WO2013007163A1

WO2013007163A1 - Rotary compressor

Info

Publication number: WO2013007163A1
Application number: PCT/CN2012/078229
Authority: WO
Inventors: 苏晓耕
Original assignee: 艾默生环境优化技术(苏州)有限公司
Priority date: 2011-07-14
Filing date: 2012-07-05
Publication date: 2013-01-17

Abstract

A rotary compressor comprises a housing (12); a compressing mechanism provided within the housing; a rotary shaft (100), a first end of the rotary shaft being provided with an eccentric crank pin (102), which eccentric crank pin drives the compressing mechanism via a driving bearing (64); a main bearing (62) for supporting part of the rotary shaft, the rotary shaft further comprising: a concentric hole (104) formed at a second end of the rotary shaft; a first eccentric hole (110) in fluid communication with the concentric hole and extending to an end face of the eccentric crank pin, a second eccentric hole (120) in fluid communication with the concentric hole and extending to the end face of the first end of the rotary shaft, and a transverse hole (130) formed at a position corresponding to the main bearing (64) and in fluid communication with the second eccentric hole (120). The present compressor enables reasonable distribution of the amounts of a lubricating oil flowing through the two eccentric holes.

Description

Rotary compressor

Cross-reference to related applications

This application is required to be submitted to the Chinese Patent Office on July 14, 2011, the application number is 201110204561.X, the Chinese patent application titled "Rotary Compressor" and submitted to the Chinese Patent Office on July 14, 2011, the application number The priority of the Chinese patent application entitled "Rotary Compressor", 201120265602.1, the entire contents of which is incorporated herein by reference. Technical field

The present invention relates to a rotary compressor. Background technique

[03] A scroll compressor is one of a rotary compressor, and generally includes: a housing; a driving mechanism housed in the housing, the driving mechanism may include a motor and a rotating shaft; and a compression mechanism driven by the rotating shaft, The compression mechanism may include an orbiting movable scroll and a fixed scroll; a main bearing that supports the rotating shaft, and the like. The rotating shaft includes a shaft body and an eccentric crank pin disposed at one end of the shaft body. The eccentric crank pin is inserted into the hub of the back side of the movable scroll via a rotary bearing to thereby drive the movable scroll. The rotating shaft further includes a concentric hole disposed at an opposite end of the rotating shaft from the eccentric crank pin and an eccentric hole communicating with the concentric hole but eccentric with respect to the concentric hole. The eccentric hole extends all the way to the end of the eccentric crank pin. During operation of the compressor, lubricating oil is supplied to the end faces of the eccentric crank pins through concentric and eccentric holes of the rotating shaft to lubricate the rotating bearings and the main bearings and other moving parts.

[04] With the above configuration, the amount of lubricating oil supplied to the rotary bearing and the main bearing tends to be different. This will not be a problem if the supply of lubricant is sufficient. However, in the case where the supply of lubricating oil in the compressor is insufficient, the amount of lubricating oil distributed to the rotary bearing and the main bearing may be significantly different, which may cause an excessive supply of lubricating oil in the main bearing and the rotating bearing, and the other Insufficient supply of lubricant to damage the compressor. Summary of the invention

A technical problem to be solved by one or more embodiments of the present invention is to provide a rotary compressor in which even if the supply of lubricating oil in the compressor is insufficient, The amount of lubricant supplied to the main bearing and the drive bearing can be reasonably distributed so that the main bearing and the drive bearing are properly lubricated at the same time.

An object of one or more embodiments of the present invention is to provide a rotary compressor capable of rationally distributing the amount of lubricating oil supplied to a main bearing and a rotary bearing.

[07] According to an aspect of the present specification, a rotary compressor is provided, comprising: a housing; a compression mechanism disposed in the housing; a rotating shaft, the first end of the rotating shaft is provided with an eccentric crank pin The eccentric crank pin drives the compression mechanism via a drive bearing; a main bearing that supports a portion of the rotating shaft; wherein the rotating shaft further includes: opposite to the eccentric crank pin formed on the rotating shaft a concentric bore of the second end; a first eccentric bore in fluid communication with the concentric bore and extending to an end face of the eccentric crank pin; an end face in fluid communication with the concentric bore and extending to a first end of the rotating shaft a second eccentric hole; a transverse hole disposed at a position corresponding to the main bearing and in fluid communication with the second eccentric hole.

Preferably, a plug is provided at an end of the second eccentric hole opposite to the concentric hole.

Preferably, the central axis of the first eccentric hole, the central axis of the second eccentric hole, and the central axis of the rotating shaft are in the same plane.

[10] Preferably, the central axis of the first eccentric hole and the central axis of the second eccentric hole are symmetrical in the plane with respect to a central axis of the rotating shaft.

Preferably, the eccentric crank pin includes a flat portion that is parallel to a plane in which the planar portion is located.

[12] Preferably, the first eccentric hole and the second eccentric hole are parallel to each other.

[13] Preferably, an overlapping length L 1 of the first eccentric hole and the concentric hole in a longitudinal direction of the rotating shaft and the second eccentric hole and the concentric hole are in a longitudinal direction of the rotating shaft The overlap length L2 is equal.

[14] Preferably, a center distance dl between a central axis of the first eccentric hole and a central axis of the concentric hole and a central axis of the second eccentric hole and a central axis of the concentric hole The hole center is equal to d2. [15] Preferably, the diameter D1 of the first eccentric hole and the diameter D2 of the second eccentric hole are equal.

[16] Alternatively, an overlapping length L1 of the first eccentric hole and the concentric hole in a longitudinal direction of the rotating shaft may be smaller or larger than the second eccentric hole and the concentric hole at the rotating axis The overlap length L2 on the longitudinal direction. The overlapping lengths L1 and L2 are determined according to a lubricating oil amount distribution ratio between the first eccentric hole and the second eccentric hole.

[17] Alternatively, the hole center distance dl between the central axis of the first eccentric hole and the central axis of the concentric hole may be smaller or larger than the central axis of the second eccentric hole and the concentric hole The hole center distance d2 _e between the center axes is determined according to the oil amount distribution ratio between the first eccentric hole and the second eccentric hole.

Alternatively, the diameter D1 of the first eccentric hole may be smaller or larger than the diameter D2 of the second eccentric hole. The diameters D1 and D2 are determined according to a distribution ratio of the amount of lubricating oil between the first eccentric hole and the second eccentric hole.

[19] Preferably, the compression mechanism includes an orbiting movable scroll and a fixed scroll, the movable scroll including a hub; wherein an eccentric crank pin of the rotating shaft is inserted into the hub via the drive bearing .

[20] Preferably, the rotary compressor further includes a main bearing housing that supports the compression mechanism and the rotating shaft, and the main bearing is disposed in the main bearing housing.

[21] Preferably, the main bearing housing is formed integrally with the housing.

[22] Preferably, the rotary compressor is a horizontal scroll compressor.

Preferably, a communication hole that allows the first eccentric hole and the second eccentric hole to communicate with each other is further provided in the rotating shaft.

Preferably, the communication hole is disposed adjacent to the first end of the rotating shaft.

[25] An advantage of a rotary compressor according to one or several embodiments of the present invention is that:

[26] Since the two eccentric holes for supplying the lubricating oil to the drive bearing and the main bearing are respectively provided in the rotating shaft, the distribution of the amount of lubricating oil between the two eccentric holes can be controlled relatively easily. Thus, the rotary shaft of the present specification can be adapted to the vertical scroll compressor and the horizontal compressor by changing one or more of the following three parameters: The overlap length of the heart hole and the concentric hole, the hole center distance of the eccentric hole and the concentric hole, and the diameter of the eccentric hole. Therefore, the overall design time of the compressor can be simplified.

[27] In the case where the above three parameters of the two eccentric holes of the rotary shaft are set to be identical, the distribution of the amount of lubricating oil between the two eccentric holes is generally substantially equal. Therefore, in the case of insufficient supply of lubricating oil, the main bearing and the drive bearing can obtain substantially the same amount of lubricating oil.

[28] A processing cartridge for a rotating shaft according to one or more embodiments of the present invention, two eccentric holes can be formed by passing two ends of a rotating shaft from an end of an eccentric crank pin. By controlling the depth of the borehole, the eccentricity of the borehole and the center of the rotary shaft, and the diameter of the borehole, an eccentric bore that meets the designer's intent can be machined. Further, since the one end of the rotating shaft provided with the eccentric crank pin is drilled and then the plug is used to block one end of the second eccentric hole, the drilling process is not interfered by the concentric hole.

[29] A communication hole that allows the first eccentric hole and the second eccentric hole to communicate with each other is further disposed in the rotating shaft, so that gas in the second eccentric hole can be discharged from the first eccentric hole through the communication hole, thereby avoiding gas Block the second eccentric hole. DRAWINGS

The features and advantages of one or more embodiments of the present invention will become more readily understood from

1 is a schematic cross-sectional view of a horizontal scroll compressor according to the present invention; [32] FIG. 2 is a schematic view of a first embodiment of a rotating shaft according to the present invention; [33] FIG. A schematic view of a second embodiment of a rotating shaft of the invention; [34] FIG. 4 is a schematic view of a third embodiment of a rotating shaft according to the present invention; [35] FIG. 5 is a fourth embodiment of a rotating shaft according to the present invention. schematic diagram. detailed description

The following description of the preferred embodiments is merely exemplary, and is in no way

The inventors of the present invention have found that: in some vertical scroll compressors, in order to improve the spindle The lubricating oil supply is provided with a transverse hole communicating with the eccentric hole at a position corresponding to the main bearing of the rotating shaft. In this compressor configuration, lubricating oil can be supplied directly to the main bearing through the transverse bore and can also be supplied directly to the swivel bearing through an eccentric bore extending to the top surface of the eccentric crank pin. Since the height of the lateral hole is lower than the top surface of the eccentric crank pin, the lubricating oil can be more easily supplied to the main bearing. In the case of insufficient supply of lubricating oil, the rotating bearing will obtain less oil than the main bearing, so the rotating bearing may fail before the main bearing.

The inventors of the present invention have also found that in the horizontal scroll compressor, the oil groove for storing the lubricating oil is located on the high pressure side and the temperature is relatively high, so the amount of lubricating oil supplied to the low pressure side has an overall performance for the compressor. Direct impact. For example, the more hot oil that is supplied to the low pressure side, the higher the inhalation of the suction. In addition, hot lubricating oil can heat the motor of the compressor, resulting in a decrease in the efficiency of the motor. Therefore, the amount of lubricating oil supplied to the low pressure side must be controlled. Further, in the horizontal scroll compressor, even if the lateral hole which is branched from the eccentric hole and leads directly to the main bearing is provided, since the main bearing and the rotary bearing are at the same level, the lubricating oil is more easily supplied to the rotary bearing. Therefore, in the case of insufficient supply of lubricating oil, the main bearing may fail before the rotating bearing.

[39] Therefore, whether in a vertical scroll compressor or a horizontal scroll compressor, it is a challenge to properly distribute the amount of lubricating oil supplied to the rotary bearing and the main bearing. In order to cope with such a challenge, the inventors of the present invention have proposed the concept of providing two eccentric holes in a rotating shaft, thereby being capable of distributing and controlling the amount of lubricating oil supplied to the rotary bearing and the main bearing. Therefore, in the case of insufficient lubrication supply, the two bearings can obtain substantially the same amount of lubricating oil.

The invention will now be described in detail with reference to the specific embodiments shown in Figures 1-5.

1 is a schematic cross-sectional view of a horizontal scroll compressor in accordance with one or more embodiments of the present invention.

As shown in FIG. 1, a horizontal scroll compressor (hereinafter simply referred to as "compressor") 10 includes a housing 12, a front end cover 14 and a partition 18 fixedly coupled to the housing 12 by bolts, and A rear end cover 16 to which the bolt is fixedly coupled to the housing 12. An intake joint 20 for sucking a refrigerant (working fluid) is disposed on the casing 12, and an exhaust joint 22 for discharging a refrigerant (working fluid) is disposed on the front end cover 14.

The internal space of the compressor 10 is partitioned into a high pressure side and a low pressure side by a partition plate 18. Specifically, the space enclosed by the casing 12, the rear end cover 16, and the partition 18 constitutes a low-pressure side for sucking a low-pressure refrigerant (working fluid). The space enclosed by the partition 18 and the front end cover 14 constitutes a high pressure The side is used to discharge the compressed high pressure refrigerant (working fluid). In the present embodiment, the lubricating oil is mainly stored on the high pressure side, that is, in the space surrounded by the front end cover 14 and the partition plate 18. In other words, the high pressure side of the compressor defines an oil sump that stores lubricating oil.

The housing 12 is provided with an orbiting scroll 30 and a fixed scroll 40 as a compression mechanism, and a motor 50 and a rotating shaft 100 as driving mechanisms. The compression mechanism can be driven by the drive mechanism and supported by the spindle housing 60. Main bearing housing 60 can be secured to housing 12 in any desired manner. In the example shown in Fig. 1, the main bearing housing 60 is formed integrally with the housing 12.

The movable scroll 30 includes an end plate 32, and a scroll roll 34 is provided on one surface (the left surface in Fig. 1) of the end plate 32, and a cylinder is provided on the other surface (the right surface in Fig. 1). The hub portion 36. The fixed scroll 40 includes an end plate 42 and a scroll 44. The scroll 34 of the movable scroll 30 meshes with the scroll 44 of the fixed scroll 40 and forms a fluid chamber which gradually decreases from the outside to the center volume when the movable scroll 30 and the fixed scroll 40 move relative to each other to thereby convect The refrigerant (working fluid) in the body cavity is compressed.

The motor 50 includes a stator 52 and a rotor 54. The stator 52 is fixedly coupled to the housing 12. The rotor 54 is fixedly coupled to the rotating shaft 100 and rotated in the stator 52. Other specific configurations in the compressor 10 can be found in the Chinese Patent Application Publication No. CN101900113A, the entire contents of which is incorporated herein by reference.

The configuration of the rotating shaft according to an embodiment of one or more embodiments of the present invention will be described in detail below.

Referring to Figures 1 and 2, the left side portion of Figure 2 shows an end view of the rotating shaft, and the right side portion shows a longitudinal plan view of the rotating shaft. The first end of the rotating shaft 100 (the left end in FIG. 1) is provided with an eccentric crank pin 102 and a first weight 72. The second end of the rotating shaft 100 opposite to the eccentric crank pin 102 (the right end in FIG. 1) is provided with The second weight 74. The first weight 72 and the second weight 74 are fixedly disposed on the rotary shaft 100, so that the rotary shaft 100 can be rotated with the rotary shaft 100 as it rotates. The left side portion of the rotary shaft 100 is rotatably supported by the main bearing 62 in the main bearing housing 60, and the right side portion thereof is rotatably supported by the support portion 17 in the rear end cover 16.

The eccentric crank pin 102 includes a substantially planar planar portion 103 (see Fig. 2). The eccentric crank pin 102 is inserted into the hub portion 36 of the movable scroll 30 via the rotary bearing 64 to rotationally drive the movable scroll 30.

The second end of the rotating shaft 100 may include an oil hole 104. Preferably, the oil hole 104 and the rotating shaft 100 The axis of rotation is concentric, so the oil hole is also referred to hereinafter as a concentric hole 104. The concentric bore 104 is in fluid communication with the oil sump of the compressor. For example, the lubricating oil in the oil sump may be supplied to the concentric hole 104 of the rotary shaft 100 through the support portion 17 in the rear end cover 16 through a pipe inside the compressor or a pipe outside the compressor.

[51] Referring also to FIG. 2, the rotating shaft 100 can further include a first eccentric bore 110 that is in fluid communication with the concentric bore 104 and that is eccentric with respect to the concentric bore 104 and that extends generally longitudinally of the axis of rotation to an end face of the eccentric crank pin 102, And a second eccentric bore 120 in fluid communication with the concentric bore 104, eccentric with respect to the concentric bore 104 and spaced apart from the first eccentric bore 110, extending generally longitudinally of the axis of rotation to an end face of the rotating shaft. The first eccentric hole 110 and the second eccentric hole 120 may be disposed in parallel. A lateral hole 130 in fluid communication with the second eccentric hole 120 is also provided at a side of the rotary shaft 100 at a position corresponding to the main bearing 62. A plug 140 is provided at an end of the second eccentric hole 120 opposite to the concentric hole, thereby preventing the lubricating oil in the second eccentric hole 120 from flowing out through the end portion and flowing through the lateral hole 130.

With the above configuration, when the compressor is in operation, the lubricating oil from the oil sump is first supplied to the concentric holes 104 of the rotating shaft 100, and then through the first eccentric hole 110 and the second eccentric hole 120 in fluid communication with the concentric holes 104 at the same time. (and the lateral holes 130) are directly supplied to the rotary bearing 64 and the main bearing 62, respectively. The distribution of the lubricating oil between the first eccentric hole 110 and the second eccentric hole 120 can be adjusted by adjusting the intersection volume VI between the first eccentric hole 110 and the concentric hole 104 and the intersection between the second eccentric hole 1120 and the concentric hole 104. Volume V2 is adjusted. Specifically, referring to FIG. 2, the upper intersecting volume VI is the overlap length L l of the first eccentric hole 110 and the concentric hole 104 in the longitudinal direction of the rotating shaft, the center distance between the center of the first eccentric hole and the center of the concentric hole. The diameter of the dl and the first eccentric hole D1 is determined by three parameters. The upper mesh volume V2 is the overlap length L2 of the second eccentric hole 120 and the concentric hole 104 in the longitudinal direction of the rotating shaft, the hole center distance d2 between the center of the second eccentric hole and the center of the concentric hole, and the diameter of the second eccentric hole. D2 is determined by three parameters.

[3] Preferably, it is desirable that the amount of lubricating oil supplied to the rotary bearing 64 via the first eccentric hole 110 and the amount of lubricating oil supplied to the main bearing 62 via the second eccentric hole 120 are substantially equal. In order to achieve this lubricant distribution target, the intersecting volumes VI and V2 can be made approximately equal by adjusting the above three parameters. Preferably, the overlapping length L 1 of the first eccentric hole 110 and the overlapping length L2 of the second eccentric hole 120 may be made equal, and the hole center distance dl of the first eccentric hole 110 and the hole center distance d2 of the second eccentric hole 120 are equal. And the diameter D1 of the first eccentric hole 110 and the diameter D2 of the second eccentric hole are equal. Figure 2 shows this optimal situation.

In order to minimize the influence of the two eccentric holes on the stiffness and strength of the rotating shaft 100, it is preferable to make the center of the first eccentric hole 110 and the center of the second eccentric hole 120 and the center of the concentric hole (ie, The center of rotation of the rotating shaft is located in the same plane P, and the plane P is parallel to the plane in which the plane portion 103 of the eccentric crank pin 102 is located. In the normal operation of the compressor, the plane P is a neutral plane of the rotating shaft 100 under the bending moment, and the tensile stress and the compressive stress caused by the bending moment are both zero on the neutral plane. Further preferably, the center of the first eccentric hole 110 and the center of the second eccentric hole 120 are symmetrical in the above plane P with respect to the center of the concentric hole (ie, the center of rotation of the rotating shaft).

Further, a communication hole 150 that allows the first eccentric hole 110 and the second eccentric hole 120 to communicate with each other is further provided in the rotary shaft 100. The communication hole 150 may be disposed at any position in the longitudinal direction of the rotary shaft 100 as long as the communication between the first eccentric hole 110 and the second eccentric hole 120 can be realized. Preferably, however, the communication hole 150 may be disposed adjacent to one end of the rotary shaft 100 provided with the eccentric crank pin 102. The communication hole 150 may allow the gas in the first eccentric hole 110 and the second eccentric hole 120 to communicate to facilitate the smooth discharge of the gas in the second eccentric hole 120. During the operation of the compressor, the rotation of the rotating shaft causes the lubricating oil in the first eccentric hole 110 and the second eccentric hole 120 to abut against the outer wall of each of the eccentric holes facing the outer side of the rotating shaft, and thus the eccentric holes are oriented toward the rotating shaft. The inner wall of the center is substantially free of lubricating oil. Therefore, the gas in the second eccentric hole 120 can enter the first eccentric hole 110 through the communication hole 150 and is finally discharged from the end of the first eccentric hole 110 at the eccentric crank pin 102.

[56] In certain situations, the designer may wish to have different amounts of lubricant dispensed in the two eccentric holes for a specific purpose. According to the concept of the present specification, the distribution and control of the amount of lubricating oil between the two eccentric holes can be achieved relatively easily.

3 shows a schematic view of a second embodiment of a rotating shaft 100 according to one or more embodiments of the present invention, wherein the left side portion of FIG. 3 shows an end view of the rotating shaft, and the right side portion shows A longitudinal plan view of the rotating shaft is taken out. In this embodiment, the longitudinal overlap length L 1 of the first eccentric hole 110 and the concentric hole 104 and the longitudinal overlap length L2 of the second eccentric hole 120 and the concentric hole 104 are different, specifically, L2 > L 1 . The other parameters of the two eccentric holes are the same. Therefore, it is possible to distribute more lubricating oil to the second eccentric hole 120 to supply the lubricating oil to the main bearing.

4 shows a schematic view of a third embodiment of a rotating shaft 100 according to one or more embodiments of the present invention, wherein the left side portion of FIG. 4 shows an end view of the rotating shaft, and the right side portion shows A longitudinal plan view of the rotating shaft is taken out. In this embodiment, the center distance dl between the center of the first eccentric hole 110 and the center of the concentric hole 104 is different from the hole ii giant d2 between the center of the second eccentric hole 120 and the center of the concentric hole 104, Specifically, dl>d2o two eccentric holes The other parameters are the same. Therefore, it is possible to distribute more lubricating oil to the second eccentric hole 120 to supply the lubricating oil to the main bearing.

5 shows a schematic view of a fourth embodiment of a rotating shaft 100 according to one or more embodiments of the present invention, wherein the left side portion of FIG. 5 shows an end view of the rotating shaft, and the right side portion shows A longitudinal plan view of the rotating shaft is taken out. In this embodiment, the diameter D1 of the first eccentric hole 110 and the diameter D2 of the second eccentric hole 120 are different, specifically, D1 > D2. The other parameters of the two eccentric holes are the same. Therefore, it is possible to distribute more lubricating oil to the first eccentric hole 110 to supply lubricating oil to the rotary bearing in priority.

With respect to the embodiment shown in Fig. 2, the inventors conducted experiments to observe the amount of lubricating oil supplied to the rotary bearing and the main bearing through the two eccentric holes, respectively. The experimental results are shown in Table 1.

[61] In the above experiment, only the rotational speed of the compressor was changed. The change in the flow of lubricating oil that appears in the table is due to the axial movement of the rotating shaft. From the ratio of DB to MB in Table 1, it can be seen that the amount of lubricating oil supplied to the rotary bearing and the main bearing is almost the same at various rotational speeds. In other words, with the configuration of one or more embodiments of the present invention, the distribution of lubricating oil by the first eccentric bore and the second eccentric bore is independent of the rotational speed of the compressor.

The inventors also experimented with the configuration shown in Fig. 2 by increasing the flow rate of the lubricating oil by three times. The experimental results are shown in Table 2. Table 2

Speed Lubricating oil flow Average of the flat main bearing obtained from the rotary bearing DB: MB (rev / sec) (g / sec) Lubricant amount DB Lubricant amount MB

(g / sec) (g / sec)

29 2.5 13 12 1.0 0.9

43 4.0 18 22 1.0 1.2

50 3.9 19 20 1.0 1.1

60 5.0 26 24 1.0 0.9

79 5.9 29 30 1.0 1.0

89 4.9 25 24 1.0 1.0

[63] From the ratio of DB to MB in Table 2, it can be seen that the amount of lubricating oil supplied to the rotary bearing and the main bearing is almost the same at various rotational speeds at various lubricating oil flows. In other words, with the configuration of one or more embodiments of the present invention, the distribution of lubricating oil achieved by the first eccentric bore and the second eccentric bore is independent of the rotational speed of the compressor and the amount of lubricating oil supplied.

[64] That is, with the configuration of one or more embodiments of the present invention, even in the case where the supply of lubricating oil is insufficient, a suitable amount of lubricating oil can be supplied to the rotary bearing and the main bearing as desired by the designer. . For example, the same amount of lubricating oil is supplied to the rotary bearing and the main bearing, or more lubricating oil is supplied to one of them.

Two of the eccentric holes of the rotating shaft of one or more embodiments of the present invention are completed only by two drilling processes from one end of the rotating shaft provided with the eccentric crank pin. And by controlling the depth of the borehole, the eccentricity of the borehole and the center of the rotary shaft, and the diameter of the borehole, an eccentric bore that meets the designer's intent can be machined. Further, since the one end of the rotating shaft provided with the eccentric crank pin is bored and then the plug 140 is used to block one end of the second eccentric hole, the drilling process is not interfered by the concentric hole.

[66] Although the specification has been described by way of example of a horizontal half-sealed scroll compressor, those skilled in the art will appreciate that one or more embodiments of the present invention are equally applicable to closed open scroll compression. And one or more embodiments of the present invention are also applicable to a vertical scroll compressor. Moreover, one or more embodiments of the present invention are also applicable to other machines that require the distribution of lubricating oil to two different locations via a rotating shaft.

Although various embodiments of the present invention have been described in detail herein, it is understood that the invention is not to Other variations and modifications can be made by those skilled in the art in the context of the nature and scope. All such variations and modifications are intended to fall within the scope of the invention. Moreover, all of the components described herein can be replaced by other technically equivalent components.

Claims

1. A rotary compressor comprising:

Housing (12);

Compression set in the housing (12)

a rotating shaft (100), the first end of the rotating shaft (100) is provided with an eccentric crank pin (102), and the eccentric crank pin (102) drives the compression mechanism via a driving bearing (64);

a main bearing (62) supporting a portion of the rotating shaft (100);

It is characterized in that the rotating shaft (100) further comprises:

Forming a concentric (104) at a second end of the rotating shaft (100) opposite the eccentric crank pin (102);

a first eccentric bore (110) in fluid communication with the concentric bore (104) and extending to an end face of the eccentric crank pin (102);

a second eccentric bore (120) in fluid communication with the concentric bore (104) and extending to an end face of the first end of the rotating shaft (100);

A transverse bore (130) is formed at a location corresponding to the main bearing (64) and in fluid communication with the second eccentric bore (120).

The rotary compressor according to claim 1, wherein a plug (140) is provided at an end of the second eccentric hole (120) opposite to the concentric hole (104).

The rotary compressor according to claim 1, wherein a central axis of the first eccentric hole (110), a central axis of the second eccentric hole (120), and a center of the rotating shaft (100) The axes are in the same plane (P).

4. The rotary compressor according to claim 3, wherein a central axis of said first eccentric hole (110) and a central axis of said second eccentric hole (120) are in said plane (P) The central axis of the rotating shaft is symmetrical.

The rotary compressor according to claim 3, wherein the eccentric crank pin (102) includes a flat portion (103) parallel to a plane in which the flat portion (103) is located,

The rotary compressor according to claim 1, wherein the first eccentric hole (110) and the second eccentric hole (120) are parallel to each other.

The rotary compressor according to claim 1, wherein an overlap length L1 of the first eccentric hole (110) and the concentric hole (104) in a longitudinal direction of the rotating shaft (100) and the The overlapping length L2 of the second eccentric hole (120) and the concentric hole (104) in the longitudinal direction of the rotating shaft (100) is equal.

8. The rotary compressor according to claim 1, wherein a center distance dl between the central axis of the first eccentric hole (110) and a central axis of the concentric hole (104) and the second The central axis of the eccentric bore (120) is equal to the bore center distance d2 between the central axes of the concentric bores (104).

The rotary compressor according to claim 1, wherein a diameter D1 of the first eccentric hole (110) and a diameter D2 of the second eccentric hole (120) are equal.

The rotary compressor according to claim 1, wherein an overlapping length L1 of the first eccentric hole (110) and the concentric hole (104) in a longitudinal direction of the rotating shaft (100) is smaller than the An overlapping length L2 of the second eccentric hole (120) and the concentric hole (104) in a longitudinal direction of the rotating shaft (100), wherein the overlapping lengths L1 and L2 are according to the first eccentric hole (110) and The amount of lubricating oil amount distribution between the second eccentric holes (120) is determined.

The rotary compressor according to claim 1, wherein an overlapping length L1 of said first eccentric hole (110) and said concentric hole (104) in a longitudinal direction of said rotating shaft (100) is larger than said An overlapping length L2 of the second eccentric hole (120) and the concentric hole (104) in a longitudinal direction of the rotating shaft (100), wherein the overlapping lengths L1 and L2 are according to the first eccentric hole (110) and The amount of lubricating oil amount distribution between the second eccentric holes (120) is determined.

The rotary compressor according to claim 1, wherein a center distance dl between a central axis of the first eccentric hole (110) and a central axis of the concentric hole (104) is smaller than the second a hole center distance d2 between a central axis of the eccentric hole (120) and a central axis of the concentric hole (104), the hole center distances d1 and d2 being according to the first eccentric hole (110) and the second The ratio of the amount of lubricating oil between the eccentric holes (120) is determined.

The rotary compressor according to claim 1, wherein a center distance dl between a central axis of the first eccentric hole (110) and a central axis of the concentric hole (104) is larger than the second a hole center distance d2 between a central axis of the eccentric hole (120) and a central axis of the concentric hole (104), the hole center distances d1 and d2 being according to the first eccentric hole (110) and the second The ratio of the amount of lubricating oil between the eccentric holes (120) is determined.

The rotary compressor according to claim 1, wherein a diameter D1 of the first eccentric hole (110) is smaller than a diameter D2 of the second eccentric hole (120), and the diameters D1 and D2 are according to A lubricating oil amount distribution ratio between the first eccentric hole (110) and the second eccentric hole (120) is determined.

The rotary compressor according to claim 1, wherein a diameter D1 of the first eccentric hole (110) is larger than a diameter D2 of the second eccentric hole (120), the diameters D1 and D2 being according to A lubricating oil amount distribution ratio between the first eccentric hole (110) and the second eccentric hole (120) is determined.

The rotary compressor according to claim 1, wherein said compression mechanism includes an orbiting movable scroll (30) and a fixed scroll (40), and said movable scroll (30) includes a hub (36). The eccentric crank pin (102) of the rotating shaft (100) is inserted into the hub (36) via the drive bearing (64).

17. The rotary compressor according to claim 1, further comprising a main bearing housing (60) supporting said compression mechanism and said rotating shaft (100), said main bearing (62) being disposed at said main bearing In the seat (60).

The rotary compressor according to claim 17, wherein said main bearing housing (60) is formed integrally with said housing (12).

The rotary compressor according to claim 1, wherein the rotary compressor is a horizontal scroll compressor.

The rotary compressor according to claim 1, wherein the first eccentric hole (110) and the second eccentric hole (120) are communicated with each other in the rotating shaft (100). Connect the hole (150).

The rotary compressor according to claim 20, wherein said communication hole (150) is provided near a first end of said rotating shaft (100).