JP3255018B2 - Clutchless variable displacement compressor and method of assembling the same - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutchless variable displacement compressor used in, for example, a vehicle air conditioner and a method of assembling the same.

[0002]

2. Description of the Related Art Generally, in a clutchless variable displacement compressor of this type, a control pressure chamber and a crank chamber are formed inside a housing of the entire compressor, and a drive shaft is rotatably supported. A plurality of cylinder bores are formed in a cylinder block constituting a part of the housing, and a housing hole is provided. A piston is reciprocally housed in each cylinder bore. A cam plate made of, for example, a swash plate is inserted into the drive shaft so as to be integrally rotatable and swingable. In the accommodation hole, a suction passage from the external refrigerant circuit to the suction pressure region is opened, and a shutoff that opens and closes the suction passage in conjunction with swinging of the swash plate is accommodated. In addition, a capacity control valve is provided in a communication path between at least one of the discharge pressure region and the suction pressure region and the control pressure chamber.

In this clutchless variable displacement compressor, the pressure in the control pressure chamber is changed based on the adjustment of the opening of the displacement control valve. This change in the pressure in the control pressure chamber changes the difference between the pressure in the crank chamber containing the swash plate and the pressure in the cylinder bore through the piston. Then, in accordance with the difference, the inclination angle of the swash plate is changed, and the discharge capacity is controlled.

In a conventional clutchless variable displacement compressor of this type, a receiving hole 112 is formed at the center of a cylinder block 111, for example, as shown in FIG. A large-diameter portion 112a is formed on the inner peripheral surface on the front end side of the accommodation hole 112, a small-diameter portion 112b is formed on the inner peripheral surface on the rear end side, and a step portion 112c is provided at the boundary therebetween. I have.

[0005] In the large diameter portion 112a of the accommodating hole 112, a cylindrical blocking body 1 for opening and closing the suction passage 113 is provided.
14 is slidably fitted and supported from the front end side of the cylinder block 111. Step 11 of accommodation hole 112
A spring 115 for opening the suction passage is provided between the block 2c and the blocking member 114.
The blocking member 114 is urged in the opening direction of the suction passage 113 by the spring 115.

[0006] A radial bearing 116 is fitted and disposed in the blocking body 114.
The rear end of the drive shaft 117 is slidably fitted into and supported by 6. A thrust bearing 119 is inserted into the drive shaft 117 so as to be located between the swash plate 118 on the drive shaft 117 and the front end of the blocking body 114.

[0007]

However, in this conventional clutchless variable displacement compressor, the large diameter portion 112 is formed on the inner peripheral surface of the housing hole 112 of the cylinder block 111.
a and a small-diameter portion 112b are formed, and a step portion 112c is provided at a boundary between them. For this reason, there is a problem that the processing of the housing hole 112 for the cylinder block 111 is troublesome, and the processing cost is increased.

In general, each component of the clutchless variable displacement compressor has a processing tolerance, and when these components are assembled, an assembly tolerance occurs. When such processing and assembly tolerances are concentrated, for example, the minimum discharge capacity varies among the compressors, and a compressor having a large minimum discharge capacity may cause a problem such as an increase in power loss. However, in the compressor having the conventional configuration, the large-diameter portion 112a is formed on the inner peripheral surface on the front end side of the housing hole 112, and the blocking body 114 can slide in the large-diameter portion 112a from the front end side of the cylinder block 111. It is fitted and supported. For this reason, in order to reduce the concentration of the processing tolerance and the assembly tolerance of each part, it is necessary to disassemble and replace the entire compressor even if it is necessary to detach and replace some parts inside the compressor, which is very troublesome. there were. In particular, even when it is desired to replace a component disposed behind the swash plate 118, it is necessary to disassemble and replace the component from the front end side of the cylinder block 111.
In other words, for example, when the blocking member 114 or the thrust bearing 119 is to be replaced, the small-diameter portion 112b on the inner peripheral surface on the rear end side of the housing hole 112 hinders the replacement of the blocking member 114.
And the thrust bearing 119 cannot be detached from the rear end side of the accommodation hole 112. As described above, there has been a problem that the work of detaching and replacing these parts is very troublesome and time-consuming.

The present invention has been made by paying attention to such problems existing in the prior art. A main object of the present invention is to provide a clutchless variable displacement compressor capable of easily and inexpensively forming an accommodation hole for accommodating a blocking body in a cylinder block, and an assembling method thereof.

A further object of the present invention is to provide a clutchless variable displacement compressor and a clutchless variable displacement compressor which can easily ease the concentration of the processing tolerance and the assembly tolerance of each part and can easily adjust the minimum inclination angle of the cam plate. It is to provide an assembling method.

[0011]

According to the first aspect of the present invention, a control pressure chamber and a crank chamber are formed inside a housing and a drive shaft is rotatably supported. A plurality of cylinder bores are formed in a cylinder block that constitutes a part of the housing, and accommodation holes are provided. A piston is reciprocally accommodated in the cylinder bore, and a cam plate is integrally rotatable and swingable with the drive shaft. And a housing for opening a suction passage from the external refrigerant circuit to the suction pressure region in the housing hole and opening and closing the suction passage in conjunction with swinging of the cam plate. A capacity control valve is provided in the communication path between at least one of the pressure control area and the suction pressure area and the control pressure chamber, and the control is performed based on adjustment of the opening degree of the capacity control valve. By changing the pressure in the chamber, the difference between the pressure in the crank chamber accommodating the cam plate and the pressure in the cylinder bore through the piston is changed, and the tilt angle of the cam plate is changed in accordance with the difference to discharge. In the clutchless variable displacement compressor configured to control the capacity, the inner peripheral surface of the receiving hole is formed to have substantially the same diameter, and the blocking body is provided in the receiving hole from the rear end side of the cylinder block. It is detachably fitted and supported.

According to a second aspect of the present invention, in the clutchless variable displacement compressor according to the first aspect, an annular groove is formed in a rear end inner periphery of the accommodation hole, and a spring receiver is attached to and detached from the annular groove. The rear end of the spring for urging the blocking body in the opening direction of the suction passage is hooked to the spring receiver.

According to a third aspect of the present invention, in the clutchless variable displacement compressor according to the first or second aspect, a thrust bearing is inserted on a drive shaft between the cam plate and the interrupter, and the thrust bearing is inserted. The minimum inclination angle of the cam plate is adjusted by changing the thickness of the bearing race.

According to a fourth aspect of the present invention, in the clutchless variable displacement compressor according to the first or second aspect, a thrust bearing is inserted on a drive shaft between the cam plate and the interrupter, and the thrust bearing is inserted. The minimum tilt angle of the cam plate is adjusted by changing the thickness of the spacer disposed adjacent to the bearing.

According to a fifth aspect of the present invention, in the clutchless variable displacement compressor according to the first or second aspect, the minimum inclination angle of the cam plate is adjusted by changing the length of the interrupter. It was done.

According to a sixth aspect of the present invention, there is provided the clutchless variable displacement compressor assembling method, wherein the drive shaft, the cam plate and the piston are assembled to the housing.
A thrust bearing, a blocking body, and a suction passage opening spring are detachably incorporated into the receiving hole from the rear end side of the cylinder block, and a spring receiver is attached to the rear end side of the cylinder block. The rear end is latched and held.

Therefore, in the clutchless variable displacement compressor according to the first aspect, when machining the accommodation hole in the cylinder block, it is necessary to form a large diameter portion, a small diameter portion and a step portion on the inner peripheral surface of the accommodation hole. And the inner peripheral surface can be formed to have substantially the same diameter. Therefore, the processing of the accommodation hole becomes easy, and the processing cost can be reduced.

Further, the blocker and its peripheral parts can be easily attached and detached from the rear end side of the housing hole with the rear end side of the cylinder block opened without disassembling the cylinder block from the front end side. For this reason, the components on the rear side of the cam plate can be detached and replaced, and the concentration of the tolerance can be easily adjusted, so that the work such as the adjustment of the minimum inclination angle of the cam plate can be performed in a short time.

In the clutchless variable displacement compressor according to the second aspect, a spring receiver is detachably fitted in the annular groove of the housing hole, and the rear end of the suction passage opening spring is engaged with the spring receiver. I have. For this reason, by fitting the spring receiver into the annular groove in a state where the blocking body and the suction passage opening spring are incorporated in the housing hole from the rear end side of the cylinder block,
They can be retained and retained in the receiving holes. Therefore, when the rear end side of the cylinder block is opened, for example, when the minimum inclination angle of the cam plate is adjusted, the suction passage opening spring does not protrude from the accommodation hole.

In the clutchless variable displacement compressor according to the third aspect, the minimum inclination angle of the cam plate is adjusted by changing the thickness of the race of the thrust bearing interposed between the cam plate and the interrupter. It is supposed to. For this reason, the minimum inclination angle of the cam plate can be adjusted with a simple structure without providing another component, and the number of components does not increase. That is, the minimum inclination angle of the cam plate can be easily adjusted only by detaching and replacing the race of the thrust bearing with one having an appropriate thickness.

In the clutchless variable displacement compressor according to the fourth aspect, the minimum inclination angle of the cam plate is adjusted by changing the thickness of the spacer disposed adjacent to the thrust bearing. For this reason, the minimum inclination angle of the cam plate can be easily adjusted by detaching and replacing only the spacer with one having an appropriate thickness regardless of the thrust bearing.

In the clutchless variable displacement compressor according to the fifth aspect, the minimum inclination angle of the cam plate is adjusted by changing the length of the interrupter housed in the housing hole. For this reason, the minimum inclination angle of the cam plate can be easily adjusted by detaching and replacing the blocking body with one having an appropriate length.

In the method for assembling a clutchless variable displacement compressor according to the sixth aspect, the thrust bearing and the blocking member are easily detached from the rear end of the cylinder hole with the rear end of the cylinder block opened. can do.
For this reason, by detaching and replacing these parts, it is possible to easily adjust the tolerance concentration of each part, and it is possible to perform work such as adjustment of the minimum inclination angle of the cam plate in a short time.

[0024]

BEST MODE FOR CARRYING OUT THE INVENTION

(First Embodiment) Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.

As shown in FIG. 1, a front housing 12 also forming a part of the housing is joined to a front end of a cylinder block 11 forming a part of the housing. A rear housing 13, which also forms a part of the housing, is joined and fixed to the rear end of the cylinder block 11 via a valve plate 14. The crank chamber 15 also serving as a control pressure chamber is formed between the front housing 12 and the cylinder block 11.

The drive shaft 16 is rotatably supported between the front housing 12 and the cylinder block 11. The front end of the drive shaft 16 protrudes from the crank chamber 15 to the outside, and a pulley 17 is fixed to the protruding end. The pulley 17 has a belt 18
, Is always operatively connected to a vehicle engine (not shown) serving as an external drive source. The pulley 17 is supported by the front housing 12 via an angular bearing 19. The axial load and the radial load acting on the pulley 17 are received by the front housing 12 via the angular bearing 19.

A lip seal 20 is interposed between the front end of the drive shaft 16 and the front housing 12. The lip seal 20 prevents pressure leakage in the crank chamber 15.

A rotary support 21 is fixed to the drive shaft 16 and the swash plate 2 as a cam plate is fixed.
2 is supported so as to be slidable and swingable in the axial direction of the drive shaft 16. A pair of guide pins 23 each having a spherical tip are fixed to the swash plate 22. A support arm 24 protrudes from the rotary support 21,
The support arm 24 has a pair of guide holes 25 formed therein. The guide pin 23 is slidably fitted in the guide hole 25.

The swash plate 22 can swing in the axial direction of the drive shaft 16 and can rotate integrally with the drive shaft 16 by the cooperation of the support arm 24 and the pair of guide pins 23. The swing of the swash plate 22 is guided by the slide guide relationship between the guide hole 25 and the guide pin 23 and the slide support action of the drive shaft 16. When the center of the radius of the swash plate 22 moves toward the cylinder block 11, the inclination angle of the swash plate 22 decreases. Also, the rotating support 21
On the rear surface, an inclination regulating protrusion 21a for regulating the maximum inclination of the swash plate 22 is formed.

The inclination reducing spring 26 is provided on the rotary support 21.
And the swash plate 22. The inclination reducing spring 26 causes the swash plate 22 to move the cylinder block 11.
It is urged toward the side to decrease the tilt angle.

In the center of the cylinder block 11, a housing hole 27 is provided in the axial direction of the drive shaft 16, and the inner peripheral surface thereof is formed to have substantially the same diameter over the entire length. A cylindrical blocking body 28 is slidably fitted and accommodated in the accommodation hole 27 from the rear end side of the cylinder block 11. The blocking body 28 includes a large diameter portion 28a and a small diameter portion 28.
b.

The drive shaft 16 is provided in the cylinder of the blocking body 28.
The rear end is inserted. A radial bearing 3 made of a needle bearing is provided on the inner peripheral surface of the large diameter portion 28a.
0 is inserted and supported. This radial bearing 30
Is prevented from falling out of the cylinder of the blocking body 28 by a circlip 31 attached to the inner peripheral surface of the large diameter portion 28a. The radial bearing 30 is provided on the drive shaft 1.
6 is slidably fitted to the rear end of the rear end. And
The rear end of the drive shaft 16 has a radial bearing 30
And, it is rotatably supported on the peripheral surface of the housing hole 27 via the blocking body 28.

An annular groove 27a is formed in the inner peripheral surface of the rear end of the accommodation hole 27.
A circlip 27b as a spring receiver is detachably fixed to the annular groove 27a. The intake passage opening spring 29 as a shaft supporting spring is
8 is interposed between the step between the large diameter portion 28a and the small diameter portion 28b and the circlip 27b. The elastic coefficient of the suction passage opening spring 29 is set to be smaller than the elastic coefficient of the inclination reducing spring 26.
The resultant of the biasing forces 6, 29 is a force in the rear direction of the compressor. The resultant of the urging forces of these springs 26 and 29 acts on the swash plate 22, a thrust bearing 34 and a blocking body 28 described later.

In the center of the rear housing 13, there is formed a suction passage 32 constituting a suction pressure region. The drive shaft 1 serving as a movement path of the blocking body 28
It is on the extension of 6. The suction passage 32 is opened at the rear end side of the accommodation hole 27, and a positioning surface 33 is formed around the opening of the suction passage 32 on the accommodation hole 27 side. The positioning surface 33 is on the valve plate 14. Blocker 28
The distal end surface of the small diameter portion 28b can contact the positioning surface 33. Then, the distal end face of the small diameter portion 28b is
By abutting on 3, the movement of the blocking body 28 toward the rear end side is restricted.

On the drive shaft 16 between the swash plate 22 and the blocking body 28, a thrust bearing 34 is slidably supported on the drive shaft 16. The rotation of the swash plate 22 depends on the presence of the thrust bearing 34.
8 is blocked. A single-head type piston 35 is accommodated in a plurality of cylinder bores 11 a penetrating through the cylinder block 11. The rotational movement of the swash plate 22 is converted into a reciprocating swing of each piston 35 via a pair of shoes 36, and as a result, the piston 35 is moved back and forth in the cylinder bore 11a.

In the rear housing 13, a suction chamber 37 forming a suction pressure region and a discharge chamber 3 forming a discharge pressure region are provided.
8 are sectioned. On the valve plate 14,
A suction port 39 and a discharge port 40 are formed corresponding to each cylinder bore 11a, and a suction valve 41 and a discharge valve 42 are formed so as to correspond to the suction port 39 and the discharge port 40. The refrigerant gas in the suction chamber 37 pushes back the suction valve 41 from the suction port 39 and flows into the cylinder bore 11 a by the reciprocating operation of the piston 35.
The refrigerant gas that has flowed into the cylinder bore 11 a is compressed by the forward movement of the piston 35 until a predetermined pressure is reached, and is then discharged from the discharge port 40 to the discharge chamber 38 by pushing the discharge valve 42. The opening of the discharge valve 42 is regulated by contacting the retainer 43.

Rotary support 21 and front housing 12
, A thrust bearing 44 is interposed. The thrust bearing 44 receives a compression reaction force acting on the rotary support 21 from the cylinder bore 11a via the piston 35, the shoe 36, the swash plate 22, and the guide pin 23.

The suction chamber 37 is connected to the accommodation hole 2 through the opening 45.
It communicates with 7. Then, the blocking body 28 is positioned on the positioning surface 3.
3, when the front end of the suction passage 32 is closed,
The opening 45 is shut off from the suction passage 32.

An axial passage 46 is formed in the drive shaft 16. An inlet 46a of the axial passage 46 opens into the crank chamber 15 near the lip seal 20, and an outlet 46b of the axial passage 46 opens into the cylinder of the shut-off body 28. A pressure release port 47 is provided through the peripheral surface of the blocking body 28. The pressure release port 47 is provided between the inside of the cylinder of the blocking body 28 and the accommodation hole 27.
And communicates.

The discharge chamber 38 and the crank chamber 15 are connected by an air supply passage 48 as a communication passage. A capacity control valve 49 for opening and closing the air supply passage 48 is provided in the middle of the air supply passage 48. Further, the suction passage 3
Between the pressure control valve 2 and the displacement control valve 49, a pressure detection passage 50 for guiding the suction pressure Ps into the displacement control valve 49 is formed.

The suction passage 32 serving as an inlet for introducing the refrigerant gas into the suction chamber 37 and the discharge flange 51 discharging the refrigerant gas from the discharge chamber 38 are connected by an external refrigerant circuit 52. In the external refrigerant circuit 52, a condenser 53, an expansion valve 54, and an evaporator 55 are interposed. The expansion valve 54 is composed of a temperature-type automatic expansion valve, and controls the flow rate of the refrigerant according to a change in the gas temperature at the outlet of the evaporator 55. A temperature sensor 56 is provided near the evaporator 55. The temperature sensor 56 detects the temperature in the evaporator 55, and the detected temperature information is sent to the control computer 57. Further, the control computer 57 is connected to a room temperature setting device 58, a room temperature sensor 59, an air conditioner operation switch 60, an engine speed sensor 61, and the like for designating a temperature in a vehicle compartment.

The control computer 57 includes, for example, a room temperature specified in advance by the room temperature setting device 58, a detected temperature obtained from the temperature sensor 56, a detected temperature obtained from the room temperature sensor 59, an on / off signal from the air conditioner operation switch 60, The input current value is commanded to the drive circuit 62 based on an external signal such as the engine speed obtained from the engine speed sensor 61. The drive circuit 62 outputs the commanded input current value to the solenoid 63 of the displacement control valve 49 described later.
Output to Other external signals include, for example, a signal from an outdoor temperature sensor, and the input current value is determined according to the environment of the vehicle.

The displacement control valve 49 is constructed by joining a valve housing 64 and a solenoid 65 near the center. A valve chamber 66 is defined between the valve housing 64 and the solenoid portion 65, and the valve chamber 66
The valve body 67 is accommodated therein. The valve body 6 has a valve body 6.
A valve hole 68 is opened so as to be opposed to. The valve hole 68 is formed to extend in the axial direction of the valve housing 64. A forced release spring 69 is interposed between the valve body 67 and the inner wall surface of the valve chamber 66,
In the opening direction of the valve hole 68. The valve chamber 66 communicates with a discharge chamber 38 in the rear housing 13 via a valve chamber port 70 and the air supply passage 48.

A pressure-sensitive chamber 71 is defined above the valve housing 64. The pressure sensing chamber 71 is connected to the suction passage 32 of the rear housing 13 via the suction pressure introduction port 72 and the pressure detection passage 50. Pressure sensing chamber 7
A bellows 73 is housed inside 1. A pressure-sensitive rod guide 74 that is continuous with the valve hole 68 is formed between the pressure-sensitive chamber 71 of the valve housing 64 and the valve chamber 66. The pressure-sensitive rod 75 is connected to the pressure-sensitive rod guide 7.
4 is slidably inserted into the inside. This pressure-sensitive rod 75
Thereby, the valve body 67 and the bellows 73 are operatively connected. The portion of the pressure sensing rod 75 on the side joined to the valve body 67 has a small diameter in order to secure a passage for the refrigerant gas in the valve hole 68.

A port 76 is formed in the valve housing 64 between the valve chamber 66 and the pressure sensing chamber 71 so as to be orthogonal to the valve hole 68. The port 76 is connected to the crank chamber 15 via the air supply passage 48. That is, the valve chamber port 70, the valve chamber 66, the valve hole 68, and the port 76 form a part of the air supply passage 48.

A fixed core 78 is fitted into the upper opening of the accommodation chamber 77 of the solenoid portion 65, and the fixed core 78
A solenoid chamber 79 is defined in the accommodation room 77 by the above. A movable iron core 80 having a substantially closed cylindrical shape is housed in the solenoid chamber 79 so as to be able to reciprocate. Movable iron core 80
A follow-up spring 81 is interposed between and the bottom of the storage chamber 77. The follower spring 81 has a smaller elastic coefficient than the forcible release spring 69.

The fixed iron core 78 has a solenoid chamber 79.
A solenoid rod guide 82 that communicates with the valve chamber 66 is formed. The solenoid rod 83 is connected to the valve 6
7 and the solenoid rod guide 82
It is slidably inserted in the inside. The end of the solenoid rod 83 on the movable iron core 80 side is
9 and the follower spring 81 are in contact with the movable iron core 80. The movable core 80 and the valve body 67 are operatively connected via a solenoid rod 83.

Outside the fixed iron core 78 and the movable iron core 80, a cylindrical solenoid 63 is disposed so as to straddle the two iron cores 78, 80. The solenoid 63 has a drive circuit 62 based on a command from the control computer 57.
Is supplied with a predetermined current.

Now, in the compressor of this embodiment,
A thrust bearing 34 interposed between the swash plate 22 and the blocking body 28 is constituted by a needle bearing having a plurality of needles 34c sandwiched between a front end race 34a and a rear end race 34b. . The rear end side race 34b of the thrust bearing 34 is
It is an adjusting member for adjusting the minimum inclination angle of. Several types of the rear end side races 34b having different plate thicknesses are prepared.

Further, the inner peripheral surface of the accommodation hole 27 for accommodating the blocking body 28 is formed to have substantially the same diameter. A thrust bearing 34, a blocking body 28, and a suction passage opening spring 29 are provided in the accommodation hole 27.
Is detachably assembled from the rear end side of the cylinder block 11, and is prevented from falling off by fitting a circlip 27b into the annular groove 27a.

With these configurations, when adjusting the minimum inclination angle of the swash plate 22 in assembling the compressor, first, the thrust bearing 34 is replaced with the rear end side race 34b.
The compressor is assembled using a measuring race having a predetermined plate thickness, and the stroke of the piston 35 is measured in this state. Then, based on the measurement result, a rear end side race 34b having a thickness corresponding to the predetermined minimum inclination angle of the swash plate 22 is selected, and the rear end side race 34b is detached and replaced with the measurement race.

At the time of removing and replacing the race, the circlip 27b is removed from the annular groove 27a of the receiving hole 27 with the front end side of the cylinder block 11 open and the rear end side opened without disassembling. In this state, the suction passage opening spring 29, the blocking body 28 and the rear end race 34 b of the thrust bearing 34 are detached from the rear end side of the cylinder lock 11 into the accommodation hole 27, and the rear end race 34 b Is exchanged.

Next, the operation of the thus constructed clutchless variable displacement compressor will be described. When the detected temperature obtained from the room temperature sensor 59 is equal to or higher than the temperature set by the room temperature setter 58 with the air conditioner operation switch 60 turned on, the control computer 57 commands the solenoid 63 to be excited. Then, a predetermined current is supplied to the solenoid 63 via the drive circuit 62, and as shown in FIGS. 1 and 2, an attraction force corresponding to the input current value is generated between the iron cores 78 and 80. This suction force is applied to the forcible release spring 6.
9 is transmitted to the valve body 67 via the solenoid rod 83 as a force in a direction in which the valve opening decreases in opposition to the urging force of No. 9. On the other hand, the bellows 73 is displaced in accordance with the fluctuation of the suction pressure Ps introduced from the suction passage 32 to the pressure sensing chamber 71 via the pressure detection passage 50. Then, when the solenoid 63 is excited, a displacement corresponding to the suction pressure Ps of the bellows 73 is transmitted to the valve body 67 via the pressure-sensitive rod 75.
Accordingly, the displacement control valve 49 is operated by the urging force from the solenoid 65, the urging force from the bellows 73, and the forcible release spring 69.
The valve opening is determined by the balance of the urging forces.

When the cooling load is large, for example, the difference between the temperature detected by the room temperature sensor 59 and the temperature set by the room temperature setting device 58 becomes large. The control computer 57
The input current value is controlled so as to change the set suction pressure based on the detected temperature and the set room temperature. That is, the control computer 57 instructs the drive circuit 62 to increase the input current value as the detected temperature increases. Therefore, the attraction force between the fixed iron core 78 and the movable iron core 80 is increased, and the urging force in the direction of reducing the valve opening of the valve body 67 is increased. Then, the valve body 67 is opened and closed at a lower suction pressure Ps. Accordingly, the capacity control valve 49 operates to maintain a lower suction pressure Ps by increasing the current value.

When the valve opening of the valve body 67 is reduced, the amount of refrigerant gas flowing from the discharge chamber 38 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 37 via the axial passage 46 and the pressure release port 47. Therefore, the pressure Pc in the crank chamber 15 decreases. When the cooling load is large, the pressure P in the cylinder bore 11a is also high, and the pressure Pc in the crank chamber 15 and the pressure in the cylinder bore 11a are large.
The difference from the internal pressure P becomes smaller. For this reason, the inclination angle of the swash plate 22 increases.

When the passage cross-sectional area in the air supply passage 48 is zero, that is, when the valve body 67 of the capacity control valve 49 completely closes the valve hole 68, the supply of the high-pressure refrigerant gas from the discharge chamber 38 to the crank chamber 15 is performed. Will not be performed. Then, the pressure Pc in the crank chamber 15 becomes substantially the same as the pressure Ps in the suction chamber 37, and the inclination angle of the swash plate 22 becomes maximum. Swash plate 22
Is regulated by the contact between the inclination regulating protrusion 21a of the rotary support 21 and the swash plate 22, and the discharge capacity becomes maximum.

Conversely, when the cooling load is small, for example, the temperature detected by the room temperature sensor 59 and the room temperature setting device 5
The difference from the set temperature of 8 becomes small. Control computer 5
7 instructs the drive circuit 62 to reduce the input current value as the detected temperature is lower. Therefore, the suction force between the fixed iron core 78 and the movable iron core 80 is weakened, and the urging force in the direction of reducing the valve opening of the valve body 67 is reduced. Then, the valve body 67 is opened and closed at a higher suction pressure Ps. Therefore, the capacity control valve 49 operates so as to maintain a higher suction pressure Ps by reducing the current value.

When the valve opening of the valve body 67 increases, the amount of refrigerant gas flowing from the discharge chamber 38 into the crank chamber 15 increases, and the pressure Pc in the crank chamber 15 increases. When the cooling load is small, the pressure P in the cylinder bore 11a is low, and the difference between the pressure Pc in the crank chamber 15 and the pressure P in the cylinder bore 11a increases. For this reason, the inclination angle of the swash plate 22 becomes small.

As the cooling load is approached, the temperature in the evaporator 55 decreases so as to approach the temperature at which frost occurs. When the temperature detected by the temperature sensor 56 becomes lower than the set temperature, the control computer 57 instructs the drive circuit 62 to demagnetize the solenoid 63. The set temperature reflects a situation in which frost is likely to occur in the evaporator 55. Then, the supply of the current to the solenoid 63 is stopped, the solenoid 63 is demagnetized, and the attractive force between the fixed core 78 and the movable core 80 disappears.

For this reason, as shown in FIG.
Is a follower spring 81 that acts via the movable iron core 80 and the solenoid rod 83 by the urging force of the forcible release spring 69.
Is moved downward against the urging force of And the valve body 67
Shifts to the valve opening position where the valve hole 68 is maximally opened. Therefore, a large amount of the high-pressure refrigerant gas in the discharge chamber 38 is supplied to the crank chamber 15 through the air supply passage 48, and the pressure Pc in the crank chamber 15 increases. Due to the pressure increase in the crank chamber 15, the inclination angle of the swash plate 22 shifts to the minimum inclination angle.

Further, based on the OFF signal of the air conditioner operation switch 60, the control computer 57 causes the solenoid 63 to operate.
, And the tilt angle of the swash plate 22 also shifts to the minimum tilt angle.

As described above, the opening / closing operation of the capacity control valve 49 changes according to the magnitude of the input current value to the solenoid 63. When the input current value increases, the switching operation is performed at a low suction pressure Ps, and when the input current value decreases, the opening and closing operation is performed at a high suction pressure Ps. The compressor changes the inclination of the swash plate 22 to maintain the set suction pressure Ps, and changes the discharge capacity. That is, the capacity control valve 49
Has a role of changing the set value of the suction pressure Ps by changing the input current value and a role of performing the minimum displacement operation regardless of the suction pressure Ps. By providing such a capacity control valve 49, the compressor plays a role of changing the refrigeration capacity of the refrigeration circuit.

As the swash plate 22 moves toward the blocking body 28, the swing of the swash plate 22 is transmitted to the blocking body 28 via the thrust bearing 34. By this swing transmission, the interrupter 2
8 is moved to the positioning surface 33 side against the urging force of the suction passage opening spring 29. Here, the blocking body 28 gradually reduces the passage cross-sectional area of the suction passage 32. The throttle action due to the slow change of the cross-sectional area gradually reduces the amount of refrigerant gas flowing from the suction passage 32 into the suction chamber 37. For this reason, the amount of the refrigerant gas sucked into the cylinder bore 11a from the suction chamber 37 also gradually decreases, and the discharge capacity gradually decreases. Therefore, the discharge pressure Pd gradually decreases, and the load torque in the compressor does not greatly change in a short time. As a result, the fluctuation of the load torque in the clutchless compressor during the transition from the maximum discharge capacity to the minimum discharge capacity becomes slow, and the impact due to the fluctuation of the load torque is reduced.

As shown in FIG. 3, when the inclination angle of the swash plate 22 is minimized, the blocking body 28 comes into contact with the positioning surface 33, and the suction passage 32 is blocked. In this state, the passage cross-sectional area in the suction passage 32 becomes zero, and the flow of the refrigerant gas from the external refrigerant circuit 52 into the suction chamber 37 is prevented. This swash plate 22
Is set to be a predetermined value slightly larger than 0 ° by adjusting the thickness of the rear end race 34b of the thrust bearing 34. In this minimum inclination state, the blocking body 28 is connected to the suction passage 32 and the accommodation hole 2.
7 when placed in a closed position that interrupts communication with 7. The blocking body 28 is switched between the closed position and the open position separated from the closed position in conjunction with the swing of the swash plate 22.

Since the minimum inclination angle of the swash plate 22 is not 0 °,
Even in the minimum tilt state, the refrigerant gas is discharged from the cylinder bore 11a to the discharge chamber 38. The refrigerant gas discharged from the cylinder bore 11a into the discharge chamber 38 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 37 through the shaft passage 46, the pressure release port 47, and the port 45. Inhalation chamber 37
Is sucked into the cylinder bore 11a,
It is discharged to the discharge chamber 38 again. That is, in the minimum tilt state, the discharge chamber 38, the air supply passage 48, the crank chamber 15, the axial passage 46, the pressure release passage 47,
7, a circulation passage passing through the communication port 45, the suction chamber 37 serving as a suction pressure region, and the cylinder bore 11a is formed in the compressor. A pressure difference occurs between the discharge chamber 38, the crank chamber 15, and the suction chamber 37. Therefore, the refrigerant gas circulates in the circulation passage, and the lubricating oil flowing together with the refrigerant gas lubricates each sliding portion in the compressor.

With the air conditioner operation switch 60 turned on and the swash plate 22 in the minimum inclination position, when the temperature in the passenger compartment rises and the cooling load increases, the room temperature sensor 59
Temperature exceeds the set temperature of the room temperature setter 58. The control computer 57 instructs the solenoid 63 to be excited based on the detected temperature change. By the excitation of the solenoid 63, the air supply passage 48 is closed, and the pressure Pc in the crank chamber 15 is reduced based on the pressure released through the shaft passage 46 and the pressure relief port 47. Due to this reduced pressure,
The suction passage opening spring 29 extends from the contracted state in FIG.
Then, the blocking body 28 is separated from the positioning surface 33, and the inclination angle of the swash plate 22 increases from the minimum inclination state in FIG.

With the separation of the blocking body 28, the suction passage 3
2, the passage cross-sectional area gradually increases, and the refrigerant gas inflow from the suction passage 32 to the suction chamber 37 gradually increases. Therefore, the amount of the refrigerant gas sucked into the cylinder bore 11a from the suction chamber 37 also gradually increases, and the discharge capacity gradually increases. Therefore, the discharge pressure Pd gradually increases, and the load torque in the compressor does not greatly change in a short time. As a result, the fluctuation of the load torque in the clutchless variable displacement compressor during the period from the minimum discharge capacity to the maximum discharge capacity becomes slow, and the impact due to the change in the load torque is reduced.

When the vehicle engine serving as the external drive source stops, the operation of the compressor also stops, that is, the rotation of the swash plate 22 also stops, and the power supply to the solenoid 63 of the displacement control valve 49 also stops. Therefore, the solenoid 63 is demagnetized, the air supply passage 48 is opened, and the inclination angle of the swash plate 22 is minimized.

When adjusting the minimum inclination angle of the swash plate 22 in this clutchless variable displacement compressor, a measuring race having a predetermined plate thickness is previously installed in place of the rear end race 34b of the thrust bearing 34. Leave. In this state, the stroke of the piston 35 is measured, and based on the measurement result, the rear end side race 34b having a thickness corresponding to the predetermined minimum inclination angle of the swash plate 22 is selected. Then, the rear end side race 34b of the selected plate thickness is detached and replaced with the measurement race.

At the time of removing and replacing the race, the circlip 27b is removed from the annular groove 27a of the housing hole 27 with the rear end opened without disassembling the front end of the cylinder block 11. At this time, since the inner peripheral surfaces of the housing holes 27 have substantially the same diameter, the cylinder lock 11
The suction passage opening spring 29, the blocking body 28, and the rear end race 34b of the thrust bearing 34 are detached from the rear end side into the accommodation hole 27, and the rear end race 34b can be easily replaced. .

According to the first embodiment configured as described above, the following effects are expected. (A) In this clutchless variable displacement compressor,
When the receiving hole 27 is formed in the cylinder block 11, it is not necessary to form a large diameter portion, a small diameter portion, and a step portion on the inner peripheral surface of the receiving hole 27, and the inner peripheral surface is formed to have substantially the same diameter. I just need. For this reason, the processing of the accommodation hole 27 becomes easy, and the processing cost can be reduced.

(B) In this clutchless variable displacement compressor, the inner peripheral surface of the housing hole 27 is formed to have substantially the same diameter. For this reason, the cylinder block 11
Without disassembling from the front end side of the cylinder block 11
The rear end race 3 of the suction passage opening spring 29, the blocking body 28 and the thrust bearing 34 is opened in a state where the rear end of the rear race 3 is opened.
4b can be detached from the accommodation hole 27 from the rear end side. Then, the thickness of the rear end side race 34b can be easily changed to an appropriate one, and the concentration of tolerance of each component of the compressor can be reduced. Therefore, adjustment of the minimum inclination angle of the swash plate 22 can be performed easily and in a short time.

(C) In this clutchless variable displacement compressor, a circlip 27b as a spring receiver is removably fitted in the annular groove 27a of the accommodation hole 27, and the suction passage opening spring 29 is fitted to the circlip 27b. The rear end is hooked. For this reason, by inserting the circlip 27b into the annular groove 27b from the rear end side of the cylinder block 11 in a state in which the blocking body 28 and the suction passage opening spring 29 are incorporated in the accommodation hole 27, these are inserted into the accommodation hole 27. 27 can be retained and retained. Therefore, when adjusting the minimum inclination angle of the swash plate 22, when the rear end side of the cylinder block 11 is opened, it is possible to prevent the suction passage opening spring 29 from jumping out of the accommodation hole 27. Then, workability at the time of adjusting the minimum inclination angle of the swash plate 22 can be improved.

(D) In this clutchless variable displacement compressor, the swash plate is changed by changing the thickness of the rear end side race 34b of the thrust bearing 34 interposed between the swash plate 22 and the interrupter 28. The minimum inclination angle 22 is adjusted. For this reason, it is possible to adjust the minimum inclination angle of the swash plate 22 with a simple structure without equipping other parts,
There is no increase in the number of parts. That is, the minimum inclination angle of the swash plate 22 can be easily adjusted only by detaching and replacing the rear end side race 34b of the thrust bearing 34 with one having an appropriate thickness.

By adjusting the minimum tilt angle of the swash plate 22, the minimum discharge capacity can be set within a predetermined range. For this reason, the minimum discharge capacity does not become larger than the predetermined range and the amount of work performed by the compressor at the time of the minimum capacity operation does not increase.

(Second Embodiment) Next, a second embodiment of the present invention will be described.
The second embodiment will be described focusing on the differences from the first embodiment.

In the clutchless variable displacement compressor according to the second embodiment, as shown in FIG.
A spacer 85 is interposed between the shaft 8 and the thrust bearing 34. The spacer 85 is configured to adjust the minimum tilt angle of the swash plate 22.

When adjusting the minimum inclination angle of the swash plate 22 in the compressor of the second embodiment, a spacer for measurement having a predetermined thickness is preliminarily installed in place of the spacer 85. In this state, the stroke of the piston 35 is measured, and based on the measurement result, a spacer 85 having a plate thickness suitable for the predetermined minimum inclination angle of the swash plate 22 is selected. Then, the spacer 85 having the selected thickness is detached and replaced with the measuring spacer.

At the time of removing and replacing the spacer, the cylinder block 11 is removed in the same manner as in the first embodiment.
Without disassembling the front end of the circlip 27, open the rear end of the circlip 27 through the annular groove 27a of the accommodation hole 27.
Remove b. At this time, since the inner peripheral surface of the housing hole 27 has substantially the same diameter, the suction passage opening spring 29, the blocking body 28, and the spacer 85 are detached from the rear end side of the cylinder lock 11 into the housing hole 27. And the spacer 85
Can be easily replaced.

According to the second embodiment configured as described above, the following effects are expected. (A) In the clutchless variable displacement compressor according to the second embodiment, similarly to the first embodiment, the inner peripheral surface of the housing hole 27 is formed to have substantially the same diameter. Then, the cylinder block 11 is accommodated in the accommodation hole 27.
From the rear end side, a blocking body 28, a suction passage opening spring 29, and the like are detachably incorporated. For this reason, the thickness of the spacer 85 arranged adjacent to the rear end side race 34b of the thrust bearing 34 can be easily changed to an appropriate one, and the tolerance concentration of each component of the compressor can be reduced. it can. Therefore, adjustment of the minimum inclination angle of the swash plate 22 can be performed easily and in a short time.

(B) Further, in the second embodiment, the minimum inclination angle of the swash plate 22 is adjusted by changing the thickness of the spacer 85 disposed adjacent to the rear end race 34b of the thrust bearing 34. It has become.
Therefore, regardless of the thrust bearing 34, only the spacer 85 is detached and replaced with a spacer having a predetermined thickness, whereby the minimum inclination angle of the swash plate 22 can be easily adjusted, and the minimum discharge capacity can be adjusted within a predetermined range. Can be set within. Therefore, similarly to the first embodiment, the work performed by the compressor during the minimum capacity operation does not increase, and deterioration of fuel efficiency due to an increase in power loss can be suppressed.

(Third Embodiment) Next, a third embodiment of the present invention will be described.
The second embodiment will be described focusing on the differences from the first embodiment.

In the clutchless variable displacement compressor according to the third embodiment, as shown in FIGS. 5 and 6, the crank chamber 15 forms a part of the suction passage. That is,
As shown in FIG. 5, the second suction passage 91 is formed in the cylinder block 11, and has a rear end communicating with the housing chamber 27 and a front end communicating with the crank chamber 15.
Refrigerant gas supplied from the suction passage 32 into the housing hole 27 flows through the second suction passage 91 into the crank chamber 1.
5 is introduced.

The introduction passage 92 is formed to penetrate between the crank chamber 15 and the suction chamber 37, and the refrigerant gas is introduced from the crank chamber 15 into the suction chamber 37 via the introduction passage 92. ing. In addition, the introduction passage 92
Is a shaft passage 46 formed at the center of the drive shaft 16.
And an adjustment passage 93 formed from the cylinder block 11 to the valve plate 14 and the rear housing 13. The axial passage 46 is provided at the front end entrance 4.
6a is opened into the crank chamber 15 near the lip seal 20, and an outlet 46b at the rear end is opened inside the shut-off body 28. The through hole 94 is formed on the outer periphery of the blocking body 28, and the inside of the blocking body 28 communicates with the adjustment passage 93 via the through hole 94.

The adjustment valve chamber 95 is formed in the introduction passage 92 in the middle of the adjustment passage 93, and has a tapered adjustment valve hole 96 formed at the front end thereof. Spool valve 97
Is movably accommodated in the regulating valve chamber 95. A tapered throttle valve portion 98 for adjusting the cross-sectional area of the passage of the adjustment valve hole 96 is formed at the front end of the spool valve 97 so as to face the adjustment valve hole 96. The spring 99 is interposed between the spool valve 97 and the front end of the adjustment valve chamber 95, and biases the spool valve 97 in a direction away from the adjustment valve hole 96 by the spring 99.

The pressure applying passage 100 as a communication passage connects the discharge chamber 38 to the regulating valve chamber 95 on the rear side of the spool valve 97.
It is formed in the rear housing 13 so as to communicate with the control pressure chamber 101 therein. The pressure release passage 102 is formed continuously with the rear housing 13, the valve plate 14, and the cylinder block 11 so that the control pressure chamber 101 on the back side of the spool valve 97 communicates with the crank chamber 15. The capacity control valve 49 is mounted on the rear housing 13 so as to be located in the middle of the pressure applying passage 100.

In the third embodiment, the radial bearing 30 for supporting the rear end of the drive shaft 16 is formed of a cylindrical plain bearing. Similarly, a thrust bearing 103 inserted into the drive shaft 16 between the swash plate 22 and the blocking body 28.
However, it is composed of a plain bearing composed of a pair of disk-shaped races 103a and 103b.

Further, in the third embodiment,
The minimum oblique angle of the swash plate 22 is adjusted by the blocking body 28. The minimum displacement is set within a predetermined range by adjusting the minimum inclination angle of the swash plate 22 by detaching and replacing the blocking body 28 with a predetermined length.

Further, in the third embodiment,
Unlike the first embodiment, the receiving hole 27 has an annular groove 27a.
Is not formed, and the circlip 27b is not fitted in the annular groove 27a. The valve plate 14 also serves as a spring receiver, and the cylinder block 1
When the rear housing 13 is attached to the rear end face of the housing 1 via the valve plate 14, the rear end of the suction passage opening spring 29 in the housing hole 27 is hooked and held by the valve plate 14.

Next, the operation of the thus constructed clutchless variable displacement compressor will be described. When the cooling load is large, as shown in FIG. 5, the input current to the solenoid 63 of the capacity control valve 49 is increased, the solenoid 63 is strongly excited, and the valve body 67 opens the valve hole 68. It is biased in a direction to decrease the degree. If the valve opening of the valve body 67 is reduced, the amount of refrigerant gas flowing from the discharge chamber 38 through the pressure applying passage 100 into the control pressure chamber 101 on the back side of the spool valve 97 is reduced. On the other hand, the refrigerant gas in the control pressure chamber 101 flows out to the crank chamber 15 via the pressure release passage 102.

For this reason, the pressure in the control pressure chamber 101 is reduced, the spool valve 97 is moved rearward, the throttle degree of the throttle valve section 98 is reduced, and the passage sectional area of the adjustment valve hole 96 is increased. Become. Then, the amount of refrigerant gas flowing from the crank chamber 15 into the suction chamber 37 via the introduction passage 92 increases in accordance with the degree of restriction of the throttle valve section 98, and the pressure in the suction chamber 37 is increased. For this reason, the pressure difference between the pressure Pc in the crank chamber 15 and the pressure P in the cylinder bore 11a opposed via the piston 35 becomes small, and the swash plate 22 is swung to the maximum tilt angle side.

In this state, the refrigerant gas supplied from the external refrigerant circuit 52 to the suction passage 32 is supplied to the storage hole 27 and the second
After being introduced into the crank chamber 15 through the suction passage 91, the axial passage 46 of the introduction passage 92, the inside of the blocking body 28,
It is introduced into the suction chamber 37 through the through hole 94 and the adjustment passage 93.

When the passage cross-sectional area of the pressure applying passage 100 is zero, that is, when the valve body 67 of the capacity control valve 49 completely closes the valve hole 68, the supply of the refrigerant gas from the discharge chamber 38 to the control pressure chamber 101 is performed. Will not be performed. Then, the pressure P in the cylinder bore 11a and the pressure Pc in the crank chamber 15 become substantially the same, the swash plate 22 is maintained at the maximum inclination state, and the discharge capacity becomes maximum.

In this state, the pressure application passage 100 is closed by closing the capacity control valve 49. For this reason, the high-pressure refrigerant gas discharged into the discharge chamber 38 is supplied to the crank chamber 1 through the pressure application passage 100 and the pressure release passage 102.
5 is supplied to the external refrigerant circuit 52 without being supplied.

Conversely, when the cooling load is small, as shown in FIG. 6, the input current to the solenoid 63 of the capacity control valve 49 is reduced, and the exciting force of the solenoid 63 is weakened. , The urging force in the direction of decreasing the valve opening decreases. If the valve opening of the valve body 67 increases, the discharge chamber 3
8 through the pressure applying passage 100, and the spool valve 97
The amount of the refrigerant gas flowing into the control pressure chamber 101 on the back side of the pressure chamber increases, and the pressure in the control pressure chamber 101 increases.

As a result, the spool valve 97 is arranged to move forward, the degree of throttle of the throttle valve section 98 increases, and the cross-sectional area of the passage of the adjustment valve hole 96 decreases. Then, the amount of refrigerant gas flowing from the crank chamber 15 into the suction chamber 37 via the introduction passage 92 decreases in accordance with the degree of restriction of the throttle valve section 98, and the pressure in the suction chamber 37 decreases. For this reason, the pressure difference between the pressure Pc in the crank chamber 15 and the pressure P in the cylinder bore 11a opposed via the piston 35 increases, and the swash plate 22 swings to the minimum tilt angle side.

When there is no cooling load, supply of current to the solenoid 63 of the capacity control valve 49 is stopped, and the solenoid 63 is demagnetized. For this reason, the urging force in the direction to decrease the valve opening of the valve body 67 is lost, and the capacity control valve 49 is opened at the maximum opening.

When the pressure applying passage 100 is fully opened, a large amount of the refrigerant gas in the discharge chamber 38 is supplied to the control pressure chamber 101 on the back side of the spool valve 97, and the pressure in the control pressure chamber 101 further increases. Thereby, the spool valve 97
Are moved to the forefront, the throttle degree of the throttle valve portion 98 is maximized, and the passage cross-sectional area of the adjustment valve hole 96 is minimized. Then, the pressure Pc of the crank chamber 15 and the cylinder bore 11a
The pressure difference between the internal pressure P and the internal pressure P further increases,
Is held at the minimum tilt position and the discharge capacity is minimized.

When the swash plate 22 is in the minimum inclination state, the suction passage 32 is shut off by the shutoff 28 as in the first embodiment. At this time, the discharge chamber 38, the pressure application passage 10
0, control pressure chamber 101, pressure release passage 102, crank chamber 1
5, the introduction passage 92, the suction chamber 37 and the cylinder bore 11a
A circulation passage is formed in the cooling medium, and the refrigerant gas and the lubricating oil are circulated through the circulation passage inside.

When adjusting the minimum inclination angle of the swash plate 22 in the compressor according to the third embodiment, a measuring length of a predetermined length is installed in place of the above-mentioned barrier 28 in advance. . In this state, the stroke of the piston 35 is measured, and based on the measurement result, the blocker 28 having a length adapted to the predetermined minimum inclination angle of the swash plate 22 is selected. Then, the blocking body 28 having the selected length is detached and replaced with the measuring blocking body.

At the time of detaching / replacement / replacement of the blocker, the cylinder block 1 is substantially similar to the case of the first embodiment described above.
1 without disassembling the front end side of the cylinder block 11.
Open the rear end of At this time, since the inner peripheral surface of the housing hole 27 has substantially the same diameter, the suction passage opening spring 29 is inserted into the housing hole 27 from the rear end side of the cylinder lock 11.
In addition, the blocking body 28 can be detached, and the blocking body 28 can be easily replaced.

According to the third embodiment configured as described above, the following effects are expected. (A) In the clutchless variable displacement compressor of the third embodiment, similarly to the first embodiment, the inner peripheral surface of the housing hole 27 is formed to have substantially the same diameter. Then, the cylinder block 11 is accommodated in the accommodation hole 27.
From the rear end side, a blocking body 28, a suction passage opening spring 29, and the like are detachably incorporated. For this reason, the length of the blocking body 28 can be easily changed to an appropriate length, and the concentration of the tolerance of each component of the compressor can be reduced. Therefore, adjustment of the minimum inclination angle of the swash plate 22 can be performed easily and in a short time.

(B) In the third embodiment, the swash plate 2 is changed by changing the length of the interrupter 28.
2, the minimum inclination angle is adjusted. For this reason,
Irrespective of the thrust bearing 34, the minimum inclination angle of the swash plate 22 can be easily adjusted by detaching and replacing only the blocker 28 with a predetermined length, so that the minimum discharge capacity is set within a predetermined range. can do. Therefore, similarly to the first embodiment, the work performed by the compressor during the minimum capacity operation does not increase, and deterioration of fuel efficiency due to an increase in power loss can be suppressed.

(C) In the third embodiment,
The valve plate 14 also serves as a spring receiver at the rear end of the suction passage opening spring 29. For this reason, the suction passage opening spring 29
It is not necessary to separately provide a spring receiver for latching and holding the rear end, and the number of components can be reduced.

The present invention can be embodied with the following modifications. (1) In the first embodiment, the minimum inclination angle of the swash plate 22 is adjusted by detaching and replacing the front end race 34a of the thrust bearing 34 with one having a predetermined thickness.

(2) In the first embodiment, both races 3 on the front end side and the rear end side of the thrust bearing 34 are used.
The minimum inclination angle of the swash plate 22 is adjusted by removing and replacing the 4a and 34b with those having a predetermined thickness.

(3) In the second embodiment, a spacer 85 is interposed between the swash plate 22 and the thrust bearing 34 adjacent to the front end side race 34a of the thrust bearing 34. Board 22
To adjust the minimum tilt angle of the camera.

(4) In the second embodiment, both races 3 on the front end side and the rear end side of the thrust bearing 34
A pair of spacers 85 are provided adjacent to 4a and 34b, and the spacers 58 adjust the minimum inclination angle of the swash plate 22.

(5) In the second embodiment, the minimum inclination angle of the swash plate 22 is adjusted by changing the number of spacers 85 disposed adjacent to the thrust bearing 34.

(6) In the third embodiment, the minimum inclination angle of the swash plate 22 is adjusted by changing the thickness of at least one of the races 103a and 103b of the thrust bearing 103 formed of a plain bearing. To be configured.

(7) In the third embodiment, the minimum inclination angle of the swash plate 22 is adjusted by changing the number of races 103a and 103b of the thrust bearing 103 composed of a plain bearing.

(8) As in the first embodiment, in the compressor provided with the radial bearing 30 and the thrust bearing 34, which are needle bearings, the third
As in the embodiment, the minimum inclination angle of the swash plate 22 is adjusted by changing the length of the blocking body 28.

(9) In each of the above embodiments, the radial bearing 30 is omitted, and the rear end of the drive shaft 16 is made of, for example, a self-lubricating shutoff body 28 made of synthetic resin.
To be directly rotatably fitted and supported.

With such a configuration, substantially the same effects as those of the above embodiments can be obtained.

[0115]

As described in detail above, the present invention has the following excellent effects. According to the first aspect of the present invention, when machining a housing hole for a blocking body in a cylinder block, it is not necessary to form a large-diameter portion, a small-diameter portion, and a step portion on an inner peripheral surface of the housing hole. What is necessary is just to form so that an inner peripheral surface may become substantially the same diameter. Therefore, the processing of the accommodation hole can be easily performed, and the processing cost can be reduced.

Further, with the rear end side of the cylinder block opened, the blocker and its peripheral parts can be easily attached and detached from the rear end side of the accommodation hole. Therefore, it is possible to easily adjust the tolerance concentration by detaching and replacing these parts, and it is possible to perform work such as adjustment of the minimum inclination angle of the cam plate in a short time.

According to the second aspect of the present invention, the spring receiver is fitted into the annular groove from the rear end side of the cylinder block in a state where the blocking body and the suction passage opening spring are incorporated in the receiving hole. , Can be retained in the receiving hole. Therefore, when the rear end side of the cylinder block is opened, for example, when the minimum inclination angle of the cam plate is adjusted, the suction passage opening spring does not protrude from the accommodation hole. Therefore, workability at the time of adjusting the minimum inclination angle of the cam plate can be improved.

According to the third aspect of the present invention, the minimum inclination angle of the cam plate can be adjusted with a simple structure without providing another component, and the number of components does not increase.
That is, the minimum inclination angle of the cam plate can be easily adjusted only by detaching and replacing the race of the thrust bearing with one having an appropriate thickness.

According to the fourth aspect of the present invention, the minimum tilt angle of the cam plate can be easily reduced by detaching and replacing only the spacer arranged adjacent to the thrust bearing with an appropriate thickness regardless of the thrust bearing. Can be adjusted.

According to the fifth aspect of the present invention, the minimum inclination angle of the cam plate can be easily adjusted by detaching and replacing the blocking member with one having an appropriate length. According to the invention as set forth in claim 6, the thrust bearing and the blocking body can be easily attached and detached from the rear end side in the accommodation hole with the rear end side of the cylinder block opened.
Therefore, the work for adjusting the minimum inclination of the cam plate can be performed in a short time by detaching and replacing these parts without disassembling the work for adjusting the minimum inclination of the cam plate from the front end side of the cylinder block. it can.

[Brief description of the drawings]

FIG. 1 is a sectional view of a compressor according to a first embodiment.

FIG. 2 is a partially enlarged cross-sectional view showing a maximum tilt state of the compressor of FIG.

FIG. 3 is a partially enlarged cross-sectional view showing the compressor of FIG. 1 in a minimum tilt state;

FIG. 4 is a partial cross-sectional view showing a compressor according to a second embodiment.

FIG. 5 is a cross-sectional view illustrating a maximum inclination state of the compressor according to the third embodiment.

FIG. 6 is a cross-sectional view illustrating the compressor of FIG. 5 in a minimum tilt state;

FIG. 7 is a partial sectional view of a conventional compressor.

[Explanation of symbols]

11 ... Cylinder block forming a part of housing
11a: Cylinder bore, 12: Front housing that forms part of the housing, 13: Rear housing that forms part of the housing, 14: Valve plate that also serves as a spring receiver in the third embodiment, 15: Control pressure chamber Crank chamber 16 serving also as a drive shaft, 22 swash plate as a cam plate, 27 receiving hole, 27a annular groove,
27b: a circlip as a spring receiver, 28: a blocking body, 29: a suction passage opening spring, 32: a suction passage constituting a suction pressure region, 34: a thrust bearing, 34a: a front end side race, 34b: a rear end side race, 35 ... piston,
37: a suction chamber constituting a suction pressure region, 38: a discharge chamber constituting a discharge pressure region, 48: an air supply passage as a communication passage, 4
9: capacity control valve, 52: external refrigerant circuit, 85: spacer, 100: pressure applying passage as communication passage, 101: control pressure chamber, 103: thrust bearing.

────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Koji Kawamura 2-1-1, Toyota-machi, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation (56) References JP-A-7-310655 (JP, A) 7-189902 (JP, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) F04B 27/10 F04B 39/14

Claims (6)

(57) [Claims] 1. A control pressure chamber and a crank chamber are formed inside a housing, and a drive shaft is rotatably supported. A plurality of cylinder bores are formed in a cylinder block constituting a part of the housing, and a housing hole is provided. A piston is reciprocally accommodated in the cylinder bore, a cam plate is rotatably and swingably inserted into the drive shaft, and a suction passage from the external refrigerant circuit to the suction pressure region is provided in the housing hole. And a shut-off member for opening and closing the suction passage in conjunction with the swinging movement of the cam plate, and in the middle of the communication passage between at least one of the discharge pressure region and the suction pressure region and the control pressure chamber. Is provided with a capacity control valve, and the pressure of the control pressure chamber is changed based on the adjustment of the opening of the capacity control valve, whereby the crank chamber housing the cam plate is provided. A clutchless variable displacement compressor configured to change the difference between the pressure of the cylinder bore and the pressure in the cylinder bore through the piston, and change the inclination of the cam plate in accordance with the difference to control the discharge capacity. The inner peripheral surface of the accommodation hole is formed to have substantially the same diameter,
A clutchless variable displacement compressor in which the blocking body is detachably fitted and supported in the housing hole from the rear end side of the cylinder block. 2. An annular groove is formed in the inner periphery of the rear end of the accommodation hole, and a spring receiver is detachably fitted in the annular groove, and a blocking member is attached to the spring receiver in the opening direction of the suction passage. 2. The clutchless variable displacement compressor according to claim 1, wherein a rear end of a spring for urging is latched. 3. A minimum inclination angle of the cam plate is adjusted by inserting a thrust bearing on the drive shaft between the cam plate and the interrupter and changing the thickness of the race of the thrust bearing. The clutchless variable displacement compressor according to claim 1 or 2. 4. A minimum tilt angle of the cam plate is adjusted by inserting a thrust bearing on a drive shaft between the cam plate and the blocking member and changing a thickness of a spacer disposed adjacent to the thrust bearing. The clutchless variable displacement compressor according to claim 1 or 2, wherein 5. The clutchless variable displacement compressor according to claim 1, wherein a minimum inclination angle of the cam plate is adjusted by changing a length of the blocker. 6. A control pressure chamber and a crank chamber are formed inside a housing, and a drive shaft is rotatably supported. A plurality of cylinder bores are formed in a cylinder block constituting a part of the housing, and a housing hole is provided. A piston is reciprocally accommodated in the cylinder bore, a cam plate is rotatably and swingably inserted into the drive shaft, and a suction passage from an external refrigerant circuit to a suction pressure region is provided in the housing hole. And a shut-off body for opening and closing the suction passage in conjunction with the swing of the cam plate, and in the middle of the communication passage between at least one of the discharge pressure region and the suction pressure region and the control pressure chamber. Is provided with a capacity control valve, and the pressure in the control pressure chamber is changed based on the opening degree adjustment of the capacity control valve, whereby the crank chamber accommodating the cam plate is provided. A clutchless variable displacement compressor configured to change a difference between the pressure in the cylinder bore and the pressure in the cylinder bore through the piston, and to change a tilt angle of a cam plate in accordance with the difference to control a discharge capacity. With the drive shaft, cam plate, and piston assembled to the housing, the thrust bearing, blocker, and suction passage opening spring are detachably incorporated into the receiving hole from the rear end of the cylinder block, and attached to the rear end of the cylinder block. A method for assembling a clutchless variable displacement compressor in which a spring receiver is attached and the rear end of the suction passage opening spring is latched and held by the spring receiver.