DE102014206100A1 - Wheel bearing assembly comprising an inner ring with helix angle - Google Patents

Abstract

The invention relates to a wheel bearing arrangement for a vehicle, wherein a wheel bearing (3) is arranged between a fixed outer ring flange (1) and a rotatably mounted wheel hub (2), comprising a first row of rolling elements (4a) which is arranged between outer ring flange (1) and wheel hub (1). 2) and a second row of rolling elements (4b) disposed between the outer ring flange (1) and an inner ring (5) fitted to an annular recess of the wheel hub (2), the inner ring (5) having an outer and an inner peripheral surface (4). 6, 7), wherein the outer circumferential surface (6) is divided into a raceway (8) for the second rolling element row (4b) and a region (9) not in contact with the second rolling element row (4b), wherein the inner circumferential surface (7) has a radial and an axial bearing surface (10, 11) which come to rest on the wheel hub (2), wherein the axial bearing surface (11) of the inner ring (5) on a Nietbund (12) of Radnab e (2) for axial securing of the inner ring (5) on the wheel hub (2) is arranged. According to the invention, the axial contact surface (11) of the inner ring (5) has a helix angle which is greater than 90 ° and converges conically at least in sections from the outer to the inner peripheral surface (6, 7) of the inner ring (5).

Description

Field of the invention

The invention relates to a wheel bearing assembly for a vehicle, wherein between a fixed Außenringflansch and a rotatably mounted wheel hub, a wheel bearing is arranged, comprising a first row of rolling elements, which is arranged between Außenringflansch and wheel hub and a second row of rolling elements, the between Außenringflansch and one at an annular recess the inner ring has an outer and an inner peripheral surface, wherein the outer peripheral surface is divided into a raceway for the second row of rolling elements and a non-contacting with the second row of rolling elements, the inner peripheral surface of a radial and has an axial contact surface, which come to rest on the wheel hub, wherein the axial bearing surface of the inner ring is disposed on a rivet collar of the wheel hub for axially securing the inner ring to the wheel hub.

From the DE 10 2012 215 247 A1 goes out a wheel bearing assembly for vehicles, comprising a wheel bearing and a wheel flange which is rotatably supported by means of the wheel bearing about a rotation axis and to which a wheel can be fastened. The wheel bearing has an inner ring, an outer ring flange and a rolling element, which are arranged in a cage between the inner ring or the wheel flange and the outer ring flange. The inner ring is held axially by the rivet collar of the wheel flange. To counteract the expansion during rolling riveting, the inner ring is reinforced. For this purpose, the inner ring has a small radial dimension but a high axial dimension. The rigidity of the inner ring is due to its wall thickness, which can be seen in particular in the two figures. Due to the wall thickness and the rigidity of the inner ring, the compression of the inner ring is considerably more difficult.

Object of the invention

It is therefore the object of the invention to further develop a wheel hub assembly for a vehicle in order to increase the clamping force of the inner ring and the component strength of the wheel hub at the same time.

Solution according to the invention

According to the invention, the axial contact surface of the inner ring has a helix angle which is greater than 90 °, and converges conically at least in sections from the outer to the inner peripheral surface of the inner ring. In other words, the axial contact surface, which comes to rest on the rivet collar of the wheel hub, does not extend radially outward at a 90 ° angle but obliquely radially outward. The angle is more than 90 ° and thus represents a helix angle that deviates from a vertical. As a result, on the one hand, the degree of deformation during the forming of the wheel hub into a rivet collar is reduced, wherein the wheel hub as a whole is shorter, since the rivet collar does not extend axially beyond the inner ring.

Preferably, the helix angle is at most 120 °. Thus, the helix angle deviates by up to 30 ° from the vertical. Particularly preferably, the helix angle between 100 ° and 110 °.

Furthermore, the rivet collar is preferably designed corresponding to the axial contact surface of the inner ring and has the same helix angle. Thus, the inner ring is not plastically deformed during riveting but only elastically deformed. The inner ring thus springs back to its original position and rests with the axial bearing surface on the Nietbund. The axial contact surface of the inner ring runs parallel to the contact surface on the rivet collar.

According to an embodiment, the portion not in contact with the second row of rolling elements is formed perpendicular to the outer peripheral surface of the inner ring. Thus, an exit straight of the raceway of the second row of rolling elements extends radially outward at a 90 ° angle. An end face of the inner ring preferably runs parallel thereto. This contributes to the improvement of the rigidity of the inner ring.

According to a further embodiment, the non-contacting with the second row of rolling elements on the outer peripheral surface of the inner ring has a helix angle of up to 125 °. In other words, the deviation from the previously described embodiment is up to 35 °. Particularly preferably, the helix angle between 100 ° and 115 °. Thus, the exit line of the raceway of the second row of rolling elements extends radially obliquely outwards and thus tapers the inner ring outwards. In order to generate sufficient stability for the inner ring, the radial dimension of the inner ring is increased to the outside.

Furthermore, the wall thickness of the inner ring between the raceway for the second row of rolling elements and the axial contact surface is preferably at most 10 mm. Particularly preferably, the wall thickness of the inner ring between the raceway for the second row of rolling elements and axial contact surface is 6mm.

Preferably, the wall thickness of the inner ring between the raceway for the second row of rolling elements and inner peripheral surface is highest 4mm. This small wall thickness also improves the compression of the inner ring and increases the component strength of the hub due to the smaller depth of the annular recess on the hub.

The invention includes the technical teaching that the rolling elements of the two rows of rolling elements are spherical. Thus, the wheel bearing is a ball bearing.

According to a preferred embodiment, the maximum radial distance between the raceway for the second row of rolling elements and outer peripheral surface is greater than 60% of a diameter of the spherical rolling elements. In other words, the inner ring extends radially outward over 60% of the ball diameter, whereby a stiffness increase is generated.

The increased radial dimension of the inner ring makes it possible to arrange means for speed and / or direction of rotation detection on the outer peripheral surface as well as on an adjoining end face of the inner ring. Advantageously, the means for speed and / or direction of rotation detection are designed as encoders and lie over their entire length on the inner ring.

Brief description of the drawing

Further details and features of the invention will become apparent from the following description taken in conjunction with the drawings. The figures show:

1 a schematic representation for illustrating the construction of a wheel bearing assembly according to the invention for a vehicle according to a first embodiment, and

2 a schematic representation for illustrating the construction of a wheel bearing assembly according to the invention for a vehicle according to a second embodiment.

Detailed description of the drawing

The representation according to 1 shows a wheel bearing assembly for a vehicle, comprising one on a fixed Außenringflansch 1 over a wheel bearing 3 rotatably mounted wheel hub 2 , The wheel bearing 3 includes a first row of rolling elements 4a between the outer ring flange 1 and wheel hub 2 is arranged and a second row of rolling elements 4b between the outer ring flange 1 and one on an annular recess of the wheel hub 2 fitted inner ring 5 is arranged. The inner ring 5 is preferably by Wälznieten the wheel hub 2 fitted by a rivet collar 12 in the direction of the inner ring 5 is transformed. The rivet bond 12 comes on an axial contact surface 11 of the inner ring 5 to the plant and thus axially secures the position of the inner ring 5 at the wheel hub 2 ,

In this case, the axial contact surface 11 of the inner ring 5 a helix angle α, which is 20 °. The angle α represents the deviation from a vertical. The rivet collar 12 is to the axial contact surface 11 of the inner ring 5 formed corresponding to and has the same helix angle of 20 °.

The inner peripheral surface 7 also has a radial contact surface 10 on that at the wheel hub 2 comes to the plant. The outer peripheral surface 6 of the inner ring 5 is divided into a career 8th for the second row of rolling elements 4b and one with the second row of rolling elements 4b not in contact area 9 , The unrelated area 9 serves as a radial run-out slope of the raceway 8th and has a helix angle φ of 25 °. Again, the angle φ represents the deviation from a vertical.

The wall thickness a of the inner ring 5 is between career 8th for the second row of rolling elements 4b and inner peripheral surface 7 4mm. As inner peripheral surface 7 of the inner ring 5 is a bore diameter of the inner ring 5 to understand. The wall thickness c of the inner ring 5 is between career 8th for the second row of rolling elements 4b and axial contact surface 11 6mm. Furthermore, the maximum radial distance b between the raceway 8th for the second row of rolling elements 4b and outer peripheral surface 6 120% of a diameter of the spherical rolling elements.

These dimensions of the inner ring 5 especially improve the clamping force in the wheel bearing 3 , Furthermore, this also increases the component strength of the wheel hub 2 , Because the rivet collar 12 is not formed up to a 90 ° angle, but due to the helix angle α only up to 70 °, learns this less deformation, creating a possible subsequent spur toothing of the rivet head 12 has a better tooth filling. Furthermore, the force can be reduced to Wälznieten, since even with less deformation higher clamping forces in the wheel bearing 3 can be realized, in particular the wall thickness a of the inner ring 5 between career 8th for the second row of rolling elements 4b and inner peripheral surface 7 contributes to this. Due to the radial dimension b of the inner ring 5 is the arrangement of an encoder 14 for speed and / or direction of rotation detection on the outer peripheral surface 6 as well as on an adjoining end face 13 of the inner ring 5 possible.

According to 2 is the one with the second row of rolling elements 4b unrelated area 9 on the outer peripheral surface 6 of the inner ring 5 formed vertically. Thus, the run-out edge of the raceway runs 8th the second row of rolling elements 4b at a 90 ° angle radially outwards. As an axial wall thickness of the inner ring 5 due to the missing helix angle φ larger than in 1 , is the maximum radial distance b between the raceway 8th for the second row of rolling elements 4b and outer peripheral surface 6 80% of the diameter of the spherical rolling elements large.

LIST OF REFERENCE NUMBERS

1

 Außenringflansch

2

 wheel hub

3

 Wheel bearings

4a, 4b

rolling body row

5

 inner ring

6

 outer peripheral surface

7

 inner peripheral surface

8th

 career

9

 Area

10

 radial contact surface

11

 axial contact surface

12

 rivet collar

13

 face

14

 encoder

a

 Wall thickness

b

 maximum radial distance

c

 Wall thickness

α

 helix angle

φ

 helix angle

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102012215247 A1 [0002]

Claims (10)

Wheel bearing arrangement for a vehicle, wherein between a fixed outer ring flange ( 1 ) and a rotatably mounted wheel hub ( 2 ) a wheel bearing ( 3 ) is arranged, comprising a first row of rolling elements ( 4a ), which between outer ring flange ( 1 ) and wheel hub ( 2 ) is arranged and a second row of rolling elements ( 4b ), which between outer ring flange ( 1 ) and one at an annular recess of the wheel hub ( 2 ) fitted inner ring ( 5 ), wherein the inner ring ( 5 ) an outer and an inner peripheral surface ( 6 . 7 ), wherein the outer peripheral surface ( 6 ) is divided into a career ( 8th ) for the second row of rolling elements ( 4b ) and one with the second row of rolling elements ( 4b ) not in contact ( 9 ), wherein the inner peripheral surface ( 7 ) a radial and an axial bearing surface ( 10 . 11 ), which at the wheel hub ( 2 ) come to rest, the axial bearing surface ( 11 ) of the inner ring ( 5 ) on a rivet collar ( 12 ) of the wheel hub ( 2 ) for axially securing the inner ring ( 5 ) at the wheel hub ( 2 ), characterized in that the axial abutment surface ( 11 ) of the inner ring ( 5 ) has a helix angle that is greater than 90 °, and from the outer to the inner peripheral surface ( 6 . 7 ) of the inner ring ( 5 ) converges conically at least in sections. Wheel bearing arrangement according to claim 1, characterized in that the helix angle is at most 120 °. Wheel bearing arrangement according to claim 1, characterized in that the rivet collar ( 12 ) to the axial contact surface ( 11 ) of the inner ring ( 5 ) is formed correspondingly and has the same helix angle. Wheel bearing arrangement according to claim 1, characterized in that the with the second row of rolling elements ( 4b ) not in contact ( 9 ) on the outer peripheral surface ( 6 ) of the inner ring ( 5 ) is formed vertically. Wheel bearing arrangement according to claim 1, characterized in that the with the second row of rolling elements ( 4b ) not in contact ( 9 ) on the outer peripheral surface ( 6 ) of the inner ring ( 5 ) has a helix angle of up to 125 °. Wheel bearing arrangement according to claim 1, characterized in that the wall thickness of the inner ring ( 5 ) between career ( 8th ) for the second row of rolling elements ( 4b ) and axial contact surface ( 11 ) is at most 10mm. Wheel bearing arrangement according to claim 1, characterized in that the wall thickness of the inner ring ( 5 ) between career ( 8th ) for the second row of rolling elements ( 4b ) and inner peripheral surface ( 7 ) is at most 4mm. Wheel bearing arrangement according to claim 1, characterized in that the rolling elements of the two rows of rolling elements ( 4a . 4b ) are spherical. Wheel bearing arrangement according to claim 8, characterized in that the maximum radial distance between the track ( 8th ) for the second row of rolling elements ( 4b ) and outer peripheral surface ( 6 ) is greater than 60% of a diameter of the spherical rolling elements. Wheel bearing arrangement according to claim 1, characterized in that means for speed and / or direction of rotation detection on the outer peripheral surface ( 6 ) and at a subsequent end face ( 13 ) of the inner ring ( 5 ) are arranged.

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