Bearing

Abstract

A bearing includes: an inner ring having an inner raceway; the outer ring is provided with an outer raceway; the rolling body is positioned between the inner raceway and the outer raceway; the retainer is used for retaining the rolling bodies; wherein the diameter Dr of the rolling body is smaller than or equal to 0.35 * (H1-H2), H1 is the outer diameter of the outer ring, and H2 is the inner diameter of the inner ring; and wherein the relative groove curvature Ri of the inner raceway satisfies 0.52 < = Ri < = 0.58, and / or the relative groove curvature Re of the outer raceway satisfies 0.53 < = Re < = 0.58. Preferably, the relative groove curvature Ri of the inner raceway satisfies 0.54 < = Ri < = 0.56, and / or the relative groove curvature Re of the outer raceway satisfies 0.55 < = Re < = 0.58.

Description

Technical Field

[0001] The present disclosure relates to a bearing, and more particularly, to a bearing with a relatively small frictional torque. Background Art

[0002] Some devices using bearings require the bearings to have a relatively small frictional torque during operation; for example, in a lithium battery film winding machine, if the frictional torque of the bearing during operation is relatively large, it may cause uneven film thickness or even film breakage.

[0003] Therefore, it is desirable to provide a bearing with a relatively small frictional torque during operation. Summary of the Invention

[0004] According to a first aspect of the present disclosure, there is provided a bearing, comprising: an inner ring having an inner raceway; an outer ring having an outer raceway; rolling elements located between the inner raceway and the outer raceway; a cage for holding the rolling elements; wherein, the diameter Dr of the rolling elements satisfies Dr ≤ 0.35*(H1 - H2), where H1 is the outer diameter of the outer ring and H2 is the inner diameter of the inner ring; and wherein, the relative groove curvature Ri of the inner raceway satisfies 0.52 ≤ Ri ≤ 0.58, and / or, the relative groove curvature Re of the outer raceway satisfies 0.53 ≤ Re ≤ 0.58. Preferably, the relative groove curvature Ri of the inner raceway satisfies 0.54 ≤ Ri ≤ 0.56, and / or, the relative groove curvature Re of the outer raceway satisfies 0.55 ≤ Re ≤ 0.58.

[0005] According to this solution, for a bearing with a relatively small diameter of the rolling elements, by using an inner raceway and / or an outer raceway with a relatively large relative groove curvature, the friction between the rolling elements and the inner ring and / or the outer ring is reduced, thereby significantly reducing the frictional torque suffered by the bearing during rotation and bringing an unexpected improvement to the overall performance of the bearing.

[0006] In some solutions, the diameter Dr of the rolling elements satisfies Dr ≥ 0.2*(H1 - H2); preferably, the diameter Dr of the rolling elements satisfies 0.25*(H1 - H2) ≤ Dr ≤ 0.32*(H1 - H2).

[0007] In some solutions, the inner diameter H2 of the inner ring satisfies 7 mm ≤ H2 ≤ 40 mm; preferably, the inner diameter H2 of the inner ring satisfies 10 mm ≤ H2 ≤ 30 mm.

[0008] In some solutions, the bearing further comprises a seal, the seal is arranged at an axial end of the bearing, the seal is fixed to one of the outer ring or the inner ring, and a gap is provided between the seal and the other of the outer ring or the inner ring. Preferably, the seal can be fixed to the outer ring, and a gap is provided between the seal and the inner ring.

[0009] According to this solution, by adopting non-contact sealing, the friction between the seal and the outer ring or inner ring is reduced, thereby further reducing the frictional torque suffered by the bearing during rotation.

[0010] In some solutions, the gap between the seal and the inner ring has a width extending in the radial direction of the bearing, and the width is between 0.1 mm and 0.2 mm.

[0011] According to this solution, if the gap is too large, a good sealing effect cannot be obtained, and if the gap is too small, the seal may hinder the rotation of the bearing, thereby increasing the frictional torque suffered by the bearing during rotation. Therefore, setting the width of the gap within a suitable range helps to both reduce the frictional torque suffered by the bearing during rotation and basically isolate the internal space of the bearing from the external environment.

[0012] In some solutions, the gap between the seal and the inner ring has a length extending in the axial direction of the bearing, and the length is between 0.1 mm and 2 mm.

[0013] In some solutions, lubricating oil is attached to the inner raceway and the outer raceway, and the viscosity of the lubricating oil at a temperature of 40 °C is less than 25 cst; preferably, the viscosity of the lubricating oil at a temperature of 40 °C is less than 20 cst; more preferably, the viscosity of the lubricating oil at a temperature of 40 °C is less than 15 cst.

[0014] According to this solution, by using liquid lubricating oil instead of solid grease as the lubricant, the frictional torque suffered by the bearing during rotation is further reduced. And using lubricating oil with a smaller viscosity helps to reduce the friction between the rolling elements and the inner ring and / or outer ring, thereby reducing the frictional torque suffered by the bearing during rotation.

[0015] In some solutions, the oil film thickness of the lubricating oil attached to the inner raceway and / or outer raceway is less than 0.06 mm; preferably, the oil film thickness is greater than 0.01 mm and less than 0.05 mm.

[0016] In some solutions, there is lubricating oil in the free space inside the bearing. The lubricating oil is attached to at least the surfaces of the inner raceway and the outer raceway. The volume of the lubricating oil accounts for less than 5% of the volume of the free space inside the bearing. The free space inside the bearing is the space inside the bearing excluding the rolling elements and the cage. The internal space of the bearing is the space defined by the inner ring, the outer ring and the seal.

[0017] According to this solution, by controlling the proportion of the volume of the lubricating oil in the volume of the free space inside the bearing to be below a certain specific value, the frictional torque suffered by the bearing during rotation is further reduced.

[0018] According to a second aspect of the present disclosure, there is provided a winding cylinder, comprising: a shaft; a bearing according to the first aspect of the present disclosure, disposed on the shaft; and a rotatable cylinder, disposed on the bearing.

[0019] According to a third aspect of the present disclosure, there is provided a method for attaching lubricating oil to a bearing, characterized by comprising: immersing the bearing in lubricating oil, the bearing comprising an inner ring having an inner raceway, an outer ring having an outer raceway, rolling elements located between the inner raceway and the outer raceway, a cage for holding the rolling elements, and a seal; performing a centrifugal drying operation on the bearing; wherein, the diameter Dr of the rolling elements satisfies Dr ≤ 0.35*(H1 - H2), where H1 is the outer diameter of the outer ring and H2 is the inner diameter of the inner ring; and, wherein, the relative groove curvature Ri of the inner raceway satisfies 0.52 ≤ Ri ≤ 0.58, and / or, the relative groove curvature Re of the outer raceway satisfies 0.53 ≤ Re ≤ 0.58.

[0020] In some embodiments, the volume of the lubricating oil in the internal free space of the bearing to which the lubricating oil is attached accounts for less than 5% of the volume of the internal free space of the bearing; wherein, the lubricating oil is at least attached to the surfaces of the inner raceway and the outer raceway, the internal free space of the bearing is the space in the bearing internal space excluding the rolling elements and the cage, and the bearing internal space is the space defined by the inner ring, the outer ring, and the seal. Description of the Drawings

[0021] Figure 1 A schematic diagram showing a bearing according to some embodiments of the present disclosure;

[0022] Figure 2 A partial schematic diagram showing a bearing according to some embodiments of the present disclosure;

[0023] Figure 3 A schematic diagram showing the relative groove curvature according to some embodiments of the present disclosure;

[0024] Figure 4 A partially enlarged schematic diagram showing a seal according to some embodiments of the present disclosure;

[0025] Figure 5 A flowchart showing a method for attaching lubricating oil to a bearing according to some embodiments of the present disclosure.

[0026] Reference Numerals: 100 Bearing, 102 Inner Ring, 104 Outer Ring, 106 Rolling Elements, 108 Cage, 110 Inner Raceway, 120 Outer Raceway, 130 Seal, 140 Gap. Detailed Description

[0027] To make the objectives, solutions, and advantages of the technical solutions of the present disclosure clearer, the technical solutions of some embodiments of the present disclosure will be clearly and completely described below with reference to the accompanying drawings of some specific embodiments of the present disclosure. Unless otherwise specified, the terms used herein have the ordinary meanings in the art. The same reference numerals in the drawings represent the same components.

[0028] Figure 1 and Figure 2 FIG. shows a schematic diagram of a bearing 100 according to some embodiments of the present disclosure. The bearing 100 includes an inner ring 102, an outer ring 104, rolling elements 106, and a cage 108. The inner ring 102 and the outer ring 104 can rotate concentrically relative to each other. The inner ring 102 and the outer ring 104 respectively have an inner raceway 110 and an outer raceway 120, and the rolling elements 106 are interposed between the inner raceway 110 and the outer raceway 120.

[0029] To reduce the frictional torque suffered by such a bearing 100 during rotation, a relatively large relative groove curvature is designed for the inner raceway 110 and / or the outer raceway 120 of the bearing 100. The relative groove curvature can be defined as the raceway radius divided by the diameter of the rolling element 106; the raceway radius is the radius of the circle where the arc of the adapted raceway is located, that is, the curvature radius of the raceway. That is to say, the relative groove curvature represents the degree of bending of the inner raceway 110 and / or the outer raceway 120 relative to the rolling element 106, which is equal to the ratio of the curvature radius of the inner raceway 110 and / or the outer raceway 120 to the diameter of the rolling element 106. According to the definition of the relative groove curvature, if the relative groove curvature is equal to 0.5, it means that the degree of bending of the inner raceway 110 and / or the outer raceway 120 is the same as that of the rolling element 106. In order to enable the rolling element 106 to be accommodated in the inner raceway 110 and / or the outer raceway 120, obviously the relative groove curvature needs to be greater than 0.5.

[0030] In some embodiments, the relative groove curvature of the inner raceway 110 is greater than 0.52, and the relative groove curvature of the outer raceway 120 is greater than 0.53.

[0031] As Figure 3 shown, the relative groove curvature of the inner raceway 110 is smaller than the relative groove curvature of the inner raceway 110'. It can be intuitively seen from this that the larger the relative groove curvature of the inner raceway 110, the larger the gap between the rolling element 106 and the inner raceway 110. It should be understood that the relative groove curvature of the outer raceway 120 is similar to that of the inner raceway 110, and will not be described in detail here for the sake of brevity. And Figure 3It is only schematic and not necessarily drawn to scale. In the bearing 100 of the present disclosure, the relative groove curvature of the inner raceway 110 is greater than 0.52 and / or the relative groove curvature of the outer raceway 120 is greater than 0.53. Appropriately designing a relatively large relative groove curvature of the inner raceway 110 and / or the outer raceway 120 makes the clearance between the rolling elements 106 and the inner raceway 110 and / or the outer raceway 120 larger, which can reduce the friction between the rolling elements 106 and the inner raceway 110 and / or the outer raceway 120, thereby reducing the frictional torque exerted on the bearing 100 during rotation.

[0032] Bearings in the prior art do not design the relative groove curvature of the inner raceway 110 and / or the outer raceway 120 to be greater than 0.52, and even do not set it to be greater than 0.51. However, in the present disclosure, by designing a relative groove curvature of the inner raceway and / or the outer raceway that is significantly greater than that of bearings in the prior art, the performance of the bearing 100, especially the frictional performance, has been unexpectedly improved. Especially for the bearing 100 with a relatively small diameter of the rolling elements 106 (for example, the diameter Dr of the rolling elements 106 ≤ 0.35 * (H1 - H2), where H1 and H2 are the outer diameter and inner diameter of the outer ring 104 respectively), the frictional torque exerted on the bearing 100 during rotation is significantly reduced compared to that of bearings in the prior art.

[0033] Preferably, the relative groove curvature of the inner raceway 110 and / or the outer raceway 120 can be greater than 0.55. More preferably, the relative groove curvature of the inner raceway 110 and / or the outer raceway 120 can even be greater than 0.57. A larger relative groove curvature of the inner raceway 110 and / or the outer raceway 120 makes the clearance between the rolling elements 106 and the inner raceway 110 and / or the outer raceway 120 larger, which can further reduce the friction between the rolling elements 106 and the inner raceway 110 and / or the outer raceway 120, thereby further reducing the frictional torque exerted on the bearing 100 during rotation.

[0034] The present disclosure is particularly suitable for bearings 100 with a relatively small diameter of the rolling elements 106. Specifically, when the diameter Dr of the rolling elements 106 ≤ 0.35 * (H1 - H2), by combining technical features such as the volume ratio of the lubricating oil in the bearing free space, the oil film thickness, and the relative curvature of the raceway of the present disclosure, the frictional torque exerted on the bearing 100 during rotation can be significantly reduced. Preferably, the inner diameter H2 of the inner ring satisfies 7 mm ≤ H2 ≤ 40 mm; more preferably, the inner diameter H2 of the inner ring satisfies 10 mm ≤ H2 ≤ 30 mm.

[0035] Preferably, a seal 130 may also be provided at the axial end of the bearing 100. The seal 130 is fixed to one of the outer ring 104 or the inner ring 102, and a slender-shaped gap 140 is provided between the seal 130 and the other of the outer ring 104 or the inner ring 102. In other words, the seal 130 may be fixed to the outer ring 104 and a gap 140 is provided between it and the inner ring 102, or the seal 130 may be fixed to the inner ring 102 and a gap 140 is provided between it and the outer ring 104. The gap 140 has a width extending in the radial direction of the bearing 100 and a length extending in the axial direction of the bearing 100. During the rotation of the bearing 100, this non-contact sealing of the seal 130 avoids the frictional torque generated on the bearing 100 due to the contact between the seal 130 and the outer surface of the inner ring 102 or the inner surface of the outer ring 104, thereby reducing the frictional torque received by the bearing 100 during rotation.

[0036] Preferably, referring to Figure 4 , the width L2 of the gap 140 between the seal 130 and the inner ring 102 may be between 0.1 mm and 0.2 mm. If the gap 140 is too wide, a good sealing effect cannot be obtained, while if the gap 140 is too narrow, it may cause the seal 130 to hinder the rotation of the bearing 100, thereby increasing the frictional torque received when the bearing 100 rotates. Therefore, setting the width of the gap 140 within a suitable range helps to both reduce the frictional torque received when the bearing 100 rotates and basically isolate the internal space of the bearing from the external environment. In addition, the length L1 of the gap 140 between the seal 130 and the inner ring 102 may be between 0.1 mm and 2 mm.

[0037] Different from the traditional lubrication method of applying grease in the bearing 100, the present disclosure coats lubricating oil instead of grease in the bearing 100, especially coating lubricating oil at the inner raceway 110 and / or the outer raceway 120 where the rolling elements 106 contact the bearing 100 to achieve the lubrication effect. Since the lubricating oil has a lower viscosity than the grease, compared with the scheme of applying grease, coating the lubricating oil can reduce the friction between the rolling elements 106 and the inner raceway 110 and / or the outer raceway 120, thereby reducing the frictional torque received by the bearing 100 during rotation. In this solution, by adjusting the relative groove curvature, adjusting the grease to lubricating oil, controlling the oil quantity, and preferably combining non-contact sealing, the performance of the bearing, especially the frictional performance, has been unexpectedly improved. In some cases, the frictional torque received when the bearing 100 of this solution rotates is reduced by about 50% or more compared with the frictional torque of the bearings in the prior art during rotation; preferably, the frictional torque can be reduced to less than 1.5 N·mm.

[0038] Preferably, the viscosity of the lubricating oil at a temperature of 40 °C can be less than 25 cst. Using a lubricating oil with a lower viscosity helps to further reduce the friction between the rolling elements 106 and the inner ring 102 and / or the outer ring 104, thereby reducing the frictional torque experienced when the bearing 100 rotates. This solution is particularly applicable when the external load on the bearing 100 is not large, because the oil film is not easily damaged by the external load due to its lower viscosity. Preferably, the viscosity of the lubricating oil at a temperature of 40 °C can be greater than 5 cst. It should be understood that the present disclosure is not intended to limit the specific value of the viscosity of the lubricating oil, and any other lubricating oil with a suitable viscosity can be used.

[0039] In the bearing 100 of the present disclosure, the volume of the lubricating oil accounts for less than 5% of the volume of the free space inside the bearing. The free space inside the bearing is the space inside the bearing excluding the rolling elements 106 and the cage 108. The internal space of the bearing is the space defined by the inner ring 102, the outer ring 104, and the seal 130. Using less lubricating oil helps to further reduce the friction between the rolling elements 106 and the inner ring 102 and / or the outer ring 104, thereby reducing the frictional torque experienced when the bearing 100 rotates. This solution is particularly applicable when the external load on the bearing 100 is not large, because the oil film is not easily damaged by the external load due to its smaller volume. In addition, the volume of the lubricating oil can also account for less than 3% of the volume of the free space inside the bearing, preferably less than 2%, which helps to further reduce the friction between the rolling elements 106 and the inner ring 102 and / or the outer ring 104, thereby further reducing the frictional torque experienced when the bearing 100 rotates. In some embodiments, the volume of the lubricating oil accounts for more than 0.5% of the volume of the free space inside the bearing.

[0040] Correspondingly, an appropriate volume of lubricating oil can also be obtained by designing an appropriate oil film thickness of the lubricating oil. As Figure 2 shown, the black bold part represents the oil film, and the thickness formed in the radial direction of the bearing 100 is the oil film thickness. The relationship between the oil film thickness h and the oil film volume V is V = S * h, where S is the surface area of the oil film in contact with the outer surface of the inner ring 102 and the inner surface of the outer ring 104. In the solution of the present disclosure, the oil film thickness can be less than 0.05 mm. Using a thinner oil film helps to reduce the friction between the rolling elements 106 and the inner ring 102 and / or the outer ring 104, thereby reducing the frictional torque experienced when the bearing 100 rotates. The oil film thickness can also be greater than 0.01 mm. If the oil film thickness is too thin, the lubrication effect may be insufficient. Therefore, the oil film thickness is set to be greater than 0.01 mm to achieve a sufficient lubrication effect. It should be understood that the present disclosure is not intended to limit the specific value of the oil film thickness, and any other lubricating oil with a suitable oil film thickness can be used.

[0041] The bearing 100 of the present disclosure can be used in a winding machine, which is arranged on a winding shaft supported by the bearing 100. The winding machine can be used for winding lithium battery films. Through the solution of the present disclosure, the frictional torque received by the bearing 100 during rotation is reduced, and the uneven thickness or even breakage of the lithium battery film caused by a large frictional torque is avoided.

[0042] The low friction requirement restricts the diameter of the rolling elements 106. If the diameter of the rolling elements 106 is too large relative to the overall size of the bearing 100, a greater external force is required for the rotation of the rolling elements 106, resulting in higher friction. In addition, if the rolling elements 106 are too large relative to the overall size of the bearing 100, the overall size space of the bearing 100 will be compressed, causing the wall thicknesses of the inner ring 102 and the outer ring 104 to become thinner, increasing the processing difficulty. And if the diameter of the rolling elements 106 is too small relative to the overall size of the bearing 100, it will bring extremely high processing difficulty to the cage and the seal 130. Therefore, the diameter Dr of the rolling elements 106 is preferably designed to satisfy Dr≥0.2*(H1-H2); in some embodiments, the diameter Dr of the rolling elements 106 is preferably designed to satisfy 0.25*(H1-H2)≤Dr≤0.32*(H1-H2).

[0043] Please refer to Figure 5 , Figure 5 which shows a flowchart of a method for attaching lubricating oil to a bearing according to some embodiments of the present disclosure.

[0044] In step S1, the bearing is immersed in lubricating oil. The bearing includes an inner ring having an inner raceway, an outer ring having an outer raceway, rolling elements located between the inner raceway and the outer raceway, a cage for holding the rolling elements, and a seal.

[0045] In step S2, a centrifugal drying operation is performed on the bearing; wherein, the diameter Dr of the rolling elements satisfies Dr≤0.35*(H1-H2), H1 is the outer diameter of the outer ring, and H2 is the inner diameter of the inner ring; and, wherein, the relative groove curvature Ri of the inner raceway satisfies 0.52≤Ri≤0.58, and / or, the relative groove curvature Re of the outer raceway satisfies 0.53≤Re≤0.58.

[0046] In some embodiments, the relative groove curvature Ri of the inner raceway satisfies 0.54≤Ri≤0.56, and / or, the relative groove curvature Re of the outer raceway satisfies 0.55≤Re≤0.58. In some embodiments, the diameter Dr of the rolling elements satisfies Dr≥0.2*(H1-H2); preferably, the diameter Dr of the rolling elements satisfies 0.25*(H1-H2)≤Dr≤0.32*(H1-H2). In some embodiments, the inner diameter H2 of the inner ring satisfies 7mm≤H2≤40mm; preferably, the inner diameter H2 of the inner ring satisfies 10mm≤H2≤30mm.

[0047] In some embodiments, a seal is provided at an axial end of the bearing. The seal is fixed to one of the outer ring or the inner ring, and a gap is provided between the seal and the other of the outer ring or the inner ring. Preferably, the seal is fixed to the outer ring, and a gap is provided between the seal and the inner ring. In some embodiments, the gap has a width extending in a radial direction of the bearing, and the width L2 is between 0.1 mm and 0.2 mm. In some embodiments, the gap has a length extending in an axial direction of the bearing, and the length L1 is between 0.1 mm and 2 mm.

[0048] In some embodiments, the viscosity of the lubricating oil adhered to the inner raceway and the outer raceway is less than 25 cst at a temperature of 40 °C; preferably, the viscosity of the lubricating oil is less than 20 cst at a temperature of 40 °C; more preferably, the viscosity of the lubricating oil is less than 15 cst at a temperature of 40 °C.

[0049] In some embodiments, a bearing in which the volume of the lubricating oil in the internal free space of the bearing with the lubricating oil adhered thereto obtained through the above steps accounts for less than 5% of the volume of the internal free space of the bearing; wherein, the lubricating oil is adhered to at least the surfaces of the inner raceway and the outer raceway, the internal free space of the bearing is the space in the bearing internal space excluding the rolling elements and the cage, and the bearing internal space is the space defined by the inner ring, the outer ring and the seal. In some embodiments, the volume of the lubricating oil accounts for less than 3% of the volume of the internal free space of the bearing; preferably less than 2%. In some embodiments, the volume of the lubricating oil accounts for more than 0.5% of the volume of the internal free space of the bearing.

[0050] In some embodiments, the oil film thickness of the lubricating oil adhered to the inner raceway and / or the outer raceway obtained through the above steps is less than 0.06 mm; preferably, the oil film thickness is greater than 0.01 mm and less than 0.05 mm.

[0051] The present disclosure has been described in detail with reference to some preferred embodiments. However, those skilled in the art can understand that various modifications and variations can be made to the above specific embodiments without departing from the concept of the present disclosure, and various technical features and structures proposed by the present disclosure can also be combined without exceeding the protection scope of the present disclosure. The protection scope of the present disclosure is determined by the appended claims.

Claims

1. A bearing, characterized in that, Comprising: An inner ring having an inner raceway; An outer ring having an outer raceway; Rolling elements located between the inner raceway and the outer raceway; A cage for holding the rolling elements; Wherein, the diameter Dr of the rolling elements satisfies Dr ≤ 0.35 * (H1 - H2), H1 is the outer diameter of the outer ring, and H2 is the inner diameter of the inner ring; and Wherein, the relative groove curvature Ri of the inner raceway satisfies 0.52 ≤ Ri ≤ 0.58, and / or, the relative groove curvature Re of the outer raceway satisfies 0.53 ≤ Re ≤ 0.

58.

2. The bearing according to claim 1, wherein, The relative groove curvature Ri of the inner raceway satisfies 0.54 ≤ Ri ≤ 0.56, and / or, the relative groove curvature Re of the outer raceway satisfies 0.55 ≤ Re ≤ 0.

58.

3. The bearing according to claim 1, wherein, The diameter Dr of the rolling elements satisfies Dr ≥ 0.2 * (H1 - H2); preferably, the diameter Dr of the rolling elements satisfies 0.25 * (H1 - H2) ≤ Dr ≤ 0.32 * (H1 - H2).

4. The bearing according to claim 1, wherein, The inner diameter H2 of the inner ring satisfies 7mm ≤ H2 ≤ 40mm; preferably, the inner diameter H2 of the inner ring satisfies 10mm ≤ H2 ≤ 30mm.

5. The bearing according to claim 1, characterized in that, It further includes a seal, the seal is arranged at the axial end of the bearing, the seal is fixed to one of the outer ring or the inner ring, and there is a gap between the seal and the other of the outer ring or the inner ring; preferably, the seal is fixed to the outer ring, and there is a gap between the seal and the inner ring.

6. The bearing according to claim 5, characterized in that, The gap has a width extending in the radial direction of the bearing, and the width L2 is between 0.1mm and 0.2mm.

7. The bearing according to claim 5, characterized in that, The gap has a length extending in the axial direction of the bearing, and the length L1 is between 0.1mm and 2mm.

8. The bearing according to claim 1, characterized in that, The inner raceway and the outer raceway are attached with lubricating oil, and the viscosity of the lubricating oil at a temperature of 40°C is less than 25cst; preferably, the viscosity of the lubricating oil at a temperature of 40°C is less than 20cst; more preferably, the viscosity of the lubricating oil at a temperature of 40°C is less than 15cst.

9. The bearing according to claim 8, characterized in that, The oil film thickness of the lubricating oil attached to the inner raceway and / or the outer raceway is less than 0.06mm; preferably, the oil film thickness is greater than 0.01mm and less than 0.05mm.

10. The bearing according to claim 8, characterized in that, There is lubricating oil in the free space inside the bearing, the lubricating oil is at least attached to the surfaces of the inner raceway and the outer raceway, the volume of the lubricating oil accounts for less than 5% of the volume of the free space inside the bearing, the free space inside the bearing is the space inside the bearing excluding the rolling elements and the cage, and the inner space of the bearing is the space defined by the inner ring, the outer ring and the seal.

11. A winding cylinder, characterized in that, Comprising: A shaft; The bearing according to any one of claims 1 to 10, arranged on the shaft; And A rotatable cylinder, arranged on the bearing.

12. A method for attaching lubricating oil to a bearing, characterized in that, Comprising: Immersing the bearing in lubricating oil, the bearing includes an inner ring having an inner raceway, an outer ring having an outer raceway, rolling elements located between the inner raceway and the outer raceway, a cage for holding the rolling elements and a seal; Performing a centrifugal drying operation on the bearing to obtain a bearing attached with lubricating oil; Wherein, the diameter Dr of the rolling element satisfies Dr ≤ 0.35 * (H1 - H2), H1 is the outer diameter of the outer ring, and H2 is the inner diameter of the inner ring; and Wherein, the relative groove curvature Ri of the inner raceway satisfies 0.52 ≤ Ri ≤ 0.58, and / or, the relative groove curvature Re of the outer raceway satisfies 0.53 ≤ Re ≤ 0.

58.

13. The method according to claim 12, wherein, A bearing in which the volume of lubricating oil in the internal free space of the bearing with lubricating oil attached thereto is less than 5% of the volume of the internal free space of the bearing; Wherein, the lubricating oil is attached at least to the surfaces of the inner raceway and the outer raceway, the internal free space of the bearing is the space in the bearing internal space excluding the rolling elements and the cage, and the bearing internal space is the space defined by the inner ring, the outer ring, and the seal.

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