Bearing assembly and motor and fan having the bearing assembly
By introducing capillary gaps into the bearing assembly, the oil is allowed to adhere to the bearing surface and flow using capillary action, thus solving the oil leakage problem and improving lubrication performance while reducing noise.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- SUNONWEALTH ELECTRIC MACHINE IND CO LTD
- Filing Date
- 2025-05-26
- Publication Date
- 2026-05-26
AI Technical Summary
In existing bearing assemblies, oil is prone to leakage due to centrifugal force during shaft rotation, resulting in poor lubrication and increased noise.
A bearing assembly was designed that utilizes capillary action to allow oil to adhere to the bearing surface and flow through a capillary gap formed between the fixture and the bearing, thus preventing leakage.
It effectively prevents oil leakage, improves lubrication, reduces noise, and ensures smooth shaft rotation.
Smart Images
Figure CN224283252U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to a motor part, particularly a bearing assembly within a motor, and a motor and fan having the bearing assembly. Background Technology
[0002] Generally, to avoid excessive wear and noise during motor or fan operation, oil-impregnated bearings are often used instead of traditional bearings. The circulation of oil within the bearing reduces wear and noise. Specifically, the bearing typically has a bore extending through both ends. This bore allows the bearing to absorb oil by immersing it in oil or dripping oil into it, creating an oil-impregnated bearing. A shaft is then connected to the oil-impregnated bearing through this bore, thus providing lubrication between the shaft and the bearing. However, during shaft rotation, the oil can easily detach from the circulation path between the shaft and the bearing due to centrifugal force, leading to leakage.
[0003] In view of this, there is indeed a need to improve the existing bearing assemblies. Utility Model Content
[0004] To solve the above problems, the purpose of this utility model is to provide a bearing assembly and a motor and fan having the bearing assembly, which can prevent oil leakage.
[0005] The directional terms or similar terms used throughout this utility model, such as "front", "back", "left", "right", "top", "bottom", "inner", "outer", "side", etc., are mainly for reference to the directions in the accompanying drawings. Each directional term or similar term is only used to assist in explaining and understanding the various embodiments of this utility model and is not intended to limit this utility model.
[0006] The use of the quantifiers “a” or “an” for the elements and components described throughout this utility model is merely for convenience and to provide the general meaning of the scope of this utility model; in this utility model, it should be interpreted as including one or at least one, and a single concept also includes multiple cases, unless it clearly means otherwise.
[0007] The terms “first,” “second,” … and “Nth” used throughout this utility model are mainly used to distinguish different elements or features (such as elements, directions, or steps), and do not indicate the maximum or minimum number of these elements or features possessed by a corresponding subject or method, nor do they limit the order of priority.
[0008] The terms "combination," "integration," or "assembly" used throughout this utility model mainly include those that allow for separation without damaging the components after connection, or those that make the components inseparable after connection. Those skilled in the art can choose the appropriate term based on the material of the components to be connected or the assembly requirements.
[0009] The bearing assembly of this utility model includes: a bearing having a shaft hole; a fixing member having an annular protrusion axially positioned opposite the bearing, the annular protrusion forming a capillary gap with the bearing; and a rotating shaft rotatably passing through the shaft hole of the bearing.
[0010] Therefore, the bearing assembly of this utility model has a ring protrusion in the fixing member, which is axially positioned opposite the bearing so that the ring protrusion and the bearing surface form a capillary gap, allowing oil to flow through the capillary gap and adhere to the bearing surface. This can guide the oil back into the shaft hole, thus preventing oil leakage.
[0011] The bearing has a major diameter section and a minor diameter section in the axial direction, and an abutting surface is formed between the major diameter section and the minor diameter section. The fixing member abuts against the abutting surface. In this way, the fixing member can abut against the abutting surface, so that the bearing can be positioned in the sleeve.
[0012] The fastener has a through hole axially aligned with the shaft hole, and the radial distance between the through hole and the rotating shaft is 0.05 to 0.25 mm. This allows the rotating shaft to rotate smoothly within the through hole.
[0013] The capillary gap is 0.05 to 0.1 mm. This allows oil to flow onto the bearing surface through the capillary effect created by the gap.
[0014] The annular protrusion is axially positioned opposite one end face of the bearing, and a capillary gap is formed between the annular protrusion and the end face of the bearing. This allows oil to flow by adhering to the end face of the bearing through the capillary effect created by the capillary gap.
[0015] The fastener has an annular wall portion, one end of which abuts against the bearing, and the other end of which has a top plate, with an annular protrusion located on the top plate. Thus, the annular protrusion can axially align with the end face of the bearing to create the capillary gap.
[0016] The annular protrusion has a bottom edge, and the annular protrusion forms a capillary gap with the end face through the bottom edge. In this way, oil can adhere to the end face of the bearing and flow through the capillary phenomenon formed by the capillary gap.
[0017] The end face has an inner edge adjacent to the shaft hole and an outer edge away from the shaft hole. The bottom edge is at a first radial distance from the inner edge and at a second radial distance from the outer edge. The first radial distance is 1.5 to 3 times the second radial distance. Thus, the bottom edge is positioned appropriately on the end face, allowing oil to adhere to and flow onto the end face.
[0018] The annular protrusion has an inner edge and an outer edge on the inner surface of the top plate, and the axial dimension of the annular protrusion gradually decreases from the bottom edge towards the inner edge and the outer edge, respectively. In this way, a better capillary force can be formed between the end face and the bottom edge, thereby guiding the oil to adhere to the end face for flow when passing through the capillary gap.
[0019] The bearing has a first guide surface between its bottom edge and inner edge, and a second guide surface between its bottom edge and outer edge. The angle between the first guide surface and the end face of the bearing is smaller than the angle between the second guide surface and the end face of the bearing. This allows the first guide surface to further guide oil to adhere to and flow on the end face of the bearing.
[0020] The annular protrusion has a bottom end face, which forms the capillary gap with the end face of the bearing. This extends the capillary gap between the bottom end face and the end face, further guiding oil to adhere to and flow on the end face of the bearing.
[0021] The bottom end face of the annular protrusion has a first radial width dimension, which is 1 / 3 to 1 / 4 of the second radial width dimension of the bearing end face. In this way, the bottom end face can be guided by capillary action when oil passes through the capillary gap between the bottom end face and the end face through the first radial width dimension, thereby adhering to the end face of the bearing and flowing.
[0022] The outer radial circumferential surface of the rotating shaft is covered with an oil-repellent agent, which is adjacent to the upper surface of the fixing member. This prevents oil from seeping out between the fixing member and the rotating shaft, thus effectively blocking the leakage of oil.
[0023] The annular protrusion abuts axially against one end face of the bearing, and the end face has at least one oil guide groove. A capillary gap is formed between the annular protrusion and the at least one oil guide groove. In this way, oil can flow through the capillary effect formed by the capillary gap and through the at least one oil guide groove.
[0024] A motor includes: a sleeve having the aforementioned bearing assembly inside; and a stator located on the outer periphery of the sleeve. Thus, the bearing assembly can form the capillary gap, allowing oil to flow through the capillary gap and adhere to the surface of the bearing, thereby guiding the oil back into the shaft hole and preventing oil leakage.
[0025] A fan includes: a fan frame having the aforementioned motor; and a fan wheel coupled to one end of the shaft. Thus, the bearing assembly can form the capillary gap, allowing oil to flow through the capillary gap and adhere to the surface of the bearing, thereby guiding the oil back into the shaft hole and preventing oil leakage. Attached Figure Description
[0026] Figure 1 : An exploded perspective view of the first embodiment of this utility model;
[0027] Figure 2 : A cross-sectional view of the first embodiment of this utility model;
[0028] Figure 3 :like Figure 2 A magnified view of the local structure at point A shown;
[0029] Figure 4 :like Figure 3 Another radial cross-sectional shape diagram of the annular protrusion;
[0030] Figure 5 :like Figure 3 Another radial cross-sectional shape diagram of the annular protrusion;
[0031] Figure 6 :like Figure 3 Another radial cross-sectional shape diagram of the annular protrusion;
[0032] Figure 7 : A partial enlarged view of the annular protrusion in the second embodiment of this utility model;
[0033] Figure 8 :like Figure 7 Another radial cross-sectional shape diagram of the annular protrusion;
[0034] Figure 9 The bearing assembly of this utility model is located in a cross-sectional view of the fan.
[0035] Explanation of reference numerals in the attached figures:
[0036] 1: Bearing
[0037] 1a: End face
[0038] 1b: Oil guide trench
[0039] 11: Shaft Hole
[0040] 12: Large diameter section
[0041] 13: Small path section
[0042] 14: Contact surface
[0043] 15: Guide sloping surface
[0044] 16: Inner edge
[0045] 17: Outer edge
[0046] 2: Fasteners
[0047] 2a: Circumferential wall section
[0048] 2b: Top plate
[0049] 21: Through hole
[0050] 22: Ring protrusion
[0051] 221: Bottom edge
[0052] 222: Inner edge
[0053] 223: Outer edge
[0054] 23: First Guiding Surface
[0055] 24: Second guide surface
[0056] 25: Bottom surface
[0057] T: Sleeve
[0058] T1: Base Plate
[0059] T2: Ring Wall
[0060] T3: Opening
[0061] T4: Positioning ring
[0062] T41: Through-hole
[0063] T5: Abutment Block
[0064] T6: Thrust plate
[0065] B: Bearing assembly
[0066] R: Shaft
[0067] K: Radial distance
[0068] D: Capillary gap
[0069] W1: First radial distance
[0070] W2: Second radial distance
[0071] W3: First radial width dimension
[0072] W4: Second radial width dimension
[0073] F: Fan
[0074] F1: Sector
[0075] F2: Stator
[0076] F3: Fan wheel
[0077] M: Motor. Detailed Implementation
[0078] 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.
[0079] Please refer to Figure 1 , Figure 2 The image shows a first embodiment of the bearing assembly B of this utility model, comprising a bearing 1 and a fixing member 2, wherein the fixing member 2 is axially abutted against the bearing 1.
[0080] The bearing 1 can be located within a sleeve T, which serves to position the bearing 1 and to contain lubricating oil for the bearing 1 to operate. The sleeve T may have components such as 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 of the annular wall T2 can form an opening T3, allowing the bearing 1 to be installed within the sleeve T through the opening T3. Preferably, the sleeve T may have a positioning ring T4 with a through hole T41, adjacent to the base plate T1, and tightly fitted to the inner wall of the annular wall T2. Alternatively, the base plate T1 of the sleeve T may have an abutment block T5 that axially abuts against the positioning ring T4.
[0081] The bearing 1 has two end faces 1a, which are axially opposite each other and can face the locating ring T4 and the opening T3 of the sleeve T, respectively. The bearing 1 has a shaft hole 11 that penetrates the two end faces 1a and aligns with the through hole T41 located in the locating ring T4. The shaft hole 11 allows a rotating shaft R to rotatably pass through it, the other end of which can face the interior of the sleeve T and be coupled to, for example, a thrust plate T6. The bearing 1 can have a large diameter section 12 and a small diameter section 13 axially, and a contact surface 14 can be formed between the large diameter section 12 and the small diameter section 13 through their diameter difference. This contact surface 14 can face the opening T3 of the sleeve T.
[0082] In this embodiment, each end face 1a can be connected to the outer peripheral surface of the bearing 1 and the shaft hole 11 respectively through two guide slopes 15. In this way, the end face 1a can be connected to the axial outer peripheral surface through the guide slopes 15 to allow oil flow. In addition, the oil on the end face 1a can also easily flow into the shaft hole 11 through the guide slopes 15, thereby improving the smoothness of oil circulation.
[0083] The bearing 1 may have at least one oil guide groove 1b, which may be recessed into at least one end face 1a of the bearing 1, for example, the at least one oil guide groove 1b may be recessed into the end face 1a facing the opening T3. In this way, the oil can be concentrated in the at least one oil guide groove 1b for flow. Alternatively, there may be multiple oil guide grooves 1b, 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 1b of the two end faces 1a and the oil guide grooves 1b of the axial outer peripheral surface of the bearing 1 can be connected. This utility model does not limit the distribution pattern of the multiple oil guide grooves 1b.
[0084] Please refer to Figure 2 , Figure 3As shown, the fixing member 2 can be, for example, a dust cover, a leak-proof cover, or an anti-detachment cover; this utility model does not limit this. The fixing member 2 can be attached to the inner wall of the sleeve T by means of, for example, tight fit, welding, or gluing. The fixing member 2 can be used to position the bearing 1 inside the sleeve T. Furthermore, the fixing member 2 can have an annular wall portion 2a, one end of which abuts against the abutment surface 14 of the bearing 1. Thus, the fixing member 2 and the positioning ring T4 can axially clamp the bearing 1, so that the bearing 1 can be positioned inside the sleeve T. The other end of the annular wall portion 2a has a top plate 2b, which has a through hole 21 axially opposite to the shaft hole 11. Thus, the through hole 21 can be used for the rotating shaft R to extend into. Preferably, the radial distance K between the through hole 21 and the rotating shaft R can be 0.05 to 0.25 mm, so that the rotating shaft R can rotate smoothly within the through hole 21. Furthermore, an oil-repellent agent is applied to the radial outer circumferential surface of the rotating shaft R, adjacent to the upper surface of the fixing member 2. This oil-repellent agent can be, for example, a conventional fluorine-based oil-repellent agent, thereby preventing oil from seeping out between the fixing member 2 and the rotating shaft R, thus achieving the effect of blocking the oil flow.
[0085] Please refer to Figure 3 As shown, the fixing member 2 has an annular protrusion 22, which can be located on the lower surface of the top plate 2b. The annular protrusion 22 can be located between the annular wall portion 2a and the through hole 21, and can surround the through hole 21 so that the annular protrusion 22 can be axially aligned with the bearing 1. A capillary gap D is formed between the annular protrusion 22 and the bearing 1, which can be 0.05 to 0.1 mm. For example, the annular protrusion 22 can form the capillary gap D with the end face 1a of the bearing 1. Alternatively, in another embodiment, the annular protrusion 22 can axially abut against the end face 1a of the bearing 1, in which case the capillary gap D can be formed between the annular protrusion 22 and the at least one oil guide groove 1b.
[0086] Thus, when the oil flows out from the end face 1a through the capillary gap D, capillary action occurs at the capillary gap D, causing the oil to accumulate and adhere due to capillary action. This adhesion prevents the oil from splashing out of the capillary gap D, allowing the oil to flow by adhering to the end face 1a of the bearing 1, thereby preventing oil from splashing and seeping out through the through hole 21 of the top plate 2b. Furthermore, this invention does not limit the radial cross-sectional shape of the annular protrusion 22. For example, the radial cross-sectional shape of the annular protrusion 22 can be triangular, hemispherical, trapezoidal, or rectangular, or other geometric shapes.
[0087] In this embodiment, the annular protrusion 22 may have a bottom edge 221, through which the annular protrusion 22 and the end face 1a of the bearing 1 form the capillary gap D. Furthermore, the end face 1a has an inner edge 16 adjacent to the shaft hole 11 and an outer edge 17 away from the shaft hole 11. The bottom edge 221 and the inner edge 16 may have a first radial distance W1, and the bottom edge 221 and the outer edge 17 may have a second radial distance W2, where the first radial distance W1 is 1.5 to 3 times the second radial distance W2. Thus, the bottom edge 221 is positioned appropriately on the end face 1a, preventing it from getting too close to the inner edge 16 or the outer edge 17 of the bearing 1, thereby reducing the capillary effect of the capillary gap D on the oil.
[0088] Please refer to Figures 3-6 As shown, the annular protrusion 22 may have an inner edge 222 and an outer edge 223 on the inner surface of the top plate 2b. The inner edge 222 is adjacent to the through hole 21, and the outer edge 223 is adjacent to the annular wall portion 2a. The axial dimension of the annular protrusion 22 may gradually decrease from the bottom edge 221 toward the inner edge 222 and the outer edge 223, respectively. That is, the thickness of the annular protrusion 22 gradually decreases from the bottom edge 221 toward the opposite sides of the bottom edge 221. In this embodiment, a first guide surface 23 may be provided between the bottom edge 221 and the inner edge 222, and a second guide surface 24 may be provided between the bottom edge 221 and the outer edge 223. The first guide surface 23 and the second guide surface 24 may be, for example, inclined surfaces (e.g., Figure 3 ), concave arc surface (such as Figure 4 ), convex curved surfaces (such as Figure 6 Or a combination of inclined planes and concave or convex surfaces (such as...) Figure 5 Thus, a better adhesion force can be formed between the end face 1a of the bearing 1 and the bottom edge 221 due to capillary action, which allows the oil to be further guided to adhere to the end face 1a of the bearing 1 and flow when passing through the capillary gap D.
[0089] In this embodiment, the first guide surface 23 and the second guide surface 24 can each be an inclined surface, and the angle between the first guide surface 23 and the end face 1a of the bearing 1 can be smaller than the angle between the second guide surface 24 and the end face 1a of the bearing 1. Therefore, it can further guide the oil to adhere to the end face 1a of the bearing 1 for flow.
[0090] Please refer to Figure 7 , Figure 8As shown, this is a second embodiment of the bearing assembly B of this utility model. Compared with the first embodiment, in this embodiment, the annular protrusion 22 may have a bottom end face 25, and the annular protrusion 22 forms the capillary gap D with the end face 1a of the bearing 1 through the bottom end face 25. The bottom end face 25 may have a first radial width dimension W3, and the end face 1a of the bearing 1 may have a second radial width dimension W4. The first radial width dimension W3 may be 1 / 3 to 1 / 4 of the second radial width dimension W4. In addition, the bottom end face 25 may form the first guide surface 23 and the second guide surface 24 with the inner edge portion 222 and the outer edge portion 223 respectively (e.g., Figure 7 Alternatively, the bottom end face 25 may form a discontinuous segment with the inner surface of the top plate 2b (e.g., Figure 8 Therefore, the bottom end face 25 can extend the capillary gap D between the bottom end face 25 and the end face 1a through the first radial width dimension W3, so that the oil can be further guided by capillary phenomenon, and thus the oil can adhere to the end face 1a of the bearing 1 and flow.
[0091] Please refer to Figure 9 As shown, the bearing assembly B of this utility model, after being combined with the sleeve T, can be installed on a fan F. The fan F may have a fan frame F1, and the sleeve T may be located on the fan frame F1. The outer periphery of the sleeve T may have a stator F2 so that the stator F2 and the sleeve T with the bearing assembly B can form a motor M. One end of the rotating shaft R can be connected to a fan wheel F3, and the motor M can drive the fan wheel F3 to rotate. In this way, when the fan F is running, oil leakage from the bearing assembly B can be prevented.
[0092] In summary, the bearing assembly of this utility model and the motor and fan having the hydrodynamic bearing, by having the annular protrusion in the fixing member, the annular protrusion is axially positioned opposite the bearing, so that the annular protrusion and the bearing surface form the capillary gap, allowing oil to flow through the capillary gap and adhere to the bearing surface, thereby guiding the oil back into the shaft hole, thus achieving the effect of preventing oil leakage.
[0093] 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 in that, include: A bearing having a shaft bore; A fastener has an annular protrusion axially positioned opposite the bearing, forming a capillary gap between the annular protrusion and the bearing; and A rotating shaft is rotatably inserted through the shaft hole of the bearing.
2. The bearing assembly as claimed in claim 1, characterized in that, The bearing has a large diameter section and a small diameter section in the axial direction, and an abutting surface is formed between the large diameter section and the small diameter section, and the fixing member abuts against the abutting surface.
3. The bearing assembly as claimed in claim 1, characterized in that, The fastener has a through hole axially aligned with the shaft hole, and the radial distance between the through hole and the shaft is 0.05 to 0.25 mm.
4. The bearing assembly as claimed in claim 1, characterized in that, The capillary gap is 0.05–0.1 mm.
5. The bearing assembly as claimed in claim 1, characterized in that, The annular protrusion is axially positioned opposite one end face of the bearing, and the capillary gap is formed between the annular protrusion and the end face of the bearing.
6. The bearing assembly as claimed in claim 5, characterized in that, The fastener has a ring wall portion, one end of which abuts against the bearing, and the other end of which has a top plate, with the ring protrusion located on the top plate.
7. The bearing assembly as claimed in claim 6, characterized in that, The annular protrusion has a bottom edge, and the annular protrusion forms the capillary gap with the end face through the bottom edge.
8. The bearing assembly as claimed in claim 7, characterized in that, The end face has an inner edge adjacent to the shaft hole and an outer edge away from the shaft hole. The bottom edge has a first radial distance from the inner edge and a second radial distance from the outer edge. The first radial distance is 1.5 to 3 times the second radial distance.
9. The bearing assembly as claimed in claim 7, characterized in that, The annular protrusion has an inner edge and an outer edge on the inner surface of the top plate, and the axial dimension of the annular protrusion gradually decreases from the bottom edge toward the inner edge and the outer edge, respectively.
10. The bearing assembly as claimed in claim 9, characterized in that, There is a first guide surface between the bottom edge and the inner edge, and a second guide surface between the bottom edge and the outer edge. The angle between the first guide surface and the end face of the bearing is smaller than the angle between the second guide surface and the end face of the bearing.
11. The bearing assembly as claimed in claim 5, characterized in that, The annular protrusion has a bottom end face, through which the annular protrusion forms the capillary gap with the end face of the bearing.
12. The bearing assembly as claimed in claim 11, characterized in that, The bottom end face of the annular protrusion has a first radial width dimension, which is 1 / 3 to 1 / 4 of the second radial width dimension of the end face of the bearing.
13. The bearing assembly as claimed in claim 1, characterized in that, The radial outer circumferential surface of the shaft is covered with an oiling agent, which is adjacent to the upper surface of the fixing member.
14. The bearing assembly as claimed in claim 1, characterized in that, The annular protrusion abuts axially against one end face of the bearing, the end face having at least one oil guide groove, and the capillary gap is formed between the annular protrusion and the at least one oil guide groove.
15. A motor, characterized in that, include: A sleeve having a bearing assembly as described in any one of claims 1 to 14; and A stator is located on the outer periphery of the sleeve.
16. A fan, comprising: A fan frame having a motor as described in claim 15; and A fan wheel is attached to one end of the shaft.