Bearing sealing member, bearing sealing assembly, and bearing assembly

Abstract

The present disclosure relates to a bearing sealing member, a bearing sealing assembly, and a bearing assembly. The bearing sealing assembly comprises: a frame, a radial outer end face of the frame being provided with a wave recess extending in a circumferential direction; a sealing body, the sealing body being attached to an outer wall of the frame; and a felt material, the felt material being filled in the wave recess of the frame and protruding out of a wave crest of the wave recess in the radial direction. The felt material allows gas to pass through and can prevent ingress of water and pollutants. A radial outer wave structure of a sealing head is filled and covered with the felt material, and the felt has good air permeability and waterproofness. This means that, while moisture and pollutants are prevented from entering the bearing, an appropriate amount of gas exchange between the interior of the bearing and the external environment is permitted, thereby effectively eliminating a possible vacuum state in a bearing cavity during a temperature change process, maintaining a pressure balance between the inner air and the outer air of the bearing, relieving abrasion of a sealing lip, and prolonging the service life of the sealing assembly.

Description

Bearing seal, bearing seal assembly, and bearing assembly TECHNICAL FIELD

[0001] The present application relates to the technical field of automobile hub bearing sealing, and particularly relates to a bearing seal, a bearing seal assembly and a bearing assembly. BACKGROUND

[0002] Two sides of the tapered roller bearing are respectively provided with a box type sealing assembly and an oil sealing assembly to ensure the reliability of operation. As shown in FIG. 1, two different sealing assemblies are respectively assembled on the two sides of the bearing: one side is a box type sealing assembly, and the other side is an oil sealing assembly, both of which belong to dynamic sealing. In addition to containing a framework and a sealing body, the box type sealing assembly is additionally provided with a slinger structure. The two sealing assemblies are both installed between the inner and outer rings of the bearing by means of interference fit to ensure tight connection and effective sealing. The main function of the box type sealing is to prevent impurities, moisture and other pollutants in the external environment from entering the bearing interior, thereby protecting the bearing from the influence of the external harsh conditions. The oil sealing assembly is used to prevent transmission oil from entering the bearing interior. Therefore, in order to achieve high sealing effect, the sealing lips of both the oil sealing assembly and the box type sealing assembly are arranged to be inclined away from the axial outer side of the bearing.

[0003] However, in actual operation, when the tapered roller bearing experiences long-time high-speed rotation or is affected by high temperature generated by the braking system, the air inside the bearing cavity 500 is expanded due to heat, which causes the pressure in the bearing cavity 500 to suddenly increase, as shown in FIG. 2. Under the condition of pressure rise, part of the air in the bearing cavity is forced to be extruded to the outside. However, after the temperature of the bearing decreases and cools down, the air extruded from the bearing cavity cannot be replenished due to the fact that the outwardly inclined sealing lips tightly block the passage between the bearing cavity and the external environment, thereby causing the formation of a nearly vacuum state inside the bearing cavity. The vacuum state caused by the imbalance between the internal atmosphere of the bearing and the external atmosphere will continuously exert a negative pressure on the sealing lips, thereby accelerating the wear rate of the sealing lips, which will seriously affect the sealing performance and service life of the bearing.

[0004] Therefore, it is of great importance to seek effective solutions to maintain the pressure balance between the bearing cavity and the external environment and prevent the formation of a vacuum state inside the bearing cavity, so as to improve the stability and durability of the bearing sealing system.

[0005] SUMMARY

[0006] To overcome the problems in the related art, the present application provides a bearing seal, a bearing seal assembly and a bearing assembly.

[0007] According to a first aspect of embodiments of the present disclosure, the present disclosure provides a bearing seal, comprising: a skeleton, a radial end face of the skeleton being provided with a wave surface extending in a circumferential direction, the wave surface comprising at least one valley and a peak; a sealing body attached to an outer wall of the skeleton; a felt material covering at least the valley of the skeleton and protruding radially R from the peak, the felt material allowing gas to pass through.

[0008] In some embodiments, the felt material filled and covered in adjacent valleys is separated by the peaks, so that the felt material is discontinuous in the circumferential direction.

[0009] In some embodiments, the felt material is pasted in the valley.

[0010] In some embodiments, the skeleton comprises an axial portion, and the axial portion is wavy in the circumferential direction and forms a valley at both a radially outer end face and a radially inner end face of the axial portion.

[0011] In some embodiments, the axial portion covering the felt material is used for interference fit with other elements.

[0012] In some embodiments, the skeleton further comprises a radial portion, a transition region is formed between the radial portion and the axial portion, the sealing body comprises a sealing head attached to the transition region, wherein a radially outer side face of the sealing head forms a wave structure of the same shape as the valley of the skeleton, and the felt material fills and radially protrudes from the wave structure.

[0013] In some embodiments, a chamfer portion is provided at the transition region between the radial portion and the axial portion of the skeleton, and the sealing head is attached to the chamfer portion.

[0014] In some embodiments, the total width of the axial portion of the skeleton and the sealing head in the axial direction is greater than the axial width of the felt material.

[0015] According to a second aspect of embodiments of the present disclosure, the present disclosure provides a bearing seal assembly, comprising the bearing seal according to the first aspect; wherein the bearing seal assembly is a cartridge seal assembly or an oil seal assembly.

[0016] In some embodiments, the cartridge seal assembly further comprises a slinger.

[0017] In some embodiments, the seal body further comprises: a main seal lip located radially inside the skeleton and axially outside the skeleton; a dust lip located radially inside the skeleton and axially inside the skeleton, the main seal lip and the dust lip are both inclined towards the axial outside and the radial inside of the skeleton; a centrifugal lip located axially outside the skeleton and radially outside the main seal lip, the centrifugal lip is inclined towards the axial outside and the radial outside of the skeleton and abuts against the oil slinger.

[0018] In some embodiments, the bearing seal assembly further comprises a spring, the spring is sleeved radially outside the main seal lip and compresses the main seal lip radially.

[0019] According to a third aspect of the embodiments of the present disclosure, the present disclosure provides a bearing assembly, comprising: an inner ring; an outer ring; a roller located between the inner ring and the outer ring; two bearing seal assemblies as described in the second aspect, respectively located axially inside and axially outside the roller, and the two bearing seal assemblies form a bearing cavity with the inner ring and the outer ring, wherein the skeleton and the felt material in the wave valleys of the bearing seal assembly are in interference fit with the outer ring to form a torsion-resistant connection, and the felt material allows external gas to enter the bearing cavity.

[0020] In some embodiments, the bearing seal assembly located axially outside the roller is a cartridge seal assembly, and the bearing seal assembly located axially inside the double-row tapered roller is an oil seal assembly or a cartridge seal assembly.

[0021] The technical solutions provided by the embodiments of the present disclosure can have the following beneficial effects: the radial end face of the skeleton is provided with a circumferentially extending wavy surface, and the wave valleys are covered with felt material. Since the felt has good air permeability and water resistance, it can prevent mud and contaminants from entering the bearing while allowing the inside of the bearing cavity to exchange a proper amount of gas with the external environment, effectively eliminating the vacuum state that may be formed in the bearing cavity during temperature changes, maintaining the balance of air pressure inside and outside the bearing, thereby slowing down the wear of the seal lip and prolonging the service life of the seal assembly. BRIEF DESCRIPTION OF DRAWINGS

[0022] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the present disclosure and serve to explain the principles of the present disclosure together with the specification.

[0023] FIG. 1 is a sectional view of an automobile hub bearing in the related art;

[0024] FIG. 2 is a schematic view of air being squeezed out of the bearing cavity of an automobile hub bearing in the related art;

[0025] FIG. 3 is a cross-sectional view of a cartridge seal assembly for an automotive hub bearing, according to an example embodiment;

[0026] FIG. 4 is a side view of a cartridge seal assembly for an automotive hub bearing, according to an example embodiment;

[0027] FIG. 5 is a perspective view of a cartridge seal assembly for an automotive hub bearing, according to an example embodiment. DETAILED DESCRIPTION

[0028] The example embodiments will be described in detail herein with reference to the accompanying drawings. In the following description, like reference numerals refer to like elements, unless the context clearly dictates otherwise. The implementations described in the following example embodiments are not meant to represent all implementations consistent with the present disclosure. Rather, they are simply examples of apparatuses and methods consistent with some aspects of the present disclosure as detailed in the appended claims.

[0029] To solve the above technical problems, the present disclosure provides a bearing seal assembly 100, the overall shape of the bearing seal assembly 100 of the present disclosure is annular. Unless otherwise specified, the axial direction A, the radial direction R and the circumferential direction W described in the following detailed description are the axial direction A, the radial direction R and the circumferential direction W of the tapered roller bearing assembly, respectively. In addition, in the following detailed description, the axial outer side of the tapered roller bearing assembly is the left side of FIGS. 1 and 2, and the axial inner side of the tapered roller bearing assembly is the right side of FIGS. 1 and 2; the axial outer side of the cartridge seal assembly 101 is the right side in FIG. 3, and the axial inner side of the cartridge seal assembly 101 is the left side in FIG. 3; the radial outer side is the upper side of FIG. 3, and the radial inner side is the lower side of FIG. 3.

[0030] The bearing seal assembly 100 of the present disclosure can be applied in a bearing assembly, and in particular, can be applied in a tapered roller bearing assembly at an automotive hub, which has a high protection requirement for resisting the intrusion of external contaminants, mud, etc. and preventing grease leakage.

[0031] The tapered roller bearing assembly of the present disclosure can include an inner ring 200, an outer ring 300, a roller 400, and a bearing seal assembly 100, the roller 400 being located between the inner ring 200 and the outer ring 300 to enable relative rotation between the inner ring 200 and the outer ring 300, wherein the roller 400 can be a double-row tapered roller 400. Two bearing seal assemblies 100 are respectively located on the axial inner side and the axial outer side of the double-row tapered roller 400, and form a bearing cavity 500 with the inner ring 200 and the outer ring 300, so that the bearing seal assembly 100 can be a cartridge seal assembly 101 or an oil seal assembly 102.

[0032] In some embodiments, the bearing seal assembly 100 located axially outward of the double row tapered roller 400 is a cartridge seal assembly 101, which is used to prevent contaminants, mud, etc. from the outside environment of the automobile wheel from entering the inside of the bearing, thereby effectively protecting the double row tapered roller 400 bearing from erosion damage. The bearing seal assembly 100 located axially inward of the double row tapered roller 400 is an oil seal assembly 102 or a cartridge seal assembly 101. The cartridge seal assembly 101 or the oil seal assembly 102 located axially inward can be used to prevent grease in the bearing cavity 500 from overflowing, ensuring the stability of the bearing lubrication system and the normal operation of the bearing.

[0033] The bearing seal assembly 100 provided by the present disclosure will be described taking the cartridge seal assembly 101 as an example.

[0034] As shown in FIG. 3, the cartridge seal assembly 101 includes a skeleton 10, a slinger 20, and a seal body 30. The skeleton 10 is used to be torsionally connected with the outer ring 300 of the bearing, and the skeleton 10 is made of metal material, which ensures the stability and sealing performance during rotation of the bearing. The slinger 20 is used to be torsionally connected with the inner ring 200 of the bearing, and the slinger 20 is made of stainless steel material, which is beneficial to rust prevention. The seal body 30 is firmly attached and fixed to the skeleton 10 through a vulcanization process. The surface of the skeleton 10 is usually treated by phosphating, so that the seal body 30 can be better combined during vulcanization. The radially inner side of the seal body 30 forms a dynamic sealing abutment with the slinger 20. The oil seal assembly 102 does not have a slinger 20, so in the oil seal assembly 102, the radially inner side of the seal body 30 directly forms a dynamic sealing abutment with the inner ring 200 of the bearing.

[0035] Further, the skeleton 10 includes an axial portion 11 and a radial portion 12, and a wave-shaped surface extending along the circumferential direction W is arranged on the radially outer end surface of the axial portion 11 of the skeleton 10. The wave-shaped surface is a structure continuously distributed along the circumferential direction W, and includes at least one wave trough 13 and a wave crest 131. The cartridge seal assembly 101 further includes a felt material 40, which is located in and covers at least the wave trough 13 of the skeleton 10, and protrudes radially R from the wave crest 131 of the wave-shaped surface. The felt material 40 not only allows gas to pass through, but also prevents contaminants or mud from passing through.

[0036] When the cartridge seal assembly 101 is installed in the double-row tapered roller 400 bearing, the felt material 40 protruding radially from the wave crest 131 of the wave surface can also form a stable torsion-resistant connection with the outer ring 300 of the bearing, thereby ensuring that the felt material 40 does not easily fall off the wave trough 13 during the operation of the bearing. Since the felt material 40 has good air permeability and water resistance, it allows the inside of the bearing cavity 500 to exchange a proper amount of gas with the external environment while preventing mud and contaminants from entering the bearing cavity 500, effectively eliminating the vacuum state that may be formed in the bearing cavity 500 chamber during temperature changes, maintaining the balance of air pressure inside and outside the bearing cavity 500, thereby slowing down the wear of the sealing lip and prolonging the service life of the bearing seal assembly 100.

[0037] In this embodiment, the axial portion 11 of the skeleton 10 is designed as a wave surface on its radially outer side, as shown in FIG. 4. Since the wave crest 131 of the wave surface presents a smooth arc line, when the skeleton 10 is torsionally connected with the bearing outer ring 300, the arc-shaped wave crest 131 can minimize the scratching of the inner surface of the bearing outer ring 300, while enhancing its own structural strength and reducing the risk of breakage. The wave surface can not only achieve stable torsion-resistant fixation with the bearing outer ring 300, but also provide space for the felt material 40 to store the felt material 40, thereby allowing gas to freely enter and exit.

[0038] Further, as shown in FIGS. 4 and 5, the adjacent wave troughs 13 filled and covered with felt material 40 are separated from each other in the circumferential direction W by the wave crest 131 of the wave surface itself, so that the felt material 40 appears in a discontinuous state in the circumferential direction W. It can be seen that the felt material 40 does not extend and cover the wave crest 131 of the wave surface in the circumferential direction W, which allows the wave crest 131 to directly abut against the bearing outer ring 300 and form a strong torsion-resistant connection with the outer ring 300, thereby enhancing the stability and sealing effect of the bearing seal assembly 100.

[0039] Considering the torsion-resistant connection between the wave crest 131 and the bearing outer ring 300, if the felt material 40 is completely covered on the wave crest 131, it may cause the felt material 40 to be excessively extruded in the axial direction during assembly, thereby causing the felt material 40 in the wave trough 13 to be separated from the wave trough 13. To avoid this phenomenon, the felt material 40 is designed to be in a separate and independent state in the circumferential direction W, to ensure that the felt material 40 is stably combined with the wave trough 13 during assembly, while not hindering the torsion-resistant connection of the wave crest 131 of the skeleton 10 with the outer ring 300.

[0040] In other embodiments, the radially outer end surface of the axial portion 11 of the skeleton 10 can also adopt a rectangular groove, a trapezoidal groove, or the like, all of which are designed to ensure that the skeleton 10 can be stably and torsionally connected with the bearing outer ring 300 while also forming a groove that accommodates and fixes the waterproof and breathable felt material 40. In this way, the gas in the external environment can smoothly pass through the felt material 40 into the bearing cavity 500, thereby effectively maintaining the air pressure balance between the inside and outside of the bearing cavity 500.

[0041] In some embodiments, the radially inner end surface of the axial portion 11 of the skeleton 10 can be a circular smooth curve, and only the radially outer end surface of the axial portion 11 forms a wavy surface structure, which can be formed by stamping or by machining the radially outer end surface of the axial portion 11 of the skeleton 10. In the embodiments of the present disclosure, as shown in FIG. 4, the axial portion 11 of the skeleton 10 presents a wavy curved shape in the circumferential direction W, i.e., both the radially outer end surface and the radially inner end surface of the axial portion 11 of the skeleton 10 include a wavy surface structure. Such a structure makes the axial portion 11 of the skeleton 10 easier to produce and manufacture.

[0042] Further, as shown in FIG. 3, in the cartridge seal assembly 101, the seal body 30 can include a seal head 31, a main seal lip 32, a dust lip 33, and a centrifugal lip 34. The seal head 31 is located at the transition area between the radial portion 12 and the axial portion 11 of the skeleton 10, and the seal head 31 can be flush with the axial portion 11 of the skeleton 10 and at the same time be torsionally connected with the bearing outer ring 300. The oil seal assembly 102 can not include the centrifugal lip 34.

[0043] In addition, the radially outer side surface of the seal head 31 also forms a wavy structure that is the same shape as the wavy surface of the skeleton 10, and the wavy structure is also filled and covered with the felt material 40, and the felt material 40 also radially protrudes from the wave crest of the wavy structure of the seal head 31. The seal head 31 not only enhances the sealing performance at the radially outer side of the skeleton 10, but also lengthens the length of the skeleton 10 in the axial direction A, thereby increasing the axial length of the felt material 40, and the felt material 40 with the lengthened axial direction A can more effectively prevent contaminants and mud from the external environment from entering the bearing interior without hindering the normal flow of gas, thereby improving the protection capability and service life of the bearing seal assembly 100.

[0044] In some embodiments, a chamfered portion 14 is provided between the radial portion 12 and the axial portion 11 of the skeleton 10, and the sealing head 31 is attached to the chamfered portion 14, which provides a location for the attachment of the sealing head 31. As shown in FIG. 3, the presence of the chamfered portion 14 significantly increases the attachment area of the sealing head 31 on the skeleton 10, so that the sealing head 31 can be more firmly attached to the skeleton 10, enhancing the stability and connection strength of the sealing assembly at the radial outside.

[0045] In some embodiments, as shown in FIGS. 3 and 5, the total width of the axial portion 11 of the skeleton 10 and the sealing head 31 in the axial direction can be greater than or equal to the axial width of the felt material 40.

[0046] The felt material 40 can be better supported in the axial direction A, preventing unnecessary bending deformation of the felt material 40 when subjected to radial and axial stresses, because if the felt material 40 is bent, it is easy to accumulate contaminants or mud from the external environment at the bending portion, which is not conducive to the air permeability of the felt material 40, and may even cause the internal bearing cavity 500 to fail to perform normal gas exchange, resulting in a loss of air pressure balance. Therefore, the total width of the axial portion 11 of the skeleton 10 and the sealing head 31 in the axial direction is greater than the axial width of the felt material 40, which can effectively prevent the felt material 40 from losing its water resistance and air permeability due to excessive bending.

[0047] Further, as shown in FIG. 3, the dust lip 33 and the main sealing lip 32 are located on the radial inside of the radial portion 12 of the skeleton 10, wherein the main sealing lip 32 is located on the axial outside of the skeleton 10, and the dust lip 33 is located on the axial inside of the skeleton 10, but both the main sealing lip 32 and the dust lip 33 are inclined towards the axial outside and the radial inside of the skeleton 10. On the one hand, the main sealing lip 32 and the dust lip 33 can allow the gas in the bearing cavity 500 to be discharged outward along the inclined surface of the lip, effectively preventing the risk of explosion of the bearing due to excessive internal pressure of the bearing cavity 500 caused by temperature rise during operation, thereby maintaining the air pressure balance inside and outside the bearing cavity 500 and ensuring stable operation of the bearing in a suitable environment. On the other hand, due to the design of the inclined angle of the lip, even in the face of high-speed splashing water droplets or contaminants, most of the contaminants can be effectively blocked from entering the bearing cavity 500, greatly improving the sealing performance and service life of the bearing.

[0048] Further, the main sealing lip 32 can form a larger interference fit with the axial portion of the oil thrower 20, so that the main sealing lip 32 and the oil thrower 20 form a larger contact area in the circumferential direction W. The larger contact area not only allows the main sealing lip 32 and the oil thrower 20 to fit tightly, thereby effectively preventing contaminants, moisture and other harmful substances from the outside from entering the inside of the bearing, ensuring the cleanliness and stability of the bearing operation.

[0049] Further, the centrifugal lip 34 is located axially outside the radial portion 12 of the skeleton 10 and radially outside the main sealing lip 32, and the centrifugal lip 34 is inclined towards the axial and radial outside of the skeleton 10 and in interference abuts with the radial portion of the oil slinger 20. Further, a storage groove is formed between the main sealing lip 32 and the centrifugal lip 34, and the storage groove has an inclination angle towards the radial and axial outside of the skeleton 10. When the contaminants or impurities such as mud contact the bearing, the impurities are temporarily stored in the storage groove. In the high-speed rotating state of the bearing, the impurities in the storage groove are effectively thrown out of the storage groove under the driving of the centrifugal force, so as to prevent the contaminants from staying for a long time, and further improve the sealing performance and service life of the bearing.

[0050] In some embodiments, the bearing sealing assembly 100 further comprises a spring 50, which is sleeved on the radial outside of the main sealing lip 32 and tightly compacts the main sealing lip 32 by radial force. In the cartridge sealing assembly 101, the spring 50 is used to press the contact between the main sealing lip 32 and the oil slinger 20, and in the oil sealing assembly 102, the spring 50 directly presses the main sealing lip 32 against the bearing inner ring 200 to achieve effective sealing effect. The spring 50 can be formed of metal / alloy, etc. In one example, the radial outside of the main sealing lip 32 can also be provided with a groove, and the spring 50 is clamped in the groove on the radial outside of the main sealing lip 32 to prevent the spring 50 from slipping off.

[0051] Based on the same inventive concept, the present disclosure also provides a bearing assembly, wherein the specific ways of realizing the functions in the bearing assembly have been described in detail in the specific embodiments of the bearing sealing assembly 100, and will not be described in detail here.

[0052] It can be understood that “multiple” in the present disclosure refers to two or more, and other quantifiers are similar. “And / or” describes the association relationship of the associated objects, which means that there can be three relationships, for example, A and / or B can represent three cases of A alone, A and B together, and B alone. The character “ / ” generally represents that the front and rear associated objects have an “or” relationship. The singular form of “one” and “the” also aims to include the plural form, unless the context clearly indicates otherwise.

[0053] It can be further understood that the terms “first”, “second”, etc. are used to describe various structures, but these structures should not be limited to these terms. These terms are only used to distinguish the same type of structures from each other, and do not represent a specific order or importance. In fact, the expressions of “first”, “second”, etc. can be completely interchangeable. For example, without departing from the scope of the present disclosure, the first structure can also be referred to as the second structure, and similarly, the second structure can also be referred to as the first structure.

[0054] It will be further understood that the terms "upper", "lower", "left", "right", "top", "bottom", "inside", "outside", and the like, used in this context, depend on the orientation of the apparatus or element being referred to and are used for convenience in referring to the accompanying drawings. They are not intended to refer to an absolute position or orientation.

[0055] Other embodiments of the present disclosure will be apparent to those skilled in the art from consideration of the specification and practice of the application disclosed herein. It is intended that the present disclosure cover any and all variations of the present disclosure including those variations contained within the scope of the present disclosure, as well as those adaptations resulting from the exercise of the skills of those skilled in the art, using no more than the common general knowledge and the techniques disclosed in the present disclosure. The specification and examples are to be considered exemplary only, with the true scope and spirit of the present disclosure being indicated by the following claims.

[0056] It is to be understood that the present disclosure is not limited to the precise construction described and as shown in the accompanying drawings, and that various modifications and changes can be made by those skilled in the art without departing from the scope of the present disclosure. The scope of the present disclosure is limited only by the claims that follow.

Claims

1. A bearing seal, characterized by, Comprising: a skeleton (10), a radial end face of the skeleton (10) is provided with a wave surface extending in the circumferential direction (W), the wave surface comprises at least one wave trough (13) and wave crest (131); a sealing body (30) attached to the outer wall of the skeleton (10); a felt material (40) covering at least the wave trough (13) of the skeleton (10) and protruding radially (R) from the wave crest (131), the felt material (40) allows gas to pass through.

2. The bearing seal according to claim 1, wherein: the felt material (40) filled and covered in the adjacent wave trough (13) is separated by the wave crest (131), so that the felt material (40) is discontinuous in the circumferential direction.

3. The bearing seal according to claim 1, wherein: the felt material (40) is pasted in the wave trough (13).

4. The bearing seal according to claim 1, wherein: the skeleton (10) comprises an axial portion (11), and the axial portion (11) is wavy curved in the circumferential direction (W), and the wave trough (13) is formed on both the radially outer end face and the radially inner end face of the axial portion (11).

5. The bearing seal according to claim 4, wherein: the axial portion (11) covering the felt material (40) is used for interference fit with other components.

6. The bearing seal according to claim 4, wherein: the skeleton (10) further comprises a radial portion (12), and the radial portion (12) and the axial portion (11) form a transition area, the sealing body (30) comprises a sealing head (31) attached to the transition area, wherein the radially outer side face of the sealing head (31) forms a wave structure with the same shape as the wave trough (13) of the skeleton (10), and the felt material (40) fills and protrudes radially (R) from the wave structure.

7. The bearing seal according to claim 6, wherein: the transition area between the radial portion (12) and the axial portion (11) of the skeleton (10) is provided with a chamfer portion (14), and the sealing head (31) is attached to the chamfer portion (14).

8. The bearing seal according to claim 6, wherein: the total width of the axial portion (11) of the skeleton (10) and the sealing head (31) in the axial direction is greater than the axial width of the felt material (40).

9. A bearing seal assembly (100), comprising: the bearing seal according to any one of claims 1 to 8; wherein the bearing seal assembly (100) is a cartridge seal assembly (101) or an oil seal assembly (102).

10. The bearing seal assembly (100) according to claim 9, wherein: the cartridge seal assembly (101) further comprises a slinger (20).

11. The bearing seal assembly (100) according to claim 10, wherein: The sealing body (30) further comprises: a main sealing lip (32) located radially inside and axially outside the skeleton (10); a dirt lip (33) located radially inside and axially inside the skeleton (10), the main sealing lip (32) and the dirt lip (33) both being inclined towards the axial outside and the radial inside of the skeleton (10); a centrifugal lip (34) located axially outside and radially outside the main sealing lip (32), the centrifugal lip (34) being inclined towards the axial outside and the radial outside of the skeleton (10) and abutting against the oil thrower (20).

12. The bearing sealing assembly (100) according to claim 11, wherein, the bearing sealing assembly (100) further comprises a spring (50) sleeved radially outside the main sealing lip (32) to press the main sealing lip (32) radially.

13. A bearing assembly characterized by, comprises: an inner ring (200); an outer ring (300); rollers (400) located between the inner ring (200) and the outer ring (300); two bearing sealing assemblies (100) according to any one of claims 9 to 12 located axially inside and axially outside the rollers (400) respectively, and the two bearing sealing assemblies (100) and the inner ring (200) and the outer ring (300) form a bearing cavity (500), wherein the skeleton (10) and the felt material (40) in the trough (13) of the bearing sealing assembly (100) are in interference fit with the outer ring (300) to form a torsion-resistant connection, and the felt material (40) allows external gas to enter the bearing cavity (500).

14. The bearing assembly according to claim 13, wherein, the bearing sealing assembly (100) located axially outside the rollers (400) is a cartridge sealing assembly (101), and the bearing sealing assembly (100) located axially inside the rollers (400) is an oil seal assembly (102) or a cartridge sealing assembly (101).

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