US20130195654A1 - Device and Method for Reducing Loads - Google Patents

Device and Method for Reducing Loads Download PDF

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Publication number
US20130195654A1
US20130195654A1 US13/581,990 US201113581990A US2013195654A1 US 20130195654 A1 US20130195654 A1 US 20130195654A1 US 201113581990 A US201113581990 A US 201113581990A US 2013195654 A1 US2013195654 A1 US 2013195654A1
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US
United States
Prior art keywords
drivetrain
torque
damping
loads
wind 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.)
Abandoned
Application number
US13/581,990
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English (en)
Inventor
Guenter Berger
Stefan Zimmermann
Joachim Breidert
Boris Buchtala
Bernd Schnurr
Sebastian Schmidt
Volker Knoblauch
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.)
Robert Bosch GmbH
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
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KNOBLAUCH, VOLKER, BUCHTALA, BORIS, BERGER, GUENTER, BREIDERT, JOACHIM, SCHMIDT, SEBASTIAN, SCHNURR, BERND, FUERST, HOLGER, ZIMMERMANN, STEFAN
Publication of US20130195654A1 publication Critical patent/US20130195654A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D7/00—Rotors with blades adjustable in operation; Control thereof
    • 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
    • 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
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/022—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using dampers and springs in combination
    • 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
    • F05B2270/109—Purpose of the control system to prolong engine life
    • F05B2270/1095—Purpose of the control system to prolong engine life by limiting mechanical stresses
    • 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
    • F05B2270/30—Control parameters, e.g. input parameters
    • F05B2270/334—Vibration measurements
    • 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 invention relates to a device and a method for reducing loads, in particular torsional vibrations as well as static and dynamic flexural torques, in the drivetrain of a wind turbine generator system.
  • Drivetrains comprising components such as for example gear units, clutches and connecting elements (shafts), are important constituent parts of various electrical power generating systems, such as for example wind turbine generator systems, hydroelectric installations, etc.
  • the drivetrain performs the task of establishing a mechanical connection between a drive unit (for example a rotor of a wind turbine generator system) and a driven unit (for example a corresponding generator), via which power is transmitted through a rotational movement.
  • Drivetrain components such as gear units serve the purpose of transforming the rotational speed and the torque at the drive unit to values that correspond to the operating range of the generator. Clutches are used as and when required for a disconnection between the drive unit and the driven unit and shafts establish the mechanical connection between the components involved. Further components, such as mechanical brakes or the like, may also be integrated in the drivetrain.
  • the components involved cannot be produced with any rigidity that may be desired, but have a finite rigidity, they may be induced to undergo natural vibrations. This may be caused, for example, by an non-constant input power (in the case of wind turbine generator systems for example due to wind surges or wind turbulences) or by outside disturbances. Vibrations of other origin may also increase the loads in the drivetrain, in the case of a wind turbine generator system for example tower vibrations or vibrations caused by the meshing engagements of a gear unit.
  • DE 1 993 07 51 A1 discloses a method for reducing vibrations of components in a wind turbine generator system in which bearings of an elastomeric material that has a damping angle of at least 12° and a spring stiffness chosen such that the natural frequency of the vibrating components is less than 50 Hz are used in the system.
  • a disadvantage of this is that respectively pre-known elastomeric materials must be used for the damping of specific vibrations and that adaptation to variable vibrations, for example to fluctuating vibrational amplitudes, is not possible.
  • the present invention provides a device and a method for reducing loads, in particular torsional vibrations as well as static and dynamic additional loads, in the drivetrain of a wind turbine generator system, with the features of the independent patent claims.
  • Advantageous refinements are the subject of the subclaims and of the description which follows.
  • the proposed measures allow a significant reduction of torque vibrations or torsional vibrations and loads in the drivetrain, in particular the gear unit, of wind turbine generator systems to be brought about.
  • a reduction of vibrations and loads is particularly advantageous on account of the exposed arrangement, the possible occurrence of wind surges, the periodically fluctuating loading of the rotor (reduction in wind speed immediately in front of the tower/in the wake of the tower when the tower is passed by rotor blade) as well as possible loads due to misalignment of one or more components.
  • the proposed measures make active damping of a mechanical vibration or loading possible in a drivetrain by activatable damping means.
  • a torque or a force for vibration damping or load reduction is generated by the activatable damping means.
  • the use of a suitable sensor system in particular using acceleration sensors based on the Ferraris principle, but also for example force, rotational speed, rotational angle, position and/or torque sensors and a closed-loop and/or open-loop control technique made to match, allows particularly rapid, adaptive vibration damping and load reduction to be brought about.
  • a suitable actuator system or adjustable, variable damping, as known per se, may be used for example here.
  • the actuators advantageously bring about a rotation of the drivetrain or of the corresponding gear unit and/or lead to a prescribed damping sequence of a rotational movement.
  • a slight rotational movement by a few degrees about the axis of rotation in particular in conjunction with suitable speed-transforming transmissions, can bring about significant damping of torsional vibrations.
  • raising or lowering of the gear unit may be brought about by the actuator system.
  • the moving or adjusting of at least one actuator or a combination of a number of actuators advantageously leads here to an equalizing of loads.
  • the latter may be compensated both by periodic moving (in order for example to equalize loads from the reduction in wind speed immediately in front of the tower) and by the permanent adjustment (loads due to misalignment of system components). Also in the case of this approach to a solution, significant damping of additional loads can be brought about even by very small adjusting movements.
  • damping of a rotational movement or of other loads is brought about by damping means, that is to say for example by corresponding actuators or springs, an adjusting torque resulting from a load torque or corresponding thereto being generated.
  • the corresponding adjusting torque may be generated by controlled moving or adjusting of at least one damper or by a combination of the damping means described here.
  • the damping movements can be set by suitable open-loop or closed-loop control means.
  • damping devices proposed according to the invention with the associated closed-loop and/or open-loop control technique may be advantageously integrated in torque supports of the drivetrain, that is to say supports or fastenings for diverting a torque, preferably on a gear unit housing.
  • a reduction of vibrations and loads in the drivetrain can be brought about by the measures according to the invention.
  • the mechanical loading of wind turbine generator systems is reduced, whereby the longevity of such systems is improved significantly.
  • a reduction of vibrations also has the effect in particular of improving the output power of a generator of the wind turbine generator system, since otherwise variances in speed would have to be corrected in the generator.
  • the vibrations may be detected here by way of measuring acceleration on the drivetrain, preferably at different positions of the drivetrain, and/or by speed sensors. In the case of speed sensors, it may be advisable to derive the speed for determining the acceleration.
  • the misalignment can likewise be detected at the points concerned by corresponding position sensors.
  • Parallel models as disclosed for example in EP 0 473 914 B1
  • control engineering observers with variables that occur, in particular torque, being calculated from the sensor variables with the aid of models
  • a path adaptation which takes particularities and deviations from the theoretical model into consideration, may also be advantageously provided as part of the closed-loop control. Digital and/or analog transmission of an output sensor signal may be used for the closed-loop control, visualization, open-loop control and/or switching.
  • the device according to the invention can be used with particular advantage as part of an emergency shutdown procedure, in order thereby to significantly reduce vibrations that occur.
  • damping system may also be performed using a multiplicity of sensors, for example acceleration, force, rotational speed, rotational angle, position and/or torque sensors, either on their own or in combination.
  • sensors for example acceleration, force, rotational speed, rotational angle, position and/or torque sensors, either on their own or in combination.
  • Suitable actuators comprise electrodynamic, piezoelectric, hydraulic (cylinder, membrane) and pneumatic actuators, which may for example also be realized using electroactive polymers, shape-memory actuators or electro- or magneto-rheological fluids.
  • devices that can be used as adjustable spring elements include those that are disclosed in EP 1 566 543 A1. Hydraulically pretensioned elastomer spring elements for supporting a gear unit on its torque supports are provided here. These elastomer spring elements are connected via hydraulic lines. For damping a torque of a gear unit, a throttling of the fluid exchange of the elastomer spring elements may be performed. In a corresponding way, spring elements such as those known from EP 2 003 362 A2 may be used.
  • actuators may be provided at bearing points of torque supports, it being possible for example to use a controlled oil and/or air bubble in the rubber.
  • a number of actuators may be used, in particular connected in series or in parallel, for different frequency ranges, optionally also using different types of these actuators.
  • an accumulator such as for instance a hydraulic accumulator, a storage battery, a double-layer capacitor, in the form of superconducting coils, flywheels and/or other inertial mass systems.
  • an actuator for feeding the network, so that an intercepted vibration can also be used for power generation.
  • the invention is schematically represented in the drawing on the basis of an exemplary embodiment and is described in detail below with reference to the drawing.
  • FIG. 1 shows a schematic cross-sectional view of a drivetrain of a wind turbine generator system with a device according to a particularly preferred embodiment of the invention.
  • FIG. 2 shows a schematic longitudinal sectional view of a drivetrain of a wind turbine generator system with a device according to a particularly preferred embodiment of the invention.
  • FIG. 3 shows a graph illustrating a reduction of vibrations according to a particularly preferred embodiment of the invention.
  • FIGS. 1 and 2 A transverse sectional view and a longitudinal sectional view of a drivetrain of a wind turbine generator system with a device for reducing loads according to a preferred embodiment of the invention are respectively represented in FIGS. 1 and 2 .
  • FIGS. 1 and 2 are explained together, the cross-sectional view being denoted overall by 100 and the longitudinal sectional view being denoted overall by 200 .
  • the drivetrain shown in FIGS. 1 and 2 is substantially made up of a main shaft 10 , a gear unit 20 and a generator shaft 30 .
  • the gear unit 20 may be, for example, a three-stage gear unit that is conventionally used in wind turbine generator systems.
  • the main shaft 10 is frictionally connected to a rotor, for example a vane rotor R.
  • the gear unit 20 is enclosed by a gear unit housing 21 .
  • the generator shaft 30 is connected to a generator 40 via a clutch 31 .
  • FIG. 2 additionally shows a main bearing 90 , in which the main shaft 10 is mounted.
  • Torque supports 22 are provided for fixing or supporting the gear unit housing 21 .
  • the drivetrain 10 to 30 is mounted as a whole on a machine carrier 60 .
  • the mounting itself may be configured for example as elastomer mounting 24 , with two bearing bushes 24 a and 24 b respectively for each torque support 22 .
  • Damping systems denoted overall by 25 are respectively provided between the machine carrier 60 and the torque supports 22 .
  • the damping systems 25 may have a series of different damping devices, one actuator respectively for each bearing bush 25 a and 25 b being represented by way of example within FIG. 2 .
  • the damping devices 25 are adjustable dampers. The control of such dampers is performed on the basis of a control device that is not represented in detail but is schematically indicated in FIGS. 1 and 2 by 70 . The control is performed with allowance for a measured-value output of one or more sensors 80 and 82 .
  • the sensors 80 detect a torque fluctuation, for example due to a change in acceleration, in the drivetrain 10 to 30 .
  • a torque fluctuation for example due to a change in acceleration, in the drivetrain 10 to 30 .
  • an angular offset or a deviation from the ideal alignment of the shafts is detected, for example laser-optically.
  • the control device 70 controls at least one of the provided damping systems 25 in such a way that an adjusting torque is generated and a torque fluctuation, or torsional flexural torque, is thereby minimized.
  • the adjusting torque is brought about by a rotation or by the raising or lowering of the gear unit 20 or gear unit housing 21 .
  • Dynamic loads that occur when the rotor blades pass the tower during their rotation can be reduced for example by the parallel moving of the damping systems 24 a and/or 24 b shown in FIG. 2 .
  • the exact periodic damping sequence, and consequently the moving cycle of the damping means depends on the number of rotor blades and their rotational speed, and is consequently dependent on the wind turbine generator system that is respectively under consideration.
  • the damping system 25 b on the right in FIG. 2 may, for example, be moved downward or the damping system 25 a on the left in FIG. 2 may be moved upward.
  • the respective opposite damping systems, which in FIG. 2 are concealed, are thereby likewise moved in a corresponding way.
  • a torsional torque 310 without damping and a torsional torque 320 after damping are represented in the form of a diagram 300 , in the form of a torque M on the y axis 302 against a time t of 5 s on the x axis 301 .
  • a torsional torque vibration is significantly reduced by the damping behavior according to the preferred embodiment as compared with the undamped state.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Wind Motors (AREA)
US13/581,990 2010-03-02 2011-02-09 Device and Method for Reducing Loads Abandoned US20130195654A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010009863A DE102010009863A1 (de) 2010-03-02 2010-03-02 Einrichtung und Verfahren zur Reduzierung von Lasten
DE102010009863.9 2010-03-02
PCT/EP2011/000606 WO2011107209A2 (de) 2010-03-02 2011-02-09 Einrichtung und verfahren zur reduzierung von lasten

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US20130195654A1 true US20130195654A1 (en) 2013-08-01

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US13/581,990 Abandoned US20130195654A1 (en) 2010-03-02 2011-02-09 Device and Method for Reducing Loads

Country Status (5)

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US (1) US20130195654A1 (de)
EP (1) EP2542777A2 (de)
CN (1) CN102770664A (de)
DE (1) DE102010009863A1 (de)
WO (1) WO2011107209A2 (de)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120146331A1 (en) * 2010-12-08 2012-06-14 Per Egedal Method for reducing vibrations of a wind turbine and control system for reducing vibrations
JP2013181445A (ja) * 2012-03-01 2013-09-12 Sumitomo Heavy Ind Ltd 風力発電装置
JP2016023694A (ja) * 2014-07-18 2016-02-08 シンフォニアテクノロジー株式会社 制振システム及び車両
US9866160B2 (en) 2015-01-04 2018-01-09 General Electric Company Power conversion system and controlling method thereof and wind turbine power generation system
US20180283353A1 (en) * 2017-03-30 2018-10-04 Senvion Gmbh Wind turbine and method for operating a wind turbine
US10294924B2 (en) 2014-01-28 2019-05-21 Wobben Properties Gmbh Wind turbine having a fiber winding
US10677087B2 (en) * 2018-05-11 2020-06-09 General Electric Company Support structure for geared turbomachine
CN112483312A (zh) * 2020-12-03 2021-03-12 重庆大学 一种基于冗余分组的海上风电场安全控制方法
US12467435B2 (en) 2021-09-10 2025-11-11 Zf Friedrichshafen Ag Spring-mounted gear mechanism housing
US12553414B2 (en) 2022-05-17 2026-02-17 Zf Friedrichshafen Ag Spring-mounted gearbox housing

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JP5878089B2 (ja) * 2012-06-28 2016-03-08 住友重機械工業株式会社 モニタリング方法およびモニタリング装置
JP6099185B2 (ja) * 2012-06-28 2017-03-22 住友重機械工業株式会社 モニタリング方法およびモニタリング装置
DK3063851T3 (da) 2013-10-31 2022-02-28 Gen Electric System og fremgangsmåde til styring af vindkraftgenereringssystemer
DK178642B9 (en) * 2015-03-16 2016-10-24 Envision Energy Denmark Aps Wind turbine comprising a torque dampening unit
CN117307330A (zh) * 2022-06-17 2023-12-29 通用电气公司 带有弹簧阻尼系统的旋转翼型件

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US20090230681A1 (en) * 2008-03-14 2009-09-17 Scholte-Wassink Hartmut Model based wind turbine drive train vibration damper

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US6644590B2 (en) * 2000-09-15 2003-11-11 General Dynamics Advanced Information Systems, Inc. Active system and method for vibration and noise reduction
US20090230681A1 (en) * 2008-03-14 2009-09-17 Scholte-Wassink Hartmut Model based wind turbine drive train vibration damper

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8779617B2 (en) * 2010-12-08 2014-07-15 Siemens Aktiengesellschaft Method for reducing vibrations of a wind turbine and control system for reducing vibrations
US9261080B2 (en) 2010-12-08 2016-02-16 Siemens Aktiengesellschaft Method for reducing vibrations of a wind turbine and control system for reducing vibrations
US20120146331A1 (en) * 2010-12-08 2012-06-14 Per Egedal Method for reducing vibrations of a wind turbine and control system for reducing vibrations
JP2013181445A (ja) * 2012-03-01 2013-09-12 Sumitomo Heavy Ind Ltd 風力発電装置
US10294924B2 (en) 2014-01-28 2019-05-21 Wobben Properties Gmbh Wind turbine having a fiber winding
JP2016023694A (ja) * 2014-07-18 2016-02-08 シンフォニアテクノロジー株式会社 制振システム及び車両
US9866160B2 (en) 2015-01-04 2018-01-09 General Electric Company Power conversion system and controlling method thereof and wind turbine power generation system
US20180283353A1 (en) * 2017-03-30 2018-10-04 Senvion Gmbh Wind turbine and method for operating a wind turbine
US10669991B2 (en) * 2017-03-30 2020-06-02 Senvion Gmbh Wind turbine and method for operating a wind turbine
US10677087B2 (en) * 2018-05-11 2020-06-09 General Electric Company Support structure for geared turbomachine
CN112483312A (zh) * 2020-12-03 2021-03-12 重庆大学 一种基于冗余分组的海上风电场安全控制方法
US12467435B2 (en) 2021-09-10 2025-11-11 Zf Friedrichshafen Ag Spring-mounted gear mechanism housing
US12553414B2 (en) 2022-05-17 2026-02-17 Zf Friedrichshafen Ag Spring-mounted gearbox housing

Also Published As

Publication number Publication date
EP2542777A2 (de) 2013-01-09
WO2011107209A3 (de) 2012-03-15
CN102770664A (zh) 2012-11-07
WO2011107209A2 (de) 2011-09-09
DE102010009863A1 (de) 2011-09-08

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Owner name: ROBERT BOSCH GMBH, GERMANY

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