Rolling bearings

Abstract

Rolling bearings (1) - with a torsionally rigid bearing outer ring (3) arranged around a rotation axis (2) running in the axial direction (a), which outer ring has a first raceway (4), - with a bearing inner ring (5) arranged concentrically to the bearing outer ring (3), which rotates about the rotation axis (2) and has a second raceway (6) opposite the first raceway (4) in the radial direction (r), - with a cage (7) which has a side ring (8), - with a row of rolling elements (9) arranged between the first raceway (4) and the second raceway (6), - with a first cover plate (10) which is arranged on the torsionally rigid bearing outer ring (3), - with a second cover plate (11) which is arranged on the rotating bearing inner ring (5), wherein the first cover plate (10) is arranged axially on one side, adjacent to the row of rolling elements (9), and the second cover plate (11) is arranged on one side on the axially opposite side, adjacent to the row of rolling elements (9), characterized in that the first cover plate (10) and / or the second cover plate (11) consists of a bimetal.

Description

Field of the invention

[0001] The invention relates to a rolling bearing with two cover plates. Background of the invention

[0002] As described in DE 10 2016 211 226 B3, drivetrain components in motor vehicles, such as the traction motor (i.e., the motor that provides the drive power to overcome driving resistance), or a traction transmission (i.e., a 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.

[0003] DE 10 2020 112 044 A1 discloses a rolling bearing with a rotating inner bearing ring and a stationary outer bearing ring. 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.

[0004] US Pat. No. 6,283,634 B1 discloses several embodiments of a rolling bearing with flingers. In several embodiments, a flinger formed from sheet metal is arranged on each of the bearing end faces to cover the bearing. Each flinger is positively secured to an outer radial receiving edge portion of the bearing inner ring via a fastening edge portion. The outer edge portion of the flinger forms a radial gap with a sealing edge portion of the bearing outer ring on the inner wall side, which, 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 interior from the ingress of dirt and lubricating oil.

[0005] 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.

[0006] DE 10 2017 220 661 A1 discloses a rolling bearing with a sealing device comprising two protective shields on each axial side. The protective shields are each arranged axially in a row. On each axial side of the rolling bearing, a protective shield is arranged on the bearing outer ring, which is designed to be torsionally rigid. The second protective shield is arranged on the bearing inner ring, which is designed to rotate. An annular gap is formed between the protective shields on each axial side of the rolling bearing, each having a first and a second sealing labyrinth.

[0007] A rolling bearing having the features of the preamble of claim 1 is disclosed in JP 2008-025 685 A. Object of the invention

[0008] The invention is based on the object of providing an improved rolling bearing. Description of the invention

[0009] According to the invention, this object is achieved by a rolling bearing with a torsionally rigid bearing outer ring which is arranged around an axis of rotation running in the axial direction and which has a first raceway, with a bearing inner ring which is arranged concentrically to the bearing outer ring and rotates around the axis of rotation and has a second raceway opposite the first raceway in the radial direction, with a cage which has a side ring, with a row of rolling elements which is arranged between the first raceway and the second raceway, with a first cover plate which is arranged on the torsionally rigid bearing outer ring, with a second cover plate which is arranged on the rotating bearing inner ring, wherein the first cover plate is arranged axially on one side, adjacent to the row of rolling elements, and on the axially opposite side, adjacent to the row of rolling elements,the second cover plate is arranged on one side and wherein the first cover plate and / or the second cover plate consists of a bimetal.,

[0010] The material composition of the first cover plate can differ from that of the second cover plate. Due to the bimetallic design, the gap size between a cover plate and a bearing ring can change depending on the temperature of the cover plate. The temperature of a cover plate is related to the operating condition of the rolling bearing. This allows the amount of lubricant that can enter or exit the rolling bearing to be adjusted as needed depending on the operating condition.

[0011] The rolling bearing is particularly designed as a ball bearing and is arranged around a rotational axis. The rotational axis runs in the axial direction. A radial direction runs perpendicular to the rotational axis. A bearing outer ring, a bearing inner ring, and a cage are arranged radially around the rotational axis. The bearing outer ring and bearing inner ring are arranged such that the bearing outer ring is radially further away from the rotational axis than the bearing inner ring. A radial gap is formed between the bearing inner ring and bearing outer ring, i.e. a gap in the radial direction, so that the bearing outer ring and bearing inner ring do not come into contact. The cage has a side ring, i.e. a circular ring, from which retaining arms or webs can extend. The cage can be designed as a snap cage, comb cage, or pocket cage. The bearing outer ring has a first raceway.The bearing inner ring has a second raceway radially opposite the first raceway and at a smaller radial distance from the axis of rotation than the first raceway. Rolling elements in a row of rolling elements roll on the raceways. The bearing outer ring is arranged in a rotationally fixed manner, while the bearing inner ring rotates about the axis of rotation during operation. The rolling bearing has a first cover plate on the bearing outer ring, which is arranged axially adjacent to the row of rolling elements. On the axially opposite side of the row of rolling elements, the rolling bearing has a second cover plate on the bearing inner ring.

[0012] 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 in every case. This would require additional components, additional installation space and therefore additional costs. As a result of the defined quantity of lubricating medium in the system, an excessive amount of lubricating medium can accumulate in the rolling bearing at certain operating points. Conversely, there can also be too little lubricating medium in the rolling bearing.

[0013] The invention is based on the finding that application-oriented adjustment of a lubricating medium flow through the rolling bearing using as few components as possible leads to an efficient and economical rolling bearing. In the rolling bearings from the above-mentioned prior art, cover plates are arranged axially on both sides of the bearing outer ring or on a rotating bearing inner ring. The cover plates rotate with the bearing and perform a centrifugal function. In addition, some documents that show an arrangement of cover plates on the bearing inner ring also list additional cover plates that are arranged on the bearing outer ring. What the above-mentioned documents have in common is that the respective arrangement prevents a lubricating medium from entering the rolling bearing. The designs allow neither a controlled inlet of lubricating medium into the rolling bearing nor a controlled outlet of lubricating medium.This means that a controlled flow of lubricant through the rolling bearing for efficient lubrication and cooling is not possible. As a result, lubricant that enters the rolling bearing in an uncontrolled manner can continually accumulate. This excess of lubricant in the rolling bearing leads to increased churning losses. The increased resistance during operation of the rolling elements leads to an increase in power losses. It is also possible for a large amount of lubricant to escape from the rolling bearing in an uncontrolled manner, or for the bearing to be generally undersupplied with lubricant. In this case, increased friction and internal bearing temperature can lead to rolling bearing failure. To avoid the effects described, it is necessary to regulate the amount of lubricant entering and leaving the rolling bearing. However, this regulation must be possible without cost-intensive components and without requiring additional space in the rolling bearing environment.

[0014] The invention is based on the finding that it is expedient if the first cover plate is arranged axially on one side of the row of rolling elements and the second cover plate is arranged on the axially opposite side of the row of rolling elements. The first and second cover plates are thus located axially on two different sides of the row of rolling elements. On the side of the rolling bearing on which the first cover plate is located, i.e. a cover plate which is arranged on the bearing outer ring, there is no additional second cover plate, i.e. no additional cover plate which is arranged on the bearing inner ring. The first cover plate is connected to the bearing outer ring in a force-fitting or form-fitting manner or in a force-fitting and form-fitting manner. The first cover plate runs in the radial direction towards the bearing inner ring and bridges the radial gap between the two bearing rings except for a remaining gap.The first cover plate preferably has a plurality of sections along its length. A C-shaped section is preferably arranged on the bearing outer ring, i.e. a section which has a curvature in its profile and does not have a closed course. Depending on the design, the C-shaped section can also resemble a U- or an O-shape with an interruption. In addition, the first cover plate preferably has a radially extending central section. From this section, sections preferably extend radially on both sides and run obliquely towards the row of rolling elements. The first cover plate forms a gap with a radial inboard edge of the bearing inner ring, i.e. it does not touch the bearing inner ring. A radial inboard edge of the bearing inner ring is a boundary in the radial direction, which faces the bearing outer ring and runs axially straight.Lubricating medium such as oil enters the rolling bearing through the gap between the bearing inner ring and the first cover plate. The axial side of the rolling bearing, on which the first cover plate is arranged, is therefore the inlet side for the lubricating medium. The first cover plate preferably has a section with a C-profile at the radial end, i.e. at the end at which it is not arranged on the bearing outer ring. The C-profile has a C-shape in cross section. The C-profile has a smaller curvature than the C-shaped section. The first cover plate preferably ends in a section which runs parallel to a radial inboard edge of the bearing inner ring. A gap seal is therefore preferably formed between the section of the first cover plate which runs parallel to a radial inboard edge of the bearing inner ring and a radial inboard edge of the bearing inner ring.The first cover plate preferably has the following section sequence, starting from the bearing outer ring and moving toward the bearing inner ring, with one section immediately following the next: C-shaped section, section running diagonally toward the row of rolling elements, radially extending central section, section running diagonally toward the row of rolling elements, and a C-shaped profile with a section running parallel to the radial inboard edge of the bearing inner ring. "Running diagonally toward the row of rolling elements" means that the radially extending central section is the starting point for assessing the direction of the section.

[0015] On the axially opposite side, a second cover plate is arranged on the bearing inner ring. The second cover plate is connected to the bearing inner ring by force or form fit, or by force and form fit. The second cover plate runs radially towards the bearing outer ring and bridges the radial gap between the two bearing rings except for a remaining gap. The second cover plate preferably has several sections along its length. A C-shaped section is preferably arranged on the bearing inner ring. In addition, the first cover plate preferably has a radially running central section. From this section, inclined sections preferably extend radially on both sides and run towards the row of rolling elements. The second cover plate forms a gap with a radial inner rim of the bearing outer ring, i.e. it does not touch the bearing outer ring.A radial inboard edge of the bearing outer ring is a boundary in the radial direction, which faces the bearing inner ring and runs axially straight. Lubricating medium escapes from the rolling bearing through the gap between the bearing outer ring and the second cover plate. The axial side of the rolling bearing on which the second cover plate is arranged is therefore the outlet side for lubricating medium. The second cover plate preferably has a section with a C-profile at the radial end, i.e. at the end at which it is not arranged on the bearing inner ring. The second cover plate preferably ends in a section which runs parallel to a radial inboard edge of the bearing outer ring. A gap seal is preferably formed between the section of the second cover plate running parallel to a radial inboard edge of the bearing outer ring and a radial inboard edge of the bearing outer ring.

[0016] During operation, lubricating medium enters the rolling bearing on the inlet side via the gap between the first cover plate and the bearing inner ring. A needs-based design of the gap type and geometry allows the flow of lubricating medium at the inlet to be regulated. If the gap between the first cover plate and the bearing inner ring is very narrow, there is severe throttling. If the gap is designed as a labyrinth seal, particularly disruptive particles can be trapped. Combinations of different gap designs are also possible. Due to the centrifugal force during bearing operation, lubricating medium that has entered the rolling bearing flows towards the bearing outer ring. The lubricating medium is preferably passed along a C-profile via an inclined section to a radially running central section, which merges into another inclined section.The radially extending middle section with the inclined sections extending radially on both sides can collect incoming lubricant and contribute to a more even distribution of the lubricant in the bearing. The lubricant flows further to the bearing outer ring because it cannot flow away on the side of the first cover plate, as the first cover plate has no gap to the bearing outer ring. The lubricant flows along the radial inside of the bearing outer ring to the gap between the second cover plate and the bearing outer ring. As the bearing inner ring rotates, the cover plate fixed there rotates with it. Excess lubricant is pressed out of the rolling bearing by centrifugal force between the second cover plate, which acts as a flinger, and the bearing outer ring. The level of lubricant, such as oil, inside the rolling bearing drops and churning losses are reduced.In addition, the second cover plate uses centrifugal force to expel incoming lubricant from the surrounding area away from the rolling bearing, thus shielding it from external influences. This creates a forced flow of lubricant through the rolling bearing, which has a beneficial effect on cooling and lubrication. The combination of the first cover plate, located on the bearing outer ring, with the second cover plate, located on the bearing inner ring, creates an efficient and economical rolling bearing with a small number of components.

[0017] Preferably, the second cover plate has a C-shaped section on the bearing inner ring, wherein the C-shaped section is followed by a section which, starting from a radially running central section, runs obliquely towards the row of rolling elements, wherein the section running obliquely towards the row of rolling elements is followed by the radially running central section, which is followed by a further section running obliquely towards the row of rolling elements, which is directly or indirectly followed by a section running parallel to the radial inboard rim of the bearing outer ring. Preferably, the second cover plate is designed such that it is divided into several sections. These sections have different profiles. Starting from the bearing inner ring, the second cover plate initially has a C-shaped section. The C-shaped section is a section which is curved in profile and does not have a closed profile.The C-shaped section is therefore open in one place. Depending on the design, it can also resemble a U- or an O-shape with an interruption. The C-shaped section is followed by an inclined section. The inclined section is followed by a section that runs straight in the radial direction. The center point of the second cover plate is also located in this section in the radial direction. This section is therefore referred to as the radially running middle section. The radially running middle section is followed by another inclined section. The inclined section and the further inclined section run towards the row of rolling elements. In this context, the radially running middle section serves as the starting point for defining the direction.From the radially extending central section, radial sections extend on both sides, inclined toward the row of rolling elements. A C-profile can be connected to the further inclined section. The C-profile has a C-shape in cross-section and a lesser curvature than the C-shaped section. The second cover plate tapers off in a section that runs parallel to a radial inner rim of the bearing outer ring.

[0018] During operation, lubricating medium enters the rolling bearing interior on the inlet side and is guided by the first cover plate and centrifugal force to the axially opposite side of the row of rolling elements. Lubricating medium is guided along a slope on the C-profile to the gap between a radial inboard edge of the bearing outer ring and the section of the second cover plate running parallel to a radial inboard edge of the bearing outer ring and exits the rolling bearing. Lubricating medium from the environment primarily hits the radially running middle section on the outlet side of the rolling bearing, which takes up at least half the radial length of the second cover plate. Any lubricant that hits it bounces off of it. Lubricating medium that does not bounce off flows along the radially running middle section due to centrifugal force. From there, the lubricating medium continues along the section running diagonally towards the row of rolling elements to the C-shaped profile.The C-shaped profile merges into a section running parallel to a radial inner rim. Centrifugal force forces the lubricating medium axially away from the rolling bearing. Lubricating medium present on the axially opposite side of the second cover plate in the interior of the bearing is redirected towards the rolling elements by the strong curvature of the C-shaped section. This redirection promotes lubrication of the bearing. Lubricating medium displaced radially by the rolling elements leaves the bearing interior through the gap between the second cover plate and the outer ring. Such a sequence of sections on the second cover plate enables the lubricating medium to escape in a controlled manner on the outlet side and simultaneously prevents uncontrolled entry of lubricating medium from the environment into the interior of the rolling bearing.

[0019] Preferably, the first cover plate and / or the second cover plate has recesses that are adjacent to one another around its circumference. In a preferred embodiment, the recesses are designed as slots or notches. In a preferred embodiment, the recesses are arranged on the C-shaped section of the second cover plate. Preferably, the first cover plate or the second cover plate or the first cover plate and the second cover plate have recesses. The recesses are distributed in the circumferential direction over the respective cover plate and are therefore adjacent to one another. The recesses can be arranged uniformly or in a chaotic pattern or according to a further distribution that is advantageous for a particular application. The recesses can be in the form of depressions such as grooves or holes that are circular, oval or elongated.The recesses are preferably designed as notches or slots. Notches are depressions of any shape that do not completely penetrate a cover plate. This includes, among other things, a stepped profile. Slots are depressions of any shape that completely penetrate the cover plate, i.e. pass through a cover plate and form holes there. This includes, among other things, a comb profile. Slots are particularly larger in one direction than in another. The designs of the recesses on the first cover plate can differ from the designs of the recesses on the second cover plate. Preferably, the recesses that the second cover plate has are located in the C-shaped section. The C-shaped section is arranged partially or entirely on the bearing inner ring and comprises less than a quarter or equal to a quarter of the radial length of the second cover plate.The cross-section of the C-shaped section forms a broken circle, a broken ellipse, or a broken rectangle with rounded corners. The C-shaped section is not closed in cross-section, but has an opening. Depending on the design, the C-shape also resembles a U-shape or a broken O-shape. The opening of the C-shaped section of the second cover plate is oriented either toward the bearing outer ring or away from the row of rolling elements. Starting from the bearing inner ring, the C-shaped section forms the beginning of the second cover plate.

[0020] Preferably, the bearing outer ring and / or the bearing inner ring have a current-insulating layer. Preferably, the bearing outer ring or the bearing inner ring, or the bearing inner ring and 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.

[0021] Preferably, the side ring of the cage is arranged axially directly adjacent to the first cover plate. In a preferred embodiment, the side ring of the cage is arranged on the inlet side of the rolling bearing, i.e., on the side of the rolling element row on which the first cover plate is arranged. If lubricant enters the rolling bearing interior through the gap between the bearing inner ring and the first cover plate, a portion of it is guided via the side ring to the contact surfaces between the cage and the rolling elements. The continuous flow of lubricant permanently lubricates the contact surfaces between the cage and the rolling elements. At the same time, heat is consistently dissipated, thus cooling the rolling bearing interior.

[0022] Preferably, the bearing inner ring forms a first labyrinth seal with the first cover plate and / or the bearing outer ring forms a second labyrinth seal with the second cover plate. Preferably, the bearing inner ring forms a first labyrinth seal with the first cover plate, or the bearing outer ring forms a second labyrinth seal with the second cover plate, or the bearing inner ring forms a first labyrinth seal with the first cover plate and the bearing outer ring forms a second labyrinth seal with the second cover plate. For this purpose, a gap between the first cover plate and the bearing inner ring, or between the second cover plate and the bearing outer ring, is designed such that it changes direction at least once. The orientation of the gap therefore changes at least once over the course of a gap.In particular, the bearing inner ring undercuts a portion of the first cover plate, or the bearing outer ring undercuts a portion of the second cover plate, or vice versa. A gap formed between a bearing ring and a cover plate can initially run radially. By bending, the gap can change direction and then continue axially. The gap can also initially run axially, i.e. along the axis of rotation, and then change direction and continue radially. The gap can also be angled, i.e. run diagonally in a direction that lies between a purely axial or purely radial orientation and then change direction. Any combination of at least two courses: radial, axial, diagonally in the axial direction, or diagonally in the radial direction is also possible. By changing direction, the gap implements the principle of a labyrinth seal.The bearing inner ring thus forms a first labyrinth seal with the first cover plate, and the bearing outer ring forms a second labyrinth seal with the second cover plate. This allows for fine adjustment at the inlet or outlet, or at both the inlet and outlet, to ensure the flow of lubricant as required.

[0023] The rolling bearing according to the invention is intended for use in particular in transmissions for electromobility. Preferably, the rolling bearing is arranged such that the second cover plate is aligned with the interior of a transmission. Short description of the drawings

[0024] The invention is explained below using exemplary embodiments with reference to the drawings. The drawings are schematic representations and show: Fig. 1 a schematic representation of the rolling bearing according to the invention in a sectional partial view; Fig. 2 a schematic representation of an embodiment of the rolling bearing according to the invention in a perspective, sectional partial view. Detailed description of the drawings

[0025] Fig. 1 shows a partial sectional view of a rolling bearing 1 according to the invention. The rolling bearing 1 is composed of a bearing inner ring 5 arranged around a rotation axis 2, which runs in the axial direction a, and a bearing outer ring 3 of larger diameter arranged concentrically thereto. Between the bearing outer ring 3 and the bearing inner ring 5 is a cage 7 with a side ring 8. The bearing outer ring 3 has, in the radial direction r, i.e. perpendicular to the rotation axis 2, a first raceway 4 for rolling elements 27, which are arranged circumferentially in a row of rolling elements 9. On the radially inner side, i.e. facing the rolling elements 27, the first raceway 4 merges axially on both sides into straight, axially extending rims 22, 23 on the bearing outer ring 3.The dimension between the radial boundary of the bearing outer ring 3 on the radial outside, i.e. facing away from the bearing inner ring 5, and the radial boundary on the radial inside, i.e. facing the bearing inner ring 5, decreases radially in the direction of the axial ends of the bearing outer ring 3. The bearing outer ring 3 therefore has a step on each of the ribs 22, 23. These steps each merge into a groove. The ribs 22, 23 then taper off axially on both sides. On the side of the rolling bearing 1 on which there is no side ring 8 of the cage 7, the rib 23 tapers off in a straight line in the axial direction a and thereby forms a radial inner rib 16 of the bearing outer ring 3. The bearing inner ring 5 has a second raceway 6 radially opposite the first raceway 4. Radially on the inside, i.e. facing the rolling elements 27, the second raceway 6 merges axially on both sides into straight, axially extending rims 24, 25 of the bearing inner ring 5.The dimension between the radial boundary of the bearing inner ring 5 closest to the rotational axis 2 and the radial boundary of the bearing inner ring 5 adjacent to the rolling elements 27 decreases radially toward the axial ends of the rolling bearing 1. Thus, the bearing inner ring 5 has a step on each of the ribs 24, 25. These steps each merge into a groove. The ribs 24, 25 then taper axially on both sides. On the side of the rolling bearing 1 where the side ring 8 of the cage 7 is located, the rib 24 tapers straight in the axial direction a, forming a radial inner rib 17.

[0026] Axially on the side of the side ring 8, axially on one side of the row of rolling elements 9 and directly adjacent to the cage 7, a first cover plate 10 is arranged on the bearing outer ring 3. The first cover plate 10 bridges a radially running gap between the bearing outer ring 3 and the bearing inner ring 5 and runs radially in the direction of the bearing inner ring 5. The first cover plate 10 is divided into several sections. Starting from the bearing outer ring 3, the first cover plate 10 has a C-shaped section 12, with the C opening axially outwards, i.e. away from the row of rolling elements 9. The C-shaped section 12 is followed by a section 13 which runs at an angle. The angled section 13 is followed by a radially running central section 14 which takes up approximately half the radial length of the first cover plate 10. The radially running central section 14 is followed by another obliquely running section 15.Starting from the radially extending central section 14, the inclined section 13 and the further inclined section 15 extend towards the rolling element row 9. The first cover plate 10 then transitions into a C-profile. The C-profile has a smaller curvature than the C-shaped section 12 and ends in a section 26 that runs axially parallel to the radial inboard rib 17 of the bearing inner ring 5. A gap is formed between the first cover plate 10 and the radial inboard rib 17 of the bearing inner ring 5, which, depending on the application, can function as a gap seal. The design and arrangement of the radial inboard rib 17 and the rib 24 on the bearing inner ring 5 and the section 26 on the C-profile of the first cover plate 10, which runs parallel to the radial inboard rib 17, create a labyrinth seal 20 between the first cover plate 10 and the bearing inner ring 5.

[0027] On the axially opposite side of the rolling bearing 1, a second cover plate 11 is arranged on the bearing inner ring 5, directly adjacent to the row of rolling elements 9. The second cover plate 11 bridges the radial gap between the bearing outer ring 3 and the bearing inner ring 5 and runs radially in the direction of the bearing outer ring 3. The second cover plate 11 is divided into several sections. Starting from the bearing inner ring 5, the second cover plate 11 has a C-shaped section 12, with the C opening axially outwards, i.e. away from the row of rolling elements 9. The C-shaped section 12 is followed by a section 13 which runs at an angle. The angled section 13 is followed by a radially running central section 14 which takes up approximately half the radial length of the second cover plate 11. The radially running central section 14 is followed by another angled section 15.Starting from the radially extending central section 14, the inclined section 13 and the further inclined section 15 extend towards the rolling element row 9. The second cover plate 11 then transitions into a C-profile. The C-profile has a smaller curvature than the C-shaped section 12 and ends in a section 18 which runs axially parallel to the radial inboard rib 16 of the bearing outer ring 3. A gap is formed between the second cover plate 11 and the radial inboard rib 16 of the bearing outer ring 3, which, depending on the application, can function as a gap seal. The design and arrangement of the radial inboard rib 16 and the rib 23 on the bearing outer ring 3 and the section 18 on the C-profile of the second cover plate 11, which runs parallel to the radial inboard 16, create a second labyrinth seal 21 between the second cover plate 11 and the bearing outer ring 3.

[0028] Due to the design of the rolling bearing 1 according to the invention, one side of the rolling bearing 1 is designed axially as the inlet side, and the axially opposite side as the outlet side for the lubricating medium. On one side, the inlet side, lubricating medium primarily penetrates into the rolling bearing 1, while on the other side, the outlet side, lubricating medium, such as oil, primarily exits the rolling bearing 1. During operation, centrifugal force causes lubricating medium to enter on the inlet side through the first labyrinth seal 20 and to exit on the outlet side through the second labyrinth seal 21. During operation, the bearing inner ring 5 rotates with the second cover plate 11 arranged there, while the bearing outer ring 3 remains torsionally rigid with the first cover plate 10 arranged there. The first labyrinth seal 20 cleans contamination from the lubricating medium entering on the inlet side.Secondly, the inlet quantity of lubricating medium can be individually adjusted by designing the gap sizes between the bearing inner ring 5 and the first cover plate 10. Once lubricating medium has entered the rolling bearing 1, it is accelerated radially due to centrifugal force. The lubricating medium is displaced in all directions by the rolling elements 27. The C-shaped section 12 on the first cover plate 10 collects a portion of the lubricating medium and returns it to the rolling elements 27. A portion of the lubricating medium, which is located on the axially opposite side of the row of rolling elements 9, is returned to the rolling elements 27 via the further section 15 of the second cover plate 11, which runs diagonally towards the row of rolling elements 9. A further portion of the lubricating medium present there is led out of the rolling bearing 1 through the second labyrinth seal 21 on the outlet side.The flow of lubricant at the second labyrinth seal 21 can also be individually adjusted by designing the gap size between the bearing outer ring 3 and the second cover plate 11. The rotation of the second cover plate 11 attached to the bearing inner ring 5 keeps incoming lubricant from the environment away from the rolling bearing 1. The second cover plate 11 thus functions as a flinger plate. On the one hand, it shields the rolling bearing 1 from surrounding media. On the other hand, the lubricant entering the rolling bearing 1 via the inlet can leave the rolling bearing 1 again in a controlled and unhindered manner via the outlet. This allows the flow of lubricant to be regulated according to the application and the rolling bearing 1 to be operated economically.

[0029] Fig. Figure 2 shows a sectional, perspective partial view of a further embodiment of the rolling bearing 1 according to the invention. The rolling bearing 1 has a bearing outer ring 3 and a bearing inner ring 5, both of which are arranged around a rotation axis 2 aligned in the axial direction a. The bearing outer ring 3 has a first raceway 4, the bearing inner ring 5 a second raceway 6. Rolling elements 27 roll on the raceways 4, 6 in a row of rolling elements 9, which are rotatably held by a cage 7 with a side ring 8. A first cover plate 10 is arranged on the bearing outer ring 3, and a second cover plate 11 is arranged on the bearing inner ring 5. Both cover plates 10, 11 have, analogously to the cover plates 10, 11 in Fig.1, has various sections: A C-shaped section 12 is followed by an inclined section 13, which is followed by a radially running central section 14. The radially running central section 14 is in turn followed by another inclined section 15. Starting from the radially running central section 14, the inclined section 13 and the further inclined section 15 run towards the row of rolling elements 9. The further section 15, which runs diagonally towards the row of rolling elements 9, is followed by a C-profile, which ends in a section 18 on the radial inboard 16 of the bearing outer ring 3 and in a section 26 on the radial inboard 17 of the bearing inner ring 5. The section 18 runs parallel to the radial inboard 16 of the bearing outer ring 3 and the section 26 parallel to the radial inboard 17 on the bearing inner ring 5.The first cover plate 10 is arranged with the C-shaped section 12 on the bearing outer ring 3, while the second cover plate 11 is arranged with the C-shaped section 12 on the bearing inner ring 5. The second cover plate 11 is mirrored to the first cover plate 10 in the radial direction r and in the axial direction a. The second cover plate 11 has recesses 19 on the C-shaped section 12 on the bearing inner ring 5. These recesses 19 slit the second cover plate 11 in the axial direction a and continue to the free end of the C-shaped section 12. The recesses 19 are arranged circumferentially and evenly spaced from one another. The recesses 19 enable precise and low-stress production of the C-shaped section 12. The recesses 19 can prevent cracks or bulges during the forming process.

[0030] Through the combination of a torsionally rigid first cover plate 10 and a co-rotating second cover plate 11, a lubricating medium flow into, in and out of the rolling bearing 1 can be adjusted as required. List of reference symbols 1 rolling bearing 2 rotation axis 3 Bearing outer ring 4 first career 5 Bearing inner ring 6 second career 7 cage 8 side ring 9 rolling element row 10 first cover plate 11 second cover plate 12 C-shaped section 13 section running diagonally towards the row of rolling elements 14 radial middle section 15 further section running diagonally towards the row of rolling elements 16 radial inboard of the bearing outer ring 17 radial inboard of the bearing inner ring 18 Section parallel to a radial inboard of the bearing outer ring 19 recesses 20 first labyrinth seal 21 second labyrinth seal 22 rib on the bearing outer ring 23 rib on the bearing outer ring 24 rib on the bearing inner ring 25 rib on the bearing inner ring 26 Section parallel to a radial inboard of the bearing inner ring 27 rolling elements a in axial direction r in radial direction

Claims

[1] Rolling bearings (1) - with a torsionally rigid bearing outer ring (3) arranged around a rotation axis (2) running in the axial direction (a), which outer ring has a first raceway (4), - with a bearing inner ring (5) arranged concentrically to the bearing outer ring (3), which rotates about the rotation axis (2) and has a second raceway (6) opposite the first raceway (4) in the radial direction (r), - with a cage (7) which has a side ring (8), - with a row of rolling elements (9) arranged between the first raceway (4) and the second raceway (6), - with a first cover plate (10) which is arranged on the torsionally rigid bearing outer ring (3), - with a second cover disc (11) which is arranged on the rotating bearing inner ring (5), wherein the first cover disc (10) is arranged axially on one side, adjacent to the row of rolling elements (9), and the second cover disc (11) is arranged on one side on the axially opposite side, adjacent to the row of rolling elements (9), characterized by that the first cover plate (10) and / or the second cover plate (11) consists of a bimetal. [2] Rolling bearing (1) according to claim 1, characterized byin that the second cover plate (11) has a C-shaped section (12) on the bearing inner ring (5), the C-shaped section (12) being followed by a section (13) which, starting from a radially running central section (14), runs obliquely towards the row of rolling elements (9), the radially running central section (14) adjoining the section (13) running obliquely towards the row of rolling elements (9), which section is followed by a further section (15) running obliquely towards the row of rolling elements (9), to which section (18) running parallel to the radial inner rim (16) of the bearing outer ring (3) is directly or indirectly adjoined. [3] Rolling bearing (1) according to claim 2, characterized by that the first cover plate (10) and / or the second cover plate (11) has circumferentially adjacent recesses (19). [4] Rolling bearing (1) according to claim 3, characterized by that the recesses (19) are designed as slots or notches. [5] Rolling bearing (1) according to claim 3 or 4, characterized by that the recesses (19) on the second cover plate (11) are arranged on the C-shaped section (12). [6] Rolling bearing (1) according to claim 1, characterized by that the bearing outer ring (3) and / or the bearing inner ring (5) has a current-insulating layer. [7] Rolling bearing (1) according to claim 1, characterized by that the side ring (8) of the cage (7) is arranged axially directly adjacent to the first cover plate (10). [8] Rolling bearing (1) according to claim 1, characterized by that the bearing inner ring (5) forms a first labyrinth seal (20) with the first cover plate (10) and / or the bearing outer ring (3) forms a second labyrinth seal (21) with the second cover plate (11).

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