WO2013042251A1 - 再生エネルギー型発電装置及びその回転翼着脱方法 - Google Patents

再生エネルギー型発電装置及びその回転翼着脱方法 Download PDF

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Publication number
WO2013042251A1
WO2013042251A1 PCT/JP2011/071676 JP2011071676W WO2013042251A1 WO 2013042251 A1 WO2013042251 A1 WO 2013042251A1 JP 2011071676 W JP2011071676 W JP 2011071676W WO 2013042251 A1 WO2013042251 A1 WO 2013042251A1
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WIPO (PCT)
Prior art keywords
rotor
main shaft
brake
hub
hydraulic
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.)
Ceased
Application number
PCT/JP2011/071676
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
義如 天野
和久 堤
卓 一柳
拓郎 亀田
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.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to JP2012503811A priority Critical patent/JP4969712B1/ja
Priority to CN2011800043707A priority patent/CN103124844A/zh
Priority to IN3062DEN2012 priority patent/IN2012DN03062A/en
Priority to PCT/JP2011/071676 priority patent/WO2013042251A1/ja
Priority to KR1020127010775A priority patent/KR20130059309A/ko
Priority to AU2011310935A priority patent/AU2011310935A1/en
Priority to EP11810527.9A priority patent/EP2587055B1/en
Priority to EP13160517.2A priority patent/EP2650533B1/en
Priority to JP2013504997A priority patent/JP5634595B2/ja
Priority to EP11869762.2A priority patent/EP2759700B1/en
Priority to PCT/JP2011/006695 priority patent/WO2012073505A1/en
Priority to US13/390,362 priority patent/US20120285150A1/en
Priority to JP2012507512A priority patent/JP5502190B2/ja
Priority to CN2011800307298A priority patent/CN102959240A/zh
Priority to PCT/JP2011/077625 priority patent/WO2013042279A1/ja
Priority to EP11799883.1A priority patent/EP2646685B1/en
Priority to KR1020127034108A priority patent/KR20130053416A/ko
Priority to US13/358,013 priority patent/US8710693B2/en
Priority to CN2012800017730A priority patent/CN103314211A/zh
Priority to PCT/JP2012/054617 priority patent/WO2013042385A1/ja
Priority to JP2013505001A priority patent/JP5550781B2/ja
Priority to EP12801438.8A priority patent/EP2759702B1/en
Priority to JP2014504884A priority patent/JP5836478B2/ja
Priority to PCT/JP2012/004218 priority patent/WO2013042294A1/en
Priority to EP12737897.4A priority patent/EP2758661B1/en
Publication of WO2013042251A1 publication Critical patent/WO2013042251A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • 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
    • F03D7/00—Controlling wind motors 
    • F03D7/02—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor
    • F03D7/0244—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor for braking
    • 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
    • F03D13/00—Assembly, mounting or commissioning of wind motors; Arrangements specially adapted for transporting wind motor components
    • F03D13/10—Assembly of wind motors; Arrangements for erecting wind motors
    • 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
    • F03D15/00—Transmission of mechanical power
    • 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
    • F03D15/00—Transmission of mechanical power
    • F03D15/20—Gearless transmission, i.e. direct-drive
    • 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
    • F03D7/00—Controlling wind motors 
    • F03D7/02—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor
    • F03D7/0244—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor for braking
    • F03D7/0248—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor for braking by mechanical means acting on the power train
    • 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
    • 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
    • F03D80/80—Arrangement of components within nacelles or towers
    • F03D80/88—Arrangement of components within nacelles or towers of mechanical components
    • 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
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • F03D9/10—Combinations of wind motors with apparatus storing energy
    • F03D9/17—Combinations of wind motors with apparatus storing energy storing energy in pressurised fluids
    • 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
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • F03D9/20—Wind motors characterised by the driven apparatus
    • F03D9/25—Wind motors characterised by the driven apparatus the apparatus being an electrical generator
    • 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
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • F03D9/20—Wind motors characterised by the driven apparatus
    • F03D9/28—Wind motors characterised by the driven apparatus the apparatus being a pump or a compressor
    • 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
    • F16C19/24—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 radial load mainly
    • F16C19/28—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 radial load mainly with two or more rows of rollers
    • 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
    • F16C19/38—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 two or more rows of rollers
    • F16C19/383—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller 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
    • 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
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/042—Housings for rolling element bearings for rotary movement
    • 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
    • F05B2230/00—Manufacture
    • F05B2230/60—Assembly methods
    • 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
    • F05B2230/00—Manufacture
    • F05B2230/60—Assembly methods
    • F05B2230/61—Assembly methods using auxiliary equipment for lifting or holding
    • 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
    • F05B2240/50—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
    • F05B2240/60—Shafts
    • 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
    • F05B2260/31—Locking rotor in position
    • 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
    • F05B2260/40—Transmission of power
    • F05B2260/406—Transmission of power through hydraulic systems
    • 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
    • F05B2260/90—Braking
    • F05B2260/902—Braking using frictional mechanical forces
    • 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
    • Y02E10/20—Hydro energy
    • 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
    • Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient
    • 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
    • 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
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids
    • 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
    • Y02E70/00—Other energy conversion or management systems reducing GHG emissions
    • Y02E70/30—Systems combining energy storage with energy generation of non-fossil origin
    • 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
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
    • Y02P70/50—Manufacturing or production processes characterised by the final manufactured product
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49316—Impeller making
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49316—Impeller making
    • Y10T29/49318—Repairing or disassembling

Definitions

  • the present invention relates to a regenerative energy type power generating apparatus that generates power by transmitting rotational energy of a rotor to a generator via, for example, a hydraulic pump and a hydraulic motor, and a method for attaching and removing the rotor blades.
  • the renewable energy type power generation device is a power generation device that uses renewable energy such as wind, tidal current, ocean current, and river current, and examples thereof include wind power generation devices, tidal current power generation devices, ocean current power generation devices, and river current power generation devices. be able to.
  • wind power generators using wind power and renewable energy power generators including power generators using tidal currents, ocean currents, or river currents are becoming popular.
  • the kinetic energy of wind, tidal current, ocean current or river current is converted into the rotational energy of the rotor, and the rotational energy of the rotor is converted into electric power by the generator.
  • the rotational speed of the rotor is smaller than the rated rotational speed of the generator, so that it is common to provide a mechanical (gear-type) speed increaser between the rotor and the generator. .
  • the rotational speed of the rotor is increased to the rated rotational speed of the generator by the speed increaser and then input to the generator.
  • a brake mechanism (brake disc and brake caliper) is usually provided between the above speed increaser and the generator.
  • This brake mechanism is used for the purpose of braking the rotor or holding the stopped rotor so as not to move.
  • the brake disk is provided between the speed increaser and the generator because the rotating shaft (speed increaser output shaft or generator input shaft) that rotates at high speed between the speed increaser and the generator is This is because the torque is, for example, about 1/100 times lower than that of the rotary shaft (main shaft) in the preceding stage of the speed increaser.
  • Patent Document 1 discloses a technique for storing a brake disc and a brake caliper inside a casing of a generator.
  • the main shaft is rotated by a hydraulic cylinder via an adapter disk attached to a strain washer that connects the main shaft of the wind turbine generator and the speed increaser.
  • a turning device is described. This type of turning device is used when the rotor is rotated to a desired angular position, for example, for removing and attaching the rotor blades.
  • the rotating shaft rotating at a high speed between the hydraulic motor and the generator is not connected to the rotor at the preceding stage than the hydraulic transmission. Therefore, even if the brake mechanism is provided inside the generator input shaft or the generator casing as in the prior art, the brake mechanism cannot brake the rotor or hold the rotor in a stopped state so as not to move. . Therefore, the brake mechanism is directly attached to the rotor in the preceding stage than the hydraulic transmission.
  • the present invention has been made in view of the above-described circumstances, and provides a regenerative energy type power generation apparatus in which a brake mechanism is attached to a rotor in front of a hydraulic transmission and a method for attaching and removing the rotor blades while saving space. For the purpose.
  • a regenerative energy type power generator includes a rotor having a hub to which a rotor blade is attached and a main shaft coupled to the hub, a generator that receives torque from the rotor and generates electric power, and the rotor
  • the hydraulic transmission for transmitting the torque from the generator to the generator, the brake disc fixed to the rotor by co-tightening the hub and the main shaft, the brake pad being pressed against the brake disc, and the braking force applied to the rotor
  • a brake caliper that provides
  • the brake disk which has to be increased in size as compared with the conventional one, is fixed by fastening together with the hub and the main shaft, so that space can be saved. That is, when mounting a brake disk to the main shaft, it is usual to provide a brake disk mounting flange on the main shaft and fasten the brake disk to the flange. The above problem occurs. Therefore, in the above-mentioned regenerative energy type power generation device, a fastening part between the hub and the main shaft that is indispensable is used, and the brake disk is fixed to the rotor by joint fastening with the hub and the main shaft. There is no need to provide a separate space, and space can be saved.
  • the brake caliper may include a plurality of outer calipers provided on the outer peripheral side of the brake disc and a plurality of inner calipers provided on the inner peripheral side of the brake disc.
  • a brake disc is fixed to a rotor that rotates at a lower speed than the hydraulic transmission, and therefore, it is necessary to provide a plurality of brake calipers to apply a sufficient braking force to the rotor.
  • the regenerative energy power generator further includes a nacelle that houses at least the main shaft, a main shaft bearing that rotatably supports the main shaft on the nacelle side, and a bearing box that houses the main shaft bearing, and the brake disk includes: Further, at least one of the brake calipers may be attached to the bearing housing, extending from a joint fastening position with the hub and the main shaft toward the bearing housing. By extending the brake disc from the joint tightening position with the hub and the main shaft toward the bearing housing, the position where the frictional force by the brake caliper is applied can be brought close to the main shaft bearing which is the fulcrum of the main shaft.
  • the position where the frictional force by the brake caliper is applied can be brought closer to the main shaft bearing, and the structure for supporting the brake caliper can be made compact.
  • Space saving In particular, the space on the inner peripheral side of the brake disk is difficult to access the support member from the inner wall surface of the nacelle or the nacelle base plate, so it becomes a problem how to support the inner caliper. If attached, even the inner peripheral caliper can be easily supported.
  • the regenerative energy type power generator further includes a tower and a nacelle supported by the tower and accommodating at least the main shaft, the nacelle being pivotably attached to the tower, and the nacelle.
  • a nacelle cover covering the base plate, and at least one of the brake calipers may be attached to an end of the nacelle base plate on the side close to the hub.
  • the main shaft has a flange that is fastened together with the hub and the brake disc, and the brake disc is provided so as to spread outward in the radial direction of the main shaft from a joint fastening position of the flange and the hub. It may be done.
  • the brake disc can be formed in a large diameter (that is, the lever ratio is increased). Large braking force can be applied to the rotor.
  • the regenerative energy type power generator further includes a nacelle that houses at least the main shaft, and a hydraulic cylinder that has one end fixed to the nacelle and the other end attached to the brake disk, and has a stroke of the hydraulic cylinder.
  • the rotor may be rotated together with the brake disk.
  • the brake disc is usually designed to have sufficient strength so that it can receive a large reaction force when braking and stopping the rotating rotor.
  • the nacelle When the rotor is rotated together with the brake disk by the hydraulic cylinder, the nacelle includes a nacelle base plate that is pivotably attached to the tower and a cover that covers the nacelle base plate, and the hydraulic cylinder includes the brake
  • the hydraulic cylinders may be provided on both sides of the disc, and each hydraulic cylinder may be provided upright on the nacelle base plate and attached to the brake disc via a bracket. In this way, by providing hydraulic cylinders on both sides of the brake disc, a larger torque can be transmitted to the rotor via the brake disc, so that the rotor load is unbalanced when the rotor blades are attached and detached. However, the turning operation of the rotor can be easily performed. Further, by setting up the hydraulic cylinder from the nacelle base plate, the reaction force from the hydraulic cylinder can be received by the nacelle base plate.
  • the regenerative energy type power generation device further includes a lock mechanism that fixes the rotor at a desired angular position, and the brake disc has a plurality of first holes formed in a circumferential direction, and the lock mechanism includes the first It may be a lock pin inserted into any one of the one holes and the second hole provided on the nacelle side.
  • the lock pin may be a lock pin inserted into any one of the one holes and the second hole provided on the nacelle side.
  • the regenerative energy type power generator may be a wind power generator that rotates the rotor with wind as regenerative energy and inputs the torque from the rotor to the generator via the hydraulic transmission.
  • a method for attaching and detaching a rotating blade of a regenerative energy type power generator includes a rotor having a hub to which a rotating blade is attached and a main shaft connected to the hub, and generating power by inputting torque from the rotor side.
  • a hydraulic transmission that transmits the torque from the rotor to the generator, a brake disc fixed to the rotor by co-tightening the hub and the main shaft, and a brake pad against the brake disc,
  • a method of attaching and detaching a rotor blade of a regenerative energy type power generating device comprising a brake caliper that applies a braking force to the rotor, the step of rotating the rotor to a desired angular position by a hydraulic actuator, the brake disc and the brake caliper
  • the rotor at the desired angular position by A step of lifting comprises the steps of fixing the rotor in the desired angular position, in a state in which the rotor is fixed, characterized in that it comprises a step of desorption of the rotor blades relative to the hub.
  • the rotor is rotated to a desired angular position by a hydraulic actuator, and then the rotor is fixed using a brake disc fixed together with the hub and the main shaft, and a brake caliper. Is held at the desired angular position. Then, the rotor blade is attached to and detached from the hub while the rotor is fixed.
  • the brake disc fixed to the rotor is used together with the hub and the main shaft, the space can be saved, and the brake disc with a large braking force can be saved. Can be adopted. Therefore, even when the load on the rotor during unloading operation of the rotor blades is unbalanced, the rotor can be reliably held at a desired angular position, and the rotor blades can be removed and installed efficiently. .
  • the regenerative energy type power generator includes a nacelle that houses at least the main shaft, and one end of the hydraulic actuator is fixed to the nacelle side, and the other end is the brake.
  • the rotor may be rotated to the desired angular position by rotating the brake disk by the hydraulic cylinder. Accordingly, the rotor can be rotated to a desired angular position by the turning operation of the rotor using the hydraulic cylinder.
  • the rotor can be rotated even when the load of the rotor at the time of attaching / detaching the rotor blade is unbalanced.
  • the brake disc is usually designed to have sufficient strength so that it can receive a large reaction force when braking and stopping the rotating rotor. Therefore, even when turning operation is performed by inputting a large torque from the hydraulic cylinder to the rotor via the brake disc in a state where the rotor load is unbalanced, such as when removing and installing the rotor blades, the brake disc is sufficient. Can withstand.
  • the step of rotating the rotor after connecting the other end of the hydraulic cylinder to the brake disc and changing a stroke of the hydraulic cylinder, the other end of the hydraulic cylinder is disconnected from the brake disc.
  • the operation of returning the stroke of the hydraulic cylinder may be repeated to rotate the rotor intermittently.
  • the rotor can be reliably rotated to the desired angular position.
  • the rotor may be fixed by fixing a stroke of the hydraulic cylinder.
  • the specific method for fixing the stroke of the hydraulic cylinder may be, for example, mechanically latching the piston of the hydraulic cylinder so that it does not move, or by sealing the hydraulic chamber of the hydraulic cylinder so that it is in a hydraulic lock state. May be fixed.
  • the regenerative energy type power generation device includes a nacelle that houses at least the main shaft, and the brake disk has a plurality of first holes formed in the circumferential direction.
  • a lock pin may be inserted into one of the first holes of the brake disc and a second hole provided on the nacelle side to fix the rotor. Good.
  • the brake disk can be used for the purpose of fixing the rotor with the lock pin.
  • the desired angular position is defined for each of the plurality of rotor blades
  • the first hole of the brake disk and the second hole on the nacelle side are positions of the first hole and the second hole when the rotor stops at the desired angular position defined for each rotor blade. May be formed to match.
  • the desired angular position of the rotor suitable for performing the detaching operation of the plurality of rotor blades is defined for each rotor blade
  • the hydraulic transmission rotates with the main shaft to generate pressure oil, and the generator is driven by the pressure oil supplied from the hydraulic pump.
  • the hydraulic pump is driven by the pressure oil supplied from a pressure oil source, and the rotor is moved to the desired angular position using the hydraulic pump as the hydraulic actuator. It may be rotated.
  • a rotor is desired by using the hydraulic pump of the hydraulic transmission without separately providing a hydraulic actuator. It can be rotated to the angular position.
  • the regenerative energy type power generator further includes a step of attaching dummy blades to the hub before the step of rotating the rotor, and in the step of rotating the rotor, the dummy blades are attached to the hub.
  • the rotor may be rotated.
  • the dummy blades when rotating the rotor by attaching dummy blades to the hub, the dummy blades have a cylindrical member fixed to the hub and a movable weight supported inside the cylindrical member, and the dummy blade
  • the method may further comprise the step of adjusting the position of the movable weight so that a moment around the central axis of the rotor is reduced after the step of attaching the blades.
  • the rotor can be rotated to a desired angular position with a smaller torque by reducing the moment around the central axis of the rotor.
  • the fastening portion between the hub and the main shaft, which is indispensable, is used, and the brake disc is fixed to the rotor by joint fastening with the hub and the main shaft, so the flange for mounting the brake disc is omitted. , Space can be saved.
  • a wind power generator will be described as an example of a renewable energy power generator.
  • the present invention can also be applied to other renewable energy power generation devices such as tidal current power generation devices, ocean current power generation devices, and river current power generation devices.
  • FIG. 1 is a diagram illustrating a configuration example of a wind turbine generator according to the first embodiment.
  • FIG. 2 is a cross-sectional view showing the structure inside the nacelle of the wind turbine generator.
  • FIG. 3 is a diagram showing a detailed structure around the brake disc.
  • FIG. 4 is a perspective view of the main shaft and the brake disc as viewed from the hub side.
  • FIG. 5 is a diagram showing a state in which a hydraulic cylinder for rotor turning operation is attached to a brake disk.
  • the wind turbine generator 1 mainly includes a rotor 2 that rotates by receiving wind, a hydraulic transmission 4 that accelerates the rotation of the rotor 2, and a generator 6 that generates electric power.
  • the rotor 2 includes a rotor blade 2A, a hub 2B to which the rotor blade 2A is attached, and a main shaft 2C connected to the hub 2B.
  • the entire rotor 2 is rotated by the wind force received by the rotor blades 2A, and rotation is input from the main shaft 2C to the hydraulic transmission 4.
  • the main shaft 2 ⁇ / b> C of the rotor 2 is accommodated in a nacelle 8 that is rotatably supported by the tower 7.
  • the main shaft 2C is supported on the nacelle 8 side by the main shaft bearing 3 so as to be rotatable.
  • the hydraulic transmission 4 includes a hydraulic pump 20 driven by the rotation of the main shaft 2 ⁇ / b> C, a hydraulic motor 22 connected to the generator 6, a high pressure oil line 24 provided between the hydraulic pump 20 and the hydraulic motor 22, and a low pressure. It has an oil line 26.
  • the discharge side of the hydraulic pump 20 is connected to the suction side of the hydraulic motor 22 by a high-pressure oil line 24, and the suction side of the hydraulic pump 20 is connected to the discharge side of the hydraulic motor 22 by a low-pressure oil line 26.
  • the hydraulic oil (high pressure oil) discharged from the hydraulic pump 20 flows into the hydraulic motor 22 via the high pressure oil line 24 and drives the hydraulic motor 22. Thereby, electric power is generated in the generator 6 connected to the hydraulic motor 22.
  • FIG. 1 shows an example in which the hydraulic transmission 4 and the generator 6 are housed in the nacelle 8, some or all of the hydraulic transmission 4 and the generator 6 may be housed in the tower 7. .
  • the hydraulic pump 20 of the hydraulic transmission 4 may be stored in the nacelle 8, and the hydraulic motor 22 and the generator 6 may be stored in the nacelle 8.
  • the main shaft 2 ⁇ / b> C has a front part 10 located on the side close to the hub 2 ⁇ / b> B and a rear part 12 located on the side far from the hub 2 ⁇ / b> B.
  • a step 13 is provided between the front portion 10 and the rear portion 12, and the front portion 10 is formed to have a larger diameter than the rear portion 12.
  • a pair of main shaft bearings 3 (3A, 3B) for supporting the main shaft 2C is provided.
  • each bearing box 16 is connected by the connection frame 17 and the nacelle 8 from a viewpoint of improving the rigidity with respect to the bending load etc. of the rotor 2.
  • Each bearing box 16 is supported on the nacelle 8 side.
  • the nacelle 8 includes a nacelle base plate 8A that is pivotally supported by the tower 7 and a nacelle cover 8B that covers the nacelle base plate 8A
  • each bearing box 16 is supported by the nacelle base plate 8A.
  • it may be supported by the nacelle cover 8B.
  • the nacelle cover 8B is supported by the nacelle base plate 8A and the strength member (framework) of the nacelle 8.
  • the front portion 10 of the main shaft 2 ⁇ / b> C has an end on the side close to the hub 2 ⁇ / b> B protruding outward in the radial direction of the main shaft 2 ⁇ / b> C to form a flange 11.
  • the flange 11 of the front portion 10 is fastened to the hub 2B by a bolt 14.
  • the brake disc 30 for braking the rotor 2 is fastened together with the flange 11 and the hub 2B.
  • the detailed structure of the brake disc 30 will be described later.
  • a rear main shaft bearing 3B and a hydraulic pump 20 are provided in the rear portion 12 of the main shaft 2C.
  • 2 shows an example in which the hydraulic pump 20 is provided behind the main shaft bearing 3B, the hydraulic pump 20 may be disposed between the main shaft bearings 3A and 3B, or may be integrated with the main shaft bearing 3B. It is good (that is, the main shaft bearing 3B may be used as a pump bearing of the hydraulic pump 20).
  • the configuration of the hydraulic pump 20 is not particularly limited.
  • the hydraulic pump 20 is provided on the outer periphery of the rear portion 12 of the main shaft 2C, and includes a plurality of pistons 44 that move up and down by the rotation of the main shaft 2C.
  • the hydraulic pump 20 may be configured by a cylindrical member 40, a ring cam 42, a plurality of pistons 44, a casing 46, and a pump bearing 48.
  • the cylindrical member 40 is fixed to the outer periphery of the rear portion 12 of the main shaft 2C.
  • the ring cam 42 is an annular member that is fixed to the outer periphery of the cylindrical member 40, and has a wavy unevenness (cam profile) for moving the piston 44 up and down.
  • the piston 44 is provided with a plurality of rows (three rows in the example shown in FIG. 2) of a group of pistons arranged in the circumferential direction in the longitudinal direction of the main shaft 2C.
  • the plurality of pistons 44 are accommodated in the casing 46.
  • a pump bearing 48 is provided between the casing 46 and the cylindrical member 40.
  • the brake disk 30 is fastened by a bolt 14 to be fastened together with the hub 2 ⁇ / b> B and the flange 11, and is bent from the fastened portion 31 to be bent in the bearing housing 16 of the main shaft bearing 3 ⁇ / b> A.
  • An intermediate portion 32 extending toward the center, and a disc portion 33 provided at an end of the intermediate portion 32.
  • the fastened portion 31 extends in the radial direction of the main shaft 2C along the flange 11 of the main shaft 2C, and is formed in an annular shape.
  • the intermediate portion 32 extends toward the outer side in the radial direction of the main shaft 2 from the joint tightening position of the flange 11 of the front portion 10 and the hub 2B (that is, the position of the bolt 14) toward the bearing housing 16 of the main shaft bearing 3A. It extends.
  • disk portions 33 (33A, 33B) are provided on the outer peripheral side and the inner peripheral side, respectively.
  • the outer peripheral disk portion 33A extends radially outward of the main shaft 2C
  • the inner peripheral disk portion 33B extends radially inward of the main shaft 2C.
  • the intermediate portion 32 of the brake disc 30 is provided so as to spread outward in the radial direction of the main shaft 2C from the joint tightening position of the flange 11 of the main shaft 2C and the hub 2B.
  • a large braking force can be applied to the rotor 2. That is, by providing the intermediate portion 32 that extends radially outward, the position of the disk portion 33 to which a frictional force is applied by a brake caliper 34 described later is further separated from the axial center of the main shaft 2C more radially outward.
  • a large braking force can be applied to the rotor 2.
  • the disc portion 33 to which a frictional force is applied by a brake caliper 34 described later is provided.
  • the position can be brought close to the main shaft bearing 3A which is a fulcrum of the main shaft 2C. That is, the distance between the disk portion 33 and the main shaft bearing 3A in the axial direction of the main shaft 2C can be reduced. Thereby, even if the resultant force of the friction force by all the brake calipers 34 has the radial component of the main shaft 2C, the moment load acting on the main shaft 2C due to the radial component of the resultant force of the friction force is reduced. Can do.
  • the brake caliper 34 (34 ⁇ / b> A, 34 ⁇ / b> B) is provided so as to straddle the disk portion 33 (33 ⁇ / b> A, 33 ⁇ / b> B).
  • the brake caliper 34 includes a plurality of outer calipers 34A provided corresponding to the outer peripheral disk portion 33A of the brake disc 30 and a plurality of inner calipers provided corresponding to the inner disk side 33B of the brake disc 30.
  • the brake calipers 34 (the outer caliper 34A and the inner caliper 34B) on the outer peripheral side and the inner peripheral side of the brake disc 30, a sufficient braking force can be applied to the rotor 2. .
  • Each brake caliper 34 presses the brake pad 35 against the disc portion 33 (33A, 33B) of the brake disc by hydraulic pressure to apply a braking force to the rotor 2.
  • the brake caliper 34 is directly or indirectly supported by the bearing housing 16 or the nacelle base plate 8A of the front main shaft bearing 3A.
  • the outer caliper 34 ⁇ / b> A located at the upper part of the brake disk 30 is fixed to the bearing box 16 of the main shaft bearing 3 ⁇ / b> A via the support member 36, and the outer circumference located at the lower part of the brake disk 30.
  • the side caliper 34A may be directly fixed to the end portion of the nacelle base plate 8A near the hub 2B (that is, the front portion of the side wall erected on the floor of the nacelle base plate 8A).
  • all of the inner peripheral calipers 34B may be fixed directly or indirectly to the bearing housing 16 of the main shaft bearing 3A.
  • the brake caliper 34 (a part of the outer caliper 34A and the inner caliper 34B) is directly or indirectly attached to the bearing housing 16 so that the position where the frictional force by the brake caliper 34 is applied to the main shaft bearing 3A. While being able to approach, the support structure of the brake caliper 34 can be made compact. In particular, the space on the inner peripheral side of the brake disk 30 is covered by the intermediate portion 32 (see FIG. 3), and it is difficult to access the support member from the wall surface of the nacelle cover 8B or the nacelle base plate 8A. By fixing the caliper 34B to the bearing housing 16, the support structure for the inner peripheral caliper 34B can be simplified.
  • the support structure of the brake caliper 34 can be made compact by attaching the brake caliper 34 (the outer caliper 34A located at the lower part of the brake disc 30) to the end of the nacelle base plate 8A on the side close to the hub 2B.
  • a hydraulic cylinder may be attached to the brake disk 30 so that the turning operation of the rotor 2 can be performed by the hydraulic cylinder.
  • the hydraulic cylinder 50 may be attached to the brake disc 30 via a bracket 52.
  • the hydraulic cylinder 50 is erected on the nacelle base plate 8 ⁇ / b> A, one end is fixed to the nacelle base plate 8 ⁇ / b> A, and the other end is attached to the brake disc 30 via a bracket 52.
  • the bracket 52 is fastened to the brake disc 30 by using a plurality of mounting holes 54 formed over the entire circumference of the disc portion 33A on the outer peripheral side of the brake disc 30.
  • the bracket 52 is attached to a region of the outer peripheral disk portion 33A where the outer caliper 34A is not provided.
  • the hydraulic cylinder 50 is rotatably attached at a connecting portion 51 with the nacelle base plate 8A and a connecting portion 53 with the bracket 52, and the two hydraulic cylinders 50 are in accordance with the amount of rotation of the brake disc 30.
  • the connecting portions 51 and 53 are rotated about the rotation center.
  • a two-dot chain line in FIG. 5 indicates a state in which the hydraulic cylinder 50 rotates around the connecting portions 51 and 53 as the rotation center.
  • the brake disc 30 (specifically, the outer peripheral disc portion 33A) has a relatively large diameter, even when the load of the rotor 2 is unbalanced during the operation of attaching / detaching the rotor blade 2A, The rotor 2 can be easily rotated.
  • the brake disk 30 is usually designed to have a sufficient strength so that it can receive a large reaction force when braking and stopping the rotating rotor 2.
  • the brake disc 30 can withstand sufficiently.
  • the hydraulic cylinders 50 are preferably provided on both sides of the brake disc 30 as shown in FIGS.
  • each hydraulic cylinder 50 rotates the brake disc 30 by moving its pistons in opposite directions. That is, when one hydraulic cylinder 50 applies a pressing force on the upper side in the vertical direction to the brake disc 30, the other hydraulic cylinder 50 applies a pressing force on the lower side in the vertical direction to the brake disc 30. Therefore, most of the radial components of the main shaft 2C of the pressing force by each hydraulic cylinder 50 are canceled each other, and the moment load on the main shaft 2C generated due to the radial component of the main shaft 2C of the resultant force of the pressing force of the hydraulic cylinder 50 Can be reduced.
  • the outer caliper 34A needs to be provided over a wide area in the circumferential direction of the outer disk portion 33A. Therefore, it is difficult to increase the stroke amount of the hydraulic cylinder 50 because there is concern about interference between the hydraulic cylinder 50 and the bracket 52 and the outer caliper 34A. Therefore, the intermittent turning operation of the rotor 2 may be repeated using the hydraulic cylinder 50. That is, the hydraulic cylinder 50 is attached to the brake disc 30 via the bracket 52, and the rotor 2 is rotated by a predetermined angle by changing the stroke of the hydraulic cylinder 50. Thereafter, the bracket 52 is removed from the brake disc 30, the hydraulic cylinder 50 is disconnected from the brake disc 30, and the stroke of the hydraulic cylinder 50 is restored.
  • the hydraulic cylinder 50 is attached to the brake disc 30 again via the bracket 52, the stroke of the hydraulic cylinder 50 is changed, and the rotor 2 is rotated by a predetermined angle. By repeating such a series of operations, the rotor 2 can be intermittently rotated.
  • FIG. 6 is a diagram illustrating a configuration example of a rotor lock mechanism using the mounting hole 54 of the brake disk 30.
  • the lock mechanism 60 includes a lock pin 61.
  • the lock pin 61 is configured to be insertable into any one of the first holes (mounting holes) 54 formed in the brake disc 30 and the second hole 63 formed in the stationary member 62 fixed to the nacelle 8 side.
  • the stationary member 62 is fixed to the nacelle base plate 8A, the nacelle cover 8B, the bearing box 16 of the main shaft bearing 3A, and the like.
  • the brake disk 30 By inserting the lock pin 61 into the first hole (mounting hole) 54 of the brake disk 30 and the second hole 63 on the nacelle 8 side, the brake disk 30 is also used for the purpose of fixing the rotor 2 with the lock pin 61. Thus, space saving can be achieved.
  • chamfering is performed on the corner portion 64 of the front end surface of the lock pin 61 and the corner portion 65 of the opening end surface of the first hole (mounting hole) 54 of the brake disk 30,
  • the insertion may be performed smoothly.
  • the chamfering of the corner portions 64 and 65 may be C chamfering by cutting off the corners to form, for example, an inclined surface of about 45 degrees, or R chamfering for rounding the corners.
  • the operation of inserting the lock pin 61 into the first hole 54 and the second hole 63 may be automated.
  • the rotational displacement (angular position) of the rotor 2 is detected by a rotary encoder, and based on the detection result, it is determined whether or not the positions of the first hole 54 and the second hole 63 coincide with each other.
  • the lock pin 61 may be automatically inserted into the first hole 54 and the second hole 63 by an arbitrary actuator.
  • the rotary blade 2A is attached by lifting the rotary blade 2A up to the vicinity of the hub 2B with a crane and mounting the blade root of the rotary blade 2A and the hub 2B in a state where the posture of the rotary blade 2A is vertical or horizontal.
  • the rotor 2 is rotated together with the brake disk 30 to a desired angular position using the hydraulic cylinder 50 in a state where the brake by the brake disk 30 and the brake caliper 34 is released.
  • the series of operations described above attachment of the hydraulic cylinder 50 to the brake disk 30 ⁇ change in stroke of the hydraulic cylinder 50 ⁇ disengagement of the hydraulic cylinder 50 from the brake disk 30 ⁇ returning the stroke of the hydraulic cylinder 50
  • the rotor 2 may be rotated intermittently.
  • a braking force is applied to the rotor 2 using the brake disc 30 and the brake caliper 34, and the rotor 2 is held at the desired angular position.
  • hydraulic pressure is supplied to the brake caliper 34, and the brake pad 35 is pressed against the disc portion 33 of the brake disc 30 by the hydraulic pressure, thereby applying a braking force to the rotor 2 and bringing the rotor 2 to the desired angular position. Hold.
  • the lock pin 61 is inserted into the first hole (mounting hole) 54 of the brake disk 30 and the second hole 63 of the stationary member 62 to fix the rotor 2 at the desired angular position. It is immovable.
  • the first hole 54 is arranged so that the positions of the first hole (mounting hole 54) of the brake disk 30 and the second hole 63 of the stationary member 62 coincide with each other.
  • the 2nd hole 63 is formed.
  • the brake disc 30 is preferably provided with a plurality of first holes (mounting holes) 54 so that the positions of the two coincide with each other.
  • the stroke of the hydraulic cylinder 50 may be fixed for the purpose of holding or fixing the rotor 2 at the desired angular position.
  • the piston of the hydraulic cylinder 50 may be mechanically latched to be immovable, or the hydraulic chamber of the hydraulic cylinder 50 is hermetically sealed so as to be in a hydraulic lock state. It may be fixed.
  • the rotor 2A When the rotor 2 is fixed at the desired angular position, the rotor 2A is attached to and detached from the hub 2B. For example, when the rotor blade 2A is attached to the hub 2B, the rotor blade 2A is fastened to the hub 2B by fastening the blade root of the rotor blade 2A to the blade attachment hole 2D of the hub 2B with the rotor 2 fixed at the desired angular position. Attach to.
  • the wind turbine generator 1 of the present embodiment presses the brake pad 35 against the brake disc 30 fixed to the rotor 2 by joint fastening with the hub 2B and the main shaft 2C, and the disc portion 33 of the brake disc 30. And a brake caliper 34 that applies a braking force to the rotor 2.
  • the brake disc 30 is fixed to the rotor 2 by using the fastening portion between the hub 2B and the main shaft 2C, which is indispensable, and fastened together with the hub 2B and the main shaft 2C. It is not necessary to provide a mounting flange separately, and space can be saved.
  • the rotor 2A of the wind power generator 1 when the rotor 2A of the wind power generator 1 is attached / detached, the rotor 2 is rotated to a desired angular position by the hydraulic cylinder 50, and then fixed by co-tightening with the hub 2B and the main shaft 2C. Using the brake disc 30 and the brake caliper 34, the rotor 2 is held at the desired angular position. Then, with the rotor 2 fixed, the rotor blade 2A is attached to and detached from the hub 2B. As described above, since the brake disc 30 fixed to the rotor 2 by joint fastening with the hub 2B and the main shaft 2C is used, the space can be saved and it is difficult to be restricted by the space. A large brake disc 30 can be used.
  • the rotor 2 can be reliably held at a desired angular position, and the attaching / detaching operation of the rotor blade 2A can be performed efficiently. It can be carried out.
  • the wind power generator of this embodiment is the same as that of the first embodiment except that the hydraulic pump 20 is operated by a motor without using the hydraulic cylinder 50 to perform the turning operation of the rotor 2. It is the same as the device 1. Therefore, below, it demonstrates centering on a different point from 1st Embodiment.
  • FIG. 7 is a diagram illustrating a configuration example of a hydraulic circuit around the hydraulic pump of the wind turbine generator according to the present embodiment.
  • a hydraulic pump 20 having the same configuration as that of the first embodiment is attached to the main shaft 2 ⁇ / b> C of the rotor 2. That is, the ring cam 42 is attached to the outer periphery of the main shaft 2 ⁇ / b> C via the cylindrical member 40.
  • Each hydraulic chamber 45 i is connected to the high pressure oil line 24 and the low pressure oil line 26 via a high pressure valve 70 and a low pressure valve 72.
  • the high pressure valve 70 and the low pressure valve 72 are opened and closed in accordance with the movement of the ring cam 42.
  • the hydraulic oil supplied from the low pressure oil line 26 to the hydraulic chamber 45 i via the low pressure valve 72 is boosted by the piston 44 i and is transferred from the hydraulic chamber 45 i to the high pressure oil line 24 via the high pressure valve 70. It is designed to discharge.
  • the high pressure valve 70 is a check valve that allows only the flow of hydraulic oil from the hydraulic chamber 45 i to the high pressure oil line 24, and the low pressure valve 72 is a normally open solenoid valve. Although shown, the specific configurations of the high pressure valve 70 and the low pressure valve 72 are not limited to this example.
  • the low pressure oil line 26 is provided with an oil filter 73 that removes impurities in the hydraulic oil and an oil cooler 74 that cools the hydraulic oil.
  • An oil tank 80 is connected to the low pressure oil line 26 via a replenishment line 82 and a return line 88.
  • the oil tank 80 stores supplementary hydraulic fluid.
  • the hydraulic oil stored in the oil tank 80 is pumped up by a boost pump 84 provided in the replenishment line 82 and supplied to the low-pressure oil line 26.
  • the hydraulic oil supplied to the low-pressure oil line 26 has impurities removed by the oil filter 86 provided in the replenishment line 82.
  • the return line 88 between the low-pressure oil line 26 and the oil tank 80 is provided with a relief valve 89 so that the pressure in the low-pressure oil line 26 is maintained near the set pressure of the relief valve 89. Yes.
  • a bypass passage 76 that bypasses the hydraulic motor 22 is provided between the high-pressure oil line 24 and the low-pressure oil line 26.
  • the bypass passage 76 is provided with a relief valve 78 that keeps the pressure of the hydraulic oil in the high-pressure oil line 24 below a set pressure. Therefore, when the pressure of the hydraulic oil in the high-pressure oil line 24 rises to the set pressure of the relief valve 78, the relief valve 78 is automatically opened and the high-pressure oil escapes to the low-pressure oil line 26 via the bypass passage 76. It is like that.
  • the motor operation of the hydraulic pump 20 is performed separately from the normal operation of the hydraulic pump 20 (that is, the pump operation in which the hydraulic oil supplied from the low pressure oil line 26 is boosted and discharged to the high pressure oil line 24).
  • the pressure oil supply path 92 is provided.
  • the supply passage 92 of the pressure oil is provided between the oil tank 80 and the hydraulic chambers 45 1 and 45 k which low pressure oil is stored.
  • a pump 95 as a “pressure oil source” is provided upstream of the solenoid valve 93 in the supply path 92. Hydraulic oil pumped up from the oil tank 80 by the pump 95 via the solenoid valve 93 and check valve 94, it is supplied to the hydraulic chamber 45 1 and 45 k as "pressure oil".
  • FIG. 7 shows an example in which a pump 95 as a “pressure oil source” is provided separately from the boost pump 84 provided in the replenishment line 82, but the boost pump 84 is also used as a “pressure oil source”. Also good.
  • the solenoid valve 93 and the low-pressure valve 72 are controlled to open and close in synchronization with the cycle of the reciprocating motion of the piston 44. . Specifically, the solenoid valve 93 is opened and the low pressure valve 72 is closed during the period in which the piston 44 moves from the top dead center to the bottom dead center. As a result, the pressure oil from the pump (pressure oil source) 95 is supplied to the hydraulic chamber 45, the piston 44 is pushed down by the pressure oil, and the ring cam 42 rotates (motor process).
  • the hydraulic pump 20 the purpose of delicate control of the pulsation prevention and displacement D P, it is generally designed phase of reciprocating motion period of the plurality of pistons 44 i to displace each other.
  • a plurality of groups of two or more pistons 44 i having the same phase of the reciprocating motion period are provided, and even if any of the pistons 44 has a problem, it belongs to the same group as the piston 44 in which the problem has occurred.
  • the piston 44 is designed so that the pulsation can be prevented and fine control of the displacement can be maintained as the piston 44 continues to move. In the example shown in FIG.
  • the shape of the ring cam 42 is determined so that the piston 44 1 and the piston 44 k located on the opposite side of the piston 44 1 repeat reciprocating motion in the same phase.
  • the redundancy is said to be n.
  • a common solenoid valve 93 and check valve 94 are provided for the pistons 44 1 and 44 k belonging to the same group. If the common solenoid valve 93 is controlled to open and close in synchronization with the movement of the ring cam 42, the motor operation of the hydraulic pump 20 can be realized. Further, by sharing the solenoid valve 93 and the check valve 94 corresponding to the pistons 44 1 and 44 k , the number of valves (93, 94) can be reduced.
  • the pressure oil supply path 92 is actually connected to the other hydraulic chambers 45.
  • pressure oil is supplied from the pump 95 to the hydraulic chamber 45 through the hydraulic supply passage 92, and the main shaft 2 ⁇ / b> C (rotor 2) is supplied through the ring cam 42.
  • Rotate to the desired angular position That is, pressure oil is supplied to the hydraulic pump 20 from the pump 95 as a “pressure oil source”, and the hydraulic pump 20 is driven by the pressure oil to rotate the rotor 2 to a desired angular position.
  • the angular position of the rotor 2 may be detected by the rotary encoder 29, and the opening / closing control of the solenoid valve 93 and the low pressure valve 72 may be performed by the valve control unit based on the detection result.
  • the time for which the hydraulic pump 20 performs the motor operation may be adjusted based on the deviation between the desired angular position of the rotor 2 and the angular position detected by the rotary encoder 29.
  • the lock pin 61 is inserted into the first hole (mounting hole) 54 of the brake disk 30 and the second hole 63 of the stationary member 62 to fix the rotor 2 at the desired angular position. It is immovable. At this time, it is determined from the detection result of the rotary encoder 29 whether or not the positions of the first hole (mounting hole) 54 and the second hole 63 are matched, and the positions of the first hole 54 and the second hole 63 are matched. If the determination result is obtained, the lock pin 61 may be automatically inserted into the first hole 54 and the second hole 63.
  • the high pressure valve 70 and the low pressure valve 72 of the hydraulic pump 20 are kept closed, and the hydraulic oil is sealed in the hydraulic chamber 45. By doing so, it may be in a hydraulic lock state.
  • the rotor 2A When the rotor 2 is fixed at the desired angular position, the rotor 2A is attached to and detached from the hub 2B. For example, when the rotor blade 2A is attached to the hub 2B, the rotor blade 2A is fastened to the hub 2B by fastening the blade root of the rotor blade 2A to the blade attachment hole 2D of the hub 2B with the rotor 2 fixed at the desired angular position. Attach to.
  • the hydraulic oil is supplied from the pump (pressure oil source) 95 to the hydraulic pump 20 and the hydraulic pump 20 is driven by the hydraulic oil, a hydraulic actuator for rotating the rotor 2 is separately provided. Without using the hydraulic pump 20 of the hydraulic transmission 4, the rotor 2 can be rotated to a desired angular position.
  • the turning operation of the rotor 2 is performed by the motor operation of the hydraulic cylinder 50 or the hydraulic pump 20 has been described.
  • the rotor 2 is rotated with a small torque by using dummy blades during the turning operation. You may be able to.
  • FIG. 8 is a diagram showing a configuration example of a dummy wing used during the turning operation.
  • FIG. 9 is a diagram illustrating a procedure for performing the mounting operation of the rotary blade using the dummy blade.
  • FIG. 10 is a diagram showing a procedure for performing the operation of removing the rotating blades using the dummy blades.
  • the dummy blade 100 includes a cylindrical member 102 attached to the hub 2B, a weight 104 accommodated in the cylindrical member 102, and a weight position adjusting mechanism that adjusts the position of the weight 104 in the cylindrical member 102. 106.
  • the base part of the cylindrical member 102 is fastened to the blade mounting hole 2D of the hub 2B by a bolt 103.
  • the number of the bolts 103 may be smaller than the number of bolts used when the rotary blade 2A is fastened to the blade mounting hole 2D of the hub 2B from the viewpoint of simplifying the attaching / detaching operation of the dummy blade 100.
  • the dummy blade 100 is not used when the wind turbine generator is normally operated. Therefore, a large centrifugal force caused by the rotation of the rotor 2 is applied to the fastening portion between the dummy blade 100 and the hub 2B. There is no need to receive it. Therefore, the number of bolts 103 is relatively small.
  • the cylindrical member 102 be lighter than the weight 104 from the viewpoint of increasing the adjustment margin of the center of gravity position of the dummy blade 100 by changing the position of the weight 104.
  • the cylindrical member 102 may be made lighter than the weight 104 by forming the weight 104 from steel and forming the cylindrical member 102 from FRP.
  • the weight position adjusting mechanism 106 includes a rope 107 connected to both ends of the weight 104 and a winder 108 that winds the rope 107. Accordingly, the position of the weight 104 can be adjusted by winding the rope 107 by the winder 108.
  • a tensioner (not shown) for applying tension to the rope 107 is provided to prevent the rope 107 from loosening.
  • the winder 108 can be operated remotely. Accordingly, the center of gravity of the dummy blade 100 can be adjusted by operating the winder 108 while the worker is on the ground or the nacelle while the dummy blade 100 is attached to the hub 2B.
  • FIGS. 9 (a) to 9 (k) The procedure for attaching the rotary blade 2A to the hub 2B using the dummy blade 100 having the above-described configuration is as shown in FIGS. 9 (a) to 9 (k).
  • the reference numeral 100S is assigned to the dummy wing when the weight 104 exists at the position closest to the hub 2B by the weight position adjusting mechanism 106.
  • the reference numeral 100L is assigned to the dummy wing when the weight 104 is located far from the hub 2B by the weight position adjusting mechanism 106.
  • the dummy blade 100S is mounted in one blade mounting hole 2D of the hub 2B (see FIG. 9A), and the rotor 2 is rotated 120 degrees by the motor operation of the hydraulic cylinder 50 or the hydraulic pump 20, and the rotor is rotated by the lock mechanism 60. 2 is fixed (see FIG. 9B), and the dummy blade 100S is mounted in another blade mounting hole 2D of the hub 2B (see FIG. 9C). Then, the rotor 2 is rotated 120 degrees by the motor operation of the hydraulic cylinder 50 or the hydraulic pump 20, and the rotor 2 is fixed by the lock mechanism 60 (see FIG. 9D), and the blade mounting hole 2D remaining at the end of the hub 2B is inserted. The rotor 2A is attached (see FIG. 9 (e)).
  • the weight 104 is moved farther from the hub 2B by the weight position adjusting mechanism 106 to reduce the moment around the central axis of the rotor 2 (see FIG. 9F). At this time, it is preferable to move the weight 104 to such a position that the moment about the central axis of the rotor 2 becomes substantially zero.
  • the turning operation of the rotor 2 in the next step is performed by adjusting the position of the weight 104 by the weight position adjusting mechanism 106 so that the moment around the central axis of the rotor 2 is reduced (see FIG. 9G). Can be easily performed.
  • the rotor 2 is rotated 120 degrees by the motor operation of the hydraulic cylinder 50 or the hydraulic pump 20, the rotor 2 is fixed by the lock mechanism 60, and the one dummy blade 100L is removed from the hub 2B (see FIG. 9G). . Then, another rotating blade 2A is attached to the hub 2B (see FIG. 9 (h)).
  • the rotor 2 is rotated 120 degrees by the motor operation of the hydraulic cylinder 50 or the hydraulic pump 20, and the rotor 2 is fixed by the lock mechanism 60 (see FIG. 9 (i)), and the dummy blade 100L is removed from the hub 2B (see FIG. 9 (j)), and attach the rotor blade 2A to the hub 2B (see FIG. 9 (k)).
  • the dummy blade 100L reduces the load imbalance (moment about the center axis of the rotor 2) of the rotor 2 when the rotor blade 2A is attached to the hub 2B. It can be rotated to an angular position. That is, the turning operation of the rotor 2 in the steps shown in FIGS. 9G and 9I can be easily performed.
  • FIGS. 10 (a) to 10 (j) The procedure for removing the rotating blade 2A from the hub 2B using the dummy blade 100 having the above-described configuration is as shown in FIGS. 10 (a) to 10 (j). That is, first, one rotary blade 2A is removed from the hub 2B (see FIG. 10A), and a dummy blade 100L is attached instead (see FIG. 10B). In the dummy blade 100L, the position of the weight 104 is adjusted in advance by the weight position adjusting mechanism 106 so that the moment around the central axis of the rotor 2 is reduced. Therefore, the turning operation of the rotor 2 in the next step (see FIG. 10C) can be easily performed.
  • the rotor 2 After the dummy blade 100L is attached to the hub 2B, the rotor 2 is rotated 120 degrees by the motor operation of the hydraulic cylinder 50 or the hydraulic pump 20, the rotor 2 is fixed by the lock mechanism 60, and another rotor blade 2A is removed from the hub 2B. (See FIG. 10 (c)). Then, after attaching the dummy blades 100L to the rotor 2 (see FIG. 10D), the rotor 2 is rotated 120 degrees by the motor operation of the hydraulic cylinder 50 or the hydraulic pump 20, and the rotor 2 is fixed by the lock mechanism 60. The last remaining rotary blade 2A is removed from the hub 2B (see FIG. 10E).
  • the position of the weight 104 is moved closer to the hub 2B by the weight position adjusting mechanism 106 (see FIG. 10F), and the center of gravity position of the dummy blade is brought closer to the hub 2B side (see FIG. 10G). .
  • the rotor 2 is rotated 120 degrees by the motor operation of the hydraulic cylinder 50 or the hydraulic pump 20, the rotor 2 is fixed by the lock mechanism 60, and the dummy blade 100S is removed from the hub 2B (see FIG. 10H).
  • the rotor 2 is rotated 120 degrees by the motor operation of the hydraulic cylinder 50 or the hydraulic pump 20, and the rotor 2 is fixed by the lock mechanism 60 (see FIG. 10 (i)), and the last remaining dummy blade 100S is attached to the hub 2B. (See FIG. 10 (j)).
  • the “desired angular position” suitable for the attachment / detachment operation of each rotor blade 2 ⁇ / b> A indicates that the rotor attachment hole 2 ⁇ / b> D where the rotor blade 2 ⁇ / b> A is attached / detached faces downward in the vertical direction.
  • the example of the angular position has been described. That is, in the above-described example, the attachment / detachment of the rotary blade 2A is performed when the blade attachment hole 2D to be worked is directed downward in the vertical direction.
  • the “desired angular position” suitable for the attachment / detachment operation of each rotor blade 2A is not limited to the above example, and the “desired angular position” suitable for the attachment / detachment operation of each rotor blade 2A is the attachment / detachment of the rotor blade 2A.
  • the angular position of the rotor 2 may be such that the blade attachment hole 2D in which the above is performed faces in the horizontal direction. In this case, the attachment / detachment of the rotary blade 2A may be performed when the blade attachment hole 2D to be worked is oriented in the horizontal direction.

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PCT/JP2011/071676 2010-11-30 2011-09-22 再生エネルギー型発電装置及びその回転翼着脱方法 Ceased WO2013042251A1 (ja)

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JP2012503811A JP4969712B1 (ja) 2011-09-22 2011-09-22 再生エネルギー型発電装置及びその回転翼着脱方法
CN2011800043707A CN103124844A (zh) 2011-09-22 2011-09-22 再生能源型发电装置及其旋转叶片装卸方法
IN3062DEN2012 IN2012DN03062A (enExample) 2011-09-22 2011-09-22
PCT/JP2011/071676 WO2013042251A1 (ja) 2011-09-22 2011-09-22 再生エネルギー型発電装置及びその回転翼着脱方法
KR1020127010775A KR20130059309A (ko) 2011-09-22 2011-09-22 재생 에너지형 발전 장치 및 그 회전 블레이드 착탈 방법
AU2011310935A AU2011310935A1 (en) 2011-09-22 2011-09-22 Power generating apparatus of renewable energy type and method of attaching and detaching blade
EP11810527.9A EP2587055B1 (en) 2011-09-22 2011-09-22 Regenerated-energy power generation device and rotary wing attachment/detachment method therefor
EP13160517.2A EP2650533B1 (en) 2010-11-30 2011-11-30 Power generating apparatus of renewable energy type
JP2013504997A JP5634595B2 (ja) 2011-09-22 2011-11-30 再生エネルギー型発電装置及びそのロータ固定方法
EP11869762.2A EP2759700B1 (en) 2011-09-22 2011-11-30 Renewable energy-type electric power generation device and rotor affixation method for same
PCT/JP2011/006695 WO2012073505A1 (en) 2010-11-30 2011-11-30 Power generating apparatus of renewable energy type
US13/390,362 US20120285150A1 (en) 2010-11-30 2011-11-30 Power generating apparatus of renewable energy type
JP2012507512A JP5502190B2 (ja) 2010-11-30 2011-11-30 再生エネルギー型発電装置
CN2011800307298A CN102959240A (zh) 2010-11-30 2011-11-30 可再生能源型发电装置
PCT/JP2011/077625 WO2013042279A1 (ja) 2011-09-22 2011-11-30 再生エネルギー型発電装置及びそのロータ固定方法
EP11799883.1A EP2646685B1 (en) 2010-11-30 2011-11-30 Power generating apparatus of renewable energy type
KR1020127034108A KR20130053416A (ko) 2010-11-30 2011-11-30 재생 에너지형 발전 장치
US13/358,013 US8710693B2 (en) 2011-09-22 2012-01-25 Power generating apparatus of renewable energy type and method of attaching and detaching blade
CN2012800017730A CN103314211A (zh) 2011-09-22 2012-02-15 风力发电机和用于风力发电机的部件搬运方法
PCT/JP2012/054617 WO2013042385A1 (ja) 2011-09-22 2012-02-24 再生エネルギー型発電装置及び該再生エネルギー型発電装置の操作方法
JP2013505001A JP5550781B2 (ja) 2011-09-22 2012-02-24 再生エネルギー型発電装置及び該再生エネルギー型発電装置の操作方法
EP12801438.8A EP2759702B1 (en) 2011-09-22 2012-02-24 Renewable energy-type electric power generation device and method for operating renewable energy-type electric power generation device
JP2014504884A JP5836478B2 (ja) 2011-09-22 2012-06-29 再生エネルギー型発電装置
PCT/JP2012/004218 WO2013042294A1 (en) 2011-09-22 2012-06-29 A power generating apparatus of renewable energy type
EP12737897.4A EP2758661B1 (en) 2011-09-22 2012-06-29 A power generating apparatus of renewable energy type

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PCT/JP2012/004218 Ceased WO2013042294A1 (en) 2011-09-22 2012-06-29 A power generating apparatus of renewable energy type

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EP (2) EP2587055B1 (enExample)
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CN (2) CN103124844A (enExample)
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