DE102010054319A1 - Rotor bearing for wind turbine, has spherical roller bearing with multiple rolling bodies, where spherical roller bearing has three rows of bearing rings - Google Patents

Abstract

The rotor bearing (21) has a spherical roller bearing with multiple rolling bodies. The spherical roller bearing has three rows of bearing rings. Pressure lines of the three rows of bearings are arranged in an axial section in axially symmetrical manner. The spherical roller bearing has three or five rows of bearings.

Description

Field of the invention

The invention relates to a rotor bearing of a wind turbine, comprising a spherical roller bearing with a plurality of rolling about a bearing axis in rows of bearings rolling elements.

Background of the invention

Rotor bearings are usually housed in a single housing and include z. B. two formed by bearings, angle-adjustable rotor bearings to compensate for angular errors of the machine elements to be stored to each other (eg., Rotor shaft relative to the machine housing) can. Typical rotor bearings of wind turbines include so-called large-diameter bearings as rotor bearings. In slewing bearings is a bore diameter, d. H. a free center diameter of an inner ring, 600 mm and more. Rotor bearing modern wind turbines whose performance in the range of z. B. 1.5 to 7 megawatts, have a bore diameter of z. B. about 600 to 1800 mm.

Often, double row spherical roller bearings, i. H. Radial pendulum roller bearings for radial bearings of machine parts, used as angular adjustable rolling bearings, as they can also accommodate relatively high axial loads.

As is known, bearings of machine elements can be accomplished by means of a fixed bearing point and a floating bearing point. While the floating bearing takes up only radial loads, the fixed bearing point serves to absorb in addition to the radial and the axial loads, thus axially guiding the machine elements against each other exactly. That is, the fixed bearing point should prevent axial displacements between the machine elements to be stored as far as possible and necessary.

It is known to use double-row radial spherical roller bearings as angle-adjustable bearings, z. B. as a rotor bearing. Radial pendulum roller bearings, however, always require a certain amount of radial play, so that the possibly slightly inclined in the load zone barrel rollers can reorient in the non-contact zone again and thus kinematically roll the barrel rollers in the load zone again. This radial clearance generated by the design of radial pendulum roller bearings an axial clearance, which usually makes up a multiple of the radial clearance. A precise axial guidance of the components to be stored is thus difficult. A double-row radial spherical roller bearing is therefore only conditionally used as a very tight fixed bearing. Nevertheless, double-row radial spherical roller bearings used as a fixed bearing can cause damage to the raceways due to the existing axial clearance and the resulting axial displacement of the barrel rollers during operation (eg when the axial load is swelling). Especially when using double-row spherical roller bearings in rotor bearings of wind turbines is also observed that in operation one of the two rows of bearings, due to the force acting always on the frontal wind power, is more heavily loaded during operation than the other row of bearings.

As is known, angle-adjustable fixed bearings, for example in ship propulsion systems, can be formed by a combination of a double-row radial spherical roller bearing with one or two axial spherical roller bearings. The radial spherical roller bearing is used to absorb the radial loads, while the axial spherical roller bearings, however, may only absorb axial loads and axial displacements of the components to be stored prevented. The radial spherical roller bearing and the axial spherical roller bearings have a common pivot point to ensure the Winkeleinstellbarkeit the entire storage. However, the additional Axialpendelrollenlager widened the fixed bearing overall significantly and increases the cost of storage.

From the DE 7003667 U is a three-row spherical roller bearings is known, whose axially central bearing row has a pressure angle of 0 degrees and whose two axially outer rows of bearings have a same pressure angle, ie all pressure lines are arranged axially symmetrically with respect to a plane perpendicular to the bearing axis.

Object of the invention

The present invention has for its object to provide a generic rotor bearing, which is particularly suitable to form a fixed bearing point and thereby absorb both radial loads and axial loads in both axial directions over a long life and which has a compact and thus lightweight and inexpensive construction.

Description of the invention

This object is achieved by a rotor bearing according to the independent claim. Accordingly, a generic rotor bearing is characterized in that the spherical roller bearing has at least three rows of bearings.

The invention is based on the finding that by choosing a spherical roller bearing with at least three rows of bearings a very good compromise in terms of complexity of construction, load capacity and kinematics in operation and costs of rotor bearing is achieved.

The at least three bearing rows of the spherical roller bearing, so the spherical roller bearing rows, on the one hand allow a high absorption of axial and radial forces. On the other hand, by choosing more than two rows of bearings a much better axial guidance z. B. the rotor shaft possible, so that the rotor bearing according to the invention is ideal as angle-adjustable fixed bearing.

The improved absorption of radial and axial forces enables a lower bearing cross-section height, whereby the connection parts are smaller in size and thus less expensive.

Although the structure of the rotor bearing according to the invention is more complex compared to conventional double-row spherical roller bearings due to the at least three rows of bearings in a single spherical roller bearing, the invention still represents a previously unknown cost effective solution of the above task. In particular, the structure of a rotor bearing by means of a angle adjustable fixed bearing point by a Radial pendulum roller bearings and a Axialpendelrollenlager consuming and therefore more expensive.

Embodiments of the present invention are defined in the subclaims.

According to one embodiment, it is provided that all pressure lines of the at least three rows of bearings are arranged axially symmetrically in an axial section. The pressure lines are thus arranged in mirror image in the axial section (sectional view comprising the bearing axis) with respect to a plane perpendicular to the bearing axis. Alternatively, it is conceivable that all pressure lines of the at least three rows of bearings are arranged axially asymmetrically in an axial section. The pressure line of a bearing axis can have a pressure angle of 0 degrees both with an axially symmetrical arrangement of the pressure lines and with an axially asymmetric arrangement of the pressure lines.

It is also conceivable that an axially outermost bearing row has a pressure angle of 0 degrees, namely, when in an axial section shown pressure lines of the at least three rows of bearings are arranged axially asymmetrically.

The exact choice of the pressure angle as well as the choice of the number of bearing rows can be adapted to the respective requirements. Thus, it can be provided that the spherical roller bearing an odd number of rows of bearings, in particular three or five rows of storage covers. Alternatively it can be provided that the spherical roller bearing an even number of rows of bearings, in particular four rows of storage includes.

In order to enable a high radial force absorption, an axially central bearing row can have a contact angle of 0 degrees. In this case, it is particularly conceivable that barrel rollers of the axially central bearing row have a different shape compared to barrel rollers of other bearing rows, in particular have a greater length.

All bearing rows of the rotor bearing according to the invention can in principle roll off between an integrally formed inner ring and an integrally formed outer ring. However, for assembly, manufacturing and application reasons (eg clearance adjustment), it may be advantageous to divide one or both bearing rings (inner ring, outer ring) into two or more partial rings. At least one bearing row rolls on each partial ring. The partial rings contact z. B. on the frontal contact surfaces, so that an axially compact structure is formed. For reasons of mountability, it may be necessary but also sufficient to divide only a bearing ring in partial rings. Thus, it can be provided that an outer ring of the rotor bearing is divided axially off-center or axially centered in two sub-rings. In an axially central division are two partial rings with the same axial dimension before.

It is conceivable that an outer ring of the rotor bearing has a common track for the at least three rows of bearings of the spherical roller bearing. If the outer ring is divided axially into two partial rings, the common raceway extends over the two dividing rings. This common track is in particular concave and / or has a constant curvature. The common raceway can be described in particular in an axial section through a circular arc.

The rotor bearing according to the invention can be designed and / or used in particular as a fixed bearing point.

It is conceivable that the barrel rollers of one or more, in particular all, rows of bearings are guided by one or more cages.

The spherical roller bearing of the rotor bearing according to the invention can be equipped either with symmetrical or asymmetrical barrel rollers. While symmetric barrel rollers are axially symmetric, asymmetric barrel rollers have different sized faces. It is conceivable that an axially outer bearing row is equipped with asymmetric barrel rollers. It turned out that the use of asymmetric barrel rollers in a spherical roller bearing row with a large Pressure angle produces better kinematic properties, as is the case with symmetrical barrel rollers.

Brief description of the drawings

Embodiments of the present invention are explained below with reference to the accompanying figures. Show

1 a wind turbine comprising a rotor bearing according to the invention,

2 A first embodiment of a rotor bearing according to the invention,

3 A second embodiment of a rotor bearing according to the invention,

4 A third embodiment of a rotor bearing according to the invention,

5 A fourth embodiment of a rotor bearing according to the invention,

6 A fifth embodiment of a rotor bearing according to the invention and

7 A sixth embodiment of a rotor bearing according to the invention.

Detailed description of the drawings

Identical or functionally identical elements are identified by the same reference numerals.

1 shows a wind turbine 1 comprising a rotor bearing according to the invention. The wind turbine 1 includes a machine tower 2 on which a machine house 3 with a generator 4 and a wind-driven rotor 5 with a multiple rotor blades 6 bearing rotor hub 7 is arranged. The rotor 5 is by a rotor bearing 8th (Framed by box), consisting of two axially spaced rotor bearings 21 carried. As usual with shaft bearings, forms a rotor bearing 21 a fixed bearing and a rotor bearing 21 a loose depository. Each one of the two rotor bearings 21 is in the 2 to 7 each shown in more detail with reference to an embodiment.

A first embodiment of a rotor bearing according to the invention 21 comprising a spherical roller bearing 9 which is in the wind turbine 1 in 1 is inserted, shows 2 as an illustration of an axial section.

The spherical roller bearing 9 includes two bearing rings, namely an outer ring 10 and an inner ring 11 , as well as a variety of rolling elements 12 , The rolling elements 12 rolling in a first row of storage 13 , a second row of bearings 14 and a third row of bearings 16 between the bearing rings around a bearing axis 15 from.

The first row of bearings 13 as well as the third bearing row 16 each comprise identical barrel rollers as rolling elements 12 , The barrel rolls of the second bearing row 14 however, they have a different shape. In particular, the barrel rollers of the second row of bearings 14 a greater length than the barrel rollers of the first row of bearings 12 and the third row of bearings 16 , Furthermore, a largest diameter of the barrel rolls of the second row of bearings 14 larger than the largest diameter of the barrel rollers of the first row of bearings 12 and the third row of bearings 16 , The second row of bearings 14 thus enables a high transmission of radial forces. The barrel rollers of the first bearing row 12 and the third row of bearings 16 are - which can not be seen in the drawing - executed asymmetrically.

The first row of bearings 13 as well as the third bearing row 16 each have a pressure angle of α = 22 degrees or γ = 22 degrees, and are primarily, but not exclusively, for transmitting axial loads in both axial directions. The second row of bearings 14 has a pressure angle of β = 0 degrees, ie this bearing row is used to transmit radial loads. The printing lines 22 of the spherical roller bearing 9 are thus arranged axially symmetrical, ie these pressure lines 22 are with respect to a perpendicular to the bearing axis 15 standing level 23 arranged axially mirror-inverted.

Both the outer ring 10 as well as the inner ring 11 are undivided.

3 shows a second embodiment of a rotor bearing according to the invention 21 , According to the first embodiment according to 2 exists the spherical roller bearing 9 now from four rows of warehouses 13 . 14 . 16 . 19 , The rolling elements formed by barrel rollers 12 of all warehouse rows are identical. Furthermore, the spherical roller bearing 9 an axially symmetrical structure, ie the pressure lines of all rows of bearings are axially with respect to the perpendicular to the bearing axis 15 standing level 23 arranged symmetrically. Although the structure is more complex than the post 2 and the required space slightly larger, the spherical roller bearing 9 to 3 but can transmit higher radial and axial forces.

The outer ring 10 is executed axially eccentrically divided and consists of two partial rings 17 . 18 ,

4 shows a third embodiment of an inventive rotor bearing 21 , The spherical roller bearing 9 consists of five rows of warehouses 13 . 14 . 16 . 19 . 20 ,

The printing lines of all series of warehouses 13 . 14 . 16 . 19 . 20 are arranged axially symmetrically, with an axially centrally disposed bearing row, namely the third row of bearings 16 , has a contact angle of γ = 0 degrees (therefore not visible in the figure). Otherwise, α = ε and especially α = ε = 10 degrees and β = δ and especially β = δ = 25 degrees.

5 shows a fourth embodiment of a rotor bearing according to the invention 21 , In contrast to the embodiments of the 2 to 4 the pressure lines of the three rows of bearings shown in the axial section are arranged axially asymmetrically. Ie. the drawn in the axial section pressure lines 22 of the three rows of bearings are none to the bearing axis 15 vertical plane axially mirrored positioned or positioned.

The contact angle of the first bearing row 12 corresponds to 0 degrees, ie that an axially outermost bearing row has a contact angle of 0 degrees.

Because the rolling elements 12 of the three rows of bearings is the spherical roller bearing 9 able to transmit different sized axial forces in the two axial directions. During the first camp row 13 is provided essentially for the transmission of radial forces, in particular serves the third row of bearings 16 for the transmission of axial forces.

6 shows a fifth embodiment of a rotor bearing according to the invention 21 , Again, the pressure lines of the three rows of warehouses 13 . 14 . 16 arranged axially asymmetrically in the axial section. In particular, α = β and especially α = β = 10 degrees and γ = 25 degrees.

7 shows a sixth embodiment of a rotor bearing according to the invention 21 - Again with axially asymmetrical in the axial section arranged pressure lines of this time four rows of storage 13 . 14 . 16 . 19 ,

The rolling elements of one or all bearing rows of all embodiments can be guided by one or more cages. It is possible that two axially adjacent rows of bearings have a common cage.

LIST OF REFERENCE NUMBERS

1

Wind turbine

2

machine tower

3

power house

4

generator

5

rotor

6

rotor blade

7

rotor hub

8th

rotor bearing

9

Spherical roller bearings

10

outer ring

11

inner ring

12

rolling elements

13

first bearing row

14

second bearing row

15

bearing axle

16

third row of bearings

17

partial ring

18

partial ring

19

fourth bearing row

20

fifth row of bearings

21

rotor bearing

22

pressure line

23

level

α

Pressure angle of the first bearing row

β

Pressure angle of the second bearing row

γ

Pressure angle of the third bearing row

δ

Printing angle of the fourth bearing row Printing angle of the fifth bearing series

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

• DE 7003667 U [0007]

Claims (10)

Rotor bearing ( 21 ) of a wind turbine ( 1 ) comprising a spherical roller bearing ( 9 ) with a plurality of around a bearing axis ( 15 ) in warehouse rows ( 12 . 13 . 16 . 19 . 20 ) rolling rolling elements ( 12 ), characterized in that the spherical roller bearing ( 9 ) has at least three rows of bearings. Rotor bearing ( 21 ) according to claim 1, characterized in that in an axial section shown pressure lines ( 22 ) of the at least three rows of bearings are arranged axially symmetrically. Rotor bearing ( 21 ) according to claim 1 or 2, characterized in that in an axial section shown pressure lines ( 22 ) of the at least three rows of bearings are arranged axially asymmetrically. Rotor bearing ( 21 ) according to one of claims 1 to 3, characterized in that the spherical roller bearing ( 9 ) comprises an odd number of rows of warehouses, in particular three or five rows of warehouses. Rotor bearing ( 21 ) according to one of claims 1 to 3, characterized in that the spherical roller bearing ( 9 ) comprises an even number of rows of warehouses, in particular four rows of warehouses. Rotor bearing ( 21 ) according to one of the preceding claims, characterized in that an axially central bearing row has a pressure angle of 0 degrees. Rotor bearing ( 21 ) according to claim 6, characterized in that barrel rollers of the axially central bearing row with respect to barrel rollers of other bearing rows have a different shape, in particular have a greater length. Rotor bearing ( 21 ) according to one of claims 1 to 5, characterized in that an axially outermost bearing row has a pressure angle of 0 degrees. Rotor bearing ( 21 ) according to one of the preceding claims, characterized in that the rotor bearing ( 21 ) an integrally formed inner ring ( 11 ) and one in two partial rings ( 17 . 19 ) axially divided outer ring ( 10 ), in particular that the outer ring ( 10 ) is divided axially centrally or axially off-center. Rotor bearing ( 21 ) according to one of the preceding claims, characterized in that the rotor bearing ( 21 ) forms a fixed deposit.

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