KR20160115743A - Compressor - Google Patents

Abstract

A compressor comprises: a housing; a discharge chamber provided in the housing; an oil separation member separating an oil from a refrigerant discharged from the discharge chamber; a discharge passage provided in the housing; and an oil passage provided in the housing. The discharge passage discharges the refrigerant separated from the oil by the oil separation member to an external refrigerant circuit. The oil passage introduces the oil separated by the oil separation member into an oil storage chamber. The oil separation member has a partition wall member separating the discharge chamber and the discharge passage from each other. The partition wall member has a circular part extended towards the discharge passage. A separation space is provided in the circular part. The circular part has an introduction hole connecting the discharge chamber and the discharge passage. The discharge passage includes a refrigerant discharge space. The refrigerant separated from the oil by the oil separation member is discharged to the refrigerant discharge space. The length of the refrigerant discharge space is longer than the separation space in an extension direction of the circular part. The size of the refrigerant discharge space is smaller than or equal to the size of the separation space, in a radial direction of the circular part. The compressor is configured to separate the oil from the refrigerant efficiently.

Description

COMPRESSOR

The present invention relates to a compressor.

The refrigerant circuit of the air conditioner includes a compressor and an external refrigerant circuit. The external refrigerant circuit includes a condenser, an expansion valve connected to the condenser, and an evaporator. The condenser is compressed in the compressor and condenses the refrigerant discharged from the compressor. The evaporator evaporates the refrigerant expanded by passing through the expansion valve.

The refrigerant contains oil (lubricating oil) for lubricating the sliding parts in the compressor. When the refrigerant is discharged to the external refrigerant circuit after being compressed in the compressor, the oil may be discharged to the external refrigerant circuit together with the refrigerant. In such a case, the oil adheres to the inner wall of the condenser and the evaporator and reduces the heat exchange efficiency. In this connection, the compressor disclosed in Japanese Laid-Open Patent Publication No. 2014-202160 has an oil separation structure for separating the oil from the refrigerant in order to restrict the discharge of the oil to the external refrigerant circuit together with the refrigerant.

The compressors of the publication include a housing having a discharge chamber and an outlet, a separation chamber, and a gasket. The separation chamber is located on the downstream side of the discharge chamber and on the upstream side of the outlet in the flow direction of the refrigerant and separates the oil from the refrigerant. The gasket has a recess for defining a separation chamber. The housing has a discharge conduit between the gasket and the outlet. The gasket recess has an internal tapered surface having the shape of a truncated cone having a diameter decreasing toward the discharge conduit. The recess further has a refrigerant outlet. The discharge chamber is connected to the external refrigerant circuit via the separation chamber, the refrigerant outlet, the discharge conduit, and the outlet. The refrigerant in the discharge chamber flows out to the inside of the separation chamber and is guided to the refrigerant discharge port while swirling in the separation chamber. The oil contained in the refrigerant is separated from the refrigerant by centrifugation and attached to the inner taper surface. The oil-separated refrigerant flows from the outlet to the external refrigerant circuit via the refrigerant outlet and the discharge circuit. The refrigerant outlet, the discharge conduit and the outlet constitute a discharge passage for discharging the oil separated refrigerant from the separation chamber to the external refrigerant circuit.

However, in the oil separation structure described above, when the oil-separated refrigerant in the separation chamber is stagnated in the discharge passage, the vortex of the refrigerant in the separation chamber is adversely affected. Further, when the oil is separated from the refrigerant and diffused in the discharge passage, the swirling of the refrigerant in the separation chamber is adversely affected. Such adverse effects by the swirling of the refrigerant in the separation chamber prevent effective separation of the oil from the refrigerant.

It is therefore an object of the present invention to provide a compressor configured to efficiently separate oil from refrigerant.

To achieve the foregoing objects and in accordance with one aspect of the present invention, there is provided a method of operating a compressor comprising a housing, a discharge chamber provided in the housing, an oil separation member separating oil from the refrigerant discharged from the discharge chamber, a discharge passage provided in the housing, A compressor is provided which includes an oil passage provided in the compressor. The discharge passage discharges the oil separated refrigerant to the external refrigerant circuit by the oil separating member. The oil passage introduces the oil separated by the oil separating member into the oil reservoir chamber. The oil separation member has a partition member separating the discharge chamber and the discharge passage from each other. The partition member has an annular portion extending toward the discharge passage. The separation space is provided inside the annular portion. The annular portion has an introduction hole connecting the discharge chamber and the discharge passage to each other. The discharge passage includes a refrigerant discharge space. The refrigerant in which the oil is separated by the oil separating member is discharged to the refrigerant discharge space. In the extending direction of the annular portion, the length of the refrigerant discharge space is longer than the length of the separation space. In the radial direction of the annular portion, the size of the refrigerant discharge space is smaller than or equal to the size of the separation space.

Other aspects and advantages of the present invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS The invention, together with objects and advantages thereof, may best be understood by reference to the following description of the presently preferred embodiments, together with the accompanying drawings, wherein: FIG.

1 is a side cross-sectional view illustrating a swash plate compressor according to one embodiment.
2 is an enlarged partial cross-sectional view of the swash plate compressor shown in Fig.
3 is a cross-sectional view taken along line 3-3 of Fig.

Now, a variable displacement swash plate compressor 10 (hereinafter simply referred to as compressor 10) according to an embodiment will be described with reference to Figs. The swash plate compressor 10 is used in a vehicle air conditioner.

As shown in FIG. 1, the compressor 10 has a housing 11. The housing 11 includes a cylinder block 12, a front housing member 13 connected to the front end of the cylinder block 12, and a front housing member 13 connected to the rear end of the cylinder block 12 via the valve plate assembly 14 And a rear housing member (15). The housing (11) has a crank chamber (16) defined by the front housing member (13) and the cylinder block (12). The cylinder block 12 and the front housing member 13 rotatably support the rotary shaft 17 via the two radial bearings 18. The rotation axis 17 extends through the crank chamber 16.

The rotary shaft 17 is connected to the engine E, which is a power source of the vehicle, through a clutchless type power transmission mechanism PT that transmits power constantly. Thus, when the engine E is operating, the rotary shaft 17 receives power from the engine E and is always rotated.

A lug plate 19 is connected to the rotating shaft 17 and is located in the crank chamber 16. The lug plate 19 rotates integrally with the rotary shaft 17. [ The lug plate 19 is supported by the front housing member 13 via the thrust bearing 20. [ In addition, the swash plate 21 is supported by the rotation shaft 17. The swash plate 21 can slide on the rotary shaft 17 in the direction in which the rotary axis L extends (the axial direction of the rotary shaft 17) and can be inclined with respect to the rotary axis L. [ The hinge mechanism (22) is arranged between the lug plate (19) and the swash plate (21). The hinge mechanism 22 allows the swash plate 21 to be inclined with respect to the rotation axis L of the rotation axis 17 and to rotate integrally with the rotation axis 17. [

The cylinder block 12 has a cylinder bore 12a arranged around the rotational axis 17. [ Each cylinder bore 12a accommodates a single-headed piston 23 to reciprocate. Each piston 23 is coupled to a peripheral portion of the swash plate 21 by a pair of shoe 24 and is reciprocated within the associated cylinder bore 12a through rotation of the swash plate 21. [ A compression chamber 25 is defined in each cylinder bore 12a. The volume of each compression chamber 25 is changed when the corresponding piston 23 reciprocates.

The housing 11 has an annular suction chamber 26 defined between the valve plate assembly 14 and the rear housing member 15 and a discharge chamber 27 defined inside the suction chamber 26. The valve plate assembly 14 has a suction port 28 and a suction valve flap 29 at a location between the compression chamber 25 and the suction chamber 26. The valve plate assembly 14 also has a discharge port 30 and a discharge valve flap 31 at a location between the compression chamber 25 and the discharge chamber 27.

The rear housing member 15 includes a suction passage 32 communicating with the suction chamber 26. The discharge chamber 27 has an accommodating chamber 40 provided in the rear housing member 15. The accommodating chamber 40 accommodates a disk-shaped oil separating member 50 for separating the oil contained in the refrigerant (in this embodiment, carbon dioxide). In addition, the rear housing member 15 includes a discharge passage 33 for discharging the oil separated refrigerant to the external refrigerant circuit 35 by the oil separating member 50. The discharge passage (33) includes a refrigerant discharge space (45) provided in the rear housing member (15). The oil-separated refrigerant is discharged into the refrigerant discharge space 45. The rear housing member 15 includes an oil passage 48 for introducing the oil separated from the refrigerant by the oil separating member 50 into the crank chamber 16. The oil passage 48 includes an oil storage space 46 for storing the oil separated from the refrigerant by the oil separating member 50.

The suction passage 32 and the discharge passage 33 are connected to each other via the external refrigerant circuit 35. The external refrigerant circuit 35 includes a condenser 35a connected to the discharge passage 33, an expansion valve 35b connected to the condenser 35a and an evaporator 35c connected to the expansion valve 35b. The evaporator 35c is connected to the suction passage 32. [ The compressor (10) is incorporated into a refrigerant circuit.

The refrigerant introduced from the outside of the evaporator 35c of the external refrigerant circuit 35 to the inside of the suction chamber 26 is moved by the movement of the piston 23 from the top dead center to the bottom dead center, And is sucked inward of the compression chamber 25 via the suction port 29. The refrigerant sucked into the compression chamber 25 is compressed to a predetermined pressure by the movement of the piston 23 from the top dead center to the bottom dead center and is discharged through the discharge port 30 and the discharge valve flap 31 to the discharge chamber 27).

The cylinder block 12 and the rear housing member 15 include a bleed passage 36 connecting the intake chamber 26 to the crank chamber 16. The cylinder block 12 and the rear housing member 15 also include a supply passage 37 connecting the discharge chamber 27 to the crank chamber 16. A discharge control valve 38 is provided in the supply passage 37. The discharge control valve 38 includes an electromagnetic valve and selectively opens and closes the supply passage 37 through selective excitation and de-excitation of a solenoid (not shown).

The amount of the high-pressure refrigerant supplied from the discharge chamber 27 to the crank chamber 16 is changed by selectively opening and closing the supply passage 37 by the displacement control valve 38. The pressure in the crank chamber 16 is varied according to the amount of refrigerant supplied to the crank chamber 16 and the relationship between the amount of refrigerant discharged from the crank chamber 16 via the bleed passage 36 into the suction chamber 26 do. This change alters the difference between the pressure in the crank chamber 16 and the pressure in the cylinder bore 12a acting on the opposite end of each piston 23. Therefore, the displacement is adjusted by changing the angle of the swash plate 21 (hereinafter, referred to as the inclination angle of the swash plate 21) with respect to the plane perpendicular to the axis of the rotary shaft 17.

Specifically, the selective excitation and de-excitation of the solenoid of the displacement control valve 38 is controlled by a control computer (not shown) to which an air conditioner switch (not shown) is connected. When the air conditioner switch is turned off, the control computer de-excites the solenoid of the displacement control valve (38). Thus, the displacement control valve 38 opens the supply passage 37 to connect the discharge chamber 27 to the crank chamber 16. As a result, the high-pressure refrigerant in the discharge chamber 27 is supplied to the crank chamber 16 through the supply passage 37. In addition, the pressure in the crank chamber 16 is released to the suction chamber 26 through the bleed passage 36. As a result, the difference between the pressure in the crank chamber 16 and the pressure in the cylinder bore 12a, that is, the pressure difference between the opposite sides of each piston 23, is changed to minimize the inclination angle of the swash plate 21. [ This minimizes displacement.

In contrast, when the air conditioner switch is turned on and the solenoid is excited, the displacement control valve 38 reduces the degree of opening of the supply passage 37. Accordingly, the pressure in the crank chamber 16 is lowered based on the pressure release to the suction chamber 26 via the bleed passage 36. Such pressure reduction increases the inclination angle of the swash plate 21 from the minimum inclination angle, causing the compressor 10 to operate at a displacement greater than the minimum displacement.

2, the accommodating chamber 40 includes an enlarged portion (large diameter portion) 40a and a narrow portion (small diameter portion) 40b that is narrower than the enlarged portion 40a. The narrow portion 40b is located between the enlarged portion 40a and the discharge passage 33 and is connected to the enlarged portion 40a. A first recess 41 is provided in the bottom surface 40e of the narrow portion 40b. The interior of the first recess 41 constitutes a refrigerant discharge space 45. The first recess 41 has a tapered or bowl-shaped bottom. A part of the discharge passage 33 perpendicular to the refrigerant discharge space 45 is opened to the bottom of the first recess 41. [ An annular groove 43 is provided in the bottom surface 40e of the narrow portion 40b. The annular groove 43 is connected to a part of the first recess 41 close to the narrow portion 40b.

The oil separation chamber 50 has a completely circular shape in a plan view and is a part formed separately from the rear housing member 15. [ The oil separating member 50 includes a partition member 51 and a columnar vortex shaft 52. The partition wall member 51 separates the discharge chamber 27 (specifically, the accommodating chamber 40) and the discharge passage 33 from each other. The vortex axis 52 extends from the partition member 51 toward the inlet of the discharge passage 33. The partition member 51 has an annular portion 53 around the vortex axis 52 and at a position spaced from the vortex axis. The annular portion (53) extends toward the inlet of the discharge passage (33). In other words, the annular portion 53 extends toward the refrigerant discharge space 45. The separation space 54 is defined radially inward of the annular space 53. That is, the separation space 54 is positioned between the vortex axis 52 and the annular portion 53. The separation space 54 constitutes a part of the discharge passage 33. The direction in which the annular portion 53 extends or the axial direction of the annular portion 53 coincides with the axial direction of the rotary shaft 17. The axial direction of the vortex shaft 52 corresponds to the axial direction of the rotary shaft 17.

The partition member 51 has a disc-shaped support portion 55 for supporting the swirl axis 52. The annular portion 53 protrudes from the entire outer periphery of the support portion 55 and surrounds the vortex axis 52 from the outside in the radial direction. The vortex axis 52 extends linearly in a direction perpendicular to the end face 55a of the support portion 55 to which the vortex axis 52 is provided. The annular portion (53) extends parallel to the axis of the vortex axis (52).

The oil separation member 50 has an annular plate-shaped flange portion 56 extending radially outward from the outer peripheral edge of the annular portion 53 on the opposite side of the support portion 55. The oil separating member 50 has an end face (not shown) of the flange portion 56 which is received in the receiving chamber 40 and is on the opposite side of the supporting portion 55 which is kept in contact with the bottom surface 40e of the narrow portion 40b 56a are pressed into the narrow portion 40b.

The end face 56a of the flange portion 56 on the opposite side of the support portion 55 and the end face 53e of the annular portion 53 on the opposite side of the support portion 55 And the end surface 52e of the vortex axis 52 opposite the support portion 55 (the distal end surface 52e of the vortex axis 52) are located on a common plane. A portion of the end face 56a of the flange portion 56 and an end face 53e of the annular portion 53 are arranged to face the bottom surface of the annular groove 43. [ A portion of the end face 56a of the flange portion 56, an end face 53e of the annular portion 53 and the annular groove 43 define the oil reservoir space 46. The oil storage space 46 is connected to the refrigerant discharge space 45 and is located radially outward of the refrigerant discharge space 45. In this embodiment, since the oil storage space 46 and the refrigerant discharge space 45 are continuous, a viewable boundary between the oil storage space 46 and the refrigerant discharge space 45 is not actually seen. However, in order to clearly show that the refrigerant discharge space 45 is the space (or the separation space 54) reaching the bottom surface 40e of the narrow portion 40b, the oil storage space 46 and the refrigerant discharge space 45 Is shown in the figure.

The length (maximum length) L1 of the refrigerant discharge space 45 is larger than the length L2 of the separation space 54 in the extending direction (axial direction) of the annular portion 53. [ The width (size) H1 of the refrigerant discharge space 45 is smaller than the width (size) H2 of the separation space 54 in the radial direction of the annular portion 53. [ The width (size) H2 of the separation space 54 in the radial direction of the annular portion 53 is referred to as the inner diameter of the annular portion 53. [ The length L3 of the oil storage space 46 is smaller than the length L1 of the refrigerant discharge space 45 in the extending direction of the annular portion 53. [ The oil storage space 46 is connected to the displacement control valve 38 via the passage 48a.

The discharge passage 33 includes a downstream passage 33e located on the downstream side of the refrigerant discharge space 45 in the flow direction of the refrigerant. The downstream passage 33e extends in a direction perpendicular to the extending direction of the annular portion 53 and communicates with the refrigerant discharge space 45. [ The width (size) H1 of the refrigerant discharge space 45 in the radial direction of the annular portion 53 is equal to the width (size) H3 of the downstream passage 33e in the direction perpendicular to the extending direction of the downstream passage 33e, . In other words, the open cross-sectional area of the refrigerant discharge space 45 is larger than the open cross-sectional area of the downstream passage 33e.

An annular space (47) is arranged outside the annular portion (53) in the accommodating chamber (40). The annular portion 53 has an introduction hole 57 for connecting the annular space 47 (the discharge chamber 27) to the separation space 54 (discharge passage 33) 4 in the embodiment. The introduction holes 57 extend in a direction perpendicular to the extending direction of the annular portion 53, respectively. The openings of the respective introduction holes 57 connected to the separation space 54 are oriented in a direction perpendicular to the extending direction of the annular portion 53.

As shown in Fig. 3, each introducing hole 57 extends linearly through the annular portion 53 in a tangential direction on the inner peripheral surface of the annular portion 53. As shown in Fig. Thus, the opening of each introduction hole 57 connected to the separation space 54 is tangentially directed to the inner peripheral surface of the annular portion 53. The introduction holes 57 are arranged so as to be separated from each other by a predetermined angular interval such that the openings of any two introduction holes 57 adjacent in the circumferential direction are oriented substantially perpendicular to each other.

Now, the operation of the present embodiment will be described.

2, the refrigerant is introduced into the space 47 by the partition member 51 and the annular portion 53, and is discharged through the introduction hole 57 into the separation space 27, (54). The refrigerant flowing into the separation space 54 is swirled along the separation space 54 so that the oil contained in the refrigerant is separated from the refrigerant by centrifugal separation and attached to the inner peripheral surface of the annular portion 53. Oil adhering to the inner peripheral surface of the annular portion 53 is introduced into the oil storage space 46 by flowing along the annular portion 53. The oil-separated refrigerant is discharged from the separation space 54 into the refrigerant discharge space 45.

The refrigerant introduced into the separation space 54 via the introduction hole 57 flows from the inside of the annular space 53 to the inside of the annular space 53, It swirls easily. Each of the introduction holes 57 extends in a direction perpendicular to the extending direction of the annular portion 53. The number of vortex rotations of the refrigerant introduced into the separation space 54 through the introduction hole 57 is increased as compared with the case where the introduction holes 57 extend obliquely with respect to the extending direction of the annular portion 53, Oil separation performance.

The length L1 of the refrigerant discharge space 45 is longer than the length L2 of the separation space 54 in the extending direction (axial direction) of the annular portion 53. [ The refrigerant discharged into the refrigerant discharge space 45 is stagnated in the refrigerant discharge space 45 as compared with the case where the length L2 of the refrigerant discharge space 45 is shorter than the length L2 of the separation space 54. [ Is more effectively suppressed. As a result, the vortex of the refrigerant in the separation space 54 is suppressed from being adversely affected by such stagnation.

The width (size) H1 of the refrigerant discharge space 45 is smaller than the width (size) H2 of the separation space 54 in the radial direction of the annular portion 53. [ Therefore, as compared with the case where the width (size) H1 of the refrigerant discharge space 45 is larger than the width (size) H2 of the separation space 54, the refrigerant discharged into the refrigerant discharge space 45 flows, It is more effectively suppressed from diffusing in the radial direction of the base plate 53. As a result, the vortex of the refrigerant in the separation space 54 is suppressed from being adversely affected by such diffusion.

After being stored in the oil storage space 46, the oil is supplied to the crank chamber 16 via the passage 48a, the displacement control valve 38 and the supply passage 37 and lubricates the sliding parts. The oil storage space 46, the passage 48a, and the supply passage 37 constitute the oil passage 48. [ The crank chamber 16 corresponds to the oil storage chamber into which the oil separated from the refrigerant is introduced by the oil separating member 50. The refrigerant whose oil is separated by the oil separating member 50 is supplied to the external refrigerant circuit 35 via the downstream passage 33e.

The above-described embodiment provides the following advantages.

 (1) The length L1 of the refrigerant discharge space 45 is longer than the length L2 of the separation space 54 in the extending direction (axial direction) of the annular portion 53. [ Compared to the case where the length L1 of the refrigerant discharge space 45 is smaller than or equal to the length L2 of the separation space 54 in this configuration, It is more effectively suppressed to be stagnated in the body 45. Therefore, the vortex of the refrigerant in the separation space 54 is suppressed from being adversely affected by such stagnation. The width (size) H1 of the refrigerant discharge space 45 is smaller than the width (size) H2 of the separation space 54 in the radial direction of the annular portion 53. [ In the case of this configuration, as compared with the case where the width (size) H1 of the refrigerant discharge space 45 is larger than the width (size) H2 of the separation space 54, The refrigerant is more effectively suppressed from diffusing in the radial direction. Therefore, the vortex of the refrigerant in the separation space 54 is suppressed from being adversely affected by such diffusion. For the reasons described above, the oil is effectively separated from the refrigerant.

 (2) The width (size) H1 of the refrigerant discharge space 45 in the radial direction of the annular portion 53 is equal to the width (size) of the downstream passage 33e in the direction perpendicular to the extending direction of the downstream passage 33e, (H3). Compared with the case where the width (size) H1 of the refrigerant discharge space 45 is smaller than the width (size) H3 of the downstream passage 33e in this configuration, The smooth flow of the refrigerant is less likely to be disturbed by the pressure loss in the refrigerant discharge space 45.

 (3) In the extending direction of the annular portion 53, the length L3 of the oil storage space 46 is smaller than the length L1 of the refrigerant discharge space 45. In this configuration, the refrigerant discharged into the refrigerant discharge space 45 does not easily flow into the oil storage space 46. Accordingly, the oil stored in the oil storage space 46 is suppressed from swirling upward by the refrigerant discharged into the refrigerant discharge space 45, and is remixed with the refrigerant.

 (4) The end face 52e of the vortex axis 52 on the opposite side of the side on which the support portion 55 is provided has an end face 52e of the annular portion 53 on the opposite side to which the support portion 55 is provided And 53e. When the end face 52e of the vortex shaft 52 projects further into the refrigerant discharge space 45 than the end face 53e of the annular portion 53 and is located in the refrigerant discharge space 45, 45) may be narrow, and the refrigerant in the refrigerant discharge space 45 may easily flow into the oil storage space 46. In this case, the oil in the oil storage space 46 will swirl up by the refrigerant. However, this embodiment avoids such disadvantages.

The above-described embodiment can be modified as follows.

The length L3 of the oil storage space 46 in the extending direction of the annular portion 53 may be larger than the length L1 of the refrigerant discharge space 45. In this embodiment,

The length L3 of the oil storage space 46 in the extending direction of the annular portion 53 may be equal to the length L1 of the refrigerant discharge space 45. In this embodiment,

 The width (size) H1 of the refrigerant discharge space 45 in the radial direction of the annular portion 53 is larger than the width (size) H1 of the downstream passage 33e in the direction perpendicular to the extending direction of the downstream passage 33e Width (size) (H3).

 In the embodiment illustrated above, the width (size) H1 of the refrigerant discharge space 45 may be equal to the width (size) H2 of the separation space 54 in the radial direction of the annular portion 53.

The end face 52e of the vortex axis 52 on the opposite side of the side on which the support portion 55 is provided has an annular portion 53 on the opposite side to which the support portion 55 is provided, And may be in a retracted position from the end face 53e.

The end face 52e of the vortex axis 52 on the opposite side of the side on which the support portion 55 is provided has an annular portion 53 on the opposite side to which the support portion 55 is provided, The refrigerant can be further protruded to the refrigerant discharge space 45 beyond the end surface 53e of the refrigerant discharge tube 45. [

In the embodiment illustrated above, the introduction holes 57 may each extend diagonally with respect to the extending direction of the annular portion 53.

In the embodiment illustrated above, the oil separation member 50 need not necessarily have the vortex axis 52.

In the embodiment illustrated above, the flange portion 56 may be omitted from the oil separation member 50. [ In this case, the oil storage space 46 may be defined by a part of the end surface 53e of the annular portion 53 and the annular groove 43. [

In the embodiment illustrated above, instead of using a portion of the oil separation member 50 as a member for defining the oil storage space 46, the rear housing member 15 additionally includes an oil reservoir 46 It can have a prescribed groove.

In the embodiment illustrated above, the number of the introduction holes 57 is not particularly limited.

In the embodiment illustrated above, the oil storage space 46 may be connected to the suction chamber 26 via a passage provided in the rear housing member 15. [ In this case, the oil stored in the oil storage space 46 is supplied to the suction chamber 26 through the passage and introduced into the suction chamber 26 from the outlet side of the evaporator 35c of the external refrigerant circuit 35 ≪ / RTI > The oil mixed with the refrigerant lubricates the sliding parts of the swash plate type compressor (10).

In the embodiment illustrated above, the oil separating member 50 may be arranged such that the extending direction of the annular portion 53 intersects the axial direction of the rotary shaft 17.

In the embodiment illustrated above, the oil separating member 50 may have an elliptical shape in plan view.

In the embodiment illustrated above, a part of the oil separation member 50 may be constituted by a part of the housing 11. [ For example, the vortex axis 52 and the annular portion 53 may extend from the housing 11 toward the support portion 55.

In the embodiment illustrated above, the compressor 10 is a variable displacement compressor. However, the compressor 10 may be a fixed capacity type compressor.

In the embodiment illustrated above, the compressor 10 is in the form of a single-piston-piston, but may also be in the form of a double-headed piston.

In the embodiment illustrated above, the compressor 10 may be used in any type of air conditioner instead of a vehicle air conditioner.

In the embodiment illustrated above, the compressor 10 is a swash plate compressor, but may be a scroll compressor, a vane compressor, or a Roots type compressor.

In the embodiment illustrated above, carbon dioxide is used as the refrigerant. However, chlorofluorocarbons can be used as the refrigerant.

Therefore, the examples and embodiments of the present invention should be considered as illustrative and not restrictive, and the invention is not to be limited to the details given in the present invention, but may be modified within the scope and equivalents of the appended claims.

Claims (6)

housing,
A discharge chamber provided in the housing,
An oil separation member for separating the oil from the refrigerant discharged from the discharge chamber,
A discharge passage provided in the housing, the discharge passage releasing refrigerant from which oil has been separated by the oil separating member to an external refrigerant circuit;
The oil passage introducing the oil separated by the oil separating member into the oil reservoir chamber, wherein the oil passage is provided in the housing,
Wherein the oil separating member has a partition member separating the discharge chamber from the discharge passage,
Wherein the partition member has an annular portion extending toward the discharge passage, a separation space is provided inside the annular portion,
The annular portion having an introduction hole connecting the discharge chamber and the discharge passage to each other,
Wherein the discharge passage includes a refrigerant discharge space in which the oil separated by the oil separating member is discharged into the refrigerant discharge space,
The length of the refrigerant discharge space in the direction of extension of the annular portion is longer than the length of the separation space,
And the size of the refrigerant discharge space in the radial direction of the annular portion is smaller than or equal to the size of the separation space. The method according to claim 1,
Wherein the discharge passage includes a downstream passage positioned on a downstream side of the refrigerant discharge space in a flow direction of the refrigerant,
The downstream passage extending in a direction intersecting the extending direction of the annular portion,
Wherein the size of the refrigerant discharge space is larger in the radial direction of the annular portion and in the direction perpendicular to the extending direction of the downstream passage than the size of the downstream passage. The method according to claim 1,
Wherein the oil passage includes an oil storage space located radially outward of the refrigerant discharge space in the radial direction of the annular portion and the oil separated from the refrigerant by the oil separation member is stored in the oil storage space,
And the length of the oil storage space is shorter than the length of the refrigerant discharge space in the direction of extension of the annular portion. 4. The method according to any one of claims 1 to 3,
The oil separation member has a disc-shaped support portion,
And the annular portion extends from the support portion toward the refrigerant discharge space. 5. The method of claim 4,
Wherein the oil separating member has a columnar vortex axis,
The vortex axis being located radially inside the annular portion and extending from the support portion in a direction parallel to the direction of extension of the annular portion. 6. The method of claim 5,
Wherein the distal end surface of the annular portion and the distal end surface of the vortex axis are located on a common plane.

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