Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
  • F03D—WIND MOTORS
  • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
  • F03D80/70—Bearing or lubricating arrangements
  • F03D80/703—Shaft bearings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
  • F03D—WIND MOTORS
  • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
  • F03D80/70—Bearing or lubricating arrangements
• • 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
  • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
• • 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
  • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
  • F16C23/02—Sliding-contact bearings
  • F16C23/04—Sliding-contact bearings self-adjusting
• • 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
  • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
  • F16C25/02—Sliding-contact bearings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
  • F05B2240/00—Components
  • F05B2240/10—Stators
  • F05B2240/14—Casings, housings, nacelles, gondels or the like, protecting or supporting assemblies there within
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
  • F05B2260/00—Function
  • F05B2260/30—Retaining components in desired mutual position
  • F05B2260/301—Retaining bolts or nuts
• • 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
  • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
  • F16C23/02—Sliding-contact bearings
  • F16C23/04—Sliding-contact bearings self-adjusting
  • F16C23/043—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings
  • F16C23/048—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings for axial load mainly
• • 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
  • F16C2300/00—Application independent of particular apparatuses
  • F16C2300/10—Application independent of particular apparatuses related to size
  • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
• • 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
  • F16C2360/00—Engines or pumps
  • F16C2360/31—Wind motors
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
  • Y02E10/00—Energy generation through renewable energy sources
  • Y02E10/70—Wind energy
  • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

• the invention relates to a nacelle for a wind turbine.
• EP3783237A1 discloses a wind turbine with a nacelle with a nacelle housing, a rotor shaft, a rotor hub and a first and second roller bearing for La delay of the rotor shaft on the nacelle housing.
• the object of the present invention was to overcome the disadvantages of the prior art and to provide a nacelle for a wind turbine which has improved storage.
• a nacelle for a wind turbine is designed.
• the gondola includes:
• a rotor hub which is arranged on the rotor shaft
• a second rotor shaft bearing for bearing the rotor shaft on the nacelle housing, the first rotor shaft bearing and the second rotor shaft bearing being arranged at an axial distance from one another and the first rotor shaft bearing being arranged closer to the rotor hub than the second rotor shaft bearing.
• the first rotor shaft bearing has a first sliding surface, which has an average first sliding surface diameter.
• the second rotor shaft bearing has a second sliding surface, which has an average second sliding surface diameter, the first sliding surface facing away from the rotor hub at least in sections, the first sliding surface and the second sliding surface facing each other at least in a partial section. 2
• first rotor shaft bearing and the second rotor shaft bearing are designed as independent plain bearings.
• the nacelle according to the invention has the advantage that the first rotor shaft bearing and the second rotor shaft bearing are designed as plain bearings.
• the fiction, contemporary arrangement of the first sliding surface and the second sliding surface to one another or to the rotor hub, an axial load occurring due to the wind force or a tilting moment occurring due to the weight of the rotor hub can be absorbed or transmitted particularly efficiently.
• a surprisingly good suitability for use in a nacelle of a wind turbine can thus be achieved by the arrangement according to the invention.
• the fact that the first sliding surface mostly faces away from the rotor hub in sections means that at least at a specific point a tangent applied to the sliding surface is tilted away from the rotor hub.
• the first sliding surface has an average first sliding surface diameter and that the axial distance between the first rotor shaft bearing and the second rotor shaft bearing is measured from the innermost contact point of the first sliding surface to the innermost contact point of the second sliding surface, with the axial distance between 20 % and 1,000%, in particular between 50% and 500%, preferably between 90% and 300%, in particular between 120% and 200% of the mean first sliding surface diameter.
• the mean first sliding surface diameter is that diameter which lies in the mean of the area integral over the first sliding surface.
• the innermost contact point of the first sliding surface and the innermost contact point of the second sliding surface are those points at which the respective sliding surface still contacts the respective counter surface and which are arranged next to one another.
• first sliding surface is in the form of a first spherical cap and that the second sliding surface is in the form of a second spherical cap, with the first sliding surface forming a first spherical cap curve in the initial section and the second sliding surface forming a first spherical segment in the initial section second 3
• Kugelkalottenbogen forms, with a first tangent in a first Kugelkalottenbogen- center and a second tangent in a second Kugelkalottenbogenmitte V-shaped zueinan are arranged.
• first sliding surface and the second sliding surface results in good transferability of axial forces while simultaneously absorbing the radial forces and coupling moments applied by the rotor hub.
• the first rotor shaft bearing has a first outer ring and that the second rotor shaft bearing has a second outer ring
• the first rotor shaft bearing has a first inner ring and that the second rotor shaft bearing has a second inner ring
• the first sliding surface is arranged between the first outer ring and the first inner ring and wherein the second sliding surface is arranged between the second outer ring and the second inner ring
• the position of the first outer ring and the second outer ring is fixed relative to one another and wherein the position of the first inner ring is fixed relative to the rotor shaft and the second inner ring or a second plain bearing element is pretensioned in the axial direction towards the first inner ring by means of a tensioning means, the tensioning means acting between the second inner ring and the rotor shaft.
• such a design of the first sliding surface and the second sliding surface results in a good transferability of axial forces while at the same time absorbing
• the two inner rings are arranged at a fixed distance from one another in their axial position.
• the two outer rings or the two bearing blocks can be pushed relative to one another.
• the first bearing block it is conceivable for the first bearing block to be fixed and for the purpose of tensioning the bearing to be moved away from the second bearing block or tensioned.
• the clamping means prefferably be designed in the form of a shaft nut. This has the advantage that the two inner rings can be positioned exactly in relation to one another using a shaft nut in order to achieve the necessary preloading of the plain bearing. It is also conceivable that the lock nut is tightened with a predefined tightening torque in order to achieve a defined preload.
• a spring element is arranged between the clamping means and the second inner ring or between the clamping means and the second plain bearing pads. This brings with it the advantage that any thermal expansion or, to a lesser extent, wear can be compensated for by the spring element.
• first rotor shaft bearing and/or the second rotor shaft bearing are designed to additionally absorb the weight of the generator. This has the advantage that no separate storage is needed to store the generator.
• first sliding surface and/or the second sliding surface are formed on plain bearing pads. This has the advantage that plain bearing pads are easy to insert into the plain bearing and easy to change. In addition, plain bearing pads have an exact sliding surface and are easy to manufacture in an industrial process.
• the average first sliding surface diameter is greater than the average second sliding surface diameter, in particular that the average second sliding surface diameter is between 50% and 90%, preferably between 70% and 80% of the average first sliding surface diameter.
• first outer ring it is possible for the first outer ring to be accommodated in a first bearing block and for the second outer ring to be accommodated in a second bearing block.
• first rotor shaft bearing and the second rotor shaft bearing can be designed independently of one another.
• first rotor shaft bearing and the second rotor shaft bearing are designed as hydrodynamic slide bearings.
• first rotor shaft bearing and the second rotor shaft bearing are designed as hydrostatic plain bearings.
• an independent lubricating oil pump can be seen in front of each other.
• the first rotor shaft bearing and the second rotor shaft bearing are supplied with lubricating oil by means of a common lubricating oil pump.
• FIG. 1 shows a schematic representation of a wind turbine
• Fig. 3 is a catch section of a second embodiment of the plain bearing.
• Fig. 1 shows a first embodiment of a wind power plant 1 for generating electrical energy from wind energy in a schematic representation.
• the wind turbine 1 includes a nacelle 2 which is rotatably mounted on a tower 3 .
• the gondola 2 6 comprises a nacelle housing 4 which forms the main structure of the nacelle 2 .
• the electrical components such as a generator of the wind turbine 1 are arranged.
• a rotor 5 is formed, which leaves a rotor hub 6 with arranged thereon rotor 7 has.
• the Rotomabe 6 is seen as part of the Nacelle 2.
• the rotor hub 6 can be accommodated in a rotatably movable manner on the nacelle housing 4 by means of a first rotor shaft bearing 8 and a second rotor shaft bearing 9 .
• the rotor hub 6 is arranged on a rotor shaft 13 , the rotor shaft 13 being mounted by means of the first rotor shaft bearing 8 and the second rotor shaft bearing 9 .
• the first rotor shaft bearing 8 and the second rotor shaft bearing 9 can be designed to absorb a radial force 10 and an axial force 11 .
• the axial force 11 is due to the force of the wind.
• the radial force 10 is due to the weight of the rotor 5 and acts on the center of gravity of the rotor 5 . Since the center of gravity of the rotor 5 is outside of the first rotor shaft bearing 8, a tilting moment 12 is caused in the rotor shaft 13 by the radial force 10, which can be absorbed by the first rotor shaft bearing 8 and the two th rotor shaft bearing 9.
• the tilting moment 12 can also be caused by an uneven load on the rotor blades 7 .
• a gear 14 is formed, which is coupled to the rotor shaft 13 .
• the transmission 14 can be coupled to the rotor shaft 13 in such a way that it is also carried by the first rotor shaft bearing 8 and the second rotor shaft bearing 9 .
• a generator 15 is formed, which is coupled to the transmission 14 .
• first rotor shaft bearing 8 is arranged closer to the rotor hub 6 than the second rotor shaft bearing 9.
• Fig. 2 shows a first embodiment of the built-in nacelle 2 first rotor shaft bearing 8 and second rotor shaft bearing 9 in a longitudinal sectional view.
• the first rotor shaft bearing 8 has a first inner ring 16 and a first outer ring 17 . Between the first inner ring
• a first sliding bearing element 18 can be arranged, wel Ches for rotational sliding bearing of the first inner ring 16 relative to the first outer ring
• the first inner ring 16 can be formed directly on the rotor shaft 13 . Furthermore, it is also conceivable that the first inner ring 16 is designed as an independent component which is accommodated on the rotor shaft 13 .
• first outer ring 17 can be accommodated in a first bearing block 19 .
• first bearing block 19 is coupled to the nacelle housing 4 or, alternatively, is formed directly in the nacelle housing 4 .
• first outer ring 17 is rigidly coupled to the nacelle housing 4 and the first inner ring 16 can be rotated relative to the first outer ring 17 with respect to an axis of rotation 20 by means of the first plain bearing element 18 .
• the first plain bearing element 18 comprises a plurality of individual first plain bearing pads 21 which are distributed over the circumference between the first inner ring 16 and the first outer ring 17 .
• the individual first plain bearing pads 21 can be firmly coupled to the first inner ring 16 in the operating state and thus rotate with it relative to the first outer ring 17 .
• a first sliding surface 22 is formed on each of the individual first plain bearing pads 21 , which abuts against a first mating surface 23 of the first outer ring 17 .
• the first mating surface 23 can be arranged on an inside of the first outer ring 17 .
• the first sliding surface 22 of the first plain bearing pad 21 and the first mating surface 23 of the first outer ring 17 are designed as sliding surfaces which slide on one another when the wind turbine 1 is in operation.
• the first mating surface 23 of the first outer ring 17 is designed as a hard, wear-resistant surface, which can be formed, for example, by hardened steel.
• the first sliding surface 22 of the first plain bearing pad 21 can be formed from a plain bearing material that is soft compared to the first mating surface 23 .
• the first sliding surface 22 has a sliding coating.
• first sliding bearing pads 21 each have a first sliding surface 22 that is curved when viewed in the axial direction.
• the mean first sliding surface diameter 24 is the mean value of the diameters from the diameters of the first sliding surface 22 over the entire length of the sliding surface 22.
• the first sliding surface 22 has an innermost contact point 25 .
• the innermost contact point 25 of the first sliding surface 22 is that point of the first sliding surface 22 at which the first mating surface 23 still contacts the first sliding surface 22 and which is arranged closest to the second rotor shaft bearing 9 .
• the first sliding surface 22 of the first plain bearing pad 21 is in the form of a spherical cap.
• the first sliding surface 22 forms a first spherical cap arch 26 in longitudinal section.
• a first tangent 27 to the first sliding surface 22 in a first spherical segment arc center 28 can be arranged at a first angle 29 to the axis of rotation 20 .
• the second rotor shaft bearing 9 has a second inner ring 30 and a second outer ring 31 .
• a second sliding bearing element 32 can be arranged between the second inner ring 30 and the second outer ring 31 - 9 - which is used for the rotary sliding bearing of the second inner ring 30 relative to the second outer ring 31.
• the second inner ring 30 can be formed directly on the rotor shaft 13 . Furthermore, it is also conceivable that the second inner ring 30 is designed as an independent component which is accommodated on the rotor shaft 13 .
• the second outer ring 31 is rigidly coupled to the nacelle housing 4 and the second inner ring 30 can be rotated relative to the second outer ring 31 with respect to the axis of rotation 20 by means of the second plain bearing element 32 .
• the individual second plain bearing pads 34 can be firmly coupled to the second inner ring 30 in the operating state and thus rotate with it relative to the second outer ring 31 dre.
• the individual second plain bearing pads 34 can be firmly coupled to the second inner ring 30 in the operating state and thus rotate with it relative to the second outer ring 31 dre.
• a second sliding surface 35 is formed on each of the second sliding bearing pads 34, which abuts against a second mating surface 36 of the second outer ring 31.
• the second mating surface 36 can be arranged on an inside of the second outer ring 31 .
• the second sliding surface 35 of the second slide bearing pads 34 and the second mating surface 36 of the second outer ring 31 are designed as sliding surfaces which slide against each other during operation of the wind power plant 1 . 10
• the second mating surface 36 of the second outer ring 31 is designed as a hard, wear-resistant surface, which can be formed, for example, by hardened steel.
• the second sliding surface 35 of the second plain bearing pad 34 can be made of a plain bearing material that is soft compared to the second mating surface 36 .
• the second sliding surface 35 has a sliding coating.
• the individual second sliding bearing pads 34 each have a second sliding surface 35 that is curved when viewed in the axial direction.
• the mean second sliding surface diameter 37 is the mean value of the diameters of the diameters of the second sliding surface 35 over the entire length of the second sliding surface 35.
• the second sliding surface 35 has an innermost contact point 38 .
• the innermost contact point 38 of the second sliding surface 35 is that point of the second sliding surface 35 at which the second mating surface 36 still contacts the second sliding surface 35 and which is located next to the first rotor shaft bearing 8 .
• the second sliding surface 35 of the second plain bearing pad 34 can be in the form of a spherical cap.
• the second sliding surface 35 forms a second spherical cap 39 in longitudinal section.
• a second tangent 41 to the second sliding surface 35 in a second spherical cap center 40 can be arranged at a second angle 42 to the axis of rotation 20 .
• first tangent 27 and the second tangent 41 provision can be made for the first tangent 27 and the second tangent 41 to be arranged in a V-shape with respect to one another.
• first angle 29 is measured on the side of the rotor hub 6 .
• the second angle 42 can be measured on the side facing away from the rotomabe.
• first angle 29 and the second angle 42 are of the same size, the V-shaped arrangement resulting from the different side of the measurement. 11
• the described structure and the prestressing by means of the clamping means 43 result in an O-shaped arrangement of the first rotor shaft bearing 8 and the second rotor shaft bearing 9, as a result of which radial forces, axial forces and tilting moments can be absorbed.
• the innermost contact point 25 of the first sliding surface 22 and the innermost contact point 38 of the second sliding surface 35 are arranged at an axial distance 44 from one another.
• first inner ring 16 and the second inner ring 30 are formed as independent components.
• clamping means 43 acts directly on the second inner ring 30 .
• first sliding surface 22 and the second sliding surface 35 can be designed conically. In the longitudinal sectional view, the first sliding surface 22 and the second sliding surface 35 are shown as a straight line. As can also be seen from FIG. 3, provision can be made for the first sliding surface 22 and the second sliding surface 35 to be V-shaped in relation to one another. In particular, it can be provided that the first sliding surface 22 and the second sliding surface 35 face each other.
• clamping means 43 can be pressed directly against the second inner ring 30 or to act on the second inner ring 30 .
• All information on value ranges in the present description is to be understood in such a way that it also includes any and all sub-ranges, e.g. the information 1 to 10 is to be understood as including all sub-ranges, starting from the lower limit 1 and the upper limit 10 i.e. all sub-ranges start with a lower limit of 1 or greater and end with an upper limit of 10 or less, e.g. 1 to 1.7, or 3.2 to 8.1, or 5.5 to 10.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Life Sciences & Earth Sciences (AREA)
• Sustainable Development (AREA)
• Sustainable Energy (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Wind Motors (AREA)

Priority Applications (5)

Applications Claiming Priority (2)

Publications (1)

Family

ID=81927423

Family Applications (1)

Country Status (7)

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Families Citing this family (2)

Citations (6)

Family Cites Families (10)

• 2021
  • 2021-05-14 AT ATA50374/2021A patent/AT524591B1/de active
• 2022
  • 2022-05-12 US US18/290,337 patent/US12123403B2/en active Active
  • 2022-05-12 CN CN202280034706.2A patent/CN117295901A/zh active Pending
  • 2022-05-12 DK DK22727239.0T patent/DK4337872T3/da active
  • 2022-05-12 WO PCT/AT2022/060167 patent/WO2022236356A1/de not_active Ceased
  • 2022-05-12 JP JP2023570217A patent/JP2024517343A/ja active Pending
  • 2022-05-12 EP EP22727239.0A patent/EP4337872B1/de active Active

Patent Citations (6)

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