WO2010020418A1

WO2010020418A1 - Rolling bearing arrangement and wind turbine equipped therewith

Info

Publication number: WO2010020418A1
Application number: PCT/EP2009/006040
Authority: WO
Inventors: Frank Hubertus
Original assignee: Imo Holding Gmbh
Priority date: 2008-08-20
Filing date: 2009-08-20
Publication date: 2010-02-25
Also published as: US20110229312A1; DE102008038534A1; CN102132055A

Abstract

The invention relates to a rolling bearing arrangement comprising two concentric rings, at least sections of which are arranged inside one another and comprising a gap between said rings, allowing the latter to rotate in opposition to one another about an imaginary axis in the centre of the rings that runs approximately perpendicularly to the ring plane. A race for at least one row of rotationally symmetrical rolling bodies that roll between the rings is situated in the vicinity of a gap section between the rings that surrounds the rotational axis at a constant radius, said race forming a closed loop on one plane. The rolling bodies in one row are guided through a cage at approximately equidistant intervals, said cage having at least one disc-shaped region set into a continuous circular groove-type depression in the vicinity of the race of a bearing ring and a comb-type form with a plurality of spacer pieces that are interconnected in combination along a back region, each piece having a pocket formed between neighbouring spacer pieces for receiving a respective rolling body, the opening of each pocket extending continuously in the upper face of the cage beyond the edge of said cage lying opposite the back region into the lower face. According to the invention, the cage is completely interrupted in at least one place and formed from a resilient material, so that it can be bent up and/or together in the region of the approximately disc-shaped region. The invention further relates to a wind turbine equipped with said bearing arrangement.

Description

Rolling bearing assembly and thus equipped wind turbine

The invention is directed to a rolling bearing arrangement, in particular in the context of a (drivable) rotary joint, preferably for a main, leaf and / or engine house bearing a wind turbine, with two concentric with each other and at least partially arranged in each other, annular connecting elements, and with a gap between These connecting elements, so that they are rotated about an imaginary, about the axis of the ring about vertical axis in the center of the connecting elements against each other, wherein in the region of a rotation axis of approximately constant radius surrounding gap portion between the connecting elements at least one within a plane circular self-contained career is arranged for at least one row of rolling rolling between the connecting elements rolling elements of rotationally symmetrical shape, wherein the rolling elements of a series are guided by a cage in approximately equidistant intervals, which at least one e has a disc-shaped area which is inserted into a circumferential, groove-shaped depression in the region of the track of a connecting element, and wherein the cage is formed as a comb, with a plurality of spacers, which are simply connected together along a back region, and with one each pocket arranged between adjacent spacers for accommodating a preferably spherical rolling element, wherein the opening of a pocket extends continuously in the upper side of the cage over its edge opposite the back region into its underside, furthermore onto a wind turbine equipped with at least one rolling bearing.

Rolling bearings or provided therewith, possibly drivable rotary joints are used in many places. Large rolling bearings, for example with a raceway diameter of 1000 mm or more, are used, inter alia, in wind turbines, preferably in wind turbines having a wind turbine having one or more wings, the axis of rotation of which is set approximately parallel to the wind direction during operation. In particular, in the storage of the leaves and the entire machine house, but also as a main bearing or rotor bearing for supporting the hub of a wind turbine trusts in such large rolling bearings, which are able to absorb all occurring axial and radial forces and tilting moments with suitable dimensioning. In some such applications, for example in leaf bearings, preloaded, ie play-free raceways are used. An advantage of this is an improved load distribution in the raceway system and thus an improved service life. Frequently, a rolling bearing of the design four-point bearing is used, ie a bearing with spherical rolling elements and with two raceways, which are designed such that each ball has two points of contact with each career. Such bearings can be easily provided with a bias. However, in particular in such four-point bearings under combined load in the raceway system (axial and radial forces and tilting moments) to different contact angles between a ball and a raceway; In addition, depending on the load combination and position of a single rolling element - instead of a four-point contact, a two-point contact can even result. Such displacements of the contact points of individual rolling elements can change their position relative to adjacent balls, and to prevent uneven distribution of the balls, a cage is therefore often used in preloaded four-point bearings to keep the balls at equal intervals. However, a cage requires a larger gap width than a roller bearing without a cage, because the connection between the spacers of the cage for stability reasons must not fall below a minimum thickness. However, this reduces the achievable load capacity because the contact area of a rolling element approaches the edge of a track more quickly and more frequently. Therefore, it has already been proposed, for example in DE 33 0655 A1, to provide a separate groove in the region of a raceway, in which individual cage segments are guided, each having two pockets for receiving a rolling element, so that the width of the gap between the two annular connecting elements despite using a cage over an embodiment with separate spacers instead of a cage must not be increased. A disadvantage, however, is that instead of a single cage, a large number of small cage segments must be used, each with only two pockets for rolling elements, which just in large-diameter bearings of the order of a diameter of about 1000 mm or more at a great effort during assembly leads. Even more, only loose juxtaposed Käfigsegemente can pose further problems with preloaded bearings, because - under the considerable forces which act during operation on a large roller bearing, for example, in a wind turbine - despite best efforts shifts between the individual cage segments can occur, creating individual Rolling elements can be clamped and then subject to increased wear.

From the disadvantages of the prior art described results in the invention initiating problem, a generic rolling bearing assembly with a cage in such a way that the mounting of the cage is as simple as possible; In addition, it should be ensured that all rolling elements are held at the same intervals, without being clamped.

The solution to this problem is achieved in that the cage is completely interrupted at least one point and formed of a resilient material so that it is within the surface, in particular level, of the approximately disc-shaped area elastically up and / or zusammenbiegbar.

Preferably, a cage is interrupted only once and thus overall in one piece or simply connected. It is, however possible to divide this possibly even with particularly large bearings twice or more times, but preferably not more often than, for example, five times, preferably not more than four times, especially not more often than three times. The resilient material is able to change its bending radius to 5, thereby optimally and with minimal effort to insert into a groove, wherein it is first forcibly deformed to be striped over the end face of an annular connecting element to its career ; only within the groove provided for this purpose, the cage relaxes again and springs back again in the direction of its original lo shape.

It has proved to be favorable that the cage consists of a metal, for example. Steel, preferably spring steel or tempered steel. In particular, such a material has a high compressive strength in order to assert itself against the high forces within a roller bearing.

Preferably, four, more or all spacers of the cage are connected to each other, so that three, more or all pockets are connected to each receiving a rolling element. Since just the joints between 20 non-contiguous cage segments can lead to shifts within the camp, they should be avoided as far as possible.

The cage should be designed such that do not deform in a change in the distance between the end faces of two adjacent spacers whose end faces, in particular their upper and lower edges do not move against each other. Only this ensures that the rolling elements are not clamped even when the ring is deformed, for example due to thermal expansion.

30

A preferred means of providing high shear strength within the cage is to use only a single (material) Able to make. Thus, at most macroscopic deformations of the material itself could lead to jamming, which, however, is not to be feared, in particular in the case of the design of the metal cage.

It is within the scope of the invention that at least one spacer has a greater height than the back region of the cage. This makes it possible to embrace a sphere over a large area; This can always be forced to the desired position with only a slight surface pressure and thus extremely gentle and wear-free.

All pockets of the cage should be open at the longitudinal side of the cage opposite the back. This results on the one hand a good flexibility of the cage, because the pockets can open or narrow if necessary; On the other hand, all pockets can thus be filled with rolling elements from the same side or raceway, ie through one and the same filling opening.

According to the invention, the cage has at least one desired bending surface, preferably in its back region. This may preferably be a cross-sectional constriction of the cage, where - thanks to approximately homogeneous material properties of the cage - whose bending strength is reduced.

At least one desired bending surface preferably runs transversely to the circumferential direction of the rolling bearing and in this case follows approximately a line of the smallest cross section through it.

At least one such desired bending surface can be provided in the region Qe) of a spacer, because the spacers lie just between two adjacent rolling elements and therefore no deformation of a rolling element is triggered in a deformation in this area - for example. Due to overstretching during assembly. The invention recommends to form at least one desired bending surface as a notch of the cage, in particular in the front side of the back region. This gives the cage deliberately lines of weakness, where it can deform in an overload, without affecting its functionality.

The maximum depth of at least one notch should be approximately equal to the minimum width of the back area at the bottom of a pocket. The back area can be completely interrupted at the notch locations, so that the cage is only connected at these locations via the spacers. This results in a very high bending capacity of the cage in the region of the spacers. Although they are barely deformable on their vertical center or symmetry plane, but directly next to it, that is approximately in or at the foot of the two flanks of a spacer.

Furthermore, a notch should pass through the back region of the cage from its top to its underside, so that it is equally flexible over the entire back cross section and local overstress is avoided.

It is within the scope of the invention that at least one notch has rounded edges, preferably at the edges with a vertical course, relative to the base of the rolling bearing, in particular in the region of the transition between the edges of the notch, ie at the bottom of the notch, and / or beyond their two flanks, ie the transition into the subsequent back area.

Preferably, the rolling elements are encompassed by the cage where, during their rolling, their peripheral speed is highest, preferably thus approximately in the region of their equator. In particular, in such an embodiment, the cage back leader receiving groove is about in the middle of the raceway of the relevant connecting ring, that is approximately at half the height of the raceway. Such an arrangement has the advantage that the rolling elements are encompassed on their plane of symmetry and thus exchange no radial forces with the cage, which thereby experiences no bending moment transverse to its longitudinal direction.

It is sufficient if the rolling elements are encompassed at most 270 ° of their circumference, for example only to 230 ° of its circumference or less, preferably only 190 ° or less, in particular only to about 180 ° of its circumference. The spacer elements of the cage should not be too long because their free ends move the most during a bend, which can significantly change their spacing. In particular, an inelastic deformation of individual cage sections - for example during assembly - could therefore lead to a jamming of individual rolling elements. Such can be prevented if the length of the spacers approximately perpendicular to the cage back, so in the radial direction relative to the axis of rotation of a radial bearing, only about the (maximum) radius of a rolling element corresponds, so the rolling elements only up to two approximately diametrically opposite surface areas be seized.

If, as the invention further provides, the inside of at least one pocket for accommodating one rolling element has a concave curvature parallel to the plane of the rolling bearing approximately at the level of the back region of the cage, such a hollow curvature can optimally fit the convex surface curvature of a rolling element Rolling be adapted so that only a very small gap between the rolling elements and cage pocket remains in the encompassed area, therefore, the rolling elements are guided in close tolerance intervals.

Further advantages are obtained by the fact that the concavely curved area follows approximately a semicircle or a smaller circular arc segment. This allows the balls from the open side of a bag into this to use, in particular after assembly of the rolling bearing, for example. Through a filling channel.

The subsequent infestation of the cage with rolling elements in particular

5 also favors that after inserting the cage in the groove provided for the radius of the concave curved area within the

Surface, in particular level, of the back region of the cage is equal to or greater than the equatorial radius of curvature of the rolling body received in the pocket in question. Thus, the rolling elements can be used without the risk of l o terminals.

The invention is particularly suitable for rolling bearings whose rolling elements have a double-curved, in particular doubly convexly curved lateral surface or surface, preferably for spherical rolling elements, 15 in particular in the context of a four-point bearing.

In the context of a preferred embodiment, it can further be provided that the inside of at least one pocket for accommodating one rolling element is at least partially double, i. in two mutually 20 perpendicular directions, has concave curvature. In particular, spherical rolling elements can thus be encompassed in a planar manner, so that an adjustment of the rolling elements can be carried out at equal intervals with the lowest possible surface pressure, thus precluding local overloading of the cage.

25

This aspect of the invention can be further developed such that the double concave region of a pocket approximately follows the surface of a hemisphere or two spaced-apart quarter spheres or one or two smaller surface segment (s) of a hollow sphere. Thus, a compromise is found between a maximum enclosure of a ball-shaped rolling element on the one hand and a sufficiently sized opening to allow subsequent insertion of the ball. It follows that one or preferably both, depending on the direction of rotation of

Rolling bearing front or rear sides of a spacer each one

Surface segment of a hollow sphere follow, preferably about one quarter of the surface of a hollow sphere or a smaller part thereof.

In this case results in a symmetrical structure of the rolling body receiving pockets with respect to a centrally extending between two spacers vertical plane an arrangement with two mutually symmetrical, double concave flanks of a spacer at the front and rear, based on the respective direction of rotation.

A roller bearing assembly according to the invention may well have two or more rows of rolling elements, which are offset from each other in the axial direction of the bearing. Preferably, cages according to the invention are inserted in all rows of rolling elements.

One, several or all rows of rolling elements can be designed in the manner of a four-point ball bearing, in particular in the manner of a prestressed four-point ball bearing. A cage according to the invention is capable of applying the forces required in the adjustment of such preloaded rolling elements without deformation.

The invention further provides that the gap between the two rings at one or preferably at both end sides of the rolling bearing is sealed in order to avoid the penetration of foreign bodies, which could damage the raceways, balls and / or the cage.

By a double-sided seal, it is also possible that the gap between the two rings, in particular within the two end seals, with a lubricant, in particular with grease, filled. Since the lubricant can not escape, the Regreasing intervals very long, which is particularly advantageous in wind turbines, possibly even in the off-shore area.

Further advantages of a front or shell side reaching to the raceway filling channel in an annular connection element for filling of rolling elements, in particular balls. It has proven particularly worthwhile, the

Filling channel in an annular connecting element without a groove for receiving the cage back to arrange to use the rolling elements from the open side into a pocket of the cage can. Such a filling channel may preferably open into a lateral surface of the respective connecting element opposite the gap, so that it is straight, that is to say straight, that is to say flat. parallel to the ground plane of the camp.

Furthermore, one or preferably both annular connecting elements should have annularly distributed fastening means for connection to a chassis,

Have machine or equipment part, preferably distributed in a ring

Holes perpendicular to a front. Only by such an arrangement, the often large, between the juxtaposed

System parts occurring forces are safely absorbed by a bearing according to the invention.

The invention can be further developed to the effect that at least one of the annular connection elements has a circular row of teeth, in particular on a lateral surface opposite the gap. On such a circular row of teeth torques can be introduced into the rotary joint or tapped from there, for example. To specifically approach a predetermined rotation angle and / or to keep stable, and or to drive the rotary connection.

For rotary adjustment of the two annular connecting elements against each other, the invention further provides a rotary drive, in particular one or more electric or hydraulic motors. In this case, such a rotary drive via (one) with a circular row of teeth of an annular connecting element meshing pinion, gear, worm od. Like. Coupled with the relevant connection element and fixed to the other annular connection element or an associated housing or chassis part.

An inventive rolling bearing is preferably used as Rotorbzw. Main bearing of a wind turbine, and / or - in particular in the form of a rotary drive with an internally or externally toothed connecting ring - as a blade bearing a wind turbine, and / or as a machine house bearing a wind turbine.

A wind turbine according to the invention is characterized by a rotor or main bearing, which is designed according to the criteria explained above, and / or by at least one thus constructed blade bearing, and / or by a likewise constructed engine house bearing.

Further features, details, advantages and effects on the basis of the invention will become apparent from the following description of a preferred embodiment of the invention and from the drawing. Hereby shows:

1 shows a cross section through the rings of a rolling bearing according to the invention.

Fig. 2 shows the outer ring of the rolling bearing of FIG. 1, in a perspective

View as well as partially broken, as well as a guided in it

Cage with a plurality of pockets for holding one each

Rolling elements, wherein in a pocket, for example, a rolling element is inserted; Fig. 3 shows the cage of the rolling bearing of Fig. 1 and 2 in a perspective view, as well as largely straight.

Fig. 4 is an enlarged view of a detail of Fig. 2; such as

Fig. 5 is a perspective view of a cage according to another embodiment of the invention.

The exemplified in the drawing rolling bearing 1 is used for rotatable connection of a first plant or machine part with a foundation or a second plant or machine part. For this purpose, the rolling bearing 1 has two annular connecting elements 2, 3rd

The section through the rolling bearing 1 of FIG. 1 reveals its internal structure. It can be seen the typical structure of a radial bearing, wherein a first connecting element 2 is formed as a flat outer ring, which can be seen on the left in Fig. 1, while the second connecting element 3 is formed as concentrically arranged within the outer ring 2 inner ring 3, in Fig. 1st right. The two connection elements 2, 3 each have an approximately rectangular cross-section. Between the inner lateral surface 4 of the outer connecting element 2 and the outer lateral surface 5 of the inner connecting element 3 exists a narrow gap 6 with an approximately vertical course and a constant, small width, so that the two Anschlußeiemente 2, 3 about an axis in the center of the rings 2, 3 perpendicular to the bearing base plane against each other are rotatable.

In such Relatiwerdrehung the two connection elements 2, 3 remain aligned exactly concentric with each other thanks to a plurality of rolling elements 7, which are arranged within the gap 6 between the two connecting elements. These rolling elements 7 each have a spherical shape and roll between two tracks 8, 9 from, from an 8 in the inner circumferential surface 4 of the outer terminal member 2 is arranged and the other 9 in the outer circumferential surface 5 of the inner terminal member 3rd

The two raceways 8, 9 each have an approximately semicircular cross-section, which, however, deviates minimally from the Kugeiquerschnitt; For example, the radius of the raceway cross section may be minimally greater than the radius of the ball cross section.

In the manner of a single-row four-point bearing, each rolling element 7 therefore has, with each of the two raceways 8, 9, two nearly punctiform contact regions, each of which is approximately at an angle of + 45 °, as seen from the center of a spherical rolling element 7; However, in the case of a load of the rolling bearing 1, these contact areas may shift in different directions.

Preferably, the bearing is also biased, i. play. The spherical rolling elements 7 and / or the raceways 8, 9 are each minimally elastically deformed.

Furthermore, the gap 6 is closed in the region of its mouths on the two bearing end faces 10, 11 by a respective seal 12, 13. The thus closed outward gap 6 is filled with a lubricant, in particular with grease.

1, both annular connecting elements 2, 3 each have a larger number of annularly distributed fastening means, in particular in the form of fastening bores 14, 15, which can optionally be designed as blind bores introduced from a bearing end face 10, 11 and / or as the relevant connection element 2, 3 between the two bearing end faces 10, 11 completely penetrating through holes, as shown in Fig. 1. Such mounting holes 14, 15 are used for screwing or insertion of machine screws, which are anchored simultaneously to a machine or system part.

Further, on one of the two, the gap 6 facing lateral surfaces 16, 17 of the two connecting elements 2, 3, a toothing may be provided with the example of a. Driven pinion, gear, worm od. Like. May be engaged, while the housing such a drive would preferably be fixable to the respective other connection element 2, 3.

About equidistant positions of the rolling elements 7 along the raceways 8, 9 are kept as constant as possible by a cage 18, which is shown in isolation in FIG.

Such a cage 18 is preferably made of a resilient material, for example. Of spring steel, and can thereby be bent without damage and without permanent deformation.

It is also interrupted in at least one place and therefore has the shape of a band with two ends 19, 20, so it is not endless. Because of these two measures, the cage 18 does not have to be pre-bent according to the raceway diameter of the rolling bearing 1, but can optionally be made as a straight stretched part, in particular punched out of a (metal) metal or (metal) band or cut out with a laser. The cage could also be pre-bent with a standard curvature and would nevertheless be usable for a large number of rolling bearings 1, regardless of their exact raceway diameter; he could possibly also be shortened if necessary by certain measures.

In Fig. 3, the basic structure of the cage 18 can be seen: It has the shape of a flat band, in which of both originally, for example, straight or concentric to a common center running two narrow longitudinal sides 21, 22 regularly recurring recesses 23, 24 are cut.

From a longitudinal side 21 ago larger recesses 23 are cut with an approximately semicircular base surface whose radius corresponds approximately to the radius of a ball 7 or is minimally larger than that; These recesses 23 serve as pockets for receiving each of a spherical Wälzköφers. 7

From the opposite longitudinal side 22 ago are smaller recesses

24 incised; these indentations 24 serve to locally reduce the stiffness of the cage 18 and can serve as desired bending surfaces when needed.

Preferably, the indentations 24 are each on the line of symmetry between two adjacent pocket recesses 23. Since the centers of the pocket recesses 23 have a (slightly) greater distance in relation to the width of a pocket recess 23, just remains on the symmetry line between two adjacent pocket recesses 23 a survey, which serves as a spacer 25 between two adjacent rolling elements 7, to avoid direct contact thereof and instead to ensure a constant distance between them. The free end face of such a spacer

25 may be rounded and / or have rounded edges.

Since the cage band 18 is wider than the depth of a pocket recess 23, or preferably wider than the radius of a ball 7 received therein, and also wider than the depth of a notch 24, the spacers 25 on the opposite to the pockets 23 lying longitudinal side 22 simply together; The result is a comb-like structure, wherein the comb teeth correspond to the spacers 25 and the comb back or cage back 26 is to be assigned to the cage area near it by the notches 24 only slightly gezinkter long side 22.

The cage 18 is not, as usual, bent in the manner of a cylinder jacket and inserted into the gap 6 of the rolling bearing 1; instead, the cage back 26 is bent within a plane in the manner of a circular disk and inserted into a circumferential groove 27 which is incorporated in a raceway 8, 9, in the illustrated case in the raceway 8 of the radially outer connecting element 2. Since this groove 27 (approximately) is located at half the height of the track 8 and the same divided into two (approximately) equal halves, each with approximately quarter-circular cross-section, the inserted therein, flat cage 18 extends at the level of the centers of the spherical rolling elements. 7 The free ends of the spacers 25 are approximately on a circular line, which passes through the centers of all spherical rolling elements 7 simultaneously.

In order for the cage 18 to bend easily to a circle corresponding to the respective gap or raceway diameter, a notch 24 is provided on the line of symmetry of each spacer body 25, which is opposite to this one. The depth of each notch 24 is about the minimum width of the cage back 26 in the region of the bottom of a pocket 23, or may even be greater than that. The notches 24 may have approximately a V-shaped base surface, preferably with rounded edges in the region of the notch bottom and at the two transition areas in the approximately straight longitudinal side 22 of the cage eighth

A notch 24 may be configured such that a cut through the cage 18, taken from the bottom of a notch 24 and / or the adjoining portion of an edge of the notch 24, approximately radially to the center of the adjacent pocket 23 has a relatively small or even Has smallest cross-section of the cage 18, so that it is inclined due to the local material weakening, if necessary to bend at these locations. Even if there was a permanent deformation at a local bending due to a local overload that would hardly affect the functionality of the cage 18 of the invention, because thereby the base of the adjacent pockets 23 is hardly changed and therefore a rolling element 7 received therein is not clamped.

FIG. 5 shows a further embodiment of a cage 28 according to the invention.

The cage 28 differs from the previously described cage 18 primarily in the shape of the spacers 29, while the cage back 30 to be inserted into the groove 27 is identical to the cage back 26 of the cage 18. Also, a horizontal longitudinal section along the central main plane of the cage 28th is identical to a corresponding longitudinal section through the cage 18th

However, in contrast to the cage 18, the cage 28 does not have a flat shape with a constant thickness, but the spacers 28 additionally extend upwards over the plane of the cage back 30 and also downwards into the third dimension.

Each spacer 29 is bounded substantially by five surfaces and is formed on the remaining side with the cage back 30.

Corresponding to the transverse curvature of the track 8, the upper side 31, the underside 32 of a spacer 28 have a curvature complementary thereto, so that they can slide as smoothly as possible within the raceway 8. The Querwölbungsdurchmesser the spacers 28 may be slightly smaller for this purpose than the Querwölbungsradius the career 8. Ggf. For example, the upper side 31 and the lower side 32 may also have a slight curvature in the longitudinal direction of the cage 18, approximately corresponding to the longitudinal curvature of the raceway 8. From the cage back 30 from the top 31 and the bottom 32 diverge from each other to a free edge of both surfaces 31, 32 interconnecting end face 33. This end face 33 follows approximately the course of the gap 6 above and below the track 8; it may be flat or slightly curved in the manner of a cylinder jacket surface, corresponding to the cylindrically curved course of the gap 6.

The two, adjacent to the adjacent pockets 34 surfaces 35, 36 of a spacer 28 each follow a surface segment of a hollow sphere; they form the counterpart to the spherical rolling elements 7 accommodated in these pockets 34 and are approximately doubly curved with the same radius as those, but not convex, but concave. Towards the bottom of the pocket 34, these surfaces 35, 36 taper to the cross section of the cage back 30. However, they settle in this preferably without step and without kink, ie, continuous and differentiable, preferably in the form of a section of a cylinder jacket surface or a section of a hollow spherical surface.

The two, mutually facing pocket boundary surfaces 35, 36 of adjacent spacers 28 could also merge directly into each other, especially if the pockets 34 do not extend into the groove 27, so if their depth is equal to the width of the cage 28 minus the depth of the groove 27. However, between the mutually facing pocket boundary surfaces 35, 36, a gap extending approximately to the level of the cage back 30 should remain approximately constant width, so that the rolling body 7 accommodated in the relevant pocket 34 has sufficient clearance to form planar contact areas with the raceway 8. Therefore, the pocket boundary surfaces 35, 36 are each preferably slightly smaller than a quarter of the surface of a hollow sphere. Although in the illustrated embodiment, the groove 27 is provided in the radially outer connection element 2, it could just as well be arranged in the radially inner connection element 3. The longitudinal side 22 of the cage 18, 28 in the cage back 26, 30 would then not be curved convex, but concave.

For filling the pockets 23, 34 after the assembly of the connecting elements 2, 3 at least serves a closable filling channel whose cross section corresponds at least to the cross section of a ball-shaped rolling element 7. Preferably, such a filling channel is provided in each not provided with a groove 27 connecting element 2, 3; it begins at the local track 8, 9 and terminates in a surface region of the relevant connection element 2, 3 outside the gap 6, in particular beyond the two seals 12, 13, preferably on a side facing away from the gap 6 lateral surface 16, 17. If one of these two For example, for coupling a rotary drive, it is advisable to arrange the groove 27 in just this toothed connection element 2, 3, the Einfüllöffhung (s), however, in the other, not toothed connection element 2, 3.

Thanks to the cages 18, 28, the rolling elements 7 of the rolling bearing 1 are always performed under heavy loads at approximately equidistant relative positions. With such cages 18, 28 equipped bearings 1 can therefore also be operated in a prestressed state, wherein the spherical rolling elements 7 are constantly loaded on pressure. Such, heavy-duty rolling bearings 1 are particularly suitable for wind turbines, where they can find application as a blade bearing, rotor main bearing and engine house bearings. LIST OF REFERENCE NUMBERS

Rolling bearings 26 cage backs

Outer ring 27 groove

Inner ring 28 cage

Inner lateral surface 29 Spacer

Outer jacket surface 30 cage backs

Gap 31 top

Rolling elements 32 underside

Running track 33 front side

Running track 34 bag

Bearing face 35 Pocket interface

Bearing face 36 Pocket interface

poetry

Seal mounting hole

mounting hole

lateral surface

Cage

The End

long side

pocket recess

notch

spacer

Claims

claims

1. Rolling bearing assembly (1), preferably for a main, blade and / or machine house bearing a wind turbine, with two concentric with each other and at least partially arranged one inside the other, annular connecting elements (2,3), and with a gap (6) between these connecting elements (2,3), so that they are rotated about an imaginary, about the ring plane approximately perpendicular axis in the center of the connecting elements (2,3) against each other, wherein in

A region of the rotational axis with approximately constant radius surrounding gap portion between the connecting elements (2,3) at least one within a plane circular self-contained track (8,9) is arranged for at least one row of rolling between the connecting elements (2,3) rolling elements (7) each of rotationally symmetrical shape, wherein the rolling elements (7) of a row are guided by a cage (18,28) at approximately equal intervals, which has at least one approximately disc-shaped area in a circular, groove-shaped recess (27) in A portion of the track (8,9) of a terminal element (2,3) is inserted, and wherein the cage (18,28) is formed as a comb, with a plurality of spacers (25,29) which along a back portion (26, 30) are simply connected together, and each with a between adjacent spacers (25,29) arranged pocket (23,34) for receiving one each vorzu spherical

Rolling elements (7), wherein the opening of a pocket (23,34) extends continuously in the top of the cage (18,28) over the back portion (26,30) opposite edge (21) to the bottom, characterized in that the cage (18, 28) is completely interrupted at at least one point and is formed from a spring-elastic material, so that it can move within the frame Surface, in particular level, of the approximately disk-shaped region elastically up and / or zusammenbiegbar.

2. Rolling arrangement according to claim 1, characterized in that the cage (18,28) consists of a metal, for example. Steel, preferably

Spring steel or tempered steel.

3. Rolling arrangement according to claim 1 or 2, characterized in that four, more or all spacers (25,29) of the cage (18,28) are interconnected, so that three, more or all pockets

(23,34) for receiving a respective rolling element (7) are interconnected.

4. Rolling arrangement according to one of claims 1 to 3, characterized in that in a change in the distance between the end faces (33) of two adjacent spacers (25,29) whose end faces (33) do not deform, in particular their upper and lower edges not move against each other.

5. Rolling arrangement according to one of claims 1 to 3, characterized in that the cage (18,28) consists only of a single layer.

6. Rolling bearing arrangement according to one of the preceding claims, characterized in that at least one spacer (25,29) has a greater height than the back region (26,30) of the cage (18,28).

7. rolling bearing assembly according to one of the preceding claims, characterized in that all the pockets (23,34) of the cage (18,28) on the back region (26,30) opposite the longitudinal side (21) of the cage (18,28) are open ,

8. Rolling arrangement according to one of the preceding claims, characterized in that the cage (18,28) has at least one predetermined bending surface, preferably in its back region.

9. Rolling bearing arrangement according to one of the preceding claims, characterized in that at least one Soll- bending surface transverse to the circumferential direction of the rolling bearing (1).

2 10. Rolling arrangement according to one of the preceding claims, characterized in that there is at least one desired bending surface in the region (each) of a spacer (25,29).

11. Rolling bearing arrangement according to one of the preceding claims, characterized in that at least one desired bending surface as

Notch (24) of the cage (18,28) is formed, in particular in the end face (22) of the back region (26,30).

12. Rolling arrangement according to one of the preceding claims, characterized in that the maximum depth of at least one

Notch (24) corresponds approximately to the minimum width of the back region (26, 30) at the bottom of a pocket (23, 34).

13. Rolling arrangement according to one of the preceding claims, characterized in that a notch (24) the back region

(23,34) of the cage (18,28) from the top to the bottom passes through.

14. Rolling bearing arrangement according to one of the preceding claims, characterized in that at least one notch (24) has rounded edges, preferably at the edges with a vertical course, relative to the base of the rolling bearing (1), in particular in the region of the transition between the flanks of the notch (24) and / or beyond its two flanks.

15. Rolling bearing arrangement according to one of the preceding claims, characterized in that the rolling bodies (7) of the cage (18,28) are embraced there, where their during their unwinding

Circumferential speed is highest, preferably approximately in

Area of her equator.

16. Rolling arrangement according to one of the preceding claims, characterized in that the rolling elements (7) are encompassed at most 270 ° of its circumference, for example, only 230 ° of its original or less, preferably only 190 ° or less, in particular only about 180th ° of their scope.

17. Rolling bearing arrangement according to one of the preceding claims, characterized in that the inside of at least one pocket (23,34) for receiving each one rolling element (7) approximately at the level of RGckenbereichs (26,30) of the cage (18,28) at least partially a concave curvature parallel to the plane of the rolling bearing (1).

18. Rolling bearing arrangement according to claim 17, characterized in that the concavely curved region approximately follows a semicircle or a smaller circular arc segment.

19. Rolling arrangement according to one of claims 17 or 18, characterized in that after insertion of the cage (18,28) in the designated groove (27), the radius of the concave portion within the surface, in particular plane, of the back region (26, 30) of the cage (18, 28) is equal to or greater than the equatorial one

The radius of curvature of the rolling element (7) received in the relevant pocket (23, 34).

20. Rolling bearing arrangement according to one of the preceding claims, characterized in that the rolling elements (7) have a double-curved, in particular double convex curved shell or surface.

21. Rolling arrangement according to claim 20, characterized in that the rolling elements (7) are formed as balls.

22. Rolling arrangement according to one of the preceding claims, characterized in that the inside of at least one pocket (23,34) for receiving each of a rolling element (7) at least partially a double, i. in two mutually perpendicular directions, has concave curvature.

23. Rolling arrangement according to claim 22, characterized in that the double concave portion of a pocket (23,34) follows approximately the surface of a hemisphere or two spaced VΛertelkugelπ or one or two smaller surface segment (s) of a hollow sphere.

24. Rolling arrangement according to claim 22 or 23, characterized in that one or preferably both, depending on the direction of rotation of the rolling bearing (1) front or rear sides (35,36) of a spacer (25,29) each follow a surface segment of a hollow sphere, preferably approximately one quarter of the surface of a hollow sphere or a smaller part thereof.

25. Rolling arrangement according to one of the preceding claims, characterized by two or more rows of rolling elements (7) which are offset in the axial direction of the rolling bearing assembly (1) against each other.

26. Rolling arrangement according to one of the preceding claims, characterized in that one, several or all rows of Wälzkörpem (7) and their raceways (8.9) are designed in the manner of a four-point ball bearing, in particular in the manner of a prestressed four-point ball bearing.

27. Rolling arrangement according to one of the preceding claims, characterized in that the gap (6) between the two connecting elements (2,3) on one or preferably both

End faces (10,11) of the rolling bearing (1) is sealed.

28. Rolling arrangement according to one of the preceding claims, characterized in that the gap (6) between the two connecting elements (2,3), in particular within the two end seals (12,13), with a lubricant, in particular with grease, filled ,

29. Rolling arrangement according to one of the preceding claims, characterized in that in an annular connecting element

(2,3) one of a front or shell side (10,11,16,17) up to the respective track (8,9) reaching filling channel for filling rolling elements (7), in particular balls, is provided, in particular in one annular connecting element (2,3) without a groove (27) for receiving the cage back (26,30).

30. Rolling bearing arrangement according to one of the preceding claims, characterized in that one or preferably both annular connecting elements (2,3) annularly distributed fastening means for connection to a chassis, machine or

Have plant part, preferably annularly distributed holes (14,15) perpendicular to a front side (10,11).

31. Rolling bearing arrangement according to one of the preceding claims, characterized in that at least one of the annular connecting elements (2,3) has a circular row of teeth, in particular on a gap (6) opposite lateral surface

(16,17).

32. Rolling arrangement according to one of the preceding claims, characterized in that the circular row of teeth on that annular connection element (2,3) is provided, which has a groove (27) for inserting the Käfigrückeπs.

33. Rolling arrangement according to one of the preceding claims, characterized by a rotary drive, in particular electric motor, for rotational adjustment of the two annular connecting elements (2,3) against each other.

34. Rolling arrangement according to one of claims 30 or 31 in conjunction with claim 32, characterized in that the rotary drive via a meshing with a circular row of teeth

Pinion gear, worm od. Like. Coupled with an annular connecting element (2,3) and fixed to the other annular connecting element (2,3).

35. Wind power plant, characterized by a rotor or main bearing (1), which is designed according to one of claims 1 to 33.

36. Wind power plant, characterized by at least one blade bearing (1), which is designed according to one of claims 1 to 33.

37. Wind power plant, characterized by a machine house bearing (1), which is designed according to one of claims 1 to 33.