High-bearing-capacity hub bearing

Abstract

The invention provides a high-bearing-capacity hub bearing which comprises a flange outer ring, a flange inner ring, a first ball, a second ball, a third ball and a small inner ring, the flange inner ring is provided with a first lower channel, the small inner ring is provided with a second lower channel and a third lower channel, and the first lower channel is communicated with the second lower channel. And three raceways for accommodating the first ball, the second ball and the third ball are respectively formed between the first lower channel, the second lower channel and the flange outer ring, between the second lower channel and the flange outer ring, and between the third lower channel and the flange outer ring. Aiming at the defects in the prior art, the invention provides the high-bearing-capacity hub bearing which ensures high bearing capacity and rigidity and can effectively avoid the problem of noise failure of a product on the premise of ensuring small friction force.

Description

Technical Field

[0001] The present invention relates to the field of hub bearings, and more particularly to a high-load hub bearing. Background Art

[0002] Bearings are important components used for the rotational support of mechanical bodies and are widely applied in various types of mechanical equipment and appliances. As a result, various types of bearings have been derived. Among them, hub bearings are a type of bearing used in various vehicles. Their main function is to bear the weight of the vehicle itself and various loads generated during vehicle driving, and to provide precise guidance for the rotation of the hub, enabling the wheels to rotate smoothly on a specified track. In the prior art, hub bearings often adopt a two-row ball structure. When applied in the electric vehicle hub motor drive system, due to space limitations, the bearing capacity and rigidity are insufficient, which easily leads to early fatigue failure, and the contact stress is too large, which easily leads to impact failure. While a two-row tapered roller structure has the problem of high frictional torque, which affects the cruising range of new energy vehicles. Therefore, it is necessary to further optimize the structure of the hub bearing. Summary of the Invention

[0003] In view of the deficiencies of the prior art, the present invention provides a high-load hub bearing that ensures high bearing capacity and rigidity while ensuring relatively small friction.

[0004] To achieve the above object, the present invention provides a high-load hub bearing, which includes a flange outer ring and a flange inner ring, and further includes a first ball, a second ball, a third ball, and a small inner ring. A first lower raceway is provided on the flange inner ring, and a second lower raceway and a third lower raceway are provided on the small inner ring. Three raceways for accommodating the first ball, the second ball, and the third ball are respectively formed between the first lower raceway, the second lower raceway, and the third lower raceway and the flange outer ring.

[0005] The advantages of adopting the above technical solution are as follows: By arranging the first ball, the second ball, the third ball, and the small inner ring between the flange outer ring and the flange inner ring, a first lower raceway is provided on the flange inner ring, and a second lower raceway and a third lower raceway are provided on the small inner ring. Three raceways for accommodating the first ball, the second ball, and the third ball are respectively formed between the three lower raceways and the flange outer ring. Through the ball and multi-raceway structure, multiple rows of balls can disperse and transmit complex loads such as radial force and axial force, effectively improving the bearing capacity and meeting the requirements of high load and strong rigidity under low friction.

[0006] The present invention can be further configured as follows: a first upper channel, a second upper channel, and a third upper channel are provided on the outer ring of the flange. The first upper channel, the second upper channel, the third upper channel, the first lower channel, the second lower channel, and the third lower channel are all inclined. The first upper channel, the second upper channel, and the third upper channel are respectively arranged opposite to the first lower channel, the second lower channel, and the third lower channel. A connecting step surface is provided between the second lower channel and the third lower channel. The two axial ends of the connecting step surface are respectively connected to the edge of the second lower channel away from the axis and the edge of the third lower channel close to the axis.

[0007] Through further configuration, three upper channels are provided, forming three pairs of raceway structures with the correspondingly inclined lower channels on the inner ring of the flange and the small inner ring, making the balls more conform to the force direction during rolling, effectively reducing friction loss and improving transmission efficiency; the three pairs of relatively arranged inclined channels can reasonably decompose the radial force and axial force, significantly enhancing the bearing's load-bearing capacity for complex loads; the connecting step surface between the second lower channel and the third lower channel is respectively connected to the edge of the second lower channel away from the axis and the edge of the third lower channel close to the axis, making the second ball and the third ball placed in a staggered manner with one higher and one lower, facilitating installation.

[0008] The present invention can be further configured as follows: the diameter of the first ball is 15% to 30% larger than the diameter of the second ball, and the diameter of the third ball is 15 to 25% larger than the diameter of the second ball.

[0009] Through further configuration, the diameter of the first ball is 15% to 30% larger than that of the second ball, and the diameter of the third ball is 15% to 25% larger than that of the second ball. This differential diameter setting enables each ball to perform its own functions during load bearing. The first ball with a larger diameter can mainly bear the larger radial load and disperse the pressure; while the second and third balls, with relatively smaller diameters, can flexibly adapt to complex axial forces and slight radial force changes, reducing the mutual interference between the balls.

[0010] The present invention can be further configured as follows: the pitch diameter of the first ball is 5% to 15% larger than the pitch diameter of the second ball, and the pitch diameter of the third ball is 8% to 15% larger than the pitch diameter of the second ball.

[0011] Through further settings, the pitch diameter of the first ball is 5% to 15% larger than that of the second ball, and the pitch diameter of the third ball is 8% to 15% larger than that of the second ball. The first ball with a larger pitch diameter can bear the main radial load, while the second and third balls focus on dispersing the axial force and assisting in radial load bearing, effectively avoiding local overload. At the same time, the reasonable difference in pitch diameter ensures that the contact stress between each ball and the inclined raceway is evenly distributed, reducing frictional losses. The balls of different sizes cooperate with each other during rotation, reducing operating vibration and enhancing the bearing rigidity, enabling it to maintain efficient and stable operation under complex working conditions.

[0012] The present invention can be further set as follows: the contact angle of the first ball is 5° to 15° larger than the contact angle of the second ball, and the contact angle of the third ball is 5° to 15° larger than the contact angle of the second ball.

[0013] Through further settings, the contact angle of the first ball is 5° to 15° larger than the contact angle of the second ball, and the contact angle of the third ball is also 5° to 15° larger than the contact angle of the second ball. This angle difference makes the division of labor of each ball clear. The first ball with a larger contact angle can efficiently bear a larger radial load and disperse the force along the inclined raceway. The second and third balls with relatively smaller contact angles focus on dealing with the axial force and complex lateral forces, effectively avoiding stress concentration.

[0014] The present invention can be further set as follows: including a first sealing ring and a first retaining ring provided corresponding to the first ball. The first retaining ring is sleeved between the flange of the inner flange and the first lower raceway and forms a radially extending section. The first sealing ring includes a first lip, a second lip, and a third lip arranged in sequence. The first lip and the third lip are in clearance fit with the first retaining ring, and the second lip is in interference fit against the radially extending section.

[0015] Through further settings, by providing a first sealing ring and a first retaining ring corresponding to the first ball, the first retaining ring is sleeved between the flange of the inner flange and the first lower raceway and forms a radially extending section. And the first lip, the second lip, and the third lip arranged in sequence on the first sealing ring. The first lip and the third lip are in clearance fit with the first retaining ring. By making the first lip and the third lip in clearance fit with the retaining ring and using labyrinth seals, on the basis of ensuring a certain sealing effect, the torque is reduced. And the second lip is in interference fit against the radially extending section to form a lateral contact seal, ensuring the sealing effect and also ensuring a relatively small torque.

[0016] The first lip and the third lip are in clearance fit with the retaining ring to reduce contact friction and thus reduce the torque; the second lip is in interference fit against the extending section to form a tight sealing barrier to block the intrusion of impurities.

[0017] The present invention can be further configured as follows: the first retaining ring includes a side extension portion and an upper extension portion. The side extension portion bends and extends toward the direction of the first ball. The upper extension portion is arranged at the end of the side extension portion and extends radially. The first sealing ring includes a first section portion, a second section portion, and a side portion. The first section portion and the upper extension portion are spaced apart and extend in parallel. The side portion is bent and arranged above the first section portion and is spaced apart from the end of the upper extension portion. The second section portion is bent and arranged below the first section portion and extends corresponding to the side extension portion. The first lip portion, the second lip portion, and the third lip portion are successively arranged on the second section portion, and there is a clearance fit between the first lip portion and the side extension portion. Through further configuration, the retaining ring includes a side extension portion and an upper extension portion, and the first sealing ring includes a first section portion, a second section portion, and a side portion. The side extension portion bends and extends toward the direction of the first ball, the upper extension portion is arranged at the end of the side extension portion and extends radially, the first section portion is parallel and spaced apart from the upper extension portion, and there is a clearance fit between the first lip portion and the side extension portion, greatly extending the non-contact labyrinth sealing channel. While reducing friction, the fluid resistance is used to block contaminants, and the gap between the side portion and the end of the upper extension portion further extends the leakage path, strengthening the dust-proof effect without affecting the torque.

[0018] The present invention can be further configured as follows: it includes a second sealing ring and a second retaining ring corresponding to the third ball. The second retaining ring is recessed to form an annular groove. The second sealing ring includes a fourth sealing lip, a fifth sealing lip, and a sixth sealing lip. The fourth sealing lip, the fifth sealing lip, and the sixth sealing lip all extend into the annular groove. The fourth sealing lip and the sixth sealing lip are both in clearance fit with the inner wall of the annular groove, and the fifth sealing lip is press-fitted against the inner wall of the annular groove.

[0019] Through further configuration, by providing a second retaining ring with an annular groove and providing a fourth sealing lip, a fifth sealing lip, and a sixth sealing lip on the second sealing ring, the fourth sealing lip, the fifth sealing lip, and the sixth sealing lip all extend into the annular groove and form a fit with the inner wall of the annular groove. Among them, the fourth sealing lip and the sixth sealing lip are both in clearance fit with the inner wall of the annular groove, and the fifth sealing lip is press-fitted, forming a combination of multiple sealing forms such as labyrinth sealing and contact sealing, so as to achieve low torque and high sealing performance.

[0020] The present invention can be further configured as follows: the second sealing ring includes a socket portion formed to be sleeved on the outer ring of the flange. The second retaining ring includes a first bent section and a second bent section. The first bent section is spaced apart and extends in parallel with the socket portion. The second bent section is sleeved on the inner ring of the flange. The fourth sealing lip and the sixth sealing lip are respectively in clearance fit with the first bent section and the second bent section.

[0021] Through further setting, the first bent section of the second retaining ring is parallel and spaced from the socket part. In combination with the setting that the fourth sealing lip, the fifth sealing lip, and the sixth sealing lip all extend into the annular groove, the length of the non-contact labyrinth channel is extended, and the sealing effect is strengthened. Moreover, the fourth sealing lip and the sixth sealing lip are respectively arranged on both sides of the fifth sealing lip and are in clearance fit with the two bent sections respectively. While maintaining a micro-gap to reduce friction, the sealing effect is enhanced through a multi-stage barrier effect.

[0022] The present invention can be further set as follows: a spline end is arranged at the position corresponding to the small inner ring on the inner circle of the flange.

[0023] Through further setting, the spline end forms a tight circumferential fixation with the mating part through a tooth-shaped structure. Compared with the traditional smooth connection method, it can withstand a greater torque transmission, avoid wear and frictional loss caused by relative sliding. At the same time, the high-precision positioning characteristic of the spline fit ensures the coaxiality of the inner circle of the flange and the small inner circle, reduces the off-axis load phenomenon during operation, and further improves the overall rigidity of the bearing. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 is a schematic structural diagram of an embodiment of the present invention; Figure 2 is an enlarged view of part a in the embodiment of the present invention; Figure 1 Figure 3 Figure 1 is an enlarged view of part b in the embodiment of the present invention; Figure 4 Figure 5 is a perspective view of the inner circle of the flange in the embodiment of the present invention; Figure 5 is a schematic structural diagram of the spline end in the embodiment of the present invention; Wherein: outer flange 1; first upper groove 11; second upper groove 12; third upper groove 13; inner flange 2; first lower groove 21; spline end 22; first ball 31; second ball 32; third ball 33; small inner ring 4; second lower groove 41; third lower groove 42; connecting step surface 43; first sealing ring 5; first lip 51; second lip 52; third lip 53; first section 54; second section 55; side part 56; first retaining ring 6; radially extending section 61; side extending part 62; upper extending part 63; second sealing ring 7; fourth sealing lip 71; fifth sealing lip 72; sixth sealing lip 73; socket part 74; second retaining ring 8; annular groove 81; first bent section 82; second bent section 83. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0025] An embodiment of a high-load hub bearing of the present invention is as Figures 1-5As shown in the figure, it includes a flange outer ring 1 and a flange inner ring 2, and also includes a first ball 31, a second ball 32, a third ball 33 and a small inner ring 4. A first lower raceway 21 is provided on the flange inner ring 2, and a second lower raceway 41 and a third lower raceway 42 are provided on the small inner ring 4. Three raceways for accommodating the first ball 31, the second ball 32 and the third ball 33 are respectively formed between the first lower raceway 21, the second lower raceway 41, the third lower raceway 42 and the flange outer ring 1.

[0026] A first upper raceway 11, a second upper raceway 12 and a third upper raceway 13 are provided on the flange outer ring 1. The first upper raceway 11, the second upper raceway 12, the third upper raceway 13, the first lower raceway 21, the second lower raceway 41 and the third lower raceway 42 are all inclined. The first upper raceway 11, the second upper raceway 12, the third upper raceway 13 are respectively arranged opposite to the first lower raceway 21, the second lower raceway 41 and the third lower raceway 42. A connecting step surface 43 is provided between the second lower raceway 41 and the third lower raceway 42. The two axial ends of the connecting step surface 43 are respectively connected to the edge far from the axis of the second lower raceway 41 and the edge close to the axis of the third lower raceway 42.

[0027] The diameter of the first ball 31 is 15% to 30% larger than the diameter of the second ball 32, and the diameter of the third ball 33 is 15 to 25% larger than the diameter of the second ball. In this embodiment, the diameter of the first ball 31 is φ11.906mm; the diameter of the second ball 32 is φ9.525mm; the diameter of the third ball 33 is φ11.1125mm.

[0028] The pitch diameter of the first ball 31 is 5% to 15% larger than the pitch diameter of the second ball 32, and the pitch diameter of the third ball 33 is 8% to 15% larger than the pitch diameter of the second ball 32. In this example, the ratio of the pitch diameters of the first ball 31 and the second ball 32 is 1.06; the ratio of the pitch diameters of the third ball 33 and the second ball 32 is 1.09.

[0029] The contact angle of the first ball 31 is 5° to 15° larger than the contact angle of the second ball 32, and the contact angle of the third ball 33 is 5° to 15° larger than the contact angle of the second ball 32, as shown by a1, a2 and a3 in the appendix. Figure 1 in the appendix.

[0030] It further includes a first sealing ring 5 and a first retaining ring 6 provided corresponding to the first ball 31. The first retaining ring 6 is sleeved between the flange of the inner flange 2 and the first lower channel 21 and forms a radially extending section 61. The first sealing ring 5 includes a first lip 51, a second lip 52, and a third lip 53 arranged in sequence. The first lip 51 and the third lip 53 are in clearance fit with the first retaining ring 6, and the second lip 52 is in interference fit against the radially extending section 61.

[0031] The first retaining ring 6 includes a side extending portion 62 and an upper extending portion 63. The side extending portion 62 bends and extends towards the first ball 31. The upper extending portion 63 is arranged at the end of the side extending portion 62 and extends radially. The first sealing ring 5 includes a first section 54, a second section 55, and a side section 56. The first section 54 and the upper extending portion 63 are spaced apart and extend in parallel. The side section 56 is bent and arranged above the first section 54 and is spaced from the end of the upper extending portion 63. The second section 55 is bent and arranged below the first section 54 and extends corresponding to the side extending portion 62. The first lip 51, the second lip 52, and the third lip 53 are arranged in sequence on the second section 55, and the first lip 51 is in clearance fit with the side extending portion 62. It further includes a second sealing ring 7 and a second retaining ring 8 provided corresponding to the third ball 33. The second retaining ring 8 is recessed to form an annular groove 81. The second sealing ring 7 includes a fourth sealing lip 71, a fifth sealing lip 72, and a sixth sealing lip 73. The fourth sealing lip 71, the fifth sealing lip 72, and the sixth sealing lip 73 all extend into the annular groove 81. The fourth sealing lip 71 and the sixth sealing lip 73 are in clearance fit with the inner wall of the annular groove 81, and the fifth sealing lip 72 is in interference fit against the inner wall of the annular groove 81.

[0032] The second sealing ring 7 includes a socket portion 74 that is sleeved and fastened to the outer flange 1. The second retaining ring 8 includes a first bent section 82 and a second bent section 83. The first bent section 82 is spaced from the socket portion 74 and extends in parallel. The second bent section 83 is sleeved on the inner flange 2. The fourth sealing lip 71 and the sixth sealing lip 73 are in clearance fit with the first bent section 82 and the second bent section 83 respectively.

[0033] The inner flange 2 is provided with a spline end 22 corresponding to the small inner ring 4. In this embodiment, the included angle of the end face tooth grooves of the spline end is 4°47'.

[0034] The above examples are only one of the preferred specific examples of the present invention. The ordinary variations and substitutions made by those skilled in the art within the scope of the technical solution of the present invention are included in the protection scope of the present invention.

Claims

1. A high-load hub bearing, comprising a flange outer ring and a flange inner ring, characterized in that: It includes a first ball, a second ball, a third ball and a small inner ring. A first lower raceway is provided on the flange inner ring, and a second lower raceway and a third lower raceway are provided on the small inner ring. Three raceways for accommodating the first ball, the second ball and the third ball are respectively formed between the first lower raceway, the second lower raceway and the third lower raceway and the flange outer ring.

2. The high-load hub bearing according to claim 1, characterized in that: A first upper raceway, a second upper raceway and a third upper raceway are provided on the flange outer ring. The first upper raceway, the second upper raceway, the third upper raceway, the first lower raceway, the second lower raceway and the third lower raceway are all inclined. The first upper raceway, the second upper raceway and the third upper raceway are respectively arranged opposite to the first lower raceway, the second lower raceway and the third lower raceway. A connecting step surface is provided between the second lower raceway and the third lower raceway. Axial ends of the connecting step surface are respectively connected to the edge far from the axis of the second lower raceway and the edge close to the axis of the third lower raceway.

3. The high-load hub bearing according to claim 1 or 2, characterized in that: The diameter of the first ball is 15% to 30% larger than the diameter of the second ball, and the diameter of the third ball is 15 to 25% larger than the diameter of the second ball.

4. The high-load hub bearing according to claim 1 or 2, characterized in that: The pitch diameter of the first ball is 5% to 15% larger than the pitch diameter of the second ball, and the pitch diameter of the third ball is 8% to 15% larger than the pitch diameter of the second ball.

5. The high-load hub bearing according to claim 2, characterized in that: The contact angle of the first ball is 5° to 15° larger than the contact angle of the second ball, and the contact angle of the third ball is 5° to 15° larger than the contact angle of the second ball.

6. The high-load hub bearing according to claim 1, characterized in that: It includes a first sealing ring and a first retaining ring provided corresponding to the first ball. The first retaining ring is sleeved between the flange of the flange inner ring and the first lower raceway and forms a radially extending section. The first sealing ring includes a first lip, a second lip and a third lip arranged in sequence. The first lip and the third lip are both in clearance fit with the first retaining ring, and the second lip is in interference fit with the radially extending section.

7. The high-load hub bearing according to claim 6, wherein: The first retaining ring includes a side extending portion and an upper extending portion. The side extending portion bends and extends towards the first ball. The upper extending portion is arranged at the end of the side extending portion and extends radially. The first sealing ring includes a first section portion, a second section portion and a side portion. The first section portion and the upper extending portion are spaced and extend in parallel. The side portion is bent above the first section portion and is spaced from the end of the upper extending portion. The second section portion is bent below the first section portion and extends corresponding to the side extending portion. The first lip, the second lip and the third lip are arranged in sequence on the second section portion, and the first lip is in clearance fit with the side extending portion.

8. The high-load hub bearing according to claim 1, wherein: It includes a second sealing ring and a second retaining ring provided corresponding to the third ball. The second retaining ring is recessed to form an annular groove. The second sealing ring includes a fourth sealing lip, a fifth sealing lip and a sixth sealing lip. The fourth sealing lip, the fifth sealing lip and the sixth sealing lip all extend into the annular groove. The fourth sealing lip and the sixth sealing lip are both in clearance fit with the inner wall of the annular groove, and the fifth sealing lip is in interference fit with the inner wall of the annular groove.

9. The high-load hub bearing according to claim 8, characterized in that: The second sealing ring described includes a socket part formed to be sleeved on the outer ring of the flange. The second retaining ring includes a first bending section and a second bending section. The first bending section extends at intervals and in parallel with the socket part. The second bending section is sleeved on the inner ring of the flange. The fourth sealing lip and the sixth sealing lip are in clearance fit with the first bending section and the second bending section respectively.

10. The high-load hub bearing according to claim 1 or 2 or 5, characterized in that: A spline end is provided at the position corresponding to the small inner ring on the inner ring of the flange.

Images