storage

Abstract

Storage (1) - with an outer element (3) which is arranged around an axis of rotation (2) extending in the axial direction (a) and which has a first raceway (4), - with an inner element (5) which has a second raceway (6), wherein the outer element (3) forms a sealing gap (7) with the inner element (5), axially adjacent to the first raceway (4) and to the second raceway (6), which extends in axial direction (a) to an axial end of the inner element (5) and / or the outer element (3), - with roller elements (8) which are arranged between the first track (4) and the second track (6) and are guided by a cage (9), - with a sealing agent (10) combined with the cage (9), wherein the sealing agent (10) has a first sealing lip (11) which is tangent to the outer element (3) and a second sealing lip (12) which is tangent to the inner element (5), wherein the sealing gap (7) is immediately adjacent to the sealing agent (10) in the axial direction (a) such that the sealing gap (7) is located upstream of the sealing agent (10) in the axial direction (a), - wherein the inner element (5), axially adjacent to the second raceway (6), has a profile (13) which extends in the axial direction (a), immediately thereafter extends in a radial direction (r) towards the outer element (3), and immediately thereafter transitions into the axial direction (a) such that a projection (14) on the inner element (5) and an end section (15) of the outer element (3) overlap in the axial direction (a), and - the inner element (5) has a profile (13) with a U-shape which is rotated clockwise by 90° and the extension (14) forms the last element of the profile (13) in a U-shape.

Description

Field of invention

[0001] The invention relates to a bearing comprising an outer element, an inner element, a sealing agent and a cage for guiding rolling elements. Background of the invention

[0002] DE 10 2020 212 588 A1 discloses a transmission for a motor vehicle comprising a housing and a shaft. The transmission features a radial shaft seal with a sealing lip for sealing an oil chamber, a shaft grounding device for creating an electrically conductive sliding contact, and a sleeve-shaped cover element for protecting the sliding contact from environmental influences. The cover element, together with the grounding device, forms a labyrinth seal.

[0003] DE 10 2018 123 495 A1 discloses a ball bearing with a rotating inner bearing ring and a torsionally rigid outer bearing ring, which has a sealing arrangement on both sides. The sealing arrangement consists of a one-piece, steel centrifugal disc that is positively locked to the inner bearing ring. A sealing collar of the centrifugal disc is guided without contact to a sealing surface of the outer bearing ring, maintaining a gap dimension.

[0004] German patent DE 19 05 766 A describes a needle bearing with a plastic cage. This can be seen in the... Fig. 1, Fig. 2, that the aforementioned cage transitions at both ends into a sealing body with V-shaped, splayed legs. One of the legs rests against an inner raceway and the other leg against an outer raceway of the bearing.

[0005] DE 10 2005 027 486 A1 discloses a sleeve bearing with needles designed for direct contact with a shaft. The bearing is enclosed by a thin-walled outer ring with radially inward-facing flanges. The needles are cage-guided. A separate sealing ring is provided according to [reference to relevant document]. Fig. 1 between one of the outer ring's edges and the cage. The outer ring's edges overlap with the cage's edges. Object of the invention

[0006] The invention is based on the objective of providing an improved storage solution. Description of the invention

[0007] According to the invention, this problem is solved by a storage system. - with an outer element which is arranged around an axially extending axis of rotation and which has a first raceway, - with an inner element which has a second raceway, wherein the outer element forms a sealing gap with the inner element, axially adjacent to the first raceway and to the second raceway, which extends in the axial direction to an axial end of the inner element and / or the outer element, - with roller elements which are arranged between the first track and the second track and are guided by a cage, - with a sealant combined with the cage, wherein the sealant has a first sealing lip which is tangent to the outer element and a second sealing lip which is tangent to the inner element, wherein the sealing gap is immediately adjacent to the sealant in the axial direction, such that the sealing gap is located upstream of the sealant in the axial direction, - wherein the inner element, axially adjacent to the second raceway, has a profile which extends in the axial direction, immediately thereafter extends in a radial direction towards the outer element, and immediately thereafter transitions into the axial direction, such that a projection on the inner element and an end section of the outer element overlap in the axial direction, and - the inner element has a U-shaped profile that is rotated 90° clockwise and the extension forms the last link of the U-shaped profile.

[0008] The demands placed on components, such as bearing units, with regard to reducing production and operating costs are constantly increasing. At the same time, the bearing units must continue to operate with a long service life. The invention is based on the understanding that reducing the number of individual components by exploiting physical effects is a viable approach. The bearing assembly consists of an outer element and an inner element, both arranged around an axially extending axis of rotation. The outer element has a first raceway, and the inner element has a second raceway opposite the first. The raceways can be directly radially opposed or inclined, as in an angular contact ball bearing. Rolling elements are arranged between the first and second raceways and roll on both.The rolling elements can be designed as spherical rollers or cylindrical rollers. These elements are guided by a cage. To prevent premature wear of the bearing, it must be protected from environmental media such as dirt particles and liquids, like water. At the same time, the number of components used should be kept to a minimum to minimize production costs. To meet this requirement, a reduced-component double seal is employed. This involves using the basic components required for the bearing to create a sealing gap, while the cage is simultaneously combined with a sealant. The sealing gap is designed to prevent or at least hinder the ingress of surrounding media, such as dirt or liquids, into the interior of the bearing.The cage and the sealant can be made of different materials. The cage and the sealant can be designed as a single component. In particular, the cage can include a support section that incorporates the sealant and from which the sealing lips extend. The center of gravity of the support section is selected such that it is positioned on the same diameter as the roller elements with respect to the axis of rotation of the bearing. The sealant has at least two sealing lips. A first sealing lip makes contact with the outer element, and a second sealing lip makes contact with the inner element. In this way, the sealant bridges a gap between the outer and inner elements and protects the first and second raceways and the roller elements from external influences.The first sealing lip and the second sealing lip, or the first sealing lip or the second sealing lip, can extend obliquely radially outwards. Obliquely radially outwards in this context means obliquely towards the outer element. This compensates for relative displacement of the cage and the rolling elements during operation. The different positioning of the first and second sealing lips also results in different sliding speeds at the respective contact surfaces, which reduces friction and thus improves the wear behavior of the sealant. The integration of the cage and sealant also allows for high flexibility in the design of the rows of rolling elements. The outer and inner elements overlap at least partially in the axial direction and are spaced apart from each other in the radial direction.An axially extending gap is formed between the outer and inner elements. This gap is also referred to as a sealing gap. The gap is relatively narrow, with a radial dimension of less than 10% of the diameter of a roller element held in the cage. With an inner element diameter of 80 millimeters, it is advantageous for the gap to have an axial width of more than 5 millimeters. In a particularly advantageous embodiment, the width of the sealing gap is between 10 and 15 millimeters. The sealing gap originates from a starting position that is axially adjacent to the first and second raceways. The sealing gap extends axially to an axial end of the outer element and an axial end of the inner element. The axial end of the outer element is the end closest to the first raceway.The axial end of the inner element is the end closest to the second raceway. The sealing gap terminates at the same end as the outer and inner elements if both components terminate simultaneously. Alternatively, the sealing gap terminates at the axial end of either the outer or inner element, whichever terminates first. The sealing gap is positioned axially upstream of the cage containing the sealant. This means that, starting from the axial end of the outer element and extending to the first raceway, the arrangement is as follows: sealing gap, sealant with cage, first raceway. Similarly, the arrangement at the inner element is: sealing gap, sealant with cage, second raceway. In this way, a component-reduced double seal is achieved, consisting of the sealing gap and the cage containing the sealant.This double seal requires fewer individual components than conventional sealing systems, as one part of the seal consists of essential components for the bearing, such as the outer and inner elements, while the second part is a modified cage with a sealing function. During operation, either the outer or the inner element rotates. Preferably, the inner element rotates. Different rotational speeds occur depending on the operating conditions. A seal could be designed to act as a barrier against the ingress of dirt particles and liquids from the environment into the bearing at low rotational speeds. However, to ensure a reliable seal of the bearing even at high rotational speeds, the seal would simultaneously have to meet other requirements, such as contact force.A design for high contact force, on the other hand, would lead to high frictional heat and significant seal wear. Alternatively, additional seals would have to be incorporated into the bearing to provide sealing at high speeds, such as a centrifugal disc. To avoid the use of additional components or increased wear, a component-reduced double seal is employed. The cage is combined with the sealant. A sealing gap is positioned upstream of the sealant in the axial direction. While the sealing efficiency of the sealant is potentially reduced at high rotational speeds during operation, a usable sealing effect is generated in the upstream sealing gap: The rotational movement between the inner and outer elements creates overpressure in the sealing gap at high rotational speeds. This overpressure acts as a reliable barrier against the ingress of media from the bearing's environment.The effect is particularly advantageous from 2500 revolutions per minute. The sealing gap makes it so difficult for media to enter at high rotational speeds that the sealant, combined with the cage, can be designed to be wear-resistant and suitable for low contact forces. This is because the sealant only needs to provide a reliable seal at low rotational speeds; at high rotational speeds, the overpressure in the sealing gap provides the necessary seal. By using the reduced-component double seal, a bearing can therefore be realized that has fewer components than conventional systems and can thus be manufactured at lower production costs. At the same time, the bearing meets the requirement of operating reliably and with minimal wear under various operating conditions.

[0009] The inner element, axially adjacent to the second raceway, has a profile that extends axially, then immediately radially towards the outer element, and then immediately transitions into an axial direction such that a projection on the inner element and an end section of the outer element overlap axially. The inner element has a U-shaped profile rotated 90° clockwise, with the projection forming the last segment of the U-shaped profile. In a preferred embodiment, the second sealing lip contacts the projection. Preferably, the inner element has a U-profile rotated 90° clockwise on an axial side where the inner element terminates, in a cross-sectional plane that also contains the axis of rotation. The opening of the U-profile thus faces the rolling element.The U-profile can connect directly to a shoulder of the second raceway, so that the shoulder transitions into the U-profile. The U-profile can also be axially spaced from the shoulder, offset radially towards the outer element, or offset towards the axis of rotation. The U-profile has boundary surfaces of the inner element that define the inner element radially or axially. The U-profile begins with a first section that runs axially, parallel to the axis of rotation. This first section has a first boundary surface of the inner element facing the outer element in the radial direction. The first section then transitions into a second section that runs radially, perpendicular to the axis of rotation. This second section has a second boundary surface of the inner element facing the roller element in the axial direction.In particular, the first section can be at least as long as the second section. The second section is followed by an extension on the inner element that runs parallel to the first section, such that part of the first section and part of the extension overlap. The extension has a third boundary surface of the inner element directed radially to the first boundary surface. The extension on the inner element also overlaps, at least partially, with the end section of the outer element. The extension on the inner element is located in an end section of the inner element. The end section of the inner element comprises a portion of the inner element that does not exceed one-third of the entire inner element and whose termination forms the axial end of the inner element.The overlap of the outer element's end section and the extension on the inner element creates a gap that forms part of the sealing gap between the outer and inner elements. Simultaneously, the U-profile can form a cavity that serves as a reservoir for lubricants such as grease. In a preferred embodiment, the second sealing lip contacts the extension on the inner element. This extension forms the last segment of the U-profile. The second sealing lip thus contacts the third boundary surface of the inner element. If the cavity is used, for example, as a lubricant reservoir, the contact between the second sealing lip and the third boundary surface prevents any lubricant from escaping through the sealing gap and allows it to be retained inside the bearing.

[0010] Preferably, the inner and outer elements overlap radially, forming an undercut. More preferably, the outer and inner elements partially overlap radially, maintaining a minimum gap in the axial direction. In this way, they can form a labyrinth seal at the entrance to the sealing gap, together with the sealing gap itself. The labyrinth seal is such that any penetrating medium must change direction at least once to reach the interior of the bearing. The entrance to the sealing gap is located at the axial end of either the outer or inner element. Alternatively, the outer and inner elements can also overlap radially at the outlet of the sealing gap, forming a labyrinth seal there together with the sealing gap. The outlet of the sealing gap is located axially directly in front of the sealing medium.The undercut, in combination with the sealing gap, forms a pre-labyrinth for the sealant. This pre-labyrinth assists the sealant in sealing the bearing, particularly at speeds where the effect of overpressure in the sealing gap has not yet occurred.

[0011] Preferably, the sealing gap has an axial width that is at least twice the maximum of the axial widths of the first raceway and the second raceway. Preferably, the gap, which extends radially between a portion of the outer element and a portion of the inner element and is axially long, is relatively long. This sealing gap is significantly wider in the axial direction than in conventional bearing arrangements where shoulders or flanges face each other radially. To achieve a wide sealing gap in the axial direction, the width is at least two raceways wide. Depending on which raceway has the greatest width, a combination of the axial widths of the first and second raceways is selected.Only above a certain axial width of the sealing gap does the physical effect of overpressure build-up occur at high rotational speeds. This overpressure shields the interior of the bearing from disruptive media from the environment.

[0012] Preferably, the outer and inner elements, in the axial direction adjacent to the first and second raceways, together form a cavity, distinct from the sealing gap, with an opening that is closed by the sealant. Preferably, a cavity is formed in the area of ​​the rolling element and the first and second raceways, i.e., a hollow space located between the outer and inner elements. This cavity can, in particular, serve as a reservoir for lubricants such as grease. In this case, the sealant fulfills a dual function: On the one hand, it keeps out disruptive influences from the environment, and on the other hand, it retains lubricant in the immediate vicinity of the rolling elements and raceways, thus ensuring continuous lubrication of the bearing.

[0013] Preferably, the cage is made of a thermoplastic and the sealant of an elastomer. Preferably, the cage and the sealant are made of different materials. Combining the properties of two materials can increase the functionality of the component. One possible combination is a two-component component made of a thermoplastic and an elastomer. While the thermoplastic provides the necessary stiffness for the cage, the elastomer provides the necessary elasticity for the sealant. Applying an elastomeric sealant to a thermoplastic cage is a robust and cost-effective production process. Complex and expensive assembly processes for individual components are eliminated.

[0014] Preferably, the outer element consists exclusively of an outer ring having the first raceway, and / or the inner element consists exclusively of an inner ring having the second raceway. In a preferred embodiment, the bearing arrangement is such that the outer element corresponds to an outer ring and the inner element corresponds to an inner ring, or the outer element corresponds to an outer ring, or the inner element corresponds to an inner ring. In a case where the outer element corresponds to an outer ring, the outer ring itself is part of the double seal. The first sealing lip thus rests against the outer ring, and the sealing gap is formed between the outer ring and the inner element. In a case where the inner element corresponds to an inner ring, the inner ring itself is part of the double seal.The first sealing lip rests against the outer element, the second sealing lip rests against the inner ring, and the sealing gap is formed between the outer element and the inner ring. In a case where the outer element corresponds to an outer ring and the inner element corresponds to an inner ring, the double seal is formed between the outer ring and the inner ring. The first sealing lip rests against the outer ring, the second sealing lip rests against the inner ring, and the sealing gap is formed between the outer ring and the inner ring.

[0015] Preferably, the sealing gap is formed between a shaft and a housing, wherein an inner ring sits on the shaft or is part of the shaft, and / or the housing sits on an outer ring, or the outer ring is part of the housing. Preferably, the sealing gap formed between the outer and inner elements is formed between a shaft and a housing. Accordingly, the outer element consists at least partially of a housing having the first raceway or of a housing with an outer ring having the first raceway. Similarly, the inner element consists at least partially of a shaft having the second raceway or of a shaft with an inner ring having the second raceway. During operation, the shaft rotates, and the housing remains stationary. The shaft and the housing are designed such that they jointly form a long sealing gap through axial overlap.At high shaft rotation speeds, an overpressure builds up in this sealing gap, fulfilling the sealing function. At low rotation speeds, the sealant combined with the cage seals the space between the shaft and the gearbox. This type of design can be used particularly in gearboxes for electric vehicles.

[0016] Preferably, the sealant is bonded to the cage by material bonding, force bonding, or form bonding. Preferably, the cage is firmly bonded to the sealant. In particular, the cage can be inseparably bonded to the sealant. The cage can be formed as a single piece with the sealant. The cage can be made of the same material or material composition. The cage can be integrated into the sealant. The cage can be formed as a single piece with the sealant and be made of a material different from the sealant. The cage and the sealant can be connected to each other by a connecting element, adhere to each other, or be shaped in such a way as to create a firm connection. Brief description of the drawings

[0017] The invention is explained below with reference to exemplary embodiments and the drawings. The drawings are schematic representations and show: Fig. 1 a section of an embodiment of the bearing according to the invention in a cross-sectional view, Fig. 2 a cross-sectional view of a further embodiment of the bearing according to the invention in a partial view, Fig. 3 a schematic representation of a further embodiment of the bearing according to the invention in an application. Detailed description of the drawings

[0018] Fig. Figure 1 shows a section of a bearing 1 with a ball rolling element 8. The illustration shows a cross-section through a plane in which an axis of rotation 2 also runs in the axial direction a. Perpendicular to this is a radial direction r. An axis in the radial direction r spans the plane together with the axis of rotation 2. An outer element 3 is arranged around the axis of rotation 2 and has a first raceway 4. An inner element 5, which has an inner ring 19, has a second raceway 6 on the inner ring 19. The second raceway 6 is opposite the first raceway 4 in the radial direction r. The second raceway 6 is spaced closer to the axis of rotation 2 in the radial direction r than the first raceway 4. The rolling element 8 rolls between the first raceway 4 and the second raceway 6 and is guided by a cage 9. The cage 9 is designed as a snap cage and is combined with a sealing element 10.The inner ring 19 has a shoulder 22 axially adjacent to the second raceway 6. Offset axially a relative to the shoulder 22 and radially closer to the axis of rotation 2 than the second raceway 6, the inner element 5 has a U-shaped profile 13. The U-shape is rotated 90° clockwise, so that it resembles a C-shape without rounded corners. Axially adjacent to the first raceway 4 and the second raceway 6, on the side where the axial end of the outer element 3 is located, the inner element 5 and the outer element 3 overlap extensively in the axial direction a. They are spaced apart from each other in the radial direction r. Thus, the outer element 3 and the inner element 5 form a sealing gap 7. The sealing gap 7 has a significantly larger dimension in the axial direction a than in the radial direction r and is relatively long and narrow.The sealant 10 has a first sealing lip 11, which contacts an end section 15 of the outer element 3, and a second sealing lip 12, which contacts a projection 14 on the inner element 5. The projection 14 forms the last segment of the U-shaped profile 13. The sealing gap 7 is located upstream of the combination of cage 9 and sealant 10 in the axial direction a. This forms a double seal with fewer components. During operation, either the outer element 3 or the inner element 5 rotates. At high rotational speeds, overpressure builds up in the sealing gap 7, preventing dirt particles or liquids from penetrating the interior of the bearing 1. Therefore, it is sufficient to design the first sealing lip 11 and the second sealing lip 12 such that they have low contact forces with the outer element 3 and the inner element 5 and provide sufficient sealing at low rotational speeds.This means that the component-reduced double seal ensures low-wear and cost-effective operation of bearing 1, even under different operating conditions.

[0019] Fig. Figure 2 shows an embodiment of the bearing 1 according to the invention in a partial view of a cross-section. The cross-sectional plane is spanned by an axis of rotation 2 extending in an axial direction a and by an axis extending in a radial direction r perpendicular to the axial direction a. An outer element 3 and an inner element 5 are radially opposite each other and are both arranged around the axis of rotation 2. The outer element 3 has a first raceway 4 with a width b1 in the axial direction a, and the inner element 5 has a second raceway 6 with an axial width b2. A rolling element 8, designed as a ball bearing, is arranged between the first raceway 4 and the second raceway 6. Adjacent to the second raceway 6 in the axial direction a, the inner element 5 has a profile 13 with a U-shape rotated 90° clockwise, so that a cavity 16 is formed between the inner element 5 and the rolling element 8.The profile 13 on the inner element 5 is divided into three sections. A first section 23 adjoins the second raceway 6 and has a first boundary surface 24 of the inner element 5 in the radial direction r, which faces the outer element 3. Adjoining the first section 23 on the profile 13 is a second section 25, which has a second boundary surface 26 of the inner element 5 in the axial direction a. The second boundary surface 26 faces the roller element 8. Following the second section 25 is a projection 14 on the inner element 5, which forms the third section. The projection 14 has a third boundary surface 28 in the radial direction r, which faces the first boundary surface 24. The third boundary surface 28 of the inner element 5 faces a further boundary surface 29 in the radial direction r, which is located at an end section 15 of the outer element 3.The third boundary surface 28 and the further boundary surface 29 largely overlap in the axial direction a and are spaced apart from each other in the radial direction r. Thus, the outer element 3 and the inner element 5 form a sealing gap 7. The sealing gap 7 is designed as an elongated gap and has a width b in the axial direction a, which is approximately twice the width b2 of the second raceway 6 in the axial direction a. The cage 9, in combination with the sealant 10, is arranged in the axial direction a between the sealing gap 7 and the rolling element 8. The sealant 10 has a first sealing lip 11, which contacts the further boundary surface 29 of the end section 15 of the outer element 3, and a second sealing lip 12, which contacts the third boundary surface 28 of the extension 14 on the inner element 5. The sealant 10 thus seals an opening 17 of the cavity 16.Starting from the axial end of the bearing 1, which is closest to the rolling element 8, the sealing gap 7 is positioned axially a in front of the cage 9 with sealant 10, thus forming a component-reduced double seal. Additionally, the outer element 3 overlaps the inner element 5 radially r at the axial end of the bearing 1, which is closest to the rolling element 8, forming an undercut 27. The undercut 27, together with the sealing gap 7, forms a pre-labyrinth. During operation, at low rotational speeds of the outer element 3 or the inner element 5, surrounding media are kept away from the interior of the bearing 1 by the pre-labyrinth and the combination of cage 9 and sealant 10. Media that are located inside the bearing 1 and are intended to remain there, such as lubricants, are retained inside by the first sealing lip 11 and the second sealing lip 12.At high rotational speeds, the overpressure that forms in the sealing gap 7 prevents the ingress of interfering media into the bearing 1.

[0020] Fig.Figure 3 shows a partial cross-sectional view of a further embodiment of the bearing 1 according to the invention. The illustration shows the cross-section through a plane in which an axis of rotation 2 also runs in the axial direction a. A radial direction r runs perpendicular to this. An axis in the radial direction r spans the plane together with the axis of rotation 2. The outer element 3 is designed as a shaft 20 with an outer ring 18. The shaft 20 runs along the axis of rotation 2. The inner element 5 is designed as a housing 21 with an inner ring 19 and runs along the axis of rotation 2. The shaft 20 is completely surrounded by the housing 21. The outer ring 18 has a first raceway 4. The inner ring 19 has a second raceway 6 opposite the first raceway 4 in the radial direction r. A rolling element 8 designed as a ball bearing is arranged between the first raceway 4 and the second raceway 6.The shaft 20 and the housing 21 overlap in axial direction a, so that a sealing gap 7 is formed in the region of one axial end of the shaft 20 and the housing 21. The shaft 20 has a U-shaped profile 13 at one axial end, open towards the rolling element 8. A portion of the profile 13 extending in axial direction a, which is a projection 14 of the inner element 5, forms the sealing gap 7 together with an end section 15 of the outer element 3. A cavity 16 is formed between the rolling element 8 with first raceway 4 and second raceway 6 and the shaft 20 by the profile 13. The cavity 16 is closed by a cage 9, which guides the rolling elements 8 and is designed in combination with a sealant 10. The sealant 10 has a first sealing lip 11 that is tangent to the housing 21 and a second sealing lip 12 that is tangent to the shaft 20.During operation, the shaft 20 rotates, and at high speeds, overpressure builds up in the sealing gap 7, preventing surrounding media from entering the interior of the bearing 1. At low speeds, the combination of cage 9 and sealant 10 seals the bearing 1. Thus, a cost-effective and low-wear operation of applications with a rotating shaft 20 and a static housing 21 is achieved using a component-reduced double seal. Such applications are used, for example, in gearboxes for electric vehicles. Reference symbol list 1 Storage 2 Rotation axis 3 Outer element 4 first career 5 interior elements 6 second career 7 Sealing gap 8 rolling elements 9 cage 10 sealants 11 first sealing lip 12 second sealing lip 13 Profile on the inner element 14 Extension on the inner element 15 End section of the outer element 16 Cavity 17 Opening the cavity 18 Outer ring 19 inner ring 20th wave 21 cases 22 Shoulder 23 first section 24 first boundary surface 25 second section 26 second boundary surface 27 Undercut 28 third boundary surface 29 additional boundary areas a axial direction b axial width of the sealing gap b1 axial width of the first raceway b2 axial width of the second raceway r radial direction

Claims

[1] Storage (1) - with an outer element (3) which is arranged around an axis of rotation (2) extending in the axial direction (a) and which has a first raceway (4), - with an inner element (5) which has a second raceway (6), wherein the outer element (3) forms a sealing gap (7) with the inner element (5), axially adjacent to the first raceway (4) and to the second raceway (6), which extends in axial direction (a) to an axial end of the inner element (5) and / or the outer element (3), - with roller elements (8) which are arranged between the first track (4) and the second track (6) and are guided by a cage (9), - with a sealing agent (10) combined with the cage (9), wherein the sealing agent (10) has a first sealing lip (11) which is tangent to the outer element (3) and a second sealing lip (12) which is tangent to the inner element (5), wherein the sealing gap (7) is immediately adjacent to the sealing agent (10) in the axial direction (a) such that the sealing gap (7) is located upstream of the sealing agent (10) in the axial direction (a), - wherein the inner element (5), axially adjacent to the second raceway (6), has a profile (13) which extends in the axial direction (a), immediately thereafter extends in a radial direction (r) towards the outer element (3), and immediately thereafter transitions into the axial direction (a) such that a projection (14) on the inner element (5) and an end section (15) of the outer element (3) overlap in the axial direction (a), and - the inner element (5) has a profile (13) with a U-shape which is rotated clockwise by 90° and the extension (14) forms the last element of the profile (13) in a U-shape. [2] Storage (1) according to claim 1, characterized by , that the second sealing lip (12) contacts the extension (14) on the inner element (5). [3] Storage (1) according to claim 1, characterized by , that the inner element (5) and the outer element (3) overlap in radial direction (r) and form an undercut (27). [4] Storage (1) according to claim 1 characterized by , that the sealing gap (7) has a width (b) in the axial direction (a) which is at least twice the maximum of a width (b1) of the first raceway (4) in the axial direction (a) and a width (b2) of the second raceway (6) in the axial direction (a). [5] Storage (1) according to claim 1, characterized by, that the outer element (3) and the inner element (5), in axial direction (a) adjacent to the first raceway (4) and to the second raceway (6), together form a cavity (16) different from the sealing gap (7) with an opening (17) which is closed by the sealing medium (10). [6] Storage (1) according to claim 1 characterized by , that the cage (9) is made of a thermoplastic and the sealant (10) is made of an elastomer. [7] Storage (1) according to claim 1 characterized by , that the outer element (3) consists exclusively of an outer ring (18) having the first raceway (4) and / or the inner element (5) consists exclusively of an inner ring (19) having the second raceway (6). [8] Storage (1) according to claim 1, characterized by, that the sealing gap (7) is formed between a shaft (20) and a housing (21), wherein an inner ring (19) sits on the shaft (20) or is part of the shaft (20) and / or the housing (21) sits on an outer ring (18) or the outer ring (18) is part of the housing (21). [9] Storage (1) according to claim 1, characterized by , that the sealant (7) is bonded to the cage (9) by material bonding, force bonding or form bonding.

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