Hub bearing

Abstract

The utility model provides a kind of hub bearing, including flange outer ring and flange inner ring, further including several ball rollers and several tapered rollers, the first raceway and two second raceways are formed between the flange outer ring and flange inner ring, the first raceway is for tapered roller accommodation, two the second raceway is for ball roller accommodation, two second raceways are inclined arrangement towards axis direction, and it is oppositely arranged with the first raceway. In view of the deficiency of prior art, the utility model provides a kind of hub bearing, which realizes larger bearing capacity, lower torque level, and better maintains low energy consumption level.

Description

Technical Field

[0001] This utility model relates to the field of bearings, and in particular to a wheel hub bearing. Background Technology

[0002] Wheel bearings are a key component of automobiles, primarily used to connect tires, brake discs, and steering knuckles, serving functions such as load-bearing and guiding wheel rotation. For mid-to-large-sized pure electric SUVs / MPVs, rugged off-road SUVs, pickup trucks, and light trucks, the increased weight and complex road conditions of these vehicles place higher demands on the load-bearing capacity, impact resistance, and energy efficiency of wheel bearings. Existing wheel bearing technologies are mainly divided into two categories: one is a two-row ball bearing structure. While this structure can achieve lower operating torque and meets the vehicle's energy consumption control requirements to some extent, it is limited by the contact of the balls... One type is the contact bearing, which has weak radial and axial load-bearing capacity. When dealing with complex road conditions or heavy loads, it is prone to problems such as raceway impact indentation and premature bearing failure. Another type is the two-row tapered structure. With the line contact characteristics of tapered rollers, this structure has strong load-bearing capacity and impact resistance, and can be adapted to heavy loads and complex road conditions. However, the motion characteristics of tapered rollers lead to a significant increase in running torque, which directly increases the energy consumption of the vehicle. This is contrary to the current design goals of low emissions and high range of new energy vehicles. Therefore, it is necessary to optimize the load-bearing capacity of the wheel hub bearing and reduce the bearing torque to maintain a low energy consumption level as much as possible. Utility Model Content

[0003] To address the shortcomings of existing technologies, this invention provides a wheel hub bearing that achieves greater load-bearing capacity, lower torque levels, and better maintains low energy consumption.

[0004] To achieve the above objectives, this utility model provides a wheel hub bearing, including an outer flange ring and an inner flange ring. The inner flange ring includes a flange portion, as well as a plurality of ball rollers and a plurality of tapered rollers. A first raceway and two second raceways are formed between the outer flange ring and the inner flange ring. The first raceway accommodates the tapered rollers, and the two second raceways accommodate the ball rollers. The two second raceways are arranged obliquely toward the axial direction and are opposite to the first raceway.

[0005] The advantages of the above technical solution are: by forming a first raceway and two second raceways between the outer ring and the inner ring of the flange, and filling the first raceway and the second raceway with tapered rollers and ball rollers respectively, a structure of two rows of ball rollers and one row of tapered rollers is formed. The tapered rollers improve the radial and axial load-bearing capacity and impact resistance of the bearing, while the two rows of ball rollers maintain a low operating torque while ensuring a certain load-bearing capacity, and avoid the defects of excessive torque and high energy consumption of the two-row tapered structure, thus achieving a balance between high load-bearing capacity and low energy consumption.

[0006] The present invention can be further configured such that: a first collar is provided on the inner ring of the flange, the first collar is stepped and has a first groove and a second groove, the first collar is fitted on the inner ring of the flange, and the two second raceways are respectively formed by the first groove and the second groove and the outer ring of the flange.

[0007] By further configuring the first and second grooves onto the first ring, the first ring can be formed independently, allowing for better machining of the first and second grooves and effectively reducing the machining difficulty of complex structures.

[0008] The present invention can be further configured such that: one of the second raceways near the axis is smaller than the other second raceway, and the ball rollers on the one second raceway are also smaller than the ball rollers on the other second raceway.

[0009] By further refining the design, the second raceway and its corresponding ball rollers, which are closer to the axis, are made smaller than the outer second raceway and their corresponding ball rollers, thus better adapting to the limited space on the inner side and avoiding structural interference with components such as the flange inner ring and the first raceway.

[0010] The present invention can be further configured such that: the inner ring of the flange is stepped at one end near the flange portion and has a third groove and a fourth groove; the two second raceways are respectively formed by the third groove and the fourth groove and the outer ring of the flange; a second collar is fitted at the other end of the inner ring of the flange; and the first raceway is formed by the second collar and the outer ring of the flange.

[0011] By further designing the second raceway, which forms the first raceway with the outer ring, it becomes an independent component, offering greater advantages in scenarios where tapered rollers require adjustment. Furthermore, compared to the first raceway, the structural dimensions of the second raceway can be directly manufactured using existing equipment.

[0012] The present invention can be further configured as follows: a first sealing ring is fitted at one end of the flange portion near the flange inner ring of the flange outer ring; the flange inner ring is provided with a stepped surface near its flange portion; the first sealing ring includes a first lip and several second lips; the first lip abuts radially against the stepped surface; the second lips abut axially against the flange portion; and the several second lips are arranged radially at intervals.

[0013] By further designing the system, multiple radially spaced second lips abut against the flange axially, forming multiple axial sealing barriers. Even if one lip fails due to wear or deformation, the remaining lips can still maintain a sealing effect, significantly reducing the risk of bearing damage caused by the failure of a single sealing structure. In addition, a first lip is provided, which abuts tightly against the stepped surface of the inner ring of the flange radially, better blocking external impurities and inhibiting the radial leakage of internal grease. Furthermore, the first and second lips adopt axial and radial abutment fits respectively, resulting in stronger stability.

[0014] The present invention can be further configured such that: the first sealing ring includes a skeleton, the skeleton is bent to form a first section and a second section, the first section is sleeved on the outer diameter of the flange outer ring, and the second section abuts against the axial end of the flange outer ring.

[0015] With further design, the first section is fitted onto the outer diameter of the flange outer ring, providing radial positioning for the sealing ring through a tight fit. Since it is fitted onto the outer diameter and occupies limited internal space, it is better suited for this type of bearing. The second section abuts against the axial end of the flange outer ring, forming an axial limit to prevent axial movement.

[0016] The present invention can be further configured such that: a second sealing ring is fitted at the other end of the outer ring of the flange, and a retaining ring is provided on the inner ring of the flange corresponding to the position of the second sealing ring. The retaining ring includes a third section and a fourth section. The third section is fitted onto the inner ring of the flange, and the fourth section is bent and extended toward the outer ring of the flange. The second sealing ring includes a plurality of third sealing lips, which respectively abut against the third section and the fourth section.

[0017] By further configuring the fourth section of the retaining ring to provide shielding and ensure basic sealing, several third sealing lips are then provided on the second sealing ring. These third sealing lips abut against the third and fourth sections respectively, effectively preventing external impurities from radially intruding along the inner ring of the flange while preventing internal grease from radially leaking, thus enhancing the sealing effect.

[0018] The present invention can be further configured such that: the second sealing ring includes a fourth sealing lip, the retaining ring includes a fifth segment located at the end of the fourth segment, the fifth segment bends and extends toward the direction of the ball roller, and the fourth sealing lip abuts against the fifth segment.

[0019] By further modifying the design, a fourth sealing lip is added to the second sealing ring, and a fifth section is provided at the end of the fourth section of the retaining ring, which bends and extends toward the direction of the ball bearing. The fourth sealing lip abuts against the fifth section, thus adding an extra seal on the basis of the original sealing structure to ensure the sealing effect. Attached Figure Description

[0020] Figure 1 This is a schematic diagram of the structure of Embodiment 1 of the present utility model; Figure 2 This is Embodiment 1 of the present utility model. Figure 1 An enlarged view of part a; Figure 3 This is Embodiment 1 of the present utility model. Figure 1 Enlarged view of section b; Figure 4 This is a schematic diagram of the structure of Embodiment 2 of the present invention; Wherein: flange outer ring 1; flange inner ring 2; flange part 21; first collar 22; first groove part 221; second groove part 222; third groove part 23; fourth groove part 24; second collar 25; stepped surface 26; ball roller 3; tapered roller 4; first raceway 5; second raceway 6; first sealing ring 7; first lip part 71; second lip part 72; skeleton 73; first section part 731; second section part 732; second sealing ring 8; third sealing lip 81; fourth sealing lip 82; retaining ring 9; third section part 91; fourth section part 92; fifth section part 93. Detailed Implementation

[0021] An embodiment of the hub bearing of this utility model is as follows: Figure 1-3 As shown: It includes an outer flange ring 1 and an inner flange ring 2. The inner flange ring 2 includes a flange portion 21, which includes a plurality of ball rollers 3 and a plurality of tapered rollers 4. A first raceway 5 and two second raceways 6 are formed between the outer flange ring 1 and the inner flange ring 2. The first raceway 5 is used to accommodate the tapered rollers, and the two second raceways 6 are used to accommodate the ball rollers. The two second raceways 6 are arranged obliquely towards the axial direction and are opposite to the first raceway 5.

[0022] The flange inner ring 2 is provided with a first collar 22, which is stepped and has a first groove 221 and a second groove 222. The first collar 22 is fitted onto the flange inner ring 2, and the two second raceways 6 are respectively formed by the first groove 221 and the second groove 222 and the flange outer ring 1.

[0023] One of the second raceways 6, which is closer to the axis, is smaller than the other second raceway 6, and the ball rollers on the one second raceway 6 are also smaller than the ball rollers on the other second raceway 6, so that the ball rollers can be arranged in an inclined manner, which corresponds exactly to the conical rollers.

[0024] A first sealing ring 7 is fitted at one end of the flange portion 21 of the outer ring 1 of the flange near the inner ring 2 of the flange. The inner ring 2 of the flange has a stepped surface 26 near its flange portion 21. The first sealing ring 7 includes a first lip 71 and a plurality of second lips 72. The first lip 71 abuts radially against the stepped surface 26, and the second lips 72 abut axially against the flange portion 21. The plurality of second lips 72 are arranged radially at intervals.

[0025] The first sealing ring 7 includes a skeleton 73, which is bent to form a first section 731 and a second section 732. The first section 731 is fitted onto the outer diameter of the flange outer ring 1, and the second section 732 abuts against the axial end of the flange outer ring 1.

[0026] A second sealing ring 8 is fitted at the other end of the outer ring 1 of the flange. A retaining ring 9 is provided on the inner ring 2 of the flange corresponding to the position of the second sealing ring 8. The retaining ring 9 includes a third section 91 and a fourth section 92. The third section 91 is fitted onto the inner ring 2 of the flange, and the fourth section 92 is bent and extended toward the outer ring 1 of the flange. The second sealing ring 8 includes a plurality of third sealing lips 81, which abut against the third section 91 and the fourth section 92 respectively.

[0027] The second sealing ring 8 includes a fourth sealing lip 82, and the retaining ring 9 includes a fifth section 93 located at the end of the fourth section 92. The fifth section 93 is bent and extends toward the ball roller, and the fourth sealing lip 82 abuts against the fifth section.

[0028] Embodiment 2 of the present invention is as follows: Figure 4 As shown, the difference from Embodiment 1 is that: it includes an outer flange ring 1 and an inner flange ring 2. The inner flange ring 2 includes a flange portion 21, a plurality of ball rollers 3 and a plurality of tapered rollers 4. A first raceway 5 and two second raceways 6 are formed between the outer flange ring 1 and the inner flange ring 2. The first raceway 5 is for accommodating the tapered rollers, and the two second raceways 6 are for accommodating the ball rollers. The two second raceways 6 are arranged obliquely towards the axial direction and are opposite to the first raceway 5. The inner flange ring 2 has a stepped third groove 23 and a fourth groove 24 at one end near its flange portion 21. The two second raceways 6 are formed by the third groove 23 and the fourth groove 24 and the outer flange ring 1, respectively. A second collar 25 is fitted at the other end of the inner flange ring 2. The first raceway 5 is formed by the second collar 25 and the outer flange ring 1.

[0029] The above examples are merely one preferred embodiment of this utility model. Ordinary variations and substitutions made by those skilled in the art within the scope of this utility model's technical solution are all included within the protection scope of this utility model.

Claims

1. A hub bearing, comprising an outer flange ring and an inner flange ring, wherein the inner flange ring includes a flange portion, characterized in that: It includes a plurality of ball rollers and a plurality of tapered rollers. A first raceway and two second raceways are formed between the outer ring and the inner ring of the flange. The first raceway is for accommodating the tapered rollers, and the two second raceways are for accommodating the ball rollers. The two second raceways are arranged at an angle toward the axial direction and are positioned opposite to the first raceway.

2. The hub bearing according to claim 1, characterized in that: The flange inner ring is provided with a first collar, which is stepped and has a first groove and a second groove. The first collar is fitted onto the flange inner ring, and the two second raceways are respectively formed by the first groove and the second groove and the flange outer ring.

3. The hub bearing according to claim 1 or 2, characterized in that: One of the second raceways closer to the axis is smaller than the other second raceway, and the ball rollers on the one second raceway are also smaller than the ball rollers on the other second raceway.

4. The hub bearing according to claim 1, characterized in that: The inner ring of the flange is stepped at one end near the flange portion and has a third groove and a fourth groove. The two second raceways are formed by the third groove and the fourth groove and the outer ring of the flange, respectively. A second raceway is fitted at the other end of the inner ring of the flange. The first raceway is formed by the second raceway and the outer ring of the flange.

5. The hub bearing according to claim 1, 2, or 4, characterized in that: A first sealing ring is fitted at one end of the flange portion near the inner ring of the flange. The inner ring of the flange has a stepped surface near its flange portion. The first sealing ring includes a first lip and several second lips. The first lip abuts radially against the stepped surface, and the second lips abut axially against the flange portion. The several second lips are arranged radially at intervals.

6. The hub bearing according to claim 5, characterized in that: The first sealing ring includes a skeleton, which is bent to form a first section and a second section. The first section is fitted onto the outer diameter of the flange outer ring, and the second section abuts against the axial end of the flange outer ring.

7. The hub bearing according to claim 1, 2, 4, or 6, characterized in that: A second sealing ring is fitted at the other end of the outer ring of the flange, and a retaining ring is provided on the inner ring of the flange corresponding to the position of the second sealing ring. The retaining ring includes a third section and a fourth section. The third section is fitted onto the inner ring of the flange, and the fourth section is bent and extended toward the outer ring of the flange. The second sealing ring includes a plurality of third sealing lips, which respectively abut against the third section and the fourth section.

8. The hub bearing according to claim 7, characterized in that: The second sealing ring includes a fourth sealing lip, and the retaining ring includes a fifth section located at the end of the fourth section, the fifth section being bent and extended toward the ball roller, and the fourth sealing lip abutting against the fifth section.

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