WO2022052297A1

WO2022052297A1 - Scroll compressor

Info

Publication number: WO2022052297A1
Application number: PCT/CN2020/129228
Authority: WO
Inventors: 黄幼玲; 杨东辉; 束宏飞; 吴凌云
Original assignee: 艾默生环境优化技术(苏州)有限公司
Priority date: 2020-09-11
Filing date: 2020-11-17
Publication date: 2022-03-17

Abstract

A scroll compressor (100; 200) comprising: a scroll assembly (CM1; CM2) that comprises an orbiting scroll member, the orbiting scroll member comprising a drive coupling part that projects downwardly from a center of a bottom surface; a drive shaft (140; 240) that comprises a spindle part (145; 245) and an eccentric part provided on the top end of the spindle part (145; 245); a support seat (150; 250); and a bearing assembly comprising at least a first bearing member (101; 103; 201; 203) and a second bearing member (102; 104; 202; 204), the first bearing member (101; 103; 201; 203) being arranged between the drive coupling part and the eccentric part, and the second bearing member (102; 104; 202; 204) being arranged between the drive shaft (140; 240) and the support seat (150; 250). The first bearing member (101; 103; 201; 203) axially supports the scroll assembly (CM1; CM2) and directly or indirectly transfers a scroll axial force from the scroll assembly (CM1; CM2) to the second bearing member (102; 104; 202, 204)), and the second bearing member (102; 104; 202; 204) is supported by the support seat (150; 250) to transfer the scroll axial force to the support seat (150; 250). The scroll compressor can effectively avoid abrasion between the bottom surface of the scroll assembly and the support seat.

Description

scroll compressor

This application claims the priority of the following Chinese patent applications: the Chinese patent application with the application number 202010953125.1 and the invention-creation titled "Scroll Compressor" filed with the China Patent Office on September 11, 2020 and filed on September 11, 2020 The Chinese patent application with the application number 202021990381.X and the invention-creation name "scroll compressor" submitted to the China Patent Office. The entire contents of the above patent applications are incorporated herein by reference.

technical field

The present disclosure relates to a scroll compressor. In particular, the present disclosure relates to a scroll compressor with improvements in the axial support of the scroll assembly.

Background technique

The content in this section merely provides background information related to the present disclosure and may not constitute prior art.

A scroll compressor is a machine that compresses refrigerant to achieve cooling or heating. The core assembly for compressing the refrigerant is called a scroll assembly, and the scroll assembly includes a fixed scroll member and a movable scroll member, which cooperate to form a sealed chamber therebetween. During the operation of the compressor, the translation of the movable scroll member relative to the fixed scroll member makes the volume of the sealed chamber change continuously, thereby generating suction, compressed gas and exhaust.

When the scroll assembly of the scroll compressor is working, the pressure of the compressed internal gas will generate an axial gas force, which makes the movable scroll part and the fixed scroll part have a tendency to separate. In order to avoid the separation of the two, it is necessary to provide a support force on the back of the scroll, and the support force can be gas force or can be provided by a special structure.

For the orbiting scroll member, a common way of back support is to provide a back pressure cavity on the back of the orbiting scroll member to generate gas force to support the orbiting scroll member. This method requires high machining accuracy to achieve good sealing, and in order to avoid wear caused by direct contact between the upper surface of the orbiting scroll member and the fixed scroll member, good lubrication of the contact surface is required.

Another common way of back support is to support through the back mechanical structure. A common support structure is to support the back of the orbiting scroll part through the main bearing seat, but this support is usually the back of the orbiting scroll part and the main bearing. The support surface of the seat is in surface contact and there is relative sliding. This also requires good lubrication and high machining accuracy of the contact surfaces.

In addition, in some compressors, the orbiting scroll member is supported by a back ball mechanism or ball bearing. Such structures are usually complex, and require very high machining accuracy for related components, and it is not easy for the scroll assembly to achieve radial flexibility.

Accordingly, it would be desirable to provide a scroll compressor with an improved axial support structure for the scroll assembly.

SUMMARY OF THE INVENTION

It is an object of the present disclosure to provide a scroll compressor that reduces or avoids wear to the backside of the scroll assembly.

Another object of the present disclosure is to provide an improved scroll assembly support structure that is simple in construction and highly adaptable.

In order to achieve one or more of the above objects, according to one aspect of the present disclosure, a scroll compressor is provided. The scroll compressor includes: a scroll assembly including an orbiting scroll member including a drive coupling portion protruding downward from a center of a bottom surface; a drive shaft, the drive shaft For providing rotational driving force for the movable scroll member, the drive shaft includes a main shaft portion and an eccentric portion arranged at the top end of the main shaft portion; a support seat, the support seat is arranged below the scroll assembly to the scroll assembly provides axial support; and a bearing assembly including at least a first bearing member and a second bearing member, the first bearing member being disposed between the drive coupling portion and the eccentric portion To allow rotation of the drive shaft relative to the drive coupling, the second bearing member is disposed between the drive shaft and the bearing seat to allow rotation of the drive shaft relative to the bearing seat. The first bearing member axially supports the scroll assembly and transmits scroll axial forces from the scroll assembly, directly or indirectly, to the second bearing member, the second bearing member Supported by the bearing seat to transmit the scroll axial force to the bearing seat.

In order to achieve one or more of the above objects, according to another aspect of the present disclosure, a scroll compressor is provided. The scroll compressor includes: a scroll assembly including an orbiting scroll member including a drive coupling portion protruding downward from a center of a bottom surface; a drive shaft, the drive shaft For providing rotational driving force for the movable scroll member, the drive shaft includes a main shaft portion and an eccentric portion arranged at the top end of the main shaft portion; a support seat, the support seat is arranged below the scroll assembly to the scroll assembly provides axial support; and a bearing assembly including a first bearing member disposed between the drive coupling portion and the eccentric portion and disposed between the drive shaft and the bearing seat between the second bearing components. The first bearing member and the second bearing member are disposed between the orbiting scroll member and the bearing seat to space a bottom surface of the orbiting scroll member from the bearing seat.

In the above scroll compressor, the first bearing member has a support surface that is in direct contact with a corresponding contact surface of the orbiting scroll member to axially support the orbiting scroll member, the support surface is configured to remain stationary relative to the corresponding contact surfaces.

In the above scroll compressor: the scroll compressor includes a bushing having a bushing flange disposed between the drive coupling portion and the eccentric portion, the first bearing member via the bushing A flange transmits the scroll axial force to the second bearing member; alternatively, the drive shaft is provided with a support portion adapted to support the first bearing member via which the first bearing member is supported or the scroll compressor includes a bushing with bushing flanges disposed between the drive coupling portion and the eccentric portion , and the drive shaft is provided with a support portion adapted to support the bushing flange, the first bearing member transmits the scroll axial force to the bushing flange via the bushing flange and the support portion the second bearing member.

In the above scroll compressor: the scroll compressor includes a bushing disposed between the drive coupling portion and the first bearing member, the bushing being configured to be able to be integral with the drive coupling portion movement; alternatively, the scroll compressor includes a bushing disposed between the eccentric portion and the first bearing member, the bushing configured to move integrally with the eccentric portion.

In the above scroll compressor: the bushing is an unloading bushing; and/or, where the bushing is configured to move integrally with the eccentric portion, the bushing is provided with a counterweight of counterweight bushings.

In the above scroll compressor, the drive coupling portion is a cylindrical hub portion, the eccentric portion is an eccentric pin arranged inside the hub portion, and the first bearing member is arranged around the eccentric pin Between the hub portion and the eccentric pin, the second bearing member is arranged around the main shaft portion between the main bearing arrangement portion of the support seat and the main shaft portion.

In the above scroll compressor, the drive coupling portion is a cylindrical column shaft, the eccentric portion is an eccentric groove provided at the shaft head at the top end of the main shaft portion, and the first bearing member surrounds the shaft. The column shaft is arranged between the eccentric groove and the column shaft, and the second bearing member surrounds the main shaft portion or the shaft head and is arranged between the main bearing setting portion of the support seat and the between the drive shafts.

In the above scroll compressor, the shaft head is eccentrically arranged relative to the main shaft portion and the eccentric groove is centrally arranged relative to the shaft head, or the shaft head is centrally arranged relative to the main shaft portion and the eccentric groove is eccentrically arranged with respect to the shaft head.

In the above scroll compressor, the first bearing component is a rolling bearing suitable for transmitting radial force and axial force or a sliding bearing provided with a bearing flange suitable for transmitting bearing force, and/or the The second bearing part is a rolling bearing suitable for transmitting radial and axial forces or a sliding bearing provided with a bearing flange suitable for transmitting bearing forces.

In the above scroll compressor, the drive coupling portion is a cylindrical column shaft, and the eccentric portion is an eccentric flat-topped shaft head disposed at the top end of the main shaft portion.

In the above scroll compressor, the first bearing member and the second bearing member are rolling bearings suitable for transmitting axial force and radial force, and the second bearing member is an eccentric rolling bearing and is provided with A radial protrusion extending radially inwardly from the inner peripheral surface of the inner ring of the second bearing member, and the second bearing member is arranged such that the inner peripheral surface of the inner ring of the second bearing member surrounds and engages The outer peripheral surface of the outer ring of the first bearing member and the outer peripheral surface of the eccentric flat-topped shaft head, and the radial protrusion is axially placed between the outer ring of the first bearing member and the eccentric between the flat top shaft heads.

The advantages of the scroll compressor according to one or more embodiments of the present disclosure are at least that: the wear on the bottom surface of the scroll assembly and the wear on the thrust surface of the bearing seat are avoided, and the scroll compression is advantageously improved The reliability of the machine is improved; the axial force from the scroll assembly is supported by the bearing, and the radial flexibility of the scroll assembly is not limited; and the structure is simple, easy to manufacture, and strong in applicability. Some embodiments according to the present disclosure also facilitate compact design of the compressor and load management of the drive bearing.

Description of drawings

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

FIG. 1 is a longitudinal sectional view of a conventional scroll compressor.

FIG. 2 shows a partial cross-sectional view of the scroll compressor according to the first embodiment of the present disclosure.

3 shows a schematic diagram of a bearing assembly of a scroll compressor according to a first embodiment of the present disclosure.

4 shows a partial cross-sectional view of a scroll compressor according to a first variation of the first embodiment of the present disclosure.

5 shows a partial cross-sectional view of a scroll compressor according to a second variation of the first embodiment of the present disclosure.

6 shows a partial cross-sectional view of a scroll compressor according to a third variation of the first embodiment of the present disclosure.

7 shows a partial cross-sectional view of a scroll compressor according to a fourth variation of the first embodiment of the present disclosure.

8 shows a partial cross-sectional view of a scroll compressor according to a fifth variation of the first embodiment of the present disclosure.

9 shows a partial cross-sectional view of a scroll compressor according to a second embodiment of the present disclosure.

10 shows a partial cross-sectional view of a scroll compressor according to a first variation of the second embodiment of the present disclosure.

11 shows a partial cross-sectional view of a scroll compressor according to a second variation of the second embodiment of the present disclosure.

12 shows a partial cross-sectional view of a scroll compressor according to a third variation of the second embodiment of the present disclosure.

detailed description

Exemplary embodiments according to the present disclosure will now be described with reference to the accompanying drawings. It is to be understood that the following description is merely exemplary in nature and is not intended to limit the present disclosure and its application and uses. It should be understood that throughout the drawings, like reference numerals refer to the same or similar parts and features. The drawings only schematically represent the concept and principle of the embodiments of the present disclosure, and do not necessarily show the specific dimensions and proportions of the embodiments of the present disclosure, and certain parts in certain drawings may be exaggerated. Relevant details or structures of various embodiments of the present disclosure are illustrated.

In the art, a scroll compressor whose driving mechanism is located in the discharge pressure region (ie, high pressure region) is generally referred to as a high-pressure side scroll compressor, while a scroll whose driving mechanism is located in the suction pressure region (ie, low pressure region) is generally referred to as a scroll compressor on the high side. The compressor is called a low-side scroll compressor. The inventive concept of the present disclosure is not limited to be applied in a high-pressure side scroll compressor, and the inventive concept of the present disclosure can also be applied in a low-pressure side scroll compressor.

First, the general configuration and operation principle of a conventional scroll compressor 1 will be described with reference to FIG. 1 . As shown in FIG. 1 , the scroll compressor 1 is a high-pressure side scroll compressor and generally includes a casing 12 , a top cover 14 disposed at one end of the casing 12 , and a bottom cover 16 disposed at the other end of the casing 12 . In the low pressure side scroll compressor, a partition plate disposed between the top cover 14 and the casing 12 to separate the internal space of the compressor into the high pressure side and the low pressure side may also be included. A motor 40 including a stator 42 and a rotor 43 is provided in the casing 12 . A drive shaft 45 is provided in the rotor 43 to drive a compression mechanism (also referred to as a scroll assembly) composed of the fixed scroll member 20 and the orbiting scroll member 30 . The orbiting scroll member 30 includes an end plate 34 , a hub portion 32 formed on one side of the end plate 34 , and helical vanes 36 formed on the other side of the end plate 34 . The fixed scroll member 20 includes an end plate 24, a helical vane 26 formed on one side of the end plate, and an exhaust port 28 formed at a substantially central position of the end plate.

A series of compression chambers (also referred to as working fluid chambers) whose volumes gradually decrease from the radially outer side to the radially inner side are formed between the helical blades 26 of the fixed scroll member 20 and the helical blades 36 of the orbiting scroll member 30 . Among them, the radially outermost compression chamber is at the suction pressure and is also called a suction chamber, and the radially innermost compression chamber is at an exhaust pressure and is also called a discharge chamber. The middle compression chamber is between the suction pressure and the discharge pressure and is thus also called the middle pressure chamber.

One side of the orbiting scroll member 30 is supported by an upper portion (also referred to as a thrust plate) of the main bearing housing 50 , and one end of the drive shaft 45 is supported by a main bearing 47 provided in the main bearing housing 50 . The top end of the drive shaft 45 is provided with an eccentric pin 46 , and an unloading bush 48 is arranged between the eccentric pin 46 and the hub portion 32 of the orbiting scroll member 30 , and the unloading bush 48 rotates with the eccentric pin. A drive bearing 49 is provided between the hub 32 and the unloading bushing 48 , the drive bearing 49 allows the eccentric pin 46 together with the unloading bushing 49 to rotate within the hub 32 and applies a radial drive force to the hub 32 . Driven by the motor 40, the orbiting scroll 30 will rotate relative to the fixed scroll 20 in translation (ie, the central axis of the orbiting scroll 30 rotates about the central axis of the fixed scroll 20, but the orbiting scroll 30 It does not rotate about its own central axis) to achieve the compression of the fluid. The fluid compressed by the fixed scroll member 20 and the orbiting scroll member 30 is discharged through the exhaust port 28 .

In order to achieve the compression of the fluid, an effective seal is required between the fixed scroll member 20 and the orbiting scroll member 30 .

On the one hand, between the tip of the spiral blade 26 of the fixed scroll member 20 and the end plate 34 of the orbiting scroll member 30 and between the tip of the spiral blade 36 of the orbiting scroll member 30 and the end plate 24 of the fixed scroll member 20 Axial sealing is required. In some examples, a back pressure chamber may be provided on the back of the end plate 24 of the fixed scroll member 20, and one side of the orbiting scroll member 30 is supported by the main bearing seat 50, and the pressure in the back pressure chamber can effectively The fixed scroll member 20 and the orbiting scroll member 30 are pressed together. When the pressure in the compression chamber exceeds a predetermined value, the pressure in the compression chamber will cause the fixed scroll member 20 to move upward. At this time, the fluid in the compression chamber will pass through the gap between the top end of the spiral blade 26 of the fixed scroll member 20 and the end plate 34 of the orbiting scroll member 30 and the top end of the spiral blade 36 of the orbiting scroll member 30 and the fixed scroll The gap between the end plates 24 of the scroll member 20 leaks to the low pressure area for unloading, thereby providing axial flexibility to the scroll compressor. In other examples (such as the example shown in FIG. 1 ), the fixed scroll member 20 may be axially fixed, and a back pressure cavity may be provided on the back of the end plate 34 of the orbiting scroll member 30 to make the orbiting scroll member 30 . The scroll member 30 can float axially, thereby providing axial flexibility to the scroll compressor.

On the other hand, radial sealing is also required between the side surfaces of the helical blades 26 of the fixed scroll member 20 and the side surfaces of the helical blades 36 of the orbiting scroll member 30 . This radial seal between the two is usually achieved by means of the centrifugal force of the orbiting scroll member 30 during operation and the driving force provided by the drive shaft 45 . Specifically, during operation, driven by the motor 40, the orbiting scroll member 30 will rotate relative to the fixed scroll member 20 in translation, so that the orbiting scroll member 30 will generate centrifugal force. In addition, the eccentric pin 46 of the drive shaft 45 also generates a driving force component during the rotation process that helps to achieve the radial sealing of the fixed scroll member and the orbiting scroll member. The helical blades 36 of the orbiting scroll member 30 will abut against the helical blades 26 of the fixed scroll member 20 by means of the above centrifugal force and driving force components, thereby achieving radial sealing therebetween. When incompressible substances (such as solid impurities, lubricating oil, and liquid refrigerant) enter the compression chamber and become stuck between the

helical vanes

26 and 36, the

helical vanes

26 and 36 can be temporarily separated from each other in the radial direction to allow Foreign matter passes through, thus preventing damage to the

screw blades

26 or 36 . This ability to be radially separated provides the scroll compressor with radial flexibility, increasing the reliability of the compressor. In the compressor, there are usually some auxiliary elements for achieving radial flexibility and dynamic balance, such as unloading bushings, counterweight bushings, and the like.

However, as described above and in FIG. 1 , the backside of the orbiting scroll member 30 is supported in direct contact with the top surface (also referred to as a thrust surface or support surface) of the main bearing housing 50 , at the bottom of the motor 40 and its drive shaft 45 . Under driving, the orbiting scroll member 30 will rotate relative to the fixed scroll member 20 in translation, so when the orbiting scroll member 30 moves, between its back and the top surface (ie, the supporting surface) of the main bearing seat 50 due to There will be severe friction due to flat contact. In order to reduce or even eliminate such friction to improve the operating efficiency of the compressor, reduce the wear of the back surface of the movable scroll member and the support surface of the main bearing seat, the present disclosure improves the axial support structure of the scroll assembly, so that the main bearing The bearing surface of the seat is not in direct contact with the bottom surface of the orbiting scroll member, so that there is no contact translational rotation.

A scroll compressor according to an embodiment of the present disclosure will be described below with reference to FIGS. 2 to 12 .

FIG. 2 shows a partial cross-sectional view of the scroll compressor 100 according to the first embodiment of the present disclosure. The scroll compressor 100 includes at least: a casing 112 ; a scroll assembly CM1 including a fixed scroll member 120 and an orbiting scroll member 130 , the orbiting scroll member 130 includes a first end plate 134 and a first end plate formed on the first end plate 134 . The helical vanes 136 on the upper surface of 134, the fixed scroll includes the second end plate 124 and the helical vanes 126 formed on the lower surface of the second end plate 124, in particular, the bottom surface of the first end plate 134 corresponds to The bottom surface of the orbiting scroll and also corresponds to the bottom surface of this scroll assembly CM1, and at the center of the bottom surface is formed a downwardly extending drive coupling in the form of a cylindrical hub 132; bearing seat 150 (ie, the main bearing seat), which is disposed below the scroll assembly CM1 and fixed to the housing 112 to provide axial support for the scroll assembly CM1, in particular, the bearing seat 150 has a main bearing setting portion, at the main bearing setting portion The inner side is provided with the main bearing (ie the second bearing part); the drive shaft 140 , a part of which (via the second bearing part) is accommodated in the central hole of the main bearing setting part of the support seat 150 , which includes the main shaft part 145 And an eccentric portion in the form of an eccentric pin 146 at the top end of the main shaft portion 145, around which an unloading bush 148 is provided.

As shown in FIG. 2, unlike the aforementioned scroll compressor 1, the scroll compressor 100 further includes a bearing assembly consisting of at least a first bearing part 101 and a second bearing part 102, and the first bearing part 101 and The second bearing member 102 separates the scroll assembly CM1 from the bearing seat 150 so that the bearing surface of the bearing seat 150 is not in direct contact with the bottom surface of the orbiting scroll member. In this embodiment, the first bearing part 101 is arranged above the second bearing part 102, and both are exemplarily implemented as rolling bearings comprising an inner ring and an outer ring. It should be noted that in this context, the term "rolling bearing" may refer to any suitable rolling bearing having a configuration for transmitting radial and axial forces, such as tapered roller bearings and angular contact ball bearings, among others. The first bearing member 101 is arranged between the scroll assembly CM1 and the drive shaft 140 , specifically: the first bearing member 101 is arranged inside the hub portion 132 , and its outer ring 101A can be tightly fitted (fixedly fitted with the inner wall of the hub portion 132 ) ), the inner ring 101B can be tightly fitted on the outside of the unloading bushing 148 surrounding the eccentric pin 146; the second bearing component 102 is arranged between the drive shaft 140 and the support seat 150, and its inner ring 102B can be tightly fitted on the outside of the main shaft portion 145 , the outer ring 102A is closely matched with the inner wall of the support seat 150 .

In this embodiment, the inner ring 101B of the first bearing part 101 rests directly on the inner ring 102B of the second bearing part 102 . In this way, the axial force (also referred to as scroll axial force) from the scroll assembly CM1 is received by the top surface of the outer ring 101A of the first bearing member 101 and transmitted to the inner ring 101B through the first bearing member 101 The direct contact between the bottom surface of the inner ring 101B and the top surface of the inner ring 102B of the second bearing part 102 , this axial force is further received by the top surface of the inner ring 102B of the second bearing part 102 , and via the second bearing part 102 . The bottom surface of the outer ring 102A is transmitted to the bearing seat 150 , thereby realizing the transmission of the axial force from the scroll assembly CM1 to the bearing seat 150 , in other words, realizing the axial support of the scroll assembly CM1 by the bearing seat 150 .

In addition to transmitting the axial force, the bearing assembly also undertakes the task of transmitting the driving force to the scroll assembly CM1. When the drive shaft 140 rotates around the longitudinal center axis under the driving of the motor, it drives the inner ring 102B of the second bearing member 102 to rotate together, while the outer ring 102A of the second bearing member 102 is stationary relative to the support seat 150, and the eccentric pin 146 is integrally A circular motion with a radius of gyration R is then performed around the longitudinal center axis, wherein the radius of gyration is the distance between the eccentric axis of the eccentric pin 146 and the longitudinal center axis. The circular motion of the eccentric pin 146 about the longitudinal center axis drives the coaxial unloading bushing 148 (and the inner ring 101B of the first bearing member 101 ) to do the same circular motion, thereby driving the orbiting scroll member 130 relative to the fixed scroll The member 120 rotates in translation.

In other words, the bearing assembly achieves axial support and driving force transmission to the scroll assembly CM1 by providing the following configuration: the first bearing member 101 includes a first surface that receives the axial force from the scroll assembly CM1 (here, Namely, the top surface of the outer ring 101A) and the second surface (here, the bottom surface of the inner ring 101B) that transmits the axial force to the second bearing member 102, which includes receiving the transmission through the first bearing member 101. The third surface of the axial force (here, the top surface of the inner ring 102B) and the fourth surface (here, the bottom surface of the outer ring 102A) that transmits the axial force to the bearing seat 150, thereby realizing the shaft The force is transmitted from the scroll assembly CM1 to the bearing seat 150; with the rotation of the drive shaft 145, the inner ring 101B of the first bearing member 101 and the inner ring 102B of the second bearing member 102 rotate together with the drive shaft 140, while The outer ring 101A of the first bearing member 101 (correspondingly, the orbiting scroll member 130 ) is driven by the eccentric pin 146 of the drive shaft 140 relative to the outer ring 102A of the second bearing member 102 (correspondingly, the support seat 150 ) The translational rotation is performed, thereby realizing the transmission of the driving force from the drive shaft 140 to the movable scroll member 130 .

In addition, in this embodiment, the dimensions of the inner ring 101B and the inner ring 102B should be set such that between the bottom surface (ie, the second surface) of the inner ring 101B and the top surface (ie, the third surface) of the inner ring 102B Has some degree of axial contact (overlap) to transmit axial forces.

In order to facilitate the description of the dimensional relationship between the two, FIG. 3 shows a top view showing the positional relationship of the two bearing components during operation according to the first embodiment of the present disclosure, and a longitudinal cross-sectional view taken along lines AA and BB, wherein , the line AA passes through the centerline O2 of the second bearing part 102 , and the line BB is perpendicular to the line AA and passes through the centerline O1 of the first bearing part 101 and the centerline O2 of the second bearing part 102 . In order to ensure the contact between the second surface and the third surface, on the one hand, when the third surface is larger, it should be ensured that the outer edge of the second surface (corresponding to the outer diameter D2 of the inner ring 101B) is always in the radial direction Beyond the inner edge of the third surface (corresponding to the inner diameter M1 of the inner ring 102B), on the other hand, when the second surface is large, the outer edge of the third surface (corresponding to the outer diameter of the inner ring 102B) M2) always extends beyond the inner edge of the second surface (corresponding to the inner diameter D1 of the inner ring 101B) in the radial direction. Furthermore, in an example where a first bearing component (such as the member with the second surface of the first bearing component) rotates in translation relative to the second bearing component (such as the component with the third surface of the second bearing component), in When the distance Ror between the centerline O1 of the first bearing member 101 and the centerline O2 of the second bearing member 102 is known, the dimensions between the second surface and the third surface should simultaneously satisfy the following relational expression (1) and (2):

D2>M1+2Ror (1)

M2>D1+2Ror (2)

in:

D1 is the inner diameter of the inner ring 101B of the first bearing component 101 (ie, the inner diameter of the inner ring 101B at the second surface);

D2 is the outer diameter of the inner ring 101B of the first bearing component 101 (ie, the outer diameter of the inner ring 101B at the second surface);

M1 is the inner diameter of the inner ring 102B of the second bearing component 102 (ie, the inner diameter of the inner ring 102B at the third surface); and

M2 is the outer diameter of the inner ring 102B of the second bearing member 102 (ie, the outer diameter of the inner ring 102B at the third surface).

According to the above-described first embodiment, the first bearing member supports the scroll assembly in the axial direction and transmits the axial force from the scroll assembly directly to the second bearing member, which is supported by the bearing seat to transmit the axial force is transmitted to the bearing seat, so that the bearing assembly transmits the rotational driving force to the scroll assembly CM1 while also transmitting the axial force from the scroll assembly CM1 to the bearing seat 150, which allows the scroll assembly CM1 to be spaced from the bearing seat 150 , to avoid the wear of the bottom surface of the scroll assembly CM1 due to the contact translational rotation with the support surface of the bearing seat 150, in addition, the first surface of the first bearing part is adjacent to and opposite to the bottom surface of the scroll assembly Stationary, therefore, avoids severe friction of the first bearing member against the bottom surface of the scroll assembly. Through this structure, the bottom surface of the scroll assembly does not have contact translational rotation with any adjacent surface, which advantageously reduces friction and friction loss during operation, thereby improving the reliability of the scroll compressor. It will be particularly advantageous for scroll compressors of the following types: inverter compressors with a wide range of rotational speeds; high pressure refrigerant compressors with large scroll axial loads; and oil mist with poor lubrication on the back of the orbiting scroll components Lubricate compressors, etc.

According to the first embodiment, through the direct contact between the second surface of the first bearing part 101 and the third surface of the second bearing part 102 , the transmission of the axial force therebetween is achieved. However, this direct transmission method is only exemplary, and the axial force can also be transmitted between the two through an intermediate component. Compared with the direct contact transmission method, the axial force is transmitted through the intermediate member because there is no restriction on the dimensional relationship between the first bearing member 101 and the second bearing member 102, so the structure design can be simplified and the impact on the machining accuracy can be reduced. requirements, making it easier to implement and more adaptable.

FIG. 4 shows a variation of the first embodiment. For the sake of brevity, only the differences between this embodiment and the first embodiment will be described below. In this embodiment, the second bearing member 102 is not in direct contact with the first bearing member 101 , but provides axial support for the drive shaft 140 through interference fit with the main shaft portion 145 of the drive shaft 140 , specifically, the axial direction The force is transmitted in the following manner: the top surface of the outer ring 101A of the first bearing member 101 faces the scroll assembly CM1 and is in direct contact with the bottom surface of the scroll assembly CM1, thereby serving as the first source for receiving the axial force from the scroll assembly CM1. A surface on which the bottom surface of the inner ring 101B of the first bearing member 101 abuts against the shoulder surface 147 of the drive shaft 140 (the shoulder surface may be the boundary between the eccentric pin and the main shaft portion and the shoulder surface serves as a The disclosed support part) and transmit the axial force to the drive shaft 140, where the bottom surface of the inner ring 101B is used as the second surface for transmitting the axial force to the second bearing part 102; The inner ring 102B is in an interference fit with the main shaft portion 145, and the outer ring 102A of the second bearing member 102 is supported by the support seat 150, so that the axial force transmitted from the second surface to the drive shaft 140 will be transmitted to the first through the interference fit. The inner ring 102B of the two bearing components 102, at this time, the inner surface of the inner ring 102B is the third surface, and is in contact with the thrust surface 152 of the support seat 150 to transmit the axial force to the outer ring 102A of the support seat 150. The bottom surface is the fourth surface.

This configuration provides substantially the same advantages as the bearing assembly in the first embodiment. Here, force transmission may be achieved between the inner ring 102B of the second bearing component 102 and the main shaft portion 145 through other fitting manners other than interference fit, such as form fit. Here, the so-called "form fit" refers to a manner in which two mutually cooperating parts can be positioned relative to each other without the aid of a third part, but only by the relationship of the shapes and/or sizes of the two parts. Therefore, in the embodiment according to the present disclosure, instead of the interference fit, the positioning between the components, especially the axial direction, can also be achieved by, for example, a form-fit structure such as a stepped fit structure and a concave-convex fit structure, etc. formed at the mating surface. orientation in the direction.

FIG. 5 shows another variation of the first embodiment. For the sake of brevity, only the differences between this embodiment and the previous embodiments will be described below. In this embodiment, the second surface of the first bearing member 101 is not in direct contact with the third surface of the second bearing member 102, and therebetween is through the radial protrusion of the unloading bushing 160 (ie, the bushing flange) 162 and a radial protrusion 149 formed on the upper end of the main shaft part 145 of the drive shaft 140 (the radial protrusion 149 may be a boundary between the eccentric pin and the main shaft part) to transmit the axial force. Here, it should be noted that, in this embodiment, the radially protruding portion 149 serves as a support portion according to the present disclosure.

In the embodiment according to the present disclosure, the type of the unloading bushing is not limited whether it is used for transmitting axial force or not, for example, it may be a swing unloading bushing or a sliding unloading bushing. When it needs to transmit the axial force, it only needs to make a simple modification to the existing unloading bushing, for example, adding a radial extension (protrusion) suitable for receiving and outputting the axial force, as in the previous embodiment shown.

Accordingly, those skilled in the art may appreciate that bearing assemblies according to embodiments of the present disclosure may be applied to existing scroll compressors with little or no structural modifications to the existing scroll compressors , therefore, its structure is simple and very easy to implement; in addition, its setting does not hinder the unloading bushing and the counterweight type bushing (that is, a counterweight assembly formed by adding a counterweight to the bushing, especially the unloading bushing), etc. The placement of the auxiliary elements has no or substantial effect on the achievement of radial flexibility of the scroll assembly.

In addition, in addition to the aforementioned rolling bearing, one or both of the first bearing component and the second bearing component may be replaced by a rolling bearing with a sliding bearing according to the structural features and design requirements of the compressor. When a cylindrical sliding bearing is used, in order to achieve the transmission of the axial force, the sliding bearing may be in the form of a flange having an end portion extending radially outwards.

As an example, Figures 6 to 8 respectively show embodiments in which the first bearing part, the second bearing part and both the first and second bearing parts are replaced by plain bearings.

In the embodiment shown in FIG. 6 , the first bearing member 103 is implemented as a sliding bearing, which includes a cylindrical body 103A and a flange (ie, a bearing flange) 103B at the bottom end of the cylindrical body 103A, wherein the cylindrical body The inner surface of 103A, as well as the lower surface of flange 103B, are smooth to allow the mating components to slide relative to the surface. The outer surface of the cylindrical body 103A is tightly fitted (eg, a fixed interference fit) with the hub portion 132, so that the sliding bearing always remains stationary relative to the scroll assembly CM1 during operation. In this embodiment, the upper surface of the flange 103B is the first surface that receives the axial force from the scroll assembly CM1, and the lower surface of the flange 103B abuts against the inner ring 102B of the second bearing member 102, ie serves as a The second surface to which the axial force is transmitted to the second bearing member 102 . Likewise, the flange 103B should be sized so that it is always in contact with the third surface of the second bearing member 102 during its translational rotation with the orbiting scroll member (the third surface is defined by the Inner ring 102B provides) contact. However, the configuration of the first bearing member 103 is not limited to this, and for example, the outer surface of the cylindrical body 103A and the upper surface of the flange 103B may be provided as smooth sliding surfaces so that the first bearing member 103 is relatively opposed to the bushing 148 and the upper surface of the flange 103B. The drive shaft 140 remains stationary and freely slidable relative to the hub 132 .

In the embodiment shown in FIG. 7 , the second bearing part 104 is embodied as a sliding bearing. Similar to the example shown in FIG. 6 , the second bearing member 104 includes a cylindrical body 104A and a flange (ie, a bearing flange) 104B at the top end of the cylindrical body 104A, wherein the inner surface of the cylindrical body 104A and the flange The upper surface of 104B is smooth to allow mating components to slide relative to the surface. The outer surface of the cylindrical body 104A is tightly fitted with the support base 150 , so that the second bearing member 104 always remains stationary relative to the support base 150 during operation. In this embodiment, the upper surface of the flange 104B is the third surface that receives the axial force transmitted by the first bearing member 101 , and the lower surface of the flange 104B is the fourth surface that transmits the axial force to the bearing seat 150 . surface. Likewise, the flange 104B should be dimensioned so that it is always in contact with the second surface of the first bearing member 101 during rotation.

In the embodiment shown in FIG. 8 , both the first bearing part 103 and the second bearing part 104 are implemented as plain bearings. Among them, as an example, the first bearing member 103 is tightly fitted with the bushing 148 , and the outer surface of the cylindrical body 103A and the upper surface of the flange (ie, the bearing flange) 103B are smooth and thus can slide freely relative to the hub portion 132 , the second bearing member 104 mates closely with the bearing seat 150, the inner surface of the cylindrical body 104A and the upper surface of the flange (ie, bearing flange) 104B are smooth to allow the drive shaft 140 to slide freely relative to this surface. In this embodiment, the lower surface of the flange 103B of the first bearing member 103 and the upper surface of the flange 104B of the second bearing member 104 serve as the second and third surfaces for transmitting the axial force, respectively, and in order to reduce the Requirements for design and machining accuracy, the second surface and the third surface transmit the axial force by respectively abutting the upper and lower surfaces of the radial protrusions 149 formed on the drive shaft 140 . Similar to the previous embodiment, as a variant, the first bearing member 103 can be made to fit tightly with the hub 132 to slide freely relative to the bushing 148 .

An example of a scroll compressor according to the first embodiment of the present disclosure and its variants has been described above with reference to FIGS. 2 to 8 , wherein the drive coupling of the scroll assembly CM1 is the cylindrical hub 132 and the bearing The assembly comprises a

first bearing part

101 or 103 in the form of an inner bearing housed inside the cylindrical hub 132 and a

second bearing part

102 or 104 in the form of an outer bearing surrounding the drive shaft 140 . While the bearing assembly (in particular, the first bearing member) transmits the rotational driving force to the scroll assembly CM1, the first and second bearing members of the bearing assembly also transmit the axial force from the scroll assembly CM1 to the bearing seat 150 that allows the scroll assembly CM1 to be spaced from the support seat 150 (ie, the scroll assembly CM1 is spaced from the support seat 150 by the bearing assembly) and such that the bottom surface of the scroll assembly is not adjacent to any Contact translational rotation of the surface occurs. However, the arrangement of the

first bearing member

101 or 103 and the

second bearing member

102 or 104 may be changed accordingly depending on the configuration of the drive coupling portion of the scroll assembly CM1 and the drive shaft 140 . Several exemplary embodiments of scroll compressors with different configurations of the drive coupling and the eccentric portion of the drive shaft 140 will be described below with reference to FIGS. 9 to 12 , which will provide the first embodiment and its variations. The same or even more favorable advantages of the body.

9 shows a scroll compressor 200 according to a second embodiment of the present disclosure. Unlike the first embodiment, the drive coupling portion of the scroll assembly CM2 of the scroll compressor 200 is the end of the driven scroll member 230 The center of the bottom surface of the plate 234 (ie, the bottom surface of the scroll assembly CM2 ) is a cylindrical column shaft 236 extending downward, and the top end of the drive shaft 240 is provided with an eccentric portion, which is the axis relative to the main shaft portion of the drive shaft 240 Eccentric groove 262 (corresponding to an eccentric groove in accordance with the present disclosure) with an offset axis of 245 .

As shown in FIG. 9 , both the first bearing member 201 and the second bearing member 202 are exemplarily rolling bearings. The first bearing member 201 is arranged between the scroll assembly CM2 and the drive shaft 240 (specifically, between the cylindrical column shaft 236 and the eccentric portion), and the second bearing member 202 is arranged between the drive shaft 240 and the support seat 250 Specifically: fit in the eccentric groove 262, the inner ring 201B of the inner ring 201B is closely matched with the outer surface of the column shaft 236, the outer ring 201A is closely matched with the inner wall of the eccentric groove 262, and the inner ring 202B of the second bearing component 202 Then form an interference fit (or other form of fit such as form fit) with the shaft head 260 of the drive shaft 240, and the outer ring 202A forms an interference fit (or other form of fit such as the inner wall (thrust surface) 254 of the bearing seat 250 form fit). In this way, the axial force from the scroll assembly CM2 is received by the top surface (first surface) of the inner ring 201B of the first bearing member 201 and transmitted to the outer ring 201A, and then passes through the bottom surface (second surface) of the outer ring 201A When an axial force is applied to the eccentric groove 262, the inner ring 202B of the second bearing part 202 provides axial support for the drive shaft 240 through the interference fit with the shaft head 260; The third surface of the first bearing component 201 that transmits the axial force is the inner surface of the inner ring 202B, and the outer surface of the outer ring 202A is the fourth surface that transmits the axial force to the bearing seat 250 . Likewise, the first surface may be stationary relative to the bottom surface of the scroll assembly CM2, and the fourth surface may be stationary relative to the bearing seat 250, so as to avoid wear on the scroll assembly CM2 and the inner wall (thrust surface of the bearing seat 250) ) 254 wear. Here, it should be noted that, in this embodiment, the groove bottom wall of the eccentric groove 262 (ie, the portion supporting the outer ring 201A) serves as the support portion according to the present disclosure.

Compared with the first embodiment, due to the change in the configuration of the drive coupling part and the drive shaft (especially the shaft head and the eccentric part), in the second embodiment, the first bearing part, which was originally in the form of an inner bearing, is adapted to become In the form of an outer bearing. This embodiment can also provide the advantageous effects brought by the first embodiment. Besides, by transforming the first bearing component into the form of an outer bearing, it also has the following additional advantages: on the one hand, the movable vortex can be made The design of the radial space of the scroll member is more compact, which is beneficial to the weight reduction of the orbiting scroll member; on the other hand, the relative position between the first bearing member and the second bearing member in the axial direction becomes closer or even The first bearing part and the second bearing part are partially overlapped (for the partially overlapping scheme, please refer to the embodiments shown in Fig. 9, Fig. 11 and Fig. 12), so the axial space of the compressor is also allowed to be more compact; In the case of a counterweight bushing, this arrangement not only does not hinder the installation of the counterweight, but also allows the center of mass of the counterweight to be higher, making it easier to achieve the center of mass of the counterweight and the drive bearing (here, the first bearing component ) at the same height, thereby improving the force of the drive bearing and improving the stability.

It is understood that in this structure, either of the first bearing member and the second bearing member may be replaced by a sliding bearing. Figure 10 shows a variant of the second embodiment. Compared to the second embodiment, the difference is that both the first bearing member 203 and the second bearing member 204 are in the form of sliding bearings. Where, by way of example, the first bearing member 203 is tightly fitted in the groove 262, the inner surface of its cylindrical body 203A and the upper surface of the flange (ie, bearing flange) 203B are sliding surfaces to allow the column shaft 236 and the bushing The sleeve 248 slides freely inside the first bearing member 203, the second bearing member 204 is tightly fitted inside the bearing seat 250, and the inner surface of the cylindrical body 204A and the upper surface of the flange (ie, bearing flange) 204B are sliding surfaces. Similar to the previous embodiment, as a variant, the first bearing member 203 can be made to fit tightly with the bushing 248 (the column shaft 236 ) to freely slide relative to the bushing 248 .

Also the first bearing part is in the form of an outer bearing, Figure 11 shows another variant of the second embodiment. Compared with the second embodiment, except that the first bearing part 203 is a sliding bearing provided with a bearing flange, the difference is that the eccentric part of the drive shaft 240 is a grooved eccentric shaft head 270 located at the top of the main shaft part 245 . The groove is a central groove 272 coaxial with the eccentric shaft head 270 . The first bearing part 203 is embodied as a sliding bearing, and the second bearing part 202 is an eccentric rolling bearing arranged between the eccentric shaft head 270 and the bearing seat 250 . The inner ring 202B of the eccentric rolling bearing has an eccentric inner hole, so its wall thickness is not uniform. The eccentric inner hole forms a form fit with the outer surface of the eccentric shaft head 270 , and the distance between the center line of the eccentric inner hole and the center line of the second bearing component 202 is equal to the distance between the eccentric shaft head 270 and the inner wall 254 of the support seat 250 The distance is equal to the radius of gyration of the eccentric shaft head 270 to compensate for the radial offset between the eccentric shaft head 270 and the support seat 250 .

Here, it should be noted that, in the embodiment shown in FIG. 9 , the shaft head is arranged centrally with respect to the main shaft portion and the eccentric groove is arranged eccentrically with respect to the shaft head, thereby realizing the eccentric groove serving as the eccentric portion. groove, in contrast, in the embodiment shown in Figures 10 and 11, the shaft head is arranged eccentrically relative to the main shaft portion and the eccentric groove is arranged centrally relative to the shaft head (so-called central groove 272), An eccentric groove serving as an eccentric portion is thereby achieved. In addition, in the embodiment shown in FIGS. 10 and 11 , since the first bearing member is implemented as a sliding bearing provided with a bearing flange adapted to transmit the bearing force, the top surface of the side wall of the eccentric groove (ie the support bearing part of the flange) serves as a support according to the present disclosure. In summary, in the present disclosure, the support portion is a portion adapted to transmit the axial force of the scroll from the first bearing member to the second bearing member.

Figure 12 shows yet another variation of the second embodiment. The main difference from the second embodiment is that in this embodiment, the eccentric part is an eccentric flat-topped shaft head 280 , the first bearing member 201 is arranged around the column shaft 236 to be coaxial with the flat-topped shaft head 280 , and the second bearing member 202 is an eccentric rolling bearing, the outer ring 202A of which is closely fitted with the bearing seat 250, and the eccentric inner hole 202H surrounds the eccentric flat-topped shaft head 280 and is form-fitted with the outer surface of the first bearing part 201 - that is, by forming in the second bearing part A radially inwardly extending radial protrusion 202C of the inner ring 202B of 202 - to provide axial support for the first bearing component 201 . Therefore, in this embodiment, the third surface is the top surface of the radial protrusions 202C of the inner ring 202B, and the fourth surface is the outer surface of the outer ring 202A of the second bearing member 202 .

Two different embodiments and variants of these two embodiments have been described in detail above, generally depending on the difference in the arrangement position of the first bearing part relative to the drive coupling. It should be understood, however, that the present disclosure is not limited to the specific embodiments described and illustrated in detail herein, for example, the radius of gyration of the orbiting scroll may not be provided by the drive shaft, but may be provided by means of being disposed between the drive shaft and the hub portion eccentric bushing. In the case of a bushing or counterweight, although in the foregoing embodiments, the bushing or counterweight is shown as being located on the inner side of the first bearing member, however, the bushing or counterweight may be Fitted on the outside of the first bearing member.

In addition, it should be noted that although in the embodiments specifically described above, the scroll axial force is directly transmitted from the orbiting scroll member (eg, the bottom surface) to the first bearing member (specifically, the first bearing member first surface), however, it is also contemplated that an intermediate member may be provided between the orbiting scroll component (eg, the bottom surface) and the first bearing component (eg, in FIG. 10 , the bushing 248 is configured to have an arrangement A bushing flange between the bottom surface of the orbiting scroll member and the bearing flange 203B) so that the scroll axial force is indirectly transferred from the orbiting scroll member to the first bearing member.

In addition, it should be noted that, although in the above-described embodiment, the general unloading bushing is particularly described, however, a bushing that cannot slide or swing relative to the orbiting scroll member or the drive shaft may also be used, On the other hand, a counterweight type bushing formed by adding a counterweight to the bushing, especially the unloading bushing, can also be used. For example, in the unloading bushing 160 shown in FIG. 5 , a counterweight portion extending radially outward from the radial protrusion (ie, bushing flange) 162 may be added on the radial side of the unloading bushing 160 Thus, a counterweight bushing is formed. By providing the counterweight bushing, the counterweight balancing force can act on the hub portion of the orbiting scroll member, so that the dynamic balance of the scroll compressor can be reliably improved, and by providing the unloading balancer that has both unloading and dynamic balancing functions The heavy-duty bushing advantageously improves the dynamic balance of the scroll compressor while achieving radial flexibility.

Furthermore, it should be noted that the bearing surface of the first bearing member corresponds to the above-described corresponding contact for receiving the axial force from the scroll assembly and with, for example, the bottom surface of the orbiting scroll member (ie the orbiting scroll member). surface) the first surface in direct contact with. In the present disclosure, preferably, the support surface remains stationary relative to the corresponding contact surface of the orbiting scroll member both when the scroll compressor is not operating and when the scroll compressor is operating.

In addition, it should be noted that in this application document, the use of the orientation terms "downward", "below", "top" and "bottom" is only for the convenience of description and should not be regarded as limiting . For example, "top" for vertical compressors may correspond to "left side" or "right side" in the case of horizontal compressors.

Accordingly, other modifications and variations can be effected by those skilled in the art without departing from the spirit and scope of this disclosure. All such modifications and variations fall within the scope of this disclosure. Furthermore, all components described here may be replaced by other technically equivalent components.

Claims

A scroll compressor (100; 200), comprising:

a scroll assembly (CM1; CM2) including an orbiting scroll member including a drive coupling protruding downward from a center of the bottom surface;

A drive shaft (140; 240), the drive shaft (140; 240) is used to provide a rotational driving force for the orbiting scroll member, the drive shaft (140; 240) includes a main shaft portion (145; 245) and an arrangement an eccentric portion at the top end of the main shaft portion (145; 245);

a bearing seat (150; 250) disposed below the scroll assembly (CM1; CM2) to provide axial support for the scroll assembly (CM1; CM2); and

A bearing assembly comprising at least a first bearing part (101; 103; 201; 203) and a second bearing part (102; 104; 202; 204), the first bearing part (101; 103; 201; 203) arranged between the drive coupling and the eccentric to allow the drive shaft (140; 240) to rotate relative to the drive coupling, the second bearing member being arranged on the drive shaft (140) ; 240) and the bearing seat (150; 250) to allow the drive shaft (140; 240) to rotate relative to the bearing seat (150; 250),

wherein the first bearing member (101; 103; 201; 203) supports the scroll assembly (CM1; CM2) in the axial direction and absorbs the scroll axial force from the scroll assembly directly or indirectly to the second bearing member (102; 104; 202; 204), which is supported by the bearing seat to transmit the scroll axial force to the bearing seat (150; 250).
A scroll compressor (100; 200), comprising:

a scroll assembly (CM1; CM2) including an orbiting scroll member including a drive coupling protruding downward from a center of the bottom surface;

A drive shaft (140; 240), the drive shaft (140; 240) is used to provide a rotational driving force for the orbiting scroll member, the drive shaft (140; 240) includes a main shaft portion (145; 245) and an arrangement an eccentric portion at the top end of the main shaft portion (145; 245);

a bearing seat (150; 250) disposed below the scroll assembly (CM1; CM2) to provide axial support for the scroll assembly (CM1; CM2); and

A bearing assembly comprising a first bearing member (101; 103; 201; 203) arranged between the drive coupling portion and the eccentric portion and a first bearing member (101; 103; 201; 203) arranged between the drive shaft (140; 240) and the the second bearing parts (102; 104; 202; 204) between the support seats (150; 250),

Wherein, the first bearing member (101; 103; 201; 203) and the second bearing member (102; 104; 202; 204) are arranged between the orbiting scroll member and the support seat to The bottom surface of the orbiting scroll member is spaced from the bearing seat (150; 250).
The scroll compressor (100; 200) according to claim 1 or 2, wherein the first bearing member (101; 103; 201; 203) has a support surface which is in contact with the orbiting scroll Corresponding contact surfaces of the components are in direct contact to axially support the orbiting scroll components, the support surfaces being configured to remain stationary relative to the corresponding contact surfaces.
The scroll compressor (100; 200) according to claim 1 or 2, wherein:

The scroll compressor includes a bushing having a bushing flange disposed between the drive coupling portion and the eccentric portion, the first bearing member attaching the scroll shaft via the bushing flange transmitting force to said second bearing member; or

the drive shaft is provided with a support portion adapted to support the first bearing member via which the first bearing member transmits the scroll axial force to the second bearing member; or

The scroll compressor includes a bushing with a bushing flange disposed between the drive coupling portion and the eccentric portion, and the drive shaft is provided with a support portion adapted to support the bushing flange , the first bearing member transmits the scroll axial force to the second bearing member via the bushing flange and the support portion.
The scroll compressor (100; 200) according to claim 1 or 2, wherein:

the scroll compressor includes a bushing disposed between the drive coupling and the first bearing member, the bushing configured to move integrally with the drive coupling; or

The scroll compressor includes a bushing disposed between the eccentric portion and the first bearing member, the bushing being configured to move integrally with the eccentric portion.
The scroll compressor (100; 200) of claim 5, wherein:

the bushing is an unloading bushing; and/or

Where the bushing is configured to move integrally with the eccentric portion, the bushing is a counterweighted bushing provided with a counterweight.
The scroll compressor (100) according to claim 1 or 2, wherein the drive coupling portion is a cylindrical hub portion (132), and the eccentric portion is arranged inside the hub portion (132) an eccentric pin (146), the first bearing part (101; 103) is arranged around the eccentric pin (146) between the hub and the eccentric pin, and the second bearing part (102; 104) Around the main shaft part (145), it is arranged between the main bearing setting part of the support seat (150) and the main shaft part.
The scroll compressor (200) according to claim 1 or 2, wherein the drive coupling part is a cylindrical column shaft (236), and the eccentric part is provided at the top end of the main shaft part (245) The eccentric groove at the head of the shaft, the first bearing member (201; 203) is arranged between the eccentric groove and the column shaft around the column shaft, and the second bearing member (202; 204) around the main shaft part (245) or the shaft head and arranged between the main bearing setting part of the support seat (250) and the drive shaft.
The scroll compressor (200) according to claim 8, wherein the shaft head is arranged eccentrically with respect to the main shaft portion and the eccentric groove is arranged centrally with respect to the shaft head, or, the The shaft head is arranged centrally with respect to the main shaft portion and the eccentric groove is arranged eccentrically with respect to the shaft head.
The scroll compressor (100; 200) according to claim 1 or 2, wherein:

The first bearing part (101; 103; 201; 203) is a rolling bearing suitable for transmitting radial and axial forces or a sliding bearing provided with a bearing flange suitable for transmitting bearing forces, and/or

The second bearing part (102; 104; 202; 204) is a rolling bearing suitable for transmitting radial and axial forces or a sliding bearing provided with a bearing flange suitable for transmitting bearing forces.
The scroll compressor (200) according to claim 1 or 2, wherein the drive coupling part is a cylindrical column shaft (236), and the eccentric part is provided at the top end of the main shaft part (245) eccentric flat top shaft head.
The scroll compressor (200) of claim 11, wherein:

The first bearing part and the second bearing part are rolling bearings suitable for transmitting axial force and radial force,

the second bearing member is an eccentric rolling bearing and is provided with a radial protrusion (202C) extending radially inward from the inner peripheral surface of the inner ring of the second bearing member, and

the second bearing member is arranged such that the inner peripheral surface of the inner ring of the second bearing member surrounds and engages the outer peripheral surface of the outer ring of the first bearing member and the outer peripheral surface of the eccentric flat head, And the radial protrusion is placed between the outer ring of the first bearing member and the eccentric flat-topped shaft head in the axial direction.