KR100756578B1 - Variable displacement compressor - Google Patents

Abstract

(Problem) To provide a variable displacement compressor capable of sufficiently cooling the shaft seal member.

(Solution means) In the variable displacement compressor 10, the suction chamber 30 is partitioned on the outer circumferential side of the discharge chamber 31. The supply passage formed separately from the gas passage from the discharge chamber 31 to the external refrigerant circuit 40 is cranked with the discharge chamber 31 through the shaft seal chamber 20 in which the lip seal 21 of the drive shaft 16 is accommodated. The thread 15 is connected in series. A part of the supply passage is arranged to be adjacent to the suction chamber 30.

compressor

Description

Variable displacement compressor {VARIABLE DISPLACEMENT COMPRESSOR}

BRIEF DESCRIPTION OF THE DRAWINGS It is a longitudinal cross-sectional view which shows the variable displacement compressor of 1st Embodiment.

FIG. 2 is a cross-sectional view taken along the line 2-2 of FIG. 1 showing the variable displacement compressor of the first embodiment. FIG.

3 is a longitudinal sectional view showing the variable displacement compressor of the second embodiment.

Fig. 4 is a longitudinal sectional view showing the variable displacement compressor of the third embodiment.

Fig. 5 is a cross-sectional view taken along line 5-5 of Fig. 4 showing the capacity variable compressor of the third embodiment.

6 is a cross-sectional view of a variable displacement compressor showing another example of an arrangement position of a part of a supply passage.

7 is a cross-sectional view of a variable displacement compressor showing another example of an arrangement position of a part of a supply passage.

8 is a cross-sectional view of a variable displacement compressor showing another example of an arrangement position of a part of a supply passage.

9 is a cross-sectional view of a variable displacement compressor showing another example of an arrangement position of a part of a supply passage.

[Description of the code]

10: variable capacity compressor

11: Cylinder block making up the housing

12: front housing constituting the housing

14: rear housing constituting the housing

14a: partition wall

15: crankcase

16: drive shaft

16c: outlet that forms part of the outlet passage

20: Axial seal chamber forming part of the supply passage

21: Lip seal as shaft seal member

24: Saphan

30: suction chamber

31: discharge chamber

31a: discharge port constituting the gas passage

40: external refrigerant circuit

50: storage chamber constituting part of supply passage and gas passage

51: discharge passage forming part of the supply passage and the gas passage

59: communication passages forming part of the supply passage

60: displacement control valve as a control valve

61 to 66: first to sixth passages forming part of the supply passage

67 to 69: seventh to ninth passages that form part of the discharge passage

71 to 74: first to fourth passages that form part of the supply passage

77: discharge passage

80: discharge passage forming part of the supply passage

81 to 85: first to fifth passages constituting part of the supply passage

87: discharge passage

(Patent Document 1) JP 4-179874 A

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

In this type of variable displacement compressor (hereinafter, simply referred to as a compressor), the refrigerant gas of the discharge chamber is supplied to the crank chamber through the supply passage, and the refrigerant gas of the crank chamber is supplied to the suction chamber through the discharge passage. It discharges and adjusts the pressure in a crank chamber, and the inclination angle of a swash plate is adjusted by the pressure control. 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 degree of the control valve. In addition, by adjusting the inclination angle of the swash plate, the stroke amount of the piston is adjusted to adjust the discharge capacity of the compressor.

Further, in the housing of the compressor, a shaft seal chamber is formed in the outer circumferential portion of the drive shaft, and the shaft seal member accommodates the shaft seal member for preventing leakage of refrigerant gas along the circumferential surface of the drive shaft. Since the shaft seal member is always in sliding contact with the circumferential surface of the rotating drive shaft, the shaft seal member generates heat during operation of the compressor. In the compressor, a configuration is provided in which the shaft seal member is cooled in order to suppress deterioration caused by the shaft seal member becoming a high temperature state due to heat generation (see Patent Document 1, for example).

That is, the shaft seal chamber is formed on the supply passage, and the refrigerant gas is supplied from the discharge chamber to the crank chamber through the supply passage. The refrigerant gas is depressurized by the control valve, and after the temperature is lowered, the refrigerant gas is supplied to the crank chamber through the shaft seal chamber. For this reason, the refrigerant gas is injected to the shaft seal member in the shaft seal chamber, the shaft seal member is cooled by the refrigerant gas, and the deterioration accompanying the high temperature of the shaft seal member is suppressed.

By the way, in the compressor disclosed in Patent Document 1, since the temperature of the refrigerant gas discharged into the discharge chamber is high, the refrigerant gas is depressurized through the control valve, and the refrigerant gas injected into the shaft seal member in the shaft seal chamber even if the temperature drops. High temperature. For this reason, the cooling effect of the shaft sealing member by refrigerant gas could not be fully exhibited.

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

In order to solve the above problems, the present invention provides a swash plate which constitutes a refrigerant circulation circuit together with an external refrigerant circuit and is connected with a variable inclination angle with respect to a drive shaft rotatably supported by the housing in a crank chamber partitioned in the housing. A supply passage communicating with the discharge chamber and the crank chamber through an axial seal chamber in which the shaft seal member of the drive shaft is accommodated, and through the supply passage, an amount of refrigerant gas supplied from the discharge chamber to the crank chamber on the supply passage. Variable capacity for adjusting by opening degree of the installed control valve, changing the inclination angle of the swash plate by varying the inclination angle of the swash plate by controlling the pressure of the crank chamber by discharging the refrigerant gas of the crank chamber to the suction chamber through the discharge passage; In the compressor, the supply passage is an external refrigerant from the discharge chamber. It is formed separately from the gas passage to a circuit, and a part of the supply passage is adjacent to the said suction chamber.

According to this, the refrigerant gas supplied from the discharge chamber to the crank chamber through the supply passage is depressurized by passing through the control valve, and in addition to being reduced in pressure when passing through a part of the supply passage disposed adjacent to the suction chamber, Cooled by refrigerant gas. Then, the cooled refrigerant gas is introduced into the shaft seal chamber through the supply passage, and is injected into the shaft seal member from the shaft seal chamber. Therefore, the temperature of the refrigerant gas introduced into the shaft seal chamber can be lowered as compared with the case where the refrigerant gas supplied to the crank chamber through the control valve after being discharged to the discharge chamber is directly introduced into the shaft seal chamber. As a result, the shaft sealing member can be sufficiently cooled in the shaft sealing chamber.

In addition, a gas passage for drawing a part of the refrigerant gas to the external refrigerant circuit and a passage (supply passage) for drawing a 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 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 of the refrigerant gas discharged into the discharge chamber is directed toward the external refrigerant circuit and all of the refrigerant gas is cooled by the refrigerant gas in the suction chamber while being directed toward the external refrigerant circuit, the refrigerant gas in the suction chamber is different. The temperature of the configuration is hard to rise.

The suction chamber may be partitioned on the outer circumferential side of the discharge chamber, and a part of the supply passage may be disposed on the outer circumferential side of the partition wall that divides the discharge chamber and the suction chamber.

The suction chamber may be partitioned on the inner circumferential side of the discharge chamber, and a part of the supply passage may be disposed on the inner circumferential side of the partition wall that divides the discharge chamber and the suction chamber.

According to this, a partition wall is interposed between a part of supply path and a discharge chamber. For this reason, the refrigerant gas passing through a part of the supply passage is less likely to be affected by the high temperature refrigerant gas in the discharge chamber.

In addition, a part of the said supply passage may be arrange | positioned at the outer peripheral side of the said suction chamber in the outer peripheral side of the partition wall which divides the said discharge chamber and the said suction chamber.

According to this, a suction chamber and a partition wall are interposed between a part of a supply passage and a discharge chamber, and a part of a supply passage is arrange | positioned in the position furthest from a discharge chamber. For this reason, the refrigerant gas passing through part of the supply passage is not affected by the high temperature refrigerant gas in the discharge chamber, and the refrigerant gas passing through part of the supply passage is directly cooled by the refrigerant gas in the suction chamber. Therefore, the refrigerant gas passing through a part of the supply passage can be efficiently cooled by the refrigerant gas in the suction chamber.

In addition, a part of the supply passage may be arranged to traverse the inside of the suction chamber.

According to this, the refrigerant | coolant in a suction chamber contacts the whole outer peripheral surface of a part of the supply passage which traverses the inside of a suction chamber. For this reason, part of the supply passage is cooled by the refrigerant in the suction chamber as a whole of its outer peripheral surface.

A part of the said supply passage may be formed downstream from the control valve on a supply passage.

According to this, the refrigerant gas is cooled by the refrigerant in the suction chamber after depressurizing and lowering the temperature by the control valve. For this reason, in addition to the pressure reduction by a control valve, the refrigerant gas in a part of supply path can be cooled effectively by cooling by the refrigerant | coolant in a suction chamber.

In addition, a part of the supply passage may be formed in the drive shaft.

According to this, the refrigerant gas in the crank chamber passes through the discharge passage between the outer circumferential surface of the drive shaft and a part of the supply passage, and is discharged into the suction chamber while insulating between the outer circumferential side of the drive shaft and the supply passage. 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 injecting the refrigerant refrigerant at low temperature into the shaft seal member.

To practice the invention  Best form for

(1st embodiment)

EMBODIMENT OF THE INVENTION Hereinafter, the 1st Embodiment which actualized this invention with the variable displacement compressor (henceforth simply a "compressor") is demonstrated based on FIG. 1 and FIG.

1 shows a longitudinal cross-sectional view of the compressor 10 of 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 bonded and fixed to the front end thereof, and a valve port forming body 13 at a rear end of the cylinder block 11. The rear housing 14 which is joined and fixed through is provided. The housing of the compressor 10 is configured by the cylinder block 11, the front housing 12, and the rear housing 14.

The crank chamber 15 is partitioned between the cylinder block 11 and the front housing 12. In addition, the drive shaft 16 is rotatably supported by the cylinder block 11 and the front housing 12 through the crank chamber 15. The drive shaft 16 has a hollow cylindrical shape in which front and rear ends (both left and right ends in FIG. 1) are opened inside a first shaft 16a having a hollow cylindrical shape in which a rear end (right end in FIG. 1) is opened. The two shafts 16b are formed into a double tube shape by being press-fitted (inserted). On the front end side (left end side in FIG. 1) of the second shaft 16b, an O ring 17 is fitted between the inner circumferential surface of the first shaft 16a and the outer circumferential surface of the second shaft 16b.

In addition, both sides (left and right sides in FIG. 1) of the drive shaft 16 are rotatably supported by the radial bearings 18 and 19. As shown in FIG. In the front housing 12, the shaft seal chamber 20 is formed on the front side of the radial bearing 18. A lip seal 21 as an axial seal member is formed between the circumferential surface in front of the drive shaft 16 (first shaft 16a) and the axial seal chamber 20. The lip seal 21 is in sliding contact with the rotating drive shaft 16 at all times, and the lip seal 21 cools out of the compressor 10 from the crank chamber 15 along the circumferential surface of the drive shaft 16. Gas leakage is prevented.

Moreover, in the cylinder block 11, the accommodating space S is partitioned in the back side rather than the said radial bearing 19. As shown in FIG. And the rear side of the drive shaft 16 is accommodated in the said accommodation space S. As shown in FIG.

In the crank chamber 15, the rotation support 22 is fixed to the drive shaft 16, and the rotation support 22 is fixed to be rotatable integrally with the drive shaft 16. A thrust bearing 23 is provided between the rotary support 22 and the inner wall surface of the front housing 12. In addition, the swash plate 24 is housed in the crank chamber 15. The insertion through hole 24a is drilled 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 is driven by a hinge connection between the rotary support 22 by the hinge mechanism 25 and by the support of the drive shaft 16 through the insertion hole 24a. 22, the synchronous rotation is possible, and the inclination angle with respect to the drive shaft 16 can be changed while accompanying the slide movement to the center axis T direction of the drive shaft 16. FIG.

In the cylinder block 11, a plurality of cylinder bores 26 (only one is shown in FIG. 1) are formed around the drive shaft 16 in the front-rear direction at equal angle intervals. In the cylinder bore 26, a migrating piston 27 is housed so as to be movable in the front-rear direction. The front and rear openings of the cylinder bore 26 are closed by the front face of the valve port forming body 13 and the piston 27, and the piston 27 moves in the front and rear direction in the cylinder bore 26. Therefore, a compression chamber (not shown) in which the volume changes is partitioned. The piston 27 is fixed to the outer peripheral part of the swash plate 24 via the pair of shoes 29.

In the rear housing 14, the suction chamber 30 and the discharge chamber 31 are formed to face the valve port forming body 13. Specifically, the discharge chamber 31 is formed in the central portion of the rear housing 14, and the partition wall 14a is formed on the outer circumferential side of the discharge chamber 31. In the rear housing 14, the suction chamber 30 is formed in an annular shape so as to surround the discharge chamber 31 on the outer circumferential side of the discharge chamber 31 with the partition wall 14a interposed therebetween. . In the rear housing 14, a peripheral wall 14c of the rear housing 14 is formed on the outer circumferential side of the suction chamber 30. In addition, a suction port 32 and a suction valve (not shown) are provided in the valve port forming body 13 so as to be located between the compression chamber and the suction chamber 30. In addition, 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.

In the rear housing 14, a storage chamber 50 is partitioned, and the storage chamber 50 and the discharge chamber 31 communicate with each other via the discharge passage 51. The discharge chamber 31 is connected to an external refrigerant circuit 40 through the discharge passage 51 and the accommodation chamber 50 so that the high-pressure refrigerant gas discharged into the discharge chamber 31 is discharge passage ( The external refrigerant circuit 40 is led out through the 51 and the storage chamber 50. For this reason, the said discharge passage 51 and the accommodation chamber 50 comprise the gas passage which guides the refrigerant gas discharged | emitted to the discharge chamber 31 to the external refrigerant circuit 40. As shown in FIG.

The refrigerant gas drawn out to the external refrigerant circuit 40 through the gas passage is cooled in the condenser 40a constituting the external refrigerant circuit 40, decompressed by the expansion valve 40b, and then to the evaporator 40c. Transported and evaporated. The gas returned from the evaporator 40c (external refrigerant circuit 40) again is sucked into the suction chamber 30, so that the compressor 10 of the present embodiment circulates with the refrigerant together with the external refrigerant circuit 40. It constitutes a circuit.

An oil separator 52 for separating lubricating oil contained in the refrigerant gas discharged into the discharge chamber 31 from the refrigerant gas is disposed in the storage chamber 50 on the gas passage. The oil separator 52 includes a separating section 52a for separating lubricating oil from the refrigerant gas by centrifugation, and a storage section 52b for storing oil separated at the separating section 52a once.

In the oil separator 52, the separating part 52a has a cylindrical shape, and the lower end side of the separating part 52a is opened toward the storage part 52b. The discharge passage 51 is opened to the storage chamber 50 at a position where the discharge passage 51 meets the separation unit 52a. Then, the refrigerant gas drawn from the discharge chamber 31 through the discharge passage 51 to the storage chamber 50 is pivoted in the circumferential direction of the separating part 52a. Then, the lubricating oil is separated from the refrigerant gas by the centrifugal separation action, and the separated lubricating oil is once stored in the storage 52b. In addition, a part of the refrigerant gas from which the lubricating oil has been separated passes through the separating portion 52a and is supplied to the condenser 40a of the external refrigerant circuit 40 through the storage chamber 50.

In the rear housing 14, below the said storage chamber 50, the capacity | capacitance control valve 60 as a control valve which consists of solenoid valves is attached. And the rear housing 14 is provided with the communication path 59 which connects the storage part 52b and the capacity | capacitance control valve 60 in the said accommodation chamber 50 in communication. Moreover, the 1st channel | path 61 is formed in the rear housing 14, and this 1st channel | path 61 is the 2nd channel | path 62 formed in the displacement control valve 60 and the valve port formation body 13. As shown in FIG. Through one after another. As shown in FIG. 2, a part of the first passage 61 penetrates through the thickness of the circumferential wall 14c in the rear housing 14. That is, a part of the 1st passage 61 is arrange | positioned in the outer peripheral side of the suction chamber 30 in the area | region outside the partition wall 14a which divides the suction chamber 30 and the discharge chamber 31, and a suction is carried out. It is arrange | positioned adjacent to the chamber 30. That is, 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 the third passage 63 formed in the cylinder block 11, and the third passage 63 communicates with the accommodation space S. Doing. In the drive shaft 16, a fourth passage 64 is formed inside the second shaft 16b through the central axis T direction of the drive shaft 16, and the fourth passage 64 is formed in the accommodation space. It communicates with (S). Moreover, in the drive shaft 16, the 5th passage 65 which connects to the said 4th passage 64 in the front of the 1st shaft 16a penetrates in the center axis T direction of the drive shaft 16, and is formed. The fifth passage 65 communicates with the shaft seal chamber 20 in the front housing 12, and the shaft seal chamber 20 passes through the sixth passage 66 formed in the front housing 12. It communicates with the crank chamber 15 in succession.

Thus, the discharge passage 51, the storage chamber 50 (storage portion 52b), the communication passage 59, the displacement control valve 60, the first passage 61, the second passage 62, the third The passage 63, the fourth passage 64, the fifth passage 65, the shaft seal chamber 20, and the sixth passage 66 supply the refrigerant gas of the discharge chamber 31 to the crank chamber 15. The supply passage is formed separately from the gas passage, and the opening passage is adjusted by opening the valve mechanism by the operation of the displacement control valve 60. In addition, a control computer (not shown) that executes current supply control (duty control) is connected to the capacity control valve 60. The capacity control valve 60 is adjacent to the suction chamber 30 in the supply passage. Is formed upstream from the first passage 61 arranged, that is, the first passage 61 constituting a part of the supply passage. And it is disposed on the downstream side of the displacement control valve 60 in the supply passage.

In the drive shaft 16, a discharge port 16c is formed between the swash plate 24 and the rotary support 22 in the first shaft 16a. This discharge port 16c communicates with the seventh passage 67 formed between the inner circumferential surface of the first shaft 16a and the outer circumferential surface of the second shaft 16b. This seventh passage 67 communicates with the eighth passage 68 formed in the cylinder block 11, and the eighth passage 68 is the ninth passage 69 formed in the valve-port forming body 13. It leads to succession. The ninth passage 69 communicates with the suction chamber 30 so that the discharge port 16c, the seventh passage 67, the eighth passage 68, and the ninth passage 69 The discharge passage which discharges the refrigerant | coolant of the crank chamber 15 to the suction chamber 30 is comprised. In the storage space S, a lip seal L is interposed between the wall surface of the storage space S and the rear circumferential surface of the second shaft 16b in the drive shaft 16. The supply passage and the discharge passage are partitioned and sealed by a seal L.

Next, operation | movement of the compressor 10 which has the said structure is demonstrated.

By the way, when the drive shaft 16 rotates by a drive source (not shown), the swash plate 24 rotates and the piston 27 reciprocates in the cylinder bore 26. 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 a compression chamber (not shown). The compressed refrigerant gas is discharged to 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 is discharged from the refrigerant gas in the separating portion 52a of the oil separator 52. Lubricant is separated.

A part of the refrigerant gas from which the lubricating oil is separated passes through the separating portion 52a and passes through the storage chamber 50 to be led to the external refrigerant circuit 40 (condenser 40a). That is, part of the refrigerant gas is led to the external refrigerant circuit 40 through the gas passage formed of the storage chamber 50 and the discharge passage 51. In addition, a part of the refrigerant gas from which the lubricating oil is separated by the oil separator 52 passes through the reservoir 52b and passes through the communication path 59 together with the lubricating oil of the reservoir 52b. ). That is, the refrigerant gas discharged into the discharge chamber 31 is divided into a gas passage to the external refrigerant circuit 40 and a communication path 59 to the capacity control valve 60, so that the external refrigerant circuit 40 and the capacity control valve ( 60).

The flow rate of the refrigerant gas supplied to the crank chamber 15 through the supply passage is adjusted by adjusting the opening degree of the refrigerant gas led to the capacity control valve 60 by the capacity control valve 60. In addition, when the refrigerant gas passes through the capacity control valve 60, the refrigerant gas is depressurized by being tightened by a valve portion (not shown) of the capacity control valve 60. The refrigerant gas is depressurized by the capacity control valve 60 to lower the temperature.

And the refrigerant gas whose temperature fell is passing through the 1st passage 61 which comprises a part of supply passage, and a part of 1st passage 61 is arrange | positioned at the circumferential wall 14c so that it may be adjacent to the suction chamber 30. As shown in FIG. . In the suction chamber 30, a refrigerant gas circulated through the external refrigerant circuit 40 and decompressed by the external refrigerant circuit 40 and lowered in temperature is sucked in. The refrigerant gas in the suction chamber 30 is supplied with a supply passage (first). The temperature is lower than that of the refrigerant gas passing through the one passage 61. 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 passed through the capacity control valve 60 and a part of the supply passage is cooled by two cooling means of the capacity control valve 60 and the suction chamber 30, The temperature is lower than the refrigerant gas after being discharged into the discharge chamber 31.

In the drive shaft 16, the seventh passage 67 is formed on the outer circumferential side of the fourth passage 64 so as to surround the fourth passage 64 constituting a part of the supply passage. Therefore, the refrigerant gas passing through the seventh passage 67 and the inside thereof exerts a heat insulating effect of blocking the outer circumferential side heat of the drive shaft 16 with respect to the fourth passage 64, and thus the fourth passage 64 ( The refrigerant gas in the supply passage) can be kept at a low temperature.

In addition, the refrigerant gas whose temperature has passed through the supply passage (the first passage 61) is further reduced by the second passage 62, the third passage 63, the fourth passage 64, and the fifth passage 65. It is introduced into the shaft seal chamber 20 after passing through, and sprayed on the lip seal 21 in the shaft seal chamber 20. Then, the lip seal 21 which generates heat by always slidingly contacting 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.

In addition, the refrigerant gas in the crank chamber 15 is discharged from the discharge port 16c to the discharge passage (seventh passage 67), and again through the eighth passage 68 and the ninth passage 69, the suction chamber 30 Is discharged. Then, the balance between the amount of refrigerant gas supplied to the crank chamber 15 through the supply passage and the amount of refrigerant gas discharged from the crank chamber 15 through the discharge passage is controlled to determine the crank chamber pressure of the crank chamber 15 ( Pressure of the crank chamber 15 is adjusted). When the crank chamber pressure is changed, the pressure difference in the crank chamber 15 and the cylinder bore 26 through 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 (discharge capacity of the compressor 10) is adjusted.

According to the said embodiment, the following effects can be acquired.

(1) The discharge chamber 31 and the crank chamber 15 are connected to each other through the supply passage, and a part of the supply passage (the first passage 61) is provided on the outer circumferential side of the partition wall 14a, and the suction chamber ( It arrange | positioned adjacent to the suction chamber 30 in the outer peripheral side (circle wall 14c) of 30). For this reason, the refrigerant gas discharged to 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 injected into the lip seal 21 from the shaft seal chamber 20. Therefore, 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, the refrigerant gas introduced into the shaft seal chamber 20 is reduced. Can lower the temperature. As a result, the temperature of the refrigerant gas injected into 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, the discharge chamber 31 is formed in the center of the rear housing 14, and the suction chamber has a ring shape on the outer circumferential side of the discharge chamber 31 with the partition wall 14a therebetween. 30 is partitioned. In this compressor 10, a part of the supply passage (first passage 61) is disposed at a position with the partition wall 14a and the suction chamber 30 interposed with respect to the discharge chamber 31. have. For this reason, the refrigerant gas passing through the first passage 61 can be prevented from being influenced 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 addition, in this compressor 10, a part of the supply passage (the first passage 61) is disposed on the circumferential wall 14c serving as the outer circumferential side of the suction chamber 30. For this reason, for example, as in the case where the first passage 61 is arranged to cross the inside of the suction chamber 30, the refrigerant in the suction chamber 30 is caused by the refrigerant gas passing through the first passage 61. The gas does not warm up directly. Therefore, it is possible to prevent the cooling efficiency in the external refrigerant circuit 40 from lowering as the refrigerant gas in the suction chamber 30 warms up.

(4) The rear housing 14 is discharged with a gas passage for delivering a portion of the refrigerant gas to the external refrigerant circuit 40 and a communication passage 59 for drawing a portion of the refrigerant gas to the capacity control valve 60. It is formed branching off from the passage 51. That is, the supply passage is formed separately from the gas passage. For this reason, the refrigerant gas discharged to the discharge chamber 31 is led to the external refrigerant circuit 40 and the supply passage separately, 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 toward the external refrigerant circuit 40, and the refrigerant gas is discharged toward the external refrigerant circuit 40. Unlike the configuration in which all are cooled by the refrigerant gas in the suction chamber 30, the configuration is difficult to increase the temperature of the refrigerant gas in the suction chamber 30. As a result, as described in the above (3), it is possible to prevent the cooling efficiency in the external refrigerant circuit 40 from decreasing by cooling the refrigerant gas in the suction chamber 30.

(5) Moreover, in the rear housing 14, the gas passage which leads a part of refrigerant gas to the external refrigerant circuit 40, and the communication path 59 which leads a part of the refrigerant gas to the capacity control valve 60 ( The supply passage) is formed separately. For this reason, for example, the passage of the refrigerant gas discharged into the discharge chamber 31 to the external refrigerant circuit 40 is combined with the supply passage, so that the refrigerant gas to the external refrigerant circuit 40 It is possible to prevent the passage diameter from being greatly reduced in order to secure the leaded amount and 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 formed downstream from the displacement control valve 60. For this reason, after the refrigerant gas is depressurized by the capacity control valve 60, the refrigerant gas is cooled by the refrigerant gas in the suction chamber 30. Therefore, the refrigerant gas in the supply passage can be cooled effectively.

(7) A part of the supply passage (the fourth passage 64 and the fifth passage 65) is formed in the drive shaft 16, and a part of the discharge passage (the seventh passage 67) is a part of the supply passage (the first passage 64). It is formed in the outer peripheral side of 4 channel | path 64 and the 5th channel | path 65. As shown in FIG. For this reason, the refrigerant gas in the crank chamber 15 passes through the discharge passage between the outer circumferential surface of the drive shaft 16 and a part of the supply passage, and insulates the space between the outer circumferential side of the drive shaft 16 and the supply passage 30. ) Is discharged. 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 injecting a low temperature refrigerant gas into the lip seal 21.

(2nd embodiment)

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

As shown in FIG. 3, the drive shaft 16 of 2nd Embodiment does not form the double pipe structure which consists of the 1st shaft 16a and the 2nd shaft 16b, but is formed in the columnar shape. The rear housing 14 is provided with a first passage 71 in communication with the displacement control valve 60, and the first passage 71 communicates with the second passage 72 formed in the cylinder block 11. Doing. A part of the first passage 71 is a peripheral wall 14c serving as an outer circumferential side of the suction chamber 30 on the outer circumferential side of the partition wall 14a that divides the suction chamber 30 and the discharge chamber 31. ), And is disposed at a position adjacent to the suction chamber 30. In other words, a part of the first passage 71 is disposed at a position at which 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 the third passage 73 formed in the front housing 12, and the third passage 73 communicates with the shaft seal chamber 20.

The axial seal chamber 20 is in series with the crank chamber 15 via a fourth passage 74 formed in the front housing. Therefore, the discharge passage 51, the storage chamber 50 (storage portion 52b), the communication passage 59, the displacement control valve 60, the first passage 71, the second passage 72, the third The passage 73, the shaft seal chamber 20, and the fourth passage 74 constitute a supply passage for supplying the refrigerant gas of the discharge chamber 31 to the crank chamber 15. Further, the cylinder block ( 11) and a discharge passage 77 through which the crank chamber 15 and the suction chamber 30 are connected to each other and the valve port forming body 13 to discharge the refrigerant gas of the crank chamber 15 to the suction chamber 30. ) Is formed through.

Therefore, according to 2nd Embodiment, the following effects can be acquired in addition to the effect as described in (1)-(6) of 1st Embodiment.

(8) In 2nd Embodiment, the supply passage was formed in the housing (cylinder block 11, the front housing 12, and the rear housing 14) of the compressor 10. As shown in FIG. For this reason, the supply passage is cooled by the outside air outside the housing of the compressor 10. Therefore, the temperature of the refrigerant gas injected into 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 by a variable displacement compressor (hereinafter, simply referred to as a "compressor") will be described with reference to FIGS. 4 and 5. In the third embodiment, since the positions of the supply passage and the discharge passage are changed by reversing the positions of the discharge chamber and the suction chamber of the first embodiment, overlapping descriptions of the same portions are omitted.

As shown in FIG. 4, the suction chamber 30 is formed in the center part of the rear housing 14. As shown in FIG. On the other hand, in the rear housing 14, the partition wall 14a is formed in the outer peripheral side of the said suction chamber 30. As shown in FIG. In the rear housing 14, the discharge chamber 31 is formed in an annular shape so as to surround the suction chamber 30 on the outer circumferential side of the suction chamber 30 with the partition wall 14a interposed therebetween. In addition, a discharge port 31a is formed in the rear housing 14 through the discharge chamber 31, and the discharge chamber 31 is connected to the external refrigerant circuit 40 through the discharge port 31a. . The high pressure refrigerant gas discharged into the discharge chamber 31 is led to the external refrigerant circuit 40 from the discharge port 31a. For this reason, the discharge port 31a comprises the gas passage.

The rear housing 14 is provided with a capacity control valve 60. The rear housing 14 is provided with a discharge passage 80 through which the discharge chamber 31 and the capacity control valve 60 communicate with each other. Moreover, the 1st channel | path 81 is formed in the rear housing 14, and this 1st channel | path 81 is the 2nd channel | path 82 formed in the displacement control valve 60 and the valve port formation body 13. Through one after another.

In addition, 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 circumferential side of the partition wall 14a that divides the discharge chamber 31 and the suction chamber 30, and a part of the first passage 81 is the suction chamber 30. It is arrange | positioned in the position adjacent to. A part of the first passage 81 is disposed at a position at which 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 the third passage 83 formed in the cylinder block 11, and the third passage 83 is the fourth passage formed in the front housing 12. (84) is connected in succession. In addition, the fourth passage 84 communicates with the shaft seal chamber 20 in series. The shaft seal chamber 20 communicates with the crank chamber 15 via the fifth passage 85 formed in the front housing 12. Therefore, the discharge passage 80, the displacement 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 constitutes a supply passage for supplying the refrigerant gas of the discharge chamber 31 to the crank chamber 15. The crank chamber 15 and the suction chamber 30 are connected to the cylinder block 11 and the valve port forming body 13 to discharge the refrigerant in the crank chamber 15 to the suction chamber 30. The discharge passage 87 is formed through.

Therefore, according to 3rd Embodiment, the effect similar to the effect of (1), (3)-(6) of 1st Embodiment can be acquired.

In addition, you may change this embodiment as follows.

○ 1st or 2nd embodiment WHEREIN: As shown in the dashed-dotted line of FIG. 1 and FIG. 3, and FIG. 6, the 1st channel | path 61 and 71 which comprise a part of a supply channel | part are partition walls 14a May be arranged so as to cross the inside of the suction chamber 30 in the outer region, so that a part of the first passages 61 and 71 are adjacent to the suction chamber 30. If comprised in this way, the refrigerant | coolant in the suction chamber 30 will contact the whole outer peripheral surface of the 1st channel | path 61 and 71. As shown in FIG. For this reason, the entire outer peripheral surface of the first passages 61 and 71 is cooled by the refrigerant in the suction chamber 30.

○ In 1st or 2nd embodiment, as shown in FIG. 7, the peripheral wall 14c which makes a part of 1st channel | path 61 and 71 which comprise a part of supply channel | path become an area | region outside than the partition wall 14a. You may arrange | position to the inner wall surface of the). Alternatively, as shown in FIG. 8, a part of the first passages 61 and 71 constituting a part of the supply passage may be disposed on the outer wall surface of the partition wall 14a serving as the outer circumferential side of the partition wall 14a. do. In such a configuration, the outer peripheral surfaces of the first passages 61 and 71 are more than the case where a part of the first passages 61 and 71 penetrates within the thickness of the circumferential wall 14c or the partition wall 14a. The area of contact with the refrigerant gas in the suction 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 traversed within the suction chamber 30 in the region inside the partition wall 14a. It may arrange | position so that a part of 1st channel | path 81 may adjoin the suction chamber 30. FIG. In such a configuration, the refrigerant in the suction chamber 30 comes into contact with the entire outer circumferential 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, it is good also as a structure which provided the capacity | capacitance control valve 60 downstream from the suction chamber 30 on a supply passageway.

In the first embodiment, only the fourth passage 64 and the fifth passage 65 are 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 structure in which only a part of the supply passage is formed therein and no part of the discharge passage is formed. In this case, the discharge passage is formed in the cylinder block 11.

The oil separator 52 may be omitted, and in this case, the refrigerant gas discharged into 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 constituting a part of the supply passage is allowed to cross the inside of the suction chamber 30, and a supply passage is formed in the drive shaft 16 to provide the crank chamber 15 and The discharge chamber 31 may be connected in series.

Next, the technical idea grasped | ascertained from the said embodiment and another example is added below.

(1) A portion of the supply passage and the discharge passage is formed in the drive shaft, the discharge passage in the drive shaft is formed between the supply passage in the drive shaft and the outer peripheral surface of the drive shaft, the drive shaft is formed in a double tube shape The variable displacement compressor according to any one of claims 1 to 7.

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

Claims (14)

A swash plate which forms a refrigerant circulation circuit together with an external refrigerant circuit and is connected with a variable inclination angle with respect to a drive shaft rotatably supported by the housing is housed in a crank chamber partitioned in the housing, A control valve having a supply passage communicating with the discharge chamber and the crank chamber through a shaft seal chamber in which the shaft seal member of the drive shaft is accommodated, the control valve provided on the supply passage for the amount of refrigerant gas supplied from the discharge chamber to the crank chamber through the supply passage; By adjusting the opening degree of the variable, the refrigerant gas of the crank chamber through the discharge passage to the suction chamber to control the pressure of the crank chamber to change the inclination angle of the swash plate to vary the discharge capacity In The supply passage is formed separately from the gas passage from the discharge chamber to the external refrigerant circuit, and a part of the supply passage is adjacent to the suction chamber and is formed on the suction chamber side rather than the discharge chamber side. Variable displacement compressor. The method of claim 1, The suction chamber is partitioned on an outer circumferential side of the discharge chamber, and a part of the supply passage is disposed in an area outside the partition wall separating the discharge chamber and the suction chamber. The method of claim 1, The suction chamber is partitioned on an inner circumferential side of the discharge chamber, and a part of the supply passage is disposed in an inner region than a partition wall partitioning the discharge chamber and the suction chamber. The method of claim 1, The suction chamber is partitioned on the outer circumferential side of the discharge chamber, and a part of the supply passage is disposed on the outer circumferential side of the partition wall partitioning the discharge chamber and the suction chamber. The method of claim 1, The suction chamber is partitioned on the inner circumferential side of the discharge chamber, and a part of the supply passage is disposed on the inner circumferential side of the partition wall that divides the discharge chamber and the suction chamber. The method of claim 2, A part of said supply passage is a variable displacement compressor arranged on the outer peripheral side of the suction chamber. The method of claim 2 or 3, And a part of the supply passage is disposed across the suction chamber. The method according to any one of claims 1 to 6, And a portion of the supply passage is formed downstream from the control valve on the supply passage. The method according to any one of claims 1 to 6, The other part of the said feed passage is a variable displacement compressor formed in the said drive shaft. The method according to any one of claims 1 to 6, At least a portion of the supply passage and the discharge passage are formed in the drive shaft, the supply passage in the drive shaft communicates with the shaft seal chamber, 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. Variable displacement compressor formed. The method of claim 10, The drive shaft includes a hollow cylindrical first shaft and a hollow cylindrical second shaft inserted into the first shaft, and the discharge passage in the drive shaft includes an inner circumferential surface of the first shaft and the second shaft. And a supply passage in the drive shaft is partitioned by an inner circumferential surface of the second shaft. The method of claim 11, The housing is provided with a compartment for accommodating the rear end of the drive shaft is partitioned, the accommodating space is divided into the supply passage and the discharge passage by a seal member provided on the second shaft. The method of claim 12, And a part of the supply passage is connected to the accommodation space through a valve port forming body. The method according to any one of claims 1 to 6, The housing includes a rear housing having the suction chamber, and a part of the supply passage is formed in the rear housing.

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