the suction chamber 38.
Therefore, the refrigerant gas circulates through the circulation passage, and the lubricating oil flowing together with the refrigerant gas lubricates each sliding portion inside the compressor.

The present embodiment having the above configuration has the following effects. (1) The terminal base 93 and the insulating coating 102 are made of synthetic resin, and the cathode fixing piece 97 and the anode fixing piece 9
8 is connected. The terminal base 93 and the insulating coating 102 tend to expand due to the operating heat of the solenoid 52 and the like. Therefore, the space between the fixing pieces 97 and 98 tends to be widened. In addition, the terminal base 93 and the insulating coating 102 tend to contract due to a decrease in outside air temperature or the like.
Therefore, the space between the fixing pieces 97 and 98 tends to be reduced.
However, the fixing pieces 97 and 98 are also connected by the diode 100, and thermal stress occurs in the terminal base 93 and the insulating coating 102.

Here, the diode 100 has expansion and contraction portions 104a and 105a in the middle of the terminals 104 and 105, and as shown in FIG.
Is actively expanded and contracted by the thermal stress acting on both fixing pieces 97 and 98. Accordingly, the entire length of the diode 100 is changed, and the distance between the fixed pieces 97 and 98 can be changed.
As a result, the thermal stress acting on the fixing pieces 97 and 98 is reduced, and the load on the soldering portion 101 is reduced. In particular, it is possible to prevent the soldering portion 101 having low strength from being broken by fatigue. Therefore, it is possible to prevent the occurrence of conduction failure between the terminals 104 and 105 and the corresponding fixing pieces 97 and 98, and to improve the reliability of the flywheel circuit and the reliability of the capacity control valve 49.

(2) The extension portions 104a and 105a are formed by bending the terminals 104 and 105 halfway. That is, the expansion and contraction portions 104a and 105a are formed by processing a part of the configuration of the diode 100, and do not require a separate member from the diode 100. Therefore, the elastic portions 104a and 105a can be formed at low cost without increasing the number of parts.

(3) The diode body 100a is disposed in the housing space 103 formed by the fixing pieces 97 and 98. Therefore, the protection effect of the fixing pieces 97 and 98 can be expected. For example, when assembling the capacity control valve 49, other members may interfere with the diode body 100a,
An operator or a tool can be prevented from touching the diode body 100a. As a result, the diode body 10
0a can be prevented from being assembled in a damaged state,
The quality of the displacement control valve 49 is improved.

(4) The terminal base 93 is a bobbin 91
And the related configuration of the coil 92 (terminals 94 and 95, fixing pieces 96 to 98, connector pins 9).
9, a diode 100, etc.). Therefore, at the time of assembling the capacity control valve 49, handling of these electric components becomes easy, and assemblability is improved.

(5) The diode 100 is a solenoid 5
A flywheel circuit is configured for the two coils 92. Therefore, even if a back electromotive force is generated in the coil 92 due to the excitation / demagnetization of the solenoid 52, the current based on the back electromotive force is not consumed through the flyhole circuit and flows into the drive circuit 74 side. . As a result, the driving circuit 74
The driving circuit 74 and, consequently, the durability and reliability of the vehicle air conditioning system are improved.

(6) The diode 100 is an inexpensive element compared to other electric elements (transistors, resistors, etc.) that can form a flywheel circuit, and can form a flywheel circuit of the coil 92 at low cost. This leads to cost reduction of the compressor.

Note that the present invention is not limited to the above embodiment, and can be implemented, for example, in the following modes. (1) As shown in FIG.
Is bent along the direction perpendicular to the extending direction of the fixing pieces 97 and 98 to form the elastic portions 104a and 105a. By doing so, the diode body 100a
Height from the terminal base 93 is
a, 105a does not change compared to before the formation.
Therefore, even when the height of the fixing pieces 97, 98 is set lower than in the above-described embodiment in which the elastic portions 104a, 105a are bent toward the terminal base 93, the diode main body 1 is formed.
00a does not interfere with other electric parts and the like.

(2) If the positional relationship between the cathode fixing piece 97 and the anode fixing piece 98 is different from that of the above-described embodiment, the embodiment may be carried out in a manner as shown in FIGS. 8B and 8C. . (3) Connect the telescopic part 104a (105a) to the terminal 104 on one side.
Provided only in the middle of (105). (4) In the above embodiment, the flywheel circuit of the coil 92 is constituted by the diode 100. However, the present invention is not limited to this.
A flywheel circuit may be formed by connecting a diode such as an S (Metal Oxide Semiconductor) transistor to the coil 92 of the solenoid 52 by diode connection. That is, the electric element may be a transistor such as a bipolar transistor or a MOS transistor.

(5) In the above embodiment, the compressor is embodied to control the displacement by adjusting the amount of refrigerant gas discharged into the crank chamber 15. But,
The present invention is not limited to this, and may be embodied in a compressor that performs displacement control by adjusting the amount of refrigerant gas discharged from the crank chamber 15. Further, the present invention may be embodied in a compressor that performs capacity control by adjusting both the amount of refrigerant gas discharged into the crank chamber 15 and the amount of refrigerant gas discharged from the crank chamber 15 (6) The above embodiment. Has been embodied in a compressor that performs displacement control by adjusting the pressure of the crank chamber 15. However, it is not limited to this,
The present invention may be embodied in a compressor that performs capacity control by adjusting the pressure of the cylinder bore 12a.

(7) Implementation in a variable displacement compressor with a clutch. The control valve according to claim 6, wherein the electric element is a diode 100, when describing a technical idea that can be understood from the embodiment.

In this way, a flywheel circuit for the coil 92 can be formed at low cost.

[0069]

According to the first, third, fifth and seventh aspects of the present invention, it is possible to prevent the occurrence of a conduction failure between each terminal of the coil and the corresponding element fixing piece, and it is possible to prevent the control valve from being damaged. Reliability is improved.

According to the second aspect of the present invention, for example, at the time of assembling the control valve, the effect of protecting the element main body by the element fixing piece can be expected, and it is possible to prevent the element main body from being assembled in a damaged state. Therefore, the quality of the control valve is improved.

According to the fourth aspect of the present invention, the related configuration of the coil can be unitized, and the assemblability of the control valve is improved. According to the sixth aspect of the present invention, even if a back electromotive force is generated in the solenoid coil, the current caused by the back electromotive force is consumed via the flywheel circuit and does not flow into the drive circuit. Therefore, it is possible to prevent a malfunction from occurring in the drive circuit, which leads to an improvement in the durability and reliability of the drive circuit, and furthermore, the air conditioning system to which the compressor is applied.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a clutchless type variable displacement compressor.

FIG. 2 is an enlarged view of a main part of FIG. 1;

FIG. 3 is an enlarged view of a main part showing a minimum discharge capacity state.

FIG. 4 is an enlarged view of a main part of FIG. 2, with the insulating coating broken away.

FIG. 5 is a front view showing a solenoid coil unit of the displacement control valve.

FIG. 6 is a bottom view of the coil unit.

FIG. 7 is an enlarged view of a main part of FIG. 5, illustrating the operation of a telescopic unit.

8A to 8C are diagrams showing another example.

FIG. 9 is a front view showing a conventional solenoid coil unit.

FIG. 10 is a bottom view of the coil unit.

[Explanation of symbols]

49: capacity control valve as control valve, 52: solenoid,
54 ... valve element, 92 ... coil, 92a ... power supply side terminal, 92
b: ground terminal, 93: terminal base as spacer, 94: power supply terminal, 95: ground terminal, 97: cathode fixing piece as element fixing piece, 98 ...
Anode fixing piece as element fixing piece, 100... Diode as electric element, 102... Insulating coating as spacer, 104... Cathode terminal as terminal, 104 a.
Extendable part, 105... Anode terminal as terminal, 105
a ... elastic part.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Masahiro Kawaguchi 2-1-1, Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation (72) Inventor Ryo Matsubara 2-1-1, Toyota-cho, Kariya-shi, Aichi Prefecture Shares Inside Toyota Industries Corporation (72) Inventor Rinpo Nosaka 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside DENSO Corporation (72) Inventor Kazuhito Miyagawa 1-1-1, Showa-cho, Kariya-shi, Aichi Co., Ltd. Inside DENSO (72) Inventor Mutsumi Yoshino 1-1-1 Showa-cho, Kariya, Aichi Prefecture Inside DENSO Corporation

Claims (7)

[Claims] 1. A control valve for controlling a compressor by operating a valve body by exciting and demagnetizing a solenoid, wherein at least one of a pair of terminals, which are conductors, is connected to a terminal of a coil constituting the solenoid. Each terminal is provided with an element fixing piece for connecting an electric element to the coil, and both element fixing pieces are connected via a spacer made of insulating synthetic resin, and are connected to the element fixing piece of one terminal. Is fixed to one terminal extending from the element main body of the electric element, and the other terminal extending from the element main body is also fixed to the element fixing piece of the other terminal. Is formed, and the electric element is configured to allow a change in the distance between the two element fixing pieces by expansion and contraction of the expansion and contraction portion. 2. The control valve according to claim 1, wherein the two element fixing pieces are arranged to face each other, and the element body is arranged in a space surrounded by the two element fixing pieces. 3. The control valve according to claim 1, wherein the spacer is a terminal base fixedly supporting both terminals. 4. The control valve according to claim 3, wherein the coil is wound around a bobbin made of an insulating synthetic resin, and the terminal base is formed integrally with the bobbin. 5. The control valve according to claim 1, wherein the spacer is an insulating coating that fills both element fixing pieces. 6. The pair of terminals includes a power supply terminal to which a power supply terminal of a coil is connected, and a ground terminal to which a ground terminal of the coil is connected. The control valve according to any one of claims 1 to 5, which constitutes a flywheel circuit. 7. The compressor, wherein a crank chamber and a control pressure chamber are formed inside a housing, a drive shaft is rotatably supported, and a cylinder block is formed in a cylinder block constituting a part of the housing. Has a piston reciprocally housed, a cam plate is inserted into the drive shaft so as to be rotatable and tiltable, and the pressure in the control pressure chamber is changed to change the piston pressure between the crank chamber pressure and the cylinder bore pressure. And controlling the discharge capacity by changing the inclination angle of the cam plate according to the difference. The control valve according to claim 1, wherein The valve is operated by at least one of a bleed passage communicating the chamber with the suction pressure region and an air supply passage communicating the control pressure chamber with the discharge pressure region, and energizes and demagnetizes the solenoid. And in then adjusting the opening of the passage is a displacement control valve to change the pressure in the control pressure chamber.