Scroll compressor

Abstract

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 orbiting scroll end plate, and a hub portion protruding from the other side of the orbiting scroll end plate opposite the orbiting spiral wrap, the orbiting spiral wrap being engaged with the fixed spiral wrap in a meshing manner to generate a fluid chamber for compressing a working fluid; a bearing assembly on which the orbiting scroll end plate is slidingly supported, the bearing assembly and the orbiting scroll end plate each having a thrust face in sliding contact with each other; and a drive assembly including a shaft to drive the hub portion, wherein an oil supply passage is provided on the hub portion such that lubricating oil within the hub portion is splashed to the thrust face via the oil supply passage.

Description

TECHNICAL FIELD

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

[0002] This section provides background information to the disclosure which is not necessarily prior art.

[0003] In the operation of a scroll compressor, in order to ensure the sealing of the fluid chamber and thus the effective compression of the working fluid, a relatively large axial load needs to be applied. The axial load acting on the scroll member is ultimately borne by the main bearing seat or the thrust assembly provided between the scroll member and the main bearing seat. Therefore, the thrust surface between the scroll member and the main bearing seat or the thrust assembly needs to be well lubricated.

[0004] Whether the scroll compressor is provided with a main bearing seat or additionally provided with a thrust assembly, the rotation of the orbiting scroll member is used to stir the lubricating oil in the oil pool formed at the bottom of the main bearing seat, so that the oil is splashed to and lubricates the thrust surface between the scroll member and the main bearing seat or the thrust surface between the scroll member and the thrust assembly.

[0005] In the case of splashing lubrication by the above-mentioned method, when the rotational speed of the scroll compressor is low, the amount of oil stirred is relatively small, which causes insufficient lubrication of the thrust surface. In the case of providing a thrust assembly, the radially extending surface of the thrust assembly will block part of the splashed oil, further reducing the amount of lubrication of the thrust surface. In addition, in the case where a drive bushing is provided outside the eccentric crank pin provided at the top end of the shaft of the drive assembly of the scroll compressor and a balance weight component is provided on the drive bushing, the balance weight component can also block part of the oil splashing area, which is more detrimental to splashing lubrication. In addition, after the compressor is stopped, the above-mentioned oil pool will flow back to the base of the scroll compressor. Therefore, when the scroll compressor is started again, it takes a certain period of time to raise the oil level in the oil pool to the height at which the hub of the orbiting scroll member or the balance weight component can stir the oil, and during this period of time, the lubrication condition of the thrust surface is poor, which can easily cause early wear and failure of the thrust surface. SUMMARY

[0006] This section provides a general summary of the disclosure, but not a comprehensive disclosure of the full scope or all the features of the disclosure.

[0007] The purpose of the present invention is to provide a scroll compressor which overcomes the above-mentioned defects in the prior art.

[0008] In one form, the present application relates to a scroll compressor, comprising: a fixed scroll member 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 member including an orbiting scroll end plate, an orbiting spiral wrap extending from one side of the orbiting scroll end plate, and a hub portion protruding from the opposite side of the orbiting scroll end plate from the orbiting spiral wrap, the orbiting spiral wrap being engaged with the fixed spiral wrap in a meshing manner to create a fluid pocket for compressing a working fluid; a bearing assembly on which the orbiting scroll end plate is slidingly supported, the bearing assembly and the orbiting scroll end plate each having a thrust face in sliding contact with each other; and a drive assembly including a shaft to drive the hub portion, wherein an oil supply passage is provided on the hub portion such that lubricating oil within the hub portion is splashed to the thrust face via the oil supply passage.

[0009] In some forms, an oil passage is provided in the shaft for supplying lubricating oil into the hub portion.

[0010] In some forms, the oil supply passage is provided adjacent to the orbiting scroll end plate.

[0011] In some forms, the oil supply passage is provided in a plurality and in a circumferential direction on the hub portion, the plurality of oil supply passages having the same diameter or different diameters from each other.

[0012] In some forms, a throttle device is provided in the oil supply passage, the throttle device having a through oil passage through which lubricating oil is splashed to the thrust face.

[0013] In some forms, the throttle device is a throttle screw, and a threaded hole engaging with the throttle screw is provided in the oil supply passage.

[0014] In some forms, the oil supply passage includes an inclined section that guides lubricating oil to the thrust face.

[0015] In some forms, the scroll compressor further includes a slinger ring provided between the hub portion and the bearing assembly, the slinger ring being located axially below the oil supply passage and fixed to the hub portion, the slinger ring having an inclined guide surface that guides lubricating oil toward the thrust face.

[0016] In some forms, the scroll compressor further includes an intermediate member provided between the hub portion and the bearing assembly, wherein the intermediate member has a top portion proximate to the orbiting scroll end plate, and the oil supply passage is provided corresponding to a region between the top portion of the intermediate member and the orbiting scroll end plate.

[0017] In some forms, the top portion of the intermediate member has an inclined surface that guides lubricating oil toward the thrust face, and / or a plurality of involute oil grooves that guide lubricating oil toward the thrust face are provided on the top portion of the intermediate member.

[0018] In some forms, the scroll compressor further comprises a drive bushing fitted radially outward of the eccentric crank pin of the shaft, and a balance weight component comprising a mounting base connected to the drive bushing or the shaft, and a weight portion extending axially from the mounting base; wherein the weight portion constitutes the intermediate member.

[0019] The scroll compressor according to the present application can effectively reduce the early wear failure of the thrust surface caused by the temporary oil shortage during the start of the scroll compressor, and can improve the insufficient oil splashing and splattering lubrication during the low-speed operation of the scroll compressor. The present application is particularly suitable for high-speed variable frequency compressors with a balance weight component, and the lubrication state of the thrust surface can be significantly improved by splashing lubrication. The axial position of the oil supply channel of the present application should be as close to the thrust surface as possible.

[0020] Other areas of application will become apparent from the description provided herein. The description and specific examples in this summary are intended only to illustrate certain embodiments and are not intended to limit the scope of the disclosure. BRIEF DESCRIPTION OF DRAWINGS

[0021] The drawings described herein are for purposes of illustration only and are not intended to limit the scope of the present disclosure.

[0022] Figure 1 is a cross-sectional view of a scroll compressor of the prior art;

[0023] Figure 2 shows a partial cross-sectional view of the hub portion of the orbiting scroll and its peripheral components of the scroll compressor according to the present application provided with an oil supply channel;

[0024] Figure 3 shows a partial cross-sectional view of the hub portion of the orbiting scroll provided with a throttle screw in the oil supply channel; Figure 2 shows a top cross-sectional view taken along the axis of the oil supply channel;

[0025] Figure 4 shows a partial cross-sectional view of the hub portion of the orbiting scroll provided with a throttle screw in the oil supply channel; Figure 2

[0026] Figure 5 shows a partial cross-sectional view of the hub portion of the orbiting scroll provided with a throttle screw in the oil supply channel; Figure 4

[0027] Figure 6 shows an assembled perspective view of the oil flinger ring mounted to the hub portion of the orbiting scroll of the scroll compressor according to the present application;

[0028] Figure 7 shows an exploded perspective view of the oil flinger ring of Figure 6 ;

[0029] ​​Figure 8 It shows Figure 6 The oil slinger ring is installed at Figure 2 A partial cross-sectional view of the hub of the moving scroll component is shown.

[0030] Figure 9 It shows Figure 8 A partially enlarged cross-sectional view of the hub with the oil slinger ring installed.

[0031] Figure 10 A perspective view of a counterweight component with an inclined surface at the top is shown;

[0032] Figure 11 yes Figure 10 The diagram shows a partial cross-sectional view of the counterweight component installed around the hub.

[0033] Figure 12 A perspective view of a counterweight component with an involute oil groove at the top is shown;

[0034] Figure 13 A top view of a counterweight component with an involute oil groove at the top is shown;

[0035] Throughout the various views in the accompanying drawings, corresponding reference numerals indicate the corresponding components. Detailed Implementation

[0036] Exemplary embodiments will now be described more fully with reference to the accompanying drawings.

[0037] 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, such as examples of particular components, apparatuses, and methods, are set forth to provide a thorough understanding of embodiments of this disclosure. It will be apparent to those skilled in the art that specific details are not required, that exemplary embodiments may be implemented in many different forms, and should not be construed as limiting the scope of this disclosure. In some exemplary embodiments, well-known methods, well-known apparatus structures, and well-known techniques are not described in detail.

[0038] When an element or layer is referred to as “located on another element or layer,” “joined to,” “connected to,” or “linked to” another element or layer, the element or layer may be directly located on, joined to, connected to, or linked to the other element or layer, or there may be intermediate elements or layers. Conversely, when an element is referred to as “directly located on another element or layer,” “directly joined to,” “directly connected to,” or “directly linked to” another element or layer, there are no intermediate elements or layers. Other terms used to describe relationships between elements (e.g., “located between” vs. “directly located between,” “adjacent” vs. “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.

[0039] Although the terms first, second, third, etc., may be used herein to describe various elements, components, regions, layers, and / or segments, these elements, components, regions, layers, and / or segments should not be limited by these terms. These terms may be used only to distinguish one element, component, region, layer, or segment from another region, layer, or segment. Unless the context clearly indicates otherwise, terms such as “first,” “second,” and other numerical terms used herein do not imply order or sequence. Therefore, the first element, component, region, layer, or segment discussed below may be referred to as a second element, component, region, layer, or segment without departing from the teachings of the exemplary embodiments.

[0040] The principles of this disclosure are adaptable to many different types of equipment, such as scroll compressors and rotary compressors, including hermetic machines, open-drive machines, and hermetic machines. For illustrative purposes, scroll compressor 10 is shown as a low-pressure-side hermetic scroll refrigeration compressor (i.e., a compressor in which the motor is located in the suction pressure region of the compressor), such as... Figure 1 As shown in the diagram. It will be understood that the principles of this disclosure also apply to high-pressure side compressors (i.e., compressors in which the motor is located in the discharge pressure zone of the compressor).

[0041] Figure 1 A prior art scroll compressor 10 is shown. The scroll compressor 10 may include a hermetically sealed housing assembly 12, a bearing housing assembly 14, a drive assembly 16, and a compression mechanism 18, etc. The bearing housing assembly 14, the drive assembly 16, and the compression mechanism 18 may be housed within the housing assembly 12.

[0042] The shell assembly 12 can generally form a compressor housing and can 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 to form a base of the upright scroll compressor 10. The end cover 28 and the partition 30 can generally define a discharge chamber 34. The shell 26, the partition 30, and the bottom cover can generally define a suction chamber 40. A suction inlet fitting 38 can be attached to the cylindrical shell 26 of the shell assembly 12 and can be in communication with the suction chamber 40. The partition 30 can include a discharge passage 42 through which the compression mechanism 18 communicates with the discharge chamber 34.

[0043] The bearing bracket assembly 14 can be attached to the shell assembly 12 (specifically, the shell 26) and can include a main bearing bracket 44 and a bearing 46 housed in the main bearing bracket 44.

[0044] The drive assembly 16 can include a stator (not shown), a rotor (not shown), and a shaft 54. The stator can be press-fit into the shell assembly 12 (specifically, the shell 26). The rotor can be attached to the shaft 54 and can rotatably drive the shaft 54. The shaft 54 can be rotatably supported by the main bearing bracket 44 via the bearing 46 near the upper end. Lubricating oil is housed in the bottom cover. A through oil passage 52 (as shown) is provided in the shaft 54 to draw the lubricating oil housed in the base from the lower end of the shaft 54 to the upper end of the shaft 54 via the oil passage 52. Figure 2

[0045] The compression mechanism 18 can generally include an orbiting scroll 58 and a non-orbiting scroll 60. The orbiting scroll 58 can include an orbiting scroll end plate 62, an orbiting scroll spiral wrap 64 extending upwardly from the orbiting scroll end plate 62. The non-orbiting scroll 60 can include a non-orbiting scroll end plate 74 and a non-orbiting scroll spiral wrap 76 projecting downwardly from one side of the non-orbiting scroll end plate 74. The non-orbiting scroll spiral wrap 76 of the non-orbiting scroll 60 can meshingly engage the orbiting scroll spiral wrap 64 of the orbiting scroll 58 to create a series of moving fluid cavities. The fluid cavities defined by the orbiting scroll spiral wrap 64, the non-orbiting scroll spiral wrap 76 can decrease in volume as they move from a radially outer position (at suction pressure) through a radially intermediate position (at intermediate pressure) to a radially inner position (at discharge pressure) to thereby compress working fluid throughout a compression cycle of the compression mechanism 18. The non-orbiting scroll 60 includes a discharge port 77 at a center of the non-orbiting scroll spiral wrap 76 for discharging the compressed working fluid.

[0046] ​The driven scroll end plate 62 of the driven scroll member 58 may have a downwardly projecting cylindrical hub 68. The cylindrical hub 68 may have a drive bushing 70 rotatably disposed within the cylindrical hub 68. The shaft 54 ​​may include an eccentric crank pin 56 (also referred to as an eccentric portion). The crank pin 56 is driven into the drive bushing 70. That is, the drive bushing 70 is driven radially outward of the eccentric crank pin 56 of the shaft 54.

[0047] The crank pin 56 can engage the drive bushing 70 in a transmission manner to provide radial flexible transmission. Thus, the driving force generated by the drive assembly 16 is transmitted via the crank pin 56 of the shaft 54 ​​to the drive bushing 70, and then from the drive bushing 70 to the cylindrical hub 68 of the moving scroll member 58, thereby driving the moving scroll member 58 to rotate.

[0048] like Figure 2 As shown, the thrust assembly 48 is formed separately and disposed between the main bearing housing 44 and the moving scroll member 58. The thrust assembly 48 and the main bearing housing 44 constitute the support assembly described in this application. It should be understood that the thrust assembly 48 can be formed integrally with the main bearing housing 44, that is, the support assembly is integral. Without the thrust assembly 48, the main bearing housing 44 constitutes the support assembly (…). Figure 1 ).

[0049] When the scroll compressor 10 is running, the moving scroll member 58 revolves relative to the stationary scroll member 60 under the drive of the shaft 54. At the same time, the moving scroll end plate 62 of the moving scroll member 58 slides on the thrust assembly 48. Therefore, the moving scroll end plate 62 and the thrust assembly 48 each include thrust surfaces 63 and 49 that slide in contact with each other.

[0050] In the illustrated example, a counterweight 72 is also provided between the hub 68 of the moving scroll 58 and the thrust assembly 48. During operation of the scroll compressor 10, lubricating oil flows upward through the oil passage 52 in the shaft 54 ​​to the top surface of the eccentric crank pin 56 under centrifugal force, then flows downward along the outer circumference of the eccentric crank pin 56 to lubricate the drive bushing 70, and then accumulates at the bottom of the main bearing housing 44 to form an oil sump 47. Figure 1The hub 68 of the moving scroll 58 (together with the counterweight 72 in this example) agitates the lubricating oil in the oil sump, causing the lubricating oil to splash between the thrust assembly 48 and the moving scroll end plate 62 of the moving scroll 58, thereby lubricating the thrust surfaces of the thrust assembly 48 and the moving scroll end plate 62. In this case, the oil level in the oil sump 47 needs to reach a height that the hub 68 or the counterweight 72 can agitate. Therefore, after the scroll compressor starts, a period of time is required for the lubricating oil to accumulate so that the oil level in the oil sump 47 reaches a sufficient height to be agitated by the hub 68 or the counterweight 72 and to allow the agitated lubricating oil to splash onto the moving scroll end plate 62 and the thrust surfaces of the thrust assembly 48.

[0051] First Implementation Method

[0052] like Figure 2 and Figure 3 As shown, at least one oil supply channel 66 is provided on the hub 68 of the moving scroll member 58. Preferably, two or more oil supply channels 66 are provided. For example, the oil supply channel 66 is provided on the side of the hub 68 of the moving scroll member 58 near the moving scroll end plate 62 of the moving scroll member 58. Figure 2 and Figure 3 As indicated by the arrow, lubricating oil is drawn from the base of the scroll compressor 10 through the oil passage 52 of the shaft 54 ​​to the top of the shaft 54 ​​(between the end face of the shaft 54 ​​and the moving scroll end plate 62 of the moving scroll component 58). Under the pressure of the oil and the centrifugal force generated by the rotation of each component, the lubricating oil inside the hub 68 is thrown out to the outside of the hub 68 through the oil supply passage 66 and splashed onto the moving scroll end plate 62 of the moving scroll component 58 and the thrust surface of the thrust assembly 48.

[0053] Compared to the oil sump at the bottom of the main bearing housing, which accumulates to a predetermined height by agitation of the hub 68 and / or the counterweight 72, the oil supply channel 66 allows for significantly faster spraying of lubricating oil onto the thrust surface. This is because it eliminates the need to wait for the scroll compressor 10 to run for a period of time until the oil level in the sump formed at the bottom of the main bearing housing 44 reaches a certain height before the thrust surface can be lubricated by splashing lubricating oil. Therefore, lubricating oil is supplied to the thrust surface as quickly as possible through the oil supply channel 66, thereby preventing premature wear failure of the thrust surface. Even when the scroll compressor 10 is running at low speed, lubricating oil can be supplied to the thrust surface quickly through the oil supply channel 66, thus improving the situation where the agitation speed of the lubricating oil by the hub 68 and / or the counterweight 72 is too low to spray sufficient lubricating oil onto the thrust surface.

[0054] Meanwhile, the lubricating oil splashed via the oil supply passage 66 can still flow back to the oil pool 47, and when the oil level reaches a certain height, the lubricating oil can still be splashed to the thrust face by the hub 68 and / or the balance weight member 72 and lubricate the thrust face. Therefore, the arrangement does not affect the original system of splashing the lubricating oil to the thrust face by the hub 68 and / or the balance weight member 72 and lubricating the thrust face.

[0055] In order to facilitate splashing of the lubricating oil inside the hub to the end plate and the thrust face of the thrust assembly outside the hub via the oil supply passage 66, the oil supply passage 66 can be arranged adjacent to the orbiting scroll end plate 62 of the orbiting scroll 58, i.e. adjacent to the orbiting scroll end plate 62 of the orbiting scroll 58 and the thrust face of the thrust assembly 48. Also, as shown in Figure 3 the oil supply passage 66 extends in the radial direction. Alternatively, those skilled in the art can conceive that the oil supply passage 66 can extend in other directions, such as deflecting in the rotational direction or tilting in the axial direction, to facilitate the centrifugal force to throw the oil to the thrust face.

[0056] In addition, 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 face, the axial position of the oil supply passage 66 can be arranged to be higher than the top of the balance weight member 72.

[0057] The amount of oil splashed via the oil supply passage 66 can be changed by the size of the diameter of the oil supply passage 66. The larger the diameter of the oil supply passage 66, the more the amount of oil splashed, and vice versa.

[0058] In addition, as shown in Figure 4 and Figure 5 in order to control the amount of oil splashed by the oil supply passage 66, a throttling device can also be arranged in the oil supply passage 66, and a through oil hole is arranged in the throttling device. For example, the throttling device is a throttling screw 80, and a threaded hole 78 is arranged in the oil supply passage 66. The threaded hole 78 cooperates with the throttling screw 80. An axial through oil hole 82 is arranged in the center of the throttling screw 80. The amount of oil splashed can be adjusted by changing the diameter of the through oil hole 82 of the throttling screw 80. By using the throttling screw 80, the machining of the oil supply passage 66, and thus the machining of the orbiting scroll 58, can be simplified, and only the corresponding throttling screw 80 needs to be replaced according to different types of compressors. In addition, when machining the oil supply passage 66 on the hub 68, it is difficult to machine a small-diameter oil supply passage 66. By using the throttling screw 80, the problem of machining a small-diameter oil supply passage 66 on the hub 68 can be better solved.

[0059] Preferably, to further improve the splashing effect of the lubricating oil, the structure of the oil supply passage 66 itself can be modified. For example, the oil supply passage 66 can include an inclined section that splashes the lubricating oil toward the thrust face of the thrust assembly 48 and the orbiting scroll end plate 62.

[0060] Preferably, as shown in Figures 6 to 9 order to better splash oil to the thrust face and to avoid excessive machining of the oil supply passage 66, an oil splatter ring 84 can be provided around the hub 68 radially outward of the oil supply passage 66. The oil splatter ring 84 is disposed between the hub 68 and the thrust assembly 48 and is fixed to the hub 68 below the oil supply passage 66. As shown in Figure 6 and Figure 7 the oil splatter ring 84 can have an inclined guide surface 85 (i.e., a tapered truncated inner conical surface) that directs the lubricating oil toward the thrust face of the thrust assembly 48 and the orbiting scroll end plate 62. The lubricating oil splashed from the oil supply passage 66 is guided by the inclined (or tapered) guide surface 85 of the oil splatter ring 84 to splash to the thrust face. The oil splatter ring 84 can be a circular ring formed by two semicircular rings hingedly or snap connected together. The two semicircular rings of the oil splatter ring 84 are hingedly or snap connected together after being mounted on the hub 68 of the orbiting scroll 58. The oil splashed from the oil supply passage 66 is guided by the inclined (or tapered) guide surface 85 of the oil splatter ring 84 to splash to the thrust face. Moreover, the generally bowl-shaped oil splatter ring 84 can function as a small oil pool to facilitate more uniform splashing of oil to the thrust face.

[0061] As shown in Figure 10 and Figure 11 the balance weight member 72 includes a mounting base 73 connected to the drive bushing 70 (and can also be connected to the shaft 54) and a weight portion 75 extending axially from the mounting base 73. The weight portion extends axially between the hub 68 and the thrust assembly 48 and constitutes an intermediate member disposed between the hub 68 of the orbiting scroll 58 and the thrust assembly 48. The balance weight member 72 also has a top portion 79 proximate the orbiting scroll end plate 62. The general configuration of the balance weight member 72 is generally known in the art.

[0062] Alternatively, to better splash oil to the thrust face, the top portion 79 of the balance weight member 72 can have an inclined surface 86. The inclined surface 86 is located radially outward of the oil supply passage 66 around the hub 68. The oil supply passage 66 is configured to correspond to the area between the top portion 79 of the balance weight member 72 and the orbiting scroll end plate 62 so that the inclined surface 86 of the top portion 79 of the balance weight member 72 guides the oil splashed from the oil supply passage 66 to splash to the thrust face. Moreover, the inclined surface 86 can also prevent the balance weight member 72 from blocking the oil supply passage 66 due to up and down movement.

[0063] Alternatively, asFigure 12 and Figure 13 As shown in FIG. 8, a plurality of involute oil grooves 88 can be provided on the top 79 of the balance weight member 72. The involute oil grooves 88 can more effectively direct the lubricating oil toward the end plate 68 and the thrust face of the thrust assembly 48.

[0064] (1) The present application uses the oil supply passage to forcibly splash lubricate the thrust face, which can effectively reduce the early wear failure of the thrust face caused by temporary oil shortage during the start of the scroll compressor; and can also improve the insufficient splash lubrication of the oil during the low-speed operation of the scroll compressor.

[0065] (2) The present application is particularly suitable for high-speed variable frequency compressors with balance weight members, and the lubrication state of the thrust face can be significantly improved by splash lubrication.

[0066] The foregoing description of the implementations has been presented for the purposes of illustration and description. It is not intended to be exhaustive or to limit the disclosure to the precise form disclosed. The various elements or features of a specific implementation are generally not limited to the particular implementation unless specifically recited therein. Even though an element or feature can not have been specifically shown or described herein, it is within the scope of the disclosure, if it is in keeping with the spirit of the disclosure. Individual elements or features of a specific implementation can be substituted for individual elements or features of another implementation. Changes in form and substitution of individual elements or features can be made without departing from the spirit of the disclosure and the disclosure is intended to cover all such modifications.

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; a movable scroll including a movable scroll end plate, a movable spiral wrap extending from one side of the movable scroll end plate, and a hub portion protruding from the side of the movable scroll end plate opposite the movable spiral wrap, the movable spiral wrap being engaged with the fixed spiral wrap in a meshing manner to create a fluid chamber for compressing a working fluid; a bearing assembly on which the movable scroll end plate is slidingly supported, the bearing assembly and the movable scroll end plate each having a thrust face in sliding contact with each other, wherein an oil supply passage is provided on the hub portion, lubricating oil in the hub portion being splashed to the thrust face via the oil supply passage; a drive assembly including a shaft to drive the hub portion; an intermediate member provided between the hub portion and the bearing assembly, the intermediate member having a top surface close to the movable scroll end plate, the oil supply passage being provided corresponding to a region between the top surface of the intermediate member and the movable scroll end plate so that the lubricating oil splashed from the oil supply passage is guided to the thrust face by means of the top surface of the intermediate member; a drive bush fitted radially outward of an eccentric crank pin of the shaft; and a balance weight member including a mounting base connected to the drive bush or the shaft and a weight portion extending axially from the mounting base, wherein the weight portion constitutes the intermediate member.

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

3. The scroll compressor of claim 1, wherein, The oil supply passage is provided adjacent to the movable scroll end plate.

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

5. The scroll compressor of claim 1, wherein, A throttle device is provided in the oil supply passage, the throttle device having a through oil passage through which the lubricating oil is splashed to the thrust face.

6. The scroll compressor of claim 5, wherein, The throttle device is a throttle screw, a threaded hole engaging with the throttle screw being provided in the oil supply passage.

7. The scroll compressor of claim 1, wherein, The oil supply passage includes an inclined section that guides the lubricating oil to the thrust face.

8. The scroll compressor of claim 1, wherein, The scroll compressor further includes a slinger provided between the hub portion and the bearing assembly, the slinger being located axially below the oil supply passage and fixed to the hub portion, the slinger having an inclined guide surface that guides lubricating oil toward the thrust face.

9. The scroll compressor of claim 1, wherein, The top surface of the intermediate member has an inclined surface that guides lubricating oil toward the thrust face, and / or a plurality of involute oil grooves that guide lubricating oil toward the thrust face are provided on the top surface of the intermediate member.

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