DE102011088692A1 - Roller bearing for wind power plant, has outer and inner rim portions whose contact surfaces are arranged at preset angle in longitudinal section so that cylindrical roller tilting moment generated due to axial load is counteracted - Google Patents

Abstract

The roller bearing (1) has an outer rim portion (9) and an inner rim portion (8) that are arranged in a longitudinal section at a rotational axis (2). A cylindrical roller (5) is extended through contact surfaces along the axial direction. The contact surfaces of the outer and inner rim portions are arranged at predetermined angle in the longitudinal section with respect to a radial plane such that the cylindrical roller tilting moment generated due to axial load is counteracted. An independent claim is included for a method for manufacturing roller bearing.

Description

The invention relates to a cylindrical roller bearing with an inner race carrier, which provides an inner race, with an outer race carrier, which provides an outer race, with a plurality of cylindrical rollers, wherein the cylindrical rollers are arranged in a Wälzkörperraum rolling between the inner and the outer race, so that the inner race carrier and the outer race carrier can rotate relative to each other about an axis of rotation, and with at least one outboard and at least one inboard, which are arranged in a longitudinal section through the axis of rotation of the cylindrical roller bearing with respect to the Wälzkörperraum diagonally to each other and which the cylindrical rollers on thrust surfaces in axial Lead direction.

Cylindrical roller bearings in conventional construction comprise an inner ring, an outer ring and a plurality of cylindrical rollers arranged therebetween, which roll on the raceways of the rings in a relative rotation of inner ring and outer ring. Cylindrical roller bearings serve primarily to transmit radial loads from the inner ring to the outer ring or in the opposite direction. Axial loads can be significantly worse transmitted via cylindrical roller bearings due to the design. However, it is quite common that inner ring and outer ring each have ribs which support the cylindrical rollers in the axial direction, so that at least a certain axial load can be removed via the cylindrical roller bearing.

The publication DE 10 2007 058 824 A1 relates to a single-row cylindrical roller bearing with a bearing outer ring and a bearing inner ring, as well as from a plurality between the bearing rings arranged roller rolling elements. For axial guidance of the roller rolling elements guide rims are arranged integrally on the bearing rings. The cylindrical roller bearing is characterized in that the one guide board on the raceway of the inner bearing ring and a diagonally opposite guide board on the raceway of the outer bearing ring are each formed radially extended beyond the pitch circle diameter of the cylindrical roller bearing and arranged on their inner sides in each case in the region of the pitch circle diameter Have ring contact surfaces through which the axial forces of the radial roller bearing, the opposing resulting axial forces in each case at the height of the pitch circle diameter of the cylindrical rollers are approximately kippmomentfrei receivable.

The publication DE 1818601 , which is probably the closest prior art, also discloses a radial cylindrical roller bearing with loose or solid shelves, wherein two each other in the bearing cross section diagonally opposite shelves are higher than the or the other shelves.

Field of the invention

The invention has for its object to propose a cylindrical roller bearing, which can absorb axial loads particularly well. The invention is also based on the object to disclose a method for the design of such a cylinder bearing.

This object is achieved by a cylindrical roller bearing with the features of claim 1 and by a method having the features of claim 8. Preferred or advantageous embodiments of the invention will become apparent from the dependent claims, the following description and the accompanying drawings.

In the context of the invention, a cylindrical roller bearing, in particular designed as a radial rolling bearing proposed. Particularly preferably, the cylindrical roller bearing is formed in a single row. The cylindrical roller bearing has an inner race which has an inner race and an outer race which provides an outer race. Inner raceway carrier and / or outer raceway carrier may each be formed as a Wälzkörperring. However, it is also possible that one or both may form part of another, more complex structure, such as e.g. a shaft, an axis or a receiving geometry is or are formed.

The cylindrical roller bearing comprises a plurality of cylindrical rollers, wherein the cylindrical rollers between the inner and the outer raceway are arranged rolling in a Wälzkörperraum. This makes it possible for the inner race carrier and the outer race carrier to rotate relative to each other about a rotation axis. In particular, the cylindrical rollers are formed in the shape of a straight cylinder. Particularly preferably, the axes of rotation of the cylindrical rollers with the axis of rotation of the cylindrical roller bearing rectified or even aligned in parallel.

In possible embodiments, the cylindrical roller bearing has a cage, which is designed to space the cylindrical rollers from each other in the direction of rotation. However, it is particularly preferred, in particular in order to obtain a very stable cylindrical roller bearing, that the cylindrical rollers are arranged fully rolling in the cylindrical roller bearing, so that this is cage-free.

The cylindrical roller bearing comprises at least one outboard and at least one inboard, wherein the two rims in longitudinal section through the axis of rotation of the cylindrical roller bearing with respect to the Wälzkörperraum are arranged diagonally to each other. If one thus sets a cutting plane through the cylindrical roller bearing, wherein the axis of rotation lies in the cutting plane, then the rolling body space is based on the shape of the cylindrical rollers as a rectangular or cuboid receiving space. The outboard is associated with the outer raceway carrier and preferably integrally connected thereto, in particular with the outer raceway. The inboard is associated with the inner raceway carrier and preferably integrally connected thereto, in particular with the inner raceway. Due to the diagonal arrangement of outboard and inboard, it is possible to transmit axial loads on the cylindrical rollers from one carrier to the other carrier. The cylindrical roller bearing may be limited to the inboard and outboard one, optionally, inner raceway carriers or outer raceway carriers may include additional rims.

In the context of the invention it is proposed that the contact surfaces of the outboard and the diagonally opposite inboard for the cylindrical rollers in the longitudinal section relative to radial planes to the axis of rotation of the cylindrical roller bearing each have an on-board angle. This structural design has the effect of counteracting a tilting moment of the cylindrical roller which is produced during an axial load. The on-board angle is measured in the longitudinal section between the radial plane and the contact surface of the respective shelf and is greater than 0 °, preferably greater than 5 ° and in particular greater than 10 ° dimensioned.

The contact surfaces are preferably formed straight in said longitudinal section. In modified embodiments, one or both contact surfaces may also be curved, wherein the board angle in this case by an approximate straight line through the contact surfaces, e.g. via a least square algorithm, is determined.

It is a consideration of the invention that at an axial load of the cylindrical roller bearing, the cylindrical rollers incline without an on-board angle to the contact surfaces in the plane of the longitudinal section for tilting and thereby produce an asymmetric surface pressure on the track. This asymmetrical surface pressure is an influencing variable which limits the permissible axial force of the cylindrical roller bearing. By chamfering the contact surfaces of the outboard and the inboard a Gegenkippmoment is caused in the axial load, which compensates in an ideal case, resulting from the axial load overturning moment of the cylindrical rollers. Thus, the on-board angle of the contact surfaces of the outboard and the diagonally opposite inboard results in that despite an axial load of the cylindrical roller bearing a symmetrical or homogeneous surface pressure along the cylindrical rollers on the inner and outer raceway can be achieved and thus the load capacity of the cylindrical roller bearing for axial loads is increased.

In a preferred embodiment of the invention, the cylindrical rollers are curved on the front side, preferably formed torusballig. Particularly preferably, the torus is realized as a so-called donut. A torusballige end face is a rotationally symmetrical cylindrical roller having a convexly outwardly curved end face in an area adjacent to the lateral surface region of the end face, the imaginary radius of curvature maintains a distance from the axis of rotation of the cylindrical roller, and wherein between the curved edge regions of the end faces a flat or is provided flat area through which the axis of rotation of the cylindrical roller occurs. The curvature can be spherical or have a different profile, for example a logarithmic profile. Such cylindrical rollers with torusballiger face are from the writings DE 10 2005 061 103 A1 and DE 10 2005 061 102 A1 which is expressly incorporated herein by reference. In other embodiments, the end face may also be convex, ie convex or in particular part-circular.

In a first possible embodiment of the invention, in particular in a static design, the board angle for the contact surfaces of the outboard and inboard are selected so that in the longitudinal section a normal, ie a vertical, the contact surface of the outboard and a normal, ie a vertical in that the leading surface of the inboard forms a common straight line passing through a center of the cylindrical roller. The center of the cylindrical roller is the center of the axis of rotation of the cylindrical roller. This configuration in a static design is easy to implement and causes the two acting on-board forces act substantially directly against each other, so are largely on a line of action. Thus, there is no lever arm between the two airborne forces and thus no more tilting moment.

In a possible concretization of the invention, the base of the normal of the approach surface of the outboard and / or the base of the normal of the contact surface of the inboard in a contact of the cylindrical roller with the respective contact surface, wherein the cylindrical roller bearing is in an axially unloaded state. With this design guideline, the on-board angles can be determined and implemented in a simple manner.

In principle, it is possible that the two on-board angles are different in size in order to achieve optimum tuning. However, one To implement manufacturing as simple as possible, it is preferred that the board angle of the two contact surfaces is the same size.

In a second possibility of the invention, in particular in a dynamic design, the on-board angles are selected so that the forces transmitted from the inboard and outboard to the cylindrical rollers in the axial direction lie on a common line of action. Such a dynamic design is usually carried out by model calculations, in particular FEM calculations, whereby the on-board angles are varied while the geometry of the cylindrical roller bearing remains constant and, if appropriate, the radius of curvature of the end faces of the cylindrical rollers until a local or global maximum is reached in the optimization.

Particularly preferably, the dynamic design is carried out at a maximum axial load of the cylindrical roller bearing. This maximum axial load can then be used at a later time as the basis for a nominal maximum axial load of the cylindrical roller bearing.

Another object of the invention relates to a method for designing or manufacturing the cylindrical roller bearing, as described above or according to one of the preceding claims, wherein the two board angles and optionally complementing the radius of curvature of the end faces of the cylindrical rollers with the same geometry of the cylindrical roller bearing as long be varied until a tilting of the cylindrical rollers is minimized and / or a surface pressure of the cylindrical rollers on the raceways at a predetermined axial load homogenized or symmetrized.

Particularly preferably, the cylindrical roller bearing is designed as a large roller bearing with a pitch circle diameter of greater than 500 mm, preferably greater than 1,000 mm. Furthermore, it is preferred that the cylindrical roller bearing for slow-rotating applications, ie for applications with rotational speeds less than 10 revolutions / s and in particular less than 5 revolutions / s is formed.

Further features, advantages and effects of the invention will become apparent from the following description of preferred embodiments of the invention and the accompanying figures. Showing:

1 a schematic longitudinal section through a cylindrical roller bearing in detail as a first embodiment of the invention;

2 in the same representation as in 1 A second embodiment of the invention.

The 1 shows a highly schematic longitudinal section of a cylindrical roller bearing 1 as a first embodiment of the invention, wherein the longitudinal section through the axis of rotation 2 of the cylindrical roller bearing 1 runs. The cylindrical roller bearing 1 is preferably designed as a slow-rotating cylindrical roller bearing with rotational speeds less than 10 revolutions / s. For example, it is a rotor bearing of a wind turbine. The cylindrical roller bearing 1 includes an inner ring 3 as well as an outer ring 4 , between which a plurality of cylindrical rollers 5 are arranged. The inner ring 3 represents an inner career 6 and the outer ring 4 an outer career 7 available, with the cylindrical rollers 5 on the careers 6 . 7 roll over so that the inner ring 3 and the outer ring 4 relative to each other about the axis of rotation 2 are rotatable. The ring area in which the cylindrical rollers 5 are arranged, is also referred to as Wälzkörperraum.

The inner ring 3 points in the 1 right side an inboard 8th on, which is formed continuously encircling and the cylindrical rollers 5 leads laterally. The outer ring 4 has an outboard diagonally opposite the roller body space nine on which also the cylindrical rollers 5 leads. outboard nine and inboard 8th serve to an axially acting force according to arrow F of the outer ring 4 on the inner ring 3 transferred to. In the same way, the shelves 8th . nine serve, from the opposite side a force according to arrow F 'of the inner ring 3 on the outer ring 4 transferred to.

However, the transmission of the axial force F or F 'leads to a tilting moment of the cylindrical rollers 5 in the in 1 shown longitudinal section plane, so that the cylindrical rollers 5 on the inner raceway 6 and the outer raceway 7 When viewed in axial extension, they no longer roll smoothly but asymmetrically. Instead of a uniform, elongated and symmetrically arranged pressure ellipse on the raceways 6 . 7 it comes to a displaced in the axial direction pressure load. This asymmetric pressure load limits the bearing capacity of the cylindrical roller bearing 1 for axial loads.

To compensate for this tilting moment in an axial load, both the end faces of the cylindrical rollers 5 as well as the contact surfaces of the inboard 8th and from the outboard nine designed as follows:

The front ends 10a , b of cylindrical rollers 5 each have a radius r, so that the end faces are formed spherical segment. It is possible that the front ends 10a , b the cylindrical rollers 5 in a middle area, which is not from the Borden 8th . nine is contacted, flattened. Instead of a radius r or a spherical segment-shaped configuration, it is also possible to provide a torus-shaped embodiment, wherein - in terms of figures - a donut is applied to each of the front sides 10a , b is formed.

The contact surfaces of the outboard nine and in the same way from inboard 8th are - as in the 1 using the example of the outboard nine slanted in the longitudinal section shown, being between a radial plane R, perpendicular to the axis of rotation 2 stands, and the course of the chamfer results in an on-board angle α. The on-board angle α is dimensioned so that a normal N on the contact surface in a contact point between the cylindrical roller 5 and outboard nine through the center of the cylindrical roller 5 runs and in the same way through the contact point between the cylindrical roller 5 and inboard 8th runs and again as normal N on the approach surface of the inboard 8th incident.

In the 1 illustrated embodiment is a static design for the shelves 8th . nine and the cylindrical roller 5 , Once the axial force F on the cylindrical roller bearing 1 acts, the in-flight forces resulting from the axial force F largely against each other and are in this embodiment approximately on a line of action. Thus, the lever arm is reduced and the tilting moment of the cylindrical roller between the two on-board forces 5 significantly reduced.

The 2 on the other hand shows a dynamic design of the cylindrical roller bearing 1 as a second embodiment of the invention. In this embodiment, the shelves 8th . nine and the front ends 10a , B of the cylindrical roller bearing designed dynamically, the design has been defined so that the airborne forces Fb for a predetermined axial force F and F 'are on a common line of action W, so that the tilting moment for the previously defined axial force F is fully compensated.

LIST OF REFERENCE NUMBERS

1

 Cylindrical roller bearings

2

 axis of rotation

3

 inner ring

4

 outer ring

5

 cylindrical rollers

6

 inner career

7

 outer career

8th

 inboard

9

 outboard

10a

 front

10b

 front

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 102007058824 A1 [0003]
• DE 1818601 [0004]
• DE 102005061103 A1 [0014]
• DE 102005061102 A1 [0014]

Claims (8)

Cylindrical roller bearings ( 1 ) with an inner race carrier ( 3 ), which has an inner career ( 6 ) with an outer-track carrier ( 4 ), which has an outer career ( 7 ), with a plurality of cylindrical rollers ( 5 ), whereby the cylindrical rollers ( 5 ) in a Wälzkörperraum between the inner and outer raceway ( 6 . 7 ) are arranged rollingly so that the inner race carrier ( 3 ) and the outer raceway girder ( 4 ) relative to each other about a rotation axis ( 2 ), with at least one outboard ( nine ) and at least one inboard ( 8th ), which in a longitudinal section through the axis of rotation ( 2 ) of the cylindrical roller bearing ( 1 ) are arranged with respect to the Wälzkörperraum diagonally to each other and which the cylindrical rollers ( 5 ) run over contact surfaces in the axial direction, characterized in that the contact surfaces of the outboard ( nine ) and the inboard ( 8th ) in the longitudinal section opposite to a radial plane (R) to the axis of rotation ( 2 ) each have an on-board angle (alpha), so that a tilting moment of the cylindrical rollers (FIG. 5 ) is counteracted. Cylindrical roller bearings ( 1 ) according to claim 1, characterized in that the cylindrical rollers ( 5 ) curved at the end-side end face, preferably formed torusballig. Cylindrical roller bearings ( 1 ) according to claim 1 or 2, characterized in that the board angle (alpha) are selected so that in the longitudinal section a normal (N) of the contact surface of the outboard ( nine ) and a normal (N) of the inboard surface of the inboard ( 8th ) a common straight line through a center of the cylindrical rollers ( 5 ) form. Cylindrical roller bearings ( 1 ) according to claim 3, characterized in that the base point of the normal of the contact surface of the outboard ( nine ) and / or the base point of the in-plane surface of the inboard ( 8th ) in a contact point of the cylindrical roller ( 5 ) with the respective contact surface in an axially unloaded state of the cylindrical roller bearing ( 1 ) lies. Cylindrical roller bearings ( 1 ) according to one of the preceding claims 3 or 4, characterized in that the board angle (alpha) of the two contact surfaces is selected to be the same size. Cylindrical roller bearings ( 1 ) according to one of the preceding claims, characterized in that the board angle (alpha) are selected so that the of the inboard ( 8th ) and the outboard ( nine ) on the cylindrical rollers ( 5 ) forces transmitted in the axial direction lie on a common line of action (W). Cylindrical roller bearings ( 1 ) according to claim 6, characterized in that the board angle selection at a maximum axial load of the cylindrical roller bearing ( 1 ) he follows. Method for designing the cylindrical roller bearing ( 1 ) according to one of the preceding claims, characterized in that the two on-board angles (alpha) are varied at a predefinable axial load (F, F ') until a tilting or a tilting moment of the cylindrical rollers ( 5 ) and / or a surface pressure of the cylindrical rollers ( 5 ) on the raceways ( 6 . 7 ) is homogenized.

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