• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a wind turbine with a rotor and a generator, between the rotor and the generator a planetary gear (1) is arranged, which is in operative connection with the rotor and the generator, wherein the planetary gear (1) a plurality of planetary gears (4), a plurality of planet pins (8), and a planet carrier (9), wherein in each case a planetary gear (4) is mounted on a respective planet pin (8), wherein the planet pin (8) on the planet carrier (9) is fixed, wherein the planetary gear ( 4) is formed in several parts and a - viewed in the radial direction - outer part (13) and at least one with the outer part (13) connected inner part (14), wherein the at least one inner part (14) on the planet pin (8) and abuts at least a portion of its surface (15) has a sliding coating (16), and wherein the connection of the at least one inner part (14) formed with the outer part (13) via a connecting element (20) is that has its largest dimension in the axial direction of the planet gear (4), wherein the connecting element (2) is formed by a screw or rivet.
    公开号:AT512436A1
    申请号:T39/2012
    申请日:2012-01-16
    公开日:2013-08-15
    发明作者:
    申请人:Miba Gleitlager Gmbh；
    IPC主号:
    专利说明:

    «4 4t •« · 4 4 · · 4 4 4
    * «··· * · • t · · -ft« «« > * * * * * • • • * * * * * * * * * * * * * Λ Λ «r ·
    The invention relates to a wind turbine with a rotor and a generator, wherein between the rotor and the generator, a planetary gear is arranged, which is in operative connection with the rotor and the generator, wherein the planetary gear has a plurality of planet gears, a plurality of bolts, and a planet carrier, wherein each planet gear is mounted on a respective Boizen, wherein the bolt is fixed to the planet carrier.
    Pianetengetriebe for wind turbines for generating electric power, as they are known for example from DE 102 60 132 A1, are used to translate the relatively low speed of the rotor of the wind turbine into a higher speed of the generator rotor. Usually, in such planetary gears, as also described in DE 102 60 132 A1, rolling bearings are used as bearing elements for the planetary gears. However, the prior art also describes slide bearings as bearing elements, for example EP 1 544 504 A2 or AT 509 624 A1.
    The high elastic deformation of the planet carrier a wind gear, especially in the multi-megawatt power range, leads in conjunction with a circumferential point of attack to a so-called Außenringwandern of rolling bearings. Even by a very high coverage of the outer ring with the inner diameter of the planetary gear, this relative movement can not be avoided and is often solved by the waiver of the outer ring and the execution of the planet bore as Wälzkörperlauffiäche. in the embodiment with plain bearings, such a solution is practically impossible, but at least not practical. With regard to the rolling bearing arrangement, these are readily available. N2011 / 33000: i «· • · • * 9 Μ • * 9 9 · 9 9 9 9 9 9 9 9 9 9 9 9 9 9 9 9 9 9 9 9 9 9 9 ·
    The solution to the problem would be direct coating of the planetary bore. In practice, this fails because of the necessary heat treatment for hardening the planet gears, which is why all known metallic and synthetic bearing materials are eliminated. Furthermore, due to the large wall thickness of the planet gears, a spout of the planetary bore in the rotational process with metallic materials is very problematic. Not least, the direct coating is also a logistical problem, since the planetary gears of a wind turbine transmission usually have several hundred kilograms per planetary gear.
    In AT 509 624 A1 it is described that a radial displaceability of the multilayer plain bearings is possible, so that edge beams can also be formed. This is compensated or intercepted by a hard sliding layer and possibly an inlet layer.
    It is the object of the present invention to improve the sliding bearing in a equipped with plain bearings planetary gear of a wind turbine.
    This object of the invention is achieved in the wind turbine mentioned above in that the planetary gear is formed in several parts and one -in the radial direction - outer part and at least one inner part, wherein the at least one inner part rests against the bolt and at least a portion of its surface a sliding layer.
    It should be noted that in the following with respect to the planetary gear, the singular is used. It goes without saying, however, that the invention is applicable to all planet wheels of such a planetary gear and in the preferred embodiment, all planetary gears are formed according to the invention.
    With such a distribution of the planetary gear on several components is achieved that can be dispensed with additional plain bearings, since the planet itself can take over the task of sliding bearing. In addition, a weight reduction is achieved. Another advantage is that the inner part of the N2011 / 33000 • * *
    If necessary, the planetary gear can be replaced or recoated without the entire planetary gear itself having to be subjected to extensive manipulation. It is thus also possible to carry out the coating relatively thin-walled in a hydrodynamic sliding bearing, whereby a weight reduction is also possible. Due to the sum of the weight reductions, a lower mechanical load on the bearing of the Pianetenräder can be realized, whereby the bearings can have a longer life despite hydrodynamic operation. In addition, local peak loads can be reduced because the inner part completely independent of the outer part in terms of conscious elasticity can be designed freely designed.
    According to an embodiment, it is provided that the at least one inner part is connected to the outer part. Relative movements of the slide bearing with respect to the outer part of the planetary gear wheel are therefore avoided, as a result of which peak loads as a result of tilting moments and thus also the possible destruction of the slide bearings can be better avoided.
    It may be provided that the connection of the at least one inner part with the outer part is formed via a connecting element which has its largest dimension in the axial direction. It is thus achievable a further reduction of local peak loads of sliding bearings, since thus by the introduction of torque forces on the connecting element exclusively in the axial direction of the rolling effect of the sliding bearings can be at least largely excluded because it only arises between them relatively moving radial surfaces, caused by the combination of elastic deformation and circumferential force input.
    In the preferred embodiment, the at least one inner part is connected to the outer part via a screw connection, that is, the connecting elements are designed in the form of a screw, since a detachable connection can thus be made available which can easily be released in the event of repair. In addition, the screw can also be designed as a solid break point in case of overload. N2011 / 33000 * 4 · «· · · · ·
    According to another embodiment, it can be provided that the at least one inner part is positively connected to the outer part additionally or alternatively to the above connection method. It is thus a better power transmission achievable. In addition, the form-fitting element can also be used as an installation aid of the inner part on the outer part by the right positioning is specified via the positive-locking element. This is particularly advantageous with regard to split bearing shells, that is to say plain bearing half shells or sliding bearing segments, for example.
    According to a further embodiment, it is provided that the outer part has a web pointing inwards in the radial direction on the pin, against which the at least one inner part rests. It is thus a larger-scale power transmission in the axial direction from the outer part to the inner part and vice versa allows, which can be achieved as a result also due to the improved power flow, a longer life of storage.
    For simpler arrangement of the connecting element, in particular for the formation of the screw can be provided that the Innenteii has a radially outwardly facing web, with which the at least one inner part rests against the outer part. By projecting in the radial direction web, it is possible to form the joint further away from the bearing surface, whereby their accessibility is improved. In addition, however, the contact surface between the outer part and the inner part can be improved or the processing of these parts of the planet gear to form these contact surfaces can be simplified via the web.
    It is also possible that in order to improve the connection of the outer part with the at least one inner part, at least one of the contact surfaces in the region of the connection is roughened and / or provided with a friction-increasing coating. It is thus created an additional connection due to an additional "wedging" of the components of the planetary gear, whereby higher forces can be transmitted through the joint. N2011 / 33000 • * «* * * - 5
    In the preferred embodiment, the at least one inner part is formed as a socket, since thus the integration of the plain bearing in the planetary gear can be made simpler by fewer joints compared to half shells or segments are required.
    It is also possible that the outer part has a further radially inwardly pointing to the pin web, which is at least partially disposed between two inner parts. It is thus also a further improvement of the connection with between the at least one inner part and the outer part achieved by an additional contact surface for the internal parts is provided. In addition, this further web can act as centering for the two inner parts, which are arranged one behind the other in the axial direction.
    For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
    Each shows in a schematically simplified representation:
    Fig. 1 shows a gear in the form of a planetary gear cut in side view;
    2 shows a detail of a planetary gear in cross section.
    Fig. 3 shows a detail of a planetary gear of a variant in the
    Cross-section;
    Fig. 4 shows a detail of a planetary gear of a further Ausführungsva-variant in cross section.
    By way of introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same component names, wherein the disclosures contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or component names. Audi are the locations specified in N2011 / 33000 ί * * '* * * * * 1 * _ * * & * * of the description, e.g. 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.
    1 shows a transmission in the form of a simple planetary gear 1 for a wind turbine cut in side view,
    As is known, wind turbines comprise a tower at whose upper end a nacelle is arranged, in which the rotor is mounted with the rotor blades. This rotor is via the planetary gear 1 with a generator, which is also located in the nacelle, operatively connected, via the planetary gear 1, the low speed of the rotor is translated into a higher rotational speed of the generator rotor. Since such embodiments of wind turbines belong to the prior art, reference should be made at this point to the relevant literature.
    The planetary gear 1 has a sun gear 2, which is rotatably connected to a shaft 3, which leads to the generator rotor. The sun gear 2 is surrounded by a plurality of planetary gears 4, for example two, preferably three or four. Both the sun gear 2 and the planet wheels 4 have serrations 5, 6, which are in meshing engagement with each other, these spur gears 5, 6 are indicated in Fig. 1 with a cross. The planetary gears 4 are respectively mounted on plain bearings 7 on an axis formed by a planetary pin 8, the so-called planetary axis. These planet pins 8 can either be integrally formed with at least one part of a planetary carrier 9 or they are used as separate components in bores of the planet carrier 9, above the planetary gears 4, a ring gear 10 is arranged, which also at least partially has a toothing 11 on an inner surface, which is in meshing engagement with the face gear 6 of the Pianetenräder 4. The ring gear 10 is rotatably connected to a rotor shaft 12 of the rotor of the wind turbine. The spur gears 5.6 and the teeth 11 may be designed as a straight or helical toothing.
    Since such planetary gears are also already known from the prior art, for example, from the above-cited N2011 / 33000 documents »· *« «• *
    technology, there is no need for further discussion here. It should be noted, however, that not only single-stage versions of planetary gears within the scope of the invention are possible, but also multi-stage, for example, two or three stages, including at least one planet further Stirnradstufen can be integrated.
    Fig. 2 shows a first embodiment of the planetary gear 4 according to the invention. The planetary gear 4 is or includes an outer part 13 and at least one inner part 14, wherein in objective representation the planetary gear 4 has two inner parts 14.
    The outer part 13 of the planetary gear 4 is that component which in the radial direction of the planetary gear 4 outside, i. above, the at least one inner part 14 is arranged and which carries the spur toothing 6. Accordingly, the inner part 14 of the planetary gear 4 is understood to mean the component which is located in the radial direction within, i. below, of the outer part 13 is arranged, but a portion of the outer part 13 can extend in the radial direction to the height of the inner part 14, as will be explained below. The planetary gear 4 rests against the planetary pin 8 via the at least one inner part 14. The outer part 13, however, has no contact with the planet shaft. 8
    In the representational representation of FIG. 2, the two inner parts 14 are arranged one behind the other in the axial direction of the planetary gear 4 and preferably at an axial distance from one another.
    The inner part 14 is formed separately from the outer part 13, that is not integrally formed therewith.
    The at least one inner part 14 has a sliding coating 16 on at least one surface 15. The surface 15 points in the direction of the planetary pin 8, so that therefore the planetary gear 4 rests on this slide coating 16 on the planetary pin 8.
    In addition to the coating of this surface 15, other surfaces of the inner part may also be at least partially provided with the sliding coating 16, for example an axially outer end face 17 which bears on a thrust washer IM2011 / 33000 18 is present. The thrust washer 18 is held in or by the planet carrier. The inner part 14 can thus also fulfill an axial bearing function in addition to the radial bearing function.
    The start-up slide 18 may for example consist of steel.
    In principle, the sliding coatings 16 on several surfaces of the inner part 14 may be different from each other, for example with regard to the composition of the coating and / or in the structure of different layers. It may therefore be the sliding coating 16 on the surface 15 to that on the end face 17 differently formed. Preferably, however, an embodiment is used in which all sliding coatings 16 of the planetary gear 4 are the same.
    It should be noted that the above and subsequent embodiments of the inner part 14 in the presence of more than one inner part 14 can be transferred to all or more inner parts 14, although a mirror image training, as shown in Fig. 2, is possible.
    The sliding coating 16 consists in the simplest case of a sliding layer. This sliding layer forms a running surface 19 for the planetary bolt 8.
    In addition to this single-layered embodiment of the sliding coating 16, there is also the possibility within the scope of the invention that intermediate layers are arranged between the sliding layer and the surface 15 of the inner part 14, for example a bearing metal layer and / or at least one bonding layer and / or one diffusion barrier layer.
    Examples of bearing metal layers are:
    Aluminum-based bearing metals, in particular: AISn6CuNi, AISn20Cu, AISi4Cd, AICd3CuNi, AISi11Cu, AISn6Cu, AISn40, AISn25CuMn, AISi1 ICuMgNi; νήμ * «vtnn« «» «· ·« • * * t · * * ·· «+ * · t
    Bearing metals based on copper, in particular:
    CuSnIO, CuAl10Fe5Ni5, CuZn31Si1, CuPb24Sn2, CuSn8Bi10;
    Tin-based bearing metals, in particular:
    SnSb8Cu4, SnSb12Cu6Pb.
    It is also possible to use bearing metals other than the bearing metals based on nickel, silver, iron or chromium alloys.
    A bonding layer or a diffusion barrier layer can be formed, for example, by an aluminum layer, tin layer, copper layer, nickel layer, silver layer or their alloys, in particular binary alloys.
    The sliding layer is preferably made of a material selected from a group comprising alloys based on Al, AlZn, AlSi, AlSnSi, CuAl, CuSn, CuZn, CuSnZn, CuZnSn, CuBi, Bi, Ag, AIBi base, bonded coatings.
    Examples of preferred alloys for the sliding layer are AISn20Cu, AIZn4Si3, AIZnSi4.5.
    For example, polytetrafluoroethylene, fluorine-containing resins, e.g. Perfluoroalkoxy copolymers, polyfluoroalkoxy-polytetrafluoroethylene copolymers, ethylene-tetrafluoroethylene, polychlorotrifluoroethyl-ene, fluorinated ethylene-propylene copolymers, polyvinyl fluoride, polyvinylidene fluoride, alternating copolymers, random copolymers, e.g. Perfluoroethylene-propylene, polyester-imides, bismaleimides, polyimide-resins, e.g. Carborane imides, aromatic polyimide resins, hydrogen-free polyimide resins, polytriazo-pyromellithimides, polyamideimides, especially aromatic, polyaryletherimides, optionally modified with isocyanates, polyetherimides, optionally modified with isocyanates, epoxy resins, epoxy resin esters, phenolic resins, polyamide 6, polyamide 66, polyoxyethylene , Silicones, polyaryl ethers, polyaryl ketones, polyaryl ether ketones, polyaryl ether ether ketones, polyether ether ketones, polyether ketones, polyvinylidene diflourides, polyethylene sulfides, allylene sulfide, polytriazo-pyromellithimides, polyester imides, polyaryl sulfides, polyvinyl sulfides, polyphenylene sulfides, polysulfones, N2011 / 33000 * * ΊΟ · **
    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 M0S2, 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.
    There is also the possibility that on the sliding layer an inlet layer, for example, from the lubricating varnish, is arranged. On the other hand, there is the possibility that a hard layer is additionally applied to the overlay, for example a so-called DLC layer, for example SiC, or C.
    The slip coating 16 or the layers of the slide coating 16 can be deposited by methods known from the prior art, for example by means of a PVD method, in particular by sputtering, or by means of a CVD method, or galvanically or by centrifugal casting or by flame spraying.
    The inner part 14 is preferably connected to the outer part 13. In particular, for this purpose at least one connecting element 20 is used which has its largest dimension in the axial direction. The at least one connecting element 20 can be, for example, a rivet. In the preferred embodiment, the connecting element 20 is formed by a threaded screw which, viewed from the outside in the axial direction, projects outwardly into the outer part 13 through the inner part 14bis. Preferably, this connecting element 20 is arranged so that it does not protrude beyond this in the axial direction of the planetary gear 4. In particular, a head of the connecting means 20 is sunk in the inner part.
    The screw can be a simple threaded screw. But it is also possible to use threaded screws with a self-locking thread or a screw with a multi-start thread. For a better connection of the inner part 14 to the outer part 13, the outer part 13 can have a web 21 pointing inwards in the radial direction on the Planetenbotzen 8, on which the at least one inner part 14 is present. Preferably, this web 21 is formed so that it is partially placed in the radial direction over the inner part 14. For this purpose, it can be provided according to a further embodiment, that the inner part 14 has a radially outwardly facing web 22, with which the at least one inner part 14 on the outer part 13, in particular on the web 21 of the outer part 13 rests. A contact surface 23 of the inner part 14 and a voltage applied to this contact surface 24 of the outer part 13 are at least approximately vertically or vertically oriented, as shown in FIG. 2 can be seen.
    To improve the connection can be provided that the contact surface 23 of the inner part 14 and / or the abutment surface 24 of the outer part 13 is roughened at least partially or are and / or at least partially provided with a friction-enhancing coating or are. As the friction-enhancing coating, for example, an adhesive layer or resin layer, e.g. from a phenolic or acrylate resin, in which hard particles such as oxides, nitrides or carbides of transition metals, or corundum, etc. ,, are stored, these hard particles preferably projecting beyond the coating surface, so that they are in the other bearing surface 23 or 24 when connecting the inner part 14 with the outer part 13 impress.
    The inner part 14 is preferably designed as a bushing, thus extending over the entire circumference of the planetary pin 8 without interruption. The inner part 14 may, however, in principle also be designed in the form of a half-shell or a segment, in which case a plurality of inner parts 14 are arranged behind one another and preferably without spacing in the circumferential direction.
    En Fig. 3 is a further and possibly separate embodiment of the planetary gear 4 is shown, again with the same parts the same reference numerals or component names as in the preceding Figs. 1 and 2 are used. In order to avoid unnecessary repetition, reference is made to N2011 / 33000 * 12 *** for the detailed description in the preceding FIGS. 1 and 2.
    Fig. 3 shows a section of the planetary gear 4 in cross section. This again comprises the outer part 13 and at least one inner part 14, which the Gleitbeschichtung 16 aulweist.
    The connection of the two components of the planetary gear 4 takes place in this variant Ausführung-variant positive-locking element 25, which is arranged on the inner part 14, in particular on the web 22 of the inner part 14, and projects beyond the contact surface 23 of the inner part 14. The outer part 13, in particular the web 21 of the outer part 13, has for this purpose a corresponding recess 26 into which the positive-locking element 25 protrudes. The cross section of the recess 26 is adapted to the cross section of the positive-locking element 25 in terms of its size, i. that the two cross sections are approximately the same size, wherein the cross section of the recess 26 is slightly larger than the cross section of the positive locking element 25 (viewed in the same direction).
    In principle, the positive-locking element 25 can have any desired shape, wherein also shapes with at least one undercut are possible. For example, the form-fitting element may be formed in the shape of a knob or a bar. It is also possible that the form-fitting element is formed extending in the direction of the circumference of the inner part 14 with its longitudinal extent. Furthermore, viewed in plan view, a cross-sectional area may be designed to taper or widen.
    As indicated by dashed lines in Fig. 3, there is the possibility that the positive connection is used not only alternatively but also in addition to the connection with the connecting element 20 in the planetary gear 4.
    Of course, not only a positive locking element 25 can be arranged, but a plurality of discrete positive locking elements 25 may be formed distributed over the contact surface 23 of the inner part 14 and / or the contact surface 14 of the outer part 13. N2011 / 33000
    There is also the possibility that the inner part 14 is produced by fracture separation from the outer part 13, in which case the break point can also act as a positive-locking element 25.
    FIG. 4 shows a further embodiment of the planetary gear 4, which is possibly independent of itself, wherein the same reference numerals or component designations are used again for the same parts as in the preceding FIGS. 1 and 2. In order to avoid unnecessary repetition, reference is made to the detailed description in the preceding Figs. 1 and 2 or reference.
    With this embodiment, it should be clarified that it is also possible in the context of the invention that the planetary gear 4 has only a single inner part 14 which extends over the entire width of the planetary gear 4 in the axial direction, that is not only over a portion of this width as shown in Figs. 2 and 3, although such a design is also possible, ie that only a single inner part 14 is connected to the outer part 13, wherein the inner part 14 extends only over a partial region of the width of the planetary gear 4.
    Also in this embodiment, the outer part 13 on the web 21. The inner part 14, however, has two webs 22 which are so far away in the axial direction, that the web 21 of the outer part 13 between these two webs 22 can be accommodated and preferably rests against these.
    It is within the scope of the invention further possible that the outer part 13 has a further radially inwardly pointing on the bolt web (not shown in the figures), which is at least partially disposed between two in the axial direction one behind the other arranged inner parts 14.
    In all embodiments, 16 channel-shaped recesses may be provided for guiding a lubricant in the sliding coating 1Θ or in at least one layer of the sliding coating. In the preferred embodiment of the planetary gear, the sliding coating 16 can be operated purely hydrodynamically without hydrostatic assistance. Nnm0 * m * * * * φ * * φ φ • φ φ «φ § * · φ φ * • *« φ φ φ φ φ φ * · · · φ φ · φ φ φ φ * * * φ * φ φ φ φ φ φ φ φ * φ φφ φφ φ ^ ΙΙ «φφ den. There are therefore no oil pumps or the like for the lubricating oil supply and to maintain a hydrostatic pressure required. The oil is supplied in this purely hydrodynamic solution on the unloaded bearing side and pulled by the rotational movement of the planetary gear 4 in the camp.
    The embodiments show possible embodiments of the planetary gear 1 and the planetary gear 4, it being noted at this point that various combinations of the individual variants are possible with each other and this variation possibility due to the teaching of technical action by objective invention in the skill of the technical field professional.
    For the sake of order, it should finally be pointed out that for a better understanding of the structure of the planetary gear 1 or of the planetary gear 4, these or their components have been shown partly unevenly and / or enlarged and / or reduced in size. N2011 / 33000 ··· # # # # # # # # # # # # # # # # # # # # # # # # # # # # # # # #
    REFERENCE NUMBERS
    planetary gear
    sun
    wave
    planet
    spur gearing
    spur gearing
    bearings
    planet shaft
    planet carrier
    ring gear
    gearing
    rotor shaft
    outer part
    inner part
    surface
    slide coating
    face
    thrust washer
    tread
    connecting element
    web
    web
    contact surface
    contact surface
    Form-fitting element
    Deepening N2011 / 33000
    权利要求:
    Claims (10)
    [1]
    1. Wind turbine with a rotor and a generator, wherein between the rotor and the generator, a planetary gear (1) is arranged, which is in operative connection with the rotor and the generator, wherein the planetary gear (1) a plurality of planet gears ( 4), a plurality of planet pins (8), and a planet carrier (9), wherein in each case a planet gear (4) is mounted on a respective planet pin (8), wherein the planet pin (8) is fixed to the planet carrier (9), characterized characterized in that the planetary gear (4) is designed in several parts and a -in the radial direction - outer part (13) and at least one inner part (14), wherein the at least one inner part (14) on the planet pins (8) and at least a sliding coating (16) in a region of its surface (15).
    [2]
    2. wind power plant according to claim 1, characterized in that the at least one inner part (13) with the outer part (13) is connected.
    [3]
    3. Wind power plant according to claim 2, characterized in that the connection of the at least one inner part (14) with the outer part (13) via a connecting element (20) is formed, which has its largest dimension of the axial direction of the planet gear (4).
    [4]
    4. Wind turbine according to claim 3, characterized in that the at least one inner part (14) is connected to the outer part (13) via a screw connection.
    [5]
    5. Wind power plant according to one of claims 2 to 4, characterized in that the at least one inner part (13) with the outer part (14) is positively connected. N2011 / 33000
    [6]
    6. Wind power plant according to one of claims 1 to 5, characterized in that the outer part (14) in the radial direction inwardly on the planet pin (8) facing web (21) on which abuts the at least one inner part (14)
    [7]
    7. Wind turbine according to one of claims 1 to 6, characterized in that the inner part (14) has a radially outwardly facing web (22), with which the at least one inner part (14) rests against the outer part (13).
    [8]
    8. Wind turbine according to one of claims 2 to 7, characterized in that a contact surface (23) of the inner part (14) and / or a contact surface (24) of the outer part (13) in the region of the connection of the inner part (14) with the outer part (13) are roughened and / or provided with a friction-increasing coating.
    [9]
    9. Wind power plant according to one of claims 1 to 8, characterized in that the at least one inner part (14) is designed as a socket.
    [10]
    10. Wind power plant according to one of claims 1 to 9, characterized in that the outer part (13) has a further radially inwardly on the planet pins (8) facing web, which is at least partially disposed between two inner parts (14). Miba Gleitlager GmbH

    Q lawyers bu Jer & Partner Attorney at Law N2011 / 33000
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    同族专利:
    公开号 | 公开日
    WO2013106879A1|2013-07-25|
    AT512436B1|2013-10-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US20110092330A1|2009-10-16|2011-04-21|Mitsubishi Heavy Industries, Ltd.|Planetary bearing structure|
    WO2011127509A1|2010-04-14|2011-10-20|Miba Gleitlager Gmbh|Gear train for a wind turbine|
    WO2012029121A1|2010-08-31|2012-03-08|三菱重工業株式会社|Planetary gear mechanism, bearing structure, wind power generator, and method for producing planetary gears|US20180299006A1|2015-09-15|2018-10-18|Miba Gleitlager Austria Gmbh|Planetary gearing for a wind turbine having mounted planetary gears|
    DE102017221353A1|2017-11-29|2019-05-29|Zf Friedrichshafen Ag|Spread planetary plain bearings|
    DE102019209944A1|2019-07-05|2021-01-07|Zf Friedrichshafen Ag|Planet gear with flexible bearing seat|
    US10948071B2|2016-10-05|2021-03-16|Flender Gmbh|Bearing arrangement for a planet gear of a planetary gear set|SU1090941A1|1981-07-20|1984-05-07|Предприятие П/Я А-1125|Bearing unit of satellite gear|
    DE20023443U1|2000-09-29|2004-04-01|Desch Antriebstechnik Gmbh & Co. Kg|Planetary transmission with bearing and components has shell bearing surfaces at least surface-hardened|
    DE10260132A1|2002-12-19|2004-07-01|Winergy Ag|Planetary gear for a wind turbine|
    DE10360693A1|2003-12-19|2005-07-14|Winergy Ag|Planetary gear, especially for wind turbines|
    US20110140448A1|2009-12-15|2011-06-16|Mitsubishi Heavy Industries, Ltd.|Wind-turbine-generator-system transmission and wind turbine generator|
    DK2383480T3|2010-04-30|2013-01-21|Winergy Ag|Planetary gear for a wind turbine|DE102013220063A1|2013-10-02|2015-04-02|Schaeffler Technologies Gmbh & Co. Kg|Planetary wheel bearing assembly|
    EP2933483A1|2014-04-15|2015-10-21|Siemens Aktiengesellschaft|Drive system for a wind turbine|
    EP2975299A1|2014-07-18|2016-01-20|Siemens Aktiengesellschaft|Slide bearing for a planetary carrier|
    EP3301315A1|2016-09-30|2018-04-04|Flender GmbH|Sliding bearing, torque converter and wind turbine|
    AT15975U1|2017-05-23|2018-10-15|Miba Gleitlager Austria Gmbh|Wind Turbine Gearbox|
    EP3489548B1|2017-11-24|2022-01-05|Rolls-Royce Deutschland Ltd & Co KG|Planetary gear unit|
    DE102017127876A1|2017-11-24|2019-05-29|Rolls-Royce Deutschland Ltd & Co Kg|Planetary gear and plain bearing pin for a planetary gear|
    EP3489549B1|2017-11-24|2022-01-05|Rolls-Royce Deutschland Ltd & Co KG|Planetary gear and journal bearing pin for a planetary gear|
    CN108253128A|2018-03-06|2018-07-06|杭州前进齿轮箱集团股份有限公司|A kind of wind turbine gearbox planetary structure|
    DE102018009737A1|2018-12-13|2020-06-18|Miba Gleitlager Austria Gmbh|Wind turbine gearbox with at least one plain bearing|
    法律状态:
    2019-06-15| PC| Change of the owner|Owner name: MIBA GLEITLAGER AUSTRIA GMBH, AT Effective date: 20190430 |
    2021-09-15| MM01| Lapse because of not paying annual fees|Effective date: 20210116 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA39/2012A|AT512436B1|2012-01-16|2012-01-16|WIND TURBINE|ATA39/2012A| AT512436B1|2012-01-16|2012-01-16|WIND TURBINE|
    PCT/AT2013/050012| WO2013106879A1|2012-01-16|2013-01-15|Wind turbine|
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