Back lining bearing

Abstract

The utility model relates to a backing bearing which comprises an outer ring and a bearing sealing structure, the axial outer end face of the outer ring is concaved inwards in the axial direction to form an annular groove, the bearing sealing structure comprises a sealing assembly and a sealing fixing ring, and the sealing assembly and the sealing fixing ring are pressed into the annular groove in an interference fit mode in the axial direction. The sealing fixing ring abuts against the axial outer side of the sealing assembly. The axial end face of the outer ring is directly sunken to form the annular groove, so that the machining process of the annular groove is simplified, the process and material cost is reduced, the sealing assembly and the sealing fixing ring are convenient to mount and dismount, and the damage risk in the maintenance process is reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of bearing sealing, in particular to a backing bearing. Background Art

[0002] The bearing seal structure of the backing bearing usually includes a seal assembly and a seal retaining ring, such as Figure 1 As shown, the outer ring 10 of the backing bearing is provided with an annular groove 50, and the sealing fixing ring is installed and fixed in the annular groove of the outer ring.

[0003] However, conventional backing bearings have the following issues: The outer ring groove is difficult to machine. If the groove is machined during soft turning, the bottom of the groove may crack after heat treatment due to stress concentration caused by deformation of the outer ring during heat treatment, resulting in a high scrap rate. If the groove is machined during hard turning, the higher surface hardness of the outer ring after heat treatment makes hard turning the groove very difficult, resulting in high processing costs.

[0004] Furthermore, the retaining ring is difficult to remove once installed in the groove. A set of backing bearings has a service life of approximately two years, and typically requires about ten disassembly and repair during its lifespan. Therefore, frequent disassembly and assembly increases the complexity of the disassembly process and the difficulty of maintenance when the bearing needs repair, increasing maintenance costs. Furthermore, once the retaining ring is installed in the groove, the groove is very close to the axial end face of the outer ring, making it very easy to fracture during frequent disassembly and maintenance, thus reducing the bearing's service life. Utility Model Content

[0005] In order to overcome the problems existing in the related art, the present disclosure provides a backing bearing.

[0006] According to a first aspect of an embodiment of the present disclosure, the present disclosure provides a backing bearing, comprising: an outer ring, the axial outer end surface of the outer ring being axially recessed inward to form an annular groove, a bearing sealing structure, comprising a sealing assembly and a sealing retaining ring, the sealing assembly and the sealing retaining ring being pressed into the annular groove with an axial interference fit, and the sealing retaining ring abutting the axial outer side of the sealing assembly.

[0007] In some embodiments, the annular groove is stepped along the axial direction, and includes: a small-diameter annular groove and a large-diameter annular groove, and the large-diameter annular groove is located axially outside the small-diameter annular groove.

[0008] In some embodiments, the sealing assembly is located in the small-diameter ring groove with an interference fit, and the sealing fixing ring is a Z-shaped structure, including an axial portion, a first radial portion and a second radial portion. The axial portion of the sealing fixing ring is located in the small-diameter ring groove and has an interference fit with the radial inner wall of the small-diameter ring groove. The first radial portion of the sealing fixing ring is located in the large-diameter ring groove and is in abutment with the axial wall of the large-diameter ring groove. The second radial portion is connected to the axial inner end of the axial portion, and the second radial portion is in abutment with the axial outer side of the sealing assembly.

[0009] In some embodiments, the sealing fixing ring is a C-shaped clamping ring or a closed circular ring in the circumferential direction.

[0010] In some embodiments, the radial length of the first radial portion is less than the radial length of the second radial portion.

[0011] In some embodiments, the axial length of the small-diameter annular groove is greater than the axial length of the large-diameter annular groove, and the thickness of the first radial portion is less than or equal to the axial length of the large-diameter annular groove.

[0012] In some embodiments, the backing bearing further includes an inner ring; the bearing sealing structure further includes an oil slinger, the axial portion of the oil slinger is interference fit with the outer wall of the inner ring, and the radial portion of the oil slinger radially overlaps with the second radial portion of the sealing fixing ring.

[0013] In some embodiments, the sealing assembly includes: a skeleton in the shape of a ring cake; a rubber body attached to the radial outer end, axial outer end face and radial inner end of the skeleton through a vulcanization process, and the sealing fixing ring abuts against the axial outer end face of the rubber body.

[0014] In some embodiments, the rubber body is provided with a sealing lip at the radial inner end of the skeleton. The sealing lip extends obliquely toward the radial outer side and the axial outer side and is in dynamic sealing contact with the radial portion of the oil slinger.

[0015] In some embodiments, the backing bearing further includes rolling elements radially disposed between the inner ring and the outer ring for rolling motion. The rolling elements are cylindrical rolling elements, and two rows of the rolling elements are provided.

[0016] The technical solutions provided by the embodiments of the present disclosure may have the following beneficial effects:

[0017] 1. Easy Processing: The annular groove can be created during the outer ring soft machining phase, reducing both processing difficulty and cost. 2. Easy Installation: The annular groove, formed directly from the outer ring's axial end face, simplifies the installation of the seal assembly and retaining ring. 3. Easy Disassembly: If the seal assembly becomes damaged during the backing bearing's service life, the annular groove facilitates removal of the retaining ring, simplifying maintenance. 4. Reduced Damage Risk: The outer ring is less likely to be damaged during disassembly, extending the backing bearing's service life. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present disclosure and, together with the description, serve to explain the principles of the present disclosure.

[0019] Figure 1 Schematic diagram of a ring groove for mounting a sealing retaining ring in a bearing outer ring in the related art;

[0020] Figure 2 is a cross-sectional view of a backing bearing according to an exemplary embodiment;

[0021] Figure 3 is an enlarged schematic diagram of a bearing sealing structure according to an exemplary embodiment;

[0022] Figure 4 is an enlarged schematic diagram of an annular groove according to an exemplary embodiment;

[0023] Figure 5 FIG. 1 is a schematic structural diagram of a sealing fixing ring according to an exemplary embodiment. DETAILED DESCRIPTION

[0024] Exemplary embodiments will be described in detail herein, with examples illustrated in the accompanying drawings. In the following description, when referring to the drawings, identical numerals in different figures represent identical or similar elements, unless otherwise indicated. The embodiments described in the following exemplary embodiments are not intended to represent all possible embodiments consistent with the present disclosure. Rather, they are merely examples of apparatus and methods consistent with certain aspects of the present disclosure, as detailed in the appended claims.

[0025] According to an embodiment of the present invention, the backing bearing is used in a silicon steel rolling mill in the raw material industry. In order to better understand the present invention. In the present invention, unless otherwise specified, the axial, radial and circumferential directions refer to the axial, radial and circumferential directions of the backing bearing respectively; the axial outer side or the axial outer end refers to the Figure 3 The right side or right end of the axial direction refers to Figure 3 The left side of the radial direction is the radial direction away from Figure 2 On the side of the central axis O ( Figure 2The radial inner side refers to the side closer to the central axis O in the radial direction ( Figure 2 The term "torsionally rigid connection" refers to a connection between two components that prevents rotation relative to each other. This can be achieved through a press fit (i.e., an interference fit) or by integrally forming the two components. The specific meanings of the above terms in the present invention will be understood by those skilled in the art depending on the specific circumstances.

[0026] In order to solve the above technical problems, the present disclosure provides a bearing, preferably, as Figure 2 As shown, the bearing is a backing bearing 100. Specifically, the backing bearing 100 may include an outer ring 10, an inner ring 20, and rolling elements 30. The rolling elements 30 are arranged in two rows along the axial direction A. The two rows of rolling elements 30 are both disposed in a rolling manner along the radial direction R between the inner ring 20 and the outer ring 10, allowing the outer ring 10 and the inner ring 20 to rotate relative to each other.

[0027] The backing bearing 100 further includes a bearing seal structure 40, such as Figure 2 As shown, the bearing sealing structure 40 is arranged at both axial ends of the rolling element 30 and radially arranged between the inner ring 20 and the outer ring 10. A sealed chamber is formed between the bearing sealing structure 40 and the inner ring 20 and the outer ring 10, and the rolling element 30 is located in the chamber. This design can effectively prevent the leakage of lubricating grease inside the chamber, and can also prevent dust particles and water vapor outside the backing bearing 100 from entering the chamber, thereby protecting the rolling element 30, the inner ring 20 and the raceway of the outer ring 10 from damage.

[0028] like Figure 3 As shown, the bearing seal structure 40 generally includes a seal assembly 41, a seal retaining ring 42 and an oil slinger 43. In this embodiment, as shown in FIG. Figure 3 As shown, the seal assembly 41 is connected to the outer ring 10 in a torsionally fixed manner, and the oil slinger 43 is connected to the inner ring 20 in a torsionally fixed manner. The seal assembly 41 and the oil slinger 43 can rotate with the relative rotation of the outer ring 10 and the inner ring 20. It should be noted that in other embodiments, the seal assembly 41 can also be connected to the inner ring 20 in a torsionally fixed manner, and the oil slinger 43 can also be connected to the outer ring 10 in a torsionally fixed manner. This is not specifically limited here.

[0029] In this embodiment, taking the sealing assembly 41 and the outer ring 10 as examples of a torsionally anti-connected connection, and the oil slinger 43 and the inner ring 20 as examples, the sealing fixing ring 42 is the same as the sealing assembly 41, and is torsionally anti-connected to the outer ring 10, and is arranged on the axial outside of the sealing assembly 41, and is used to axially A resist the sealing assembly 41, limit the axial position of the sealing assembly 41, avoid axial movement or axial disengagement of the sealing assembly 41, and thus prevent failure of the bearing sealing structure 40.

[0030] Among them, in this embodiment, Figure 4 As shown, the inner wall of the outer ring 10 is provided with an annular groove 11, which is formed by directly recessing the axial outer end surface of the outer ring 10 inward along the axial direction A. Furthermore, the sealing assembly 41 and the sealing retaining ring 42 of the bearing sealing structure 40 are pressed into the annular groove 11 with an axial interference fit to achieve a torsion-resistant connection with the outer ring 10.

[0031] As can be seen above, the seal retainer ring 42 abuts the axially outer side of the seal assembly 41, preventing the seal assembly 41 from axially separating from the outer ring 10. The axial wall of the annular groove 11 abuts the axially inner side of the seal assembly 41. Therefore, the annular groove 11, through its axial wall, can restrict the axial movement of the seal assembly 41 toward the rolling element 30. The axial wall of the annular groove 11 and the seal retainer ring 42 jointly restrict the axial position of the seal assembly 41, preventing axial movement of the seal assembly 41 and improving the overall sealing performance of the bearing seal structure 40.

[0032] For example Figure 4 As shown, the annular groove 11 is connected to the axial outer end surface and radial inner wall of the outer ring 10. Figure 1 Compared to the annular groove 50 in the embodiment of the present invention, the annular groove 11 of the present invention does not need to be formed by cutting a groove from the radial inner wall of the outer ring 10, thus reducing machining difficulty and cost. Furthermore, the annular groove 11 of the present invention can be machined during the soft machining stage of the outer ring 10. After the outer ring 10 is heat treated, the annular groove 11 of the present invention communicates with the axial outer end surface of the outer ring 10 and has a large axial length. Even if the outer ring 10 deforms due to the heat treatment, the stress generated by the deformation will not significantly affect the structure of the annular groove 11, further reducing machining difficulty and cost, and improving the yield rate.

[0033] Furthermore, the annular groove 11, formed by a direct depression in the axial end surface of the outer ring 10, allows the seal assembly 41 and the retaining seal ring 42 to be directly pressed into the annular groove 11 from the axial outer end surface of the outer ring 10, facilitating installation of the seal assembly 41 and the retaining seal ring 42. If the seal assembly 41 becomes damaged during the life of the backing bearing 100, the annular groove 11, formed by the direct depression in the axial outer end surface of the outer ring 10, also facilitates removal of the retaining seal ring 42 without damaging the outer ring 10 and the annular groove 11 during removal.

[0034] Further, if Figure 4 As shown, the annular groove 11 is stepped along the axial direction A, and includes a small-diameter annular groove 111 and a large-diameter annular groove 112 . The large-diameter annular groove 112 is located axially outside the small-diameter annular groove 111 .

[0035] The sealing assembly 41 is located in the small-diameter annular groove 111 , and the radial outer end of the sealing assembly 41 is interference-fitted with the radial inner wall of the small-diameter annular groove 111 to achieve a torsional connection with the outer ring 10 .

[0036] Among them, Figure 5 As shown, the cross section of the sealing fixing ring 42 is a Z-shaped structure. The sealing fixing ring 42 includes an axial portion 421 extending in the axial direction and a first radial portion 422 and a second radial portion 423 extending in the radial direction.

[0037] The axial portion 421 of the sealing retainer ring 42 is located within the small-diameter annular groove 111, and the radial outer wall of the axial portion 421 of the sealing retainer ring 42 is interference fit with the radial inner wall of the small-diameter annular groove 111, thereby achieving a torsion-resistant connection between the sealing retainer ring 42 and the outer ring 10. The first radial portion 422 of the sealing retainer ring 42 is connected to the axial outer end of the axial portion 421, and the first radial portion 422 is located within the large-diameter annular groove 112, abutting against the axial wall of the large-diameter annular groove 112.

[0038] The annular groove 11 is stepped and forms a large-diameter annular groove 112 and a small-diameter annular groove 111. This structure allows at least a portion of the seal retainer ring 42 to be located within the small-diameter annular groove 111 and abut against the seal assembly 41, thereby axially limiting the seal assembly 41. Furthermore, the design of the large-diameter annular groove 112 ensures that the first radial portion 422 of the seal retainer ring 42 is located within the large-diameter annular groove 112, axially abutting against the axial wall of the large-diameter annular groove 112. This prevents the seal retainer ring 42 from being excessively pressed in the axial direction when it is pressed in, thereby preventing damage to the seal assembly 41.

[0039] Furthermore, Figure 5 As shown, the second radial portion 423 of the sealing fixing ring 42 is connected to the axial inner end of the axial portion 421 , and the second radial portion 423 is in contact with the axial outer end of the sealing assembly 41 .

[0040] Specifically, the second radial portion 423 increases the contact area between the seal retainer ring 42 and the seal assembly 41, helping to evenly distribute the force exerted by the seal retainer ring 42 on the seal assembly 41 and reducing the risk of deformation of the seal assembly 41 caused by local stress concentration. This not only increases the service life of the seal assembly 41 but also ensures its reliability and stability during long-term use.

[0041] In addition, the sealing retainer ring 42 includes both a first radial portion 422 and a second radial portion 423. When the sealing assembly 41 tends to move axially outward, the sealing assembly 41 axially pushes or squeezes the second radial portion 423. The second radial portion 423 is squeezed and tends to flip axially outward. This tendency is transmitted to the first radial portion 422 via the Z-shaped structure of the sealing retainer ring 42, allowing the first radial portion 422 to fit more closely against the axial wall of the large-diameter annular groove 112. This enhances the stability of the sealing retainer ring 42, prevents the sealing retainer ring 42 from axially separating from the outer ring 10, improves the axial limiting effect of the sealing assembly 41, and further enhances the overall sealing performance of the bearing sealing structure 40, ensuring the reliable operation of the backing bearing 100 under various operating conditions.

[0042] It will be further understood that the terms "first," "second," and the like are used to describe various structures, but these structures should not be limited to these terms. These terms are merely used to distinguish structures of the same type from one another and do not indicate a particular order or level of importance. In fact, the terms "first," "second," and the like are fully interchangeable. For example, the first radial portion 422 could also be referred to as the second radial portion 423, and similarly, the second radial portion 423 could also be referred to as the first radial portion 422, without departing from the scope of this disclosure.

[0043] In some embodiments, the sealing retainer ring 42 is circumferentially a C-shaped retaining ring or a closed circular ring. Because the sealing retainer ring 42 can be directly pressed into the annular groove 11 from the axially outer end surface of the outer ring 10, a closed circular ring structure can be selected for the sealing retainer ring 42, which provides better structural and performance stability. Alternatively, an existing C-shaped retaining ring can be used as the sealing retainer ring 42, utilizing readily available standard parts, simplifying the procurement process, and reducing manufacturing costs. Whether a closed circular ring or a C-shaped retaining ring is selected, both ensure reliable installation and axial positioning of the sealing assembly 41, while increasing the versatility and applicability of the sealing retainer ring 42.

[0044] In some embodiments, as Figure 3 and Figure 5 As shown, the radial length of the first radial portion 422 is smaller than the radial length of the second radial portion 423. This ensures that the first radial portion 422 provides axial restraint for the seal retainer ring 42 while avoiding excessive size. The smaller first radial portion 422 not only helps reduce material costs but also avoids the problem of reduced strength of the outer ring 10 caused by overly large grooves in the outer ring 10. The larger radial length of the second radial portion 423 increases the contact area between the seal retainer ring 42 and the seal assembly 41, helping to axially restrain the seal assembly 41 and further enhancing the sealing performance of the seal assembly 41.

[0045] In some embodiments, as Figure 4 As shown, the axial length of the small-diameter annular groove 111 is greater than the axial length of the large-diameter annular groove 112, and the thickness of the first radial portion 422 is less than or equal to the axial length of the large-diameter annular groove 112, ensuring that the first radial portion 422 does not protrude axially from the axial outer end surface of the outer ring 10, reducing the risk of wear and damage to the second radial portion 423 and the external structure of the backing bearing 100.

[0046] In some embodiments, as Figure 3 As shown, the axial portion 431 of the oil slinger 43 has an interference fit with the outer wall of the inner ring 20, and the radial portion 432 of the oil slinger 43 radially overlaps with the first radial portion 422 of the seal retainer ring 42. The overlap of the radial portion 432 of the oil slinger 43 and the first radial portion 422 of the seal retainer ring 42 effectively prevents dust particles and moisture from entering the backing bearing 100 from contacting the surface of the seal assembly 41, and also prevents dust particles and moisture from entering the interior of the bearing, providing excellent protection and blocking effects, thereby improving the sealing effect and stability of the entire bearing seal structure 40.

[0047] In this embodiment, if Figure 3 As shown, the sealing assembly 41 includes a skeleton 411 and a rubber body 412. The skeleton 411 is in the shape of a ring cake; the rubber body 412 is attached to the radial outer end, axial outer end surface, and radial inner end of the skeleton 411 through a vulcanization process, and the sealing retaining ring 42 abuts the axial outer end surface of the rubber body 412.

[0048] The rubber body 412 is arranged at the radial outer end of the skeleton 411. When the sealing assembly 41 is connected to the outer ring 10 of the backing bearing 100 to achieve torsion-resistant connection, the rubber body at the radial outer end of the skeleton 411 avoids direct contact between the skeleton 411 and the outer ring 10, increases the friction between the sealing assembly 41 and the radial inner wall of the outer ring 10, and at the same time eliminates the gap between the skeleton 411 and the outer ring 10, thereby improving the sealing effect.

[0049] The skeleton 411 is in the shape of a torus, meaning its axially outer end surface is flat. The rubber body 412 is tightly bonded to the axially outer end surface of the skeleton 411 through a vulcanization process. This allows the second radial portion 423 to better mate with the seal assembly 41 when the seal retainer ring 42 abuts the seal assembly 41, increasing the contact area. It also prevents wear of the seal retainer ring 42 on the seal assembly 41, reducing wear and improving reliability.

[0050] Furthermore, if Figure 3As shown, the rubber body 412 is provided with a sealing lip 4121 at the radially inner end of the frame 411. This lip 4121 extends radially and axially outward at an angle, and dynamically seals against the radial portion 432 of the oil slinger 43. This effectively blocks external dust particles and moisture from entering the bearing, improving the sealing effect, reducing wear on internal bearing components caused by external contaminants, and extending the bearing's service life. The dynamic sealing contact between the sealing lip 4121 and the radial portion 432 of the oil slinger 43 enhances the stability of the bearing seal structure 40 and reduces the risk of seal failure due to external factors.

[0051] In some embodiments, as Figure 2 As shown, the rolling element 30 is a cylindrical rolling element 30. The use of the cylindrical rolling element 30 not only improves the radial load-bearing capacity and the life of the bearing, but also simplifies the processing process and improves work efficiency and reliability.

[0052] It can be further understood that the orientation or position relationship indicated by the terms "center", "bottom", "inside", "outside", etc. is based on the orientation or position relationship shown in the accompanying drawings, and is only for the convenience of describing this embodiment and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation.

[0053] Those skilled in the art will readily appreciate other embodiments of the present disclosure after considering the specification and practicing the utility model 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 common knowledge or customary techniques in the art not disclosed herein. The description and examples are to be considered merely as exemplary, and the true scope and spirit of the present disclosure are indicated by the following claims.

[0054] It should be understood that the present disclosure is not limited to the exact structures described above and shown in the drawings, and that various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the scope of the appended claims.

Claims

1. A backing bearing (100), characterized in that: include: An outer ring (10), wherein the axial outer end surface of the outer ring (10) is recessed inwardly along the axial direction (A) to form an annular groove (11), A bearing sealing structure (40) comprises a sealing assembly (41) and a sealing fixing ring (42), wherein the sealing assembly (41) and the sealing fixing ring (42) are pressed into the annular groove (11) in an interference fit along the axial direction (A), and the sealing fixing ring (42) abuts against the axial outer side of the sealing assembly (41).

2. The backing bearing (100) according to claim 1, characterized in that The annular groove (11) is stepped along the axial direction (A), and comprises a small-diameter annular groove (111) and a large-diameter annular groove (112), wherein the large-diameter annular groove (112) is located axially outside the small-diameter annular groove (111).

3. The backing bearing (100) according to claim 2, characterized in that The sealing assembly (41) is located in the small-diameter annular groove (111) with an interference fit. The sealing fixing ring (42) is a Z-shaped structure, comprising an axial portion (421), a first radial portion (422) and a second radial portion (423). The axial portion (421) of the sealing fixing ring (42) is located in the small-diameter annular groove (111) and is interference-fitted with the radial inner wall of the small-diameter annular groove (111). The first radial portion (422) of the sealing fixing ring (42) is located in the large-diameter annular groove (112) and is in close contact with the axial wall of the large-diameter annular groove (112). The second radial portion (423) is connected to the axial inner end of the axial portion (421), and the second radial portion (423) is in close contact with the axial outer side of the sealing assembly (41).

4. The backing bearing (100) according to claim 1, characterized in that The sealing fixing ring (42) is a C-shaped clamping ring or a closed circular ring in the circumferential direction.

5. The backing bearing (100) according to claim 3, characterized in that The radial length of the first radial portion (422) is smaller than the radial length of the second radial portion (423).

6. The backing bearing (100) according to claim 3, characterized in that The axial length of the small-diameter annular groove (111) is greater than the axial length of the large-diameter annular groove (112), and the thickness of the first radial portion (422) is less than or equal to the axial length of the large-diameter annular groove (112).

7. The backing bearing (100) according to claim 3, characterized in that The backing bearing (100) further includes an inner ring (20); The bearing sealing structure (40) further includes an oil slinger (43), wherein an axial portion (431) of the oil slinger (43) is interference-fitted with a radial outer wall of the inner ring (20), and a radial portion (432) of the oil slinger (43) radially overlaps with a second radial portion (423) of the sealing fixing ring (42).

8. The backing bearing (100) according to claim 7, characterized in that The sealing assembly (41) comprises: The skeleton (411) is in the shape of a ring cake; The rubber body (412) is attached to the radial outer end, the axial outer end surface and the radial inner end of the skeleton (411) through a vulcanization process, and the sealing fixing ring (42) is in contact with the axial outer end surface of the rubber body (412).

9. The backing bearing (100) according to claim 8, characterized in that The rubber body (412) is provided with a sealing lip (4121) at the radial inner end of the skeleton (411). The sealing lip (4121) extends obliquely toward the radial outer side and the axial outer side and is in dynamic sealing contact with the radial portion (432) of the oil slinger (43).

10. The backing bearing (100) according to claim 7, characterized in that The backing bearing (100) further includes a rolling element (30) which is arranged to roll between the inner ring (20) and the outer ring (10) in a radial direction (R). The rolling element (30) is a cylindrical rolling element (30) and two rows of the rolling elements (30) are provided.

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