DE202016003040U1 - Seal for a rotary bearing, and a wind turbine whose main bearing is equipped with such a seal - Google Patents

Abstract

Rotary bearing (1) with at least two annular connecting elements (2, 3) which are rotatable relative to each other about a common bearing axis of rotation (4), which passes through the ground plane (5) of each annular connecting element (2, 3) perpendicular, and with a bearing gap (14) between the two connecting elements (2, 3) which is annularly sealed at at least one annular mouth (23) with a sealing means (24), wherein the sealing means (24) at least one at the mouth (23) of the bearing gap (14 ) along running profile of a soft material having at least one extending in the longitudinal direction of the profile, of two mutually opposite groove flanks (37, 38) and a groove bottom (39) limited groove-shaped notch (36) whose depth extent approximately parallel to the bearing axis ( 4), characterized in that the two groove flanks (37, 38) the inner sides of two legs (26, 33) of the profile cross-section of the seal center ls (24), which are connected to one another in the region of the groove base (39), and one leg (26) serves to anchor the sealing means (24) to an annular connection element (2, 3), while the other leg (33 ) has on its outer side (41) a sealing lip (25) for abutment with the other connection element (2, 3), wherein in the groove-shaped notch (36) a spring element (44) is inserted, which at least partially to the opposite one another Grooves (37, 38) creates from the inside and endeavors to push them apart by an inherent spring force and thereby the two legs (26, 33) of the sealing means (24) in the bearing gap (14) between the two connecting elements (2, 3) spread apart, so that the sealing lip (25) on the outer side (41) of the one leg (33) experiences an increased contact pressure against its contact surface.

Description

The invention is directed to a rotary bearing with at least two annular connecting elements, which are rotatable relative to each other about a common bearing axis of rotation, which penetrates the ground plane of each annular connecting element perpendicular, and with a gap between the two connecting elements, at least one annular mouth with a Sealing means is annularly sealed, wherein the sealing means comprises at least one running at the mouth of the bearing gap profile of a soft material with at least one extending in the longitudinal direction of the profile, of two opposing groove flanks and a groove base limited groove-shaped notch whose depth extension is approximately parallel to the bearing axis of rotation is oriented; and to a wind turbine with a about a horizontal axis rotating wind turbine whose hub is rotatably connected to a rotor shaft which is mounted in at least one main bearing with at least two annular, about the common bearing axis of rotation rotatable relative to each other connecting elements, one of which with the rotor shaft the wind turbine is rotatably connected, while the other is rotatably connected to the chassis of the wind turbine engine housing, and with a bearing gap between the two connecting elements, which is annularly sealed at least one annular mouth with a sealant, wherein the sealing means as in the above-mentioned Drehlagerung is configured.

Rotary bearings usually form a transition between a rotating machine or plant part and a foundation, chassis or other stationary machine or plant part. They have for this purpose two annular connecting elements, one of which is connected to the rotating part, the other to a fixed abutment.

Rolling bearings are widely used where, in a gap between the two annular connection elements, rolling bodies roll between mutually facing raceways, for example ball, barrel, roller or tapered roller bodies. This is responsible for opposing a relative rotational movement between the two connecting elements a minimum resistance, each other relative movement, however, a maximum resistance.

The wear of such rolling elements can be minimized by providing or filling the gap region with a lubricant, in particular with lubricating grease or lubricating oil. To keep such a lubricant in the gap area and at the same time to prevent dirt particles from penetrating, the gap is sealed at both mouths.

As a sealant between the two connection elements is usually a ring made of a flexible and / or elastic material. Its profile has a blunt anchoring area, which is anchored to one of the two connecting elements, as well as a tapered area, which opens into a narrow sealing lip, which abuts or runs against a contact surface in the region of the other connecting element.

Especially in this contact area between a contact surface and the sealing lip running along there is a risk of increased leakage of the lubricant, because this area is closed only by the elastic or restoring properties of the flexible and / or elastic sealing material. If the sealing material becomes tired or is subject to increased wear at one point, the leakage effect increases continuously.

It is therefore already gone over to increase the contact pressure of a sealant in that a tensioning wire is arranged radially circumferentially along a sealing gap. By a tensile stress in the direction of rotation of the inside diameter can be reduced within the annularly closed tension wire, whereby a radially inwardly directed contact pressure can be realized. With such a measure, it is possible to press a sealing lip having the region of a sealing means radially inward, against a stop surface on the radially inner connecting element.

In large-scale systems usually large roller bearings are used, which differ from normal bearings in that the contact with the relevant, rotating or stationary machine or equipment part, etc. does not take place via a curved outer surface of the relevant connection element, but over a flat end face thereof, in conjunction with screws, threaded bolts od. Like., Which in Kranzförmig distributed holes in the relevant connection element in or reach through those to press the terminal face firmly and frictionally against a connecting structure.

However, it should be noted that as the diameter of a rolling bearing increases, the curvature of the gap in its circumferential direction decreases or the radius of curvature of a connecting element in the region of the gap increases. However, the straighter the course of a gap, the lower is a radially inwardly directed contact pressure, and thus is the effect of the seal supporting effect such a tension wire in large rolling bearings relatively low. In addition, a tensioning wire of appropriate length deforms with increasing tension and thus can not be tensioned as much as desired.

Another aspect is that in many applications the rotating part is to be stored within a fixed, outer part. If the seal is anchored to the radially outer connection element with the sealing lip pointing inwards, then the orientation of the seal in the room does not change because it is anchored to the fixed part.

Due to wear, the game of storage may increase over time, then under external influences such as gravity, a permanent - albeit initially only slight - Relative displacement between the fixed and rotating connection element occurs in the radial direction, wherein the respective stored part occupies its lowest possible position , As a result, the gap width can change at certain points of the gap circumference. For example, a rotatably mounted, heavy shaft with horizontal longitudinal extent under its weight will move as far down as possible. The gap width is then reduced at the lowest point of the gap and increases at the top of the gap.

Now, if a seal member anchored to the outer, usually fixed connection element, it does not run around, but always remains unchanged, and its section at the lowest point of the gap is permanently subjected to a radial compression and is therefore exposed to increased wear, while its section In the upper part of the gap, it is necessary to permanently seal an enlarged gap width. Both effects lead to a deterioration of the sealing effect.

This problem occurs, inter alia, especially in the main bearing of a wind turbine, which supports the connected or coupled to the hub of the wind turbine rotor shaft. Since the rotor shaft is disposed within the chassis of the nacelle, it is connected to the inner terminal, while the outer terminal is anchored to the nacelle and thus never changes its vertical orientation.

In the case of the main bearing of a wind turbine as well as in some other cases, it would therefore be desirable to be able to anchor a sealant to an inner, rotating connection element so that it rotates constantly and its sealing lip is not exposed to a purely static load, but a dynamically changing load which would result in a more uniform and locally lower wear over the entire circumference of an annular sealant. In such a case, however, a tension wire completely fails to improve the sealing effect.

From the disadvantages of the described prior art, the invention initiates the problem of developing a generic pivot bearing such that by means of a clamping element of the contact pressure between the sealing lip and the contact surface is increased, regardless of whether the sealant at the radially inner or at the radial anchored outer terminal and its sealing lip starts at the rdial outer or at the radially inner connection element.

The solution of this problem is achieved in the context of a generic pivot bearing in that the two groove flanks form the inner sides of two legs of the profile cross section of the sealant, which are interconnected in the region of the groove base, and one leg of which serves to anchor the sealant to an annular connection element, while the other leg has on its outer side a sealing lip for abutment with the other connecting element, wherein in the groove-shaped notch, a spring element is used, which at least partially applies to mutually opposite groove flanks and endeavors to push them apart by an inherent spring force and thereby spread apart the two legs of the sealing means in the gap between the two connecting elements, so that the sealing lip experiences an increased contact pressure against its contact surface.

The invention thus dispenses with a tensile stress running in the longitudinal direction of a tensioning wire, which is associated with the above-described disadvantages, and replaces this with a spreading effect, which is independent of the radial direction to the bearing main axis. Rather, an all-round anchoring portion and a likewise all-round sealing lip are always spread apart, regardless of whether the sealing lip is located radially within the anchoring portion, or vice versa. By, this spreading force is always the anchoring portion pressed against one of the two connection elements and the sealing lip against the respective other connection element. Furthermore, this spreading is at most dependent on the gap width, but not on the circumference of the gap, so that the pressure effect between the sealing lip and contact surface does not decrease with increasing size of the bearing. The inventive sealing principle is therefore particularly suitable for improving the sealing effect in large rolling bearings.

It has proved to be favorable that the groove base of the groove-shaped notch is preferably arched concavely over the entire groove width. As a result, inner edges in the region of the groove base can be completely avoided, and consequently, on the one hand a material fatigue promoting notch effect is avoided, and on the other hand can be a spring element of a consistent, concave curvature better fit than a sharp inner edge.

The width of the groove-shaped notch may increase from the groove bottom to the groove mouth, preferably continuously. This measure can favor the onset of a spring element in a groove-shaped notch.

Such an enlargement of the groove toward its mouth region can be achieved by diverging the leg of the sealing means carrying the sealing lip from the leg serving for anchoring to the groove mouth, in particular along a conical surface. Thus, the sealing lip is located at a maximum exposed position of the leg in question.

Preferably, the leg of the sealing means carrying the sealing lip and / or its leg serving for anchoring has a middle section between the groove base and the groove mouth, which has an approximately constant thickness. This gives the leg a defined bending behavior.

It is within the scope of the invention that the leg of the sealing means carrying the sealing lip is thinner than the leg serving for anchoring. Thus, the leg carrying the sealing lip is significantly more flexible than the anchoring Aba cut, whereby an increased contact pressure is generated.

Advantageously, the leg of the sealing means carrying the sealing lip is shorter than the leg serving for anchoring. In this way, it is ensured within a cavity receiving the sealant that the latter enjoys sufficient freedom of movement in the event of a bending movement which may be necessary.

The invention recommends that the sealing means in the region of the groove base facing away from the groove muzzle, having a flat outer side. Thanks to such a flat outside, the sealant can be firmly clamped in a groove by means of a cover.

There is the possibility that the leg serving to anchor has an approximately rectangular or square cross-section, possibly with bevelled and / or rounded corners, so that such an anchoring portion can receive a maximum compressive force, in particular in a direction parallel to the bearing axis of rotation.

The groove facing the inside of the lip having the sealing lip may follow in a central portion between the groove bottom and the groove mouth of a conical surface. In such an embodiment, a maximum range of motion for the leg carrying the sealing lip remains.

The invention can be further developed such that the side facing away from the groove outside of the lip having the sealing lip in addition to the sealing lip has a second sealing lip and / or an outwardly directed web, which is formed approximately at the level of the groove bottom of the respective leg and from there away extends through the bearing gap in the direction of the opposite terminal element. Thus, an additional sealing effect can be realized.

Further advantages result from the fact that the second sealing lip and / or the outwardly directed web extends inclined to the flat outer side of the sealing means facing away from the groove mouth. As a result, an overpressure directed, for example, from inside the bearing gap can be pressed firmly against the other connecting element.

The invention is further distinguished by the fact that an acute-angled notch is located between the second sealing lip and / or the outwardly directed web on the one hand and the flat outer side of the sealing means facing away from the groove mouth, preferably with an opening angle of 60 ° or smaller, in particular with one Opening angle of 45 ° or smaller. There, a lubricant bag is formed naturally.

Due to the principle according to the invention, the spring element is subject to no or only a minimal tensile stress in its longitudinal direction, d. H. in the circumferential direction of the bearing gap. The principle is fundamentally different from previous tension wires, all of which are loaded in the circumferential direction of the bearing gap on train.

The advantageous features of the invention are based on the fact that the spring element is subjected to a compressive stress transversely to its longitudinal direction. This principle is far more universal because it is completely independent of whether the sealing lip faces the inner ring or the outer ring.

As part of a preferred construction, the spring element facing two opposite each other lying on peripheral regions, which bear against a respective groove flank and be pressed against the respective groove flank due to an inherent bias. It is these peripheral areas that are responsible for spreading the groove flanks apart.

The invention can be further developed such that the pressure forces are introduced approximately perpendicular to the two groove flanks in the spring element. As a result, shear forces are largely avoided.

Preferably, the approximately perpendicular to the two groove flanks introduced into the spring element pressure forces are directed approximately radially to the axis of rotation of the bearing. As a result, the sealing lip is always pressed against its contact surface.

Further advantages are obtained in that the cross sections through the two mutually opposite groove flanks, where pressure forces are introduced into the spring element, with the axis of rotation of the bearing include a smaller angle than with the ground plane of the bearing. The groove flanks are therefore in the cross section therefore approximately parallel to the contact surface against which the sealing lip is to be pressed.

The effect of the invention is based on the fact that the counterforce for pressing the sealing lip is not produced at its contact surface via a tensile stress of the spring element in the longitudinal direction, but by a pressure in the region of the anchoring serving leg of the sealant. This principle is particularly suitable for slewing bearings with a minimal curvature of the lateral surfaces in the region of the bearing gap.

Further advantages provides a construction, wherein the spring element is bent from a wire or linear element, preferably from a metallic element, in particular from a resilient material such as spring steel od. Like.

The invention undergoes an advantageous development in that the spring element is bent three-dimensionally from a wire or linear element. It is precisely such a three-dimensional bend that allows the spring element to exert pressure forces pointing in opposite directions in different circumferential regions.

The bent from a wire or linear element spring element should have one or preferably a plurality of sections which extend in or near a plane which passes at a small distance on the bearing axis and / or is inclined relative to the bearing axis by a small angle. Such a geometry ensures that the (counter) forces to be transmitted within a section run in a nearly radial plane.

Another design rule states that the bent from a wire or linear element spring element has one or preferably a plurality of sections which extend from a groove flank over the groove bottom to directly to the other groove flank. This results in a shortest possible connection between the mutually facing flanks of the groove-shaped notch, and the spring element can therefore generate large spreading forces with relatively low leverage.

According to the invention, it is further provided that the section (s) of the spring element extending from one groove flank over the groove base to the other groove flank snugly fits (-en) to the respective groove flank and preferably also to the groove base. Maximum contact minimizes local contact pressure against the flexurally elastic sealant and, therefore, does not anticipate premature material fatigue.

The invention allows a development to the effect that the (the) one groove flank over the groove bottom to the other groove flank following (n) section (s) of the bent from a wire or linear element spring element each has a C- or U-shaped course ( to have). This geometry corresponds approximately to the (inner) cross section of the groove-shaped notch.

Further, the invention teaches that two mutually adjacent in the circumferential direction of the gap, each extending from one groove flank over the groove bottom to the other groove edge extending portions of the bent from a wire or linear element spring element are interconnected. As a result, on the one hand adjacent portions of the spring element are kept at defined distances, and also the spring element is thereby combined to form a single, easily assembled assembly. Ideally, a single spring element extends once along the entire (circumferential) course of the sealant.

Further advantages are provided by an arrangement, wherein each one end of a central, extending from a groove flank over the groove base to the other groove flank portion of the bent wire or linear element spring element is connected to one of two adjacent portions of the spring element. Since a portion of the spring member bent from an elongated wire has two ends and also two adjacent spring portions, it is very efficient to connect each of the two ends to each of the two adjacent portions.

For a connection between two adjacent portions of the spring element bent from a wire or linear element, the invention proposes an arcuately curved transition piece or region. Such an arcuate connection can be made of the elongated or linear wire itself, so that the spring element over its entire length - according to the length of the sealant - can be made integral from a single part, in particular by bending.

In the context of a preferred embodiment, two portions of the spring element bent from a wire or line-shaped spring element, each extending from one groove flank over the groove base to the other groove flank, are connected via a transition piece or region at one end to the same groove flank connected. In such an embodiment, the transition piece or region does not extend transversely across the groove mouth, but extends completely along a single groove flank. An advantage of this arrangement is that such a spring element can be compressed considerably in the region of the transition pieces transversely to its longitudinal direction, for example in order to be inserted into the groove-shaped notch. Such an embodiment is therefore recommended for almost all conceivable applications. With the cross-sectional thickness of the wire or linear element and with the material used, the spring constant can be set to a desired value; On the one hand, the spring element should be hard enough to produce a sufficient contact pressure and, on the other hand, if necessary, it can be temporarily deformed while exceeding the force required for elastic deformation, for example for assembly or disassembly.

On the other hand, two sections of the spring element bent from a wire or linear element, each extending from one groove flank over the groove base to the other groove flank, could in principle also be connected via an end piece of the two sections of mutually opposite flanks connecting (-en) transition piece or area. In this case, the transition piece or the transition region does not extend completely along a single groove flank but extends transversely across the groove flute. In this arrangement, it may be possible to generate an increased compressive force between the two groove flanks, but such a spring element in the region of the transition pieces can compress only a small portion transversely to its longitudinal direction and is thus relatively stiff, which may be less desirable for some applications. Such an arrangement should therefore be suitable at most for a few, very specific applications.

An arched transition piece or region should have a radius of curvature equal to or less than half the spacing of the two groove flanks in the region of the groove orifice. In this case, an arcuately curved (-er) transition piece or area can go over completely or almost kink-free in the adjacent portions of the bent spring element.

A particularly preferred embodiment of the invention is characterized in that the maximum radius of curvature of an arcuately curved transition piece or region is smaller than the minimum radius of curvature of the associated, each of a groove flank over the groove bottom to the other groove flank extending portions of the spring element. In such a case, adjacent portions of the bent spring element can be arranged relatively close to each other, whereby the total spring force increases without the spring element is too stiff to compressive forces in a direction transverse to its longitudinal axis.

A transition piece or region may have a bulge in a section transverse to the longitudinal direction of the sealing means. This makes it possible to follow, for example, a receding in the region of the Nutmündung edge of a leg and also there to cling to those legs.

Finally, it is the teachings of the invention that the curvature of the transition piece or region in a section transverse to the longitudinal direction of the sealant is directed opposite to the curvature of the associated portions of the spring element in the groove bottom. Such, outwardly directed curvature can serve to anchor the bent spring element in a wedge-shaped cavity between the surface of the sealing means having the groove mouth and a surface of a connecting element which is in contact therewith at least in regions.

A generic wind turbine with a about a horizontal axis rotating wind turbine whose hub is rotatably connected to a rotor shaft which is mounted in at least one main bearing with at least two annular, about the common bearing axis of rotation rotatable relative to each other connecting elements, one of which with the rotor shaft of Wind turbine is rotatably connected, while the other is rotatably connected to the chassis of the wind turbine engine housing, and with a bearing gap between the two connecting elements, which is annularly sealed at least one annular mouth with a sealant, wherein the sealing means at least one at the mouth of the Bearing gap along running profile of a soft Material having at least one extending in the longitudinal direction of the profile, of two opposing groove flanks and a groove base limited groove-shaped notch whose depth extension is oriented approximately parallel to the bearing axis of rotation, according to the invention is characterized in that the two groove flanks the inner sides of two legs of the profile cross-section form of the sealing means which are interconnected in the region of the groove base, and one leg of the anchoring of the sealant to an annular connection element is used, while the other leg has on its outer side a sealing lip for abutment with the other connection element, wherein in the groove-shaped notch a spring element is used, which at least partially applies to the opposing groove flanks from the inside and strives to push them apart by an inherent spring force and thus the two gift el of the sealant in the bearing gap between the two connection elements spread apart so that the sealing lip on the outside of the one leg experiences an increased contact pressure against its contact surface.

In the main bearing of a wind turbine, the seal according to the invention can be used for a rotary bearing with great advantages. On the one hand, the contact pressure of the sealing lip against the contact surface can be further increased by a spring element in order to achieve a particularly high sealing effect, and on the other hand the sealing ring itself is anchored to the radially inner connecting element connected to the rotor shaft, thus rotating with the rotor shaft, so that all areas of the sealing ring are uniformly loaded, and run over a gap of possibly fluctuating width, so that the material is not fatigued locally at certain points and thereby loses its sealability.

In particular, in the case of application as the main bearing of a wind turbine, the rotary bearing used therefor can have all the features which were also generally proposed above for rotary mounting.

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 a section across the annular connection elements of a rolling bearing according to the invention sealed;

2 a section across a sealing ring for sealing the bearing gap between the annular connection elements of a rolling bearing, for example. According to the structure according to 1 ; such as

3 a modified embodiment of a sealing ring according to the invention for the sealing of a bearing gap between the annular elements of a rolling bearing, in one of 2 corresponding sectional view.

In the drawing is a pivot bearing 1 with two annular connection elements 2 . 3 shown, which are arranged radially in one another. In the center of both connection elements 2 . 3 is the bearing axis of rotation 4 around which the two connection elements 2 . 3 to turn against each other. The bearing axis of rotation 4 intersects the ground plane 5 the pivot bearing 1 , which is approximately in the middle between the flat end faces 6 . 7 . 8th . 9 the connection elements 2 . 3 runs, at right angles.

Not shown are mounting holes for fixing the two connection elements 2 . 3 by means of screws or threaded bolts on a respective connecting structure, for example on a machine or system part od. The like. For this purpose are on each connection element 2 . 3 - Each around the bearing axis 4 distributed in a circle - in a flat face 6 . 7 . 8th . 9 of the connection element 2 . 3 provided a plurality of blind holes, preferably with an internal thread for screwing in a screw, and / or between two opposite end faces 6 . 7 . 8th . 9 of the relevant connection element 2 . 3 through holes for passing through a threaded bolt or a screw.

At the inner, concave curved surface 10 the radially inner connection element 2 and / or on the outer, convexly curved lateral surface 11 the radially outer connection element 3 could be a toothing on which by means of a pinion or a worm in any direction of rotation drivingly on the relevant connection element 2 . 3 can be acted upon, and / or a kind of flat brake disc on which retards brake shoes against a current direction of rotation to the relevant connection element 2 . 3 can be acted upon.

Between the outer, convexly curved lateral surface 12 the radially inner connection element 2 and the inner, concavely curved lateral surface 13 the radially outer connection element 3 there is a bearing gap 14 , At her this camp gap 14 facing surfaces 12 . 13 have the two connection elements 2 . 3 preferably one or more raceways each 15 . 16 for one or more rows of between in the gap 14 along rolling rolling elements 17 on, and / or one or more slideways on which the connection elements 2 . 3 either slide directly against each other or on arranged therebetween slider.

In the illustrated embodiment, that is the gap 14 facing surface 12 . 13 a connection element 2 . 3 with an all-round alliance 18 , a so-called nose, provided, and in the gap 14 facing surface 13 . 12 of the other connection element 3 . 2 There is an all-round, groove-shaped depression 19 into which the nose 18 can intervene.

To the assembly of the pivot bearing 1 to enable, in this arrangement, one of the two connection elements 2 . 3 namely that with the groove-shaped depression 19 , in two successive in the direction of the bearing axis of rotation rings 20 . 21 divided, preferably along a plane, to the ground plane 5 the pivot bearing 1 parallel parting line 22 , That's the depression 19 having connecting element 2 . 3 can get it around your nose 18 of the other connection element 3 . 2 be assembled around.

The two flanks and the free front of the nose 18 as well as the two flanks and the bottom of the groove-shaped depression 19 each serve as raceways 15 . 16 for each of a series of rolling rolling along it 17 ,

Preference is given to roller-shaped rolling elements 17 used, although ball, cone or barrel-shaped rolling elements can be used.

The bearing gap 14 between the two connection elements 2 . 3 may be wholly or partially filled with a lubricant to the rolling elements 17 to assist in their rolling movement and to minimize wear. Lubricating grease has proven its worth, although lubricating oil can also be used.

To the lubricant within the bearing gap 14 to hold back, is the gap 14 preferably in the region of its two mouths 23 by at least one sealant each 24 sealed.

Every sealant 24 is at one of the two connection elements 2 . 3 anchored and has a sealing lip 25 on, which at a surface area of the other connecting element 3 . 2 - or at a specified there ring or band - during each relative rotation between the two connecting elements 2 . 3 along strips.

One of the sealing lip 25 opposite anchoring section 26 can be anchored to a connecting element 2 . 3 For example, be inserted in a local, all-round groove or - as in 1 shown - in a groove 27 in which they pass through a cover 28 - Eg. An annular part or more, each ring segment-shaped parts - covered and thus in the then narrowed to a groove shape groove 27 can be held.

Of the 2 it can be seen that the anchoring section 26 has a cross-sectionally approximately rectangular shape, possibly with bevelled and / or rounded corners 29 . 30 . 31 which edges of the profile-shaped sealant 24 correspond. In 2 is the cross section through the anchoring section 26 by a pure hatching of the remaining area 32 of the sealant 24 offset, which is highlighted by a crossed hatching.

The height of the anchoring section 26 corresponds approximately to the bearing axis of rotation 4 parallel extension of the groove 27 or is slightly larger than those, so the sealant 24 from the cover 28 in the groove 27 gets trapped so that it is opposite the the groove 27 having connecting element 2 . 3 can not twist.

The rest of the area 32 of the sealant 24 is roughly divided into two sections: one to the anchoring section 26 in approximately parallel leg section 33 is with the former along a flat Stirnfäche 34 of the sealant 24 over a footbridge 35 connected, which has a much lower height than the height of the sealant 24 in total, so that between the anchoring section 26 and and about the parallel leg portion 33 a groove-shaped notch 36 remains.

The two flanks of this groove-shaped notch 35 become through the mutually facing insides 37 . 38 of the anchoring section 26 on the one hand and the leg portion approximately parallel thereto 33 formed while the groove bottom by the notch 35 facing inside 39 of the footbridge 35 is formed.

As the 2 can be further seen, the leg portion diverges 33 from the anchoring section 26 in the direction of the groove bottom 39 to the Nutmündung 40 to a certain extent, leaving the inside 38 of the leg section 33 with the inside 37 of the anchoring section 26 encloses an acute angle, on the order of 30 ° or less, or 15 ° or less.

The groove bottom 39 However, it is not flat, but preferably concave in cross-section, such as 2 lets recognize. Of the Radius of curvature can be about half the width of the groove-shaped notch 35 correspond to their lowest point.

The sealing lip 25 is on the outside 41 of the leg section 33 , approximately in the region of the free end of this leg section 33 , A striking feature of the sealing lip 25 is a relatively sharp edge 42 which is beyond the gap 14 opposite lying arranged region of the other connecting element 2 . 3 is facing.

Furthermore, the sealant 24 a second, all-round, web-like extension 43 which is from the outside 41 of the leg section 33 extends away and in 2 can also be seen. This web-like extension 42 can to the flat face 34 of the footbridge 35 Run inclined and there with the outer surface 41 of the leg section 33 include an approximately V-shaped groove at an acute angle. Preferably, the web-like extension is located 41 approximately at the level of the groove bottom 39 ,

As the 2 can be further seen, which is the sealing lip 25 carrying thighs 33 in terms of movement is not left to itself, but is by a in the groove-shaped notch 36 inserted spring element 44 supported.

The spring element 44 is bent from a wire, preferably made of spring steel or a comparable, resilient material. To avoid corrosion damage, it is recommended to use a stainless material or to coat the material itself with a corrosion protective layer.

The spring element 44 However, it is by no means straight and does not follow directly the arcuate course of the groove-shaped notch 36 , Rather, the wire of the spring element 44 meandering curved, so with a variety of loops, which bulge in each alternating directions. This series of successive meander loops now follows the course of the groove-shaped notch 36 ,

Just as the serpentines of a road meander along a slope, so does the meandering spring element 44 along the inside 37 . 38 . 39 the groove-shaped notch 36 and clings to them. In this case, each meander loop of the spring element comprises 44 two mutually approximately parallel sections 45 the meandering spring element 44 of which each section 45 initially across a groove flank 37 runs, then across the bottom of the groove 39 and then again across the other groove flank 38 , Thus, such a section extends 45 completely or almost completely from one longitudinal edge 46 the Nutmündung 40 to the opposite longitudinal edge 47 the Nutmündung 40 , and always clings tightly to the Nutinnenfläche 37 . 38 . 39 at.

To get out of two adjacent sections 45 a common loop 48 to shape is between two adjacent sections 45 in the region of a longitudinal edge 46 . 47 the Nutmündung 40 a connection area 49 provided, that is, a bending region of the wire-shaped spring element 45 where this is bent by about 180 °. Such a connection area 49 In general, it has a narrower radius of curvature than the portion of the spring element that lies against the groove bottom 44 so that two are on the same groove flank 37 . 38 adjacent, adjacent portions of the wire-shaped spring element 45 have a smaller distance than two at different groove flanks 37 . 38 opposite lying portions of the wire-shaped spring element 44 ,

The spring element 44 may have an intrinsic shape, with two connection areas 49 on both sides of a common section 45 have a greater distance than the two longitudinal edges 46 . 47 the Nutmündung 40 , This requires the spring element 44 for insertion into the groove-shaped notch 35 be temporarily squeezed into the groove 35 fit in. Then tries the spring element 44 to relax and widens the groove-shaped notch 35 on. This is the the sealing lip 25 having thighs 33 in the region of its free end from the anchoring section 24 pushed away. As a result of this pressure, the contact pressure of the sealing lip 25 against its contact surface on the respective other connection element 2 . 3 increased, and leakage is avoided or at least significantly reduced.

This mode of action is independent of the installation of the sealant 24 , and also works when the anchoring section 26 not on the radially inner connection element 2 . 3 is set, but at the radially outer connection element 2 . 3 as by the sealant 24 ' in 3 is shown.

One recognizes there an opposite curvature of the sealant 24 '; while the sealant 24 in 2 is curved to the left, ie, the bearing axis of rotation is to the left of the 2 while the sealing lip 25 is recognizable on the right, so the bearing axis 4 turned away, undergoes the sealant 24 ' to 3 a curvature to the right, ie, the bearing axis of rotation 4 is in this case also right, and therefore is the sealing lip 25 ' in this embodiment, the bearing axis of rotation 4 facing.

In 3 is further shown that the connection areas 49 ' between two adjacent sections 44 ' in addition to a bulge in the circumferential direction of the groove-shaped notch 25 may also have a curvature transverse to it. This vault 44 ' can the curvature in the groove bottom 39 be directed opposite. So while at the bottom of the groove 39 a concave transverse curvature is provided, corresponding to the concavely curved Innneseite the groove bottom 39 , so the transverse curvature at a Veabindungsbereich 49 ' be formed convex. This allows the spring element 44 ' under a cover 28 pinch.

Not shown in the drawing, a preferred application of the pivot bearing according to the invention as a main bearing for connected to the hub of a wind turbine or coupled, approximately horizontally extending rotor shaft on the chassis of the machine house or the nacelle of the wind turbine in question, wherein the radially inner connection element with the rotor shaft coupled, the radially outer connection element, however, with the chassis of the nacelle or the nacelle of the wind turbine. In particular, all the features of the in the 2 and 3 be realized and described above realized seals.

LIST OF REFERENCE NUMBERS

1

pivot bearing

2

connecting element

3

connecting element

4

Bearing axis of rotation

5

ground plane

6

face

7

face

8th

face

9

face

10

lateral surface

11

lateral surface

12

lateral surface

13

lateral surface

14

bearing gap

15

career

16

career

17

rolling elements

18

Federation

19

deepening

20

ring

21

ring

22

parting line

23

muzzle

24

sealant

25

sealing lip

26

anchoring section

27

groove

28

cover

29

corner

30

corner

31

corner

32

Area

33

leg portion

34

face

35

web

36

notch

37

inside

38

inside

39

inside

40

groove mouth

41

outside

42

sharp edge

43

ridge-like extension

44

spring element

45

section

46

longitudinal edge

47

longitudinal edge

48

loop

49

connecting area

Claims (37)

Pivot bearing ( 1 ) with at least two, annular connecting elements ( 2 . 3 ), which are rotatable relative to each other about a common bearing axis of rotation ( 4 ), which the ground plane ( 5 ) of each annular connection element ( 2 . 3 ) penetrated vertically, and with a bearing gap ( 14 ) between two connection elements ( 2 . 3 ), which at least one annular mouth ( 23 ) with a sealant ( 24 ) is sealed annularly, wherein the sealant ( 24 ) at least one at the mouth ( 23 ) of the bearing gap ( 14 ) along running profile of a soft material having at least one extending in the longitudinal direction of the profile, of two opposing groove flanks ( 37 . 38 ) and a groove bottom ( 39 ) limited groove-shaped notch ( 36 ) whose depth extent is approximately parallel to the bearing axis of rotation ( 4 ), characterized in that the two groove flanks ( 37 . 38 ) the insides of two legs ( 26 . 33 ) of the profile cross section of the sealant ( 24 ), which in the region of the groove bottom ( 39 ), and of which one leg ( 26 ) the anchoring of the sealant ( 24 ) on an annular connection element ( 2 . 3 ), while the other leg ( 33 ) on its outside ( 41 ) a sealing lip ( 25 ) for engagement with the other connection element ( 2 . 3 ), wherein in the groove-shaped notch ( 36 ) a spring element ( 44 ) is used, which at least partially to the mutually opposite groove edges ( 37 . 38 ) is applied from the inside and strives to push them apart by an inherent spring force and thereby the two legs ( 26 . 33 ) of the sealant ( 24 ) in the bearing gap ( 14 ) between the two connection elements ( 2 . 3 ) spread apart so that the sealing lip ( 25 ) on the outside ( 41 ) of one leg ( 33 ) experiences an increased contact pressure against its contact surface. Pivot bearing ( 1 ) according to claim 1, characterized in that the groove bottom ( 39 ) of the groove-shaped notch ( 36 ) is preferably arched concavely over the entire groove width. Pivot bearing ( 1 ) according to claim 1 or 2, characterized in that the width of the groove-shaped notch ( 36 ) of the groove bottom ( 39 ) up to the groove mouth ( 40 ) is preferably continuously increased. Pivot bearing ( 1 ) according to one of claims 1 to 3, characterized in that the sealing lip ( 25 ) supporting thighs ( 33 ) of the sealant ( 24 ) and / or its anchoring leg ( 26 ) a middle section between the groove bottom ( 39 ) and the groove mouth ( 40 ), which has an approximately constant thickness. Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the sealing lip ( 25 ) supporting thighs ( 33 ) of the sealant ( 24 ) is thinner than the anchorage serving leg ( 26 ). Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the sealing lip ( 25 ) supporting thighs ( 33 ) of the sealant ( 24 ) is shorter than the anchorage serving leg ( 26 ). Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the sealing lip ( 25 ) supporting thighs ( 33 ) of the sealant ( 24 ) of the anchorage serving leg ( 26 ) to the groove mouth ( 40 ) diverge, in particular along a conical surface. Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the sealant ( 24 ) in the region of the groove bottom ( 39 ) one of the groove mouth ( 40 ) facing away, has flat outer side. Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the leg serving to anchor ( 26 ) has an approximately rectangular or square cross-section, possibly with bevelled and / or rounded corners ( 29 . 30 . 31 ). Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the nutföprmigen notch ( 36 ) facing inside ( 38 ) of the sealing lip ( 25 ) having thigh ( 33 ) in a middle section between the groove bottom ( 39 ) and the groove mouth ( 40 ) follows a conical surface. Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the groove-shaped notch ( 36 ) facing away from outside ( 41 ) of the sealing lip ( 25 ) having thigh ( 33 ) in addition to the sealing lip ( 25 ) a second sealing lip and / or an outwardly directed web ( 43 ), which approximately at the level of Nutgrundes ( 39 ) to the respective leg ( 33 ) is formed and extends away from there through the bearing gap ( 14 ) therethrough in the direction of the opposite connection element ( 2 . 3 ). Pivot bearing ( 1 ) according to claim 11, characterized in that the second sealing lip and / or the outwardly directed web ( 43 ) to the groove mouth ( 40 ) facing away, flat outside of the sealant ( 24 ) slopes down. Pivot bearing ( 1 ) according to claim 12, characterized in that between the second sealing lip and / or the outwardly directed web ( 43 ) on the one hand and the groove mouth ( 40 ) facing away, flat outside of the sealant ( 24 ) is an acute-angled notch, preferably with an opening angle of 60 ° or smaller, in particular with an opening angle of 45 ° or smaller. Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the spring element ( 44 ) is subject to no or only a minimal tensile stress in its longitudinal direction. Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the spring element ( 44 ) is subjected to a compressive stress transverse to its longitudinal direction. Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the spring element ( 44 ) has two mutually opposite circumferential regions, which in each case a groove flank ( 37 . 38 ) and due to an inherent bias to the respective groove flank ( 37 . 38 ) are pressed. Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the pressure forces are approximately perpendicular to the two groove flanks ( 37 . 38 ) in the spring element ( 44 ) be initiated. Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the approximately perpendicular to the two groove flanks ( 37 . 38 ) in the spring element ( 44 ) introduced compressive forces approximately radially to the axis of rotation ( 4 ) of the warehouse ( 1 ) are directed. Pivot bearing ( 1 ) according to any one of the preceding claims, characterized in that the cross sections through the two mutually opposite groove flanks ( 37 . 38 ), in which in the spring element ( 44 ) Pressure forces are introduced, with the axis of rotation ( 4 ) of the warehouse ( 1 ) include a smaller angle than the ground plane ( 5 ) of the warehouse ( 1 ). Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the counterforce for pressing the sealing lip ( 25 ) at the contact surface not via a tensile stress of the spring element ( 44 ) is produced in its longitudinal direction, but by a serving in the region of the anchoring leg ( 26 ) of the sealant ( 24 ) introduced compressive force. Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the spring element ( 44 ) is bent from a wire or line-shaped element. Pivot bearing ( 1 ) according to one of the preceding claims, characterized in that the spring element ( 44 ) is bent three-dimensionally from a wire or linear element. Pivot bearing ( 1 ) according to claim 21 or 22, characterized in that the spring element ( 44 ) one or preferably several sections ( 45 ), which run in or near a plane which is at a small distance at the bearing axis ( 4 ) passes over and / or opposite the bearing axis ( 4 ) is inclined at a small angle. Pivot bearing ( 1 ) according to one of claims 21 to 23, characterized in that the spring element ( 44 ) one or preferably several sections ( 45 ), which of a groove flank ( 37 . 38 ) over the groove bottom ( 39 ) right up to the other groove flank ( 38 . 37 ). Pivot bearing ( 1 ) according to claim 24, characterized in that the (the) of a groove flank ( 37 . 38 ) over the groove bottom ( 39 ) to the other groove flank ( 38 . 37 ) section (e) ( 45 ) of the spring element ( 44 ) of the respective groove flank ( 37 . 38 ) and preferably also the groove bottom ( 39 ) clings flat (-en). Pivot bearing ( 1 ) according to one of claims 23 to 25, characterized in that the (the) a groove flank ( 37 . 38 ) over the groove bottom ( 39 ) to the other groove flank ( 38 . 37 ) the following section (s) of the spring element ( 44 ) each have a C- or U-shaped course. Pivot bearing ( 1 ) according to one of claims 23 to 26, characterized in that two mutually in the circumferential direction of the bearing gap ( 14 ) adjacent, each of a groove flank ( 37 . 38 ) over the groove bottom ( 39 ) to the other groove flank ( 38 . 37 ) the following section (s) ( 45 ) of the spring element ( 44 ) are interconnected. Pivot bearing ( 1 ) according to claim 27, characterized in that each one end of a middle, of a groove flank ( 37 . 38 ) over the groove bottom ( 39 ) to the other groove flank ( 38 . 37 ) section ( 45 ) of the spring element ( 44 ) each with one of two adjacent sections ( 45 ) of the spring element ( 44 ) connected is. Pivot bearing ( 1 ) according to claim 27 or 28, characterized in that the connection between two adjacent sections ( 45 ) of the spring element ( 44 ) via an arcuately curved transition piece or region ( 49 ) he follows. Pivot bearing ( 1 ) according to any one of claims 27 to 29, characterized in that each two of a groove flank ( 37 . 38 ) over the groove bottom ( 39 ) to the other groove side ( 38 . 37 ) extending sections ( 45 ) of the spring element ( 44 ) over one (s) two ends on the same groove flank ( 37 . 38 ) connecting (-en) transition piece or region ( 49 ) are connected. Pivot bearing ( 1 ) according to any one of claims 27 to 30, characterized in that each two of a groove flank ( 37 . 38 ) over the groove bottom ( 39 ) to the other groove side ( 38 . 37 ) extending sections ( 45 ) of the spring element ( 44 ) via one (s) two ends on mutually opposite groove flanks ( 37 . 38 ) connecting (-en) transition piece or region ( 49 ) are connected. Pivot bearing ( 1 ) according to one of claims 27 to 31, characterized in that an arcuately curved (-er) transition piece or region ( 49 ) has a radius of curvature equal to half the distance of the two groove flanks ( 37 . 38 ) in the region of the groove mouth ( 40 ) or less than that. Pivot bearing ( 1 ) according to one of claims 27 to 32, characterized in that the maximum radius of curvature of an arcuately curved transition piece or region ( 49 ) is smaller than the minimum radius of curvature of the associated, each of a groove flank ( 37 . 38 ) over the groove bottom ( 39 ) to the other groove flank ( 38 . 37 ) extending sections ( 45 ) of the spring element ( 44 ). Pivot bearing ( 1 ) according to one of claims 27 to 33, characterized in that a Transition piece or area ( 49 ) in a section transverse to the longitudinal direction of the sealant ( 24 ) has a curvature. Pivot bearing ( 1 ) according to claim 34, characterized in that the curvature of the transition piece or region ( 49 ) in a section transverse to the longitudinal direction of the sealant ( 24 ) is directed opposite to the curvature of the sections ( 45 ) of the spring element ( 44 ) in the region of the groove bottom ( 39 ). Wind turbine with an approximately horizontal axis ( 4 ) rotating wind turbine whose hub is rotatably connected to a rotor shaft, in at least one main bearing ( 1 ) with at least two annular, about the common bearing axis of rotation ( 4 ) relative to each other rotatable connection elements ( 2 . 3 ) is mounted, one of which is rotatably connected to the rotor shaft of the wind turbine, while the other is rotatably connected to the chassis of the nacelle of the wind turbine, and with a bearing gap ( 14 ) between the two connection elements ( 2 . 3 ), which at least one annular mouth ( 23 ) with a sealant ( 24 ) is sealed annularly, wherein the sealant ( 24 ) at least one at the mouth ( 23 ) of the bearing gap ( 14 ) along running profile of a soft material having at least one extending in the longitudinal direction of the profile, of two opposing groove flanks ( 37 . 38 ) and a groove bottom ( 39 ) limited groove-shaped notch ( 36 ) whose depth extent is approximately parallel to the bearing axis of rotation ( 4 ), characterized in that the two groove flanks ( 37 . 38 ) the insides of two legs ( 26 . 33 ) of the profile cross section of the sealant ( 24 ), which in the region of the groove bottom ( 39 ), and of which one leg ( 26 ) the anchoring of the sealant ( 24 ) on an annular connection element ( 2 . 3 ), while the other leg ( 33 ) on its outside ( 41 ) a sealing lip ( 25 ) for engagement with the other connection element ( 2 . 3 ), wherein in the groove-shaped notch ( 36 ) a spring element ( 44 ) is used, which at least partially to the mutually opposite groove edges ( 37 . 38 ) is applied from the inside and strives to push them apart by an inherent spring force and thereby the two legs ( 26 . 33 ) of the sealant ( 24 ) in the bearing gap ( 14 ) between the two connection elements ( 2 . 3 ) spread apart so that the sealing lip ( 25 ) on the outside ( 41 ) of one leg ( 33 ) experiences an increased contact pressure against its contact surface. Wind turbine according to claim 36, characterized in that at least one sealant ( 24 ) at least one annular mouth ( 23 ) of the bearing gap ( 14 ) of the main bearing ( 1 ) of the rotor shaft according to one of claims 2 to 34 is formed.

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