DE102009036688A1 - Roller bearing for use as e.g. tapered roller bearing to support transmission shaft of housing of transmission, has additional load-bearing mechanism transmitting axial loads between roller bodies and inner and/or outer ring board - Google Patents

Abstract

The bearing (1) has an inner ring (2) comprising an inner ring board (3), an outer ring (4) comprising an outer ring board (5), and multiple roller bodies (6) e.g. cylindrical rollers, for transmission of radial loads. The roller bodies are arranged between the inner ring and the outer ring. An additional load-bearing mechanism (7) transmits axial loads between the roller bodies and the inner ring board and/or the outer ring board. The load-bearing mechanism is partly made of metal or metallic alloy such as through-hardening steel or bronze, and/or friction-reducing material such as plastic.

Description

Field of the invention

The The invention relates to a roller bearing.

When Rolling bearings are called bearings in which two are related movable bodies, in the case of support a shaft an inner ring and an outer ring, through the rolling elements rolling off the two bodies are separated. Rolling bearings for the transmission of loads in the radial direction of the bearing of an inner ring, which for example, on a rotating shaft within a respect the wave fixed housing is arranged on one Outer ring, which is arranged in this housing and fixed, are well known. Such bearings can be designed as roller bearings whose Rolling elements in the form of different roles Geometry present.

As well It is well known rolling bearings as cylindrical roller bearings perform, in which the inner peripheral surface the outer ring and the outer peripheral surface the inner ring are each substantially cylindrical in shape, parallel to each other and to the bearing axis and in which the rolling elements are formed in the shape of cylindrical rollers.

Such Cylindrical roller bearings are very suitable for transmission loads in the radial direction and for the application high speeds. In addition, they are at the same time compact dimensions, also for the transmission of axial loads, as for example by the helical gearing of a with the shaft rotatably connected gear, such as a Use of the cylindrical roller bearing as a fixed bearing for the storage of a Gear shaft, arise, suitable. The inclusion of axial loads in at least one direction is usually for example This allows both the outer ring as well as the inner ring with at least one circumferential board, the so-called outer ring board or inner ring board provided are. These rims of the inner and outer rings are on axially opposite sides of the rolling element arranged.

at an axial load of a cylindrical roller bearing of this construction run through the rotation of the inner ring opposite to the Outer ring the cylindrical rollers during their rolling movement to inner ring board and outer ring board. The axial force is from the inner ring board to the rolling elements and from this transferred to the outer ring board. This arises a sliding contact between the rolling elements facing inner surfaces of the shelves and the adjacent End faces of the rolling elements (on-board contact). A friction occurring in this way in the contact of the rolling elements with the Borden leads through the generated frictional heat to a more or less large temperature increase and to an increased wear on the rubbing stressed surfaces. These properties should be avoided since they result in lower allowable bearing speeds being able to lead. Additionally, in the episode an increased load of used for bearing lubrication Lubricants occur, whereby their aging is accelerated. These must then be replaced consuming.

moreover is due to the sliding contact of board and rolling elements resulting sliding friction the distribution of Wälzkörperdrehzahlen along the bearing circumference, which occurs cyclically Deceleration and acceleration of the returned individual rolling elements can be unfavorably influenced.

A Possibility to reduce friction in sliding contact when absorbing axial loads consists in the combination of pure radial rolling bearing with a purely axially supporting Roller bearing. Such a combination may, for example, also by arranging the two rolling bearings within a Sheet metal molded one-piece socket can be achieved if this is the occurring loads and therefore no massively designed bearing rings are required.

Such an arrangement is based on the example of a radially supporting roller or needle bearing, which is combined with an axially supporting roller or needle roller bearing, in the German Patent DE 1 525 205 C described. However, the problem with a combination of a separate radial rolling bearing with an axial roller bearing also designed separately is that the resulting bearing assembly is not very compact and requires a relatively large space, which make these rolling bearings cost-intensive as a result.

The transmission of an axial load acting on a radial roller bearing from a shoulder of the shaft to a flange of an outer sleeve bent from thin sheet metal is described in the German Utility Model DE 1 910 794 U described. In this bearing, an inner raceway for the radial bearing is arranged directly on the shaft without forming an inner ring. The transmission of the axial force takes place by means disposed between the shaft shoulder and the flange of the outer bush balls or rollers, if necessary via a voltage applied to this paragraph ring.

In highly loaded bearings, however, it is advantageous to provide a separate inner ring, so that in case of wear of the formed on the bearing inner race rolling element no Replacement of the entire shaft is necessary. In addition, a bearing ring provided as an independent component can be more easily surface-coated or heat-treated without having to consider this in the production of the shaft.

Another way to reduce the friction during contact of the rollers with axially acting guide surfaces of the bearing rings shows the FR 731 895 A , A radially supporting roller bearing is provided with a cage for guiding the rollers. The front side of the cage and a flange of the outer ring form contact surfaces for an additional thrust ball bearing. In this case, the transmission of an axial load is not possible. Only the weight of Radialwälzkörper is supported. In another in the FR 731 895 A shown roller bearing the transfer of an axial load via an annular collar of the inner ring is accomplished on the flange of the outer ring. Here, however, the radially supporting rollers continue to run, especially in the FR 731 895 A described vertical mounting position, rubbing on the annular collar of the inner ring by its own weight.

It is therefore an object of the present invention, a for recording to provide thrust bearing suitable for axial loads, which guaranteed in every mounting position a reduced friction in the on-board contact and designed to save space, especially in the axial direction can be.

These Task is inventively by a roller bearing solved with the features of claim 1.

Accordingly a roller bearing is provided, with an inner ring, which has an inner ring board, with an outer ring, which has an outer ring board comprising, with a plurality of rolling elements for transmission radial loads, between the inner ring and the outer ring and with an additional load-bearing device, for transmitting axial loads between at least one of the rolling elements and the inner ring board and / or the outer ring board is arranged.

The The invention relates to roller bearings for transmission radial and axial loads, for example, for the storage of transmission shafts in housings, which in every mounting position a reduced friction guaranteed in on-board contact of the roles and thereby in axial Direction can be carried out space-saving. By means of the Roller bearing according to the invention can axial loads with low axial space requirement and with less Friction of rolling elements in on-board contact in each Installation position can be recorded. This is by the additional load-bearing device possible. The between the rolling elements and the inner ring board, and / or between the rolling elements and the outer ring board, provided additional load-bearing device is advantageous because when working an outer Axial load on the one hand and also by a force of gravity the rolling elements caused axial power contribution in the case of a different than horizontal mounting position of the roller bearing On the other hand, the sliding friction in the on-board contact can be reduced. Thus, axial loads with low axial space requirements and with low friction of the rolling elements in the on-board contact be included in any mounting position.

Another advantage of the roller bearing according to the invention is that the inner ring and the outer ring of the roller bearing with the usual and standardized external dimensions and installation dimensions, for example DIN 5412 , can be manufactured, since only the internal structure of the roller bearing relative to a roller bearing of conventional design changes. This is advantageous for the use of the roller bearing according to the invention, for example, in the redesign of machines, but especially in an exchange of conventional roller bearings by an inventive roller bearing with reduced friction in board contact.

advantageous Embodiments and developments emerge from the others Subclaims and with reference to the figures of the drawing specified embodiments.

at a preferred embodiment of the invention Roller bearing is for transmitting axial loads of the For example, connected to a shaft inner ring of the roller bearing on the example defined in a housing outer ring the outer ring board on the outer ring on a re an axial direction of the roller bearing opposite the inner ring board Page provided. In addition, of course on both bearing rings, both to the outer ring as well on the inner ring, two shelves are provided to loads pick up in two directions along the axial direction to be able to. To ensure mountability In this case, at least one board can also be considered loose, thus not integral with the associated bearing ring connected board be executed.

Further Preferably, the additional load bearing device a support member which relative to the inner ring and / or to the outer ring and / or to the rolling elements is movably arranged. In particular, the support element is in the Circumferential direction of the roller bearing with respect to the bearing rings and the rolling elements as well as opposite the positions of the axes of rotation of the individual rolling elements rotatably arranged.

In a further preferred embodiment of the invention Roller bearing is the additional load bearing device for transmitting axial loads from the inner ring to the Outer ring between at least one of the rolling elements and the inner ring board provided, but at the same time between at least one of the rolling elements and the outer ring board arranged. Are also, for example, on both bearing rings respectively provided two shelves, so can the additional load-bearing device for transmitting axial loads in both directions along the bearing axis also between each of the outer ring rims and at least one of the rolling elements, as well as between each of the inner ring rims and at least one of the rolling elements be provided.

Further preferred is a cage or a cage-like Structure provided for guiding the rolling elements. This cage ensures that the rolling elements the desired, ie defined, predetermined distances have each other in the circumferential direction of the roller bearing. A mutual rubbing contact of adjacent rolling elements is thereby effectively avoided. Such a cage can, for example solid from a metallic material, such as a special brass or made of steel, but also by deformation of sheet steel become. Also, the cage can be made of plastic be.

advantageously, is the cage for guiding the rolling elements designed as a solid cage made of a metal.

Yet more preferably is the additional load-bearing device in sliding contact with a surface of the inner ring flange or the outer ringboard and with an adjacent to this End face of the at least one rolling body, that axial loads from the inner ring board or the outer ring board over the additional load carrying device on the at least a rolling element are transferable. The Frictional stress on the surfaces of the inner ring flange or the outer ring board or both and the end faces of the rolling element in a sliding contact between Board and rolling elements in the conventional Way is distributed in this development on two sliding contacts. These are in detail the sliding contact between the board surface and the additional load-bearing device and the Sliding contact between the additional load bearing device and the end face of the rolling element.

In a preferred, advantageous development of the invention Roller bearing has the additional load-bearing device a plurality of Axialwälzkörpern on. About that In addition, at least one axial end face of the cage formed with a track and the Axialwälzkörper are in rolling contact with a surface in the manner the inner ringboard or the outer ringboard and with the track, that axial loads from the inner ring board or from the outer ring board over the additional load bearing device is transferable to the cage. The use of Axialwälzkörpern for transmission An axial load is of particular advantage because the Axialwälzkörper roll on the surfaces of the shelves, thus essentially rolling friction occurs and therefore hardly any power losses and wear caused by sliding friction.

In a development is to guide the Axialwälzkörper a thrust bearing cage provided. The thrust bearing cage serves to guide the Axialwälzkörper between the trained on the front side of the cage Raceway and the inner surface of the adjacent inner ring or outer ring boards, and avoid mutual contact the Axialwälzkörper during their rolling motion on the track. Also, the thrust bearing cage can be as massive Metal cage be formed, but also by forming be made of sheet metal or made of plastic.

Further Preferably, the cage in the range of at least one of his axial end faces a substantially in the radial direction extending flange. The raceway is ring-shaped formed and arranged in the region of the flange, and the flange is at its radially inner or outer end provided with a circumferential projection, which leads to the leadership serves the thrust bearing cage. This way becomes an uncontrolled Emigration of Axiallagerkäfigs from its desired location prevented.

According to one Continuing are the Axialwälzkörper in shape formed by needles. The use of needles to form a axially acting needle bearing between the cage and one or several Lagerringborden is special in the present case advantageous because axially acting needle bearings in the axial direction clearly shorter than corresponding axially acting cylindrical roller bearings can be executed. This way you can the space requirement optimized and the roller bearing according to the invention be carried out in a space-saving manner.

According to a further preferred development, the additional load-bearing device is designed as a closed in the circumferential direction, annular sliding disk. If this is required to ensure the mountability of the roller bearing, then the sliding disk can also be designed as a circumferentially open, slotted ring or as a multi-part ring. The dimensions of the sliding disk are advantageously chosen so that a free relative movement of the ringför migem sliding disk and the adjacent inside surface of the board is possible. In this way, the sliding disk abuts on the surface of the adjacent board and on the adjacent front surface of the rolling element and can slide on both surfaces. An advantage of this embodiment is also that the respective relative speeds of the sliding components on each other in both sliding contacts compared to the conventional solution, which consists in a direct contact of the inner surface of the board and the end face of the rolling elements, is significantly reduced. In this way, a structurally very simple and robust roller bearing is created in which a cost-effective measures a reduced friction in the absorption of axial loads is guaranteed.

Preferably are the inner ring board or the outer ring board or both integral with the inner ring or the outer ring educated.

According to one Further advantageous development are the surfaces the additional load-bearing device in whole or in part provided with a sliding friction reducing coating. On This way, the friction in the absorption of axial forces be further reduced by the roller bearing. If desired is, alternatively or additionally, the surfaces the inner ring board or the outer ring board or both partly or completely, but especially their facing the rolling elements, in the axial direction to the bearing center facing surfaces as well with a superficial coated friction reducing and / or wear-reducing layer become. Such a partial or complete coating can also on the facing in the axial direction faces be provided of the rolling elements.

According to one further training is the additional load-bearing facility from a friction-reducing material, for example from a suitable plastic, manufactured for this purpose.

at a further advantageous embodiment of the invention Roller bearing is the additional load bearing device at least partially made of a metal or a metallic one Alloy made. For this purpose, for example, a through-hardening Steel, as well as for the production of bearing rings and the rolling element is widespread, or a bronze, such as a lead or tin bronze, into consideration. Are conceivable but also sliding discs for the load-bearing device.

According to one Particularly advantageous development of the invention are the rolling elements formed of the roller bearing in the form of cylindrical rollers. Cylindrical roller bearings are particularly suitable for absorbing high radial loads and for use at high speeds.

Farther can the roller bearing according to the invention in a another embodiment as a tapered roller bearing and the rolling elements be designed as tapered rollers, resulting in a combined load from radial and comparatively high axial loads advantageous is.

The above embodiments and developments can be - if which makes sense - to combine with each other.

The Invention will be described below with reference to the schematic figures specified embodiments explained in more detail. It show here:

1 in a radial sectional view of a first embodiment of the roller bearing according to the invention,

2 in a radial sectional view of a second embodiment of the roller bearing according to the invention,

3 in a radial sectional view of a third embodiment of the roller bearing according to the invention,

4 in a radial sectional view of a fourth embodiment of the roller bearing according to the invention,

5 in a radial sectional view of a fifth embodiment of the roller bearing according to the invention.

In The figures are the same and functionally identical elements - if nothing else is indicated - with the same reference numerals been provided.

1 shows a first embodiment of a roller bearing according to the invention 1 , The roller bearing 1 has an inner ring 2 and an outer ring 4 , the so-called bearing rings, on. The inner ring 2 and the outer ring 4 are arranged concentrically to each other. The outer ring 4 of the rolling bearing 1 is z. B. in an in 1 not shown, fixed gear housing, for example, held with a clearance fit, while the inner ring 2 on a shaft rotating about its longitudinal axis A. 8th can sit up. By choosing a transitional or interference fit is the inner ring 2 through a tight fit with the shaft 8th connected. The longitudinal axis of the shaft 8th coincides with the axial direction A, which also represents the longitudinal axis of the roller bearing together. Between the inner ring 2 and the outer ring 4 are along the circumference of the bearing rings more rolling elements 6 at regular intervals distributed. In the illustrated embodiment, the rolling elements 6 designed as cylindrical rollers.

The outer ring 4 has in this embodiment of the roller bearing according to the invention 1 two circumferentially extending outer annular rims 5 on which at two axial ends of the outer ring 4 are provided. In addition, the inner ring 2 at its one axial end an inner ring board 3 in the same way as the outer ring rims 5 Circumferentially provided in the circumferential direction. These storage ring shelves 3 . 5 are each made in one piece with the associated bearing ring. Integral in this context means inseparable, z. B. made of a single material.

In the axial direction A is the outer ring 4 on a left hand side of a flange of the transmission housing, not shown, while the inner ring 2 with its right-hand axial end, which the inner ring board 3 has, at one in the 1 indicated by dashed lines, on the shaft 8th fitted sleeve rests. The axial dimension of the rolling elements 6 is slightly less than the distance between the two outer ring rims 5 in the axial direction A.

Between an outer ring board 5 and the illustrated rolling elements 6 is an additional load bearing facility 7 arranged.

Will now be the wave 8th offset in a rotational movement about its longitudinal axis A, so also rotates on the shaft 8th pressed on inner ring 2 around the axis A, while the outer ring 4 opposite the wave 8th stationary. The rolling elements roll 6 , which contact the two bearing rings in the range also not shown raceways, on the raceways, and thus allow the transmission of a force in the radial direction R from the inner ring 2 on the outer ring 4 ,

A simultaneous load on the outer ring 4 in the axial direction A, as in FIG 1 indicated by arrows, caused by a contact between the additional load-bearing device 7 and the adjacent outer ring board 5 a transmission of the axial force on the additional load-bearing device 7 ,

2 shows a further embodiment of a roller bearing according to the invention in a radial sectional view. In contrast to the general embodiment of the 1 Here are the extra load bearing facility 7 as sliding disks 17 . 18 educated.

Between the inner ring board 3 and the rolling element 6 Here is a first sliding washer 17 intended. This first sliding washer 17 has the shape of a ring closed in the circumferential direction. The first sliding washer 17 is not with a press fit on the inner ring 2 but has this opposite game. In this way is the sliding disk 17 opposite the rolling elements 6 and opposite the inner ring board 3 movable. In particular, the first sliding washer 17 opposite the inner ring 2 rotatable about the axial axis A.

Between one of the two outer ring rims 5 , which from the rolling element 6 seen in the axial direction A the inner ring board 3 opposite, and the rolling element 6 is another sliding washer 18 intended. Also this other sliding washer 18 has the shape of a closed ring, which with respect to the outer ring 4 is arranged rotatable. Both sliding disks 17 . 18 are thus opposite the two bearing rings 2 . 4 and against the rolling elements 6 , In particular also with respect to the variable circumferential position of the instantaneous axes of rotation of the rolling elements 6 , rotatable. In the axial direction A of the roller bearing 1 corresponds to the axial extent of the rolling elements 6 taken together with the axial thicknesses of the two sliding discs 17 . 18 essentially with little play the axial distance between the two outer ring rims 5 ,

The outer ring 2 , the inner ring 4 and the rolling elements 6 are made in the shown roller bearing from a hardening bearing steel. Furthermore, the sliding discs 17 . 18 in the embodiment according to the 2 each also made of a hardening steel and coated with a sliding friction-reducing and wear-resistant surface coating.

The sliding disks 17 . 18 slide at an axial load of the roller bearing 1 during the rotation of the shaft 8th on the surfaces 10 the shelves 3 . 5 as well as on the frontal surfaces 11 the rolling elements 6 , As a result, a direct sliding and rubbing contact of the Wälzkörperstirnflächen 11 with the in-board surfaces 10 , which is one of the speed of the shaft 8th resulting relative speed of the rolling elements 6 and the shelves 3 . 5 takes place, converted into two sliding contacts, each with the opposite reduced relative speed. Due to the advantageously existing friction-reducing and wear-resistant surface coating of the two sliding discs 17 . 18 is the sliding contact between the respective board 3 . 5 and the sliding washer 17 . 18 on the one hand, and between the sliding washer 17 . 18 and the rolling element 6 on the other hand optimized with the aim of low sliding friction.

The in the 2 as sliding disks 17 . 18 trained additional load bearing facility 7 is thus in sliding contact with the surface 10 of the inner ringboard 3 and with the adjacent to this end face 11 of the rolling element 6 , so as in sliding contact with the surface 10 of the outer ringboard 5 and with the adjacent to this end face 11 of the rolling element 6 in that axial loads from the inner ring board 3 by means of the sliding disk 17 the additional load-bearing device 7 on the rolling elements 6 can be transmitted. The way in the rolling elements 6 initiated axial loads can in the roller bearing according to the invention 1 further by means of the sliding disk 18 the additional load-bearing device 7 on the outer ring board 5 be transmitted.

By training the additional load-bearing device 7 as sliding disks 17 . 18 is a reduction in friction in on-board contact in any mounting position of the roller bearing 1 achieved in a structurally particularly simple and space-saving manner. In this solution, only a few additional components compared to a conventional roller bearings are required, which are also finished with little extra effort. The low number of components also leads to a robust and inexpensive roller bearings.

Of course, that can be done in 2 shown roller bearings 1 if desired, even with only one, either the inner ring board 3 touching sliding disk 17 , or the outer ring board 5 touching sliding disk 18 be executed. In this way, only one of the on-board contacts of the rolling elements 6 , either with the inner ring board 3 or the outer ring board 5 Optimized for friction reduction.

3 shows a third embodiment of a roller bearing according to the invention in a radial sectional view. In contrast to the embodiment in the 2 has the roller bearing in 3 in addition a cage 9 for guiding the rolling elements 6 on. This cage 9 can in solid construction, z. B. made of a special brass, steel or sheet steel or plastic.

4 shows a fourth embodiment of a roller bearing according to the invention in a radial sectional view. Unlike the in 2 illustrated roller bearings 1 are now on both bearing rings 2 . 4 as in the known roller bearing design NUP, two circumferential ribs 3 . 5 . 23 intended. To ensure the mountability of the bearing, the right side inner ring board is 23 not integral with the inner ring 2 but executed as a loose board.

Also with the roller bearing 1 of the 4 is the axial dimension of the rolling elements 6 slightly smaller than the distance between the two outer ring rims 5 in the axial direction A. Likewise, the axial dimension of the rolling elements 6 also less than the axial distance between the two inner ring rims 3 . 23 ,

Between the loose inner ring board 23 and the rolling element 6 is a sliding washer 19 , between the fixed inner ring board 3 and the rolling element 6 a sliding washer 22 intended. Furthermore, between the two fixed Außenringborden 5 and the rolling element 6 one sliding washer each 20 . 21 arranged.

The sliding disks 19 . 20 . 21 . 22 each have the shape of a circumferentially extending ring, and in turn are with play in the outer ring 4 inserted or on the inner ring 2 put on, and thus compared to the other bearing components, and also against each other, freely rotatable.

Due to the additional loose inner ring board 23 gets the roller bearing 1 given the ability to accommodate axial loads in both directions along the longitudinal axis A. At an axial load of the outer ring 4 by a load acting on these from left to right cause the sliding discs 19 . 21 a reduction in friction when absorbing the axial load. In the case of a load on the outer ring 4 The sliding disks take over in exactly the opposite direction 20 . 22 this function.

5 shows a fifth embodiment of a roller bearing according to the invention in a radial sectional view. Also this roller bearing 1 has rolling elements designed as cylindrical rollers 6 as well as an inner ring 2 and an outer ring 4 in the same way as above with respect to the embodiment in 1 described trained and with an inner ring board 3 and outer ring rims 5 are provided. The bearing ring rims 3 . 5 have the rolling elements 6 facing inner surfaces 10 on. Furthermore, the roller bearing 1 According to this embodiment, a cage designed in a special manner as described below 9 on.

Again, between the inner ring board 3 and the rolling element 6 and between one of the two outer ring rims 5 , which from the rolling element 6 seen in the axial direction A the inner ring board 3 opposite, and the rolling element 6 an additional load-bearing device 7 intended. The additional load bearing device 7 has a plurality of Axialwälzkörpern 12 on which each between the inner ring board 3 and the rolling element 6 and between the outer ring board 5 and the rolling element 6 are arranged.

As Axialwälzkörper 12 are in the in 5 shown embodiment, needles provided. In addition, in the circumferential direction of the roller bearing 1 extended thrust bearing cages 14 the needles 12 ,

Two opposite axial ends 13 of the cage 9 are each provided with an annular, closed in the circumferential direction raceway for the associated Axialwälzkörper 12 educated. For this purpose, the cage 9 each in the region of its axial end faces 13 a flange extending substantially in the radial direction R. 15 on. The ring-shaped track for the Axialwälzkörper 12 is on both sides of the cage 9 in the area of the flange 15 arranged concentrically to the bearing rings.

At its radially outer end is the outer ring board 5 facing flange 15 with a circumferential projection 16 Mistake. In addition, it has the inner ring board 3 facing flange 15 in the region of its radially outer end also a circumferential projection 16 on.

The Axialwälzkörper 12 are at the in 5 shown roller bearings 1 as well as the outer ring 4 , the inner ring 2 and the rolling elements 6 made of a suitable bearing steel. The cage 9 is designed as a massive steel cage. Here, roll between the outer ring board 5 and the rolling element 6 provided Axialwälzkörper 12 on the one hand on the rolling elements 6 facing inner surface 10 one outer ring board 5 , on the other hand, on the adjacent end face 13 of the cage 9 intended career, from.

Furthermore, roll between the inner ring board 3 and the rolling element 6 provided Axialwälzkörper 12 on the rolling element 6 facing inner surface 10 of the inner ringboard 3 as well as on the adjacent front side 13 of the cage 9 intended career path.

The Axialwälzkörper 12 are thus in rolling contact with a surface 10 of the inner ringboard 3 and with a surface 10 of the outer ringboard 5 and with those on the front ends 13 of the cage 9 trained raceways, that by the rolling movement axial loads from the inner ring 2 on the outer ring 4 can be transferred at very low sliding friction occurring. This power transmission takes place starting from the inner ring 2 over the inner ring board 3 by means of on its surface 10 and the raceway rolling Axialwälzkörper 12 on the cage 9 , The axial load introduced into the cage in this way is made by means of the on the opposite side of the cage 9 trained career and on the surface 10 of the outer ringboard 5 rolling Axialwälzkörper 12 on the outer ring 4 transfer.

An execution of the cage 9 in solid construction of a steel ensures the ability to absorb relatively large axial loads. An embodiment of the cage in sheet metal construction is conceivable. Still possible is the use of a plastic cage, but the metal design allows higher allowable axial loads due to the greater strength.

During its rolling motion during the rotation of the shaft 8th become the Axialwälzkörper 12 through the thrust bearing cages 14 guided along a predetermined path. In addition, the axial bearing cages ensure 14 in that the axial rolling elements 12 do not touch each other during the rolling process. A frictional wear due to the mutual contact of Axialwälzkörper 12 is thus avoided.

The on the flange 15 provided projection 16 serves to guide the thrust bearing cage 14 , This will emigrate the Axiallagerkäfigs 14 together with the guided by him Axialwälzkörpern 12 from its position in the area concentric with the bearing rings 2 . 4 arranged career prevented. It would also be conceivable, however, a version without projections 16 , which has the advantage of better the contact of the axial rolling elements 12 Has.

By the choice of needles as Axialwälzkörper 12 is the space required for the Axialwälzkörper 12 kept as low as possible. This is beneficial to reducing the axial extent of the rolling elements 6 and thus their radial load capacity while maintaining unchanged outer dimensions of the roller bearing 1 to keep low compared to a conventional roller bearing of this size.

Of course it is also possible, sliding discs, as in the in the 2 . 3 and 4 illustrated developments of the roller bearing according to the invention 1 are provided for transmitting an axial load of an inner ring board 3 or an outer ring board 5 by sliding contact with the faces 13 of the cage 9 to use on this cage.

Although the present invention above based on preferred embodiments was described, it is not limited thereto, but can be modified in many ways, without that deviates from the subject of the present invention.

So the invention is not necessarily for use in roller bearings limited for or in gear, but lets in any application, such as in electric motors and apply the same.

The specified construction can also be modified. The same applies to the materials used, which are merely advantageous examples were given.

LIST OF REFERENCE NUMBERS

1

roller bearing

2

inner ring

3

Inner ring rib

4

outer ring

5

Outer ring board

6

rolling elements

7

additional load bearing device

8th

wave

9

Cage

10

surface the inner ringboard or outer ringboard

11

face of the at least one rolling element

12

Axialwälzkörper

13

axial Front side of the cage

14

axial bearing cage

15

flange

16

surrounding head Start

17

sliding disk

18

sliding disk

19

sliding disk

20

sliding disk

21

sliding disk

22

sliding disk

23

loose Inner ring rib

A

axial Direction (bearing longitudinal axis)

R

radial direction

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - DE 1525205 C [0008]
• - DE 1910794 U [0009]
• FR 731895 A [0011, 0011, 0011]

Cited non-patent literature

• - DIN 5412 [0016]

Claims (15)

Roller bearings ( 1 ), with an inner ring ( 2 ), which has an inner ring board ( 3 ) having; with an outer ring ( 4 ), which has an outer ring board ( 5 ) having; with a plurality of rolling elements ( 6 ) for transmitting radial loads between the inner ring ( 2 ) and the outer ring ( 4 ) are arranged; and with an additional load-bearing device ( 7 ) for transmitting axial loads between at least one of the rolling elements ( 6 ) and the inner ring board ( 3 ) and / or the outer ring board ( 5 ) is arranged. Roller bearing according to claim 1, characterized in that the outer ring board ( 5 ) on the outer ring ( 4 ) on a relative to an axial direction (A) of the roller bearing ( 1 ) the inner ring board ( 3 ) opposite side is provided. Roller bearing according to one of the preceding claims, characterized in that the additional load-bearing device ( 7 ) has a support element which relative to the inner ring ( 2 ) and / or to the outer ring ( 4 ) and / or to the rolling elements ( 6 ), in particular in the circumferential direction of the roller bearing ( 1 ) is rotatable, is arranged. Roller bearing according to one of the preceding claims, characterized in that the additional load-bearing device ( 7 ) for transmitting axial loads from the inner ring ( 2 ) on the outer ring ( 4 ) between at least one of the rolling elements ( 6 ) and the inner ring board ( 3 ) and between at least one of the rolling elements ( 6 ) and the outer ring board ( 5 ) is provided. Roller bearing according to one of the preceding claims, characterized in that a cage ( 9 ) for guiding the rolling bodies ( 6 ) is provided. Roller bearing according to claim 5, characterized in that the additional load-bearing device ( 7 ) a plurality of Axialwälzkörpern ( 12 ), at least one axial end face ( 13 ) of the cage ( 9 ) is formed with a raceway, and the Axialwälzkörper ( 12 ) in rolling contact with a surface ( 10 ) of the inner ring board ( 3 ) or outer ringboard ( 5 ) and with the track such that axial loads from the inner ring board ( 3 ) or from the outer ring board ( 5 ) on the additional load-bearing device ( 7 ) on the cage ( 9 ) are transferable. Roller bearing according to claim 6, characterized in that a thrust bearing cage ( 14 ) for guiding the Axialwälzkörper ( 12 ) is provided. Roller bearing according to claim 7, characterized in that the cage ( 9 ) in the region of at least one of its axial end faces ( 13 ) extending substantially in the radial direction (R) extending flange ( 15 ), wherein the raceway is annular and in the region of the flange ( 15 ), and the flange ( 15 ) at its radially inner or outer end with a circumferential projection ( 16 ) for guiding the thrust bearing cage ( 14 ) is provided. Roller bearing according to one of claims 6 to 8, characterized in that the Axialwälzkörper ( 12 ) are formed as needles. Roller bearing according to one of the preceding claims, characterized in that the additional load-bearing device ( 7 ) in sliding contact with a surface ( 10 ) of the inner ring board ( 3 ) or outer ringboard ( 5 ) and with an adjacent end face ( 11 ) of the at least one rolling body ( 6 ) that axial loads from the inner ring board ( 3 ) or from the outer ring board ( 5 ) on the additional load-bearing device ( 7 ) on the at least one rolling element ( 6 ) are transferable. Roller bearing according to claim 10, characterized in that the additional load-bearing device ( 7 ) as a circumferentially closed, annular sliding disk ( 17 . 18 ) is trained. Roller bearing according to one of the preceding claims, characterized in that the inner ring board ( 3 ) in one piece with the inner ring ( 2 ) is formed and / or the outer ring board ( 5 ) in one piece with the outer ring ( 4 ) is trained. Roller bearing according to one of the preceding claims, characterized in that the surface of the additional load-bearing device ( 7 ) and / or the inner ring board ( 3 ) and / or the Außenringbordes ( 5 ) and / or the end faces ( 11 ) of the rolling elements ( 6 ) are wholly or partially provided with a sliding friction reducing coating. Roller bearing according to one of the preceding claims, characterized in that the additional load-bearing device ( 7 ) is at least partially made of a metal or of a metallic alloy, for example a hardening steel or a bronze, and / or of a friction-reducing material, for example of a suitable plastic. Roller bearing according to one of the preceding claims, characterized in that the rolling bodies ( 6 ) are designed as cylindrical rollers or as tapered rollers.

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