WO2009065381A1

WO2009065381A1 - Roller bearing for a shaft component

Info

Publication number: WO2009065381A1
Application number: PCT/DE2008/001867
Authority: WO
Inventors: Tim LÖSCHNER; Rudolf Zeidlhack
Original assignee: Schaeffler Kg
Priority date: 2007-11-20
Filing date: 2008-11-12
Publication date: 2009-05-28
Also published as: DE102007055362A1

Abstract

The invention relates to a roller bearing (1), for a shaft component, comprising at least two rows of roller bodies (2, 3), wherein one row of roller bodies (2) is made up of spherical roller bodies (20) and at least one other row of roller bodies (3) is made up of cylindrical roller bodies (30). According to the invention, the cylindrical roller bodies (30) have a barreled shape and the at least two rows of roller bodies (2, 3) run on at least two tracks (La1, La2; La1', La2'; Li1',Li2'; LiI'', Li2'') which make up a track contour (La1+La2; La1'+La2'; Li1'+Li2'; Li1''+Li2'') in the radial section of the bearing, wherein the track contour,(La1+La2; La1'+La2'; Li1'+Li2'; Li1''+Li2'') has straight sections (La10, La30) and also curved sections (La20, La40) each being curved in essentially one direction, wherein the straight sections (La10, La30) lie directly or indirectly on adjacent tracks (La1, La2; La1', La2'; Li1', Li2'; Li1'',Li2'') making up said track contour (La1+La2; La1'+La2'; Li1'+Li2'; Li1''+Li2'').

Description

Schaeffler KG Industriestr. 1 - 3, 91074 Herzogenaurach

Name of the invention

Rolling bearing for a wave-shaped component

description

Field of the invention

The invention relates to a rolling bearing for a corrugated component with at least two rows of rolling elements, wherein a row of rolling elements is formed by spherical rolling elements and at least one other row of rolling elements by roller-shaped rolling elements.

Background of the invention

Asymmetrical rolling bearings of the generic type are suitable for carrying high axial and radial loads, as they occur for example in the storage of a rotor of wind turbines. In this case, the rotor of a wind turbine generally supports itself via a shaft in the rotor bearing formed by generic slewing bearings. The achievement of the desired output or generator side speed is da- achieved over a corresponding gear. The bearing of the rotor shaft is usually done by a fixed-floating bearing with at least two spatially spaced rolling bearings. The fixed bearing must be able to compensate for angular errors caused, for example, by misalignments and manufacturing inaccuracies.

From WO 2005/110032 A2 a generic rolling bearing unit for the storage of a gear shaft of a wind turbine is known. The bearing unit has a tapered roller bearing combined with a angular ball bearing. The outer ring of the angular ball bearing is also formed by a bolted to the gearbox of the wind turbine housing part. At the same time, the housing part serves for movably receiving the outer ring of the angular contact ball bearing, whereby the axial adjustment required for the angular contact ball bearing takes place via a disk spring pressing against the outer ring. The axial forces occurring in the main load case (generator operation, ie the rotor blades drive generator) are intercepted via the tapered roller bearing, while in the reverse load case (motor operation, the rotor blades are driven) with lower axial forces they are supported by the angular contact ball bearing.

From DE 27 53 108 A1 a generic rolling bearing is also known, which is used for the storage of a pinion shaft in a transmission. The rolling bearing has a first row of rolling elements with a spherical and a second row of rolling elements with cylindrical rolling elements and is suitable for receiving high axial and radial loads in a compact design.

Object of the invention

Based on the stated disadvantages of the solutions of the known prior art, the invention is therefore based on the object, a generic rolling bearing to develop such that angular errors can be compensated by the bearing reliable.

Description of the invention

The invention is based on the finding that angular errors, ie alignment deviations between the longitudinal axis of the shaft to be supported and the longitudinal axis of the roller bearing, can be reliably compensated by suitable design of the roller bearing raceways.

The invention is therefore according to the features of the main claim of a rolling bearing for a corrugated component having at least two rows of rolling elements, wherein a row of rolling elements by spherical Wälz- body and at least one other row of rolling elements is formed by roller-shaped rolling elements.

In addition, according to the invention, it is provided that the roller-shaped rolling elements are barrel-shaped, and that the at least two rolling element rows roll on at least two raceways, which complement each other in the radial bearing section to form a track contour, wherein the track contour is both rectilinear sections as well as curved sections, each having a substantially unidirectional curvature, wherein the rectilinear portions are in the region of the said career contour complementary, directly or indirectly adjacent tracks.

By this construction it is achieved that the rolling bearing according to the invention is able to compensate angular errors reliably. In addition, a compact design and good mountability is given, the bearing can be mounted without play to slightly biased. A bearing row serves to absorb the axial forces in the main load direction. This allows an op- Timely distribution of the rolling element rows, since the opposite to the main load direction oversized bearing row made smaller (space reduction) or even larger load capacity can be achieved with the same size. In this case, the rolling bearing according to the invention have the same outer dimensions such as a standard spherical roller bearings.

The subclaims describe preferred developments or refinements of the invention.

According to a first advantageous embodiment of the invention it is provided that the resulting raceway contour at least partially corresponds approximately to the radius of curvature of the spherical rolling elements and at least partially the radius of curvature of the barrel-shaped rolling elements. By this design, an optimization of the carrying capacity and running calm of the camp is achieved.

According to a second advantageous embodiment of the invention, the resulting raceway contour is formed by the raceways of two outer rings of the rolling bearing. Alternatively, however, it can also be provided that the resulting raceway contour is formed by the raceways of two inner rings.

A rolling bearing designed in accordance with the variants mentioned can basically have two inner rings and two outer rings, or one inner ring and two outer rings, or two inner rings and one outer ring. In the two last-mentioned variants, on the one hand the bearing rigidity is increased and tolerances are reduced, and on the other hand, a good mountability is ensured. Thus, it can be provided that either the inner ring or the outer ring of the rolling bearing with the described, resulting raceway contour is integrally formed, or that on this one-piece inner ring or on the one-piece outer ring to the resulting career contour opposite contour is trained.

As mentioned, it is also possible to provide two inner rings and two outer rings on the rolling bearing, which brings an increase in the adaptability of the bearing to special conditions with it. Thus, in this case, both between the inner rings and between the outer rings further machine elements, such as spacers and / or spring elements may be installed, with which a needs-based adjustment of the rolling bearing is optimally possible.

For example, at least one spacer may be provided between said inner rings and / or outer rings. Due to this structure, the bearing clearance can be adjusted without an adaptation or grinding to measure the bearing rings is necessary.

Alternatively, a bias of the bearing can be achieved most simply and advantageously but also by the fact that between the inner rings or outer rings at least one spring element, preferably in the manner of a plate spring, is installed in the rolling bearing.

A roller bearing with at least one rolling bearing according to the invention can be made compact, carry large loads and at the same time compensate for angular errors to a certain extent.

It should be noted that the raceway contour resulting from the raceways ideally in radial section has a substantially continuous, continuous course without appreciable edges or heels, wherein the rectilinear sections are approximately radially flush with each other go over and run approximately parallel to the axis of rotation of the bearing.

The idea of the invention is of course not be relied on in that, for example, spacers are arranged between the raceways which supplement the raceway contour whose inner or outer lateral surface interrupts or completes the continuity of the raceway contour, or in that the ends of the raceways are viewed in radial section have slight rounding, which only serve to simplify assembly of Wälz- body cages.

Brief description of the drawings

A preferred embodiment of the inventively embodied rolling bearing will be explained in more detail with reference to the accompanying drawings. Each show in radial or longitudinal section:

Figure 1 shows a first embodiment of an inventively designed roller bearing;

FIG. 2 shows the roller bearing according to FIG. 1 with an angular offset of the outer rings;

FIG. 3 shows an inventively embodied roller bearing according to a second embodiment;

Figure 4 shows a third embodiment of an inventively designed roller bearing;

Figure 5 shows a fourth embodiment of a rolling bearing according to the invention. Detailed description of the drawings

The rolling bearing 1 according to FIG. 1 has two outer rings 4, 5 as well as two inner rings 6, 7, between which ball-shaped rolling elements 20 and in a second rolling-element row 3 barrel-shaped rolling elements 30 in raceways of FIGS Bearing rings are arranged rollable. The rolling elements 20, 30 at a distance holding rolling elements cages are not shown. The spherical rolling elements 20 have a radius of curvature Rk and the barrel-shaped rolling elements 30 have a radius of curvature Rt.

As can further be seen, the inner ring 6 for the spherical rolling elements 20 has a raceway designated Li1 and the inner ring 7 for the barrel-shaped rolling elements 30 has a raceway designated Li2. The raceway Li1 is divided into a rectilinear portion Lh0 and a radially inwardly curved portion Li20, the curved portion Li20 axially inwardly opening into a radial projection 60 of the inner ring 6. The other radially inner raceway Li2 is in contrast not divided into sections and has a radially inwardly curved course, which also opens axially inward, in the transition region to the adjacent inner ring 6, in a radial projection 70 of the second inner ring 7.

The outer ring 4 for the spherical rolling elements 20 has a track La1 and the outer ring 5 for the barrel-shaped rolling elements 30 has a track La2. The raceway La1 is divided into a radially outward curved portion La20 and a straight line portion La10, the raceway La2 is also divided into a straight line portion La30 and a radially outward curved portion La40. The curved portion La20 has a radius of curvature approximately corresponding to the radius of curvature Rk of the spherical rolling element 20, and extends approximately over a quarter circle of the circumference of one of the spherical rolling elements 20. This curved section La20 enters into said rectilinear portion LaIO, to the radially flush of the straight section La30 of the track La2 of the second outer ring 5 connects, the two rectilinear sections LaIO and La30 are aligned approximately parallel to the axis of rotation of the rolling bearing 1 and formed of unequal length. The rectilinear section La30 in turn merges into the curved section La40, which (La40) has a radius of curvature which corresponds approximately to the radius of curvature Rt of one of the barrel-shaped rolling elements 30.

It can be clearly seen that the raceways La1 and La2 of the axially adjacent outer rings 4, 5 complement each other to form a raceway contour which includes both rectilinear sections La10, La30 and curved sections La20, La40 with a substantially radial direction (FIG. in this exemplary embodiment, radially outward) curvature, wherein the rectilinear sections La10, La30 lie in the region of the raceways La1 and La2 that are complementary to the said track contour and are directly approximately radially flush with each other. The rolling elements 20 and 30 roll under such a pressure angle Dk or Dt in their associated tracks La1, Li1 and La2, Li2 from that the rolling bearing 1 is one in X-arrangement of the rows of rolling elements.

In Figure 2 is indicated schematically how the rolling bearing 1 can compensate for angular errors to a certain extent. Thus, the starting position of the outer rings 4, 5 is indicated by dashed lines and, in a solid line, a possible deviating position of the outer rings 4 and 5, which corresponds to an angular play α. This is accompanied by an axial displacement of the axial outer side 50 of the outer rings 4, 5. It is also to be considered that the deviation of the outer rings 4, 5 in the other direction (not shown) can be made and the adjustability of the angular play α by a suitable choice Oscillation (quotient between raceway radius and Wälzkörper- diameter) and the pressure angle can be influenced. FIG. 3 shows in construction an alternative rolling bearing 1 'according to the invention. In contrast to the embodiment shown in Figure 1, a common, so one-piece inner ring 8 is provided with tracks LiV and Li2 '. Further, although two outer rings 4 'and 5' with trays LaV and La2 'are present, between the two outer rings 4' and 5 ', however, a spacer 9' is arranged. By means of a suitable choice of the spacer 9 ', the bearing clearance can be adjusted without any need for adaptation, that is, for example, grinding to a degree of the outer rings 4', 5 '.

4 shows a further embodiment of a roller bearing 1 "according to the invention, which, in contrast to the exemplary embodiment shown in FIG. 3, is in principle a radial reversal of inner and outer ring inside two inner rings 6 "and 7" with tracks LM "and Li2" are arranged, which in turn form a track contour Li1 "+ Li2" described in more detail in Figure 1, wherein the curvature of the track contour shows radially inward Also in Figure 3 is a spacer 9 "to the bearing adjustment available. Between the outer ring 10 and the two inner rings 6 ", 7" spherical and barrel-shaped rolling elements 20 "and 30" roll in a kind of O arrangement.

5 shows an antifriction bearing V "according to the invention, showing two inner rings 6"'and7'"axially spaced by a spacer disk 9 '", which in turn defines a raceway defined by the two raceways LiV "and Li2"' Contour LiV "+ Li2 '" exhibit. In contrast to the embodiment shown in Figure 4, however, two outer rings 4 '"and 5'" are present, between which a spring element in the form of a plate spring 11 is arranged to produce an axial biasing force Fv. As can be seen, the inner lateral surface of the spacer disc 9 '"does not interrupt the geometric course of the track contour LiV" + Li2'". LIST OF REFERENCE NUMBERS

1, 1 ', 1 ¹ M'"bearings

2 First rolling element series 20 'Spherical rolling elements

3 Second rolling element series 30 Barrel-shaped rolling elements

4, 4 ', 4' "First outer ring

40 Radial projection of the first outer ring

5, 5 ', 5' "Second outer ring

50 outside of the second outer ring

6, 6 ", 6 '" First inner ring

60 Radial projection of the first inner ring

7, 7 ", 7 '" Second inner ring

70 Radial projection of the second inner ring

8 common inner ring

9 ', 9 ", 9'" spacer

10 Common outer ring

11 plate spring

Dk pressure line of the spherical rolling elements

Dt pressure line of the barrel-shaped rolling elements

Fv Axially acting pretensioning force

La1 raceway of the first outer ring

La10 Linear section of the track of the first outer race

La20 Curved section of the raceway of the first outer ring

La2 raceway of the second outer ring

La30 Linear section of the track of the second outer ring

La40 Curved section of the raceway of the second outer ring

LM raceway of the first inner ring

Li10 Straight section of the raceway of the first inner ring

Li20 Curved section of the raceway of the first inner ring

Li2 raceway of the second inner ring

Rk radius of curvature of the spherical rolling elements

Rt radius of curvature of the barrel-shaped rolling elements α Possible angular play of the bearing unit

Claims

Schaeffler KG Industriestr. 1 - 3, 91074 HerzogenaurachPatentansprüche

1. rolling bearing (1, 1 ', 1 ", 1'") for a wave-shaped component having at least two rows of rolling elements (2, 3), wherein a row of rolling elements (2) by spherical rolling elements (20) and at least one other rolling element

Row (3) is formed by roller-shaped rolling elements (30), characterized in that the roller-shaped rolling elements (30) are barrel-shaped, and that the at least two rolling element rows (2, 3) on at least two raceways (La1, La2; LaV "La2", Li1 ", Li2", LiV ", Li2 '"), which in the radial bearing section become a raceway

Contour (La1 + La2; LaV + La2 '; Li1 "+ Li2"; UV "+ ü2'"), where the trajectory contour (La1 + La2; LaV + La2 '; Li1 "+ Li2"; LiV "+ Li2 '") has both rectilinear portions (La10, La30) and curved portions (La20, La40) each having a substantially unidirectional curvature, the rectilinear portions (La10, La30) in FIG

Range of directly or indirectly adjacent raceways (La1, La2, LaV, La2 ', LiV , Li2 ";LiV", Li2 '").

2. Rolling bearing according to claim 1, characterized in that the resulting raceway contour (La1 + La2, La1 '+ La2', Li1 "+ Li2"; Li1 "'+ Li2'") at least in regions (La20) in about the Radius of curvature (Rk) of the spherical rolling elements (20) and at least partially (La40) corresponds to the radius of curvature (Rt) of the barrel-shaped rolling elements (30).

3. Rolling bearing according to claim 1 or 2, characterized in that the resulting raceway contour (La1 + La2; La1 '+ La2') through the raceways (La1, La2, La1 \ La2 ') of two outer rings (4, 5) is formed.

4. rolling bearing according to claim 1 or 2, characterized in that the resulting raceway contour (Li1 "+ ü2"; Li1 '"+ Li2'") through the tracks (LiI ", U2", Li1 "\ Li2 '" ) of two inner rings (6 ", 7", 6 "', T") is formed.

5. Rolling bearing according to claim 3 or 4, characterized in that this roller bearing has two inner rings (6, 7, 6 '", T") and two outer rings (4, 5, 4', 4 '", 5'") or a Inner ring (8) and two outer rings (4 ', 5') or two inner rings (6 ", 7") and an outer ring (10).

6. Rolling bearing according to one of claims 3 to 5, characterized in that the inner ring or the outer ring with the resulting raceway contour (La1, La2, La1 ', La2', Ü1 "+ Li2", Li1 '"+ Li2"') is formed in one piece, or that on this one-piece inner ring or one-piece outer ring to the resulting career contour (La1, La2, LaV, La2', Li1 "+ Li2", Li1 "'+ ü2'") opposite contour ( U1 + Li2; U1 '+ Li2').

7. Rolling bearing according to one of claims 1 to 6, characterized in that the resulting by the raceway track contour (La1 + La2, La1 '+ La2', Li1 "+ Li2", Li1 "'+ Li2'") in Radial section has a substantially continuous, continuous course without appreciable edges or edges, wherein the rectilinear sections (La10,

La30) in approximately radially flush with each other and extend approximately parallel to the axis of rotation of the rolling bearing (1, 1 ', 1 ", 1'").

8. Rolling bearing according to one of the preceding claims, character- ized in that between the inner and / or outer rings (4 ', 5';

6 ", 7"; 6 '", T") a spacer (9, 9 ", 9'") is arranged.

9. Wälzla ger according to any one of the preceding claims, characterized in that between the inner or outer rings (4 '", 5'") at least one spring element (11) is arranged.

10. rolling bearing with at least one rolling bearing (1, 1 ', 1 ", 1'") according to at least one of the preceding claims.