Bearing assembly, motor having the same, and fan

Abstract

A bearing assembly is used to solve the problem of oil leakage of the existing bearing assembly. It comprises a shaft tube with a closed end and an open end opposite to each other, the shaft tube has a linear segment and a reduced diameter segment connected from the closed end to the open end, the reduced diameter segment is connected to the open end; a bearing has a shaft hole, the shaft hole penetrates through two end faces of the bearing, the two end faces have a side peripheral surface therebetween, the side peripheral surface is radially opposite to the linear segment, an inner surface of the reduced diameter segment abuts between the end face and the side peripheral surface of the bearing; and a rotating shaft is rotatably arranged in the shaft hole of the bearing. The utility model also relates to a motor and a fan with the bearing assembly. Thus, the effect of avoiding oil leakage can be achieved.

Description

Technical Field

[0001] This utility model relates to a motor part, and more particularly to a bearing assembly within a motor, as well as 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, a 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 leak out of the circulation path between the shaft and the bearing, 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 components, directions, or steps, etc.) 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 shaft tube having a closed end and an open end opposite to each other, the shaft tube having a straight line segment and a reduced diameter segment connected from the closed end to the open end, the reduced diameter segment connecting to the open end; a bearing having a shaft hole penetrating through two end faces of the bearing, a side circumferential surface between the two end faces, the side circumferential surface being radially opposite to the straight line segment, an inner surface of the reduced diameter segment abutting between the end face of the bearing and the side circumferential surface; and a rotating shaft rotatably passing through the shaft hole of the bearing.

[0010] Therefore, the bearing assembly of this utility model and the motor and fan having the bearing assembly are connected to the open end through the reduced diameter section of the shaft tube. The inner surface of the reduced diameter section abuts between the end face and the side peripheral surface of the bearing, so that a capillary effect is formed between the inner surface and the end face. When the oil flows through the inner surface of the reduced diameter section and out of the end face, the oil will generate an adhesion force due to the capillary effect. This adhesion force can prevent the oil from splashing and allow the oil to flow by adhering to the end face of the bearing, thereby preventing the oil from splashing and seeping out of the open end.

[0011] The reduced-diameter section is thermoformed and inclined towards the axis of the shaft tube, so that the inner surface of the reduced-diameter section abuts against the end face and the side circumferential surface of the bearing. In this way, the inner diameter of the shaft tube can gradually decrease from the reduced-diameter section towards the open end, so that the inner diameter of the open end is smaller than the inner diameter of the straight section of the shaft tube, which has the effect of reducing the leakage of oil from the shaft tube through the open end.

[0012] The tube has a first wall thickness in the reduced diameter section and a second wall thickness in the straight section, the first wall thickness being less than the second wall thickness. This allows the heating fixture to easily perform hot-press molding of the reduced diameter section.

[0013] The wall thickness of the shaft tube gradually decreases as the diameter reduction section forms. This allows the heated fixture to easily perform hot-press molding of the diameter reduction section.

[0014] The wall thickness of the shaft tube is formed by the difference between the straight section and the reduced diameter section. This allows the heating fixture to easily hot-press and mold the reduced diameter section.

[0015] The wall thickness of the reduced-diameter section is equal to that of the straight section. This results in the overall shaft tube having better strength.

[0016] Each end face is connected to the side circumferential surface of the bearing and the shaft hole by two guide bevels, and the inner surface abuts between the end face and the guide bevel. In this way, oil can flow through the oil guide groove of the end face and the side circumferential surface.

[0017] The inner surface of the reduced diameter section forms an acute angle with the guide slope connecting the side circumference, and the guide slope connecting the bearing to the shaft hole forms an acute angle with the rotating shaft. In this way, the oil can accumulate and adhere at the aforementioned acute angle, allowing the oil to flow along the guide slopes on both sides of the end face, thereby preventing oil from splashing and seeping out from the opening end.

[0018] The inner surface and the end face have an included angle of 10° to 40°. This included angle can create a capillary effect, and the oil will accumulate and adhere at the included angle due to the capillary effect.

[0019] The inner surface facing the end face is covered with an oil-repellent agent. In this way, the oil-repellent agent achieves the effect of blocking the oil.

[0020] The shaft has an annular recess located radially opposite the reduced diameter section. This annular recess on the circumferential wall of the shaft effectively obstructs the axial flow of oil.

[0021] The annular recess is covered with an oil-repellent agent. In this way, the oil-repellent agent achieves the effect of blocking the oil flow.

[0022] The annular recess is located axially at a depth not lower than the end face of the bearing. This allows oil to flow into the shaft hole through the guide bevel without being blocked by the annular recess.

[0023] In this design, one axial dimension of the annular recess is greater than the wall thickness of the narrowed section. Thus, the annular recess can have a better axial extension range on the shaft, thereby effectively hindering oil flow.

[0024] The radial depth of the annular recess is 1 / 8 to 1 / 4 of the outer diameter of the shaft. This allows the annular recess to have a suitable depth, creating an appropriate radial step relative to the shaft's circumferential wall, thereby hindering oil flow.

[0025] The motor of this invention includes: the aforementioned bearing assembly, with the rotating shaft coupled to a hub; and a stator located on the outer periphery of the shaft tube, the stator driving the hub to rotate. In this way, the oil in the bearing assembly can adhere to the surface of the bearing and flow, thereby guiding the oil back into the shaft hole, achieving the effect of preventing oil leakage.

[0026] The fan of this utility model includes: a fan frame having the aforementioned motor; and a fan wheel having a hub and a plurality of fan blades arranged around the hub. In this way, the oil in the bearing assembly can adhere to the surface of the bearing and flow, thereby guiding the oil back into the shaft hole, thus preventing oil leakage. Attached Figure Description

[0027] Figure 1 : An exploded perspective view of a preferred embodiment of the present invention; Figure 2 : A cross-sectional view of a preferred embodiment of the present invention; Figure 3 :like Figure 2 A magnified view of the local structure at point A shown; Figure 4 :like Figure 3 The straight section of the shaft tube and another embodiment of the reduced diameter section are shown in the diagram. Figure 5 :like Figure 3 Another implementation diagram of the straight section and the reduced diameter section of the shaft tube; Figure 6 The bearing assembly of this utility model is located in a cross-sectional view of the fan.

[0028] Explanation of reference numerals in the attached figures: 1: Shaft tube 11: Base Plate 12: Encircling wall 12a: Closed end 12b: Open end 13: Position the shoulder 14: Straight line segment 15: Reduced diameter section 15a: Inner surface 16: Wear-resistant pads 2: Bearings 2a: End face 2b: Lateral surface 21: Shaft Hole 22: Oil guide trench 23: Guide sloping surface 3: Shaft 3a: First end 3b: Second end 31: Annular depression B: Bearing assembly S: Oil storage space O: Axis H1: First wall thickness H2: Second wall thickness D1: Axial dimension D2: Radial depth dimension θ: included angle J: Wheel hub F: Fan F1: Sector F2: Stator F3: Fan blades P: Fan wheel M: Motor. Detailed Implementation

[0029] 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.

[0030] Please refer to Figure 1 As shown, it is the first embodiment of the bearing assembly B of this utility model, which includes a shaft tube 1, a bearing 2 and a rotating shaft 3. The bearing 2 is located inside the shaft tube 1, and the rotating shaft 3 is rotatably connected to the bearing 2.

[0031] The shaft tube 1 may have a base plate 11 and an annular wall 12. One end of the annular wall 12 may be formed into a closed end 12a by the base plate 11, and the other end of the annular wall 12 may be formed into an open end 12b. Thus, the shaft tube 1 can be used to position the bearing 2 and to contain lubricating oil so that the lubricating oil can be supplied to the bearing 2 for operation. The shaft tube 1 may have a positioning shoulder 13, which may be adjacent to the base plate 11. The positioning shoulder 13 can be used for the bearing 2 to abut against, so that an oil storage space S can be formed between the bearing 2 and the base plate 11.

[0032] Please refer to Figures 2-5As shown, the shaft tube 1 may have a connected straight line segment 14 and a reduced diameter segment 15. The straight line segment 14 connects to the closed end 12a, and the reduced diameter segment 15 connects to the open end 12b. The inner diameter of the shaft tube 1 may gradually decrease from the reduced diameter segment 15 towards the open end 12b, so that the inner diameter of the open end 12b is smaller than the inner diameter of the straight line segment 14 of the shaft tube 1, thereby preventing oil from seeping out of the shaft tube 1 from the open end 12b. In this embodiment, the open end 12b of the shaft tube 1 can be hot-pressed and molded by a heating fixture to make the shaft tube 1 bend in an inclined direction towards the axis O of the shaft tube 1 near the open end 12b to form the reduced diameter segment 15. For example, the shaft tube 1 near the open end 12b can be hot-pressed and molded into an arc shape or a straight line inclined towards the axis O, so that an inner surface 15a of the reduced diameter segment 15 can face the bearing 2 (described in detail later). Preferably, the shaft tube 1 has a first wall thickness H1 in the reduced diameter section 15, and the straight section 14 has a second wall thickness H2, wherein the first wall thickness H1 is smaller than the second wall thickness H2. For example, the wall thickness (first wall thickness H1) of the shaft tube 1 can gradually decrease in the reduced diameter section 15 (e.g., Figure 3 Alternatively, the wall thickness of the shaft tube 1 can be formed by a step difference between the second wall thickness H2 of the straight segment 14 and the first wall thickness H1 of the reduced diameter segment 15 (e.g., Figure 4 This allows the heating fixture to easily hot-press the reduced diameter section 15. Alternatively, the first wall thickness H1 of the reduced diameter section 15 can be equal to the second wall thickness H2 of the straight section 14 (e.g., Figure 5 This ensures that the shaft tube 1 has better overall strength.

[0033] Please refer to Figure 1 , Figure 2 As shown, the bearing 2 is located inside the shaft tube 1. For example, the annular wall 12 and the base plate 11 can be integrally formed (not shown). The bearing 2 can be inserted into the shaft tube 1 through the open end 12b of the annular wall 12, and then the open end 12b of the shaft tube 1 can be hot-pressed and shaped by a heating fixture. Alternatively, in this embodiment, the annular wall 12 and the base plate 11 can be assembled together (e.g., Figure 1 The bearing 2 can be inserted into the shaft tube 1 from below the annular wall 12 and then closed by the base plate 11. The bearing 2 can have two end faces 2a, which are axially opposite each other, and a circumferential surface 2b between the two end faces 2a. One end face 2a can face the opening end 12b of the shaft tube 1, and the other end face 2a can face the base plate 11. The bearing 2 has a shaft hole 21 that passes through the two end faces 2a.

[0034] The bearing 2 may have at least one oil guide groove 22, which may be recessed into the outer surface of the bearing 2. For example, the at least one oil guide groove 22 may extend into the two end faces 2a and the side peripheral surface 2b of the bearing 2, so that the at least one oil guide groove 22 can connect to the opening of the shaft hole 21 located on the two end faces 2a. In this way, the oil can be concentrated in the at least one oil guide groove 22 and circulate between the outer surface of the bearing 2 and the shaft hole 21. Alternatively, there may be several oil guide grooves 22, which may be recessed into the two end faces 2a and the side peripheral surface 2b of the bearing 2, respectively. The oil guide grooves 22 on the two end faces 2a and the oil guide grooves 22 on the side peripheral surface 2b of the bearing 2 can form a communication. This invention does not limit the distribution pattern of the multiple oil guide grooves 22.

[0035] In this embodiment, each end face 2a is connected to the side peripheral surface 2b of the bearing 2 and the shaft hole 21 respectively via two guide ramps 23. Thus, the oil guide groove 22 recessed in the end face 2a communicates with the oil guide groove 22 of the side peripheral surface 2b through the guide ramps 23 to allow oil flow. Furthermore, the oil in the oil guide groove 22 recessed in the end face 2a can also easily flow into the shaft hole 21 through the guide ramps 23 connected to the shaft hole 21, thereby improving the smoothness of oil circulation.

[0036] Please refer to Figure 2 As shown, it is worth noting that the side circumferential surface 2b of the bearing 2 is radially opposite to the straight segment 14 located in the shaft tube 1, so that the inner surface 15a of the reduced diameter section 15 can be inclined to abut against the end face 2a and the side circumferential surface 2b. For example, the inner surface 15a of the reduced diameter section 15 can abut against the periphery of the end face 2a. In this embodiment, the inner surface 15a can abut against the end face 2a and the guide slope 23, and the oil can flow through the oil guide groove 22 of the end face 2a and the side circumferential surface 2b.

[0037] The inner surface 15a and the end face 2a can have an included angle θ, which can be 10° to 40°. This included angle θ creates capillary action. When oil flows through the inner surface 15a of the narrowed section 15 and out through the end face 2a, the oil accumulates at the included angle θ due to capillary action. This adhesion prevents the oil from splashing out from the included angle θ, allowing the oil to flow by adhering to the end face 2a of the bearing 2, thus preventing oil from splashing and seeping out from the open end 12b. Preferably, the portion of the inner surface 15a facing the end face 2a can be covered with an oil-repellent agent, such as a conventional fluorine-based oil-repellent agent, thereby achieving the effect of blocking the oil flow.

[0038] Furthermore, the inner surface 15a and the guide slope 23 connecting the side peripheral surface 2b can form an acute angle; also, the guide slope 23 of the bearing 2 adjacent to the shaft 3 can form an acute angle with the shaft 3. Therefore, capillary action can also be formed through the aforementioned acute angle, causing the oil to accumulate and adhere at the aforementioned acute angle, allowing the oil to adhere to the guide slope 23 on both sides of the end face 2a for flow, thereby preventing the oil from splashing and seeping out from the opening end 12b.

[0039] Please continue reading. Figure 1 , Figure 2 As shown, the rotating shaft 3 is rotatably inserted into the shaft hole 21 of the bearing 2. The rotating shaft 3 may 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, and the second end 3b can face the interior of the shaft tube 1. Preferably, the oil storage space S of the shaft tube 1 may have a wear-resistant plate 16, and the second end 3b can abut against the wear-resistant plate 16. The rotating shaft 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 shaft 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 shaft 3 can hinder the axial flow of oil. Furthermore, the annular recess 31 covers the aforementioned oil-repellent agent, thereby preventing the oil from adhering to the annular recess 31 and further enhancing the oil-blocking effect of the annular recess 31.

[0040] Please continue reading. Figure 3 As shown, the annular recess 31 is radially located opposite the reduced diameter section 15. The annular recess 31 is axially not lower than the end face 2a of the bearing 2. Therefore, oil can flow into the shaft hole 21 through the guide slope 23 without being blocked by the annular recess 31. In this embodiment, the annular recess 31 may have an axial dimension D1, which may be greater than the first wall thickness H1 of the reduced diameter section 15. Thus, the annular recess 31 can have a better axial extension range on the shaft 3, thereby hindering oil flow. The annular recess 31 may have a radial depth dimension D2, which may be 1 / 8 to 1 / 4 of the outer diameter of the shaft 3. Thus, the annular recess 31 can have a better depth, forming an appropriate radial step relative to the peripheral wall of the shaft 3, thereby hindering oil flow.

[0041] Please refer to Figure 6As shown, the bearing assembly B of this utility model can be installed in a fan F, which may have a fan frame F1, and the shaft tube 1 may be located in the fan frame F1. The outer periphery of the shaft tube 1 may have a stator F2, so that the stator F2 and the bearing assembly B can form a motor M. The first end 3a of the rotating shaft 3 can be connected to a hub J, which may have, for example, a magnet, so that the iron core coil of the stator F2 can drive the hub J to rotate. Several fan blades F3 can be arranged around the hub J to form a fan wheel P, and the motor M can drive the several fan blades F3 to rotate. In this way, when the fan F is running, oil can be prevented from leaking out from the bearing assembly B.

[0042] In summary, the bearing assembly of this utility model connects the open end to the reduced diameter section of the shaft tube. The inner surface of the reduced diameter section abuts against the end face and the side circumferential surface of the bearing, thereby creating a capillary effect between the inner surface and the end face. When oil flows through the inner surface of the reduced diameter section and out of the end face, the oil will generate an adhesion force due to the capillary effect. This adhesion force can prevent the oil from splashing, allowing the oil to flow by adhering to the end face of the bearing, thus preventing the oil from splashing and seeping out from the open end.

[0043] 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 shaft tube has a closed end and an open end, and the shaft tube has a straight section and a reduced diameter section connected from the closed end to the open end, the reduced diameter section being connected to the open end; A bearing has a bore extending through both end faces of the bearing, with a circumferential surface between the two end faces, the circumferential surface being radially opposite to a straight section, and an inner surface of the reduced-diameter section abutting between the end face of the bearing and the circumferential surface; and A rotating shaft that is rotatably inserted through the shaft hole of the bearing.

2. The bearing assembly as claimed in claim 1, characterized in that, The reduced diameter section is thermoformed and inclined toward the axis of the shaft tube, so that the inner surface of the reduced diameter section abuts between the end face of the bearing and the side circumferential surface.

3. The bearing assembly as claimed in claim 1, characterized in that, The tube has a first wall thickness in the reduced diameter section and a second wall thickness in the straight section, the first wall thickness being less than the second wall thickness.

4. The bearing assembly as described in claim 3, characterized in that, The initial wall thickness of the tube gradually decreases as the diameter reduction section forms.

5. The bearing assembly as described in claim 3, characterized in that, The tube forms a step difference between the second wall thickness of the straight section and the first wall thickness of the narrowed section.

6. The bearing assembly as claimed in claim 1, characterized in that, The wall thickness of the narrowed section is equal to the wall thickness of the straight section.

7. The bearing assembly as claimed in claim 1, characterized in that, Each end face is connected to the side circumferential surface of the bearing and the shaft hole by two guide bevels respectively, and the inner surface abuts between the end face and the guide bevel.

8. The bearing assembly as claimed in claim 7, characterized in that, The inner surface of the reduced diameter section forms an acute angle with the guide bevel connecting the side circumference, and the guide bevel connecting the bearing to the shaft hole forms an acute angle with the rotating shaft.

9. The bearing assembly as claimed in claim 1, characterized in that, The inner surface and the end face have an included angle, which is 10° to 40°.

10. The bearing assembly as claimed in claim 1, characterized in that, The portion of the inner surface facing the end face is covered with an oil-removing agent.

11. The bearing assembly as claimed in any one of claims 1 to 10, characterized in that, The shaft has an annular recess that is radially opposite to the reduced diameter section.

12. The bearing assembly as claimed in claim 11, characterized in that, The annular depression is covered with an oil-removing agent.

13. The bearing assembly as claimed in claim 11, characterized in that, The annular recess is not lower than the end face of the bearing in the axial direction.

14. The bearing assembly as claimed in claim 11, characterized in that, One axial dimension of the annular recess is greater than the wall thickness of the narrowed section.

15. The bearing assembly as claimed in claim 11, characterized in that, The radial depth of the annular recess is 1 / 8 to 1 / 4 of the outer diameter of the shaft.

16. A motor, characterized in that, include: A bearing assembly as claimed in any one of claims 1 to 15, wherein the shaft is coupled to a hub; and A stator, located on the outer periphery of the shaft tube, drives the hub to rotate.

17. A fan, characterized in that, include: A fan frame having a motor as described in claim 16; and A fan wheel has a hub and several fan blades arranged around the hub.

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