DE102007014562A1 - Sealing arrangement on a rolling bearing - Google Patents

Abstract

The object to provide a non-contact seal assembly on a rolling bearing, which an axially applied overpressure, especially a high pressure (> 1 bar), and / or increased media pressures with changing pressure amplitudes and maximum pressure tolerates, is also space-saving and is also suitable substantially reducing the volume flow of lubricating oil or cooling oil flowing through the rolling bearing to a necessary degree is essentially achieved by a first and a second cover element (5, 7) which are arranged and constructed in such a way that a labyrinth seal with a plurality of pressure loss-affected Provision is made, whereby a leakage volume flow covers a long distance, wherein at least the second cover member (7) has such rigidity that operating media overpressures and / or changing pressures and pressure peaks lead to any significant deformation of the second cover member (7).

Description

Field of the invention

The The invention relates to a sealing arrangement on a roller bearing according to the features of claim 1.

Background of the invention

Rolling bearing seals have long been known in a variety of embodiments. So are for oil-lubricated bearings, for example, from the textbook "Dubbel", 20th edition, p. G90 ff. for keeping away from contaminants touching seals known, such as felt rings and radial shaft seals, the special design, such. B. sealing washers (suffix RS), can also be integrated into the rolling bearing, and mechanical seals, but which require a complex processing of the shaft surfaces. In addition, for oil-lubricated bearings at the same place in this textbook non-contacting seals are known, with integrated in the bearing cover plates (suffix Z), or outer labyrinths as Anwendungsungsspezi fiche construction or as purchased parts, such as Z-blades and resilient washers.

By way of example, this is the DE 43 09 813 A1 called, which discloses an outer labyrinth seal for rolling bearings, but requires a relatively large axial space.

From the DE 32 12 976 A1 Furthermore, a rolling bearing is known, which in the local 1 an RS-disc seal, so a touching seal shows, wherein at the two end faces of the bearing inner ring depending an annular disc is fixed, which extends from the bearing inner ring into the region of the inner circumferential surface of the bearing outer ring and the remaining between the bearing outer ring and bearing inner ring gap and the sealing element covers. The two washers are connected to the bearing inner ring by welding. Together with the axially inner RS sealing elements, the annular disks form a bearing seal that acts as a labyrinth seal at low speeds and as a spinning disk seal at high speeds. In the 2 This document, however, a rolling bearing is shown, which has instead of axially inner RS discs on both sides so-called, non-contacting Z-discs as sealing elements. However, it is known in the art that the said RS-disc seals or Z-plate seals for overpressures, which go beyond the measures provided for conventional sealing arrangements pressures, as well as permanently or temporarily applied to one side of the bearing, are in themselves unsuitable.

So For example, in a built-in a transmission and from Lubricating oil flowed through bearings in a particular Operating situation an increased overpressure in the lubricating oil occur. Are such bearings not sufficiently sealed, so can such increased pressures and / or pressure fluctuations disadvantageous to the sealing effect of the rolling bearing seals or affect the mentioned actuator functions. A complete seal of the bearing is but also not desirable because a lower, the bearings penetrating lubricant flow rather favored the operation of the same.

Object of the invention

Of these, Based on the object of the invention, a further improved non-contact sealing arrangement on a To provide rolling bearings, which have an axially applied overpressure, Above all, a high overpressure (> 1 bar) and / or increased media pressures with varying pressure amplitudes and pressure maxima coped with, moreover Space-saving and is also suitable, by the rolling bearing flowing through the medium volume flow (lubricating and / or Cooling oil) to a desired necessary To reduce the measure.

Summary of the invention

According to the Features of the main claim therefore relates to a sealing arrangement at a rolling bearing for leakage reduction of the same axially applied media overpressure and / or media with changing Press and pressure peaks, with a first axially spaced arranged to the rolling elements of the bearing and connected to a first bearing ring and largely disc-shaped trained cover, as well as a second largely Disc-shaped cover, which with a second bearing ring is connected and the first cover frontally of the rolling bearing or on the outside the same covered, wherein the first and the second cover member arranged and formed such that a labyrinth seal created with a plurality of pressure-lossy places, whereby a leakage volume flow a comparatively long distance covers and at least the second cover has such rigidity that operational media overpressures and / or changing pressures and pressure peaks to no significant Deformation of the second cover lead.

The Subclaims describe preferred developments or Embodiments of the invention.

After that can according to a first possible embodiment the first cover member within a circumferential groove of the first bearing ring be held positive and / or non-positive and avoidance a radial and axial contact of the second bearing ring in the radial direction over the end face, the same at least partially covering, extend.

By These measures are in the light of the prior art create effective labyrinths within the rolling bearing, due to the comparatively to be covered by the medium Long distances advantageous with pressure losses in the medium flow rate or leakage volume flow associated and accordingly the Flow between the overpressure and the low pressure side the rolling bearing to a desired order of magnitude to minimize.

According to one second variant, the first cover member within a circumferential groove the form of the first bearing ring and / or positively held be and avoid radial and axial contact of the second bearing ring is in a radial direction to the circumferential groove opposite arranged recess of the second bearing ring extend into it, whereby the zurückzulegenden of the medium Routes extended and accordingly the Labyrinths are further improved in their sealing effect.

As the invention further provides, the first cover in the direction cup-shaped to the rolling elements formed, whereby the space required for the same minimized and its rigidity are increased.

What As far as the axially outer, second cover element is concerned, so this is sealingly on the second bearing ring positive and / or non-positive or cohesively held and can while avoiding a radial and axial contact of the ers th bearing ring extend into an axial recess thereof, whereby the number the labyrinth is further advantageously increased.

In contrast, the outer second cover element can also while avoiding a radial and axial contact until close to a radially adjacent to the first bearing ring and connected to the same Be introduced component, reducing the number of mazes is also advantageously increased. In that component, with which the first bearing ring is connected, it may, for example to act a wave.

Possible it is further that the second cover member by defined shaping is supported in sections on the first bearing ring and at least the support area of the second cover element and / or of the first bearing ring oil pockets and / or microstructures to obtain a hydrodynamic lubricating film, whereby on the one hand as far as possible the claim to a non-contact Seal and on the other elevated, from the outside up the rolling bearing and its sealing arrangement act Press is taken into account.

Further it is judged useful if at least the second cover according to the expected media pressures and / or changing pressures (overpressure, negative pressure) and pressure maxima increased rigidity due to increased Wall thickness and / or a stiffening shape in shape having beads, tangential grooves and / or radial webs.

Furthermore it can be provided that the first and the second cover element of metal or plastic or other suitable material, such as a composite material.

After all is provided in a preferred embodiment that the first bearing ring as the inner ring and the second bearing ring as the outer ring of Rolling bearing is formed.

Brief description of the drawings

The The invention will be described below with reference to the accompanying drawings some embodiments explained in more detail. It shows:

1 FIG. 2 a partial axial sectional view of a rolling bearing with the sealing arrangement according to the invention according to a first embodiment; FIG.

2 a second embodiment of the seal assembly on the rolling bearing,

3 a third variant of the seal assembly, and

4 A fourth embodiment of the seal assembly.

Detailed description the drawings

1 shows a rolling bearing in the manner of a known deep groove ball bearing with a first radially inner bearing ring 1 and a second, radially outer bearing ring 2 , between which in raceways rolling elements 3 are guided in the form of balls. The rolling elements 3 are from a pertinent known cage 4 held.

Again 1 is further shown axially spaced from the rolling elements 3 of the rolling bearing largely disc-shaped first cover 5 arranged, which within a circumferential groove 6 of the first bearing ring 1 , In this case, the bearing inner ring, held positively and / or non-positively, preferably in the same is blasted.

The first cover element 5 extends in the radial direction outwards over the end face of the second bearing ring 2 without touching it radially or axially. Next covers the first cover 5 on the one hand between the two bearing rings 1 . 2 on the other hand, at least partially the end face of the second, radially outer bearing ring 2 ,

As already mentioned above, are by this structural design of the rolling bearing in the region of the end face of the bearing outer ring 2 created effective labyrinths, which are advantageous due to the zurückzulegenden from the liquid medium, comparatively long distances associated with pressure losses in the medium volume flow or in the leakage flow and thus allow to minimize the flow between the pressure side and the low pressure side of the bearing.

Due to the fact that the first cover element 5 towards the rolling elements 3 is designed cup-shaped, its rigidity is advantageously increased. Furthermore, the required space is minimized because of the formed bottom of the cup-shaped first cover 5 axially into the free space of the annular gap between the two bearing rings 1 . 2 extends into it.

However, it is also possible and by the invention accordingly detected that the first cover member 5 while avoiding a radial and axial contact of the second, radially outer bearing ring 2 in one of the circumferential groove 6 in the radial direction opposite arranged recess of the second bearing ring 2 extends, thereby further extending the distance traveled by the medium and thus the labyrinths are further improved in terms of their sealing effect (not shown in detail).

Furthermore, a second, largely disc-shaped cover 7 provided, which with the second bearing ring 2 , in this case, the bearing outer ring, sealingly connected by positive and / or frictional connection or by material bond, for example by welding, and the first cover member 5 the end face of the rolling bearing or the outside of the same covered.

Conveniently, the axially outer, second cover member 7 within an annular recess 8th of the bearing outer ring 2 held and extends radially inward to an annular axial recess 9 of the bearing inner ring 1 and extends into the same axially, without the first bearing ring 1 to touch radially and axially.

hereby is the desired labyrinth seal even further improved, since the distance to be traveled by the media volume flow is further extended by this when entering in the rolling bearing from radially inside to radially outside and back again to flow radially inward and Furthermore, exceed extremely small gap widths got to.

The embodiment according to 2 differs from the according to 1 merely in that the second cover element 7 instead of in a prepared recess 9 of the first bearing ring 1 close to one to the first bearing ring 1 adjacent and connected to the same component 10 For example, a shaft bearing the rolling bearing without the same and the first bearing ring 1 radially and axially touching, introduced, whereby also an extremely narrow gap is created, which is to be overcome by said media volume flow. By meaningful dimensioning of said column is achieved that even with pressure fluctuations in the lubricating or pressure medium only a small but desirable flow of lubricant is passed through the bearings.

To the above-mentioned overpressures, which act mainly from the outside on the rolling bearing and its seal arrangement, to be able to effectively and effectively counteract, the second cover 7 by a defined shaping sections on the first bearing ring 1 be supported.

Like the embodiment of 3 is to accomplish such support the in 2 shown second cover 7 in the area of the first bearing ring 1 or bearing inner ring with at least one of the first bearing ring 1 pointing bulge 11 Mistake. This at least one bulge 11 can hereby be annular or ring-segment-shaped or locally highly limited, so for example punctiform.

In order to meet the demand for a non-contact and thus low-friction seal, have at least the support area (bulge 11 ) of the second cover member 7 and / or the first bearing ring 1 Oil pockets and / or microstructures unspecified on their surfaces for producing a hydrodynamic lubricating film.

In contrast, or in combination with the above measure to increase the rigidity of the seal assembly, in particular the radially äuße ren second cover member 7 , The same may have an increased wall thickness with respect to conventional cover elements or cover plates. Furthermore, stiffening shapes in the form of beads, tangential grooves and / or radial webs can be provided (not shown in detail).

Such stiffening shapes can be quite easily in the production of cover elements 5 . 7 made of sheet steel by deep drawing and cover elements 5 . 7 made of plastic by injection molding. Certainly, other cheap materials for the production of the cover 5 and or 7 , such as composites, for use cases with media overpressions possible.

Likewise, it may also be useful, the radially outer, second cover 7 in such a way that although a deflection of the same as a result of the acting pressure is possible, however, the maximum bending only to the extent that a contact with the first bearing ring 1 (Bearing inner ring) and connected to the same component 10 (Wave) is avoided.

Such a disadvantageous contact can, for example, be counteracted by the free disk section of the second cover element 7 in the initial state or unpressurized state axially outward, that is bent away from the rolling bearing ( 4 ) and is deformed elastically only to a limited extent axially to the rolling bearing when a pressure is applied.

The embodiments described in more detail on a first bearing ring 1 in the form of a bearing inner ring and on a second bearing ring 2 in the form of a bearing outer ring. However, the invention is not limited to these embodiments, but also covers the reverse case, by the first bearing ring 1 is formed by the bearing outer ring, on which the first cover member 5 supported, and the second bearing ring 2 is formed by the bearing inner ring, on which the outer second cover member 7 supported, based on the 2 to 4 the component 10 then formed by, for example, a bearing housing carrying the outer bearing ring (not shown in detail).

1

first bearing ring

2

second bearing ring

3

rolling elements

4

Cage

5

first cover

6

circumferential groove

7

second cover

8th

Annular recess (second bearing ring 2 )

9

Annular recess (first bearing ring 1 )

10

component

11

bulge

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 4309813 A1 [0003]
• - DE 3212976 A1 [0004]

Cited non-patent literature

• - "Dubbel", 20th Edition, p. G90 et seq. [0002]

Claims (10)

Sealing arrangement on a roller bearing for reducing the same leakage at axially applied media overpressure and / or media with changing pressures and pressure peaks, with a first axially spaced from the rolling elements ( 3 ) of the rolling bearing and with a first bearing ring ( 1 ) connected and largely disc-shaped cover ( 5 ), as well as with a second largely disc-shaped cover ( 7 ), which with a second bearing ring ( 2 ) and the first cover element ( 5 ) frontally of the rolling bearing or the outside of the same, wherein the first and the second cover ( 5 . 7 ) are arranged and formed such that a labyrinth seal is provided with a plurality of pressure-loss-bearing points, whereby a leakage volume flow travels a long distance, and wherein at least the second cover element ( 7 ) has such rigidity that operational media overpressures and / or changing pressures and pressure peaks do not lead to any substantial deformation of the second cover element ( 7 ) to lead. Sealing arrangement according to claim 1, characterized in that the first cover element ( 5 ) within a circumferential groove ( 6 ) of the first bearing ring ( 1 ) is held positively and / or non-positively and while avoiding a radial and axial contact of the second bearing ring ( 2 ) extends in the radial direction over the end face, the same at least partially overlapping. Sealing arrangement according to claim 1, characterized in that the first cover element ( 5 ) within a circumferential groove ( 6 ) of the first bearing ring ( 1 ) is held positively and / or non-positively and while avoiding a radial and axial contact of the second bearing ring ( 2 ) in one of the circumferential groove ( 6 ) in the radial direction opposite arranged recess of the second bearing ring ( 2 ) extends into it. Sealing arrangement according to at least one of claims 1 to 3, characterized in that the first cover ( 5 ) in the direction of the rolling elements ( 3 ) is formed cup-shaped. Sealing arrangement according to at least one of claims 1 to 4, characterized in that the axially outer, second cover member ( 7 ) sealing on the second bearing ring ( 2 ) held positively and / or non-positively or cohesively and while avoiding a radial and axial contact of the first bearing ring ( 1 ) in an axial recess ( 9 ) extends it. Sealing arrangement according to at least one of claims 1 to 4, characterized in that the outer second cover element ( 7 ) from the second bearing ring ( 2 ) held positively and / or non-positively or cohesively and while avoiding a radial and axial contact to close to a first bearing ring ( 1 ) radially adjacent and connected to the same component ( 10 ) is introduced. Sealing arrangement according to at least one of claims 1 to 6, characterized in that the second cover ( 7 ) by defined shaping in sections on the first bearing ring ( 1 ) is supported and at least the support region of the second cover ( 7 ) and / or the first bearing ring ( 1 ) Have oil pockets and / or microstructures on their surface to achieve a hydrodynamic lubricating film. Sealing arrangement according to at least one of claims 1 to 7, characterized in that at least the second cover element ( 7 ) has increased rigidity due to increased wall thickness and / or stiffening shape in the form of beads, tangential grooves and / or webs according to the expected media pressures and / or changing pressures and pressure peaks. Sealing arrangement according to at least one of claims 1 to 8, characterized in that the first and the second cover element ( 5 . 7 ) made of metal or plastic or other suitable material, such as a composite material. Sealing arrangement according to at least one of claims 1 to 9, characterized in that the first bearing ring ( 1 ) as inner ring and the second bearing ring ( 2 ) is formed as an outer ring of the rolling bearing.