Roll bearing
By setting continuous spiral oil grooves on the inner ring end surface of the roll bearing, the problem of insufficient lubrication of the roll bearing is solved, and the service life of the roll bearing is significantly extended.
Patent Information
- Application Number
- CN202311610825.0
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2023-11-28
- Publication Date
- 2025-05-30
AI Technical Summary
During the steel rolling process, roll bearings bear large radial and axial loads, resulting in insufficient lubrication between the end faces of the inner ring, which is prone to adhesion wear and thermal cracks, which leads to failure of roll bearings.
A roll bearing is designed, with a continuous spiral oil groove on the end surface of the inner ring, ensuring that the lubricating oil can be evenly applied to the contact area and improving the lubricating condition.
The lubrication condition of the inner ring end surface is significantly improved through the continuous spiral oil groove, reducing the risk of adhesion wear and thermal cracks, and extending the service life of the roll bearing.
Smart Images
Figure CN120062242A_ABST
Abstract
Description
Technical Field
[0001] The present invention relates to the technical field of rolling bearings, and particularly to a roll bearing applied to a rolling mill. Background Art
[0002] Roll bearings are widely used in rolling mills. Roll bearings are used to support the rotation of rolls and are important components in the working stand of a rolling mill. The service life of roll bearings is related to the utilization rate of the rolling mill.
[0003] Roll bearings are supported at both ends of the roll. During the rolling process, due to the large rolling torque and accompanied by impact loads, the roll bearings simultaneously bear radial loads and axial loads from the roll. Correspondingly, the inner ring of the roll bearing also simultaneously bears large radial loads and axial loads. Therefore, in related technologies, roll bearings often have multiple inner rings and outer rings arranged side by side to bear large radial loads and axial loads.
[0004] In addition, during the process of rolling plate-shaped or wire-shaped rolling materials to form plates and wires through rolls, the rolls are worn due to heavy-load contact with the rolling materials, resulting in die collapse. The surface roughness of the rolls also gradually decreases.
[0005] The shape and surface roughness of the rolls directly affect the shape of the rolling materials. If rolling is repeated, the shape and surface roughness of the rolls will deteriorate, and the required shape and dimensional accuracy of the plates and wires cannot be maintained.
[0006] The rolling process includes hot rolling and cold rolling. In hot rolling, since the temperature of the rolling material is 1000 degrees or higher, the surface wear and deterioration of the rolls are more obvious. In addition, in cold rolling, the rolling speed is high (1500 m / min), and the rolling material undergoes work hardening during the rolling process, resulting in an increase in rolling resistance. To perform rolling, a heavy load exceeding the deformation resistance needs to be applied. Therefore, it is difficult to maintain the oil film between the rolling material and the rolls, and there is a lack of lubrication. As a result, the wear and deterioration of the roll surface are aggravated.
[0007] Therefore, in a hot rolling mill, the rolls and roll bearings are taken out of the rolling mill every about 3 hours, and in a cold rolling mill, every about 8 hours. The rolls with the shape and surface roughness corrected are immediately assembled and rolling is carried out again.
[0008] The removed roll is installed on the polishing machine and the roll surface is polished to correct the surface shape and surface roughness. At the same time, the roll bearings are inspected. As described above, both hot rolling and cold rolling require regular shape correction of the roll surface. In order to improve work efficiency, the inner ring hole wall of the roll bearing and the outer wall of the roll shaft often require a clearance fit, so that during the actual steel rolling process, relative circumferential slip occurs between the end faces of two adjacent inner rings, resulting in abnormal wear and heat generation between the end faces of the two inner rings. More than 40% of the damage causes of the rolling mill bearings are caused by poor lubrication.
[0009] Therefore, in the application of rolling mill machinery, in order to avoid abnormal wear and heat generation between the end faces of two inner rings, oil grooves are widely used on the end faces of the inner rings of roll bearings. It is used to retain and guide lubricants, so as to provide better lubrication for the end faces of adjacent inner rings and avoid frictional damage to the end faces of adjacent inner rings.
[0010] However, in the related art, the oil grooves 16 on the inner ring end face 11 are usually discontinuous and intermittent. Figure 1 and Figure 2 For the typical four-row tapered rolled bearing (4r-TRB) structure in the related art, as can be seen from Figure 1 and Figure 2 , there are 6 oil grooves 16 provided on the inner ring end face 11 of the four-row tapered rolled bearing. The 6 oil grooves 16 are arranged at equal intervals along the circumferential direction W. Since these 6 oil grooves 16 on the inner ring end face 11 are discontinuous and intermittent, it is difficult for the oil grooves 16 to continuously transport lubricating oil to the contact area when two adjacent inner rings 10 undergo circumferential relative slip, and there is a high risk of insufficient lubrication of the inner ring end face 11. Under high contact pressure and insufficient lubrication conditions, adhesive wear and thermal cracks are likely to occur on the inner ring end face 11, resulting in the failure of the roll bearing. Summary of the Invention
[0011] To overcome the problems existing in the related art, the present disclosure provides a roll bearing.
[0012] According to the first aspect of the embodiments of the present disclosure, the present disclosure provides a roll bearing, including: a plurality of inner rings, the plurality of inner rings are arranged side by side along the axial direction and the end faces of two adjacent inner rings are in contact with each other. Among them, a continuous spiral oil groove is provided on the end face of the inner ring.
[0013] In some embodiments, the inner ring includes an outer wall and an inner wall. The spiral oil groove includes a first port and a second port. Among them, the first port of the spiral oil groove is located on the outer wall of the inner ring, and the second port of the spiral oil groove is located on the inner wall of the inner ring. The spiral oil groove communicates the outer wall and the inner wall of the inner ring.
[0014] In some embodiments, the spiral oil groove comprises multiple turns, and the multiple turns of the spiral oil groove are helical with equal pitch along the radial direction on the end face of the inner ring.
[0015] In some embodiments, the pitch of the spiral oil groove is 1 mm to 10 mm.
[0016] In some embodiments, the depth of the spiral oil groove is 0.1 mm to 5 mm.
[0017] In some embodiments, the width of the spiral oil groove is 0.1 mm to 5 mm.
[0018] In some embodiments, the spiral oil groove is one or a combination of more of triangle, rectangle, trapezoid, and curve.
[0019] In some embodiments, the roll bearing further comprises: an outer ring sleeved outside the inner ring; rolling elements located radially between the outer ring and the inner ring; and a cage for circumferentially spacing and holding the rolling elements.
[0020] In some embodiments, the roll bearing is a double-row spherical roller bearing, a four-row tapered roller bearing, or a multi-row cylindrical roller bearing.
[0021] The technical solutions provided by the embodiments of the present disclosure may include the following beneficial effects: The spiral oil grooves on the end faces of the inner rings are continuous and unbroken. When the end faces of the two inner rings slide relative to each other circumferentially, the continuous spiral oil grooves facilitate coating the lubricant in the oil grooves onto the contact areas of the end faces of the two inner rings. Therefore, the lubrication condition of the end faces of the two inner rings can be significantly improved, thereby reducing the risk of adhesive wear and thermal cracks in the contact areas of the end faces of the inner rings and extending the service life of the roll bearing. BRIEF DESCRIPTION OF THE DRAWINGS
[0022] The accompanying drawings herein are incorporated into the specification and form a part of the specification, showing embodiments consistent with the present disclosure and, together with the specification, are used to explain the principles of the present disclosure.
[0023] Figure 1 is an axial sectional view of a four-row tapered roller bearing in the related art;
[0024] Figure 2 is a side view of a four-row tapered roller bearing in the related art;
[0025] Figure 3 is a side view of a roll bearing shown according to an exemplary embodiment;
[0026] Figure 4 is a partial schematic view of the inner ring of a roll bearing shown according to an exemplary embodiment;
[0027] Figure 5It is a cross-sectional view of the inner ring in the spiral oil groove shown according to an exemplary embodiment. Detailed Description of the Invention
[0028] Here, the exemplary embodiments will be described in detail, and the examples are shown in the drawings. When the following description refers to the drawings, unless otherwise indicated, the same numerals in different drawings represent the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present disclosure. On the contrary, they are merely examples of devices and methods consistent with some aspects of the present disclosure as detailed in the appended claims.
[0029] In the present invention, unless otherwise specified, the axial direction A, the radial direction R, and the circumferential direction W respectively refer to the axial direction A, the radial direction R, and the circumferential direction W of the roll bearing 100.
[0030] To solve the above technical problems, the present disclosure provides a roll bearing 100, which often includes a plurality of inner rings 10, a plurality of outer rings 20, a plurality of rows of rolling elements 30, and a cage (not shown in the figure) that keeps the rolling elements 30 at equal intervals. The roll bearing 100 may include a double-row spherical roller bearing, a four-row tapered roller bearing, and a multi-row cylindrical roller bearing. In the present embodiment, a four-row tapered roller bearing (4-row tapered rolled bearing, abbreviated as 4r-TRB) will be taken as an example for detailed description.
[0031] Among them, the plurality of inner rings 10 are arranged side by side in the axial direction A, and the end faces 11 of two adjacent inner rings 10 are in contact with each other. In the present embodiment, as Figure 1 In the structure shown in the related art, a four-row tapered roller bearing also includes two inner rings 10, two outer rings 20, and four rows of tapered rollers. As Figure 1 As can be seen in the middle of the axial direction A shown in, the end faces 11 of the two inner rings 10 are in contact with each other, and the area where they are in contact with each other is defined as the contact area of the end face 11 of the inner ring 10.
[0032] Among them, as Figure 4 Shown, a continuous and uninterrupted spiral oil groove 12 is provided on the end face 11 of the inner ring 10, that is, there is only one spiral oil groove 12 on the end face 11 of the inner ring 10, and the spiral oil groove 12 on the end face 11 of the inner ring 10 is continuous and uninterrupted. The spiral oil groove 12 also divides the contact area into a continuous and uninterrupted contact area.
[0033] When the end faces 11 of the two inner rings 10 slide relative to each other circumferentially, the continuous spiral oil groove 12 facilitates the uniform coating of the lubricant in the oil groove onto the contact area of the end faces 11 of the two inner rings 10. Therefore, the lubrication condition of the end faces 11 of the two inner rings 10 can be significantly improved, thereby reducing the risk of adhesive wear and thermal cracks in the contact area of the end faces 11 of the inner rings 10 and extending the service life of the roll bearing 100.
[0034] In some embodiments, the inner ring 10 includes an outer wall 13 and an inner wall 14. The outer wall 13 of the inner ring 10 is used to carry the rolling elements 30. The inner wall 14 of the inner ring 10 is used for clearance fit with the outer wall 13 of the roll shaft.
[0035] Since there is only one spiral oil groove 12 on the end face 11 of the inner ring 10 and the spiral oil groove 12 is continuous on the end face 11 of the inner ring 10, the spiral oil groove 12 only includes two ports, namely the first port and the second port. Among them, the first port of the spiral oil groove 12 can be located on the outer wall 13 of the inner ring 10, that is, the spiral oil groove 12 communicates with the outer wall 13 of the inner ring 10 through the first port. The second port of the spiral oil groove 12 is located on the inner wall 14 of the inner ring 10, that is, the spiral oil groove 12 can communicate with the inner wall 14 of the inner ring 10 through the second port. The spiral oil groove 12 enables the outer wall 13 and the inner wall 14 of the inner ring 10 to communicate at the end face of the inner ring.
[0036] In this way, through the first port and the second port of the spiral oil groove 12, the lubricant can flow into the spiral oil groove 12 from the first port on the outer wall 13 of the inner ring 10 and flow out from the second port to the inner wall 14 of the inner ring 10, or the lubricant can flow into the spiral oil groove 12 from the second port on the inner wall 14 of the inner ring 10 and flow out from the first port to the outer wall 13 of the inner ring 10. This can not only enable the lubricant in the spiral oil groove 12 to be replenished from the inner wall 14 and / or the outer wall 13 of the inner ring 10, but also enable the lubricant in the spiral oil groove 12 to flow out from the inner wall 14 and / or the outer wall 13 of the inner ring 10, so that the lubricant in the spiral oil groove 12 can be updated to ensure that the quality of the lubricant on the end face 11 of the inner ring 10 always meets the lubrication requirements.
[0037] The spiral oil groove 12 can be provided only on the end face 11 of one inner ring 10, or can be provided on the end faces 11 of both inner rings 10.
[0038] It should be noted that when observing the spiral oil groove 12 from the Figure 4 direction shown, the spiral oil groove 12 can rotate counterclockwise or clockwise, and no specific limitation is made here.
[0039] In some embodiments, the spiral oil groove 12 includes multiple turns, and the multiple turns of the spiral oil groove 12 are equi-pitch spirals on the end face 11 of the inner ring 10 along the radial direction. From the above, it can be seen that there is one and only one spiral oil groove 12 on the end face 11 of the inner ring 10, and the spiral oil groove 12 can be provided with multiple turns, such as Figure 4 Exemplarily, the spiral oil groove 12 is provided with two turns. The number of turns of the spiral oil groove 12 is determined by the groove width of the spiral oil groove 12 and the radial dimension of the end face 11 of the inner ring 10.
[0040] In addition, the equi-pitch spiral can enable the spiral oil groove 12 to more evenly divide the end face 11 of the inner ring 10. In this way, the lubricant in the spiral oil groove 12 can be evenly coated on the end face 11 of the inner ring 10.
[0041] In some embodiments, as Figure 5 shown, the pitch of the spiral oil groove 12 is 1 mm to 10 mm. In some embodiments, the depth of the spiral oil groove 12 is 0.1 mm to 5 mm. In some embodiments, the width of the spiral oil groove 12 is 0.1 mm to 5 mm.
[0042] It should be noted that the pitch, depth, and width of the above-mentioned spiral oil groove 12 are all exemplary and are not intended to limit the protection scope of the present disclosure. In some other embodiments, the number of turns, pitch, depth, and width of the spiral oil groove 12 can be adjusted according to the radial dimension of the end face 11 of the inner ring 10, and no specific limitation is made here.
[0043] In some embodiments, the spiral oil groove 12 is one or a combination of a triangle, a rectangle, a trapezoid, a curved shape, etc. The curved shape can include an arc shape, an elliptical arc shape, a hyperbolic shape, a parabolic shape, etc. Those skilled in the art can select according to the design requirements, and no specific limitation is made here.
[0044] Among them, the shapes of the spiral oil grooves 12 on the end faces 11 of two adjacent inner rings 10 can be the same or different. The shape of the spiral oil groove 12 on the end face 11 of the same inner ring 10 can also vary, and no specific limitation is made here.
[0045] It can be understood that "a plurality of" in the present disclosure means two or more, and other quantifiers are similar. Further, it can be understood that the terms "first", "second", etc. are used to describe various structures, but these structures should not be limited to these terms. These terms are only used to distinguish the same type of structures from each other and do not represent a specific order or importance. In fact, the expressions such as "first" and "second" can be used interchangeably. For example, without departing from the scope of the present disclosure, the first structure can also be called the second structure, and similarly, the second structure can also be called the first structure.
[0046] It can be further understood that the orientation or positional relationship indicated by terms such as "inner", "outer", "longitudinal", "transverse", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing this embodiment and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation.
[0047] Other embodiments of the present disclosure will be readily apparent to those skilled in the art upon consideration of the specification and practice of the invention disclosed herein. This application is intended to cover any variations, uses, or adaptations of the present disclosure that follow the general principles of the present disclosure and include known common general knowledge or conventional technical means in the technical field not disclosed herein. The specification and examples are only considered exemplary, and the true scope and spirit of the present disclosure are pointed out by the following claims.
[0048] It should be understood that the present disclosure is not limited to the exact structures described above and shown in the drawings, and various modifications and changes can be made without departing from its scope. The scope of the present disclosure is only limited by the appended claims.
Claims
1. A roll bearing (100), characterized in that, it includes: A plurality of inner rings (10), the plurality of inner rings (10) are arranged side by side along the axial direction, and the end faces (11) of two adjacent inner rings (10) are in contact with each other. Wherein, a continuous spiral oil groove (12) is provided on the end face (11) of the inner ring (10).
2. The roll bearing (100) according to claim 1, characterized in that, the inner ring (10) includes an outer wall (13) and an inner wall (14), the spiral oil groove (12) includes a first port and a second port, wherein, the first port of the spiral oil groove (12) is located on the outer wall (13) of the inner ring (10), the second port of the spiral oil groove (12) is located on the inner wall (14) of the inner ring (10), and the spiral oil groove (12) connects the outer wall (13) and the inner wall (14) of the inner ring (10).
3. The roll bearing (100) according to claim 1, characterized in that, the spiral oil groove (12) includes multiple turns, and the multiple turns of the spiral oil groove (12) are helical with equal pitch along the radial direction of the end face (11) of the inner ring (10).
4. The roll bearing (100) according to claim 3, characterized in that, the pitch of the spiral oil groove (12) is 1 mm to 10 mm.
5. The roll bearing (100) according to claim 1, characterized in that, the depth of the spiral oil groove (12) is 0.1 mm to 5 mm.
6. The roll bearing (100) according to claim 1, characterized in that, the width of the spiral oil groove (12) is 0.1 mm to 5 mm.
7. The roll bearing (100) according to claim 1, characterized in that, the spiral oil groove (12) is one or a combination of triangle, rectangle, trapezoid, and curve.
8. The roll bearing (100) according to claim 1, characterized in that, the roll bearing (100) further includes: an outer ring (20), sleeved outside the inner ring (10); rolling elements, located radially between the outer ring (20) and the inner ring (10); and a cage, used for circumferentially spacing and holding the rolling elements.
9. The roll bearing (100) according to claim 1, characterized in that, the roll bearing (100) is a double-row spherical roller bearing, a four-row tapered roller bearing, and a multi-row cylindrical roller bearing.