Main bearing, pump body assembly and compressor

Abstract

The utility model relates to the technical field of compressors, and discloses a main bearing. The main bearing comprises a main bearing neck, a central through hole is formed in the main bearing neck in the axial direction, an oil guide groove is formed in the hole wall of the central through hole, and the oil guide groove spirally extends in the axial direction of the main bearing neck; wherein the width of the oil guide groove is H, the inner diameter of the central through hole is D, and H / D is larger than or equal to 0.15 and smaller than or equal to 0.2. The spiral oil guide groove is formed in the hole wall of the central through hole, lubricating oil can be more directly conveyed to key parts needing to be lubricated, a lubricating film is formed, and therefore it is guaranteed that the main bearing is fully lubricated in the running process, friction and abrasion are reduced, and the service life of the main bearing is prolonged. The range of the ratio of the width H of the oil guide groove to the inner diameter D of the central through hole is limited to be larger than or equal to 0.15 and smaller than or equal to 0.2, the lubricating effect and the strength of the main bearing can be within the balance range, the lubricating effect and the oil pumping amount of the main bearing are effectively improved, and it is ensured that the sufficient oil pumping amount enables the main bearing to be fully lubricated. The utility model further discloses a pump body assembly and a compressor.

Description

Technical Field

[0001] The present application relates to the technical field of compressors, and in particular to a main bearing, a pump body assembly and a compressor. Background Art

[0002] At present, the existing rotary compressor mainly relies on the oil guide plate arranged in the crankshaft to rotate and supply oil, which may cause insufficient oil supply to the crankshaft. Insufficient oil supply causes a thin lubricating oil film, which can easily cause wear between the crankshaft and the bearing, and then cause damage to the compressor.

[0003] The related technology provides a self-lubricating crankshaft, in which a spiral oil guide groove is opened on the outer surface of the short half-shaft of the crankshaft. When working, the spiral oil guide groove rotates at high speed with the crankshaft, which increases the oiling height, enhances the lubrication of the main and secondary bearings and eccentric circle parts of the crankshaft, increases the oil film thickness, and improves the reliability of the compressor.

[0004] In the process of implementing the embodiments of the present disclosure, it is found that there are at least the following problems in the related art:

[0005] In the related art, a spiral oil guide groove is provided on the outer surface of the short half-shaft of the crankshaft. When lubricating the main bearing, the spiral oil guide groove cannot reach the key parts of the main bearing that need lubrication in a timely and accurate manner, resulting in low lubrication efficiency.

[0006] It should be noted that the information disclosed in the above background technology section is only used to enhance the understanding of the background of the present application, and therefore may include information that does not constitute the prior art known to ordinary technicians in the field. Utility Model Content

[0007] In order to provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. The summary is not an extensive review, nor is it intended to identify key / critical components or delineate the scope of protection of these embodiments, but rather serves as a prelude to the detailed description that follows.

[0008] The disclosed embodiments provide a main bearing and a compressor, so that lubricating oil can be more directly delivered to key parts requiring lubrication through oil guide grooves on the main bearing, thereby improving the lubrication of the main bearing and the amount of oil pumped.

[0009] According to a first aspect of an embodiment of the utility model, a main bearing is provided, comprising: a main bearing neck, a central through hole is provided in the axial direction, an oil guide groove is opened in the hole wall of the central through hole, and the oil guide groove extends in a spiral shape along the axial direction of the main bearing neck; wherein, the width of the oil guide groove is H, the inner diameter of the central through hole is D, and 0.15≤H / D≤0.2.

[0010] Optionally, the ratio of the oil guide groove width to the inner diameter of the central through hole is H / D=0.175.

[0011] Optionally, the oil guide groove has a depth of T, 0.23≤T / H≤0.28.

[0012] Optionally, the ratio of the oil guiding groove depth to the oil guiding groove width is T / H=0.255.

[0013] Optionally, the starting angle of the oil guide groove is α, 20°≤α≤90°; the ending angle of the oil guide groove is β, 90°≤β≤180°.

[0014] Optionally, the starting angle α of the oil guiding groove is 45°, and the ending angle β of the oil guiding groove is 140°.

[0015] According to a second aspect of an embodiment of the utility model, a pump body assembly is provided, comprising a main bearing as described in any one of the above embodiments.

[0016] Optionally, the pump body assembly further comprises: a cylinder, which is arranged adjacent to the main bearing; wherein the starting position of the oil guide groove is at the high-pressure side of the cylinder, and the ending position of the oil guide groove is at the low-pressure side of the cylinder.

[0017] According to a third aspect of an embodiment of the utility model, a compressor is provided, comprising a pump body assembly as described in the above embodiment.

[0018] Optionally, the compressor comprises a high speed compressor having an operating frequency greater than or equal to 140 Hz.

[0019] The main bearing, pump assembly and compressor provided by the embodiments of the present disclosure can achieve the following technical effects:

[0020] The spiral oil guide groove is opened on the wall of the center through hole, which can effectively distribute the lubricating oil to the friction surface of the main bearing, and more directly transport the lubricating oil to the key parts that need lubrication to form a lubricating film, thereby ensuring that the main bearing is fully lubricated during operation, effectively improving the lubrication effect of the main bearing, reducing friction and wear, and extending the service life of the main bearing. The oil guide groove is directly opened on the main bearing, which can more directly, quickly and accurately guide the lubricating oil into the friction surface of the main bearing, thereby improving the lubrication efficiency. The ratio range of the oil guide groove width H to the inner diameter D of the center through hole is limited to 0.15≤H / D≤0.2, which can make the lubrication effect and strength of the main bearing within a balanced range, effectively improve the lubrication effect and oil pumping amount of the main bearing, and ensure that the main bearing is fully lubricated with sufficient oil pumping amount.

[0021] The above general description and the following description are exemplary and explanatory only and are not intended to limit the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] One or more embodiments are exemplarily described by corresponding drawings, which do not limit the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements, and the drawings do not constitute a scale limitation, and wherein:

[0023] Figure 1 is a schematic structural diagram of a main bearing provided by an embodiment of the present disclosure;

[0024] Figure 2 is a schematic structural diagram of another main bearing provided by an embodiment of the present disclosure;

[0025] Figure 3 yes Figure 2 A partial enlarged schematic diagram of the portion A shown;

[0026] Figure 4 is a schematic diagram of an oil guide groove provided in an embodiment of the present disclosure;

[0027] Figure 5 is a schematic structural diagram of a pump assembly provided by an embodiment of the present disclosure;

[0028] Figure 6 is a structural schematic diagram of a compressor provided by an embodiment of the present disclosure;

[0029] Figure 7 is a schematic structural diagram of a secondary bearing provided by an embodiment of the present disclosure;

[0030] Figure 8 It is a schematic structural diagram of another auxiliary bearing provided in an embodiment of the present disclosure.

[0031] Reference numerals:

[0032] 10: main bearing; 11: main bearing neck; 12: center through hole; 13: oil guide groove;

[0033] 20: Cylinder;

[0034] 30: pump assembly; 31: crankshaft; 311: long shaft; 312: short shaft; 32: auxiliary bearing; 321: oil channel;

[0035] H: width of oil guide groove; T: depth of oil guide groove; α: starting angle of oil guide groove; β: ending angle of oil guide groove; D: inner diameter of center through hole. DETAILED DESCRIPTION

[0036] In order to be able to understand the features and technical contents of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure is described in detail below in conjunction with the accompanying drawings. The attached drawings are for reference only and are not used to limit the embodiments of the present disclosure. In the following technical description, for the convenience of explanation, a full understanding of the disclosed embodiments is provided through multiple details. However, one or more embodiments can still be implemented without these details. In other cases, to simplify the drawings, well-known structures and devices can be simplified for display.

[0037] The terms "first", "second", etc. in the specification and claims of the disclosed embodiments and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the terms used in this way can be interchanged where appropriate for the disclosed embodiments described herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions.

[0038] In the embodiments of the present disclosure, the terms "upper", "lower", "inside", "middle", "outside", "front", "back" and the like indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. These terms are mainly intended to better describe the embodiments of the present disclosure and their embodiments, and are not intended to limit the indicated devices, elements or components to have a specific direction, or to be constructed and operated in a specific direction. Moreover, in addition to being used to indicate directions or positional relationships, some of the above terms may also be used to indicate other meanings. For example, the term "upper" may also be used to indicate a certain dependency or connection relationship in certain circumstances. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0039] In addition, the terms "disposed", "connected", and "fixed" should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection, or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, elements, or components. For those of ordinary skill in the art, the specific meanings of the above terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0040] Unless otherwise stated, the term "plurality" means two or more.

[0041] In the embodiment of the present disclosure, the character " / " indicates that the preceding and following objects are in an "or" relationship. For example, A / B indicates: A or B.

[0042] The term "and / or" is a description of the association relationship between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or, A and B.

[0043] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present disclosure may be combined with each other.

[0044] Combination Figure 1-4 As shown, the embodiment of the present disclosure provides a main bearing 10, including a main bearing neck 11, the main bearing neck 11 is provided with a center through hole 12 in the axial direction, the hole wall of the center through hole 12 is provided with an oil guide groove 13, and the oil guide groove 13 extends in a spiral shape along the axial direction of the main bearing neck 11; wherein, the width of the oil guide groove 13 is H, the inner diameter of the center through hole 12 is D, and 0.15≤H / D≤0.2.

[0045] The oil guide groove 13 extends in a spiral shape to adapt to the rotation of the crankshaft 31, so that the lubricating oil can be continuously guided to the main bearing 10 when the crankshaft 31 rotates, and a dynamic lubricating film can be formed during the rotation of the crankshaft 31, thereby reducing friction and wear.

[0046] By adopting the main bearing 10 provided by the embodiment of the present disclosure, a spiral oil guide groove 13 is provided on the hole wall of the central through hole 12, so that the lubricating oil can be effectively distributed to the friction surface of the main bearing 10, and the lubricating oil can be more directly delivered to the key parts that need lubrication to form a lubricating film, thereby ensuring that the main bearing 10 is fully lubricated during operation, effectively improving the lubrication effect of the main bearing 10, reducing friction and wear, and extending the service life of the main bearing 10. The oil guide groove 13 is directly provided on the main bearing 10, which can more directly, quickly and accurately guide the lubricating oil into the friction surface of the main bearing 10, thereby improving the lubrication efficiency.

[0047] Since the main bearing 10 pumps a large amount of oil, in order to meet the lubricating oil demand under high-speed rotation of the compressor, it is necessary to limit the relevant parameters of the oil guide groove 13.

[0048] The main bearing 10 is sleeved on the outside of the crankshaft 31. During the rotation of the crankshaft 31, the friction between the surface roughness of the crankshaft 31 and the main bearing 10 and the lubricating oil causes the lubricating oil in the crankshaft 31 to flow into the main bearing 10 along the rotation angle. The oil guide groove width H is limited within a certain range to ensure that sufficient lubricating oil can flow into the main bearing 10 through the oil guide groove 13, and at the same time, it can avoid affecting the structural strength and stability of the main bearing 10.

[0049] The width H of the oil guide groove and the inner diameter D of the central through hole maintain an appropriate ratio, so that the oil guide groove 13 occupies an appropriate ratio of the inner wall surface area of ​​the main bearing 10 , ensuring the balance between the lubrication effect and the strength of the main bearing 10 .

[0050] When the ratio of the oil guide groove width H to the inner diameter D of the central through hole is greater than or equal to 0.15, the lubricating oil can flow smoothly, so that the main bearing 10 is fully lubricated, friction and wear are avoided, and the service life of the main bearing 10 is extended.

[0051] When the ratio of the oil guide groove width H to the inner diameter D of the center through hole is less than or equal to 0.2, the proportion of the oil guide groove 13 to the inner wall surface area of ​​the main bearing 10 can be limited to a relatively small range, thereby ensuring the structural strength of the main bearing 10, especially under high load or high-speed operation, and avoiding deformation or damage of the main bearing 10.

[0052] In the disclosed embodiment, a spiral oil guide groove 13 is provided on the main bearing 10 for pumping oil, and the ratio range of the oil guide groove width H to the inner diameter D of the center through hole is limited to 0.15≤H / D≤0.2, which can make the lubrication effect of the main bearing 10 and the strength of the main bearing 10 within a balanced range, effectively improve the lubrication effect and oil pumping amount of the main bearing 10, and ensure that the main bearing 10 is adequately lubricated.

[0053] It will be appreciated that H / D may be 0.15, 0.16, 0.18, 0.19, 0.20, and so on.

[0054] Optionally, combined Figure 3-4 As shown, the ratio of the oil guide groove width H to the inner diameter D of the central through hole is H / D=0.175.

[0055] When the ratio of the oil guide groove width H to the center through hole inner diameter D is H / D=0.175, the oil guide groove width H can accommodate enough lubricating oil, the main bearing 10 has a large oil pumping amount, and ensures that the lubricating oil can flow smoothly to the parts that need lubrication. At the same time, the ratio of the oil guide groove width H to the center through hole inner diameter D is appropriate, and the structural strength of the main bearing 10 can also be avoided from being affected.

[0056] Optionally, combined Figure 3-4 As shown, the depth of the oil guide groove 13 is T, and 0.23≤T / H≤0.28.

[0057] During the rotation of the crankshaft 31 relative to the main bearing 10, the crankshaft 31 can take away the lubricating oil in the oil guide groove 13 through friction when passing through the surface of the oil guide groove 13, and the lubricating oil moves with the crankshaft 31 to achieve lubrication. The ratio of the oil guide groove depth T to the oil guide groove width H has a certain influence on the oil guide effect, and limiting the ratio within a reasonable range can ensure that the main bearing 10 is properly lubricated.

[0058] When T / H is less than or equal to 0.28, the oil guide groove 13 is relatively shallow and wide, which can reduce the flow resistance of the lubricating oil and the difficulty of the lubricating oil flowing from the oil guide groove 13 to the surface of the crankshaft 31, so that the lubricating oil can quickly reach the lubrication point of the main bearing 10. At the same time, it can also reduce the manufacturing cost and difficulty.

[0059] When T / H is greater than or equal to 0.23, it can ensure that the oil guide groove 13 has a certain depth, so that the oil guide groove 13 can accommodate enough lubricating oil, ensuring that the main bearing 10 can be adequately lubricated during operation, thereby avoiding friction and wear.

[0060] The disclosed embodiment optimizes the width and depth of the oil guide groove 13 and limits the ratio range of the oil guide groove depth T to the oil guide groove width H to 0.23≤T / H≤0.28, so that the oil guide groove 13 can achieve a balance between the amount of lubricating oil contained and the difficulty of the lubricating oil moving to the crankshaft 31. While ensuring a sufficient amount of pumped oil, the lubricating oil in the oil guide groove 13 can also flow more easily to the surface of the crankshaft 31 to achieve lubrication, thereby effectively improving the lubrication effect of the main bearing 10.

[0061] It will be appreciated that T / H may be 0.23, 0.24, 0.25, 0.26, 0.27, 0.28, and so on.

[0062] Optionally, combined Figure 3-4 As shown, the ratio of the oil guide groove depth T to the oil guide groove width H is T / H=0.255.

[0063] When the ratio of the oil guide groove depth T to the oil guide groove width H is T / H=0.255, the main bearing 10 can ensure a larger amount of pumped oil, and the lubricating oil in the oil guide groove 13 can flow to the surface of the crankshaft 31 more easily.

[0064] Optionally, combined Figure 3-4 As shown, the ratio of the oil guide groove width H to the inner diameter D of the central through hole is H / D=0.175, and the ratio of the oil guide groove depth T to the oil guide groove width H is T / H=0.255.

[0065] A simulation comparison experiment was conducted on the original scheme and the embodiment of the present disclosure. Under the same other conditions, the H / D of the oil guide groove of the original scheme is 0.124, T / H is 0.43, and the H / D of the oil guide groove 13 of the embodiment of the present disclosure is 0.175, T / H is 0.255. The simulation experiment found that the oil supply per unit time of the main bearing 10 of the embodiment of the present disclosure is increased by 1.18 times compared with the original scheme.

[0066] Optionally, combined Figure 3-4 As shown, the starting angle of the oil guide groove 13 is α, 20°≤α≤90°; the ending angle of the oil guide groove 13 is β, 90°≤β≤180°.

[0067] Within this range, the amount of oil directed upward by the oil groove is relatively large, which can ensure the lubrication effect of the crankshaft 31 and the bearings.

[0068] The vane slot is a key component in the compressor, and the position and movement state of the vane slot directly affect the compression efficiency and stability of the compressor. The center line of the vane slot is usually located at the center of the compressor, so the starting angle and the ending angle of the oil guide groove 13 in this application are based on the center line of the vane slot as a reference line.

[0069] The starting angle of the oil guide groove 13 is the angle at which the oil guide groove 13 starts. When the starting angle α is greater than or equal to 20°, the time for the lubricating oil to enter the working area of ​​the main bearing 10 will be shortened, thereby providing more sufficient lubrication for the main bearing 10 in the initial stage of the compressor operation, reducing the risk of wear during startup, and avoiding the risk of damage to the main bearing 10 due to friction overheating.

[0070] At the same time, when the starting angle α is less than or equal to 90°, it can effectively prevent the lubricating oil from entering the working area of ​​the main bearing 10 too early, thereby ensuring the uniform distribution of the lubricating oil inside the main bearing 10, reducing the risk of wear of the main bearing 10, and ensuring the operating efficiency and life of the compressor.

[0071] The embodiment of the present disclosure limits the angle range of the starting angle to 20°≤α≤90°, which can ensure the lubrication efficiency and distribution uniformity of the lubricating oil at the same time. It can ensure that the main bearing 10 can be fully lubricated while avoiding excessive oil accumulation or leakage. It ensures that effective distribution begins when the main bearing 10 is started, and the oil can smoothly enter the oil guide groove 13 and start its lubrication path to form a uniform oil film, reduce starting friction and wear, and effectively improve the lubrication effect of the main bearing 10, thereby extending the service life of the main bearing 10 and improving energy efficiency.

[0072] The end angle of the oil guide groove 13 is the angle at which the oil guide groove 13 ends. When the end angle β is greater than or equal to 90°, the lubricating oil can be fully distributed in the working area of ​​the main bearing 10, especially when rotating at high speed, a sufficient oil film thickness can be formed to reduce the friction and wear of the bearing. At the same time, the flow path of the lubricating oil can be extended, the number of circulations of the lubricating oil inside the bearing can be increased, and the oil can be prevented from being discharged from the oil guide groove 13 too early, thereby ensuring sufficient lubrication time for the main bearing 10, thereby improving the heat dissipation efficiency and cleaning ability of the main bearing 10.

[0073] When the end angle β is less than or equal to 180°, it is possible to prevent the lubricating oil from prematurely gathering or stagnating in a certain area of ​​the main bearing 10, so that the lubricating oil can be smoothly discharged from the end of the oil guide groove 13, avoiding local overheating and reducing local pressure, thereby reducing the risk of fatigue and wear of the main bearing 10. It is also possible to effectively reflux the lubricating oil in the oil guide groove 13, making the oil film thickness more uniform, and enhancing the lubrication effect and overall performance of the main bearing 10.

[0074] The disclosed embodiment limits the angle range of the termination angle to 90°≤β≤180°, which enables the oil in the oil guide groove 13 to have a good oil film thickness and flow effect at the same time. The lubricating oil can be evenly distributed on the entire bearing surface, and it can also ensure that the oil can be discharged smoothly after flowing through the entire bearing, and may return to the lubrication system of the compressor, thereby forming an effective cycle, providing stable and appropriate lubrication for the main bearing 10, and effectively improving the lubrication effect of the main bearing 10.

[0075] Optionally, combined Figure 3-4 As shown, the starting angle α of the oil guide groove 13 is 45°, and the ending angle β of the oil guide groove 13 is 140°.

[0076] When the starting angle α of the oil guide groove 13 is 45° and the ending angle β of the oil guide groove 13 is 140°, the flow path of the lubricating oil can be optimized, and the lubricating oil will enter the working area of ​​the main bearing 10 from one side of the main bearing 10 at a moderate angle, so that the lubricating oil forms a good flow, thereby achieving effective lubrication. At the same time, the lubricating oil can also cover a larger area of ​​the main bearing 10 along the oil guide groove 13, which can ensure that the entire inner surface of the main bearing 10 including the outlet area of ​​the main bearing 10 can be fully lubricated, reduce wear and maintain the performance of the main bearing 10.

[0077] Combination Figure 5 As shown, an embodiment of the present disclosure provides a pump body assembly 30, comprising a main bearing 10 as described in any of the above embodiments.

[0078] The pump body assembly 30 provided in the embodiment of the present disclosure includes the main bearing 10 described in any one of the above embodiments, and thus has all the beneficial effects of the main bearing 10 described in any one of the above embodiments, which will not be described in detail here.

[0079] Optionally, combined Figure 5 As shown, the pump body assembly 30 also includes a cylinder 20, which is arranged adjacent to the main bearing 10; wherein the starting position of the oil guide groove 13 is at the high-pressure side of the cylinder 20, and the ending position of the oil guide groove 13 is at the low-pressure side of the cylinder 20.

[0080] Since the pressure on the high-pressure side of the cylinder 20 is higher than that on the low-pressure side, the starting position of the oil groove is located on the high-pressure side of the cylinder 20, and the ending position of the oil guide groove 13 is located on the low-pressure side of the cylinder 20, so that the pressure gradient can be used to promote the flow of lubricating oil. The lubricating oil will naturally flow from the high-pressure area to the low-pressure area, thereby achieving more efficient lubrication.

[0081] Optionally, combined Figure 5 and Figure 7 As shown, the pump assembly 30 also includes a crankshaft 31 and a secondary bearing 32. The crankshaft includes a long shaft 311 and a short shaft 312. The main bearing 10 is sleeved on the outside of the long shaft 311, and the secondary bearing 32 is sleeved on the outside of the short shaft 312. The contact length between the main bearing 10 and the long shaft 311 is M (as shown in FIG. Figure 6 As shown), the contact length between the secondary bearing 32 and the short shaft 312 is N (as shown Figure 7 As shown), 0.6≤N / M≤0.8.

[0082] The disclosed embodiment limits the ratio range of the contact length N between the secondary bearing 32 and the short shaft 312 and the contact length M between the main bearing 10 and the long shaft 311 to 0.6≤N / M≤0.8. By increasing the height of the secondary bearing 32, a better supporting area can be provided for the short shaft 312, thereby reducing the swing of the long shaft 311, effectively improving the oil film thickness between the crankshaft 31 and the main bearing 10 and the secondary bearing 32, and improving the stability of the oil film thickness, thereby improving the lubrication effect between the main bearing 10 and the long shaft 311, and between the secondary bearing 32 and the short shaft 312, reducing friction, and reducing thermal stress and wear.

[0083] Optionally, combined Figure 7-8 As shown, the auxiliary bearing 32 is provided with an oil passage 321 , and the oil passage 321 extends along the axial direction of the auxiliary bearing 32 .

[0084] The oil passage 321 is provided in the auxiliary bearing 32 so that the lubricating oil can be evenly distributed on the entire contact surface of the auxiliary bearing 32 , thereby improving the lubrication effect on the auxiliary bearing 32 and reducing the risk of wear caused by friction between the auxiliary bearing 32 and the crankshaft 31 .

[0085] Optionally, the oil passage 321 extends vertically along the axial direction of the auxiliary bearing 32 .

[0086] The vertical extension of the oil passage 321 can make the structure of the oil passage 321 relatively simple, and can directly guide the lubricating oil from the oil pool to the auxiliary bearing 32, and is easier to manufacture and maintain.

[0087] It is understandable that the oil passage 321 may also extend in a spiral shape or other shapes along the axial direction of the auxiliary bearing 32 , which is not limited here.

[0088] Combination Figure 6As shown, an embodiment of the present disclosure provides a compressor, comprising a pump body assembly 30 as described in any one of the above embodiments.

[0089] The compressor provided in the embodiment of the present disclosure includes the pump body assembly 30 described in any one of the above embodiments, and thus has all the beneficial effects of the pump body assembly 30 described in any one of the above embodiments, which will not be described in detail here.

[0090] Optionally, the compressor comprises a high speed compressor having an operating frequency greater than or equal to 140 Hz.

[0091] The compressor mentioned in the above disclosed embodiment is suitable for a compressor running at a high speed. The operating frequency of the compressor is limited to be greater than or equal to 140 Hz, which can achieve a high speed environment.

[0092] The above description and the accompanying drawings sufficiently illustrate the embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Unless explicitly required, individual components and functions are optional, and the order of operations may vary. Portions and features of some embodiments may be included in or replace portions and features of other embodiments. The embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A main bearing, characterized in that: include: The main bearing neck is provided with a central through hole along the axial direction, and the hole wall of the central through hole is provided with an oil guide groove, which extends in a spiral shape along the axial direction of the main bearing neck; Among them, the width of the oil guide groove is H, the inner diameter of the central through hole is D, and 0.15≤H / D≤0.

2.

2. The main bearing according to claim 1, characterized in that: The ratio of the oil guide groove width to the inner diameter of the central through hole is H / D=0.

175.

3. The main bearing according to claim 1, characterized in that: The depth of the oil guide groove is T, 0.23≤T / H≤0.

28.

4. The main bearing according to claim 3, characterized in that: The ratio of the oil guide groove depth to the oil guide groove width is T / H=0.

255.

5. The main bearing according to any one of claims 1 to 4, characterized in that: The starting angle of the oil guide groove is α, 20°≤α≤90°; the ending angle of the oil guide groove is β, 90°≤β≤180°.

6. The main bearing according to claim 5, characterized in that: The starting angle α of the oil guide groove is 45°, and the ending angle β of the oil guide groove is 140°.

7. A pump assembly, characterized in that: Comprising a main bearing as claimed in any one of claims 1 to 6.

8. The pump assembly according to claim 7, characterized in that: Also includes: A cylinder is disposed adjacent to the main bearing; The starting position of the oil guide groove is at the high-pressure side of the cylinder, and the ending position of the oil guide groove is at the low-pressure side of the cylinder.

9. A compressor, characterized in that: Comprising a pump body assembly as described in any one of claims 7 or 8.

10. The compressor according to claim 9, characterized in that The compressor includes a high speed compressor that can operate at a frequency greater than or equal to 140 Hz.

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