Bearing assembly

Abstract

The invention relates to a bearing assembly comprising a rolling bearing, a shaft (4, 31) having a slinger (6) arranged there, and a housing (5) having a sealing ring (10) arranged there, a projection (7) of the slinger (6) surrounding a part (12) of the housing (5), and at least said part (12) of the housing (5) forms an undercut (13) with the projection (7) of the slinger (6) in the axial direction (a) and in the radial direction (r). The projection (7) has a reduction from a first diameter (d1) to a second diameter (d2) at an inner side (15) of the slinger (6) facing the shaft (4, 31). The housing (5) has a reduction from a third diameter (d3) to a fourth diameter (d4) at an outer side (16) facing an inner side (15) of the slinger (6).

Description

Technical Field

[0001] The present invention relates to a bearing assembly, comprising a rolling bearing, an axially extending shaft, a housing, and an oil slinger arranged at the shaft, wherein the rolling bearing is arranged around an axially extending rotation axis, the oil slinger having an axially extending protrusion and a radially extending base body, the base body having a first gripping arm, the protrusion circumferentially surrounding a portion of the housing, and at least the portion of the housing forming an undercut with the protrusion of the oil slinger in the axial and radial directions, and the bearing assembly comprising a sealing ring arranged at the housing, the sealing ring having a first sealing lip extending in the direction of the base body of the oil slinger, wherein the first gripping arm of the oil slinger extends toward the sealing ring. Background Art

[0002] DE 10 2022 130 974 A1 discloses a bearing assembly in a transmission, which comprises a pre-sealing element (oil slinger) and a radial shaft sealing ring on the bearing side (see Figure 1 、 Figure 2 ). The pre-sealing element bridges the housing section with an annular projection.

[0003] DE 10 2016 209 109 A1 discloses a bearing having a two-part sealing device arranged between an outer ring and an inner ring. The first part is arranged on the inner ring, extends in a C-shape with multiple steps, and surrounds a portion of the outer ring. The second part of the sealing device is arranged on the outer ring. The second part contacts the first part of the sealing device with both a radially extending sealing lip and a second sealing lip extending primarily in the axial direction.

[0004] JP 7137184 B2 discloses a two-part sealing device. The first part of the sealing device consists of a stepped cover disk. The second part of the sealing device has two sealing lips that contact the cover disk in the radial direction and one sealing lip that contacts the cover disk in the axial direction. The cover disk is arranged on the first component, and the second part having the sealing lips is arranged on the second component. The cover disk surrounds a region of the second component with an axially extending section and has a projection that extends axially toward the second part of the sealing device. Summary of the Invention

[0005] It is an object of the present invention to provide a bearing assembly having an improved sealing effect.

[0006] According to the invention, this object is achieved in that the projection of the oil slinger has a reduction from a first diameter to a second diameter on an inner side of the oil slinger facing the shaft, wherein the housing has a reduction from a third diameter to a fourth diameter on an outer side of the housing facing the inner side of the oil slinger, wherein a sealing gap is formed between the inner side of the oil slinger and the outer side of the housing.

[0007] Alternatively, the object is achieved in that the portion of the housing has a first recess at the outside of the projection of the housing facing the oil slinger, and the inside of the portion of the projection facing the housing has a second recess, the first and second recesses being in the form of circumferential grooves.

[0008] To ensure that rolling bearings function optimally, they must be protected from ambient interference such as dirt particles or liquids in their installation environment. Particularly in high-speed applications, such as electric motors, such interference, especially dirty water, can significantly impair function and even cause vehicle failure.

[0009] In order to solve this problem, the bearing assembly according to the present invention is used. A cover disk is arranged on the shaft of the bearing assembly, and the cover disk is also called an oil slinger due to its function.

[0010] During operation, the shaft rotates, and the oil slinger arranged on the shaft rotates with it. The shaft is at least one shaft, meaning the oil slinger can also be arranged on another shaft that rotates and is coupled to the first shaft. Liquid or other particles impinging on the oil slinger are ejected by the rotational motion. During operation, the housing remains stationary. A sealing ring, in particular a radial shaft seal, is arranged on the housing. The oil slinger is designed to consist of a base, in addition to a base for mounting on the shaft, and a projection, wherein the base transitions into the projection. The base extends radially between the housing and the shaft. Preferably, the base is straight, i.e., without bends, to provide a high degree of resilient action. The projection extends along the axis of rotation, i.e., in the axial direction. The base has a first gripping arm that extends toward the sealing ring. The first gripping arm is a projection extending from the base. The sealing ring has a first sealing lip that projects toward the base of the oil slinger. The first gripping arm and the first sealing lip thus form a barrier to prevent interfering dirt particles or water particles from entering the interior of the rolling bearing.

[0011] If interfering particles or liquids reach the aforementioned barrier, they are already very close to the rolling bearing. Particularly at high operating speeds, particles strike the first gripper arm and the first sealing lip at very high speeds, and liquids strike at high pressure. The first sealing lip in particular carries the risk of allowing particles or liquids to pass through. The intruding particles and dirty water corrode and wear the rolling bearing, as well as the sealing rings and slingers. This results in a loss of sealing effectiveness and potential long-term failure of the bearing assembly and the vehicle.

[0012] A key challenge in rolling bearings used in electric motors is preventing contaminated water from penetrating the rolling bearing. Simply placing a seal directly upstream of the rolling bearing is not sufficient; the potential ingress of contaminated water in the surroundings of the rolling bearing must also be considered. To this end, essential components required for the operating conditions are used to form an upstream sealing gap. A sealing gap is a gap whose function is to prevent, or at least hinder, the ingress of surrounding media, such as dirt particles or liquids, into the interior of the rolling bearing. To this end, the oil slinger is arranged so that its projection encompasses a portion of the housing. The projection of the housing or the oil slinger is designed so that the portion of the housing enclosed by the projection at least partially overlaps the projection in the axial and radial directions. In particular, the projections of the housing and the oil slinger are designed so that the portion of the housing enclosed by the projection at least partially overlaps the projection in the axial and radial directions. Preferably, the portion of the housing enclosed by the projection of the oil slinger and the adjacent area of the housing are arranged so that the projection of the oil slinger at least partially overlaps in the axial and radial directions. In this way, undercuts are formed in two directions between the projection of the oil slinger and the housing.

[0013] By means of undercuts in two directions, a labyrinth-like pre-seal is realized using existing components. The pre-seal itself reduces the ingress of sewage. During operation, depending on the embodiment, a siphon effect can also be generated in the pre-seal by the rotation of the shaft, which, by creating an overpressure, also makes it more difficult for sewage to enter. The undercuts in two directions simultaneously reduce the speed of the inflowing sewage. Even if sewage does pass through the pre-seal, the sealing lip of the sealing ring is hardly subjected to pressure due to the low liquid pressure caused by the slowing down of the sewage in the labyrinth. As a result, only small amounts of sewage can enter the inner area between the sealing ring and the oil slinger at a low speed. The embodiment of the bearing assembly with partial components arranged in a labyrinth shape produces a complex flow path. This slows down the sewage and seals the rolling bearing.

[0014] Furthermore, according to the present invention, the embodiment according to the independent claim further comprises: the projection of the oil flinger has a reduction from a first diameter to a second diameter on the inner side of the oil flinger facing the shaft, and the housing has a reduction from a third diameter to a fourth diameter on the outer side of the housing facing the inner side of the oil flinger, wherein a sealing gap is formed between the inner side of the oil flinger and the outer side of the housing. Preferably, there is a first diameter, and the first diameter is measured from the inner side of the oil flinger projection to the radially opposite inner side of the oil flinger projection. The second diameter is measured from the inner side of the oil flinger projection to the radially opposite inner side of the oil flinger projection, but with an axial offset. In this case, the first diameter is greater than the second diameter. The projection of the oil flinger reduces its distance from the axis of rotation. The reduction is preferably step-shaped. The third diameter is measured from the outer side of the housing portion to the radially opposite outer side of the housing portion. The fourth diameter is measured from the outer side of the housing portion to the radially opposite outer side of the housing portion, but with an axial offset. Here, the third diameter is greater than the fourth diameter. The outer side of the housing portion reduces its distance from the axis of rotation. This reduction is particularly step-shaped. A gap is formed between the inner side of the oil flinger and the housing portion. This gap fulfills the function of a sealing gap, namely, it prevents the surrounding medium from entering the area located spatially behind the sealing gap. In this case, the sealing gap is Z-shaped. The inner side of the projection of the oil flinger and the outer side of the housing portion extend parallel to each other and change direction together in sections. In other words, the sealing gap is designed in a labyrinthine manner.

[0015] The stepped design of the sealing gap lengthens the flow path of incoming liquid media, such as sewage. During changes in direction, the resulting constrictions in the sealing gap disrupt the flow path and slow the incoming medium. During operation, this arrangement creates a siphon effect due to the high rotational speed of the shaft. This creates an overpressure in the sealing gap, making it difficult for the medium to enter. Consequently, this arrangement allows only a portion of the surrounding medium to enter the sealing gap. The medium is decelerated in the labyrinthine sealing gap and, if it does pass through, only at a reduced speed.

[0016] According to the accompanying claim, a portion of the housing has a first recess on the outer side of the housing projection facing the oil flinger, and a second recess on the inner side of the portion of the projection facing the housing. These recesses are configured as circumferential grooves. The portion of the housing facing the projection is configured as a recess, or notch. Similarly, a notch is configured on the side of the projection opposite the portion of the housing. Specifically, the notch in the portion of the housing is V-shaped in a cross-section through a radial plane extending along the axis of rotation. Specifically, the notch in the projection of the oil flinger is V-shaped in a cross-section through a radial plane extending along the axis of rotation, but rotated 180° so that the tip of the V points away from the axis of rotation. Viewed in a three-dimensional diagram, the notch is configured as a circumferential groove. The notch increases the contact surface between the inflowing medium and the projection and the portion of the housing. The notch acts as a damper and reduces the flow velocity of the medium. Furthermore, the notch collects the fluid, allowing it to drain downwards under the force of gravity.

[0017] In a further development, the housing portion at least partially forms a channel, which serves as a fluid passage. The channel can be formed entirely or only partially in the housing portion. Preferably, a housing section adjoins the channel, which radially extends beyond the projection of the oil flinger and is angled away from the projection. The channel serves as a passage for the fluid in the housing. Media, such as contaminated water, collects in the channel rather than being pushed further into the gap between the projection and the housing portion and flowing away from the bearing assembly along the channel due to gravity.

[0018] Preferably, the sealing ring has at least one second sealing lip, so that a capture chamber is formed between the first sealing lip and the second sealing lip. Preferably, the second sealing lip does not contact the shaft to prevent the second sealing lip from being worn.

[0019] Preferably, the radially outer side of the portion of the protruding portion of the oil slinger facing away from the housing has a recess. In particular, the recess is circumferentially configured. In particular, the recess is configured as a V-shaped groove, the purpose of which is to reduce the velocity of the inflowing medium and prevent the medium, such as sewage, from entering the sealing gap at the inlet. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 shows a partial cross-sectional view of an embodiment of a bearing assembly,

[0021] Figure 2 FIG. 1 shows a partial cross-sectional view of an embodiment of a bearing assembly according to the present invention,

[0022] Figure 3 shows a partial cross-sectional view of another bearing assembly,

[0023] Figure 4 shows a partial cross-sectional view of another embodiment of a bearing assembly according to the present invention,

[0024] Figure 5 A partial cross-sectional view of a bearing assembly is shown. DETAILED DESCRIPTION

[0025] Figure 1 A detail of a bearing assembly 1 having a rolling bearing 2 equipped with ball-type rolling elements 29 is shown. The schematic diagram shows a cross-section through a plane in which the axis of rotation 3, extending in the axial direction a, lies. A radial direction r extends perpendicular thereto. The axis in the radial direction r and the axis of rotation 3 define a plane, also called a radial plane. The rolling bearing 2 is arranged between a rotatable shaft 4, 31 and a housing 5. A sealing ring 10 is arranged between the housing 5 and the shaft 4, 31, offset axially with respect to the rolling bearing 2. The sealing ring 10 has a first sealing lip 11, which projects on the side facing away from the rolling bearing 2. The sealing ring 10 has a second sealing lip 14 and a third sealing lip 33, the third sealing lip not contacting the shaft 4, 31. The sealing ring 10 also has an additional sealing lip 30, which contacts the shaft 4, 31. The sealing ring 10 is arranged on the housing 5, while the oil slinger 6 is arranged on the shaft 4, 31. In addition to a base for mounting the oil slinger on the shaft 4, 31, the oil slinger 6 comprises a base 8 and a projection 7. The oil flinger 6 extends radially r away from the shaft 4, 31 beyond the portion 12 of the housing 5. The projection 7 of the oil flinger 6 thus circumferentially surrounds the portion 12 of the housing 5. The portion 12 of the housing 5 forms an undercut 13 with the projection 7 of the oil flinger 6, so that the portion 12 overlaps with the projection 7 in the radial direction r and the axial direction a. A sealing gap 17 remains between the housing 5 and the oil flinger 6. This sealing gap changes direction at least once, thereby forming a labyrinth seal. The base 8 of the oil flinger 6 has a first gripping arm 9 that extends toward the sealing ring 10. The first gripping arm 9 overlaps the first sealing lip 11 without contact. During operation, when the shaft 4, 31 and the oil flinger located thereon rotate at high speeds, the bearing assembly generates an overpressure in the sealing gap 17. This creates a siphon effect in the sealing gap 17. Dirt water is prevented from entering the interior between the oil flinger 6 and the sealing ring 10 at the inlet. If dirty water still enters, the interaction between the first gripping arm 9 and the first sealing lip 11 prevents the dirty water from moving further forward.

[0026] Figure 2 A partial view of a first embodiment of a bearing assembly 1 according to the present invention is shown. Figure 1A similar arrangement is shown in the bearing assembly, which includes a housing 5, a shaft 4, 31, a sealing ring 10, and an oil slinger 6 with a projection 7. The sealing ring 10 has a first sealing lip 11 that extends toward the oil slinger 6. Furthermore, the sealing ring 10 has a non-contacting second sealing lip 14, a non-contacting third sealing lip 33, and an additional sealing lip 30, wherein the additional sealing lip 30 contacts the shaft 4, 31. The oil slinger 6 is arranged on the shaft 4, 31 and, in addition to the first gripping arm 9, has a second gripping arm 20 that is inclined toward the sealing ring 10. The first gripping arm 9 extends in the axial direction a toward the sealing ring 10 and has a section that extends toward the housing 5. From the housing 5 toward the shaft 4, 31, the first gripping arm 9, the first sealing lip 11, and the second gripping arm 20 are arranged alternately. The housing 5 has a portion 12 that faces the projection 7. This portion 12 of the housing 5 forms an overlap with the projection 7 of the oil slinger 6 in the axial direction a and in the radial direction r, i.e., an undercut 13. Here, an inner side 15 of the projection 7 facing the housing 5 and an outer side 16 of the housing 5 face each other in a spaced-apart manner.

[0027] The projection 7 tapers in a stepped manner on the inner side 15, reducing the first diameter d1 from the inner side of the projection 7 to the second diameter d2. Similarly, the diameter d3 from the outer side 16 of the housing 5 decreases to the diameter d4. The resulting sealing gap 17 has a Z-shaped profile. This arrangement also creates a siphon effect, which prevents dirty water from entering the interior from the inlet. Any dirty water that does enter is blocked by the specially designed first gripper arms 9. On the other hand, the alternating arrangement of overlapping sections between the first gripper arms 9, the first sealing lip 11, and the second gripper arms 20 creates a further labyrinthine structure, resulting in a double labyrinth in this embodiment. The first gripper arms 9 and the second gripper arms 20 engage with the first sealing lip 11, creating a deliberately complex flow path for the medium, making it difficult for the medium to enter critical areas.

[0028] exist Figure 3A bearing assembly 1 is also shown in FIG. A housing 5 is shown, which surrounds the shaft 4, 31 in a circumferential manner. The shaft 4, 31 extends along the axis of rotation 3, which extends in the axial direction a and in the radial direction r perpendicular to the axis of rotation 3. The housing 5 has a portion 12, which in turn has an end section 19 of the housing 5. The sealing ring 10 is arranged at the housing 5. The first sealing lip 11 extends from the radially extending base 8 of the sealing ring 10. The first sealing lip 11 first extends parallel to the axis of rotation 3 and is then bent so that the first sealing lip extends obliquely away from the axis of rotation 3 in the direction of the oil slinger 6. In addition, the sealing ring 10 has a second sealing lip 14 and a third sealing lip 33, and an additional sealing lip 30, the second sealing lip and the third sealing lip do not touch the shaft 4, 31, and the additional sealing lip is in contact with the shaft 4, 31. The first sealing lip 11 strikes the first gripping arm 9 of the oil slinger 6 approximately perpendicularly, wherein the first gripping arm 9 and the first sealing lip 11 are Figure 3 In the illustrated ready-to-run state, they are spaced apart from one another. The oil slinger 6 is arranged on the shaft 4, 31 and extends in the radial direction r toward the housing 5, wherein a projection 7 of the oil slinger 6, which extends in the axial direction a, surrounds a portion 12 of the housing 5. The projection 7 has a tail 18 that extends in the radial direction r. At the same time, the housing 5 has an end section 19 that extends in the axial direction a and forms an overlap with the projection 7 of the oil slinger 6. Consequently, an undercut 13 is formed in both directions, namely in the axial direction a and in the radial direction r, between the projection 7 of the oil slinger 6 and the portion 12 and end section 19 of the housing 5. The geometry of the oil slinger 6 and the housing 5 forms a sealing gap 17 that extends in a labyrinthine manner. This forms a pre-labyrinth that particularly prevents contaminated water from entering the interior from the inlet.

[0029] Figure 4A cross-sectional view of a second embodiment of a bearing assembly 1 according to the present invention is disclosed. Here, an oil slinger 6 is arranged on a further shaft 31, which is at least partially surrounded by the shaft 4. In this embodiment, the projection 7 of the oil slinger 6 also extends in the axial direction a and surrounds a portion 12 of the housing 5. Because the housing 5 extends beyond the projection 7 in the radial direction r, an undercut 13 is formed between the projection 7 and the housing 5. A sealing gap 17 remains between the oil slinger 6 and the housing 5, which makes access to the interior difficult. The oil slinger 6 has a first gripping arm 9 that extends toward the sealing ring 10. The sealing ring 10 is arranged on the housing 5 and has a first sealing lip 11 that extends toward the oil slinger 6. Furthermore, the sealing ring 10 has a non-contacting second sealing lip 14, a non-contacting third sealing lip 33, and an additional sealing lip 30 that contacts the first shaft 4. The projection 7 has an inner side 15 that faces the outer side 16 of the housing 5. Radially opposite, the projection 7 has a radially outer side 25. A first depression 23 is formed on the outer side 16 of the housing portion 12, which is V-shaped in the cross-sectional view shown. Simultaneously, a second depression 24 is formed on the inner side 15 of the oil flinger 6, which is V-shaped in the cross-sectional view rotated 180°. A recess 26 is also formed on the radially outer side 25 of the projection 7, which is also V-shaped in the cross-sectional view shown. Viewed in three dimensions, the recess is a groove with a V-shaped cross-section on the inner side 15 and radially outer side 25 of the projection 7, as well as on the outer side 16 of the housing portion 12. The housing portion 12 comprises approximately one half of a channel 28, which is completed in the adjoining housing section 32 by the second half of the channel 28. The adjoining housing section 32 has a surface radially facing away from the projection 7 of the oil flinger 6. The inclined surface of housing section 32 guides the medium collected in channel 28 back out of channel 28. The first and second recesses 23, 24 increase the contact surface for incoming medium, such as sewage. This reduces the flow velocity of the incoming medium. The illustrated geometry of sealing gap 17 limits the velocity of the medium. During operation, bearing assembly 1 rotates, and the medium collected in first and second recesses 23, 24 is continuously drained away due to gravity. The recesses 26 on radially outer side 25 collect the medium and drain it away again as the slinger 6 rotates.

[0030] Figure 5Another bearing assembly 1 is shown having a shaft 4, 31 and a housing 5, wherein a sealing ring 10 is arranged between the shaft 4, 31 and the housing 5. The sealing ring 10 is arranged on the housing 5, while an oil slinger 6 is arranged on the shaft 4, 31. The projection 7 of the oil slinger 6 is designed in a stepped manner on the inner side 15. Complementarily, the outer side 16 of the part 12 of the housing 5 opposite the projection 7 is also designed in a stepped manner, as shown in FIG. Figure 2 As shown in . Because the portion 12 of the housing 5 is spaced apart from the projection 7 of the oil flinger 6, a labyrinth-shaped sealing gap 17 is formed. The portion 12 of the housing 5 and the projection 7 of the oil flinger 6 form an undercut 13. This differs from the previously shown embodiment in that the oil flinger 6 has a further gripping arm 22 in addition to the first and second gripping arms 9 and 20. Simultaneously, the sealing ring 10, starting from the base body 8, has a further sealing lip 21 in addition to the first sealing lip 11. The following sequence is used in the radial direction r from the shaft 4, 31 to the housing 5: second gripping arm 20, first sealing lip 11, first gripping arm 9, further sealing lip 21, further gripping arm 22. Thus, in addition to the preceding labyrinth seal formed by the portion 12 of the housing 5 and the projection 7 of the oil flinger 6, a labyrinth seal is also formed internally. The second sealing lip 14 and the third sealing lip 33 form a catch chamber. The additional sealing lip 30 forms a barrier, acting as a last resort to prevent the ingress of media into the critical area.

[0031] The double seal can thus prevent interfering liquids, such as contaminated water, from entering the rolling bearing 2 under extreme conditions, such as very high pressures.

[0032] Reference Signs List

[0033] 1 bearing assembly

[0034] 2 Rolling bearings

[0035] 3 Rotation axis

[0036] 4 First axis

[0037] 5. Housing

[0038] 6 Oil slinger

[0039] 7 protrusion

[0040] 8 Matrix

[0041] 9 First grabbing arm

[0042] 10 Sealing ring

[0043] 11 First sealing lip

[0044] 12 Shell parts

[0045] 13 Undercut

[0046] 14 Second sealing lip

[0047] 15 Inside of the oil slinger

[0048] 16 Outside of the housing

[0049] 17 Sealing gap

[0050] 18 The tail of the protruding part of the oil slinger

[0051] 19 End section of the housing

[0052] 20 Second grab arm

[0053] 21 Additional sealing lip

[0054] 22 Additional grab arms

[0055] 23 first recessed portion

[0056] 24 Second recessed portion

[0057] 25 The radially outer side of the protrusion

[0058] 26 notches

[0059] 27 Section at the first gripping arm

[0060] 28 Channel at the shell

[0061] 29 ball rolling element

[0062] 30 Additional sealing lip

[0063] 31 Additional Axis

[0064] 32 Shell section

[0065] 33 Third sealing lip

[0066] a Axial

[0067] d1 first diameter

[0068] d2 second diameter

[0069] d3 third diameter

[0070] d4 fourth diameter

[0071] r Radial

Claims

1. A bearing assembly (1), comprising: a rolling bearing (2) arranged about an axis of rotation (3) extending in an axial direction (a), - a shaft (4, 31) extending in the axial direction (a), - a housing (5), an oil slinger (6) arranged on the shaft (4, 31), the oil slinger having a projection (7) extending in the axial direction (a) and a base (8) extending in the radial direction (r), the base having a first gripping arm (9), the projection (7) circumferentially surrounding a portion (12) of the housing (5), and at least the portion (12) of the housing (5) forming an undercut (13) with the projection (7) of the oil slinger (6) in the axial direction (a) and in the radial direction (r), a sealing ring (10) arranged on the housing (5), the sealing ring having a first sealing lip (11) which extends in the direction of the base body (8) of the oil slinger (6), wherein a first gripping arm (9) of the oil slinger (6) extends towards the sealing ring (10), The invention is characterized in that the projection (7) of the oil slinger (6) has a reduction from a first diameter (d1) to a second diameter (d2) on the inner side (15) of the oil slinger (6) facing the shaft (4, 31), wherein the housing (5) has a reduction from a third diameter (d3) to a fourth diameter (d4) on the outer side (16) of the housing (5) facing the inner side (15) of the oil slinger (6), wherein a sealing gap (17) is formed between the inner side (15) of the oil slinger (6) and the outer side (16) of the housing (5).

2. Bearing assembly according to the preamble of claim 1, characterized in that The portion (12) of the housing (5) surrounded by the projection (7) has a first recess (23) at the outer side (16) of the projection (7) of the housing (5) facing the oil slinger (6), and the inner side (15) of the portion (12) of the projection (7) facing the housing (5) has a second recess (24), the first recess (23) and the second recess being in the form of circumferential grooves.

3. The bearing assembly according to claim 2, wherein: The portion (12) of the housing at least partially forms a channel (28) which is configured as a fluid passage.

4. The bearing assembly according to claim 1 or 2, characterized in that: The sealing ring (10) has at least one second sealing lip (14).

5. The bearing assembly according to claim 2, wherein: The radially outer side (24) of the projection (7) of the oil slinger (6) facing away from the part (12) of the housing (5) has a circumferential recess (26).

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