DE102005033355A1 - Radial rolling bearing includes elastomer ring mounted in circumferential ring groove in rolling face of individual rolling bodies as tension element to pretension bodies permanently and radially towards both tracks of bearing rings - Google Patents

Abstract

The radial rolling bearing has an outer bearing ring (2) with inner track (3) and an inner bearing ring (4) with outer track (5) with several rolling bodies (6) rolling inbetween held evenly spaced in a bearing cage (8). One or more elastic tension elements (9) which prevent slip between the rolling bodies and bearing rings are each formed as an elastomer ring (11) mounted in a circumferential ring groove (10) in the rolling face (7) of one or all rolling bodies. The elastomer ring projects by its profiled cross-section beyond the rolling faces of the relevant body to generate a permanent radial pretension on the rolling bodies in the direction of both tracks of the rings. To reduce their load pick-up the driving rolling bodies (12) can have a slightly smaller diameter than the remaining bodies and their cage pockets are formed with additional recesses in the axial webs for the protruding elastomer rings.

Description

Territory of invention

The The invention relates to a radial rolling bearing the preamble-forming features of claim 1, and they is particularly useful when storing lightly loaded shafts in heavy machinery, such as the vertical shaft of a cone crusher, feasible.

background the invention

the Specialist in rolling bearing technology It is well known that radial rolling bearings with sufficient load have an optimal kinematic operating state, in which the rolling elements without to slide on the raceways of the inner and outer bearing ring roll. Furthermore, it is known from low loaded, heavy radial rolling bearings, that is from the rolling elements and their camp cage existing rolling element set due to the friction in the bearing or due to the high Mass force of the rolling element set and the low contact force between the Wälzkör cars and the tracks not rotates with the kinematic speed. The speed of the rolling element remains consequently opposite the kinematic speed back, so that the rolling elements in a kinematic not optimal state by the between these rolling elements and at least one career slip is present. It can be at the contact surfaces between the rolling elements and the runway build up a lubricating film, but at a sudden Speed or load change destroyed so that at the slip-contact points within short Time is no longer sufficient lubricating film. This has to Consequence, that it leads to a metallic contact of the raceway with the Rolling comes and these slide on the track until the rolling elements on the kinematic speed are accelerated. This size Differential speed between the raceway and the rolling elements as well The lack of a separating lubricating film is thus the reason that it in the surfaces the raceway and the rolling elements to high tangential tensions comes with the strongest signs of wear, Such as roughening of the tracks, Materialaufreißungen and lubrication mostly associated with micropittings and premature Failure of the radial rolling bearing to lead.

To avoid this slip effect and the resulting disadvantages was therefore due to the DE 932 942 a roller bearing proposed with increased rolling resistance, which consists essentially of an outer bearing ring with an inner raceway and an inner bearing ring with an outer raceway and a plurality between the bearing rings on the raceways rolling rolling elements, which are spaced by a bearing cage in the circumferential direction at regular intervals be held. In this rolling bearing, a circumferential groove is axially centrally in the track of the outer bearing ring incorporated, in which an elastic, acting in the direction of the bearing longitudinal clamping element is arranged, which protrudes slightly beyond the raceway of the outer bearing ring and the rolling elements pressed against the raceway of the inner bearing ring ,

A similar solution for preventing slippage between the rolling elements and their raceways is also by the DE 1 947 726 A1 previously known. In the disclosed in this document cylindrical roller bearing having substantially the same structure as the rolling bearing described above, two step-shaped shoulders are incorporated into the raceway of the inner bearing ring at both axial edge portions in which two plastic rings formed with a larger outer diameter than the bearing ring force or positively secured are that press the rolling elements against the raceway of the outer race.

adversely in the known radial rolling bearings However, it is that in the raceways of the inner or the outer bearing ring arranged grooves or heels in any case have a negative effect on the load capacity of the bearings, because with it the bearing length the raceways for the rolling elements is shortened. The carrying length the raceways for the rolling elements is However, one of the essential parameters of the load rating for the service life calculation, so that such radial bearings for Achieve the intended bearing length of the tracks costly axial wider and / or with reinforced Storage rings must be trained. additionally have the in the raceways of the inner or the outer bearing ring arranged grooves or heels still proved to be disadvantageous in that also the carrying capacity the bearing rings against external constraining forces, such as for example, in the bearing seat or during handling in production, weakened becomes. An arranged in a groove in the raceway of the outer race Plastic ring also has the disadvantage that this by his flexibility change his form greatly can and thus makes the bearing assembly difficult.

Task of invention

Based on the stated disadvantages of the solutions of the known prior art The invention therefore has the object of the invention, a radial rolling bearings, especially for the storage of lightly loaded shafts in Schwerma machines to conceive, in which to avoid slippage between the rolling elements and their tracks, a clamping element is used, with neither the bearing length of the raceways shortened for the rolling elements nor the bearing capacity of the bearing rings is weakened against external constraining forces and which is characterized by a simple mountability.

description the invention

According to the invention this Task at a radial rolling bearing solved according to the preamble of claim 1 such that each clamping element as arranged in a circumferential annular groove in the tread of individual or all rolling elements Elastomer ring is formed, with its profile cross-section the treads surmounted by the respective rolling elements and a permanent radial preload on the rolling elements in Direction of both raceways of the bearing rings generated.

preferred Embodiments and developments of the invention formed radial roller bearing are in the subclaims described.

After that it is according to claim 2 in the inventively designed radial bearings provided that in the tread single or all rolling elements either axially centered an annular groove or alternatively axially laterally two annular grooves is arranged with each rectangular profile cross section / are, in which either an elastomer ring or two elastomer rings is attached with each circular profile cross-section is / are. The embodiment with an elastomeric ring secured in an axially central annular groove has the advantage that it is easier to manufacture and thus cost-effective is while the embodiment with two elastomer rings attached in two lateral grooves has the advantage that thus adverse Schränkbewegungen the rolling elements almost can be excluded. The Fixation of the elastomeric rings in the annular grooves takes place by their elasticity, the arrangement of circular in profile cross-section elastomeric rings in annular grooves with a rectangular profile cross section the advantage has that the elastomeric rings under load of the corresponding rolling elements without bruising Completely be displaced into the annular grooves and thus before early Wear are protected.

To Claim 3, it is a further feature of the invention formed Radial roller bearing, that of the total number of rolling elements is preferred only a small number arranged at regular intervals to each other Rolling element with a Ring groove and an elastomeric ring is formed in its tread, which the larger number of conventionally trained Rolling elements over the bearing cage drives. As are enough while three on the circumference of the raceways evenly distributed Rolling elements proved thus due to their radial tension between the bearing rings as drive elements for the remaining Rolling elements and for the bearing cage serve. About that In addition, thereby, the number of a shortened by the annular grooves carrying Length having Rolling on reduced to a minimum, so that the rolling elements without ring groove and elastomer ring continue the original Load capacity exhibit and the carrying capacity of the radial roller bearing Overall, only slightly reduced.

When advantageous embodiment of the inventively embodied radial roller bearing it is by claim 4 finally nor suggested that the driving rolling elements reduce their Load bearing a slight smaller diameter than the rest Have rolling elements and that the cage pockets this rolling element in their axial webs with additional Recesses for the above the treads protruding from these rolling elements Elastomer rings are formed. By training the driving Rolling elements with a slight smaller diameter than the other rolling elements thus the driving rolling elements from an overload protected but at the same time as supporting elements of the radial rolling bearing with reduced load absorption used. This also contributes helping to increase the carrying capacity an inventively designed radial roller bearing Overall, only slightly reduced. The additional Recesses for the above the treads the water rolling bodies protruding Elastomeric rings in the cage pockets this rolling body on the other hand serve the free rotation of these rolling elements and are preferred as formed in profile rectangular notches.

The inventively embodied radial roller bearing thus has the advantage over the known from the prior art radial rolling bearings that to avoid slippage between the rolling elements and their tracks no clamping elements in the bearing rings but one or more elastomeric ring (s) are used on only individual rolling elements and Thus, neither the bearing length of the raceways for the rolling elements shortened nor the bearing capacity of the bearing rings is weakened against external constraining forces. Although in the formed with one or more elastomeric rings also their bearing length is shortened, however, the associated payload reduction moves compared to known radial roller bearings with one or two complete circumferential groove (s) in the running surface of the bearing rings in negligible sizes. In addition, the inventively designed radial roller bearing opposite radial roller bearings with plastic rings as clamping elements characterized by a simple mountability of the elastomeric rings used, since they can be easily slipped over the rolling elements due to their high elasticity. Thereby, the mounting of an inventively designed radial roller bearing is similar cost as that of a conventional radial roller bearing. However, since the slip effect described above between the rolling elements and their raceways occurs not only in radial roller bearings but also in axial rolling bearings, it is of course also possible to form them in accordance with the invention.

Short description the drawings

A preferred embodiment of the inventively designed radial roller bearing will be explained in more detail with reference to the accompanying drawings. there demonstrate:

1 an enlarged cross-section through a first embodiment of an inventively designed radial roller bearing;

2 an enlarged cross section through a second embodiment of an inventively designed radial roller bearing;

3 an overall view of a longitudinal section through an inventively designed radial roller bearing;

4 an enlarged view of a cage pocket of the inventively designed radial roller bearing with a rolling element.

Full Description of the drawings

From the 1 and 2 clearly goes each one designed as a cylindrical roller bearing radial roller bearing 1 which essentially consists of an outer bearing ring 2 with an inner career 3 and an inner bearing ring 4 with an outer career 5 as well as a variety between the bearing rings 2 . 4 arranged rolling elements 6 that exists with their treads 7 on the careers 3 . 5 the bearing rings 2 . 4 unroll and through a storage cage 8th be held in the circumferential direction at regular intervals to each other. Furthermore, in 1 to see that in this radial rolling bearing 1 to prevent slippage between the rolling elements 6 and the bearing rings 2 . 4 within the radial rolling bearing 1 one or more elastic clamping elements 9 are arranged, which are the rolling elements 6 between the careers 3 . 5 the bearing rings 2 . 4 radially bias.

In addition, the 1 and 2 removable, that each of these clamping elements 9 according to the invention as in a circumferential annular groove 10 in the tread 7 single or all rolling elements 6 arranged elastomeric ring 11 is formed, with its profile cross-section of the treads 7 the respective rolling elements 6 surmounted and a permanent radial preload on the rolling elements 6 in the direction of both careers 3 . 5 the bearing rings 2 . 4 generated.

At the in 1 shown first embodiment is in the tread 7 single or all rolling elements 6 only axially centrally an annular groove 10 arranged in the only one elastomeric ring 11 is attached with circular profile cross-section, while at the in 2 illustrated second embodiment in the tread 7 single or all rolling elements 6 axially laterally two annular grooves 10 . 10 ' are arranged in each case with a rectangular profile cross-section, in which accordingly two elastomer rings 11 . 11 ' are fastened in each case with a circular profile cross-section. The elastomer rings 11 . 11 ' are only slightly smaller than the outer diameter of the rolling elements in the inner diameter 6 designed so that these easily during assembly over the rolling elements 6 can be overstretched and by their elasticity in the annular grooves 10 . 10 ' be fixed. Out 3 is further seen that in the radial rolling bearing exemplified 1 from the total number of rolling elements 6 only three uniformly spaced rolling elements 12 with an annular groove 10 and an elastomeric ring 11 in her tread 7 are formed and that these rolling elements 12 the larger number of conventionally trained rolling elements 6 over the camp cage 8th drives. In this case, the driving rolling elements 12 to reduce their load bearing a slightly smaller diameter than the other rolling elements 6 so that they are protected from overloading but at the same time as supporting elements of the radial rolling bearing 1 be used with reduced load absorption.

By 4 Finally, it becomes clear that the cage pockets 13 the driving rolling elements 12 in the bearing cage 8th in their axial webs 14 with additional recesses 15 for the over the treads 7 this rolling element 12 protruding elastomer rings 11 are formed. These recesses 15 are clearly visible formed by rectangular notches and serve the free rotation of the driving rolling elements 12 ,

1

radial bearings

2

outer bearing ring

3

inner career

4

internal bearing ring

5

outer career

6

rolling elements

7

treads

8th

bearing cage

9

clamping element

10

ring groove

10 '

ring groove

11

elastomer ring

11 '

elastomer ring

12

driving rolling elements

13

cage pockets

14

axial webs

15

recesses

Claims (4)

Radial rolling bearing, in particular for the storage of lightly loaded shafts in heavy machinery, which consists essentially of an outer bearing ring ( 2 ) with an inner raceway ( 3 ) and an inner bearing ring ( 4 ) with an outer raceway ( 5 ) and a plurality between the bearing rings ( 2 . 4 ) arranged rolling elements ( 6 ), with their treads ( 7 ) on the raceways ( 3 . 5 ) of the bearing rings ( 2 . 4 ) and through a bearing cage ( 8th ) are held in the circumferential direction at regular intervals to each other, wherein to avoid slippage between the rolling elements ( 8th ) and the bearing rings ( 2 . 4 ) within the radial rolling bearing ( 1 ) one or more elastic tension elements ( 9 ) are arranged, which the rolling elements ( 6 ) between the tracks ( 3 . 5 ) of the bearing rings ( 2 . 4 ) radially bias, characterized in that each clamping element ( 9 ) than in a circumferential annular groove ( 10 ) in the tread ( 7 ) individual or all rolling elements ( 6 ) arranged elastomer ring ( 11 ) is formed, with its profile cross-section of the running surfaces ( 7 ) of the respective rolling bodies ( 6 ) and a permanent radial bias on the rolling elements ( 6 ) in the direction of both careers ( 3 . 5 ) of the bearing rings ( 2 . 4 ) generated. Radial rolling bearing according to claim 1, characterized in that in the tread ( 7 ) individual or all rolling elements ( 6 ) either axially centrally an annular groove ( 10 ) or alternatively axially laterally two annular grooves ( 10 . 10 ' ) is arranged in each case with a rectangular profile cross-section, in which / which either an elastomeric ring ( 11 ) or two elastomer rings ( 11 . 11 ' ) is attached with each circular profile cross-section is / are. Radial rolling bearing according to claim 2, characterized in that of the total number of rolling elements ( 6 ) preferably only a small number of uniformly spaced rolling elements ( 12 ) with an annular groove ( 10 ) and an elastomeric ring ( 11 ) in its tread ( 7 ) is formed, which the larger number of conventionally trained rolling elements ( 6 ) over the bearing cage ( 8th ) drives. Radial rolling bearing according to claim 3, characterized in that the driving rolling bodies ( 12 ) to reduce their load bearing a slightly smaller diameter than the other rolling elements ( 6 ) and that the cage pockets ( 13 ) of these rolling elements ( 12 ) in their axial webs ( 14 ) with additional recesses ( 15 ) for the over the treads ( 7 ) of these rolling elements ( 12 ) protruding elastomer rings ( 11 ) are formed.