Face splined hub bearing with protective element

Abstract

The end face spline hub bearing comprises a flange inner ring, a small inner ring and an outer ring, the small inner ring is sleeved on the outer side of the flange inner ring, the flange inner ring is provided with a retaining wall and an outer flange used for being limited with the small inner ring, a rolling assembly is arranged between the retaining wall and the outer flange, and a sealing assembly is arranged between the small inner ring and the outer ring. The outer side of the small inner ring is provided with a sealing matching surface, and the axial outer end of the outer flange is provided with an end face spline. A cylindrical protection element is fixedly installed at the axial outer end of the small inner ring, covers the outer flange and at least covers the end face spline meshing position. The axial outer end of the small inner ring is provided with a first matching surface, a second matching surface and a third matching surface, the first matching surface is in riveting fit with the outer flange, the second matching surface axially abuts against the protection element for limiting, and the third matching surface is in radial pressing contact with the inner side of the protection element. The radial outer side of the outer flange and the protective element are spaced to form an annular gap, and the inner and outer peripheral walls are respectively provided by the two. The end face spline hub bearing with the protection element is provided with the protection element, can prevent foreign matters from entering, and is simple in structure and convenient to process, manufacture and assemble.

Description

Technical Field

[0001] This utility model relates to an end-face splined hub bearing with protective elements. Background Technology

[0002] End-face spline wheel hub bearings are key components of automotive wheel hubs. Existing end-face spline wheel hub bearings typically consist of a flange inner ring, a smaller inner ring, and an outer ring. The smaller inner ring and the flange inner ring are fixedly connected by riveting. The outer ring is located radially outside the flange inner ring and the smaller inner ring. Two sets of rollers are arranged axially between the outer ring and the inner ring. The inner side of the outer ring has two first raceways that mate with the two sets of rollers, respectively. The outer sides of the flange inner ring and the smaller inner ring each have two second raceways that mate with the two sets of rollers, respectively. The end of the flange inner ring has an outwardly flanged edge formed by riveting, used for riveting and fixing the smaller inner ring. The axial end face of the outwardly flanged edge has toothed end-face splines for transmission connection with the vehicle's transmission components to transmit torque.

[0003] The outer flange of a face splined hub bearing is typically located axially outside the end face of the smaller inner ring and is exposed to external environmental conditions, such as mud, sand, and metal filings. This harsh environment degrades the performance of the riveted flange, thus affecting the bearing's service life. For example, exposure to mud and water often leads to rust on the riveted flange, potentially causing changes in raceway stress. Similarly, face splines present similar problems; hard particles like sand and metal filings can affect the meshing of the end face teeth, leading to decreased transmission efficiency and other abnormalities.

[0004] In the current technology, in order to solve the above problems, an annular boss is usually machined on the axial end of the small inner ring. The boss is located on the radial outer side of the outward flange and has a certain blocking effect on foreign objects such as mud, sand, and iron filings. However, the setting of the boss also makes the structure of the small inner ring more complicated and is not conducive to processing and manufacturing. Summary of the Invention

[0005] In order to overcome the defects of the prior art, this utility model provides an end splined hub bearing with protective elements, which can prevent foreign objects such as mud, water, sand, and iron filings from entering the outer flange and the meshing point of the end spline. It also has a simple structure and is easy to process, manufacture and assemble.

[0006] This utility model discloses an end-face splined hub bearing with a protective element, comprising an inner flange ring, a smaller inner ring, and an outer ring. The smaller inner ring is fitted onto the outer side of the inner flange ring. The inner flange ring includes a retaining wall that engages with and limits one axial end of the smaller inner ring. One end of the inner flange ring includes a riveted outward flange, which engages with and limits the other axial end of the smaller inner ring. A rolling assembly is provided between the inner flange ring, the smaller inner ring, and the outer ring. The rolling assembly includes at least two rows of axially arranged steel balls. A sealing assembly is provided between the smaller inner ring and the outer ring. The outer side of the smaller inner ring includes a sealing mating surface that engages with and connects to the sealing assembly. An end-face spline is provided on the axial outer end of the outward flange. A cylindrical protective element is fixedly installed on the axial outer end of the smaller inner ring. The protective element covers the outer side of the outward flange and at least covers the meshing of the end-face spline. At the joint, the axial outer end of the small inner ring includes a first mating surface, a second mating surface, and a third mating surface located on the radial outer side. The first mating surface is located radially inner to the second mating surface. The first mating surface and the outer flange are riveted together. The second mating surface and the protective element form an axial abutment and limiting fit. The second mating surface can serve as an axial limit for the protective element during installation. The third mating surface and the inner side of the protective element form a radial pressing contact fit. The third mating surface is used to connect the protective element. The third mating surface can effectively surround the meshing part of the outer flange and the end face teeth and form a static seal, preventing wear and other problems. An annular gap is formed between the radial outer side of the outer flange and the protective element. The inner and outer peripheral walls of the annular gap are provided by the outer flange and the protective element, respectively.

[0007] In one preferred embodiment, the second mating surface is located radially outside the first mating surface and radially inside the third mating surface, respectively. The axial inner end of the protective element includes an L-shaped connecting structure, which includes a radially extending section extending radially outward and an axially extending section extending axially. The axially extending section is connected to the radially outside of the radially extending section. The protective element forms an axial abutment and limiting fit through its radially extending section and the second mating surface. The protective element forms a radial pressing contact fit through its axially extending section and the third mating surface. The radial width of the second mating surface is greater than the radial width of the radially extending section.

[0008] Furthermore, the outer diameter of the sealing mating surface is larger than the outer diameter of the third mating surface. This design allows the protective element and the bearing sealing assembly to be misaligned, preventing interference with the bearing seal. A smaller groove can be formed by appropriately grinding the axial outer ring of the smaller inner ring, resulting in a third mating surface with an outer diameter smaller than the sealing mating surface. The grinding amount at the axial outer end of the smaller inner ring is relatively small, increasing grinding efficiency.

[0009] Furthermore, the outer diameter of the sealing mating surface is the same as that of the third mating surface, so the third mating surface does not need to undergo additional grinding to reduce its outer diameter, thus reducing the number of manufacturing steps.

[0010] In another preferred embodiment, the third mating surface is located radially outside the first mating surface and radially inside the second mating surface. The second mating surface is located between the sealing mating surface and the third mating surface. The outer diameter of the sealing mating surface is larger than the outer diameter of the third mating surface. The protective element includes an axially extending section. The protective element forms a radial pressing contact with the third mating surface through its axially extending section and an axial abutment limiting contact with the second mating surface. The radial width of the first mating surface is larger than the radial width of the portion of the outwardly flange that contacts the first mating surface.

[0011] In the above preferred embodiment, a groove can be formed on the outer side of the axial outer end of the small inner ring. The second and third mating surfaces respectively constitute two adjacent sidewalls of the groove. The radial depth of the groove is approximately the same as the radial width of the second mating surface. The groove is formed by grinding the outer axial end of the small inner ring. Compared with the previous preferred embodiment, the design structure of the protective element can be simpler, less material is used, and the overall structure is more compact. In addition, the groove design can reduce the excessive circumferential stress (i.e., hoop stress) on the outer diameter of the small inner ring after deformation caused by interference fit and riveting of the small inner ring and flange inner ring, thus avoiding problems such as cracking.

[0012] Furthermore, the protective element also includes a radial extension section connected to the outer side of the end of the axial extension section, and the radial extension section of the protective element and the second mating surface constitute an axial abutment and limiting fit.

[0013] In the above scheme, when the protective element only includes the axial extension section, it can form a straight seal with the third mating surface; when it also includes the radial extension section, it can cooperate with the second mating surface to form an L-shaped seal. That is, the second mating surface can not only be used to limit the protective element during axial installation, but also to provide a seal.

[0014] Furthermore, the axial width of the third mating surface is L3, and the axial distance between the first mating surface and the second mating surface is L4, where L3 > 0.5L4, to ensure sufficient pull-out force and prevent the protective element from falling off the inner ring.

[0015] Furthermore, the radial width of the outer flange is L5, and the inner ring of the flange includes an annular support portion located inside the small inner ring and integrally connected with the outer flange. The radial width of the annular support portion is L8, where L5 > 1.2L8, ensuring the meshing width of the teeth of the end face spline and improving the transmitted torque.

[0016] Furthermore, the turned-out edge is processed by spin riveting. The first mating surface includes a flat surface that is radially outward and an inclined surface that is radially inward. The inclined surface is spin-riveted with the turned-out edge. The setting of the inclined surface can reduce the end face area of the small inner ring, reducing the grinding amount. At the same time, it avoids too large difference in the end face areas at both axial ends of the small inner ring, causing uneven grinding problems and being unfavorable for mass production. In addition, since the turned-out edge is processed by spin riveting and spin riveting has a certain processing angle, the setting of the inclined surface can cooperate with the spin riveting processing angle, improving the processing accuracy of the spline on the upper end face of the riveted turned-out edge and improving the pressing performance of the turned-out edge on the small inner ring. It can make the overall structure more compact, provide sufficient processing space for the riveting of the turned-out edge, reduce the volume of the small inner ring, reduce the weight of the bearing, and improve fuel economy.

[0017] Furthermore, the included angle A between the inclined surface and the radial direction of the bearing is 3 to 20 degrees, which can reduce the deformation of the small inner ring caused by riveting during the spin-riveting forming process of the turned-out edge.

[0018] Furthermore, the minimum axial distance between the part of the first mating surface in contact with the turned-out edge and the lowest point of the tooth bottom of the end face spline of the turned-out edge is L6, and the maximum distance between the highest point of the tooth top of the end face spline of the part of the first mating surface in contact with the turned-out edge is L7, and 0.15 < L6 / L7 < 0.8. Such a setting can ensure the thickness of the spin-riveted turned-out edge to provide sufficient clamping force and can also prevent cracks from occurring at the tooth bottom during riveting processing or operation.

[0019] Furthermore, 0.8 < L8 / L7 < 1.8 to ensure sufficient material for tooth forming.

[0020] The beneficial effects of the present utility model are as follows: By providing a cylindrical protection element, it effectively blocks foreign matters such as mud, sand, and iron filings from entering the meshing part of the turned-out edge and the end face spline. The protection element and the small inner ring are stably installed through multi-faceted cooperation. At the same time, the overall structure of the bearing is simple, facilitating processing, manufacturing, and assembly. Description of the Drawings

[0021] Figure 1 Partial cross-section of Embodiment 1 of the present utility model Figure 1 ;

[0022] Figure 2 Partial cross-section of Embodiment 1 of the present utility model Figure 2 ;

[0023] Figure 3 Partial cross-section of Embodiment 1 of the present utility model Figure 3 [[ID=​​​​​ Figure 5 This is a partial cross-sectional view of Embodiment 3 of the present invention;

[0026] Figure 6 This is a partial cross-sectional view of Embodiment 4 of the present invention. Detailed Implementation

[0027] The basic part of the end-face splined hub bearing with protective elements in various embodiments of this utility model, such as Figures 1 to 6 As shown, the flange includes an inner ring 1, a small inner ring 2, and an outer ring 3. The small inner ring 2 is fitted onto the outside of the inner ring 1. The outer side of the inner ring 1 includes a baffle 11 that engages with and limits one axial end of the small inner ring 2. One end of the inner ring 1 includes a riveted outward flange 12, which engages with and limits the other axial end of the small inner ring 2. A rolling assembly is provided between the inner ring 1, the small inner ring 2, and the outer ring 3. The rolling assembly includes two rows of steel balls and a cage that engages with the steel balls. Raceways that engage with the two rows of steel balls are provided on the outer sides of both the inner ring 1 and the small inner ring 2. A sealing assembly 4 is provided between the small inner ring 2 and the outer ring 3. The outer side of the small inner ring 2 includes a sealing mating surface 21 that engages with and connects to the sealing assembly 4. An end face spline 121 is provided on the outer axial end of the outward flange 12. A cylindrical protective element 5 is fixedly installed at the outer axial end of the inner ring 12. The protective element 5 covers the outer side of the outer flange 12 and at least covers the meshing point between the end face spline 121 and the transmission component. The outer axial end of the inner ring 2 includes a first mating surface 22, a second mating surface 23 on the axial side, and a third mating surface 24 on the radial side. The first mating surface 22 is located radially inside the second mating surface 23. The first mating surface 22 and the outer flange 12 are riveted together. The second mating surface 23 and the protective element 5 form an axial abutment and limiting fit. The third mating surface 24 and the inner side of the protective element 5 form a radial pressing contact fit. An annular gap 6 is formed between the radial outer side of the outer flange 12 and the protective element 5. The inner and outer peripheral walls of the annular gap 6 are provided by the outer flange 12 and the protective element 5, respectively. The outer flange 12 is manufactured by riveting.

[0028] In Examples 1 and 2, respectively, as follows: Figures 1 to 3 and Figure 4As shown, the third mating surface 24 is located radially outside the first mating surface 22 and radially inside the second mating surface 23. The second mating surface 23 is located between the sealing mating surface 21 and the third mating surface 24. The outer diameter of the sealing mating surface 21 is larger than the outer diameter of the third mating surface 24, resulting in a height difference between the sealing mating surface 21 and the third mating surface 24. The protective element 5 includes an axial extension section 51. The protective element 5 forms a radial pressing contact with the third mating surface 24 through its axial extension section 51 and an axial abutment and limiting contact with the second mating surface 23. The radial width L1 of the first mating surface 22 is larger than the radial width L2 of the portion of the outer flange 12 that contacts the first mating surface 22. Figure 2 As shown.

[0029] In such Figure 5 In Embodiment 3 shown, unlike Embodiment 1, the protective element 5 further includes a radial extension 52 connected to the outer side of the end of the axial extension 51. The radial extension 52 and the second mating surface 23 of the protective element 5 constitute an axial abutment and limiting fit.

[0030] In Examples 3 and 4, respectively, as follows: Figure 5 , 6 As shown, the second mating surface 23 is located radially outside the first mating surface 22 and radially inside the third mating surface 24. The axial inner end of the protective element 5 includes an L-shaped connecting structure. The connecting structure includes a radially extending section 52 extending radially outward and an axially extending section 51 extending axially. The axially extending section 51 is connected to the radially outside of the radially extending section 52. The protective element 5 forms an axial abutment and limiting fit through its radially extending section 52 and the second mating surface 23. The protective element 5 forms a radial pressing contact fit through its axially extending section 51 and the third mating surface 24. The radial width of the second mating surface 23 is greater than the radial width of the radially extending section 52. The first mating surface 22 includes a radially outward flat surface and a radially inward inclined surface. The inclined surface and the outer flange 12 are riveted together. The flat surface is set at a position corresponding to the annular gap 6.

[0031] In Example 3, as Figure 5 As shown, the outer diameter of the sealing mating surface 21 is slightly larger than the outer diameter of the third mating surface 24.

[0032] In Example 4, as Figure 6 As shown, the outer diameter of the sealing mating surface 21 is the same as the outer diameter of the third mating surface 24.

[0033] Furthermore, in various embodiments of this utility model, with Figure 3Taking the example of Embodiment 1 shown, the axial width of the third mating surface 24 is L3, which is also the axial width of the part in contact between the third mating surface 24 and the protective element 5. The axial distance between the first mating surface 22 and the second mating surface 23 is L4, where L3 > 0.5L4.

[0034] The radial width of the outer flange 12 is L5, which does not include the radial width L8 of the annular support portion 13. The inner ring of the flange includes an annular support portion 13 located inside the small inner ring 2 and integrally connected with the outer flange 12. The radial width of the annular support portion 13 is L8, and L5 > 1.2L8.

[0035] The included angle A between the inclined surface and the radial direction of the bearing is 3 to 20 degrees.

[0036] The following is a record of experimental data on riveting force and riveting deformation at different angles A:

[0037] Angle A 0° (i.e., plane) 5° 10° 15° 20° Riveting force a 1.1a 1.3a 1.8a 2.2a Riveting deformation b 0.8b 0.6b 0.5b 0.48b

[0038] In the above experimental data, with the included angle A being 0°, the riveting force being 'a' and the riveting deformation being 'b', the ratios of riveting force and riveting deformation at other angles are illustrated. The riveting force refers to the force applied to the outer flange, and the riveting deformation refers to the radial thickness change of the inner ring. When the riveting deformation is large, the inner ring experiences greater circumferential stress, making it more prone to cracking. Cracks can damage the structural integrity of the bearing components, reduce their load-bearing capacity, and decrease their resistance to corrosion from mud and salt water.

[0039] The above test data shows that when the included angle of the inclined surface is between 5 and 20 degrees, it can withstand greater riveting force and less riveting deformation compared to 0 degrees.

[0040] The minimum axial distance between the contact portion of the first mating surface 22 and the outer flange and the lowest point of the tooth root of the end face spline of the outer flange 12 is L6, and the maximum distance between the highest point of the tooth tip of the end face spline of the contact portion of the first mating surface 22 and the outer flange 12 is L7, 0.15 <L6 / L7<0.8。

[0041] In addition, 0.8 <L8 / L7<1.8。

[0042] The above embodiments are merely one preferred embodiment of the present utility model. Ordinary changes and substitutions made by those skilled in the art within the scope of the present utility model's technical solution are all included within the protection scope of the present utility model.

Claims

1. A face splined hub bearing with protective elements, comprising an inner flange ring, a small inner ring, and an outer ring, wherein the small inner ring is fitted onto the outer side of the inner flange ring, the inner flange ring includes a retaining wall that engages and limits one axial end of the small inner ring, one end of the inner flange ring includes a riveted outward flange that engages and limits the other axial end of the small inner ring, a rolling assembly is provided between the inner flange ring, the small inner ring, and the outer ring, a sealing assembly is provided between the small inner ring and the outer ring, the outer side of the small inner ring includes a sealing mating surface that engages and connects with the sealing assembly, and a face spline is provided on the outer axial end of the outward flange, characterized in that: A cylindrical protective element is fixedly installed at the axial outer end of the small inner ring. The protective element covers the outer side of the outer flange and at least covers the meshing part of the end face spline. The axial outer end of the small inner ring includes a first mating surface, a second mating surface, and a third mating surface located on the radial outer side. The first mating surface is located on the radial inner side of the second mating surface. The first mating surface and the outer flange are riveted together. The second mating surface and the protective element form an axial abutment and limiting fit. The third mating surface and the inner side of the protective element form a radial pressing contact fit. An annular gap is formed between the radial outer side of the outer flange and the protective element. The inner and outer peripheral walls of the annular gap are provided by the outer flange and the protective element, respectively.

2. The end-face splined hub bearing with protective elements according to claim 1, characterized in that: The second mating surface is located radially outside the first mating surface and radially inside the third mating surface. The axial inner end of the protective element includes an L-shaped connecting structure. The connecting structure includes a radially extending section extending radially outward and an axially extending section extending axially. The axially extending section is connected to the radially outside of the radially extending section. The protective element forms an axial abutment and limiting fit through its radially extending section and the second mating surface. The protective element forms a radial pressing contact fit through its axially extending section and the third mating surface. The radial width of the second mating surface is greater than the radial width of the radially extending section.

3. The end-face splined hub bearing with protective elements according to claim 2, characterized in that: The outer diameter of the sealing mating surface is larger than the outer diameter of the third mating surface.

4. The end-face splined hub bearing with protective elements according to claim 2, characterized in that: The outer diameter of the sealing mating surface is the same as the outer diameter of the third mating surface.

5. The end-face splined hub bearing with protective elements according to claim 1, characterized in that: The third mating surface is located radially outside the first mating surface and radially inside the second mating surface. The second mating surface is located between the sealing mating surface and the third mating surface. The outer diameter of the sealing mating surface is larger than the outer diameter of the third mating surface. The protective element includes an axial extension section. The protective element forms a radial pressing contact with the third mating surface through its axial extension section and forms an axial abutment limiting contact with the second mating surface. The radial width of the first mating surface is larger than the radial width of the portion of the outward flange that contacts the first mating surface.

6. The end-face splined hub bearing with protective elements according to claim 5, characterized in that: The protective element also includes a radial extension section connected to the outer side of the end of the axial extension section, and the radial extension section and the second mating surface of the protective element constitute an axial abutment and limiting fit.

7. The end-face splined hub bearing with protective elements according to claim 5, characterized in that: The axial width of the third mating surface is L3, and the axial distance between the first mating surface and the second mating surface is L4, where L3 > 0.5L4.

8. The end-face splined hub bearing with protective elements according to claim 1, characterized in that: The radial width of the outer flange is L5, and the inner ring of the flange includes an annular support portion located inside the small inner ring and integrally connected with the outer flange. The radial width of the annular support portion is L8, where L5 > 1.2L8.

9. The end-face splined hub bearing with protective elements according to claim 1, characterized in that: The outer flange is manufactured by riveting. The first mating surface includes a radially outward flat surface and a radially inward inclined surface. The inclined surface and the outer flange are riveted together. The included angle A between the inclined surface and the radial direction of the bearing is 3~20 degrees. The minimum axial distance between the contact portion of the first mating surface and the outer flange and the lowest point of the tooth root of the spline on the end face of the outer flange is L6. The maximum distance between the contact portion of the first mating surface and the outer flange and the highest point of the tooth tip of the spline on the end face of the outer flange is L7. 0.15 <L6 / L7<0.8。 10. The end-face splined hub bearing with protective elements according to claim 1, characterized in that: The maximum distance between the first mating surface and the end spline of the outward-flared flange is L7, and the radial width of the annular support is L8, 0.

8. <L8 / L7<1.8。

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