WO2025132011A1 - Palier de pale de rotor pour une turbine sous-marine - Google Patents

Palier de pale de rotor pour une turbine sous-marine Download PDF

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Publication number
WO2025132011A1
WO2025132011A1 PCT/EP2024/085994 EP2024085994W WO2025132011A1 WO 2025132011 A1 WO2025132011 A1 WO 2025132011A1 EP 2024085994 W EP2024085994 W EP 2024085994W WO 2025132011 A1 WO2025132011 A1 WO 2025132011A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
rotor blade
bearing
designed
rotor hub
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
PCT/EP2024/085994
Other languages
German (de)
English (en)
Inventor
Matthias Hofmann
Michael Baumann
Marcel Alfred Memmel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SKF AB
Original Assignee
SKF AB
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by SKF AB filed Critical SKF AB
Publication of WO2025132011A1 publication Critical patent/WO2025132011A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/14—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load specially adapted for operating in water
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/56—Systems consisting of a plurality of bearings with rolling friction in which the rolling bodies of one bearing differ in diameter from those of another
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H3/00—Propeller-blade pitch changing
    • B63H3/02—Propeller-blade pitch changing actuated by control element coaxial with propeller shaft, e.g. the control element being rotary
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii

Definitions

  • the present invention relates to a rotor blade bearing arrangement for an underwater turbine according to the preamble of claim 1, as well as a rotor hub arrangement with such a rotor blade bearing arrangement.
  • the rotor blades of underwater turbines are typically attached to a rotor hub and can be mounted so they can rotate relative to the rotor hub. By rotating or pivoting the rotor blades, the drive power can be varied. Furthermore, the rotor blade pitch control rotates the rotor blades in such a way that no torque is transferred from the rotor blades to the rotor hub, allowing the turbine to come to a complete standstill. In some designs, the blade pitch control is used to adapt to changing water flow directions without having to rotate the entire underwater turbine.
  • such an arrangement and spacing can compensate for the thermal growth of the rotor blade shaft as well as the growth of the bearing inner rings compared to the bearing outer rings, thus reducing the risk of preload loss in the bearing.
  • the rotor hub itself preferably has a rotor hub housing that defines an interior space.
  • the rotor hub housing can be further reinforced with stiffening ribs arranged in the interior space and increasing the structural stability of the rotor hub housing.
  • an assembly opening can be provided in the rotor hub housing, ensuring accessibility to the interior of the rotor hub.
  • the rotor blade bearing assembly is then designed as a module that is simply inserted into the rotor hub.
  • the module then preferably has pre-adjusted and/or pre-loaded bearing units and can be inserted into the rotor hub without further adjustment.
  • the rotor hub bearing module can also, as further preferred embodiments show, also have the rotor blade shaft and/or a seawater seal and/or possibly other drive components (e.g. gears), etc., which are pre-assembled outside the rotor hub in the separate housing and installed in the rotor hub as a unit in a further assembly step.
  • the advantage of the modular design is the simplified assembly of the bearing units, since this can be carried out outside the hub housing with good accessibility, and as mentioned above, They can be adjusted and pre-tensioned and inserted into the rotor hub.
  • the individual modules can also be replaced very quickly for service work or in the event of damage.
  • the rotor blade bearing assembly further comprises at least one seawater seal assembly with at least one sealing lip, wherein the seawater seal assembly is designed to provide a seal between the housing and the rotor blade shaft.
  • the seawater seal assembly is designed to be attachable to the housing and the at least one sealing lip abuts the rotor blade shaft.
  • the seawater seal assembly is a redundant lip seal for long maintenance intervals and can include a relubrication function and a condition monitoring system.
  • the rotor blade bearing assembly is preferably designed as a module and can advantageously also include the rotor blade shaft in addition to the housing and the bearing units.
  • the rotor blade shaft itself typically has a first rotor-hub end designed to be received in an interior of the rotor hub and a second seaward end designed to be non-rotatably fastened to a rotor blade.
  • the rotor blade bearing module can comprise the housing and the seawater seal.
  • the rotor blade shaft regardless of whether it is a module or not, can have at least one drive component at its first rotor hub-side end, which is designed to interact with a central drive for rotating the rotor blade shaft. Since the rotor shaft extends relatively far into the interior of the rotor hub due to the above-mentioned relationship, the rotor shaft is particularly well suited for central adjustment drives. In this case, all rotor blades are connected via a mechanism and controlled centrally via an actuator (e.g., electric motor, hydraulic cylinder). In other words, the rotor blades are not adjusted individually, but together.
  • an actuator e.g., electric motor, hydraulic cylinder
  • the drive components are bevel gears, wherein the adjustment drive is preferably driven by an electric gear motor or a hydraulic motor and the torque distribution takes place via a central bevel gear transmission.
  • the central drive wheel distributes the torque to the individual rotor blades via a bevel gear stage, with the size of the bevel gears ensuring torque multiplication.
  • a small central drive wheel and larger output wheels are provided on the rotor blade shaft.
  • the drive component is a push rod connected to the rotor blade shafts via a connecting rod/crank pulley mechanism.
  • the push rod itself is axially movable by means of a linear drive and ensures adjustment of the rotor blade shafts.
  • a rotor hub assembly for an underwater turbine, comprising a rotor hub and a rotor blade bearing assembly received within the rotor hub, as discussed above.
  • the rotor blade bearing assembly is configured to support and secure the rotor blade to the rotor hub.
  • the rotor hub assembly in turn, is typically non-rotatably connected to a rotor main shaft, which in turn drives a generator for power generation.
  • the rotor hub arrangement comprises at least two rotor blades arranged opposite one another, which are fastened to rotor blade shafts, which in turn are each mounted and fastenable by means of the rotor blade bearing arrangement.
  • the rotor blade shafts each have a first end, which projects into an interior of the rotor hub, and a second seaward end, which is rotatably fastenable to the rotor blade.
  • the opposing rotor blade shafts are arranged in the rotor hub with the aid of the rotor blade bearing arrangement in such a way that a diameter X of a circle described by the first ends of the rotor blade shafts and a Diameter Y of a circle described by the second ends of the rotor blade shafts satisfies the following relation:
  • a central bevel gear stage (central drive gear) driven by an electric or hydraulic motor (drive motor) can preferably be integrated into the system solution. It is particularly preferred if the drive motor is integrated into the main shaft to achieve greater compactness and a higher degree of modularization.
  • Each rotor blade is driven by the central drive gear, which meshes with the bevel gear mounted on the rotor blade shaft.
  • the rotor blade bearing arrangement is thus designed for maximum compactness, allowing for a significant reduction in the seawater seal, resulting in a significant cost reduction for the overall design.
  • the rotor hub assembly comprises a push rod which is axially movable by means of a linear drive and which is connected to the hub-side ends of the rotor blade shafts via a connecting rod-crank pulley mechanism.
  • a so-called spinner is arranged on the rotor hub, which is designed to improve the flow dynamics of the turbine.
  • a spinner is a streamlined fairing mounted in the center of the rotor hub. Spinners make the turbine more streamlined overall, thereby reducing flow resistance and smoothing the flow pattern.
  • the spinner can also be designed to accommodate the gear motor for the bevel gear drive or the linear drive for the push rod.
  • the above-mentioned features provide a compact and cost-effective centralized rotor blade pitch system for an underwater turbine.
  • the modularization of the rotor blade bearing assembly and the rotor hub assembly allows for easy assembly and disassembly.
  • the system's susceptibility to failure is reduced because the pitching mechanism is centralized and thus contains as few components as possible.
  • the bevel gear drive also enables 360° pitching of the rotor blades, which is not possible with conventional pitching mechanisms.
  • the rotor hub arrangement and/or the underwater turbine as a whole is also protected against corrosion by providing a corrosion-protective coating and/or at least one sacrificial anode.
  • the first bearing unit of the rotor shaft bearing arrangement is arranged in such a way that a continuous force flow path occurs from the rotor shaft via the bearing unit into the rotor hub and/or a stiffening rib formed on the rotor hub.
  • the rotor hub arrangement has an outer bearing seat for the first bearing unit, wherein the rotor hub has a special contour on the outer bearing seat, which enables a continuous force flow from the rotor blade via the shaft to the bearing and thus into the hub.
  • the idea of a continuous force flow is also implemented in the contour of possible internal stiffening ribs that are formed on the rotor hub.
  • a force flow transfer can take place from the rotor blade shaft to the inner bearing and then via the specially shaped stiffening ribs to the outer contour of the hub.
  • the theoretical force lines converge at the flange connection between the rotor hub and the main rotor shaft and are introduced here into the surrounding structure (main rotor shaft).
  • Fig. 1 to Fig. 23 schematic sectional views of various different preferred embodiments of an underwater turbine.
  • FIG. 1 shows a schematic sectional view of an underwater turbine 1.
  • the underwater turbine 1 comprises, as its main components, a rotor hub 2, which is designed to support and mount rotor blades 4, and a main rotor shaft 6 which is rigidly connected to the rotor hub 2 and extends into a nacelle 8 in which a generator 10 for generating electricity is accommodated.
  • the main rotor shaft 6 can be fastened to the rotor hub 2, for example, by means of fastening means, in particular screws 5.
  • the rotor blades 4 are subjected to a water flow, thereby causing the rotor hub 2 to rotate.
  • the rotor 12 can be attached directly to the main rotor shaft 6, but it is also possible for a gearbox (not shown) to be arranged between the main rotor shaft 6 and the generator 10, which converts the slow rotation of the main rotor shaft 6 into a fast rotation for power generation.
  • the bearing units 14, 16 are designed in particular to be able to absorb axial and radial loads.
  • the main rotor shaft 6 can be mounted on axial and radial bearing units.
  • the rotor blades 4 are preferably also mounted so that they can be adapted to the respective flow direction without having to rotate the entire nacelle 8.
  • the adjustment of the rotor blades 4 also allows the rotor blades 4 to be rotated into the so-called feathered position, in which the flow does not cause the rotor hub 2 to rotate. This allows the underwater turbine 1 to be shut down entirely.
  • the rotor blades 4 themselves are usually arranged symmetrically to one another and, in the case of two rotor blades 4-1, 4-2, are arranged directly opposite one another, for example. With more than two rotor blades, such as three or four rotor blades 4, these can be arranged at a distance of 120° or 90° from one another.
  • a two-bladed rotor which has two opposing rotor blades 4-1; 4-2.
  • Figures 2 to 23 show various details and embodiments of the underwater turbine 1.
  • Figures 2 to 5 show various basic designs of a rotor hub assembly 200.
  • the rotor hub assembly 200 typically comprises a rotor hub housing 202 into which a rotor blade shaft 204 is inserted.
  • the rotor blade shaft 204 is designed to be connected to the actual rotor blades 4 (see Fig. 1) and can be constructed in one piece or in multiple parts. It is also possible for the rotor blade shaft to be designed as a shaft stub.
  • the two-part design, rotor blade 4 and rotor blade shaft 204 allows the rotor hub assembly 200 to be transported pre-assembled, and the rotor blades to be connected to the rotor hub assembly 200, and more precisely to the rotor blade shaft 204, only at the site of use. In some embodiments, it is even possible to mount the rotor blades on the rotor blade shaft underwater. For this purpose, it is particularly advantageous if a rotor hub interior 210 is sealed off from the water into which the underwater turbine is installed.
  • the rotor blade shafts 204-1, 204-2 each have a seaward end 207 and a rotor hub end 208.
  • the seaward end 206 is designed to be connected to the actual rotor blades 4.
  • the rotor hub-side end 208 projects into an interior space 210 of the rotor hub assembly 200 and is designed to be connected to a preferably central rotor blade twisting device 300.
  • the rotor blade shafts 204 are rotatably mounted relative to the housing 202 of the rotor hub 2 by means of a rotor blade bearing assembly 214.
  • the rotor blade shafts 204 themselves define a length L of the rotor blade shaft 204 between their seawater-side end 207 and their rotor hub-side end 208.
  • the two rotor hub-side ends 208-1 and 208-2 and the two seawater-side ends 207-1, 207-2 are in turn spaced apart by a distance X and Y, respectively. If more than two rotor blades are present, the rotor hub-side ends 207 and the seawater-side ends 208 each lie on a circle with a diameter X and Y, respectively.
  • the rotor blade bearing assembly 214 further comprises a first offshore bearing unit 220 and a second rotor hub-side bearing unit 230.
  • the bearing units 220 and 230 can be designed as rolling bearing units 221, 231, as shown in Figures 2 to 5. However, it is also possible, as shown in Figures 6 to 8, to design the bearing units 214 as plain bearing units 225; 235.
  • bearing units 220; 230 are designed as rolling bearings 221; 231, they each have an inner ring 222; 232 and an outer ring 223; 233, which define a bearing interior between them in which rolling elements 224; 234 are arranged.
  • the rolling elements 224; 234 can optionally be guided in a rolling bearing cage (not shown).
  • bearing units 220; 230 are designed as plain bearings 225; 235, plain bearing bushes 226; 236 can be provided, which ensure particularly good plain bearing support.
  • the inner diameters d1i, d2i are usually dimensioned such that they overlap with an outer diameter of the rotor blade shaft 204, so that the Bearing inner rings 222, 232 or the plain bearing bushes 226; 236 can be fastened to the rotor blade shaft 204 with a press fit.
  • the housing section 252 has, in particular, a first rotor hub-side section 254 and a second seaside section 255, which are designed as outer sliding surfaces 281, 291.
  • the inner sliding surfaces 282; 292 are formed by the plain bearing bushes 226; 236.
  • the inner and outer sliding surfaces 281, 291, 282, 292 are designed as radial sliding surfaces that serve to radially support the rotor blade shaft 204 with respect to the rotor hub housing section 252.
  • the second end 336 can extend through the entire rotor shaft 6, but it is also possible, as shown in particular in Figure 15, for the nacelle-side end 336 of the push rod 332 to also be received in the rotor main shaft 6.
  • the second end 336 of the push rod 332 is subjected to axial force directly or indirectly by means of a linear drive 400.
  • the push rod 332 is designed at its second end 336 as a hydraulic piston 402, which is received in a hydraulic cylinder 404.
  • the hydraulic cylinder 404 is received in the housing section 272, while in the embodiment of Figure 15, the hydraulic cylinder is inserted into the rotor main shaft 6.
  • any other linear drive 400 can be used, e.g. a pneumatic linear drive or a worm drive.
  • the push rod-piston connecting housing 426 of the embodiments illustrated in Figures 19 to 23 is also stationary, while in the embodiment of Figures 20, 21 it rotates together with the rotor main shaft 6, the linear drive housing 428, and the push rod 332.
  • the linear drive 400 is also designed as a hydraulic piston drive in this exemplary embodiment.
  • the piston 402 is guided in a cylinder 404 and, together with the cylinder, forms a first working chamber 406 and a second working chamber 408, which are alternately supplied with hydraulic fluid by means of a hydraulic fluid provided by the hydraulic pump 410 in order to move the piston 402 from a first position I to a second position II.
  • the piston 402 has a flange 405 at the cylinder-housing-side end 422, with which the piston 402 is sealingly guided in the piston housing 404 and separates the working chambers 406, 408 from one another.
  • Rotor hub housing section Rotor hub-side first housing section Sea-side second housing section

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Turbines (AREA)

Abstract

La présente invention concerne un agencement de palier de pale de rotor (214) pour une turbine sous-marine (1) ayant une première unité de palier (220 ; 230) avec une première bague externe (223 ; 233) qui est conçue pour être reçue dans une partie de logement de moyeu de rotor (252 ; 262), et une première bague interne (222 ; 232) qui est conçue pour être reliée à l'arbre de pale de rotor (204) pour une rotation conjointe, et ayant une seconde unité de palier (220 ; 230) avec une seconde bague externe (223 ; 233) qui est conçue pour être reçue dans la partie de logement de moyeu de rotor (252 ; 262), et une seconde bague interne (222 ; 232) qui est conçue pour être reliée à l'arbre de pale de rotor (204) pour une rotation conjointe, la première bague interne (222 ; 232) ayant un premier alésage de bague interne (227 ; 237) ayant un premier diamètre d'alésage de bague interne (d1i), et la première unité de palier (220 ; 230) et la seconde unité de palier (220 ; 230) étant disposées à une distance de palier (W) l'une par rapport à l'autre, ce qui suit s'appliquant pour la distance de palier W : 0.8*d1i ≤ W ≤ 2*d1i, de préférence 1*d1i ≤ W ≤ 1.5*d1i.
PCT/EP2024/085994 2023-12-21 2024-12-12 Palier de pale de rotor pour une turbine sous-marine Pending WO2025132011A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102023213221.4 2023-12-21
DE102023213221.4A DE102023213221A1 (de) 2023-12-21 2023-12-21 Rotorblattlagerung für Unterwasserturbine

Publications (1)

Publication Number Publication Date
WO2025132011A1 true WO2025132011A1 (fr) 2025-06-26

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ID=94129803

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2024/085994 Pending WO2025132011A1 (fr) 2023-12-21 2024-12-12 Palier de pale de rotor pour une turbine sous-marine

Country Status (2)

Country Link
DE (1) DE102023213221A1 (fr)
WO (1) WO2025132011A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB572940A (en) * 1943-09-20 1945-10-30 English Electric Co Ltd Improvements in swivelling bladed adjustable pitch propellers
DE69913655T2 (de) * 1998-02-07 2004-10-07 Futuretech Technologies Ltd Antriebssystem
EP2947339A1 (fr) * 2014-05-20 2015-11-25 Eolotec GmbH Grand palier, en particulier palier principal pour une éolienne, et éolienne dotée d'un tel grand palier

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB572940A (en) * 1943-09-20 1945-10-30 English Electric Co Ltd Improvements in swivelling bladed adjustable pitch propellers
DE69913655T2 (de) * 1998-02-07 2004-10-07 Futuretech Technologies Ltd Antriebssystem
EP2947339A1 (fr) * 2014-05-20 2015-11-25 Eolotec GmbH Grand palier, en particulier palier principal pour une éolienne, et éolienne dotée d'un tel grand palier

Also Published As

Publication number Publication date
DE102023213221A1 (de) 2025-06-26

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