Scroll compressor

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 to slide-support the compression mechanism and to rotationally support the drive shaft, a central recess defined by the body, and an inflow passage disposed 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

TECHNICAL FIELD

[0001] The present disclosure relates to a scroll compressor. BACKGROUND

[0002] This section provides background information only and can not necessarily be prior art.

[0003] A scroll compressor generally 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 an orbiting scroll member. The orbiting scroll member is supported on the main bearing housing and performs an orbiting motion relative to the fixed scroll member under the drive of the drive shaft, such that the blades of the orbiting scroll member and the fixed scroll member engage each other to form compression pockets that compress a working fluid (e.g., refrigerant) with a gradually decreasing volume. The drive shaft is rotated by the motor and drives the orbiting scroll member via the drive bearing.

[0004] The drive bearing can reduce lubrication effect at high temperature and thus increase wear. As such, the drive bearing can fail prematurely. The friction between each of the orbiting scroll member and the drive shaft and the drive bearing can increase the temperature of the drive bearing. The high temperature generated by the motor when in operation can also transfer heat to the drive bearing, further increasing the temperature of the drive bearing. If the temperature of the surrounding lubricating oil or the discharge port of the compression mechanism is too high, the temperature of the drive bearing can also increase through 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.

[0005] In some existing compressors, the temperature of the drive bearing is reduced by controlling the source of high temperature. For example, the temperature of the discharge port is reduced by injecting lubricating oil, thereby reducing the temperature of the drive bearing. However, the injected lubricating oil can increase the oil circulation rate, and the improvement in the temperature of the drive bearing is limited. For example, the temperature of the drive bearing is reduced by optimizing the motor such that the heat generated by the motor is reduced. However, the optimized motor can significantly increase the cost, and the improvement in the temperature of the drive bearing is limited. SUMMARY

[0006] In view of the above problems in the prior art, the present disclosure provides a scroll compressor that can significantly reduce or control the temperature of the drive bearing at a lower cost.

[0007] According to one aspect of the present disclosure, 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 slide supporting the compression mechanism and rotationally supporting the drive shaft, a central recess defined by the body, and an inflow passage provided in the body and allowing fluid to enter the central recess to cool the drive bearing.

[0008] In some embodiments, the scroll compressor includes a plurality of the inflow passages arranged along a circumferential direction of the body.

[0009] In some embodiments, the scroll compressor further includes a pipe configured to introduce fluid to at least one of the inflow passages.

[0010] In some embodiments, the pipe has a first section connected to or oriented toward the inflow passage, and a second section connected to or oriented toward a suction joint of the scroll compressor.

[0011] In some embodiments, the inflow passage extends linearly from the inlet deviated from a radial direction.

[0012] In some embodiments, the inflow passage is disposed tangentially to an inner circumferential surface of the body.

[0013] In some embodiments, the scroll compressor further includes a cover radially inside the body, forming a space communicating with the inflow passage between the body and the cover.

[0014] In some embodiments, the cover is annular.

[0015] 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.

[0016] In some embodiments, the cover is formed as one piece with the body of the main bearing housing.

[0017] In some embodiments, an outflow passage is provided in the body of the main bearing housing radially opposite to the inflow passage.

[0018] In some embodiments, the scroll compressor includes a suction port for introducing a working fluid to be compressed and a motor for driving the driving shaft in rotation, the suction port being located between the compression mechanism and the motor in an axial direction of the scroll compressor.

[0019] In some embodiments, the suction port is located radially outward of the main bearing housing.

[0020] In some embodiments, the scroll compressor further includes a partition that separates a space within a casing of the scroll 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.

[0021] The scroll compressor according to the present disclosure can achieve some advantages as follows.

[0022] By providing the inflow passage or pipe, the cooling fluid (e.g., gas, gaseous refrigerant, etc.) can be actively introduced to the driving bearing, whereby the temperature of the driving bearing can be directly and effectively reduced. Thus, the lubrication condition of the driving bearing can be significantly improved, thereby increasing the reliability of the operation of the compressor.

[0023] The desired cooling effect on the driving bearing is achieved by providing the inflow passage in the main bearing housing (i.e., by designing the flow passage area). Thus, such improvement is low in cost.

[0024] The scroll compressor according to the present disclosure further includes the pipe, and thus the fluid can be introduced from a required fluid source to reduce the temperature of the driving bearing. That is, the cooling fluid and space are not limited, and the cost is low.

[0025] In addition, by designing the orientation of the inflow passage or providing the cover, the cooling fluid does not directly flow to the driving bearing, and thus the increase in the oil circulation rate can be prevented.

[0026] In the scroll compressor according to the present disclosure, the working fluid at a low temperature and a low pressure can be introduced into a chamber in which the main bearing housing and the motor are located, whereby the driving bearing can be directly cooled using the working fluid before the working fluid is compressed. BRIEF DESCRIPTION OF DRAWINGS

[0027] The features and advantages of one or more embodiments of the present disclosure will become more apparent from the following description with reference to the accompanying drawings, in which:

[0028] Figure 1 is a partial longitudinal sectional view of a scroll compressor according to a first embodiment of the present disclosure;

[0029] Figure 2A and Figure 2B is Figure 1 is a perspective view of a main bearing housing of

[0030] Figure 3 is a partial longitudinal sectional view of a scroll compressor according to a second embodiment of the present disclosure;

[0031] Figure 4 is a partial longitudinal sectional view of a scroll compressor according to a second embodiment of the present disclosure; Figure 3

[0032] Figure 5 is a perspective view of a main bearing housing according to an embodiment of the present disclosure;

[0033] Figure 6 is a perspective view of a main bearing housing according to an embodiment of the present disclosure; Figure 5

[0034] Figure 7 is a longitudinal sectional view of a scroll compressor according to a second embodiment of the present disclosure. Figure 5 DETAILED DESCRIPTION

[0035] The following description of the preferred embodiment is merely exemplary in nature and is in no way intended to limit the disclosure, its application, or uses.

[0036] First, a scroll compressor 100 according to a first embodiment of the present disclosure will be described with reference to Figure 1 , Figure 2A and Figure 2B . As shown in Figure 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 an enclosed space.

[0037] The scroll compressor 100 can further include a partition 80. The partition 80 divides the enclosed space into a high-pressure chamber 181 and a low-pressure chamber 182. The low-pressure chamber 182 has introduced therein a low-temperature and low-pressure working fluid (e.g., refrigerant). In the low-pressure chamber 182 are housed a compression mechanism 10 for compressing the working fluid, a motor 20, a drive shaft 30 that rotates under the driving of the motor 20 and is used to drive 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 via the compression mechanism 10 is discharged into the high-pressure chamber 181.

[0038] ​​​An orifice 112 is provided on the cylindrical casing 110. The suction joint 70 is fitted in the orifice 112. A suction pipe (not shown) is connected to the scroll compressor 100 through the suction joint 70 to deliver low-temperature and low-pressure working fluid into the scroll compressor 100 (the example in the drawing is the 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.

[0039] The compression mechanism 10 includes a fixed scroll member 150 and an orbiting scroll member 160. The fixed scroll member 150 and the orbiting scroll member 160 are engaged to form compression chambers between the scroll wraps of the fixed scroll member 150 and the orbiting scroll member 160. The fixed scroll member 150 can be mounted to a housing (e.g., the cylindrical casing 110) or a main bearing housing 40 of the scroll compressor 100. The orbiting scroll member 160 is capable of orbiting motion (i.e., the central axis of the orbiting scroll member 160 moves around the central axis of the fixed scroll member 150, but the orbiting scroll member 160 itself does not rotate around its own central axis) relative to the fixed scroll member 150, such that the compression chambers move from radially outer side to radially inner side and have gradually decreasing volumes, thereby achieving compression of the working fluid.

[0040] The orbiting scroll member 160 includes a hub portion 162. The hub portion 162 extends in a direction opposite to the orbiting scroll wrap 166 on one side of the end plate 164. The hub portion 162 is generally cylindrical. The hub portion 162 can define a space for receiving the drive shaft 30. When the drive shaft 30 rotates, the drive shaft 30 can drive the orbiting scroll member 160 to do the orbiting motion via the hub portion 162. A drive bearing 50 is provided between the hub portion 162 and the drive shaft 30. The drive bearing 50 is used to support the orbiting motion of the hub portion 162 and reduce the wear of the hub portion 162.

[0041] It should be understood that the specific structure of the orbiting scroll member should not be limited to the specific example shown in the drawing. For example, the orbiting scroll member 160 can be provided with a central recess instead of the hub portion 162, in which the drive shaft 30 is fitted to drive the orbiting scroll member 160. In this unshown example, a drive bearing can also be provided between the side wall of the central recess and the drive shaft 30. For example, the hub portion can be a solid column and is fitted in the recess of the drive shaft 30. In this unshown example, a drive bearing can also be provided between the solid column hub portion and the side wall of the recess of the drive shaft 30. The central recess or hub portion of the orbiting scroll member mentioned here forms a driven portion driven by the drive shaft.

[0042] The drive shaft 30 is provided at its end (shown as the upper end in the figures) with an eccentric crank pin 32. The eccentric crank pin 32 is configured to eccentrically drive the orbiting scroll member 160 (e.g., the hub portion 162) with respect to the central rotational axis of the drive shaft 30. The eccentric crank pin 32 is received in the hub portion 162. When the motor 20 drives the drive shaft 30 to rotate, the eccentric crank pin 32 drives the hub portion 162 and, via the hub portion 162, the orbiting scroll member 160 to perform a translational motion. The drive bearing 50 is provided between the eccentric crank pin 32 and the hub portion 162.

[0043] It should be understood that the structure of the eccentric crank pin should not be limited to the specific example shown. For example, the eccentric crank pin can have a recess as described above for receiving the hub portion. The eccentric crank pin of the drive shaft mentioned herein forms a driving portion for driving the compression mechanism (e.g., the orbiting scroll member) as shown. Thus, the drive bearing is provided between the driven portion of the compression mechanism and the driving portion of the drive shaft.

[0044] Optionally, an unloading bushing 60 can also be provided between the eccentric crank pin 32 and the drive bearing 50. The unloading bushing 60 is movable in the radial direction with respect to the eccentric crank pin 32 by a predetermined distance, thereby providing radial flexibility to the compression mechanism 10.

[0045] The main bearing housing 40 is fixed to the housing (e.g., the cylindrical housing 110) of the scroll compressor 100. The main bearing housing 40 rotationally supports the drive shaft 30 via the main bearing 90. In addition, the main bearing housing 40 (e.g., the upper end face as shown) slidably supports the orbiting scroll member 160.

[0046] The main bearing housing 40 includes a body 140. Referring to Figure 2A and Figure 2B the body 140 includes mounting portions 141 for mounting the main bearing housing 40, a cylindrical portion 143 for rotationally supporting the rotational shaft 30, and an annular portion 145 for slidably supporting the orbiting scroll member 160.

[0047] The mounting portions 141 are configured for fixing the main bearing housing 40 to the cylindrical housing 110 of the scroll compressor 100. In the example shown, the main bearing housing 40 includes four mounting portions 141 discretely arranged in the circumferential direction. The mounting portions 141 can be connected or mounted to the housing of the scroll compressor 100 by any means known, e.g., fasteners, interference fit, welding, etc. In some examples, the fixed scroll member 150 can be mounted or connected to the mounting portions 141, e.g., by bolts, etc.

[0048] 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 as shown 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. The main bearing 90 is provided between the cylindrical portion 143 and the drive shaft 30, thereby allowing the drive shaft 30 to rotate with respect to the cylindrical portion 143.

[0049] The annular portion 145 has a bearing surface (upper end surface as shown in the figure) 144. The compression mechanism 10 (specifically, the orbiting scroll member 160) is placed on the bearing surface 144 and is supported by the annular portion 145. The orbiting scroll member 160 slides on the bearing surface 144 when the scroll compressor 100 is operating.

[0050] The annular portion 145 defines a central recess 146, as Figure 1 clearly shown. The eccentric crank pin 32 of the drive shaft 30, the drive bearing 50, and the hub portion 162 of the orbiting scroll member 160 can be accommodated in the central recess 146. The central recess 146 can be sized to provide a movement space for the hub portion 162 and the eccentric crank pin 32. In some unillustrated examples, the central recess 146 can also be formed as a back pressure cavity for receiving fluid to apply a force to the orbiting scroll member 160. To this end, for example, the central recess 146 can extend radially outward with respect to the cylindrical portion 143.

[0051] It should be understood that the structure of the main bearing housing 40 should not be limited to the specific example illustrated, but can vary. For example, the main bearing housing is a single member in the illustrated example, however the main bearing housing can also be a split structure.

[0052] 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 can collect the lubricating oil that lubricates the drive bearing 50. The collected lubricating oil can also flow along the drive shaft 30 to the main bearing 90 to lubricate the main bearing 90.

[0053] In a high temperature environment, the lubricating effect of the lubricating oil can be significantly reduced. To this end, an inflow passage 142 is provided in the main bearing housing 40 (the annular portion 145 as shown in the figure). The inflow passage 142 is configured to allow fluid to flow into the central recess 146 to cool the drive bearing 50.

[0054] Multiple inflow passages 142 can be provided in the main bearing housing 40. As Figure 2A and Figure 2BAs shown, a plurality of inflow passages 142 is provided in the annular portion 145 of the body 140. There are three inflow passages 142 between adjacent mounting portions 141. The plurality of inflow passages 142 is arranged in a circumferential direction. The plurality of inflow passages 142 can have the same size (e.g., inner diameter). Each inflow passage 142 extends through the body 140 of the main bearing housing 40 in a radial direction. Each inflow passage 142 has a circular cross section with a substantially constant diameter.

[0055] The plurality of inflow passages can increase the amount of introduced fluid, whereby the temperature of the drive bearing can be significantly reduced. The inventors have tested this and it was proven. In a test, two inflow passages were provided, each with an area of 5 square millimeters (mm 2 ), which resulted in a reduction of the temperature of the drive bearing by 4 degrees Celsius (°C). In another test, six inflow passages were provided, each with an area of 5 square millimeters (mm 2 ), which resulted in a reduction of the temperature of the drive bearing by 18 degrees Celsius (°C). Furthermore, the inventors have tested different working conditions for the same arrangement of inflow passages and found that the temperature of the drive bearing was reduced in each working condition. Thus, the desired cooling effect on the drive bearing can be obtained by designing the inflow passages,

[0056] Therefore, the structure of the inflow passages (e.g., number, size, shape, position, and orientation, etc.) should not be limited to the specific examples shown in the figures, but can be varied as needed. For example, the inflow passages linearly extend at an angle with respect to the radial direction of the body 140 from the inlet (i.e., the opening on the outer surface of the body 140 opposite to the outlet) rather than extending in the radial direction towards the center of the central recess 146. In this way, the oil circulation rate can be increased and the lubrication effect can be reduced by avoiding that the introduced fluid directly blows against the drive bearing. In particular, the inflow passages can be provided tangentially to the inner surface of the main bearing housing 40 (e.g., the inner circumferential surface of the annular portion 145), whereby the fluid flow along the inner circumferential surface of the body 140 can be facilitated, thereby further avoiding that the introduced fluid blows against the drive bearing.

[0057] As described above, only the provision of the inflow passages is required to significantly reduce the temperature of the drive bearing, so that the cost increase of the scroll compressor according to the present disclosure is not large, i.e., the cost is low.

[0058] Figure 3 is a partial longitudinal sectional view schematically showing a scroll compressor 200 according to a second embodiment of the present disclosure. The scroll compressor 200 differs from the scroll compressor 100 in that it further comprises a pipe 201 for introducing fluid into the inflow passages 142. The scroll compressor 200 will be described below with reference to the scroll compressor 100. Figure 3The differences between scroll compressor 200 and scroll compressor 100 will be described in detail. The similarities between scroll compressor 200 and scroll compressor 100 will not be described.

[0059] like Figure 3 As shown, pipe 201 is placed in inlet channel 142. Pipe 201 is configured to connect inlet channel 142 to inlet connector 70. Therefore, the working fluid (e.g., refrigerant) to be compressed, introduced via inlet connector 70, can be conveniently delivered through pipe 201 to central recess 146 for cooling drive bearing 50. Thus, in the compressor of this disclosure, by providing pipe 201, the working fluid in the inlet pipe can be actively and directly directed to the drive bearing.

[0060] It should be understood that by providing pipe 201, other external fluids besides the aforementioned working fluid can be introduced to cool the drive bearing. These include, for example, the ambient atmosphere where the compressor operates, working fluids from other compressors in the system, or fluids from independent fluid sources. Therefore, by providing pipe 201, the external fluid source is no longer restricted and can be selected as needed.

[0061] Furthermore, since the external fluid source is unrestricted, it is understood that the scroll compressor 200 may not be limited to the low-pressure side compressor shown in the figure (i.e., the motor is located in an environment with suction pressure, for example separated by the 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, without the partition 80).

[0062] Refer again Figure 3 The conduit 201 is disposed in one of a plurality of inlet channels 142. The conduit 201 has a first section 211 disposed in the inlet channel 142 and a second section 212 adjacent to the intake connector 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 section 211 to be oriented toward the intake connector 70. A certain gap may exist between the second section 212 and the intake connector 70 to facilitate assembly.

[0063] The intake joint 70 can be located between the compression mechanism 10 and the motor 20 in the axial direction of the scroll compressor 100. Specifically, the intake joint 70 can be located between the end plate 164 of the orbiting scroll member 160 and the end face 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 intake joint 70 is located radially outward of the main bearing housing 40. More preferably, in the axial direction of the compressor 100, the intake joint 70 is at least partially aligned with the at least one inflow passage 142, i.e. the at least one inflow passage 142 at least partially faces the flow channel of the intake joint 70.

[0064] It is to be understood that the number, installation, structure, etc. of the ducts should not be limited to the specific examples illustrated, as long as they can achieve the functions described herein. For example, in the example of the variant illustrated, the second section 312 of the duct 301 can have an increasing size towards the intake joint 70. Furthermore, the ducts can for example be in the form of hoses, whereby they can not be limited in space. For example, the second section of the ducts can be connected to or abut the intake joint, or the first section is oriented towards the intake passage. Figure 4 In the example of the variant illustrated, the second section 312 of the duct 301 can have an increasing size towards the intake joint 70. Furthermore, the ducts can for example be in the form of hoses, whereby they can not be limited in space. For example, the second section of the ducts can be connected to or abut the intake joint, or the first section is oriented towards the intake passage.

[0065] Figures 5 to 7 A main bearing housing 41 according to another embodiment of the present disclosure is illustrated. The main bearing housing 41 comprises a body 240. The body 240 comprises a mounting portion 241, a cylindrical portion 243 and an annular portion 245. The structure of the mounting portion 241, the cylindrical portion 243 and the annular portion 245 is similar to that of the mounting portion 141, the cylindrical portion 143 and the annular portion 145, and therefore will not be described in detail.

[0066] The main bearing housing 41 differs from the main bearing housing 40 in the arrangement of the inflow passage 242 and the outflow passage 248 and the provision of a cover 247. This will be described in detail below with reference to Figures 5 to 7 The differences between the main bearing housing 41 and the main bearing housing 40 will be described in detail.

[0067] As Figures 5 to 7 A cover 247 is provided radially inward of the annular portion 245. The cover 247 extends along the inner circumferential face of the annular portion 245, i.e. in the circumferential direction. In the example illustrated in the figures, the cover 247 extends 360 degrees in the circumferential direction and is annular. An annular space 249 is formed between the cover 247 and the annular portion 245. The inflow passage 242 and the 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 via the inflow passage 242 enters the space 249, flows in opposite directions from both sides and then exits from the outflow passage 248.

[0068] The cover 247 can separate the introduced working fluid from the driving bearing. Due to the cover 247, it is possible to prevent the introduced working fluid from blowing away the lubricating oil at the driving bearing and causing deterioration of lubrication.

[0069] Referring again to Figures 5 to 7 The cover 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 can be interference-fitted with the inner circumferential surface of the annular portion 245, whereby the cover 247 is installed. Alternatively, the flange 2472 can be clearance-fitted with the inner circumferential surface of the annular portion 245 to cover the space 249 to some extent. The annular portion 245 can include a stepped portion 2451 for supporting the cylindrical wall 2471 of the cover 247.

[0070] It is to be understood that the structure of the cover and the main bearing housing should not be limited to the specific examples shown in the drawings, but can be changed as needed. For example, the cover and the main bearing housing can be formed as one piece. For example, an annular groove, i.e., the space 249, can be formed in the circumferential direction and in the axial direction from the support surface of the main bearing housing. For example, the cover can extend partially in the circumferential direction, e.g., semicircularly, as long as it can achieve the functions described herein.

[0071] Although the present disclosure has been described with reference to the examples shown in the drawings, it is to be understood that the respective features of the examples shown in the drawings can be combined with each other without contradiction. For example, the inflow passage 242 and the outflow passage 248 can be plural. For example, a pipe can be provided also in the inflow passage 242.

[0072] The specific examples illustrated are merely for the purpose of illustrating the present disclosure and are not intended to limit the present disclosure, and thus, the above specific examples can have various changes. While some embodiments and modifications of the present disclosure have been specifically described, it is to be understood that the present disclosure is not limited to the embodiments and modifications described above and shown in the drawings but can include other various possible combinations and combinations. Other modifications and variations can be made by those skilled in the art without departing from the spirit and scope of the present disclosure. All such modifications and variations fall within the scope of the present disclosure. Moreover, all the components described herein can be replaced by other technically equivalent components.

Claims

1. A scroll compressor, wherein, The scroll compressor includes: Compression mechanism (10); A drive shaft (30) configured to drive the compression mechanism (10); Drive bearing (50), the drive bearing being disposed between the compression mechanism and the drive shaft; and A main bearing housing (40) comprising: a body (140) configured to include an annular portion (145) for sliding support of the compression mechanism and a cylindrical portion (143) for rotating support of the drive shaft, the cylindrical portion (143) extending from the lower end of the annular portion (145); a central recess (146) defined by the annular portion (145), wherein the drive bearing (50) is accommodated in the central recess (146); and an inflow channel (142) disposed in the annular portion (145) and allowing fluid to enter the central recess (146) via the inflow channel (142) to cool the drive bearing (50).

2. The scroll compressor as described in claim 1, wherein, The scroll compressor includes a plurality of inflow channels arranged along the circumferential direction of the body.

3. The scroll compressor as described in claim 1, wherein, The scroll compressor also includes pipes (141, 241) configured to introduce fluid into at least one inflow channel in the inflow channel.

4. The scroll compressor as described in claim 3, wherein, The conduit has: a first section (211) connected to or oriented toward the inflow channel; and a second section (212, 312) connected to or oriented toward the inflow channel of the scroll compressor.

5. The scroll compressor as described in any one of claims 1 to 4, wherein, The inflow channel extends linearly from the inlet in a direction deviating from the radial direction, wherein the inflow channel is configured to be tangent to the inner circumferential surface of the body.

6. The scroll compressor as claimed in claim 1, wherein, The scroll compressor also includes a cover (247) located radially inside the body, forming a space (249) between the body and the cover that communicates with the inflow channel.

7. The scroll compressor as claimed in claim 6, wherein, The cover is annular and has cylindrical walls (2471) for defining the space. The body has a stepped portion (2451) for supporting one end of the cylindrical wall and / or the cover has a flange (2472) extending radially outward from the other end of the cylindrical wall.

8. The scroll compressor as claimed in claim 6 or 7, wherein, An outflow channel (248) is provided in the main bearing housing body in a radial direction opposite to the inflow channel.

9. The scroll compressor according to any one of claims 1 to 4, 6 to 7, wherein, The scroll compressor includes an inlet connector (70) for introducing the working fluid to be compressed and a motor (20) for driving the drive shaft to rotate, the inlet connector being located between the compression mechanism and the motor along the axial direction of the scroll compressor.

10. The scroll compressor according to any one of claims 1 to 4, 6 to 7, wherein, The scroll compressor also includes a partition (80) that divides the space inside the compressor housing into a high-pressure chamber (181) and a low-pressure chamber (182), wherein the compression mechanism and the main bearing housing are located in the low-pressure chamber.

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