JP2009264127A - Variable displacement compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement compressor suppressing discharge of lubricating oil to the outside regardless of arrangement of a refrigerant outlet in a header housing. <P>SOLUTION: In this compressor, all delivery refrigerants to be led out from a delivery chamber 53 to a downstream side through the refrigerant outlet are routed through a control valve. The compressor is provided with a connecting pipe 75 connecting the downstream outlet of the main valve of the control valve in the valve storage chamber of a rear housing 104 to the refrigerant outlet of the compressor. The inside of the connecting pipe 75 is isolated from the delivery chamber 53 to form a separate refrigerant passage. Therefore, even if an outlet port 64 for leading out a refrigerant passed through the main valve of the control valve is disposed in a lower position, the liquefied refrigerant does not enter from the outlet port and is not led to the refrigerant outlet. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a variable capacity compressor, and more particularly to a variable capacity compressor constituting a refrigeration cycle suitable for an automotive air conditioner.

  In the refrigeration cycle of an automotive air conditioner, a variable capacity compressor (also simply referred to as “compressor”) that can vary the refrigerant discharge capacity is used so that a constant cooling capacity is maintained regardless of the engine speed. It has been. In this compressor, a piston for compression is connected to a swing plate attached to a rotating shaft that is driven to rotate by an engine, and the angle of the swing plate is changed to change the stroke of the piston in the cylinder. Adjust the discharge rate. The angle of the swing plate can be continuously changed by introducing a part of the discharged refrigerant into the sealed crank chamber and changing the balance of pressure applied to both surfaces of the piston. The pressure in the crank chamber (also referred to as “crank pressure”) is, for example, a solenoid-operated variable displacement compressor control valve provided between the discharge chamber and the crank chamber of the compressor or between the crank chamber and the suction chamber. (Also referred to simply as “control valve”) (see, for example, Patent Document 1).

Such a compressor is generally configured by integrally assembling a main body housing in which a crank chamber and a cylinder are defined and a header housing in which a refrigerant suction chamber, a discharge chamber and a valve storage chamber are defined. . A control valve is accommodated in the valve accommodating chamber. The refrigerant introduced into the suction chamber from the upstream side of the compressor through the refrigerant inlet of the header housing is sucked into the cylinder and compressed along with the stroke of the piston. The compressed refrigerant is discharged into the discharge chamber, and is led out from the refrigerant outlet of the header housing to the downstream side of the compressor. At that time, the control valve controls the crank pressure by adjusting the flow rate of the refrigerant guided from the discharge chamber to the crank chamber.
JP 2006-17035 A

  However, a problem may arise depending on the mounting position of the control valve in such a compressor, that is, the position of the valve accommodating chamber in the header housing. That is, in general, oil for lubrication is circulated together with the refrigerant in order to facilitate the operation of the internal mechanism in the compressor, but if the compressor is placed in a low temperature environment when the operation is stopped, the refrigerant in which the oil is dissolved May be liquefied in the header housing. Further, in general, the compressor is installed at a location where the ambient temperature is relatively low, which is shaded in the engine room, whereas the downstream condenser is installed at a location where the ambient temperature is higher than that. For this reason, when the operation of the compressor is stopped, a part of the refrigerant on the condenser side may return to promote liquefaction of the refrigerant in the header housing.

  When the refrigerant containing oil is liquefied and collected in the lower part of the discharge chamber in this way, if the refrigerant outlet is at a low position where the liquefied refrigerant is accumulated, the liquefied refrigerant will be discharged at the next operation of the compressor. As a result, even the lubricating oil may be discharged. As a result, when the oil in the compressor is insufficient, the smooth operation of the internal mechanism may be hindered. In this case, it is conceivable to dispose the refrigerant outlet at a high position to prevent the discharge of the liquefied refrigerant. However, in a compressor of the type in which all of the discharged refrigerant passes through the control valve as described in Patent Document 1. The position of the refrigerant outlet is restricted by the installation position of the control valve. That is, in order to efficiently guide the refrigerant from the outlet port of the control valve to the refrigerant outlet of the compressor, it is necessary to bring the outlet port close to the refrigerant outlet. In such a case, it is difficult to provide the refrigerant outlet at a high position.

  The present invention has been made in view of such problems, and an object thereof is to provide a variable capacity compressor capable of suppressing the discharge of lubricating oil to the outside regardless of the arrangement of the refrigerant outlet in the header housing. .

  A variable capacity compressor according to an aspect of the present invention includes a main body housing having a crank chamber and a cylinder defined therein, a variable inclination compressor provided in the crank chamber with a variable inclination angle with respect to the rotation shaft, and being oscillated by rotational driving of the rotation shaft. The oscillating body, which has a dynamic motion and whose inclination angle changes according to the crank pressure of the crank chamber, and is coupled to the oscillating body, and is reciprocated in the axial direction by the oscillating motion of the oscillating body, so A piston that sucks in the refrigerant, compresses the refrigerant in the cylinder, and discharges the refrigerant from the cylinder to the discharge chamber, and the main body housing are provided integrally with the suction chamber, the discharge chamber, and the valve storage chamber. And a refrigerant inlet for introducing refrigerant into the suction chamber from the upstream side of the refrigeration cycle and a refrigerant for discharging the discharged refrigerant from the discharge chamber to the downstream side of the refrigeration cycle A header housing provided with a port; a control valve housed in a valve housing chamber; a first refrigerant passage communicating the discharge chamber and a refrigerant outlet; a main valve opening and closing the first refrigerant passage; and a discharge chamber A second refrigerant passage that communicates with the crank chamber, a sub-valve that opens and closes the second refrigerant passage by being displaced relative to the main valve, and drives the sub-valve in the opening / closing direction. A control valve for controlling the flow rate of the refrigerant led out from the refrigerant outlet through the main valve so as to be a set flow rate according to the current value supplied to the solenoid, A pipe housing that extends through the discharge chamber in the header housing and connects the outlet on the downstream side of the main valve in the valve storage chamber and the refrigerant outlet.

  In this aspect, since the main valve for opening and closing the first refrigerant passage for communicating the discharge chamber and the refrigerant outlet is provided, all of the discharged refrigerant led out from the discharge chamber to the downstream side of the compressor passes through the control valve. Will do. However, a pipe part that connects the outlet on the downstream side of the main valve in the valve storage chamber and the refrigerant outlet is provided so as to penetrate the discharge chamber, so that the refrigerant in the discharge chamber is prevented from flowing directly into the pipe part. . For this reason, even if the liquefied refrigerant is accumulated in the discharge chamber, the liquefied refrigerant is not led directly to the refrigerant outlet. As a result, even if the lubricating oil is dissolved in the liquefied refrigerant, the lubricating oil can be prevented from being discharged to the outside. Further, since the downstream outlet of the main valve and the refrigerant outlet are directly connected by the piping portion, the design can be performed without particularly considering the positional relationship between the refrigerant outlet and the valve storage chamber.

  ADVANTAGE OF THE INVENTION According to this invention, the variable capacity compressor which can suppress discharge | emission of the lubricating oil to the exterior irrespective of arrangement | positioning of the refrigerant | coolant exit in a header housing can be provided.

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

[First Embodiment]
FIG. 1 is a system configuration diagram showing a refrigeration cycle according to the first embodiment.
This refrigeration cycle constitutes a vehicular air conditioner, a variable capacity compressor (hereinafter simply referred to as “compressor”) 1 that compresses the refrigerant circulating in the refrigeration cycle, and condenses and cools the compressed refrigerant. A condenser 2 (corresponding to an “external heat exchanger”), an expansion device 3 that adiabatically expands the condensed refrigerant, and an evaporator 4 that evaporates the expanded refrigerant are provided. In addition, in the figure, the arrow cross section seen from the downward direction is shown about the compressor 1 for convenience.

  The compressor 1 introduces and compresses the refrigerant gas introduced from the evaporator 4 side into the suction chamber 51 into the cylinder 52 and discharges high-temperature and high-pressure refrigerant from the discharge chamber 53 to the condenser 2 side. A part of the discharged refrigerant is introduced into the crank chamber 54 via a variable capacity compressor control valve (hereinafter simply referred to as “control valve”) 5 and is used for capacity control of the compressor 1. The control valve 5 is configured as a solenoid-driven electromagnetic valve, and a control unit (not shown) drives a drive circuit to control energization of the drive circuit.

  In a refrigerant passage (not shown) that connects the crank chamber 54 and the suction chamber 51, an orifice having a fixed cross-sectional area is provided, and a predetermined minimum flow rate of refrigerant flows from the crank chamber 54 to the suction chamber 51. The internal circulation of the refrigerant in the compressor 1 is ensured. In the refrigerant passage between the discharge chamber 53 of the compressor 1 and the condenser 2, a check valve (not shown) that allows the refrigerant to flow in one direction may be provided.

  The compressor 1 includes, as its housing, a cylinder block 101 in which a plurality of cylinders 52 are formed, a front housing 102 joined to the front end side thereof, and a rear housing 104 joined to the rear end side thereof via a valve plate 103. And. In the present embodiment, the cylinder block 101 and the front housing 102 constitute a “main body housing”, and a crank chamber 54 and a cylinder 52 are defined in an internal space surrounded by these. The rear housing 104 functions as a “header housing”, and a suction chamber 51, a discharge chamber 53, and a valve storage chamber 55 are defined in the internal space. The rear housing 104 is also provided with a refrigerant inlet 56 that introduces refrigerant into the suction chamber 51 from the evaporator 4 side, and a refrigerant outlet 57 that leads the discharged refrigerant from the discharge chamber 53 to the condenser 2 side.

  A rotation shaft 106 is disposed in the crank chamber 54 so as to penetrate the center thereof. The rotating shaft 106 is rotatably supported by a bearing 107 provided on the cylinder block 101 and a bearing 108 provided on the front housing 102. A lug plate 109 is fixed to the rotating shaft 106, and a swing plate 111 (corresponding to a “swing body”) is supported via a support arm 110 protruding from the lug plate 109. The swing plate 111 can tilt with respect to the axis of the rotary shaft 106, and is connected via a shoe 114 to a piston 112 slidably disposed in the plurality of cylinders 52. The rotating shaft 106 has a front end portion extending through the front housing 102 and extending to the outside, and a bracket 117 is screwed to the tip portion. Further, a lip seal 115 as a shaft seal member is provided so as to seal a gap between the front end portion of the rotary shaft 106 and the front housing 102 from the outside. The lip seal 115 is in sliding contact with the peripheral surface of the rotating shaft 106 and prevents leakage of refrigerant gas along the peripheral surface.

  A pulley 118 that transmits driving force from the engine is rotatably supported on the front end portion of the front housing 102 via a bearing 119. The pulley 118 transmits the driving force of the engine to the rotating shaft 106 via the bracket 117.

  The suction chamber 51 of the rear housing 104 communicates with the cylinder 52 via a suction relief valve 121 provided on the valve plate 103 and also communicates with the evaporator 4 via a refrigerant inlet 56. The discharge chamber 53 communicates with the cylinder 52 via a discharge relief valve (not shown) provided on the valve plate 103 and also communicates with the condenser 2 via a refrigerant outlet 57. The valve housing chamber 55 protrudes on the opposite side of the rear housing 104 from the cylinder block 101 and communicates with the discharge chamber 53 and the crank chamber 54, respectively. The control valve 5 is inserted into the valve accommodating chamber 55 from the upper end side, and is fixed via a sealing O-ring 59, a washer 60, and the like.

  The swing plate 111 of the compressor 1 has an angle of the load of the springs 125 and 126 urging the swing plate 111 in the crank chamber 54 and the load due to the pressure applied to both surfaces of the piston 112 connected to the swing plate 111. Etc. are held in a balanced position. The angle of the oscillating plate 111 of the compressor 1 is changed continuously by introducing a part of the refrigerant discharged into the crank chamber 54 to change the crank pressure Pc and changing the balance of pressure applied to both surfaces of the piston 112. Can be changed. The refrigerant discharge capacity is adjusted by changing the stroke of the piston 112 by changing the angle of the swing plate 111. The pressure in the crank chamber 54 is controlled by the control valve 5.

FIG. 2 is a view of the rear housing as viewed from the opening side. Note that the vertical direction in the figure corresponds to the height direction of the compressor 1. FIG. 3 is a cross-sectional view taken along the line AA of FIG. 4 is a cross-sectional view taken along line BB in FIG.
As shown in FIG. 2, the rear housing 104 has a circular lid shape formed by die casting of an aluminum alloy, a partition wall 62 is provided inside the circular side wall 61, and a discharge chamber 53 is located inside the rear housing 104. And a suction chamber 51 is formed outside. At the bottom of the discharge chamber 53, an inlet port 63 and an outlet port 64 that communicate with the valve storage chamber 55, and a lead-out port 66 that communicates with the refrigerant outlet 57 are provided. Further, a communication passage 67 that penetrates the partition wall 62 and communicates with the valve storage chamber 55 is provided. In the present embodiment, the outlet port 64 is provided at a height where the refrigerant liquefied in the discharge chamber 53 may accumulate.

  As shown in FIG. 3, the inlet port 63 communicates with the inlet port 71 of the control valve 5, and the outlet port 64 communicates with the outlet port 72 of the control valve 5. The communication path 67 communicates with the communication port 73 of the control valve 5. As shown in FIG. 4, a connection pipe 75 (corresponding to a “pipe portion”) is provided so as to connect the outlet port 64 and the outlet port 66. As shown in the figure, the connecting pipe 75 is disposed so as to penetrate the discharge chamber 53 while being curved. Since both ends of the connection pipe 75 are press-fitted into the bottom of the discharge chamber 53, the discharge refrigerant passing through the connection pipe 75 is not diffused into the discharge chamber 53 and is efficiently guided to the refrigerant outlet 57. . Further, the refrigerant in the discharge chamber 53 is not directly led out from the outlet port 66 without passing through the control valve 5.

  Returning to FIG. 1, a control unit (not shown) includes a CPU that executes various arithmetic processes, a ROM that stores various control programs, a RAM that is used as a work area for data storage and program execution, an input / output interface, and the like. The control unit determines the set flow rate of the refrigerant flowing through the refrigeration cycle based on predetermined external information detected by various sensors such as the engine speed, the temperature inside and outside the vehicle interior, the temperature of the air blown from the evaporator 4, and the like. The energization of the control valve 5 is controlled so that a solenoid force that maintains the set flow rate is obtained.

  The expansion device 3 is configured as a so-called temperature expansion valve, feeds back the refrigerant temperature on the outlet side of the evaporator 4, adjusts the valve opening, and supplies liquid refrigerant according to the heat load to the evaporator 4. To do. The refrigerant that has passed through the evaporator 4 is returned to the compressor 1 and compressed again.

FIG. 5 is a cross-sectional view showing the configuration of the control valve. FIG. 6 is an enlarged view of the upper half of the control valve shown in FIG.
The control valve 5 is configured as a flow rate control valve that controls the flow rate of the refrigerant introduced from the discharge chamber 53 to the crank chamber 54 so that the flow rate of the refrigerant derived from the compressor 1 is maintained at a set flow rate.
As shown in FIG. 5, the control valve 5 is configured by integrally assembling a valve body 8 having a main valve and a sub-valve therein and a solenoid 9 that drives the valves of the valve body 8 to open and close. The control valve 5 includes a bottomed cylindrical body 10 (first body) and a stepped cylindrical body 12 (second body) connected to the body 10. The body 12 is connected to the upper end opening of the body 10 so that the lower end of the body 10 is press-fitted, and the lower end of the body 12 also functions as a yoke of the solenoid 9. Part of it. An inlet port 71 is provided at the side of the body 10, and an outlet port 72 is provided at the upper end opening. A communication port 73 is provided on the side of the body 12. As described above, the inlet port 71 communicates with the inlet port 63 of the rear housing 104, the outlet port 72 communicates with the outlet port 64, and the communication port 73 communicates with the communication path 67 (see FIG. 3).

  As shown in FIG. 6, a refrigerant passage (corresponding to a “first refrigerant passage”) that connects the inlet port 71 and the outlet port 72 extends in the axial direction in the upper portion of the body 10. A valve hole 15 is formed in the middle portion of the. A tapered surface whose diameter is increased upward is formed at the opening end of the valve hole 15 on the outlet port 72 side, and the valve seat 16 is formed by the tapered surface. On the other hand, a solid valve body 18 (corresponding to a “main valve body”) is detachably disposed so as to face the valve seat 16 from the outlet port 72 side. The valve body 18 and the valve seat 16 constitute a main valve. The valve body 18 has a conical side surface that is reduced in diameter toward the lower side, and is attached to and detached from the valve seat 16 on the side surface to open and close the main valve. A plurality of leg portions 17 are provided on the side surface of the valve body 18 at regular intervals in the circumferential direction (in the present embodiment, three legs are provided at an angle of 120 degrees). The leg portion 17 has a triangular plate shape extending radially outward from the side surface of the valve body 18, and the distal end surface thereof is in contact with the valve hole 15. That is, the stability of the operation of the valve body 18 in the axial direction is ensured by the leg 17 being guided so as to slide in the valve hole 15. Further, a cylindrical valve seat forming portion 19 projects downward from the lower surface of the valve body 18.

  A bottomed cylindrical spring receiving member 11 is fitted into the upper end opening of the body 10, and a spring 13 that biases the valve body 18 in the valve closing direction between the spring receiving member 11 and the valve body 18. Is intervening. The spring receiving member 11 is provided with a plurality of communication holes communicating between the inside and the outside, and allows the refrigerant that has passed through the main valve to be led to the downstream side.

  The discharged refrigerant led out from the discharge chamber 53 is introduced into the control valve 5 through the inlet port 71, and a part thereof passes through the main valve and is led out from the outlet port 72. This refrigerant is led out to the downstream side of the compressor 1 through the lead-out port 66 and the refrigerant outlet 57 (see FIGS. 1 and 3). As the discharge refrigerant passes through the main valve in this way, the discharge pressure Pd is slightly reduced from the discharge chamber pressure Pdh of the discharge chamber 53 to be output to the condenser 2 as the outlet pressure Pdl of the compressor 1. become. In the following description, the discharge chamber pressure Pdh and the outlet pressure Pdl may be collectively referred to as the discharge pressure Pd without particular distinction.

  On the other hand, the lower part of the body 10 is gradually reduced in diameter, and a guide hole 20 is formed in the center of the bottom. A cylindrical valve element 22 (corresponding to a “sub-valve element”) is inserted so as to penetrate the guide hole 20 and is supported so as to be slidable in the axial direction. The inlet port 71 and the communication port 73 communicate with each other through the guide hole 20. However, since the V ring 23 as a seal member is interposed between the bottom portion of the body 10 and the valve body 22, the valve body 22. Leakage of the refrigerant transmitted along the outer peripheral surface of the is prevented. A ring-shaped stopper 24 is press-fitted directly above the V-ring 23 at the bottom of the body 10 to restrict the displacement of the V-ring 23 in the axial direction.

  The valve body 22 has a bottomed cylindrical shape, and a communication hole 25 that communicates the inside and the outside is provided in a side portion near the bottom. The inside of the valve body 22 forms a valve hole 26, and the upper end thereof opens and closes the auxiliary valve by being attached to and detached from a valve seat 27 formed on the lower surface of the valve seat forming portion 19. That is, the valve body 18 described above also functions as a movable valve seat, and the valve body 22 and the valve seat 27 constitute a secondary valve. The lower end portion of the valve body 22 is disposed in the pressure chamber 28 that communicates with the crank chamber 54 via the communication port 73, and the valve body 22 is placed in the valve opening direction between the lower end portion and the body 10. An urging spring 29 is interposed.

  A part of the discharged refrigerant introduced through the inlet port 71 is reduced to the crank pressure Pc by passing through the auxiliary valve, led to the pressure chamber 28, and led out from the communication port 73. This refrigerant is further introduced into the crank chamber 54 via the communication passage 67 and used for controlling the discharge capacity of the compressor 1 (see FIGS. 1 and 3).

  Returning to FIG. 5, the solenoid 9 is magnetized by a case 31 that also functions as a yoke, a core 32 that is fixed in the case 31, a plunger 33 that is disposed so as to face the core 32 in the axial direction, and a current supplied from the outside. And an electromagnetic coil 34 for generating a circuit. The case 31 is assembled such that its upper end press-fits the lower end of the body 12, and constitutes the body of the solenoid 9 together with the body 12. The upper end portion of the core 32 is press-fitted into the lower half portion of the body 12.

  The core 32 is provided with an insertion hole 35 penetrating the center in the axial direction, and a shaft 36 for transmitting a solenoid force to the valve body 22 is inserted therethrough. A bearing portion 38 having a slightly reduced inner diameter is formed at the upper end portion of the core 32, and the upper end portion of the shaft 36 is slidably supported by the bearing portion 38. The crank pressure Pc in the pressure chamber 28 can be introduced into the solenoid 9 through a minute gap between the shaft 36 and the bearing portion 38. The shaft 36 supports the valve body 22 from below by its upper end surface.

  Further, a bottomed sleeve 39 having a closed lower end is externally inserted into the core 32. In the bottomed sleeve 39, the plunger 33 is disposed below the core 32 so as to be able to advance and retract in the axial direction. A spring receiving member 40 is disposed at the bottom of the bottomed sleeve 39. The plunger 33 has a cylindrical shape and is press-fitted into the lower half of the shaft 36. Between the plunger 33 and the spring receiving member 40, a spring 41 that biases the plunger 33 in the closing direction of the sub valve (the opening direction of the main valve) is interposed. Further, a spring 45 that urges the plunger 33 in the valve opening direction (the valve closing direction of the main valve) is interposed between the core 32 and the plunger 33. Since the spring load by the spring 29 and the spring 45 is set to be larger than the spring load by the spring 41, the sub-valve is held in a fully open state when the solenoid 9 is not energized.

  A sealing member 42 that seals the inside of the solenoid 9 from below is provided at the lower end opening of the case 31. The sealing member 42 is made of a magnetic member that forms a magnetic circuit together with the case 31, and is pulled out so that a harness 43 connected to the electromagnetic coil 34 penetrates through a rubber bush 44 for sealing.

  In the above configuration, the thickness of the cylindrical portion of the valve body 22 is relatively small, and the outer diameter of the valve body 22 (inner diameter of the guide hole 20) is slightly larger than the inner diameter of the opening end of the valve hole 26, but is substantially the same. Since it has a magnitude | size, the influence of the crank pressure Pc which acts on the valve body 22 is canceled substantially. Therefore, when the sub-valve is closed while the energization control of the solenoid 9 is performed, a force in the valve opening direction corresponding to the solenoid force acts on the valve body 18.

Next, basic operations of the control valve 5 and the compressor 1 will be described.
In the control valve 5, when the solenoid 9 is in a non-energized state, the valve element 18 is seated on the valve seat 16 by the biasing force of the spring 13, and the main valve is closed. On the other hand, due to the resultant force of the springs 29, 41, 45, the valve body 22 is integrated with the shaft 36 and operates in the valve opening direction, and is separated from the valve seat 27 and is fully opened. In this state, when the rotating shaft 106 of the compressor 1 shown in FIG. 1 is rotated by driving the vehicle engine, the swing plate 111 performs swinging motion, and the piston 112 coupled thereto reciprocates. As a result, the refrigerant introduced into the suction chamber 51 is sucked into the cylinder 52 and compressed, and the compressed refrigerant is discharged into the discharge chamber 53. At this time, since the main valve is in the fully closed state, the discharged refrigerant passes through the fully opened sub valve and is introduced into the pressure chamber 28, and further introduced into the crank chamber 54 via the communication port 73 and the communication passage 67. The As a result, since the crank pressure Pc is increased, the compressor 1 performs the minimum capacity operation.

  When a predetermined control current is supplied to the solenoid 9, the plunger 33 is attracted to the core 32, so that the valve element 22 balances the force in the valve opening direction due to the resultant force of the spring and the solenoid force in the valve closing direction. It is held at the position to do. At this time, since the valve body 22 is momentarily seated on the valve body 18 in the closed state and the sub-valve is fully closed, the introduction of the refrigerant into the crank chamber 54 is interrupted, and the crank pressure Pc decreases, The compressor 1 immediately shifts to the maximum capacity operation. As a result, the discharge pressure Pd increases rapidly and the valve body 18 is lifted against the urging force of the spring 13, and the main valve is opened by the lift amount corresponding to the flow rate of the refrigerant. In addition, the valve body 18 as the movable valve seat is thereby separated from the valve body 22 and the sub-valve is opened, so that the refrigerant flow rate according to the relative position of the two valve bodies is transferred to the crank chamber 54. As a result, the compressor 1 is kept in an operating state with a predetermined capacity.

  Here, when the rotational speed of the vehicle engine is increased and the discharge pressure Pd is increased, the flow rate of the refrigerant discharged from the discharge chamber 53 is increased, and the valve body 18 is further lifted accordingly, and the valve opening degree of the main valve is increased. In order to increase the flow rate, the flow rate of the refrigerant discharged from the compressor 1 tends to increase. However, when the relative distance from the valve body 22, that is, the opening degree of the sub-valve, is further increased by the lift of the valve body 18, the refrigerant flow rate introduced into the crank chamber 54 increases, and the crank pressure Pc increases. As a result, the compressor 1 is controlled to reduce the refrigerant discharge flow rate. Conversely, when the rotational speed of the vehicle engine decreases, the refrigerant flow rate discharged from the discharge chamber 53 decreases, the refrigerant flow rate introduced into the crank chamber 54 also decreases, and the crank pressure Pc decreases. As a result, the compressor 1 is controlled to increase the refrigerant discharge flow rate. Thus, since the control valve 5 performs control so that the change in the flow rate of the discharged refrigerant becomes small even if the engine speed changes and the flow rate of the discharged refrigerant changes, the flow rate of the discharged refrigerant from the compressor 1 Is controlled to be constant. The set flow rate of the discharged refrigerant can be changed according to the current value supplied to the solenoid 9. The control unit determines the set flow rate based on external information and performs energization control to the solenoid 9.

  In the present embodiment, all of the refrigerant discharged from the discharge chamber 53 to the downstream side of the compressor 1 via the refrigerant outlet 57 passes through the control valve 5. A connecting pipe 75 that connects the outlet on the downstream side of the main valve and the refrigerant outlet 57 of the compressor 1 is provided. Since the inside of the connecting pipe 75 is isolated from the discharge chamber 53 to form another refrigerant passage, even if the liquefied refrigerant is accumulated in the discharge chamber 53, the liquefied refrigerant is led to the refrigerant outlet 57. Can be prevented or suppressed. In particular, in the present embodiment, as shown in FIG. 2, an outlet port 64 from which the refrigerant that has passed through the main valve of the control valve 5 is led is provided at a low position. It is not led to the outlet 57. For this reason, even if lubricating oil is dissolved in the liquefied refrigerant, the lubricating oil can be prevented from being discharged to the outside of the compressor 1. Further, since the outlet port 64 and the refrigerant outlet 57 are directly connected by the connecting pipe 75, the rear housing 104 can be designed without particularly considering the positional relationship between the refrigerant outlet 57 and the valve storage chamber 55.

[Second Embodiment]
Next, a second embodiment of the present invention will be described. The present embodiment is substantially the same as the first embodiment except that the configuration of the piping portion that connects the outlet port of the main valve and the refrigerant outlet in the valve storage chamber is different. For this reason, about the component similar to 1st Embodiment, the same code | symbol is attached | subjected as needed, and the description is abbreviate | omitted suitably. FIG. 7 is a view of the rear housing according to the second embodiment as viewed from the opening side, and corresponds to FIG. FIG. 8 is a cross-sectional view taken along the line AA of FIG.

  As shown in FIG. 7, also in the rear housing 204, the inlet port 63 and the outlet port 64 are provided at a height position where the refrigerant liquefied in the discharge chamber 53 may accumulate. On the other hand, in the present embodiment, the piping part that connects the outlet port 64 and the outlet port 66 has grooves 210 and 212 formed on the bottom surface of the rear housing 204, and a lid member 214 that is assembled so as to cover both grooves. (Corresponding to “cover member”). Both groove portions are formed as long grooves formed in the bank portion 205 slightly raised on the bottom surface of the rear housing 204. The groove portion 210 extends vertically, and the inlet port 63 communicates with the lower end portion thereof. On the other hand, the groove portion 212 is bent in a U shape and extends vertically, and the outlet port 64 communicates with the lower end portion thereof, and the outlet port 66 communicates with the upper end portion thereof.

  The lid member 214 has a Y-shape that is substantially the same shape as the bank portion 205, and is joined by welding or the like while being placed on the bank portion 205 as shown in FIG. 8. The lid member 214 forms a refrigerant passage that seals the entire groove 212 (corresponding to the “first groove”) and connects the outlet port 64 and the outlet port 66. The refrigerant having the outlet pressure Pdl flowing into the groove portion 212 from the outlet port 64 is guided to the upper outlet port 66 through this refrigerant passage as shown by a one-dot chain line arrow in the figure. On the other hand, the lid member 214 opens without sealing the upper end portion of the groove portion 210 (corresponding to the “second groove portion”), and forms a refrigerant passage that connects the inlet port 63 and the opening portion 218 thereof. The refrigerant having the discharge chamber pressure Pdh discharged into the discharge chamber 53 flows into the groove portion 210 through the upper open portion 218, and passes through this refrigerant passage as shown by the one-dot chain line arrow in the drawing. 63 to the valve accommodating chamber 55.

  As described above, in this embodiment, the inlet port 63 is not exposed to the lower portion of the rear housing 204. In other words, by disposing the refrigerant inlet in the discharge chamber 53 at a substantially high position, even if the liquefied refrigerant is accumulated in the discharge chamber 53, the liquefied refrigerant is stored in the inlet port 63 and the valve storage chamber 55. Then, it can be prevented or suppressed from being led to the refrigerant outlet 57.

[Third Embodiment]
Next, a third embodiment of the present invention will be described. This embodiment is substantially the same as the first embodiment except that the configuration of the sub valve of the control valve is slightly different. For this reason, about the component similar to 1st Embodiment, the same code | symbol is attached | subjected as needed, and the description is abbreviate | omitted suitably. FIG. 9 is an enlarged view of the upper half of the control valve according to the third embodiment.
In the control valve 305, instead of the V ring 23 of the first embodiment, a square ring 323 which is a seal member having a rectangular cross section is disposed.

  The valve seat forming portion 319 of the valve body 318 of the main valve is provided with a circular recess 320 having the same inner diameter as the guide hole 20, and the valve seat 27 is formed by the opening edge of the recess 320. On the other hand, a valve body 324 whose outer diameter is slightly enlarged is provided at the upper end of the valve body 322 of the sub-valve, and the tapered surface of the tip is configured to be attached to and detached from the valve seat 27. Therefore, the effective pressure receiving diameter of the valve body 322 as the auxiliary valve is substantially equal to the inner diameter of the recess 320. That is, since the effective pressure receiving diameter of the valve body 322 is equal to the inner diameter of the guide hole 20, the crank pressure Pc can be canceled accurately. As a result, good controllability can be obtained in the control valve 305.

[Fourth Embodiment]
Next, a fourth embodiment of the present invention will be described. This embodiment is substantially the same as the third embodiment except that the configuration of the control valve is different. For this reason, about the component substantially the same as 3rd Embodiment, the same code | symbol is attached | subjected as needed, and the description is abbreviate | omitted suitably. FIG. 10 is an enlarged view of the upper half of the control valve according to the fourth embodiment.

  In the control valve 405, the square ring 323 and the stopper 24 are not provided, and a cylindrical strainer 420 is disposed so as to surround the main valve. The filter portion of the strainer 420 blocks inflow of dust and the like contained in the discharged refrigerant, and prevents clogging of dust in the main valve and inflow of dust and the like into the crank chamber 54.

  The body 412 is formed longer than the body 12 of the first embodiment, and a partition member 425 is provided between the body 10 and the core 32. The valve body 422 is also formed longer in the axial direction than the valve body 22 of the first embodiment. The spring 29 is interposed between the lower end portion of the valve body 322 and the partition member 425.

  A communication port 430 that communicates with the suction chamber 51 and introduces the suction pressure Ps is provided between the body 10 and the partition member 425. As a result, even if the high-pressure discharged refrigerant introduced from the inlet port 71 leaks along the outer peripheral surface of the valve body 422, the leaked refrigerant is released from the communication port 430 to the suction chamber 51. Never reach the side. That is, even if a seal member is not provided on the outer periphery of the valve body 422, it is possible to prevent the discharged refrigerant from flowing toward the crank chamber 54 and unnecessarily increasing the crank pressure Pc. In particular, when it is desired to shift the compressor 1 to the minimum capacity operation, this can be surely executed.

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

  In each embodiment, the control valve is installed in the discharge side refrigerant passage of the variable capacity compressor to control the flow rate of the refrigerant introduced into the crank chamber. However, the control valve is installed in the suction side refrigerant passage, The valve may sense the flow rate of the refrigerant flowing through the suction side refrigerant passage and control the flow rate of the refrigerant flowing out from the crank chamber to the suction chamber.

  In each embodiment, although the example which employ | adopted what is called a temperature type expansion valve as the expansion apparatus 3 was shown, the orifice tube which has a fixed orifice, for example can also be employ | adopted.

  Although the compressor of each embodiment is suitably applied to a refrigeration cycle that uses an alternative chlorofluorocarbon (HFC-134a) or the like as a refrigerant, the variable capacity compressor of the present invention is a refrigerant having a high operating pressure such as carbon dioxide. It is also possible to apply to a refrigeration cycle using In that case, an external heat exchanger such as a gas cooler is arranged in place of the condenser in the refrigeration cycle.

It is a system configuration figure showing the refrigerating cycle concerning a 1st embodiment. It is the figure which looked at the rear housing from the opening part side. It is AA sectional drawing of FIG. It is BB sectional drawing of FIG. It is sectional drawing which shows the structure of a control valve. It is an upper half enlarged view of the control valve shown in FIG. It is the figure which looked at the rear housing which concerns on 2nd Embodiment from the opening part side. It is AA sectional drawing of FIG. It is the upper half enlarged view of the control valve which concerns on 3rd Embodiment. It is an upper half enlarged view of the control valve concerning a 4th embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Compressor, 2 Condenser, 3 Expansion device, 4 Evaporator, 5 Control valve, 8 Valve body, 9 Solenoid, 10 Body, 12 Body, 15 Valve hole, 16 Valve seat, 18 Valve body, 19 Valve seat formation part , 20 guide hole, 22 valve body, 25 communication hole, 26 valve hole, 27 valve seat, 51 suction chamber, 52 cylinder, 53 discharge chamber, 54 crank chamber, 55 valve storage chamber, 56 refrigerant inlet, 57 refrigerant outlet, 61 Side wall, 62 partition wall, 63 inlet port, 64 outlet port, 66 outlet port, 67 communication path, 71 inlet port, 72 outlet port, 73 communication port, 75 connecting pipe, 101 cylinder block, 102 front housing, 104 rear housing, 106 Rotating shaft, 111 Swing plate, 112 Piston 204 rear housing, 205 bank portion, 210 groove portion, 212 groove portion, 214 lid member, 218 opening portion, 305 control valve, 318 valve body, 319 valve seat forming portion, 322 valve body, 324 valve body portion, 405 control valve, 412 Body, 420 strainer, 422 Disc.

Claims (5)

A main body housing having a crank chamber and a cylinder defined therein;
An oscillating body provided in the crank chamber with a variable tilt angle with respect to the rotation shaft and swinging by rotation driving of the rotation shaft, and the tilt angle changing with the crank pressure of the crank chamber;
The refrigerant is connected to the rocking body and reciprocates in the axial direction by the rocking motion of the rocking body, so that the refrigerant is sucked into the cylinder, compressed in the cylinder, and discharged from the cylinder. A piston for discharging refrigerant into the chamber;
A refrigerant inlet that is provided integrally with the main body housing, and in which the suction chamber, the discharge chamber, and the valve storage chamber are partitioned, and that introduces a refrigerant from the upstream side of the refrigeration cycle to the suction chamber; and the discharge chamber A header housing provided with a refrigerant outlet for deriving refrigerant discharged from the refrigeration cycle downstream to
A control valve housed in the valve housing chamber, the first refrigerant passage for communicating the discharge chamber and the refrigerant outlet, a main valve for opening and closing the first refrigerant passage, the discharge chamber, and the crank chamber A second refrigerant passage that communicates with the main valve, a sub-valve that opens and closes the second refrigerant passage by relative displacement with respect to the main valve, and drives the sub-valve in the opening and closing direction. A solenoid capable of driving the main valve in the valve opening direction, and controlling the flow rate of the refrigerant led out from the refrigerant outlet through the main valve to be a set flow rate corresponding to the current value supplied to the solenoid A control valve to
A pipe portion extending through the discharge chamber in the header housing and connecting the outlet on the downstream side of the main valve in the valve storage chamber and the refrigerant outlet;
A variable capacity compressor characterized by comprising:   2. The variable capacity according to claim 1, wherein an outlet on the downstream side of the main valve in the valve housing chamber is provided at a height position where the refrigerant liquefied in the header housing may be accumulated. Compressor.   The said piping part is comprised by the groove part formed in the said header housing, and the cover member assembled | attached so that the groove part may be covered, and forming a pipe line, The Claim 1 or 2 characterized by the above-mentioned. Variable capacity compressor. While the inlet port opened to the discharge chamber at the end of the first refrigerant passage is provided at a height position where the refrigerant liquefied in the header housing may be accumulated,
The groove includes a first groove that communicates the outlet on the downstream side of the main valve and the refrigerant outlet, and a second groove that communicates the discharge chamber and the inlet port.
The cover member seals the entire first groove portion, while at least opening the upper end portion of the second groove portion and sealing at least a height at which the liquefied refrigerant may accumulate in the header housing. The variable capacity compressor according to claim 3, wherein the variable capacity compressor is stopped.   As the main valve, the control valve is connected to and separated from the valve seat from the downstream side with the valve seat formed in the first refrigerant passage and being biased in the valve closing direction by the biasing member. The sub-valve is a cylindrical body that receives a solenoid force in the valve opening direction and contacts and separates the main valve body as a movable valve seat, and one opening thereof is in contact with and separated from the main valve body. A valve body that communicates with the inlet port that opens to the discharge chamber and the other opening communicates with the communication port that communicates with the crank chamber. The variable capacity compressor according to any one of claims 1 to 4, further comprising a sub-valve element that can be transmitted as an urging force in the valve opening direction of the main valve element.

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