DE102016211144A1 - Double row tapered roller bearing, as well as including the same realized bearing arrangement, in particular for a pinion head - Google Patents

Abstract

The invention relates to a tapered roller bearing, with a bearing outer ring, with a formed by the inner surface first outer conical surface raceway, and also formed by the inner surface second outer conical surface raceway, a first bearing inner ring, with a formed by the outer peripheral surface first inner conical surface raceway, a second bearing inner ring with a second inner conical surface race formed by the outer peripheral surface thereof, first tapered rollers received in a clearance formed between the first inner conical surface raceway and the first outer conical surface raceway, and second tapered rollers received in a gap formed between the second inner conical surface raceway and the second outer conical surface raceway are, wherein the first inner bearing ring and the second inner bearing ring have facing inner end faces and this end face n in the assembled state axially abut each other with a bearing preload, and the raceway geometry of the first bearing inner ring and the raceway geometry of the second bearing inner ring are tuned such that the conical surface races formed by this only when reaching a bearing preload corresponding axial clamping force in each case one for the rolling of the tapered rollers to achieve the intended target crown.

Description

Field of the invention

The invention relates to a double-row tapered roller bearing with a bearing outer ring, a first bearing inner ring, a second bearing inner ring, first tapered rollers which are received in a defined between the first bearing inner ring and the bearing outer ring first track space, and second tapered rollers in a between the second bearing inner ring and the bearing outer ring defined second track space are received, wherein the tapered roller bearing is designed such that the first and second tapered rollers face each other over their end faces with the respective smaller diameter.

Furthermore, the invention also relates to a realized under inclusion of such a double-row tapered roller bearing bearing assembly for a pinion head, for example, an angular gear for driving the web or rotary housing of a axle differential of a motor vehicle.

Out EP 1 321 687 A1 is a double-row tapered roller bearing of the above type, as well as a formed with inclusion of such a tapered roller bearing rack and pinion bearing assembly is known. The tapered roller bearing is designed as asymmetrical with respect to a radial plane bearing and the tapered rollers of a first row of flights are larger than the tapered rollers of the first row of races axially offset second row of races. The bearing inner rings of this tapered roller bearing are designed such that the provided for guiding the larger tapered roller conical surface of a first bearing inner ring increases in axial section by a certain minimum angle, whereas provided for guiding the smaller tapered conical surface of the second bearing inner ring increases in axial section by an angle which is smaller than the aforementioned minimum angle. The bearing inner rings are axially secured on a shaft journal which carries a pinion head.

Out DE10 2013 212 989 A1 a bearing arrangement for a pinion head is known, which also comprises a double row and with respect to a radial plane asymmetric tapered roller bearing. The two outer raceways of the tapered roller bearing are formed by a built-in part, which has a mounting flange. The two inner raceways of the tapered roller bearing are formed by outer peripheral surfaces of a pinion pin, and a Antriebswellenanschlussflansches. The pinion and the drive shaft flange are axially clamped together via a threaded structure.

Object of the invention

The invention has for its object to provide solutions by which it is possible to ensure a particularly advantageous mechanical performance in a provided for the storage of a pinion head double-row tapered roller bearing with separate inner bearing rings.

Inventive solution

• – einem Lageraußenring, mit einer durch dessen Innenfläche gebildeten ersten äußeren Kegelflächenlaufbahn, sowie einer ebenfalls durch dessen Innenfläche gebildeten zweiten äußeren Kegelflächenlaufbahn,
• – einem ersten Lagerinnenring, mit einer durch dessen Außenumfangsfläche gebildeten ersten inneren Kegelflächenlaufbahn,
• – einem zweiten Lagerinnenring, mit einer durch dessen Außenumfangsfläche gebildeten zweiten inneren Kegelflächenlaufbahn,
• – ersten Kegelrollen die in einem zwischen der ersten inneren Kegelflächenlaufbahn und der ersten äußeren Kegelflächenlaufbahn gebildeten Zwischenraum aufgenommen sind, und
• – zweiten Kegelrollen die in einem zwischen der zweiten inneren Kegelflächenlaufbahn und der zweiten äußeren Kegelflächenlaufbahn gebildeten Zwischenraum aufgenommen sind,
• – wobei der erste innere Lagerring und der zweite innere Lagerring einander zugewandte innere Stirnflächen aufweisen und diese Stirnflächen in verbautem Zustand sich mit einer Lagervorspannkraft axial aneinander abstützen, und
• – die Laufbahngeometrie des ersten Lagerinnenringes und die Laufbahngeometrie des zweiten Lagerinnenringes derart abgestimmt sind, dass die durch diese gebildeten Kegelflächenlaufbahnen erst bei Erreichen einer der Lagervorspannkraft entsprechenden axialen Spannkraft jeweils eine für das Abwälzen der Kegelrollen vorgesehene Soll-Balligkeit erlangen.

This object is achieved by a double-row tapered roller bearing, with:

• A bearing outer race having a first outer conical surface raceway formed by the inner surface thereof and a second outer conical surface raceway likewise formed by the inner surface thereof,
• A first inner bearing race, with a first inner conical surface raceway formed by its outer peripheral surface,
• A second inner bearing race, with a second inner conical surface race formed by its outer peripheral surface,
• - first tapered rollers which are received in a space formed between the first inner conical surface raceway and the first outer conical surface raceway, and
• Second tapered rollers received in a space formed between the second inner conical surface raceway and the second outer conical surface raceway,
• - Wherein the first inner bearing ring and the second inner bearing ring having mutually facing inner end faces and these end faces are supported in the assembled state axially with a bearing preload force against each other, and
• - The raceway geometry of the first bearing inner ring and the raceway geometry of the second bearing inner ring are tuned such that the conical surface runways formed by this only obtain upon reaching a bearing preload corresponding axial clamping force in each case provided for the rolling of the tapered rollers target crowning.

This makes it possible in an advantageous manner to provide a rolling bearing, in which the bearing inner rings can be stretched under a relatively high axial biasing force on a shaft and provide in this state career geometries, in which a Lagespielreduktion and at the same time a tribologically advantageous expiration of the tapered rollers gives the inner bearing rings. Advantageously, the bearing inner rings can also be designed such that, as a result of the mounting forces acting thereon, a change in shape of the raceways axially limiting inner ring rims results, so that they now provide a contact surface geometry each Preload heights is adjusted and prevents load peaks in on-board contact (avoiding seizure of the Obrflächen).

The inventive concept results in a bearing with contoured bearing rings and raceways with initially reduced profiling. Due to the clamping forces, the inner ring rims deform into the ideal state. Likewise, the raceway of the respective bearing inner ring deforms towards a required, e.g. higher crowning, which then equals for example standard profiles. As a result, the friction of the bearing is reduced and the optimized contact profile improves the load capacity and service life.

To determine advantageous basic geometries of the bearing inner rings in the unloaded state, it is possible to subject them to fine finishing in an axially tensioned state until they provide a desired raceway geometry. After axial unloading the dimensions can then be recorded and used as a default measure for a general manufacturing process in which the fine machining of the bearing inner rings takes place without axial load. The optimization of the geometry of the bearing rings can be carried out iteratively in subsequent test steps until a basic geometry is determined, which ensures an optimal running of the tapered rollers in axially loaded condition both in terms of crowning the tread, as well as in terms of location and shape of the inner surfaces.

The determination of the basic geometry in the unloaded state can also be done in conjunction with structural mechanics calculations in which the elastic deformation of the respective bearing inner ring, including its relevant for the axial Wälzkörperführung board geometries under the effect of the axial biasing force in terms of size and Einleitungsart, i. Surface pressure distribution is taken into account. As will be explained below, it is possible to match the introduction of force of the biasing force in the end faces of the bearing inner rings by special design of these end faces, in particular slightly convex design of the same. In the way of influencing the surface pressure distribution in the axial load of the bearing inner rings then also the intrinsic deformation of the bearing inner rings can be optimized. A weakening of the bearing inner rings in the region of the inner circumferential surface makes it possible to tune the deformation behavior of the two bearing inner rings so that they together achieve ideal track geometries, as well as ideal movement games, lubrication gap geometries and crowns in the range of the conical rollers axially supporting sides of the vehicle when reaching the target biasing force.

The tapered roller bearing according to the invention can be designed so that under the effect of axial load then a desired crowning of the raceways formed by the bearing inner rings we achieved, which is greater than the crown of these raceways in the axially unloaded state of the bearing inner rings. The bearing rings are curved in this interpretation by the axial clamping forces in the region of the substantially conical raceways to the outside.

As an alternative to the above-described measure, however, it is also possible to design the bearing rings in such a way that they are compressed by the axial clamping force, but in this case a desired crowning is established which is smaller than the crowning in the axially unloaded state. This can be achieved by the axial clamping force is introduced by appropriate profiling of the end faces of the bearing ring on one of the seat radially relatively widely spaced circumferential level in the bearing ring and thus over the peripheral region of the tread an "indentation" of the bearing inner ring on the shaft carrying it results.

The elastic deformation of the first and second bearing rings can advantageously be improved by the design of the axially outward, i.e. be matched by the tapered rollers pioneering faces of these bearing rings. Thus, these faces may be shaped as axially profiled, e.g. slightly curved convex convex torus side surfaces are formed which also determine the attack radius and the orientation of the resulting axial force due to the thus influenced surface pressure distribution.

Furthermore, the elastic deformation of the first and the second bearing ring can also be matched via the design of the voltage applied to the outer end faces of these bearing rings structures. The elastic deformation of the first and the second bearing ring can be tuned in an advantageous manner also on the design of the inner peripheral surfaces of these bearing rings.

In particular, in the case of the profiling of the end faces of the bearing rings, it is possible to provide there settling surfaces, which in conjunction with sufficiently complementary mating surfaces, that upon reaching the desired biasing force, a large-scale contact between the end faces of the bearing inner rings and exerting pressure on this axially adjacent, the above mating surface forming structures is obtained.

The inventive concept of taking into account the deformation behavior of both bearing inner rings in achieving the desired bias can advantageously also on the consideration of the deformation of the tapered rollers axially supporting Inland surfaces are applied. Thus, the first and the second bearing inner ring each form inner surfaces on which the tapered rollers are movably guided, wherein those the inner surfaces forming the inner surfaces of the bearing inner rings are designed such that the inboard surfaces upon reaching the Lagerervorspannkraft a desired geometry and with respect to the end faces of the incoming rolling elements a target position gain.

The double-row tapered roller bearing is preferably formed as an asymmetric tapered roller bearing, in which the axial extent of the first inner race formed by the first bearing inner ring is greater than the axial extent of the second inner raceway formed by the second bearing inner ring. The running on the first bearing inner race tapered rollers are larger in terms of their maximum diameter, as rolling on the second bearing inner ring "small" tapered rollers. The tapered roller bearing is further preferably designed such that the angle of attack of the first inner raceway in axial section is greater than the angle of attack of the second inner raceway in axial section.

• – einem Achszapfen der einen Ritzelkopf trägt und einen Wellenabschnitt aufweist, der durch den ersten und zweiten Lagerinnenring hindurchgeführt ist,
• – einer Spannmutter die über einen Gewindeabschnitt mit dem Wellenabschnitt in Eingriff steht und die beiden Lagerinnenringe gegen den Ritzkopf spannt,
• – wobei die axial tragenden Stirnflächen der Lagerinnenringe, sowie die an einem der Lagerinnenringe anliegende Stirnfläche der Spannmutter derart aufeinander abgestimmt ausgebildet sind, dass durch die Aufbringung der Lagervorspannkraft eine definierte Verformung der Lagerinnenringe erzwungen wird und die Laufflächen der Lagerinnenringe hierbei eine definierte Soll-Balligkeit erlangen.

The invention further includes a pinion head bearing assembly with a double row tapered roller bearing of the above type, comprising:

• A journal carrying a pinion head and having a shaft portion passing through the first and second bearing inner rings,
• A clamping nut which engages with the shaft section via a threaded section and biases the two bearing inner rings against the scoring head,
• - Wherein the axially bearing end faces of the bearing inner rings, as well as applied to one of the bearing inner rings end face of the clamping nut are designed coordinated so that a defined deformation of the bearing inner rings is enforced by the application of the bearing preload and the treads of the bearing inner rings hereby achieve a defined nominal crowning ,

Furthermore, the inner surfaces of the bearing ring rims facing the rolling body end faces only reach a defined setpoint geometry and setpoint position when the bearing preloading force is reached.

The rolling bearing itself forms a complete bearing assembly comprising the bearing outer ring, as well as the two separate bearing inner rings. The bearing outer ring forms two raceways, the two bearing inner rings each form only one raceway. The bearing inner rings have the same inner diameter and initially form between their facing end faces a narrow setting gap is calculated such that it is overcome during clamping of the bearing under construction of a bearing preload, wherein the bearing inner rings are designed so that when reaching the required bearing preload still sufficient smooth running of the bearing is guaranteed. According to the invention, the bearing inner rings are designed in such a way that their deformation behavior is taken into account so that they only acquire ideal geometries in the region of their raceways when the required pretension is reached. As far as the bias increases the crown of the track, the crown in the ground state is realized correspondingly lower. As far as the bias lowers the crown of the track, the crown in the ground state is realized correspondingly higher. The deformation behavior of the bearing inner rings is also tuned by geometric details of the same, so the end faces can have a profiling by which there is a special surface pressure distribution, especially at a high or a low level level. By a surface pressure of the end faces of the bearing inner rings at a high circumferential level results in an inward curvature of the rolling elements axially supporting shelves. By a surface pressure of the faces near the bearing seat results in a more pronounced increase in the crown. The bearing inner rings can be provided with weakening geometries and geometries for providing certain deformation receiving spaces, in particular flat grooves or cross-sectional reductions can be made in the bearing seat. Furthermore, the bearing inner rings can be formed so that they obtain a particularly high rigidity in the region of the shelves. In each case for themselves independent invention complexes can thus represent in particular the vote of the increase in crown by geometries, in particular shallow grooves in the inner peripheral wall of the bearing inner rings. A likewise for itself, or in combination with the above measures realizable invention complex represents the influence of the deformation behavior of the bearing inner rings by profiling the annular end faces. Another independent, as well as combinable invention of the invention is the coordination of the geometry of the bearing inner rings in the region of the shelves , in which case according to the invention, the ideal geometries are reached only when the desired preload force is present.

Brief description of the figures

Further details and features of the invention will become apparent from the following description taken in conjunction with the drawings. It shows:

1 a schematic representation to illustrate the structure of a bearing assembly formed under inclusion of a rolling bearing according to the invention;

2 a further illustration to illustrate the structure of a roller bearing according to the invention.

Detailed description of the figures

The representation after 1 shows an embodiment of a sprocket head bearing assembly according to the invention for supporting one on a pinion shaft 1 attached pinion head 2 in a bearing housing 3 in which a two-row asymmetric tapered roller bearing L1 according to the invention is used, which has a clamping nut 4 is axially tensioned.

The tapered-roller bearing L1 comprises a bearing outer race RA, having a first outer raceway RAL1 formed by its inner surface, which has a larger path radius adjacent to a first outer-ring end face RAS1 than in the middle region of the bearing outer race RA. The bearing outer ring RA also forms a second outer, substantially cone-shaped raceway RAL2 adjacent to a second outer ring end surface RAS2 has a path radius which is greater Kegelmantelradius in the axially opposite inner end region. i.e. in the vicinity of the first outer raceway RAL1.

The tapered roller bearing L1 further comprises a first bearing inner race RI1, having a first inner raceway RIL1 formed by the outer peripheral surface thereof, a second bearing inner race RI2 having a second inner raceway RIL2 formed by the outer peripheral surface thereof, first tapered rollers W1 disposed between the first inner raceway RIL1 and and the second tapered rollers W2 are received in a space formed between the second inner raceway RIL2 and the second outer raceway RAL2.

The first inner bearing ring RI1 and the second inner bearing ring RI2 have mutually facing inner end faces RI1a, RI2a and these end faces RI1a, RI2a are based in the installed state with a bearing preloading force axially against each other. The raceway geometry of the first bearing inner race RI1 and the raceway geometry of the second bearing inner race RI2 are tuned such that the raceways RIL1, RIL2 formed by these each achieve a predetermined desired crowning upon reaching an axial clamping force corresponding to the bearing preload force. In the embodiment shown here, this target crown is greater than the crown in the axially unloaded state.

This elastic deformation of the first and second bearing inner ring RI1, RI2 is here inter alia on the design of the against the pinion head 2 , as well as against a clamping nut 4 axially supporting end faces RI1b, RI2b of these bearing rings RI1, RI2 matched. For this purpose, the axially outer end faces RI1b, RI2b of the bearing inner rings RI1, RI2 are precision-profiled in axial section, ie they have a slight elevation at selected areas, so that these areas primarily contribute to the introduction of force.

The elastic deformation of the first and second bearing ring RI1, RI2 is also tuned on the design of the inner peripheral surfaces of these bearing rings RI1, RI2. For this purpose, flat circumferential grooves N1, N2 are formed in the region of the inner circumferential walls.

The first and the second bearing inner ring RI1, RI2 respectively form inner surfaces RI1c, RI2c on which the tapered rollers W1, W2 are movably guided and axially supported, wherein those areas of the bearing inner rings RI1, RI2 forming the inner surfaces RI1c, RI2c are designed such that the inner surfaces of the inner surfaces RI1c, RI2c on reaching the bearing preload force a target geometry and Sollaxialspiel over the tapered rollers W1, W2 obtain.

The tapered roller bearing L1 is formed as an asymmetrical tapered roller bearing in which the axial extent of the first inner raceway RIL1 formed by the first bearing inner race RI1 is greater than the axial extent of the second inner raceway RIL2 formed by the second bearing inner race R2. Also, the angle of attack Q1 of the first inner raceway RIL1 in the axial section shown here is greater than the angle of attack Q2 of the second inner raceway RIL2 in axial section. The angle of attack Q1 is preferably in the range above 20 ° and the angle of attack Q2 is preferably in a range of less than 23 °.

The clamping nut 4 it stands over a threaded section 5 with the shaft section 1 engages and biases the two bearing inner rings RI1, RI2 axially against the pinion head 2 , wherein the bearing inner rings RI1, RI2 and the voltage applied to one of the bearing inner rings RI2 end face of the clamping nut 4 are designed to be coordinated with each other such that a defined deformation of the bearing inner rings RI1, RI2 is forced by the application of the bearing preload and the running surfaces RIL1, RIL2 of the bearing inner rings RI1, RI2 in this case obtain a defined crowning.

The representation after 2 now shows that in the Ritzelkopflageranordnung according to 1 used double-row tapered roller bearings L1 in a unique position. As stated above, the double row tapered roller bearing L1 includes a bearing outer race RA having a first one formed by the inner surface thereof outer race RAL1 and also formed by the inner peripheral surface second outer raceway RAL2. The first outer raceway RAL1 is formed as a conical surface, wherein the tip of the conical surface is located on the bearing axis X and with a first center Z1 comes over. The second outer race RAL2 is formed as a conical surface. Its tip again lies on the bearing axis X and coincides with a second center Z2. The tips of the two cones defined by the outer raceways RAL1, RAL2 face in opposite directions. The centers Z1, Z2 are spaced from the nearest end face of the bearing inner rings RI1, RI2 by at least 60% of the total width of these two bearing inner rings , The center Z1 on which the tip of the cone defined by the first outer race RAL1 lies is spaced from the end face RI2a of the second bearing inner race RI2 by an amount smaller than that of the center Z2 from the end face RI1b of the first bearing inner race RI1 is spaced.

The cone angle Q1 of the tread RIL1 is in the range of 16 to 23 °, in particular 19 °. The cone angle Q12 of the tread RAL1 is in the range of 19 to 27 °, in particular 26 °. The cone angle Q2 of the tread RIL2 is in the range of 9 to 18 °, in particular 12 °. The cone angle Q22 of the tread RAL2 is in the range of 14 to 18 °, in particular 16 °. The axial length of the second bearing ring RI2 is shorter than the axial length of the first bearing inner ring RI1. The aspect ratios of the long bearing inner ring RI1 to the short bearing inner ring RI2 are in the range 1.65 to 2.75, in particular 2.0. the first bearing inner ring RI1 which carries the larger tapered rollers W1 is here twice as long as the second bearing inner ring RI2.

The first bearing inner ring RI1 is designed in this embodiment in such a way that, in the axially unloaded state, it has a base crown B1 that is too small for optimum rolling body guidance. After an axial clamping of the first bearing inner ring RI1, this crowning increases to a Sollballigkeit SB1. Simultaneously with the increase in the crown of the inner race RI1L, the geometry and position of the inner rim RI1c also changes. As shown here by way of example and greatly exaggerated, the inboard surface RI1c assumes a position and curvature RI1c 'in which an optimal start of the tapered rollers W1 results. The transfer of the inboard surface RI1c in an ideal configuration RI1c ', can be brought about by the bearing inner ring RI1 is formed and axially loaded so that the inboard surface RI1c bulges outward and thus defines a larger gap angle with the Wälzkörperstirnfläche in tensioned. However, it is also possible to design and load the arrangement in such a way that as a result of the elastic geometry change, an initially large-sized gap angle is reduced to an ideal angle dimension. For the first bearing inner ring RI1, these effects can be tuned, in particular via the profiling of the end face RI1b of the first bearing inner ring RI1. Thus, by forming a slightly convex spherical bulge of the end face RI1b, either the seat-near or primarily rather the seat-remote annular region of the end face RI1b is primarily loaded in the direction of the bearing axis X. By the here indicated profiling with slight elevation near the inner seating surface of the first bearing inner ". radially further inward ", it is achieved that the crowning of the raceway RI1l increases and the board forming the inboard surface RI1c bulges outwards and generates a somewhat larger gap angle with respect to the rolling elements W1. If one changes the profiling of the end surface RI1b in such a way that the introduction of axial force takes place at a somewhat higher radial level, then the inside surface of the rim RI1c tends to tilt toward the rolling element end surface under the effect of the axial load, thus reducing the gap angle. The increase in crowning of the track RI1L is lower in this case. The comments on the deformation behavior of the first bearing inner ring and possibly for profiling of its end face RI1b apply mutatis mutandis to the second bearing inner ring RI2. A special feature of the present bearing arrangement consists in the fact that the deformation behavior of the two bearing rings RI1, RI2 are coordinated such that the ideal geometries result in an identical axial force at the same time corresponds to the prevailing in the installation of the bearing biasing force.

The deformation behavior of the two bearing inner rings RI1, RI2 is considered in addition to the acquisition of ideal crowns in the raceways RIL1, RIL2 also for the alignment and positioning of the tapered rollers W1, W2 axially leading inside surfaces with the proviso that only in the tensioned state for the Wälzkörperlauf ideal railway conditions result. In addition to the creation of ideal web geometries on the bearing inner rings RI1, RI2 is also the position of lying on the bearing axis X tips of the conical shells adjusted by matching the geometry and the position of the contacting end faces RI1a, RI2a the bearing inner rings RI1, RI2, so here relative to the position of the tips of the conical shells of the outer raceways RAL1, RAL2 yields a defined ΔZ1, ΔZ2. The axial pressure of the bearing inner rings RI1, RI2 takes place taking into account the geometry of the applied pressure surfaces. These are preferably realized as flat surfaces, so that the structural mechanics influencing the deformation behavior of the bearing inner rings can be accomplished by geometric details realized on these rings are. However, it is also possible to design the geometry of the bearing surfaces on the bearing inner rings RI1, RI2 pressing surfaces as surfaces deviating from planar surfaces and hereby additionally take influence on the ring deformation. Thus, in particular, the voltage applied to the second bearing inner ring RI2 end face of the clamping nut 4 (see. 1 ) profiled in axial section and thus cause a certain surface pressure distribution. On the sprocket head 2 facing side of the bearing, the surface pressure distribution can be influenced in particular by the profiling of a washer.

Furthermore, it is possible in the inner peripheral region of the two bearing inner rings RI1, RI2 circumferential geometries, e.g. in the form of flat circumferential grooves N1, N2 provided, which affect the deformability of the bearing inner rings RI1, RI2 defined and provide in addition to a cross-sectional reduction also movement spaces.

The bearing L1 shown here is designed so that it is tensioned with an axial force of 200kN. The diameter of the shaft 1 is about 30mm.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 1321687 A1 [0003]
• DE 102013212989 A1 [0004]

Claims (10)

Double row tapered roller bearing, with: A bearing outer race (RA) having a first outer raceway (RAL1) formed by its inner surface which has a larger path radius adjacent to a first outer race end surface (RAS1) than in the middle region of the bearing outer race (RA) and a second outer raceway (RAL2) which has a path radius adjacent to a second outer ring end surface (RAS2) that is greater than the radius of the path (RAL2) adjacent to the first outer raceway (RAL1), A first bearing inner ring (RI1), having a first inner raceway (RIL1) formed by its outer peripheral surface, A second inner bearing race (RI2), having a second inner raceway (RIL2) formed by its outer peripheral surface, - First tapered rollers (W1) which are received in a space formed between the first inner raceway (RIL1) and the first outer raceway (RAL1), and Second tapered rollers (W2) received in a space formed between the second inner raceway (RIL2) and the second outer raceway (RAL2), - Wherein the first inner bearing ring (RI1) and the second inner bearing ring (RI2) have mutually facing inner end faces (RI1a, RI2a) and these end faces (RI1a, RI2a) in the installed state axially abut each other with a bearing biasing force, and - The raceway geometry of the first bearing inner ring (RI1) and the raceway geometry of the second bearing inner ring (RI2) are tuned such that the respective raceways formed by this (RIL1, RIL2) achieve a desired crowning (SB1) upon reaching an axial clamping force corresponding to the Lagerervorspannkraft , Tapered roller bearing according to claim 1, characterized in that the desired crown (SB1) is greater than the crown (B1) in the axially unloaded state. Tapered roller bearing according to claim 1, characterized in that the desired crowning (SB1) is smaller than the crowning (B1) in the axially unloaded state. Tapered roller bearing according to at least one of claims 1 to 3, characterized in that the elastic deformation of the first and the second bearing ring (RI1, RI2) on the design of the axially outwardly facing end faces (RI1b, RI2b) of these bearing rings (RI1, RI2) matched becomes. Tapered roller bearing according to at least one of claims 1 to 4, characterized in that the axially outer end faces (RI1b, RI2b) of the bearing inner rings (RI1, RI2) represent annular surfaces which are profiled in axial section. Taper roller bearing according to at least one of claims 1 to 5, characterized in that the elastic deformation of the first and the second bearing inner ring (RI1, RI2) on the design of the outer end faces (RI1b, RI2b) of these bearing rings adjacent structures ( 2 . 4 ). Tapered roller bearing according to at least one of claims 1 to 6, characterized in that the elastic deformation of the first and the second bearing inner ring (RI1, RI2) on the design of the inner peripheral surfaces of these bearing rings is tuned. Tapered roller bearing according to at least one of claims 1 to 7, characterized in that the first and the second bearing inner ring (RI1, RI2) respectively inner surfaces Bordeln (RI1c, RI2c) form, on which the tapered rollers (W1, W2) are movably guided, wherein the On-board surfaces (RI1c, RI2c) forming area of the bearing inner rings (RI1, RI2) are designed such that the inboard surfaces (RI1c, RI2c) achieve a desired geometry (RI1c ') upon reaching the bearing preload. Tapered roller bearing according to at least one of claims 1 to 8, characterized in that the bearing is formed as an asymmetrical tapered roller bearing, wherein the axial extent of the first inner race (RI1) formed by the first inner raceway (RIL1) is greater than the axial extent of the the second bearing inner race (RI2) formed second inner raceway (RIL2), and that the angle (Q1) of the first inner raceway (RIL1) in axial section is greater than the angle of attack (Q2) of the second inner raceway (RIL2) in axial section. Pinion head bearing assembly with a double row tapered roller bearing (L1) of the above type, comprising: a journal of a pinion head ( 2 ) and a shaft section ( 1 ), which is passed through the first and second bearing inner ring (RI1, RI2), a clamping nut ( 4 ) via a threaded section ( 5 ) with the shaft section ( 1 ) and the two bearing inner rings (RI1, RI2) against the pinion head ( 2 ) axially, wherein the axially bearing end faces (RI1b, RI2b) of the bearing inner rings (RI1, RI2), as well as on one of the bearing inner rings (RI1, RI2) abutting end face of the clamping nut ( 4 ) are formed so coordinated that by the application of the bearing preload a defined deformation of the bearing inner rings (RI1, RI2) is enforced and the running surfaces (RIL1, RIL2) of the bearing inner rings (RI1, RI2) in this case obtain a defined crown.

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