WO2010037373A1

WO2010037373A1 - Rotor bearing for a wind turbine, comprising a double, multi-row rolling bearing with three concentric bearing rings

Info

Publication number: WO2010037373A1
Application number: PCT/DE2009/001366
Authority: WO
Inventors: Rudolf Zeidlhack
Original assignee: Schaeffler Kg
Priority date: 2008-09-30
Filing date: 2009-09-29
Publication date: 2010-04-08
Also published as: DE102008049811A1

Abstract

The invention relates to a rotor bearing (1) for a wind turbine, comprising an inner ring (83), which is or can be rotationally fixed to a first rotational partner, an outer ring (5), which likewise is or can be rotationally fixed to the first rotational partner and an intermediate ring (4), which is or can be rotationally fixed to a second rotational partner. According to the invention, the inner ring (3) is mounted to rotate in relation to the intermediate ring (4) by means of at least one inner rolling body row (7) and the outer ring (5) is mounted to rotate in relation to the intermediate ring (4) by means of at least one outer rolling body row (6).

Description

10 Name of the invention

ROTOR STORAGE FOR A WIND POWER PLANT, COMPRISING A DOUBLE, MULTILING ROLLER BEARING WITH THREE CONCENTRIC BEARING RINGS

15

description

Field of the invention

20 The invention relates to a rotor bearing for a wind turbine and a wind turbine with a corresponding rotor bearing. Such rotor bearings are usually designed as slewing bearings.

25 Background of the Invention

Rolling bearings are usually referred to as slewing bearings whose outer diameter exceeds a range of about 800 mm to 1000 mm. Slewing bearings, which are used in wind turbines as rotor bearings 30 to rotatably support a rotor relative to a housing, may have an outside diameter of, for example, 3000 mm. The rule is that more rolling elements are used as the bearing pitch increases can, so that the bearing capacity increases. A larger bearing pitch circle thus ultimately allows the absorption of larger forces and possibly moments.

Due to constantly increasing power of wind turbines and associated larger dimensions of these systems, the forces and moments to be absorbed by the rotor bearing also increase. However, the thus required increase in the bearing capacity can be absorbed only partially by a corresponding increase in the bearing pitch circle. A larger bearing pitch circle pulls namely a larger outer diameter of the large rolling bearing by itself, which can result in manufacturing difficulties, since, for example, ever larger hardening furnaces are required. In addition, an increase in the outer diameter leads to larger bearing components and thus also to a larger tower head weight, which in turn requires a more massive tower construction. On the other hand, a larger storage capacity can not be easily achieved by more rows of storage, as this increases the cross-sectional profile of the bearing rings, which can manufacturing difficulties, such as during curing, arise.

It should also be noted that rotor bearings are permanently exposed to speeds that are relatively high for the input bearing pitch circles mentioned above. Such slewing bearings must be designed, for example, for speeds of up to 30 revolutions per minute over a period of more than 130,000 operating hours.

From DE 102 42 707 B3 a bearing of a rotor shaft for a wind turbine is known, in which the rotor shaft is supported by means of a two-point support by two pairs of tapered rollers in the machine housing. A disadvantage is the limited carrying capacity of the bearing assembly, which is essentially determined by the number of positionable on the pitch circle of the tapered roller pairs tapered rollers. To a larger one To achieve load capacity, for example, the bearing pitch circle and thus the outer diameter of the large roller bearing would have to be increased. However, this measure prepares, as described above, manufacturing problems.

Object of the invention

The invention has for its object to provide a rotor bearing a wind turbine, which allows a significant borrowing capacity compared to previous solutions and thus can take over larger forces and moments with the same bearing pitch circle and reaches a longer life. It should also be easy and inexpensive to manufacture.

Summary of the invention

The object is achieved by a rotor bearing for a wind turbine with an inner ring, which is non-rotatably connected or connectable with a first rotary partner, with an outer ring, which is rotatably connected to the first rotating partner or connectable, and with an intermediate ring, which with a second rotational partner rotatably connected or connectable, wherein the inner ring is rotatably arranged via at least one inner row of rolling elements relative to the intermediate ring and wherein the outer ring is rotatably arranged on at least one outer row of rolling relative to the intermediate ring.

The two rotary partners are rotatable relative to one another, so that, for example, the first rotary partner represents or is connectable to the rotor, while the second rotary partner is a housing or connected or connectable to it. The at least one inner row of rolling elements has a smaller bearing pitch circle than the at least one outer row of rolling elements, wherein all the rows of rolling elements have a common rotary pitch. Have axis. The at least two rows of rolling elements ensure that the intermediate ring can hardly tilt.

The rotor bearing according to the invention thus comprises a double track system. As a result, much higher load capacities can be achieved compared to simple rotor bearings. Basically, almost twice the forces or tilting moments can be transmitted without having to significantly increase the Innkreisdurchmesser the cross-sectional profile of the bearing rings or the outer diameter of the rotor bearing.

According to one embodiment, there are at least two inner rows of rolling elements and / or at least two outer rows of rolling elements, each of the at least two inner or outer rows of rolling elements transmitting either only axial or only radial forces. So there is a controlled division of the axial and radial forces on different rows of rolling elements. As a result, the game conditions can be set separately and there are lower tilting of the rings to each other. For example, the rows of rolling elements transmitting only radial forces can be formed by cylindrical roller bearings and / or the series of rolling elements transmitting only axial forces can be formed by axial tapered roller bearings. In order to enable a transmission of axial forces in both axial directions, theoretically already a correspondingly arranged outer and inner row of rolling elements for axial force transmission would be sufficient in each opposite direction; However, the transmittable axial forces would not be as large as would be possible in principle in a double track system. Advantageously, therefore, two rows of rolling elements are provided for Axialkraftübertragung in both axial directions between the outer ring and intermediate ring or intermediate ring and inner ring, whereby a better support against tilting moments takes place. To increase the radial load capacity several rows of rolling elements for radial force transmission, ie, for example, several cylindrical roller rows, can be provided. According to one embodiment, in the case of a plurality of internal rolling element rows, each of the at least one inner row of rolling elements and / or in the case of a plurality of outer rows of rolling elements each of the at least one outer row of rolling elements transmits both axial forces and radial forces. In particular, two inner rows of rolling elements and / or two outer rows of rolling elements are each formed by two axially adjacent conical roller rows or by two axially adjacent rows of oblique ball. In this case, two axially adjacent tapered roller rows or two axially adjacent angular contact ball rows can be arranged such that essentially no axial gap remains in order to further reduce the installation space. In particular, no further rolling element row lies axially in between. Two axially adjacent rows of tapered rollers or two axially adjacent rows of angular pitches can form either an O-arrangement or an X-arrangement. In this case, the same but also different arrangements can be selected for the outer and inner rows of rolling elements. For example, two axially adjacent conical roller rows between outer ring and intermediate ring form an X-arrangement, while two axially adjacent conical roller rows between inner ring and intermediate ring form an O-arrangement.

In addition to a pure division of the axial and radial forces on separate rows of rolling elements on the one hand and the exclusive use of Wälzkörperreihen for the transmission of axial and radial forces on the other hand, of course, combinations of both embodiments are conceivable. In this case, e.g. between the outer ring and intermediate ring a division of the axial and radial forces on separate rows of rolling elements, while between inner ring and intermediate ring only Wälzkörperreihen be used, which can transmit both axial and radial forces. Of course, combinations within a career system are also conceivable.

According to one embodiment, the inner ring, the intermediate ring and / or the outer ring on at least one row of holes distributed over the circumference for attachment to the respective rotation partner. examples For example, through holes, threaded holes and / or blind bores can be arranged on an annular end face. These mounting options are matched to the higher load capacity of the rotor bearing according to the invention. In particular, holes can therefore be arranged in two concentrically arranged rows on an annular end face. Such holes can also serve to connect individual elements in multi-part outer ring, intermediate ring or inner ring. Thus, it is conceivable, for example, to assemble the inner ring from a plurality of individual rings, wherein, for example, each individual ring forms a raceway for rolling elements.

It is also within the scope of the invention that further rolling element rows are provided between inner ring and intermediate ring and / or between outer ring and intermediate ring, which is arranged coaxially and / or concentrically with the respective Wälzkörperreihenpaar or are. According to one embodiment, therefore, the rotor bearing comprises further bearing rings which are non-rotatably connected or connectable to the first or the second rotary partner and rotate together with the inner ring or the outer ring or the intermediate ring.

According to one embodiment, the connecting end faces of the bearing rings of a rotary partner are formed plane-parallel. In this development, e.g. The first turning partner will only provide a flat surface as a connecting structure, with the optional advantage that grades and the like in the connection contour are avoided.

According to one embodiment, the rolling elements of at least one row of rolling elements are guided through a cage. Typically, a separate cage is provided for each row of rolling elements, so that each row of rolling bodies can freely adapt to the rotational movements of the bearing rings independently of the other rows. According to one embodiment, axial forces in both axial directions, radial forces and tilting moments can be absorbed by the rotor bearing. The rotor bearing according to the invention is thus particularly well suited to be used in a so-called Einlagerkonzept. Conventionally, the rotor shaft of a wind turbine is supported by two-point or three-point supports with two or three separate bearings in the machine housing. Meanwhile, storage concepts are used for the storage of the rotor, ie, a single bearing assumes both all axial and radial forces and tilting moments. Accordingly, the rotor bearing according to the invention can serve as part of a Einlagerkonzepts in a wind turbine, for example, the first rotary partner is connected to a housing or connectable and the second rotary partner is connected to a rotor or connectable.

According to one embodiment, at least one of the rings, in particular the inner ring, outer ring or intermediate ring, is made of case-hardened steel. The use steels preferably include unalloyed or low alloy steels, up to a maximum carbon content of 0.20%. During curing, the case steels are "used" in a carbonaceous atmosphere and heated to temperatures between 880 ° C and 1050 ° C, so that the carbon of the carbonaceous atmosphere diffuses into the edge layer of the case steel, wherein the carbon content in the surface layer, for example, to about As a result, the bearing ring is formed inside with a high toughness and on the surface, especially on the raceways, with a considerably greater hardness and thus with a high resistance to fatigue and wear.

Even if at least one of the rings, in particular the inner ring, outer ring or intermediate ring, is made of case-hardened steel and is through-hardened, it is also conceivable to produce this ring of tempered steel. Another object of the invention relates to a wind turbine, which has a housing and a rotor which is rotatably mounted on the housing. The wind turbine is characterized in that the bearing for rotating the rotor relative to the housing is formed as a rotor bearing, as described above.

In principle, the invention is not limited to rotor main bearings, but can be used wherever appropriate large rolling bearings are required with high load capacities. Another application example of the invention is the main storage of a tunnel boring machine.

Brief description of the drawings

Embodiments of the present invention will now be described with reference to the accompanying drawings, in which:

1 is a schematic sectional view of a first embodiment of the invention,

2 is a schematic sectional view of a second embodiment of the invention,

Fig. 3 is a schematic sectional view of a third embodiment of the invention and

Fig. 4 is a schematic sectional view of a fourth embodiment of the invention. Detailed description of the drawing

1 shows a half of a rotor bearing 1 according to the invention in a sectional view along the axis of rotation 2 of the rotor bearing 1. Shown is the inner ring 3, the intermediate ring 4 and the outer ring 5 with rolling elements 6 both between outer ring 5 and intermediate ring 4, as well as with rolling elements. 7 between intermediate ring 4 and inner ring. 3

Both the inner ring 3 and the outer ring 5 consist of a plurality of ring elements 3a, 3b, 3c, 5a, 5b, 5c, while the intermediate ring 4 consists of a single ring element. The intermediate ring 4 has circumferentially arranged holes, by means of which he is attached to a rotor piece 8 of the rotor, not shown. The outer ring and the inner ring have corresponding holes to be connected to a housing, not shown.

There are two rows of rolling bodies both between the outer ring 5 and the intermediate ring 4 and between the inner ring 3 and the intermediate ring 4, wherein each row of rolling elements is suitable for absorbing axial and radial forces. The rows of rolling elements are formed by tapered roller bearings each axially adjacent, i. are arranged without intervening rows of rolling elements. The two tapered roller bearings between outer ring 5 and intermediate ring 4 form an X-arrangement. The two tapered roller bearings between inner ring 3 and intermediate ring 4 form an O-arrangement. Instead of tapered roller bearings and angular contact ball bearings can be used, which also this example. can form an O-arrangement.

The connection end faces 9 of inner ring 3 and outer ring 5 are made plane-parallel to allow a simple and defined investment in a housing. Fig. 2 shows a second embodiment, reference being made to the previous description with respect to like elements or reference numerals. Also in this embodiment, all rows of rolling elements are able to absorb axial and radial forces, since it is tapered roller bearings. In this case, however, the outer rows of rolling elements form an O-arrangement and the inner rows of rolling elements form an X-arrangement. The inner ring 3 and the outer ring 5 consist of a single ring element. The intermediate ring 4, however, is composed of a plurality of ring elements 4a, 4b, 4c, 4d, 4e. In this case, the circular ring-shaped ring element 4e acts as a bearing cap, and can be connected to the ring element 4a with screws and a multiplicity of bores distributed over the bore pitch circle 10.

3 shows a third exemplary embodiment, reference being made to the preceding description with regard to identical elements or reference symbols. Again, the rolling bearing rows are formed by tapered roller bearings and can absorb both axial and radial forces. The outer and inner rows of rolling elements each form an O arrangement.

4 shows a fourth exemplary embodiment, reference being made to the preceding description with regard to identical elements or reference symbols. The inclusion of axial and radial forces takes place by separate rows of rolling elements, both between the outer ring 5 and intermediate ring 4 and between inner ring 3 and intermediate ring 4. The radial forces are transmitted exclusively by cylindrical roller bearings 12. The axial forces are transmitted through two rows of axial taper roller bearings 13, respectively. The intermediate ring 4 consists of a ring. Inner ring 3 and outer ring 5 consist of three ring elements 3a, 3b, 3c, 5a, 5b, 5c, which are connected by means of screws. LIST OF REFERENCE NUMBERS

1 rotor bearing

axis of rotation

3 inner ring

3a, 3b, 3c ring elements of the inner ring

4 intermediate ring

5 outer ring

5a, 5b, 5c ring elements of the outer ring

6, 7 rolling elements

8 rotor piece

9 connection faces

10 hole pitch circle of the intermediate ring

11 hole pitch circle of the inner ring

12 cylindrical roller bearings

Claims

claims

1. Rotor bearing for a wind turbine with an inner ring which is rotatably connected or connectable to a first rotary partner, with an outer ring which is also rotatably connected or connectable to the first rotary partner, and with an intermediate ring which rotatably connected to a second rotary partner or is connectable, wherein the inner ring is rotatably arranged via at least one inner row of rolling elements relative to the intermediate ring and wherein the outer ring is rotatably disposed relative to the intermediate ring via at least one outer row of rolling elements.

2. rotor bearing according to claim 1, characterized in that at least two inner rows of rolling elements and / or at least two outer rows of rolling elements are present, each of the at least two inner or outer rows of rolling elements transmits either only axial or only radial forces.

3. rotor bearing according to claim 2, characterized in that only radial forces transmitted rolling element rows are formed by cylindrical roller bearings.

4. rotor bearing according to claim 2 or 3, characterized in that only axial forces transmitted Wälzkörperreihen be formed by axial tapered roller bearings

5. rotor bearing according to claim 1, characterized in that each of the at least one inner row of rolling elements and / or the at least one outer row of rolling elements transmits both axial forces and radial forces.

6. rotor bearing according to claim 5, characterized in that two inner rows of rolling elements and / or two outer rows of rolling elements are each formed by two axially adjacent tapered roller rows or two axially adjacent rows of angular pitch.

7. Rotor bearing according to claim 6, characterized in that two axially adjacent tapered roller rows or two axially adjacent rows of angular pitches form an O-arrangement and / or two axially adjacent tapered roller rows or two axially adjacent rows of angular pitches an X-arrangement.

8. Rotor bearing according to one of the preceding claims, characterized in that the inner ring, the intermediate ring and / or the outer ring has at least one row of holes distributed over the circumference for attachment to the respective rotation partner.

9. rotor bearing according to one of the preceding claims, characterized by further bearing rings which are rotatably connected to the first or the second rotary partner or connectable and rotate together with the inner ring or the outer ring or the intermediate ring.

10. Rotor bearing according to one of the preceding claims, characterized in that one of the rings, in particular the inner ring, outer ring or intermediate ring, is made of case-hardened steel.

11. Rotor bearing according to one of the preceding claims, characterized in that rolling elements of at least one row of rolling elements are guided by a cage.

12. rotor bearing according to one of the preceding claims, characterized in that by the rotor bearing axial forces in both

Axial directions, radial forces and tilting moments can be recorded.

13. Rotor bearing according to one of the preceding claims, characterized in that the rotor bearing is used as Einlagerkonzept.

14. Rotor bearing according to one of the preceding claims, characterized in that the first rotary partner is connected to a housing or connectable and the second rotary partner with a

Rotor is connected or connectable.

15. Wind turbine, which has a housing and a rotor which is rotatably mounted on the housing, characterized in that the bearing is designed for rotation of the rotor relative to the housing as a rotor bearing according to one of the preceding claims.