DE102013206349B4 - seal and bearing - Google Patents

Abstract

A seal (210) for a bearing (100) comprising a first (120) and a second bearing ring (140), comprising:an elastomeric structure (220); anda reinforcement structure (290) connected to the elastomeric structure (220) and configured to be attachable to a first race (120) of the bearing (100);wherein the seal (210) is configured to at least partially Seal volume (230) between the first (120) and the second bearing ring (140) with respect to a medium;wherein the seal (210) is designed in such a way that the medium cannot pass through the seal (210);wherein the elastomer structure (220) is designed in such a way that it reacts to a change in pressure on one side of the elastomeric structure (220) with a change in shape without essentially changing the sealing effect during the change in shape; wherein the seal (210) is designed to engage with a first bearing ring (120) of the Bearing (100) to be connected; wherein the seal (210) is further formed so that it with respect to a different from the first bearing ring (120) second bearing ring (140) without contact i st;wherein the elastomeric structure (220) comprises a membrane area (240) and a connecting area (330);wherein the connecting area (330) is arranged between the reinforcement structure (290) and the membrane area (240) and is designed in such a way that the change in shape of the elastomeric structure (220) is caused at least in part by deformation of the connection region (330); andwherein the reinforcement structure (290) has a conical section (310) which is arranged at a central recess (320) of the reinforcement structure (290) and which extends axially towards a section (280) of a base body (160) of the second bearing ring , and the elastomeric structure (220) is attached to the conical portion (310).

Description

Exemplary embodiments relate to a seal and a bearing.

In many areas of machine, plant and vehicle construction, the challenge that arises when guiding rotary movements is that the bearing used for this is filled with a lubricant or a lubricant that should not be released into the environment. At the same time, the bearing or its lubricant should not be contaminated by environmental influences. For this purpose, a seal is often used in the corresponding bearings, which is intended to prevent both the discharge of the lubricant and the entry of contamination, for example water, dust or other dirt particles.

In many cases, this challenge is made more difficult by the fact that the bearing in question is exposed to very different temperatures, which can occur due to environmental factors, for example, but also due to operational factors. As a result of such a temperature change, a volume of a gas, for example the air, which is enclosed in the bearing, can expand or contract to such an extent that pressure equalization with the environment takes place via the seal. If the temperature rises, lubricant can get into the environment through a seal that opens, at least for a short time, while if the temperature drops sharply, contamination can also be carried along with a gas (e.g. air) flowing into the interior of the bearing from the environment can become.

Conventionally, this behavior is constructively counteracted by minimizing the internal volume of the bearing. Depending on the specific application, however, such a reduction in the free volume of the bearing may not solve the problem described above. For example, even if the volume of gas in question is minimized, the bearing can heat up to such an extent that gas can escape or enter and thus possibly cause lubricant to escape or contamination to enter. It may also be difficult to reduce the relevant free volume of the bearing in terms of design.

the US 3,149,883A refers to a protective cover for a hub. the US 3,642,327A refers to bearing seals while the U.S. 7,185,955 B2 to a visible indicator of a pressurized hub, the DE 11 2009 002 661 T5 on a wheel bearing device with integrated wheel speed detection device, the US 5,172,984A on a vent end cap for a vehicle wheel bearing and the U.S. 8,157,657 B2 refer to a selectively inflatable and contractible barrier.

The aforementioned challenges can arise not only with changing temperatures, but also with other changes in operating or environmental conditions, for example in the form of pressures.

There is therefore a need to improve sealing behavior of a seal under different conditions.

A seal according to patent claim 1 and a bearing according to patent claim 6 take this requirement into account.

A seal according to an exemplary embodiment for a bearing comprising first and second bearing rings has an elastomeric structure, the seal being configured to at least partially seal a volume between the first and second bearing rings with respect to a medium. The seal is designed in such a way that the medium cannot pass through the seal. The elastomeric structure is further configured to respond to a change in pressure on one side of the elastomeric structure by deforming without substantially causing or permitting a change in sealing performance during the deforming.

A seal according to one embodiment is based on the finding that by providing the elastomer structure, which reacts to a pressure change on one side with a corresponding change in shape, without a change in the sealing effect, for example by reducing the pressure difference between the environment and the bearing interior, while the change in shape occurs, the sealing behavior of such a seal can also be improved under different environmental conditions. For example, at different temperatures and/or different pressures, the use of a seal according to an exemplary embodiment can improve its sealing behavior. The elastomer structure is thus designed in such a way that it makes it possible to at least partially compensate for a change in pressure by means of a corresponding change in shape. A change in the sealing effect, for example a brief collapse of the same, can thus be avoided if necessary by the ability of the elastomer structure to bring about a corresponding change in shape.

The seal is designed to be connected to a first bearing ring of the bearing. The seal is also designed so that it is non-contact with respect to a second bearing ring that is different from the first bearing ring. In this way it may be possible to reduce, if not completely avoid, friction between the seal and the second bearing ring. Wear of the seal and, alternatively or additionally, also friction caused by an interaction of the seal with the second bearing ring can thereby be reduced, possibly even completely avoided. As a result, any temperature development between the seal and the second bearing ring due to friction existing between them can be reduced or avoided.

In a seal according to an exemplary embodiment, the elastomeric structure may comprise a membrane region which is configured in such a way as to allow the elastomeric structure to be deformed at least in part by deflection of the membrane region. In this way, if necessary, a corresponding pressure equalization can already be created by structurally simple means, in which case the membrane area can, for example, cover or bridge a recess in a reinforcement structure of the seal.

The seal further includes a reinforcing structure connected to the elastomeric structure and configured to be attachable to a first race of the bearing. As a result, a mechanically reliable and mechanically stable connection of the seal to the first bearing ring can be created if necessary. Likewise, z. B. the aforementioned membrane area of the elastomeric structure cover or bridge a recess in the reinforcement structure.

The elastomer structure comprises a membrane area and a connection area, the connection area being arranged between the reinforcement structure and the membrane area and being designed in such a way that the change in shape of the elastomer structure is caused at least partially by a deformation of the connection area. In addition or as an alternative to a deformation of the membrane area itself, the connection area between the elastomer structure and the membrane area can also contribute to the change in shape and thus to the pressure equalization. The connection area can be designed, for example, in a wavy, folded, S-shaped manner or in some other way, so that it enables the elastomer structure to be deformed easily.

In such a seal according to an exemplary embodiment, the connecting area can be designed in such a way as to enable the change in shape of the elastomeric structure at least partially by a movement of the membrane area along an axial direction of the bearing. The axial direction of the bearing can, for example, correspond to an axis of symmetry of the seal, ie coincide with it or run parallel to it.

For example, a seal according to an exemplary embodiment can be designed to be rotationally symmetrical. A component can have an n-fold rotational symmetry, for example, where n is a natural number greater than or equal to 2. An n-fold rotational symmetry is present if the component in question can be rotated by (360°/n) around an axis of rotation or symmetry, for example, and essentially merges into itself in terms of shape, i.e. with a corresponding rotation essentially onto itself mathematical sense is mapped. In contrast to this, in the case of a completely rotationally symmetrical configuration of a component, with any rotation by any angle about the axis of rotation or symmetry, the component essentially transforms into itself in terms of shape, i.e. is essentially mapped onto itself in the mathematical sense. Both an n-fold rotational symmetry and a complete rotational symmetry are referred to here as rotational symmetry.

In a seal according to an exemplary embodiment, which comprises a reinforcement structure, the reinforcement structure can comprise a bearing area which is designed to be placed on the first bearing ring in such a way that the bearing area statically seals the seal with respect to the first bearing ring. As a result, a sealing effect of the seal can optionally be improved.

The contact area of the reinforcement structure can be subjected to a smoothing process, for example, so that it can develop a corresponding static sealing effect with a mating surface that may be ground or turned.

In such a seal according to an exemplary embodiment, the contact area can have an elastomer at least partially on a side facing the first bearing ring. As a result, it may be possible to further increase the sealing effect of the contact area for the static sealing of the seal relative to the first bearing ring.

A bearing according to an embodiment includes an inner ring and an outer ring and a seal according to an embodiment, which is connected to the outer ring and is non-contact with respect to the inner ring. Such a bearing according to an exemplary embodiment can also have a contacting further seal which is arranged on a side facing away from the seal between the inner ring and the outer ring. The inner ring can be designed in such a way that it forms an essentially closed volume together with the seal, the further seal and the outer ring. The seal and the further seal can be designed in such a way that the seal enables such a change in shape that even with a pressure change, for example due to heating or cooling, of a gas in the volume during operation of the bearing, the further seal inner ring and the outer ring are always in contact. As a result, it may be possible to prevent a lubricant from escaping and/or contamination from entering through the further seal during subsequent cooling down again.

To put it another way, the reinforcement structure and thus, if necessary, the seal can be designed in the form of a cap. For example, the first bearing ring can be the outer ring of the bearing and the second bearing ring can be the inner ring of the bearing.

In the case of exemplary embodiments of a bearing or a seal, the elastomeric structure can in principle be made of any elastomer suitable for the relevant operating conditions. For example, acrylonitrile butadiene rubber (NBR=nitrile butadiene rubber) can be used, as well as silicone rubber, fluorine rubber, ethylene propylene diene rubber (EPDM=ethylene propylene diene monomer). Optionally, the elastomeric structure may be fully or partially reinforced by a fabric, such as a polyester fabric, carbon fiber fabric, or other fabric to ensure the strength and/or mobility of the elastomeric structure. Depending on the specific implementation and design of such a seal, the seal can be designed for higher pressures, for example by a factor of 10, than those in which no fabric reinforcement is implemented, for example by using a corresponding fabric reinforcement. However, it may also be possible to use a thinner and therefore more sensitive membrane as a result of the fiber reinforcement.

The reinforcement structure can, for example, have been produced from a metal or an alloy, for example from a sheet-like workpiece, using a deep-drawing process. For example, it can be a workpiece made from sheet metal. Of course, it may also be advisable, if appropriate, to produce the reinforcement structure on the basis of a machining manufacturing process. In principle, another material can also be used for the reinforcement structure, for example a plastic that is optionally reinforced with fillers or fibers, for example. Depending on the specific implementation, duration of use and place of use, it may be advisable to implement an additional metal structure in order to improve the long-term stability of the seal, for example.

In the case of such a seal, the elastomer structure can, for example, be at least partially thin-walled. For example, the elastomer structure can have wall thicknesses of between 0.2 mm and 3 mm in the membrane area and/or in the connection area. In other exemplary embodiments, however, a wall thickness can also be at least 0.3 mm, at least 0.4 mm or at least 0.5 mm. Likewise, the wall thickness of the elastomer structure in the above-mentioned areas can be, for example, at most 2 mm, at most 1.5 mm or at most 1 mm.

Of course, the elastomer structure can also have different wall thicknesses or thicknesses in different areas. For example, a larger, but also a smaller thickness can be provided in the membrane area than in the possibly implemented connection area. A larger and/or smaller thickness can also be implemented in a further area of the elastomer structure, via which a corresponding connection to the first bearing ring is created, for example.

The elastomer structure and the reinforcement structure that may be implemented can in principle be connected to one another using a wide variety of connection techniques. For example, they can be connected to one another with the aid of a non-positive, positive and/or material connection. For example, the elastomeric structure can be connected to the connecting structure using a vulcanization process. Here, a non-positive or frictional connection comes about through static friction, a material connection through molecular or atomic interactions and forces and a form-fitting connection through a geometric connection of the respective connection partners. The static friction thus sets in particular a normal force compo between the two connection partners.

In an exemplary embodiment of a seal, the reinforcement structure can have a pot-like and/or ring-shaped structure, at least in sections, via which the connection to the first bearing ring can be created, for example. Likewise, the connection structure can have the aforementioned central recess, over which the elastomer structure can extend completely, for example. For example, the elastomer structure can have the membrane structure in the area of the recess, it being possible for the membrane area to be connected to the reinforcement structure via the optional connection area already mentioned.

The bearing according to an exemplary embodiment can be a roller bearing, for example, but it can also be a sliding bearing. Regardless of this, the bearing can be a radial bearing, for example. In the case of a rolling bearing, with regard to the question of the rolling element geometries, these can be, for example, spherical rolling elements, cylindrical rolling elements, roller-shaped rolling elements, needle-shaped rolling elements, barrel-shaped rolling elements or frustoconical rolling elements. In other words, it can be a ball bearing, a cylindrical roller bearing, a needle bearing or a tapered bearing. Of course, bearings according to an exemplary embodiment can be designed in one row or also in multiple rows, for example two rows, three rows or with a correspondingly higher number of rows, regardless of whether they are designed as roller bearings or plain bearings.

• 1 zeigt eine Querschnittsdarstellung durch ein Lager mit einer Dichtung gemäß einem Ausführungsbeispiel;
• 2 zeigt eine Querschnittsdarstellung durch ein weiteres Lager mit einer Dichtung gemäß einem Ausführungsbeispiel; und
• 3 zeigt eine Querschnittsdarstellung durch ein weiteres Lager mit einer Dichtung gemäß einem Ausführungsbeispiel.

Exemplary embodiments are described and explained in more detail below with reference to the attached figures.

• 1 shows a cross-sectional view through a bearing with a seal according to an embodiment;
• 2 shows a cross-sectional view through another bearing with a seal according to an embodiment; and
• 3 shows a cross-sectional view through another bearing with a seal according to an embodiment.

In the following description of the accompanying figures, which show exemplary embodiments, the same reference symbols denote the same or comparable components. Furthermore, summarizing reference symbols are used for components and objects that appear several times in an exemplary embodiment or in a drawing, but are described together with regard to one or more features. Components or objects that are described with the same or collective reference symbols can be identical with regard to individual, several or all features, for example their dimensions, but may also be different, unless something else is explicitly or implicitly stated in the description.

1 12 shows a cross-sectional illustration through a bearing 100 according to an exemplary embodiment which, as the following description will show, is more precisely a double-row angular contact ball bearing 110 . The bearing 100 has a first bearing ring 120 which is an outer ring 130 . The bearing 100 also includes a second bearing ring 140, which is an inner ring 150, which is designed in several parts in the exemplary embodiment shown here. Thus, the second bearing ring 140 here has a base body 160 on which a first raceway 170-1 is formed. The inner ring 150 further includes another body 180 on which a second raceway 170-2 is formed. The outer ring 130 correspondingly comprises a first mating track and a second mating track 190 - 1 , 190 - 2 , which are opposite the two tracks 170 of the inner ring 150 . To hold the additional body 180 , the base body 160 is beaded in order to create a form-fitting connection between the two parts of the inner ring 150 , ie the base body 160 and the additional body 180 .

The raceways 170 and the mating raceways 190 can be created, for example, in the case of a production of the base body 160, the further body 180 and the outer ring 130 from steel within the framework of grinding and optionally hardening the same. Between the raceways 170 and the corresponding mating raceways 190 are in the in 1 shown embodiment, spherical rolling elements 200 are arranged, which form the two rows of rolling elements of this bearing 100 .

In the exemplary embodiment shown here, the rolling bodies 200 of the bearing 100 are guided by two cages 205-1, 205-2 and kept at a distance. These are optional components that can also be designed as a common cage, for example. However, the implementation of such a cage can optionally also be omitted entirely.

Of course, in other exemplary embodiments of a bearing 100 according to one exemplary embodiment, other types of rolling bodies, for example roller-shaped, needle-shaped, cone-shaped truncated or cylindrical rolling elements are used. Depending on the specific implementation, it may be advisable in such a case to adapt the raceways 170 and the mating raceways 190 to the geometries of the rolling bodies 200 accordingly.

Of course, bearings 100 according to an exemplary embodiment can also be implemented with more or fewer than two rows. A bearing 100 according to an exemplary embodiment can also be implemented as a plain bearing. In such a case, the raceways 170 and the counter-raceways 190--regardless of their number--can be replaced by corresponding sliding surfaces. In summary, raceways 170, 190 and corresponding sliding surfaces are also referred to as functional surfaces of the relevant bearing rings 120, 140 or of the relevant bearing 100.

The bearing 100 further includes a seal 210 according to one embodiment, which in turn has an elastomeric structure 220 . In principle, the elastomer structure can be made of any material that is technically suitable for a seal in the relevant area of use. For example, the elastomer of the elastomer structure 220 can be acrylonitrile butadiene rubber (NBR=nitrile butadiene rubber), silicone rubber, fluorine rubber or ethylene propylene diene rubber (EPDM=ethylene propylene diene monomer). This can optionally be reinforced by a fabric or a fabric, the fabric being able to comprise, for example, a polyester fabric or another fibrous and woven material. For example, it can be carbon fiber or glass fiber fabric. In principle, other techniques for reinforcing the elastomeric structure 220 can also be used if necessary.

The seal 210 is designed in such a way that it at least partially seals a volume 230 between the first bearing ring 120 and the second bearing ring 140 with respect to a medium located in this volume 230 . The medium in question can be, for example, a lubricant or a lubricant, ie, for example, an oil, a grease or another material suitable for lubricating the rolling elements with respect to the raceways 170 , 190 . The terms “lubricant” and “lubricant” are used synonymously here.

As will be explained below, the seal 210 is designed in such a way that the medium, for example the lubricant, cannot pass through the seal 210 . Thus, the seal 210 is not a labyrinth or gap seal, in which it is fundamentally possible for the relevant medium to diffuse or pass through the gap or the labyrinth.

The elastomeric structure 220 is shaped and designed in such a way that it reacts with a change in shape when there is a pressure change on one side of the elastomeric structure 220, without there being any change in its sealing effect during the change in shape. It is therefore not a question of a contacting seal, where there is a risk that the sealing lip will lift off the corresponding counter-component if a very small change in shape should occur.

Thus, the seal 210 in the in 1 The exemplary embodiment shown has a membrane region 240 which is designed in such a way that the change in shape of the elastomer structure 220 is made possible by the membrane region 240 deflecting. The membrane area 240, as shown in 1 shown, for example, along an axial direction 250.

The volume 230 in which, for example, the two cages 205 and the rolling elements 200 are arranged in the bearing 100 shown here is thus delimited by the seal 210 and a further seal 260 . The further seal 260 represents a contacting seal with a corresponding sealing lip, which is in contact both with the first bearing ring 120 and with the second bearing ring 140, ie touches them. In the exemplary embodiment shown here, the further seal 260 is connected in a torque-proof manner to the first bearing ring 120 (outer ring 130), with a sealing lip of the further seal 260 being in contact with a corresponding sealing surface which is also formed on the base body 160. In other words, the sealing lip of the further seal 260 is in contact with the inner ring 150, ie the second bearing ring 140.

The fact that the elastomer structure 220 can now react by changing the shape of a change in pressure on one side of the elastomer structure 220 without its sealing effect changing in the process can improve the sealing behavior of the seal 260 even under different operating or environmental conditions, for example under different temperatures and/or pressures, may be achievable since a reduced pressure differential can minimize or prevent media exchange. Thus, the volume 230, which is sometimes also referred to as the inner volume, can be at least partially filled with a lubricant, for example. If, due to a change in the operating conditions - whether due to a change in an external influence or due to the operation of the bearing 100 - a Tem temperature rise or an external drop in pressure, a gas contained next to the medium (lubricant), for example air, can now increase in volume in volume 230 due to the change to such an extent that the change in shape of the elastomer structure 220 causes the sealing lip to lift and thus a brief collapse of the sealing effect of the further seal 260 can be suppressed or prevented. In this way, if the temperature of the bearing 100 rises, the lubricant can possibly be prevented from escaping. The same can also apply if, for example, an external pressure acting on the bearing 100 abruptly decreases.

If the temperature of the bearing 100 drops or falls, however, there is a risk that the gas in the volume 230 will contract in such a way that gas from the outside will flow through the further seal 260 into the bearing. This could be loaded with particles and other contaminants and thus contribute to damage to the bearing 100 or the lubricant it contains. Due to a corresponding temperature drop or a corresponding increase in external pressure, the sealing lip of the further seal 260 can lift off the corresponding sealing surface on the base body 160 at least briefly, so that the contamination can penetrate into the volume 230 .

In the case of the seal 210 according to one exemplary embodiment, this problem is solved in that a flexible rubber membrane (elastomer structure 220) is implemented in the seal 210, which allows the volume of air contained in the volume 230 to move with it in the different temperature states of the bearing 100 can change with as little resistance as possible. By implementing the elastomer structure 220, it may therefore be possible to enable volume compensation between a cold and an operating temperature state of the bearing 100, so that pressure differences between an interior and an exterior of the bearing 100 can be minimized, or at least reduced, without causing too much pressure a breakdown of the sealing effect of the further seal 260 occurs. In this way, a discharge of the lubricant, for example a discharge of grease, but also an entry of water, dirt or other contamination into the bearing 100 can be prevented. If necessary, it is also possible to prevent the seals from being sucked in, which can lead to high rotational resistance and corresponding lip wear.

The camp 100 as it is in 1 is shown here represents a wheel bearing, which includes mounting devices for attachment to the corresponding components. Thus, in the exemplary embodiment shown here, flange connection structures 270 are provided both on the outer ring 130 and on the inner ring 150, via which the bearing 100 can be mounted in the relevant vehicle. For this reason, the bearing 100 is also referred to as a storage unit, or unit for short.

In the exemplary embodiment of a bearing 100 shown here, the inner ring 150 is designed in such a way that, together with the seal 210 , the further seal 260 and the outer ring 130 , it delimits the volume 230 between the two bearing rings 120 , 150 . For this purpose, the base body 160 has a section 280 which extends essentially perpendicular to the axial direction 250, ie along a radial direction. The base body 160 is therefore essentially shaped like a cap or pot, with the volume 210 being formed on an outer side of the base body 160 and thus of the bearing 100 .

The bearing 100 is therefore a bearing unit for a non-driven wheel of a vehicle, more precisely in the present exemplary embodiment a wheel bearing for a non-driven wheel of a passenger vehicle. For this reason, the unit is also often referred to as a hub unit (HUB unit) without drive functionality. A hub with drive functionality can be equipped with such a seal 210 according to an exemplary embodiment, for example, if it can be pulled on or installed after a corresponding drive shaft has been installed.

In addition to being used as a wheel bearing, bearings 100 according to one exemplary embodiment can also be used in the area of fans in passenger cars and trucks, for example as a fan bearing, for example in conjunction with a viscous coupling. With these, there is also often the challenge that on one side of the bearing a seal has to seal against environmental influences and grease leakage, but there is often a high temperature difference between operation and standstill of the bearing.

This difference can also cause the air within the unit in question to expand during operation of the bearing and, in a conventional bearing, to release excess pressure via the outwardly opening main lip of the seal. In the process, grease or other lubricant can be discharged and is no longer available for lubrication. In the opposite case, there is also a risk that the main lip as the unit cools down, which can create high resistance when starting and possibly lead to increased lip wear. In addition, it can mean that water, dirt and other contaminants are sucked in, usually as soon as there is relative movement between the seal and the bearing ring in question. Attempts have conventionally been made to at least partially compensate for this by using a cover on the bearing in question, in that the air volume inside the corresponding bearing unit was restricted to the lowest possible value by design.

With a bearing 100 according to an exemplary embodiment, there is the possibility of operating with better lubrication over the service life with a reduced risk of grease discharge, dirt or water entry and/or increased lip wear, so that an increased service life may be possible for an otherwise identically designed bearing Stock could be achievable compared to a conventional stock unit.

Of course, bearing 100 and/or seal 210 according to one exemplary embodiment can also be used in technical systems other than the wheel bearings and fan bearings described above. The corresponding bearing 100 can be, for example, that of a viscous coupling used elsewhere in vehicle or system construction.

The seal 210 as shown in 1 is designed in such a way that although it can be connected to the first bearing ring 120 of the bearing 100, it is designed with regard to the second bearing ring 140 in such a way that it is not in contact with it, i.e. not in connection with it or contact is established. As a result, wear on the seal 210 and/or friction can be reduced if necessary. This is constructive with the in 1 The solution shown is realized in that the seal 210 is designed essentially in the shape of a pot or cap. For this purpose, the seal has a reinforcement structure 290 which has a shape adapted to an outer shape of the bearing 100 . The reinforcement structure 290 is connected here on the one hand to the elastomer structure 220 and on the other hand is therefore designed in such a way that it can be fastened to the first bearing ring 120 of the bearing 100 . The reinforcement structure 290, and thus the seal 210, are frictionally or non-positively connected to the outer ring 130 serving as the first bearing ring 120 via a positive connection, in the present case via a press fit. The reinforcement structure 290 is not in contact with the second bearing ring 140, ie the inner ring 150.

In order to enable the best possible static sealing of the seal 210 with respect to the first bearing ring 120 , the reinforcement structure has a bearing area 300 which is arranged and designed in such a way that it can be placed on the first bearing ring 120 . For example, the contact area 300 can have been subjected to a smoothing process in this area in order to improve the static sealing effect of the seal 210 in relation to the first bearing ring 120 . Likewise, a corresponding counter-sealing surface on the first bearing ring 120 can have been subjected to a corresponding surface treatment, so that it is turned or ground, for example, in order to enable the best possible static sealing effect.

Likewise, to improve the static sealing effect, the contact area can have an elastomer at least partially on a side facing first bearing ring 120, which can be separate from elastomer structure 220, but can also be designed to be connected to it. For example, it can be a part of the elastomer structure 220 that is vulcanized thinly in this area.

Of course, in other embodiments, other implementations of the elastomer structure 220, the reinforcement structure 290 and the others in 1 structural features shown are implemented. For example, the membrane area 240 of the elastomer structure 220 can also be attached to the reinforcement structure 290 in a different manner. In the case of the bearing 100 shown here according to an exemplary embodiment, the reinforcement structure 290 has a conical section 310 which is arranged on a central recess 320 of the reinforcement structure 290 . In the exemplary embodiment of a bearing 100 shown here, the elastomer structure 220, more precisely the membrane structure 240, is fastened to this conical section 310, which extends axially toward the section 280 of the base body 160. As a result, even if membrane region 240 expands or deforms outwards along axial direction 250, i.e. in 1 to the right, an overall dimension of the bearing 100 along the axial direction 250 can be kept constant.

2 shows another embodiment of a bearing 100 according to an embodiment that differs from that in FIG 1 shown differs only with regard to the exact design of the elastomeric structure 220 of the seal 210. With regard to the other components is therefore related to the description 1 referred.

The elastomeric structure 220 of the seal 210 from 2 In addition to the membrane area 240, it also has a connection area 330, which is arranged between the reinforcement structure 290 and the membrane area 240. More specifically, the connection area 330 of the elastomeric structure 220 is connected to the conical portion 310 of the reinforcement structure 290 and has an S-shaped configuration. As a result, the membrane area 240 of the elastomer structure 220 has moved closer to the section 280 of the base body 160, so that compared to the bearing 100 1 the volume 230 between the bearing rings 120, 140 is reduced.

The connection area 330 is designed in such a way that the change in shape of the elastomer structure 220 can also be brought about at least partially by a deformation of this connection area 330 . If, for example, there is an increase in pressure in the volume 230, the connection area 330 can also be subjected to a deformation as an alternative or in addition to a deformation of the membrane area 240, so that the volume 230 can adapt accordingly to the newly prevailing pressure conditions. In such a case, for example, the deformation of the connection area 330 can enable a movement of the membrane area 240 along the axial direction 250 by further compressing the structure of the connection area 330 .

However, even if the temperature drops, a corresponding deformation of the connection area 330 in the opposite direction can lead to a reduction in the relevant volume 230 , so that in this case the membrane area 240 moves closer to the section 280 of the base body 160 .

At the in 2 In the exemplary embodiment of a bearing 100 or a seal 210 shown, depending on the specific design, both the connection area 330 and the membrane area 240 can be deformed at the same time. Such a parallel deformation could be observed in the case of the in 1 shown exemplary embodiment, since this does not include a significantly deformable connection area 330.

3 Finally, FIG. 1 shows a further exemplary embodiment of a bearing 100 as a cross-sectional view, which differs only slightly from that shown in the figures previously shown. Apart from the differently configured seal 210 according to one embodiment, the one in 3 The representation shown, for example, with regard to the sectional plane through the bearing 100. The corresponding rolling elements 200 can be seen more clearly here, while the corresponding cages 205 are at least partially covered by them. The flange connection structures 270 can also be seen more clearly.

With regard to the precise configuration of the seal 210, the two elastomer structures 220 differ from FIGS 2 and 3 essentially with regard to the precise configuration of the connecting region 330. In the present case, this is more meandering or fold-like. In addition, the connecting area 330 does not, as previously shown, open into the membrane area 240 on the radially outer side, but is offset slightly inwards in relation to a radial extension of the membrane area 240 . This forms a small section 340 of the membrane area 240 which, depending on the deformation of the connection area 330, can optionally come into contact with the latter and can thus limit a movement of the same. The portion 340 therefore serves as a restraining member (stop member) or stop to limit the movement of the elastomeric structure 220 due to deformation or deformation of the connection portion 330 .

Correspondingly, the connection area 330 also has a further section 350, which is arranged on a side of the elastomer structure 220 that faces away from the section 340 and likewise limits a movement or deformation of the connection area 330 by coming into contact with the same. It therefore also serves as a stop. As a result, a deformation of the connection area 330 along the axial direction 250 can be limited by one or both sections 340, 350.

The connection area 330 is compared to the connection area 330 of the in 2 shown embodiment executed more meandering. In this way, an easier deformation of the connection region 330 can be achieved, if necessary, so that the change in shape of the elastomer structure 220 as a whole occurs during the in 3 shown embodiment is more strongly caused by a deformation of the connecting portion 330. In the exemplary embodiment shown here, a change in the shape of the membrane area 240 can therefore only become significant if the change in shape has already taken place completely through the connection area 330 and has been limited by the corresponding section 340, 350.

Merely for the sake of completeness, it should also be mentioned at this point that the seal 210 can be designed to be rotationally symmetrical, for example. For example, it can be completely rotationally symmetrical, but it can also have only an n-fold rotational symmetry rie. In principle, however, there is also the possibility of embodying the seal 210 asymmetrically.

By using a seal 210 according to an exemplary embodiment, a sealing behavior of the seal 210 can be improved under different conditions.

The features disclosed in the above description, the claims and the drawings can be important and implemented both individually and in any combination for the realization of an exemplary embodiment in its various configurations.

Reference List

100

camp

110

Angular ball bearing

120

first bearing ring

130

outer ring

140

second bearing ring

150

inner ring

160

body

170

career

180

another body

190

counter track

200

rolling elements

205

Cage

210

poetry

220

elastomer structure

230

volume

240

membrane area

250

axial direction

260

additional seal with sealing lip

270

flange connection structure

280

section

290

reinforcement structure

300

support area

310

conical section

320

central recess

330

connection area

340

section

350

another section

Claims (7)

Seal (210) for a bearing (100) comprising a first (120) and a second bearing ring (140), with the following features: an elastomeric structure (220); and a reinforcement structure (290) connected to the elastomeric structure (220) and configured to be attachable to a first race (120) of the bearing (100); wherein the seal (210) is configured to at least partially seal a volume (230) between the first (120) and the second bearing ring (140) with respect to a medium; wherein the seal (210) is formed in such a way that the medium cannot pass through the seal (210); wherein the elastomeric structure (220) is configured to respond to a change in pressure on one side of the elastomeric structure (220) with a change in shape without substantially changing the sealing effect during the change in shape; wherein the seal (210) is adapted to be connected to a first bearing ring (120) of the bearing (100); wherein the seal (210) is further configured so that it is non-contact with respect to a second bearing ring (140) different from the first bearing ring (120); wherein the elastomeric structure (220) comprises a diaphragm portion (240) and a connecting portion (330); wherein the connecting area (330) is arranged between the reinforcement structure (290) and the membrane area (240) and is designed in such a way that the change in shape of the elastomeric structure (220) is caused at least partially by a deformation of the connecting area (330); and wherein the reinforcement structure (290) has a conical section (310) which is arranged at a central recess (320) of the reinforcement structure (290) and which extends axially towards a section (280) of a base body (160) of the second bearing ring , and the elastomeric structure (220) is attached to the conical portion (310). Gasket (210) after claim 1 , In which the elastomeric structure (220) comprises a membrane region (240) which is formed in such a way as to allow the change in shape of the elastomeric structure (220) at least in part by deflection of the membrane region (240). Seal (210) according to one of the preceding claims, in which the connecting region (330) is designed in such a way that the change in shape of the elastomeric structure (220) is at least partially caused by a movement of the membrane region (240). to allow along an axial direction (250) of the bearing (100). Seal (210) according to one of the preceding claims, in which the reinforcing structure (290) comprises a bearing area (300) which is designed to be placed on the first bearing ring (120) in such a way that the bearing area (300) the seal ( 210) statically seals against the first bearing ring (120). Gasket (210) after claim 4 , wherein the bearing area (300) has an elastomer at least partially on a side facing the first bearing ring (120). Bearing (100) with the following features: an inner ring (150) and an outer ring (130); and a seal (210) according to any one of the preceding claims bonded to the outer ring (130) and non-contacting with respect to the inner ring (150). Stock (100) after claim 6 , which further comprises a contacting further seal (260) which is arranged on a side facing away from the seal (210) between the inner ring (150) and the outer ring (130), the inner ring (150) being designed in such a way that this together with the seal (210), the further seal (260) and the outer ring (130) forms a substantially closed volume (230), and wherein the seal (210) and the further seal (260) are designed such that the seal (210) allows such a change in shape that the further seal (260) always touches the inner ring (150) and the outer ring (130) even if the pressure of a gas in the volume (230) changes during operation of the bearing (100).

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