JP6020130B2 - Variable capacity swash plate compressor - Google Patents

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.

  When the valve opening of the valve body is the largest, the amount of refrigerant supplied from the discharge chamber to the crank chamber via the communication passage is the largest, the crank chamber pressure is maximum, and the inclination angle of the swash plate is The minimum tilt 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, when the refrigerant containing the lubricating oil supplied from the discharge chamber to the valve chamber is supplied to the suction chamber, the amount of refrigerant supplied to the crank chamber is reduced by the amount supplied to the suction chamber, There is a risk that compression at the minimum discharge capacity may be difficult to maintain.

  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. It is an object of the present invention to provide a variable capacity swash plate compressor that can supply the refrigerant to the suction chamber and prevent the compression at the minimum discharge capacity from becoming difficult to maintain.

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 capacity swash plate type compressor having a displacement control valve for adjusting the supply amount of the refrigerant containing lubricating oil to the crank chamber, the displacement control valve,
A driving force transmission body driven by an electromagnetic solenoid; a valve body that is provided in the driving force transmission body and adjusts an opening of the supply passage; and senses the pressure of the suction chamber to detect the driving force transmission body. A pressure-sensitive body that expands and contracts in the moving direction and adjusts the valve opening of the valve body; a communication path that communicates the supply passage and the suction chamber; a throttle portion provided in the communication path; and the communication path together provided during the valve opening of the valve body is most sizes rather, the is closed to close the communication passage, the valve body is the supply passage when the open state to open the supply passage and a off valve that are opened to open the communicating passage when the closed state of closing the said feeling together with the communication passage is disposed between the supply passage and the suction chamber A pressure sensing chamber in which a pressure body is accommodated, and the pressure sensing chamber and the supply passage. It is summarized as the driving force transmitting member has a through hole to be inserted while being disposed.

  When the valve body is in the closed state, the flow of the refrigerant containing lubricating oil from the discharge chamber to the crank chamber via the supply passage is blocked. This lowers the pressure in the crank chamber, increases the tilt angle of the swash plate, and increases the discharge capacity. At this time, since the on-off valve is opened, the refrigerant containing the lubricating oil discharged into the discharge chamber flows into the supply passage and is supplied to the suction chamber through the throttle portion and the communication passage. The Here, when the valve body is in a closed state, the refrigerant containing the lubricating oil discharged from the discharge chamber is supplied to the suction chamber, and the pressure-sensitive body is affected by the pressure of the refrigerant containing the lubricating oil. Even if it receives, the pressure-sensitive body does not fulfill the function of adjusting the valve opening degree of the valve body. Therefore, the refrigerant containing the lubricating oil discharged to the discharge chamber can be supplied to the suction chamber without causing a problem in the adjustment of the valve opening of the valve body.

  When the valve opening of the valve element is the largest, the supply amount of refrigerant containing lubricating oil from the discharge chamber to the crank chamber via the supply passage is the largest, and the pressure in the crank chamber is maximum. The tilt angle of the swash plate is the minimum tilt 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 on-off valve is closed and the communication passage is closed, all of the refrigerant containing the lubricating oil flowing through the supply passage can be supplied to the crank chamber. Therefore, when the compression with the minimum discharge capacity is performed, the suction chamber and the supply passage communicate with each other through the communication passage, and the supply amount of the refrigerant including lubricating oil to the crank chamber is reduced. It can be prevented that the flow is reduced by the amount flowing into the chamber, and it becomes difficult to maintain the compression with the minimum discharge capacity.

Invention according to claim 2, the inventor smell of claim 1, prior SL-off valve and the throttle portion is provided in the driving force transmitting member which is inserted into the insertion hole, the on-off valve, The gist is to open and close the communication path as the driving force transmitting body moves.

  According to the present invention, for example, the configuration of the capacity control valve is simplified compared to a configuration in which the on-off valve that opens and closes the communication path is configured to open and close with the movement of the driving body different from the movement of the driving force transmission body. Can be

The invention according to claim 3 is summarized in that, in the invention according to claim 2, the throttle portion is a groove portion formed by cutting out a part of the outer surface of the driving force transmitting body.
For example, when the throttle portion is a groove formed by cutting out the entire outer surface of the driving force transmission body, if the driving force transmission body is moved to the pressure sensitive chamber side and the communication path is opened by the on-off valve, When the chamber and the supply passage communicate with each other through the groove portion, the contact portion between the outer surface of the driving force transmitting body and the inner surface of the insertion hole is eliminated. Then, when the communication path is closed by the opening / closing valve, it becomes difficult to move the driving force transmitting body to the side opposite to the pressure sensing chamber so that the opening / closing valve is disposed in the insertion hole. However, according to the present invention, even if the driving force transmitting body is moved to the pressure sensing chamber side, the communication passage is opened by the on-off valve, and the pressure sensing chamber and the supply passage are communicated via the groove portion, the driving force can be obtained. A contact portion between the outer surface of the transmission body and the inner surface of the insertion hole can be left. As a result, when the communication path is closed by the opening / closing valve, the driving force transmission body can be easily moved to the side opposite to the pressure sensing chamber.

  According to the present invention, the refrigerant containing the lubricating oil discharged to the discharge chamber can be supplied to the suction chamber without causing trouble in the adjustment of the valve opening of the valve body, and the minimum discharge capacity Therefore, it is possible to prevent the compression of the image from becoming difficult to maintain.

1 is a side sectional view showing a variable capacity swash plate compressor according to a first 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 2nd housing. Sectional drawing of the capacity | capacitance control valve which shows the state in which the electric current supply with respect to an electromagnetic solenoid is performed. Sectional drawing of the capacity | capacitance control valve which shows the state by which the electric current supply with respect to the electromagnetic solenoid in 2nd Embodiment is stopped. Sectional drawing of the capacity | capacitance control valve which shows the state in which the electric current supply with respect to an electromagnetic solenoid is performed.

(First embodiment)
Hereinafter, a first embodiment of 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, a cylindrical second housing 54 assembled to the first housing 53, and a second housing 54. And a lid 56 having a closed cylindrical shape that closes the opening opposite to the first housing 53.

  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 second housing 54 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. A valve hole 54 h is provided between the valve chamber 57 and the pressure sensitive chamber 58 in the second housing 54. Around the valve hole 54h on the valve chamber 57 side in the second housing 54 is a seat portion 54e with which the end surface of the valve body 60 on the pressure sensing chamber 58 side can come into contact. The valve body 60 can open and close the valve hole 54h by contacting and separating from the seat portion 54e. 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 sensing chamber 58 through the valve hole 54h. Further, an annular gap 594 is left around the small diameter portion 591 in the valve hole 54h.

  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 body 63 is disposed between the pressure receiving body 64 and the second housing 54.

  The second housing 54 is formed with a communication hole 54r communicating with the valve hole 54h. 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 seat 54e of the second housing 54, and the supply passage 70 is opened by being separated from the seat 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 portion 74 is formed by cutting out a part of the outer peripheral surface (outer 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, in the valve hole 54h, a portion of the communication hole 54r closer to the pressure sensing chamber 58 than the opening position on the valve hole 54h side is disposed between the pressure sensing chamber 58 and the supply passage 70. It is an insertion hole 541h through which the large diameter portion 592 is inserted. Therefore, the capacity control valve 50 of the present embodiment includes the communication passage 71 that is formed by the insertion hole 541h and the pressure sensing chamber 58 and that connects the supply passage 70 and the suction chamber 31 via the passage 68.

  The portions other than the groove portion 74 in the large-diameter portion 592 are closed when the valve opening degree of the valve body 60 is the largest to close the communication passage 71 and open when the valve body 60 is in the closed state. Thus, an open / close valve 592s is provided to open the communication passage 71. In the moving direction of the driving force transmission body 59, the seal length L1 between the on-off valve 592s and the insertion hole 541h is smaller than the stroke length L2 of the valve body 60.

Next, the operation of the first 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 transmission body 59 is pressure-sensitive. Move to chamber 58 side. Then, the valve body 60 comes into contact with the seat portion 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, the large diameter portion 592 moves to the pressure sensing chamber 58 side with the movement of the driving force transmission body 59, whereby the on-off valve 592s is opened, and the groove portion 74 and the pressure sensing chamber 58 communicate with each other. Then, the pressure sensitive chamber 58 and the supply passage 70 communicate with each other through the gap 594 and the groove 74. At this time, the contact part of the outer peripheral surface of the large diameter part 592 and the inner peripheral surface of the insertion hole 541h remains. 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 lubricating oil that has flowed into the supply passage 70 is supplied to the suction chamber 31 via the gap 594, the groove 74, the pressure sensing chamber 58, and the passage 68. 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 71.

  Thereby, the refrigerant containing the lubricating oil separated from the refrigerant by the separation cylinder 45 a of the oil separator 45 is supplied to the suction chamber 31. Here, when the valve body 60 is in the closed state, 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, and the bellows 62 is used as the lubricating oil. The bellows 62 does not perform the function of adjusting the valve opening degree of the valve body 60 even if it is affected by the pressure of the refrigerant containing the. Therefore, the refrigerant containing the lubricating oil discharged into the discharge chamber 30 is supplied to the suction chamber 31 without causing a problem in the adjustment of the valve opening degree of the valve body 60.

  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 seat portion 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 on-off valve 592s is closed, and the communication path 71 is closed. 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 71 is closed by the on-off valve 592s, the suction chamber 31 and the supply passage 70 communicate with each other via the communication passage 71 when compression with the minimum discharge capacity is performed, and the crank chamber It is prevented that the supply amount of the refrigerant containing the lubricating oil to 15 is reduced by the amount flowing into the suction chamber 31 and it becomes difficult to maintain the compression with the minimum discharge capacity.

  The communication passage 71 is also closed by the on-off valve 592s 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). That is, in the ON operation state, when the inclination angle of the swash plate 22 is larger than the minimum inclination angle, the communication path 71 is closed by the on-off valve 592s. 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 first 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, a valve body 60 provided in the driving force transmission body 59 and adjusting the opening of the supply passage 70, and the suction chamber 31. It has a pressure sensitive body 61 that expands and contracts in the moving direction of the driving force transmission body 59 by sensing the pressure and adjusts the valve opening degree of the valve body 60. Further, the capacity control valve 50 is provided in the communication passage 71 that communicates the supply passage 70 and the suction chamber 31, the groove portion 74 provided in the communication passage 71, the communication passage 71, and the valve opening of the valve body 60. And an on-off valve 592s that closes when the degree is the highest and opens when the valve body 60 is in the closed state. Therefore, when the valve body 60 is in the closed state, the flow of the refrigerant containing lubricating oil from the discharge chamber 30 to the crank chamber 15 via 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. At this time, since the on-off valve 592s is open, the refrigerant containing the lubricating oil discharged into the discharge chamber 30 flows into the supply passage 70 and is sucked through the groove 74 and the communication passage 71. It is supplied to the chamber 31. Here, when the valve body 60 is in the closed state, the refrigerant containing the lubricating oil discharged from the discharge chamber 30 is supplied to the suction chamber 31, and the pressure sensitive body 61 contains the lubricating oil. Even under the influence of the pressure due to the pressure sensor 61, the pressure sensitive body 61 does not fulfill the function of adjusting the valve opening degree of the valve body 60. Therefore, the refrigerant containing the lubricating oil discharged into the discharge chamber 30 can be supplied to the suction chamber 31 without causing a problem in the adjustment of the valve opening degree of the valve body 60.

  When the valve opening 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 through the supply passage 70 is the largest, and the pressure in the crank chamber 15 is 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 on-off valve 592s is closed and the communication passage 71 is closed, all of the refrigerant including 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 suction chamber 31 and the supply passage 70 communicate with each other via the communication passage 71, and supply of the refrigerant containing lubricating oil to the crank chamber 15 is performed. It can be prevented that the amount is reduced by the amount flowing into the suction chamber 31 and it becomes difficult to maintain the compression with the minimum discharge capacity.

  (2) The on-off valve 592s opens and closes the communication path 71 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 71 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.

  (3) The groove portion 74 is formed by cutting out a part of the outer peripheral surface of the large diameter portion 592 in the circumferential direction of the large diameter portion 592. For example, when the groove portion is a groove portion formed by cutting out the entire outer peripheral surface of the large diameter portion 592, the driving force transmission body 59 is moved to the pressure sensing chamber 58 side, and the communication passage 71 is opened by the on-off valve 592s. Then, the pressure sensitive chamber 58 and the supply passage 70 communicate with each other through the groove portion, so that the contact portion between the outer peripheral surface of the large diameter portion 592 and the inner peripheral surface of the insertion hole 541h is eliminated. Then, when the communication passage 71 is closed by the opening / closing valve 592s, it becomes difficult to move the driving force transmission body 59 to the opposite side of the pressure sensing chamber 58 so that the opening / closing valve 592s is disposed in the insertion hole 541h. . However, according to this, the driving force transmission body 59 is moved to the pressure sensing chamber 58 side, the communication passage 71 is opened by the on-off valve 592s, and the pressure sensing chamber 58 and the supply passage 70 are communicated via the groove 74. Even if it makes it, the contact site | part of the outer peripheral surface of the large diameter part 592 and the inner peripheral surface of the insertion hole 541h can be left. As a result, when the communication passage 71 is closed by the on-off valve 592s, the driving force transmission body 59 can be easily moved to the side opposite to the pressure sensing chamber 58.

  (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.

(Second Embodiment)
Hereinafter, a second embodiment of the present invention will be described with reference to FIGS. In the embodiment described below, the same components as those in the first embodiment described above are denoted by the same reference numerals, and the redundant description thereof is omitted or simplified.

  As shown in FIG. 5, a suction pressure space 82 communicating with the suction chamber 31 through a passage 81 is defined between the second housing 54 and the fixed iron core 52a, and the second housing 54, the lid portion 56A, A pressure sensitive chamber 58 </ b> A communicating with the crank chamber 15 through a passage 83 is defined between them. Further, the second housing 54 is provided with a valve hole 85 having one end opened to the pressure sensing chamber 58A and the other end opened to the suction pressure space 82. The valve hole 85 communicates with the reservoir 45b of the oil separator 45 through the communication hole 54r and the passage 66. Therefore, in the present embodiment, the supply including the coolant containing the lubricating oil discharged to the discharge chamber 30 is supplied to the crank chamber 15 by the passage 66, the communication hole 54r, the valve hole 85, the pressure sensing chamber 58A, and the passage 83. A passage 70A is formed.

  The driving force transmission body 59 is provided with a valve body 60 </ b> A accommodated in the valve hole 85. An end surface of the valve body 60A on the pressure sensing chamber 58A side can come into contact with a seat portion 54E formed between the communication hole 54r and the valve hole 85 in the second housing 54. Then, the valve body 60 </ b> A adjusts the opening of the supply passage 70 </ b> A to adjust the supply amount of the refrigerant containing the lubricating oil from the discharge chamber 30 to the crank chamber 15. 60 A of valve bodies will be in the valve closing state which closes supply passage 70A by contact | abutting to the seat part 54E, and will be in the valve opening state which opens 70 A of supply passages by separating from the seat part 54E.

  The driving force transmission body 59 is formed with a facing portion 86 that faces the end surface of the fixed iron core 52a on the suction pressure space 82 side. A pressure sensitive space 87 is defined between the pressure sensing chamber 58 </ b> A side end face of the driving force transmission body 59 and the pressure receiving body 64. Further, an internal passage 88 is formed in the driving force transmission body 59. One end of the internal passage 88 communicates with the pressure-sensitive space 87, and the other end communicates with the suction pressure space 82 through the space between the facing portion 86 and the fixed iron core 52a. Then, the suction pressure from the suction pressure space 82 is guided to the pressure sensitive space 87 through the internal passage 88.

  The bellows 62 is introduced into the pressure sensing space 87 and 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 side of the driving force transmission body 59. The expansion and contraction of the bellows 62 is used for positioning the valve body 60A and contributes to the adjustment of the valve opening degree of the valve body 60A. The valve opening degree of the valve body 60A 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 of the pressure sensitive body 61 in the direction to open the valve body 60A.

  A groove 74 is formed on the outer peripheral surface of the valve body 60A. The groove 74 is formed by cutting out a part of the outer peripheral surface (outer surface) of the valve body 60A in the circumferential direction of the valve body 60A. The groove 74 extends linearly from the end surface of the valve body 60A on the suction pressure space 82 side toward the pressure sensing chamber 58A to the middle of the valve body 60A.

  In the valve hole 85, a portion of the communication hole 54r closer to the suction pressure space 82 than the opening position on the valve hole 85 side is disposed between the suction pressure space 82 and the supply passage 70A and the valve body 60A is inserted. An insertion hole 89 is formed. Therefore, the capacity control valve 50 according to the present embodiment includes the communication passage 71 </ b> A that is formed by the insertion hole 89 and the suction pressure space 82 and communicates the supply passage 70 and the suction chamber 31 via the passage 81.

  The portions other than the groove portion 74 in the valve body 60A are closed when the valve opening degree of the valve body 60A is the largest to close the communication passage 71A, and are opened when the valve body 60A is in the closed state. The on-off valve 592s opens the communication path 71A. In the moving direction of the driving force transmission body 59, the seal length L1 between the on-off valve 592s and the insertion hole 89 is smaller than the stroke length L2 of the valve body 60A.

Next, the operation of the second embodiment will be described.
FIG. 6 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 transmission body 59 is pressure-sensitive. Move to the chamber 58A side. Then, the valve body 60 </ b> A contacts the seat portion 54 </ b> E of the second housing 54. Then, the valve body 60A 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 70A 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.

  Further, the valve body 60A moves to the pressure sensing chamber 58A side with the movement of the driving force transmission body 59, whereby the on-off valve 592s is opened, and the groove 74 and the communication hole 54r communicate with each other. Then, the suction pressure space 82 and the supply passage 70 </ b> A communicate with each other via the groove 74. At this time, a contact portion between the outer peripheral surface of the valve body 60A and the inner peripheral surface of the insertion hole 89 remains. Then, the refrigerant containing the lubricating oil separated from the refrigerant by the separation cylinder 45a of the oil separator 45 flows into the supply passage 70A. The refrigerant containing the lubricating oil that has flowed into the supply passage 70 </ b> A is supplied to the suction chamber 31 through the groove 74, the suction pressure space 82, and the passage 81. At this time, the amount of the refrigerant containing the lubricating oil supplied from the supply passage 70A to the suction chamber 31 is narrowed down by the groove 74.

  Thereby, the refrigerant containing the lubricating oil separated from the refrigerant by the separation cylinder 45 a of the oil separator 45 is supplied to the suction chamber 31. Here, when the valve body 60A is in the closed state, 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, and the bellows 62 is used as the lubricating oil. The bellows 62 does not perform the function of adjusting the valve opening degree of the valve body 60A. Therefore, the refrigerant containing the lubricating oil discharged to the discharge chamber 30 is supplied to the suction chamber 31 without causing any trouble in adjusting the valve opening of the valve body 60A.

  FIG. 5 shows a state where the 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 60A is separated from the seat portion 54E of the second housing 54, and is in a valve-open state in which the supply passage 70A is opened. At this time, the valve opening degree of the valve body 60A 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 70A is the largest, and the pressure in the crank chamber 15 is the maximum.

  The facing portion 86 of the driving force transmitting body 59 is in contact with the end surface of the fixed iron core 52a on the suction pressure space 82 side, and suction pressure is introduced from the suction pressure space 82 to the pressure sensitive space 87 via the internal passage 88. It is regulated.

  At this time, the on-off valve 592s is closed and the communication path 71A is closed. As a result, all the refrigerant containing the lubricating oil flowing through the supply passage 70 </ b> A 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 71A is closed by the on-off valve 592s, the suction chamber 31 and the supply passage 70A communicate with each other via the communication passage 71A when compression with the minimum discharge capacity is performed. It is prevented that the supply amount of the refrigerant containing the lubricating oil to 15 is reduced by the amount flowing into the suction chamber 31 and it becomes difficult to maintain the compression with the minimum discharge capacity.

  The communication passage 71A is also closed by the on-off valve 592s 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). That is, in the ON operation state, when the inclination angle of the swash plate 22 is larger than the minimum inclination angle, the communication path 71A is closed by the on-off valve 592s. 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 70A 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.

Therefore, according to the second embodiment, the same effects as the effects (1) to (4) of the first embodiment can be obtained.
In addition, you may change the said embodiment as follows.

  In each of the above embodiments, the on-off valve 592s is closed at least when the valve opening degree of the valve bodies 60, 60A is the largest, and is opened when the valve bodies 60, 60A are in the closed state. Just do it.

  (Circle) in each said embodiment, the shape of the groove part 74 is not specifically limited. Further, for example, it may be an annular groove formed over the entire circumference of the large diameter portion 592 or the valve body 60A, or a part of the outer diameter surface of the large diameter portion 592 or the valve body 60A may be a flat surface. It may be a groove formed by cutting into a shape.

  In the above embodiments, the oil separator 45 may be deleted. In this case, for example, it is preferable that the supply passages 70 and 70 </ b> A communicate with each other in the discharge chamber 30 at a relatively large amount of lubricating oil.

In each of the above embodiments, the power transmission mechanism PT may be a clutch mechanism (for example, an electromagnetic clutch) that can select transmission and interruption of power by external electrical control.
Next, the technical idea that can be grasped from the above embodiment and other examples will be described below.

  (A) A pressure-sensitive chamber in which the pressure-sensitive body is accommodated communicates with the crank chamber, and the communication path is disposed between the suction chamber and the supply path, and the driving force transmission body A suction pressure space that communicates with the suction chamber on the side opposite to the pressure sensing chamber in the moving direction, and an insertion hole that is disposed between the suction pressure space and the supply passage and through which the driving force transmission body is inserted. The on-off valve and the throttle portion are provided in the driving force transmission body inserted through the insertion hole, and the on-off valve opens and closes the communication path as the driving force transmission body moves. The variable capacity swash plate compressor according to claim 1.

  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 ... electromagnetic solenoid, 58, 58A ... pressure sensing chamber, 59 ... driving force transmission body, 60, 60A ... valve body, 61 ... pressure sensing body, 70, 70A ... Supply passage, 71, 71A ... communication passage, 74 ... groove portion functioning as a throttle portion, 82 ... suction pressure space, 89, 541h ... insertion hole, 592s ... open / close valve.

Claims (3)

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 body that expands and contracts in the moving direction of the driving force transmission body by sensing the pressure of the suction chamber and adjusts the valve opening of the valve body;
A communication passage communicating the supply passage and the suction chamber;
A throttle provided in the communication path;
Together provided in said communication passage, rather most large, the valve opening of the valve body, and closed the to close the communication passage when the open state to open the supply passage, wherein the valve body is and a said you are open to open the communication path on-off valve when closed to close the supply passage,
The communication path is
A pressure-sensitive chamber disposed between the suction chamber and the supply passage and containing the pressure-sensitive body;
A variable displacement swash plate compressor, which is disposed between the pressure sensing chamber and the supply passage and has an insertion hole through which the driving force transmission body is inserted . Before SL-off valve and the throttle portion is provided in the driving force transmitting member which is inserted into the insertion hole,
The variable capacity swash plate compressor according to claim 1, wherein the on-off valve opens and closes the communication path as the driving force transmission body moves.   The variable capacity swash plate compressor according to claim 2, wherein the throttle part is a groove part formed by cutting out a part of the outer surface of the driving force transmission body.