Compressor and refrigeration equipment

Abstract

The utility model discloses a compressor and refrigeration equipment, and relates to the technical field of compressors, the compressor comprises a motor assembly, a crankshaft and a bearing assembly; the crankshaft is connected with the motor assembly and provided with a center oil hole, the connecting section of the crankshaft is provided with an oil outlet, one end of the oil outlet is communicated with the center oil hole, and the other end of the oil outlet penetrates through the outer surface of the connecting section. The bearing assembly is provided with a shaft hole and rotationally connected to the connecting section through the shaft hole, and an anti-attrition layer is arranged on the inner wall of the shaft hole. By arranging the anti-friction layer, the friction force between the crankshaft and the shaft hole can be reduced, the lubricity between the crankshaft and the shaft hole is improved, and the abrasion of the crankshaft and the bearing assembly is reduced. In addition, by arranging the oil outlet hole, lubricating oil can flow between the outer surface of the connecting section and the hole wall of the shaft hole through the center oil hole and the oil outlet hole, the purpose of oil lubrication is achieved, the crankshaft and the bearing assembly are kept in a good lubrication state all the time, and abrasion of the crankshaft and the bearing assembly can be further reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, in particular to a compressor and a refrigeration device. Background Art

[0002] With the high speed and high efficiency of rotary compressors and the use of high-thickness motors in specific environments, it is particularly important to ensure the coaxiality of the stator and rotor of the motor during operation and reduce the deformation of the crankshaft end to ensure the reliability of the rotary compressor. To this end, some rotary compressors achieve the above purpose by installing motor bearings at the end of the motor. However, when conventional sliding bearings are used as motor bearings, the motor bearings themselves are prone to wear and have relatively poor reliability, which affects the overall reliability of the rotary compressor. Utility Model Content

[0003] The utility model aims to solve at least one of the technical problems existing in the prior art. To this end, the utility model provides a compressor that can reduce the wear of the crankshaft and the bearing assembly and improve the reliability of the compressor.

[0004] The utility model also provides a refrigeration device having the compressor.

[0005] A compressor according to an embodiment of the first aspect of the utility model comprises:

[0006] Motor components;

[0007] A crankshaft connected to the motor assembly, the crankshaft being provided with a central oil hole extending axially along the crankshaft, the crankshaft comprising a connecting section, the connecting section being provided with an oil outlet hole, one end of the oil outlet hole being connected to the central oil hole, and the other end of the oil outlet hole penetrating the outer surface of the connecting section; and

[0008] The bearing assembly is provided with an axial hole, the bearing assembly is rotatably connected to the connecting section through the axial hole, and the inner wall of the axial hole is provided with a friction-reducing layer.

[0009] The compressor according to the embodiment of the utility model has at least the following beneficial effects:

[0010] By providing a friction-reducing layer on the inner wall of the shaft hole, the friction between the crankshaft connecting section and the inner wall of the shaft hole can be reduced, the lubricity between the crankshaft and the shaft hole can be improved, and the wear of the crankshaft and the bearing assembly can be reduced. In addition, by providing an oil outlet hole connected to the central oil hole on the connecting section of the crankshaft, and the oil outlet hole is connected to the gap between the outer surface of the connecting section and the inner wall of the shaft hole, when the compressor is running, the lubricating oil can flow through the central oil hole and the oil outlet hole to the space between the outer surface of the connecting section and the inner wall of the shaft hole, so that the lubricating oil exists between the crankshaft connecting section and the inner wall of the shaft hole, achieving the purpose of oil lubrication, so that the crankshaft and the bearing assembly always maintain a good lubrication state, which can further reduce the wear of the crankshaft and the bearing assembly, and effectively improve the reliability of the bearing assembly and the compressor.

[0011] According to some embodiments of the present utility model, the bearing assembly comprises:

[0012] A first bearing is provided with a bearing inner hole; and

[0013] A shaft sleeve is arranged in the inner hole of the bearing, and the inner wall of the shaft sleeve is provided with the friction-reducing layer.

[0014] According to some embodiments of the utility model, the sleeve includes a base layer and a connecting layer, the base layer and the connecting layer are stacked along the radial direction of the sleeve, the connecting layer is located on the inner side of the base layer, and the friction reducing layer is arranged on the side of the connecting layer away from the base layer.

[0015] According to some embodiments of the present utility model, a groove body is provided on the outer surface of the connecting section, the groove body is communicated with the oil outlet hole, and the groove body and the inner wall of the sleeve define an oil outlet groove.

[0016] According to some embodiments of the present invention, at least a portion of the side wall of the trough body is inclined relative to the axis of the oil outlet hole.

[0017] According to some embodiments of the present invention, the maximum length of the opening of the groove body along the axial direction of the crankshaft is L1, and the axial length of the sleeve is L, which satisfies: 0.1≤L1 / L≤0.75.

[0018] According to some embodiments of the present invention, along the circumferential direction of the crankshaft, the maximum central angle corresponding to the portion removed by the connecting segment to form the groove body is β, which satisfies: 20°≤β≤60°.

[0019] According to some embodiments of the present utility model, the inner diameter of the oil outlet hole is d, and the maximum outer diameter of the connecting section is D, satisfying: 5d≤D≤9d.

[0020] According to some embodiments of the present utility model, the compressor further comprises a pump body assembly;

[0021] The crankshaft also includes an eccentric portion, the eccentric portion and the connecting section are respectively located at the axial ends of the crankshaft, and the eccentric portion is connected to the pump body assembly; wherein, an angle α is formed between a first reference plane passing through the axis of the center oil hole and the axis of the oil outlet hole and a second reference plane passing through the center axis of the eccentric portion and the axis of the center oil hole, satisfying: 90°≤α≤270°.

[0022] According to some embodiments of the present utility model, the crankshaft includes a top end surface, and the central oil hole extends axially along the crankshaft to penetrate the top end surface;

[0023] The compressor further comprises an oil baffle, which is arranged in the central oil hole and between the top end surface and the oil outlet hole, and is used for blocking a part of the central oil hole.

[0024] The refrigeration device according to the second embodiment of the utility model comprises the compressor described in any one of the above embodiments.

[0025] The refrigeration device according to the embodiment of the utility model has at least the following beneficial effects:

[0026] In the compressor using the first embodiment, the compressor can reduce the friction between the crankshaft connecting section and the inner wall of the shaft hole by providing a friction-reducing layer on the inner wall of the shaft hole, improve the lubricity between the crankshaft and the shaft hole, and reduce the wear of the crankshaft and the bearing assembly. In addition, an oil outlet hole connected to the central oil hole is provided on the connecting section of the crankshaft, and the oil outlet hole is connected to the gap between the outer surface of the connecting section and the inner wall of the shaft hole. When the compressor is running, the lubricating oil can flow through the central oil hole and the oil outlet hole to the outer surface of the connecting section and the inner wall of the shaft hole, so that the lubricating oil exists between the crankshaft connecting section and the inner wall of the shaft hole, achieving the purpose of oil lubrication, so that the crankshaft and the bearing assembly are always in a good lubrication state, which can further reduce the wear of the crankshaft and the bearing assembly, and effectively improve the reliability of the bearing assembly and the compressor.

[0027] Additional aspects and advantages of the present invention will be given in part in the following description, and in part will become apparent from the following description, or will be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] The present invention is further described below with reference to the accompanying drawings and embodiments, wherein:

[0029] Figure 1 A cross-sectional view of a partial structure of a compressor according to an embodiment of the utility model;

[0030] Figure 2 for Figure 1 A partial enlarged view of the middle A;

[0031] Figure 3 A cross-sectional view of a shaft sleeve along the axial direction of an embodiment of the utility model;

[0032] Figure 4 for Figure 3 A partial enlarged view of point B in the middle;

[0033] Figure 5 This is a schematic structural diagram of a crankshaft according to an embodiment of the utility model;

[0034] Figure 6 A schematic structural diagram of a crankshaft in another embodiment of the utility model;

[0035] Figure 7 for Figure 6 A cross-sectional view of the middle crankshaft along section CC;

[0036] Figure 8 for Figure 6 A partial enlarged view of point E in the middle;

[0037] Fig. 9 A graph showing the minimum oil film thickness changing with the length of the slot opening in the embodiment of the utility model;

[0038] Fig.10 It is a curve diagram showing the change of the minimum oil film thickness with the change of the central angle β in the embodiment of the utility model;

[0039] Fig.11 It is a radial cross-sectional view of a crankshaft according to an embodiment of the present utility model.

[0040] Figure Number:

[0041] Compressor 10;

[0042] Motor assembly 100; rotor 110; stator 120;

[0043] Crankshaft 200; central oil hole 210; connecting section 220; oil outlet hole 221; groove body 222; conical surface 222a;

[0044] Eccentric portion 230; first eccentric portion 230a; second eccentric portion 230b; oil blocking member 240; top end surface 250;

[0045] Bearing assembly 300; first bearing 310; bearing inner hole 311; sleeve 320; shaft hole 320a;

[0046] Base layer 321 ; connecting layer 322 ; friction reducing layer 323 ; second bearing 330 ; third bearing 340 . DETAILED DESCRIPTION

[0047] The embodiments of the present invention are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0048] In the description of the present invention, it should be understood that the descriptions involving orientation, such as the orientation or positional relationship indicated as up, down, etc., are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0049] In the description of the present utility model, "a plurality" refers to two or more than two. If there is a description of "first" or "second", it is only used for the purpose of distinguishing technical features, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0050] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, connecting, etc. should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present invention based on the specific content of the technical solution.

[0051] With the high speed and high efficiency of compressors and the use of high-thickness motors in specific environments, it is particularly important to ensure the coaxiality of the stator and rotor of the motor during operation and reduce the deformation of the crankshaft end to ensure the reliability of the compressor. To this end, some compressors achieve the above purpose by installing motor bearings at the end of the motor.

[0052] However, when conventional sliding bearings are used as motor bearings, on the one hand, the motor bearings themselves are prone to wear and have relatively poor reliability; on the other hand, the lubricating oil sprayed into the top space of the crankshaft flows into the gap between the crankshaft and the motor bearing under the action of gravity. The amount of lubricating oil in the gap is small and the oil film thickness is small, which makes it difficult to meet the lubrication performance under high-speed operation, causing increased wear of the crankshaft and motor bearings, affecting the service life and reliability of the motor bearings, and further affecting the overall reliability of the compressor.

[0053] In this regard, the present application provides a compressor, wherein the compressor may be a rotary compressor, a scroll compressor, or a vehicle-mounted compressor, and the rotary compressor will be described in detail below as an example.

[0054] Please refer to Figure 1 , Figure 1The compressor 10 includes a motor assembly 100 , a crankshaft 200 and a bearing assembly 300 .

[0055] The motor assembly 100 is connected to the crankshaft 200. Specifically, the motor assembly 100 includes a stator 120 and a rotor 110. Generally speaking, the stator 120 is fixedly connected to the housing of the compressor 10. The stator 120 is annular, and the rotor 110 is arranged in the inner ring of the stator 120, that is, the stator 120 is arranged around the rotor 110, and the crankshaft 200 is passed through the rotor 110 and is fixedly connected to the rotor 110. The rotor 110 can rotate relative to the stator 120. Under the action of the magnetic field, the rotor 110 can be driven to rotate relative to the stator 120, so that the rotor 110 drives the crankshaft 200 to rotate.

[0056] It can be understood that the compressor 10 also includes a pump body assembly (not shown), which is used to move under the drive of the motor assembly 100 and the crankshaft 200 to compress the refrigerant. Taking a two-cylinder rotary compressor as an example, the pump body assembly includes a first cylinder and a second cylinder, the first cylinder is arranged on the upper side of the second cylinder, and a partition is arranged between the first cylinder and the second cylinder. The first cylinder is provided with a first cavity and a first roller installed in the first cavity, and similarly, the second cylinder is provided with a second cavity and a second roller installed in the second cavity.

[0057] One end of the crankshaft 200 away from the motor assembly 100 can be sequentially penetrated in the first cylinder, the partition and the second cylinder. The crankshaft 200 can be provided with two eccentric parts 230, and the eccentric directions of the two eccentric parts 230 are different. For example, the eccentric directions of the two eccentric parts 230 are opposite, and the eccentric direction of the eccentric part 230 is the direction from the central axis of the crankshaft 200 toward the center of the eccentric part 230. The two eccentric parts 230 are arranged at intervals up and down and are respectively arranged in the first cavity and the second cavity, so that the first cylinder and the second cylinder are connected to the crankshaft 200 respectively. Specifically, the motor assembly 100 drives the crankshaft 200 to rotate, drives the two eccentric parts 230 to rotate eccentrically, drives the first cylinder and the second cylinder to move, thereby realizing the compression of the refrigerant in the first cavity and the second cavity.

[0058] It can be understood that since one end of the crankshaft 200 connected to the pump body assembly rotates eccentrically, in order to reduce the flexural deformation of the crankshaft 200, while improving the coaxiality of the stator 120 and the rotor 110 and preventing the stator 120 and the rotor 110 from scratching each other, the crankshaft 200 can be supported and positioned by the bearing assembly 300.

[0059] like Figure 1As shown, the bearing assembly 300 may include a second bearing 330 and a third bearing 340, the second bearing 330 is arranged on the upper side of the first cylinder, and the third bearing 340 is arranged on the lower side of the second cylinder, that is, the first cylinder and the second cylinder are arranged between the second bearing 330 and the third bearing 340. It can be understood that by arranging the second bearing 330 and the third bearing 340, the end of the crankshaft 200 provided with the eccentric portion 230 is supported and positioned to bear the reaction force of the compressed gas in the first cylinder and the second cylinder during the operation of the compressor 10, thereby improving the working stability of the first cylinder and the second cylinder.

[0060] In order to further reduce the flexural deformation of the end of the crankshaft 200, it is also necessary to support and position the other end of the crankshaft 200 (the end away from the pump body assembly, that is, the top end of the crankshaft 200).

[0061] Please refer to Figure 2 , Figure 2 for Figure 1 A partial enlarged view of the part A in the middle. The crankshaft 200 includes a connecting section 220, which is located at one end of the crankshaft 200 away from the pump body assembly, that is, the top part of the crankshaft 200, and the connecting section 220 is cylindrical. The bearing assembly 300 also includes an axial hole 320a, and the bearing assembly 300 is rotatably connected to the connecting section 220 through the axial hole 320a, thereby achieving support and positioning of the upper end of the crankshaft 200. It can be understood that there is a clearance fit between the connecting section 220 and the axial hole 320a.

[0062] Among them, the inner wall of the shaft hole 320a is provided with a friction-reducing layer, which can be made of non-rigid materials, for example, the friction-reducing layer can be made of materials such as polymer resin or graphite, which can reduce the friction between the shaft hole 320a and the connecting section 220 of the crankshaft 200, improve the lubricity between the crankshaft 200 and the shaft hole 320a, reduce the wear of the crankshaft 200 and the bearing assembly 300, thereby improving the reliability of the rotation of the crankshaft 200, and further improving the reliability of the compressor 10.

[0063] like Figure 2 As shown, the crankshaft 200 is provided with a central oil hole 210, and the central oil hole 210 extends along the axial direction of the crankshaft 200. Generally speaking, an oil pool is provided in the shell of the compressor 10, and the oil pool is used to store lubricating oil. The oil pool is located below the pump body assembly, and the lower end of the central oil hole 210 is open and connected to the oil pool. When the compressor 10 is running, the crankshaft 200 rotates at a high speed, and a continuous oiling state is formed in the central oil hole 210, so that the lubricating oil in the oil pool is transported upward through the central oil hole 210 to lubricate the pump body assembly, the crankshaft 200, etc., reduce wear, and can take away part of the heat generated during the rotation of the crankshaft 200 through the lubricating oil, thereby improving the reliability of the compressor 10.

[0064] Please continue to refer to Figure 2 In the embodiment of the present application, the connecting section 220 is provided with an oil outlet hole 221, one end of the oil outlet hole 221 is connected to the central oil hole 210, and the other end (indicating the end of the oil hole 221 away from the central oil hole 210, that is, the oil outlet end of the oil outlet hole 221) passes through the outer surface of the connecting section 220, that is, the oil outlet end of the oil outlet hole 221 is connected to the gap between the outer surface of the connecting section 220 and the inner wall of the shaft hole 320a.

[0065] Then, during the operation of the compressor 10, the lubricating oil can flow through the center oil hole 210 and the oil outlet hole 221 to the gap between the outer surface of the connecting section 220 and the inner wall of the shaft hole 320a, thereby providing lubrication to the contact area between the crankshaft 200 and the inner wall of the shaft hole 320a, increasing the amount of lubricating oil in the gap, increasing the minimum oil film thickness in the contact area, and enhancing the lubrication effect, which can further reduce the wear of the crankshaft 200 and the bearing assembly 300.

[0066] In order to facilitate the processing of the oil outlet hole 221 , the oil outlet hole 221 can be arranged along the radial direction of the connecting section 220 .

[0067] Of course, in other optional embodiments, the oil outlet hole 221 can also be arranged radially inclined to the connecting section 220, for example, it can be arranged upwardly inclined or downwardly inclined, so as to ensure that one end of the oil outlet hole 221 is connected to the center oil hole 210, and the other end is connected to the gap between the outer surface of the connecting section 220 and the inner wall of the sleeve 320.

[0068] The present application provides a friction-reducing layer on the inner wall of the shaft hole 320a, thereby reducing the friction between the connecting section 220 of the crankshaft 200 and the inner wall of the shaft hole 320a, improving the lubricity between the crankshaft 200 and the shaft hole 320a, and reducing the wear of the crankshaft 200 and the bearing assembly 300. An oil outlet hole 221 connected to the center oil hole 210 is also provided in the connecting section 220, and the oil outlet hole 221 is connected to the gap between the outer surface of the connecting section 220 and the inner wall of the shaft hole 320a. When the compressor 10 is running, the lubricating oil can flow through the center oil hole 210 and the oil outlet hole 221 to between the outer surface of the connecting section 220 and the inner wall of the shaft hole 320a, so that the lubricating oil exists between the connecting section 220 of the crankshaft 200 and the inner wall of the shaft hole 320a, thereby achieving the purpose of oil lubrication, so that the crankshaft 200 and the bearing assembly 300 are always kept in a good lubrication state, which can further reduce the wear of the crankshaft 200 and the bearing assembly 300, and effectively improve the reliability of the bearing assembly 300 and the compressor 10.

[0069] In one embodiment, the friction reducing layer is made of PTFE (Polytetrafluoroethylene) or graphite material.

[0070] Please refer to Figure 1 and Figure 2 The bearing assembly 300 includes a first bearing 310, and the first bearing 310 is provided with a bearing inner hole 311, and the bearing inner hole 311 extends along the axial direction of the first bearing 310 and penetrates the upper and lower surfaces of the first bearing 310. The first bearing 310 can be connected to the housing of the compressor 10 through a support frame.

[0071] The bearing assembly 300 further includes a sleeve 320, which is disposed in the bearing inner hole 311. The outer surface of the sleeve 320 contacts the inner surface of the bearing inner hole 311. In other words, the first bearing 310 is sleeved on the sleeve 320 through the bearing inner hole 311. The sleeve 320 and the bearing inner hole 311 are interference fit. Specifically, the bearing inner hole 311 can be a stepped hole, such as Figure 2 As shown, the bearing inner hole 311 includes a first through hole (not marked) and a second through hole (not marked) arranged along the axial direction, the aperture of the first through hole is smaller than the aperture of the second through hole, the sleeve 320 is arranged in the second through hole, and a step surface is formed at the connection between the first through hole and the second through hole, and the step surface can limit the sleeve 320 to prevent the sleeve 320 from moving upward.

[0072] The inner wall of the sleeve 320 is provided with the above-mentioned friction-reducing layer, and the connecting section 220 is inserted into the sleeve 320. Then, by setting the sleeve 320 in the first bearing 310 and inserting the connecting section 220 of the crankshaft 200 into the sleeve 320, that is, the sleeve 320 is arranged between the connecting section 220 and the first bearing 310, so that the outer surface of the connecting section 220 will never contact the first bearing 310, and the wear of the first bearing 310 can be prevented.

[0073] It can be understood that the first bearing 310 supports and positions the crankshaft 200. The first bearing 310 mainly bears the radial load and impact generated during the rotation of the crankshaft 200. Therefore, the rigidity, strength and precision of the first bearing 310 are relatively high. The first bearing 310 needs to be processed as a whole. Therefore, it is difficult to directly set a wear-reducing layer on the bearing inner hole 311 of the first bearing 310. In this embodiment, a sleeve 320 is further provided in the first bearing 310, and the wear-reducing layer is provided on the inner wall of the sleeve 320. Since the rigidity and strength requirements of the sleeve 320 are lower than those of the first bearing 310, the sleeve 320 does not need to be processed as a whole, which can reduce the difficulty of processing and manufacturing the wear-reducing layer, reduce production costs, and make it easier to control the processing precision of the sleeve 320.

[0074] Specifically, the sleeve 320 can be manufactured by a rolling process. Before rolling, the blank used to make the sleeve 320 is in a flat plate shape, and a wear-reducing layer can be formed on one surface of the flat plate blank. For example, the wear-reducing layer can be formed on one surface of the blank by spraying. After the wear-reducing layer is completely formed, the flat plate blank is rolled to obtain the final shape of the sleeve 320. This facilitates the processing and manufacturing of the wear-reducing layer, and at the same time facilitates the control of the overall processing accuracy of the sleeve 320.

[0075] In one embodiment, please refer to Figure 3 and Figure 4 , Figure 3 This is a cross-sectional view of the shaft sleeve of an embodiment of the utility model along the axial direction. Figure 4 for Figure 3 The shaft sleeve 320 includes a base layer 321 and a connection layer 322 which are stacked radially along the shaft sleeve 320 . The connection layer 322 is disposed on the inner side of the base layer 321 . The friction-reducing layer 323 is disposed on the side of the connection layer 322 which is away from the base layer 321 .

[0076] The base layer 321 can be made of a rigid material such as a metal material, so that the sleeve 320 has good rigidity, can enable the sleeve 320 to maintain its own shape, and ensure that the sleeve 320 can be stably installed in the bearing inner hole 311 of the first bearing 310. For example, the base layer 321 can be made of copper metal.

[0077] It is understandable that, since the base layer 321 is relatively smooth and has poor adhesion, the connection layer 322 is provided, and the connection layer 322 is used for connection, so that the friction-reducing layer 323 and the base layer 321 can be connected as a whole. Among them, the surface of the connection layer 322 is an uneven structure, so that the friction-reducing layer 323 can be embedded in the groove of the connection layer 322, which can enhance the connection adhesion of the friction-reducing layer 323, thereby ensuring that the friction-reducing layer 323 is firmly connected to the connection layer 322. It is understandable that the connection layer 322 can be provided with multiple layers.

[0078] Of course, in other embodiments of the present application, the bearing assembly 300 may also only be provided with a first bearing without a sleeve, the first bearing is provided with an axial hole, and the friction-reducing layer is directly provided on the inner wall of the axial hole of the first bearing.

[0079] Please refer to Figure 5 and Figure 6 , Figure 5 This is a schematic diagram of the structure of a crankshaft according to an embodiment of the utility model. Figure 6Schematic diagram of the structure of a crankshaft in another embodiment of the utility model. A groove body 222 is provided on the outer surface of the connecting section 220. The groove body 222 is a groove structure formed by cutting off a part of the solid structure from the outer surface of the connecting section 220. The groove body 222 is recessed relative to the outer surface of the connecting section 220 toward the inside of the connecting section 220, and the groove body 222 can be formed by machining.

[0080] Please refer to Figure 7 , Figure 7 for Figure 6 The sectional view of the middle crankshaft along the section CC. The groove body 222 is arranged at the oil outlet end of the oil outlet hole 221, so that the groove body 222 is connected with the oil outlet hole 221, and the groove body 222 and the inner wall of the sleeve 320 define an oil outlet groove.

[0081] Then, during the rotation of the crankshaft 200, the lubricating oil flowing through the center oil hole 210 and the oil outlet hole 221 enters the oil tank, and a certain amount of lubricating oil can always be stored in the oil tank, thereby further increasing the minimum oil film thickness between the connecting section 220 and the inner wall of the sleeve 320, so that the crankshaft 200 and the sleeve 320 always maintain a good lubrication state, further reducing the wear of the crankshaft 200 and the sleeve 320, and greatly improving the reliability of the crankshaft 200 and the bearing assembly 300.

[0082] At least part of the side wall of the groove body 222 is inclined relative to the axis of the oil outlet hole 221. Figure 7 As shown, the side wall of the groove body 222 is inclined to the axis of the oil outlet hole 221, the side wall of the groove body 222 can be set as a conical surface, the groove body 222 can be processed into a chamfered shape (also called a C-shaped groove), and the groove body 222 can also be processed into an elliptical groove (also called a waist-shaped groove).

[0083] That is to say, in this embodiment, the groove body 222 is processed into a non-planar groove, and a gap of appropriate size can be formed between one side of the groove body 222 and the inner wall of the sleeve 320, thereby preventing the gap between one side of the groove body 222 and the inner wall of the sleeve 320 from being too large (when the gap is too large, the surface tension of the lubricating oil itself cannot maintain it in the oil groove), and the cooperation between the side wall of the groove body 222 and the inner wall of the sleeve 320 blocks the lubricating oil in the oil groove, preventing the lubricating oil in the oil groove from quickly flowing away from the gap between the outer surface of the crankshaft 200 and the inner wall of the sleeve 320, so that a stable oil film can be formed between the outer surface of the crankshaft 200 and the inner wall of the sleeve 320.

[0084] It can be understood that the thickness of the oil film between the outer surface of the connecting section 220 and the inner wall of the sleeve 320 is closely related to the shape and size of the groove body 222 .

[0085] Please refer to Figure 2 and Figure 8 , Figure 8 for Figure 6The maximum length of the opening of the slot body 222 along the axial direction of the crankshaft 200 is defined as L1. It is easy to understand that the maximum length of the opening of the slot body 222 along the axial direction of the crankshaft 200 refers to: the distance between the two most distant end points of the opening of the slot body 222 along the axial direction of the crankshaft 200, such as Figure 8 The distance between the middle end point a and the end point b is L1. The axial length of the sleeve 320 is defined as L, that is, the matching length of the sleeve 320 and the connecting section 220 is L, which satisfies the following relationship: 0.1≤L1 / L≤0.75.

[0086] When the axial length L of the sleeve 320 is constant, if the ratio L1 / L is larger, the maximum length of the opening of the slot body 222 along the axial direction of the crankshaft 200 is larger, and the bearing area of ​​the connecting section 220 of the crankshaft 200 is reduced (the slot body 222 is enlarged, and the area of ​​the outer surface of the connecting section 220 is reduced), resulting in an increase in surface pressure (the bearing area is reduced, and the pressure is increased), which will cause the oil film thickness to decrease. Moreover, when L1 / L=1, that is, the maximum length of the opening of the slot body 222 along the axis of the crankshaft 200 is equal to the axial length of the sleeve 320, at this time, the axial ends of the slot body 222 are directly connected to the gaps at the axial ends of the sleeve 320, and the lubricating oil in the oil groove is easy to flow directly from the bottom or top connection, resulting in the inability to form a stable oil film between the outer surface of the connecting section 220 and the inner wall of the sleeve 320. At the same time, the larger the ratio of L1 / L is, the lower the structural rigidity of the connecting section 220 is, making the connecting section 220 prone to deformation, which can easily cause abnormal wear of the crankshaft 200 and the sleeve 320, affecting the reliability of the compressor 10.

[0087] Please refer to Fig. 9 , Fig. 9The graph is a graph showing the variation of the minimum oil film thickness with the change of the slot opening length in the embodiment of the utility model. It should be pointed out that the minimum oil film thickness refers to the thickness of the oil film at the thinnest point between the outer surface of the crankshaft 200 and the inner wall of the sleeve 320. The graph is obtained by experimenting with the length of the sleeve 320 set to 20 mm as an example. It can be seen from the figure that under the same working conditions, as the slot opening length L1 increases, that is, as the L1 / L ratio increases, the minimum oil film thickness between the outer surface of the crankshaft 200 and the inner wall of the sleeve 320 decreases. When the slot opening length L1 is greater than 15 mm, that is, the ratio L1 / L is greater than 0.75, the minimum oil film thickness between the outer surface of the crankshaft 200 and the inner wall of the sleeve 320 decreases rapidly, and the oil film thickness deteriorates. Therefore, by making L / L1≤0.75, under the premise of increasing lubricity by providing the groove body 222, it is possible to ensure that the axial length of the groove body 222 is not too long, so that the oil film thickness between the outer surface of the crankshaft 200 and the inner wall of the sleeve 320 is large, so that the crankshaft 200 and the sleeve 320 maintain good lubricity and reduce wear. At the same time, it is possible to ensure that the structural rigidity of the connecting section 220 meets the support and positioning requirements, effectively ensuring the reliability of the compressor 10.

[0088] At the same time, the ratio of L1 / L cannot be too small. When the ratio of L1 / L is very small, the diameter of the oil outlet hole 221 is required to be very small, which makes it inconvenient to process the oil outlet hole 221, and the lubricating oil is not easy to flow out of the oil outlet hole 221. Therefore, making L1 / L ≥ 0.1 can facilitate the processing of the oil outlet hole 221 and the flow of lubricating oil from the oil outlet hole 221.

[0089] Please refer to Figure 7 , along the circumferential direction of the crankshaft 200, the maximum central angle β corresponding to the portion removed by the connecting section 220 to form the groove body 222 satisfies: 20°≤β≤60°. The larger the degree of the central angle β, the wider the width of the opening of the groove body 222 along the circumferential direction of the crankshaft 200, and the bearing area of ​​the connecting section 220 of the crankshaft 200 is reduced, resulting in an increase in surface pressure, which will cause the oil film thickness to decrease. Moreover, the larger the degree of the central angle β, the larger the oil groove space formed between one side of the groove body 222 and the inner wall of the sleeve 320, so that the fluidity of the lubricating oil is better, and it is more difficult to retain the lubricating oil, so that the lubricating oil is easy to flow away from the gap between the outer surface of the crankshaft 200 and the inner wall of the sleeve 320, and it is not easy to form a stable oil film. Similarly, the larger the degree of the central angle β, the more solid structure needs to be cut off to form the groove body 222, and the structural rigidity of the connecting section 220 is reduced, making the connecting section 220 prone to deformation, easily causing abnormal wear of the crankshaft 200 and the sleeve 320, and affecting the reliability of the compressor 10.

[0090] Please refer to Fig.10 , Fig.10The graph is a graph showing the minimum oil film thickness in the embodiment of the utility model as the center angle β changes. It can be seen from the figure that when the center angle β is between 20°-60°, the minimum oil film thickness between the outer surface of the crankshaft 200 and the inner wall of the sleeve 320 is maintained between 0.601-0.603 μm, and when the center angle β exceeds 60°, as the center angle β gradually increases, the minimum oil film thickness between the outer surface of the crankshaft 200 and the inner wall of the sleeve 320 gradually decreases. Therefore, by making 20°≤β≤60°, it can be ensured that the width of the groove body 222 along the circumferential direction of the crankshaft 200 will not be too wide, so that the oil film thickness between the outer surface of the crankshaft 200 and the inner wall of the sleeve 320 is larger, so that the crankshaft 200 and the sleeve 320 can maintain good lubricity and reduce wear.

[0091] It has been pointed out above that the size of the groove body 222 affects the thickness of the oil film, and the size of the groove body 222 is directly related to the diameter of the oil outlet hole 221. The larger the diameter of the oil outlet hole 221, the larger the processing size of the groove body 222. For example, taking the groove body 222 as a waist-shaped groove as an example, the waist-shaped groove itself has a large length along the axial direction of the crankshaft 200. If the diameter of the oil outlet hole 221 is large, the waist-shaped groove needs to be processed to a larger size, and the gap formed between one side of the groove body 222 and the inner wall of the sleeve 320 is large. The lubricating oil can easily flow away through the gap between the outer surface of the crankshaft 200 and the inner wall of the sleeve 320, and it is not easy to store the lubricating oil, and a stable oil film cannot be formed. Of course, the oil outlet hole 221 should not be too small. On the one hand, if the diameter of the oil outlet hole 221 is too small, it is inconvenient to process the oil outlet hole 221, and the cost of processing a small hole is high; on the other hand, less lubricating oil enters the oil outlet hole 221 from the central oil hole 210, resulting in less lubricating oil entering between the outer surface of the connecting section 220 and the inner wall of the sleeve 320, making it more difficult to form a larger oil film thickness. Please refer to Figure 2 and Figure 7 , the inner diameter of the oil outlet hole 221 is defined as d, and the maximum outer diameter of the connecting section 220 is defined as D, satisfying the following relationship: 5d≤D≤9d.

[0092] Among them, the above relationship between the inner diameter d of the oil outlet hole 221 and the maximum outer diameter D of the connecting section 220 is obtained through simulation. Within the above range, the size of the oil outlet hole 221 is neither too large nor too small, so that the size of the groove body 222 can be processed within the above required range. For example, the maximum axial length L1 of the groove body 222 opening along the crankshaft 200 can be made to satisfy 0.1≤L1 / L≤0.75, and the central angle β of the portion removed from the crankshaft 200 to form the groove body 222 along the circumferential direction can be made to satisfy 20°≤β≤60°, thereby ensuring that a larger oil film thickness can be maintained between the outer surface of the crankshaft 200 and the inner wall of the sleeve 320, thereby reducing the wear of the crankshaft 200.

[0093] When the crankshaft 200 rotates and drives the eccentric part 230 to rotate to compress the refrigerant, in the radial direction of the crankshaft 200, the side of the crankshaft 200 facing the eccentric part 230 is the load-bearing side. Generally, since the load-bearing side bears the largest load, the oil film thickness of the part of the crankshaft 200 corresponding to the load-bearing side is the smallest. When the slot body 222 is provided, the load-bearing area of ​​the side of the crankshaft 200 where the slot body 222 is located is small. When the slot body 222 is located on the load-bearing side, the load-bearing area of ​​the crankshaft 200 at the load-bearing side is reduced. Under the condition that the load remains unchanged, the surface pressure will increase, and the oil film thickness of the crankshaft 200 at the load-bearing side will be further reduced. The oil film here is ultra-thin, which will cause aggravated wear. When the slot body 222 is closer to the load-bearing side, along the radial direction of the crankshaft 200, the load borne by the side of the crankshaft 200 where the slot body 222 is located is greater, the surface pressure is greater, and the oil film thickness is smaller, that is, the oil film thickness deteriorates.

[0094] To do this, refer to Fig.11 , Fig.11 It is a radial cross-sectional view of the crankshaft of the embodiment of the utility model. A plane passing through the axis of the center oil hole 210 and the axis of the oil outlet hole 221 is defined as the first reference plane, and a plane passing through the center axis of the eccentric part 230 and the axis of the center oil hole 210 is defined as the second reference plane. The angle between the first reference plane and the second reference plane is α, which satisfies the following relationship: 90°≤α≤270°. When there are multiple eccentric parts 230, the second reference plane can be a plane passing through the center axis of any one of the eccentric parts 230.

[0095] Taking one of the eccentric parts 230 as an example, when α<90° or α>270°, the distance between the groove body 222 and the load-bearing side where the eccentric part 230 is located is relatively close. Along the radial direction of the crankshaft 200, the side of the crankshaft 200 where the groove body 222 is located bears a relatively large load, the surface pressure increases, and the oil film thickness here decreases, that is, the oil film thickness deteriorates, especially the oil film thickness of the groove body 222 close to the edge of the side of the eccentric part 230 is smaller, which will cause aggravated wear. It can be understood that when α=180°, the position of the groove body 222 on the crankshaft 200 and the position of the eccentric part 230 are mutually separated. At this time, the distance between the groove body 222 and the load-bearing side where the eccentric part 230 is located is the farthest. Along the radial direction of the crankshaft 200, the side of the crankshaft 200 where the groove body 222 is located bears the smallest load and the smallest surface pressure, thereby having the best oil film thickness.

[0096] Then, in order to further reduce the wear of the crankshaft 200, in one embodiment, the angle α between a first reference plane passing through the axis of the center oil hole 210 and the axis of the oil outlet hole 221 and a second reference plane passing through the center axis of the eccentric portion 230 and the axis of the center oil hole 210 satisfies the following relationship: 120°≤α≤240°. When the angle α is within this angle range, the groove body 222 is located on the crankshaft 200 at a position farther away from the load-bearing side where the eccentric portion 230 is located. Along the radial direction of the crankshaft 200, the load on the side of the crankshaft 200 where the groove body 222 is located is smaller, and can have a larger oil film thickness.

[0097] In one embodiment, if Fig.11 As shown, the crankshaft 200 includes two eccentric parts 230, namely a first eccentric part 230a and a second eccentric part 230b, and the eccentric directions of the first eccentric part 230a and the second eccentric part 230b are just opposite, that is, the direction from the central axis of the crankshaft 200 toward the center of the eccentric part 230. In actual operation, when the crankshaft 200 rotates, the centrifugal forces acting on the two eccentric parts 230 are generally not equal, so in the radial direction of the crankshaft 200, the sides of the crankshaft 200 facing the two eccentric parts 230 are all load-bearing sides. In this case, when α=90°, the distance between the groove body 222 and the load-bearing side where the first eccentric portion 230a is located is equal to the distance between the groove body 222 and the load-bearing side where the second eccentric portion 230b is located. That is to say, when α=90°, the distances between the groove body 222 and the load-bearing sides where the two eccentric portions 230 are located are equal, and the distances are maximum. At this time, the load borne by the side of the crankshaft 200 where the groove body 222 is located is the smallest, which can effectively increase the oil film thickness there.

[0098] Please refer to Figure 1 and Figure 2 In one embodiment, the crankshaft 200 includes a top end surface 250, and the center oil hole 210 extends axially along the crankshaft 200 to penetrate the top end surface 250. The compressor 10 also includes an oil baffle 240, which is arranged in the center oil hole 210. The oil baffle 240 is used to block part of the center oil hole 210.

[0099] Specifically, the oil baffle 240 needs to be arranged between the top end surface 250 and the oil outlet hole 221 to avoid blocking the lubricating oil that needs to enter the oil outlet hole 221, so that the lubricating oil can pass through the oil outlet hole 221 into between the outer surface of the crankshaft 200 and the inner wall of the sleeve 320 to ensure the lubrication between the crankshaft 200 and the sleeve 320 and reduce the wear of the crankshaft 200 and the sleeve 320.

[0100] It can be understood that the oil blocking member 240 blocks part of the central oil hole 210, that is, the oil blocking member 240 can block most of the lubricating oil from flowing through, and only allows a small part of the lubricating oil to pass through and flow along the central oil hole 210 to the top end surface 250, thereby reducing the oil discharge amount of the compressor 10 and further improving the reliability of the compressor 10. The oil blocking member 240 can be a spring or a pin.

[0101] The present application also provides a refrigeration device, which includes a compressor 10 based on any of the above embodiments. The refrigeration device can be an electrical appliance such as an air conditioner or a refrigerator.

[0102] Since the refrigeration device adopts all the technical solutions of the compressor 10 of the above embodiment, it has at least all the beneficial effects brought by the technical solutions of the above embodiment.

[0103] The embodiments of the present invention are described in detail above in conjunction with the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge scope of ordinary technicians in the relevant technical field without departing from the purpose of the present invention.

Claims

1. A compressor, characterized in that include: Motor components; A crankshaft connected to the motor assembly, the crankshaft being provided with a central oil hole extending axially along the crankshaft, the crankshaft comprising a connecting section, the connecting section being provided with an oil outlet hole, one end of the oil outlet hole being connected to the central oil hole, and the other end of the oil outlet hole penetrating through the outer surface of the connecting section; and The bearing assembly is provided with an axial hole, the bearing assembly is rotatably connected to the connecting section through the axial hole, and the inner wall of the axial hole is provided with a friction-reducing layer.

2. The compressor according to claim 1, characterized in that The bearing assembly comprises: A first bearing is provided with a bearing inner hole; and A shaft sleeve is arranged in the inner hole of the bearing, and the inner wall of the shaft sleeve is provided with the friction-reducing layer.

3. The compressor according to claim 2, characterized in that The shaft sleeve comprises a base layer and a connecting layer, wherein the base layer and the connecting layer are stacked along the radial direction of the shaft sleeve, and the connecting layer is located on the inner side of the base layer, and the friction-reducing layer is arranged on a side of the connecting layer away from the base layer.

4. The compressor according to claim 2, characterized in that A groove body is provided on the outer surface of the connecting section, the groove body is communicated with the oil outlet hole, and the groove body and the inner wall of the shaft sleeve define an oil outlet groove.

5. The compressor according to claim 4, characterized in that At least part of the side wall of the groove body is arranged obliquely relative to the axis of the oil outlet hole.

6. The compressor according to claim 4, characterized in that The maximum length of the opening of the groove body along the axial direction of the crankshaft is L1, and the axial length of the sleeve is L, which satisfies: 0.1≤L1 / L≤0.

75.

7. The compressor according to claim 4, characterized in that Along the circumferential direction of the crankshaft, the maximum central angle corresponding to the portion removed by the connecting section to form the groove body is β, which satisfies: 20°≤β≤60°.

8. The compressor according to any one of claims 1 to 3, characterized in that: The inner diameter of the oil outlet hole is d, and the maximum outer diameter of the connecting section is D, satisfying: 5d≤D≤9d.

9. The compressor according to any one of claims 1 to 3, characterized in that: The compressor also includes a pump body assembly; The crankshaft also includes an eccentric portion, the eccentric portion and the connecting section are respectively located at the axial ends of the crankshaft, and the eccentric portion is connected to the pump body assembly; wherein, an angle α is formed between a first reference plane passing through the axis of the center oil hole and the axis of the oil outlet hole and a second reference plane passing through the center axis of the eccentric portion and the axis of the center oil hole, satisfying: 90°≤α≤270°.

10. The compressor according to any one of claims 1 to 3, characterized in that: The crankshaft comprises a top end surface, and the central oil hole extends axially along the crankshaft to penetrate the top end surface; The compressor further comprises an oil baffle, which is arranged in the central oil hole and between the top end surface and the oil outlet hole, and is used for blocking a part of the central oil hole.

11. Refrigeration equipment, characterized in that A compressor comprising the compressor according to any one of claims 1 to 10.

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