DE102022127976B4 - Rolling bearings - Google Patents

Abstract

Rolling bearings (1)
- with a bearing outer ring (5) arranged around an axially extending rotation axis (2), having a first outer ring rim (3) and an axially opposite second outer ring rim (4), which bearing outer ring has a radial first raceway (6),
- with a bearing inner ring (9) arranged concentrically to the bearing outer ring (5), having a first inner ring rim (7) and an axially opposite second inner ring rim (8), which has a second raceway (10) radially opposite the first raceway (6),
- with a cage (11) which has an annular cage ring (13) which has a cage back (12) and is arranged around the rotational axis (2), from which cage ring axially extend webs (14) for forming rolling element pockets (15), and which guides rolling elements (16) rolling on the raceways (6, 10) in a rolling element row (17) rotatably in the rolling element pockets (15), wherein the cage back (12) has a first cage rim (18) and a second cage rim (19) at its radial boundary surfaces, wherein one of the two bearing rings (5, 9) rotates around the rotational axis (2) during operation of the rolling bearing (1), while the other of the two bearing rings (5, 9) is designed to be torsionally rigid, and wherein on an axially opposite side, adjacent to the rolling element row (17), the cage back (12) has a radial gap (21) between the bearing outer ring (5) and the bearing inner ring (9) in such a way that the first cage rim (18) forms a first gap seal (22) with the first outer ring rim (4) and the second cage rim (19) forms a second gap seal (23) with the first inner ring rim (7) for regulating a lubricating medium flow, characterized by a cover plate (20) running radially between the bearing outer ring (5) and the bearing inner ring (9), which cover plate is arranged axially on one side, adjacent to the row of rolling elements (17), on the rotating bearing ring (5, 9) for covering the bearing, wherein a further cover plate (27) is arranged axially adjacent to the cover plate (20).

Description

Field of the invention

The invention relates to a rolling bearing with a centrifugal disc.

Background of the invention

As in DE 10 2016 211 226 B3 As described above, components of the powertrain in motor vehicles, such as the traction motor (the motor that provides the drive power to overcome driving resistance), or a traction transmission (the transmission that adapts the drive power provided by the traction motor to the driving resistance), are lubricated and cooled. The general goal is to provide this lubrication/cooling functionality using the simplest means possible, yet with the greatest possible efficiency.

In DE 10 2020 112 044 A1 A rolling bearing with a rotating inner bearing ring and a stationary outer bearing ring is disclosed. A centrifugal disk formed from sheet metal is arranged on at least one bearing end face to cover the bearing and is attached to the inner bearing ring. The centrifugal disk forms a gap with the radial boundary surface of the outer bearing ring. A radially extending stop section is also located between the centrifugal disk and the rolling elements, which adjoins an axially extending flange section of the outer bearing ring.

Out of US 6,283,634 B1 Several designs of a rolling bearing with flingers emerge. In several designs, a flinger made from sheet metal is arranged on each of the bearing end faces to cover the bearing. Each flinger is positively attached to an outer radial receiving edge section of the bearing inner ring via a fastening edge section. The outer edge section of the flinger forms a radial gap with a sealing edge section of the bearing outer ring on the inner wall side. This gap, on the one hand, allows relative rotation between the bearing inner ring and the bearing outer ring and, on the other hand, ensures the most complete shielding of the bearing inner ring against the ingress of dirt and lubricating oil.

DE 10 2018 123 495 A1 discloses a ball bearing with a rotating inner bearing ring and a torsionally rigid outer bearing ring, which has a sealing arrangement on both sides. The sealing arrangement consists of a one-piece steel flinger that is frictionally fixed to the bearing inner ring. A sealing collar of the flinger is guided contactlessly to a sealing surface of the bearing outer ring, maintaining a gap.

The DE 699 25 976 T2 reveals a cage for a ball bearing.

Object of the invention

The invention is based on the object of providing an improved rolling bearing.

Description of the invention

According to the invention, this object is achieved by a rolling bearing with a bearing outer ring arranged around an axially extending axis of rotation, having a first outer ring rim and an axially opposite second outer ring rim, which bearing outer ring has a radial first raceway, with a bearing inner ring arranged concentrically to the bearing outer ring, having a first inner ring rim and an axially opposite second inner ring rim, which bearing inner ring has a second raceway radially opposite the first raceway, with a cage which has an annular cage ring having a cage back and is arranged around the axis of rotation, from which webs extend axially to form rolling element pockets, and which guides rolling elements rolling on the raceways in a row of rolling elements rotatably in the rolling element pockets, wherein the cage back has a first cage rim and a second cage rim at its radial boundary surfaces and with a cover plate extending radially between the bearing outer ring and the bearing inner ring, wherein one of the two bearing rings rotates around the axis of rotation during operation of the rolling bearing, while the other of the both bearing rings are designed to be torsionally rigid, wherein the cover plate for covering the bearing is arranged axially on one side, adjacent to the row of rolling elements, on the rotating bearing ring and on an axially opposite side, adjacent to the row of rolling elements, the cage back bridges a radial gap between the bearing outer ring and the bearing inner ring in such a way that the first cage rim forms a first gap seal with the first outer ring rim and the second cage rim forms a second gap seal with the first inner ring rim for regulating a lubricating medium flow. The rolling bearing is designed in particular as a ball bearing and is arranged around an axis of rotation. The axis of rotation runs in the axial direction. A radial direction runs perpendicular to the axis of rotation. A bearing outer ring, a bearing inner ring and an annular cage are arranged radially around the axis of rotation. The bearing outer ring and bearing inner ring are arranged such that the bearing outer ring is radially further away from the rotation axis than the bearing inner ring. Both bearing rings are arranged axially in the same direction. The cage has a cage ring which is arranged axially offset between the bearing outer ring and the bearing inner ring. Webs extend axially from the cage ring. These webs, together with the cage ring, form holding pockets for the rolling elements. The rolling elements are arranged axially in the same direction in a row of rolling elements. The bearing outer ring has a first raceway radially. Radially opposite this raceway and radially closer to the axis of rotation than the first raceway, the bearing inner ring has a second raceway. The rolling elements roll on these raceways in the rolling element pockets. The section of the cage which has the side which is axially facing away from the rolling elements forms the cage back. The cage back is arranged radially between the bearing outer ring and the bearing inner ring. The bearing outer ring has a first outer ring rib on the interface which faces the bearing inner ring, on the side on which the cage is located. On the axially opposite side, the bearing outer ring has a second outer ring rib. Similarly, the bearing inner ring has a first inner ring rib at the interface facing the bearing outer ring, on the side where the cage is located. On the axially opposite side, the bearing inner ring has a second inner ring rib. Radially opposite the first outer ring rib, the cage back has a first cage rib. Analogously, the cage back has a second cage rib radially opposite the first inner ring rib. In addition, the rolling bearing has a cover plate which is arranged between the bearing outer ring and the bearing inner ring. During operation, the bearing outer ring or the bearing inner ring rotates. One of the two bearing rings therefore rotates around the axially aligned axis of rotation, while the other bearing ring is fixed in position and does not rotate.

Axially adjacent to the cover plate is another cover plate. This can be arranged on the rotating bearing ring and function as a centrifugal disc similar to the cover plate. However, the additional cover plate can also be arranged on the torsionally rigid bearing ring. Depending on the application, it either serves the purpose of centrifuging incoming lubricant away using centrifugal force. Or the cover plate centrifuges incoming lubricant away, while the additional cover plate acts as an additional barrier to prevent the penetration of lubricants or dirt particles.

If a generic rolling bearing is installed in a gearbox, for example, the supply of a lubricating medium is not designed to meet the needs of each subcomponent of the system. There is a defined quantity of lubricating medium in the gearbox chamber, which must provide appropriate cooling and lubrication of the components for each operating point. An individual supply of lubricating medium to individual components, for example through controlled injection, cannot be implemented. This would require additional components, additional installation space and therefore additional costs. As a result of this flat rate of lubricating medium in the system, a large quantity of lubricating medium can accumulate on the rolling bearing. To prevent a lubricating medium from entering the rolling bearing, a cover plate can be used to cover the rolling bearing.

The invention is based on the finding that the use of cover plates on both sides of the rolling bearing has a detrimental effect, particularly in applications with high speeds. Due to the high centrifugal force, a cover plate acts as a flinger and can significantly restrict the entry of a lubricating medium such as oil into the rolling bearing. However, a flinger on the axially opposite side simultaneously prevents the lubricating medium from escaping from the rolling bearing. Lubricating medium continuously accumulates in the rolling bearing. This excess of lubricating medium in the rolling bearing leads to increased churning losses. The increased resistance during operation of the rolling elements leads to increased friction and thus to an increase in the internal bearing temperature. This, in turn, requires more intensive cooling and thus reduces the energy efficiency of the system. To avoid the described effect, the amount of lubricating medium in the rolling bearing must be regulated. However, this regulation must be possible without cost-intensive components and without requiring additional space in the rolling bearing environment.

The invention is based on the finding that it is expedient to attach a cover plate to the outer side of the rolling bearing axially opposite the cage ring to cover the bearing in order to prevent the inflow of lubricating media such as oil into the bearing. The cover plate is arranged radially between the bearing outer ring and the bearing inner ring, axially next to the row of rolling elements. The cover plate is firmly connected to the bearing ring, which rotates during operation of the rolling bearing. The other bearing ring is mounted in a rotationally fixed manner. If, for example, the bearing inner ring is intended for rotational movement during operation, the cover plate is mounted on the bearing inner ring, not on the bearing outer ring, which would be mounted in a rotationally fixed manner in this case. Analogously, the cover plate is connected to the bearing outer ring if this is the component that rotates during operation. The rotation of the corresponding bearing ring causes the bearing to rotate. the cover plate fixed there and can thus largely shield the rolling bearing from lubricating media flows. The cover plate can be connected in a form-fitting or force-fitting manner. The cover plate throws incoming lubricant away from the rolling bearing using centrifugal force and thus acts as a flinger plate. It keeps some of the incoming lubricant away. However, in order to regulate the amount of lubricant in the rolling bearing, lubricant must also be able to escape. At the same time, it must be prevented that an excessive volume of medium flows out in order to avoid the rolling bearing becoming insufficiently lubricated. For this purpose, the cage back on the axially opposite side of the row of rolling elements is designed with an optimized radial gap. The radial dimension of the cage back is selected such that the cage back forms a gap radially with the rim of the outer ring radially opposite it and with a rim of the inner ring radially opposite it. These gaps seal the rolling bearing against the ingress of dirt and particles, thus acting as gap seals. They also allow a corresponding amount of lubricant to escape. This eliminates the need for a flinger on the bearing side of the cage back. The lubricant can escape unhindered, but in a controlled manner as required. The respective gap seals can be adjusted as needed by adjusting the dimensions of the cage back, with the aim of ensuring an appropriate flow of lubricant in the rolling bearing. At the same time, this solution, which uses a single-sided flinger, enables component savings and thus reduces _CO2 emissions and costs.

Preferably, an annular disc is radially connected to the cage ring in such a way that the side of the cage ring facing away from the rolling elements and the side of the annular disc facing away from the rolling elements together form the cage back. The cage back is preferably made up of different sections. One section is formed by the part of the cage ring axially facing away from the rolling elements. Another section of the cage back is formed by part of an annular disc. The annular disc is radially connected to the cage ring. The annular disc can be radially connected to the cage ring on one side or both sides. It can be designed as a single piece with the cage ring. It can also be connected to the cage ring by a form-fitting, friction-fitting, or material fit. The annular disc can be made of the same material as the cage ring or a different material than the cage ring. If the annular disc is radially connected to the cage ring on one side, the cage back is made up of a section of the annular disc facing away from the rolling elements and a section of the cage ring facing away from the rolling elements. If the annular disc connects radially to the cage ring on both sides, the cage back consists of a section of the annular disc facing away from the rolling elements, a section of the cage ring facing away from the rolling elements, and another section of the annular disc facing away from the rolling elements. The dimensions of the cage back can be designed depending on the application. By designing its radial dimensions as required, it can prevent a sufficient amount of lubricant from entering the rolling bearing. At the same time, the cage back can ensure that the lubricant can be discharged as required thanks to the gap seals it forms with the bearing rings.

Preferably, the bearing outer ring has a section with a first radial projection between the first outer ring rim and the second outer ring rim and/or the bearing inner ring has a section with a second radial projection between the first inner ring rim and the second inner ring rim. Preferably, the bearing outer ring has, in addition to the area of the raceways, radially different dimensions. The area which lies axially between the first outer ring rim and the second outer ring rim can have a larger radial dimension than the area of the first and second outer ring rim. The first raceway can be located in the area with the larger radial dimension. Due to the recess required for the raceway, the radial dimension can be continuously reduced axially. This means that the radial dimension in the area of the first raceway can also be smaller than the radial dimension in the area of the first and second outer ring rim. Analogously, in addition to the bearing outer ring, or even instead of it, the bearing inner ring can have a larger radial dimension than the area of the first and second inner ring rim. Similarly, the second raceway can lead to a reduction in the radial dimension. The increase in the radial dimension on the bearing outer ring and/or inner ring can be sudden, in the form of a step, or continuously increasing. Adjusting a radial projection on the respective bearing ring also influences the gap seals. By varying the axial width of the annular washer, the gaps between the cage back and the bearing rings can be further adjusted.

Preferably, the annular disc engages radially behind the first radial projection and/or the second radial projection. Preferably, the annular disc is arranged such that an axial inner surface of the annular disc engages with an axial outer side of the first and/or second radial projection. radially overlapped. A section of the surface of the annular disc axially facing the rolling element is therefore directly axially opposite a section of the surface of the first and/or second radial projection axially facing away from the rolling element. Thus, the first and/or second gap seal can function like a labyrinth seal, since the orientation of the gaps between the bearing rings and the annular disc changes. Preferably, a radial dimension of a first radially extending gap and/or an axial dimension of a first axially extending gap between the bearing outer ring and a section of the annular disc directly opposite it each has a smaller value than a radial dimension from the first outer ring rim to the radial boundary surface of the first radial projection oriented towards the cage and/or a radial dimension of a second radially extending gap and/or an axial dimension of a second axially extending gap between the bearing inner ring and a section of the annular disc directly opposite it each has a smaller value than a radial dimension from the first inner ring rim to the radial boundary surface of the second radial projection oriented towards the cage. Preferably, the shortest radial distance between the first outer ring rim and the first cage rim has a value that is less than the radial height of the first radial projection, starting from the first outer ring rim. Or the shortest axial distance between the bearing outer ring and a section of the annular disc which is axially directly opposite the bearing outer ring is less than the radial height of the first radial projection, starting from the first outer ring rib. Or both the shortest radial distance between the first outer ring rib and the first cage rib and the shortest axial distance between the bearing outer ring and a section of the annular disc which is axially directly opposite the bearing outer ring each have a smaller dimension than the radial height of the first radial projection, starting from the first outer ring rib. The same applies to radial and axial gaps of the shortest distance that arise between the bearing inner ring and the annular disc. It can be the case that all gaps of the shortest distance between the bearing rings and the annular disc have a smaller dimension than the radial height between the radial projection on one of the bearing rings and the axially adjacent bearing ring rib. Likewise, only one of these gaps can have a smaller distance between the ring disc and a bearing ring than the respective radial projection on one of the bearing rings to the adjoining bearing ring rim.

Preferably, the radial dimension of the first gap seal and the radial dimension of the second gap seal differ from one another. Preferably, the radial distance between the first cage rim and the first outer ring rim and the radial distance between the second cage rim and the first inner ring rim differ from one another. By individually adjusting the respective gap seal, a more needs-based adjustment of the outlet openings for a lubricant can be implemented. Depending on the requirements, a directed lubricant flow can also be achieved.

Preferably, the cover plate forms a labyrinth seal with the additional cover plate, during which the orientation of a gap between the cover plate and the additional cover plate changes at least once. The additional cover plate can also be arranged adjacent to the cover plate in such a way that a gap in the form of a labyrinth seal is formed between the cover plates as required. This means that a penetrating medium must change its direction of movement at least once in order to pass through the labyrinth seal. This requirement can be implemented, among other things, by an L-shaped, Z-shaped, or C-shaped gap between the cover plate and the additional cover plate.

The cage is preferably made of plastic. Preferably, the cage is made of PA66-GF25 or PA46-GF30.

Preferably, the bearing outer ring and/or the bearing inner ring have a current-insulating layer. Preferably, the bearing outer ring and/or the bearing inner ring have a layer that does not conduct electricity. This prevents current from flowing through the rolling bearing, thereby increasing the service life of the rolling bearing.

The rolling bearing according to the invention is preferably used for electric drives, but the application of the rolling bearing according to the invention is not limited to this application.

Short description of the drawings

• 1 eine Prinzipdarstellung des erfindungsgemäßen Wälzlagers in einer geschnittenen Teilansicht,
• 2 eine Prinzipdarstellung einer Ausführungsform des erfindungsgemäßen Wälzlagers in einer geschnittenen Teilansicht,
• 3 eine Prinzipdarstellung einer Ausführungsform einer Lagerhälfte des erfindungsgemäßen Wälzlagers in einer geschnittenen Teilansicht.

The invention is explained below using exemplary embodiments with reference to the drawings. The drawings are schematic representations and show:

• 1 a schematic representation of the rolling bearing according to the invention in a sectional partial view,
• 2 a schematic representation of an embodiment of the rolling bearing according to the invention in a sectional partial view,
• 3 a schematic representation of an embodiment of a bearing half of the rolling bearing according to the invention in a sectional partial view.

Detailed description of the drawings

1 shows a sectional partial view of a rolling bearing 1 according to the invention designed as a ball bearing. The rolling bearing 1 is composed of a bearing inner ring 9 arranged around a rotation axis 2 and a bearing outer ring 5 of larger diameter arranged concentrically thereto, such that a radial gap 21 is formed between the bearing outer ring 5 and the bearing inner ring 9. The bearing outer ring 5 is delimited radially inwardly by boundary surfaces which form a first outer ring rim 3 and a second outer ring rim 4. Axially between the first outer ring rim 3 and the second outer ring rim 4, the bearing outer ring 5 has a first radial projection 25. The contour of the bearing outer ring 5 thus has a step on both sides axially on the radial inside. The first radial projection 25 has an arc-shaped recess which forms a first raceway 6 for rolling elements 16. The bearing inner ring 9 is delimited radially inwardly by boundary surfaces which form a first inner ring rim 7 and a second inner ring rim 8. Axially between the first inner ring rim 7 and the second inner ring rim 8, the bearing inner ring 9 has a second radial projection 26. The contour of the bearing inner ring 9 thus has a step on both sides axially on the radial inside. Between the first inner ring rim 7 and the second radial projection 26 there is a radially circumferential groove. The second radial projection 26 has an arc-shaped recess which forms a second raceway 10 for the rolling elements 16. Between the bearing inner ring 9 and the bearing outer ring 5 there is a cage 11 which comprises an annular cage ring 13. Webs 14 extend axially from this on one side and, together with the cage ring 13, form rolling element pockets 15 for rolling elements 16. The rolling elements 16 are arranged circumferentially in a rolling element row 17 and are guided by the cage 11 between the bearing outer ring 5 and the bearing inner ring 9 on the first and second raceways 6, 10. An annular disc 24 extends both from the cage ring 13 radially in the direction of the bearing outer ring 5 and from the cage ring 13 radially in the direction of the bearing inner ring 9. The cage ring 13 is thus flanked radially on both sides by the annular disc 24, which adjoins the cage ring 13 seamlessly. The axially outer sides of the cage ring 13 and the annular disc 24, i.e. the sides facing away from the rolling elements 16, together form a cage back 12. The cage back 12 is radially delimited on the side opposite the bearing outer ring 5 by a first cage rim 18. Analogously, the cage back 12 is delimited on the radially opposite side by a second cage rim 19. The cage back 12 extends radially over a large part of the radial gap 21. A gap remains radially between the first outer ring rim 3 and the first cage rim 18, which forms a first gap seal 22. Analogously, a gap remains radially between the first inner ring rim 7 and the second cage rim 19, which forms a second gap seal 23. Axially adjacent to the rolling element row 17, on the axially outer side without the cage back 12, there is a cover plate 20. This cover plate is arranged on the bearing inner ring 9 and extends radially in the direction of the bearing outer ring 5. A gap remains radially between the cover plate 20 and the second outer ring rim 4. Starting from the bearing inner ring 9, the cover plate 20 has a C-shaped curvature in a first section, followed by a non-curved, radially extending second section, before it transitions back to a C-shaped curvature in the third section. A radial gap is formed between the bearing outer ring 5 and the cover plate 20, which helps prevent the penetration of dirt or other particles. During operation, the bearing inner ring 9 rotates together with the cover plate 20 arranged on the bearing inner ring 9. Lubricating medium flowing in axially, on the side of the cover plate 20, bounces off the rotating cover plate 20 or is thrown away from the cover plate 20 by centrifugal force. Lubricating media located inside the bearing escape from the bearing interior through the gap seals 22, 23. The special geometry and arrangement of the cage ring 13, which is radially widened by the annular disc 24, and the resulting cage back 12, allows a path for a medium 29 to be defined to the outlet from the rolling bearing 1, and corresponding gap sizes can be adjusted as required. At the same time, disruptive particles are prevented from entering the bearing interior axially, on the side of the cage back 12. The cover disc 20 can regulate the ingress of lubricant into the bearing interior, and the escape of lubricant from the bearing interior through the cage back 12. This prevents uncontrolled buildup of lubricant inside the bearing, which leads to splashing losses.

2 shows a sectional partial view of a further embodiment of the rolling bearing 1 according to the invention. The rolling bearing 1 is analogous to 1 designed as a ball bearing with a bearing inner ring 9 arranged around a rotation axis 2 and a bearing outer ring 5 arranged concentrically thereto and a radial gap 21 between the bearing outer ring 5 and the bearing inner ring 9. The bearing outer ring 5 has, analogous to rolling bearings1 in 1 , a first outer ring rim 3, a second outer ring rim 4 and a first radial projection 25 on the bearing outer ring 5 and a second radial projection 26 on the bearing inner ring 9, which each form a raceway 6, 10 for rolling elements 16. The bearing inner ring 9 has a first inner ring rim 7 and a second inner ring rim 8. Between the bearing inner ring 9 and the bearing outer ring 5 there is a cage 11 with an annular cage ring 13, from which webs 14 extend axially on one side, which, together with the cage ring 13, form rolling element pockets 15 for the rolling elements 16. These are arranged in a row of rolling elements 17. An annular disc 24, which is directly connected to the cage ring 13, extends radially from the cage ring 13 in the direction of the bearing outer ring 5 as well as from the cage ring 13 radially in the direction of the bearing inner ring 9. The side of the annular disc 24 and the cage ring 13 facing away from the rolling elements 16 together form one cage back 12. This has a first cage rim 18 and a second cage rim 19 radially. A first gap seal 22 is formed between the first cage rim 18 and the first outer ring rim 3. Analogously, a second gap seal 23 is formed between the second cage rim 19 and the first inner ring rim 7. The annular disc 24 extends radially far enough in the direction of the first outer ring rim 3 that it overlaps the first radial projection 25. A partial surface of the annular disc 24 is therefore arranged axially opposite a partial surface of the first radial projection 25. Analogously, the annular disc 24 extends radially far enough in the direction of the first inner ring rim 3 that it overlaps the second radial projection 26. A partial surface of the annular disc 24 is therefore arranged axially opposite a partial surface of the second radial projection 26. The annular disc 24 thus engages radially on both sides behind the radial projections 25, 26 on the bearing rings 5, 9. Due to this arrangement, the gap seals 22, 23 function as a labyrinth seal 28 and define a path for a medium 29, in particular for the outlet of a lubricating medium. On the side of the rolling element row 17 axially opposite the cage 11, a cover disc 20 is arranged on the bearing inner ring 9. The cover disc 20 runs radially. Starting from the bearing inner ring 9, it has a C-shaped end section, then a straight section and finally a C-shaped initial section. Radially offset in the direction of the bearing outer ring 5, another cover disc 27 is arranged, which is located on the bearing outer ring 5. This cover disc has a radial gap to the second outer ring rim 4. An initial section of the additional cover plate 27 runs axially parallel to the second outer ring rim 4, then transitions into a radial course in the direction of the bearing inner ring 9 and has an end section curved axially away from the rolling element 16. The additional cover plate 27 overlaps radially with the cover plate 20. An end section of the additional cover plate 27 is axially offset from the initial section of the cover plate 20, so that a gap forms between the cover plates 20, 27. This gap is such that, starting from the additional cover plate 27, it initially runs radially straight in the direction of the bearing inner ring 9, but then aligns obliquely, away from the rolling element 16. The gap thus functions like a labyrinth seal 28. During operation, the bearing inner ring 9 rotates with the cover plate 20 arranged thereon. The additional cover plate 27 remains static, as does the bearing outer ring 5. Lubricating medium flowing in axially on the side of the cover plates 20, 27 bounces off the cover plates 20, 27 or is thrown away from the cover plate 20 by centrifugal force. Lubricating medium thrown from the cover plate 20 onto the additional cover plate 27 is carried away by the latter. The labyrinth seal 28 can be used to adjust a gap as needed, allowing the required amount of lubricant to enter the rolling bearing 1. At the same time, disruptive particles are prevented from entering. Lubricating media located inside the bearing escape from the bearing interior through the gap seals 22, 23. The special geometry and arrangement of the cage ring 13, which is radially widened by the annular disk 24, and the resulting cage back 12, defines a path for a medium 29, and corresponding gap sizes can be adjusted as required. At the same time, disruptive particles are prevented from entering the bearing interior axially on the side of the cage back 12. By combining the cover disk 20 with the additional cover disk 27, the ingress of lubricating medium into the bearing interior can be individually adjusted to suit the respective application. The cage back 12, in turn, ensures a controlled escape of lubricating medium from the bearing interior. A buildup of lubricating medium inside the bearing, which leads to efficiency losses in the rolling bearing 1, can be prevented in this way.

3 shows an embodiment of a rolling bearing 1 according to the invention in a double sectioned partial view. The rolling bearing 1 is arranged around an axially extending rotation axis 2 and has a bearing outer ring 5, a bearing inner ring 9 and, arranged between them, a cage 11 with a circular cage ring 13. The bearing outer ring 5 has a first outer ring rim 3 and a first radial projection 25. The first radial projection 25 has a dimension d _V1 , which extends radially from the radial boundary surface of the first outer ring rim 3 to the radial boundary surface of the axially adjoining first radial projection 25, which is radially opposite the cage ring 13. The bearing inner ring 9 has a first inner ring rim 7 and a second radial projection 26. The second radial projection 26 has a dimension d _V2 which runs radially from the radial boundary surface of the inner ring rim 7 to the radial boundary surface of the axially adjoining second radial projection 26, which is radially opposite the cage ring 13. Webs 14 extend axially on one side of the cage ring 13 and, together with the cage ring 13, form rolling element pockets 15 for rolling elements 16. An annular disk 24, which is directly connected to the cage ring 13, extends both radially from the cage ring 13 in the direction of the bearing outer ring 5 and radially from the cage ring 13 in the direction of the bearing inner ring 9. The side of the annular disc 24 and the cage ring 13 facing away from the rolling elements 16 together form a cage back 12. This has a first cage rim 18 and a second cage rim 19 radially. A first gap seal 22 is formed between the first cage rim 18 and the first outer ring rim 3. Analogously, a second gap seal 23 is formed between the second cage rim 19 and the first inner ring rim 7. The first gap seal 22 is smaller in its radial dimension than the second gap seal 23. The annular disc 24 extends radially so far in the direction of the first outer ring rim 3 that it overlaps with the first radial projection 25. Various gaps are formed in the process: A first radial gap is formed between the first outer ring rim 3 and the first cage rim 18 and has a dimension d _r1 . A first axial gap is formed between a partial surface of the annular disc 24 and an axially opposite partial surface of the first radial projection 25 and has a dimension d _a1 . On the radially opposite side of the cage ring 13, the annular disc 24 does not overlap the second radial projection 26. Here, a second radial gap is formed between the second cage rim 19 and the first inner ring rim 7, which second radial gap has a dimension d _r2 . A second axial gap is formed between a virtual radial extension of a partial surface of the annular disc 24, which is axially opposite the rolling elements 16, and a partial surface of the second radial projection 26 axially opposite this virtual radial extension. This gap has a dimension d _a2 . The dimensions d _r1 and d _a1 have a smaller value than the dimension d _V1 . d _r2 and d _a2 have a smaller value than the dimension d _V2 . This allows for the specification of outlet gaps and thus a path for a medium 29 as required. This ensures that the gap seals 22, 23 can implement the required discharge of a lubricating medium.

List of reference symbols

1

Rolling bearings

2

axis of rotation

3

first outer ring rim

4

second outer ring rim

5

Bearing outer ring

6

first career

7

first inner ring rim

8

second inner ring rim

9

Bearing inner ring

10

second career

11

cage

12

Cage back

13

Cage ring

14

Footbridges

15

Rolling element pockets

16

Rolling elements

17

Rolling element row

18

first cage board

19

second cage shelf

20

cover plate

21

Radial gap

22

first gap seal

23

second gap seal

24

Ring disc

25

first radial projection

26

second radial projection

27

additional cover plate

28

Labyrinth seal

29

Path of a medium

da1

Dimension of first axial gap

da2

Dimension of second axial gap

dr1

Dimension of first radial gap

dr2

Dimension of second radial gap

dV1

Dimension of first radial projection

dV2

Dimension of second radial projection

Claims (9)

Rolling bearing (1) - with a bearing outer ring (5) arranged around an axially extending rotation axis (2), having a first outer ring rim (3) and an axially opposite second outer ring rim (4), which has a first raceway (6) radially, - with a bearing outer ring (5) concentric with the bearing outer ring arranged, having a first inner ring rim (7) and an axially opposite second inner ring rim (8), which has a second raceway (10) radially opposite the first raceway (6), - with a cage (11) which has an annular cage ring (13) having a cage back (12) and arranged around the axis of rotation (2), from which webs (14) extend axially to form rolling element pockets (15), and which guides rolling elements (16) rolling on the raceways (6, 10) in a rolling element row (17) rotatably in the rolling element pockets (15), wherein the cage back (12) has a first cage rim (18) and a second cage rim (19) at its radial boundary surfaces, wherein one of the two bearing rings (5, 9) rotates around the axis of rotation (2) during operation of the rolling bearing (1), while the other of the two bearing rings (5, 9) is designed to be torsionally rigid, and wherein on an axially opposite side, adjacent to the row of rolling elements (17), the cage back (12) bridges a radial gap (21) between the bearing outer ring (5) and the bearing inner ring (9) in such a way that the first cage rim (18) forms a first gap seal (22) with the first outer ring rim (4) and the second cage rim (19) forms a second gap seal (23) with the first inner ring rim (7) for regulating a flow of lubricating media, characterized by a cover disk (20) running radially between the bearing outer ring (5) and the bearing inner ring (9), which cover disk is arranged axially on one side, adjacent to the row of rolling elements (17), on the rotating bearing ring (5, 9) for covering the bearing, wherein a further cover disk (27) is arranged axially adjacent to the cover disk (20). Rolling bearings (1) according to Claim 1 , characterized in that an annular disc (24) is radially connected to the cage ring (13) in such a way that the side of the cage ring (13) facing away from the rolling elements (16) and the side of the annular disc (24) facing away from the rolling elements (16) together form the cage back (12). Rolling bearings (1) according to Claim 1 , characterized in that the bearing outer ring (5) has a section with a first radial projection (25) between the first outer ring rim (3) and the second outer ring rim (4) and/or the bearing inner ring (9) has a section with a second radial projection (26) between the first inner ring rim (7) and the second inner ring rim (8). Rolling bearings (1) according to Claim 1 until 3 , characterized in that the annular disc (24) radially engages behind the first radial projection (25) and/or the second radial projection (26). Rolling bearings (1) according to Claim 4 , characterized in that a radial dimension of a first radially extending gap (d _r1 ) and/or an axial dimension of a first axially extending gap (d _a1 ) between the bearing outer ring (5) and a section of the annular disc (24) directly opposite thereto each has a smaller value than a radial dimension (d _V1 ) from the first outer ring rim (3) to the radial boundary surface of the first radial projection (25) oriented towards the cage (11) and/or that a radial dimension of a second radially extending gap (d _r2 ) and/or an axial dimension of a second axially extending gap (d _a2 ) between the bearing inner ring (9) and a section of the annular disc (24) directly opposite thereto each has a smaller value than a radial dimension (d _V2 ) from the first inner ring rim (7) to the radial boundary surface of the second radial projection (26) oriented towards the cage (11). Rolling bearings (1) according to Claim 2 , characterized in that the radial dimension of the first gap seal (22) and the radial dimension of the second gap seal (23) differ from one another. Rolling bearings (1) according to Claim 1 , characterized in that the cover plate (20) forms a labyrinth seal with the further cover plate (27), in the course of which the orientation of a gap between the cover plate (20) and the further cover plate (27) changes at least once. Rolling bearings (1) according to Claim 1 , characterized in that the cage (11) is designed as a plastic cage. Rolling bearings (1) according to Claim 1 , characterized in that the bearing outer ring (5) and/or the bearing inner ring (9) has a current-insulating layer.

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