CN215634412U - Impact-resistant hub bearing - Google Patents

Abstract

The utility model discloses an impact-resistant hub bearing, which comprises a flange inner ring and a flange outer ring sleeved on the flange inner ring, wherein a plurality of rollers and a retainer for keeping the distance between the rollers are arranged between the flange inner ring and the flange outer ring; the shoulder height of the raceway corresponding to the roller with larger diameter on one side relative to the flange plate is 30-50% of the diameter of the roller; a gap g is formed between the flange outer ring and the flange plate, and the length of the gap g is less than 0.3 mm. The utility model can improve the impact resistance effect of the hub bearing under the condition of not increasing the material cost and the bearing quality.

Description

Impact-resistant hub bearing

Technical Field

The utility model relates to a bearing, in particular to an impact-resistant hub bearing.

Background

When a car passes through a concave pit or a convex pit on the road surface at high speed, the inner ring of the flange connected with the wheel bears impact force, and the impact force is transmitted to the steel ball component, so that the impact roller path forms an indent. The typical failure of the impact is that noise or vibration is generated when the automobile bearing runs, the driving experience of a customer is affected, and customer complaints are caused.

A common design solution is to increase the diameter or axial dimension of the bearing or the size or number of rolling elements of the bearing, which typically results in increased bearing mass and cost, and makes the bearing design less efficient in straight running and cornering capability. The shoulder height of the bearing raceway will also increase with the diameter of the ball, providing additional raceway support for the ball in extreme lateral force situations. However, this approach increases the cost of the process. All conventional improvements come at the expense of increased bearing mass, rotational torque, and cost of the bearing and components that mate with the bearing.

Therefore, in addition to basic requirements such as high load capacity, high reliability, long life, and light weight, the demand for impact resistance and high moment rigidity is also increasing.

SUMMERY OF THE UTILITY MODEL

Aiming at the defects in the prior art, the utility model aims to provide an impact-resistant hub bearing, which can improve the impact-resistant effect of the hub bearing under the condition of not increasing the material cost and the bearing quality.

In order to achieve the purpose, the utility model provides the following technical scheme: a rotating member (flange inner race) defined in the axial direction; a non-rotating member (flange outer ring) connecting a suspension structure (e.g., a knuckle or an axle) of a vehicle, and an inner small inner ring clamped by a caulking-formed bead and rolling bodies coupling the rotating member to the non-rotating member to enable the rotating member to rotate about an axis relative to the non-rotating member. The inner small inner ring defines an inner bearing raceway and the non-rotating component defines an inner outer bearing raceway, the rotating component defines an outer inner bearing raceway and the non-rotating component defines an outer bearing raceway. The hub bearing comprises two rows of raceways, each row of raceways capable of holding a plurality of rolling elements in motion. When the rolling elements are steel balls, the height of the rims of the raceways is preferably between about 30% and 50% of the diameter of their respective steel balls. The journal surface of the wheel rotating member and the non-rotating annular surface have a gap g, the gap g having a length less than about 0.30 mm.

As a further improvement of the utility model, the thickness of the contact surface of the flange outer ring on one side relative to the flange plate is 2 mm-5 mm.

As a further improvement of the utility model, an annular groove coaxial with the flange plate is arranged at the position of the contact surface of the flange plate relative to the outer ring of the flange, the position of the outer ring of the flange corresponding to the annular groove is positioned in the annular groove, and the gap g is positioned between the groove bottom of the annular groove and the outer ring of the flange.

As a further improvement of the utility model, a sealing ring is arranged between the outer side surface of one end of the outer ring of the flange, which is positioned in the annular groove, and a sealing lip is arranged on one side of the sealing ring, which faces the bottom of the annular groove, and the sealing lip is attached to the bottom of the annular groove.

As a further improvement of the utility model, the length of the gap g is equal to or greater than 0.13mm and less than 0.3 mm.

As a further development of the utility model, the two rows of raceways correspond to rollers of different diameters, the roller of larger diameter being located on the side close to the flange.

As a further improvement of the utility model, the end face of one end of the flange outer ring opposite to the flange plate is also provided with a plurality of grooves.

As a further improvement of the utility model, the position of the flange corresponding to the outer ring of the flange is in inclined surface fit.

As a further improvement of the utility model, the matched inclined plane of the flange plate and the flange outer ring inclines from the flange plate to the roller direction.

The utility model has the advantages that,

1. the length of clearance g is less than 0.3mm, means that the distance between flange outer lane and the flange inner circle is nearer, when wheel hub received the impact, can let flange outer lane and inner circle contradict through the stroke of extremely short to can reduce substantially and transmit the impact load to the raceway, avoid the raceway to appear strikeing the brinell indentation.

2. When the length of the gap g is 0.13mm, the shoulder height of the roller can be reduced to 30% of the roller diameter, at which point the weight and material costs can be reduced considerably.

3. Through the clearance design, can adopt the steel ball of less diameter or reduce the steel ball quantity, reduce material cost and weight when keeping high shock resistance.

4. The bearing can be applied to bearings with limited bearing size or limited bearing internal space layout, and not only can the high impact resistance be achieved, but also other performances of the bearing are not reduced.

5. Since the gap g is small, entry of debris/cement can be blocked, and some large dust can be directly blocked out without damaging the seal.

Drawings

FIG. 1 is a schematic cross-sectional view of one embodiment of the present invention;

FIG. 2 is a schematic cross-sectional view of another embodiment of the present invention;

FIG. 3 is an enlarged view of the part A of FIG. 1;

FIG. 4 is an enlarged view of the portion B of FIG. 2;

FIG. 5 is a schematic structural view of a planar end embodiment of the present invention;

FIG. 6 is a schematic structural view of an embodiment of a beveled end of the present invention;

fig. 7 is a schematic structural view of an end slotting embodiment of the present invention.

Reference numerals: 1. an inner ring of the flange; 2. an outer ring of the flange; 3. a roller; 4. a holder; 5. a flange plate; 6. a raceway; 7. shoulder height; 8. an annular groove; 9. a seal ring; 10. a sealing lip; 11. a bevel; 12. and (4) a groove.

Detailed Description

The utility model will be further described in detail with reference to the following examples, which are given in the accompanying drawings.

As shown with reference to figures 1-7,

the impact-resistant hub bearing comprises a flange inner ring 1 and a flange outer ring 2 sleeved on the flange inner ring 1, wherein a plurality of rollers 3 and a retainer 4 for keeping the distance between the rollers 3 are arranged between the flange inner ring 1 and the flange outer ring 2, one end of the flange inner ring 1 is provided with a coaxial flange plate 5, the other end of the flange inner ring is provided with a turned edge which is formed by riveting and tilted towards the flange outer ring 2, the flange inner ring 1 is provided with a roller path 6 for the rollers 3 to roll, the roller path 6 is provided with two rows, the two rows of roller paths 6 correspond to the rollers 3 with different diameters, and the roller 3 with the larger diameter is positioned at one side close to the flange plate 5; the shoulder height 7 of the raceway 6 corresponding to the roller 3 with larger diameter at one side relative to the flange plate 5 is 30-50% of the diameter of the roller 3; a gap g is formed between the flange outer ring 2 and the flange plate 5, and the length of the gap g is less than 0.3 mm.

Based on above-mentioned scheme, the roller 3 size that two rows of raceways 6 correspond is different, and the great roller 3 of a row of diameter is close to ring flange 5 one side moreover, because ring flange 5 one side is used for installing wheel hub, consequently when wheel hub received the impact, can let the great roller 3 of diameter share the impact, and the shoulder height 7 of cooperation raceway 6 can share with the cooperation of roller 3. As shown in the figure, the length of the gap g is less than 0.3mm, which means that the distance between the flange outer ring 2 and the flange inner ring 1 is short, when the hub is impacted, the flange outer ring 2 and the flange inner ring can collide through a very short stroke, and the requirement on the shoulder height 7 of the raceway 6 can be reduced to 30% -50% of the diameter of the roller 3 through experiments, so that the method has great advantages for reducing cost. In particular, when the length of the gap g is 0.13mm, the diameter of the roller 3 can be reduced to 30% of the diameter of the roller 3, at which point the weight and material costs can be greatly reduced. When the corresponding gap g is 0.3mm, the shoulder height 7 of the raceway 6 is 50% of the diameter of the roller 3, and the cost can be kept low. And because clearance g is less, can block the entering of debris/cement, some big dust can directly block outside, can not harm the sealing member.

The thickness of the contact surface of the flange outer ring 2 on the side opposite to the flange 5 is 2mm to 5 mm.

The design of the thickness means that the contact area is reduced, the friction caused by continuous rotation of the hub after the hub is impacted is reduced, the damage is reduced, and the noise and the vibration are reduced.

In another embodiment, an annular groove 8 coaxial with the flange 5 is formed in the position of the flange 5, which is opposite to the contact surface of the flange outer ring 2, the position of the flange outer ring 2, which corresponds to the annular groove 8, is located in the annular groove 8, and the gap g is located between the groove bottom of the annular groove 8 and the flange outer ring 2.

Utilize annular groove 8 and the cooperation of flange outer lane 2, flange outer lane 2 enters into this annular groove 8 in, can produce certain air flow when flange inner circle 1 rotates, can utilize annular groove 8 to prevent dust, can reduce the entering of dust to select to fix a position and spacing flange outer lane 2 according to annular groove 8's size of a dimension, can optimize the vibration after spacing flange outer lane 2.

Based on another embodiment of the above scheme, a sealing ring 9 is arranged between the outer side surface of one end of the flange outer ring 2 located in the annular groove 8 and the annular groove 8, a sealing lip 10 is arranged on one side of the sealing ring 9 facing the bottom of the annular groove 8, and the sealing lip 10 is attached to the bottom of the annular groove.

Increase annular groove 8's size under this scheme to utilize sealing washer 9 to seal flange outer lane 2 and annular groove 8, isolated outside dust, the air flow that brings when coming through flange inner circle 1 rotation disturbs the dust, reduces and gets into the bearing inner space, two keep apart the great piece of volume etc. and can utilize flange inner circle 1's rotation to throw away the dust.

The roller 3 may be a conical, cylindrical, spherical roller 3, or any combination of two, and may be applied to this embodiment.

Furthermore, the end face of the flange outer ring 2 opposite to one end of the flange plate 5 is also provided with a plurality of grooves 12.

When the flange outer ring 2 collides with the flange 5, abnormal noise caused by friction can be reduced by the groove 12. While also absorbing a part of the noise by means of the grooves 12. The groove 12 may have various shapes, and may be a plurality of blind-hole-shaped grooves 12, or an annular groove 12 formed in the circumferential direction.

The flange 5 and the flange outer ring 2 may be matched in a plane, but it is also possible to match the flange 5 and the flange outer ring 2 at a corresponding position by an inclined plane 11 as another embodiment. The engagement of the inclined surface 11 has a larger contact surface than the engagement of a flat surface, and thus can withstand a larger impact. Moreover, the inclined surface 11 can be used for decomposing the impact force, so that the impact force is reduced, and the service life is prolonged.

Specifically, the inclined surface 11 of the flange 5 and the flange outer ring 2 is inclined from the flange 5 toward the roller 3.

The above-mentioned inclined direction is more convenient for processing, and of course, a person skilled in the art can also adopt the opposite inclined direction, and the technical effect to be achieved by the present scheme can also be achieved.

The above description is only a preferred embodiment of the present invention, and the protection scope of the present invention is not limited to the above embodiments, and all technical solutions belonging to the idea of the present invention belong to the protection scope of the present invention. It should be noted that modifications and embellishments within the scope of the utility model may occur to those skilled in the art without departing from the principle of the utility model, and are considered to be within the scope of the utility model.

Claims (9)

1. The shock-resistant hub bearing comprises a flange inner ring and a flange outer ring sleeved on the flange inner ring, wherein a plurality of rollers and a retainer for keeping the distance between the rollers are arranged between the flange inner ring and the flange outer ring; the shoulder height of the raceway corresponding to the roller with larger diameter on one side relative to the flange plate is 30-50% of the diameter of the roller; a gap g is formed between the flange outer ring and the flange plate, and the length of the gap g is less than 0.3 mm.

2. The impact resistant hub bearing of claim 1 wherein the thickness of the contact surface of the flange outer race on the side opposite the flange plate is between 2mm and 5 mm.

3. The impact-resistant hub bearing of claim 2, wherein the flange plate defines an annular groove coaxial with the flange plate at a location opposite to the contact surface of the flange outer ring, the flange outer ring is located in the annular groove at a location corresponding to the annular groove, and the gap g is located between the groove bottom of the annular groove and the flange outer ring.

4. The impact-resistant hub bearing of claim 3, wherein a seal ring is disposed between the outer side surface of the end of the flange outer ring located in the annular groove and the annular groove, and a seal lip is disposed on a side of the seal ring facing the bottom of the annular groove and is attached to the bottom of the annular groove.

5. The impact resistant hub bearing of claim 1, wherein the length of the gap g is 0.13mm or more and 0.3mm or less.

6. The impact resistant hub bearing of claim 1 wherein said raceways correspond to rollers of different diameters, the larger diameter roller being located on the side adjacent to the flange.

7. The impact resistant hub bearing of claim 1 wherein said flange outer race is further provided with a plurality of grooves in an end face thereof opposite said flange plate.

8. The impact resistant hub bearing of claim 1 wherein said flange plate is beveled at a location corresponding to the flange outer race.

9. The impact resistant hub bearing of claim 8, wherein the mating ramp surfaces of the flange plate and the flange outer race are inclined from the flange plate toward the rollers.

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