Angular contact ball bearings

Abstract

Angular contact ball bearings (1) - with a bearing outer ring (3) arranged around an axially extending rotation axis (2), which has a first outer ring rim (4) and a first raceway (5) radially on the inside, which is axially limited by a first bearing shoulder (6) with a second outer ring rim (7), - with a cage (13) consisting of a first side ring (14) with a first radial dimension (SR1) and a second side ring (15) with a second radial dimension (SR2), which are connected to one another by webs (16) and form rolling element pockets (17), - with a bearing inner ring (8) arranged concentrically to the bearing outer ring (3), which has a first inner ring rim (9) oriented radially towards the cage (13) and a second raceway (10) opposite the first raceway (5), which is axially limited by a further bearing shoulder (31) with a second inner ring rim (12), wherein the cage (13) has on the first side ring (14) a first cage rim (18) radially opposite the bearing outer ring (3) and a second cage rim (19) radially opposite the bearing inner ring (8), on the second side ring (15) a third cage rim (20) radially opposite the bearing outer ring (3) and a fourth cage rim (21) radially opposite the bearing inner ring (8) and rotatably guides rolling elements (22) rolling on the raceways (5, 10) in a row of rolling elements (23), wherein a first gap (24) with a third radial dimension (Sp1) is formed between the second outer ring rim (7) and the first cage rim (18), and a second gap (25) with a fourth radial dimension (Sp2) is formed between the first outer ring rim (4) and the third cage rim (20), the bearing outer ring (3) tapers at the first outer ring rim (4) and has a third outer ring rim (26), and the first radial dimension (SR1) is greater than the second radial dimension (SR2), characterized in that, for covering the bearing, a radially extending cover disk (27) is arranged axially on one side, adjacent to the row of rolling elements (23), on the bearing inner ring (8) between the bearing outer ring (3) and the bearing inner ring (8), and a radial dimension of a gap (33) which is formed between the third outer ring rim (26) and a rim (28) of the cover disk directly opposite the bearing outer ring (3) (27) is formed,is greater than the third radial dimension (Sp1) and the fourth radial dimension (Sp2).

Description

[0001] The invention relates to an angular contact ball bearing with a cage. 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] CN 1 01 788 016 A shows a copper angular contact ball bearing with a reduced cage cross-section. The cage consists of two interconnected ring sections. One ring section has a smaller cross-section than the other. The goal is to reduce the weight of the cage and improve the lubrication performance of the angular contact ball bearing.

[0004] JP 2015-218 786 A discloses an angular contact ball bearing that generates an airflow for the circulation of lubricating grease within the bearing to improve lubrication performance. The angular contact ball bearing has an outer ring and an inner ring with a counterbore on one axial end. A cage is guided between the bearing rings and consists of two ring portions connected by webs. The cage has a first clearance between an outer peripheral surface of the first circular ring portion and an inner peripheral surface of the outer ring, which is set larger than a second clearance between an outer peripheral surface of the second circular ring portion and the inner peripheral surface of the outer ring. Cover disks are arranged on both axial sides of the outer ring.

[0005] DE 10 2012 206 376 B3 discloses a generic angular contact ball bearing.

[0006] JP 2012- 189 181 A and JP 2018- 62 942 A disclose rolling bearings. Object of the invention

[0007] The invention is based on the object of providing an improved angular contact ball bearing. Description of the invention

[0008] According to the invention, this object is achieved by an angular contact ball bearing - with a bearing outer ring arranged around an axially extending axis of rotation, which has a first outer ring rim radially on the inside and a first raceway which is axially limited by a first bearing shoulder with a second outer ring rim, - with a cage consisting of a first side ring with a first radial dimension and a second side ring with a second radial dimension, which are connected to each other by webs and form rolling element pockets, - with a bearing inner ring arranged concentrically to the bearing outer ring, which has a first inner ring rim oriented radially towards the cage and a second raceway opposite the first raceway, which is axially limited by a further bearing shoulder with a second inner ring rim, wherein the cage has a first cage rim radially opposite the bearing outer ring and a second cage rim radially opposite the bearing inner ring on the first side ring, a third cage rim radially opposite the bearing outer ring and a fourth cage rim radially opposite the bearing inner ring on the second side ring, and rotatably guides rolling elements rolling on the raceways in a row of rolling elements, wherein a first gap with a third radial dimension is formed between the second outer ring rim and the first cage rim, and a second gap with a fourth radial dimension is formed between the first outer ring rim and the third cage rim, the bearing outer ring tapers at the first outer ring rim and has a third outer ring rim, the first radial dimension being greater than the second radial dimension, and wherein, for bearing coverage, a radially extending cover disk is arranged axially on one side, adjacent to the row of rolling elements, on the bearing inner ring between the bearing outer ring and the bearing inner ring. A radial dimension of a gap formed between the third outer ring rim and a rim of the cover disk directly opposite the bearing outer ring is greater than both the third radial dimension and the fourth radial dimension.

[0009] The angular contact ball bearing is arranged concentrically around an axial axis of rotation. The angular contact ball bearing has an outer bearing ring and an inner bearing ring with a smaller diameter than that of the outer bearing ring. The outer bearing ring has a first raceway in the form of a circular, radial recess which runs circumferentially along the outer bearing ring. The recess merges axially on one side into a first outer ring rib. On the axially opposite side of the angular contact ball bearing, the outer bearing ring has a first bearing shoulder. This limits the first raceway in the axial direction. On the radial inside, i.e. in the direction of the inner bearing ring, the first bearing shoulder has a second outer ring rib. The first and second outer ring ribs as well as the first raceway limit the outer bearing ring radially on the inside.The bearing inner ring has a second raceway on the radial inside, towards the bearing outer ring, which is designed in the form of a circular arc-shaped recess running radially around the bearing inner ring. The second raceway is located diagonally opposite the first raceway. Axially, on the side of the first outer ring rib, the second raceway is delimited by a second bearing shoulder. The radial boundary of the bearing inner ring is formed by a first inner ring rib on the second bearing shoulder, the second raceway, and a second inner ring rib. The angular contact ball bearing has a cage between the bearing outer ring and the bearing inner ring. The cage consists of a first side ring and a second side ring. Webs that connect the two side rings to one another are arranged circumferentially between the two side rings. The first side ring is delimited radially in the direction of the bearing outer ring by an axially running first cage rib.Radially opposite, the first side ring is delimited in the direction of the bearing inner ring by an axially running second cage rib. The first side ring has a first radial dimension running radially from the first cage rib to the second cage rib. The second side ring is delimited radially in the direction of the bearing outer ring by an axially running third cage rib. Radially opposite, the second side ring is delimited in the direction of the bearing inner ring by an axially running fourth cage rib. The second side ring has a second radial dimension running radially from the third cage rib to the fourth cage rib. The first and second side rings, together with the webs, form rolling element pockets in which rolling elements, such as ball rolling elements, are rotatably guided. The rolling elements are arranged in a rolling element row, i.e. circumferentially, axially parallel, and roll on the first and second raceways.A first gap and a second gap are formed radially between the cage and the bearing outer ring. The first gap runs between the radial boundary of the first side ring oriented towards the bearing outer ring, i.e. the first cage rim, and the boundary of the bearing outer ring directly radially opposite the first cage rim, i.e. the second outer ring rim. The first gap has a third radial dimension, starting radially from the first cage rim towards the second outer ring rim. The second gap runs between the radial boundary of the second side ring oriented towards the bearing outer ring, i.e. the third cage rim, and the boundary of the bearing outer ring directly radially opposite the third cage rim, i.e. the first outer ring rim. The second gap has a fourth radial dimension, starting radially from the third cage rim towards the first outer ring rim.

[0010] If a generic rolling bearing is installed, for example, in a reduction gear of an electric drive train, the supply of a lubricant is not necessarily designed to meet the needs of each subcomponent of the system. Typically, lubrication is implemented as a splash lubrication system, with gears partially rotating through an oil sump during operation, thus ensuring an oil mist inside the gearbox housing. A large amount of lubricant is present in the gearbox chamber, which must provide appropriate cooling and lubrication of the components for each operating point. This blanket lubrication causes significant drag losses, which lead to increased fuel consumption, reduced range, and increased CO2 emissions.

[0011] The invention is based on the realization that an increase in the efficiency of the entire system can be achieved through individual, needs-based lubrication of components in a system. Due to centrifugal force during operation, the design of lubricated angular contact ball bearings results in a lubricant flow, like an oil flow, from smaller openings to larger openings. This results in a conveying effect with a conveying direction in the rolling bearing. This oil flow is uncoordinated and can lead to a large amount of lubricant accumulating in the rolling bearing. In order to be able to adjust demand-based lubrication, both a demand-based inlet, i.e. an inflow of lubricant into, and a demand-based outlet, i.e. an outflow of lubricant from the rolling bearing, must be ensured.The invention is based on the finding that it is expedient for the bearing outer ring to be tapered at the first outer ring rim and to have a third outer ring rim, and for the first radial dimension to be larger than the second radial dimension. In order to restrict the inlet of lubricant into the rolling bearing, the cage is thickened on one inlet side, i.e. the side on which the lubricant enters or is intended to enter. This means that the radial dimension of the first side ring is increased. This can be done in the direction of the bearing outer ring or the bearing inner ring, or even in the direction of the bearing outer ring and the bearing inner ring. The implementation depends on how a needs-based lubrication flow is designed in the specific application. For example, it can be expedient for the first gap to be designed as an inlet.In addition, it can also be effective if a gap formed between the second cage rim on the first side ring and the second inner ring rim on the bearing inner ring is designed as an inlet. In any case, the radially enlarged first side ring reduces the gap, which is designed as an inlet, and thus reduces the inflow of the lubricating medium. Depending on how much the inflow is to be throttled, the first side ring can be thickened accordingly. A thickening on the side of the angular contact ball bearing where the lubricating medium is to escape from the rolling bearing, i.e. an outlet side, would not be effective. Due to the conveying effect, the lubricating medium would be conveyed into the bearing interior on the inlet side or, depending on the gap size, on the outlet side. The lubricating medium would collect on the outlet side and could not escape or would only be hindered.It is therefore essential that the radial dimension of the first side ring is larger than the radial dimension of the second side ring. To also facilitate the outflow from the angular contact ball bearing, the bearing outer ring tapers at the first outer ring rib, thereby forming a third outer ring rib oriented towards the bearing inner ring. Due to this taper, the radial height of the bearing outer ring decreases towards the axial outside of the angular contact ball bearing, which is axially opposite the first bearing shoulder. As a result, the second gap transitions into a gap with a larger radial dimension than the fourth radial dimension of the second gap. Lubricating medium, which is conveyed through the rolling bearing and arrives at the outlet, is guided from the second gap along an axially outward-facing, radially running edge on the bearing outer ring towards the third outer ring rib and thus discharged.These measures allow the inlet, flow and outlet of a lubricating medium to be adjusted, thus avoiding drag losses due to an excess of lubricating medium.

[0012] To cover the bearing, a radially extending cover plate is arranged axially on one side, adjacent to the row of rolling elements, on the bearing inner ring between the bearing outer ring and the bearing inner ring. The angular contact ball bearing has a cover plate which is arranged on the bearing inner ring and extends radially in the direction of the bearing outer ring. The cover plate is arranged axially on one side of the angular contact ball bearing. It is located adjacent to the row of rolling elements guided in the cage and is arranged in particular on the side on which the third outer ring rib is located. Depending on the application, in a system such as a gearbox, lubricating medium from the environment can also be present on the outlet side of the angular contact ball bearing and flow into the bearing. If the surrounding lubricating medium is also under pressure, it can enter the angular contact ball bearing through the second gap.This would result in a buildup of lubricant in the angular contact ball bearing, resulting in drag losses and an increase in the system's power loss. To ensure that the pumping effect on the outlet side is not impeded by the thickened cage, the cover plate is located specifically on the outlet side of the angular contact ball bearing. During operation, the bearing inner ring and the cover plate located there also rotate. It acts as a flinger, forcing surrounding lubricant away from the outlet side of the angular contact ball bearing, so that the pumping effect at the outlet set by the thickened cage is not impaired. In other words, the oil removal from the rolling bearing is facilitated by the suction effect of the oil quantity rejected by the flinger.

[0013] The angular contact ball bearing with a cover plate is particularly used in a gearbox. The cover plate is specifically aligned with the interior of the gearbox. During operation, the cover plate rotates together with the bearing inner ring and shields the outlet side of the angular contact ball bearing from surrounding lubricating oil from the gearbox interior through a centrifugal force-induced centrifugal effect.

[0014] Preferably, the third radial dimension is less than or equal to the fourth radial dimension. Preferably, the radial dimension of the first gap is less than or equal to the radial dimension of the second gap. If the first gap is primarily intended for the inlet and the second gap primarily for the outlet of a lubricating medium, it is beneficial if the second gap has at least the flow volume of the first gap. The basis for this is the respective radial dimensions of the gaps. This ensures that the quantity of lubricating medium that is pumped into the interior of the rolling bearing via the inlet can also escape again through the outlet, at a speed at which new lubricating medium flows in through the inlet. This can prevent a build-up of lubricating medium inside the rolling bearing.

[0015] A radial dimension of a gap formed between the third outer ring rim and a rim of the cover plate directly opposite the bearing outer ring is larger than the third radial dimension and the fourth radial dimension. A radial gap is formed between the cover plate and the third outer ring rim, i.e. a gap which runs in the radial direction and whose radial dimension is larger than the radial dimension of the first gap and the radial dimension of the second gap. The cover plate forms a rim on a side axially opposite a starting section of the cover plate. The starting section is arranged on the bearing inner ring. The rim of the cover plate can be axial, radial, inclined, or curved.The minimum radial distance between the third outer ring rim and the rim of the cover plate is used as the radial dimension of the gap between the third outer ring rim and the rim of the cover plate. In this case, the cover plate does not have a minimum distance from the bearing outer ring, as is usual in standard applications with cover plates, in order to impede the penetration of disruptive particles (see, for example, JP 2015- 218 786 A). In this design, the cover plate has the main task of keeping surrounding lubricating medium such as oil away from the bearing by rotation, with the aim of preventing the surrounding lubricating medium from impairing the pumping effect, which is set by the thickened cage. At the same time, the cover plate itself must not negatively influence the outlet. This requires that the cover plate has a defined distance from the bearing outer ring, i.e. an outlet gap.If this gap is larger than the first and second gaps, it is ensured that the volume of lubricating medium that enters the angular contact ball bearing through the first gap on the inlet side can also leave it again on the outlet side.

[0016] The cover plate is preferably made of a bimetal. The material of the cover plate is preferably bimetal. This allows the size of the gap formed between the third outer ring rim and the rim of the cover plate to change depending on the temperature of the cover plate. The temperature of the cover plate is related to the operating state of the angular contact ball bearing. This allows the amount of lubricant that can escape from the angular contact ball bearing to be adjusted as needed, depending on the operating state.

[0017] The cover plate is preferably made of a plastic. In a preferred embodiment, the plastic from which the cover plate is made is PA66-GF25 or PA46-GF30.

[0018] The cover plate preferably has recesses on its surfaces facing the bearing outer ring and / or the bearing inner ring. The recesses are preferably designed as slots or notches. The cover plate is preferably characterized by recesses which are located on the surfaces of the cover plate which contact a partial area of ​​the bearing outer ring or the bearing inner ring or the bearing outer ring and the bearing inner ring or on surfaces of the cover plate which lie opposite a partial area of ​​the bearing outer ring or the bearing inner ring or the bearing outer ring and the bearing inner ring. A combination of recesses on surfaces of the cover plate, wherein some of the surfaces contact a partial area of ​​one of the bearing rings or partial areas of both bearing rings and some of the surfaces lie opposite a partial area of ​​one of the bearing rings or partial areas of both bearing rings, is also feasible.The recesses are preferably designed as notches or slots. Notches are depressions of any shape that do not completely penetrate the cover plate, such as a stepped profile. Slots are depressions of any shape that completely penetrate the cover plate, i.e., pass through the cover plate and form holes there. Slots are particularly large in one direction than in another.

[0019] Preferably, the bearing outer ring and cover plate together form a labyrinth seal. Preferably, a gap formed between the bearing outer ring and the cover plate is designed as a labyrinth seal. Along the course of the gap, the orientation of the gap changes at least once. In particular, the cover plate undercuts a portion of the bearing outer ring or vice versa. The gap formed between the bearing outer ring and the cover plate can initially run radially, i.e. from the direction of the bearing outer ring towards the bearing inner ring. Bending can change the direction of the gap and it can 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., inclined in a direction that lies between a purely axial or purely radial orientation, and then change direction. Any combination of at least two paths: radial, axial, inclined in the axial direction, or inclined in the radial direction is also possible. By changing the direction, the gap implements the principle of a labyrinth seal, so that the bearing outer ring and cover plate together form a labyrinth seal. This allows for fine adjustment at the outlet to ensure the flow of lubricant as required.

[0020] The angular contact ball bearing according to the invention is intended for use in the drive train of an electrically powered motor vehicle. The lubrication concept integrated into the angular contact ball bearing for bearing points in reduction gears of an electrically powered drive train can enable increased efficiency in the drive train. Short description of the drawings

[0021] 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 angular contact ball bearing according to the invention in a sectional, perspective partial view, Fig. 2 a schematic representation of an embodiment of the angular contact ball bearing according to the invention in a sectional partial view. Detailed description of the drawings

[0022] Fig. 1 shows a sectional, perspective partial view of an angular contact ball bearing 1 according to the invention. The angular contact ball bearing 1 consists of a bearing inner ring 8 arranged around a rotational axis 2 and a bearing outer ring 3 of larger diameter arranged concentrically thereto. A cage 13 is located between the bearing outer ring 3 and the bearing inner ring 8. The bearing outer ring 3 has a radial first raceway 5 for rolling elements 22. On the radial inside, i.e., facing the cage 13, the first raceway 5 merges into a straight, axially extending first outer ring rim 4. 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 8, and the radial boundary on the radial inside, decreases radially in the direction of an axial end of the angular contact ball bearing 1. The bearing outer ring 3 thus has a step on one side of the first outer ring rim 4 with a third outer ring rim 26 oriented radially on the inside.On the axially opposite side, the bearing outer ring 3 has a first bearing shoulder 6, which axially delimits the first raceway 5 and has a second outer ring rim 7 on the radially inner side. The bearing inner ring 8 has a second raceway 10 diagonally opposite the first raceway 5. The second raceway 10 is axially delimited on one side by a second bearing shoulder 11, which has a first inner ring rim 9 on the radially inner side, i.e., oriented toward the cage 13. On the axially opposite side, the bearing inner ring 8 has a further bearing shoulder 31, which has a second inner ring rim 12 on the radially inner side. Axially, on the side of the third outer ring rim 26 on the bearing outer ring 3, the bearing inner ring 8 also has a radial recess that extends axially to the axial edge of the bearing inner ring 8. Thus, the bearing inner ring 8 also has a step with a third inner ring rim 32 oriented radially inward.The rolling elements 22 are arranged circumferentially in a rolling element row 23 and are guided by the cage 13 between the bearing outer ring 3 and the bearing inner ring 8 on the first raceway 5 and the second raceway 10. Axially on the side of the third outer ring rim 26, adjacent to the rolling element row 23 and the cage 13, a cover plate 27 is arranged on the bearing inner ring 8. The cover plate 27 bridges a radially extending gap between the bearing outer ring 3 and the bearing inner ring 8 and extends radially in the direction of the bearing outer ring 3. Starting from the bearing inner ring 8, the cover plate 27 has an initial section, with a partial region of the initial section being curved and arranged axially on the third inner ring rim 32. An adjoining partial region of the initial section contacts a surface of the second bearing shoulder 11 facing axially away from the rolling element row 23.The initial section of the cover plate 27 thus has a partial area with a C-shaped profile, wherein the C is open axially outwards, i.e. away from the row of rolling elements 23. An adjoining middle section of the cover plate 27 has a partial area running diagonally away from the row of rolling elements 23. This merges into a straight, radial partial area, followed by a partial area running diagonally towards the row of rolling elements 23, which merges into a partial area with a C-shaped profile at an end section. This C-profile is less curved than the C-profile in the initial section. In the last partial area, it runs axially parallel to the third outer ring rim 26 on the bearing outer ring 3, where it forms a rim 28 of the cover plate 27. Here, too, the C is open axially outwards, i.e. away from the row of rolling elements 23.Adjacent to the row of rolling elements 23, the cage 13 has a first side ring 14 on the side where the first bearing shoulder 6 is located. Axially opposite, adjacent to the row of rolling elements 23, the cage 13 has a second side ring 15. Both side rings 14, 15 are circular in shape and arranged radially and axially offset from one another around the axis of rotation 2. The first side ring 14 and the second side ring 15 are connected via webs 16, which together with the side rings 14, 15 form rolling element pockets 17 for rotatably receiving the rolling elements 22. The first side ring 14 has a first cage rim 18, an axially extending surface for the radial delimitation of the first side ring 14, which surface lies radially opposite the bearing outer ring 3.Radially opposite, the first side ring 14 has a second cage rim 19, an axially extending surface for radially delimiting the first side ring 14, which is radially opposite the bearing inner ring 8. Similarly, the second side ring 15 has a third cage rim 20, which is radially opposite the bearing outer ring 3. Radially in the direction of the bearing inner ring 8, the second side ring 15 is correspondingly delimited by a fourth cage rim 21.

[0023] The first side ring 14 has a first radial dimension SR1, which extends radially from the first cage rim 18 to the second cage rim 19. The second side ring 15 has a second radial dimension SR2, which extends radially from the third cage rim 20 to the fourth cage rim 21. The first side ring 14 is radially thickened so that the first radial dimension SR1 is greater than the second radial dimension SR2. A first gap 24 is formed between the first cage rim 18 and the second outer ring rim 7, which serves as an inlet for a lubricating medium. A second gap 25 is formed between the third cage rim 20 and the first outer ring rim 4. A third gap 33 is formed between the third outer ring rim 26 and the rim 28 of the cover plate 27. The second gap 25 and the third gap 33 serve as an outlet for a lubricating medium. The first gap 24 has a third radial dimension Sp1 for the inlet of a lubricating medium.The second gap 25 has a fourth radial dimension Sp2 for the outlet of a lubricating medium. Sp1 is larger than Sp2.

[0024] Due to centrifugal force during operation, the design of the angular contact ball bearing 1 causes lubricant to flow from the first gap 24 on the inlet side, i.e. the inlet side, to the second gap 25 on the outlet side, i.e. the outlet side. During operation, the bearing inner ring 8 rotates with the cover plate 27 arranged there, while the bearing outer ring 3 remains torsionally rigid. By radially thickening the first side ring 14 of the cage 13 on one side, the radial distance between the cage 13 and the bearing outer ring 3 and, if necessary, also to the bearing inner ring 8 is reduced. The first gap 24 is thus narrowed and the amount of a lubricating medium such as oil that can flow through the first gap 24 into the angular contact ball bearing 1 is reduced. This throttles the supply of lubricating medium.By rotating the cover plate 27 mounted on the bearing inner ring 8 during operation, incoming lubricant from the environment is kept away from the angular contact ball bearing 1. The cover plate 27 acts as a flinger and shields the angular contact ball bearing 1, allowing the lubricant entering through the inlet to exit the angular contact ball bearing 1. A third gap 33 between the rim 28 of the cover plate 27 and the third outer ring rim 26 ensures that the cover plate 27 itself does not obstruct the outlet of the lubricant, but rather allows the lubricant to flow away in a controlled manner.

[0025] Fig. 2 shows a sectional, perspective partial view of another embodiment of the angular contact ball bearing 1 according to the invention. The angular contact ball bearing 1 is analogous to the rolling bearing from Fig.1 has a bearing inner ring 8 arranged around a rotation axis 2 and a bearing outer ring 3. The bearing outer ring 3 has a first outer ring rim 4, a second outer ring rim 7 and a third outer ring rim 26. The bearing outer ring 3 also has a first raceway 5. The bearing inner ring 8 has a first inner ring rim 9, a second inner ring rim 12 and a third inner ring rim 32 as well as a second raceway 10. Between the bearing inner ring 8 and the bearing outer ring 3 there is a cage 13 which guides rolling elements 22 in a row of rolling elements 23 so that they roll on the raceways 5, 10. The cage 13 has a first side ring 14 with a first radial dimension SR1 and a second side ring 15 with a second radial dimension SR2, where SR1 is larger than SR2. Both side rings 14, 15 are connected to each other by webs 16 and together form rolling element pockets 17.Axially, on one side of the angular contact ball bearing 1, adjacent to the row of rolling elements 23, a cover plate 27 is arranged on the bearing inner ring 8. The cover plate 27 runs radially in the direction of the bearing outer ring 3. It extends so far in the direction of the bearing outer ring 3 that a portion of the cover plate 27 radially overlaps with a surface of the step on the bearing outer ring 3 that is oriented axially away from the cage 13. Due to this arrangement, the bearing outer ring 3 and the cover plate 27 form a labyrinth seal 30. This means that a gap formed between the bearing outer ring 3 and the cover plate 27 changes direction at least once. The cover plate 27 has circumferential recesses 29 in the form of slots, which are arranged at an end section of the cover plate 27, i.e. at a section which has a relatively large distance from the bearing inner ring 8 and in which the cover plate 27 ends.The slots are a supplementary means of adjusting the flow of lubricant to suit the application.

[0026] The cage 13, which is thickened on one side, in combination with the cover plate 27 on the axially opposite side, allows the lubricant flow through the angular contact ball bearing 1 to be adjusted and the lubricant quantity in the angular contact ball bearing 1 to be limited. This prevents the accumulation of lubricant and prevents drag losses and the associated loss of performance in the system. List of reference symbols 1 angular contact ball bearing 2 rotation axis 3 Bearing outer ring 4 First outer ring rim 5 First career 6 First bearing shoulder 7 Second outer ring rim 8 Bearing inner ring 9 First inner ring rim 10 Second career 11 Second bearing shoulder 12 Second inner ring rim 13 Cage 14 First side ring 15 Second side ring 16 bridges 17 rolling element pockets 18 First cage board 19 Second cage shelf 20 Third cage shelf 21 Fourth cage shelf 22 rolling elements 23 rolling element row 24 First gap 25 Second gap 26 Third outer ring rim 27 Cover plate 28 Edge of the cover plate 29 Recess on the cover plate 30 Labyrinth seal 31 Additional bearing shoulder 32 Third inner ring rim 33 Third gap SR1 first radial dimension SR2 second radial dimension Sp1 third radial dimension Sp2 fourth radial dimension

Claims

[1] Angular contact ball bearings (1) - with a bearing outer ring (3) arranged around an axially extending rotation axis (2), which has a first outer ring rim (4) and a first raceway (5) radially on the inside, which is axially limited by a first bearing shoulder (6) with a second outer ring rim (7), - with a cage (13) consisting of a first side ring (14) with a first radial dimension (SR1) and a second side ring (15) with a second radial dimension (SR2), which are connected to one another by webs (16) and form rolling element pockets (17), - with a bearing inner ring (8) arranged concentrically to the bearing outer ring (3), which has a first inner ring rim (9) oriented radially towards the cage (13) and a second raceway (10) opposite the first raceway (5), which is axially limited by a further bearing shoulder (31) with a second inner ring rim (12), wherein the cage (13) has on the first side ring (14) a first cage rim (18) radially opposite the bearing outer ring (3) and a second cage rim (19) radially opposite the bearing inner ring (8), on the second side ring (15) a third cage rim (20) radially opposite the bearing outer ring (3) and a fourth cage rim (21) radially opposite the bearing inner ring (8) and rotatably guides rolling elements (22) rolling on the raceways (5, 10) in a rolling element row (23), wherein a first gap (24) with a third radial dimension (Sp1) is formed between the second outer ring rim (7) and the first cage rim (18), and a second gap (25) with a fourth radial dimension (Sp2) is formed between the first outer ring rim (4) and the third cage rim (20), the bearing outer ring (3) tapers at the first outer ring rim (4) and has a third outer ring rim (26), and the first radial dimension (SR1) is greater than the second radial dimension (SR2) characterized byin that, for covering the bearing between the bearing outer ring (3) and the bearing inner ring (8), a radially extending cover plate (27) is arranged axially on one side, adjacent to the row of rolling elements (23), on the bearing inner ring (8), and a radial dimension of a gap (33) which is formed between the third outer ring rim (26) and a rim (28) of the cover plate (27) directly opposite the bearing outer ring (3) is larger than the third radial dimension (Sp1) and the fourth radial dimension (Sp2). [2] Angular contact ball bearing (1) according to claim 1, characterized by that the third radial dimension (Sp1) is less than or equal to the fourth radial dimension (Sp2). [3] Angular contact ball bearing (1) according to claim 1, characterized by that the cover plate (27) consists of a bimetal. [4] Angular contact ball bearing (1) according to claim 1, characterized by that the cover plate (27) is made of a plastic. [5] Angular contact ball bearing (1) according to claim 4, characterized by that the plastic is PA66-GF25 or PA46-GF30. [6] Angular contact ball bearing (1) according to claim 1, characterized by that the cover plate (27) has recesses (29) on its surfaces facing the bearing outer ring (3) and / or the bearing inner ring (8). [7] Angular contact ball bearing (1) according to claim 6, characterized by that the recesses (29) are designed as slots or notches. [8] Angular contact ball bearing (1) according to claim 1, characterized by that the bearing outer ring (3) and cover plate (27) together form a labyrinth seal (30).

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