KR100748915B1 - Refrigerant compressor - Google Patents

Abstract

(Problem) To provide a refrigerant compressor capable of compacting an oil separator while securing a separation capability of lubricating oil.

(Solution means) The oil separator 50 has an inlet port 54a into the separation space S of the refrigerant gas and an outlet port 52c out of the separation space S of the refrigerant gas. The pivot member 52 is arrange | positioned between the sphere 54a and the exit port 52c. The inlet port 54a and the outlet port 52c are arranged such that the direction Z1 of the refrigerant gas from the outlet port 52c is the same direction as the direction Z2 of the introduction of the refrigerant gas into the inlet port 54a. have.

   Refrigerant compressor, compressor

Description

Refrigerant compressor {REFRIGERANT COMPRESSOR}

1 is a longitudinal sectional view showing a refrigerant compressor of the first embodiment.

2 is an enlarged cross-sectional view illustrating an oil separator of the first embodiment.

3 is an enlarged cross-sectional view illustrating the oil separator of the second embodiment.

(A) is a perspective view which shows the spiral channel | path in the oil separator of 2nd Embodiment, (b) is sectional drawing 4b-4b of FIG. 4 (a).

5 is an enlarged cross-sectional view illustrating an oil separator of a third embodiment.

6 is a cross-sectional view showing an oil separator of the background art.

7 is a cross-sectional view showing an oil separator of the background art.

(Explanation of the sign)

M: Axial direction

S: Separation Space

Z1: Derivation direction

Z2: Introduction direction

10: refrigerant compressor

15: crankcase constituting the compression mechanism

16: drive shaft constituting the compression mechanism

18: swash plate constituting the compression mechanism

23: piston constituting the compression mechanism

27: discharge chamber constituting the discharge passage

49: connection passage constituting the discharge passage

50: oil separator

50b: oil outlet

51a: perimeter wall

52: swing member constituting the swing portion

52a: Spiral groove as a means of forced turn

52c, 68, 72c: outlet

54a: inlet

66: protrusion part constituting the turning part

67: spiral passage as a means of forced turn

72: tube part constituting the turning part

74: guide hole as a forced turning means

Patent Document 1: Japanese Unexamined Patent Publication No. 2002-5021

Patent Document 2: Japanese Patent Application Laid-Open No. 2001-165049

This invention relates to the refrigerant | coolant compressor which arrange | positioned the oil separator which isolate | separates the lubricating oil contained in refrigerant gas by turning refrigerant gas along a turning part in a separation space.

In a refrigerant compressor that constitutes a refrigerating circuit and compresses refrigerant gas, the compression mechanism is smoothly operated by incorporating lubricant oil into the refrigerant gas and supplying the lubricant oil to the compression mechanism. In the refrigerant compressor, in order to prevent the lubricating oil from being carried out to the external refrigerant circuit together with the refrigerant gas, an oil separator is formed on the discharge passage of the refrigerant gas (see, for example, Patent Documents 1 and 2). This is because when lubricating oil is carried out to the external refrigerant circuit, the lubricating oil is attached to the inner wall surface of the gas cooler or the evaporator, for example, and the heat exchange efficiency is lowered.

As shown in FIG. 6, the oil separator of patent document 1 has the oil separation chamber 92 which consists of a cylindrical inner cylinder 90 and the cylindrical outer cylinder 91 which surrounds the inner cylinder 90, A separation space 93 is formed between the inner cylinder 90 and the outer cylinder 91. In addition, the lower end 90b of the inner cylinder 90 serves as a gas outlet and communicates with an external refrigerant circuit (not shown). The discharge chamber 94 and the oil separation chamber 92 communicate with each other by the inflow pipe 95. In addition, an oil outlet 97 is formed above the outer cylinder 91, and an oil reservoir 96 communicating with the oil separation chamber 92 via the oil outlet 97 is provided around the oil separation chamber 92. Formed.

And in the refrigerant | coolant compressor provided with the oil separator of the said structure, the refrigerant gas discharged | emitted to the discharge chamber 94 is introduce | transduced into the oil separation chamber 92 via the inflow pipe 95. As shown in FIG. The refrigerant gas introduced into the separation space 93 of the oil separation chamber 92 spirals around the inner cylinder 90. The lubricating oil is separated from the refrigerant gas by the centrifugal force by the spiral turning, and the separated lubricating oil is attached to the inner circumferential surface of the outer cylinder 91. Thereafter, the lubricating oil attached to the inner circumferential surface of the outer cylinder 91 is raised together with the refrigerant gas and flows out from the oil outlet 97 of the outer cylinder 91 to the oil storage chamber 96. On the other hand, the refrigerant gas from which the lubricating oil has been separated is lowered in the inner cylinder 90 and supplied to the external refrigerant circuit from the gas outlet, which is the lower end 90b of the inner cylinder 90.

7, the oil separator described in patent document 2 is formed in the chamber 108 in a housing. The oil separator includes a cylindrical gas having a separation chamber 100 and a bottomed base, and a gas 101 extending downward from the upper opening edge of the separation chamber 100 concentrically with the gas 101. A flanged conduit (102). A passage hole 101a is formed in the side wall of the base 101, and the passage hole 101a communicates with the discharge passage 104 communicating the separation chamber 100 and the discharge chamber 103. The discharge passage 104 is formed through a fixture 106 for fixing the discharge valve to the housing. In addition, a through hole 105 is formed in the bottom wall of the base 101.

And in the refrigerant | coolant compressor provided with the oil separator of the said structure, the refrigerant gas discharged | emitted to the discharge chamber 103 is introduce | transduced into the separation chamber 100 from the discharge passage 104 via the passage hole 101a. The refrigerant gas introduced into the separation chamber 100 rotates around the flanged conduit 102. Then, the lubricating oil is separated from the refrigerant gas by the centrifugal force by the turning, and the separated lubricating oil is attached to the inner circumferential surface of the side wall of the base 101. Thereafter, the lubricating oil is allowed to pass through the through-hole 105 formed in the bottom wall of the separation chamber 100 to stay in the bottom of the chamber 108. On the other hand, the refrigerant gas from which the lubricating oil has been separated passes through the flanged conduit 102 and is supplied to the external refrigerant circuit through another discharge passage.

However, the oil separator described in Patent Document 1 collides the refrigerant gas introduced into the oil separation chamber 92 through the inflow pipe 95 to the inner cylinder 90 so that the flow of the refrigerant gas into the oil separation chamber 92. By changing in the direction orthogonal to the introduction direction of, the refrigerant gas flows along the inner cylinder 90, and is spirally rotated in the separation space 93. For this reason, the flow rate of refrigerant gas introduced into the separation space 93 is lower than before it is introduced into the separation space 93. In order to separate as much lubricating oil as possible from the refrigerant gas at which the flow rate is lowered, it is necessary to make the turning distance of the refrigerant gas longer, and as a result, the length of the inner cylinder 90 and the outer cylinder 91 in the axial direction becomes longer and the oil becomes longer. The separator has become large.

In addition, in the oil separator described in Patent Document 2, the refrigerant gas introduced into the separation chamber 100 through the discharge passage 104 is caused to collide with the flanged conduit 102 so that the flow of the refrigerant gas is separated from the separation chamber. By changing the direction perpendicular to the introduction direction into the (100), the refrigerant gas flows along the flanged conduit 102 and spirally rotates around the flanged conduit 102. For this reason, the flow rate of the refrigerant gas introduced into the separation chamber 100 is lower than before it is introduced into the separation chamber 100. And in order to separate as much lubricating oil as possible from the refrigerant gas whose flow velocity fell, it is necessary to speed up the rotation speed of the refrigerant gas around the flanged conduit 102. As a result, it is necessary to increase the flow velocity of the refrigerant gas before it collides with the flanged conduit 102, and in order to do so, it is necessary to make the passage distance of the discharge passage 104 long, so that the oil separator is enlarged. Discarded.

An object of the present invention is to provide a piston compressor capable of compacting an oil separator while securing a separation capability of lubricating oil.

Means to solve the problem

In order to solve the said problem, the invention of Claim 1 compresses refrigerant gas by the operation of a compression mechanism, and turns on the turning part and the axial direction of the turning part on the discharge passage of the compressed refrigerant gas. An oil separator having a circumferential wall surrounding the portion and having a separation space between the turning portion and the circumference wall and separating the lubricating oil contained in the refrigerant gas by turning the refrigerant gas along the turning portion in the separation space. In the refrigerant compressor which is arranged and formed in the peripheral wall and the oil outlet for flowing out the lubricant oil separated from the refrigerant gas out of the oil separator, the oil separator is the inlet of the refrigerant gas into the separation space and the separation The outlet port of the refrigerant gas out of the space is provided, and an image is formed between the inlet port and the outlet port. While the pre-turn portion is arranged, the introduction port and the outlet port are arranged so that the direction of derivation of the refrigerant gas from the outlet port is the same as the direction of introduction of the refrigerant gas into the inlet port.

According to this configuration, the refrigerant gas introduced into the separation space from the inlet port flows toward the outlet port while turning around the turning part, and is led out of the separation space from the outlet port. At this time, since the derivation direction of the refrigerant gas derived from the outlet port is in the same direction as the introduction direction of the refrigerant gas introduced from the inlet port, the refrigerant gas introduced into the separation space is changed when turning around the turning part. It does not change the flow direction to the direction different from the introduction direction, and it flows toward an exit port and is derived from it as it is. For this reason, the refrigerant gas is rotated around the turning part at a flow rate close to that when introduced into the separation space without lowering the flow rate in the separation space, and the lubricant gas is efficiently centrifuged from the refrigerant gas. Therefore, according to the oil separator, the turning distance of the refrigerant gas is increased to increase the separation ability of the lubricating oil from the refrigerant gas, or the passage length of the refrigerant gas before being introduced to the oil separator is increased to increase the flow rate of the refrigerant gas. There is no need. As a result, the oil separator can be made compact while ensuring the separation ability of the lubricating oil from the refrigerant gas.

In addition, the introduction direction of the refrigerant gas into the introduction port and the direction of introduction of the refrigerant gas from the outlet port may be parallel.

According to this structure, even if the direction of derivation of the refrigerant gas from the outlet port does not coincide with the direction of introduction of the refrigerant gas into the inlet port, but slightly shifts in parallel with each other, the direction intersecting with the introduction direction in the separation space ( The refrigerant gas is derived from the outlet port without changing the direction in which the refrigerant gas flows in the orthogonal direction). Therefore, the refrigerant gas is led out of the separation space from the outlet port without lowering the flow velocity in the separation space. And since the lubricating oil separation ability is ensured even when the derivation direction is shifted parallel to the introduction direction, the degree of freedom in selecting the arrangement position of the outlet port can be increased, so that the arrangement of the oil separator in the refrigerant compressor can be adjusted to the structure of the refrigerant compressor. It becomes possible to respond flexibly.

The inlet and the outlet may be located on the same straight line, and the introduction direction of the refrigerant gas into the introduction port may coincide with the introduction direction of the refrigerant gas from the outlet.

According to this configuration, since the refrigerant gas introduced into the separation space from the inlet port flows toward the outlet port, it becomes difficult to change the direction in which the refrigerant gas flows when turning around the turning part. Since the flow velocity decreases as the crossing angle of the direction in which the refrigerant gas flows in the separation space with respect to the introduction direction to the introduction port increases, it becomes possible to suppress the decrease in the flow velocity of the refrigerant gas.

Further, the direction in which the straight line connecting the inlet port and the outlet port extends may coincide with the axial direction of the pivot part extending from the inlet port side of the swing section to the outlet port side.

According to this configuration, the refrigerant gas flows toward the outlet port while turning around the turning part. However, the flow of the refrigerant gas flowing from the inlet port toward the outlet port coincides with the axial direction of the turning part. It becomes possible to flow to the outlet while making it follow. Therefore, the refrigerant gas can be swung around the turning part while suppressing the decrease in the flow rate of the refrigerant gas, thereby making it possible to increase the separation capability of the lubricating oil.

Moreover, the said oil separator may be provided with the forced turning means which spirally rotates refrigerant gas around a turning part along the axial direction of the said turning part.

According to this structure, by the forced swing means, the refrigerant gas can be spirally rotated along the axial direction of the swing portion. For this reason, the lubricating oil is centrifuged more efficiently from the refrigerant gas by the spirally turning of the refrigerant gas introduced into the separation space from the inlet by the forced turning means without lowering its flow velocity.

Moreover, the said forced turning means may be comprised by the spiral groove extended spirally from the one end side along the axial direction of the said turning part to the other end side in the circumferential surface of the said turning part.

According to this structure, only by providing a spiral groove in a turning part, refrigerant gas can be spirally rotated along the axial direction of a turning part. That is, the refrigerant gas can be spirally rotated with a simple configuration, and the lubricating oil can be centrifuged more efficiently from the refrigerant gas.

Moreover, the said forced swing means may be comprised by the spiral channel which spirally extends from the one end side along the axial direction of the said turning part to the other end side in the said separation space.

According to this configuration, the refrigerant gas introduced into the separation space can flow only in the spiral passage. For this reason, the spiral passage can reliably rotate the refrigerant gas around the turning portion, and the spiral passage can efficiently centrifuge the lubricant oil from the refrigerant gas.

Moreover, the said forced turning means may be comprised by the guide hole which communicates with the said inlet opening, extends toward the said separation space from the inlet opening, and extends in the direction diagonally crossing with respect to the axial direction of the said turning part. do.

According to this configuration, the refrigerant gas introduced into the separation space from the inlet is guided to the separation space by the guide hole. For this reason, the refrigerant gas flows along the circumferential surface of the swing portion and spirally rotates along the swing portion. Therefore, the refrigerant gas can be spirally rotated with a simple configuration.

To practice the invention  Best form for

EMBODIMENT OF THE INVENTION Hereinafter, one Embodiment which actualized this invention with the refrigerant | coolant compressor used for the refrigeration circuit of the vehicle air conditioner is described in detail based on drawing. In the following description, "up", "down", "before" and "after" of the refrigerant compressor 10 make the direction of arrow Y1 shown in FIG. 1 the up-down direction, and make the direction of the arrow Y2 the front-back direction.

1 shows a longitudinal cross-sectional view of the refrigerant compressor 10. As shown in FIG. 1, the housing of the refrigerant compressor 10 includes a cylinder block 11, a front housing 12 bonded and fixed to the front end of the cylinder block 11, and a rear end of the cylinder block 11. It consists of the rear housing 14 joined and fixed through the valve port forming body 13.

In the housing, a crank chamber 15 is partitioned between the cylinder block 11 and the front housing 12. Moreover, the drive shaft 16 is rotatably supported by the cylinder block 11 and the front housing 12 so that the said crank chamber 15 may be inserted. The engine E, which is the driving drive source of the vehicle, is operatively connected to the drive shaft 16 via a clutchless type (always transmission type) power transmission mechanism PT. Therefore, at the time of operation of the engine E, the drive shaft 16 is always rotated by receiving power from the engine E. FIG.

In the crank chamber 15, a lug plate 17 is fixed to the drive shaft 16 so as to be integrally rotatable with the drive shaft 16, and in the crank chamber 15 as a cam plate having a disc shape. The swash plate 18 is housed. The drive shaft 16 is inserted through a central portion of the swash plate 18, and the swash plate 18 is supported by the drive shaft 16 so as to be integrally rotatable and inclined. A hinge mechanism 19 is interposed between the lug plate 17 and the swash plate 18. The swash plate 18 is synchronously rotated with the lug plate 17 and the drive shaft 16 by the hinge connection between the lug plate 17 through the hinge mechanism 19 and the support of the drive shaft 16. In addition, it is possible to incline the drive shaft 16 with the slide movement of the drive shaft 16 in the axial direction (the center axis L direction).

In the cylinder block 11, around the center axis L of the drive shaft 16, the some cylinder bore 22 penetrates in the front-back direction at equal angle intervals. The migrating piston 23 is housed in each cylinder bore 22 so as to be movable in the front-rear direction. The front and rear openings of the cylinder bore 22 are closed by the front face of the valve port forming body 13 and the rear end face of the piston 23, and the inside of the cylinder bore 22 includes the piston 23. The compression chamber 24 which changes volume according to the movement to the front-back direction is partitioned.

Each said piston 23 is moored to the outer peripheral part of the swash plate 18 via the pair of shoes 25. Therefore, when the swash plate 18 rotates by the rotation of the drive shaft 16, the swash plate 18 is swung back and forth in the direction of the center axis L of the drive shaft 16. By oscillation of the swash plate 18, the piston 23 reciprocates linearly in the front-rear direction. And in this embodiment, the compression mechanism is comprised by the crank chamber 15, the drive shaft 16, the swash plate 18, the piston 23, etc. As shown in FIG.

In the housing, a suction chamber 26 and a discharge chamber 27 are respectively formed between the valve port forming body 13 and the rear housing 14. In the valve port forming body 13, the suction port 28 and the suction valve 29 are formed so as to be located between the compression chamber 24 and the suction chamber 26, and the compression chamber ( The discharge port 30 and the discharge valve 31 are each formed so as to be located between the 24 and the discharge chamber 27.

Carbon dioxide is used as the refrigerant gas of the refrigeration circuit. The refrigerant gas introduced into the suction chamber 26 from the external refrigerant circuit 41 (in particular, the outlet side of the evaporator 41a) of the refrigerating circuit is moved from the top dead center position of each piston 23 to the bottom dead center position side. The suction chamber 28 is sucked into the compression chamber 24 via the suction port 28 and the suction valve 29. The refrigerant gas sucked into the compression chamber 24 is compressed to a predetermined pressure by moving from the bottom dead center position of the piston 23 to the top dead center position and discharged through the discharge port 30 and the discharge valve 31. It is discharged to the chamber 27.

The rear housing 14 is provided with a connection passage 49 for connecting the discharge chamber 27 and the external refrigerant circuit 41 (specifically, the inlet side of the gas cooler 41b). The refrigerant gas in the discharge chamber 27 is led to the external refrigerant circuit 41 through the connection passage 49. The refrigerant drawn out to the external refrigerant circuit 41 is cooled in the gas cooler 41b and decompressed by the expansion valve 41c, and then sent to the evaporator 41a to be evaporated. In the present embodiment, the discharge chamber 27 and the connection passage 49 form the discharge passage of the refrigerant gas in the refrigerant compressor 10.

As shown in FIG. 2, in the said rear housing 14, the accommodating hole 37 which is a part of the said connection passage 49, and comprises a part of the said discharge passage is formed in the front-back direction. A first pedestal (37a; 형성) is formed inward at an almost center circumferential surface in the front-rear direction of the accommodation hole 37, and a rearward side of the first pedestal (37a) is provided. The 2nd base 37b which becomes smaller than 37a) is provided. The oil separator 50 which isolate | separates the lubricating oil contained in refrigerant gas is arrange | positioned in the said accommodation hole 37. The oil separator 50 communicates with the discharge chamber 27 and is connected to the inlet side of the gas cooler 41b in the external refrigerant circuit 41 via the connection passage 49. . Therefore, the refrigerant gas discharged from the discharge chamber 27 is supplied to the external refrigerant circuit 41 via the oil separator 50.

As shown in FIG. 1, the bleeding passage 32, the air supply passage 33, and the control valve 34 are formed in the housing of the refrigerant compressor 10. The bleeding passage 32 connects the crank chamber 15 and the suction chamber 26. Moreover, the said air supply passage 33 connects the connection passage 49 (oil separator 50) which is discharge pressure area | region, and the crank chamber 15 as a low pressure area | region lower than the connection passage 49. As shown in FIG. A control valve 34 is disposed in the middle of the air supply passage 33.

And by adjusting the opening degree of the said control valve 34, the introduction amount of the high pressure discharge gas into the crank chamber 15 through the air supply passage 33, and from the crank chamber 15 through the bleeding passage 32 The balance of the gas extraction amount is controlled, and the internal pressure of the crank chamber 15 is determined. As a result of changing the internal pressure of the crank chamber 15 and the internal pressure of the compression chamber 24 in accordance with the change of the internal pressure of the crank chamber 15, the inclination angle of the swash plate 18 is changed, resulting in a stroke of the piston 23. That is, the discharge capacity of the refrigerant compressor 10 is adjusted. That is, the refrigerant compressor 10 of the present embodiment is a variable displacement compressor having a variable discharge capacity.

For example, when the valve opening degree of the control valve 34 decreases, the internal pressure of the crank chamber 15 decreases. Therefore, the inclination angle of the swash plate 18 is increased, the stroke of the piston 23 is increased, and the discharge capacity of the refrigerant compressor 10 is increased. On the contrary, when the valve opening degree of the control valve 34 increases, the internal pressure of the crank chamber 15 will increase. Therefore, the inclination angle of the swash plate 18 decreases, the stroke of the piston 23 decreases, and the discharge capacity of the refrigerant compressor 10 decreases.

Next, the oil separator 50 will be described.

As shown in FIG. 2, in the discharge passage, an oil separator 50 is disposed on the downstream side of the discharge chamber 27 and upstream of the external refrigerant circuit 41 to separate the lubricant oil from the refrigerant gas. . The oil separator 50 is provided with the casing 51 which forms the cylinder pressed into the said accommodation hole 37. As shown in FIG. In the state where the case 51 is press-fitted in the accommodation hole 37, the rear end of the case 51 abuts on the said 1st base 37a, and the movement to the back of the case 51 is regulated.

On the outer circumferential surface of the circumferential wall 51a of the case 51, a seal member 48 made of a rubber O ring is mounted to suppress leakage of refrigerant gas between the accommodation hole 37 and the case 51. have. Moreover, the oil outlet 50b for flowing out the lubricating oil isolate | separated from refrigerant gas out of the case 51 (oil separator 50) is formed in the lower part in the circumferential wall 51a of the case 51. As shown in FIG. This oil outlet 50b is connected to the said control valve 34 via the channel | path 60 (refer FIG. 1).

Moreover, in the said case 51, the turning member 52 as a turning part is accommodated, and the circumferential wall 51a in the case 51 surrounds the turning member 52 along the axial direction M. Moreover, as shown in FIG. Is arranged. And the separation space S which comprises a circular form is formed between the inner peripheral surface of the circumferential wall 51a, and the circumferential surface of the turning member 52. As shown in FIG. The pivot member 52 extends along the direction in which the refrigerant gas in the discharge passage (accommodating hole 37) flows. The pivot member 52 is accommodated so that its axial direction M extends in the front-rear direction in the case 51, and the front end (one end) side of the pivot member 52 is a discharge side that is the front end side of the case 51. It is arrange | positioned at the chamber 27 side, and the rear end (other end) side of the turning member 52 is arrange | positioned at the external refrigerant circuit 41 side which is the rear end side of the case 51. On the circumferential surface of the pivot member 52, a spiral groove 52a is formed which extends spirally from the front end (one end) side to the rear end (other end) side along the axial direction M of the pivot member 52, have. The spiral groove 52a constitutes a forced swing means for spirally turning the refrigerant gas around the swing member 52 along the axial direction M of the swing member 52.

Moreover, as for the said spiral groove 52a, the groove depth in radial direction becomes gradually shallower toward the rear end side from the front end side of the turning member 52, and is converging toward the axial center of the turning member 52 at the rear end side. Moreover, the flange part 52b is formed in the rear end of the turning member 52, The flange part 52b has the multiple exit port 52c (four in this embodiment); three outlet port 52c in FIG. ) Is formed at equal intervals. The refrigerant gas introduced into the separation space S is led out of the separation space S from the outlet port 52c. In addition, the derivation direction Z1 of the refrigerant gas from the derivation port 52c is made into the direction shown by the arrow Z1 of FIG. 2, and the derivation direction Z1 of this refrigerant gas is the front end in the turning member 52 ( It is in the same direction as the axial direction M from one end) side to the rear end (other end) side.

In the oil separator 50, a cylindrical cover member 54 is fitted to the front end of the case 51 via a stopper 53 and a variable throttle 55 as a throttle from the outside. The cover member 54 is provided with an inlet port 54a for introducing refrigerant gas into the case 51 (separation space S), and the inlet port 54a has a discharge chamber 27 and a case 51. Communicate in In addition, the four outlets 52c are formed so as to shift their positions outward in the radial direction of the pivot member 52 with respect to the inlet port 54a. Moreover, each introduction port 54a is arrange | positioned around the shaft center of the turning member 52. As shown in FIG. The refrigerant gas discharged into the discharge chamber 27 is introduced into the separation space S from the introduction port 54a. In addition, the introduction direction Z2 of the refrigerant gas from the inlet port 54a into the separation space S is set to the direction shown by the arrow Z2 of FIG. 2, and the introduction direction Z2 of the refrigerant gas is the turning member 52. It is in the same direction as the axial direction M from the front end (one end) side to the rear end (other end) side. The stopper 53 has a cylindrical shape, and a communication port 53b for communicating the inlet port 54a and the inside of the case 51 is formed at the center thereof. The refrigerant gas passing through the introduction port 54a is introduced into the separation space S in the case 51 through the communication port 53b.

Moreover, between the outer peripheral part of the stopper 53 and the outer peripheral part of the said lid member 54, the outer peripheral part of the variable throttle 55 is pinched | interposed. The said variable throttle 55 is equipped with the some (two in this embodiment) throttle valve 55a which forms a lead shape. Moreover, the relief part 53a which allows the elastic deformation of the said throttle valve 55a is formed in the center of the front side of the said stopper 53 in concave shape. 2, the variable throttle 55 receives the refrigerant gas flow, and the two throttle valves 55a are elastically deformed to allow the flow of the refrigerant gas. In addition, the variable throttle 55 increases the cross sectional area of the refrigerant gas by increasing the amount of elastic deformation of each throttle valve 55a as the refrigerant gas flow rate increases, and decreases the flow rate of the refrigerant gas, thereby reducing each throttle valve. By reducing the amount of elastic deformation of the 55a, the cross-sectional area of the refrigerant gas is reduced. For this reason, when the flow volume of refrigerant gas increases, it becomes difficult to produce the differential pressure upstream and downstream of the variable throttle 55, and when the flow volume of refrigerant gas decreases, the differential pressure on the upstream and downstream of the variable throttle 55 is reduced. This tends to occur.

In the accommodation hole 37, a valve seat forming member 56 having a cylindrical shape is accommodated in the rear side (the external refrigerant circuit 41 side) of the case 51, and the outer circumference of the valve seat forming member 56 is accommodated. Is fitted with a cylindrical fitting member 57. The outer circumference of the check valve 58 is sandwiched between the outer circumference of the valve seat forming member 56 and the outer circumference of the fitting member 57. A valve hole 56a is formed in the center of the valve seat forming member 56, and the periphery of the valve hole 56a in the valve seat forming member 56 is a valve seat 56b with the check valve 58. ) In the fitting member 57, a relief 57a that allows elastic deformation of the check valve 58 is formed on the front face of the valve seat forming member 56. As shown in FIG. As shown by the dashed-dotted line in FIG. 2, the check valve 58 receives the refrigerant gas flow and elastically deforms to allow the flow of the refrigerant gas out of the separation space S, while entering the separation space S. It is to block the flow of the refrigerant gas. Moreover, the gas outlet 57b of the refrigerant gas out of the oil separator 50 is formed in the center of the fitting member 57, The gas outlet 57b is a valve hole 56a and connection in the case 51. Moreover, as shown in FIG. It communicates with the passage 49.

The oil separator 50 includes the case 51, the swing member 52, the stopper 53, the lid member 54, the variable throttle 55, and the valve seat forming member 56. And the fitting member 57 and the check valve 58 are assembled to be accommodated in the receiving hole 37. Specifically, the fitting member 57, the check valve 58, the valve seat forming member 56, the case 51, the pivot member 52, the stopper 53, the variable throttle 55, and the lid member ( The oil separator 50 is configured by accommodating 54 on the external refrigerant circuit 41 side of the accommodation hole 37 in the same order.

The oil separator 50 is configured to separate the lubricant oil from the refrigerant gas by centrifugation. Moreover, in the oil separator 50, the said inlet port 54a is arrange | positioned at the position corresponding to the front end (one end) along the axial direction M of the turning member 52, and the said axial direction M is The said outlet port 52c is arrange | positioned and formed in the position corresponding to the rear end (the other end) which followed. The turning member 52 has an axial direction M of the separation space S from the introduction direction Z2 and the outlet 52c of the refrigerant gas from the introduction port 54a into the separation space S. It is arrange | positioned so that it may extend in the same direction as the extraction direction Z1 of the refrigerant gas outside), and the turning member 52 is fitted in the inlet port 54a and the outlet port 52c. Moreover, the derivation direction Z1 of refrigerant gas is parallel to the introduction direction Z2 of refrigerant gas, and is also parallel to the axial direction M of the turning member 52.

The passage 60 connected to the oil outlet 50b of the oil separator 50 is located on the air supply passage 33, and the oil separator 50 and the crank chamber 15 include the air supply passage 33. (60). The lubricating oil separated by the oil separator 50 is returned to the crank chamber 15 through the passage 60, that is, the air supply passage 33, together with the refrigerant gas supplied to the crank chamber 15 for capacity control. Lose. The control valve 34 is displaced in accordance with the difference between the pressure on the upstream side (pressure of the discharge chamber 27) and the pressure on the downstream side (pressure of the case 51) of the variable throttle 55. This differential pressure reflects the refrigerant flow rate in the refrigerating circuit.

By the way, the refrigerant gas introduced into the case 51 from the discharge chamber 27 through the inlet port 54a is introduced into the separation space S after the flow rate is adjusted by the variable throttle 55. In the case 51, the turning member 52 extends along the introduction direction Z2 of the refrigerant gas from the introduction port 54a into the separation space S. As shown in FIG. That is, since the axial direction M of the revolving member 52 extends in parallel with the introduction direction Z2 of the refrigerant gas from the introduction port 54a, the refrigerant gas is introduced with respect to the introduction direction Z2 thereof. The inside of the separation space S flows along the axial direction M of the turning member 52, without changing the direction which flows in a perpendicular direction. And the refrigerant gas flows along the turning member 52, and is forcibly spirally rotated by the spiral groove 52a formed in the peripheral surface of the turning member 52. As shown in FIG. Since the spiral groove 52a is formed over the whole axial direction M of the turning member 52, refrigerant gas turns spirally over the whole axial direction M of the turning member 52. As shown in FIG.

The lubricant oil is separated from the refrigerant gas that spirally rotates the separation space S along the spiral groove 52a of the swing member 52 by a centrifugal separation action, and the separated lubricant oil has a circumference of the case 51. It is attached to the inner peripheral surface of the wall 51a. Thereafter, the lubricating oil attached to the circumferential wall 51a flows down by its own weight, flows out of the case 51 (oil separator 50) from the oil outlet 50b together with the refrigerant gas, and passes through the passage 60. It is provided to the control valve 34, the crank chamber 15 through.

On the other hand, the refrigerant gas from which the lubricating oil has been separated flows toward the outlet port 52c, but the direction in which the refrigerant gas is discharged from the outlet port 52c Z1 is the direction in which the refrigerant gas is introduced into the inlet port 54a (Z2). ), The introduction port 54a and the exit port 52c are arranged so as to be the same as). For this reason, when the refrigerant gas flows toward the outlet port 52c, the refrigerant gas flows without changing the direction of flow in a direction different from the introduction direction to the inlet port 54a, and is directly drawn out of the separation space S from the outlet port 52c. do. Thereafter, the refrigerant gas derived from the outlet port 52c is supplied to the external refrigerant circuit 41 through the connection passage 49.

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

(1) The oil separator 50 has the inlet port 54a of the refrigerant gas at a position corresponding to the front end (one end) along the axial direction M of the turning member 52, and the axial direction M ), The outlet port 52c of the refrigerant gas is provided at a position corresponding to the rear end (the other end) along. Then, the direction in which the refrigerant gas introduction direction Z2 from the inlet port 54a into the separation space S and the induction direction Z1 of the refrigerant gas out of the separation space S from the outlet port 52c are the same Inlet port 54a and outlet 52c are arrange | positioned as much as possible. For this reason, the refrigerant gas introduced into the separation space S from the inlet port 54a flows to the outlet port 52c while turning along the axial direction M of the turning member 52, without changing the flowing direction. It is derived out of the separation space S from the outlet 52c. Therefore, as in the background art, it is possible to eliminate the flow of the refrigerant gas in the direction orthogonal to the introduction direction, and to suppress the flow rate decrease of the refrigerant gas. As a result, in order to compensate for the decrease in the separation ability of the lubricating oil due to the decrease in the flow rate of the refrigerant gas, it is necessary to lengthen the turning member 52 or to secure the introduction distance of the refrigerant gas in order to secure the turning distance of the refrigerant gas. Is eliminated, and the oil separator 50 can be made compact.

(2) The four outlet ports 52c are arranged around the axis of the inlet port 54a, and are introduced from the inlet direction Z2 of the refrigerant gas into the inlet port 54a and from each outlet port 52c. The derivation direction Z1 of the refrigerant gas is parallel. The refrigerant gas introduced into the separation space S from the inlet port 54a flows to each outlet port 52c while pivoting along the axial direction M of the pivot member 52, and the outlet port 52c. Derived from. Here, although the derivation direction Z1 of the refrigerant gas from the outlet port 52c does not coincide with the direction Z2 of introduction of the refrigerant gas into the inlet port 54a, the direction in which the refrigerant gas flows in the separation space S is here. Is derived from the derivation port 52c without changing. Therefore, the refrigerant gas is efficiently separated from the lubricant gas without lowering the flow velocity in the separation space S. FIG. That is, since the lubricating oil can be efficiently separated as long as the derivation direction Z1 and the introduction direction Z2 of the refrigerant gas are the same direction, the arrangement position of the derivation port 52c may be arbitrarily changed, The degree of freedom in selecting the arrangement position can be increased, and the arrangement in the refrigerant compressor 10 of the oil separator 50 can be flexibly corresponded to the structure of the refrigerant compressor 10.

(3) In the oil separator 50, the oil outlet 50b is formed in the peripheral wall 51a of the case 51 to which the lubricating oil centrifuged from the refrigerant gas adheres. And the lubricating oil attached to the circumferential wall 51a flows down toward the oil outlet 50b by its own weight, and flows out from the oil separator 50 out of the oil outlet 50b. Thus, for example, the lubricating oil adhered to the circumferential wall 51a is formed, as in the case where the oil outlet 50b is formed not at the circumferential wall 51a but at the flange portion 52b in which the outlet port 52c is formed. There is no need to move through the flange portion 52b via the flow of the refrigerant gas. As a result, the lubricating oil can be quickly flowed out of the oil separator 50, and further, lubrication can be promptly applied to the compression mechanism or the like.

(4) The lubricating oil centrifuged by the oil separator 50 is not stored in the oil separator 50 but flows out of the oil separator 50 from the oil outlet 50b. Therefore, the lubricating oil centrifuged by the oil separator 50 can be suppressed from carrying out to the external refrigerant circuit 41 with refrigerant gas.

(5) Moreover, since it is not necessary to form the structure for storing lubricating oil in the oil separator 50, the oil separator 50 can be made more compact.

(6) A spiral groove 52a is formed on the circumferential surface of the swinging member 52 to spirally rotate the refrigerant gas along the circumferential surface of the swinging member 52. For this reason, the refrigerant gas introduced into the separation space S is forcibly spirally rotated along the flowing direction thereof. Therefore, in the oil separator 50, in addition to suppressing the flow rate fall of the refrigerant gas, the ability to separate the lubricant gas from the refrigerant gas can be improved by forcibly spiraling the refrigerant gas.

(7) The oil separator 50 includes a case 51, a swing member 52, a stopper 53, a lid member 54, a variable throttle 55, and a valve seat forming member 56. And the fitting member 57 and the check valve 58 are integrally assembled. Each member is formed side by side along the introduction direction of the refrigerant gas into the oil separator 50. Therefore, unlike the background art in which the inner cylinder extends in the direction orthogonal to the direction in which the refrigerant gas flows, for example, the entire oil separator 50 can be made compact. Moreover, since the oil separator 50 is comprised only by assembling each member in the accommodation hole 37 in a predetermined order, the oil separator 50 can be easily formed in the refrigerant | coolant compressor 10. FIG.

(8) In the oil separator 50, the turning member 52 and the outlet port 52c are formed side by side along the introduction direction Z2 of the refrigerant gas into the separation space S, and the variable throttle 55 is formed side by side. And check valve 58 are also formed side by side. Therefore, for example, assembling the variable throttle 55 and the check valve 58 integrally with the oil separator 50, as in the configuration in which the refrigerant gas flows in a direction orthogonal to the introduction direction Z2 of the refrigerant gas. The oil separator 50 can be made compact compared with the case where it is impossible.

(2nd embodiment)

Next, 2nd Embodiment which actualized this invention as the refrigerant | coolant compressor used for the refrigeration circuit of the vehicle air conditioner is described in detail based on drawing. In 2nd Embodiment described below, about the structure similar to 1st Embodiment mentioned previously, the same code | symbol is attached | subjected and the duplication description is abbreviate | omitted or simplified.

As shown to FIG. 3 and FIG. 4, the bottom part 65 is integrally formed in the back side of the case 51 which comprises the oil separator 50. As shown in FIG. The bottom part 65 protrudes and is formed in the circumferential shape toward the front side of the case 51, and this protrusion 66 constitutes the turning part which the refrigerant gas turns around. . Moreover, the separation space S is partitioned between the projection part 66 and the circumferential wall 51a. As shown to Fig.4 (a) and (b), the recessed part 66a is formed in the front end of the projection part 66 concave. Moreover, the guide part 66b which communicates with the said recessed part 66a in the front part of the projection part 66, and inclined obliquely toward the back side in the projection part 66 is formed. In the case 51, between the protrusion 66 and the circumferential wall 51a, it communicates with the recess 66a and the guide portion 66b, and spirally extends along the circumferential direction of the protrusion 66. The spiral passage 67 is formed. The spiral passage 67 constitutes forced swing means for forcibly spiraling the refrigerant gas along the swing member 52. Moreover, it is the rear end side of the projection part 66, and the outlet part 68 is formed in the said bottom part 65 for drawing out refrigerant gas out of the separation space S. As shown in FIG.

In the second embodiment, the projection portion 66 has an axial direction M from the introduction direction Z2 of the refrigerant gas into the separation space S from the introduction port 54a and the outlet port 68. It is arrange | positioned so that it may extend in the same direction as the derivation direction Z1 of the refrigerant gas out of the separation space S, and the turning member 52 is fitted in the inlet port 54a and the inlet port 68. As shown in FIG. In addition, the derivation direction Z1 of the refrigerant gas and the introduction direction Z2 of the refrigerant gas coincide, and the derivation direction Z1 and the introduction direction Z2 also coincide with the axial direction M of the projection 66. Doing.

In the second embodiment, the refrigerant gas introduced into the separation space S from the inlet port 54a flows from the recess 66a toward the rear side of the separation space S by the guide part 66b. Guided to the spiral passage 67. Then, the refrigerant gas flows along the spiral passage 67 to forcibly spiral around the protrusion 66, and the lubricant oil is separated from the refrigerant gas turning the spiral passage 67 by centrifugal separation. do.

Therefore, according to 2nd Embodiment, the following effects can be acquired in addition to the same effect as (1)-(8) of 1st Embodiment.

(9) In 2nd Embodiment, the spiral channel | path 67 is formed in the case 51, and the spiral channel 67 can spirally rotate refrigerant gas more reliably. Therefore, the separation ability of the lubricating oil from the refrigerant gas can be improved.

(Third embodiment)

Next, 3rd Embodiment which actualized this invention as the refrigerant | coolant compressor used for the refrigeration circuit of the vehicle air conditioner is described in detail based on drawing. In 3rd Embodiment described below, about the same structure as 1st Embodiment mentioned previously, the same code | symbol is attached | subjected and the duplication description is abbreviate | omitted or simplified.

As shown in FIG. 5, the bottom forming member 70 is integrally assembled with the case 51 at the rear side of the case 51 constituting the oil separator 50. The bottom portion forming member 70 includes a bottom plate 71 that forms a disc shape, and a cylindrical cylinder portion 72 protruding from the bottom plate 71. In a state where the bottom portion forming member 70 is assembled to the case 51, the cylinder portion 72 protrudes toward the front side of the case 51, and the cylinder portion 72 is such that the refrigerant gas pivots around it. Consists of a pivot made. A gas passage 72a is formed inside the cylinder portion 72. Moreover, the pair of permeation holes 72b are formed in the cylinder part 72 so as to oppose each other, and each permeation hole 72b communicates with the said gas passage 72a. In addition, it is the rear end of the cylinder part 72, and the outlet port 72c of the refrigerant gas is formed in the rear end of the gas passage 72a, and the inlet port 54a and the outlet port 72c are located on the same straight line. . And the separation space S is formed between the cylinder part 72 and the circumferential wall 51a.

Moreover, the cover part 73 is integrally formed in the front side of the case 51, The guide part 74 which penetrates the cover part 73 in the thickness direction (front-back direction) is formed in the cover part 73, have. And the guide hole 74 is formed so that it may extend obliquely toward the edge from the center of the cover part 73, and the extending direction is oblique with respect to the axial direction M of the cylinder part 72. As shown in FIG. Moreover, the guide hole 74 is opened toward the separation space S which is outer side than the said cylinder part 72. As shown in FIG. The guide hole 74 constitutes a forced swing means for forcibly spiraling the refrigerant gas along the cylinder portion 72.

In the third embodiment, the cylinder portion 72 has its axial direction M separated from the introduction direction Z2 of the refrigerant gas into the separation space S from the inlet port 54a and the outlet port 72c. It is arrange | positioned so that it may extend in the same direction as the derivation direction Z1 of the refrigerant gas out of space S. As shown in FIG. In addition, the direction in which the coolant gas is drawn out Z1 and the direction in which the coolant gas is introduced Z2 are the same direction, and the direction in which the straight line connecting the inlet port 54a and the outlet port 72c extends and the cylinder portion 72 are extended. The axial directions M coincide.

And the refrigerant gas introduced into the separation space S from the inlet port 54a is guided so that it may flow toward the rear side of the separation space S by the guide hole 74. FIG. Then, the refrigerant gas flows along the cylinder portion 72, thereby forcibly spiraling around the cylinder portion 72. The lubricating oil is separated from the refrigerant gas turning the separation space S by the centrifugal separation action, and the refrigerant gas from which the lubricating oil is separated is transferred from the permeation hole 72b located in the middle of the turning to the gas passage 72a. It flows and is led out of the separation space S from the gas passage 72a through the outlet 72c.

Therefore, according to 3rd Embodiment, the following effects can be acquired in addition to the effect similar to (1)-(8) of 1st Embodiment.

(10) In the third embodiment, the refrigerant gas can be spirally rotated by forming the guide hole 74 at an angle. Therefore, the refrigerant gas can be spirally rotated with a simple configuration.

Each embodiment may be changed as follows.

In the above embodiment, the refrigerant compressor 10 is embodied in a swash plate type variable displacement type, but may be a wobble type variable displacement type provided with a rocking plate as a cam plate.

In the above embodiment, the refrigerant compressor 10 is embodied in a variable displacement type, but may be a fixed displacement type.

In the above embodiment, the refrigerant compressor 10 is a piston type, but may be a scroll type or a vane type.

In the above embodiment, carbon dioxide was used as the refrigerant gas, but freon (for example, R134a) may be used as the refrigerant.

In the said embodiment, although the refrigerant compressor 10 was made into the unilateral piston type, you may make it the double headed piston type.

○ In the first embodiment, the variable throttle 55 and the check valve 58 in the oil separator 50 are removed, and the oil separator 50 is replaced with the lid member 54, the pivot member 52, and the case. You may comprise with (51).

In the said embodiment, although it embodied by the variable throttle 55 as a throttle, you may set it as a fixed throttle.

In the above embodiment, the lubricating oil separated by the oil separator 50 is configured to be returned to the crank chamber 15, but the lubricating oil separated by the oil separator 50 may be returned to the suction chamber 26.

In the above embodiment, the lubricating oil separated by the oil separator 50 is configured to be returned to the crank chamber 15, but the lubricating oil separated by the oil separator 50 may be stored in the oil storage unit. In this case, for example, in the above embodiment, the upstream side of the air supply passage 33 is outside the oil separator 50 and the discharge passage on the downstream side (for example, the check valve space 37a) than the variable throttle 55. Connect to

Next, the technical idea grasped | ascertained by the said embodiment and another example is further described below.

(1) The oil separator includes a throttle formed side by side on the downstream side of the inlet port along the introduction direction of the refrigerant gas from the inlet to the separation space, and further provided with a check valve formed on the downstream side of the turning part. The refrigerant compressor as described in any one of Claims 1-8.

(2) The oil separator includes an introduction port into the separation space of the refrigerant gas and an outlet port outside the separation space of the refrigerant gas, and the axial direction of the swing member is along the direction of introduction of the refrigerant gas into the introduction port. The refrigerant compressor according to any one of claims 1 to 8, wherein the refrigerant gas from the outlet port extends along the introduction direction.

According to the present invention, the oil separator can be made compact while securing the separation ability of the lubricating oil.

Claims (8)

The refrigerant gas is compressed by the operation of the compression mechanism, and on the discharge passage of the compressed refrigerant gas, the swing portion and the circumferential wall surrounding the swing portion along the axial direction of the swing portion, An oil separator having a separation space between the circumferential walls and separating the lubricating oil contained in the refrigerant gas by pivoting the refrigerant gas along the turning portion in the separation space; A refrigerant compressor having an oil outlet for flowing lubricant out of an oil separator, The oil separator includes an introduction port of the refrigerant gas into the separation space and a discharge port of the refrigerant gas out of the separation space, and the pivot portion is disposed between the introduction port and the discharge port. And the introduction port and the outlet port are arranged such that the direction of derivation of the refrigerant gas from the port is the same as the direction of introduction of the refrigerant gas into the inlet port. The method of claim 1, And a direction in which refrigerant gas is introduced into the inlet port and a direction in which refrigerant gas from the outlet port is parallel. The method of claim 1, And the introduction port and the outlet port are located on the same straight line, and the introduction direction of the refrigerant gas into the introduction port coincides with the introduction direction of the refrigerant gas from the discharge port. The method of claim 3, wherein And a direction in which a straight line connecting the inlet port and the outlet port extends, and an axial direction of the pivot part extending from the inlet port side of the pivot section to the outlet port side coincides. The method according to any one of claims 1 to 4, The oil separator comprises a forced turning means for spirally turning the refrigerant gas around the turning part along the axial direction of the turning part. The method of claim 5, And the forced swing means is constituted by a spiral groove spirally extending from one end side along the axial direction of the swing portion to the other end side on the circumferential surface of the swing portion. The method of claim 5, And the forced swing means is constituted by a spiral passage spirally extending from one end side along the axial direction of the swing portion to the other end side in the separation space. The method of claim 5, The forced swing means communicates with the inlet, extends from the inlet toward the separation space, and is configured by a guide hole extending in a direction crossing obliquely to the axial direction of the pivot. .

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