JP2014118938A - Variable displacement swash plate type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To supply into a suction chamber cooling medium containing lubricating oil discharged into a discharge chamber without causing a trouble in adjusting the valve opening of a valve element.SOLUTION: A capacity control valve 50 includes a driving force transmitter 59 to be driven by an electromagnetic solenoid 52, and a valve element 60 provided in the driving force transmitter 59 for adjusting the opening of a supply passage 70. The capacity control valve 50 further includes a pressure sensitive chamber 58 in which a pressure sensitive body 61 (a bellows 62) is stored to be expanded/contracted in the moving direction of the driving force transmitter 59 when sensing a pressure in a suction chamber 31, to adjust the valve opening of the valve element 60, a communication passage 75 communicating the supply passage 70 with the suction chamber 31, not via the pressure sensitive chamber 58, and a grooved part 74 provided in the communication passage 75.

Description

  The present invention relates to a variable displacement swash plate compressor.

  In a variable capacity swash plate compressor equipped with a crank chamber that houses a swash plate with a variable tilt angle, the swash plate tilt angle decreases as the crank chamber pressure increases, and the swash plate tilt angle decreases as the crank chamber pressure decreases. growing. When the tilt angle of the swash plate decreases, the stroke of the piston decreases and the discharge capacity decreases. When the tilt angle of the swash plate increases, the stroke of the piston increases and the discharge capacity increases.

  For adjusting the crank chamber pressure, for example, a capacity control valve disclosed in Patent Document 1 is used. The capacity control valve disclosed in Patent Document 1 includes a valve casing. A pressure-sensitive space communicating with the suction chamber is provided at one end in the valve casing, and a bellows for receiving the suction pressure from the suction chamber is disposed in the pressure-sensitive space. A valve chamber that communicates with the discharge chamber is formed in the valve casing, and a valve body that opens and closes a communication passage that communicates the discharge chamber and the crank chamber is accommodated in the valve chamber. Furthermore, a pressure sensitive rod is provided in the valve casing. One end of the pressure sensitive rod is in contact with the support member of the bellows, and the other end is in contact with the valve body.

  A fixed iron core that slidably supports the shaft portion of the valve body is disposed on the other end side in the valve casing, and a plunger is provided on the opposite side of the fixed iron core from the valve body. . A tube is attached to the valve casing so as to cover the plunger and the fixed iron core. A plunger chamber is defined by the fixed iron core and the tube. The plunger chamber and the pressure sensitive space communicate with each other via a communication path. A solenoid that applies an electromagnetic force to the gap between the plunger and the fixed iron core is disposed in the tube. And when the electromagnetic force from a solenoid acts on the clearance gap between a plunger and a fixed iron core, a valve body will be pressed in the direction which closes the communicating path which connects a discharge chamber and a crank chamber.

  The bellows expands and contracts by sensing the suction pressure from the suction chamber, and the expansion and contraction of the bellows is used for positioning the valve element via the pressure sensitive rod to adjust the valve opening of the valve element. It contributes to. Then, by adjusting the valve opening of the valve body, the opening of the communication passage that connects the discharge chamber and the crank chamber is adjusted, and the amount of refrigerant flowing from the discharge chamber to the crank chamber is adjusted. The pressure of is adjusted. As a result, the inclination angle of the swash plate is changed, and the stroke of the piston, that is, the discharge capacity is changed.

  The variable capacity swash plate compressor is incorporated in an external refrigerant circuit (refrigeration cycle) of a vehicle air conditioner. The external refrigerant circuit includes a condenser that condenses the refrigerant compressed by the variable capacity swash plate compressor, an expansion valve that expands the refrigerant condensed by the condenser, and an evaporator that evaporates the refrigerant expanded by the expansion valve. It consists of. Further, in the variable capacity swash plate compressor, lubricating oil is used for lubricating each sliding portion inside, and a part of the lubricating oil is contained in the refrigerant in a mist form. . Here, when the lubricating oil is discharged to the external refrigerant circuit together with the refrigerant when the refrigerant compressed by the variable capacity swash plate compressor is discharged and circulated to the external refrigerant circuit, the lubricating oil is discharged to the external refrigerant circuit. It adheres to the inner wall of the evaporator and prevents heat exchange in the external refrigerant circuit.

  Therefore, in a variable capacity swash plate compressor, an oil separator that separates the lubricating oil contained in the refrigerant from the refrigerant is used in order to prevent the lubricating oil from being discharged together with the refrigerant to the external refrigerant circuit. Is disclosed in Patent Document 2. The oil separator separates lubricating oil from the refrigerant discharged into the discharge chamber after compression. The lubricating oil separated from the refrigerant by the oil separator is stored in an oil storage chamber formed in the cylinder block. The variable capacity swash plate compressor is provided with an oil passage that communicates the oil storage chamber and the suction chamber. Further, in the cylinder block, an attachment hole that forms a part of the oil passage is provided at the inlet of the oil passage on the oil storage chamber side, and a throttle member is inserted into the attachment hole. By this throttle member, the amount of lubricating oil supplied from the oil storage chamber to the suction chamber via the oil passage is narrowed down, and depletion of the lubricating oil in the oil storage chamber is prevented. Then, the lubricating oil stored in the oil storage chamber is supplied to the suction chamber through the throttle member and the oil passage, and is used for lubricating each sliding portion inside the variable capacity swash plate compressor.

JP 2003-301773 A JP 2010-96167 A

  However, in the variable displacement swash plate compressor of Patent Document 2, a throttle member is used as a configuration for supplying lubricating oil to the suction chamber. Further, a mounting hole is provided in the cylinder block for mounting the throttle member. Since it forms, the structure has become complicated. Therefore, for example, it is conceivable to supply the lubricating oil separated from the refrigerant by the oil separator to the suction chamber using a capacity control valve having an existing configuration as a variable capacity swash plate compressor.

  Here, in the capacity control valve of Patent Document 1, the discharge pressure from the discharge chamber acts on the valve chamber, and the suction pressure from the pressure sensitive space acts on the plunger chamber. Therefore, the refrigerant containing the lubricating oil supplied from the discharge chamber to the valve chamber flows from the valve chamber toward the plunger chamber and flows into the pressure sensitive space. Then, the bellows that expands and contracts by sensing the suction pressure from the suction chamber is affected by the pressure of the refrigerant containing the lubricating oil flowing into the pressure-sensitive space, which causes a problem in adjusting the valve opening of the valve element. May occur. As a result, the amount of refrigerant flowing from the discharge chamber to the crank chamber does not become a desired amount, and the pressure in the crank chamber does not become a desired pressure, and as a result, a desired discharge capacity cannot be obtained. There is a fear.

  The present invention has been made to solve the above-mentioned problems, and its object is to include lubricating oil discharged into the discharge chamber without causing a problem in adjusting the valve opening of the valve body. Another object of the present invention is to provide a variable capacity swash plate compressor that can supply the refrigerant to the suction chamber.

  In order to achieve the above object, according to the first aspect of the present invention, pistons are respectively housed in a plurality of cylinder bores formed in the cylinder block so as to be able to reciprocate, and a driving force is obtained from the rotating shaft in the crank chamber. And a swash plate that is tiltable in the axial direction with respect to the rotation shaft. The piston is moored on the swash plate. A compression chamber is defined in the cylinder bore by the piston. A suction chamber and a discharge chamber communicate with the chamber, and the refrigerant is sucked into the compression chamber from the suction chamber by the reciprocating motion of the piston, and the refrigerant in the compression chamber is compressed and discharged into the discharge chamber. The refrigerant containing the lubricating oil discharged to the discharge chamber is disposed in the supply passage for supplying the crank chamber, and the opening of the supply passage is adjusted so that the front of the discharge chamber is adjusted. A variable displacement swash plate compressor having a displacement control valve for adjusting a supply amount of refrigerant including lubricating oil to a crank chamber, wherein the displacement control valve is a driving force transmission body driven by an electromagnetic solenoid And a valve body that is provided in the driving force transmission body and adjusts the opening degree of the supply passage, and expands and contracts in the moving direction of the driving force transmission body by sensing the pressure in the suction chamber. A pressure sensing chamber in which a pressure sensing element for adjusting the valve opening is accommodated; a communication passage that communicates the supply passage and the suction chamber without passing through the pressure sensing chamber; and a throttling portion provided in the communication passage The main point is that

  According to this invention, the refrigerant containing the lubricating oil discharged into the discharge chamber flows into the supply passage and is supplied to the suction chamber via the throttle portion and the communication passage. Therefore, the refrigerant containing the lubricating oil can be supplied to the suction chamber without going through the pressure sensing chamber, and the pressure sensitive body that expands and contracts by sensing the suction pressure from the suction chamber contains the lubricating oil. It is possible to prevent the refrigerant from being affected by the pressure. As a result, the refrigerant containing the lubricating oil discharged into the discharge chamber can be supplied to the suction chamber without causing any trouble in adjusting the valve opening of the valve element.

  According to a second aspect of the present invention, in the first aspect of the present invention, in the communication path, the communication path is opened and closed with the movement of the driving force transmission body, and the valve opening of the valve body is the largest. The gist is to have an on-off valve that is closed when it is large.

  When the valve opening of the valve element is the largest, the supply amount of the refrigerant containing lubricating oil from the discharge chamber to the crank chamber through the supply passage is the largest, the crank chamber pressure is maximum, The inclination angle of the plate is the minimum inclination angle. As a result, the stroke of the piston becomes the smallest, and the compression with the minimum discharge capacity is performed. At this time, since the communication path is closed by the on-off valve, all the refrigerant containing the lubricating oil flowing through the supply path can be supplied to the crank chamber. Therefore, when the compression with the minimum discharge capacity is performed, the communication passage and the supply passage are in communication, and the supply amount of the refrigerant containing lubricating oil to the crank chamber is changed from the supply passage to the communication passage. It can be prevented that the flow is reduced and the compression at the minimum discharge capacity becomes difficult to maintain.

  The refrigerant containing the lubricating oil discharged into the discharge chamber can be supplied to the suction chamber without causing any trouble in adjusting the valve opening of the valve body.

A side sectional view showing a variable capacity type swash plate type compressor in an embodiment. Sectional drawing of the capacity | capacitance control valve which shows the state by which the electric current supply with respect to an electromagnetic solenoid is stopped. The longitudinal cross-sectional view which shows a large diameter part of a driving force transmission body, and a part of press-fit member. Sectional drawing of the capacity | capacitance control valve which shows the state in which current supply with respect to an electromagnetic solenoid is performed. Sectional drawing of the capacity | capacitance control valve in another embodiment.

Hereinafter, an embodiment embodying the present invention will be described with reference to FIGS. A variable capacity swash plate compressor (hereinafter simply referred to as “compressor”) is mounted on a vehicle.
As shown in FIG. 1, the housing H of the compressor 10 includes a cylinder block 11, a front housing 12 joined to the front end surface of the cylinder block 11, and a valve / port forming body 13 on the rear end surface of the cylinder block 11. And a rear housing 14 joined together. In the housing H, a crank chamber 15 is defined in a space surrounded by the cylinder block 11 and the front housing 12. A rotating shaft 16 is rotatably supported on the cylinder block 11 and the front housing 12, and a lug plate 21 is fixed to the rotating shaft 16 in the crank chamber 15 so as to be integrally rotatable.

  A vehicle engine E as an external drive source is operatively connected to the projecting end portion of the rotary shaft 16 from the housing H via a power transmission mechanism PT. In the present embodiment, the power transmission mechanism PT is a constant transmission type clutchless mechanism (for example, a combination of a belt and a pulley).

  The crank chamber 15 houses a swash plate 22 that rotates by obtaining a driving force from the rotary shaft 16 and that can tilt in the axial direction with respect to the rotary shaft 16. The swash plate 22 is slidably supported by the rotary shaft 16 in the crank chamber 15, and the swash plate 22 is urged by a pressing spring 25 in a direction in which the inclination angle is minimized. A hinge mechanism 23 is interposed between the lug plate 21 and the swash plate 22. The swash plate 22 can rotate synchronously with the lug plate 21 and the rotary shaft 16 by the biasing force of the pressing spring 25, the hinge connection with the lug plate 21 via the hinge mechanism 23, and the support of the rotary shaft 16. In addition, the rotary shaft 16 can be tilted with respect to the rotary shaft 16 while being slid in the axial direction.

  A plurality of cylinder bores 11a (only one is shown in the drawing) are provided in the cylinder block 11 so as to surround the rotating shaft 16, and a piston 26 is accommodated in each cylinder bore 11a so as to be able to reciprocate. Yes. Both openings of each cylinder bore 11a are closed by a valve / port forming body 13 and a piston 26, and a compression chamber 24 whose volume is changed according to the reciprocation of the piston 26 is defined in each cylinder bore 11a. Each piston 26 is anchored to the outer peripheral portion of the swash plate 22 via a shoe 29. Then, the rotational movement of the swash plate 22 accompanying the rotation of the rotary shaft 16 is converted into the reciprocating linear movement of the piston 26 via the shoe 29.

  A discharge chamber 30 is annularly defined between the rear housing 14 and the valve / port forming body 13, and a suction chamber 31 is defined inside the discharge chamber 30. Further, the valve / port forming body 13 is formed with a suction port 31h communicating with the suction chamber 31 and a suction valve 31v for opening and closing the suction port 31h, and a discharge port 30h communicating with the discharge chamber 30 and a discharge port A discharge valve 30v that opens and closes 30h is formed.

  The refrigerant in the suction chamber 31 is sucked into the cylinder bore 11a through the suction port 31h and the suction valve 31v by the movement from the top dead center to the bottom dead center of the piston 26. The refrigerant sucked into the cylinder bore 11a is compressed to a predetermined pressure by the movement from the bottom dead center to the top dead center of the piston 26, and is discharged from the discharge port 30h to the discharge chamber 30 by pushing out the discharge valve 30v. .

  In the rear housing 14, a discharge passage 30 a that communicates with the discharge chamber 30 is formed, and a suction passage 31 a that communicates with the suction chamber 31 is formed. The discharge passage 30a and the suction passage 31a are connected by an external refrigerant circuit 40. The external refrigerant circuit 40 includes a condenser 41 connected to the discharge passage 30a, an expansion valve 42 connected to the condenser 41, and an evaporator 43 connected to the expansion valve 42. A passage 31a is connected. The compressor 10 is incorporated in the refrigeration cycle.

  The rear housing 14 is formed with a storage chamber 44 that is a part of the discharge passage 30a. The storage chamber 44 is provided with an oil separator 45 for separating the lubricating oil contained in the refrigerant discharged into the discharge chamber 30. The oil separator 45 includes a separation cylinder 45a that is accommodated in the accommodation chamber 44, and a reservoir 45b that stores lubricating oil separated from the refrigerant. The crank chamber 15 and the suction chamber 31 are connected by a throttle passage 35 that penetrates the cylinder block 11 and the valve / port forming body 13. An electromagnetic capacity control valve 50 is assembled in the rear housing 14.

  As shown in FIG. 2, the valve housing 51 of the capacity control valve 50 includes a first housing 53 in which the electromagnetic solenoid 52 is accommodated, and a cylindrical second housing 54 that is assembled to the first housing 53. . Furthermore, the valve housing 51 includes a cylindrical press-fitting member 55 that is press-fitted into an end wall 54e of the second housing 54 opposite to the first housing 53, and an opening of the press-fitting member 55 that is opposite to the second housing 54. And a covered cylindrical lid portion 56. The press-fitting member 55 is press-fitted into a press-fitting recess 54 a formed in the end wall 54 e of the second housing 54.

  The electromagnetic solenoid 52 has a fixed iron core 52a and a movable iron core 52b that is attracted to the fixed iron core 52a based on excitation by current supply to the coil 52c. The fixed iron core 52 a is provided on the opening side of the first housing 53 on the second housing 54 side, and the movable iron core 52 b is provided on the opposite side of the first housing 53 from the second housing 54. Between the fixed iron core 52a and the movable iron core 52b, a spring 52d that urges the fixed iron core 52a and the movable iron core 52b away from each other is disposed. The electromagnetic force of the electromagnetic solenoid 52 attracts the movable iron core 52b toward the fixed iron core 52a against the biasing force of the spring 52d. The electromagnetic solenoid 52 receives energization control (duty ratio control) of a control computer (not shown).

  A valve chamber 57 is defined between the second housing 54 and the fixed iron core 52 a, and a pressure sensitive chamber 58 is defined between the press-fitting member 55 and the lid portion 56. Further, a cylindrical driving force transmission body 59 is attached to the movable iron core 52b, and can move integrally with the movable iron core 52b. The driving force transmission body 59 is provided with a valve body 60 accommodated in the valve chamber 57. Further, a valve hole 54 h is provided through the end wall 54 e of the second housing 54. The valve body 60 can contact and separate from the end wall 54e of the second housing 54 to open and close the valve hole 54h. The electromagnetic force of the electromagnetic solenoid 52 urges the valve body 60 toward the position where the valve hole 54h is closed against the urging force of the spring 52d.

  Furthermore, the driving force transmission body 59 is continuous with the valve body 60 and has a small diameter portion 591 having a smaller outer diameter than the valve body 60 and a large diameter having a larger outer diameter than the small diameter portion 591 and continuous with the small diameter portion 591. It has a diameter portion 592 and a shaft portion 593 that is continuous with the large diameter portion 592 and has a smaller outer diameter than the large diameter portion 592. A part of the large diameter portion 592 and the shaft portion 593 protrude into the pressure sensitive chamber 58 through the valve hole 54 h and the through hole 55 h of the press-fitting member 55. The large diameter portion 592 blocks communication between the pressure sensitive chamber 58 and the valve chamber 57. Furthermore, an annular gap 594 is left around the small diameter portion 591 inside the valve hole 54 h and the press-fitting member 55.

  A pressure sensitive body 61 is accommodated in the pressure sensitive chamber 58. The pressure sensitive body 61 includes an expandable / contractible bellows 62, a support 63 coupled to the end of the bellows 62 on the lid 56 side, and a pressure receiving body coupled to the end of the bellows 62 on the driving force transmitting body 59 side. 64 and a spring 65 for urging the support 63 and the pressure receiving body 64 away from each other in the bellows 62. The distal end portion of the shaft portion 593 of the driving force transmission body 59 can contact and separate from the pressure receiving body 64. In the pressure sensing chamber 58, a spring 69 that urges the pressure receiving body 64 toward the support 63 is disposed between the pressure receiving body 64 and the press-fitting member 55.

  A communication hole 54r communicating with the valve hole 54h is formed in the end wall 54e of the second housing 54. The communication hole 54r opens in a gap 594 around the small diameter portion 591 in the valve hole 54h. A filter 54f is disposed at the opening of the communication hole 54r opposite to the valve hole 54h. The valve hole 54 h communicates with the reservoir 45 b of the oil separator 45 through the communication hole 54 r and the passage 66. Further, the valve chamber 57 communicates with the crank chamber 15 through a passage 67. Therefore, in the present embodiment, the supply passage that supplies the refrigerant including the lubricating oil discharged to the discharge chamber 30 to the crank chamber 15 by the passage 66, the communication hole 54r, the valve hole 54h, the valve chamber 57, and the passage 67. 70 is formed. The capacity control valve 50 is disposed in the supply passage 70.

  The valve body 60 adjusts the supply amount of the refrigerant containing lubricating oil from the discharge chamber 30 to the crank chamber 15 by adjusting the opening degree of the supply passage 70. The valve body 60 comes into a valve-closing state in which the supply passage 70 is closed by contacting the end wall 54e of the second housing 54, and the supply passage 70 is opened by being separated from the end wall 54e of the second housing 54. The valve opens.

  In the bellows 62, a stopper 63a is integrally formed with the support 63. Further, the pressure receiving body 64 is formed with a stopper 64 a that protrudes toward the stopper 63 a of the support 63. The stopper 63 a of the support body 63 and the stopper 64 a of the pressure receiving body 64 define the shortest length of the bellows 62.

  The pressure sensing chamber 58 communicates with the suction chamber 31 through a passage 68. The bellows 62 expands and contracts in the moving direction of the driving force transmission body 59 according to the suction pressure from the suction chamber 31 received by the surface of the pressure receiving body 64 on the driving force transmission body 59 side. The expansion and contraction of the bellows 62 is used for positioning the valve body 60 and contributes to the adjustment of the valve opening degree of the valve body 60. The valve opening degree of the valve body 60 is determined by the balance of the electromagnetic force generated by the electromagnetic solenoid 52, the urging force of the spring 52d, and the urging force in the direction in which the pressure sensing body 61 opens the valve body 60.

  As shown in FIG. 3, a groove 74 is formed on the outer peripheral surface of the large-diameter portion 592 of the driving force transmission body 59. The groove 74 is formed on a part of the outer peripheral surface of the large diameter portion 592 in the circumferential direction of the large diameter portion 592. The groove 74 extends linearly from the end surface on the small diameter portion 591 side of the large diameter portion 592 to the middle of the large diameter portion 592 toward the shaft portion 593 side.

  As shown in FIG. 2, the capacity control valve 50 has a communication passage 75 that communicates the supply passage 70 and the suction chamber 31 without passing through the pressure sensing chamber 58. The communication path 75 includes a first communication path 71 formed between the press-fit member 55 and the press-fit recess 54 a, a second communication path 72 formed in the press-fit member 55, and a through hole 55 h of the press-fit member 55. Has been. The second communication path 72 has one end communicating with the first communication path 71 and the other end opening toward the through hole 55h. The communication passage 75 communicates with the suction chamber 31 through the passage 73.

Next, the operation of this embodiment will be described.
FIG. 4 shows a state in which current is supplied to the electromagnetic solenoid 52 (duty ratio is greater than 0, hereinafter referred to as ON operation). When the compressor 10 is turned on, the movable iron core 52b is attracted toward the fixed iron core 52a against the urging force of the spring 52d by the electromagnetic force generated by the electromagnetic solenoid 52, and the driving force transmitting body 59 is covered with the lid portion. Move to 56 side. Then, the valve body 60 comes into contact with the end wall 54 e of the second housing 54. Then, the valve body 60 is closed, and the flow of the refrigerant containing the lubricating oil discharged into the discharge chamber 30 to the crank chamber 15 through the supply passage 70 is blocked. As a result, the pressure in the crank chamber 15 is lowered, the inclination angle of the swash plate 22 is increased, and the discharge capacity is increased.

  In the ON operation, when the current supply to the electromagnetic solenoid 52 becomes large, the inclination angle of the swash plate 22 becomes the maximum inclination angle, the stroke of the piston 26 becomes the largest, and the compression with the maximum discharge capacity is performed.

  Further, as the driving force transmission body 59 moves, the large diameter portion 592 moves to the lid portion 56 side, so that the groove portion 74 and the communication path 75 communicate with each other. Then, the communication path 75 and the supply path 70 communicate with each other via the gap 594 and the groove 74. The refrigerant containing lubricating oil separated from the refrigerant by the separation cylinder 45 a of the oil separator 45 flows into the supply passage 70. At this time, foreign matters such as dust contained in the lubricating oil are removed by the filter 54f. The refrigerant containing the lubricating oil that has flowed into the supply passage 70 is supplied to the suction chamber 31 through the gap 594, the groove 74, the communication passage 75, and the passage 73. At this time, the amount of the refrigerant containing the lubricating oil supplied from the supply passage 70 to the suction chamber 31 is narrowed down by the groove 74. Therefore, the groove portion 74 functions as a throttle portion provided in the communication path 75.

  As a result, the refrigerant containing the lubricating oil separated from the refrigerant by the separation cylinder 45a of the oil separator 45 is supplied to the suction chamber 31 without passing through the pressure sensing chamber 58, and the bellows 62 contains the lubricating oil. It is prevented from being influenced by the pressure of the refrigerant. The lubricating oil supplied to the suction chamber 31 is used for lubricating each sliding portion inside the compressor 10.

  Further, when the refrigerant compressed in the compression chamber 24 is discharged and circulated to the external refrigerant circuit 40, the lubricating oil is prevented from being discharged together with the refrigerant to the external refrigerant circuit 40. Therefore, it is suppressed that this lubricating oil adheres to the inner wall of the evaporator 43 of the external refrigerant circuit 40 and hinders heat exchange in the external refrigerant circuit 40.

  FIG. 2 shows a state in which current supply to the electromagnetic solenoid 52 is stopped (duty ratio is 0, hereinafter referred to as OFF operation). When the compressor 10 is turned off, the movable iron core 52b is separated from the fixed iron core 52a by the biasing force of the spring 52d. The valve body 60 is separated from the end wall 54e of the second housing 54 and is in a valve open state in which the supply passage 70 is opened. At this time, the valve opening degree of the valve body 60 is the largest. Therefore, the supply amount of the refrigerant containing lubricating oil from the discharge chamber 30 to the crank chamber 15 via the supply passage 70 is the largest, and the pressure in the crank chamber 15 is the maximum.

  At this time, the space between the communication path 75 and the groove 74 is sealed by the large diameter portion 592. For this reason, the communication path 75 is closed by the large diameter portion 592. As a result, all the refrigerant containing the lubricating oil flowing through the supply passage 70 is supplied to the crank chamber 15. Further, the refrigerant in the crank chamber 15 flows out from the throttle passage 35 only to the suction chamber 31. Thereby, the inclination angle of the swash plate 22 becomes the minimum inclination angle, the stroke of the piston 26 becomes the smallest, and the compression with the minimum discharge capacity is performed.

  Since the communication passage 75 is closed by the large-diameter portion 592, the communication passage 75 and the supply passage 70 communicate with each other when the compression with the minimum discharge capacity is performed, and the crank chamber 15 is lubricated. The supply amount of the refrigerant containing oil is reduced by the amount flowing from the supply passage 70 to the communication passage 75, and it is prevented that it is difficult to maintain the compression with the minimum discharge capacity. Therefore, in the present embodiment, the large diameter portion 592 functions as an on-off valve that opens and closes the communication path 75 as the driving force transmission body 59 moves.

  Further, even when the discharge capacity is larger than the minimum discharge capacity and smaller than the maximum discharge capacity (hereinafter referred to as small capacity operation), the gap between the communication path 75 and the groove 74 is sealed by the large diameter portion 592. That is, in the ON operation state, the communication path 75 is closed by the large diameter portion 592 when the inclination angle of the swash plate 22 is larger than the minimum inclination angle. For this reason, when the compression in the small capacity operation is performed, the supply of the refrigerant containing the lubricating oil discharged to the discharge chamber 30 to the suction chamber 31 through the supply passage 70 is not performed. As a result, it is possible to prevent the pressure in the suction chamber 31 from increasing in the small capacity operation and the pressure in the pressure sensing chamber 58 from increasing, and a stable small capacity operation can be maintained.

In the above embodiment, the following effects can be obtained.
(1) The capacity control valve 50 includes a driving force transmission body 59 driven by the electromagnetic solenoid 52 and a valve body 60 that is provided in the driving force transmission body 59 and adjusts the opening degree of the supply passage 70. Further, the capacity control valve 50 is accommodated in a pressure sensitive body 61 (bellows 62) that adjusts the valve opening degree of the valve body 60 by expanding and contracting in the moving direction of the driving force transmission body 59 by sensing the pressure in the suction chamber 31. The pressure sensing chamber 58, the communication passage 75 that communicates the supply passage 70 and the suction chamber 31 without passing through the pressure sensing chamber 58, and the groove 74 provided in the communication passage 75. According to this, the refrigerant containing the lubricating oil discharged into the discharge chamber 30 flows into the supply passage 70 and is supplied to the suction chamber 31 through the groove 74 and the communication passage 75. Therefore, the refrigerant containing the lubricating oil can be supplied to the suction chamber 31 without passing through the pressure sensing chamber 58, and the pressure sensitive body 61 that expands and contracts by sensing the suction pressure from the suction chamber 31 is lubricated. It can be prevented from being affected by the pressure of the refrigerant containing the working oil. As a result, the refrigerant containing the lubricating oil discharged into the discharge chamber 30 can be supplied to the suction chamber 31 without causing any trouble in the adjustment of the valve opening degree of the valve body 60.

  (2) The communication path 75 is closed by the large diameter portion 592 when the valve opening degree of the valve body 60 is the largest. When the valve opening degree of the valve body 60 is the largest, the supply amount of the refrigerant containing lubricating oil from the discharge chamber 30 to the crank chamber 15 via the supply passage 70 is the largest, and the pressure in the crank chamber 15 is maximized. Thus, the inclination angle of the swash plate 22 is the minimum inclination angle. As a result, the stroke of the piston 26 becomes the smallest, and compression with the minimum discharge capacity is performed. At this time, since the communication passage 75 is closed by the large diameter portion 592, all of the refrigerant containing the lubricating oil flowing through the supply passage 70 can be supplied to the crank chamber 15. Therefore, when the compression with the minimum discharge capacity is performed, the communication passage 75 and the supply passage 70 communicate with each other, and the supply amount of the refrigerant containing the lubricating oil to the crank chamber 15 is the supply passage 70. Therefore, it is possible to prevent the compression with the minimum discharge capacity from becoming difficult to maintain.

  (3) The large diameter portion 592 opens and closes the communication path 75 as the driving force transmission body 59 moves. According to this, for example, the configuration of the capacity control valve 50 is compared with a configuration in which the on-off valve that opens and closes the communication path 75 is configured to open and close with the movement of the driving body different from the movement of the driving force transmission body 59. Can be simplified.

  (4) A filter 54f is disposed at the opening of the communication hole 54r. According to this, foreign matter such as dust contained in the lubricating oil can be removed by the filter 54 f, and thus foreign matter such as dust can be prevented from entering the capacity control valve 50. As a result, it is possible to prevent foreign matters such as dust from getting into each sliding portion inside the capacity control valve 50 and deteriorating the slidability of each sliding portion.

In addition, you may change the said embodiment as follows.
In the embodiment, the communication path 75 and the supply path 70 may always communicate with each other. For example, as shown in FIG. 5, the small diameter portion 591 of the driving force transmission body 59 is provided with an annular flange portion 595. The flange portion 595 has an opening position on the valve hole 54 h side in the through hole 55 h of the press-fitting member 55 and an opening position on the opposite side of the first communication path 71 of the second communication path 72 in the through-hole 55 h of the press-fit member 55. It is arranged to be movable between. Further, an annular clearance 596 is left around the collar portion 595. The flange 595 and the large diameter portion 592 in the gap 594 are always in communication with the second communication path 72. Therefore, the communication path 75 and the supply path 70 are always in communication with each other through the clearance 596 and the flange portion 595 and the large diameter portion 592 in the gap 594.

  The refrigerant containing lubricating oil separated from the refrigerant by the separation cylinder 45 a of the oil separator 45 flows into the supply passage 70. The refrigerant containing the lubricating oil that has flowed into the supply passage 70 is supplied to the suction chamber 31 via the clearance 596 and between the flange portion 595 and the large diameter portion 592 in the gap 594, the communication passage 75, and the passage 73. The At this time, the amount of refrigerant containing lubricating oil supplied from the supply passage 70 to the suction chamber 31 is narrowed down by the clearance 596. Therefore, the clearance 596 functions as a throttle portion provided in the communication path 75. According to this, the refrigerant containing the lubricating oil separated from the refrigerant by the oil separator 45 can be efficiently supplied to the suction chamber 31 without passing through the pressure sensitive chamber 58.

  In the embodiment, the shape of the groove 74 is not particularly limited. Further, for example, it may be an annular groove formed over the entire outer peripheral surface of the large-diameter portion 592, or may be formed by cutting a part of the outer peripheral surface of the large-diameter portion 592 into a flat surface. It may be a groove.

  In the embodiment, the oil separator 45 may be deleted. In this case, for example, it is preferable that the supply passage 70 communicates with the position where the lubricating oil is relatively large in the discharge chamber 30.

  In the embodiment, the power transmission mechanism PT may be a clutch mechanism (for example, an electromagnetic clutch) that can select transmission and interruption of power by electric control from the outside.

  DESCRIPTION OF SYMBOLS 10 ... Compressor (variable capacity type swash plate type compressor), 11 ... Cylinder block, 11a ... Cylinder bore, 15 ... Crank chamber, 16 ... Rotating shaft, 22 ... Swash plate, 24 ... Compression chamber, 26 ... Piston, 30 ... Discharge Chamber 31, suction chamber 50, capacity control valve 52 solenoid valve 58 pressure-sensitive chamber 59 drive force transmission body 60 valve body 61 pressure-sensitive body 70 supply passage 74 throttle Groove part functioning as a part, 75... Communication path, 592. Large diameter part functioning as an on-off valve, 596. Clearance functioning as a throttle part.

Claims (2)

Pistons are respectively housed in a plurality of cylinder bores formed in the cylinder block so as to be able to reciprocate,
The crank chamber receives a driving force from the rotation shaft and rotates, and a swash plate that can tilt in the axial direction with respect to the rotation shaft is housed.
The piston is moored to the swash plate,
A compression chamber is defined by the piston in the cylinder bore,
A suction chamber and a discharge chamber communicate with the compression chamber,
Refrigerant is sucked into the compression chamber from the suction chamber by the reciprocating motion of the piston, and the refrigerant in the compression chamber is compressed and discharged into the discharge chamber.
The refrigerant containing the lubricating oil discharged into the discharge chamber is disposed in a supply passage that supplies the crank chamber, and the opening of the supply passage is adjusted to transfer the refrigerant from the discharge chamber to the crank chamber. A variable capacity swash plate compressor having a capacity control valve for adjusting a supply amount of refrigerant containing lubricating oil,
The capacity control valve is
A driving force transmission body driven by an electromagnetic solenoid;
A valve body that is provided in the driving force transmission body and adjusts the opening of the supply passage;
A pressure-sensitive chamber containing a pressure-sensitive body that expands and contracts in the moving direction of the driving force transmitting body by adjusting the pressure of the suction chamber and adjusts the valve opening of the valve body;
A communication passage that communicates the supply passage and the suction chamber without passing through the pressure sensing chamber;
A variable capacity swash plate compressor having a throttle portion provided in the communication path.   The open / close valve is provided in the communication path, which opens and closes the communication path with the movement of the driving force transmission body and is closed when the valve opening of the valve body is the largest. Item 2. The variable capacity swash plate compressor according to Item 1.