Main bearing seat for scroll compressor and scroll compressor

Abstract

The application provides a main bearing seat for a scroll compressor, which comprises a supporting part and a cavity located inside the supporting part in the radial direction of the main bearing seat, and is provided with an oil discharge pipeline for communicating the cavity with the radial outside of the main bearing seat, the oil discharge pipeline comprises a protruding part protruding inward from the inner side wall of the supporting part in the radial direction and located in the cavity, the protruding part comprises a first end face and a circumferential side wall extending from the first end face, and the protruding part comprises an oil inlet, wherein the oil inlet is at least partially formed on the circumferential side wall. The application also provides a scroll compressor. According to the main bearing seat and the scroll compressor, the oil discharge efficiency is high, the oil circulation rate is good, and the system is stable and efficient.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of scroll compressor, and more particularly, to a main bearing housing for scroll compressor. BACKGROUND

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

[0003] Scroll compressor generally comprises a compression mechanism, a drive shaft and a motor. The compression mechanism comprises a fixed scroll component and an orbiting scroll component, wherein the orbiting scroll component performs orbiting motion relative to the fixed scroll component under the driving of the drive shaft. The drive shaft is supported by bearings in the bearing housing and is driven to rotate by the motor. These moving components all need lubricating oil for lubrication to maintain the stability and reliability of the compressor.

[0004] In the existing low-pressure-side compressor, generally, the lubricating oil, after lubricating the eccentric crank pin pair unloading bushing and the hub of the orbiting scroll via the oil supply channel in the drive shaft, falls into the chamber formed by the recess of the main bearing housing. There is a gap of 1-2mm between the inner side wall of the main bearing housing and the outer peripheral wall of the hub of the orbiting scroll for pushing the oil in the chamber to the thrust face for lubrication, while the excess oil is discharged from the oil discharge channel in the main bearing housing to the outside of the main bearing housing and falls back to the oil pool at the bottom of the scroll compressor.

[0005] However, due to the small gap, the lubricating oil at the inlet of the oil discharge channel is squeezed once per revolution of the orbiting scroll, resulting in discontinuous oil discharge and affecting the oil discharge efficiency. Especially when the frequency conversion compressor is running at high speed, the amount of oil needed to be discharged from the chamber increases, but due to the small gap and the inertia of the lubricating oil, the oil discharge efficiency is actually significantly reduced, which is exactly the opposite of the ideal situation.

[0006] Therefore, there is a need for a main bearing housing with improved oil discharge capacity. SUMMARY

[0007] This section provides a general summary of the application, but is not a comprehensive disclosure of its full scope or all of its features.

[0008] One of the objectives of the present application is to provide a main bearing housing with good oil discharge capacity, especially under high speed conditions of the compressor.

[0009] Another objective of the present application is to provide a scroll compressor with improved oil circulation rate (OCR) to avoid the decrease of compressor efficiency and even compressor failure caused by excessively high oil circulation rate.

[0010] The application provides a main bearing seat for a scroll compressor, the main bearing seat comprising a bearing portion and a chamber located inside the bearing portion in a radial direction of the main bearing seat, the main bearing seat being provided with an oil discharge channel for communicating the chamber with a radially outer side of the main bearing seat, the oil discharge channel comprising a protrusion protruding inwardly from an inner side wall of the bearing portion in the radial direction and located in the chamber, the protrusion comprising a first end face and a circumferential side wall extending from the first end face, the protrusion comprising an oil inlet, wherein the oil inlet is formed at least partially on the circumferential side wall.

[0011] Optionally, a portion of the oil inlet formed on the circumferential side wall extends in the circumferential direction of the protrusion by a length not more than half of a circumference of the protrusion.

[0012] Optionally, the inner side wall of the bearing portion is provided with a groove, the protrusion at least partially overlapping the groove when viewed in the radial direction.

[0013] Optionally, the groove is configured as a circular annular groove extending in the circumferential direction of the chamber.

[0014] Optionally, the groove comprises a bottom wall extending substantially in an axial direction of the main bearing seat, the oil inlet extending from the bottom wall towards the first end face.

[0015] Optionally, the portion of the oil inlet formed on the circumferential side wall is entirely located within the groove when viewed in the radial direction.

[0016] Optionally, the portion of the oil inlet formed on the circumferential side wall substantially faces a compression direction in which oil is compressed within the chamber.

[0017] Optionally, the oil inlet is entirely formed on the circumferential side wall, and the first end face is entirely closed.

[0018] Optionally, the oil inlet comprises a first opening portion formed on the circumferential side wall and a second opening portion formed on the first end face, the first end face being closed except for the second opening portion.

[0019] Optionally, the first opening portion communicates with the second opening portion.

[0020] Optionally, the bearing portion comprises a through hole extending from the inner side wall of the bearing portion to an outer side of the main bearing seat, the oil discharge channel being integrally formed with the main bearing seat, the oil discharge channel comprising the through hole and the protrusion formed around the through hole; or the oil discharge channel being formed separately from the main bearing seat, wherein the oil discharge channel is inserted in the through hole and partially protrudes from the through hole towards the chamber to form the protrusion.

[0021] The application also provides a scroll compressor, wherein the scroll compressor comprises the main bearing seat described above.

[0022] In general, the main bearing housing and the scroll compressor using the main bearing housing according to the present invention bring at least the following beneficial effects: Since the oil inlet is at least partially provided on the circumferential sidewall of the protrusion, the oil in the chamber can enter the oil discharge pipe along the non-radial direction of the main bearing housing, such as the circumferential direction (tangential direction), thereby increasing the oil discharge volume. In addition, with the movement of the moving scroll hub, the oil can more easily enter the oil discharge pipe, so that the higher the compressor speed, the greater the oil discharge volume, which meets the ideal situation of high speed and high oil discharge, and low speed and low oil discharge. Since the groove is formed on the inner sidewall of the main bearing housing, the oil inlet area is guaranteed, which is more conducive to the oil entering the oil discharge pipe, thereby increasing the oil discharge volume. Since the lubricating oil in the chamber can be effectively discharged through the oil discharge channel of the main bearing housing, excessive oil supply to the thrust surface is avoided, thereby preventing excessive lubricating oil from being sucked into the scroll with the airflow after passing through the thrust surface, thereby effectively controlling the oil circulation rate of the compressor. Therefore, the main bearing housing according to the present invention not only has good oil discharge capability, meeting the ideal situation of high oil discharge at high speed and low oil discharge at low speed, but also has a simple structure, is easy to manufacture, and has wide applicability. Attached Figure Description

[0023] The foregoing and other features and characteristics of the invention will become clearer from the following detailed description with reference to the accompanying drawings, which are by way of example only and are not necessarily drawn to scale. The same reference numerals are used in the drawings to indicate the same parts, in which:

[0024] Figure 1 A partial longitudinal sectional view of a scroll compressor according to the present invention is shown, wherein the oil drain pipe in the main bearing housing is not shown.

[0025] Figure 2 and Figure 3 A longitudinal and cross-sectional view showing details of a scroll compressor according to the present invention is shown, with particular emphasis on the through-hole in the main bearing housing;

[0026] Figure 4 A cross-sectional perspective view of a scroll compressor according to the present invention is shown, with particular emphasis on the main bearing housing and its oil drain pipe according to a first embodiment of the present invention.

[0027] Figure 5 A perspective view of an oil drain pipe according to a first embodiment of the present invention is shown schematically.

[0028] Figure 6 A perspective view of an oil drain pipe according to a second embodiment of the present invention is schematically shown; and

[0029] Figure 7 A three-dimensional schematic diagram of an oil drain pipe according to a comparative example of the present invention is shown. Detailed Implementation

[0030] Now we will combine Figures 1 to 6 Preferred embodiments of the invention will be described in detail below. In the various views, corresponding components or portions are given the same reference numerals. The following description is exemplary in nature and is not intended to limit the invention or its application or use.

[0031] First, refer to Figures 1 to 3 The overall structure and operating principle of the scroll compressor according to the present invention are described.

[0032] like Figure 1 As shown, a scroll compressor 100 (sometimes referred to as a compressor below) generally includes a housing 10, a compression mechanism consisting of a fixed scroll component 20 and a moving scroll component 30, a main bearing housing 40, and a drive shaft 50 and a motor (not shown) for driving the compression mechanism, wherein the compression mechanism, the main bearing housing 40, the drive shaft 50 and the motor are all arranged in the internal space surrounded by the housing 10.

[0033] The moving scroll component 30 includes an end plate 31, a hub 33 formed on one side of the end plate 31, and a helical blade 32 formed on the other side of the end plate 31. The stationary scroll component 20 includes an end plate 21, a helical blade 22 formed on one side of the end plate 21, and an exhaust port 23 formed at approximately the center of the end plate 21. A series of compression chambers with volumes gradually decreasing from the radially outer to the radially inner side are formed between the helical blade 22 of the stationary scroll component 20 and the helical blade 32 of the moving scroll component 30.

[0034] An eccentric crank pin 51 is provided at one end of the drive shaft 50 adjacent to the moving scroll member 30. The eccentric crank pin 51 is inserted into the hub 33 of the moving scroll member 30. An unloading bushing (not shown) can be provided between the eccentric crank pin 51 and the hub 33 to provide radial flexibility for the compression mechanism. In addition, a drive bearing (not shown) is also provided between the unloading bushing and the hub 33 of the moving scroll member 30. Driven by a motor, the drive shaft 50 causes the moving scroll member 30 to revolve relative to the stationary scroll member 20 via the eccentric crank pin 51, the unloading bushing, and the drive bearing (i.e., the central axis of the moving scroll member 30 moves around the central axis of the stationary scroll member 20, but the moving scroll member 30 itself does not rotate around its own central axis) to achieve compression of the working fluid. The aforementioned revolve motion is achieved by a cross-slip ring.

[0035] The main bearing housing 40 is configured to support the compression mechanism, particularly the moving scroll component 30, and can accommodate a main bearing therein to provide rotational support for the drive shaft 50. Figure 1 and Figure 2As shown, the main bearing housing 40 includes a support portion 48 (including a thrust face 42 in contact with the end plate 31 of the orbiting scroll member 30) for supporting the orbiting scroll member 30 and a main body portion 49 for mounting and housing a drive shaft 50, etc., the support portion 48 being disposed around the main body portion 49. A recessed portion recessed from the thrust face 42 toward the main body portion 49 and a central hole 43 (see Figure 4 ) disposed at a substantially central portion of the bottom of the recessed portion are formed in the main bearing housing 40. That is, the inner side wall of the support portion 48 defines the circumferential profile of the recessed portion, and the top surface of the main body portion 49 defines the bottom surface of the recessed portion. The main bearing housing 40 and the recessed portion are not limited to the circular shape as shown, but can be formed in other suitable shapes such as a rectangular shape, etc. The drive shaft 50 passes through the central hole 43 of the main bearing housing 40, and a main bearing is disposed between the drive shaft 50 and the inner hole wall of the central hole 43, so that the drive shaft 50 is rotatably supported by the main bearing. The recessed portion of the main bearing housing 40 can be disposed substantially concentrically with the central hole 43. The recessed portion of the main bearing housing 40 forms a cavity Co that can house the eccentric crank pin 51 of the drive shaft 50, the unloading bushing, the hub portion 33 of the orbiting scroll member 30, etc., on the radially inner side of the support portion 48.

[0036] In Figure 1 the scroll compressor shown, an oil pool (not shown) for storing lubricating oil can be formed in the bottom of the housing 10. Accordingly, a lubricating oil supply passage is formed in the drive shaft 50, extending substantially in the axial direction thereof. The lubricating oil supply passage includes a central hole formed in the lower end of the drive shaft 50 and an eccentric hole 52 extending upward from the central hole to the end surface of the eccentric crank pin 51. During operation of the compressor, lubricating oil in the oil pool is supplied into the central hole in the lower end of the drive shaft 50, and the lubricating oil entering the central hole is pumped or flung into the eccentric hole 52 by centrifugal force during rotation of the drive shaft 50 and flows upward along the eccentric hole 134 up to the end surface of the eccentric crank pin 51, as indicated by the arrow direction in Figure 1 . The lubricating oil discharged from the end surface of the eccentric crank pin 51 lubricates the drive bearing on the eccentric crank pin 51 and the unloading bushing, and flows downward along the gap between the eccentric crank pin 51, the unloading bushing, the drive bearing, and the hub portion 33 and collects in the cavity Co on the inner side of the main bearing housing 40.

[0037] Referring to Figure 2Due to the orbiting movement of the orbiting hub 33 within the chamber C0, a small gap d, typically of about 1 mm, exists between the outer peripheral wall of the orbiting hub 33 and the inner side wall of the main bearing housing 40 forming the chamber C0. Under the agitation of the orbiting hub 33 and the extrusion of the small gap d, part of the lubricating oil within the chamber C0 is sent to the thrust face 42 to provide cooling and lubrication, while the remaining lubricating oil within the chamber C0 needs to be discharged from the chamber C0 back to the oil sump at the bottom of the compressor. In other words, in the chamber C0, the lubricating oil is extruded along the orbiting direction of the orbiting hub within the chamber C0, which is referred to herein as the compression direction of the lubricating oil.

[0038] To this end, referring to Figure 3 and Figure 4 , the main bearing housing 40 is further provided with a through hole 41 extending from the inner side wall of the support portion 48 to the outside of the main bearing housing in a substantially radial direction, the through hole 41 being inserted with an oil discharge conduit, so as to communicate the chamber C0 inside the main bearing housing with the outside of the main bearing housing 40, so that the lubricating oil within the chamber C0 can be discharged to the outside of the main bearing housing 40. Preferably, the through hole 41 and / or the oil discharge conduit extends to a position of the housing 10 (as shown in Figure 2 , 3 indicated) so that the discharged lubricating oil can flow downward along the inner wall of the housing 10 to the bottom of the compressor, avoiding excessive lubricating oil being sucked into the scroll with the gas flow to cause the oil circulation rate to rise.

[0039] The specific structure of the oil discharge conduit 45a according to the first embodiment of the present application will be described below with reference to Figure 4 and Figure 5 . The oil discharge conduit 45a comprises a first portion 455 extending substantially in the radial direction of the main bearing housing 40, and a second portion 456 and a third portion 457 extending substantially in the axial direction of the main bearing housing 40. The first portion 455, the second portion 456 and the third portion 457 are connected to each other in sequence. The oil discharge conduit 45a is designed to be inserted into the main bearing housing 40 from the radial outside of the main bearing housing. In the case where the oil discharge conduit 45a is installed in place in the main bearing housing 40, the first portion 455 is inserted into the through hole 41 of the main bearing housing 40 and partially protrudes from the through hole 41 towards the chamber C0, and the second portion 456 and the third portion 457 are arranged outside the main bearing housing 40. Preferably, the second portion 456 and the third portion 457 are arranged to tightly fit the outer side wall of the main bearing housing 40 in accordance with the shape of the outer side of the main bearing housing 40, so as to easily limit the distance of the first portion 455 inserted into the through hole 41 and protruding, and limit the movement of the first portion 455.

[0040] The first portion 455 is configured in a substantially cylindrical shape, comprising a first end face 451a, a second end face opposite to the first end face 451a, and a circumferential side wall connecting the first end face 451a and the second end face. The circumferential side wall of the first portion 455 is provided with a sealing ring groove 454, in which a sealing ring can be installed to seal the gap between the first portion 455 of the oil discharge conduit 45a and the through hole 41 when the first portion 455 is inserted into the through hole 41 from the outside of the main bearing housing 40. After the first portion 455 of the oil discharge conduit 45a is installed in place in the through hole 41, a portion of the first portion 455 protrudes substantially radially inward from the inner side wall of the support portion 48 into the chamber C0 to form a protruding portion 450, which comprises the first end face 451a and a circumferential side wall 453 extending from the first end face 451a. The protruding portion 450 is further provided with an oil inlet 452a formed on the circumferential side wall 453, which is arranged close to the first end face 451a. Preferably, as shown in Figs. 4 and 5, the oil inlet 452a is substantially oriented in the circumferential direction of the chamber C0, and preferably substantially oriented in the compression direction in which the lubricating oil is compressed by the rotation of the hub portion 33 of the orbiting scroll member 30. Here, the term "substantially" means that the oil inlet is partially or completely oriented in the circumferential direction, as long as it allows the lubricating oil to enter the oil inlet in a substantially circumferential direction. The first end face 451a is completely closed, while the second end face is open, so that under the agitation and compression of the hub portion 33 of the orbiting scroll member 30, the configuration of the oil discharge conduit 45a produces a "scoop" effect, which facilitates the introduction of the lubricating oil in the chamber C0 into the oil discharge conduit 45a from the oil inlet 452a. Figure 4 、 5 The first portion 455 is configured in a substantially cylindrical shape, comprising a first end face 451a, a second end face opposite to the first end face 451a, and a circumferential side wall connecting the first end face 451a and the second end face. The circumferential side wall of the first portion 455 is provided with a sealing ring groove 454, in which a sealing ring can be installed to seal the gap between the first portion 455 of the oil discharge conduit 45a and the through hole 41 when the first portion 455 is inserted into the through hole 41 from the outside of the main bearing housing 40. After the first portion 455 of the oil discharge conduit 45a is installed in place in the through hole 41, a portion of the first portion 455 protrudes substantially radially inward from the inner side wall of the support portion 48 into the chamber C0 to form a protruding portion 450, which comprises the first end face 451a and a circumferential side wall 453 extending from the first end face 451a. The protruding portion 450 is further provided with an oil inlet 452a formed on the circumferential side wall 453, which is arranged close to the first end face 451a. Preferably, as shown in Figs. 4 and 5, the oil inlet 452a is substantially oriented in the circumferential direction of the chamber C0, and preferably substantially oriented in the compression direction in which the lubricating oil is compressed by the rotation of the hub portion 33 of the orbiting scroll member 30. Here, the term "substantially" means that the oil inlet is partially or completely oriented in the circumferential direction, as long as it allows the lubricating oil to enter the oil inlet in a substantially circumferential direction. The first end face 451a is completely closed, while the second end face is open, so that under the agitation and compression of the hub portion 33 of the orbiting scroll member 30, the configuration of the oil discharge conduit 45a produces a "scoop" effect, which facilitates the introduction of the lubricating oil in the chamber C0 into the oil discharge conduit 45a from the oil inlet 452a.

[0041] Although the oil inlet 452a is shown as being arranged substantially in the circumferential direction of the chamber C0, it will be appreciated by those skilled in the art that the oil inlet 452a can also be arranged in other directions other than the radial direction of the main bearing housing 40. For example, at least a portion of the oil inlet is arranged in the top region or the bottom region of the circumferential side wall 453 of the protruding portion 450 to be oriented in the axial direction of the main bearing housing. Such an arrangement is particularly advantageous in the case where a large amount of lubricating oil accumulates in the chamber C0, as it allows the lubricating oil to be efficiently discharged from the chamber C0 without or with little compression, further ensuring the oil discharge effect.

[0042] The lubricating oil entering the first portion 455 from the oil inlet 452a flows through the first portion 455, the second portion 456 and the third portion 457 in turn, and is discharged to the outside of the main bearing housing 40 through the discharge port formed on the third portion 457. Preferably, the third portion 457 is configured to have a first discharge port portion 4571 facing the inner side wall of the housing 10 and a second discharge port portion 4572 facing the bottom of the housing 10, whereby the lubricating oil can be discharged from the main bearing housing from a position further away from the suction port of the compression mechanism under the joint guidance of the second portion 456 and the third portion 457, and the lubricating oil is more easily returned to the oil pool at the bottom of the housing, thereby further reducing the possibility of the lubricating oil being sucked into the suction port of the compression mechanism along with the working fluid, and reducing the oil circulation rate. Preferably, the cross-sectional area of the second portion 456 is smaller than that of the third portion 457, thereby reducing the flow rate of the lubricating oil in the oil discharge channel 45a, avoiding the generation of small oil droplets due to excessive flow rate and being sucked into the compression mechanism.

[0043] In the first embodiment of the present application, under the stirring and extrusion action of the hub portion 33 of the orbiting scroll member 30, the lubricating oil is more easily entered into the oil discharge channel 45a from the oil inlet 452a on the circumferential side wall 453 in directions other than the radial direction of the main bearing housing 40, so that a greater oil discharge amount is obtained according to the first embodiment of the present application compared to the case where the lubricating oil directly enters the through hole 41 in the radial direction of the main bearing housing 40.

[0044] For example, Figure 7 An oil discharge channel 45c of a comparative example is shown in FIG. 6. Similar to the oil discharge channel 45 according to the first embodiment of the present application, the oil discharge channel 45c is configured in a substantially cylindrical shape, including a first end surface located on the radially inner side, a second end surface opposite to the first end surface, and a circumferential side wall connecting the first end surface and the second end surface, and a seal ring groove 454 for mounting a seal ring is provided on the circumferential side wall. The difference is that the oil inlet 452c of the oil discharge channel 45c is provided on the first end surface, and the lubricating oil enters the oil discharge channel 45c substantially in the radial direction from the oil inlet 452c. Due to the small gap d between the outer peripheral wall of the orbiting scroll hub portion 33 and the inner side wall of the main bearing housing 40 forming the chamber CO, the lubricating oil at the oil inlet 452c is extruded as the hub portion 33 of the orbiting scroll member rotates, making it difficult for the lubricating oil to enter the oil inlet 452c in the radial direction. In addition, for a variable frequency compressor, the higher the rotational speed of the orbiting scroll member, the more severe the extrusion of the lubricating oil at the oil inlet 452c, the less oil that can enter the oil inlet 452c, and the more oil that is sent to the thrust surface 42 due to the extrusion. Too much lubricating oil is supplied to the thrust surface 42 and crushed into small oil droplets at the thrust surface 42, which is easily sucked into the scroll along with the gas flow, increasing the oil circulation rate of the compressor.

[0045] In contrast, in the first embodiment according to the present application, for example, the lubricating oil enters the oil discharge passage 45a from the oil inlet 452a on the peripheral side wall 453 along the circumferential direction (or tangential direction) of the chamber C0, the higher the rotational speed of the compressor, the greater the agitation and extrusion of the hub 33 of the orbiting scroll member to the lubricating oil in the chamber C0, the more easily the lubricating oil enters the oil inlet 452a, and the greater the oil discharge amount, thus achieving the goal of high rotational speed and high oil discharge, low rotational speed and low oil discharge. In addition, since the lubricating oil in the chamber C0 is discharged in time through the oil discharge passage 45a, the oil storage is less, and excessive lubricating oil is also avoided from being pushed to the thrust surface 42, thereby avoiding excessive oil from being sucked into the scroll mechanism, which is beneficial to control the oil circulation rate of the compressor.

[0046] Preferably, the length of the oil inlet 452a extending along the circumferential direction of the oil discharge passage 45a is not more than half of the circumference of the oil discharge passage 45a, so as to ensure that the lubricating oil can be sufficiently guided into the oil discharge passage 45a without easily bypassing the protrusion 450.

[0047] Those skilled in the art can understand that, although the design of the oil discharge passage 45a being formed separately from the main bearing seat 40 is shown in Figure 5 , the oil discharge passage can also be formed integrally with the main bearing seat 40. That is, the inner side wall of the main bearing seat 40 (the support portion 48) is directly formed with the protrusion 450 arranged around the through hole 41, and the hollow cavity of the protrusion 450 directly communicates with the through hole 41. The main bearing seat 40 can also be directly formed with passages similar to the second portion 456 and the third portion 457 and communicating with the through hole 41, thereby collectively forming the oil discharge passage for discharging the lubricating oil from the chamber C0 to the outside of the main bearing seat.

[0048] In addition, due to the size limitation of reducing the small gap d between the outer peripheral wall of the orbiting scroll hub 33 and the inner side wall of the main bearing seat 40, the radial length of the protrusion 450 is increased and the flow area of the oil inlet 452a is increased, thereby increasing the oil discharge amount, and the inner side wall of the main bearing seat 40 is also provided with a groove 44 (see Figure 4 ). Preferably, the groove 44 is configured as a circular annular groove extending along the circumferential direction of the chamber C0, thereby facilitating overall machining and manufacturing. When viewed along the radial direction of the main bearing seat, the protrusion 450 at least partially overlaps with the groove 44, that is, the protrusion 450 is partially or completely located in the groove 44. In this way, the protrusion 450 can be as exposed as possible in the chamber C0, thereby ensuring the flow area of the oil inlet 452a.

[0049] Preferably, the oil inlet 452a extends from the bottom wall of the groove 44 extending substantially in the axial direction of the main bearing seat towards the first end face 451a, so as to maximize the flow area of the oil inlet 452a, thereby as much as possible to increase the oil discharge amount.

[0050] Preferably, the oil inlet 452a is located completely within the recess 44, or further, the protrusion 450 is located completely within the recess 44, when viewed in the radial direction of the main bearing seat 40, so as to avoid the limitation of the size of the small gap d on the protrusion 450 and the oil inlet 452a on the one hand, and to make full use of the guiding effect of the recess 44 on the lubricating oil, so that the lubricating oil is more easily introduced into the oil inlet 452a.

[0051] Those skilled in the art can understand that, although in the first embodiment of the present application, the first end face is configured to be completely closed, the first end face can also be configured to be partially open, such as Figure 6 as shown in the second embodiment according to the present application.

[0052] Referring to Figure 6 , the oil discharge pipe 45b of the second embodiment according to the present application is similar to the oil discharge pipe 45a of the first embodiment according to the present application, and also includes a first part 455, a second part 456 and a third part 457. The first part 455 is also configured as a substantially cylindrical shape, including a first end face 451b, a second end face opposite to the first end face, and a circumferential side wall connecting the first end face 451b and the second end face, and the circumferential side wall is provided with a sealing ring groove 454 for mounting a sealing ring. The remaining similar structures will not be described again. The difference between the oil discharge pipe 45b and the oil discharge pipe 45a is that the oil inlet 452b of the oil discharge pipe 45b includes a first opening part formed on the circumferential side wall 453 of the protrusion 450 and a second opening part formed on the first end face 451b, and the first opening part and the second opening part are communicated. Therefore, the lubricating oil can not only enter the oil discharge pipe 45b from the first opening part on the circumferential side wall 453 along the circumferential direction (or tangential direction) of the chamber C0, but also enter the oil discharge pipe 45b along a direction inclined to the circumferential direction of the chamber C0 and along the radial direction, so that the lubricating oil is more easily introduced into the oil discharge pipe 45b, thereby further improving the oil discharge efficiency. In addition, the first opening part and the second opening part communicated with each other also make the flow area of the oil inlet 452b larger, further improving the oil discharge amount. In addition, as shown in Figure 6 , preferably, the second opening part occupies a part of the first end face 451b, and the remaining part of the first end face 451b except the second opening part is closed, so as to ensure that the lubricating oil can be sufficiently guided into the oil discharge pipe 45b without easily flowing out of the oil discharge pipe 45b.

[0053] Figure 5 and Figure 6Only two exemplary embodiments under the concept of the present application are shown. It is understood by those skilled in the art that the present application is not limited to the above-described exemplary embodiments, but includes variations or combinations of the above-described various examples. For example, the first end surface can also be configured to be completely open, and the first and second opening portions of the oil inlet can also be configured to be not communicated with each other. In addition, the oil inlet can be configured to be in various shapes, such as a circular shape, an elliptical shape, a rectangular shape, and an irregular shape, as needed, and the oil inlet can also be configured to be one or more, as needed. For another example, although the oil discharge conduit is configured to include the first portion, the second portion, and the third portion in the embodiments, it is understood by those skilled in the art that the second and third portions can also be omitted.

[0054] The main bearing housing for a scroll compressor and the scroll compressor according to the preferred embodiments of the present application are described above in conjunction with specific embodiments. It is understood that the above description is merely exemplary and not limiting, and those skilled in the art can conceive of various modifications and changes in light of the above description without departing from the scope of the present application. Such modifications and changes are also included in the scope of protection of the present application.

Claims

1. A main bearing housing (40) for a scroll compressor (100), the main bearing housing including a support portion (48) and a chamber (C0) located inside the support portion (48) in a radial direction of the main bearing housing, the main bearing housing being provided with an oil drain pipe for communicating the chamber with the radially outer side of the main bearing housing, the oil drain pipe including a protrusion (450) protruding inward from the inner sidewall of the support portion along the radial direction and located within the chamber, the protrusion including a first end face (451a, 451b) and a circumferential sidewall (453) extending from the first end face, the protrusion including an oil inlet (452a, 452b). Its features are, The oil inlets (452a, 452b) are at least partially formed on the circumferential sidewall.

2. The main bearing housing (40) for a scroll compressor (100) according to claim 1, wherein, The portion of the oil inlet (452a, 452b) formed on the circumferential sidewall extends in the circumferential direction of the protrusion for a length not exceeding half the circumference of the protrusion.

3. The main bearing housing (40) for a scroll compressor (100) according to claim 1, wherein, A groove (44) is provided on the inner wall of the support portion, and the protrusion at least partially overlaps with the groove when viewed along the radial direction.

4. The main bearing housing (40) for a scroll compressor (100) according to claim 3, wherein, The groove is constructed as an annular groove extending along the circumferential direction of the chamber.

5. The main bearing housing (40) for a scroll compressor (100) according to claim 3, wherein, The groove includes a bottom wall extending generally along the axial direction of the main bearing housing, and the oil inlets (452a, 452b) extend from the bottom wall toward the first end face.

6. The main bearing housing (40) for a scroll compressor (100) according to claim 3, wherein, When viewed along the radial direction, the portion of the oil inlet (452a, 452b) formed on the circumferential sidewall is completely located within the groove.

7. The main bearing housing (40) for a scroll compressor (100) according to any one of claims 1 to 6, wherein, The portions of the oil inlets (452a, 452b) formed on the circumferential sidewall are generally oriented toward the compression direction in which the oil in the chamber is squeezed.

8. The main bearing housing (40) for a scroll compressor (100) according to any one of claims 1 to 6, wherein, The oil inlet (452a) is completely formed on the circumferential sidewall, and the first end face is completely closed.

9. The main bearing housing (40) for a scroll compressor (100) according to any one of claims 1 to 6, wherein, The oil inlet (452b) includes a first opening formed on the circumferential sidewall and a second opening formed on the first end face, wherein the remaining portion of the first end face except for the second opening is closed.

10. The main bearing housing (40) for a scroll compressor (100) according to claim 9, wherein, The first opening is connected to the second opening.

11. The main bearing housing (40) for a scroll compressor (100) according to any one of claims 1 to 6, wherein the support portion includes a through hole (41) extending from the inner sidewall of the support portion to the outer side of the main bearing housing. in, The oil drain pipe is integrally formed with the main bearing housing, and the oil drain pipe includes the through hole and the protrusion formed around the through hole; or The oil drain pipe is formed separately from the main bearing housing, wherein the oil drain pipe is inserted into the through hole and partially protrudes from the through hole toward the chamber to form the protrusion.

12. A scroll compressor (100), characterized in that, The scroll compressor includes a main bearing housing (40) according to any one of claims 1 to 11.

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