CN212536075U

CN212536075U - Scroll compressor having a plurality of scroll members

Info

Publication number: CN212536075U
Application number: CN202021511823.8U
Authority: CN
Inventors: 刘轩; 秦岩; 张琼宇; 刘畅
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Copeland Suzhou Co Ltd
Priority date: 2020-07-27
Filing date: 2020-07-27
Publication date: 2021-02-12
Anticipated expiration: 2030-07-27

Abstract

The utility model relates to a scroll compressor, include: a fixed scroll including a fixed scroll end plate, a fixed spiral wrap extending from one side of the fixed scroll end plate, and a discharge port provided in the fixed scroll end plate; an orbiting scroll including an orbiting scroll end plate, an orbiting spiral wrap extending from one side of the driven scroll end plate, and a boss portion protruding from the driven scroll end plate on a side opposite to the orbiting spiral wrap, the orbiting spiral wrap and the fixed spiral wrap being engaged in a meshing manner, thereby generating a fluid chamber for compressing a working fluid; a bearing assembly upon which the orbiting scroll end plate is slidably supported, the bearing assembly and orbiting scroll end plate each having a thrust surface in sliding contact with each other; and the driving assembly comprises a shaft for driving the hub, wherein an oil supply channel is arranged on the hub, so that lubricating oil in the hub is sprayed to the thrust surface through the oil supply channel.

Description

Scroll compressor having a plurality of scroll members

Technical Field

The utility model relates to a scroll compressor.

Background

This section provides background information related to the present disclosure and is not necessarily prior art.

During operation of the scroll compressor, a large load is applied in an axial direction in order to ensure sealing of the fluid pockets for effective compression of the working fluid. The axial load acting on the scroll member is ultimately borne by the main bearing housing, or a thrust assembly disposed between the scroll member and the main bearing housing. The thrust surfaces between the scroll member and the main bearing housing or thrust assembly require good lubrication.

In a scroll compressor provided with a main bearing housing or a thrust assembly additionally, by utilizing the rotation of the movable scroll, the hub of the movable scroll alone or together with other additional components agitates lubricating oil in an oil pool formed at the bottom of the main bearing housing, so that the lubricating oil splashes to and lubricates a thrust surface between the scroll and the main bearing housing or a thrust surface between the scroll and the thrust assembly.

In the case of performing the splash lubrication in the above manner, when the rotational speed of the scroll compressor is low, the amount of oil stirred up is small, and the lubrication of the thrust surface is insufficient. In the case where a thrust assembly is provided, the radially extending surface of the thrust assembly may trap some of the oil that splashes, further reducing the amount of thrust surface lubrication. In addition, in the case where a drive bushing is provided outside an eccentric crank pin provided at the tip end of the shaft of the drive assembly of the scroll compressor and a balance weight member, for example, is provided on the drive bushing, the balance weight member may also block a part of the oil splash region, which is more disadvantageous for splash lubrication. In addition, after the compressor is shut down, the oil sump flows back to the base of the scroll compressor. Therefore, when the scroll compressor is started again, a certain time is needed to raise the oil level of the oil pool to the height that the hub of the movable scroll member or the balance weight component can stir oil, and during the time, the lubrication condition of the thrust surface is poor, so that the early wear failure of the thrust surface is easily caused.

SUMMERY OF THE UTILITY MODEL

This section provides a general summary of the disclosure, and is not a comprehensive disclosure of its full scope or all of its features.

An object of the utility model is to provide a scroll compressor, this scroll compressor has overcome the above-mentioned defect among the prior art.

In one form, the present invention relates to a scroll compressor comprising: a fixed scroll including a fixed scroll end plate, a fixed spiral wrap extending from one side of the fixed scroll end plate, and a discharge port provided in the fixed scroll end plate; an orbiting scroll including an orbiting scroll end plate, an orbiting spiral wrap extending from one side of the driven scroll end plate, and a boss portion protruding from the driven scroll end plate on a side opposite to the orbiting spiral wrap, the orbiting spiral wrap and the fixed spiral wrap being engaged in a meshing manner, thereby generating a fluid chamber for compressing a working fluid; a bearing assembly upon which the orbiting scroll end plate is slidably supported, the bearing assembly and orbiting scroll end plate each having a thrust surface in sliding contact with each other; and the driving assembly comprises a shaft for driving the hub, wherein an oil supply channel is arranged on the hub, so that lubricating oil in the hub is sprayed to the thrust surface through the oil supply channel.

In some forms, an oil passage for supplying lubricating oil into the hub portion is provided in the shaft.

In some forms, the oil supply passage is disposed adjacent the orbiting scroll end plate.

In some forms, the oil supply passage is plural and provided on the hub in a circumferential direction, the plural oil supply passages having the same diameter or different diameters from each other.

In some forms a throttle is provided in the oil supply passage, and a through oil passage is provided in the throttle, through which lubricating oil is splashed to the thrust surface.

In some forms the restriction device is a restriction screw, and the oil supply passage has a threaded bore disposed therein for engagement with the restriction screw.

In some forms the oil supply passage includes a beveled section that directs lubricating oil to the thrust surface.

In some forms the scroll compressor further comprises an oil slinger disposed between the hub and the bearing assembly, the oil slinger being located axially below the oil supply passage and being secured to the hub, the oil slinger having a ramped leading face which directs lubricating oil towards the thrust face.

In some forms the scroll compressor further comprises an intermediate member disposed between the hub and the support assembly, wherein the intermediate member has a top portion proximate the orbiting scroll end plate, and the oil supply passage is disposed to correspond to a region between the top portion of the intermediate member and the orbiting scroll end plate.

In some forms the top of the intermediate member has an inclined surface directing lubricant towards the thrust surface and/or the top of the intermediate member is provided with a plurality of involute oil grooves directing lubricant towards the thrust surface.

In some forms the scroll compressor further comprises: a driving bush fitted radially outside the eccentric crank pin of the shaft; and a balance weight component comprising a mounting base connected to the drive bushing or shaft and a weight extending axially from the mounting base; wherein the weight constitutes the intermediate member.

According to the scroll compressor, the oil supply channel is utilized to perform forced splash lubrication on the thrust surface, so that early wear failure of the thrust surface caused by transient oil shortage can be effectively reduced when the scroll compressor is started; the condition that oil stirring splashing lubrication is insufficient when the scroll compressor runs at a low speed can also be improved. The utility model discloses especially, be fit for taking the high-speed variable frequency compressor of balance weight part, can show through splash lubrication and improve its thrust surface lubrication state. The axial position of the oil supply channel of the utility model needs to be close to the thrust surface as much as possible.

Further areas of applicability will become apparent from the description provided herein. The description and specific examples in this summary are intended for purposes of illustration only and are not intended to limit the scope of the present disclosure.

Drawings

The drawings described herein are for illustrative purposes only of selected embodiments and not all possible implementations, and are not intended to limit the scope of the present disclosure.

FIG. 1 is a cross-sectional view of a prior art scroll compressor;

fig. 2 shows a partial cross-sectional view of a boss portion of an orbiting scroll provided with an oil supply passage of a scroll compressor and its peripheral parts according to the present invention;

FIG. 3 shows a top cross-sectional view taken along the axis of the oil supply passage shown in FIG. 2;

FIG. 4 is a partial cross-sectional view of the hub portion of the orbiting scroll shown in FIG. 2 with a throttle screw disposed in the oil supply passage;

FIG. 5 is an enlarged partial cross-sectional view of the oil supply passage shown in FIG. 4 provided with a throttle screw;

fig. 6 is an assembled perspective view showing an oil slinger mounted to a hub of an orbiting scroll of a scroll compressor according to the present invention;

FIG. 7 illustrates an exploded perspective view of the oil slinger of FIG. 6;

FIG. 8 shows a partial cross-sectional view of the oil slinger of FIG. 6 mounted to the hub of the orbiting scroll member shown in FIG. 2;

FIG. 9 illustrates an enlarged partial cross-sectional view of the hub portion of FIG. 8 with the oil slinger mounted thereto;

FIG. 10 shows a perspective view of a balance weight component with an inclined surface on top;

FIG. 11 is a partial cross-sectional view of the balance weight member of FIG. 10 mounted about a hub portion;

FIG. 12 shows a perspective view of a balance weight component with an involute oil groove disposed at the top;

FIG. 13 shows a top view of a balance weight component with an involute oil groove disposed at the top;

corresponding reference characters indicate corresponding parts throughout the several views of the drawings.

Detailed Description

Exemplary embodiments will now be described more fully with reference to the accompanying drawings.

The exemplary embodiments are provided so that this disclosure will be thorough and will fully convey the scope to those skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and that should not be construed as limiting the scope of the disclosure. In some exemplary embodiments, well-known methods, well-known device structures, and well-known technologies are not described in detail.

When an element or layer is referred to as being "on," "engaged to," "connected to" or "coupled to" another element or layer, the element or layer may be directly on, engaged, connected or coupled to the other element or layer or intervening elements or layers may be present. In contrast, when an element is referred to as being "directly on," "directly engaged to," "directly connected to" or "directly coupled to" another element or layer, there are no intervening elements or layers present. Other terms used to describe the relationship between elements (e.g., "between … …" and "directly between … …", "adjacent" and "directly adjacent", etc.) should be interpreted in a similar manner. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

Although the terms first, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by these terms. These terms may be only used to distinguish one element, component, region, layer or section from another region, layer or section. Terms such as "first," "second," and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.

The principles of the present disclosure are suitable for incorporation in many different types of equipment, such as scroll compressors and rotary compressors, including hermetic machines, open drive machines, and non-hermetic machines. For purposes of illustration, the scroll compressor 10 is shown as a low side hermetic scroll refrigeration compressor (i.e., a compressor in which the motor is disposed in the suction pressure region of the compressor), as shown in FIG. 1. It will be understood that the principles of the present disclosure also apply to high side compressors (i.e., compressors in which the motor is disposed in the discharge pressure region of the compressor).

FIG. 1 illustrates a prior art scroll compressor 10. The scroll compressor 10 may include, among other things, a sealed housing assembly 12, a bearing housing assembly 14, a drive assembly 16, and a compression mechanism 18. The bearing block assembly 14, the drive assembly 16, and the compression mechanism 18 may be housed in the housing assembly 12.

The housing assembly 12 may generally form a compressor housing and may include a cylindrical shell 26, an end cover 28 at an upper end of the cylindrical shell 26, a transversely extending partition 30, and a bottom cover (not shown) at a lower end of the cylindrical shell 26 forming a base of the vertical scroll compressor 10. The end cap 28 and the partition 30 may generally define a discharge chamber 34. The housing 26, the partition 30, and the bottom cover may generally define a suction chamber 40. The suction inlet fitting 38 may be attached to the cylindrical housing 26 of the housing assembly 12 and may be in communication with the suction chamber 40. Partition 30 may include a discharge passage 42, with compression mechanism 18 communicating with discharge chamber 34 via discharge passage 42.

The bearing housing assembly 14 may be attached to the housing assembly 12 (specifically the housing 26 in the figures) and may include a main bearing housing 44 and a bearing 46 housed in the main bearing housing 44.

The drive assembly 16 may include a stator (not shown), a rotor (not shown), and a shaft 54. The stator may be press-fit into the housing assembly 12 (specifically housing 26 in the figures). The rotor may be attached to the shaft 54 and may rotatably drive the shaft 54. Shaft 54 may be rotatably supported near an upper end by main bearing housing 44 via bearing 46. Lubricating oil is contained in the bottom cover. A through oil passage 52 (shown in fig. 2) is provided in the shaft 54 to suck the lubricating oil contained in the base portion from the lower end of the shaft 54 to the upper end of the shaft 54 via the oil passage 52.

Compression mechanism 18 may generally include an orbiting scroll 58 and a non-orbiting scroll 60. The orbiting scroll 58 may include an orbiting scroll end plate 62, an orbiting spiral wrap 64 extending upwardly from the orbiting scroll end plate 62. Non-orbiting scroll member 60 may include a non-orbiting scroll end plate 74 and a non-orbiting spiral wrap 76 projecting downwardly from one side of non-orbiting scroll end plate 74. The fixed spiral wrap 76 of the fixed scroll member 60 may meshingly engage the movable spiral wrap 64 of the movable scroll member 58 to create a series of moving fluid pockets. Throughout the compression cycle of compression mechanism 18, the fluid pockets defined by orbiting and stationary spiral wraps 64, 76 may decrease in volume as one moves from a radially outer position (at a suction pressure) through a radially intermediate position (at an intermediate pressure) to a radially inner position (at a discharge pressure), thereby compressing the working fluid. The fixed scroll 60 includes a discharge port 77 at the center of the fixed spiral wrap 76 for discharging the compressed working fluid.

An orbiting scroll end plate 62 of the driven scroll member 58 may have a cylindrical hub 68 projecting downwardly therefrom. The cylindrical hub 68 may have a drive bushing 70 rotatably disposed therein the cylindrical hub 68. The shaft 54 may include an eccentric crank pin 56 (also referred to as an eccentric). Crank pin 56 is drivingly engaged in drive bushing 70. That is, the drive bushing 70 is fitted radially outward of the eccentric crank pin 56 of the shaft 54.

Crank pin 56 may drivingly engage drive bushing 70 to provide a radially compliant drive. Thus, the driving force generated by the driving unit 16 is transmitted to the driving bush 70 via the crank pin 56 of the shaft 54, and then transmitted to the cylindrical boss 68 of the orbiting scroll 58 via the driving bush 70, thereby orbiting the orbiting scroll 58.

As shown in fig. 2, the thrust assembly 48 is separately formed and disposed between the main bearing housing 44 and the orbiting scroll 58. Thrust assembly 48 and main bearing housing 44 constitute the bearing assembly described herein. It should be understood that thrust assembly 48 may be formed as one piece with main bearing housing 44, i.e., the bearing assembly is one piece. In the case where the thrust assembly 48 is not provided, then the main bearing housing 44 constitutes a bearing assembly (FIG. 1).

When the scroll compressor 10 is in operation, the orbiting scroll member 58 orbits relative to the fixed scroll member 60 upon actuation of the shaft 54. At the same time, the orbiting scroll end plate 62 of the orbiting scroll 58 slides over the thrust assembly 48. Thus, orbiting scroll end plate 62 and thrust assembly 48 include thrust surfaces 63, 49, respectively, in sliding contact with each other.

In the illustrated example, a balance weight member 72 is also disposed between the hub 68 of the orbiting scroll 58 and the thrust assembly 48. When the scroll compressor 10 is operating, lubricating oil flows under centrifugal force up the top surface of the eccentric crank pin 56 via the oil passage 52 in the shaft 54, then flows down the outer peripheral surface of the eccentric crank pin 56 to lubricate the drive bushing 70, and then accumulates in the bottom of the main bearing housing 44 to form an oil sump 47 (FIG. 1). Hub 68 of orbiting scroll 58 (along with balance weight member 72 in this example) agitates the oil pool, causing oil to splash between thrust assembly 48 and orbiting scroll end plate 62 of orbiting scroll 58, thereby lubricating the thrust surfaces of thrust assembly 48 and orbiting scroll end plate 62. In this case, the oil level of the oil reservoir 47 needs to reach a height at which the boss portion 68 or the balance weight member 72 can be agitated. Thus, after the scroll compressor is started, it takes a period of time to collect the lubricant such that the oil level of oil sump 47 reaches a sufficient level to be able to be agitated by hub 68 or balance weight member 72 and such that the agitated lubricant is able to splash against the thrust surfaces of orbiting scroll end plate 62 and thrust assembly 48.

First embodiment

As shown in fig. 2 and 3, at least one oil supply passage 66 is provided in a hub portion 68 of the orbiting scroll 58. Preferably, two or more oil supply passages 66 are provided. For example, the oil supply passage 66 is provided on a side of a boss portion 68 of the orbiting scroll 58 close to the orbiting scroll end plate 62 of the orbiting scroll 58. As shown by arrows in fig. 2 and 3, the lubricating oil is pumped from the base of the scroll compressor 10 to the top of the shaft 54 (between the end surface of the shaft 54 and the movable scroll end plate 62 of the movable scroll 58) through the oil passage 52 of the shaft 54, and under the pressure of the oil and the centrifugal force generated by the rotation of the components, the lubricating oil inside the hub 68 is thrown out of the hub 68 through the oil supply passage 66 and splashed to the thrust surface between the movable scroll end plate 62 of the movable scroll 58 and the thrust assembly 48.

By providing the oil supply passage 66, oil can be sprayed at the thrust face significantly faster than by scraping a pool of a predetermined height of oil at the bottom of the main bearing housing by the hub portion 68 and/or the balance weight member 72. This is so because there is no need to wait for the scroll compressor 10 to operate for a period of time such that the level of liquid in the oil sump formed at the bottom of main bearing housing 44 reaches a certain height before the thrust surfaces can be lubricated by the splash of lubricating oil. Therefore, the lubricating oil is supplied to the thrust surface through the oil supply passage 66 as quickly as possible, thereby avoiding causing early wear failure of the thrust surface. Even if the scroll compressor 10 is operating at a low speed, the lubricant is supplied to the thrust surface through the oil supply passage 66 as quickly as possible, thereby improving the situation where the agitation speed of the hub portion 68 and/or the balance weight member 72 with respect to the lubricant is too low to splash enough lubricant to the thrust surface.

At the same time, the lubricant sprayed via the oil supply passage 66 still flows back to the oil sump 47, and when the oil level reaches a certain level, the lubricant may be stirred by the boss portion 68 and/or the balance weight member 72 to splash against and lubricate the thrust surface. Thus, this arrangement does not interfere with the original system of agitating the lubricant through the hub portion 68 and/or the balance weight member 72 to splash against and lubricate the thrust surface.

To facilitate the splash of lubricant from the interior of the hub through oil supply passage 66 to the end plate outside the hub and the thrust surface of the thrust assembly, oil supply passage 66 may be disposed adjacent orbiting scroll end plate 62 of orbiting scroll member 58, i.e., adjacent orbiting scroll end plate 62 of orbiting scroll member 58 and the thrust surface of thrust assembly 48. Also, as shown in fig. 3, the oil supply passage 66 extends in the radial direction. Alternatively, one skilled in the art may contemplate that the oil supply passage 66 may extend in other directions, such as being offset in the direction of rotation or axially inclined, to facilitate centrifugal force to throw oil to the thrust surface.

Further, in order to prevent the lubricating oil led out from the oil supply passage 66 from being blocked by the balance weight member 72 and failing to reach the thrust surface, the axial position of the oil supply passage 66 may be set higher than the top of the balance weight member 72.

The amount of oil sprayed through the oil feed passage 66 can be varied by the size of the diameter of the oil feed passage 66. The larger the diameter of the oil supply passage 66, the more the amount of oil injected, and vice versa.

As shown in fig. 4 and 5, a throttle device may be provided in the oil supply passage 66 and an oil passage hole may be provided in the throttle device to control the amount of oil injected into the oil supply passage 66. The throttle device is, for example, a throttle screw 80, and a threaded hole 78 is provided in the oil supply passage 66. The threaded hole 78 is fitted with a throttle screw 80. An oil passage hole 82 that penetrates in the axial direction is provided in the center of the throttle screw 80. The amount of oil injected can be adjusted by changing the diameter of the oil passage hole 82 of the throttle screw 80. By using the throttle screw 80, the machining of the oil supply passage 66 and thus the movable scroll 58 can be simplified, and only the corresponding throttle screw 80 needs to be replaced depending on the type of compressor. When the oil supply passage 66 is machined in the boss portion 68, if the diameter of the oil supply passage 66 is too small, it is difficult to machine. By using the throttle screw 80, the difficulty of machining the small diameter oil supply passage 66 in the boss portion 68 can be solved well.

Preferably, in order to further improve the splashing effect of the lubricating oil, the structure of the oil supply passage 66 itself may be modified. For example, oil supply passage 66 may include a sloped section that splashes lubricant toward the thrust surfaces of orbiting scroll end plate 62 and thrust assembly 48.

Preferably, as shown in fig. 6-9, to better spray oil against the thrust surface and avoid excessive machining of the oil supply passage 66, an oil slinger 84 may be provided around the hub 68 radially outward of the oil supply passage 66. An oil slinger 84 is disposed between the hub 68 and the thrust assembly 48 and is secured to the hub 68 below the oil supply passage 66. As shown in fig. 6 and 7, oil slinger 84 may have a sloped guide surface 85 (i.e., a tapered frusto-conical surface) that guides lubricant toward the thrust surface of orbiting scroll end plate 62 and thrust assembly 48. The lubricating oil is directed to splash against the thrust surface by the inclined (or tapered) guide surface 85. Oil slinger 84 may be a circular ring formed by two semi-circular rings hinged or snap-fit together. The two semi-circular rings of oil slinger 84 are hinged or snap-fit together, such as by a pin, after being mounted on the hub 68 of the orbiting scroll member 58. The oil sprayed from the oil supply passage 66 is guided by the inclined (or tapered) guide surface 85 of the oil slinger 84, and the oil is sprayed to the thrust surface. Moreover, the substantially bowl-shaped oil slinger 84 may act as a small oil sump to facilitate more uniform slinging of oil against the thrust surface.

As shown in fig. 10 and 11, the balance weight component 72 includes a mounting base 73 connected to the drive bushing 70 (which may also be connected to the shaft 54) and a weight portion 75 extending axially from the mounting base 73. The counterweight extends axially between the hub 68 and the thrust assembly 48, forming an intermediate member disposed between the hub 68 of the orbiting scroll 58 and the thrust assembly 48. Balance weight member 72 also has a top portion 79 adjacent orbiting scroll end plate 62. The general configuration of the balance weight component 72 is substantially known in the art.

Alternatively, the top portion 79 of the balance weight member 72 may be provided with a sloped surface 86 for better oil spray to the thrust surface. The inclined surface 86 is located radially outward of the oil supply passage 66 around the hub portion 68. The oil supply passage 66 is provided to correspond to the area between the tip portion 79 of the balance weight member 72 and the orbiting scroll end plate 62, so that the oil splashed from the oil supply passage 66 is guided to be splashed to the thrust surface by the inclined surface 86 of the tip portion 79 of the balance weight member 72. Also, the inclined surface 86 may prevent the oil supply passage 66 from being blocked by the counterweight member 72 due to the up-and-down shaking.

Alternatively, as shown in fig. 12 and 13, a plurality of involute oil grooves 88 may be provided on the top portion 79 of the balance weight member 72. The use of the involute oil groove 88 more effectively directs the lubrication oil toward the thrust surfaces of the end plate 68 and thrust assembly 48.

(1) The utility model utilizes the oil supply channel to carry out forced splash lubrication on the thrust surface, which can effectively reduce the early wear failure of the thrust surface caused by transient oil shortage when the scroll compressor is started; the condition that oil stirring splashing lubrication is insufficient when the scroll compressor runs at a low speed can also be improved.

(2) The utility model discloses especially, be fit for taking the high-speed variable frequency compressor of balance weight part, can show through splash lubrication and improve its thrust surface lubrication state.

The foregoing description of embodiments has been presented for purposes of illustration and description. These descriptions are not intended to be exhaustive or to limit the disclosure. Individual elements or features of a particular embodiment are generally not limited to that particular embodiment, but, where applicable, are interchangeable and can be used in a selected embodiment, even if not specifically shown or described. The various elements or features of a particular embodiment may also be varied in many ways. Such variations are not to be regarded as a departure from the disclosure, and all such modifications are intended to be included within the scope of the disclosure.

Claims

1. A scroll compressor, comprising:

a fixed scroll including a fixed scroll end plate, a fixed spiral wrap extending from one side of the fixed scroll end plate, and a discharge port provided in the fixed scroll end plate;

an orbiting scroll including an orbiting scroll end plate, an orbiting spiral wrap extending from one side of the orbiting scroll end plate, and a boss portion protruding from a side of the orbiting scroll end plate opposite to the orbiting spiral wrap, the orbiting spiral wrap meshingly engaged with the fixed spiral wrap to thereby create a fluid pocket for compressing a working fluid;

a bearing assembly on which said orbiting scroll end plate is slidably supported, said bearing assembly and said orbiting scroll end plate each having a thrust surface in sliding contact with each other; and

a drive assembly including a shaft to drive the hub,

the hub is provided with an oil supply channel, and lubricating oil in the hub is sprayed to the thrust surface through the oil supply channel.

2. The scroll compressor of claim 1, wherein an oil passage is provided in the shaft for supplying lubricating oil into the hub portion.

3. The scroll compressor of claim 1, wherein the oil supply passage is disposed adjacent the orbiting scroll end plate.

4. The scroll compressor of claim 3, wherein the oil supply passage is plural and provided on the hub in a circumferential direction, the plural oil supply passages having the same diameter or different diameters from each other.

5. The scroll compressor of claim 1, wherein a throttle device is provided in the oil supply passage, wherein an oil through hole is provided in the throttle device, and wherein the lubricating oil is splashed to the thrust surface via the oil through hole.

6. The scroll compressor of claim 5, wherein the throttling device is a throttle screw, and the oil supply passage has a threaded hole disposed therein that engages the throttle screw.

7. The scroll compressor of claim 1, wherein the oil supply passage includes a sloped section that directs the lubrication oil to the thrust surface.

8. The scroll compressor of claim 1, further comprising an oil slinger disposed between the hub and the bearing assembly, the oil slinger located axially below the oil supply passage and secured to the hub, the oil slinger having a sloped leading face that directs lubricating oil toward the thrust face.

9. The scroll compressor of claim 1, further comprising an intermediate member disposed between the hub portion and the bearing assembly, wherein the intermediate member has a top portion proximate the orbiting scroll end plate, and wherein the oil supply passage is disposed to correspond to a region between the top portion of the intermediate member and the orbiting scroll end plate.

10. The scroll compressor of claim 9, wherein the top portion of the intermediate member has an inclined surface that directs lubricant toward the thrust surface, and/or wherein the top portion of the intermediate member is provided with a plurality of involute oil grooves that direct lubricant toward the thrust surface.

11. The scroll compressor of claim 9 or 10, further comprising:

a drive bushing fitted radially outward of an eccentric crank pin of the shaft; and

a balance weight component including a mounting base connected to the drive bushing or the shaft and a weight extending axially from the mounting base;

wherein the weight portion constitutes the intermediate member.