阅读说明：本技术 滚动元件轴承组件 (Rolling element bearing assembly ) 是由 扬·克勒格尔 彼得·兰帕尔 汉斯·尤尔根·利泽冈 克劳斯·迪特尔·舒尔茨 于 2020-11-09 设计创作，主要内容包括：公开了一种滚动元件轴承组件(100),特别是双列圆锥滚子轴承,包括第一轴承圈(2；6)和第二轴承圈(2；6),第一轴承圈(2；6)和第二轴承圈(2；6)之间形成轴承内部(8),滚动元件(10)被布置在所述轴承内部(8)中以允许第一轴承圈(2；6)与第二轴承圈(2；6)的相对旋转,其中,滚动元件轴承组件(100)还包括用于密封轴承内部(8)的密封组件,其中,密封组件包括密封架(12)和密封元件(16),密封架(12)连接到第一轴承圈(2；6)使得它们一起旋转,密封元件(16)连接到密封架(12)使得它们一起旋转,其中,密封架(12)由纤维增强塑料制成。(A rolling element bearing assembly (100), in particular a double row tapered roller bearing, is disclosed, comprising a first bearing ring (2; 6) and a second bearing ring (2; 6), the first bearing ring (2; 6) and the second bearing ring (2; 6) forming a bearing interior (8) therebetween, rolling elements (10) being arranged in said bearing interior (8) to allow relative rotation of the first bearing ring (2; 6) and the second bearing ring (2; 6), wherein the rolling element bearing assembly (100) further comprises a sealing assembly for sealing the bearing interior (8), wherein the seal assembly comprises a seal carrier (12) and a seal element (16), the seal carrier (12) being connected to the first bearing ring (2; 6) such that they rotate together, the seal element (16) being connected to the seal carrier (12) such that they rotate together, wherein the seal carrier (12) is made of a fibre-reinforced plastic.)

1. Rolling element bearing assembly (100), in particular a double row tapered roller bearing, comprising a first bearing ring (2; 6) and a second bearing ring (2; 6), the first bearing ring (2; 6) and the second bearing ring (2; 6) forming a bearing interior (8) between them, rolling elements (10) being arranged in the bearing interior (8) to allow relative rotation of the first bearing ring (2; 6) and the second bearing ring (2; 6), wherein the rolling element bearing assembly (100) further comprises a seal assembly for sealing the bearing interior (8), wherein the seal assembly comprises a seal carrier (12) and a seal element (16), the seal carrier (12) being connected to the first bearing ring (2; 6) such that the seal carrier (12) rotates together with the first bearing ring (2; 6), the sealing element (16) is connected to the sealing frame (12) such that the sealing element (16) rotates together with the sealing frame (12), characterized in that the sealing frame (12) is made of fiber reinforced plastic.

2. The rolling element bearing assembly (100) according to claim 1, wherein the seal carrier (12) is made of glass Fiber Reinforced Plastic (FRP).

3. Rolling element bearing assembly (100) according to claim 1 or 2, wherein the sealing cage (12) is compression moulded from a fibre matrix composite plate.

4. The rolling element bearing assembly (100) according to any of the preceding claims, wherein the seal cage (12) is multi-piece formed from a plurality of seal cage segments (12) abutting each other.

5. Rolling element bearing assembly (100) according to claim 4, wherein the seal carrier segments (12) comprise mutually complementary structures (38; 40) on their abutment surfaces, the structures (38; 40) being formed such that a one-to-one engagement and connection between two adjacent seal carrier segments (12) in radial, axial and/or circumferential direction is ensured.

6. Rolling element bearing assembly (100) according to claim 5, characterised in that the structure (38; 40) comprises a radial stop and/or an axial stop.

7. Rolling element bearing assembly (100) according to any of the preceding claims, characterised in that the sealing element (16) carried by the sealing cage (12) is circumferentially attached to the sealing cage (12) by a clamping ring (18).

8. Rolling element bearing assembly (100) according to any of the preceding claims, wherein the sealing element (16) and/or the seal carrier (12) comprises a structure (28; 32) for attaching the sealing element (16) to the seal carrier (12) such that the sealing element (16) rotates together with the seal carrier (12).

9. Rolling element bearing assembly (100) according to any of the preceding claims, characterised in that the sealing element (16) comprises a primary sealing lip (24) and a secondary sealing lip (26), wherein the primary sealing lip (24) and the secondary sealing lip (26) axially abut an end side of the second bearing ring (2; 6) or radially abut a raceway surface of the second bearing ring (2; 6).

10. Rolling element bearing assembly (100) according to any of the preceding claims, wherein the primary sealing lip (24) abuts an end surface (30) or a radial surface of the second bearing ring (2; 6) with a predetermined contact force.

11. Rolling element bearing assembly (100) according to any of the preceding claims, characterised in that the contact force of the primary sealing lip (24) is determined by the length of the sealing lip (24), the angle of incidence of the sealing lip (24) with respect to the end surface (30), the material of the sealing lip (24), the geometrical design of the sealing lip (24) and/or the defined distance of the sealing carrier (12) to the end surface (30) of the second bearing ring (2; 6).

Technical Field

The invention relates to a rolling-element bearing assembly, in particular a double-row tapered roller bearing, according to the preamble of scheme 1, wherein the rolling-element bearing assembly has a diameter of more than one meter.

Background

In particular, rolling element bearing assemblies having a large diameter are used in the heavy industry and are characterized in that they have a diameter of at least one meter or more, and are therefore also referred to as large rolling element bearings. Thus, large rolling element bearings are much larger than those typically used in everyday applications, such as in automobiles for example. In the construction of large rolling-element bearings, it is therefore also not possible to scale small bearings to large bearings, since other criteria, such as weight, material used for manufacture, installation costs and possibility of maintenance, play a significantly greater role.

For example, it is known in the prior art to assemble a bearing ring from a plurality of segments, so that the bearing can be serviced, for example, without disassembling a shaft supported by the bearing. However, the weight of such large rolling element bearings is particularly problematic. It has therefore been proposed in the prior art, in particular from DE102009014923a1, to reduce the size of the outer ring in the axial direction, in order thereby to save material and reduce the overall weight. However, for this purpose, the bearing rings or the sealing points inside the bearing have to be redesigned. It has therefore been proposed in this publication to attach in the axial direction a so-called seal carrier to the end surface of the outer ring, which seal carrier carries a radial shaft seal ring which in turn abuts (abuts) against the radial surface of the inner ring.

Such a seal carrier is typically attached using a plurality of screws to securely screw the ring of the seal carrier to the outer race. Thus, such installation labor and the manufacture of the ring is very time and cost consuming. Although it has been proposed in the prior art to also manufacture the seal carrier from partial segments (partial segments) and thereby simplify the mounting, it is nevertheless necessary to form specific attachment surfaces on the seal carrier and the outer ring in order to reliably attach the seal carrier to the outer ring such that the seal carrier rotates together with the outer ring even without screws. In this way, it is proposed to form undercuts (undercuts) on the sealing shelf, which can engage into corresponding complementary undercuts formed on the outer ring. Whereby attachment can be made easier. However, this design requires additional handling of the seal carrier and the outer ring, which in turn is very costly and time consuming.

Disclosure of Invention

It is therefore an object of the present invention to provide a seal carrier which is manufactured in an economical and time-saving manner and which can be easily attached to a rolling element bearing assembly.

This object is achieved by a rolling element bearing assembly, in particular a double row tapered roller bearing.

In the following, a rolling element bearing assembly is proposed, comprising a first bearing ring and a second bearing ring forming (between them) a bearing interior in which rolling elements are arranged to allow relative rotation of the first and second bearing rings. In particular, such a rolling element bearing assembly may be a double row tapered roller bearing. Furthermore, such a rolling element bearing assembly can be used in particular in the heavy industry, wherein the first bearing ring and/or the second bearing ring have a diameter of more than one meter. Furthermore, the rolling element bearing assembly comprises a seal assembly for sealing the bearing interior, wherein the seal assembly comprises a seal carrier and a seal element, the seal carrier being connected to the first bearing ring such that the seal carrier rotates with the first bearing ring, the seal element being connected to the seal carrier such that the seal element rotates with the seal carrier.

In order to reduce the overall weight of the rolling element bearing assembly and to reduce manufacturing costs and production time, it is proposed to manufacture the seal carrier from fiber-reinforced plastic (fiber-reinforced plastic). In particular, glass Fiber Reinforced Plastics (FRP) are used here. Such plastics are particularly dimensionally stable and have a considerably higher, if not higher, stability than the commonly used metal sheet materials.

However, in order to be able to obtain the necessary stability and dimensional stability even in the case of large rolling element bearings, it is preferred that the seal carrier is not manufactured from a plurality of layers as is usual, but from a fibre matrix composite plate compression moulding (SMC method). No post-processing of the seal carrier is necessary. On the one hand, this makes it possible to speed up the production process and, on the other hand, to avoid errors due to incorrect lamination of the fiber-reinforced plastic. In addition, with compression molded fiber matrix composite plates, high dimensional accuracy can be achieved, so that other sealing concepts with, for example, purely axial sealing can also be used instead of radial shaft seals.

Thus, for example, a rolling element bearing assembly is more preferred, wherein the seal carrier carries a sealing element comprising a primary and a secondary seal lip (secondary seal lip) each axially abutting an end surface of the second bearing ring. In this case, in particular, the distance between the seal carrier and the end face (or end surface) of the second bearing ring determines the contact force of the seal lip against the end face of the second bearing ring. Since the seal carrier can be manufactured particularly dimensionally stable and precisely using fiber-reinforced plastic, the axial distance between the end side of the second bearing ring and the seal carrier can be set precisely to ensure that the axially abutting sealing lips have a sufficient contact force to ensure that the bearing interior is sealed from the outside in all operating situations of the bearing.

Furthermore, the design of the sealing shelf made of fibre-reinforced plastic (FRP in particular) makes it possible to introduce structures such as grease supply holes, endoscopic holes (endoscopic holes) and exhaust holes directly during manufacture. This is particularly the ability to achieve precise fit and shape with a compression moulded fibre matrix composite plate.

Furthermore, other elements such as, for example, attachment grooves for receiving sealing elements, may be formed directly during the manufacturing process of the sealing frame.

According to a further advantageous exemplary embodiment, the sealing frame can be constructed in multiple parts. In order to achieve particularly good connection and axial, radial and/or circumferential orientation (/ orientation) of the seal carrier sections (/ seal carrier sections), the seal carrier sections comprise mutually complementary structures on their connecting surfaces, which allow one-to-one coupling and connection (/ one-to-one arrangement and connection) of the seal carrier sections. These complementary structures can also be introduced directly during the manufacturing process of the sealing frame by compression moulding.

In this case, it is particularly preferred that the arrangement comprises a radial stop and/or an axial stop, so that the seal carrier sections can be aligned radially and axially relative to one another.

In order to attach the sealing element to the seal carrier, it is also proposed to use a clamping ring (gripping ring) configured to clamp the sealing element axially between the seal carrier and the sealing element, thereby fixing the sealing element against rotation. In addition to clamping, the sealing element may additionally or alternatively be attached to the clamping ring and/or the seal carrier by a friction fit, in particular using other attachment elements (e.g. screws). It is also possible that the sealing element, the clamping ring and the seal carrier comprise structures which interact with one another in an interference fit (interference-fit), which structures can also attach the sealing element to the seal carrier with the aid of the clamping ring. Additionally or alternatively, the sealing element may also be attached to the sealing frame and/or the clamping ring in a material bonded (/ bonded) (bonded) manner, wherein in particular bonded (/ bonded/adhered) (adhering) is preferred. Of course, other or additional attachment possibilities of the sealing element to the sealing frame or the clamping ring are equally possible and included within the scope of the present application.

Preferably, the sealing element itself may comprise a sealing body supporting both the primary and secondary sealing lips, such that the sealing element is constructed as a one-piece (/ one-piece) element. However, other designs are possible in which the primary and secondary sealing lips are carried by different sealing bodies. The advantage of the one-piece design is that only one sealing element needs to be attached to the sealing frame, which in turn simplifies manufacturing and installation.

In addition to the distance between the seal carrier and the end surface, the length of the sealing lip, the angle of incidence of the sealing lip with respect to the end surface, the material of the sealing lip, the geometric design (/ geometric design) of the sealing lip also determine the contact force of the sealing lip, in particular the primary sealing lip, against the end surface of the bearing ring. It is therefore preferred that a lip-spread angle (lip-spread angle) falling in the range of 100 ° to 140 °, preferably at about 120 °, is formed between the primary and secondary sealing lips, wherein the primary and secondary sealing lips are oriented such that they point towards the inside of the bearing and the secondary sealing lip points in the opposite direction. Thus, a preferred sealing lip system can be realized on the end surface of the second bearing ring even in an axial orientation.

Furthermore, it is preferred that the sealing element can be made from nitrile rubber or hydrogenated nitrile rubber. These materials have high ozone resistance and can also be used at very low temperatures.

Further advantages and advantageous embodiments are indicated in the description, the drawing and the claims. In particular, the combinations of features specified in the description and the figures are merely exemplary here, so that the features can also be present individually or in other combinations.

In the following, the invention is described in more detail using exemplary embodiments depicted in the drawings. Here, the exemplary embodiments and combinations shown in the exemplary embodiments are merely exemplary and are not intended to limit the scope of the present invention. The scope is only limited by the pending claims.

Drawings

Fig. 1 shows a schematic perspective partial view of a rolling element bearing assembly according to a first exemplary embodiment;

figure 2 shows a schematic cross-sectional view of the rolling element bearing assembly of figure 1;

fig. 3 shows a schematic perspective detail view of the sealing element used in fig. 1 and 2;

FIG. 4 shows a schematic detail view of a seal carrier for use in a rolling element bearing assembly;

fig. 5 shows a schematic detail view of an alternatively used sealing element;

fig. 6 shows a schematic detail view of an alternatively used sealing element; and

fig. 7 shows a schematic detail view of an alternatively used sealing element;

in the following, identical or functionally equivalent elements are denoted by the same reference numerals.

List of reference numerals

100 rolling element bearing assembly

2 outer ring

4-shaft

6 inner ring

8 inside the bearing

10 rolling element

12 sealing rack

14 screw

16 sealing element

18 clamping ring

20 screw

22 sealing body

24 primary seal lip

26 auxiliary sealing lips

28 structure

30 end surface

32 undercut

34. 36 sealing projection

38. 40 complementary structure

42. 44 Flange element

46. 48 abutment surface

50 attachment element

52 projection

54 barb

56 thickened part

58 groove

60 projection

Distance D

Length of L

Angle of incidence of alpha

Beta lip spread angle

Detailed Description

Fig. 1 schematically shows a perspective partial view of a rolling element bearing assembly 100, the rolling element bearing assembly 100 comprising an outer ring 2 and an inner ring 6, the outer ring 2 being connected to a shaft 4 such that the outer ring 2 rotates with the shaft 4, wherein the outer ring 2 and the inner ring 6 form a bearing interior 8 therebetween, the rolling elements 10 being arranged in the bearing interior 8.

In order to protect the bearing interior 8 as a whole from dirt, water or particles, and to keep the lubricant, which is optionally located in the bearing interior 8, the bearing interior 8 must be sealed off from the outside. For this purpose, it is usual to attach a seal carrier 12 to the outer ring 2 or the shaft 4, the seal carrier 12 being attached by means of screws 14 and at least partially covering the bearing interior 8 in the exemplary embodiment shown in fig. 1. Here, the seal carrier 12 extends from the bearing outer ring 2 or the shaft 4 to the bearing ring 6 and carries the sealing element 16. This design is also shown enlarged in the sectional view of fig. 2, wherein, however, fig. 2 shows only the bearing inner ring 6, the rolling elements 10, and not the outer ring 2. Furthermore, a seal carrier 12 is depicted in fig. 2, the seal carrier 12 carrying a sealing element 16.

In the exemplary embodiment depicted in the figures, the sealing element 16 is configured as an axial sealing element. However, the sealing element may also be formed as a radial shaft sealing ring.

In order to attach the sealing element 16 to the seal carrier 12 such that they rotate together, a clamping ring (clamping ring)18 is additionally provided, which in turn is attached to the seal carrier 12 in the circumferential direction by means of screws 20, such that the sealing element 16 is clamped between the seal carrier 12 and the clamping ring 18. The sealing element itself is also attached to the clamping ring 18 in the circumferential direction by means of screws 20, so that the sealing element rotates together with the clamping ring 18 and is attached to the bearing inner ring 6 at a distance defined in the axial direction. Various attachment possibilities are discussed in more detail below.

As can be seen from fig. 2 and 3, the sealing element 16 comprises a sealing body 22 carrying a primary sealing lip 24 and a secondary sealing lip 26. In the depicted exemplary embodiment, the seal body 22 and the seal lips 24, 26 are integrally formed (/ formed as a single piece), but the sealing element 16 may also be made from multiple components. In the exemplary embodiment shown, the seal body 22 has a structure 28 in the form of a lug (lug), which structure 28 interacts with the seal carrier 12 to fix the seal body 22, and thus the seal body 16, on the seal carrier 12 in the axial direction and in the radial direction.

Furthermore, fig. 2 shows that the primary seal lip 24 and the secondary seal lip 26 are not oriented radially as usual, but are able to slide in the axial direction against the end surface of the inner ring 6. This is unusual, since until now it has been assumed by the person skilled in the art that the axial seal or the main seal 24 extending in the axial direction cannot exert a sufficient contact force against the end surface 30 or other axial surface to safely and reliably protect the bearing interior 8 from external contamination and to retain lubricant, which is optionally located in the bearing interior 8, in the bearing interior 8.

However, it has surprisingly been found that the sealing lip can be formed such that it can also exert a sufficient contact force in the axial direction. In addition to the distance D between the sealing frame 12 and the end face 30, the material of the sealing element, in particular the material of the main sealing lip, the length L of the main sealing lip, the angle of incidence α of the main sealing lip with respect to the end face 30, the geometric design of the main sealing lip, and the angle of spread β of the main sealing lip with respect to the secondary sealing lip 26 also play a crucial role. In order to obtain a particularly good contact force, the contact force and its behavior achieved over the entire service life of the bearing are simulated for the sealing element and the parameters are adjusted accordingly.

Thus, for example, the primary seal lip 24 depicted in FIG. 2 and enlarged in FIG. 3 shows a geometric design having a shape that is slightly curved outwardly and is centrally thickened, and the primary seal lip 24 has a lip-spread angle (β) of about 120 relative to the secondary seal lip 26. Further, the distance D between the seal holder 12 and the end surface 30 of the bearing inner race 6 is set so that the seal lip 24 is always in contact with the end surface 30 even under high load and long service life. Further, it is preferable that the incident angle α of the primary seal lip 24 with respect to the end surface 30 of the bearing inner race 6 falls within a range of about 20 ° to 60 °. Furthermore, it has been found preferable to manufacture the sealing element, in particular the main sealing lip 24, from an elastomeric material, preferably nitrile butadiene rubber (nitrile butadiene rubber) or hydrogenated nitrile butadiene rubber (hydrogenated nitrile butadiene rubber). These materials have sufficient strength, high elasticity and high smoothness (smoothness) to allow the sealing lip to sealingly abut the end surface 30 over its lifetime without being damaged by high friction torque or impeding rotation of the bearing assembly. In addition, these materials exhibit high ozone resistance (high resistance to ozone) and can also be used at low temperatures.

To attach the seal element 16 to the seal carrier 12, in the exemplary embodiment of FIG. 2, it is also depicted that the seal carrier 12 includes undercuts (undercuts) 32, the undercuts 32 interacting with the structure 28 (i.e., lugs) of the seal body 22 to secure the seal element 16 radially and axially. Furthermore, the undercut together with the lugs 28 forms a kind of labyrinth seal which further seals the bearing interior 8. For additional sealing of the bearing interior 8, as can be seen in particular also from the enlarged view of the sealing lip in fig. 3, a projection 34 extending in the radial direction is formed on the sealing element 16 in the region of the structure 28 and a projection 36 extending in the axial direction is formed in this region of the sealing body 22, in order to ensure an additional sealing between the sealing element 16 and the clamping ring 18 or the seal carrier 12. Furthermore, the seal body 22 may also be bonded (/ adhered) to the clamp ring 18 and/or the seal carrier.

As already mentioned above, the distance D between the seal carrier 12 and the end surface 30 of the bearing inner ring is particularly important, among other parameters, in order to establish the contact force of the main seal lip 24. In bearings known in the prior art, the seal carrier 12 is made of sheet metal, however, especially in large rolling element bearings, the sheet metal is slightly bent so that in conventional bearings the distance D varies greatly over the circumference. In the case of an axially extending seal, this variation prevents the primary seal lip 24 from abutting the end surface 30 of the bearing inner race 6 at all times, but rather being spaced therefrom. Accordingly, axial seal assemblies have never been considered by those skilled in the art.

In order to reduce axial imbalances as far as possible, it is therefore further proposed that the seal carrier 12 is not produced from sheet metal material, as is known from the prior art, but that the seal carrier 12 is produced from fiber-reinforced plastic, in particular glass fiber-reinforced plastic (FRP). FRP has the following properties: on the one hand, FRP is light, whereby the total weight of the large rolling-element bearing can be reduced, and on the other hand, FRP is very stable and non-deformable, so that the distance D between the seal carrier 12 and the end surface 30 can be accurately set and kept constant over the entire circumference even in the case of a large rolling-element bearing. It has been found to be advantageous here that the FRP material is not laminated as usual, but is compression-moulded from a fibre matrix composite plate, which in particular increases dimensional stability and manufacturing accuracy.

However, such a seal carrier 12 made of fiber-reinforced plastic (in particular of FRP material) can also be used as a seal carrier for a radial shaft seal.

Further, the seal carrier 12 may be formed in one or more pieces, and other structures may be formed directly during the manufacturing process, such as, for example, vent holes, lubricant supply holes, endoscopic holes (endoscopic holes), and the like.

In the multi-piece embodiment, as depicted in fig. 4, it is furthermore advantageous that two mutually abutting adjacent seal carrier sections 12a, 12b comprise mutually complementary structures 38, 40. In the exemplary embodiment depicted in fig. 4, the mutually complementary structures are realized by a projection 38 and a correspondingly configured groove 40, which projection 38 and correspondingly configured groove 40 engage each other during assembly and align the seal carrier sections 12a, 12b with each other in radial and axial direction. Further, a flange element (/ flange element) 42, 44 may be attached to each of the seal carrier sections 12a, 12b, the flange elements 42, 44 may be screwed to each other to connect the seal carrier sections 12a, 12b to each other. In addition, the engagement surfaces 46, 48 (particularly flange surfaces) of the seal carrier segments may be coated with a sealing material (particularly a liquid seal) to ensure the tightness of the seal carrier 12 in the circumferential direction. The sealing frame segments 12a, 12b can also be bonded to each other only, wherein the adhesive (adhesive) can then assume both the attachment function and the sealing function.

Instead of the tongue-and-groove connection (tongue-and-groove connection) depicted, it is of course also possible to form other suitable complementary structures, so that the sealing carrier sections can be fixed and oriented radially, axially and/or circumferentially relative to one another. However, it is particularly advantageous here for the complementary structures to comprise at least one radial stop and one axial stop, so as to simplify the orientation of the seal carrier section.

Fig. 5, 6 and 7 show further alternative attachment possibilities of the sealing element 16 to the sealing frame 12 or the clamping element 18. In other embodiments shown, the sealing element 16 is connected only to the clamping element 18 and is not directly attached to the seal carrier 12. Thus, fig. 5 and 6 each show a design in which the sealing element 16 and the clamping ring 18 are connected to each other in an interference and friction fit. Here, a purely interference and friction fit design is shown in fig. 5, whereas in fig. 6 the interference or friction fit is supplemented by a friction fit by means of an additional attachment element 50. In fig. 5, the clamping ring 18 comprises a protrusion 52, on which protrusion 52 the sealing element 16 equipped with barbs 54 is clamped (/ clamped). On the other hand, in the exemplary embodiment of fig. 6, the clamping ring 18 comprises a thickening 56 with a groove 58, into which groove 58 an extension 60 of the sealing element engages, which extension 60 is also equipped with a barb 54. In addition, an attachment element 50 is provided that attaches the sealing element 16 to the gripper ring 18 such that they rotate together. Of course, the sealing element 16 can also be screwed onto the clamping ring 18 only by means of screws 50, as depicted in fig. 7, for example.

The rolling element bearing assembly as depicted in fig. 1 to 7 is particularly advantageous in that the inner ring is configured to be fixed (/ stationary) and the outer ring is configured to be rotating, but it may also be used with a fixed outer ring and a rotating inner ring.

In summary, with the proposed rolling element bearing assembly, it is possible to provide a large rolling element bearing assembly having a diameter of more than one meter, which can both reduce weight and improve sealing performance. The combination of FRP material (in particular FRP material compression molded from fibre composite board) and the sealing element extending in axial direction may achieve an optimal axial sealing, since due to the FRP seal carrier the distance between the seal carrier and the end surface of the inner ring may be set particularly accurately.