CN217107425U

CN217107425U - Scroll compressor having a plurality of scroll members

Info

Publication number: CN217107425U
Application number: CN202220941437.5U
Authority: CN
Inventors: 耿利威; 陈惠�; 苏敏; 梁计; 丁佳欣
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Copeland Suzhou Co Ltd
Priority date: 2022-04-22
Filing date: 2022-04-22
Publication date: 2022-08-02
Anticipated expiration: 2032-04-22

Abstract

The utility model relates to a scroll compressor, including compression mechanism, drive shaft, drive bearing and main bearing seat. The drive shaft is configured to drive the compression mechanism. The drive bearing is disposed between the compression mechanism and the drive shaft. The main bearing housing includes: a body for slidably supporting the compression mechanism and rotatably supporting the drive shaft; a central recess defined by the body; and an inflow channel disposed in the body and allowing fluid to enter the central recess to cool the drive bearing. According to the utility model discloses a scroll compressor can show the temperature that reduces drive bearing, especially with lower cost.

Description

Scroll compressor having a plurality of scroll members

Technical Field

The present application relates to a scroll compressor.

Background

This section merely provides background information related to the present application and may not necessarily be prior art.

A scroll compressor typically includes a compression mechanism, a motor, a drive shaft, a drive bearing and a main bearing housing. The compression mechanism includes a fixed scroll member and a movable scroll member. The orbiting scroll part is supported on a main bearing housing and performs an orbiting motion with respect to the non-orbiting scroll part by driving of a driving shaft such that the vanes of the orbiting and non-orbiting scroll parts are engaged with each other to form a compression chamber compressing a working fluid (e.g., a refrigerant) whose volume is gradually reduced. The drive shaft is rotated by a motor and drives the orbiting scroll member via a drive bearing.

The drive bearings can reduce the lubrication effect at high temperatures and thereby increase wear. As such, the drive bearing will fail prematurely. Friction between each of the orbiting scroll member and the drive shaft and the drive bearing will cause the temperature of the drive bearing to increase. The high temperature generated by the motor during operation will also transfer heat to the drive bearing, causing the temperature of the drive bearing to rise further. If the temperature of the surrounding lubricating oil or the exhaust port of the compression mechanism is too high, the temperature of the drive bearing is also increased by heat transfer. Since the temperature of the drive bearing cannot be too high, the size of the drive bearing becomes a bottleneck in the development process of the scroll compressor.

In some existing compressors, the temperature of the drive bearings is reduced by controlling the high temperature source. For example, the temperature of the exhaust port is reduced by injecting lubricating oil, thereby reducing the temperature of the drive bearing. However, the injected lubricating oil will result in an increased oil circulation rate and a limited improvement of the temperature of the drive bearings. For example, by optimizing the motor, the motor heating is reduced, thereby reducing the temperature of the drive bearings. However, an optimized motor would add significant cost and have limited improvement in the temperature of the drive bearings.

SUMMERY OF THE UTILITY MODEL

In view of the above problems in the prior art, the present invention provides a scroll compressor that can significantly reduce or control the temperature of a drive bearing at a low cost.

According to an aspect of the present invention, there is provided a scroll compressor including a compression mechanism, a drive shaft, a drive bearing, and a main bearing housing. The drive shaft is configured to drive the compression mechanism. The drive bearing is disposed between the compression mechanism and the drive shaft. The main bearing housing includes: a body for slidably supporting the compression mechanism and rotatably supporting the drive shaft; a central recess defined by the body; and an inflow channel disposed in the body and allowing fluid to enter the central recess to cool the drive bearing.

In some embodiments, the scroll compressor includes a plurality of the inflow passages arranged along a circumferential direction of the body.

In some embodiments, the scroll compressor further comprises a conduit configured for introducing fluid to at least one of the inflow passages.

In some embodiments, the conduit has: a first section connected into or oriented towards the inflow channel; and a second section connected to or oriented toward an intake joint of the scroll compressor.

In some embodiments, the inflow channel extends linearly from the inlet offset from a radial direction.

In some embodiments, the inflow channel is disposed tangentially to an inner circumferential surface of the body.

In some embodiments, the scroll compressor further comprises a housing located radially inward of the body, a space being formed between the body and the housing in communication with the inflow passage.

In some embodiments, the cover is annular.

In some embodiments, the cover has a cylindrical wall for defining the space. Further, the body has a stepped portion for supporting one end of the cylindrical wall and/or the cover has a flange extending radially outward from the other end of the cylindrical wall.

In some embodiments, the cover is formed as one piece with the body of the main bearing housing.

In some embodiments, an outflow channel is provided in the body of the main bearing housing radially opposite the inflow channel.

In some embodiments, the scroll compressor includes an intake fitting for introducing a working fluid to be compressed and a motor for driving rotation of the drive shaft, the intake fitting being located between the compression mechanism and the motor in an axial direction of the scroll compressor.

In some embodiments, the air inlet joint is located radially outward of the main bearing housing.

In some embodiments, the scroll compressor further comprises a partition plate dividing a space within a housing of the compressor into a high pressure chamber and a low pressure chamber, the compression mechanism and the main bearing housing being located in the low pressure chamber.

According to the utility model discloses a scroll compressor can obtain following some advantages.

By providing an inflow channel or conduit, a cooling fluid (e.g., gas, gaseous refrigerant, etc.) can be actively introduced at the drive bearing, thereby directly and efficiently reducing the temperature of the drive bearing. Therefore, the lubrication condition of the driving bearing can be remarkably improved, thereby improving the reliability of the operation of the compressor.

The desired cooling effect on the drive bearing is obtained by providing an inflow channel in the main bearing housing, i.e. by designing the flow area. Therefore, such improvements are less costly.

The scroll compressor according to the present invention further includes a conduit so that fluid can be introduced from a desired source to reduce the temperature of the drive bearing. I.e. the cooling fluid and space are not restricted and the costs are lower.

Further, by orienting the inflow passage or providing a cover, the cooling fluid does not directly flow to the drive bearing, so that the oil circulation rate can be prevented from increasing.

In the scroll compressor according to the present invention, the working fluid of low temperature and low pressure can be introduced into the chamber where the main bearing housing and the motor are located, whereby the driving bearing can be cooled directly by the working fluid before compressing the working fluid.

Drawings

The features and advantages of one or more embodiments of the present invention will become more readily understood from the following description with reference to the accompanying drawings, in which:

fig. 1 is a partially schematic longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention;

FIGS. 2A and 2B are perspective views of the main bearing housing of FIG. 1;

FIG. 3 is a schematic, partially sectioned, longitudinal view of a scroll compressor according to a second embodiment of the present invention;

FIG. 4 is a fragmentary longitudinal sectional schematic view of a variation of the scroll compressor of FIG. 3;

fig. 5 is a schematic perspective view of a main bearing housing according to an embodiment of the present invention;

FIG. 6 is a cross-sectional schematic view of the main bearing housing of FIG. 5; and

fig. 7 is a longitudinal sectional view of fig. 5.

Detailed Description

The following description of the preferred embodiment(s) is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. The same reference numerals are used to designate the same components in the respective drawings, and thus the configurations of the same components will not be described repeatedly.

A scroll compressor 100 according to a first embodiment of the present invention will be described first with reference to fig. 1, 2A and 2B. As shown in fig. 1, a scroll compressor 100 includes a cylindrical housing 110, a top cover 112 disposed at one end of the cylindrical housing 110, and a bottom cover (not shown) disposed at the other end of the cylindrical housing 110. The cylindrical shell 110, top cover 112 and bottom cover form the outer shell of the scroll compressor 100 and define an enclosed space.

The scroll compressor 100 may also include a partition 80. A partition 80 divides the enclosed space into a high pressure chamber 181 and a low pressure chamber 182. Low pressure chamber 182 has a low temperature, low pressure working fluid (e.g., refrigerant) introduced therein. In the low pressure chamber 182 are housed a compression mechanism 10 for compressing a working fluid, a motor 20, a drive shaft 30 that rotates under the drive of the motor 20 and drives the compression mechanism 10, and a main bearing housing 40 for supporting the compression mechanism 10 and the drive shaft 30. The high-temperature and high-pressure working fluid compressed by the compression mechanism 10 is discharged into the high-pressure chamber 181.

An orifice 112 is provided in the cylindrical housing 110. The intake adapter 70 fits in the aperture 112. An intake pipe (not shown) is connected to the scroll compressor 100 through an intake joint 70 to deliver low-temperature, low-pressure working fluid into the scroll compressor 100 (illustrated as a low-pressure chamber 182). The low-temperature and low-pressure working fluid introduced into the low-pressure chamber 182 is sucked into the suction port of the compression mechanism 10, compressed by the compression mechanism 10, and discharged into the high-pressure chamber 181.

Compression mechanism 10 includes a non-orbiting scroll member 150 and an orbiting scroll member 160. Non-orbiting scroll member 150 and orbiting scroll member 160 engage to form compression pockets between the wraps of non-orbiting scroll member 150 and orbiting scroll member 160. The non-orbiting scroll member 150 may be mounted to the outer shell (e.g., cylindrical shell 110) or main bearing housing 40 of the scroll compressor 100. Orbiting scroll member 160 is able to orbit relative to non-orbiting scroll member 150 (i.e., the central axis of orbiting scroll member 160 orbits the central axis of non-orbiting scroll member 150, but orbiting scroll member 160 does not itself rotate about its central axis), such that the compression chambers move from the radially outer side to the radially inner side and have a gradually decreasing volume, thereby achieving compression of the working fluid.

Orbiting scroll member 160 includes a hub 162. Hub 162 extends in a direction opposite orbiting scroll wrap 166 on one side of end plate 164. The hub 162 is generally cylindrical. The hub portion 162 may define a space for receiving the driveshaft 30. As drive shaft 30 rotates, drive shaft 30 is able to drive orbiting scroll member 160 in a translational motion via hub 162. A drive bearing 50 is provided between the hub 162 and the drive shaft 30. The drive bearing 50 serves to support the translational orbiting of the hub 162 and reduce wear of the hub 162.

It should be understood that the specific structure of the orbiting scroll member should not be limited to the specific example illustrated. For example, the orbiting scroll member 160 may be provided with a central recess in which the drive shaft 30 is fitted to drive the orbiting scroll member 160, instead of the hub 162. In this not shown example, a drive bearing may also be provided between the side wall of the central recess and the drive shaft 30. For example, the hub portion may be a solid cylinder and fit into a recess in the driveshaft 30. In this not shown example, a drive bearing may also be provided between the solid cylindrical hub portion and the side wall of the recessed portion of the drive shaft 30. The central recess or hub of the orbiting scroll member referred to herein forms the driven portion which is driven by the drive shaft.

The drive shaft 30 is provided at its end (shown as the upper end in the figure) with an eccentric crank pin 32. Eccentric crank pin 32 is configured to drive orbiting scroll member 160 (e.g., hub 162) eccentrically with respect to the central axis of rotation of drive shaft 30. The eccentric crank pin 32 is received in the hub 162. As motor 20 drives rotation of drive shaft 30, eccentric crank pin 32 drives hub 162 and, via hub 162, orbiting scroll member 160 in a translational motion. The drive bearing 50 is disposed between the eccentric crank pin 32 and the hub 162.

It should be understood that the configuration of the eccentric crank pin should not be limited to the specific example illustrated. For example, the eccentric crankpin may have a recess for receiving the hub as described above. The eccentric crank pin of the drive shaft referred to herein forms the drive portion for driving the compression mechanism (the orbiting scroll member as shown). Therefore, the drive bearing is provided between the driven portion of the compression mechanism and the drive portion of the drive shaft.

Optionally, a relief bushing 60 may also be provided between the eccentric crank pin 32 and the drive bearing 50. The unloader bushing 60 is capable of moving a predetermined distance in a radial direction relative to the eccentric crank pin 32, thereby providing radial flexibility to the compression mechanism 10.

Main bearing housing 40 is secured to the outer shell (e.g., cylindrical shell 110) of scroll compressor 100. Main bearing housing 40 rotatably supports drive shaft 30 via main bearing 90. Main bearing housing 40 (upper end surface as shown) slidably supports orbiting scroll member 160.

Main bearing housing 40 includes a body 140. Referring to fig. 2A and 2B, body 140 includes a mounting portion 141 for mounting main bearing housing 40, a cylindrical portion 143 for rotatably supporting rotary shaft 30, and an annular portion 145 for slidably supporting orbiting scroll member 160.

Mounting portion 141 is configured for securing main bearing housing 40 to cylindrical housing 110 of scroll compressor 100. In the illustrated example, main-bearing housing 40 includes four mounting portions 141 discretely arranged in the circumferential direction. The mounting portion 141 may be attached or mounted to the housing of the scroll compressor 100 by any means known, such as fasteners, interference fit, welding, and the like. In some examples, non-orbiting scroll member 150 may be mounted or connected to mounting portion 141, such as by bolts or the like.

The cylindrical portion 143 and the annular portion 145 are located radially inward of the mounting portion 141. The cylindrical portion 143 extends from one end (shown as the lower end in the figure) of the annular portion 145. The cylindrical portion 143 is configured to allow the drive shaft 30 to pass through and receive the drive shaft 30. A main bearing 90 is provided between the cylindrical portion 143 and the drive shaft 30, thereby allowing the drive shaft 30 to rotate relative to the cylindrical portion 143.

The annular portion 145 has a bearing surface (upper end surface as shown) 144. Compression mechanism 10, specifically orbiting scroll member 160, rests on this bearing surface 144 and is supported by annular portion 145. As the scroll compressor 100 operates, the orbiting scroll member 160 rides on the bearing surface 144.

The annular portion 145 defines a central recess 146, as best shown in fig. 1. The eccentric crank pin 32 of drive shaft 30, drive bearing 50 and hub 162 of orbiting scroll member 160 may be received in the central recess 146. The central recess 146 may be sized to provide space for movement of the hub 162 and the eccentric crank pin 32. In some examples not shown, central recess 146 may also be formed as a back pressure chamber for receiving fluid to apply a force to orbiting scroll member 160. To this end, for example, the central recess 146 may extend outward in a radial direction relative to the cylindrical portion 143.

It should be understood that the structure of main bearing housing 40 should not be limited to the specific example illustrated, but may vary. For example, the main bearing housing is a single member in the illustrated example, however, the main bearing housing may be a split structure.

In order to achieve reliable operation, lubricating oil is supplied to the drive bearing 50 to lubricate the drive bearing 50, thereby reducing wear and increasing service life. The central recess 146 may collect lubricating oil that lubricates the drive bearing 50. The collected lubrication oil may also flow along the drive shaft 30 to the main bearing 90 to lubricate the main bearing 90.

The lubricating effect of the lubricating oil is significantly reduced in a high-temperature environment. To this end, an inflow passage 142 is provided in main bearing housing 40 (shown as an annular portion 145). The inflow channel 142 is configured to allow fluid to flow into the central recess 146 to cool the drive bearing 50.

A plurality of inflow passages 142 may be provided in main bearing housing 40. As shown in fig. 2A and 2B, a plurality of inflow passages 142 are provided in the annular portion 145 of the body 140. Three inflow passages 142 are provided between the adjacent mounting parts 141. The plurality of inflow passages 142 are arranged in the circumferential direction. The plurality of inflow channels 142 may have the same size (e.g., inner diameter). Each inflow channel 142 extends through body 140 of main bearing housing 40 in a radial direction. Each inflow channel 142 has a circular cross-section with a substantially constant diameter.

The plurality of inflow passages may increase the amount of fluid introduced, and thus may significantly reduce the temperature of the drive bearing. The inventors have also demonstrated this by making tests in this respect. In the test, two inflow channels were provided, each having an area of 5 square millimeters (mm) ² ) The temperature of the drive bearing is reduced by 4 degrees celsius (c). In another test, 6 inflow channels were provided, each having an area of 5 square millimeters (mm) ² ) The temperature of the drive bearing is reduced by 18 degrees celsius (c). Furthermore, the inventors are also directed to the same inflow channelThe arrangement of (2) makes tests under different working conditions, and finds that the temperature of the drive bearing can be reduced under various working conditions. Thus, a desired cooling effect on the drive bearing can be obtained by designing the inflow channel,

accordingly, the configuration (e.g., number, size, shape, location, orientation, etc.) of the inflow passages should not be limited to the specific examples illustrated, but may be varied as desired. For example, the inflow channel extends linearly at an angle relative to a radial direction of the body 140 from the inlet (i.e., an opening on an outer surface of the body 140 opposite the outlet) rather than extending in the radial direction toward the center of the central recess 146. In this way, it is possible to avoid the introduced fluid from directly blowing toward the drive bearing to increase the oil circulation rate and reduce the lubricating effect. In particular, the inflow channel may be disposed in a tangential manner with respect to an inner surface of main bearing housing 40 (e.g., an inner circumferential surface of annular portion 145), whereby a flow of fluid along the inner circumferential surface of body 140 may be promoted, thereby further preventing the introduced fluid from blowing toward the drive bearing.

As described above, the temperature of the drive bearing can be significantly reduced only by providing the inflow passage, and therefore the scroll compressor of the present invention has a small increase in cost, that is, a low cost.

Fig. 3 is a partially schematic longitudinal sectional view of a scroll compressor 200 according to a second embodiment of the present invention. The scroll compressor 200 differs from the scroll compressor 100 in that it further includes a conduit 201 for introducing fluid into the inflow channel 142. The differences of the scroll compressor 200 from the scroll compressor 100 will be described in detail with reference to fig. 3. The scroll compressor 200 is identical to the scroll compressor 100 and will not be described again.

As shown in fig. 3, a pipe 201 is disposed in the inflow channel 142. The conduit 201 is configured to communicate the inflow channel 142 to the intake fitting 70. Accordingly, a working fluid (e.g., a refrigerant) to be compressed, introduced via the intake joint 70, may be conveniently delivered into the central recess 146 through the conduit 201 to cool the drive bearing 50. It can be seen that, in the compressor of the present invention, by providing the pipe 201, the working fluid in the intake pipe can be actively and directly introduced to the driving bearing.

It will be appreciated that by providing a conduit 201, other external fluids than the above-described working fluid may be introduced to cool the drive bearing, for example, the ambient atmosphere in which the compressor is located, working fluid from other compressors in the system, or fluid from a separate fluid source. Thus, by providing the conduit 201, the external source of fluid is no longer restricted but can be selected as desired.

Further, since the source of external fluid is not limited, it will be appreciated that the scroll compressor 200 may not be limited to the low-side compressor illustrated (i.e., the motor is located in an environment having a suction pressure separated, for example, by the partition 80), but may be another type of scroll compressor, for example, a high-side compressor (i.e., the motor is located in an environment having a discharge pressure, for example, the partition 80 is omitted).

Referring again to fig. 3, a pipe 201 is disposed in one introduction passage 142 of the plurality of introduction passages 142. The conduit 201 has a first section 211 disposed in the inlet passage 142 and a second section 212 adjacent the inlet fitting 70. The first section 211 and the second section 212 have substantially the same dimensions. The second section 212 is angled relative to the first portion 211 to be oriented toward the air intake joint 70. The second section 212 may have a clearance with the air intake joint 70 to facilitate assembly.

The intake fitting 70 may be located between the compression mechanism 10 and the motor 20 in the axial direction of the scroll compressor 100. Specifically, intake coupling 70 may be located in the axial direction between end plate 164 of orbiting scroll member 160 and the end face of motor 20. In this way, the flow path from the intake joint 70 to the inflow channel 142 can be shortened. Preferably, intake air fitting 70 is located radially outward of main bearing housing 40. More preferably, the inlet fitting 70 is at least partially aligned with the at least one inlet passage 142 in the axial direction of the compressor 100, i.e., the at least one inlet passage 142 at least partially faces the flow passage of the inlet fitting 70.

It should be understood that the number, installation, configuration, etc. of the conduits should not be limited to the specific examples illustrated, so long as they are capable of performing the functions described herein. For example, in the modified example shown in fig. 4, the second section 312 of the conduit 301 may have a size that increases toward the air intake joint 70. Furthermore, the conduit may be in the form of a hose, for example, whereby it may not be limited by space. For example, the second section of the conduit may be connected to or abut the intake fitting, or the first section may be oriented towards the introduction passage.

Fig. 5 to 7 show a main-bearing housing 41 according to another embodiment of the present invention. Main bearing housing 41 includes a body 240. The body 240 includes a mounting portion 241, a cylindrical portion 243, and an annular portion 245. The structures of the mounting portion 241, the cylindrical portion 243, and the annular portion 245 are similar to those of the mounting portion 141, the cylindrical portion 143, and the annular portion 145, and thus will not be described in detail.

Main-bearing housing 41 differs from main-bearing housing 40 in the arrangement of inflow passage 242 and outflow passage 248 and the provision of cover 247. The difference between main-bearing housing 41 and main-bearing housing 40 will be described in detail with reference to fig. 5 to 7.

As shown in fig. 5 to 7, a cover 247 is provided radially inside the annular portion 245. The cap 247 extends along the inner peripheral surface of the annular portion 245 (i.e., in the circumferential direction). In the example shown in the figures, the shroud 247 extends 360 degrees in the circumferential direction to be annular. An annular space 249 is formed between the cap 247 and the annular portion 245. An inflow channel 242 and an outflow channel 248 are provided in the annular portion 245. The inflow passage 242 and the outflow passage 248 extend in the radial direction and are oppositely arranged. The fluid introduced through the inflow channel 242 enters the space 249, flows in opposite directions from both sides, and then flows out from the outflow channel 248.

The shroud 247 may separate the incoming working fluid from the drive bearing. Due to the cap 247, it is possible to prevent the introduced working fluid from blowing off the lubricating oil at the drive bearing to cause deterioration of the lubrication.

Referring again to fig. 5-7, the cap 247 has a cylindrical wall 2471 for defining the space 249 and a flange 2472 extending from an end of the cylindrical wall 2471. The flange 2472 may be interference-fitted with the inner peripheral surface of the annular portion 245, thereby mounting the cap 247. Alternatively, the flange 2472 may be a clearance fit with the inner circumferential surface of the annular portion 245 to cover the space 249 to some extent. The annular portion 245 may include a step 2451 for supporting the cylindrical wall 2471 of the enclosure 247.

It should be understood that the structure of the cover and main bearing housing should not be limited to the specific examples shown in the figures, but may be varied as desired. For example, the body of the main bearing housing and the cover may be formed as a unitary piece. For example, an annular groove, i.e., a space 249 is formed in a circumferential direction and in an axial direction from a support surface of a body of the main bearing housing. For example, the shroud may extend partially in the circumferential direction, e.g., semi-circular, as long as it is capable of performing the functions described herein.

Although the invention has been described with reference to the examples of the drawings, it is to be understood that various features of the examples shown in the drawings may be combined with each other without contradiction. For example, the inflow passage 242 and the outflow passage 248 may be plural. For example, a pipe may be provided in the inflow channel 242.

The specific examples illustrated are for the purpose of illustrating the invention only and are not to be construed as limiting the invention, and thus, various changes may be made in the specific examples described above. Although some embodiments and variants of the invention have been described in detail, it should be understood by a person skilled in the art that the invention is not limited to the embodiments and variants described above and shown in the drawings but may comprise other various possible combinations and combinations. Other modifications and variations may be effected by one skilled in the art without departing from the spirit and scope of the invention. All such variations and modifications are intended to fall within the scope of the present invention. Moreover, all the components described herein may be replaced by other technically equivalent components.

Claims

1. A scroll compressor, comprising:

a compression mechanism;

a drive shaft configured to drive the compression mechanism;

a drive bearing disposed between the compression mechanism and the drive shaft; and

a main bearing housing, the main bearing housing comprising: a body for slidably supporting the compression mechanism and rotatably supporting the drive shaft; a central recess defined by the body; and an inflow channel disposed in the body and allowing fluid to enter the central recess to cool the drive bearing.

2. The scroll compressor of claim 1, wherein the scroll compressor includes a plurality of the inflow passages, the inflow passages being arranged along a circumferential direction of the body.

3. The scroll compressor of claim 1, further comprising a conduit configured for introducing fluid to at least one of the inflow passages.

4. The scroll compressor of claim 3, wherein the conduit has: a first section connected into or oriented towards the inflow channel; and a second section connected to or oriented toward an intake joint of the scroll compressor.

5. The scroll compressor of any one of claims 1 to 4, wherein the inflow passage extends linearly from the inlet port away from a radial direction, wherein the inflow passage is disposed tangentially to an inner circumferential surface of the body.

6. The scroll compressor of claim 1, further comprising a housing located radially inward of the body, a space being formed between the body and the housing in communication with the inlet passage.

7. The scroll compressor of claim 6, wherein said housing is annular and has a cylindrical wall defining said space,

the body has a stepped portion for supporting one end of the cylindrical wall and/or the cover has a flange extending radially outward from the other end of the cylindrical wall.

8. The scroll compressor of claim 6 or 7, wherein an outflow passage is provided in the body of the main bearing housing radially opposite the inflow passage.

9. The scroll compressor of any one of claims 1 to 4, 6 to 7, wherein the scroll compressor comprises an intake connection for introducing a working fluid to be compressed and a motor for driving the drive shaft in rotation, the intake connection being located between the compression mechanism and the motor in an axial direction of the scroll compressor.

10. The scroll compressor of any one of claims 1 to 4, 6 to 7, further comprising a partition plate dividing a space within a housing of the compressor into a high pressure chamber and a low pressure chamber, the compression mechanism and the main bearing housing being located in the low pressure chamber.