EP2411667A2 - Commande automatique de pas pour les éoliennes à axe horizontal - Google Patents

Commande automatique de pas pour les éoliennes à axe horizontal

Info

Publication number
EP2411667A2
EP2411667A2 EP10711259A EP10711259A EP2411667A2 EP 2411667 A2 EP2411667 A2 EP 2411667A2 EP 10711259 A EP10711259 A EP 10711259A EP 10711259 A EP10711259 A EP 10711259A EP 2411667 A2 EP2411667 A2 EP 2411667A2
Authority
EP
European Patent Office
Prior art keywords
thrust
blades
centripetal
loads
turbine
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.)
Withdrawn
Application number
EP10711259A
Other languages
German (de)
English (en)
Inventor
Ralph-Peter Bailey
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.)
KINETIC HARVEST RESEARCH LTD
Original Assignee
Kinetic Harvest 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 Kinetic Harvest Ltd filed Critical Kinetic Harvest Ltd
Publication of EP2411667A2 publication Critical patent/EP2411667A2/fr
Withdrawn legal-status Critical Current

Links

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
    • 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
    • F03D7/022—Adjusting aerodynamic properties of the blades
    • F03D7/0224—Adjusting blade pitch
    • 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
    • F03D7/022—Adjusting aerodynamic properties of the blades
    • 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
    • F03D7/04—Automatic control; Regulation
    • 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
    • F05B2260/70—Adjusting of angle of incidence or attack of rotating blades
    • F05B2260/77—Adjusting of angle of incidence or attack of rotating blades the adjusting mechanism driven or triggered by centrifugal forces
    • 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 present application pertains to a novel means by which the blade pitch angle of a wind turbine can be automatically set for optimum power output in changing wind conditions.
  • the present invention relates to a mechanism that can be employed by Horizontal Axis Wind Turbines (HAWT) to set the optimum blade pitch angle for the differing conditions they are likely to encounter in order to optimize their power yield.
  • HAWT Horizontal Axis Wind Turbines
  • a principal object of this invention is to provide a means to automatically set the blade pitch to a low TSR in order to deliver maximum torque at zero rotational speed for early turbine start up.
  • a further object of this invention is to increase the TSR as the turbine accelerates and hold it stable at the ideal continuous running condition.
  • a further object of this invention is to quickly react to gusts or transient increases in wind speed by reducing the TSR to increase the torque and hence rate of rotational acceleration.
  • a further object of this invention is to quickly react to lulls or transient decreases in wind speed by increasing the TSR to reduce the torque and hence maintain rotational momentum.
  • a further object of this invention is to react to excessive wind speed in order not to exceed the safe rpm limit by reducing the TSR in these conditions - akin to feathering the blades where they generate less drag.
  • a further object of this invention is to provide for all of the above with a self powered and relatively simple mechanism that can be built at low cost.
  • the invention proposes to utilize both the axial thrust on the rotor and the centripetal forces related to its rotational velocity to achieve an optimum solution for all conditions.
  • the basic concept is that axial thrust pushes the turbine back along its shaft causing the pitch to be increased and TSR lowered, while rpm related centripetal force pulls the turbine forward causing the TSR to be increased.
  • This overload spring acts between the centripetal forcing element and the turbine and thereby enables the turbine to move back in high winds irrespective of the amount of centripetal force being generated. It is set to a preload such that it begins to permit displacement after the known thrust generated at the rpm limit is exceeded and at a spring rate appropriate to maintain that limit as the TSR is proportionately reduced.
  • a preferred embodiment Rather than utilize the blades to generate the balancing centripetal force, in a preferred embodiment separate masses are used.
  • the advantage of decoupling the centripetal force from the blades is that blade forces could become excessively high and the increase in tip diameter as they move out radially could be a problem where the blades run in a confined duct as in a system where a diffuser is used to accelerate the wind through the turbine.
  • Masses can be arranged to fly out axially, perhaps even surrounding the blade shaft, but a preferred embodiment is for them to swing up on arms much like what occurs with a speed governor.
  • This action can be arranged to cause a roller on the mass lever to act against a cam whose profile presents a local ramp angle which gears the amount of axial balancing force generated to the optimum for any given rpm.
  • the scheme requires that the blade shaft is rotated in proportion to the axial displacement of the hub.
  • a preferred means of achieving this is by employing two rollers attached to the fixed generator shaft acting on double sided cams attached to the blade shafts.
  • the cam angle progression can again be selected to vary the gearing so the relationship need not be linear.
  • the cams are obliged to rotate as the rollers are in a fixed position with respect to the generator shaft.
  • a further embodiment uses a belt firstly attached to the fixed part of the hub, then wrapped around the blade axles attached to the axially displaceable part of the hub and then returned to the fixed part via a spring. As the blade set is displaced axially, the belts cause the blades to rotate on their shafts with the slack taken up by the spring or belt lengthened by the spring.
  • the springs act as a preload device in not just maintaining belt tension, but also in trying to bull the belt in they move the blades set such that it increases their pitch angle and becomes more feathered as would be appropriate in a start up condition. In doing so it also holds the centripetal masses in their closed position.
  • the balance point is reached at the point where the turbine torque has decreased with increasing TSR such that it can no longer accelerate. This is helped by the start up spring which provides its axial force in proportion to the axial turbine displacement that sets the TSR. As such, the balance point reached tends to increase it's TSR a little as the wind speed increases (and the spring has a relatively smaller forcing effect). This is helpful in providing more torque at lower speed to better match the characteristics of the attached generator.
  • the centripetal forces are geared by a varying ramp angle on the CAM against which they act as previously explained.
  • Fig. 1 shows a first data illustration
  • Fig. 2 shows a second second data illustration
  • Fig. 3 shows a force balance relationship
  • Fig. 4 shows a tip speed ratio relationship
  • Fig. 5 Shows two isometric views of the mechanism. The left hand view shows it in start up condition where the blades are set to provide maximum torque. The right hand view shows it in maximum rpm condition where the weights have swung out, pulling the hub forward and setting the blades suitable for a high TSR.
  • Fig. 6 Shows two top views with the upper blade system sectioned through its driving CAM.
  • the left hand view shows it in start up condition with the blade CAM at its backwards limit and where it's offset between the CAM rollers has caused it to rotate to its clockwise limit.
  • the right hand view shows the hub pulled forward, moving the CAM to its anti-clockwise limit.
  • Fig. 7 Shows a side view section through the centre of the mechanism, shown in its start up condition.
  • Fig. 8 Shows a similar side view section, but with the mechanism at its maximum rpm condition.
  • Fig. 9 Shows a similar side view section, but in its overload condition where the overload springs have compressed and allowed the hub to move back despite the high centripetal force opposing it.
  • Fig. lO Shows the embodiment where a belt is used to rotate the blades axles. In this view the belts have been pulled back by their springs causing the blades to move to a high pitch feathered position.
  • Fig. 11 Shows the same embodiment as Fig. 10 but now in a running mode at a higher rpm where the centripetal masses have swung out and pulled the blade set forward, thereby stretching the springs that hold the belts and consequently causing the belts to rotate the blade's axles.
  • the mechanism is show with its frame (1 ) comprising two profile cut sheets with lengths of tubing welded in a radial pattern to support the blade axes.
  • This embodiment supports five blades, but it can be seem that other numbers are possible.
  • the hub is pushed to the back of its shaft by the spring (2), holding in the centripetal masses (3) that swing on arms to drive the roller (4) against the CAM (5) to progressively displace the hub forward as the weights swing out as shown by (12).
  • CAM roller supports (10) retain rollers (6) which act on the blade setting CAMs (7). It can be seen that the blades (8) rotate on their axes into position (11 ) as the weights force the hub forwards.
  • the sectioned mechanism in the left hand view shows the back flange (14) that supports the CAM roller retainers (19) with their rollers (20) and (22) acting on the CAM (17) to set its degree of rotation about the blade axis.
  • the roller (23) acts against the narrow wedge plate (24) and transmits the drive torque from the frame (13) to the flange (14).
  • This device enables it to be adjusted to a degree of bearing preload in the rollers consistent with stiff control.
  • the masses (15) are in their park position.
  • the sectioned view shows the flange (28) rigidly connected to the generator shaft and the shaft extension.
  • the CAM roller retainers (32) holding the rollers e.g. (34) against the CAM (38).
  • the frame (30) includes a bore that permits it to slide along the shaft as required to achieve the force balance axial offset position.
  • the frame is held up tight against a further stepped tube (29) by high force springs (33) riding on a radial array of shafts with end stops (31) trapping one of the frame's profiled plates between it and the springs. As will be seen this constitutes the overload preload device.
  • the weight is show fully retracted by the action of the spring (37) displacing the CAM (36) and frame (29 & 30) as far back as possible causing the roller (35) to rise to its top position.
  • the sectioned view now shows the mechanism in its maximum forward position where the roller (46) in swinging upwards has pulled the CAM (48) forward, dragging the stepped tube (45) and frame (39) with it - as may be found at the rpm limit.
  • the start up preload spring (47) is now fully compressed.
  • the blade rotation has been set for maximum rpm as the CAM (42) has been rotated by the action of the rollers e.g. (40) retained by the part (43) against the flange that is part of the shaft extension (44).
  • FIG 11 The same embodiment as FIG 6 is shown, but now the blade set (58) has been forced forward by the centripetal masses (56) swinging out on their lever arms as a result of the hub's rotation.
  • the springs e.g. (52) have now been stretched effectively lengthening the belts e.g. (53) which rotate the pulleys e.g. (54) and consequently adjust the blade pitch angle in this case reducing it.

Landscapes

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

Abstract

L'invention concerne un système autoalimenté et autoréglable, permettant d'ajuster les angles des pales d'une éolienne, de sorte qu'elles aient un angle d'attaque élevé lorsqu'elles sont au repos, afin de favoriser un démarrage précoce, de déplacer leur angle de calage idéal pour un fonctionnement normal, de pouvoir répondre aux rafales et aux accalmies par des changements appropriés, les pales en drapeau permettant de limiter les tours par minute et de réduire les charges en cas de tempête. Le système équilibre les charges axiales sur la turbine contre les forces centripètes générées par des masses réagissant au nombre de tours par minute, en augmentant le pas de la pale en cas de rafales, pour augmenter le couple et donc l'accélération en rotation et en réduisant le pas de la pale pendant les accalmies, pour conserver un élan de rotation. Le système utilise des ressorts établissant la position de départ et la limite de nombre de tours par minute adaptée au mécanisme de générateur.
EP10711259A 2009-03-24 2010-03-24 Commande automatique de pas pour les éoliennes à axe horizontal Withdrawn EP2411667A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0904921A GB2471060A (en) 2009-03-24 2009-03-24 Automatic pitch control for horizontal axis wind turbines
PCT/GB2010/050500 WO2010109238A2 (fr) 2009-03-24 2010-03-24 Commande automatique de pas pour les éoliennes à axe horizontal

Publications (1)

Publication Number Publication Date
EP2411667A2 true EP2411667A2 (fr) 2012-02-01

Family

ID=40639967

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10711259A Withdrawn EP2411667A2 (fr) 2009-03-24 2010-03-24 Commande automatique de pas pour les éoliennes à axe horizontal

Country Status (5)

Country Link
US (1) US20120014794A1 (fr)
EP (1) EP2411667A2 (fr)
CN (1) CN102439294A (fr)
GB (1) GB2471060A (fr)
WO (1) WO2010109238A2 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8408867B2 (en) * 2008-01-10 2013-04-02 Jonathan C. Ricker Multi directional augmenter and diffuser
KR101330016B1 (ko) * 2013-09-30 2013-11-18 지유 주식회사 소형 풍력 발전장치의 블레이드 피치 제어장치
US9631606B2 (en) 2014-04-14 2017-04-25 General Electric Company System and method for thrust-speed control of a wind turbine
CN103982375A (zh) * 2014-05-26 2014-08-13 陈鹏 用于风力发电的动力风扇
CN104989599A (zh) * 2015-07-31 2015-10-21 陈强生 飞轮式风力发电机
US10634121B2 (en) 2017-06-15 2020-04-28 General Electric Company Variable rated speed control in partial load operation of a wind turbine
EP3418760B1 (fr) * 2017-06-22 2020-08-26 IHP GmbH - Innovations for High Performance Microelectronics / Leibniz-Institut für innovative Mikroelektronik Procédé et système de suréchantillonnage d'une forme d'onde variable avec facteur de suréchantillonnage
CN109667726B (zh) * 2017-10-17 2020-09-25 新疆金风科技股份有限公司 风力发电机风轮转速测量结构、装置及风力发电机组
CN114851247B (zh) * 2022-05-17 2024-01-12 湖北省天一智能科技有限公司 一种具有向心力结构的柔性补偿器

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US2666149A (en) * 1947-05-01 1954-01-12 Fumagalli Charles Electric generator with variable propeller and governing means therefor
GB730060A (en) * 1951-12-21 1955-05-18 Allgaier Werkzeugbau G M B H Improvements in wind power plants
US4257740A (en) * 1979-01-15 1981-03-24 Duez Wayne G Speed governing hub for windmill
US4411596A (en) * 1980-03-25 1983-10-25 Sundstrand Corporation Ram air turbine control system
FR2491556A1 (fr) * 1980-10-06 1982-04-09 Creuzet Yvon Eolienne a capteur lent adaptable aux conditions de vent
NL8104118A (nl) * 1981-09-07 1983-04-05 Frans De Hoo En Nicolaas Schuu Windmolen.
US4743163A (en) * 1985-11-22 1988-05-10 Sundstrand Corporation Ram air turbine control system
JPH04314691A (ja) * 1990-12-20 1992-11-05 Honda Motor Co Ltd プロペラの可変ピッチ機構
AU2002236014A1 (en) * 2002-02-25 2003-09-09 Iskra Wind Turbine Manufacturers Ltd. Passive speed and power regulation of a wind turbine
FR2876752B3 (fr) * 2004-10-19 2007-01-05 Michel Bourriaud Dispositif de pas variable pour eolienne a axe de rotation dans la direction du vent agissant par action combinee de la poussee du vent sur les pales et de regulateurs centrifuges
GB2436599A (en) * 2006-03-30 2007-10-03 Boost Energy Systems Ltd Wind turbine blade furling system
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Title
See references of WO2010109238A2 *

Also Published As

Publication number Publication date
WO2010109238A2 (fr) 2010-09-30
WO2010109238A3 (fr) 2011-04-28
CN102439294A (zh) 2012-05-02
GB0904921D0 (en) 2009-05-06
US20120014794A1 (en) 2012-01-19
GB2471060A (en) 2010-12-22

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