DE102006050940A1 - Roller bearing for use in wheel bearing of motor vehicle, has outer ring defining outer path, and inner and outer paths formed and arranged such that ling body axis is bent towards bearing axis under angle of incidence - Google Patents

Abstract

The roller bearing has an outer ring (1) defining an outer path (BA). An inner ring (2) defines an inner path (BI) and is turned towards the outer path. Rolling bodies (W) are provided between the inner path and the outer path, where the rolling bodies are formed as ton rollers and have spherical belly-like rolling body cross-section under a profile radius (R) in a rolling body axial section plane. The inner and outer paths are formed and arranged such that a ling body axis (Y) is bent towards a bearing axis (X) under an angle of incidence. An independent claim is also included for a wheel bearing with a roller bearing.

Description

Field of the invention

The The invention relates to a rolling bearing as well on a wheel bearing including the same as such serves the storage of a vehicle wheel.

Out DE 195 37 808 C2 a wheel bearing for a motor vehicle is known which has a hub carrier and a hub flange rotatably mounted therein via an angular ball bearing pair. The angular contact ball bearing comprises inner and outer raceways. The outer raceways of the angular contact ball bearing pair are formed by a correspondingly machined inner peripheral surface of the hub carrier. The inner raceways of the angular contact ball bearing pair are formed by two ring elements which are pressed onto a journal of the hub flange and axially secured there. The inner and outer raceways of the angular contact ball bearing pair are formed in such a way that, with regard to the pressure lines running through the contact zones of the rolling elements, a so-called O-arrangement results, which permits transmission of axial and radial forces as well as tilting moments.

Out DE 103 31 936 A1 is a wheel bearing unit for vehicle wheels known in which instead of such load cases hitherto typically used tapered bearings, or double-row ball bearings, ball bearings are used as such include four careers.

Out RU 2 215 205 C2 a rolling bearing is known, in which the rolling elements designed like a barrel and in this case are designed such that the profile radius of the Wälzkörperquerschnitts along a Wälzkörper-Axialschnittebene is slightly smaller than the radius of curvature of an outer race formed by the outer ring, the bearing axis facing outer raceway. The center of curvature of the outer race forming ring inner surface is located on the bearing axis. The inner ring is tiltable relative to the outer ring.

Out RU 2 231 696 C2 is known a double-row spherical roller bearings whose rolling elements are also included in a defined between an inner ring and an outer ring space. The profile radius of curvature of the Wälzkörperquerschnittes in a rolling element axial plane corresponds to the radius of curvature of the outer raceway formed by the inner surface of the outer ring. The center of curvature is also on this bearing on the bearing axis. The inner ring of the bearing can thus be tilted relative to the outer ring about a bearing axis substantially perpendicular to the transverse axis, similar to the aforementioned bearing.

Of the Invention has for its object to provide solutions which make it possible on low cost Way to realize a storage, in particular wheel bearing which at a high motion efficiency both radially, and axially directed bearing forces, and can absorb tilting moments acting transversely to the bearing axis.

Regarding a rolling bearing In itself, this object is achieved according to the invention by a rolling bearing according to claim 1.

Thereby is it possible in an advantageous manner under recourse to use proven manufacturing technologies to create a rolling bearing that the Running characteristics of angular contact ball bearings, and tapered bearings united and in contrast to spherical roller bearings also considerable axial forces and can absorb tilting moments. The rolling bearing according to the invention is suitable especially for the use of pinion bearings, for use with final drives, suspension, Hydraulic power units, compressors and in particular also transmission shaft bearings. The rolling bearing according to the invention can with other, possibly identical rolling bearings to a bearing assembly be assembled, by means of which a tilt-resistant storage of a through the rolling bearing supported Shaft section opposite one the outer rings supporting Structure in an x or o arrangement can be accomplished.

By means of the rolling bearing according to the invention, bearing units can be created which, with a relatively small space requirement, offer high radial and axial load carrying capacity with relatively low bearing friction. The rolling bearing according to the invention is not only suitable for receiving high axial and radial forces, but in particular for absorbing tilting moments. In a particularly advantageous manner, a bearing can be realized based on the concept according to the invention, which is characterized by a relatively low Lagerreibmoment compared to tapered roller bearings. Even with tapered roller bearings occurring Bordreibungseffekte can be avoided in the rolling bearing according to the invention. In particular, when using the rolling bearing according to the invention in the field of vehicle propulsion technology improvements in mechanical efficiency and thus energy savings can be made possible. Based on the concept of the invention, a rolling bearing can be created in which no friction occurs that is verkippungsunempfind Lich, which offers a large support base through the use of a large pressure angle, which has a high radial and axial load capacity and realized a total of a small space requirement that can.

According to one particularly preferred embodiment The invention is the rolling bearing formed such that the inner and the outer raceway of the same to each other are arranged such that the Wälzkörperachse to the bearing axis under an angle of attack is inclined. This makes it possible to create a "skew-barrel bearing" Anstellwinkel is preferably in a range of 10 ° to 600 ° The angle of attack especially with regard to the expected bearing load be matched. Size Lead the angle of attack in particular to a high axial load capacity of the bearing. For smaller ones Anstellwinkeln give high load capacities in the radial direction.

Preferably the rolling elements are like that dimensioned that the axial length it is greater than the simple diameter of the rolling element. At this Design of the rolling element results a particularly high smoothness and breaking strength of the rolling elements. The Peripheral edges are preferably slightly rounded. The curvature profile is preferably under consideration the compression behavior optimized and in particular can be slightly elliptical.

It is possible, the inner ring and the outer ring so that the outer raceway with an inner peripheral edge closes the radial distance to Bearing axis substantially corresponds to the radial distance, with which an outer peripheral edge completes the inner raceway.

The with respect to the rolling element axis arranged at an angle to the bearing axis in the space Rolling be preferably guided by a Wälzkörperkäfig. This Wälzkörperkäfig can in particular be made of a plastic material.

The Rolling bearing according to the invention is preferably provided with a sealing device, through which is an annular gap defined between the inner ring and the outer ring is sealed. This sealing device can be designed as a sealing lip, either on the outer ring, on the inner ring or on the cage device is fixed.

By the inventive concept will it be possible the inner ring and the outer ring so that the remaining between these two rings Annular gap is comparatively small.

Regarding a wheel bearing for a vehicle suspension the object specified by the invention by a wheel bearing with the features specified in claim 10 solved. This makes it possible in an advantageous manner, a wheel bearing unit for driven as well as for non-driven wheels of motor vehicles, especially pickups, trucks, light trucks and to create SUVs. Based on the concept of the invention can with the same load capacity the Dimensions of the wheel bearing and in particular the mass of the same be reduced. In the design of the wheel bearing according to the invention With previously typical dimensions significantly higher wheel forces can be absorbed be achieved and increases in the life of the wheel bearing become.

The Wheel bearing according to the invention is characterized in particular by a high load capacity at relatively low Required space. It is characterized by a high torque stiffness which also improves the braking function and the Driving comfort contributes. Based on the concept of the invention results in a higher Motion efficiency, since the bearing according to the invention by a comparison to previous Bearing designs reduced friction torque is distinguished. The bearing according to the invention offers a long service life even at long intervals Radwirkungslinie (the resistance point by the wheel resistance point running) to Bearing center. The storage according to the invention can be realized by at least part of the leadership of the Rolling provided Bearings directly into structural components of the suspension, in particular a hub journal or a hub carrier is formed.

For the geometric Designs of the rolling elements and the leading one Careers apply the preceding to the rolling stock itself negotiated technical details mutatis mutandis. Further advantageous embodiments of the wheel bearing according to the invention are the subject the dependent claims.

Further Details and features of the invention will become apparent from the following Description in connection with the drawing. It shows:

1 an axial sectional view for explaining the structure of a rolling bearing according to the invention,

2 3 is a further axial sectional view of a rolling bearing according to the invention for illustrating further geometric details;

3 an axial sectional view of a wheel bearing according to the invention with a double row, built-in O-arrangement Schrägtonnenlagerung invention,

4 an axial sectional view of a further variant of a wheel bearing according to the invention in the form of a combination of a Schrägtonnenlagers invention with an angular contact ball bearing - here in O arrangement,

5 another variant of a wheel bearing according to the invention similar 4 However, with regard to the diameter of Wälzkörperteilkreise differently shaped rolling bearing devices.

This in 1 illustrated, rolling bearing according to the invention comprises an outer ring 1 defining an outer race BA facing as such a bearing axis X. The rolling bearing further comprises an inner ring 2 defining an inner race BI facing as such the outer race BA.

In one defined between the inner race BI and the outer race BA Space B rolling elements W are added. The rolling elements W are designed as barrel rollers and have in the recognizable here, along a Wälzkörperachse Y extending rolling element axial section plane a below a profile radius R convex bulging outward Wälzkörperquerschnitt on. This profile radius R is greater than the center diameter DW of the respective rolling element W.

The shown here, rolling bearings according to the invention is characterized by the fact that the profile radius R and a Bahnprofilradius P are smaller than the distance A of a maximum distance from the bearing axis X. Lane S of the outer raceway BA. The center of curvature DP of the path profile radius P is radially spaced from the bearing axis X. The radial distance DP is preferably in the range of 15 to 75% the aforementioned distance A of the outermost track S from the bearing axis X.

at the embodiment shown here are the inner race BI and the outer race BA Furthermore, designed and arranged such that the rolling member Y is inclined at an angle K to the bearing axis X. This angle of attack K can on the circumstances to be matched by the radial and axial forces to be absorbed by the bearing and is preferably in the range of 10 ° to 60 °. Larger angle values lead to high axial load capacities, lead to smaller angle values to higher radial load capacities.

As shown in the illustration 2 can be seen, the rolling element W is preferably dimensioned such that its axial length LW is greater than the simple amount of recognizable in this representation Wälzkörperdurchmessers DW. In the embodiment shown here, the outer race or the outer ring 1 and the inner ring 2 designed so that the outer race BA with an inner peripheral edge 3 closes and the inner race BI with an outer peripheral edge 4 completes, with these two peripheral edges 3 . 4 have substantially the same radial distance D to the bearing axis X.

at the rolling bearing according to the invention shown here is the fulcrum DP of the profile radius' R of the Rolling elements W "over" the central axis X of the warehouse. The pressure angle KD shown here is preferably in the range of 10 ° to 40 °.

The rolling elements W are preferably by a cage device 5 guided. As can be seen from this illustration, it is possible to design the cage device such that its axial length measured in the direction of the bearing axis X substantially corresponds to the diagonal length of the rolling bodies. Through the cage device 5 is caused in this respect no, or no significant contribution to the axial length of the camp. The rolling bearing according to the invention can in this respect also with respect to the embodiment shown here significantly shortened axial lengths of the inner ring 2 and the outer ring 1 will be realized.

Although not shown in this illustration, it is possible that between the inner ring 2 and the outer ring 1 defined annular gap area S1 and S2 seal. This sealing device may in particular comprise a sealing lip structure made of an elastomeric material, which on the inner ring 2 , on the outer ring 1 or especially on the cage 5 can be attached.

The According to the invention skew-barrel bearing advantageously used for the realization of storage systems be, in which previously skewed ball bearings or tapered bearings are used. The oblique barrel bearing according to the invention can, similar like cone bearings, in x- or o-arrangement with other identical, or in the structure deviating bearings are installed. The bearing according to the invention especially for Storage tasks are used for which previously angular contact ball bearings or tapered bearings were used.

It is possible, the axial length the rolling elements W and Adjust the angle of attack K so that the from the bearing axis X maximum spaced track S between the outer web edges of the outer raceway BA comes to rest. This makes it possible, the rolling elements W in a sunken corresponding track groove and thereby a particularly To achieve high speed stability of the skew-barrel bearing according to the invention.

The outer ring 1 and the inner ring 2 can be designed in the rolling bearing according to the invention be that a certain axial limitation of the movement path of the rolling elements W in the direction of the rolling body Y is achieved by this. Depending on which ring 1 . 2 these corresponding walls are formed, the assembled with rolling elements cage is first inserted into the outer ring or in the inner ring during assembly of the rolling bearing.

The Rolling bearing according to the invention can advantageously from typical rolling bearing materials, in particular Be made of steel. Due to the relatively low, punctual Loads of rolling elements, in particular because of the hereby possible Realization of a line contact of the rolling element outer surface with the corresponding Career it is possible the rolling elements, if necessary also the bearing rings also made of ceramic materials finished.

In the 3 illustrated wheel bearing comprises a first rolling bearing device W1 and a second rolling bearing device W2. In both rolling bearing devices W1, W2 rolling elements W are added, which are arranged in a defined between an inner race BI1, BI2, and an outer race BA1, BA2 space B1, B2. The outer Wälzkörperlaufbahnen BA1, BA2 are both the bearing axis X facing the storage. In the embodiment shown here, both outer raceways BA1, BA2 are formed so that they are concavely curved in the axial section plane shown here, containing the bearing axis X under a Bahnprofilradius P.

The Wheel bearing shown here is characterized in that the Rolling elements W1, W2 are designed as barrel rollers and thus in a along the Wälzkörperachsen Y1 and Y2 extending Wälzkörperaxialschnittebene a below a profile radius R crowned bulging Wälzkörperquerschnitt exhibit. The rolling element raceways BI1, BI2, BA1, BA2 are designed such that the rolling bodies W1, W2 so led are that their Wälzkörperachsen Y1, Y2 inclined to the bearing axis X at an angle K1, or K2 are aligned.

The profile radius R of the rolling elements W1, W2 (see. 1 and 2 ) is larger than the center diameter DW of the respective rolling element W1, W2 in the embodiment shown here. The profile radius R and the path profile radius P are further smaller than the distance A of a maximum spaced from the bearing axis X Wälzkörperlaufspur SP1, SP2 of the outer raceways BA1 and BA2.

In the embodiment according to 3 are, as already stated, both roller bearings W1, W2 designed in Schrägtonnenbauart invention. The rolling elements are replaced over previous constructions by barrel rollers in O arrangement. The contact angle of the rolling element rows is preferably in a range of 15 ° -45 °. Due to the enlarged pressure ellipse in the raceway area (large roller radius), a high load capacity and bearing stiffness is achieved. Due to the symmetrical design can be saved compared to rows of balls space.

How out 4 However, it is also possible, only one of the rolling bearings, in particular perform the Radialkraftwirkungslinie the wheel contact forces nearer rolling bearing W1 in the design of the invention and the second, typically acted upon by lower radial forces rolling bearing device W2 in the angular contact ball bearing type shown here. Also in this embodiment, the outer raceways BA1, BA2 can directly into a structural component of the suspension, in particular on the inner peripheral wall of the bearing bore of a hub carrier 8th be educated. Alternatively, it is also possible, these outer races BA1, BA2 by axially sufficiently secured, in the hub carrier 8th inserted outer rings 1 (see. 1 and 2 ) to build.

In the embodiment according to 4 is the inner race BI1 of the first rolling bearing device W1 through a correspondingly machined outer surface of a pin portion 9 a hub carrier flange formed. The journal section 9 is with a through hole 10 provided, which has a Axialverzahnungsabschnitt 11 , a straight bore section 12 and an axle nut seat 13 includes. The journal section 9 is with a seat section 14 provided on which an inner ring 2 the second rolling bearing device W2 sits. The sitting section 14 is designed such that this one ring shoulder 15 defined by which the inner ring 2 is axially positioned. The ring shoulder 15 is machined such that the rolling elements W1, W2 of the wheel bearing are taken up after tightening the axle nut not shown here with a predetermined bias between the raceways BA1, BA2, BI1, BI2. As an alternative to this design of the wheel bearing, it is also possible, the axial position of the inner ring 2 otherwise, in particular by a ring nut set on a corresponding threaded portion of the pin 9 sitting.

The wheel bearing according to the invention is further with sealing devices 16 . 17 provided by which the remaining between the mutually rotatably mounted components remaining movement gaps are sufficiently sealed. In the embodiment shown here, a ring element designed as a cartridge seal sits non-rotatably in a through the hub carrier 8th provided Peripheral wall and seals with its sealing lip through the flange 9 provided outside surface. In the sealing device 17 For example, the seal is accomplished in the manner of a cassette seal comprising two ring members, one of the two in the hub carrier 8th sits and the other on an outer peripheral portion of the inner ring 2 , Between these two ring elements, an elastomer sealing lip is arranged in a conventional manner.

For the embodiment according to 5 The explanations regarding the variant apply 4 analogous. This embodiment differs from the variant 4 in particular in that the roller bearing device W1 and the roller bearing device W2 are designed so that the centers Z1, Z2 of the rolling elements WK1, WK2 circulate on pitch circles about the bearing axis X, which differ in terms of their diameter. In the embodiment shown here, the diameter D1 of the circulation circuit of the centers of the rolling elements WK1 is greater than the diameter D2 of the circulating circuit of the centers Z2 of the rolling elements WK2. This design results in a particularly high load capacity of the first roller bearing W1 and a particularly high load capacity of the pin 9 in the field of internal career BI1.

The in the wheel bearing according to 5 realized combination of a Schrägtonnenlagerung with an angular contact ball bearing device is accomplished in this embodiment, that results in a recording of the bearing forces based on a so-called O-arrangement.

The Invention is not limited to the aforementioned embodiments. The oblique barrel bearing according to the invention as well as in particular also the inclusion of the same inventive combination bearings can also with other storage cases, In particular, find bearings within transmissions application.

In the realization of the wheel bearing, it is also possible, instead of in the embodiments of the 3 . 4 and 5 provided continuous pin 9 Here to use an axially split pin and form the inner race BI1, for example, directly to a joint bell, which can be removed after appropriate release of a central axle nut of the wheel bearing.

According to the variant 4 can be realized as a barrel roller row according to the invention in particular at strongly deviating from the bearing center Radwirkungslinien the most highly stressed row of rolling elements and the second, less loaded row are designed as a row of balls. By installing a ball and barrel roller row, the rolling element costs can be reduced. Depending on the position of the Radwirkungslinie both the right and the left row of rolling elements can be performed with barrel rollers. Likewise, the pitch circles of Wälzkörperreihen can be performed differently depending on demand.

1

outer ring

2

inner ring

3

outer edge

4

inner edge

5

Cage

X

bearing axle

Y

rolling member

S1

annular gap

S2

annular gap

LW

Wälzkörperaxiallänge

DW

Wälzkörpermaximaldurchmesser

KD

contact angle

K

angle

A

distance

B

space

P

Bahn profile radius

S

track

R

profile radius

Claims (19)

Rolling bearing with: - an outer ring ( 1 ) which defines an outer race (BA) which, as such, faces a bearing axis (X) and is concavely curved below a track profile radius (P) in an axial section plane containing the bearing axis (X), 2 ) which defines an inner race (BI) which as such faces the outer race (BA), and - rolling bodies (W) which are received in a space (B) defined between the inner race (BI) and the outer race (BA) in which the rolling elements (W) are designed as barrel rollers and have a rolling body cross-section which bulges spherically under a profile radius (R) in a rolling body axial section plane extending along a rolling body axis (Y), this profile radius (R) being greater than the center diameter ( DW) of the respective rolling body (W), - characterized in that the inner and the outer raceway (BI, BA) are formed and arranged such that the Wälzkörperachse (Y) to the bearing axis (X) at an angle (K) is inclined. Rolling bearing according to claim 1, characterized in that the profile radius (R) and the path profile radius (P) are smaller than the distance (A) one of the bearing axis (X) maximum spaced Wälzkörperlaufspur (S) of the outer raceway (BA). roller bearing according to claim 2, characterized in that in the bearing axis (X) containing the center of curvature (DP) of the web profile the outer career (BA) in the direction of the bearing axis (X) with respect to one on the Wälzkörperachse (Y) lying axial center (AZ) of the rolling body (W) by an offset distance (V) is axially offset. roller bearing according to claim 3, characterized in that the center of curvature (DP) on the intended to initiate an axially directed pressure load Pressure side (PSI) of the inner ring is located. roller bearing according to at least one of the claims 2 to 4, characterized in that the angle of attack (K) in one Range from 10 ° to 60 °. roller bearing according to at least one of the claims 1 to 5, characterized in that the axial length (LW) of the respective rolling body (W) greater than the simple diameter (DW) of the rolling element (W) is. Rolling bearing according to at least one of claims 1 to 6, characterized in that the outer race (BA) with an inner peripheral edge (BA) 3 ) and the inner raceway (BI) with an outer peripheral edge ( 4 ) with these two peripheral edges ( 3 . 4 ) have substantially the same radial distance (D) to the bearing axis (X). Rolling bearing according to at least one of claims 1 to 7, characterized in that a cage device ( 5 ) is provided, for guiding the rolling elements (W) under a predetermined rolling element circumferential distance. Rolling bearing according to at least one of claims 1 to 8, characterized in that a sealing device is provided, for sealing a between the inner ring ( 2 ) and the outer ring ( 1 ) defined annular gap (S1, S2). Wheel bearing with: - A first rolling bearing device (W1), - one second rolling bearing device (W2), and - Rolling elements (W, WK1, WK2) which in one between the inner raceway (B1, BI1, BI2) and the outer raceway (BA, BA1, BA2) defined space (B) are recorded, - in which the two rolling bearing devices (W1, W2) a respective outer rolling body raceway (BA1, BA2) each facing a bearing axis (X) and a inner rolling element raceway Include (BI1, BI2), - in which at least one of the outer raceways (BA1, BA2) in an axial section plane containing the bearing axis (X) is curved concavely under a track profile radius (P), characterized - that the Rolling elements (W) the first and / or second rolling bearing device (W1, W2) are designed as barrel rollers and in a along a Wälzkörperachse (Y) extending rolling element axial section plane a below a profile radius (R) crowned bulging Wälzkörperquerschnitt have, and - that the rolling element raceways (BI, BA) are formed such that the rolling bodies (W, WK1, WK2) are guided in such a way, that their rolling body axes (Y) inclined to the bearing axis (X) at an angle (K, K1, K2) are aligned. Wheel bearing according to claim 10, characterized in that that the profile radius (R) is larger as the center diameter (DW) of the respective rolling element (W). Wheel bearing according to claim 10, characterized in that that the profile radius (R) and the path profile radius (P) are smaller as the distance (A) one of the bearing axis (X) maximally spaced Wälzkörperlaufspur (S) the outer raceway (BA). Wheel bearing according to claim 10, characterized in that that a rolling bearing (W1 or W2) is designed in the aforementioned Schrägonnenbauart, and that, higher resilient as a row of balls that absorbs higher radial forces. Wheel bearing according to at least one of claims 10 to 13, characterized in that also the second rolling bearing (W2 or W1) is executed in the aforementioned Schrägonnenbauart. Wheel bearing according to at least one of claims 10 to 13, characterized in that the second rolling bearing (W2 or W1) by Rolling elements of a other design is designed as a skew roller. Wheel bearing according to at least one of claims 10 to 15, characterized in that at least one of the outer Wälzkörperbahnen (BA, BA1, BA2) by a hub carrier ( 8th ). Wheel bearing according to at least one of claims 10 to 16, characterized in that at least one of the inner Wälzkörperbahnen (BI1 and / or BI2) of the first or the second rolling bearing (W1 and / or W2) by a ring element ( 2 ) is formed. Wheel bearing according to at least one of claims 10 to 17, characterized in that the Wälzkörperbahnen (BA, BI) are formed such in that the axial centers of the rolling elements (W) circulate on pitch circles of substantially equal diameters. Wheel bearing according to at least one of claims 10 to 17, characterized in that the Wälzkörperbahnen (BA, BI) such are formed, that the axial centers of the rolling elements (W) of the first rolling bearing (W1) rotate on a pitch circle (TK1), which is unlike the pitch circle (TK2) on which the rolling elements W2 the second rolling bearing (W2) is round.