Bearing assembly and motor having same
By introducing a flow-blocking part of the positioning ring and an annular recess of the rotating part into the bearing assembly, combined with oil guide grooves and guide slopes, the problem of oil leakage was solved, and smooth circulation of oil and improved lubrication effect were achieved.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-05-09
- Publication Date
- 2026-03-10
AI Technical Summary
In existing oil-impregnated bearings, the oil is prone to leakage due to centrifugal force during shaft rotation, resulting in poor lubrication and increased noise.
The bearing assembly design includes a flow-blocking part of the positioning ring and an annular recess of the rotating part. By forming a blocking structure at the bearing end face and shaft hole, combined with oil guide grooves and guide slopes, it ensures smooth oil circulation and no leakage.
It effectively prevents oil leakage, improves lubrication, reduces noise, and ensures smooth circulation of oil within the bearing assembly.
Smart Images
Figure CN223984693U_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The utility model relates to a motor part, especially a bearing assembly in a motor, and a motor with the bearing assembly. BACKGROUND
[0002] Generally speaking, in order to avoid excessive wear and noise generated by the motor or fan in operation, an oil-impregnated bearing is usually used to replace the traditional bearing to reduce wear and noise through the circulation of oil in the bearing. Further, the oil-impregnated bearing usually has a shaft hole penetrating through both ends of the oil-impregnated bearing. After pouring oil into the shaft hole, a rotating shaft can be combined with the oil-impregnated bearing from the shaft hole, so that the oil can form lubrication between the rotating shaft and the oil-impregnated bearing. However, during the rotation of the rotating shaft, the oil is easy to separate from the circulation path between the rotating shaft and the oil-impregnated bearing due to centrifugal effect, thereby causing oil leakage.
[0003] Therefore, the existing bearing assembly still needs to be improved. SUMMARY
[0004] To solve the above problems, the purpose of the utility model is to provide a bearing assembly and a motor with the bearing assembly, which can avoid oil leakage.
[0005] The directionality or its approximate language in the entire description of the utility model, such as “front”, “back”, “left”, “right”, “up (top)”, “down (bottom)”, “inner”, “outer”, “side” and the like, mainly refers to the direction of the attached drawings, and each directionality or its approximate language is only used to assist in describing and understanding each embodiment of the utility model, and is not used to limit the utility model.
[0006] The quantifier “one” or “a” of the elements and components recorded in the entire description of the utility model is only used for convenience and provides the general meaning of the scope of the utility model; in the utility model, it should be interpreted as including one or at least one, and the single concept also includes multiple cases, unless it obviously means other meanings.
[0007] The “first”, “second”, … and “Nth” and the like described in the entire description of the utility model are mainly used to distinguish the description of different elements or features (which can be, for example, element, direction or step features), and do not represent the maximum or minimum number of these elements or features possessed by a corresponding subject or method, nor do they mean to limit the order.
[0008] The approximate language “combined”, “combined” or “assembled” and the like described in the entire description of the utility model mainly includes the type that the components can still be separated without being damaged after being connected, or the components cannot be separated after being connected, and those with ordinary knowledge in the art can select according to the material of the components to be connected or the assembly requirements.
[0009] The bearing assembly of the utility model, comprising: a bearing, having a shaft hole; a positioning ring, the positioning ring is pressed on one end face of the bearing, the positioning ring has an inner wall surface, and a flow blocking part is surrounded on the inner wall surface; and a rotating member, rotatably penetrating the shaft hole of the bearing, the rotating member has an annular recess, the annular recess covers a oiling agent, and the annular recess is radially opposite to the positioning ring.
[0010] Therefore, the bearing assembly of the utility model, through the flow blocking part of the positioning ring, the oil forms a block in the axial direction above the end face of the bearing, and the annular recess of the rotating member, the oil forms a block in the axial direction above the shaft hole, the oil can flow into the shaft hole after passing through the end face, so that the oil does not flow out beyond the positioning ring, and the oil does not flow out along the peripheral wall of the rotating member, away from the shaft hole, so that the effect of avoiding oil leakage can be achieved.
[0011] Among them, the bearing has at least one oil guide groove, the at least one oil guide groove is concave on the outer surface of the bearing, and the at least one oil guide groove is communicated with the shaft hole. In this way, the oil can be concentrated in the at least one oil guide groove, and the effect of circulating flow between the outer surface of the bearing and the shaft hole.
[0012] Among them, the end face is connected with the axial outer circumferential surface of the bearing and the shaft hole through two guide inclined surfaces. In this way, the two guide inclined surfaces can guide the flow of oil, and have the effect of improving the smoothness of oil circulation.
[0013] Among them, the end face has a radial width size, the positioning ring contacts at least 1 / 4 of the radial width size of the end face, and does not exceed 1 / 2 of the radial width size of the end face. In this way, the positioning ring can avoid excessive covering of the end face, so that the oil can smoothly pass through the end face.
[0014] Among them, the flow blocking part has a first axial size, the inner wall surface has a second axial size, the first axial size is greater than or equal to 1 / 5 of the second axial size, and the first axial size is less than or equal to 1 / 2 of the second axial size. In this way, the flow blocking part can have a better axial extension range on the inner wall surface, thereby having the effect of hindering the flow of oil.
[0015] Among them, the flow blocking part has a radial depth size, and the radial depth size is greater than or equal to 0.05 mm. In this way, the flow blocking part forms a proper radial difference with respect to the inner wall surface, thereby having the effect of hindering the flow of oil.
[0016] Among them, the flow blocking part covers a oiling agent. In this way, the flow blocking part has a surface tension lower than that of oil, thereby preventing the oil from adhering to the flow blocking part, and having the effect of blocking the oil.
[0017] The annular recess covers a oil repellent agent. Thus, the annular recess has a surface tension lower than that of the oil, and the oil is difficult to adhere to the annular recess, thereby having the effect of blocking the oil.
[0018] The annular recess is at least partially radially opposite to the flow blocking portion of the positioning ring. Thus, the annular recess on the peripheral wall of the rotating member can be used to prevent the oil from flowing axially.
[0019] The annular recess is completely radially misaligned with the flow blocking portion. Thus, the annular recess on the peripheral wall of the rotating member can be used to prevent the oil from flowing axially.
[0020] The lower end of the annular recess is not lower than the end face in the axial direction. Thus, the annular recess on the peripheral wall of the rotating member can be used to prevent the oil from flowing axially.
[0021] The annular recess does not exceed the positioning ring in the axial direction. Thus, when the oil flows into the shaft hole through the end face, the effect of the annular recess hindering the circulation of the oil can be avoided.
[0022] The flow blocking portion of the positioning ring is adjacent to the end face of the bearing. Thus, the effect of further ensuring that the oil only passes through the end face and does not flow to the positioning ring can be achieved.
[0023] The flow blocking portion has a first end and a second end opposite in the axial direction, and a flow blocking surface between the first end and the second end, and the second end is adjacent to the end face. Thus, the effect of further ensuring that the oil only passes through the end face and does not flow to the positioning ring can be achieved.
[0024] The radial distance between the second end and the rotating member is greater than the radial distance between the first end and the rotating member. Thus, the flow blocking surface can be substantially opposite to the end face of the bearing, thereby making it difficult for the oil to pass over the flow blocking surface.
[0025] The flow blocking surface and the end face form an included angle of 10° to 60°. Thus, the flow blocking surface has the effect of better blocking the oil.
[0026] The motor of the utility model comprises a sleeve, the sleeve has the above-mentioned bearing assembly inside, and a stator is located outside the sleeve. Thus, the oil does not flow out through the positioning ring, and the oil does not flow out along the peripheral wall of the rotating member away from the shaft hole, thereby achieving the effect of avoiding oil leakage. BRIEF DESCRIPTION OF DRAWINGS
[0027] Figure 1 The exploded perspective view of the first embodiment of the utility model
[0028] Figure 2 : A cross-sectional view of the first embodiment of this utility model;
[0029] Figure 3 :like Figure 2 A magnified view of the local structure at point A;
[0030] Figure 4 :like Figure 3 Another groove-shaped diagram of the flow-blocking section;
[0031] Figure 5 :like Figure 3 Another channel-shaped diagram of this flow-blocking section;
[0032] Figure 6 : A partial enlarged view of the structure of the second embodiment of this utility model.
[0033] Explanation of reference numerals in the attached figures:
[0034] 1: Bearing
[0035] 1a: End face
[0036] 11: Shaft Hole
[0037] 12: Oil guide trench
[0038] 13: Guide sloping surface
[0039] 2: Positioning ring
[0040] 2a: Through hole
[0041] 21: Flow-blocking section
[0042] 21a: First edge
[0043] 21b: Second edge
[0044] 21c: Flow-blocking surface
[0045] 22: Inner wall surface
[0046] 23,32: Oil-removing agent
[0047] 3: Rotating parts
[0048] 3a: First end
[0049] 3b: Second end
[0050] 31: Annular depression
[0051] 31a: Lower edge
[0052] B: Bearing assembly
[0053] T: Sleeve
[0054] T1: Base Plate
[0055] T2: Ring Wall
[0056] T3: Opening
[0057] T4: Anti-slip component
[0058] T5: Wear-resistant sheet
[0059] S: Stator
[0060] M: Motor
[0061] J: Wheel hub
[0062] W: Radial width dimension
[0063] H1: First axial dimension
[0064] H2: Second axial dimension
[0065] D: Radial depth dimension
[0066] θ: included angle. Detailed Implementation
[0067] To make the above and other objects, features and advantages of this utility model more apparent and understandable, preferred embodiments of this utility model are described below in detail with reference to the accompanying drawings; in addition, those symbols that are marked with the same symbols in different drawings are considered to be the same and their descriptions will be omitted.
[0068] Please refer to Figure 1 , Figure 2 As shown, this is the first embodiment of the bearing assembly B of the present invention, comprising a bearing 1, a positioning ring 2, and a rotating member 3. The positioning ring 2 is axially abutted against the bearing 1, and the rotating member 3 is rotatably connected to the bearing 1.
[0069] The bearing 1 can be located within a sleeve T, which serves to position the bearing 1 and to contain oil, allowing the oil to circulate on the surface of the bearing 1. The sleeve T may have, for example, a base plate T1 and an annular wall T2. One end of the annular wall T2 can be closed by the base plate T1, and the other end can form an opening T3, allowing the bearing 1 to be installed within the sleeve T through the opening T3. Furthermore, an anti-disengagement element T4 can be provided between the bearing 1 and the base plate T1 to prevent the rotating component 3 from disengaging, and a wear-resistant plate T5 for the rotating component 3 to abut against. Additionally, the sleeve T can be integrated with a stator S to form a motor M, as will be understood by those skilled in the art and will not be elaborated upon here.
[0070] The bearing 1 may have two end faces 1a, which are axially opposite each other, one end face 1a may face the opening T3, and the other end face 1a may face the base plate T1. The bearing 1 has a shaft hole 11 that passes through the two end faces 1a.
[0071] The bearing 1 may have at least one oil guide groove 12, which may be recessed into the outer surface of the bearing 1. For example, the at least one oil guide groove 12 may extend into the two end faces 1a and the outer peripheral wall of the bearing 1, so that the at least one oil guide groove 12 can connect to the opening of the shaft hole 11 located on the two end faces 1a. In this way, oil can be concentrated in the at least one oil guide groove 12 and circulate between the outer surface of the bearing 1 and the shaft hole 11. Alternatively, there may be several oil guide grooves 12, which may be recessed into the two end faces 1a and the axial outer peripheral surface of the bearing 1, respectively. The oil guide grooves 12 on the two end faces 1a and the oil guide grooves 12 on the axial outer peripheral surface of the bearing 1 can be connected. This invention does not limit the distribution pattern of the several oil guide grooves 12.
[0072] In this embodiment, each end face 1a can be connected to the axial outer peripheral surface of the bearing 1 and the shaft hole 11 respectively through two guide ramps 13. In this way, the oil guide groove 12 recessed in the end face 1a can be connected to the oil guide groove 12 on the axial outer peripheral surface through the guide ramps 13 to allow oil flow. In addition, the oil in the oil guide groove 12 recessed in the end face 1a can also easily flow into the shaft hole 11 through the guide ramps 13, thereby improving the smoothness of oil circulation.
[0073] Please refer to Figure 2 , Figure 3 As shown, the positioning ring 2 can be attached to the inner wall of the sleeve T by means of, for example, tight fit, welding, or gluing. The positioning ring 2 can be used to position the bearing 1 inside the sleeve T. The positioning ring 2 has a through hole 2a, which is axially located opposite the shaft hole 11, so that the rotating member 3 can be inserted into the through hole 2a. Specifically, the positioning ring 2 can press against the end face 1a facing the opening T3 to prevent the bearing 1 from coming out of the opening T3. Furthermore, the end face 1a can have a radial width dimension W, and the positioning ring 2 can contact at least 1 / 4 of the radial width dimension W of the end face 1a and no more than 1 / 2 of the radial width dimension W of the end face 1a. In this way, the positioning ring 2 can be prevented from excessively covering the end face 1a, thereby preventing oil from flowing through the end face 1a.
[0074] The positioning ring 2 has a flow-blocking portion 21, which can be located on an inner wall surface 22 in the radial direction of the positioning ring 2. The flow-blocking portion 21 is used to obstruct the axial flow of oil. Furthermore, the flow-blocking portion 21 can be recessed into the inner wall surface 22, so that the inner wall surface 22 forms an axial step through the flow-blocking portion 21, thereby obstructing the flow of oil and making it difficult for oil to cross the flow-blocking portion 21 and seep out of the positioning ring 2.
[0075] Please refer to Figure 3 , Figure 4 , Figure 5 As shown, in this embodiment, the flow-blocking part 21 can be an annular groove, and the flow-blocking part 21 can surround the inner wall surface 22. This invention does not limit the groove shape (radial cross-sectional shape) of the flow-blocking part 21. For example, in other embodiments, the radial cross-section of the flow-blocking part 21 can be rectangular (e.g., ...). Figure 3 ), trapezoidal (such as Figure 4 ), hemispherical (such as Figure 5 Alternatively, it can be a cross-section of other geometric shapes, such as a triangle. Furthermore, the flow-blocking portion 21 can have a first axial dimension H1, and the inner wall surface 22 can have a second axial dimension H2. The relationship between the first axial dimension H1 and the second axial dimension H2 can be 1 / 5H2≤H1≤1 / 2H2. Thus, the flow-blocking portion 21 can have a better axial extension range on the inner wall surface 22, thereby hindering the flow of oil. In addition, the flow-blocking portion 21 can have a radial depth dimension D, which can be the maximum vertical distance from a virtual plane passing through the opening of the flow-blocking portion 21 to the bottom of the groove of the flow-blocking portion 21. The radial depth dimension D can be greater than or equal to 0.05 mm, and the radial depth dimension D can be less than or equal to half the radial thickness dimension of the positioning ring 2. Thus, the flow-blocking portion 21 can have a better groove depth, so that the flow-blocking portion 21 forms an appropriate radial step relative to the inner wall surface 22, thereby hindering the flow of oil.
[0076] It is worth noting that an oil-repellent agent 23 can be applied to the flow-blocking portion 21. This oil-repellent agent 23 can be, for example, a conventional fluorine-based oil-repellent agent, giving the flow-blocking portion 21 a lower surface tension than the oil, thus preventing the oil from easily adhering to the flow-blocking portion 21 and achieving the effect of blocking the oil flow. The oil-repellent agent 23 can be applied to the flow-blocking portion 21 by coating, or it can seep into the grooves of the flow-blocking portion 21 through capillary action. In this way, the oil-repellent agent 23 can be confined within the grooves of the flow-blocking portion 21, preventing overflow, such as overflowing to the end face 1a of the bearing 1, which would prevent the oil from circulating through the end face 1a.
[0077] Please continue reading. Figure 2 , Figure 3As shown, the rotating member 3 can be, for example, a rotating shaft. The rotating member 3 is rotatably inserted into the shaft hole 11 of the bearing 1. The rotating member 3 can have a first end 3a and a second end 3b opposite to each other. The first end 3a can be used to connect, for example, a hub J, and the second end 3b can face inwards towards the sleeve T, abutting against the wear-resistant plate T5. The rotating member 3 has an annular recess 31 located between the first end 3a and the second end 3b. The annular recess 31 is radially recessed into the peripheral wall of the rotating member 3. For example, the annular recess 31 can be an arc-shaped groove, a rectangular groove, or a groove of any geometric shape, so that the annular recess 31 on the peripheral wall of the rotating member 3 serves to obstruct the axial flow of oil. Furthermore, the annular recess 31 is covered with an oil-repellent agent 32, which makes it difficult for oil to adhere to the annular recess 31, thereby further enhancing the oil-blocking effect of the annular recess 31.
[0078] The annular recess 31 is radially aligned with the positioning ring 2, such that the annular recess 31 is not lower than the end face 1a of the bearing 1 in the axial direction. Further, the annular recess 31 may be at least partially aligned with the flow-blocking portion 21 of the positioning ring 2 in the radial direction, or the annular recess 31 may be completely misaligned with the flow-blocking portion 21 in the radial direction. In this embodiment, a guide slope 13 is provided between the end face 1a and the shaft hole 11. Therefore, the lower edge 31a of the annular recess 31 is preferably not lower than the end face 1a in the axial direction. Thus, oil can flow into the shaft hole 11 through the guide slope 13 without being blocked by the annular recess 31. In another embodiment, the annular recess 31 may not extend beyond the positioning ring 2 in the axial direction. When oil flows into the shaft hole 11 through the end face 1a, the annular recess 31 can further prevent the oil from obstructing the circulation flow of the oil.
[0079] Please refer to Figure 6 As shown, this is a second embodiment of the bearing assembly of this utility model. Compared with the first embodiment, in this embodiment, the flow-blocking portion 21 of the positioning ring 2 is adjacent to the end face 1a of the bearing 1. This further ensures that the oil only passes through the end face 1a and does not flow to the positioning ring 2. Furthermore, the flow-blocking portion 21 may have a first end edge 21a and a second end edge 21b axially opposed, with a flow-blocking surface 21c between the first end edge 21a and the second end edge 21b. The first end edge 21a is adjacent to the inner wall surface 22, and the second end edge 21b is adjacent to the end face 1a.
[0080] In this embodiment, the second end edge 21b is farther away from the rotating member 3 than the first end edge 21a. That is, the radial distance between the second end edge 21b and the rotating member 3 is greater than the radial distance between the first end edge 21a and the rotating member 3, thus creating an axial misalignment between the first end edge 21a and the second end edge 21b. This allows the flow-blocking surface 21c to be approximately opposite the end face 1a of the bearing 1, making it difficult for the oil to pass over the flow-blocking surface 21c. Furthermore, the flow-blocking surface 21c and the end face 1a can together form an angle θ, which can be 10° to 60°, giving the flow-blocking surface 21c a better oil-blocking effect. Since the flow-blocking part 21 blocks the oil through the flow-blocking surface 21c, the aforementioned oil-dispensing agent 23 can be omitted, thereby reducing costs and simplifying installation. Alternatively, the flow-blocking part 21 can be further covered with the aforementioned oil-blocking agent 23 to achieve a better oil-blocking effect.
[0081] In summary, the bearing assembly of this utility model, through the flow-blocking portion of the positioning ring blocking the oil flow axially upward on the end face of the bearing, and the annular recess of the rotating component blocking the oil flow axially upward on the shaft hole, allows the oil to flow into the shaft hole after passing through the end face. This prevents the oil from flowing out beyond the positioning ring and from flowing out along the peripheral wall of the rotating component in a direction away from the shaft hole, thus achieving the effect of preventing oil leakage.
[0082] Although the present invention has been disclosed using the above preferred embodiments, it is not intended to limit the present invention. Any modifications and alterations made by those skilled in the art to the above embodiments without departing from the spirit and scope of the present invention shall still fall within the technical scope protected by the present invention. Therefore, the protection scope of the present invention shall include all changes within the meaning and equivalent scope of the appended claims. Furthermore, when the above embodiments can be combined, the present invention includes any combination of embodiments.
Claims
1. A bearing assembly characterized by, The bearing has at least one oil guide groove recessed on an outer surface of the bearing, the at least one oil guide groove being communicated with the shaft hole. The end surface is connected with an axial outer circumferential surface of the bearing and the shaft hole respectively through two guide slopes. The end surface has a radial width dimension, the positioning ring contacts at least 1 / 4 of the radial width dimension of the end surface and does not exceed 1 / 2 of the radial width dimension of the end surface. The flow resistance part has a first axial dimension, the inner wall surface has a second axial dimension, the first axial dimension is greater than or equal to 1 / 5 of the second axial dimension, and the first axial dimension is less than or equal to 1 / 2 of the second axial dimension.
2. The bearing assembly of claim 1, wherein, The flow resistance part has a radial depth dimension, the radial depth dimension is greater than or equal to 0.05 mm.
3. The bearing assembly of claim 1, wherein, The flow resistance part covers an oil agent.
4. The bearing assembly of claim 1, wherein, The annular recess is at least partially located radially opposite the flow resistance part of the positioning ring.
5. The bearing assembly of claim 1, wherein, The annular recess is completely misaligned radially with the flow resistance part.
6. The bearing assembly of claim 1, wherein, A lower end edge of the annular recess is not lower than the end surface in the axial direction.
7. The bearing assembly of claim 1, wherein, The annular recess does not exceed the positioning ring in the axial direction.
8. The bearing assembly of claim 1, wherein, The flow resistance part of the positioning ring is adjacent to the end surface of the bearing.
9. The bearing assembly of claim 1, wherein, The flow resistance part has axially opposite first and second end edges, and a flow resistance surface between the first and second end edges, the second end edge being adjacent to the end surface.
10. The bearing assembly of claim 1, wherein, The radial distance between the second end edge and the rotating member is greater than the radial distance between the first end edge and the rotating member.
11. The bearing assembly of claim 10, wherein, The flow resistance surface and the end surface jointly form an included angle, and the included angle is 10°-60°.
12. The bearing assembly of claim 1, wherein, The bearing assembly includes:
13. The bearing assembly of claim 12, wherein, A sleeve having the bearing assembly as claimed in any one of claims 1 to 15 inside the sleeve; and 14. The bearing assembly of claim 13, wherein, A stator located outside the sleeve.
15. The bearing assembly of claim 13, wherein, 16. A motor characterized by