奥地利专利AT509625A9 BEARING ELEMENT

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专利摘要:

公开号:AT509625A9
申请号:T0059910
申请日:2010-04-14
公开日:2012-01-15
发明作者:
申请人:Miba Gleitlager Gmbh；
IPC主号:

专利说明:

- 1 -
The invention relates to a bearing element for supporting the rotor hub of a wind turbine with at least one inner ring member and at least one outer ring member, wherein between the inner ring member and the outer ring member is a sliding bearing, and a wind turbine with a rotor having a rotor hub, which supported on a stator, wherein between the rotor and the stator, a bearing element is arranged.
Although plain bearings have a much longer service life compared to roller bearings, rolling bearings are still mainly used in wind turbines, especially as a main bearing for rotor bearings. Various studies on wind turbines show that the failure cause "warehouse". in addition to various other failure causes, which are to be settled in the region of the generator or the rotor blades themselves or the rotor in total, has a very high frequency, located in the middle third based on all causes of failure. Compared to other failures of wind turbines, however, a completely different picture with regard to the cost side, namely that failures in the storage of the rotor shaft significantly higher costs and downtime cause than other, usually occurring failures of wind turbines. Despite the reinforced technology "Rolling Bearing " Warehouse failures, especially in the multi-megawatt class, lead to a significant reduction in the profitability of wind turbines due to the high maintenance costs and repair costs or due to the long downtimes. In particular, in so-called off-shore applications, this represents a problem due to the poor accessibility of the facilities, which is associated with even higher costs. This high failure costs or downtimes are due to the fact that in a bearing failure when using bearings usually the entire rotor must be removed.
As a result of this problem, sliding bearing applications in wind power plants have already been described in isolation in the prior art. For example, the DE describes
I FOLLOWING I 9 9 9 9 9 9 9 9 9 9 9 -2-102 55 745 A1 a wind energy plant with a machine carrier arranged at the top of a tower, with a generator stator attached to the machine carrier, hub having a rotor blade and a generator rotor attached to the hub, wherein the generator rotor or the hub connected to the generator rotor is supported at a location radially between and / or axially adjacent to the generator stator and the generator rotor supported on the stator housing. The storage can be done by means of a hydrostatically formed sliding bearing, wherein the sliding bearing may be formed as a segmented sliding bearing, which is integrated in the pole pieces of the generator. It is thus achieved a shortening of the mechanical load paths and a weight reduction of the wind turbine in the gondola in the tower head.
Furthermore, slide bearing applications have been described in the prior art in the field of gearboxes for wind generators, for example in EP 1184 567 A2. It is described therein a transmission for wind generators with a rotor which is in driving connection via a multi-stage planetary gear arrangement and at least one spur gear with at least one generator. The rotor is mounted in the housing of the transmission, in particular guided in plain bearings, at least one bearing can absorb axial forces, and the bearings are hydrostatically liftable and can be switched by selective control of an oil pump in an operation with partial or fully hydrodynamic lubrication.
From DE 100 43 936 A1 discloses a plain bearing for a tower slewing bearing of a wind turbine is known, which has an outer ring and a concentrically arranged inner ring and Gleitbelagträger, being attached to the Gleitbelagträgem sliding linings. The Gleitbelagträger are arranged in radially extending bores of the inner ring and engage in a circumferential groove on the inside of the outer ring. It is thus the interchangeability of the plain bearing improved.
The DE 10 2005 051 912 A1, in turn, generally describes the possibility of mounting the rotor blades via plain bearings.
The object of the present invention is to provide an improved sliding bearing for the rotor hub of a wind turbine.
This object of the invention is achieved, on the one hand, by the abovementioned bearing element, in which the plain bearing is extended by at least two axial distances -3- mutually arranged sliding bearing is formed, and on the other hand by the equipped with this Lagereiement wind turbine.
The advantage here is that a better, radial or axial bearing or guiding the Rotomabe of the wind turbine is achieved by the two spaced sliding bearings. In addition, it is achieved by the two plain bearings, that the sliding bearing can be exposed to higher loads, such as these can occur in particular in the so-called whirling operation or start / stop cycles of wind turbines and also occur in wind peaks and changing wind directions. Surprisingly, it has also been found that a hydrostatic Anfahrunterstützung the sliding bearing is not required, whereby a structurally simpler solution of this slide bearing and thus a corresponding cost savings can be achieved.
According to a preferred embodiment of the invention it is provided that at least one of the slide bearing is formed by circumferentially juxtaposed Gleitla-ger pads. By dividing the entire bearing surface on individual plain bearing pads is achieved that the plain bearings are easier to handle, both in terms of the installation of the plain bearing pads as well as with regard to the expansion in the event of a possible disruption of storage. In addition, the advantage is achieved that at a caused by the storage malfunction of the wind turbine only relatively small units need to be replaced, which can be compared to rolling bearings or compared to plain half shells not only reduce downtime reduced maintenance, but also the Improve the economy of the system by reducing the maintenance costs, namely only those areas of the sliding bearing must be replaced, in which the error has occurred, so not a half shell must be replaced as in plain bearings shells where the exchange can be done in particular without disassembly of the rotor , Of course, if necessary, however, the replacement of all plain bearing pads also possible in this embodiment.
According to one embodiment variant, it is provided that the number of sliding bearing pads per sliding bearing is selected from a range with a lower limit of D / 10 and an upper limit of D / 2, in particular a range with a lower limit of D / 8 and an upper limit of D / 4, where D in centimeters is the maximum diameter of the inner ring element. It is thus achieved that despite the division of the plain bearings on individual pads a relatively large proportion of the maximum available
POSSIBLE -4- standing, theoretical slide bearing surface for storage or load transfer through the bearing is available.
An improvement in the bearing function is achieved when the two plain bearings are arranged in angled planes to each other, as this tilting moments can be better accepted.
In this case, the angle which the two planes enclose with one another is selected from a range with a lower limit of 30 ° and an upper limit of 75 °, in particular a range with a lower limit of 35 ° and an upper limit of 60 ° , It was thus possible to further improve the above-described effects with regard to the two mutually angular plain bearings.
A simple way to arrange and fix the slide bearing pads is achieved when the outer ring member has grooves on the surface facing the slide bearing pads and the slide bearing pads are partially disposed in these grooves.
A further improvement of this fixation of the slide bearing pads is achieved when the grooves have a cross-section that widens in the direction of a groove bottom, in particular have a dovetail-shaped or T-shaped cross section, and the slide bearing pads have a cross section corresponding thereto. For a simple interchangeability of the plain bearing pads and a better adjustability of the plain bearing pads, it is provided according to an embodiment of the invention that the plain bearing pads are attached with a releasable fastener on the outer Ringeie-ment.
It can further be provided that the inner ring member consists of two juxtaposed in the axial direction and spaced apart in the axial direction rings, optionally between the rings a spacer is arranged, and the fastener is at least partially disposed between these two rings. It is thus achieved a simpler interchangeability of the plain bearing pads, which rests due to the weight of the rotor, that is, the rotor hub, at a standstill in the lower sliding bearing pads, so that the upper plain bearing pads are free of load and thus removed from the sliding bearing can. Through the two rings is additionally achieved that these slide bearing pads can be removed in the area between the rings by the fastener solved
FOLLOWING THE POSITION OF THE FLIP BODY Pads on the.. outer ring element is released, so that subsequently slide bearing pads can be pushed out of the grooves simply.
According to a further embodiment of the invention, it is provided that two axially juxtaposed slide bearing pads are fixed on a common fastener on the outer ring member, which on the one hand simplify the structural design of the sliding bearing per se and also maintenance work in a shorter time to be performed can. It also simplifies the adjustment of the sliding bearing. For a better oil intake it is provided that the slide bearing pads are at least partially provided with a rounding on at least one end face.
According to a variant of the slide bearing, it is provided that the two slide bearings are arranged at a distance which amounts to at least 40% of a maximum circumferential length of the inner ring element. By so far relatively distant slide bearings tilting moments that act on the Rotomabe on the sliding bearing can be better absorbed.
There is in this embodiment, the possibility that the plain bearings are formed by plain bearing segments, so as to improve the handling of these relatively large plain bearings.
In this embodiment of the invention can be provided that between the mutually facing end surfaces of the sliding bearing segments of a sliding bearing a Keü-element is arranged, said wedge element can be screwed to the inner or outer ring member, whereby on the one hand a contact pressure, that is fixation of the sliding bearing segments is reached and thus the adjustment of the sliding bearing is improved, which is additionally achieved that the interchangeability of the sliding bearing segments can be simplified by these wedge elements by the fixation of the plain bearing segments is released by simply loosening the wedge elements.
According to one embodiment, it can be provided that the end faces of the sliding bearing segments are chamfered, whereby the wedge effect of the wedge element is supported.
REPLACED -6-
In a segment back of the sliding bearing segments grooves and / or bores may be arranged in order to achieve a targeted oil supply per segment, in those areas of the sliding bearing or sliding bearing segments, which are exposed to increased stress. It can thus be achieved that only a minimum amount of oil must be supplied to the sliding bearing segments, so that therefore no hydrostatic starting assistance, which usually works with oil pressures above 1 bar, but usually well above 100 bar, is required.
The plain bearings are preferably formed by multi-layer sliding bearings, in order to achieve an improvement in the bearing function, in particular the lubricity and the support function of this plain bearing.
In this case, an uppermost layer of the multi-layer sliding bearing may have a discontinuous surface, on the one hand to achieve an oil supply to the sliding surface. On the other hand, it has been found that it can be increased by better load distribution, the load-bearing capacity of the plain bearings.
In complete opposition to the view that the sliding layer facing the rotor hub should be relatively soft, a sliding layer according to the invention is used which has a hardness of at least 75 HV (0.001), in particular at least 100 HV (0.001), at least on the sliding surface so that no soft bearing materials are used. It is thus an increase in the life of the bearing ele- ments achieved without or without serious losses in terms of the lubricity of these bearing elements, that is, the plain bearing. In addition, it could be observed that the use of hard sliding layers improves the oil intake, especially during the start-up phase, so that no hydrostatic support is required during the start-up phase. Surprisingly, non-slip coatings are replaceable as a sliding layer, although they have a Vickers hardness of about 25 HV (0.001) to 60 HV (0.001), so are significantly softer than sliding layers described above, with an increase in hardness by adding appropriate Hard particles is possible.
It is possible by the bearing element according to the invention to operate the wind turbine exclusively hydrodynamic in the storage area, so that constructive measures to maintain a certain minimum oil pressure, usually at hydrostatic systems at least 1 bar, but usually well above 100 bar
SUBSEQUENT
»* M * * • * * * · · • · · · * * * • • ··················································································. can be omitted, so that the wind turbine can be designed structurally easier.
According to one embodiment of the wind turbine is provided that the inner ring member of the bearing element is a part of the rotor shaft and the outer ring member is a part of the stator, which in turn can simplify the structural design of the sliding bearing.
Finally, according to a variant embodiment of the wind power plant can be provided that the slide bearing pads are removable by the stator itself, whereby the accessibility of these plain bearing pads is simplified in the case of maintenance and thus on large lifting machinery, as required for example for the exchange of rolling bearings can be dispensed with, so that the downtime due to maintenance on the bearing, especially on the main bearing, can be reduced.
For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
Each shows in a highly schematically simplified representation:
1 shows a detail of a wind turbine in partial section.
FIG. 2 shows a side view of a first embodiment variant of a bearing element; FIG.
3 is a plain bearing pad in an oblique view;
4 shows a detail of an arrangement of slide bearing pads in an oblique view from below;
5 shows a section of a sliding bearing cut in side view;
6 shows a detail of a further embodiment variant of a sliding bearing cut in side view;
7 shows a plain bearing segment in view of the sliding surface;
8 shows the sliding bearing segment according to FIG. 7 in an oblique view of the back; FIG.
Wedge member.
Fig. 9 partially two Gleitlaaerseamente with anaeordneten therebetween
ADDICTION • * • · φ · · «· · · · · · · φ φφφ · * -8-
By way of introduction, it should be noted that the disclosures contained throughout the specification can be applied mutatis mutandis to the same parts or the same component designations. Also, the location information chosen in the description, such as top, bottom, side, etc. related to the immediately described and illustrated figure and are to be transferred to the new situation mutatis mutandis when a change in position. Furthermore, individual features or combinations of features from the illustrated and described different embodiments may also represent separate solutions according to the invention.
Fig. 1 shows an oblique view and partially cut a section of a wind turbine 1, as it is known in principle from the prior art. This wind turbine 1 comprises a tower 2, at the top of a nacelle 3, is arranged. in this nacelle 3 a Rotomabe 4 is arranged, which carries at one end rotor blades 5, in particular rotatably. The other end is for generating electricity, a generator 6, which is designed in this case as a ring generator assigned. The rotor shaft 4 is rotatably supported in the nacelle 3 via a bearing element 7. The bearing element 7 is the so-called main bearing of the wind turbine 1.
As can be seen from Fig. 1, it is in the wind turbine 1 to a gearless version, that is, that between the rotor itself that is the rotor blades 5, and the generator 6, no transmission gear is present. It is a so-called slow runner. In contrast, wind power plants are known from the prior art, which have a transmission gear between the rotor and the generator, often a planetary gear, so that the rotor of the generator runs faster than the rotor hub.
Preferably, the invention relates to the former, that is, the gearless type of wind turbines 1, although the invention can be applied in principle in wind turbines with transmission gear.
2 to 5 show a first embodiment of the bearing element 7 according to the invention. In FIG. 2, a section of the wind turbine 1 in the region of the rotor hub 4 is shown. The bearing element 7 is formed by a sliding bearing with two axially spaced sliding bearings 8, 9 and includes these. With axial distance, the direction along the longitudinal central axis is meant by the Rotomabe 4. r · -
I REPLACED -9-
In addition to the two plain bearings 8, 9, the bearing element 7 further comprises an inner ring element 10, and an outer ring element 11. The inner ring element 10 is designed in two parts with a first ring 12 and a second ring 13, wherein between the rings 12, 13, a spacer element 14 is arranged, so that the two rings 12, 13 are spaced apart in the axial direction.
The plain bearings 8, 9 are arranged between these two ring elements 10,11, wherein the outer ring member 11 is drehbewegiich and the inner ring member 10 is arranged stationary, that is fixed. The outer ring element 11 is also connected via a corresponding fastening arrangement 15 with the rotor hub 4 or the rotor. For fixing the inner ring element 10, that is, the two rings 12,13 in this embodiment, may be formed on a generator stand 16 which is fixed to a machine frame 17, an annular groove 18 in an outer surface in which the inner ring member 10 at least partially arranged, in particular fixed.
The two slide bearings 8, 9 are preferably arranged in this embodiment in two different planes, which enclose an angle 19 with each other. The angle 19 may be selected from a range with a lower limit of 30 ° and an upper limit of 75 °, in particular from a range with a lower limit of 35 ° and an upper limit of 60 °. Due to the angular arrangement of the two slide bearings 8, 9 tilting moments can be better absorbed by the bearing element 7.
As can be seen from FIGS. 3 and 4, the two slide bearings 8, 9 according to FIG. 2 are formed by slide bearing pads 20 or comprise these slide bearing pads 20. In this case, they are distributed around the generator stator 16 in the circumferential direction side by side, in particular at a distance, a plurality of these sliding bearing pads 20 arranged so as to form the bearing surface. In particular, the number of plain bearing pads 20 per slide bearing 8, 9 is selected from a range with a lower limit of D / 10 and an upper limit of D / 2, where D denotes the maximum diameter of the inner ring element 10 in centimeters. For example, with a bearing diameter of 2.2 m, 50 such sliding bearing pads 20 can be distributed over the circumference.
Of course, however, the number of plain bearing pads 20 depends on the size of the circumference, so that a different number of plain bearing pads 20 may be arranged. These plain bearing pads 20, for example, a length 21 in the circumferential direction of 122 mm and a width B £ acncrooht to have from 494-mm. I NACHGEKEiQHT | - 10
For example, these plain bearing pads can have a size in the size of DIN A5 to DIN A4.
There is also the possibility that only one of the plain bearings 8, 9 is provided with such slide bearing pads 20.
The plain bearing pads 20 are preferably attached to the outer ring member 11. For this purpose, according to one embodiment, it may be provided, as can be seen from FIG. 4, that grooves 23 are arranged in this outer ring element 20 on the surface facing the sliding bearing pads 20, into which the plain bearing pads 20 can be inserted. These grooves 23 preferably have a cross-section widening from the surface in the direction of a groove base 24; in particular, these grooves 23 are at least approximately dovetail-shaped or T-shaped in cross-section, with the slide-bearing pads 20 having a cross-sectional profile complementary thereto, ie one increasing cross section of a sliding surface 25 in the direction of a sliding bearing pad back 26. It is thus at least rudimentary fixation of these plain bearing pads 20 achieved in the radial direction. The cross-sectional widening can be formed on all side walls of the grooves 23 or only on individual ones of the side walls, for example only on the rear side wall.
There is also the possibility that these grooves 23 are provided in the corner areas with curves - preferably with the exception of the front corner regions on which the plain bearing pads are inserted, as can also be seen on Fig. 4.
The Gegentauffläche formed by the inner ring member 10, that is, the rings 12,13 in this embodiment, is formed in particular by steel, so that therefore this ring member 10 may be formed from steel, as well as the outer ring member eleventh
The attachment of the sliding bearing pads 20 on the outer ring member 11, so that the plain bearing pads 20 are better protected during operation against slipping out of the grooves 23, can be done by various methods, for example, by welding, solder joints, clamping elements, etc. Preferably However, the attachment, as can be seen from Fig. 5, a releasable fastener 27, in particular a screw. It should be noted that Fig. 5 shows again in a larger view, the outer ring member 11, the inner Ringeiement 10, consisting of the two rings 12,13, and arranged therebetween spacer 14. ΜΛ # " 'Ι_Ι / "' ιΓ "ΡΤ- Τ <! '· ΊίΠ " I. -11 -
The fastening element 27 is preferably formed by a threaded screw, wherein the plain bearing pads 20 are secured by washers 28 from slipping out of the grooves 23 in the outer ring member 11. For this purpose, the slide bearing pads 20, as shown in Fig. 5, in the region of the slide bearing pad back 26 at least partially in the width direction 22 opposite end portions 29, 30 are at least approximately wedge-shaped (viewed in the direction of the length 21 ), wherein a wedge 31 serves to fix the slide bearing pad 20 in the groove 23 of the outer ring element 11, for which purpose this groove 23 has a corresponding, opposite contour, and a further wedge 32 rests on the washers 28. It is thus achieved that the slide bearing pad 20 is pressed into the groove 23 of the outer ring member 11 by the inclination of the sliding bearing pads 20 and by screwing the fastening element 27.
As can be seen in particular from FIG. 5, the fastening element 27 is arranged-at least approximately centrally in the axial direction-in the outer ring element 11 so that two opposing plain bearing pads 20 of the two plain bearings 8, 9 are held and fixed by a fastening element 27 can be.
The plain bearing pads 20 preferably have a multilayer structure, as can be seen in FIG. 3, and comprise at least one support layer 33 and a sliding layer 34 arranged thereon. If appropriate, further layers, for example a layer, may be arranged between the support layer 33 and the sliding layer 34 Bearing metal layer and / or a bonding layer or a diffusion barrier layer.
The sliding layer 34 is preferably executed interrupted at least in the surface area, so that several, in particular two, Gieitschichtteilflächen 35 are formed. It has namely been found that a better load distribution can be achieved by the split sliding layer 34.
Of course, it is within the scope of the invention possible to make several subdivisions, in particular three, four, five or six Gieitschichtteilflächen 35, depending on the dependence of the size of the surface of the sliding layer 34, form.
Recesses 36, in particular grooves, can be provided between the casting layer part faces 35, which can extend, for example, only over part of the layer thickness of the sliding layer 34 or over the entire layer thickness. These grooves 36 can be used in particular as Ölzufühmuten.
I NACHGEr.ZCI-iT I -12-
It is further provided according to a Ausfühmngsvariante the invention that an end face 37 at least the sliding layer 34 is at least partially provided with a rounding, so as to achieve a better oil intake in the region of the sliding layer 33, that is, the running surface of the sliding bearing pads 20. As can be seen in particular from FIG. 4, this rounding extends in the region of at least one of the side walls of the grooves 23 in the outer ring element 11, wherein, if appropriate, both side regions, that is to say both end faces 37, which lie opposite one another and bear against the side walls of the groove, at least the sliding layer 34 may be provided with such a curve, so that the sliding layer 33 has a hyperbolic outer contour in plan view and thus a center region of the sliding layer 34 is further away from the side wall of the grooves 23 than a corner region.
Of course, the surface of the slide bearing pads 20 should also be made rounded, that is, the surface of at least the sliding layer 34 is adjusted according to the rounding of the inner ring member 10.
In particular, the sliding layer 34 consists of a relatively hard sliding bearing material having a hardness of at least 75 HV (0.001), in particular of at least 100 HV (0.001), at least on the sliding layer surface 35. For example, the sliding layer may be formed of a material selected from a group comprising aluminum-based alloys, such as AiSn20Cu, AIZn4Si3, silver-based alloys or copper-base alloys, optionally with bismuth, bismuth base alloys, if appropriate.
As already mentioned above, the sliding layer 34 may also be formed by a lubricating varnish, in which case the sliding layer 34 has a hardness between 25 HV (0.001) to 60 HV (0.001).
For example, polytetrafluoroethylene, fluorine-containing resins, e.g. Perfluoroalkoxy copolymers, polyfluoroalkoxy polytetrafluoroethylene copolymers, ethylene tetrafluoroethylene, polychlorotrifluoroethylene, fluorinated ethylene-propylene copolymers, polyvinyl fluoride, polyvinylidene fluoride, alternating copolymers, random copolymers, e.g. Perfluoroethylene-propylene, polyester-imides, bismaleimides, polyimide-resins, e.g. Carboranimide, aromatic polyimide resins, hydrogen-free polyimide resins, poly-triazo-pyromellithimides, polyamide-imides, especially aromatic, Polyarylethe-rimide, optionally modified with isocyanates, polyetherimides, optionally modified with isocyanates, epoxy resins, epoxy resin esters, phenolic resins, polyamide 6, polyamide 66, polyoxymethylene, silicones , Polyaryleth " 1 "'" isrketones, polyaryl ether ethers, polyether ether ketones, polyether ketones, polyvinylidene diflourides, polyethylene sulfides, allylene sulfide, polytriazo-pyromellithimides, polyester imides, polyaryl sulfides, polyvinyl sulfides, polyphenylene sulfides, polysulfones, polyethersulfones, polyarylsulfones, polyaryloxides, polyarylsulfides, and copolymers thereof ,
Preference is given to a lubricating varnish which, in the dry state, consists of 40% by weight to 45% by weight of MoS2.20% by weight to 25% by weight of graphite and 30% by weight to 40% by weight of polyamideimide, optionally even hard particles, such as Oxides, nitrides or carbides, in the bonded coating in a proportion of a total of 20 wt .-% may be included, which replace a proportion of solid lubricants.
The support layer 33 may be formed, for example, by steel or a copper-based alloy, in particular with zinc, for example CuZn31Si, CuSnZn, an AlZn or a CuAl alloy.
6 to 8 show another embodiment of the Lagereiementes 7 for a wind turbine 1. Again, the bearing element 7 consists of two axially spaced slide bearings 38, 39 which are arranged between an inner ring member 40 and an outer ring member 41. In the preferred embodiment, while the inner ring member 40 is a part of a Rotomabe 42 and the outer ring member 41 is part of a stator 43 of the wind turbine 1. Unlike the above-described embodiment of the invention, so in this embodiment, the inner Ringeiement 40 drehbewegiich and that outer ring member 41 fixedly arranged.
The two plain bearings 38, 39 are arranged in this embodiment in a plane, it being understood that it is of course possible that these two plain bearings 38, 39 are arranged in this embodiment in two mutually angular planes.
Preferably, these two plain bearings 38, 39 but relatively widely spaced from each other, wherein a distance 44 between the two plain bearings 38, 39, measured between the facing end faces in the circumferential direction of the plain bearings 38, 39, at least 40%, in particular at least 50%, one maximum circumferential length of the inner ring member 40 is. By this wide spacing of the two sliding bearings 38, 39, it is possible that the bearing element 7 can be subjected to higher loads,
In particular, tilting torques acting on the rotor can be better absorbed.
Preferably, the two plain bearings 38, 39 formed as sliding bearing segments 45, as can be seen from Figs. 7 and 8, so that over the circumference of the inner ring member 40 a plurality of plain bearing segments 45 form a plain bearing 38 and 39, respectively. For fixing the sliding bearing segments 45 on the stator 43 again a variety of methods and methods can be used, as already described above, wherein according to a preferred embodiment, the sliding bearing segments 45 are bevelled at end surfaces 46, 47 and between the Gleitiagersegmenten 45 to the bias or attachment a Keileiement 48 is arranged, as can be seen from Fig. 9, wherein via this wedge member 48, the sliding bearing segments 45 are pressed against the inner surface of the outer ring member 41. Thus, in this embodiment as well, the plain bearing segments 45 are arranged at a distance from one another - viewed in the circumferential direction - due to the wedge elements 48 arranged therebetween.
For the arrangement of the two sliding bearings 38, 39 between the inner ring member 40 and the outer ring member 41 is also in this embodiment, the possibility in the inner ring member 40, that is, on a surface facing the outer ring member of the inner ring member 40 and / or at one inner ring member 40 facing surface of the outer ring member 41 to provide a groove.
As can be seen in particular from FIGS. 7 and 8, the slide bearings 38, 39 grooves 50 and / or bores 51 can be arranged on a segment back 49 for the supply or generally for the guidance of lubricating oil, in order in particularly stressed areas of the plain bearings 38, 39 to build up a lubricating film better. It should be noted, however, that the Lagereiement 7 according to the invention is preferably exclusively hydrodynamically operable, so that no hydrostatic is required as Anfahrunterstützung. For the purposes of the invention, the term "exclusively hydrodynamic" means that no oil pressure of more than 1 bar is maintained, so that only a minimum amount is supplied via the at least one groove and / or the at least one bore 51 to a sliding surface 52. It is therefore possible via these grooves 50 and bores 51 a targeted supply of oil per sliding bearing segment 45.
Of course, in the embodiment with the plain bearing pads 20, the possibility of the slide bearing pad back 26 via corresponding grooves or holes
- 15- make a targeted oil supply to the sliding layer surface or Gleitschichtteilfläche 35 of Gleitla ger pads 20.
It should also be mentioned that the explanations on the choice of material for the plain bearings 8.9 of the first embodiment of the invention are also applicable to the plain bearings 38, 39, so that these plain bearings 38, 39 are preferably also designed as multilayer plain bearings.
Both the Gieitlager pads 20 and the sliding bearing segments 45 may be designed not only as Radialgleitiager, but also be provided on at least one parallel to the circumferential direction formed end face with a corresponding sliding layer material, so that therefore an additional axial bearing on these slide bearing pads 20 and the Gleitiagersegmente 45 is achieved.
It is also a targeted oil supply possible, as can be seen for example from Fig. 8, which shows 45 corresponding recesses 53 for the oil supply in these faces of the sliding bearing segments.
The replacement of the plain bearing segments 45 and the installation of these sliding bearing segments 45 in the bearing element 7 can be done by lateral removal from or lateral insertion into the bearing element 7 - viewed in the axial direction.
The plain bearing pads 20, however, can be removed via the stator in the region of an oil feed 54, as shown in Fig. 5. For this purpose, only the fastener 27 is released and optionally removed, as well as the spacer 14. As a result, these plain bearing pads 20 can each be pulled out obliquely downward from the grooves 23. The installation or replacement of these plain bearing pads 20 can be done in exactly the reverse order.
It is therefore possible in all embodiments of the invention, only individual parts of the sliding bearings 8, 9 and 38, 39 exchange, so that does not need to be replaced as in a rolling bearing, the entire bearing element 7 and the entire bearing. The embodiment of FIGS. 2 to 5 also has the advantage that this bearing element 7, a Schrägrollenwälzlager, as they are currently used as a main bearing for rotor bearings, can replace, so so such bearing elements 7 in the course of maintenance and the previously used bearings in existing Replace plants.
} RETURNED
-16-
The embodiments show possible embodiments of the bearing element 7, wherein it should be noted at this point that the invention is not limited to the specially dargesteilten embodiments thereof, but also various combinations of the individual embodiments are mutually possible and this variation possibility due to the teaching of technical action representational invention in the skill of those skilled in this technical field. So there are also other embodiments, which are possible by combinations of individual details of the illustrated and described embodiment variant, within the scope of the claims includes.
For the sake of order, it should finally be pointed out that for a better understanding of the construction of the bearing element 7, this or its components have been shown partly unevenly and / or enlarged and / or reduced in size.
The individual embodiments shown in FIGS. 1 to 9 can form the subject of independent solutions according to the invention. nachgef.sc: ΓΓ
Reference Symbols 1 Wind turbine 2 Tower 3 Gondola 4 Rotor hub 5 Rotor blade 6 Generator 7 Bearing element 8 Sliding bearing 9 Sliding bearing 10 Ring element 11 Ring element 12 Ring 13 Ring 14 Spacer element 15 Mounting arrangement 16 Generator stand 17 Machine carrier 18 Ring groove 19 Angle 20 Slide bearing pad 21 Length 22 Width 23 Groove 24 Grooved bottom 25 Sliding surface 26 Sliding bearing pad 27 Fastening element 28 Shim 29 End region 30 End region 31 Wedge 32 Wedge 33 Supporting layer 34 Sliding layer 35 Sliding layer surface 36 Groove 37 Face 38 Sliding bearing 39 Sliding bearing 40 Ring element 41 Ring element 42 Rotor hub 43 Stator 44 Distance 45 Sliding bearing segment 46 End face 47 end face 48 wedge element 49 segment back 50 groove 51 bore 52 Gieitfläche 53 recess 54 oil supply
submitted

权利要求:
Claims (23)
[1]
1. bearing element (7) for supporting the rotor hub (4) of a wind turbine (1) with at least one inner ring element (10,40) and at least one outer ring element (11,41), wherein between the inner ring member (10, 40) and the outer ring member (11, 41) is formed a sliding bearing, characterized in that the sliding bearing by at least two at an axial distance (44) mutually arranged sliding bearing (8, 9, 38, 39) is formed ,
[2]
2. bearing element (7) according to claim 1, characterized in that at least one or the sliding bearing (8,9) is formed in each case by circumferentially juxtaposed slide bearing pads (20) or are.
[3]
3. bearing element (7) according to claim 2, characterized in that the number of plain bearing pads (20) per sliding bearing (8, 9) is selected from a range having a lower limit of D / 10 and an upper limit of D / 2, where D in cm is the maximum diameter of the inner ring element (10).
[4]
4. bearing element (7) according to one of claims 1 to 3, characterized in that the two plain bearings (8,9) are arranged in planes which are at an angle to each other.
[5]
5. bearing element (7) according to claim 4, characterized in that the two planes are arranged at an angle (19) to each other, which is selected from a range having a lower limit of 30e and an upper limit of 75e.
[6]
6. bearing element (7) according to one of claims 2 to 5, characterized in that the outer ring member (11) on the sliding bearing pads (20) facing surface grooves (23) and the sliding bearing pads (20) partially are arranged in these grooves (23). _ REPLACED

[7]
7. bearing element (7) according to claim 6, characterized in that the grooves (23) aulweisen in the direction of a groove bottom (24) widening cross-section, in particular have a dovetail-shaped or T-shaped cross-section, and the plain bearing pads (20 ) have a corresponding cross-section.
[8]
8. bearing element (7) according to one of claims 2 to 7, characterized in that the slide bearing pads (20) are fastened with a releasable fastening element (27) on the outer ring element (11).
[9]
9. bearing element (7) according to claim 8, characterized in that the inner ring element (10) consists of two axially juxtaposed and spaced apart in the axial direction rings (12,13), wherein optionally between the rings (12,13 ) a spacer element (14) is arranged, and the fastening element (27) at least partially between the two rings (12,13) is arranged.
[10]
10. bearing element (7) according to claim 8 or 9, characterized in that in each case two axially juxtaposed slide bearing pads (20) via a common fastening element (27) on the outer ring member (11) are fixed.
[11]
11. Bearing element (7) according to one of claims 2 to 10, characterized in that the slide bearing pads (20) are provided on at least one end face at least partially with a rounding.
[12]
12. bearing element (7) according to claim 1, characterized in that the two sliding bearings (38, 39) are arranged at a distance which is at least 40% of a maximum circumferential length of the inner ring element (40).
[13]
13. bearing element (7) according to claim 1 or 12, characterized in that the sliding bearings (38, 39) by sliding bearing segments (45) are formed. FOLLOW-UP · «* ····» -3-
[14]
14. Bearing element (7) according to claim 13, characterized in that between mutually assigning end faces (46, 47) of the sliding bearing segments (45) of a sliding bearing (33, 39) a wedge element (46) is arranged.
[15]
15. Bearing element (7) according to claim 13 or 14, characterized in that the successive facing end faces (46,47) of the sliding bearing segments (45) of a sliding bearing (38, 39) are bevelled.
[16]
16. Bearing element (7) according to one of claims 13 to 15, characterized in that in a segment back (49) of the sliding bearing segments (45) at least one groove (50) and / or at least one bores (51) is or are arranged.
[17]
17. bearing element (7) according to one of claims 1 to 16, characterized in that the sliding bearings (8, 9, 38, 39) are formed by multilayer plain bearings.
[18]
18. bearing element (7) according to claim 17, characterized in that an uppermost layer of the multi-layer sliding bearing has a discontinuous surface.
[19]
19. Bearing element (7) according to one of claims 1 to 18, characterized in that at least one sliding layer (34) of the sliding bearing (8, 9, 38, 39) has a hardness of at least 75 HV (0.001) or between 25 HV (0.001 ) and 60 HV (0.001), if this is designed as a bonded coating, at least on the sliding surface (25).
[20]
20. Wind turbine (1) with a rotor having a rotor hub (4), which is supported on a stator, wherein between the rotor (4) and the stator, a bearing element (7) is arranged, characterized in that the bearing element (7 ) is formed according to one of claims 1 to 19.
[21]
21. Wind turbine (1) according to claim 20, characterized in that the bearing element (7) is exclusively hydrodynamically operable. SUBSEQUENT

-4-
[22]
22. Wind power plant (1) according to claim 20 or 21, characterized in that the inner ring element (40) of the bearing element (7) form part of the rotor hub (4) and the outer ring element (41) forms part of the stator.
[23]
23. Wind turbine (1) according to any one of claims 20 to 22, characterized in that the slide bearing pads (20) are removable by the stator. Miba Gleitlager GmbH by REPLACEMENT

Lawyers Burger & Partner Lawyer GmbH

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同族专利:

公开号 | 公开日

US9458880B2|2016-10-04|

AT509625B1|2012-02-15|

US20130071246A1|2013-03-21|

DK2558718T3|2017-02-20|

EP3124811A1|2017-02-01|

CN102834611B|2015-11-25|

EP2558718B1|2016-11-09|

KR20130093498A|2013-08-22|

WO2011127510A1|2011-10-20|

AT509625A1|2011-10-15|

CN102834611A|2012-12-19|

KR101749286B1|2017-06-20|

EP3124811B1|2021-12-08|

EP2558718A1|2013-02-20|

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法律状态:
2016-01-15| PC| Change of the owner|Owner name: MIBA GLEITLAGER AUSTRIA GMBH, AT Effective date: 20151116 |

2020-12-15| MM01| Lapse because of not paying annual fees|Effective date: 20200414 |

优先权:

申请号 | 申请日 | 专利标题

AT0059910A|AT509625B1|2010-04-14|2010-04-14|BEARING ELEMENT|AT0059910A| AT509625B1|2010-04-14|2010-04-14|BEARING ELEMENT|

KR1020127029761A| KR101749286B1|2010-04-14|2011-04-14|Bearing element|

PCT/AT2011/000182| WO2011127510A1|2010-04-14|2011-04-14|Bearing element|

CN201180018616.6A| CN102834611B|2010-04-14|2011-04-14|Supporting element|

EP11722706.6A| EP2558718B1|2010-04-14|2011-04-14|Bearing element|

DK11722706.6T| DK2558718T3|2010-04-14|2011-04-14|bearing member|

EP16172461.2A| EP3124811B1|2010-04-14|2011-04-14|Bearing element|

US13/640,613| US9458880B2|2010-04-14|2011-04-14|Bearing element for supporting the rotor hub of a wind turbine|

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