EP3542053A1 - Éolienne comprenant un système de freinage ainsi que procédé de fonctionnement de cette éolienne - Google Patents

Éolienne comprenant un système de freinage ainsi que procédé de fonctionnement de cette éolienne

Info

Publication number
EP3542053A1
EP3542053A1 EP17797950.7A EP17797950A EP3542053A1 EP 3542053 A1 EP3542053 A1 EP 3542053A1 EP 17797950 A EP17797950 A EP 17797950A EP 3542053 A1 EP3542053 A1 EP 3542053A1
Authority
EP
European Patent Office
Prior art keywords
braking device
switching element
hydraulic
controller
rotor
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Withdrawn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
EP17797950.7A
Other languages
German (de)
English (en)
Inventor
Sören Bilges
Eckart Hopp
Karsten Warfen
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.)
Siemens Gamesa Renewable Energy Service GmbH
Original Assignee
Senvion 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 Senvion GmbH filed Critical Senvion GmbH
Publication of EP3542053A1 publication Critical patent/EP3542053A1/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Withdrawn legal-status Critical Current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
    • F03D7/0244—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
    • 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
    • F03D7/0264—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor for stopping; controlling in emergency situations
    • 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
    • F03D7/0272—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor by measures acting on the electrical generator
    • 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
    • F05B2260/845—Redundancy
    • 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
    • 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
    • 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
    • F05B2270/303—Temperature
    • 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
    • F05B2270/303—Temperature
    • F05B2270/3032—Temperature excessive temperatures, e.g. caused by overheating
    • 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
    • F05B2270/50—Control logic embodiment by
    • F05B2270/506—Control logic embodiment by hydraulic means, e.g. hydraulic valves within a hydraulic circuit
    • 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 wind energy plant with a rotor and a braking device, wherein the braking device comprises a mechanical braking device which is mechanically coupled to the rotor, and wherein the braking device at least one electrical and / or hydraulic switching element for activation and / or deactivation of the braking device.
  • the invention relates to a method for operating a wind energy plant with a rotor and a braking device, wherein the braking device comprises a mechanical braking device, which is mechanically coupled to the rotor, and wherein the braking device is a controller and at least one electrical and / or hydraulic switching element for activating and / or deactivating the braking device, wherein the switching element is designed to be redundant and / or interference-proof.
  • Wind turbines are often set up so that their rotor is braked at high loads.
  • the braking of the rotor is initiated for example by the operation control of the wind turbine.
  • a scenario in which such a deceleration operation is performed occurs when a fault occurs in the internal or external electrical system of the wind turbine concurrently with a failure of the external supply network and an extreme year-long breeze.
  • wind turbines which are dimensioned for low-wind locations, experience in such a scenario high bending loads in the supporting structure, for example the tower. These loads can be crucial for the dimensioning of the support structure. This is especially true for specifically soft tower gondola systems.
  • the rotor is braked by moving the rotor blades via the rotor blade drives (pitch drives) into the so-called 90 ° or flag position.
  • the rotor blades brake the rotor aerodynamically.
  • a mechanical brake is used. This is often one or more disc brakes mounted on the rotor shaft. Likewise, such mechanical brakes on the fast output shaft attack the transmission of the wind turbine.
  • an overspeed of the wind turbine is detected.
  • the rotor of the wind energy plant is shut down with the assistance of the mechanical brake. During this process, the rotor blades are moved at high speed in the direction of the 90 ° position, at the same time in the range of the rated speed or at higher speed, the mechanical brake is activated and remains in continuous engagement until the rotor stops.
  • Specify braking device and a method for operating a wind turbine with a more efficient use of the mechanical braking device should be possible and at the same time the design effort for the mechanical braking device should be kept as low as possible.
  • a wind energy plant with a rotor and a braking device
  • the braking device comprises a mechanical braking device which is mechanically coupled to the rotor, and wherein the braking device at least one electrical and / or hydraulic switching element for activating and / or deactivation the braking device
  • the wind turbine is formed by the fact that the switching element is designed redundant and / or interference-proof
  • a controller is arranged, which is adapted to receive an interference signal and in response to the received interference signal, the switching element and thereby the braking device to activate, taking the control is further adapted to disable the braking device by means of the switching element before the rotor of the wind turbine comes to a standstill.
  • the electrical and / or hydraulic shifting element is in particular an electric-hydraulic shifting element.
  • it is an electrically switchable solenoid valve.
  • the electro-hydraulic switching element is also set up in particular for activating and deactivating the braking device.
  • the term "mechanically coupled” means that the braking device is directly or indirectly mechanically connected to the rotor, for example, in a direct connection, the braking device is mounted on the rotor shaft
  • the brake device is mounted on or connected to the fast output shaft of the transmission.
  • a "mechanical braking device” is understood to mean a mechanically acting brake device or brake which converts kinetic energy into frictional heat.
  • the mechanical brake device is a disc brake or a drum brake.
  • a disc brake is used.
  • the term "fail-safe” designates an embodiment of the hydraulic switching element in the sense of a fail-safe arrangement, in other words, the hydraulic switching element is designed to be redundant and / or fail-safe, ie a hydraulic switching element , which fails in a safe state, which means in particular that in the case of a normal component failure, the system assumes a safe state.
  • an energetic or thermal overloading of the mechanical rotor brake system is avoided. This is mainly the case as a temporary activation of the mechanical rotor braking system and no sustained braking until Standstill of the rotor takes place. This is particularly advantageous for large wind turbines with large rotor diameters of, for example, over 100 meters.
  • the mechanical and design effort to avoid the thermal overload of the mechanical rotor braking system increases namely with increasing braked torques considerably. Mechanical braking systems for large wind turbines are therefore a significant cost factor.
  • the wind turbine according to aspects of the invention is set up in such a way that the mechanical braking device is triggered and / or operated or can be operated in a pulsed manner. It has been found that the mechanical braking device is capable of effecting efficient speed and thrust reduction, even if it is activated only for a limited period of time. The time-limited braking process actually contributes to the reduction of the total load of the wind energy plant, while at the same time the design effort for the mechanical brake is kept low. It has been found that already positive effects on the extreme loads of the wind turbine, so reducing these extreme loads, occur when the brake device is activated at the beginning of braking only for a relatively short time interval in the order of seconds.
  • the design of the wind turbine according to aspects of the invention particularly advantageous because the mechanical braking device is set up for a limited time braking of the rotor, which allows an economical construction and economical operation of the braking device, for example, in view of the wear occurring , At the same time a significant reduction of the extreme loads of the wind turbine is achieved.
  • the fail-safe switching element is a hydraulic switching element which is open when de-energized.
  • the hydraulic switching element is open when a fluidic connection between an input and an output of the switching element is released.
  • the hydraulic switching element is for example a valve, in particular a normally open solenoid valve.
  • the redundant design of the hydraulic switching elements is effected, for example, by being fluidly integrated in parallel in a hydraulic circuit.
  • the hydraulic switching element is integrated in particular in a hydraulic supply circuit for supplying the braking device.
  • the hydraulic supply circuit In the hydraulic supply circuit there is a working pressure.
  • the hydraulic fluid is thus to operate and supply the brake device under pressure.
  • the hydraulic supply circuit is further designed in particular such that at a pressure drop within the supply circuit, wherein the hydraulic fluid emptied, for example in a reservoir, the braking effect of the braking device is lower until it is finally canceled.
  • the hydraulic switching element is integrated into the hydraulic supply circuit so that an open hydraulic switching element causes such a pressure drop in the supply circuit and thus opening or deactivating the braking device.
  • the hydraulic switching element is designed redundant. This technical feature relates in particular to the functionality of the deactivation of the brake device. This also means in particular that the hydraulic switching elements provide a redundant fluidic connection between the braking device and the reservoir and thus cause a safe pressure drop in the supply circuit.
  • a solenoid valve of the mechanical brake device this means, for example, that in case of failure of the electrical control of the solenoid valve, the failure of the control device, a breakage of an electrical or hydraulic line, the burning of the solenoid coil, the demagnetization of a valve installed in the permanent magnet or similar failures th the solenoid valve opens and the braking device is deactivated, so that a secure state is taken.
  • Such an embodiment of the hydraulic switching element is particularly advantageous since, for example, in the event of a power failure, the effect of the
  • Braking device is canceled. If, in such a case, the braking device remained permanently activated, it would constitute a potential source of fire, since there would be the risk of thermal overloading of the braking device in such a state. This is advantageous excluded.
  • the hydraulic see switching element which is open in the de-energized state, helps to improve the reliability of the wind turbine.
  • the brake device is a hydraulically operated brake device and the brake device comprises a hydraulic supply circuit for supplying the brake device with a hydraulic fluid, wherein the hydraulic supply circuit comprises at least a first and a hydraulically parallel thereto connected second hy metallic switching element, which form a redundant design of the switching element.
  • the hydraulic supply circuit connects the brake device to a hydraulic supply source and to a storage container, wherein the hydraulic supply circuit comprises at least a first fluidic path and a second fluidic path parallel thereto between the braking device and the storage container, and wherein the first hydraulic switching element is integrated in the first path and the second hydraulic switching element in the second path.
  • the hydraulic supply source is, for example, a hydraulic pump which removes hydraulic fluid from the storage container and under
  • Pressurized hydraulic fluid adds to the supply circuit.
  • the hydraulic pump is combined with a pressure accumulator.
  • a "fluidic path" in the context of the present description a hydraulic connection line or a portion of such a hydraulic connection line. It is not necessary to have exclusive use of the connection line or a section of the connection line. It is thus possible, for example, for the first and the second fluidic path to extend at least in sections along the same hydraulic connecting line.
  • first and the second path each provide a direct connection between the braking device and the storage container.
  • a direct connection means that in the fluidic
  • the redundant design of the switching element ensures that even in unlikely total failure of the first hydraulic switching element (for example, by jamming movable parts, obstruction of a channel by foreign bodies or sabotage) of existing in the hydraulic supply circuit pressure via the second hydraulic switching element at least can be partially broken down.
  • the braking device is thus configured to reduce the voltage applied to the brake device pressure of the working fluid in the direction of the storage container by a flow of the working fluid through the second switching element.
  • the second solenoid valve which is open in the de-energized state, falls into this open state, and the hydraulic fluid flows from the brake device in the direction of the supply container via the second solenoid valve.
  • the brake device opens and an example used disc brake is not permanently activated. This reduces the risk of fire in the wind turbine, which could potentially be caused by a permanently activated braking device.
  • the above embodiments thus further increase the reliability of the wind turbine. In addition, the transmission is relieved.
  • the controller is adapted to Disable braking device by means of the switching element after a predetermined time interval.
  • This time interval begins with the activation of the braking device and ends with the deactivation of the braking device.
  • the time interval is in particular between 1 second and 10 seconds. It is likewise provided that the interval is between 3 seconds and 9 seconds, and in particular between 4 seconds and 6 seconds.
  • the wind energy plant is further developed in that the control comprises a supply-independent shutdown element which is adapted to activate or keep active the switching element for the duration of a predetermined time interval and to deactivate it after the predetermined time interval has elapsed ,
  • a "supply-independent switch-off element” is to be understood as an element which operates electrically autonomously, in other words, the switch-off element operates without mains supply, ie, without power supply, it is able to apply the switching element for braking for a limited time close or to keep closed and reopen or release after the predetermined time interval,
  • a buffer module for example, a capacitor is provided, which supplies the switching element.
  • the exemplary capacitor discharges in the event of a power failure when the braking device is activated via the electrical resistance of the switching element. If the discharge process has progressed so far that the required
  • the wind energy installation comprises a shutdown device which generates the interference signal which receives the control 5 tion.
  • the shutdown device is for example a part of the operation control of the wind energy plant.
  • the wind turbine is further developed in that the controller is further configured to control a general torque such that upon activation and / or deactivation of the brake device, a torque fluctuation in the drive train of the wind turbine caused by this process is reduced. This also applies, for example, to the case when fault-free mains supply is detected.
  • Time-dependent braking device such that the sum of the generator torque and the braking torque applied by the mechanical braking device is always approximately equal to the nominal torque in the drive train. This ensures advantageous that the initiation of the braking process is smooth.
  • the braking device comprises at least one temperature sensor which is adapted to detect a temperature of at least one friction partner of the braking device, wherein the controller is further adapted to continuously evaluate temperature values detected by the temperature sensor with a predetermined temperature Limit and disable the braking device when the detected temperature exceeds the limit.
  • a friction partner of the brake device is a brake disk or a brake pad in a disc brake used by way of example as a brake device.
  • the braking device be configured redundantly.
  • each braking device is provided in each case with a temperature sensor.
  • the temperature of the braking device is monitored. If the temperature exceeds a predetermined maximum value, the braking process is interrupted. This reduces wear and increases the life of the brake device.
  • the controller is further configured to calculate a brake device cooling time from at least one of the temperature values, a value determined for this cooling time being indicative of a waiting time to be maintained before a renewed restart of the wind turbine. For example, the cooling time and the before a renewed
  • indicative means that the waiting time to be observed before the wind power plant restarts can be derived from the cooling time.
  • the Bremsvoriquessabksselzeit corresponds to the waiting time to be met.
  • the cooling time is determined, for example, by the fact that the temperature of the brake device falls below a predetermined limit. For example, it is waited until the temperature of one of the two friction partners of the braking device below 200 ° C, 150 ° C, 100 ° C, 50 ° C or at about
  • control device is set up in such a way that the brake device is deactivated when the rotor speed has increased by at least 90%, 85%, 80%, 75%, starting from an initial value at which the brake device was activated. 70%, 65%, 60%, 55% or 50%.
  • control is such is set to disable the brake device when a rotor blade angle is greater than a predetermined limit value or when a predetermined limit is exceeded on a pitch travel in the direction of the 90 ° position.
  • This value may also be a relative value added to the current pitch value at which the braking is triggered.
  • the mechanical braking device is deactivated when the rotor blade pitch is greater than 10 °, 15 °, 20 °, 25 °, 30 °, 35 °, 40 °, 45 ° or 50 °.
  • the controller is set up in such a way that it activates the drives of the rotor blades (pitch drives) simultaneously or with predetermined delay times with the activation of the braking device in response to the received interference signal
  • Rotor blades may be moved in the direction of the 90 ° position or "flag position.”
  • Such a "pitching" of the rotor blades in the direction of the 90 ° position may also be initiated, controlled or regulated by the operating control of the wind turbine or by the safety shutdown device of the wind turbine.
  • the object is further achieved by a method for operating a wind energy plant with a rotor and a braking device, wherein the braking device comprises a mechanical braking device which is mechanically coupled to the rotor, and wherein the braking device is a controller and at least one electric and / or Hydraulic switching element for activating and / or deactivating the braking device comprises, wherein the switching element is designed redundant and / or interference-proof, the method is further developed in that the
  • Control receives an interference signal and in response to the receipt of the interference signal triggers a braking operation by the controller activates the braking device by means of the switching element and, before the rotor of the wind turbine has come to a standstill, deactivated.
  • the switching element is opened by this is switched off.
  • the braking device is activated or kept active by means of the switching element for the duration of a predetermined time interval and is deactivated after the predetermined time interval. Values for this time interval are mentioned above in the text, these are provided according to further embodiments in a method according to these further embodiments.
  • the time interval lies between one second and 10 seconds, in particular between 3 seconds and 9 seconds, and in particular between 4 seconds and 6 seconds.
  • the braking device is deactivated when a rotor speed, starting from an initial value at which the braking device has been activated, by at least 90%, 85%, 80%, 75%, 70%, 65%, 60%, 55 % or 50% has dropped.
  • the brake device is deactivated when the rotor blade stop angle is at least 10 °, 15 °, 20 °, 25 °, 30 °, 35 °, 40 °, 45 ° or 50 °.
  • the switching element in case of failure of a power supply of the control, the switching element is activated with a supply-independent shutdown or kept active. After the predetermined time interval, the switching element is deactivated.
  • This supply-independent shutdown is, for example, and as also mentioned above, to a connected to the switching element buffer module, for. B. a capacitor.
  • a generator torque is controlled such that upon activation and / or deactivation of the brake device, a torque fluctuation caused by this process in a drive strlid is reduced.
  • the braking device comprises at least one temperature sensor, which detects a temperature of at least one friction partner of the braking device, wherein continuously detected by the temperature sensor
  • Temperature values are evaluated and compared with a predetermined limit, wherein the braking device is deactivated when the detected temperature values exceed the limit.
  • a brake cooling time is calculated from at least one of the temperature values, wherein a value determined for the brake cooling time is indicative of a waiting time to be maintained before a renewed restart of the wind turbine.
  • Wind energy plant is operated in trickle mode or at low speed.
  • the mechanical braking device cools faster, reducing brake cooling time and enabling the wind turbine to be re-connected to full power faster.
  • a pressure measurement of the hydraulic fluid is made.
  • the measured values of such a pressure measurement can be used for the early detection of errors, for example leaks, in the brake system.
  • chokes are present, so that targeted pressure curves for the brake pressure at the beginning of the braking process and to reduce the pressure at the end of the braking process can be realized.
  • Individual choke branches can be switched off via non-return valves (non-return valves).
  • non-return valves non-return valves
  • Fig. 2 is a schematically simplified hydraulic circuit diagram of a
  • FIGS. 3 a) to 3 f) in each case schematically over time applied exemplary
  • FIG. 3a shows a schematic simplified view of a wind turbine 2.
  • Your rotor 4 includes example three rotor blades 6, each extending between a rotor blade root 8 and a rotor blade tip 10.
  • the rotor blades 6 are attached to their rotor blade root 8 on a rotor hub 12. This drives a main drive train of the wind turbine 2, which runs inside a gondola not visible in FIG.
  • the nacelle is carried by a support structure 14, for example a tower.
  • the wind turbine 2 also comprises a braking device 20, which is arranged for example in the nacelle.
  • a braking device 20 is shown in FIG.
  • the braking device 20 includes a braking device, which is generally designated by reference numeral 22.
  • a first brake device 22a and a second brake device 22b are provided, which together form the brake device 22.
  • the mechanical brake devices 22a, 22b are disc brakes, for example.
  • the braking device 22 of the braking device 20 is therefore executed twice (partially redundant) in the illustrated embodiment. For this purpose, for example, the two disc brakes with the rotor shaft, which is directly driven by the rotor 4 of the wind turbine 2, coupled. It is also envisaged that the mechanical braking devices
  • the braking device 20 further includes, by way of example, a first hydraulic
  • Switching element 24a and a second hydraulic switching element 24b are designated together with reference numeral 24.
  • this is a first solenoid valve, which forms the first switching element 24a, and a second solenoid valve, which forms the second switching element 24b.
  • the first and second switching elements 24a, 24b together form one Switching element 24 for activating and deactivating the braking device 22.
  • the first and the second switching element 24a, 24b are designated together with reference numeral 24.
  • the switching element 24 is redundantly configured with respect to the depressurizing function by providing first and second switching elements 24a, 24b. At the same time, the switching element 24 is executed fail-safe. To ensure this function, hydraulic switching elements or solenoid valves are used as the first and second switching element 24a, 24b, for example, which are open in the direction of storage container 30 in the de-energized state.
  • the switching elements 24a, 24b are not designed to be redundant. This function is provided exclusively by valve 24a.
  • a controller 26 which is adapted to receive an interference signal S, for example, from the operational control of the wind turbine 2.
  • the controller 26 has access to the braking device 20.
  • An interference signal S is generated, for example, if a high overspeed or a high load of the wind turbine 2 occurs and consequently the rotor 4 of the wind turbine 2 is braked.
  • the rotor blade pitch drives Pitch Drives
  • the rotor blade pitch drives are also controlled such that they move the rotor blades 6 of the wind energy plant 2 in the direction of the 90 ° or flag position.
  • the rotor 4 of the wind turbine 2 is also braked aerodynamically.
  • the braking device 22 is activated in response to the received interference signal S.
  • the switching element 24 is driven accordingly.
  • controller 26 is adapted to Disable device 22 by means of the switching element 24 before the rotor 4 of the wind turbine 2 comes to a standstill.
  • the mechanical braking device 24 is driven or operated in pulses.
  • the mechanical braking device 24 is capable of efficient speed and
  • the brake device 20 comprises a hydraulic supply circuit for supplying the brake device 22.
  • the hydraulic supply circuit which is shown schematically and simplified in FIG. 2, comprises a hydraulic supply source 28, for example a hydraulic pump. This takes hydraulic
  • Fluid for example a hydraulic oil
  • a storage container 30 Via a working pressure regulator 32, which provides the working pressure pO, hydraulic fluid is supplied to the hydraulic supply circuit from the hydraulic supply source 28.
  • a safety pressure limiter 34 is also provided, which controls the pressure in the hydraulic supply circuit to a predetermined pressure
  • the hydraulic fluid passes from the working pressure regulator 32 to the first switching element 24a. If this first switching element 24a designed as a solenoid valve, for example, is energized and thus opened to supply the brake but closed in the direction of the storage container 30, the hydraulic fluid passes via the throttle D1 .0 and the throttle D1 .1 to a first branch point 36a. At the first branch point 36a, a pressure diaphragm accumulator 38 is integrated into the hydraulic supply circuit. From the first branch point 36a, the hydraulic fluid then passes to the first and the second mechanical
  • Braking device 22a, 22b At a further branching point in front of the first and second mechanical brake devices 22a, 22b, a pressure sensor 40 is provided which measures the working pressure p-Br of the first and second mechanical brake devices 22a, 22b.
  • a bypass pressure regulator 42 is also integrated in the hydraulic supply circuit.
  • a throttle D1 .2 and a non-return valve 44 (check valve) is integrated in the hydraulic supply circuit parallel to the throttle D1 .1.
  • the first switching element 24a for example, applied to a supply voltage of 24 volts, the previously described way for the hydraulic fluid, starting from the hydraulic supply source 28 to the mechanical braking device 22, released.
  • the second switching element simultaneously becomes
  • a second solenoid valve energized so that it closes and prevents backflow of the hydraulic fluid from the first branch point 36a to the storage container 30.
  • the mechanical braking device 22 engages and unfolds its effect.
  • the switching element 24 After a predetermined time interval DT, which begins with the activation of the mechanical brake device 22, and for example between 1 and 1 0 seconds long, or exceeding an allowable limit temperature in at least one friction partner of the brake device 22, the switching element 24 is de-energized.
  • the time interval DT is also more particularly between 3 and 9 seconds and, for example, between 4 and 6 seconds. If the switching element 24 is de-energized, so in particular the first and the second switching element 24a, 24b are de-energized.
  • first switching element 24a and the second switching element 24b When de-energized, the first switching element 24a and the second switching element 24b open. Starting from the first branch point 36a, there are a first and a second fluidic line between this and a second branch point 36b
  • the hydraulic supply circuit at least one fluidic path and a parallel thereto second fluidic path between the braking device 22 and the storage container 30 includes.
  • the first hydraulic switching element 24a is integrated in the first path and the second hydraulic switching element 24b is integrated in the second path.
  • the first path leads through the throttle D1 .2 and the flow direction, ie in the direction of the first switching element 24a, permeable check valve 44 and the throttle D1 .0 to the second branch point 36b.
  • the second path leads from the first branch point 36a via the throttle D2.0 and the normally open second switching element 24b to the second branch point 36b.
  • the throttles D1 .2 and D2.0 ensure the desired pressure curve during pressure reduction.
  • the first fluidic path just like the second fluidic path, respectively still comprises the connecting line between the first branch point 36a and the first and second mechanical brake devices 22a, 22b and the connecting line between the second branch point 36b and the storage container 30. These too can advantageously be made redundant so that the complete connection lines from the brake devices 22a, 22b to the reservoir 30 are made redundant.
  • the controller 26 is configured to activate or keep the braking device 22 by means of the switching element 24. After a predetermined time interval, the brake device 22 is deactivated.
  • a supply-independent shutdown element is included, which, even if a power supply of the controller 26 fails, the switching element 24 is initially activated or actively held and deactivated after a predetermined time interval DT.
  • one capacitor or else a common capacitor
  • the Capacitor via the ohmic resistance, for example, the first and / or second solenoid valve.
  • the braking device 22 remains activated. Then it switches off automatically.
  • the controller 26 is further configured to control a generator torque of the present in the drive train of the wind turbine 2 generator at detected fault-free network feed so that when activating and / or deactivating the brake device 22 caused by this process torque fluctuation in the drive train is reduced.
  • the generator torque during the activation of the mechanical brake device 22 is reduced in a time-dependent manner so that the sum of the generator torque and the braking torque applied by the mechanical brake device 22 is always approximately equal to the nominal torque in the drive train.
  • a virtually smooth triggering of the mechanical braking process can be achieved.
  • the braking device 20, in particular the braking device 22, further comprises at least one temperature sensor.
  • a first temperature sensor TS1 and a second temperature sensor TS2 are provided.
  • the first temperature sensor TS1 measures the temperature of at least one friction partner of the first brake device 22a.
  • the second temperature sensor TS2 measures the temperature of at least one friction partner of the second brake device 22b. If disk brakes are used as brake devices 22a, 22b, for example, the friction partners are the brake disk and the brake shoes or brake linings. In other words, therefore, the temperatures of the braking devices 22a, 22b are monitored with the temperature sensors T1, T2.
  • the controller 26 is able to read out, record and evaluate temperature values of the temperature sensors TS 1, TS 2 via data lines (not shown). Exceed this a predetermined limit, the brake device 22 or at least one of the two braking devices 22a, 22b is deactivated. Thus, overheating of the brake device 22 can be effectively prevented. According to a further embodiment, it is provided that the controller 26 is further configured to calculate a braking device cooling time from at least one of the temperature values detected by the temperature sensors TS1, TS2.
  • a value determined for this cooling time is indicative of a waiting time to be maintained before a renewed restart of the wind turbine 2.
  • the waiting time can be derived from the value of the brake device cooling time. While the mechanical brake device 22 cools down, the wind turbine 2 can be operated in spinning mode or at low speed, so that its rotor 4 rotates slowly. During the movement, the mechanical brake device 22 cools faster than at rest, so that a quick restart or a faster resumption of the full load operation of the wind turbine 2 is possible.
  • FIGS. 3a to 3f An exemplary braking operation during a method for operating a wind turbine 2 according to an exemplary embodiment will be explained with reference to FIGS. 3a to 3f.
  • Figures 3a to 3f are shown in seconds over the same time scale. For all figures, this is shown by way of example in Fig. 3f.
  • Fig. 3a shows the wind speed in meters per second.
  • FIG. 3b shows a rotor blade pitch or pitch angle in degrees.
  • Fig. 3c shows a generator speed in revolutions per minute (rpm).
  • the curve labeled A shows the course of the generator speed without the intervention of a mechanical braking device.
  • the curve labeled B shows the progression of the generator speed over time using a mechanical braking device.
  • Fig. 3d shows the time course of a mechanical braking torque in kilonewtonmeter (kN m).
  • kN m kilonewtonmeter
  • Fig. 3f shows a Turmfußbiegemoment in the longitudinal direction in kilonewtonmeter (kNm). Again, the history of the tower foot bending moment is shown for a case that the mechanical brake device is not used. This curve is labeled A. B is the curve that results using the mechanical brake. The significant reduction in the maximum load of the support structure 14 of the wind turbine 2 can be seen at the lower deflection of the curve B compared to the curve A at the respective maxima of the Turmfußbiegemoments.
  • the controller 26 deactivates the brake device 22 before the rotor 4 of the wind energy plant 2 has come to a standstill (compare to FIGS. 3 c and 3d). Although the mechanical brake is activated only for a relatively small period of time, namely the time period DT between the times T1 and T2, there is a significant reduction in the maximum load of the wind turbine 2.

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  • 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)
  • Control Of Eletrric Generators (AREA)

Abstract

L'invention concerne une éolienne (2) ainsi qu'un procédé de fonctionnement de cette éolienne. L'éolienne (2) comporte un rotor (4) et un système de freinage (20), le système de freinage (20) comportant un dispositif de freinage (22) mécanique qui est accouplé mécaniquement au rotor. Le système de freinage (20) comporte au moins un élément de commutation (24) électrique et/ou hydraulique servant à l'activation et/ou la désactivation du dispositif de freinage (22). L'élément de commutation (24) est conçu de manière redondante et/ou de manière à présenter une sécurité intégrée. Une commande (26) est en outre prévue, laquelle est conçue pour recevoir un signal parasite (S) et pour activer l'élément de commutation (24) et par conséquent le dispositif de freinage (22) en réponse au signal parasite (S) reçu. Le dispositif de freinage (22) est désactivé au moyen de l'élément de commutation (24) avant que le rotor (4) de l'éolienne ne s'arrête.
EP17797950.7A 2016-11-21 2017-11-15 Éolienne comprenant un système de freinage ainsi que procédé de fonctionnement de cette éolienne Withdrawn EP3542053A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016013796.7A DE102016013796A1 (de) 2016-11-21 2016-11-21 Windenergieanlage mit Bremseinrichtung sowie Verfahren zum Betreiben derselben
PCT/EP2017/079267 WO2018091497A1 (fr) 2016-11-21 2017-11-15 Éolienne comprenant un système de freinage ainsi que procédé de fonctionnement de cette éolienne

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EP3542053A1 true EP3542053A1 (fr) 2019-09-25

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EP17797950.7A Withdrawn EP3542053A1 (fr) 2016-11-21 2017-11-15 Éolienne comprenant un système de freinage ainsi que procédé de fonctionnement de cette éolienne

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EP (1) EP3542053A1 (fr)
CN (1) CN110168219A (fr)
DE (1) DE102016013796A1 (fr)
WO (1) WO2018091497A1 (fr)

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Publication number Priority date Publication date Assignee Title
WO2018188821A1 (fr) * 2017-04-12 2018-10-18 Siemens Wind Power A/S Ensemble d'arrêt de sûreté
CN112761874B (zh) * 2021-02-04 2022-09-16 湘电风能有限公司 安全停机方法、系统和风力发电机
US20230220834A1 (en) * 2022-01-12 2023-07-13 General Electric Renovables Espana, S.L. System and method for actively monitoring an air gap in a wind turbine brake assembly

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4348155A (en) * 1980-03-17 1982-09-07 United Technologies Corporation Wind turbine blade pitch control system
DE3204695A1 (de) * 1982-02-11 1983-08-18 Siemens AG, 1000 Berlin und 8000 München Einrichtung zur sicherheitsbremsung von foerdermaschinen, insbesondere trommelfoerdermaschinen
DE10036286B4 (de) * 2000-07-26 2009-07-30 Robert Bosch Gmbh Hydraulische Fahrzeugbremsanlage
US20060205554A1 (en) * 2003-08-12 2006-09-14 Osamu Nohara Speed reducer for use in yaw drive apparatus for wind power generation apparatus, and yaw drive method and apparatus for wind power generation apparatus using the speed reducer
DK2119910T3 (da) * 2008-05-14 2012-07-16 Alstom Wind Sl Metode til reduktion af vridningssvingninger i kraftoverførselssystemet i en vindmølle
DE102009006054A1 (de) * 2009-01-24 2010-07-29 Robert Bosch Gmbh Stationäre Energiegewinnungsanlage mit einer Abbremsvorrichtung
EP2284390B1 (fr) * 2009-07-10 2012-02-08 Vestas Wind Systems A/S Station hydraulique et procédé de contrôle de pression du système hydraulique des éoliennes
US8080891B2 (en) * 2009-09-25 2011-12-20 General Electric Company Hybrid braking system and method
DE102012101484A1 (de) * 2012-02-24 2013-08-29 Setec Gmbh Verfahren und Einrichtung zur Abbremsung einer Windenergieanlage in einem Notfall
US8975768B2 (en) 2013-06-05 2015-03-10 General Electic Company Methods for operating wind turbine system having dynamic brake

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CN110168219A (zh) 2019-08-23
WO2018091497A1 (fr) 2018-05-24

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