WO2024099492A1

WO2024099492A1 - Rolling bearing

Info

Publication number: WO2024099492A1
Application number: PCT/DE2023/100600
Authority: WO
Inventors: Tony ZEISS; Hans-Walter Wodtke
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2022-11-10
Filing date: 2023-08-16
Publication date: 2024-05-16
Also published as: DE102022129678A1

Abstract

The invention relates to a noise-damping rolling bearing (1) which is designed as a spherical bearing and which comprises an outer ring assembly (3) that has an outer ring (4), a spring element (6), a damping element (13), and a sleeve (5). The spring element (6) is arranged between the outer ring (4) and the sleeve (5) and is divided into segments (7). The spring element (6) forms a first support point (10) which is supported on the outer ring (4) and a second support point (11) which is supported on the sleeve (5). A first intermediate space (12) which is filled with the damping element (13) is formed between the outer ring (4) and the spring element (6).

Description

Description of the invention

Roller bearing

Field of the invention

The invention relates to a rolling bearing arranged around a rotation axis with a bearing outer ring arrangement which comprises a bearing outer ring, a spring element and a sleeve, wherein the spring element and the sleeve are arranged concentrically to the bearing outer ring and the spring element is arranged in the radial direction, which runs perpendicular to the rotation axis, between the bearing outer ring and the sleeve.

Background of the invention

DE 10 2014 220 068 A1 discloses a rolling bearing which has an insulation element on a bearing outer ring for decoupling acoustic vibrations. The insulation element is spaced apart from the bearing outer ring in the radial direction over a large part of its axial width. At the axial ends, the insulation element has radial extensions with which it is supported on the bearing outer ring and is connected to it.

DE 10 2014 118 553 A1 discloses a rolling bearing with a bearing outer ring, an adapter ring and a damping layer. The damping layer is arranged in such a way that it separates the bearing outer ring or the adapter ring into two independent parts.

DE 200 12 676 U1 discloses a connection of a bearing ring to a carrier part. The bearing ring consists of a base body and a surrounding ring. The ring is connected to the base body and has a non-planar contour throughout. The carrier part also has a non-planar contour. An elastomeric element is inserted between the carrier part and the bearing ring. Object of the invention

The invention is based on the object of specifying a rolling bearing that is improved compared to the prior art.

Description of the invention

According to the invention, the object is achieved by a rolling bearing with a bearing outer ring arrangement arranged around an axially extending axis of rotation, which has a bearing outer ring and a sleeve arranged concentrically to the bearing outer ring, wherein a spring element is arranged between the bearing outer ring and the sleeve in the radial direction, perpendicular to the axis of rotation, wherein the spring element is composed of segments all around, wherein at segment ends at which two segments meet, a first support point is formed, which contacts the bearing outer ring, wherein a segment has a second support point, which contacts the sleeve, and wherein a first intermediate space is formed between the spring element and the bearing outer ring, which is filled with a damping element. The rolling bearing is preferably designed as a ball bearing and is arranged around a rotation axis which runs in the axial direction. In the axial direction means in the direction of the rotation axis, regardless of the position of the rotation axis in space. The rolling bearing has a bearing outer ring arrangement which consists of a bearing outer ring, a spring element and a sleeve. The spring element is arranged concentrically to the bearing outer ring and surrounds the bearing outer ring in the circumferential direction. In the circumferential direction means rotating around the axis of rotation clockwise or anti-clockwise. The spring element is further away from the axis of rotation in the radial direction, which runs perpendicular to the axial direction, than the bearing outer ring. The spring element is surrounded all around by a sleeve which is arranged concentrically to the bearing outer ring. The sleeve is further away from the axis of rotation in the radial direction than the spring element. Depending on the application and installation situation, rolling bearings can cause disturbing noises during operation. In gear applications, for example, gearing noises or loose part rattling can occur. Such noises are caused by periodic excitation mechanisms. These lead to noise in the form of airborne sound through direct and indirect transmission. With direct transmission, an excitation source directly causes air pressure fluctuations, which can spread in the form of airborne sound. Indirect transmission is particularly important for the development of noise in gears. Here, a time-varying operating force is introduced into a system structure, where it follows a structure-borne sound transmission chain, also known as a transfer path. In the form of structure-borne sound, the operating force is transmitted from the source through the gear structure to the housing. From there, the structure-borne sound penetrates to the surface, which radiates the airborne sound. The key components in the transmission chain are structural components that are in direct force flow with the housing. These include, for example, bearing plates, bearing shields, ring gears, bearing shells, bearing rings and housing parts. One way to reduce noise is to isolate the components at the interfaces to the housing. Elastomers can be introduced into the rolling bearing for this purpose. However, this vibration decoupling is accompanied by a reduction in the bearing stiffness, which can have a detrimental effect on the operating behavior of other components.

The invention is based on the knowledge that damping vibrations in the rolling bearing is more effective than decoupling them. The rolling bearing according to the invention has a spring element that is divided into segments in the circumferential direction. One segment has design features that are also shown by other segments of the spring element. A number of segments are therefore constructed in the same way. The spring element consists of segments that are lined up in the circumferential direction. The lined up segments form the spring element. One segment has two ends in the circumferential direction. At each end the segment is connected to a directly adjacent segment. The point at which the ends of two circumferentially adjacent segments meet forms a first support point. The first support point is in contact with a surface of the bearing outer ring that is directed radially outwards, i.e. away from the axis of rotation, on a surface of the spring element that is directed radially inwards, i.e. towards the axis of rotation. The first support point of the spring element is supported in the radial direction on the bearing outer ring. The segment has a second support point between the two ends of a segment in the circumferential direction. The second support point is in contact with a surface of the sleeve that is directed radially inwards, on a surface that is directed radially outwards. The second support point of the spring element is supported in the radial direction on the sleeve. At the second support point, the spring element has a maximum distance from the bearing outer ring. Between two ends of a segment in the circumferential direction, a radial distance from the bearing outer ring is formed, which creates a first gap between the spring element and the bearing outer ring. The first space is filled with a material with vibration-reducing properties, a damping element. The spring element is made of metal or plastic. The spring element is preferably designed as a ring with a wave-like or polygon-like contour in the circumferential direction and is self-contained. The spring element can also be slotted axially or radially in the circumferential direction. It can have an axially running gap so that the spring element has two ends that are opposite each other in the circumferential direction. Under load, the spring element implements an elastic deformation in the form of compression. Compression is a reversible displacement of one or more areas of the spring element in one or more directions, which occurs during operation due to the application of force. The spring element has a low stiffness coefficient in relation to the surrounding housing and enclosed bearing. Due to the contact of the bearing outer ring with the spring element at the first support point, vibrations that are transmitted to the bearing outer ring via a shaft, a bearing inner ring and rolling elements, for example, are passed on to the spring element. Since the spring element has a lower stiffness than the surrounding components, the transmitted Energy is translated into an elastic deformation of the spring element, the spring element starts to move. The sleeve ensures that the position of the spring element is defined over its service life. The kinetic energy of the spring element is absorbed by the damping element in the first intermediate space. This transfer chain is a circuit in which the spread of structure-borne noise is prevented by an interaction between the spring element and the damping element. In some applications it is necessary for the spring element to be firmly connected to the bearing outer ring or the sleeve or also to the bearing outer ring and the sleeve. In these cases the spring can be secured against twisting by a weld point or can also be fastened all the way around by a weld seam. The rolling bearing according to the invention is used in particular for supporting an axially preloaded intermediate shaft or input shaft. At least one bearing point is provided with the rolling bearing according to the invention.

Preferably, a segment, starting from a first support point, has a distance from the bearing outer ring in the radial direction, which increases in the circumferential direction, reaches a maximum in a second support point and then decreases again up to a first support point. Preferably, a segment of the spring element increases the radial distance from the bearing outer ring as it runs in the circumferential direction and then reduces it again. A segment is delimited by two segment ends. At the segment ends, the distance in the radial direction from the spring element to the bearing outer ring is minimal, since the spring element contacts the bearing outer ring in this area. In the circumferential direction, the distance within a segment increases in the radial direction between the spring element and the bearing outer ring. The turning point for this is a second support point. A second support point is an area in which the distance in the radial direction between the spring element and the bearing outer ring changes from increasing to decreasing. At a second support point, the radial distance between the spring element and the bearing outer ring reaches a maximum, based on the segment in which the second support point is located. Preferably, a segment has an arcuate contour in the circumferential direction. Preferably, a segment has the profile of a pitch circle in a cross section whose plane is perpendicularly penetrated by the axis of rotation. In the same cross section, the spring element therefore has an M-shaped profile, starting from a second support point to a second support point closest in the circumferential direction, with the corners of the M being rounded. A series of segments with an arcuate contour leads to a spring element which is shaped as a ring which is corrugated in the circumferential direction. A damping element which is located in the first intermediate space therefore takes on a sickle shape in the cross section whose plane is perpendicularly penetrated by the axis of rotation.

The spring element preferably has a polygonal contour in the circumferential direction. The spring element preferably has segments which are made up of straight segment sections in a cross section whose plane is perpendicularly penetrated by the axis of rotation. Starting from two adjacent first support points, a straight segment section leads to a second support point which is located between the two first support points in the circumferential direction. A segment therefore has a tapered contour in the cross section whose plane is perpendicularly penetrated by the axis of rotation. In the same cross section, the spring element therefore has an M-shaped profile starting from a second support point towards a second support point which is closest in the circumferential direction. A series of segments leads to a spring element which has a polygonal contour in the circumferential direction. The spring element is designed as a polygonal ring. A damping element which is located in the first intermediate space therefore takes on a triangular shape in the cross section whose plane is perpendicularly penetrated by the axis of rotation.

Preferably, a second space is formed between the spring element and the sleeve, which is filled with a damping element. Preferably, the sleeve forms a continuous or segmental distance from the spring element in the radial direction. The distance creates a second intermediate space is created. The second intermediate space is filled with a damping element, i.e. a material or material composition which has damping properties. In a cross-section whose plane is penetrated perpendicularly by the axis of rotation, a damping element in the second intermediate space can take on different geometric shapes. These shapes depend on the contour of the spring element. A damping element in a second intermediate space can, among other things, be crescent-shaped in cross-section. The spring element can be partially surrounded by a damping element or completely embedded in a damping material. The material or material composition of a damping element in a second intermediate space can be different from the material or material composition of a damping element in a first intermediate space.

The sleeve preferably has a radial rim on one side axially, which is oriented in the radial direction towards the axis of rotation. The sleeve preferably curves on one side in the axial direction and then runs straight radially inwards, i.e. aligned towards the axis of rotation. The sleeve thus forms a rim on one side axially in the radial direction, i.e. a radial rim. In particular, the radial rim undercuts the bearing outer ring and forms a stop when positioning the bearing outer ring. In addition, the radial rim contributes to the homogeneous distribution of a damping element during production of the rolling bearing. The radial rim contacts the bearing outer ring over a large area. During operation, the bearing outer ring is set in motion. The bearing outer ring rubs against the radial rim of the sleeve, kinetic energy is converted into frictional energy and vibration transmission to other components is reduced. The radial rim of the sleeve therefore contributes to damping and thus noise reduction of the overall system.

Preferably, the spring element is designed in several parts. In a further embodiment, the spring element is composed of several components. In particular, the components are arranged concentrically to one another, ring-like elements. A ring-like element can be a closed or open circular ring or a wave-like or polygon-like profiled ring. The components can be arranged without contact or in contact. The components of the spring element can also be partially or completely connected to one another in a force-fitting, form-fitting or material-fitting manner. In particular, such a combination of components is beneficial as a spring element for vibration damping, in which one component is designed as a ring-like element with a wave-like profile and one component is designed as a round circular ring. The multi-part design of the spring element creates a third intermediate space. The third intermediate space is preferably filled with a damping element. The material or the material composition of a damping element in a third intermediate space can be different from the material or the material composition of a damping element in a first intermediate space or a second intermediate space.

The spring element preferably has recesses in the circumferential direction. The spring element is preferably interspersed with through holes in the circumferential direction. Through holes are holes in the spring element that penetrate the spring element in a radial direction. When a damping element is injected during the manufacturing process, empty spaces are thus accessible from several sides. By allowing the damping element to flow through the spring element, the through holes promote a homogeneous distribution of the damping element. The recesses can be round or square. In addition, the recesses can also be designed as slots.

The damping element is preferably designed as a polymer. The damping element is preferably made of a polymer material. EPDM, polyurethane foam or other elastomers are particularly suitable as materials for the damping element.

Preferably, a method for producing a rolling bearing having the features of claims 1 and 6 comprises the following steps: a) Inserting the bearing outer ring, the sleeve and the spring element into a tool b) Coaxial positioning of the sleeve and the bearing outer ring c) Positioning of the spring element axially spaced from the radial rim of the sleeve d) Axially one-sided injection of a damping element on the side of the rolling bearing axially facing away from the radial rim of the sleeve e) Curing of the damping element.

Preferably, a method for producing a rolling bearing with a bearing outer ring arrangement arranged around an axially extending axis of rotation, which has a bearing outer ring and a sleeve arranged concentrically to the bearing outer ring, wherein a spring element is arranged between the bearing outer ring and the sleeve in the radial direction, perpendicular to the axis of rotation, wherein the spring element is composed of segments in a continuous manner, wherein at segment ends at which two segments meet each other, a first support point is formed, which contacts the bearing outer ring, wherein a segment has a second support point, which contacts the sleeve, and wherein a first intermediate space is formed between the spring element and the bearing outer ring, which is filled with a damping element, wherein the sleeve has a radial rim on one side axially, which is oriented in the radial direction towards the axis of rotation, comprises five steps: In a first step, the bearing outer ring, the sleeve and the spring element are placed in a tool provided. The radial rim of the sleeve serves as a stop when positioning the bearing outer ring. In a second step, the bearing outer ring and the spring element are positioned coaxially in the tool. In a third step, the spring element is positioned at a distance in the axial direction from the radial rim of the sleeve. In a fourth step, a damping element is injected axially on the side of the rolling bearing where there is no radial rim. The damping element is distributed between the bearing outer ring and the spring element in the first space. The damping element can spread out to the axial ends of the spring element and the spring element in this way axially on both sides and radially on one side. The radial rim of the sleeve prevents the damping element from flowing into the space between the bearing outer ring and the sleeve. If the damping element hits the radial rim axially during injection, it is compressed and a part flows a little way in the opposite axial direction. In this way, any cavities that have formed can be closed and the damping element can be distributed homogeneously. In a fifth step, the damping element is cured. As a rule, the entire rolling bearing is heated to a temperature at which the damping element solidifies without the temperature having a hardening effect on the rest of the rolling bearing. One possible method for curing is vulcanization. To cure the damping element, it can also be subjected to local treatment, such as selective irradiation.

Short description of the drawings

The rolling bearing designed according to the invention is explained in more detail below in several preferred embodiments with reference to the accompanying drawings.

Figure 1 shows a perspective axial section of a schematic diagram of the rolling bearing;

Figure 2 shows a cross-section of the rolling bearing from Figure 1;

Figure 3 is an axial plan view of an embodiment of the rolling bearing;

Figure 4 is an axial plan view of another embodiment of the rolling bearing.

Detailed description of the drawings

Figure 1 shows a perspective axial top view of a rolling bearing 1 designed as a ball bearing with a bearing outer ring arrangement 3. A section of the rolling bearing 1 is shown, which shows individual components sometimes cut away in order to depict the structure of the bearing outer ring arrangement 3 in principle. The rolling bearing 1 consists of a rotation axis 2 and a larger diameter bearing outer ring 4 arranged concentrically thereto. Between the bearing inner ring 19 and the bearing outer ring 4 there is a cage 20 which guides rolling elements 21 in the form of balls. The rotation axis 2 runs in the axial direction a and a radial direction r runs perpendicular to the rotation axis 2. The bearing outer ring 4 is part of the bearing outer ring arrangement 3. In the radial direction r, the bearing outer ring 4 is surrounded all around by a spring element 6. The spring element 6 can deform elastically under the action of force. In comparison to the bearing outer ring 4, the spring element 6 has a smaller thickness in the radial direction r; its axial width corresponds approximately to that of the bearing outer ring 4. The spring element 6 has a radially inward-facing boundary surface, i.e. a surface oriented towards the rotation axis 2, and a radially outward-facing boundary surface, i.e. a surface oriented away from the rotation axis 2. The spring element 6 has a corrugated profile in the circumferential direction, i.e. its distance d in the radial direction r from the bearing outer ring 4 alternately decreases and increases. In areas of the spring element 6 in which the distance d of the spring element 6 from the bearing outer ring 4 changes from decreasing to increasing in the radial direction r, a first support point 10 is formed. The spring element 6 is divided into segments 7 in the circumferential direction. A segment 7 has an arcuate contour 14 and two segment ends 8, 9 in the circumferential direction. The spring ring 6 has a corrugated profile over the entire circumference due to a series of segments 7 with the arcuate contour 14. The first support point 10 is formed where a segment end 8 of a segment 7 meets a segment end 9 of a segment 7 adjacent in the circumferential direction. The first support point 10 of the spring element 6 makes contact with the bearing outer ring 4. The first support point 10 is supported with a surface directed radially inwards, i.e. towards the rotation axis 2, on a surface of the bearing outer ring 4 oriented radially outwards, i.e. away from the rotation axis 2. The spring element 6 has recesses 18 in the circumferential direction, which are designed as holes evenly distributed in the circumferential direction. The spring element 6 is surrounded all the way around by a circular ring-shaped sleeve 5, which is further away from the rotation axis 2 in the radial direction r. is spaced apart than the spring element 6. The sleeve 5 has an axial width comparable to that of the spring element 6. Within a segment 7, the distance d of the spring element 6 to the bearing outer ring 4 initially increases in the radial direction r, starting from one segment end 8, and then reaches a maximum distance dM in the radial direction r to the bearing outer ring 4. The distance d then decreases again in the radial direction r to the bearing outer ring 4 as it progresses to the other segment end 9. A second support point 11 is formed where the maximum distance dM in the radial direction r to the bearing outer ring 4 is located. The second support point 11 of the spring element 6 is supported with a surface directed radially outwards, i.e. away from the axis of rotation 2, on a surface of the sleeve 5 directed radially inwards, i.e. towards the axis of rotation 2. Due to the arcuate contour 14 of a segment 7 of the spring element 6 in the circumferential direction, a first intermediate space 12 is formed between the spring element 6 and the bearing outer ring 4. A second intermediate space 16 is formed between the spring element 6 and the sleeve 5. The first intermediate space 12 and the second intermediate space 16 are filled by a damping element 13. The recesses 18 enable a homogeneous distribution of the damping element 13 in the first intermediate space 12 and in the second intermediate space 16 during the manufacturing process.

During operation, vibrations in the overall system are passed on from a body on which the bearing inner ring 19 sits, via the bearing inner ring 19, the rolling elements 21 and the cage 20 to the bearing outer ring 4. The vibrations are transferred to the spring element 6 via the first support point 10. Since the spring element 6 has a lower stiffness coefficient than the surrounding components, the spring element 6 is set in motion. The damping element 13 adjacent on both sides in the radial direction r absorbs a large part of the kinetic energy of the spring element 6. The spread of vibrations and thus structure-borne noise is reduced.

Figure 2 shows a cross section of the rolling bearing 1 shown in Figure 1 in the radial direction r through a plane in which a rotation axis 2 runs. The rotation axis 2 runs in the axial direction a, perpendicular to this runs the radial direction r. The rolling bearing 1 is arranged in the radial direction r around a shaft 22 which runs along the axis of rotation 2, i.e. in the axial direction a. The rolling bearing 1 has an inner bearing ring 19 which rests continuously on the shaft 22. A bearing outer ring 4 is arranged concentrically to the bearing inner ring 19. The bearing outer ring 4 is continuously surrounded by a spring element 6. The spring element 6 is continuously surrounded by a sleeve 5. Rolling elements 21 in the form of balls are rotatably mounted in a cage 20 between the bearing inner ring 19 and the bearing outer ring 4. The axis of rotation 2 divides the cross section of the rolling bearing 1 in the radial direction r through the plane in which the axis of rotation 2 runs, into two halves. A first half of the cross-section lies in the radial direction r above the axis of rotation 2, a second half of the cross-section lies in the radial direction r below the axis of rotation 2. In the first half, starting from the axis of rotation 2, a damping element 13 adjoins the bearing outer ring 4 in the radial direction r. In the axial direction a, it has approximately the width of the bearing outer ring 4. In the radial direction r, further away from the axis of rotation 2 than the damping element 13, the spring element 6 adjoins. The damping element 13 fills a first intermediate space 12 which is formed in the radial direction r between the bearing outer ring 4 and the spring element 6. The sleeve 5, which has a radial rim 17 on one side axially, is directly adjacent to the spring element 6. The radial rim 17 runs radially inwards, i.e. oriented towards the axis of rotation 2. Starting from the rotation axis 2, the spring element 6 is arranged in the second half of the cross section of the rolling bearing 1 in the radial direction r, adjacent to the bearing outer ring 4. The damping element 13 is directly connected to the spring element 6. The end of the rolling bearing 1 in the radial direction r is formed by the sleeve 5, which has the radial rim 17. The radial rim 17 runs analogously to its course in the first half of the cross section, radially inwards, i.e. towards the rotation axis 2. The damping element 13 fills a second intermediate space 16, which is formed in the radial direction r between the spring element 6 and the sleeve 5. The bearing outer ring 4, the spring element 6, the damping element 13 and the sleeve 5 together form a bearing outer ring arrangement 3 for damping the vibrations of the rolling bearing 1. In the first half of the cross-section A second support point 11 of the spring element 6 is shown in the cross-section of the rolling bearing 1. The second support point 11 is an area in which the spring element 6 has a maximum distance dM in the radial direction r from the bearing outer ring 4. At the second support point 11, the spring element 6 is supported on the sleeve 5 in the radial direction r. A first support point 10 of the spring element 6 is shown in the second half of the cross-section of the rolling bearing 1. At the first support point 10, the spring element 6 is supported on the bearing outer ring 4 in the radial direction r, and is therefore in contact with it. During operation, vibrations are passed on to the spring element 6 via the bearing outer ring 4. The spring element 6 has a reduced rigidity, which is sufficient to bear the forces that occur during operation. The spring element 6 is set in motion and the damping element 13 absorbs a large part of the kinetic energy that occurs. The radial rim 17 of the sleeve 5 undercuts the radially extending boundary surface of the bearing outer ring 4 on this side and contacts it over a large area. This converts kinetic energy into friction energy. The radial rim 17 of the sleeve 5 thus contributes to reducing the propagation of vibrations.

In the method for producing a rolling bearing 1 according to the invention, the radial rim 17 enables the axially injected damping element 13 to strike the radial rim 17. After the injection of the damping element 13, the spring element 6 is guided in the axial direction a until it stops against the radial rim 17, which enables precise positioning of the spring element 6. The stop of the radial rim 17 initially compresses the damping element 13 in the axial direction a and then moves axially in the opposite direction. This fills up any cavities that remained when the damping element 13 was injected. This ensures that the first intermediate space 12 and the second intermediate space 16 are completely filled with the damping element 13 and that the damping element 13 is evenly distributed.

Figure 3 shows a plan view from the axial direction a of a further embodiment of the rolling bearing 1 according to the invention. A rotation axis 2, which before it is aligned in the axial direction a, penetrates the viewing plane in Figure 3 perpendicularly. A radial direction r runs perpendicular to the axis of rotation 2 and thus also perpendicular to the axial direction a. A bearing inner ring 19, a cage 20 which rotatably guides rolling elements 21, and a bearing outer ring 4 are arranged concentrically around the axis of rotation 2, starting from the axis of rotation 2. A spring element 6 is arranged circumferentially around the bearing outer ring 4. Starting from the axis of rotation 2, the spring element 6 is followed by a sleeve 5 arranged concentrically to the bearing outer ring 4. The spring element 6 is designed as a polygonal ring. The spring element 6 is divided into interconnected segments 7 which are composed of straight segment sections 26, 27. A segment 7 has two segment ends 8, 9 in the circumferential direction. An area where two segment ends 8, 9 meet forms a first support point 10. A second support point 11 is located between two first support points 10. At the second support point 11, a turning point is reached in relation to the distance d of the spring element 6 in the radial direction r to the bearing outer ring 4. The distance d in the radial direction r, which increases in the circumferential direction up to the second support point 11, decreases again after the second support point 11. At the support point 11 itself, a maximum radial distance dM between the spring element 6 and the bearing outer ring 4, relative to a segment 7, is reached. Starting from a segment end 8, a straight segment section 26 leads to the second support point 11. From there, a straight segment section 27 leads to a segment end 9. The segment sections 26, 27 together form a pointed contour within a segment 7. A series of segments 7 leads to a polygon-like contour 15 of the spring element 6 in the circumferential direction. The polygonal contour 15 creates a first gap 12 between the spring element 6 and the bearing outer ring 4 and a second gap 16 between the spring element 6 and the sleeve 5. The first gap 12 and the second gap 16 are filled with a damping element 13. The spring element 6 designed as a polygonal ring enables the stiffness coefficient of the spring element 6 to be adjusted. The higher the number of segments 7, the lower the stiffness coefficient of the spring element 6. The spring element 6 can thus deform elastically in such a way that as is appropriate for the application. This allows application-oriented damping. The bearing outer ring 4, the spring element 6, the damping element 13 and the sleeve 5 together form a bearing outer ring arrangement 3 and thus a unit for reducing the noise of the rolling bearing 1.

Figure 4 shows a plan view from the axial direction a of a further embodiment of the rolling bearing 1 according to the invention. A rotation axis 2, which is aligned in the axial direction a, penetrates the viewing plane perpendicularly in Figure 4. A radial direction r runs perpendicular to the rotation axis 2 and thus also perpendicular to the axial direction a. Starting from the rotation axis 2, a bearing inner ring 19, a cage 20 guiding several rolling elements 21 and a bearing outer ring 4 are arranged concentrically to one another. A spring element 6 is arranged around the bearing outer ring 4. An annular sleeve 5 is arranged around the spring element 6. The spring element 6 is made up of segments 7 in the circumferential direction and consists of two components 23, 24, which are arranged concentrically to one another and to the bearing outer ring 4. A segment 7 has two segment ends 8, 9 in the circumferential direction. A first component 23 of the spring element 6 has a wave-like profile. The wave-like profile is created by a series of arcuate contours 14 in the circumferential direction. The first component 23 has an arcuate contour 14 within a segment 7. A second component 24 of the spring element 6 is designed as a circular ring. Starting from the bearing outer ring 4, the first component 23 of the spring element 6 adjoins the bearing outer ring 4. The first component 23 is surrounded by the second component 24 designed as a circular ring. The second component 24 is further away from the bearing outer ring 4 in the radial direction r than the first component 23 of the spring element 6. The spring element 6 has a first support point 10 in the circumferential direction, at which a segment 7 merges into an adjacent segment 7, i.e. two segment ends 8, 9 meet. At the first support point 10, the spring element 6 makes contact with the bearing outer ring 4. Each segment 7 of the spring element 6 has a second support point 11 in the circumferential direction, at which the spring element 6 is the sleeve 5. The second support point 11 is each located centrally on a segment 7 in the circumferential direction. At the second support point 11, the spring element 6 has a maximum radial distance divi, based on a segment 7, from the bearing outer ring 4. The first component 23 with the arcuate contours 14 of the spring element 6 creates a first intermediate space 12 between the spring element 6 and the bearing outer ring 4. The circular ring shape of the second component 24 of the spring element 6 creates a third intermediate space 25 between the first component 23 and the second component 24. The first intermediate space 12 and the third intermediate space 25 are filled with a damping element 13. The bearing outer ring 4, the spring element 6, the damping element 13 and the sleeve 5 together form a bearing outer ring arrangement 3, which dampens vibrations that occur and reduces the transmission of structure-borne sound. By designing the spring element 6 in several parts, the stiffness of the spring element 6 can be designed to suit the application, and the additional, third space 25 is created for the damping element 13. This allows the damping properties of the rolling bearing 1 required for the respective application to be set for ongoing operation, whereby a low-noise rolling bearing 1 can be provided.

List of reference symbols

1 rolling bearing

2 Rotation axis

3 Bearing outer ring arrangement

4 Bearing outer ring

5 Sleeve

6 Spring element

7 Segment

8 Segment end

9 End of segment

10 first support point

11 second support point

12 first space

13 Damping element

14 arched contour

15 polygonal contour

16 second space

17 Radial edge of the sleeve

18 recesses

19 Bearing inner ring

20 cage

21 rolling elements

22 Wave

23 first component of the spring element

24 second component of the spring element

25 third space

26 Segment section

27 Segment section a axial direction d distance in radial direction to the bearing outer ring dM maximum distance in radial direction to the bearing outer ring r radial direction

Claims

Claims Rolling bearing (1) with a bearing outer ring arrangement (3) arranged around an axially extending rotation axis (2), which has a bearing outer ring (4) and a sleeve (5) arranged concentrically to the bearing outer ring (4), wherein in the radial direction (r), perpendicular to the rotation axis (2), a spring element (6) is arranged between the bearing outer ring (4) and the sleeve (5), characterized in that the spring element (6) is continuously composed of segments (7), wherein at segment ends (8, 9) at which two segments (7) meet, a first support point (10) is formed, which contacts the bearing outer ring (4), wherein a segment (7) has a second support point

(11 ) which contacts the sleeve (5), and wherein between the spring element (6) and the bearing outer ring (4) a first intermediate space

(12) which is filled with a damping element (13). Rolling bearing (1) according to claim 1, characterized in that a segment (7), starting from a first support point (10), has a distance (d) from the bearing outer ring (4) in the radial direction (r), which increases in the circumferential direction, reaches a maximum (divi) in a second support point (11) and then decreases again up to a first support point (10). Rolling bearing (1) according to claim 1, characterized in that a segment (7) has an arcuate contour (14) in the circumferential direction. Rolling bearing (1) according to claim 1, characterized in that the spring element (6) has a polygonal contour (15) in the circumferential direction. Rolling bearing (1) according to claim 1, characterized in that a second intermediate space (16) which is filled with a damping element (13). Rolling bearing (1) according to claim 1, characterized in that the sleeve (5) has a radial rim (17) on one side axially, which is oriented in the radial direction (r) towards the axis of rotation (2). Rolling bearing (1) according to claim 1, characterized in that the spring element (6) is designed in several parts. Rolling bearing (1) according to claim 1, characterized in that the spring element (6) has recesses (18) all around. Rolling bearing (1) according to claim 1, characterized in that the damping element (13) is designed as a polymer. Method for producing a rolling bearing (1) according to claim 6, dependent on claim 1, with the following steps: a) inserting the bearing outer ring (4), the sleeve (5) and the spring element (6) into a tool b) coaxial positioning of the sleeve (5) and the bearing outer ring (4) c) positioning the spring element (6) axially spaced from the radial rim (17) of the sleeve (5) d) axially one-sided injection of a damping element (13) on the side of the rolling bearing (1) axially facing away from the radial rim (17) of the sleeve (5) e) hardening of the damping element (13).