End face spline hub bearing

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 arranged on the outer side of the flange inner ring in a sleeving mode, 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 is provided with the protection element, foreign matter can be prevented from entering the bearing, the structure is simple, and machining, manufacturing and assembling are convenient.

Description

Technical Field

[0001] The invention relates to an end face spline hub bearing. Background Art

[0002] The face spline wheel hub bearing is a key component of the automobile wheel hub. The structure of the existing face spline wheel hub bearing usually includes a flange inner ring, a small inner ring, and an outer ring, wherein the small inner ring and the flange inner ring are fixedly connected by riveting, and the outer ring is arranged on the radial outer side of the flange inner ring and the small inner ring. Two groups of rollers are arranged axially between the outer ring and the inner ring, and two first raceways for rolling with the two groups of rollers are arranged on the inner side of the outer ring, and two second raceways for rolling with the two groups of rollers are arranged on the outer side of the flange inner ring and the small inner ring, respectively. The end of the flange inner ring has an outer flange formed by riveting, which is used for riveting and fixing the small inner ring. A toothed face spline is arranged on the axial end face of the outer flange, which is used for transmission connection with the transmission parts of the vehicle to transmit torque.

[0003] The outer flange of the face spline hub bearing is usually located axially outside the end face of the small inner ring and is exposed to external environmental conditions, such as muddy water, sand, gravel, iron filings, etc. This harsh external environment will reduce the performance of the riveted flange, thereby affecting the service life of the bearing. For example, exposure to muddy water environment usually causes rust on the riveted flange, which may cause changes in raceway stress. In addition, similar problems also exist for face splines. Hard particles such as sand, gravel, and iron filings will affect the meshing of the face teeth, resulting in abnormal conditions such as reduced transmission efficiency.

[0004] In the current prior art, in order to solve the above-mentioned problem, an annular boss is usually processed on the axial end of the small inner ring. The boss is located around the radial outer side of the outer flange and has a certain blocking effect on foreign matter such as mud, water, sand, gravel, and iron filings. However, the provision of the boss also makes the structure of the small inner ring complicated, which is not conducive to processing and manufacturing. Summary of the invention

[0005] In order to overcome the defects of the above-mentioned prior art, the present invention provides an end spline hub bearing with a protective element, which can prevent external mud, water, sand, gravel, iron filings and other foreign matter from entering the outer flange and the meshing part of the end spline, and has a simple structure and is easy to process, manufacture and assemble.

[0006] The end face spline wheel hub bearing of the present invention 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 comprises a retaining wall which cooperates with one axial end of the small inner ring to limit the position, one end of the flange inner ring comprises an outer flange formed by riveting, the outer flange cooperates with the other axial end of the small inner ring to limit the position, a rolling assembly is arranged between the flange inner ring, the small inner ring and the outer ring, a sealing assembly is arranged between the small inner ring and the outer ring, the rolling assembly comprises at least two rows of steel balls arranged axially, the outer side of the small inner ring comprises a sealing mating surface which cooperates with the sealing assembly, an end face spline is arranged on the axial outer end of the outer flange, a cylindrical protective element is fixedly installed on the axial outer end of the small inner ring, the protective element cover is arranged on 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 located on the axial side, a second mating surface and a third mating surface located on the radial outside, 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 and pressed together, the second mating surface and the protective element constitute an axial abutment limit fit, the second mating surface can be used as an axial limit of the protective element when the protective element is installed, the third mating surface and the inner side of the protective element constitute a radial compression contact fit, the third mating surface is used to connect the protective element, the third mating surface can effectively surround the outer flange and the meshing part of the end face tooth portion, and form a static seal without causing problems such as wear, an annular gap is formed between the radial outer side of the outer flange and the protective element, and the inner and outer circumferential walls of the annular gap are respectively provided by the outer flange and the protective element.

[0007] In one of the preferred schemes, the second mating surface is respectively 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 radial extension section extending radially outward and an axial extension section extending axially, the axial extension section is connected to the radial outside of the radial extension section, the protective element forms an axial abutment and limiting fit through its radial extension section and the second mating surface, the protective element forms a radial compression contact fit through its axial extension section and the third mating surface, and the radial width of the second mating surface is greater than the radial width of the radial extension section.

[0008] Furthermore, the outer diameter of the sealing mating surface is larger than the outer diameter of the third mating surface, so that the protection element and the sealing assembly of the bearing are misaligned and will not interfere with the bearing seal. A third mating surface with an outer diameter smaller than the sealing mating surface can be formed by appropriately grinding the axial outer ring of the small inner ring to form a smaller groove, and the grinding amount of the axial outer end of the small inner ring is small, which can increase the grinding efficiency.

[0009] Furthermore, the outer diameter of the sealing mating surface is the same as the outer diameter of the third mating surface, and the third mating surface does not need to be additionally ground to reduce its outer diameter, thereby reducing the number of manufacturing steps.

[0010] In another preferred embodiment, the third mating surface is respectively located on the radial outside of the first mating surface and the radial inside of 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 compression contact fit with the third mating surface through its axial extension section, and an axial abutment limit fit with the second mating surface, and the radial width of the first mating surface is larger than the radial width of the contact portion of the outer flange with the first mating surface.

[0011] In the above preferred solution, a groove can be formed at the outer side of the axial outer end of the small inner ring, and the second and third mating surfaces respectively constitute two adjacent side walls of the groove. The radial depth of the groove is substantially the same as the radial width of the second mating surface, and the groove is formed by grinding the axial outer end of the small inner ring. Compared with the previous preferred solution, the design structure of the protection element can be simpler, less material is used, and the overall structure is more compact. In addition, the design of the groove can reduce the excessive hoop stress (i.e., hoop stress) generated on the outer diameter of the small inner ring due to the interference fit and riveting of the small inner ring and the flange inner ring, and avoid problems such as cracks.

[0012] Furthermore, the protection 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 protection element and the second matching surface constitute an axial abutment limiting fit.

[0013] In the above solution, the protection element can form a straight seal with the third mating surface when it only includes the axial extension section, and can form an L-shaped seal with the second mating surface when it also includes the radial extension section. That is, the second mating surface can not only be used to limit the position of the protection element when it is axially installed, but also cooperate to perform sealing.

[0014] Furthermore, the axial width of the third mating surface is L3, the axial distance between the first mating surface and the second mating surface is L4, and L3>0.5L4, thereby ensuring sufficient pull-out force to prevent the protective element from falling off the small 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 on the inner side of the small inner ring and integrally connected to the outer flange, and the radial width of the annular support portion is L8, L5>1.2L8, thereby ensuring the meshing width of the teeth of the end face spline and improving the transmitted torque.

[0016] Further, the turned-out edge is processed by spin riveting. The first mating surface includes a flat surface radially outward and an inclined surface radially inward, and 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 a difference in the end face areas at both axial ends of the small inner ring, causing uneven wear 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 to improve the processing accuracy of the splines on the upper end face of the riveted and turned-out edge and improve 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] Further, 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] Further, 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 splines of the turned-out edge is L6, and the maximum distance between the highest point of the tooth top of the end face splines 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 and 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] Further, 0.8 < L8 / L7 < 1.8 to ensure sufficient material for tooth forming.

[0020] The beneficial effects of the present invention are as follows: By providing a cylindrical protective element, foreign matters such as mud, sand, and iron filings can be effectively blocked from entering the meshing part of the turned-out edge and the end face splines. The protective 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. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 Partial cross-section of Embodiment 1 of the present invention Figure 1 ; Figure 2 Partial cross-section of Embodiment 1 of the present invention Figure 2 ; Figure 3 Partial cross-section of Embodiment 1 of the present invention Figure 3 ; Figure 4 Partial cross-sectional view of Embodiment 2 of the present invention; Figure 5 Partial cross-sectional view of Embodiment 3 of the present invention; Figure 6It is a partial cross-sectional view of embodiment 4 of the present invention. DETAILED DESCRIPTION

[0022] The basic part of the end spline hub bearing of each embodiment of the present invention is as follows: Figures 1 to 6 As shown, it includes a flange inner ring 1, a small inner ring 2, and an outer ring 3. The small inner ring 2 is sleeved on the outer side of the flange inner ring 1. The outer side of the flange inner ring 1 includes a retaining wall 11 that cooperates with one axial end of the small inner ring 2 to limit the position. One end of the flange inner ring 1 includes an outer flange 12 formed by riveting. The outer flange 12 cooperates with the other axial end of the small inner ring 2 to limit the position. A rolling assembly is arranged between the flange inner ring 1, the small inner ring 2 and the outer ring 3. The rolling assembly includes two rows of steel balls and a retaining frame that cooperates with the steel balls. The outer sides of the flange inner ring 1 and the small inner ring 2 are respectively provided with raceways that cooperate with the two rows of steel balls. A sealing assembly 4 is arranged 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 cooperates with the sealing assembly 4. An end face spline 121 is arranged on the axial outer end of the outer flange 12. The small inner ring 2 The axial outer end of the small inner ring 2 is fixedly mounted with a cylindrical protective element 5, which is covered on the outer side of the outer flange 12 and at least covers the meshing portion between the end face spline 121 and the transmission component. The axial outer end of the small inner ring 2 includes a first mating surface 22, a second mating surface 23 and a third mating surface 24 located on the radial outer side, the first mating surface 22 is located on the radial inner side of the second mating surface 23, the first mating surface 22 and the outer flange 12 are riveted and pressed, the second mating surface 23 and the protective element 5 form an axial abutment and limiting fit, and the third mating surface 24 and the inner side of the protective element 5 form a radial compression contact fit, and an annular gap 6 is formed between the radial outer side of the outer flange 12 and the protective element 5, and 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 processed by a riveting process.

[0023] In Example 1 and Example 2, respectively Figures 1 to 3 and Figure 4 As shown, the third mating surface 24 is respectively located on the radial outer side of the first mating surface 22 and the radial inner side of 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 greater than the outer diameter of the third mating surface 24, and there is 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, and the protective element 5 forms a radial compression contact fit with the third mating surface 24 and an axial abutment limit fit with the second mating surface 23 through its axial extension section 51. The radial width L1 of the first mating surface 22 is greater than the radial width L2 of the contact portion of the outer flange 12 with the first mating surface 22. Figure 2 shown.

[0024] In such Figure 5 In the illustrated embodiment 3, unlike the embodiment 1, the protection element 5 further includes a radial extension section 52 connected to the outer side of the end of the axial extension section 51, and the radial extension section 52 of the protection element 5 and the second mating surface 23 form an axial abutment limit fit.

[0025] In Example 3 and Example 4, respectively Figure 5 , 6 As shown, the second mating surface 23 is respectively located on the radial outside of the first mating surface 22 and the radial inside of the third mating surface 24, the axial inner end of the protection element 5 includes an L-shaped connection structure, the connection structure includes a radial extension section 52 extending radially outward and an axial extension section 51 extending axially, the axial extension section 51 is connected to the radial outside of the radial extension section 52, the protection element 5 forms an axial abutment limit fit with the second mating surface 23 through its radial extension section 52, the protection element 5 forms a radial compression contact fit with the third mating surface 24 through its axial extension section 51, the radial width of the second mating surface 23 is greater than the radial width of the radial extension section 52, the first mating surface 22 includes a radially outer flat surface and a radially inner inclined surface, the inclined surface is riveted to the outer flange 12, and the flat surface is arranged at a position corresponding to the annular gap 6.

[0026] In Example 3, 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 .

[0027] In Example 4, 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 .

[0028] In addition, in each embodiment of the present invention, Figure 3 Taking the embodiment 1 shown as an example, the axial width of the third mating surface 24 is L3, which is also the axial width of the contact portion between the third mating surface 24 and the protective element 5. The axial spacing between the first mating surface 22 and the second mating surface 23 is L4, and L3>0.5L4.

[0029] 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 on the inner side of the small inner ring 2 and integrally connected to the outer flange 12. The radial width of the annular support portion 13 is L8, and L5>1.2L8.

[0030] The angle A between the inclined surface and the radial direction of the bearing is 3 to 20 degrees.

[0031] The following is the test data record of riveting force and riveting deformation at different angles of angle A: Angle A 0° (i.e. flat surface) 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 In the above test data, when the angle A is 0°, the riveting force is a, and the riveting deformation is b as the benchmark, the ratio of the riveting force and the riveting deformation at other angles is respectively illustrated. Among them, the riveting force refers to the force applied to the outer flange, and the riveting deformation refers to the radial thickness change of the small inner ring. When the riveting deformation is large, the annular stress on the small inner ring is greater and cracks are more likely to occur. Cracks will destroy the structural integrity of the bearing components, reduce its load-bearing capacity, and reduce its ability to resist the erosion of sediment and salt water.

[0032] The above test data show that when the angle of the inclined surface is between 5 and 20 degrees, it can withstand greater riveting force and have smaller riveting deformation than 0 degrees.

[0033] The minimum axial distance between the contact portion between the first mating surface 22 and the outer flange and the lowest point of the tooth bottom of the end face spline of the outer flange 12 is L6, and the maximum distance between the highest point of the tooth top of the end face spline of the contact portion between the first mating surface 22 and the outer flange 12 is L7, 0.15 <L6 / L7<0.8。

[0034] In addition, 0.8 <L8 / L7<1.8。

[0035] The above embodiment is only one of the preferred specific embodiments of the present invention. Common changes and substitutions made by those skilled in the art within the scope of the technical solution of the present invention are all included in the protection scope of the present invention.

Claims

1. A face spline wheel hub bearing, comprising a flange inner ring, a small inner ring, and an outer ring, wherein the small inner ring is sleeved on the outer side of the flange inner ring, the flange inner ring comprises a retaining wall which cooperates with one axial end of the small inner ring to limit the position, one end of the flange inner ring comprises an outer flange formed by riveting, the outer flange cooperates with the other axial end of the small inner ring to limit the position, a rolling assembly is arranged between the flange inner ring, the small inner ring and the outer ring, the rolling assembly comprises at least two rows of steel balls arranged axially, a sealing assembly is arranged between the small inner ring and the outer ring, the outer side of the small inner ring comprises a sealing mating surface which cooperates with the sealing assembly, and an end face spline is arranged on the axial outer end of the outer flange, characterized in that: A cylindrical protective element is fixedly installed on the axial outer end of the small inner ring, and the protective element cover is arranged on 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 located on the axial side, 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 and pressed, the second mating surface and the protective element constitute an axial abutment and limiting fit, the third mating surface and the inner side of the protective element constitute a radial compression contact fit, and an annular gap is formed between the radial outer side of the outer flange and the protective element, and the inner and outer circumferential walls of the annular gap are respectively provided by the outer flange and the protective element.

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

3. The end face spline hub bearing according to claim 2, characterized in that: The outer diameter of the sealing mating surface is greater than the outer diameter of the third mating surface.

4. The end face spline hub bearing 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 spline hub bearing according to claim 1, characterized in that: The third mating surface is respectively located on the radial outside of the first mating surface and on the radial inside of 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 compression contact fit with the third mating surface and an axial abutment limit fit with the second mating surface through its axial extension section. The radial width of the first mating surface is larger than the radial width of the contact portion of the outer flange with the first mating surface.

6. The end face spline hub bearing according to claim 5, characterized in that: The protection element further 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 protection element and the second matching surface form an axial abutment limiting fit.

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

8. The face spline hub bearing 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 on the inner side of the small inner ring and integrally connected to the outer flange, and the radial width of the annular support portion is L8, and L5>1.2L8.

9. The face spline hub bearing according to claim 1, characterized in that: The outer flange is processed by a rotary riveting process, the first mating surface includes a flat surface radially outward and an inclined surface radially inward, and the inclined surface is riveted with the outer flange; the angle A between the inclined surface and the radial direction of the bearing is 3 to 20 degrees; the minimum axial distance between the contact portion between the first mating surface and the outer flange and the lowest point of the tooth bottom of the end face spline of the outer flange is L6, and the maximum distance between the contact portion between the first mating surface and the outer flange and the highest point of the tooth top of the end face spline of the outer flange is L7, 0.15 <L6 / L7<0.8。 10. The face spline hub bearing according to claim 1, characterized in that: The maximum distance between the first mating surface and the end face spline of the outer flange is L7, the radial width of the annular support portion is L8, 0.8 <L8 / L7<1.8。

Images