WO2015093504A1

WO2015093504A1 - Compressor

Info

Publication number: WO2015093504A1
Application number: PCT/JP2014/083336
Authority: WO
Inventors: 高橋　知靖; 孝則寺屋
Original assignee: 株式会社ヴァレオジャパン
Priority date: 2013-12-20
Filing date: 2014-12-17
Publication date: 2015-06-25
Also published as: EP3156650A1; JP2015117671A; CN105814312A; JP6238726B2; EP3156650A4

Abstract

A compressor provided with a centrifugal oil separator, wherein the oil separator of the compressor is reduced in size by improving the oil separation performance of the oil separator. Even when the oil separator is reduced in size, a refrigerant inlet channel can be formed without interference between a machining drill and a separating pipe when the refrigerant inlet channel is drilled, and the refrigerant inlet channel is smoothly joined to the inner peripheral surface of a separation chamber, thereby further improving oil separation performance. Furthermore, large clearance is ensured in the region faced by the opening of the refrigerant inlet channel. [Solution] A compressor provided with an oil separator (14) having a separation chamber (22), a separation pipe (23) accommodated in the separation chamber (22), and a refrigerant inlet channel (21) communicating a discharge chamber (11) and the separation chamber (22), wherein the axial center (O) of the separation chamber (22) and the axial center (O') of the separation pipe (23) are misaligned.

Description

Compressor

The present invention relates to a compressor provided with a centrifugal oil separator, and more particularly to a compressor provided with an oil separator having high oil separation performance.

Conventionally, as a compressor including a centrifugal oil separator that separates oil from a working fluid compressed by a compression mechanism, for example, the compressors disclosed in Patent Document 1 and Patent Document 2 are known. .

Among these, the compressor shown in Patent Document 1 includes a movable member that moves as the shaft rotates, and a fixed member that forms a compression chamber together with the movable member. The fixing member is integrally provided with an oil separator that introduces the working fluid compressed in the compression chamber and separates the oil. The oil separator includes a separation chamber for introducing the working fluid compressed in the compression chamber, and a separation pipe accommodated in the separation chamber for swirling the introduced working fluid. It is integrally formed on the fixing member on the same axis.

Also, the compressor shown in Patent Document 2 includes a cyclone block (oil separator) for separating the refrigeration oil from the refrigerant gas in the rear side block constituting the housing of the compressor. This oil separator includes a centrifuge main body having a cylinder inner circumferential surface for rotating a compressed refrigerant gas, a bottom surface closing one end of the cylinder inner circumferential surface, and a circle surrounded by the cylinder inner circumferential surface. In the columnar space, an inner cylindrical gas exhaust part that is arranged along the axis of the cylindrical space and guides the refrigerant gas swirled inside from the end surface opposite to the bottom surface to the outside of the centrifugal separation body part. It is configured. Also in this compressor, the gas exhaust part and the centrifugal separation body part are constituted by separate members.

As described above, the conventional oil separator includes a separation chamber formed in a substantially columnar space and a cylindrical separation pipe accommodated in the separation chamber in a centrifugal separation body provided in the housing. It is formed by aligning the axes of each other, and the working fluid containing oil is swirled in a substantially cylindrical space defined by the inner peripheral surface of the separation chamber and the outer peripheral surface of the separation pipe. The oil is centrifuged.

Republication W2011-080865 public information JP 2007-327340 A

However, in the conventional oil separator in which the separation chamber and the separation pipe are formed concentrically, it is necessary to secure a separation chamber of a certain size in order to secure the required separation capacity. It was difficult to reduce the size of the separator, and it was difficult to reduce the size of the compressor.
For this reason, it is required to improve the oil separation performance of the oil separator and to reduce the size of the oil separator.

In addition, in the configuration shown in Patent Document 1 in which the centrifugal separation main body defining the separation chamber and the separation pipe are integrally formed, an operation of machining the refrigerant introduction path for introducing the high-pressure gas of the oil separator with a machining drill If the clearance between the outer peripheral surface of the separation pipe and the inner peripheral surface of the separation chamber is not sufficiently secured, the following inconvenience occurs. That is, when the machining drill is inserted deeply into the separation chamber when the machining drill is moved from the side of the separation main body in the tangential direction of the inner peripheral surface of the separation chamber to pierce the coolant introduction path, FIG. As shown in FIG. 2, there is a disadvantage that the machining drill 30 interferes with the separation pipe 23 and makes a hole in the separation pipe 23. On the other hand, if the machining drill 30 is shallowly inserted to avoid interference with the separation pipe 23, the coolant introduction path 21 is tangent to the inner peripheral surface of the separation chamber 22, as shown in FIG. Since the working fluid is not smoothly connected to the separation chamber 22 and is not smoothly introduced into the separation chamber 22, the working fluid is not swirled well, and the oil separation performance is deteriorated.

In order to avoid such inconvenience, the clearance between the outer peripheral surface of the separation pipe and the inner peripheral surface of the separation chamber should be sufficiently large so that it does not interfere with the separation pipe even if the machining drill is inserted deeply. Is desirable. However, in the conventional configuration described above, if the clearance is to be secured large, the oil separator itself is increased in size, and it is difficult to reduce the size of the compressor.

Also, in the configuration as shown in Patent Document 2 in which the separation pipe is separated from the centrifugal separation main body defining the separation chamber, there is a clearance between the outer peripheral surface of the separation pipe and the inner peripheral surface of the separation chamber. If it is insufficient, the opening part of the refrigerant introduction path is too close to the separation pipe, and there is a disadvantage that the working fluid introduced into the separation chamber collides with the separation pipe and the working fluid cannot be swirled well in the separation chamber.

To avoid such inconvenience, it is necessary to increase the clearance between the outer peripheral surface of the pipe part and the inner peripheral surface of the separation chamber. However, in the conventional configuration described above, if this clearance is to be secured large, the oil separator is increased in size, and it is difficult to reduce the size of the compressor.

The present invention has been made in view of such circumstances, and avoids the above-mentioned disadvantages caused by the fact that the separation chamber and the separation pipe are formed concentrically, and improves the oil separation performance of the oil separator of the compressor. The problem is to reduce the size of the oil separator by improving it. Even when the oil separator is downsized, it is possible to avoid the inconvenience that the machining drill interferes with the separation pipe when drilling the refrigerant introduction path, and to smoothly connect the refrigerant introduction path to the inner peripheral surface of the separation chamber. It is possible to further improve the oil separation performance and to provide a compressor including an oil separator that can avoid the disadvantage that the opening of the refrigerant introduction path is too close to the separation pipe. Is also an issue.

In order to achieve the above object, a compressor according to the present invention includes a housing, a compression mechanism accommodated in the housing, and a discharge chamber formed in the housing and discharged with a working fluid compressed by the compression mechanism. And an oil separator that is provided in the housing and separates oil from the working fluid compressed by the compression mechanism, and the oil separator is accommodated in the cylindrical separation chamber and the separation chamber In the case where it is configured to have a separation pipe and a refrigerant introduction path that communicates the discharge chamber and the separation chamber, the axis of the separation chamber and the axis of the separation pipe are misaligned. It is said.

Accordingly, by shifting the axis of the separation chamber and the axis of the separation pipe, the passage section of the passage in which the compressed working fluid swirls can be changed, so that the oil separation performance can be improved. . As a result, the oil separator can be miniaturized as much as the oil separation capability can be increased.

Even when the oil separator is downsized, the center of the separation chamber and the center of the separation pipe are misaligned, so the clearance between the inner peripheral surface of the separation chamber and the outer peripheral surface of the separation pipe is partially It is possible to make it larger. Therefore, by drilling the coolant introduction path so as to face this portion, the machining drill inserted when drilling the coolant introduction path does not interfere with the separation pipe. Further, there is no inconvenience that the machining drill is shallowly inserted to avoid interference with the separation pipe and the refrigerant introduction path cannot be smoothly connected to the inner peripheral surface of the separation chamber. Furthermore, there is no inconvenience that the opening of the refrigerant introduction path is too close to the separation pipe.

Here, in order to improve the oil separation performance, the axis of the separation pipe may be shifted in an arbitrary direction with respect to the axis of the separation chamber, but from the viewpoint of processing the refrigerant introduction path, the axis of the separation pipe It is preferable to shift the axis of each other so that the distance between the refrigerant introduction path and the opening part that opens into the separation chamber is longer than the distance between the axis of the separation chamber and the opening part.

With such a configuration, the coolant introduction path can be opened so as to face a region where the passage cross section between the outer peripheral surface of the separation pipe and the inner peripheral surface of the separation chamber becomes relatively large, and the machining drill It is easy to avoid interference with the separation pipe when inserting the working fluid, and the working fluid can be introduced smoothly. In addition, since the introduced working fluid flows toward a region where the distance between the separation pipe and the separation chamber is narrow, it is possible to increase the flow rate of the working fluid and efficiently separate the oil.

In particular, the axis of the separation pipe is shifted from the axis of the separation chamber in a direction substantially perpendicular to the axis of the refrigerant introduction path, so that the opening portion of the refrigerant introduction path is separated from the outer peripheral surface of the separation pipe and the separation chamber. It is possible to face the region where the cross section of the passage between the inner peripheral surface is the largest. As a result, the coolant introduction path can be easily processed, and the working fluid can be smoothly introduced into the separation chamber. Moreover, even when processing of the refrigerant introduction path is anticipated, the oil separator can be easily downsized.

The separation chamber is preferably formed integrally with the housing, and the separation pipe is preferably integrated with a portion of the housing that defines the separation chamber.
By adopting such a configuration, it is not necessary to adjust the axial center position of the separation pipe, and variations in the oil separation effect can be eliminated.

As described above, according to the present invention, in the compressor equipped with the centrifugal oil separator, the axis of the separation chamber of the oil separator and the axis of the separation pipe are shifted, so that the oil separation The oil separation performance of the compressor can be improved, and the oil separation performance can be improved, so that the oil separator can be reduced in size, and the compressor can be reduced in size. .

Even when the oil separator is downsized, the refrigerant introduction path can be formed so as to face a portion where the clearance between the outer peripheral surface of the separation pipe and the inner peripheral surface of the separation chamber is increased. An effect is obtained.
-When drilling the coolant introduction path, the machining drill will not interfere with the separation pipe.
-The refrigerant introduction path can be smoothly connected to the inner peripheral surface of the separation chamber, and the problem that the opening of the refrigerant introduction path is too close to the separation pipe is eliminated.
-It is possible to conduct the oil efficiently by guiding the working fluid smoothly to the separation chamber.

FIG. 1 is a side sectional view showing a configuration example of a compressor according to the present invention, and (a) is a sectional view in which the compressor is cut so that an oil separator and a discharge port are exposed. ) Is a cross-sectional view of the compressor cut so that the suction port is exposed. 2A shows a cross-sectional view taken along the line AA in FIG. 1A, and FIG. 2B shows a cross-sectional view taken along the line BB in FIG. 1A. FIG. 3 is a diagram showing a state in which the coolant introduction path communicating with the separation chamber of the oil separator is processed by a processing drill. FIG. 3A shows a state where the processing drill is inserted from the outside of the housing to drill the coolant introduction path. The figure explaining work, (b) is the enlarged view which expanded the part of the oil separator of (a). FIG. 4 is a diagram for explaining the behavior of the working fluid when the working fluid is introduced into the separation chamber in the compressor employing the oil separator according to the present invention. FIG. The figure explaining the behavior of a fluid, (b) is a figure explaining the behavior of the working fluid at the time of a large flow rate. FIGS. 5A and 5B are diagrams for explaining inconveniences when a refrigerant introduction path is formed with respect to a conventional oil separator. FIG. 5A is a diagram illustrating a state in which a machining drill is inserted deeply, and FIG. It is a figure which shows the state inserted shallowly.

Hereinafter, embodiments of a compressor according to the present invention will be described with reference to the accompanying drawings.

1 and 2 show a vane type compressor suitable for a refrigeration cycle using a refrigerant as a working fluid. The vane compressor accommodates a movable member 2 that is movable as the shaft 1 rotates, a fixed member 4 that forms a compression chamber 3 together with the movable member 2, and the movable member 2 and the fixed member 4. 4 and a shell member 5 constituting a housing.

The fixed member 4 includes a cylinder portion 4a that accommodates the movable member 2, and a rear side block portion 4b that is integrally formed following the rear side of the cylinder portion 4a.

The movable member 2 is rotatably accommodated in the cylinder portion 4a of the fixed member 4, and has a rotor 2a fixed to the shaft 1 and a vane 2b inserted into a vane groove 6 provided in the rotor 2a. It is configured.

The shell member 5 includes a front side block portion 5a that abuts on the front side end surface of the cylinder portion 4a, and a cylindrical portion 5b formed so as to surround the outer peripheral surfaces of the cylinder portion 4a and the rear side block portion 4b. Has been.

The shaft 1 is rotatably supported by the front side block portion 5a of the shell member 5 and the rear side block portion 4b of the fixing member 4 via a plain bearing. The shell member 5 has a suction space (low pressure) configured to include a suction port 7 and a discharge port 8 for the working fluid (refrigerant gas) and a recess 9 formed in the cylinder portion 4 a of the fixing member 4. Space) 10 is formed. Further, a discharge chamber (high-pressure space) 11 described later is defined by the cylinder portion 4 a of the fixing member 4 and the cylindrical portion 5 b of the shell member 5. The discharge chamber 11 communicates with the discharge port 8 via an oil separator 14 formed in the rear side block portion 4b of the fixing member 4.

The space surrounded by the cylinder part 4a and the cross section of the rotor 2a are formed in a perfect circle. The axial center of the cylinder portion 4a and the axial center of the rotor 2a are provided so as to be shifted so that the outer peripheral surface of the rotor 2a and the inner peripheral surface of the cylinder portion 4a are in contact at one place in the circumferential direction (the inner diameter of the cylinder portion) A compression space 13 is defined between the inner peripheral surface of the cylinder portion 4a and the outer peripheral surface of the rotor 2a. This compression space 13 is partitioned by a vane 2b and divided into a plurality of compression chambers 3, and the volume of each compression chamber 3 changes as the rotor 2a rotates.

The shell member 5 includes a boss portion 5c integrated with the front side block portion 5a, and a pulley 15 for transmitting rotational power to the shaft 1 is rotatably mounted on the shell member 5. The pulley 15 rotates from the pulley 15 via an electromagnetic clutch 16. Power is transmitted to the shaft 1.

Further, the cylinder part 4a of the fixing member 4 has a flange part 4c. 4d is formed. The front flange portion 4c is formed in a shape that matches the inner peripheral shape of the shell member 5, is fitted inside the shell member 5, and is in contact with the end surface of the front side block portion 5a. Further, the rear flange portion 4 d is also formed in a shape that matches the inner peripheral shape of the shell member 5. The rear flange portion 4d is fitted inside the shell member 5 and hermetically sealed with the shell member 5 by a sealing member such as an O-ring.

A suction port 17 communicating with the suction space 10 and a discharge port 18 communicating with the discharge chamber 11 are provided on the peripheral surface of the cylinder portion 4a. Therefore, when the cylinder portion 4a is fitted into the shell member 5, the suction space 10 communicates with the compression chamber 3 via the suction port 17, and between the outer peripheral surface of the cylinder portion 4a and the inner peripheral surface of the cylindrical portion 5b. , Both ends are flange portions 4c. The discharge chamber 11 defined by 4d is formed, and the discharge chamber 11 can communicate with the compression chamber 3 via the discharge port 18. The discharge port 18 is opened and closed by a discharge valve 19 accommodated in the discharge chamber 11.

The discharge chamber 11 is provided over almost the entire circumference of the cylinder portion 4a from a portion where the discharge valve 19 is provided with a partition wall 20 protruding in the vicinity of the discharge port 18 of the cylinder portion 4a as a boundary. . The portion of the partition 20 opposite to the side where the discharge port 18 is provided communicates with an oil separator 14 described below through a refrigerant introduction path 21 formed in the flange portion 4d (rear side block portion 4b). is doing.

The oil separator 14 is formed integrally with the rear side block portion 4b of the fixing member 4, and includes a separation chamber 22 formed in a cylindrical space through which the refrigerant introduction path 21 formed in the flange portion 4d communicates. I have. The oil separator 14 is configured by housing a substantially cylindrical separation pipe 23 formed integrally with the fixing member 4 (rear side block portion 4b) in the separation chamber 22.

As shown in FIG. 3, the refrigerant introduction path 21 is formed so as to be connected in a tangential direction to the inner peripheral surface of the upper end portion of the separation chamber 22, and is drilled by the machining drill 30 from the discharge chamber side. Is formed.

The separation chamber 22 is formed so as to extend in a direction substantially orthogonal to the axial direction of the shaft 1 and to have its axis inclined obliquely with respect to the vertical line. An upper end portion of the separation chamber 22 communicates with the discharge port 8 of the shell member 5 through a separation pipe 23, and a lower end portion is opened on a side surface of the rear side block portion 4b. The opening at the lower end of the separation chamber 22 is covered with the cylindrical portion 5 b of the shell member 5.

In this example, the cylinder part 5b is extended in the axial direction to the extent that the entire rear side block part 4b is accommodated. Further, the separation chamber 22 is hermetically sealed between the cylindrical portion 5b of the shell member 5 by a sealing member such as an O-ring provided in the circumferential direction of the rear side block portion 4b before and after the axial direction of the compressor. .

In such an oil separator 14, the separation pipe 23 is provided in a state where its axis O ′ is shifted with respect to the axis O of the separation chamber 22. The direction in which the axis O ′ of the separation pipe 23 is displaced with respect to the axis O of the separation chamber 22 may be set arbitrarily. However, in order to form the refrigerant introduction path 21, the distance between the axis O ′ of the separation pipe 23 and the opening portion where the refrigerant introduction path 21 opens into the separation chamber 22 is the distance between the axis O of the separation chamber 22 and the opening portion. The direction is longer than the distance. In particular, in this example, the axis O ′ of the separation pipe 23 is shifted from the axis O of the separation chamber 22 in a substantially vertical direction (β direction) with respect to the axis α of the refrigerant introduction path 21.

Note that the separation chamber 22 and the separation pipe 23 that constitute such an oil separator 14 are simultaneously formed when the fixing member 4 is formed by casting. Therefore, the separation chamber 22 is formed in a tapered shape whose diameter gradually increases toward the opening at the lower end so that the mold can be easily removed, and the outer peripheral surface of the separation pipe 23 toward the tip. The diameter of the taper is gradually reduced.

Therefore, the working fluid that has flowed into the separation chamber 22 swirls around the separation pipe 23 accommodated in the separation chamber 22, oil mixed in the process is separated, and the working fluid from which the oil has been separated is separated. It discharges from the discharge outlet 8 through the separation pipe 23. The separated oil is stored in an oil storage chamber 25 formed at the bottom of the fixing member 4 via an oil discharge hole 24 formed in the fixing member 4 so as to communicate with the lower end of the separation chamber 22. Thereafter, the oil is supplied to each lubrication portion through the oil supply passage 26 due to a pressure difference between the oil storage chamber 25 and each lubrication portion.

In the above configuration, rotational power from a power source (not shown) is transmitted to the shaft 1 via the pulley 15 and the electromagnetic clutch 16, and when the rotor 2a rotates, the working fluid flowing into the suction space 10 from the suction port 7 is sucked into the suction port. The air is sucked into the compression space 13 through 17. Since the volume of each compression chamber 3 partitioned by the vane 2b in the compression space changes with the rotation of the rotor 2a, the working fluid confined between the vanes 2b is compressed and is discharged from the discharge port 18 through the discharge valve 19. And discharged into the discharge chamber 11. The working fluid discharged into the discharge chamber 11 moves in the circumferential direction along the outer peripheral surface of the cylinder portion 4a (along the inner peripheral surface of the cylindrical portion 5b of the shell member 5), and makes one round around the cylinder portion 4a. And it introduce | transduces into the separation chamber 22 of the oil separator 14 integrally formed in the rear side block part 4b via the refrigerant | coolant introduction path 21 formed in the flange part 4d (rear side block part 4b). Thereafter, the oil is separated from the working fluid in the process of swirling in the separation chamber, and is discharged to the external circuit from the discharge port 8 through the separation pipe 23. The separated oil is oil formed at the lower end of the separation chamber 22. It is guided to the oil storage chamber 25 through the discharge hole 24.

At that time, in the oil separator 14, the axis O of the separation chamber 22 and the axis O ′ of the separation pipe 23 are displaced, so that the space between the outer peripheral surface of the separation chamber 22 and the inner peripheral surface of the separation pipe 23 is different. The cross section of the passage (the cross section of the passage in which the compressed working fluid swirls) changes. This change in the cross-section of the passage can improve the oil separation performance.

In particular, when the refrigerant introduction path 21 is formed so as to face a region having a relatively large passage cross section as in the above configuration, the outer peripheral surface of the separation chamber 22 and the separation pipe 23 at a small flow rate with a small discharge capacity. It becomes possible to increase the flow velocity of the working fluid in a region where the passage cross section with respect to the inner peripheral surface becomes relatively small, and it is possible to efficiently separate the oil.

In addition, when the flow rate is large and the discharge capacity is large, the working fluid is swung while being diffused in the axial direction of the separation pipe 23 in a region where the passage cross section is small, so that it is difficult to cause pressure loss while maintaining the flow rate of the working fluid. And sufficient oil separation can be performed.
For this reason, since the oil separation capability can be increased, the oil separator 14 can be made smaller by that amount, which can contribute to the downsizing of the compressor.

Even when the oil separator 14 is downsized, since the axis O of the separation chamber 22 and the axis O ′ of the separation pipe 23 are displaced, the inner peripheral surface of the separation chamber 22 and the outer peripheral surface of the separation pipe 23 By drilling so that the refrigerant introduction path 21 faces the part where the clearance between them is large, the machining drill 30 does not interfere with the separation pipe 23 when the refrigerant introduction path 21 is drilled. Further, there is no inconvenience that the processing drill 30 is shallowly inserted to avoid interference with the separation pipe 23 and the refrigerant introduction path 21 cannot be smoothly connected to the wall surface of the separation chamber 22. Furthermore, there is no inconvenience that the opening of the refrigerant introduction path 21 is too close to the separation pipe 23, and efficient oil separation can be ensured.

In particular, in the above-described configuration example, the axis O ′ of the separation pipe 23 is shifted from the axis O of the separation chamber 22 in a direction substantially perpendicular to the axis α of the refrigerant introduction path 21 (β direction). It is possible to make the refrigerant introduction path 21 face the area where the passage cross section between the outer peripheral surface of the separation pipe 23 and the inner peripheral surface of the separation chamber 22 becomes the largest in the opening portion of the path 21. Therefore, the coolant introduction path 21 can be easily processed, and the working fluid can be smoothly introduced into the separation chamber 22. Moreover, the oil separator can be easily downsized even when machining with a machining drill in the refrigerant introduction path 21 is anticipated.

In the above configuration, since the separation pipe 23 is integrally formed with the housing (rear side block portion 4b) together with the separation chamber 22, it is not necessary to adjust the axial center position of the separation pipe 23 and the oil separation effect varies. It can be eliminated. However, in order to improve the separation performance and reduce the size of the oil separator 14, the separation pipe 23 does not necessarily have to be formed integrally with the housing (rear side block portion 4 b), and the separation pipe 23 defines the separation chamber 22. You may make it comprise with another member with respect to the member (rear side block part 4b) to comprise.

In the above-described configuration, the example applied to the vane compressor has been described. However, the fixed scroll (fixed member) fixed to the housing and the movable scroll (movable member) movable (turning) with respect to the fixed scroll. The movable scroll is driven to rotate by a shaft rotatably disposed in the housing, and with the rotation of the movable scroll, the volume of the compression chamber formed by both scrolls is enlarged and reduced to suck and compress the refrigerant. For the scroll type compressor, the above-described configuration may be employed when a centrifugal separation type oil separator is provided on the fixed member.
Further, in the above-described configuration, the configuration example in which the oil separator 14 is provided in the rear side block portion 4b integrated with the cylinder portion 4a and accommodated in the shell member 5 has been described, but the front side integrated with the cylinder portion has been described. In the configuration in which an oil separator is provided in the block portion and this is accommodated in the shell member, the same configuration as described above may be adopted.

DESCRIPTION OF SYMBOLS 1 Shaft 2 Movable part 3 Compression chamber 4 Fixed part 4a Cylinder part 4b Rear side block part 5 Shell member 5a Front side block part 5b Cylindrical part 11 Discharge chamber 14 Oil separator 21 Refrigerant introduction path 22 Separation chamber 23 Separation pipe O Axle O 'Axis of separation pipe α Axis of refrigerant introduction path

Claims

A housing;
A compression mechanism housed in the housing;
A discharge chamber that is formed in the housing and discharges the working fluid compressed by the compression mechanism;
An oil separator provided in the housing and separating oil from the working fluid compressed by the compression mechanism;
With
The oil separator is a centrifugal separation type configured to have a cylindrical separation chamber, a separation pipe accommodated in the separation chamber, and a refrigerant introduction path communicating the discharge chamber and the separation chamber. In a compressor,
The compressor characterized in that an axis of the separation chamber is displaced from an axis of the separation pipe.
The distance between the axis of the separation pipe and the opening part where the refrigerant introduction path opens into the separation chamber is longer than the distance between the axis of the separation chamber and the opening part. Compressor.
3. The compressor according to claim 2, wherein the axis of the separation pipe is displaced in a direction substantially perpendicular to the axis of the refrigerant introduction path from the axis of the separation chamber.
4. The separation chamber according to claim 1, wherein the separation chamber is integrally formed with the housing, and the separation pipe is integrated with a portion of the housing that defines the separation chamber. Compressor.