WO2011107208A2 - Procédé pour freiner une éolienne et dispositif de freinage permettant de mettre en oeuvre ce procédé - Google Patents

Procédé pour freiner une éolienne et dispositif de freinage permettant de mettre en oeuvre ce procédé Download PDF

Info

Publication number
WO2011107208A2
WO2011107208A2 PCT/EP2011/000605 EP2011000605W WO2011107208A2 WO 2011107208 A2 WO2011107208 A2 WO 2011107208A2 EP 2011000605 W EP2011000605 W EP 2011000605W WO 2011107208 A2 WO2011107208 A2 WO 2011107208A2
Authority
WO
WIPO (PCT)
Prior art keywords
braking
braking torque
drive train
deceleration
rotor
Prior art date
Application number
PCT/EP2011/000605
Other languages
German (de)
English (en)
Other versions
WO2011107208A3 (fr
Inventor
Christian Eitner
Friedmar Dresig
Boris Buchtala
Original Assignee
Robert Bosch Gmbh
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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2011107208A2 publication Critical patent/WO2011107208A2/fr
Publication of WO2011107208A3 publication Critical patent/WO2011107208A3/fr

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
    • F03D7/0244—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
    • 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
    • F05B2270/00—Control
    • F05B2270/10—Purpose of the control system
    • F05B2270/107—Purpose of the control system to cope with emergencies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the invention relates to a method for braking a wind energy plant and a braking device for carrying out the method.
  • First rotor blades of a rotor are rotated in their flag positions.
  • a deceleration control unit in a control unit of the wind energy plant activates electrically controllable control valves which apply braking torques to a brake disk of the deceleration device of a drive train.
  • a braking device for braking a rotor of a wind energy plant is known.
  • the brake device has at least one hydraulically actuable brake cylinder whose brake pressure can be regulated by means of a continuously adjustable control valve.
  • the braking device has a drain line from this directional valve to a tank, wherein a check valve is arranged, which allows a leak-free shut-off of the pressure medium flow path to the tank.
  • slow braking slows down such that it comes close to a theoretically possible aperiodic limit case by gently braking each overshoot is suppressed by the braking force is metered so that a steep torque increase, as would be required in emergency situations to decelerate a rotor of a wind turbine in a very short time, with such a braking device is not feasible.
  • the transmission gear Due to the torsional vibrations occurring in such emergency braking, the transmission gear is designed to three to four times the operating load in conventional wind turbines, resulting in wind turbines disadvantageous to considerable weights in the generator nacelle.
  • Notabbremsclar the rotor blades are moved into a flag or feathered position, ie taken out of the wind and a mechanical brake is activated on the fast-rotating transmission output shaft.
  • the emergency braking may serve to prevent the rotor from spinning in the event of a generator failure or in a critical operating state in which, for example, a sensor system required for the control has failed.
  • the entire emergency stop pre-cooking must be completed within a few seconds, so that the well-known from the prior art gentle deceleration method is unsuitable.
  • the mechanical brake is abruptly applied, the above-mentioned torsional overload in the drive train, which is a multiple of the braking torque, occurs. conditions and leads to a load on the tower due to the braking torque from the inertial forces, which can result in destruction of the wind turbine.
  • the powertrain in large wind turbines consists of the slowly rotating shaft, which is directly coupled to the hub and the rotor, the gearbox and a coupled to the generator fast rotating output shaft of the transmission.
  • a mechanical braking device which is usually designed as a disc brake, wherein a static braking torque acts with the aid of the brake shoes on the disc brake and brakes the rotor shaft via the transmission.
  • the brake shoes can be closed hydraulically or pneumatically and by appropriate springs, an open position of the brake shoes and the braking device can be ensured in normal operation.
  • the drive train from the rotor to the output shaft of the transmission gear is a vibratory system whose lowest natural frequency is in the range of 2 Hz to 3.
  • the object of the invention is to avoid a torsion overload, such as occurs when inserting the disc brake emergency shutdown by exploiting the vibration characteristics of the drive train.
  • a torsion overload such as occurs when inserting the disc brake emergency shutdown by exploiting the vibration characteristics of the drive train.
  • a method for braking a wind energy plant and a braking device for carrying out the method is provided.
  • Rotor blades of a rotor are first rotated into a flag position and activated a braking unit in a control unit of the wind turbine.
  • the deceleration control unit controls electrically controllable control valves in such a way that braking torques are applied to a brake disc of the deceleration device of a drive train with stepwise increase of the brake elements in at least two brake stages.
  • This method has over the known method with a gentle increase in the braking torque has the advantage that the stepwise increased braking torque on the drive unit so affects that the rotor comes to a standstill in a few seconds.
  • the gradual increase of the braking torque also has the advantage that overshoot, as occurs in a full braking is significantly reduced because preferably in the first stage, only half the braking torque is applied and only in a second stage, the full braking torque is effective ,
  • the overshoot can be further contained, with at first one third of the maximum permissible braking torque acting on the brake disk and thus on the drive train and two thirds of the maximum permissible braking torque being applied in a second stage and finally, only in a third stage, the full braking torque is achieved, so that a torsional load for the drive train from a kinetostatic and a dynamic see composite.
  • the vibration component which characterizes the overshoot can be influenced by a corresponding control by means of electrically controllable valves.
  • This method is based on the consideration that the torsional moment of the residual vibration is composed of a static component M, which may be due to the magnitude of the total braking torque, and a dynamic residual vibration T, which is the
  • the dynamic residual vibration T can be determined analytically and is a function of the size and direction of the intended braking torque stages and the activation times, which decide the phase position of the vibration.
  • the number of brake torque stages can be denoted by i, the time of their engagement with tj, their magnitude by ⁇ , and the relevant natural angular frequency by ⁇ 0 .
  • This results in the dynamic residual vibration to: where r, ⁇ 0 • t l the phase position and bM t the i ' te brake torque level of a total of i
  • Each individual brake torque stage causes an excitation of the torsional vibrations, the total vibration resulting from the superimposition of the individual vibrations.
  • the superposition of the harmonic oscillation whose common frequency corresponds to the relevant lowest natural frequency of the drive train ⁇ 0 , can be graphically illustrated by means of a phasor diagram, as shown in FIG. 2; in the complex number plane.
  • the pointer of the resulting oscillation results as a vector addition of the partial oscillations and the resulting residual oscillation has the same frequency as the partial oscillations.
  • the resulting residual vibration is the zero vector, ie the individual vectors will form a closed polygon or an n-edge, as shown in FIG. 3 for three stages.
  • the braking process itself is subdivided according to the invention into two or more staggered braking stages and the braking stages are coordinated in time such that the resulting dynamic loads cancel out simultaneously, as stated above.
  • the natural frequency spectrum of the drive train must be determined either by means of an approximation calculation, or by a sensor, for example by a strain gauge on the rotor shaft. be grasped.
  • the detection of the natural frequency is advantageous, especially as the natural frequencies can change over time due to manufacturing tolerances and wear.
  • a possible alternative to the gradual setting of the braking torque is that the braking torque is ramped up via a ramp, wherein the startup time approximately 0.5 seconds (seconds) and thus the approximate period of the relevant lowest driveline natural vibration corresponds.
  • t is the response time of, for example, the hydraulic system and t p is the period of the relevant drive train vibration.
  • the hydraulically or pneumatically controlled braking system may preferably be implemented with electronically controlled switching valves. However, if high-frequency braking requirements of> 10 Hz are required, it is advantageous to use servo valves.
  • the Abbrems Kunststoffech for a gradual application of a braking torque with a table of values, which was previously determined based on the mechanical and in particular elastic data of the components of the drive train. This takes into account that the permissible torsional torques of the drive train from the rotor to the gearbox are not exceeded.
  • the time duration (.DELTA. ⁇ ) of the stepwise increasing the braking torque is set depending on a lowest natural frequency (f e ) of the drive train of the Abbrems askaji the time duration (.DELTA. ⁇ ) of the stepwise increasing the braking torque is set.
  • This process principle can also be used when starting up the wind power plant, whereby load torques of a generator are increased stepwise, so that the wind energy plant is not started up under full generator load.
  • This method principle can also be used for releasing a braking device.
  • Another aspect of the invention relates to a braking device of a wind turbine with a drive train of rotor, rotor shaft and transmission gear.
  • the braking device has at least one brake disk with brake shoes.
  • a deceleration control unit is activated in a control unit of the wind energy plant with electrically controllable control valves in a deceleration case. This takes place in such a way that the control unit, which cooperates with electrically controllable control valves, a stepwise increase of a braking torque for the
  • Brake disc controls depending on a permissible torque load capacity of the drive train.
  • Such a device has the advantage over conventional devices that no smooth braking is provided with a high timing, but that with this device, a rapid deceleration of a wind turbine can be performed without overloading the drive train and other equipment components.
  • the required electrically controllable valves can be either hydraulic control valves or pneumatic control valves.
  • FIG. 1 shows a schematic diagram of a wind turbine with braking device according to an embodiment of the invention.
  • FIG. 2 shows a vector diagram with two vectors in FIG
  • FIG. 2B shows the extinction of the residual oscillations within a natural frequency period of the drive train.
  • FIG. 3 shows a vector diagram with three vectors in FIG
  • FIG. 3B shows the extinction of the residual oscillations within a natural frequency period.
  • Figure 4 shows the increase of the braking torque when applying the same in a single stage and comparatively in two stages.
  • Figure 5 shows the course of the torsional moment when applying a braking torque in a single stage and comparatively in two stages.
  • Figure 6 shows in a further scale the time course of the torsional moment in two-stage application of the braking torque and after releasing a braking device.
  • Figure 1 shows a schematic diagram of a stationary wind turbine 1 with braking device 3 according to an embodiment of the invention.
  • the wind turbine 1 converts mechanical energy of a rotor 15 via mechanical components and a generator 16 into electrical energy, which by means of a frequency converter 17, for example, to a
  • the rotational frequency of the rotor 15 in a frequency range of a few tenths Hertz is translated via a transmission gear 13, which is arranged in a nacelle 19 together with the downstream generator 16 and the frequency converter 17 to a much higher rotational frequency.
  • the transmission gear 13 can thereby achieve rotational frequencies of a transmission output shaft 20 between a few 10 Hz and a few 100 Hz and thus drive the generator 16.
  • the transmission output shaft 20 may have a significantly smaller diameter and thus a lower area moment of inertia than the rotor shaft 14.
  • a braking device 3 with a brake disk 7 on the transmission output shaft 20 can be dimensioned significantly smaller than if such a braking device is arranged in the region of the rotor shaft 14.
  • the transmission shafts and gears of the transmission gear 13 must be dimensioned accordingly in order to transmit the braking torques acting on the brake disk 7 via the brake shoes 10 and 11 of the braking device 3. In this case, a maximum permissible torsional moment must not be exceeded neither for the transmission shafts nor for the rotor shaft 14.
  • a control unit 9 which applies the braking torques under stepwise increase over the brake shoes 10 and 1 1 on the brake disc 7.
  • a critical value such as 20 revolutions per minute
  • a deceleration process is initiated.
  • the rotational speed of the rotor 15 or of the rotor shaft 14m can be signaled to a control unit 9 via a rotational speed sensor 21.
  • the control unit 9 has a Abbrems Kunststoffmaschine 8, which in turn via electrically controllable valves 6 and a hydraulic line 22, the brake shoes 10 and 1 1 with gradual increase in the braking torque of the hub 7 and ' thus the drive train 2 gradually decelerates while the rotor blades 4 of the rotor 15 are adjusted to a rotated in the direction of arrow B flag position.
  • the angular velocity with which the adjustment of the rotor blades 4 is possible is at high-performance wind turbines 1 with correspondingly large rotor blades 4 at about 15 ° per second, so that starting from an operating position of 15 °, the 90 ° feathering position is reached after 5 s (seconds).
  • the application of the full braking torque takes place in a significantly shorter period of time ⁇ t when the natural vibration behavior of the drive train is utilized during the deceleration process.
  • the braking process must be initiated so quickly and quickly to prevent in emergency situations, such as the failure of the generator, to prevent the above-mentioned critical rotor shaft speed is exceeded, for example, 20 revolutions per minute, so that despite a shortened period At no increase and thus no Overload due to torsional moments occurs.
  • Figure 2 illustrates in Figure 2A shows a vector diagram with two vectors ⁇ and AM 2, the th as dynamic residual vibration in a two-step increase of the braking torque occurring, as already discussed in the introduction.
  • FIG. 3 shows in FIG. 3A a phasor diagram with three vectors AM 1 AM 2 and AM 3 , which occur as dynamic residual oscillations in the case of a three-stage increase in the braking torque and form a triangle as vector polygon.
  • FIG. 3B the extinction of the residual oscillations within a natural frequency period with the three torque stages AM, AM 2 and AM 3 is shown.
  • Figure 4 shows the time increase of the braking torque M when applying the braking torque in a single stage and comparatively in two stages.
  • the dashed line te curve the increase of the braking torque M when applying the same in a single stage and the solid curve comparatively shows the timing of application of the braking torque M in two stages, taking into account the natural frequency period of the drive train.
  • FIG. 5 shows the curve of the torsional moment when a braking torque M shown in FIG. 4 is applied.
  • the torsional moment load of the rotor shaft becomes again with a single-stage application of the braking torque with the dashed curve, and the torsional moment load with the application of a braking torque in two stages with the solid curve shown.
  • This diagram assumes that the emergency occurs at 20 seconds and the full braking torque is effective within a half natural frequency period of the powertrain.
  • Figure 6 shows in a further scale the time course of the torsional moment in two-stage application of the braking torque and after release of the braking device as soon as the rotor and the rotor shaft have come to a standstill.
  • this simulation again initially assumes an operating condition in which loaded with more than 600 kilonewtonmeter drive train and the generator fails after about 20 s on the timeline and the single-stage application of the braking torque and the two-stage application of the braking torque shortly thereafter use about a quarter of a second.
  • Figure 6 shows that the dynamic load at one-stage deceleration is significantly higher when the dashed curve is compared with the solid curve.
  • the solid curve shows the case, if with a two-stage increase of

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)
  • Wind Motors (AREA)

Abstract

La présente invention concerne un procédé pour freiner une éolienne (1) et un dispositif de freinage (3) permettant de mettre en oeuvre ce procédé. Selon l'invention, des pales (4) d'un rotor (15) sont d'abord tournées dans une position de girouette (5), puis une unité de commande de freinage (8) située dans un appareil de commande (9) de l'éolienne (1) est activée et des vannes de commande (6) à commande électrique sont commandées pour appliquer les couples de freinage à un disque de freinage (7) du dispositif de freinage d'une chaîne cinématique, tout en augmentant par palier les couples de freinage, avec au moins deux paliers.
PCT/EP2011/000605 2010-03-02 2011-02-09 Procédé pour freiner une éolienne et dispositif de freinage permettant de mettre en oeuvre ce procédé WO2011107208A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010009857.4 2010-03-02
DE102010009857A DE102010009857A1 (de) 2010-03-02 2010-03-02 Verfahren zum Abbremsen einer Windenergieanlage und Abbremsvorrichtung zur Durchführung des Verfahrens

Publications (2)

Publication Number Publication Date
WO2011107208A2 true WO2011107208A2 (fr) 2011-09-09
WO2011107208A3 WO2011107208A3 (fr) 2012-03-08

Family

ID=44502783

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2011/000605 WO2011107208A2 (fr) 2010-03-02 2011-02-09 Procédé pour freiner une éolienne et dispositif de freinage permettant de mettre en oeuvre ce procédé

Country Status (2)

Country Link
DE (1) DE102010009857A1 (fr)
WO (1) WO2011107208A2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5566609B2 (ja) * 2009-01-05 2014-08-06 三菱重工業株式会社 風力発電装置及び風力発電装置の制御方法
US20180320661A1 (en) * 2017-05-03 2018-11-08 General Electric Company Compact Multi-Disk Rotor Brake System for a Wind Turbine

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10153798C2 (de) * 2001-11-05 2003-07-31 Norbert Hennchen Verfahren und Vorrichtung zur Verzögerung eines Rotors einer Windkraftanlage
DE10320580A1 (de) * 2003-05-07 2004-11-25 Bosch Rexroth Ag Bremseinrichtung für eine Windenergieanlage mit einem die Windenergie in eine Drehbewegung umsetzenden Rotor und Verfahren zum Betrieb einer derartigen Bremseinrichtung
DE102004057072A1 (de) 2004-11-25 2006-06-01 Basf Ag Verwendung von Übergangsmetall-Carbenkomplexen in organischen Licht-emittierenden Dioden (OLEDs)
DE102006060323A1 (de) * 2006-12-20 2008-06-26 Nordex Energy Gmbh Verfahren zum Betreiben einer Windenergieanlage bei plötzlichen Spannungsänderungen im Netz
DE102007002136B4 (de) * 2007-01-10 2010-02-18 Nordex Energy Gmbh Windenergieanlage mit einer hydraulisch betätigten Rotorbremse und Verfahren zur hydraulischen Steuerung einer Rotorbremse

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Also Published As

Publication number Publication date
DE102010009857A1 (de) 2011-09-08
WO2011107208A3 (fr) 2012-03-08

Similar Documents

Publication Publication Date Title
EP2101058B1 (fr) Méthode et dispositif pour tourner un composant d'une éolienne
EP2449258B1 (fr) Engrenage différentiel destiné à une installation de production d'énergie et procédé de fonctionnement
EP1286049B1 (fr) Eolienne
DE102006029640B4 (de) Windenergieanlage mit einem Maschinenhaus
EP1029176B1 (fr) Installation eolienne
DE102009009017B4 (de) Bremssystem für eine Windturbine
EP1659286A1 (fr) Vireur pour axe de générateur entraîné par une éolienne
EP2479428B1 (fr) Eolienne avec un dispositif de freinage et procédé de freinage ainsi que l'utilisation du dispositif de freinage
EP2859222B1 (fr) Installation de production d'énergie, en particulier éolienne
EP2929176B2 (fr) Dispositif d'entraînement en rotation destiné à une éolienne et procédé servant à faire tourner l'arbre de rotor d'une éolienne
DE202012009167U1 (de) Kran
DE60305478T2 (de) Vorrichtung zur einstellung einer rotorschaufel einer windenergieturbine
EP2389509B1 (fr) Installation de production d'energie stationnaire dotee d'un dispositif de freinage
DE102008004948A1 (de) Verfahren und Vorrichtung zum Drehen eines Maschinenhauses einer Windenergieanlage
DE102005038243B4 (de) Bremsanlage für eine Windkraftanlage
AT515934B1 (de) Antriebsstrang einer Energiegewinnungsanlage
WO2011107208A2 (fr) Procédé pour freiner une éolienne et dispositif de freinage permettant de mettre en oeuvre ce procédé
DE10153798C2 (de) Verfahren und Vorrichtung zur Verzögerung eines Rotors einer Windkraftanlage
DE102004027992B4 (de) Windenergieanlage mit einem Azimutsystem
EP3404256A1 (fr) Dispositif d'ajustement des pales de rotor d'une installation génératrice d'énergie à flux
DE102017000435A1 (de) Verfahren zum Drehen des Rotors einer Windenergieanlage
DE102007042182A1 (de) Windenergieanlage sowie Verfahren zum Betreiben einer Windenergieanlage
WO2015082114A1 (fr) Dispositif de freinage d'une éolienne
WO2016042068A1 (fr) Système de positionnement, éolienne et procédé d'orientation et/ou d'asservissement d'une nacelle technique

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11703154

Country of ref document: EP

Kind code of ref document: A2

122 Ep: pct application non-entry in european phase

Ref document number: 11703154

Country of ref document: EP

Kind code of ref document: A2