Bearing assembly

Abstract

A bearing assembly is used for solving the problem that air in an existing bearing is difficult to exhaust. Comprising a sleeve which is provided with an opening and a closed part; the bearing is located in the sleeve, an oil storage space is formed between the bearing and the closed part, the bearing is provided with a section part, a gap is formed between the section part and the inner wall face of the sleeve to form an exhaust channel, and the opening is communicated with the oil storage space through the exhaust channel. Therefore, the effects that air is easy to exhaust and the rotating shaft can be smoothly installed can be achieved.

Description

Technical Field

[0001] This utility model relates to a bearing assembly, and more particularly to a bearing assembly using an oil-impregnated bearing. Background Technology

[0002] Generally speaking, in order to avoid excessive wear and noise during the operation of motors or fans, oil-impregnated bearings are mostly used instead of traditional bearings, so as to reduce wear and noise through the circulation of oil in the bearing.

[0003] Please refer to Figure 1 As shown, this is a conventional bearing assembly 9, which has a bushing 91 with a bottom 92 and an annular wall 93, the bottom 92 closing one end of the annular wall 93. The bearing assembly 9 has a bearing 94 housed within the bushing 91, and the bearing 94 has a shaft hole 95 extending through both ends of the bearing 94. After oil is injected into the shaft hole 95, a rotating shaft 96 can be connected to the bearing 94 through the shaft hole 95, thus providing lubrication between the rotating shaft 96 and the bearing 94.

[0004] However, when the shaft 96 enters through the shaft hole 95, the air in the shaft hole 95 can only be slowly squeezed out through the gap between the shaft 96 and the shaft hole 95. The air is difficult to be smoothly discharged from the shaft hole 95, which makes the shaft 96 susceptible to air pressure and unable to smoothly enter the shaft hole 95. Alternatively, the oil in the bearing 94 may be affected by pressure and overflow from the top of the shaft hole 95 as the air is squeezed out.

[0005] In view of this, there is indeed a need to improve the existing bearing assemblies. Utility Model Content

[0006] To address the aforementioned problems, the purpose of this invention is to provide a bearing assembly that allows for the smooth discharge of internal air.

[0007] 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.

[0008] 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.

[0009] The terms "combination," "integration," or "assembly" used throughout this utility model mainly include forms such as those where the components can be separated without damaging them after connection, or those where the components cannot be separated 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.

[0010] The bearing assembly of this utility model includes: a sleeve having an opening and a closing portion; and a bearing located inside the sleeve, with an oil storage space between the bearing and the closing portion, the bearing having a cross-sectional portion, and a venting channel formed by a gap between the cross-sectional portion and the inner wall surface of the sleeve, the opening communicating with the oil storage space through the venting channel.

[0011] Therefore, the bearing assembly of this utility model, by having the cross-section on the outer periphery of the bearing, forms an exhaust channel between the bearing and the inner wall of the sleeve. The exhaust channel can connect the oil storage space located in the closed part of the sleeve and the opening above the sleeve. In this way, the air compressed after the shaft enters the bearing can be smoothly discharged through the exhaust channel without forming an airtight pressure in the shaft hole. This achieves the effects of making it easy for air to be discharged, preventing oil from overflowing from the shaft hole, and enabling the shaft to be installed smoothly.

[0012] The sleeve has a reduced diameter section that connects to the closed section to form a shoulder within the sleeve. This allows the bearing to be positioned within the sleeve via the shoulder.

[0013] The bearing has a first end face and a second end face facing each other. The first end face faces the opening, and the second end face faces the closed portion. The bearing has a large diameter section connected to the first end face, and a small diameter section connected to the second end face. A contact surface is formed between the large diameter section and the small diameter section, and this contact surface abuts against the shoulder. Thus, the bearing can abut against the shoulder through the contact surface, thereby creating a gap between the bearing and the inner bottom surface of the sleeve.

[0014] The abutting surface and the second end face have a first axial distance, and the shoulder and the inner bottom surface of the closed portion have a second axial distance, the first axial distance being smaller than the second axial distance. This creates a gap between the bearing and the inner bottom surface of the sleeve, thus forming the oil storage space.

[0015] The oil reservoir includes a wear-resistant plate, and the first axial distance is less than the distance between the shoulder and the surface of the wear-resistant plate facing the second end face. This allows for a gap between the bearing and the wear-resistant plate.

[0016] There is a gap between the narrow-diameter section and the reduced-diameter section, and the exhaust passage connects to the oil storage space through this gap. This allows air from the oil storage space to smoothly enter the exhaust passage.

[0017] The cross-section has two radial ends, which are respectively connected to the circumferential surface of the large-diameter section. The axis of the bearing bore and the two radial ends of the cross-section are respectively connected by a reference line, and the included angle between the two reference lines is 10° to 120°. In this way, the cross-section can form an appropriate radial extension range in the bearing, so that the exhaust passage can be used for rapid air passage.

[0018] The cross-section has a first axial end edge, which is connected to the first end face of the bearing. The exhaust passage communicates with the opening through the first axial end edge. This allows air in the exhaust passage to be smoothly discharged through the opening.

[0019] The first end face has a recessed portion with a concave bottom surface, and the first axial end edge extends at least to the recessed portion. Thus, the recessed portion ensures unobstructed communication between the cross-section and the opening.

[0020] Specifically, in the radial direction of the bearing, the shortest vertical distance from the axis of the bore to the cross-section is less than the radius of the major diameter section of the bearing, and this shortest vertical distance is greater than or equal to the radial distance from the axis to 1 / 4 of the depth of the concave bottom surface. Thus, the cross-section can achieve the effect of forming an appropriate recess distance in the major diameter section.

[0021] The cross-section has a second axial end edge that connects to the abutment surface, and the exhaust passage communicates with the oil storage space through the second axial end edge. This allows air from the oil storage space to smoothly enter the exhaust passage.

[0022] Specifically, the shortest distance from the axis of the bearing's bore to the second axial end edge is less than the radial distance from the axis to the reduced diameter portion of the sleeve. This allows the venting passage to communicate with the oil reservoir via the second axial end edge.

[0023] The sleeve has a cap located at the opening. This cap prevents the internal components of the sleeve from coming out of the opening.

[0024] The sleeve includes an anti-detachment component located between the cover and the bearing. This anti-detachment component effectively prevents the shaft from coming loose.

[0025] The anti-detachment component has a through hole and several through grooves, one end of which is connected to the through hole. This allows the rotating shaft to be easily forced into the through hole of the anti-detachment component. Attached Figure Description

[0026] Figure 1 A diagram of an existing bearing assembly;

[0027] Figure 2 : An exploded perspective view of a preferred embodiment of the present invention;

[0028] Figure 3 : A preferred embodiment of the present invention is shown in the following diagram;

[0029] Figure 4 :along Figure 3 AA-line cross-section;

[0030] Figure 5 A top view of a bearing according to a preferred embodiment of this utility model;

[0031] Figure 6 : Schematic diagram of air being expelled when the shaft enters the bearing bore;

[0032] Figure 7 The shaft is located in the bearing diagram.

[0033] Explanation of reference numerals in the attached figures:

[0034] [This utility model]

[0035] 1: Sleeve

[0036] 1a: Inner wall surface

[0037] 11: Opening

[0038] 12: Enclosed section

[0039] 12a: Inner bottom surface

[0040] 13: Shoulders

[0041] 14: Reduction section

[0042] 15: Capping

[0043] 15a: Through hole

[0044] 16: Anti-slip component

[0045] 16a: Through hole

[0046] 161: Through-slot

[0047] 17: Wear-resistant pads

[0048] 2: Bearings

[0049] 2a: First end face

[0050] 2b: Second end face

[0051] 21: Shaft Hole

[0052] 22: Large diameter section

[0053] 23: Shortest path

[0054] 24: Contact surface

[0055] 25: Cross-section

[0056] 25a: Radial end edge

[0057] 251: First axial end edge

[0058] 252: Second axial end edge

[0059] 26: Recessed part

[0060] 261: Concave bottom surface

[0061] 262: Inner ring wall

[0062] D1: First axial distance

[0063] D2: Second axial distance

[0064] D3: First radial distance

[0065] D4: Second radial distance

[0066] D5: Shortest radial distance

[0067] T: Shaft

[0068] T1: Annular groove

[0069] S: Oil storage space

[0070] O: Axis

[0071] R: Exhaust passage

[0072] U: Shortest vertical distance

[0073] L: Baseline

[0074] θ: included angle

[0075] J: Bearing assembly

[0076] ﹝existing﹞

[0077] 9: Bearing assembly

[0078] 91: Bushing

[0079] 92: Bottom

[0080] 93: Encircling Wall

[0081] 94: Bearing

[0082] 95: Shaft hole

[0083] 96: Axle. Detailed Implementation

[0084] 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.

[0085] Please refer to Figure 2 , Figure 3 As shown, it is a preferred embodiment of the bearing assembly J of the present invention, including a sleeve 1 and a bearing 2, the bearing 2 being located inside the sleeve 1.

[0086] The sleeve 1 can be a hollow cup shape, and can be filled with oil. The sleeve 1 can have an opening 11 and a closing portion 12, located at opposite ends of the sleeve 1. The closing portion 12 is used to close one end of the sleeve 1. The sleeve 1 can have a shoulder 13 inside, which can be used for the bearing 2 to abut against. Furthermore, the sleeve 1 can have a reduced diameter portion 14 inside, which connects to the closing portion 12, thereby forming the shoulder 13.

[0087] The sleeve 1 may have a cover 15 located at the opening 11. The cover 15 may be attached to the inner wall of the sleeve 1 by means of, for example, tight fit, welding or gluing, and adjacent to the opening 11. The cover 15 has a through hole 15a that axially extends through the cover 15. The diameter of the through hole 15a is larger than the outer diameter of a rotating shaft T, so that the rotating shaft T can be inserted into the through hole 15a.

[0088] The bearing 2 is located inside the sleeve 1. The bearing 2 can be, for example, a sintered bearing or a machined bearing; this invention is not limited to these types. In this embodiment, the bearing 2 can be made of phosphor bronze. Furthermore, the bearing 2 can have a first end face 2a and a second end face 2b facing each other. The first end face 2a can face the opening 11, and the second end face 2b can face the closed portion 12. A shaft hole 21 of the bearing 2 passes through the first end face 2a and the second end face 2b. The bearing 2 can have a large diameter section 22 connected to the first end face 2a, and a small diameter section 23 connected to the second end face 2b. The large diameter section 22 and the small diameter section 23 can form an abutment surface 24 through their diameter difference. Thus, the bearing 2 can be positioned inside the sleeve 1 by the abutting surface 24 of the bearing 2 abutting against the shoulder 13 inside the sleeve 1, so that the small diameter section 23 is axially aligned with the reduced diameter section 14.

[0089] Please refer to Figure 4 As shown, the abutment surface 24 and the second end face 2b can have a first axial distance D1, and the shoulder 13 and the inner bottom surface 12a of the closed portion 12 can have a second axial distance D2. The first axial distance D1 is smaller than the second axial distance D2. Thus, the second end face 2b and the inner bottom surface 12a of the bearing 2 can be spaced apart to form an oil storage space S. In addition, there is a first radial distance D3 from the axis O of the shaft hole 21 (i.e., the center of the shaft hole 21) to the circumferential surface of the small diameter section 23, and a second radial distance D4 from the axis O to the reduced diameter portion 14 of the sleeve 1. The first radial distance D3 is smaller than the second radial distance D4, so that there is a gap between the circumferential surface of the small diameter section 23 and the reduced diameter portion 14, and this gap can communicate with the oil storage space S.

[0090] Please continue reading. Figure 2 , Figure 4 As shown, the bearing 2 has a cross-section 25, which can be formed by D-cutting the bearing 2. The cross-section 25 is located in the large diameter section 22, and there is a gap between the cross-section 25 and an inner wall surface 1a of the sleeve 1 to form an exhaust channel R. The exhaust channel R can connect the oil storage space S and the opening 11 of the sleeve 1. In this way, the air in the oil storage space S can be discharged through the exhaust channel R from the opening 11.

[0091] Please continue reading. Figure 2 , Figure 5As shown, further, when the radial cross-section of the sleeve 1 is a perfect circle, the bearing 2 can be formed in a non-perfect circular shape in the radial direction to form the cross-section 25, that is, the radial cross-section of the bearing 2 in the cross-section 25 is non-perfect circular. More specifically, the cross-section 25 can have two radial end edges 25a, which are respectively connected to the circumferential surface of the large diameter section 22. In this embodiment, in the radial direction of the bearing 2, the axis O of the shaft hole 21 and the two radial end edges 25a of the cross-section 25 can respectively pass through a virtual reference line L, and there can be an included angle θ between the two reference lines L, which can be 10° to 120°. In this way, the cross-section 25 can form an appropriate radial extension range in the bearing 2 so that the exhaust passage R can be supplied with air quickly.

[0092] Please continue reading. Figure 2 , Figure 4 As shown, the cross-sectional portion 25 may have a first axial end edge 251, which connects to the first end face 2a of the bearing 2. It is worth noting that the exhaust passage R can communicate with the opening 11 through the first axial end edge 251. Therefore, the first axial end edge 251 preferably does not completely abut against the cover 15 to avoid the cover 15 obstructing the communication between the exhaust passage R and the opening 11. In this embodiment, the first end face 2a of the bearing 2 may have a recess 26, which has a concave bottom surface 261. Thus, the first end face 2a and the concave bottom surface 261 may have a step difference, and the first axial end edge 251 extends at least to the recess 26. In this embodiment, the first axial end edge 251 extends to an inner annular wall 262 of the recess 26. Thus, the cover 15 can abut against the first end face 2a to prevent the bearing 2 from dislodging, and the recess 26 prevents the cover 15 from completely covering the first axial end edge 251, thereby obstructing the communication between the cross-section 25 and the opening 11. Preferably, in the radial direction of the bearing 2, the shortest vertical distance U from the axis O of the shaft hole 21 to the cross-section 25 can be less than the radius of the major diameter section 22 of the bearing 2, and the shortest vertical distance U can be greater than or equal to the radial distance from the axis O to 1 / 4 of the concave bottom surface 261. That is, the inner radius of the bearing 2 (the radial radius of the shaft hole 21) plus 1 / 4 of the radial dimension of the concave bottom surface 261 extending from the inner radius of the bearing 2.

[0093] Please continue reading. Figure 2 , Figure 4As shown, an anti-disengagement element 16 may also be provided between the cover 15 and the bearing 2. The anti-disengagement element 16 can be a retaining ring, which can be used to prevent the rotating shaft T from disengaging (details to follow). The anti-disengagement element 16 can be attached to the inner wall of the sleeve 1, for example, by means of tight fitting, gluing or welding. Alternatively, the anti-disengagement element 16 can be clamped between the cover 15 and the first end face 2a of the bearing 2. The anti-disengagement element 16 has a through hole 16a, which corresponds to the through hole 15a located in the cover 15. The anti-disengagement element 16 is made of flexible material. Preferably, the anti-disengagement element 16 may have several through grooves 161, which can extend radially in a radial pattern, and one end of the several through grooves 161 can be connected to the through hole 16a. Thus, the anti-detachment component 16 can form several petals around the periphery of the through hole 16a that can elastically deform and elastically return to their original position. In addition, the recessed portion 26 also ensures that the anti-detachment component 16 will only abut against the first end face 2a and will not completely cover the first axial end edge 251.

[0094] The cross-section 25 may have a second axial end edge 252, which connects to the abutment surface 24. Notably, the exhaust passage R can communicate with the oil storage space S through the second axial end edge 252. Therefore, the shortest radial distance D5 from the axis O of the bearing 2 to the second axial end edge 252 can be less than the second radial distance D4 from the axis O to the reduced diameter portion 14 of the sleeve 1. In this way, the exhaust passage R can communicate with the oil storage space S through the second axial end edge 252 and the gap between the circumferential surface of the small diameter section 23 and the reduced diameter portion 14.

[0095] Please refer to Figure 6 , Figure 7As shown, the rotating shaft T is rotatably coupled to the shaft hole 21 of the bearing 2. For example, the outer circumferential surface of the rotating shaft T may have several dynamic pressure grooves, or the inner surface of the shaft hole 21 may have several dynamic pressure grooves, so that the rotating shaft T can rotate within the shaft hole 21 through oil. The rotating shaft T can extend into the shaft hole 21 through the through hole 15a of the cover 15 and the through hole 16a of the anti-detachment member 16. Furthermore, the outer diameter of the rotating shaft T may be slightly larger than the inner diameter of the through hole 16a of the anti-detachment member 16, so that the rotating shaft T can pass through the through hole 16a by forced insertion. The rotating shaft T may have an annular groove T1, which may be formed by an annular recess from the outer circumferential surface of the rotating shaft T towards the center. The annular groove T1 is located on the anti-disengagement member 16. The outer diameter of the annular groove T1 is smaller than the inner diameter of the through hole 16a of the anti-disengagement member 16, so that the anti-disengagement member 16 forms an axial limit on the annular groove T1, preventing the shaft T from disengaging from the bearing 2 when rotating. The oil storage space S inside the sleeve 1 may also have a wear-resistant plate 17, which can be used to abut one end of the shaft T. In addition, when the oil storage space S has the wear-resistant plate 17, the first axial distance D1 is preferably less than the distance between the shoulder 13 and the surface of the wear-resistant plate 17 facing the second end face 2b. In this way, a gap can be made between the bearing 2 and the wear-resistant plate 17.

[0096] Please continue reading. Figure 6 , Figure 7 As shown, after oil is injected into the sleeve 1, the bearing 2 is positioned inside the sleeve 1. The bearing 2 can abut against the shoulder 13 to create a gap between the bottom of the bearing 2 and the sleeve 1, forming the oil storage space S, where the oil can be located. When the shaft T enters through the shaft hole 21 of the bearing 2, it will compress the air in the shaft hole 21 and the oil storage space S. At this time, the air can enter the exhaust channel R through the gap between the small diameter section 23 of the bearing 2 and the narrow diameter section 14 of the sleeve 1, and be smoothly discharged through the opening 11.

[0097] In summary, the bearing assembly of this utility model, by having a cross-section on the outer periphery of the bearing, forms an exhaust channel between the bearing and the inner wall of the sleeve. The exhaust channel can connect the oil storage space located in the closed part of the sleeve and the opening above the sleeve. In this way, the air compressed after the shaft enters the bearing can be smoothly discharged through the exhaust channel without forming an airtight pressure in the shaft hole. This achieves the effects of facilitating air discharge, preventing oil from overflowing from the shaft hole, and enabling smooth installation of the shaft.

[0098] 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.

Claims

1. A bearing assembly, characterized in that, include: A sleeve having an opening and a closing portion; and A bearing is located inside the sleeve, and an oil storage space is provided between the bearing and the closure. The bearing has a cross-section, and a gap is provided between the cross-section and the inner wall of the sleeve to form an exhaust channel. The opening is connected to the oil storage space through the exhaust channel.

2. The bearing assembly as claimed in claim 1, characterized in that, The sleeve has a reduced diameter section that connects to the closed section to form a shoulder inside the sleeve.

3. The bearing assembly as described in claim 2, characterized in that, The bearing has a first end face and a second end face facing each other. The first end face faces the opening and the second end face faces the closing portion. The bearing has a large diameter section connected to the first end face and a small diameter section connected to the second end face. An abutting surface is formed between the large diameter section and the small diameter section, and the abutting surface abuts against the shoulder.

4. The bearing assembly as described in claim 3, characterized in that, There is a first axial distance between the abutting surface and the second end face, and there is a second axial distance between the shoulder and an inner bottom surface of the closed portion. The first axial distance is smaller than the second axial distance.

5. The bearing assembly as claimed in claim 4, characterized in that, The oil storage space has a wear-resistant plate, and the first axial distance is less than the distance between the shoulder and the surface of the wear-resistant plate facing the second end face.

6. The bearing assembly as claimed in claim 3, characterized in that, There is a gap between the narrow diameter section and the reduced diameter section, and the exhaust passage connects to the oil storage space through the gap.

7. The bearing assembly as claimed in claim 3, characterized in that, The cross-section has two radial end edges, which are respectively connected to the circumferential surface of the large diameter section. The shaft center of the bearing and the two radial end edges of the cross-section pass through a reference line, and the included angle between the two reference lines is 10° to 120°.

8. The bearing assembly as claimed in claim 3, characterized in that, The cross-section has a first axial end edge, which is connected to the first end face of the bearing, and the exhaust passage communicates with the opening through the first axial end edge.

9. The bearing assembly as claimed in claim 8, characterized in that, The first end face has a recess with a concave bottom surface, and the first axial end edge extends at least to the recess.

10. The bearing assembly as claimed in claim 9, characterized in that, In the radial direction of the bearing, the shortest vertical distance from the center of the bearing bore to the cross-section is less than the radius of the major diameter section of the bearing, and the shortest vertical distance is greater than or equal to the radial distance from the center to 1 / 4 of the concave bottom surface.

11. The bearing assembly as claimed in claim 8, characterized in that, The cross-section has a second axial end edge, which is connected to the abutment surface, and the exhaust passage communicates with the oil storage space through the second axial end edge.

12. The bearing assembly as claimed in claim 11, characterized in that, The shortest distance from the bearing's axis to the second axial end is less than the radial distance from the axis to the reduced diameter portion of the sleeve.

13. The bearing assembly as claimed in claim 8, characterized in that, The sleeve has a cap located at the opening.

14. The bearing assembly as claimed in claim 13, characterized in that, The sleeve has an anti-detachment component located between the cap and the bearing.

15. The bearing assembly as claimed in claim 14, characterized in that, The anti-detachment component has a through hole and several through slots, one end of which is connected to the through hole.

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