WO2009132643A2

WO2009132643A2 - Tapered roller bearing and shaft bearing arrangement for at least one tapered roller bearing

Info

Publication number: WO2009132643A2
Application number: PCT/DE2009/000634
Authority: WO
Inventors: Jan Georgi; Martin STÜRZENBERGER
Original assignee: Schaeffler Kg
Priority date: 2008-05-02
Filing date: 2009-05-02
Publication date: 2009-11-05
Also published as: WO2009132643A3; DE102008021884A1

Abstract

The invention relates to a tapered roller bearing (3) comprising a bearing inner ring (6) having a conical inner raceway (6') and a bearing outer ring (7) having a conical outer raceway (7'). In order to rotatably receive the bearing inner ring (6) and the bearing outer ring (7) about a common axis (9), a plurality of rolling elements (8) which are designed as tapered rollers are used. The rolling elements (8) are axially supported by a rib body (16). An adjusting washer (18) for adjusting the axial play of the rolling bodies (8) in the axial direction (14) is interposed between the rib body (15) and one of the bearing rings (6).

Description

Name of the invention

Tapered roller bearing and shaft bearing for at least one tapered roller bearing

description

Field of the invention

The invention relates to a tapered roller bearing and to a shaft bearing for at least one tapered roller bearing.

Background of the invention

Such a tapered roller bearing is known for example from US 4,065,191 A. It has a bearing inner ring with a conical inner raceway and a bearing outer ring with a conical outer raceway. The bearing inner ring and the bearing outer ring are rotatably supported about a common axis by means of rolling bearings designed as tapered rollers. The rolling elements in turn are axially supported by means of a separate board body.

Such tapered roller bearings are used in pairs in the so-called X-arrangement or in the O-arrangement for shaft bearings. For Pinion bearings is an O-arrangement of the two tapered roller bearings usual.

The two tapered roller bearings should be adjusted to each other to an optimized bearing preload or to an optimized bearing clearance. In mass production, although an acceptable bearing preload or an acceptable bearing clearance can be achieved by a very precise production of all the bearing play influencing components (shaft, bearings, housing) and taking into account the probability in the combination of these components. However, if an optimized bearing preload or an optimized bearing play is desired, this must be adjusted by measuring the components and a number of shims, which are pushed onto the shaft between the two tapered roller bearings.

If a deviation from the specified value is determined after assembly during the final check of the bearing clearance or bearing preload, a tapered roller bearing must be removed from the shaft again, a different shim or other combination of shims must be pushed onto the shaft and the tapered roller bearing must be reinstalled become. The problem is the required in the final assembled state tight fit of the bearing inner rings on the shaft or the bearing outer rings with the housing, which allows mounting or dismounting only with a press as a mounting device. In addition, during the disassembly, the pressing forces are usually due to the rolling elements passed, resulting in damage to the rolling elements can result.

Object of the invention

The known procedure for adjusting the bearing clearance or the bearing preload is associated with a great deal of work and binds the press required for this purpose by a possible repeated assembly or disassembly. The invention is therefore based on the object, a Wälz- To make camp so that the setting of the bearing clearance or the bearing preload a shaft bearing with little effort and even with a tight fit of the bearing rings on the shaft without a press as a mounting device is possible.

Solution of the task

The object is achieved by the feature combination of claim 1. For this purpose, a shim is arranged in a tapered roller bearing of the type mentioned between the board body and one of the two bearing rings. Such shims are used in mechanical engineering to set the distance between individual components of a shaft bearing, in particular of rolling bearings to each other. In Germany, standard dimensions for shims are specified in DIN 988. By inserting a number of shims with a suitable thickness between the flange body and one of the two bearing rings, the height of the respective bearing and thus the bearing clearance and the bearing preload of the shaft bearing can change even with unchanged tight-fitting bearing rings. For this purpose, a number of shims with a suitable total thickness is simply selected. Subsequently, the bearing play or the bearing preload of the shaft bearing is remeasured. If necessary, the axial distance between the flange body and the bearing ring and thus the position of the rolling elements by inserting a number of shims of different thickness is changed.

If the distance between the board body and the bearing ring is increased, so does the game of shaft bearing increases. The height of the tapered roller bearing is smaller by moving the other bearing ring along the tapered rollers.

Conversely, the distance between the rim and the bearing ring is reduced, so reduces the game of shaft bearing. As a result, the height of the tapered roller bearing is larger. Depending on the roll angle In this case, there is a translation between the distance of the flange body and the change in height, which allows a relatively coarse gradation of the thickness of the shims, (so-called "inner translation".) In the usual gradation of the thickness of the stock shims according to DIN 988 Adjusting the axial clearance already very finely Since the shims are provided with an oversize relative to the shaft, they can simply be pushed onto the shaft without an additional tool.

The shims are only loosely fitted on the shaft. Furthermore, the board body is advantageously designed with an excess of the shaft. Thus, the shims and the body can be removed without effort by the use of a mechanical press manually or with a handling device and the total thickness of the shims correspondingly easy to adjust.

In an expedient development of the board body is formed in cross-section L-shaped. The transverse leg of the L is effective with its front side as a board to which the rolling elements create. The vertical L-leg accommodates the number of shims between itself and the associated bearing ring. In other words, the transverse leg is in the axial direction over the vertical leg of the L and engages in the space between the bearing inner ring and the bearing outer ring to specify the axial position of the rolling elements. How far the transverse limb projects beyond the vertical L-limb in the axial direction is predetermined by the thickness of the shim.

Due to the axial projection or by the overlapping of the transverse leg on the bearing ring, the raceway of the bearing ring can be performed to the end of the tapered rollers. Thus, the entire roller width of the tapered rollers is utilized as a load-bearing surface. The shim lies flat on the vertical L-leg and on the bearing ring. Due to the flat concerns of the shim also ensures that in the mounted state of the bearing the set axial play is maintained.

The rim ring can have any geometry and can also be formed on a more complex component. However, the board body is preferably designed as a flange, which can be produced in a simple manner in a forming process.

Further, the separate board body can be suitably adjusted with respect to material and surface texture regardless of the functional surfaces of the rolling bearing on its function as GleitVFührungsbauteil for the rolling elements. For this purpose, the board body, for example, a coating. -

In the final assembled state of the rolling bearing of the board body is braced against the bearing ring in the axial direction, so that the board body and the bearing ring are secured against each other by frictional engagement and / or frictional connection against unwanted rotation. Advantageously, additional devices for securing the flange body against uncontrolled rotation in the final assembly state can be provided. For this purpose, friction-enhancing and / or positive-locking devices are provided which can be arranged on the side of the flange body facing the shim, on the side of the bearing ring facing the shim, or on at least one side of the shim. The device is designed, for example, as a profiling, as a toothing, in particular as a Hirth toothing, as a coating or as an adhesive film. It is applied, introduced or molded on the board body, on the bearing ring or on the shim.

Alternatively, the shims and / or the board body expediently by form elements, in particular by grooves, by teeth or by Grooves or elastically formed by their material, so that for an adjustment of the bearing preload or the bearing clearance no replacement of the at least one shim must be made. The bearing clearance / preload can then be adjusted by tightening the shaft fitting more or less strongly. A change in distance between the board body and the bearing ring is possible in the context of their elasticity.

The object is further achieved by a shaft bearing with a housing, with a shaft and with at least one tapered roller bearing according to one of claims 1 to 7. The shaft is mounted on the tapered roller bearing in the housing.

For bearing the shaft via the roller bearing in the housing, the bearing inner ring is expediently pressed onto the shaft in order to ensure a tight fit of the bearing inner ring on the shaft. Furthermore, the bearing outer ring is expedient pressed in the housing and thus arranged in the housing against rotation. The pressing of the bearing inner ring on the shaft or the compression of the bearing outer ring in the housing are common practice when mounting a roller bearing.

Advantageously, the board body is provided with a transition fit with respect to the shaft, which allows easy assembly and disassembly. In other words, the number of shims and the flange body can be postponed on the shaft and reassembled in retrospect with the pressed-in roller bearing already mounted. Likewise, the distance between the body and firmly pressed bearing ring can be changed at any time in retrospect by replacing the shims to adjust the optimal bearing clearance and the optimal bearing preload.

Suitably, the rolling bearing is clamped in the axial direction by means of a shaft nut by means of a bracing device. In this way, the board body with the shim is fixed against the corresponding bearing pressed ring, so that the set axial play is maintained even in the final assembly.

In an expedient development, a receptacle for bracing the flange body against one of the two bearing rings is provided on the side of the flange body facing away from the washer. For engaging in the recording arranged on the bracing device pins or the like may be provided which produce a positive connection between the flange body and the shaft and thus prevent rotation of the rim body relative to the shaft. In this way, a positive and non-positive fixing of the board body is achieved in its position.

An embodiment of the invention will be explained in more detail with reference to a drawing. The individual figures show:

1 schematically a shaft bearing with two rolling bearings in a sectional side view,

2 shows a detail of one of the two roller bearings from FIG. 1, FIG. 3 shows a shim in a plan view, FIG. 4 shows the shim of FIG. 2 in a sectioned side view, and FIG. 5 shows a pinion shaft bearing with two roller bearings.

1 shows schematically in a sectional side view a detail of a shaft bearing 1, in which a shaft 2 is rotatably mounted in a housing 5 by means of a first rolling bearing 3 and a second rolling bearing 4. The two designed as tapered roller bearings rolling bearings 3, 4 are mounted in the so-called O-arrangement.

The first designed as a tapered roller bearing bearings 3 has a bearing inner ring 6 with a conical inner race 6 'and a bearing outer ring 7 with a conical outer race 7' on. The bearing inner ring 6 and the Bearing outer ring 7 are mounted by means of a plurality of rolling elements arranged between them 8 about a common axis which coincides in the assembled state with the central longitudinal axis 9 of the shaft 2. The second rolling bearing 4 is in turn designed as a tapered roller bearing with a conical inner race 11 'having bearing inner ring 11 and a conical outer race 12' having bearing outer ring 12. The bearing inner ring 11 and the bearing outer ring 12 of the second rolling bearing 4 are also mounted by means of rolling elements 13 designed as tapered rollers about a common axis, which coincides in the final assembled state with the central longitudinal axis 9 of the shaft 2. The leadership of the rolling elements 8,13 takes place in each case by means of a bearing cage 10. The axial position of the bearing rings 6.7 is fixed by appropriate abutment shoulders in the housing and on the shaft

For the final assembly of the two rolling bearings 3,4 their bearing inner rings 6, 11 are pressed onto the shaft 2. Your bearing outer rings 7, 12 are pressed in the housing 5. In this way, the shaft 2 is rotatably mounted in the housing 5 by means of the two tapered roller bearings 3, 4 about its central longitudinal axis 9.

The second rolling bearing 4 is a tapered roller bearing of conventional design.

The first rolling bearing 3 has a board body designed as a rim 15 with an L-shaped cross-section. This board body 15 is shown in Fig. 2 in an enlarged detail. The pointing in the axial direction 14 transverse leg 16 of the L is effective as with its front side to the rolling elements 8 abutting edge and specifies the axial clearance of the rolling bearing 8. The vertical L-leg 17 receives one or more shims 18 between itself and the bearing inner ring 6. In the figures, for the sake of simplicity, only a single shim is shown. The bearing inner ring 6, the board body 15 and the shim 18 support and thus lead together the rolling elements 8 and thus jointly perform the same function as the one-piece bearing inner ring 11 of the second rolling bearing 4th

Fig. 3 shows the shim 18 in a plan view. In Fig. 4, the fitting disc of Fig. 3 is shown in a sectional side view. The shim 18 is uniquely characterized by its outer diameter 19, by its inner diameter 20 and by its thickness 21.

The board body 15 and the shim 18 allow adjustment of the position of the rolling elements 8 within the rolling bearing 3 in the axial direction 14. For this purpose, the board body 15 is equipped with a transition fit. In other words, it can be postponed without significant resistance to the shaft 2. Also, the pushed onto the shaft 2 shims 18 are provided opposite the shaft 2 with an oversize.

For the adjustment of the bearing clearance or the bearing preload of the shaft bearing 1 from rolling bearings 3 and 4, the rolling elements 8 are moved with mounted roller bearing 3 within the camp. The shim 18 is pushed from the direction shown by arrow 22 in Fig. 1 on the shaft 2 until it rests flat against the bearing inner ring 6. Subsequently, the board body 15 is pushed onto the shaft 2, until it also lies with its the shim 18 side facing flat against this. Subsequently, the board body 15 is braced against the bearing inner ring 6 a in Figs. 1 and 2, not shown bracing device. The transverse leg 16 of the flange 15 engages in the inner race 6 'of the rolling bearing 3 and thus provides the position of the rolling elements 8 in the axial direction 14. This results in a height 23 for the rolling bearing 3 and for the shaft bearing 1 accordingly a certain bearing clearance or a certain bearing preload. If the bearing clearance or the bearing preload deviates from the pre-conditions, the bracing device is removed and the flange body 15 and the shim 18 are dismantled, ie they are withdrawn from the shaft 2 in the direction opposite to arrow 22 in the axial direction 14. At- closing the total thickness of the shims 18 is changed by replacing the shims 18 by other shims differing overall thickness. After attaching the bracing the bearing clearance and the bearing preload of the shaft bearing is measured again. In this case, a shim with a greater thickness increases the bearing clearance of the shaft bearing. A shim with a smaller thickness reduces the bearing clearance of the shaft bearing 1. This process can be repeated as often as desired with shims of different thickness until the desired bearing clearance or the desired bearing preload of the shaft bearing is reached.

Fig. 5 shows the detail of Fig. 2 without shims between the board body 15 and the bearing inner ring 6. The trained as a tapered rollers 8 move in the direction of arrow 22. As a result, the bearing clearance compared to FIG. 2 is reduced. However, since the bearing outer ring 7 moves in with the tapered rollers 8 in the direction of arrow 22, the overall height 23 'of the rolling bearing 3 increases.

Fig. 6 shows a formed as a pinion shaft bearing shaft bearing 1 in a sectional side view. For the mounting of a shaft 2, in turn, two tapered roller bearings 3, 4 are provided, which are arranged in an O-arrangement. In this case, the conditions correspond to those of the schematic view in Fig. 1. In other words, the first rolling bearing 3 is provided with an additional board body 15 and a held between the board body 15 and its bearing inner ring 6 shim 18. The second rolling bearing 4 is formed as a conventional tapered roller bearing. For bracing the first tapered roller bearing 3 in the axial direction 14, a bracing device 24 is provided, which engages with a plurality of arms 25 in the receptacles 26 on the side facing away from the shim of the rim body 15. In this case, the position of the bracing device 24 in the axial direction 14 is secured by means of a shaft nut 27. In this way, the predetermined by the shim 18 and the rim 15 axial clearance of the rolling elements 8 is also given in final assembled state. The shim 18 facing side of the flange body 15, the shim 18 facing side of the bearing inner ring 6 and the two sides of the shim 18 are provided with a profiling to increase the friction between the individual bearing components 6, 15, 18. In this way, the board body 15 is held against rotation on the bearing inner ring 6.

LIST OF REFERENCE NUMBERS

1 shaft bearing

2 wave

3 first rolling bearing 4 second rolling bearing

5 housing

6 bearing inner ring 6 'inner raceway

7 Bearing outer ring 7 'outer raceway

8 rolling elements

9 Center longitudinal axis 11 Bearing inner ring 11 'Inner race 12 Bearing outer ring 12' outer raceway

13 rolling elements

14 axial direction

15 board body 16 transverse legs

17 vertical L-leg

18 shim

19 outer diameter

20 inner diameter 21 thickness

22 arrow

23 track 23 'height

24 brace 25 arm

26 recording

27 shaft nut

Claims

claims

1. tapered roller bearing (3) with a bearing inner ring (6) with a conical inner raceway (6 ') and with a bearing outer ring (7) with a conical outer ßenlaufbahn (7'), - with a plurality of rolling elements designed as tapered rollers

(8) for the rotatable mounting of the bearing inner ring (6) and the bearing outer ring (7) about a common axis (9) and with a rolling body (8) axially supporting board body (15), characterized by a between the board body (15) and a the bearing rings (6) arranged shim (18).

2. tapered roller bearing (3) according to claim 1, characterized by a cross-sectionally L-shaped board body (15) such that the

Transverse leg (16) of the L as with its front side to the rolling elements (8) abutting board is effective and that the vertical L-leg (17) receives the shim (18) between itself and the respective associated bearing ring (6).

3. tapered roller bearing (3) according to one of claims 1 to 2, characterized by an at least partially a raceway (23) of one of the two bearing rings (6) cross-board.

4. tapered roller bearing (3) according to any one of claims 1 to 3, characterized by a Bordring (15) formed on the board body.

5. tapered roller bearing (3) according to one of claims 1 to 4, characterized by reibvergrößernde and / or formschlüssigβ devices on the shim (18) facing side of the flange body (15).

6. tapered roller bearing (3) according to one of claims 1 to 5, characterized by reibvergrößernde and / or positive locking devices on the shim (18) facing side of the bearing ring (6).

7. tapered roller bearing (3) according to one of claims 1 to 6, characterized by reibvergrößernde and / or positive locking devices on at least one side of the shim (18).

8. tapered roller bearing (3) according to one of claims 1 to 7, characterized by an elastic design of the flange body (15) and / or the at least one shim (18).

9. shaft bearing (1) with a housing (5), with a shaft (2) and with at least one tapered roller bearing (3) according to one of the preceding claims, wherein the shaft (2) via the rolling bearing (3) in the housing se (5) is stored.

10. shaft bearing (1) according to claim 9, characterized by a on the shaft (2) pressed-on bearing inner ring (6).

11. shaft bearing (1) according to claim 9 or 10, characterized by a in the housing (5) pressed bearing outer ring (7).

12. shaft bearing (1) according to any one of claims 10 to 11, characterized by a transitional fit of the flange body (15) relative to the shaft (2).

13. shaft bearing (1) according to one of claims 10 to 12, characterized by a tension of the rolling bearing (3) in the axial direction (14) by means of a shaft nut (27).

14 shaft bearing (1) according to any one of claims 10 to 13, characterized by a receptacle (26) on the the shim (18) facing away from the bracing body (15) against one of the bearing rings (6).