EP2841780A1

EP2841780A1 - Converter collar bearing for a torque converter

Info

Publication number: EP2841780A1
Application number: EP13719082.3A
Authority: EP
Inventors: Alexander Pabst; Frank Beeck
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2012-04-27
Filing date: 2013-04-24
Publication date: 2015-03-04
Also published as: DE102012222279A1; WO2013160319A1; DE102012222279B4; US20150055908A1; US9353794B2

Abstract

The invention relates to a bearing point (1) for rotatably mounting an impeller (2) of a torque converter (5) in a housing (4), said impeller (2) being connected to a converter collar (3) by means of which the impeller (2) is rotatably mounted in the housing (4) at said bearing point (1) by means of at least one roller bearing (6). The roller bearing (6) comprises an outer roller raceway (19) that is associated with the converter collar (3) and faces radially outwards, and an inner roller raceway (18) that is associated with the housing (4) and faces radially inwards, as well as rollers (17) that are arranged between said roller raceways.

Description

TRANSDUCER NECK STORAGE OF A TORQUE TRANSFORMER

The invention relates to a bearing for rotatably supporting a pump wheel of a torque converter in a housing, wherein the impeller is connected to a converter neck, via which the impeller is rotatably mounted at the bearing by means of at least one roller bearing in the housing, wherein the roller bearing a the Transducer neck associated, radially outwardly facing outer Wälzlaufbahn and a housing assigned, radially inwardly facing inner Wälzlaufbahn and arranged radially between the Wälzlaufbahnen rollers. The invention further relates to a roller bearing for such a bearing, a roller bearing in such a bearing and a transmission with a torque converter in which a connected to a transducer neck impeller of the torque converter is rotatably mounted on the transducer neck at such a bearing point.

Such an arrangement of a connected to a transmission hydrodynamic torque converter for a motor vehicle is shown in DE 41 34 369 A1. The transmission input shaft is connected in a torsionally rigid manner to the turbine wheel of the torque converter. A cylindrical extension of the impeller of the torque converter forms the transducer neck. If necessary, the impeller can be connected to a primary pump, which supplies the transmission with pressure medium and the torque converter with oil. The impeller is rotatably mounted on a housing via the transducer neck at a bearing point by means of a rolling bearing designed as a roller bearing. Due to axial misalignment or tilting of the axes of rotation in the arrangement, unfavorable, in particular non-uniform, loads of the bearing points or of the roller bearings are associated with disadvantageous noise development.

From FR 27 89 458 A1 designed as a roller bearing bearings for supporting a steering column is known. As a measure to be able to compensate for a bearing clearance in the installed state, the roller bearing comprises an outer Bearing ring which is circumferentially bounded on both sides by end portions which are connected locally via tabs with a central circumferential portion. The inside of a raceway for the rolling elements forming portion is guided on the shaft or the steering column mutually. Furthermore, the central circumferential portion for influencing the bearing clearance on a curved, narrowing each in the region of the tabs rolling element track, whereby the rolling elements are resiliently biased in the installed state of the roller bearing. The invention has for its object to provide a concept with which the bearing clearance of a rolling bearing for supporting a transducer neck of a torque converter can be largely eliminated.

The solution of this problem results from the characterizing features of claim 1 and a method according to claim 10. The dependent, back to the claim 1 claims give each advantageous developments of the invention again.

According to the invention, the bearing point has at least one radially elastically executed portion of a sleeve provided with the inner Wälzlaufbahn sleeve of the roller bearing. The sleeve is in the outline with the exception of the or the elastic sections a hollow cylindrical component. The wall thickness of this sleeve is low compared to their diameter. The ratio of inner diameter of the regions of the inner Wälzlaufbahn described by a radius to the radial wall thickness of the sleeve is preferably> the value 10. The material of the sleeve is preferably steel sheet. At least on the inner race, the section has a geometry deviating from the cylindrical shape and at the same time forms a raceway curvature for the rolling bodies designed as rollers. The section is resiliently biased radially over the raceway arch against at least one roller of one row of the roller bearing, but preferably against two, three or even more of the rollers. Characterized in that the portion of the sleeve is biased radially against the roller (s), these are based radially inwardly directed on the axis of rotation on the outer Wälzlaufbahn from. As a result, the roller bearing is biased at least in the areas and thereby at least backlash-free or largely free of play, the sleeve portion elastic wherein the sleeve portion is resiliently biased against the rollers, and thus the transducer neck is resiliently biased relative to the housing. Usually have radial bearings manufacturing and assembly due to radial games. The roller bearing is a radial bearing in which essentially only radial forces are supported. Due to manufacturing tolerances and for reasons of mountability, radial bearings usually have always radial games. The bearing clearance sets in the annular gap between the rollers or rolling elements and their associated Wälzlaufbahnen. The radial distance between the opposing Wälzlaufbahnen is the sum of the diameter of the rollers and from the radial play. The rollers can move within this game radially between the Wälzlaufbahnen. Thus, the Wälzlaufbahnen can move within this game against each other, which can lead to adverse noise.

Furthermore, disadvantages can be set at bearings of bearings for storage of the converter neck by a misalignment, radial shock, tilt or secondary axis error of the axes of rotation. A thus triggered staggering or tumbling of the rotating components causes unfavorable, especially non-uniform loads on the bearings or rolling bearings and an adverse noise. Under axial offset or offset is the inclination of the axis of rotation for ideal alignment and radial shock is the deviation from the axis-parallel ideal position of axes of rotation or axes of symmetry communicating components, as from the axis of rotation of the transducer neck to the axis of symmetry of the housing bore on the bearing seat to understand. The advantage of the arrangement according to the invention is that, for example, a production-related misalignment and radial shock are elastically received and cushioned at the bearing by the elastically clamped against the rollers portions of the inner Wälzlaufbahn. When the converter neck rotates relative to the housing, the rolling elements of the roller bearing roll on the Wälzlaufbahnen and pass successively the bottlenecks, the bearing clearance eliminating elastic first portions which protrude from the second portions further in the direction of the outer Wälzkörperlaufbahn.

Preferably, the roller bearing includes at least three uniformly circumferentially distributed first, the radial distance between the Wälzkörperbahnen narrowing portions of the sleeve, each including a transverse-bale raceway curvature with a defined roundness deviation. Through the raceway curvature of the sections, a play-free or at least largely play-free roller bearings can be realized, with individual sections of the sleeve intentionally compress elastically under radial load. Advantageously, by the structural design or the shape of the polygonal-like sections in conjunction with the raceway curvature, the elasticity, the compression can be adjusted to the self-adjusting radial load. By the roller bearing according to the invention, in which the elasticity of the sleeve completely or virtually eliminates the game, a noise-optimized roller bearing can be advantageously realized.

Roller bearings are roller bearings with rollers as rolling elements. The rolling bearings have an inner raceway and an outer raceway between which a row or more axially adjacent rows of rolling elements are circumferentially arranged about an axis of rotation in succession. The raceways are optionally on the surface of bearing rings, ie the inner raceways are inside on the surface of outer rings and the outer raceways are formed on the outside of the surface of inner rings or directly on portions of the O- berfläche of the components to be stored. The outer race of the rolling elements is formed in this case either directly on the surface portion of the converter neck or on an inner ring. The inner race is formed either in a housing, for example in a housing of a primary pump or in an outer ring, which sits in the housing. As rolling elements for the roller bearing rollers, such as needles or cylindrical rollers can be used. Rollers are formed outside cylindrically in their basic form and provided with two end faces. Optionally, rollers with a slightly convex outer surface deviating from the outer cylindrical shape can be used. The end faces are preferably flat or flat or convex or concave. Needles are roller-like rolling elements with a ratio of their length to the nominal diameter of the lateral surface, which corresponds to the numerical value 3. Cylindrical rollers have a much smaller ratio. According to a further embodiment of the invention, the roller bearing includes a cage which circumferentially and / or axially adjacent to each other leads and / or fixed the rollers or rolling elements, wherein for the positive reception or fixation of the cage comprises a rotation of the rollers not influencing holding elements. A preferred embodiment of the invention provides that the elastic first portion of the inner Wälzlaufbahn the sleeve of the roller bearing has a convex, transverse-curved track curvature. Advantageously, the aligned in the direction of the axis of rotation of the roller bearing raceway curvature improves the elasticity of the first portion of the inner sleeve Wälzlaufbahn. To increase a contact surface between the sleeve and the rollers or the rolling elements forms a central, flattened zone in the region of a vertex or inflection point of the track curvature an advantageous, cooperating with the rollers enlarged contact zone. As a further influence on the elasticity of the roller bearing, it is advisable to provide different wall thicknesses for the first sections of the inner roller raceway enclosing a raceway curvature.

According to the invention, the raceway curvature can also be constructively designed so that set in the installed state of the roller bearing in the bearing for both a career straightness and for a roundness deviation defined measurement ranges. For the track straightness, a dimension of> 0.01 mm is provided in the installed, pressed-in state. In the area of the largest diameter, the mountain, a measurement range between 0.01 0.02 mm and for the smallest diameter range, the valley, a dimension of> 0.02 to 0.05 mm. To realize these dimensional ranges, a tolerance range of the track straightness of 0.015 to 0.05 mm is intended for the production of the sleeve. As roundness deviation, a dimension of> 0.02 mm is preferably provided for the installed or pressed-in sleeve of the roller bearing. An upper limit for the roundness deviation is 0.04 mm. Accordingly, a tolerance range of 0.2 to 0.35 mm is provided, which adjusts for the roundness deviation after completion of the sleeve in the uninstalled, loose state.

A further embodiment of the invention provides that the inner Wälzlaufbahn the roller bearing, viewed in the cross-sections transverse to the axis of rotation of the converter neck, at least two or three of the first regions. The radial extent by which the portion of the inner Wälzlaufbahn at the elastic region projects radially further in the direction of the axis of rotation of the roller bearing than the remaining regions, corresponds to at least the greatest possible radial clearance, which is bridged by the prestressed first portion or approximately as large as this game. The dimensions by which at least two, better three, the sections or the first areas each project further, correspond to at least half of the radial clearance or are greater than this game.

Typically, the rolling elements of a roller bearing roll in a hollow cylindrical annular gap between the Wälzlaufbahnen on the inner and outer Wälzlaufbahn. The radial distance between the inner and the outer Wälzlaufbahn corresponds radially to the diameter of the rollers plus the radial clearance. The basic principle of the play release of the bearing of the converter neck is that the inner cylindrical inner rolling raceway, which is usually described by a radius, projects radially in the direction of the axis of rotation at the elastic portions of the sleeve in the direction of the outer cylindrical rolling raceway. At these sections, the shape of the rolling track therefore deviates from the cylindrical shape, so that bottlenecks are formed at these sections in the hollow-cylindrical annular gap. The Dimension at the bottlenecks then corresponds at most to the smallest possible diameter of the rollers or is even smaller. In this case, the respective elastic portion bulged in the direction of the axis of rotation or be flattened tangentially aligned. Alternatively, first and second regions of the circular cylindrical shape deviating geometries, so that the sleeve in cross-sections, for example, designed triangular or polygonal. Upon rotation of the roller bearing, the rollers roll on the Wälzlaufbahnen and pass one after the other or the bottlenecks. At standstill, at least one of the rollers between the two Wälzlaufbahnen remains clamped at the bottleneck. Thus, in any operating condition of the bearing for bearing an impeller in the roller bearing, the bias is ensured and rattling noises are avoided.

As a material for the sleeve of the roller bearing steel sheet is preferably provided. The sleeve is either at least partially supported radially in the bore of the housing or in a bearing outer ring with or without radial bias. However, the first portion with the first portion of the Wälzlaufbahn is freely spaced radially in the direction of the housing or the outer ring. The distance between the outer ring or the housing is at least as large as the elastic region protrudes radially from the circular cylindrical Laubahnform radially in the direction of the axis of rotation. The elastic portions can thereby evade within the allowable dimensional deviations adapted to the production-less dependent changes of the radial actual dimensions. In addition, the Wälzlaufbahnen soft at the first areas at radial impact and tilted even when the rotating converter neck, without the backlash is lost. In addition, vibrations are damped in the bearing.

A roller bearing designed in accordance with the invention is preferably intended for a bearing point enclosing a roller bearing, via which a pump wheel is mounted. Furthermore, the inventive concept for a transmission with a torque converter can be used, in which a connected to a converter neck impeller of the torque converter via the converter neck a bearing with a roller bearing according to the invention is rotatably mounted on or in a housing.

According to claim 10, a method including the following steps is provided for producing a roller bearing for a bearing. First, the production of a sleeve with a fixed board by forming a metal strip by means of a drawing process. Thereafter, a beading of the sleeve including a perforation of the flange is provided. The preferably executed as profiling in a crown perforation on the radially inwardly directed side of at least one board is used for identification and thus as protection against incorrect assembly. In addition, the perforation can be used for positive recording in an automated assembly. As a further step, inserting the sleeve into a die to form a polygon shape is provided. The tool, the die is designed so that after the forming process, the sleeve has both a defined roundness deviation and a raceway curvature in the polygonal sections. This is followed by a wear resistance improving heat treatment of the sleeve. Subsequently, the roller bearing is completed by components, such as a cage and rollers or rolling elements, are inserted into the sleeve. To form a bearing, the roller bearing is pressed into a receiving bore of a housing and positioned. Finally, an insertion and fixing of the converter neck takes place in the bearing.

Further features of the invention will become apparent from the following description of the figures in which embodiments of the invention are shown, wherein the invention is not limited to these embodiments. Showing:

Fig. 1 shows schematically a transmission with a bearing point, via which an impeller is rotatably mounted on a housing;

2 shows in a partial section the bearing point according to FIG. 1 with a roller bearing for mounting a converter neck; 3 shows a cross section through the bearing point according to FIG. 1 transverse to the axis of rotation of the roller bearing; 4 shows a measurement chart for the roundness of a sleeve of the roller bearing;

5 shows a detail section 5-5 of the roller bearing according to FIG. 1;

6 shows a measuring record for the straightness measurement of the roller bearing sleeve;

7 shows a cross section through the roller bearing of the bearing; 8 shows a detailed view of the roller bearing according to FIG. 7. FIG. 1 schematically shows, simplified, a gear 7 with a bearing 1 for rotatably supporting a pump wheel 2 on a housing 4. The pump wheel 2 of a torque converter 5 is connected to a transducer neck 3 , The transducer neck 3 is rotatably supported by means of at least one roller bearing 6 in the housing 4 about the rotation axis 8 of the impeller 2. The housing 4 is, for example, a housing 4 of a primary pump, not shown, via which the torque converter 5 and the transmission 7 are supplied with pressure medium. The axis of rotation 8 of the pump impeller 2 is also the axis of rotation 8 of a turbine wheel 9, a transmission input shaft 10 and a stator 1 1. The turbine 9 of the torque converter 5 is connected to the transmission input shaft 10 of the adjoining the torque converter 5 transmission 7, which is also aligned concentrically to the axis of rotation 8. The transmission 7 is symbolized only by the gears 12 and 13. The concentric with the axis of rotation 8 stator 1 1 of the torque converter 5 is supported via a freewheel 14.

In Fig. 2 is a partial section through the bearing 1, an arrangement of the roller bearing 6 for supporting the transducer neck 3 in a housing shown in detail. The roller bearing 1 comprises an outer ring 15, designed as According to the invention, formed from sheet metal, at least in some areas elastically yielding sleeve 16 and rollers 17 in the form of needles, which are guided on an axis of rotation 8 facing inner Wälzlaufbahn 18 and on a side facing away from the rotation axis 8 outer Wälzlaufbahn 19. The outer Wälzlaufbahn 19 is formed directly on a surface portion 20 of the converter neck 3 and the inner Wälzlaufbahn 18 inside of the sleeve 16. In the annular gap 21 between the Wälzlaufbahnen 18 a plurality of rollers 17 are arranged, all having a same nominal diameter. Of the rollers 17, however, only one roller 17 is visible in the partial section. The construction of such a roller bearing 6 is illustrated by the illustration according to FIG. 3.

FIG. 3 shows an arbitrary, transverse to the axis of rotation 8 directed cross section through the bearing 1 with the roller bearing 6. As can be seen from this illustration, the rollers 17 circumferentially adjacent in an annular gap 22 radially between the inner Wälzlaufbahn 18 and at arranged the converter neck 3 outer Wälzlaufbahn 19 and guided in a cage 24 circumferentially evenly spaced from each other. The bearing 1 has two radially elastically executed portions 23 of the provided with the inner Wälzlaufbahn 18 sleeve 16 of the roller bearing 6. Each elastic portion 23 is resiliently biased radially with a first portion of the inner Wälzlaufbahn 18 against two on the outer Wälzlaufbahn 19 supporting rollers 17. The inner Wälzlaufbahn 18 of the roller bearing 6 is in the cross section transverse to the axis of rotation 8 of the converter neck 3 viewed at least a first portion 25 of the elastically formed portion 23 further in the direction of the axis of rotation 8 forth than the other three, to the respective first area 25 circumferentially adjacent second regions 26 of the Wälzlaufbahn 18. The outer Wälzlaufbahn 19 of the roller bearing 6 is externally cylindrical. The inner Wälzlaufbahn 18 is divided into two elastic portions 23 and two adjacent to the elastic regions and each supported in the direction of housing 4 regions 27. As already mentioned, the respective first section 23 with the first area 25 is prestressed radially elastically against two rollers 17 and is deflected over the second area. sections 27 supported radially opposite to the housing 4. The length of the respective second region 26 or 26 'of the inner Wälzlaufbahn 18 corresponds in any cross-sections the radians of a circular arc, which is in each case by the angle Ch or a ₂ described. The second regions 26 and 26 'are described by a common radius originating from the axis of rotation 8 and formed on the inside of the second portions 27 of the sleeve 16. The second sections 27 nestle with the side facing away from the inner Wälzlaufbahn 18 side in the inner cylindrical bore 28 of the housing 4 and are thus supported there. Although the first regions 25 are also convexly curved when viewed from the axis of rotation 8, they have a flattened or oval profile relative to the first regions 25. On the elastic portion 23, a gap 29 forms on the rear side and thus on the side facing away from the first region 25 with respect to the inner wall of the bore 28, whereby the rollers 17 are resiliently biased and supported on the second portions 27 in the bore 28. Between the inner Wälzlaufbahn 18 and the rollers 17 are corresponding to the number of non-elastically preloaded rollers 17 radial games S1, S2, S3, S4 formed up to S _max , where S _{max is} the largest possible radial clearance S in the bearing 1. The gap 29 has at the widest point at least one gap, which corresponds to the maximum possible play S _max .

FIG. 4 shows a so-called roundness measurement chart 30, with which the result of measuring the roundness of a sleeve 16 of a roller bearing is described. In such a measurement, the centered on its axis of rotation 8 sleeve 16 is traversed either on the inner diameter or the outer diameter on a circumferential line with a probe. The deviations from the ideal circle are recorded. With the outer circumferential scale 32, the full angle 360 ° of a circle is subdivided into 36 × 10 ° measurement regions on the circumference, so that the radian which extends over the three first regions 25 and the three second regions 26 can be determined. The regions 25 and 26 are each represented by the line 33, which describes the deviations of these from an ideal line 34 or 35 which predetermines the roundness. The maximum deviation from the rounding unit at the respective first area 25 corresponds to the radial distance between the lines 34 and 35 and is preferably in a range between 40 to 60 μηη. FIG. 5 shows a detail section 5-5 of the roller bearing 6 according to FIG. 1 in a radially preloaded installation position, in which a radial force acts on the sleeve 16 via an outer contour and from there is transmitted to the roller 17 via a track curvature 36. The additionally introduced in the polygon-like contour of the sleeve 16, extending from lateral rims 37,38, extending in the direction of the rollers 17 career curvature 36 causes improved elasticity of the roller bearing 6. Furthermore, by means of a variation or different wall thicknesses S of the sleeve 16 in Range of career curvature 36 elasticity can be influenced. As a measure to reduce the surface pressure between the rollers 17 and the sleeve 16, the track curvature 36 includes centrally a flattened, a contact zone 36 enlarging area.

According to the measurement record in FIG. 6 for measuring straightness, the track curvature 36 of the sleeve 16 shows a continuous rise starting from the lateral rims 37, 38. A maximum curvature Y is established in the region of a flattened zone of the track curvature 36 forming the contact zone 36.

FIG. 7 shows a cross section through the roller bearing 6, consisting of the sleeve 16 which encloses the cage 24 and the rollers 17 inserted therein. For axial guidance of the cage 24, the sleeve 16 laterally comprises two opposite, radially inwardly facing rims 36,37.

FIG. 7 shows a detailed view of the roller bearing 6 according to the arrow direction of FIG. 7 and illustrates an end profiling 39 of the rim 38 of the sleeve 16. The profiling 39, also referred to as a crown form, preferably comprises α over the entire inner periphery of the rim 38 at an angle α spaced round recesses. The profiling simplifies, for example, Furthermore, in order to avoid incorrect assembly by means of the profiling 39, an individual identification of the roller bearing 6 can take place.

reference numeral

1 storage location

2 impeller

3 converter neck

4 housing

5 torque converter

6 roller bearings

7 gears

8 rotation axis

9 turbine wheel

10 transmission input shaft

1 1 stator

12 gear

13 gear

14 freewheel

15 outer ring

16 sleeve

17 roll

18 Wälzlaufbahn inside

19 Wälzlaufbahn outside

20 surface section

21 annular gap

22 annular gap

23 section, first elastic of the sleeve

24 cage

25 area, first of the inner Wälzlaufbahn

26 area, second of the inner Wälzlaufbahn

27 section, second supported sleeve 28 bore, internal cylindrical of the housing

29 gap

30 measurement record

31 career curvature scale

line

ideal line

contact zone

shelf

profiling

Claims

claims

Bearing point (1) for rotatably supporting a pump wheel (2) of a torque converter (5) in a housing (4), wherein the impeller

(2) is connected to a transducer neck (3), via which the impeller (2) at the bearing point (1) by means of at least one roller bearing (6) is rotatably mounted in the housing (4), wherein the roller bearing (6) has a Having transducer neck (3), radially outwardly facing outer Wälzlaufbahn (19) and a housing (4) associated, radially inwardly facing inner Wälzlaufbahn (18) and arranged radially between the Wälzlaufbahnen rollers (17), characterized in that the Bearing point (1) has at least one radially elastically executed portion (23) provided with the inner Wälzlaufbahn (18) sleeve (16) of the roller bearing (6), wherein the one elastic raceway curvature (31) enclosing portion (23) radially yielding against it on the outer Wälzlaufbahn (19) supporting at least first roller (17) of the rollers (17) biased and thereby radially opposite to the housing (4) is supported, wherein the transducer neck

(3) via the first roller (17) and the resilient portion (23) adjacent to the first roller (17) is radially elastically supported by radial play freely elastically on the housing (4).

Bearing point according to one of the preceding claims, characterized in that the convex, transverse ball raceway curvature (31) of the elastic portion (23) of the sleeve (16) is aligned in the direction of the axis of rotation (8).

Bearing point according to claim 2, characterized in that the raceway curvature (31) of the portion (23) of the sleeve (16) has different wall thicknesses (S) and with the rollers (17) cooperating, flattened contact zone (36).

4. Bearing according to one of the preceding claims, characterized in that in the installed state of the roller bearing (6) for the raceway curvature (31) of the polygonal sleeve (16) sets a career straightness> 0.01 mm and a roundness deviation> 0.02 mm ,

5. Bearing according to one of the preceding claims, characterized in that the inner Wälzlaufbahn (18) of the roller bearing (6), viewed in the cross-sections transverse to the axis of rotation (8) of the converter neck (3), at least three of the first regions (25) ,

6. Bearing according to one of the preceding claims, characterized in that at least a portion of the second regions (26) directly radially on the housing (4) bear inside, that the sleeve (16) back of the first portion (25) and the Housing (4) are radially spaced from each other, wherein the first region (25) at least over directly to the first region (25) adjacent to the remaining regions (26) on the housing (4) is supported.

7. bearing according to one of the preceding claims, characterized in that at least a portion of the second regions (26) directly radially on the housing (4) rest inside, that the rear side of the first region (25), the sleeve (16) and the housing ( 4) are radially spaced from one another, wherein the first region (25) is supported on the housing (4) at least over the remaining regions (26) adjacent to the first region (25) and in that the sleeve (16) and the Housing (4) are spaced apart by at least a first dimension, which is equal to or greater than a second dimension, around which the inner Wälzlaufbahn (18) at the first region (25) radially further protrudes than the inner Wälzlaufbahn (18) the second areas (26).

8. Bearing point according to one of the preceding claims, characterized in that the inner Wälzlaufbahn (18) of the roller bearing (6), viewed in cross-sections transverse to the axis of rotation (8) of the transducer neck (3), protruding further in the direction of the axis of rotation (8) at at least a first portion (25) of the resilient portion (23) than in the circumferential direction toward the first portion (25) adjacent second areas (26), wherein at least a portion of the inner Wälzlaufbahn (18) is described all the second areas (26) by a common, emanating from the axis of rotation (8) radius.

9. Bearing according to one of the preceding claims, character- ized in that the sleeve (16) is made of sheet metal and viewed in the cross-sections has a contour which is outlined inside of the shape of a circular cylinder and at least at the first region (25 ) deviates inwardly from the shape of the circular cylinder.

10. A method for producing a roller bearing (6) for a bearing (1) according to one of claims 1 to 9, comprising the following steps:

Producing a sleeve (16) with a fixed board by forming a metal strip by means of a drawing process;

Crimping the sleeve (16) and then profiling or perforating at least one rim (38);

Inserting the sleeve (16) into a die to form a polygon shape having a roundness deviation and raceway curvature (31); Heat treatment of the sleeve (16);

Mounting components, such as a cage (24) and rollers (17) or rolling elements in the sleeve (16) for completing the roller bearing (6);

Pressing in and fixing the roller bearing (6) in a receiving bore (28) of a housing (4) to form a bearing (1);

Inserting and fixing a converter neck (3) in the bearing (1).