JP2007023900A - Variable displacement compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement compressor capable of sufficiently cooling a shaft seal member. <P>SOLUTION: In the variable displacement compressor 10, a suction chamber 30 is partitioned and formed in an outer circumference side of a delivery chamber 31. A supply passage formed separately from a gas passage from the delivery chamber 31 to an external cooling circuit 40 establishes communication between the delivery chamber 31 and a crank chamber 15 via a shaft seal chamber 20 having a lip seal 21 of a drive shaft 16 stored therein. A part of the supply passage is provided to adjoin the suction chamber 30. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a variable displacement compressor that varies the discharge capacity by changing the inclination angle of a swash plate.

  In this type of variable capacity compressor (hereinafter simply referred to as a compressor), the refrigerant gas in the discharge chamber is supplied to the crank chamber via a supply passage, and the refrigerant gas in the crank chamber is supplied via a discharge passage. Is discharged to the suction chamber to adjust the pressure in the crank chamber, and the inclination angle of the swash plate is adjusted by the pressure adjustment. A control valve is provided on the supply passage, and the amount of refrigerant gas supplied to the crank chamber is adjusted by adjusting the opening of the control valve. By adjusting the inclination angle of the swash plate, the stroke amount of the piston is adjusted, and the discharge capacity of the compressor is adjusted.

  In the compressor housing, a shaft seal chamber is provided in the outer peripheral portion of the drive shaft, and the shaft seal chamber has a shaft for preventing leakage of refrigerant gas along the peripheral surface of the drive shaft. A seal member is accommodated. Since the shaft seal member is always in sliding contact with the peripheral surface of the rotating drive shaft, heat is generated during operation of the compressor. In the compressor, a configuration for cooling the shaft seal member is provided in order to suppress deterioration due to the shaft seal member becoming a high temperature state due to heat generation (see, for example, Patent Document 1).

That is, the shaft seal chamber is provided on the supply passage, and the refrigerant gas is supplied from the discharge chamber to the crank chamber via the supply passage. The refrigerant gas is depressurized by the control valve and, after the temperature is lowered, is supplied to the crank chamber via the shaft seal chamber. For this reason, the refrigerant gas is sprayed onto the shaft seal member in the shaft seal chamber, and the shaft seal member is cooled by the refrigerant gas, so that the deterioration due to the high temperature of the shaft seal member is suppressed.
JP-A-4-179874

  However, in the compressor disclosed in Patent Document 1, since the temperature of the refrigerant gas discharged to the discharge chamber is high, the refrigerant gas is depressurized through the control valve, and the shaft seal chamber has a shaft even if the temperature is lowered. The refrigerant gas sprayed on the seal member is high temperature. For this reason, the cooling effect of the shaft seal member by the refrigerant gas cannot be sufficiently exhibited.

  The present invention has been made to solve the above problems, and an object of the present invention is to provide a variable displacement compressor capable of sufficiently cooling a shaft seal member.

  In order to solve the above problems, the present invention comprises a swash plate that forms a refrigerant circulation circuit with an external refrigerant circuit, and that is variably connected to a drive shaft that is rotatably supported by a housing. A supply passage that is housed in a crank chamber defined in the housing and that communicates the discharge chamber and the crank chamber via a shaft seal chamber that houses a shaft seal member of the drive shaft; The amount of refrigerant gas supplied from the discharge chamber to the crank chamber via the discharge chamber is adjusted by adjusting the opening of a control valve provided on the supply passage, and the refrigerant gas in the crank chamber is sucked into the suction chamber via the discharge passage In the variable capacity compressor in which the discharge angle is varied by controlling the pressure in the crank chamber by controlling the pressure in the crank chamber, the supply passage is a gas from the discharge chamber to the external refrigerant circuit aisle Is another form, a part of the supply passage is adjacent to the suction chamber.

  According to this, the refrigerant gas supplied from the discharge chamber to the crank chamber via the supply passage passes through a part of the supply passage disposed adjacent to the suction chamber in addition to the pressure reduction caused by passing through the control valve. When passing, it is cooled by the low-temperature refrigerant gas in the suction chamber. Then, the cooled refrigerant gas is introduced into the shaft seal chamber through the supply passage, and is sprayed onto the shaft seal member in the shaft seal chamber. Therefore, the temperature of the refrigerant gas introduced into the shaft seal chamber is higher than when the refrigerant gas supplied to the crank chamber through the control valve after being discharged into the discharge chamber is introduced into the shaft seal chamber as it is. Can be lowered. As a result, the shaft seal member can be sufficiently cooled in the shaft seal chamber.

  Furthermore, a gas passage that leads part of the refrigerant gas to the external refrigerant circuit and a passage (supply passage) that leads part of the refrigerant gas to the control valve are formed separately. For this reason, the refrigerant gas discharged to the discharge chamber is led out separately to the external refrigerant circuit and the supply passage, and only the refrigerant gas supplied to the supply passage is cooled by the refrigerant in the suction chamber. Therefore, unlike the configuration in which all the refrigerant gas discharged to the discharge chamber is led out toward the external refrigerant circuit, and all the refrigerant gas is cooled by the refrigerant gas in the suction chamber while being led out toward the external refrigerant circuit. The refrigerant gas in the suction chamber is unlikely to rise in temperature.

The suction chamber may be defined on the outer peripheral side of the discharge chamber, and a part of the supply passage may be disposed on the outer peripheral side of a partition wall that partitions the discharge chamber and the suction chamber. .
The suction chamber is defined on the inner peripheral side of the discharge chamber, and a part of the supply passage is disposed on the inner peripheral side of a partition wall that partitions the discharge chamber and the suction chamber. Also good.

  According to this, the partition wall is interposed between a part of the supply passage and the discharge chamber. For this reason, the refrigerant gas passing through a part of the supply passage is not easily affected by the high-temperature refrigerant gas in the discharge chamber.

Further, a part of the supply passage may be disposed on the outer peripheral side of the partition wall that divides the discharge chamber and the suction chamber and on the outer peripheral side of the suction chamber.
According to this, a suction chamber and further a partition wall are interposed between a part of the supply passage and the discharge chamber, and a part of the supply passage is disposed at a position farthest from the discharge chamber. . For this reason, the refrigerant gas passing through a part of the supply passage is not affected by the high-temperature refrigerant gas in the discharge chamber, and the refrigerant gas passing through a part of the supply passage is directly absorbed by the refrigerant gas in the suction chamber. To be cooled. Therefore, the refrigerant gas that passes through a part of the supply passage can be efficiently cooled by the refrigerant gas in the suction chamber.

Further, a part of the supply passage may be disposed across the suction chamber.
According to this, the refrigerant in the suction chamber is in contact with the entire outer peripheral surface of a part of the supply passage that crosses the suction chamber. For this reason, as for a part of supply channel | path, all the outer peripheral surfaces are cooled with the refrigerant | coolant in a suction chamber.

A part of the supply passage may be provided downstream of the control valve on the supply passage.
According to this, the refrigerant gas is depressurized and lowered in temperature by the control valve, and then cooled by the refrigerant in the suction chamber. For this reason, in addition to the pressure reduction by the control valve, the refrigerant gas in a part of the supply passage can be effectively cooled by the cooling by the refrigerant in the suction chamber.

Further, a part of the supply passage may be provided in the drive shaft.
According to this, the refrigerant gas in the crank chamber passes through the discharge passage between the outer peripheral surface of the drive shaft and a part of the supply passage, and is sucked while insulating between the outer peripheral side of the drive shaft and the supply passage. Discharged into the room. Therefore, the refrigerant gas in the supply passage can be kept at a lower temperature, and the cooling effect of the shaft seal member can be further enhanced by spraying the low-temperature refrigerant gas onto the shaft seal member.

  According to the present invention, the shaft seal member can be sufficiently cooled.

(First embodiment)
Hereinafter, a first embodiment in which the present invention is embodied in a variable capacity compressor (hereinafter simply referred to as a “compressor”) will be described with reference to FIGS. 1 and 2.

  FIG. 1 is a longitudinal sectional view of a compressor 10 according to the first embodiment. In FIG. 1, the left side is the front of the compressor 10, and the right side is the rear of the compressor 10. As shown in FIG. 1, the compressor 10 includes a cylinder block 11, a front housing 12 joined and fixed to the front end thereof, and a rear and joined to the rear end of the cylinder block 11 via a valve / port forming body 13. And a housing 14. The cylinder block 11, the front housing 12, and the rear housing 14 constitute a housing for the compressor 10.

  A crank chamber 15 is defined between the cylinder block 11 and the front housing 12. A drive shaft 16 is rotatably supported by the cylinder block 11 and the front housing 12 so as to penetrate the crank chamber 15. The drive shaft 16 has a hollow cylindrical shape with both front and rear ends (left and right ends in FIG. 1) opened inside a first cylindrical shaft 16a having a hollow cylindrical shape with a rear end (right end in FIG. 1) opened. 16b is press-fitted (inserted) to form a double tube. On the front end side (left end side in FIG. 1) of the second shaft 16b, an O-ring 17 is sandwiched between the inner peripheral surface of the first shaft 16a and the outer peripheral surface of the second shaft 16b.

  Further, both sides (left and right sides in FIG. 1) of the drive shaft 16 are rotatably supported by radial bearings 18 and 19. In the front housing 12, a shaft seal chamber 20 is formed in front of the radial bearing 18. A lip seal 21 as a shaft seal member is provided between the front peripheral surface of the drive shaft 16 (first shaft 16a) and the shaft seal chamber 20. The lip seal 21 is always in sliding contact with the rotating drive shaft 16, and the lip seal 21 prevents leakage of refrigerant gas from the crank chamber 15 along the peripheral surface of the drive shaft 16 to the outside of the compressor 10. ing.

  Further, in the cylinder block 11, an accommodation space S is defined on the rear side of the radial bearing 19. The rear side of the drive shaft 16 is accommodated in the accommodation space S.

  In the crank chamber 15, a rotation support 22 is fixed to the drive shaft 16, and the rotation support 22 is fixed to the drive shaft 16 so as to be integrally rotatable. A thrust bearing 23 is provided between the rotary support 22 and the inner wall surface of the front housing 12. A swash plate 24 is accommodated in the crank chamber 15. An insertion hole 24a is formed in the center of the swash plate 24, and the drive shaft 16 is inserted through the insertion hole 24a. A hinge mechanism 25 is interposed between the rotary support 22 and the swash plate 24. The swash plate 24 can be rotated synchronously with the drive shaft 16 and the rotary support 22 by the hinge connection with the rotary support 22 via the hinge mechanism 25 and the support of the drive shaft 16 via the insertion hole 24a. In addition, the inclination angle of the drive shaft 16 can be changed with the sliding movement of the drive shaft 16 in the central axis T direction.

  A plurality (only one is shown in FIG. 1) of cylinder bores 26 are formed in the cylinder block 11 in the front-rear direction at equal angular intervals around the drive shaft 16. A single-headed piston 27 is accommodated in the cylinder bore 26 so as to be movable in the front-rear direction. The front / rear opening of the cylinder bore 26 is closed by the front end face of the valve / port forming body 13 and the piston 27, and a compression chamber (not shown) whose volume changes in accordance with the movement of the piston 27 in the front / rear direction in the cylinder bore 26. )). The piston 27 is anchored to the outer peripheral portion of the swash plate 24 via a pair of shoes 29.

  A suction chamber 30 and a discharge chamber 31 are defined in the rear housing 14 so as to face the valve / port forming body 13. Specifically, the discharge chamber 31 is provided at the center of the rear housing 14, and a partition wall 14 a is formed on the outer peripheral side of the discharge chamber 31. In the rear housing 14, the suction chamber 30 is annularly provided on the outer peripheral side of the discharge chamber 31 through the partition wall 14 a so as to surround the discharge chamber 31. Further, in the rear housing 14, a peripheral wall 14 c of the rear housing 14 is formed on the outer peripheral side of the suction chamber 30. The valve / port forming body 13 is provided with a suction port 32 and a suction valve (not shown) so as to be positioned between the compression chamber and the suction chamber 30. Further, the valve / port forming body 13 is provided with a discharge port 34 and a discharge valve 35 so as to be positioned between the compression chamber and the discharge chamber 31.

  The rear housing 14 has a compartment 50 defined therein, and the compartment 50 and the discharge chamber 31 communicate with each other via a discharge passage 51. The discharge chamber 31 is connected to the external refrigerant circuit 40 via the discharge passage 51 and the storage chamber 50, and the high-pressure refrigerant gas discharged to the discharge chamber 31 passes through the discharge passage 51 and the storage chamber 50. Via the external refrigerant circuit 40. Therefore, the discharge passage 51 and the storage chamber 50 constitute a gas passage that guides the refrigerant gas discharged to the discharge chamber 31 to the external refrigerant circuit 40.

  The refrigerant gas led out to the external refrigerant circuit 40 through the gas passage is cooled by the condenser 40a constituting the external refrigerant circuit 40, depressurized by the expansion valve 40b, and then sent to the evaporator 40c. Evaporated. The return gas from the evaporator 40c (external refrigerant circuit 40) is drawn into the suction chamber 30, and the compressor 10 of this embodiment forms a refrigerant circulation circuit with the external refrigerant circuit 40. ing.

  An oil separator 52 for separating the lubricating oil contained in the refrigerant gas discharged to the discharge chamber 31 from the refrigerant gas is disposed on the gas passage and in the storage chamber 50. The oil separator 52 includes a separation part 52a that separates the lubricating oil from the refrigerant gas by centrifugal separation, and a storage part 52b that temporarily stores the oil separated by the separation part 52a.

  In the oil separator 52, the separation part 52a has a cylindrical shape, and the lower end side of the separation part 52a is opened toward the storage part 52b. The discharge passage 51 is opened to the storage chamber 50 at a position facing the separation portion 52a. Then, the refrigerant gas led out from the discharge chamber 31 to the storage chamber 50 via the discharge passage 51 is swirled in the circumferential direction of the separation portion 52a. Then, the lubricating oil is separated from the refrigerant gas by a centrifugal separation action, and the separated lubricating oil is temporarily stored in the storage portion 52b. A part of the refrigerant gas from which the lubricating oil has been separated passes through the separation part 52a and is supplied to the condenser 40a of the external refrigerant circuit 40 through the storage chamber 50.

  In the rear housing 14, a capacity control valve 60 as a control valve composed of an electromagnetic valve is assembled below the storage chamber 50. The rear housing 14 is formed with a communication passage 59 that communicates the storage portion 52b in the storage chamber 50 with the capacity control valve 60. Further, a first passage 61 is formed in the rear housing 14, and the first passage 61 communicates the capacity control valve 60 and the second passage 62 formed in the valve / port forming body 13. Further, as shown in FIG. 2, a part of the first passage 61 is formed so as to penetrate through the thickness of the peripheral wall 14 c in the rear housing 14. That is, a part of the first passage 61 is disposed on the outer peripheral side of the partition wall 14 a that partitions the suction chamber 30 and the discharge chamber 31, on the outer peripheral side of the suction chamber 30, and adjacent to the suction chamber 30. It is arranged. That is, a part of the first passage 61 is disposed at a position close to the suction chamber 30 so that the refrigerant gas in the first passage 61 is cooled by the refrigerant gas in the suction chamber 30.

  As shown in FIG. 1, the second passage 62 communicates with a third passage 63 formed in the cylinder block 11, and the third passage 63 communicates with the accommodation space S. In the drive shaft 16, a fourth passage 64 is formed inside the second shaft 16 b so as to penetrate in the direction of the central axis T of the drive shaft 16, and the fourth passage 64 communicates with the accommodation space S. ing. Further, a fifth passage 65 communicating with the fourth passage 64 is formed through the drive shaft 16 in the direction of the central axis T of the drive shaft 16 on the front side of the first shaft 16a. The fifth passage 65 communicates with the shaft seal chamber 20 in the front housing 12, and the shaft seal chamber 20 communicates with the crank chamber 15 via a sixth passage 66 formed in the front housing 12. .

  Therefore, the discharge passage 51, the storage chamber 50 (reservoir 52b), the communication passage 59, the capacity control valve 60, the first passage 61, the second passage 62, the third passage 63, the fourth passage 64, the fifth passage 65, The shaft seal chamber 20 and the sixth passage 66 constitute a supply passage for supplying the refrigerant gas in the discharge chamber 31 to the crank chamber 15. The supply passage is formed separately from the gas passage. The opening degree of the supply passage is adjusted by operating the valve mechanism by the operation of the capacity control valve 60. The capacity control valve 60 is connected to a control computer (not shown) that performs current supply control (duty control). The capacity control valve 60 is provided in the supply passage on the upstream side of the first passage 61 disposed adjacent to the suction chamber 30. That is, the first passage 61 constituting a part of the supply passage is disposed on the downstream side of the capacity control valve 60 in the supply passage.

  In the drive shaft 16, a discharge port 16 c is formed between the swash plate 24 and the rotary support 22 in the first shaft 16 a. The discharge port 16c communicates with a seventh passage 67 formed between the inner peripheral surface of the first shaft 16a and the outer peripheral surface of the second shaft 16b. The seventh passage 67 communicates with an eighth passage 68 formed in the cylinder block 11, and the eighth passage 68 communicates with a ninth passage 69 formed in the valve / port forming body 13. The ninth passage 69 communicates with the suction chamber 30, and the discharge port 16 c, the seventh passage 67, the eighth passage 68, and the ninth passage 69 pass the refrigerant in the crank chamber 15 to the suction chamber 30. A discharge passage for discharging is formed. In the housing space S, a lip seal L is interposed between the wall surface of the housing space S and the rear peripheral surface of the second shaft 16b of the drive shaft 16. The lip seal L supplies the lip seal L. The passage and the discharge passage are partitioned and sealed.

Next, the operation of the compressor 10 having the above configuration will be described.
Now, when the drive shaft 16 is rotated by a drive source (not shown), the piston 27 reciprocates in the cylinder bore 26 by the rotation of the swash plate 24. Then, the refrigerant gas circulating in the external refrigerant circuit 40 enters the cylinder bore 26 from the suction chamber 30 through the suction valve and the suction port 32 and is compressed in the compression chamber (not shown). The compressed refrigerant gas is discharged into the discharge chamber 31 through the discharge port 34 and the discharge valve 35. The refrigerant gas discharged into the discharge chamber 31 is led to the oil separator 52 in the storage chamber 50 through the discharge passage 51, and the lubricating oil is separated from the refrigerant gas at the separation portion 52a of the oil separator 52.

  A part of the refrigerant gas from which the lubricating oil has been separated passes through the separation portion 52a, and further passes through the storage chamber 50 and is led to the external refrigerant circuit 40 (condenser 40a). That is, a part of the refrigerant gas is led out to the external refrigerant circuit 40 through the gas passage composed of the storage chamber 50 and the discharge passage 51. Further, a part of the refrigerant gas from which the lubricating oil is separated by the oil separator 52 passes through the storage portion 52b, and is led to the capacity control valve 60 through the communication passage 59 together with the lubricating oil in the storage portion 52b. That is, the refrigerant gas discharged to the discharge chamber 31 is branched into a gas passage to the external refrigerant circuit 40 and a communication passage 59 to the capacity control valve 60, and is separately led to the external refrigerant circuit 40 and the capacity control valve 60. Is done.

  The flow rate of the refrigerant gas supplied to the crank chamber 15 via the supply passage is adjusted by adjusting the opening degree of the refrigerant gas led to the capacity control valve 60. When the refrigerant gas passes through the capacity control valve 60, the refrigerant gas is throttled and depressurized by a valve portion (not shown) of the capacity control valve 60. The refrigerant gas is depressurized by the capacity control valve 60, and the temperature is lowered.

  Further, the refrigerant gas whose temperature has decreased passes through the first passage 61 that constitutes a part of the supply passage, and a portion of the first passage 61 is disposed on the peripheral wall 14 c so as to be adjacent to the suction chamber 30. Yes. The suction chamber 30 is circulated through the external refrigerant circuit 40, and the refrigerant gas having a reduced pressure by the external refrigerant circuit 40 is sucked in. The refrigerant gas in the suction chamber 30 is supplied to the supply passage (first passage). 61) is lower than the refrigerant gas passing through. For this reason, when the refrigerant gas passes through the first passage 61 in the supply passage, the refrigerant gas is cooled by the refrigerant gas in the suction chamber 30. That is, the refrigerant gas discharged to the discharge chamber 31 and passing through a part of the capacity control valve 60 and the supply passage is cooled by the two cooling means of the capacity control valve 60 and the suction chamber 30 and discharged to the discharge chamber 31. The temperature is lower than the later refrigerant gas.

  In the drive shaft 16, the seventh passage 67 is provided on the outer peripheral side of the fourth passage 64 so as to surround the fourth passage 64 constituting a part of the supply passage. For this reason, the refrigerant gas passing through the seventh passage 67 and the inside thereof exhibits a heat insulating effect of blocking the heat on the outer peripheral side of the drive shaft 16 with respect to the fourth passage 64, and the inside of the fourth passage 64 (supply passage). The refrigerant gas can be kept at a low temperature.

  Then, the refrigerant gas whose temperature has passed through the supply passage (the first passage 61) further passes through the second passage 62, the third passage 63, the fourth passage 64, and the fifth passage 65, and the shaft seal chamber. 20 and sprayed onto the lip seal 21 in the shaft seal chamber 20. Then, the lip seal 21 that generates heat by being always in sliding contact with the rotating drive shaft 16 is cooled by the refrigerant gas. Thereafter, the refrigerant gas introduced into the shaft seal chamber 20 is supplied from the sixth passage 66 to the crank chamber 15.

  The refrigerant gas in the crank chamber 15 is discharged from the discharge port 16 c to the discharge passage (seventh passage 67), and further discharged to the suction chamber 30 through the eighth passage 68 and the ninth passage 69. The balance between the refrigerant gas supply amount to the crank chamber 15 via the supply passage and the refrigerant gas discharge amount from the crank chamber 15 via the discharge passage is controlled to determine the crank chamber pressure of the crank chamber 15 ( The crank chamber 15 is regulated). When the crank chamber pressure is changed, the differential pressure between the crank chamber 15 and the cylinder bore 26 via the piston 27 is changed, and the inclination angle of the swash plate 24 is changed. As a result, the stroke of the piston 27 (the discharge capacity of the compressor 10) is adjusted.

According to the above embodiment, the following effects can be obtained.
(1) The discharge chamber 31 and the crank chamber 15 are communicated with each other via a supply passage, and a part of the supply passage (first passage 61) is on the outer peripheral side of the partition wall 14a and the outer peripheral side (peripheral wall) of the suction chamber 30 14c) was placed adjacent to the suction chamber 30. For this reason, the refrigerant gas discharged into the discharge chamber 31 and having passed through the capacity control valve 60 can be cooled by the low-temperature refrigerant gas in the suction chamber 30. The cooled refrigerant gas is introduced into the shaft seal chamber 20 through the supply passage, and is sprayed onto the lip seal 21 in the shaft seal chamber 20. Therefore, the temperature of the refrigerant gas introduced into the shaft seal chamber 20 is lowered as compared with the case where the refrigerant gas discharged into the discharge chamber 31 and passed through the capacity control valve 60 is introduced into the shaft seal chamber 20 as it is. Can do. As a result, the temperature of the refrigerant gas blown to the lip seal 21 in the shaft seal chamber 20 can be lowered, and the lip seal 21 can be sufficiently cooled.

  (2) In the compressor 10, a discharge chamber 31 is defined in the center of the rear housing 14, and an annular suction chamber 30 is defined on the outer peripheral side of the discharge chamber 31 via a partition wall 14a. In the compressor 10, a part of the supply passage (first passage 61) is disposed at a position sandwiching the partition wall 14 a and the suction chamber 30 with respect to the discharge chamber 31. For this reason, the refrigerant gas passing through the first passage 61 is not affected by the high-temperature discharge gas in the discharge chamber 31, and can be directly cooled by the refrigerant gas in the suction chamber 30. . Therefore, the refrigerant gas passing through the first passage 61 can be efficiently cooled by the refrigerant gas in the suction chamber 30.

  (3) In the compressor 10, a part of the supply passage (the first passage 61) is disposed on the peripheral wall 14 c which is the outer peripheral side of the suction chamber 30. For this reason, for example, the refrigerant gas in the suction chamber 30 is directly warmed by the refrigerant gas passing through the first passage 61 as in the case where the first passage 61 is disposed so as to cross the inside of the suction chamber 30. There is nothing. Therefore, it is possible to prevent the cooling efficiency in the external refrigerant circuit 40 from being lowered by warming the refrigerant gas in the suction chamber 30.

  (4) In the rear housing 14, a gas passage for leading a part of the refrigerant gas to the external refrigerant circuit 40 and a communication passage 59 for leading a part of the refrigerant gas to the capacity control valve 60 are branched from the discharge passage 51. Has been. That is, the supply passage is formed separately from the gas passage. For this reason, the refrigerant gas discharged into the discharge chamber 31 is led out separately to the external refrigerant circuit 40 and the supply passage, and only the refrigerant gas supplied to the supply passage is cooled by the refrigerant gas in the suction chamber 30. That is, in the compressor 10 of the present embodiment, all the refrigerant gas discharged to the discharge chamber 31 is led out toward the external refrigerant circuit 40, and all the refrigerant gas is sucked in the middle of being drawn out toward the external refrigerant circuit 40. Unlike the configuration that is cooled by the refrigerant gas in the chamber 30, the temperature of the refrigerant gas in the suction chamber 30 is difficult to increase. As a result, as described in the above (3), it is possible to prevent the cooling efficiency in the external refrigerant circuit 40 from being lowered by heating the refrigerant gas in the suction chamber 30.

  (5) Further, in the rear housing 14, a gas passage for leading a part of the refrigerant gas to the external refrigerant circuit 40 and a communication path 59 (a supply passage) for leading a part of the refrigerant gas to the capacity control valve 60 are separated. Is formed. For this reason, for example, the amount of refrigerant gas led to the external refrigerant circuit 40 and the passage for leading the refrigerant gas discharged to the discharge chamber 31 to the external refrigerant circuit 40 also serve as the supply passage, and It is possible to prevent the passage diameter from increasing in order to secure the supply amount of the refrigerant gas to the crank chamber 15.

  (6) A part of the supply passage (first passage 61) disposed adjacent to the suction chamber 30 in the supply passage is provided on the downstream side of the capacity control valve 60. For this reason, the refrigerant gas is cooled by the refrigerant gas in the suction chamber 30 after being decompressed by the capacity control valve 60. Therefore, the refrigerant gas in the supply passage can be effectively cooled.

  (7) A part of the supply passage (the fourth passage 64 and the fifth passage 65) is provided in the drive shaft 16, and a part of the discharge passage (the seventh passage 67) is a part of the supply passage (the fourth passage). It is provided on the outer peripheral side of the passage 64 and the fifth passage 65). Therefore, the refrigerant gas in the crank chamber 15 passes through a discharge passage between the outer peripheral surface of the drive shaft 16 and a part of the supply passage, and insulates between the outer peripheral side of the drive shaft 16 and the supply passage. While being discharged into the suction chamber 30. Therefore, the refrigerant gas in the supply passage can be kept at a low temperature, and the cooling effect of the lip seal 21 can be further enhanced by spraying the low-temperature refrigerant gas onto the lip seal 21.

(Second Embodiment)
Next, a second embodiment in which the present invention is embodied in a variable capacity compressor (hereinafter simply referred to as “compressor”) will be described with reference to FIG. In addition, since 2nd Embodiment is the structure which changed the position of the supply path and discharge path of 1st Embodiment, the overlapping description is abbreviate | omitted about the same part.

  As shown in FIG. 3, the drive shaft 16 of the second embodiment does not have a double-pipe structure composed of a first shaft 16a and a second shaft 16b, and is formed in a columnar shape. A first passage 71 communicating with the capacity control valve 60 is formed in the rear housing 14, and the first passage 71 communicates with a second passage 72 formed in the cylinder block 11. A part of the first passage 71 is disposed on the outer peripheral side of the partition wall 14 a that partitions the suction chamber 30 and the discharge chamber 31, and is adjacent to the suction chamber 30. It is arranged at the position to do. That is, a part of the first passage 71 is disposed at a position where the refrigerant gas passing through the first passage 71 can be cooled by the refrigerant gas in the suction chamber 30. The second passage 72 communicates with a third passage 73 formed in the front housing 12, and the third passage 73 communicates with the shaft seal chamber 20.

  The shaft seal chamber 20 communicates with the crank chamber 15 via a fourth passage 74 formed in the front housing. Therefore, the discharge passage 51, the storage chamber 50 (reservoir 52b), the communication passage 59, the capacity control valve 60, the first passage 71, the second passage 72, the third passage 73, the shaft seal chamber 20 and the fourth passage 74 are A supply passage for supplying the refrigerant gas in the discharge chamber 31 to the crank chamber 15 is configured. The cylinder block 11 and the valve / port forming body 13 are formed with a discharge passage 77 that allows the crank chamber 15 and the suction chamber 30 to communicate with each other and discharges the refrigerant gas in the crank chamber 15 to the suction chamber 30.

Therefore, according to 2nd Embodiment, in addition to the effect as described in (1)-(6) of 1st Embodiment, the following effects can be acquired.
(8) In the second embodiment, the supply passage is formed in the housing of the compressor 10 (the cylinder block 11, the front housing 12, and the rear housing 14). For this reason, the supply passage is cooled by outside air outside the housing of the compressor 10. Therefore, the temperature of the refrigerant gas sprayed on the lip seal 21 can be lowered, and the lip seal 21 can be sufficiently cooled.

(Third embodiment)
Next, a third embodiment in which the present invention is embodied in a variable capacity compressor (hereinafter simply referred to as “compressor”) will be described with reference to FIGS. 4 and 5. The third embodiment has a configuration in which the positions of the discharge chamber and the suction chamber of the first embodiment are reversed and the positions of the supply passage and the discharge passage are changed. Is omitted.

  As shown in FIG. 4, a suction chamber 30 is provided at the center of the rear housing 14. On the other hand, in the rear housing 14, a partition wall 14 a is formed on the outer peripheral side of the suction chamber 30. In the rear housing 14, a discharge chamber 31 is annularly provided on the outer peripheral side of the suction chamber 30 through the partition wall 14 a so as to surround the suction chamber 30. The rear housing 14 has a discharge port 31a communicating with the discharge chamber 31. The discharge chamber 31 is connected to the external refrigerant circuit 40 through the discharge port 31a. The high-pressure refrigerant gas discharged to the discharge chamber 31 is led out to the external refrigerant circuit 40 from the discharge port 31a. For this reason, the discharge port 31a constitutes a gas passage.

  A capacity control valve 60 is assembled to the rear housing 14. The rear housing 14 is formed with a discharge passage 80 that allows the discharge chamber 31 and the capacity control valve 60 to communicate with each other. Further, a first passage 81 is formed in the rear housing 14, and the first passage 81 communicates the capacity control valve 60 and the second passage 82 formed in the valve / port formation body 13.

  As shown in FIG. 5, in the rear housing 14, a part of the first passage 81 penetrates the partition wall 14a. A part of the first passage 81 is disposed on the inner peripheral side of the partition wall 14 a that partitions the discharge chamber 31 and the suction chamber 30, and a part of the first passage 81 is located adjacent to the suction chamber 30. It is arranged. A part of the first passage 81 is disposed at a position where the refrigerant gas passing through the first passage 81 can be cooled by the refrigerant gas in the suction chamber 30.

  As shown in FIG. 4, the second passage 82 communicates with a third passage 83 formed in the cylinder block 11, and the third passage 83 communicates with a fourth passage 84 formed in the front housing 12. ing. The fourth passage 84 communicates with the shaft seal chamber 20. The shaft seal chamber 20 communicates with the crank chamber 15 via a fifth passage 85 formed in the front housing 12. Therefore, the discharge passage 80, the capacity control valve 60, the first passage 81, the second passage 82, the third passage 83, the fourth passage 84, the shaft seal chamber 20, and the fifth passage 85 supply the refrigerant gas in the discharge chamber 31. A supply passage for supplying the crank chamber 15 is configured. Further, the cylinder block 11 and the valve / port formation body 13 are formed with a discharge passage 87 through which the crank chamber 15 and the suction chamber 30 communicate, and the refrigerant in the crank chamber 15 is discharged to the suction chamber 30.

Therefore, according to the third embodiment, the same effects as those described in (1) and (3) to (6) of the first embodiment can be obtained.
In addition, you may change this embodiment as follows.

  In the first or second embodiment, the two-dot chain line in FIGS. 1 and 3, and further, as shown in FIG. 6, the first passages 61 and 71 constituting a part of the supply passage are provided on the partition wall 14 a. It may be disposed so as to cross the inside of the suction chamber 30 on the outer peripheral side, and a part of the first passages 61 and 71 may be disposed adjacent to the suction chamber 30. With this configuration, the refrigerant in the suction chamber 30 comes into contact with all the outer peripheral surfaces of the first passages 61 and 71. For this reason, all the outer peripheral surfaces of the first passages 61 and 71 are cooled by the refrigerant in the suction chamber 30.

  In the first or second embodiment, as shown in FIG. 7, a part of the first passages 61 and 71 constituting a part of the supply passage is replaced with the inner wall surface of the peripheral wall 14c that is the outer peripheral side of the partition wall 14a. You may arrange in. Or as shown in FIG. 8, you may arrange | position a part of 1st channel | paths 61 and 71 which comprise a part of supply channel | path to the outer wall surface of this division wall 14a used as the outer peripheral side of the division wall 14a. . If comprised in this way, compared with the case where a part of 1st channel | paths 61 and 71 are penetrated and formed in the thickness of the surrounding wall 14c or the partition wall 14a, the outer peripheral surface of the 1st channel | paths 61 and 71 will be inhaled. The area in contact with the refrigerant gas in the chamber 30 increases. For this reason, the refrigerant gas passing through the first passages 61 and 71 can be efficiently cooled by the refrigerant gas in the suction chamber 30.

  In the third embodiment, as shown in FIG. 9, a part of the first passage 81 constituting a part of the supply passage is crossed in the suction chamber 30 on the inner peripheral side of the partition wall 14a. It may be arranged so that a part of the first passage 81 is adjacent to the suction chamber 30. With this configuration, the refrigerant in the suction chamber 30 comes into contact with the entire outer peripheral surface of the first passage 81. For this reason, the entire outer peripheral surface of the first passage 81 is cooled by the refrigerant in the suction chamber 30.

In each embodiment, the capacity control valve 60 may be provided on the supply passage on the downstream side of the suction chamber 30.
In the first embodiment, only the fourth passage 64 and the fifth passage 65 may be formed in the drive shaft 16, while the discharge port 16c and the seventh passage 67 may be deleted. That is, the drive shaft 16 may have a configuration in which only a part of the supply passage is provided therein and a part of the discharge passage is not provided. In this case, a discharge passage is provided in the cylinder block 11.

The oil separator 52 may be omitted, and in this case, the refrigerant gas discharged to the discharge chamber 31 may be directly led to the external refrigerant circuit 40 and the capacity control valve 60.
In the third embodiment, the first passage 81 that constitutes a part of the supply passage is traversed inside the suction chamber 30, and the supply passage is provided in the drive shaft 16 to connect the crank chamber 15 and the discharge chamber 31. You may make it communicate.

Next, the technical idea that can be grasped from the above embodiment and other examples will be described below.
(1) A part of the supply passage and the discharge passage is provided in the drive shaft, and the discharge passage in the drive shaft is provided between the supply passage in the drive shaft and the outer peripheral surface of the drive shaft. The variable displacement compressor according to any one of claims 1 to 7, wherein the drive shaft is formed in a double tubular shape.

The longitudinal cross-sectional view which shows the capacity | capacitance variable type compressor of 1st Embodiment. FIG. 2 is a cross-sectional view taken along line 2-2 of FIG. 1 illustrating the variable capacity compressor of the first embodiment. The longitudinal cross-sectional view which shows the capacity | capacitance variable type compressor of 2nd Embodiment. The longitudinal cross-sectional view which shows the capacity | capacitance variable type compressor of 3rd Embodiment. FIG. 5 is a cross-sectional view taken along line 5-5 of FIG. 4 showing a variable capacity compressor according to a third embodiment. Sectional drawing of the capacity | capacitance variable type compressor which shows another example of the arrangement | positioning position of a part of supply channel | path. Sectional drawing of the capacity | capacitance variable type compressor which shows the other example of the arrangement | positioning position of a part of supply channel | path. Sectional drawing of the capacity | capacitance variable type compressor which shows the other example of the arrangement | positioning position of a part of supply channel | path. Sectional drawing of the capacity | capacitance variable type compressor which shows another example of the arrangement | positioning position of a part of supply channel | path.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Variable displacement compressor, 11 ... Cylinder block which comprises housing, 12 ... Front housing which comprises housing, 14 ... Rear housing which comprises housing, 14a ... Partition wall, 15 ... Crank chamber, 16 ... Drive shaft, 16c: discharge port constituting part of the discharge passage, 20 ... shaft seal chamber constituting part of the supply passage, 21 ... lip seal as a shaft seal member, 24 ... swash plate, 30 ... suction chamber, 31 ... discharge Chamber, 31a ... discharge port constituting gas passage, 40 ... external refrigerant circuit, 50 ... storage chamber constituting part of supply passage and gas passage, 51 ... discharge passage constituting part of supply passage and gas passage, 59 ... Communication passage constituting a part of the supply passage, 60 ... Capacity control valve as a control valve, 61-66 ... First to sixth passages constituting a part of the supply passage, 67-69 ... Discharge passage Seventh to 9 passages constituting a part. 71 to 74: first to fourth passages constituting part of the supply passage, 77 ... discharge passage, 80 ... discharge passage constituting part of the supply passage, 81 to 85 ... first constituting part of the supply passage. 1st to 5th passage, 87... Discharge passage.

Claims (7)

A swash plate that constitutes a refrigerant circulation circuit with an external refrigerant circuit and is variably connected to a drive shaft rotatably supported by the housing is accommodated in a crank chamber defined in the housing. ,
Refrigerant supplied to the crank chamber from the discharge chamber via the supply passage, having a supply passage communicating the discharge chamber and the crank chamber via the shaft seal chamber in which the shaft seal member of the drive shaft is accommodated The amount of gas is adjusted by adjusting the opening of a control valve provided on the supply passage, and the refrigerant gas in the crank chamber is discharged to the suction chamber through the discharge passage to control the pressure in the crank chamber. In a variable capacity compressor that changes the discharge angle by changing the inclination angle of the swash plate,
The variable capacity compressor, wherein the supply passage is formed separately from a gas passage from the discharge chamber to the external refrigerant circuit, and a part of the supply passage is adjacent to the suction chamber. 2. The suction chamber is defined on an outer peripheral side of the discharge chamber, and a part of the supply passage is disposed on an outer peripheral side of a partition wall that partitions the discharge chamber and the suction chamber. The variable capacity compressor described. The suction chamber is partitioned and formed on an inner peripheral side of the discharge chamber, and a part of the supply passage is disposed on an inner peripheral side of a partition wall that partitions the discharge chamber and the suction chamber. The variable capacity compressor according to 1. The variable capacity compressor according to claim 2, wherein a part of the supply passage is disposed on an outer peripheral side of the suction chamber. The variable capacity compressor according to claim 2 or 3, wherein a part of the supply passage is disposed across the suction chamber. The variable capacity compressor according to any one of claims 1 to 5, wherein a part of the supply passage is provided on a downstream side of a control valve on the supply passage. The variable capacity compressor according to any one of claims 1 to 6, wherein a part of the supply passage is provided in the drive shaft.

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