WO2007025975A2

WO2007025975A2 - Angular ball bearing tandem comprising a seal on both end faces

Info

Publication number: WO2007025975A2
Application number: PCT/EP2006/065795
Authority: WO
Inventors: Wolfgang Steinberger; Manfred Winkler; Harald Peschke; Dieter Jauernig; Thomas Fickert; Frank Stolz
Original assignee: Schaeffler Kg
Priority date: 2005-09-03
Filing date: 2006-08-30
Publication date: 2007-03-08
Also published as: WO2007025975A3; DE102005041917A1

Abstract

The invention relates to an angular ball bearing tandem for supporting a drive shaft in a transfer case, in particular for a motor vehicle, comprising a one-piece outer ring (1) and a one-piece inner ring (2) between which at least two sets of roll bearings (3, 4 is) are guided in a respective bearing cage (6, 7) on two paths bearing having different diameters, wherein a seal (8, 9) provided with at least one sealing lip (10) is mounted on two flat seats of the angular ball bearing tandem, respectively. No impurity particle is able to penetrate into a bearing provided with said angular ball bearing tandem, thereby making it possible to attain the longer service life of the transfer case. In addition, the oil input in the bearing is maintained and respectively controlled and regulated.

Description

Name of the invention

Tandem angular contact ball bearings

Field of the invention

The invention relates to a tandem angular contact ball bearing for supporting a drive shaft, in particular in motor vehicle technology.

Background of the invention

The lubrication and flow of oil in transmissions of all kinds in machines, units and motor vehicles is of particular importance, since they are responsible for a long life and proper functioning of these facilities. During operation of these devices, foreign bodies such as metallic parts of iron, copper, aluminum and zinc as well as non-metallic parts such as rubber and plastics accumulate in the transmission oil. Smallest dirt and steel particles with high hardness and tooth wear in the gear oil are the cause of bearing failures due to damage to the raceway surfaces for the bearing rolling elements, in particular bearings in motor vehicle manual transmissions or axle drives.

In manual transmissions for motor vehicles bearing selection is often difficult because of the limited installation space. In addition to deep groove ball bearings, roller sleeves, cylindrical roller bearings and tapered roller bearings, more expensive tandem angular contact ball bearings, ie multi-row angular contact ball bearings, are used to support the gear shafts. Tandem angular contact ball bearings are also used in transfer cases.

With transfer cases, it is known that drive wheels of each axle shaft of a motor vehicle can roll without slip when cornering despite different speeds. From EP 1 105 662 B1 such a transfer case for a motor vehicle is known, with a bevel pinion shaft, which is mounted in a transmission housing via two spaced apart and axially biased tandem angular contact ball bearings. A disadvantage of such a transfer case is that no measures are provided to seal the tandem angular contact ball bearing against contamination and thus the bearings have only a limited life.

From the state of the art ("DIE WÄLZLAGERPRAXIS", Handbook for the calculation and design of bearings, Vereinigte Fachverlage GmbH, Mainz, 3rd edition 2002) are used in the field of oil-lubricated automotive manual dirt-resistant bearings, so-called "Clean Beahngs" , known. These are grease-lubricated roller bearings from the manufacturer with two sealing washers attached to the sides of the plan. These dirt-protected double-row angular contact ball bearings are also used for axially accurate guidance of the countershaft of a passenger car manual transmission. Other applications of dirt-protected double row angular contact ball bearings are not yet known.

In dirt-protected deep groove ball bearings with two face-side sealing discs distinction is made between contacting and non-contact arrangement of the sealing lip of the sealing washer with respect to the inner ring of the bearing. In the first embodiment, the sealing lip of the gasket is applied to the inner ring with a slight contact pressure. In the second embodiment, however, remains a small gap between the inner ring and the sealing disc according to the requirement for low friction, good lubrication and retention of dirt particles and tooth abrasion. A narrow sealing gap allows transmission oil to penetrate the bearing to support the original grease lubrication, but retains dirt particles. As a result, compared with non-sealed bearings, either a significantly longer service life can be achieved or a smaller bearing cross-section can be selected.

Object of the invention The invention is based on the object to provide a tandem angular contact ball bearing preferably for supporting a drive shaft in a transfer case, for example, for a motor vehicle, which prevents the entry of dirt particles in the camp and thus a longer life of the transfer case to be achieved. In addition, the oil entry into the camp should be maintained and controlled or controlled.

Summary of the invention

The invention makes use of the finding that a narrow sealing gap or a sealing lip of a seal which bears against the bearing ring with a defined contact or low contact pressure allows the transmission oil to penetrate into the bearing in order to support the original grease lubrication, but retains dirt particles floating in the transmission oil.

The invention is therefore based on a tandem angular contact ball bearing for supporting a drive shaft in a transfer case, for example for a motor vehicle, with a one-piece outer ring and a one-piece inner ring, between which at least two sets of bearing balls are guided in each case a bearing cage in raceways of different diameters, wherein the two plan sides of the tandem angular ball bearing is arranged in each case a seal with at least one sealing lip.

This construction advantageously ensures that the tandem angular contact ball bearing achieves a service life that is longer than an open or reinforced bearing, since the entry of metallic and non-metallic dirt particles is effectively prevented, but at the same time the oil used as lubricant can flow in a controlled manner through the tandem angular contact ball bearing. In addition, the installation space can be limited or reduced in particular in a transfer case of a motor vehicle.

As a seal in the context of the invention, a suitably trained sealing ring or a sealing washer should be understood. According to a development of the tandem angular contact ball bearing according to the invention, the seal is firmly connected to the outer ring or the inner ring. Furthermore, the seal can be connected to both the outer ring and the inner ring. Advantageously, the seal is press-fitted to the outer ring or inner ring to ensure a secure hold of the seal.

In another embodiment of the tandem angular contact ball bearing, the seal can be firmly connected to the ball cage surrounding the bearing balls.

Essentially, two types of lateral sealing of the tandem angular contact ball bearing of the transfer case are made possible. According to a first type, the at least one sealing lip of the seal bears on the outer ring and / or inner ring with a slight contact pressure. In the other type, the at least one sealing lip of the seal, leaving a small gap without contact pressure, ie non-contact, directed to the outer ring and / or inner ring. In the case of attachment of the seal on the ball cage, for example, in each case one sealing lip of the seal bears against the outer ring or the inner ring with a defined contact pressure, or leaves a gap of a specific size thereon.

Furthermore, the seals differ in the type of investment or orientation of their sealing lip to the outer ring or inner ring. According to a first type, the at least one sealing lip of the seal abuts in the axial and / or radial direction on the outer ring and / or inner ring. In the other type, the at least one sealing lip of the seal is directed in the axial and / or radial direction to the outer ring and / or inner ring.

According to a further embodiment of the tandem angular ball bearing according to the invention, the seal with a press fit and a Einschnappkontur is attached to the outer ring or inner ring. This Einschnappkontur can, for example in the form of an annular groove on the inner surface of the outer ring or be formed on the outer surface of the inner ring, and ensures in conjunction with the interference fit for an immovable and tight fit of the seal in the camp.

Similarly, the seal may be secured by means of a puncture contour on the outer ring or on the inner ring, wherein the puncture contour is formed as, for example, in cross-section arcuate groove on the outer ring or inner ring.

Another possibility for mounting the seal is that it is fastened by means of an additional locking ring on the outer ring or inner ring.

Advantageously, the gasket applied with slight contact pressure on the outer ring and / or inner ring consists in particular of an elastomer, preferably NBR (acrylonitrile-butadiene rubber), FPM (fluoroelastomer), ACM (acrylate rubber), H-NBR (acrylonitrile Butadiene rubber) or similar materials, or of a thermoplastic material.

If a gap seal is provided on the tandem angular contact ball bearing, the seal directed to the outer ring and / or inner ring leaving a small gap without contact pressure consists in particular of steel, preferably antimagnetic steel, stainless steel or titanium steel, a sintered material, a bronze material, a technical plastic or a Elastomer, preferably NBR, HNBR, ACM or FPM.

By selecting suitable materials or materials, the thermal expansion of the seal is varied, which to a certain extent is adjusted by the operating temperature of the tandem angular contact ball bearing with respect to their Dichtigen- shafts, so that the flow of oil can be controlled or controlled.

To obtain a certain bias or stability, the Seal according to another variant of the invention also be provided with a stiffening ring.

In a further embodiment of the invention, the seal is provided with a venting device in order to avoid undesired pressure conditions in the tandem angular contact ball bearing. In this case, the seal may be connected to both the outer ring and the inner ring. The seal can also be attached only to the outer ring or only on the inner ring, wherein the other free end of the seal bears as a sealing lip with a low contact pressure against the outer ring or the inner ring, or is directed in compliance with a gap to this. In this case, the seal preferably has a venting section made of a porous sintered material or foam material.

According to another embodiment of the tandem angular contact ball bearing, the seal on a gap or labyrinth channel or a groove in the seal seat or sealing lip area for venting of the bearing, with a controlled oil flow is made possible by the camp.

The various designs of the tandem angular contact ball bearing are designed so that a controlled oil flow over different gap heights and different sealing diameter is achieved. By a suitable choice of

Gap height, the entry of dirt particles is minimized or even completely prevented. For seals whose at least one sealing lip with light

Contact pressure on the outer ring or inner ring, the oil flow can be controlled by the appropriate choice of the sealing diameter.

In addition to the intended use of the tandem angular contact ball bearings according to the invention in transfer cases in motor vehicles, these can also be used, for example, as support rollers in Sendzimir rolling mills, for the storage of work rolls in printing works or calender rolls, for example in paper mills.

Brief description of the drawings The invention will be explained in more detail below with reference to the accompanying drawings of some embodiments. 1 to 27 show cross-sectional representations of only one upper region of different embodiments of a tandem angular contact ball bearing according to the invention for supporting a drive shaft, not shown, in a transfer case, for example for a motor vehicle.

Detailed description of the drawings

The tandem angular contact ball bearings shown in the drawings consists in a conventional manner essentially of a one-piece outer ring 1 and a one-piece inner ring 2. Between these are spaced from each other two sets of run in bearing balls 3 and 4 of the same size, the set shown on the left of bearing cradles 3 has a smaller raceway diameter than the respective set of bearing balls 4 shown on the right, so that a shoulder 5 forms between the two sets of bearing balls 3 and 4. Each set of bearing balls 3 and 4 is held and guided in a bearing cage 6, 7, respectively. On the two sides of the plan Tandemschrägkugellagers each seal 8 and 9 is arranged as a sealing ring or sealing disc with at least one sealing lip 10.

The aforementioned components of the tandem angular contact ball bearing will not be explained again in the following description of the drawings to avoid repetition. For the purpose of better clarity, as far as is necessary, only the necessary for further explanation of the reference numerals of the components in the drawing figures. If in a drawing figure, the seals are formed and arranged in the same way, only one of the seals will be described.

In Figures 1 to 4, the seals 8 and 9 are fixedly connected to the outer ring 1 of the tandem angular contact ball bearing, namely by a groove-shaped recess contour 1 1 according to Figures 1 and 3, by press fit 12 as shown in FIG and by a Einschnappkontur 13 of FIG. 4th

The seal 8, 9 of FIG. 1 is formed in cross-section S-shaped. The attached to the outer ring 1 opposite at the free end of the seal 8 and 9 located sealing lip 10 is respectively aligned with the inner ring 2 and forms a defined gap 14 to the inner ring 2, which is so large that the oil flow ensured by the tandem angular contact ball bearing is, but dirt particles can not enter the camp. By varying the gap size or gap height, the oil volume flow can be varied and controlled or adjusted. Occurring pressure differences can be reduced by a venting device explained later.

According to FIG. 2, the seal 8 or 9 has two sealing lips 10 arranged axially one behind the other, which bear on the inner ring 2 in the radial direction with a slight contact pressure.

In FIGS. 3 and 4, the sealing lip 10 of the seal 8, 9 lies in the radial direction with a slight contact pressure on the inner ring 2. The seal 8, 9 as shown in FIG. 3 is provided with an L-shaped stiffening ring 15.

In the figures 5 to 8, the seals 8 and 9 are fixedly connected to the inner ring 2 of the tandem angular contact ball bearing, namely by press fit 12 according to FIG. 5, by a Einschnappkontur 13 according to FIG. 6 and by a groove-shaped insertion contour 1 1 according to the FIGS. 7 and 8. The seals 8 or 9 according to FIGS. 7 and 8 are provided with stiffening rings 15.

According to FIG. 5, the seals 8, 9 have two gap seals which are arranged one behind the other and abut radially on the outer ring 1.

In Fig. 6, the sealing lip 10 of the seal 8, 9 in the radial direction with only slight contact pressure on the outer ring 1 at. In the embodiments of FIG. 7 and FIG. 8, the sealing lips 10 of the seals 8, 9 with a slight contact pressure axially on the outer ring 1, wherein according to FIG. 7, the sealing lip 10 of the seal 8 in the axial and the sealing lip 10 of the seal 9 in axial and radial direction on the outer ring 1 is applied. In the variant according to FIG. 8, the sealing lips 10 of the seals 8 and 9 are located axially inwards or axially outwards on the outer ring 1.

In Figures 9 to 12, the seals 8 and 9 are fixedly connected to the inner ring 2 of the tandem angular contact ball bearing, namely by press fit 12 as shown in FIG. 9, by a groove-shaped recess contour 11 according to Figures 10 and 1 1 and by a Einschnappkontur 13 shown in FIG. 12. The seals 8 and 9 according to Figures 9, 10 and 12 are each provided with an L-shaped stiffening ring 15.

According to FIG. 9, the seal 8 or 9 is substantially L-shaped and reinforced in the region of the press fit 12 to the inner ring 2. The sealing lip 10 of the seal 8 or 9 according to FIGS. 9, 10 and 12 is in each case in radial alignment with the outer ring 1.

On the other hand, the sealing lip 10 of the seal 8 or 9 forms according to FIG. 1 1 a defined gap 14 in axial alignment with the outer ring 1. The seal may for example consist of antimagnetic, stainless steel or titanium steel, a sintered material or a bronze material having different thermal expansion coefficients , As a result, the width of the gap 14 can be varied depending on the intended use of the tandem angular contact ball bearing.

In the figures 13 to 15, the seals 8 are fixedly connected to the outer ring 1 and the seals 9 fixed to the inner ring 2 of the tandem angular contact ball bearing, namely by press fit 12 of FIG. 13, by a Einschnappkon- tur 13 of FIG. 14 and by a 11, as shown in FIG. 15. The seals 8, 9 according to FIG. 15 are each provided with an L-shaped stiffening ring 15. The seals 8, 9 according to FIG. 13 have the seals 8, 9 two successively arranged gap seals, which rest radially on the outer ring 1.

In the gasket according to FIG. 14, the sealing lip 10 of the gasket 8 lies in the radial direction with only slight contact pressure on the inner ring 2 and the sealing lip 10 of the gasket 9 likewise on the outer ring 1.

According to FIG. 15, the sealing lip 10 of the seal 8 lies in the axial and radial direction with slight contact pressure on the inner ring 2 and the sealing lip 10 of the seal 9 only in the axial direction on the outer ring 1. The seals 8 and 9 are each provided with an L-shaped stiffening ring 15.

In Figures 16 to 18, the seal 8 is fixedly connected to the outer ring 1 and the seal 9 in each case fixed to the inner ring 2 of the tandem angular contact ball bearing, namely by press fit 12 of FIG. 18, by a puncture contour 1 1 of FIG. 17 and by The gaskets 8 and 9 according to FIGS. 16 and 18 are also provided with an L-shaped stiffening ring 15 in these embodiments as well.

According to FIG. 16, the sealing lip 10 of the seal 8 lies in the radial direction with slight contact pressure on the inner ring 2 and the sealing lip 10 of the seal 9 in the radial direction on the outer ring 1. The seals 8 and 9 are each provided with an L-shaped stiffening ring 15.

17 has in the radial direction to the inner ring 2 and forms a defined axial gap 14 with the inner ring 2. However, the sealing lip 10 of the seal 9 to the outer ring 1 and there also forms a axially defined gap 14 to the outer ring. 1

According to FIG. 18, the seals 8 and 9 have a substantially L-shaped cross-section and are reinforced in the region of the press fit 12 to the outer ring 1 or inner ring 2. The sealing lips 10 of the seals 8 and 9 are respectively in axial and radial alignment on the outer ring 1 and inner ring 2 at. The seals 8 and 9 in FIGS. 16 and 18 are each also provided here with an L-shaped stiffening ring 15.

Fig. 19 shows that the seals 8 and 9 are respectively fixed to one of the bearing cages 6 and 7, respectively. These seals 8 and 9 have at their two radial ends in each case a sealing lip 10. These two sealing lips 10 of the seals 8 and 9 are with only slight contact pressure on the outer ring 1 and inner ring 2 at.

In Fig. 20 an embodiment of the tandem angular ball bearing is shown together with an enlarged portion, in which the seal 8 as a ventilation device 16, a ventilation window made of a porous material, e.g. Sintered or foam material. This ventilation and venting window serves to avoid build-up pressure conditions in the bearing. The arrow symbolizes the exchange of air between the warehouse interior and the surroundings. The tandem angular contact ball bearing is in this case similar to the bearing in FIG. 12.

Another type of ventilation device 16 for avoiding pressure states is shown in FIG. 21 together with an enlarged partial area, which is designed as a gap or labyrinth channel. The ventilation takes place in accordance with the arrow shown on the formed between the outer ring 1 and the sealing lip 10 of the seal 8 gap 14. The tandem angular contact ball bearing is similar to the bearing in Fig. 1 1 formed.

In the embodiment of the tandem angular contact ball bearing illustrated in FIG. 22, similar to that shown in FIG. 20, near the seal 8 in the region of the transition from the sealing lip 10 to the outer ring 1 as a loading and venting device 16 is an axially extending ventilation and venting groove 17 introduced, wherein the course of the ventilation is indicated by the arrow. Fig. 23 shows a further embodiment of the tandem angular contact ball bearing, similar to that shown in FIG. 21, wherein the ventilation and venting groove 17 is formed in the region of the seal seat on the inner ring 2 and also here represents an arrow the ventilation and venting.

In Fig. 24 is an embodiment of the tandem angular ball bearing together with an enlarged portion, similar to the bearing shown in Fig. 5, which illustrates a press fit 12 of the seal 8 on the inner ring 2. The two seals 8, 9 have two successively arranged gap seals, which rest radially on the outer ring 1.

Furthermore, Fig. 25 shows another embodiment of the invention, in which the tandem angular contact ball bearing is constructed similar to that of FIG. 6, wherein the seal 8 is formed by means of press fit 12 and a Einschnappkontur 13 for attachment to the inner ring 2.

Fig. 26 shows an embodiment of the tandem angular contact ball bearing according to the invention, which is constructed similar to that shown in FIG. 10, together with a radially enlarged portion of the seal seat, by means of which the seal 8 is fixed in an annular Einstechkontur 1 1 on the inner ring 2.

Finally, Fig. 27 shows an embodiment of the tandem angular ball bearing according to the invention, similar to the bearing shown in Fig. 9, together with an axially enlarged portion. Here, the applied with press fit 12 on the inner ring 2 seal 8 is axially secured by an additional locking ring 18 in the bearing 1, which engages in an introduced into the inner ring 2 paragraph 19 or a groove.

It should be noted that the mentioned features of the invention can be used not only in the respectively indicated combinations, but also in other combinations or in details.

PAGE INTENDED EMPTY

LIST OF REFERENCE NUMBERS

1 outer ring 2 inner ring

3 bearing ball set

4 bearing ball set

5 shoulder

6 bearing cage 7 bearing cage

8 seal

9 seal

10 sealing lip

11 puncture contour 12 press fit

13 snap contour

14 gap

15 stiffening ring

16 Ventilation device 17 Vent groove

18 lock ring

19 paragraph

Claims

claims

1. Tandem angular contact ball bearings for supporting a drive shaft in a transfer case, in particular for a motor vehicle, with a one-piece outer ring (1) and a one-piece inner ring (2), between which at least two sets of bearing balls (3, 4) in each case a bearing cage (6, 7 ) are guided in raceways of different diameters, wherein in each case a seal (8, 9) with at least one sealing lip (10) is arranged on the two plan sides of the tandem angular contact ball bearing.

2. Tandem angular contact ball bearing according to claim 1, characterized in that the seal (8, 9) is designed as a sealing ring or sealing disc.

3. Tandem angular contact ball bearing according to claim 1 or 2, characterized in that the seal (8, 9) fixed to the outer ring (1) and / or the inner ring (2) is connected.

4. tandem angular contact ball bearing according to one of claims 1 to 3, characterized in that the seal (8, 9) with press fit (12) on the outer ring (1) or on the inner ring (2) is fixed.

5. Tandem angular contact ball bearing according to one of claims 1 to 4, characterized in that the seal (8, 9) is fixedly connected to the bearing cage (6, 7).

6. Tandem angular contact ball bearing according to one of claims 1 to 5, characterized in that the at least one sealing lip (10) of the seal (8, 9) with a slight contact pressure on the outer ring (1) and / or inner ring (2).

7. tandem angular contact ball bearing according to one of claims 1 to 5, characterized in that the at least one sealing lip (10) of the seal (8, 9) leaving a small gap (14) without contact pressure to the outer ring (1) and / or inner ring ( 2) is directed.

8. tandem angular contact ball bearing according to one of claims 1 to 6, characterized in that the at least one sealing lip (10) of the seal (8, 9) in the axial and / or radial direction on the outer ring (1) and / or inner ring (2).

9. tandem angular contact ball bearing according to one of claims 1 to 7, characterized in that the at least one sealing lip (10) of the seal (8,9) in the axial and / or radial direction to the outer ring (1) and / or inner ring (2) is directed ,

10. tandem angular contact ball bearing according to one of claims 1 to 9, characterized in that the seal (8, 9) with a press fit (12) and a Einschnappkontur (13) on the outer ring (1) or on the inner ring (2) is fixed.

1 1. Tandem angular contact ball bearing according to one of claims 1 to 10, characterized in that the seal (8, 9) by means of a puncture contour (11) on the outer ring (1) or inner ring (2) is fixed.

12. tandem angular contact ball bearing according to one of claims 1 to 1 1, characterized in that the seal (8, 9) by means of a locking ring (18) on the outer ring (1) or inner ring (2) is fixed.

13. Tandem angular contact ball bearing according to one of claims 1 to 12, characterized in that the light contact pressure on the outer ring (1) and / or inner ring (2) fitting seal (8, 9) made of an elastomer such as NBR, H-NBR, ACM and FPM or a thermoplastic material.

14. tandem angular contact ball bearing according to one of claims 1 to 12, characterized in that the leaving a small gap (14) without contact pressure to the outer ring (1) and / or inner ring (2) directed seal (8, 9) made of steel, such as antimagnetic Steel, stainless steel or Titanium steel, a sintered material, a bronze material, a technical plastic or an elastomer such as NBR, H-NBR, ACM and FPM consists.

15. Tandem angular contact ball bearing according to one of claims 1 to 14, characterized in that the seal (8, 9) with a stiffening ring (15) is provided.

16. Tandem angular contact ball bearing according to one of claims 1 to 15, characterized in that the seal (8, 9) with a ventilation device (16) is provided.

17. Tandem angular contact ball bearing claim 16, characterized in that the seal (8, 9) has a ventilation section of a porous sintered or foam material.

18. Tandem angular contact ball bearing according to claim 16 and / or 17, characterized in that the seal (8, 9) has a gap or labyrinth channel or a groove (17) in the seal seat or sealing lip area for ventilation of the bearing.