CN116971986A - Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a - Google Patents

Abstract

The present disclosure relates to 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 provided in the body and allowing fluid to enter the central recess to cool the drive bearing. The scroll compressor according to the present disclosure can significantly reduce the temperature of the drive bearing, particularly at a lower cost.

Description

Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a

Technical Field

The present disclosure relates to a scroll compressor.

Background

This section merely provides background information related to the present disclosure, which may not necessarily be prior art.

Scroll compressors typically include a compression mechanism, a motor, a drive shaft, drive bearings, and a main bearing housing. The compression mechanism includes a fixed scroll member and an orbiting scroll member. The orbiting scroll member is supported on the main bearing housing and is driven by the drive shaft to perform an orbiting motion with respect to the non-orbiting scroll member such that the vanes of the orbiting and non-orbiting scroll members are engaged with each other to form a compression chamber having a gradually decreasing volume for compressing a working fluid (e.g., refrigerant). The drive shaft is driven to rotate by a motor and drives the orbiting scroll member via a drive bearing.

The drive bearings may reduce the lubrication effect at high temperatures and thus increase wear. As such, the drive bearings 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 rise. The high temperatures generated by the motor during operation also transfer heat to the drive bearing, causing the temperature of the drive bearing to rise further. If the ambient oil or the exhaust port temperature of the compression mechanism is too high, the temperature of the drive bearings may also be 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 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 lowered by injecting lubricating oil, thereby lowering the temperature of the drive bearing. However, the injected lubricating oil will result in an increase in oil circulation rate and limited improvement in the temperature of the drive bearing. For example, the temperature of the drive bearing is reduced by optimizing the motor such that the motor heats up less. However, the optimized motor adds significant cost and there is limited improvement in the temperature of the drive bearings.

Disclosure of Invention

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

According to one aspect of the present disclosure, a scroll compressor is provided that includes 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 provided 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 channels 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 channels.

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 towards an intake fitting of the scroll compressor.

In some embodiments, the inflow channel extends linearly from the inlet offset from the 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 includes a shroud located radially inward of the body, a space being formed between the body and the shroud in communication with the inflow channel.

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 outwardly from the other end of the cylindrical wall.

In some embodiments, the cap is formed in one piece with the main bearing housing body.

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 joint for introducing a working fluid to be compressed and a motor for driving the drive shaft to rotate, the intake joint 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 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.

The scroll compressor according to the present disclosure may obtain some advantages as follows.

By providing inflow channels or pipes, a cooling fluid (e.g., gas, gaseous refrigerant, etc.) may be actively introduced at the drive bearing, whereby the temperature of the drive bearing may be directly and effectively reduced. Therefore, the lubrication condition of the driving bearing can be significantly improved, thereby improving the reliability of the operation of the compressor.

The desired cooling effect for the drive bearing is obtained by providing an inflow channel in the main bearing housing, i.e. by designing the flow area. Thus, such an improvement is less costly.

The scroll compressor according to the present disclosure also includes a conduit so that fluid may be introduced from a desired fluid source to reduce the temperature of the drive bearing. That is, the cooling fluid and space are not limited and the cost is low.

Furthermore, by designing the orientation of the inflow passage or providing the cover so that the cooling fluid does not directly flow to the drive bearing, an increase in the oil circulation rate can be prevented.

In a scroll compressor according to the present disclosure, a low temperature and low pressure working fluid may be introduced into the main bearing housing and the chamber in which the motor is located, whereby the working fluid may be directly utilized to cool the drive bearings prior to compressing the working fluid.

Drawings

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

FIG. 1 is a schematic view in partial longitudinal section of a scroll compressor according to a first embodiment of the present disclosure;

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

FIG. 3 is a schematic partial longitudinal cross-sectional view of a scroll compressor according to a second embodiment of the present disclosure;

FIG. 4 is a partial longitudinal cross-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 disclosure;

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

fig. 7 is a schematic longitudinal section 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 disclosure, its application, or uses. The same reference numerals are used to denote the same parts throughout the various drawings, and thus the construction of the same parts will not be repeated.

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

Scroll compressor 100 may also include a partition 80. The partition 80 divides the closed space into a high pressure chamber 181 and a low pressure chamber 182. The low pressure chamber 182 has a low temperature and low pressure working fluid (e.g., refrigerant) introduced therein. 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 are accommodated in the low pressure chamber 182. The high-temperature and high-pressure working fluid compressed by the compression mechanism 10 is discharged into the high-pressure chamber 181.

An aperture 112 is provided in the cylindrical housing 110. The air intake fitting 70 fits into the aperture 112. An intake pipe (not shown) is connected to the scroll compressor 100 through an intake joint 70 to deliver a low-temperature and low-pressure working fluid into the scroll compressor 100 (the low-pressure chamber 182 is illustrated in the drawing). The low-temperature 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. The non-orbiting scroll member 150 and the orbiting scroll member 160 are engaged to form a compression chamber between the wraps of the non-orbiting scroll member 150 and the orbiting scroll member 160. Non-orbiting scroll member 150 may be mounted to a housing (e.g., cylindrical shell 110) or main bearing housing 40 of scroll compressor 100. The orbiting scroll member 160 is capable of orbiting movement relative to the non-orbiting scroll member 150 (i.e., the central axis of the orbiting scroll member 160 moves about the central axis of the non-orbiting scroll member 150, but the orbiting scroll member 160 itself does not rotate about its central axis) such that the compression chambers move radially outward to radially inward and have progressively smaller volumes, thereby effecting compression of the working fluid.

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

It should be understood that the particular configuration of the orbiting scroll member should not be limited to the particular examples illustrated. For example, the orbiting scroll member 160 may be provided with a central recess in place of the hub 162, wherein the drive shaft 30 is fitted in the central recess to drive the orbiting scroll member 160. 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 may be solid cylindrical and fit into a recess of the drive shaft 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 recess 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 with an eccentric crank pin 32 at its end (shown as the upper end in the figure). The eccentric crank pin 32 is configured to eccentrically drive the orbiting scroll member 160 (e.g., the hub 162) relative to the central rotational axis of the drive shaft 30. The eccentric crankpin 32 is received in the hub 162. When the motor 20 drives the drive shaft 30 to rotate, the eccentric crank pin 32 drives the hub 162 and drives the orbiting scroll member 160 in translational motion via the hub 162. 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 crankpin should not be limited to the particular example illustrated. For example, the eccentric crankpin may have a recess for receiving the hub as described above. The eccentric crankpin 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, an unloading bushing 60 may also be provided between the eccentric crank pin 32 and the drive bearing 50. The unloader bushing 60 is movable a predetermined distance in a radial direction relative to the eccentric crankpin 32, thereby providing radial flexibility to the compression mechanism 10.

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

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

The mounting portion 141 is configured for securing the main bearing housing 40 to the cylindrical housing 110 of the scroll compressor 100. In the illustrated example, the 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 known means, 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 (lower end shown in the drawing) 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, and in particular orbiting scroll member 160, is disposed on the bearing surface 144 and supported by annular portion 145. When the scroll compressor 100 is in operation, the orbiting scroll member 160 slides over 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 the drive shaft 30, the drive bearing 50, and the hub 162 of the orbiting scroll member 160 may be received in the central recess 146. The central recess 146 may be sized to provide a space for movement of the hub 162 and eccentric crankpin 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. For this purpose, for example, the central recess 146 may extend outwardly in a radial direction with respect to the cylindrical portion 143.

It should be appreciated that the configuration of main bearing housing 40 should not be limited to the particular example illustrated, but may vary. For example, the main bearing housing is a single component 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 the service life. The central recess 146 may collect lubrication 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 lubrication effect of the lubricating oil is significantly reduced in a high temperature environment. For this purpose, an inflow channel 142 is provided in main bearing housing 40 (as shown by 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. There are three inflow channels 142 between adjacent mounting portions 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 the body 140 of the main bearing housing 40 in a radial direction. Each inflow channel 142 has a circular cross-section with a substantially constant diameter.

The multiple inflow channels may increase the amount of fluid introduced, thereby significantly reducing the temperature of the drive bearing. The inventors have made tests in this respect and have also demonstrated this. 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). In addition, the inventor also makes tests on the arrangement of the same inflow channel under different working conditions, and finds that the temperature of the driving bearing can be reduced under various working conditions. Thus, the desired cooling effect on the drive bearing can be obtained by designing the inflow channel,

accordingly, the configuration (e.g., number, size, shape, position, orientation, etc.) of the inflow channels should not be limited to the specific examples illustrated, but may be varied as desired. For example, the inflow channels extend linearly from the inlet (i.e., the opening opposite the outlet and located on the outer surface of the body 140) at an angle relative to the radial direction of the body 140, 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 blowing directly toward the drive bearing to increase the oil circulation rate and reduce the lubrication effect. In particular, the inflow passages may be disposed tangentially to an inner surface of main bearing housing 40 (e.g., an inner circumferential surface of annular portion 145), thereby facilitating fluid flow along the inner circumferential surface of body 140, further avoiding induced fluid blow-up against the drive bearing.

As described above, the temperature of the drive bearing can be significantly reduced only by providing the inflow passage, and thus the cost of the scroll compressor of the present disclosure is not greatly increased, i.e., the cost is low.

Fig. 3 is a schematic partial longitudinal section of a scroll compressor 200 according to a second embodiment of the present disclosure. Scroll compressor 200 differs from scroll compressor 100 in that it also includes a conduit 201 for introducing fluid into inflow channel 142. Differences between scroll compressor 200 and scroll compressor 100 will be described in detail with reference to fig. 3. The scroll compressor 200 is the same as the scroll compressor 100 and will not be described again.

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

It will be appreciated that by providing the conduit 201, other external fluids than the working fluid described above may be introduced to cool the drive bearings, 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 fluid source is no longer limited, but may be selected as desired.

Further, since the external fluid source is not limited, it is understood that scroll compressor 200 may not be limited to the illustrated low-pressure side compressor (i.e., the motor is located in an environment with suction pressure, for example, separated by partition 80), but may be other types of scroll compressors, such as a high-pressure side compressor (i.e., the motor is located in an environment with discharge pressure, for example, with partition 80 omitted).

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

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

It should be understood that the number, installation, configuration, etc. of the pipes should not be limited to the specific examples illustrated, as 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 duct 301 may have a size that increases toward the intake joint 70. Furthermore, the conduit may be in the form of a hose, for example, and thus may not be space-constrained. For example, the second section of the duct may be connected to or abut the air inlet fitting, or the first section may be oriented towards the intake passage.

Fig. 5-7 illustrate a main bearing housing 41 according to another embodiment of the present disclosure. The 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.

The main bearing housing 41 differs from the main bearing housing 40 in the arrangement of the inflow and outflow passages 242, 248 and the provision of the cap 247. Differences between main bearing housing 41 and main bearing housing 40 will be described in detail below with reference to fig. 5-7.

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

The cap 247 may separate the incoming working fluid from the drive bearings. Due to the cap 247, it is possible to prevent the lubrication from being deteriorated by the introduced working fluid blowing away the lubrication oil at the drive bearing.

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

It should be understood that the configuration 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 housing and the body of the main bearing housing may be formed as a single piece. For example, an annular groove, i.e., space 249, is formed in the circumferential direction and in an axial direction from the bearing surface of the main bearing housing body. For example, the cover may extend partially in the circumferential direction, e.g., semi-circular, so long as it is capable of performing the functions described herein.

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

The particular examples illustrated are for purposes of illustration only and not limitation of the present disclosure, and thus, various modifications are possible in the specific examples described above. Although some embodiments and variations of the present disclosure have been specifically described, it will be understood by those skilled in the art that the present disclosure is not limited to the embodiments and variations described above and shown in the drawings, but may include other various possible combinations and combinations. Other modifications and variations can be effected by those of skill in the art without departing from the spirit and scope of the disclosure. All such modifications and variations are intended to be within the scope of this disclosure. Moreover, all the components described herein may be replaced by other technically equivalent elements.

Claims (10)

1. A scroll compressor, wherein the scroll compressor comprises:

a compression mechanism (10);

-a drive shaft (30) configured for driving the compression mechanism (10);

-a drive bearing (50) arranged between the compression mechanism and the drive shaft; and

-a main bearing housing (40), the main bearing housing comprising: a body (140) for slidably supporting the compression mechanism and rotatably supporting the drive shaft; -a central recess (146) defined by the body; and an inflow channel (142) provided 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 channels arranged along a circumferential direction of the body.

3. The scroll compressor according to claim 1, wherein the scroll compressor further comprises a conduit (141, 241) configured for introducing fluid to at least one of the inflow channels.

4. The scroll compressor of claim 3, wherein said conduit has: a first section (211) connected into or oriented towards the inflow channel; and a second section (212, 312) connected to or oriented towards an intake fitting of the scroll compressor.

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

6. The scroll compressor according to claim 1, further comprising a shroud (247) radially inward of said body, a space (249) being formed between said body and said shroud in communication with said inflow passage.

7. The scroll compressor according to claim 6 wherein said shroud is annular and has a cylindrical wall (2471) defining said space,

the body has a step (2451) for supporting one end of the cylindrical wall and/or the cover has a flange (2472) extending radially outwardly from the other end of the cylindrical wall.

8. The scroll compressor according to claim 6 or 7, wherein an outflow channel (248) is provided in the body of the main bearing housing radially opposite the inflow channel (242).

9. The scroll compressor according to any one of claims 1 to 4, 6 to 7, wherein said scroll compressor comprises an intake fitting (70) for introducing a working fluid to be compressed and a motor (20) for driving said drive shaft in rotation, said intake fitting being located between said compression mechanism and said motor in an axial direction of said scroll compressor.

10. The scroll compressor according to any one of claims 1 to 4, 6 to 7, wherein said scroll compressor further comprises a partition (80) dividing the space within the housing of said compressor into a high pressure chamber (181) and a low pressure chamber (182), said compression mechanism and said main bearing housing being located in said low pressure chamber.