• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    mechanical brake for wind turbine mechanical brake consisting of a double disc (d1 and d2) that rotates along the transmission shaft and certain brake calipers (p1 and p2) that contact the disc when activated either electrically, hydraulically or pneumatically . the brake is characterized by being placed on the high-speed shaft (ea) of the power train, adapting its diameter to certain dimensions marked by the existing space and anchoring the brake calipers directly to the gearbox housing (m). the mechanical brake thus constituted is capable of braking with a pitch actuator in the power position, in the initial conditions of rated power and at the rated average wind speed for an installation smaller than 1 mw.
    公开号:BR112012020189B1
    申请号:R112012020189-1
    申请日:2011-01-26
    公开日:2022-01-11
    发明作者:César Díaz De Cerio García De Mendaza；Angel Fernandez Garcia
    申请人:Gamesa Innovation & Technology, S.L.；
    IPC主号:
    专利说明:

    Object of the invention
    [0001] The aim of the invention is to provide a wind turbine, with a power range close to 1 MW, with a mechanical brake that keeps the rotating axis blocked during the start-up and maintenance operations of the wind turbine and that in turn meets the requirements of emergency braking in a braking derived from a failure of the stepper mechanism. Background of the invention
    [0002] The mechanical transmission system or power train of a wind turbine is formed by a wind rotor, a gear box (since the speed of rotation of the turbine normally does not correspond to that of the generator) and an electrical generator. The power train includes a low-speed shaft that couples between the wind turbine and gearbox and a high-speed shaft that couples between the gearbox and generator. In addition, the power train includes the mechanical brake, whose function is to block the turbine in maintenance operations and eventually contribute to an emergency stop, such as the one that can be presented in the event of a failure of the stepping mechanism, preventing the blades from being put into operation. flag. Stopping a wind turbine is one of the most critical operations because it implies the generation of large loads that directly affect the wind turbine components.
    [0003] The physical constitution of the mechanical brake consists of a disc that rotates together with the transmission shaft and brake calipers that contact the disc when activated, whether electrically, hydraulically or pneumatically.
    [0004] One of the most relevant aspects in the mechanical brake design is its location in the power train as it can be installed either on the low-speed shaft or on the high-speed shaft.
    [0005] In reduced power turbines (around 1 MW or less power) the most appropriate location of the mechanical brake is on the low speed shaft, a location that is reflected in patents JP2004124771 (A) and NL8302191 (A). Mechanical brakes formed by a single disc and installed on the high-speed shaft are also known. Mechanical brakes formed by a disc only present the following problems: The amount of energy to be dissipated is the kinetics of the rotor assembly plus the mechanical work developed by the aerodynamic pair during braking, (which is not small, as the blades are in power position since, if the step mechanism has failed, they cannot go to the flag). This amount of energy defines the volume of the brake disc and therefore defines the disc thickness and diameter.
    [0006] The maximum energy critical braking lasts a determined time, since the torque must be of a certain value determined to stop the machine. This energy is converted into heat in the disk and its temperature rises. To maintain acceptable temperatures (above which the system overheats and fails), the volume of the disk must be of a certain value by which its thickness and diameter can be increased. The fact that the disc is very thick doesn't help much, as heat is generated on the disc's surface. During the braking time there is not enough time for much heat to be conducted from the surface to the midplane of the disc. Therefore, there is a disk temperature gradient that decreases towards the interior of the midplane. There is therefore a practical limit to disk thickness beyond which there is no benefit from significantly lowering surface temperature as thickness increases. Therefore, only the diameter of the disc remains as the last variable to increase the volume of the iron material and achieve reasonable temperatures on the surface of the disc/pad. With only one disc, the diameter of a wind turbine brake close to 1 MW power is such that it would interfere with adjacent elements in this nacelle position (mainly yaw gearmotors) and its wear and maintenance would convert it into an excessively expensive element. .
    [0007] In order to gain volume of iron material where for the accumulation of energy dissipated during a braking with failure of the step mechanism that makes it impossible to drive the blades to the flag, a mechanical brake with at least two brake discs was developed. Description
    [0008] When the mechanical brake is designed solely to lock the rotor, the torque generated in the power train that it must support is that transmitted by the wind rotor flagged in extreme wind conditions. Now, in addition to the blocking function, the mechanical brake can be used for dynamic braking of the wind rotor during emergency stop processes (with the blades in the power position).
    [0009] It is an objective of the invention to improve the mechanical brake existing in machines close to 1 MW so that they lock the rotor according to the design requirements and to incorporate the braking function in emergency stop processes.
    [00010] It is another objective of the invention to constitute a mechanical brake formed by at least two brake discs that guarantee the necessary volume of iron material to achieve reasonable temperatures on the surface of the disc and the pad.
    [00011] It is another objective of the invention to install the mechanical brake formed by at least two discs arranged on the high-speed shaft of a power train, adapting it to the dimensions allowed by the existing space and anchoring the calipers directly to the gearbox housing .
    [00012] These and other objects of the invention are obtained with a mechanical brake formed by at least two discs, which is explained in detail in the preferred embodiment according to the attached drawings. Brief description of drawings
    [00013] Figure 1 shows a general representation of certain elements of a wind turbine, including a double disc attached to the transmission shaft.
    [00014] Figure 2 represents a perspective view of the double disk and a section of it.
    [00015] Figure 3 is a perspective view of the assembly mounted on the gearbox. Description of the preferred embodiment
    [00016] As shown in figure 1 a wind turbine is comprised of a wind rotor (R), a gearbox (M) and an electrical generator (not shown in the figure). This set of elements constitutes the power train and includes a low speed shaft (Eb) that connects the wind rotor (R) to the gearbox (M) and a high speed shaft (Ea) that connects the gearbox ( M) to the generator. The use of a gearbox (M) is due to the fact that the speed of rotation of the rotor (R) does not normally correspond to that of the generator and taking advantage of the multiplication ratio the mechanical brake, whose function is to block the turbine in maintenance operations and in emergency stops, it is placed on the high axis (Ea). When placing the brake in this position, the torque needed to brake is lower as the speed is reduced by the gearbox ratio.
    [00017] The mechanical brake object of the invention is formed by two discs (D1 and D2) parallel and separated at a sufficient distance to allow the actuation of calipers (P1 and P2) provided by brake pads, located diametrically opposite and that each one of them applies its braking force to its corresponding disc.
    [00018] Figure 2 shows the two disks (D1 and D2) and a section of them. In the central part of the discs there are oval grooves (Ro) that cross the set of the two discs, allowing the insertion of strips, anchors or hooks inside them for manipulation and placement on the high axis (Ea). The central circle (Ce) has a dowel (Ch) that locks the set of discs with the movement of the shaft.
    [00019] As shown in Figure 3, the mechanical brake is arranged next to the gearbox (M) and each of the calipers (P1 and P2) is supported on a stepped and widened part (Pe) that attaches directly to the gearbox chassis (M) by means of at least one threaded screw. The discs (D1 and D2) feature a continuous braking surface (no holes, grooves or grooves) as they do not require rapid dissipation of heat accumulated during braking.
    [00020] Taking into account the administrative regulations of many jurisdictions that require wind turbines to have at least one mechanical brake capable of braking with the stepper actuator in the power position. That is: without going to the flag, in initial conditions of rated power and at the rated average wind speed for that installation. This type of braking is required to obtain the machine's certification. Thus, the disc brake required to obtain this certification, as it is a double disc, can have a smaller diameter, which allows it to adapt to the space between the gearbox (M) and the generator.
    [00021] The following graph shows a comparison between the type of disc and the temperature it reaches during braking in relation to its diameter and thickness.

    [00022] The data described in the table are considered as a practical example of application of this invention to a wind turbine of 50 to 60 meters in rotor diameter (R), with a single disc brake approximately 25 mm thick and 600 mm in diameter . In this case it has to be considered that the theoretical temperature rise when braking the rotor when the stepper mechanism is blocked and the machine is in rated conditions of power and wind speed, is approximately 600 0 C as a uniform average. If we take into account that the initial temperature of the disk is approximately 500 C, the final temperature of the disk is 650 0 C. In the case of a double disk, the diameter will be between 550 and 700 mm, preferably 610 mm in diameter and the thickness varies between 20 and 30 mm, preferably 25 mm, and finally the final temperature of the disk would be approximately 260°C. This temperature corresponds to approximately 60% less than in a single disc brake.
    [00023] Bearing in mind that the heating of the disc during braking is not uniform, due to the formation of higher temperature rings at the interface of the pad lining in contact with the front of the disc, the maximum instantaneous point temperatures on the disc surface can be hundreds of degrees higher than those mentioned above. This makes the single disc unfeasible for reference braking.
    [00024] The diameter of the single disc of the same thickness that heated up in the same way as the double disc in said braking would have a diameter of more than 800 mm and would interfere with other mechanical elements inside the nacelle, which also makes it unfeasible. Additionally, this single disc would require deeper calipers to accommodate the longer, wider, and structurally reinforced inserts with thicker material sections to support the greater loads due to greater bending moments at the connections of the two halves, with which they would be of great benefit. weight and higher cost, making installation and maintenance work difficult.
    权利要求:
    Claims (6)
    [0001]
    1. Mechanical brake for wind turbine comprising a disc element (D1, D2) which rotates with the transmission shaft and brake calipers (P1, P2) which rub against the disc element (D1, D2) when activated, characterized in that said wind turbine mechanical brake is located on a high speed shaft (Ea) and the disk element (D1, D2) is formed by at least two disks (D1, D2), each disk has a surface of continuous braking, and said wind turbine mechanical brake has at least two calipers (P1, P2) applied, one on each disc, these calipers (P1, P2) being anchored to a gearbox chassis (M).
    [0002]
    2. Mechanical brake for wind turbine according to claim 1, characterized in that at least two discs (D1, D2) and brake calipers (P1, P2) are located after the gearbox (M), the most near and as far away from a generator as possible.
    [0003]
    3. Mechanical brake for wind turbine according to claim 1, characterized in that the brake calipers (P1, P2) are anchored to the gearbox chassis (M) through fasteners.
    [0004]
    4. Mechanical brake for wind turbine according to claim 1, characterized in that the discs (D1, D2) have dimensions between 20 and 30 mm thick and between 550 and 700 mm in diameter.
    [0005]
    5. Mechanical brake for wind turbine according to claim 3, characterized in that the brake calipers (P1, P2) are anchored to the gearbox chassis (M) through threaded screws.
    [0006]
    6. Mechanical brake for wind turbine according to claim 4, characterized by the fact that the disks D1, D2) have dimensions of 25 mm thick and 610 mm in diameter.
    类似技术:
    公开号 | 公开日 | 专利标题
    BR112012020189B1|2022-01-11|MECHANICAL BRAKE FOR WIND TURBINE
    DK2333325T3|2015-08-24|Brake system, wind turbine generator and
    US6609889B1|2003-08-26|Method and a device for adjusting the pitch and stopping the rotation of the blades of a wind turbine
    US8740566B2|2014-06-03|Brake system for a wind turbine with integrated rotor lock generator and wind turbine
    EP2306008A2|2011-04-06|Yaw bearing assembly for use with a wind turbine and a method for braking the yaw movement
    JP2012522926A|2012-09-27|Maintainable yaw brake disc segment without removing nacelle
    US9470208B2|2016-10-18|Wind turbine and locking method
    US20140010656A1|2014-01-09|Fixation device
    BRPI0414684B1|2016-06-21|azimuth brake for wind power installations
    JP2011112055A5|2013-09-12|
    US9581137B2|2017-02-28|Yaw brakes for wind turbines
    WO2018204465A1|2018-11-08|Compact multi-disk rotor brake system for a wind turbine
    US20110211961A1|2011-09-01|Method and system for braking in a wind turbine
    CN106321359A|2017-01-11|Vertical-axis clutch type wind power generation device
    EP2987999B1|2019-02-20|Device and method for turning a rotor of a wind turbine
    KR20140072561A|2014-06-13|Rotor shaft locking apparatus for wind power generator
    US20150204308A1|2015-07-23|Brake system for a wind turbine generator
    EP2747252B1|2019-01-23|Air-gap secure system for a wind turbine
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    DK2486275T3|2015-12-14|Drive train and wind power plants
    US20100258390A1|2010-10-14|Hybrid electromechanical actuator brake for wind turbines
    KR20140038614A|2014-03-31|Wind power generator and method for maintaing wind power generator
    US20210033073A1|2021-02-04|Direct-Drive Wind Turbine
    CN203035454U|2013-07-03|Rotator turnplate and double-stator permanent magnet direct driven wind driven generator using same
    同族专利:
    公开号 | 公开日
    WO2011095655A1|2011-08-11|
    DK2532886T3|2019-01-07|
    ES2384140B1|2013-05-16|
    EP2532886A1|2012-12-12|
    US20130056314A1|2013-03-07|
    US8864464B2|2014-10-21|
    BR112012020189A2|2016-08-02|
    EP2532886B1|2018-10-31|
    EP2532886A4|2015-04-01|
    ES2384140A1|2012-07-02|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    NL8302191A|1983-06-20|1985-01-16|Piet Huisjes|Converter for transforming wind energy into heat - has vertical rotor, driving thermal brake submerged in liquid-filled vat|
    DE3516821A1|1985-05-10|1986-11-13|Horst 2341 Brodersby Frees|Wind motor|
    WO2000009885A1|1998-08-13|2000-02-24|Neg Micon A/S|A method and a device for adjusting the pitch and stopping the rotation of the blades of a wind turbine|
    DE20212459U1|2002-08-13|2003-12-24|Hawe Hydraulik Gmbh & Co. Kg|Electro-hydraulic brake module|
    JP2004124771A|2002-09-30|2004-04-22|Daiwa House Ind Co Ltd|Brake system for horizontal shaft type windmill|
    DE10320580A1|2003-05-07|2004-11-25|Bosch Rexroth Ag|Braking device for a wind power plant with a rotor converting the wind energy into a rotary movement and method for operating such a braking device|
    JP5479108B2|2007-01-17|2014-04-23|ニュー・ワールド・ジェネレーション・インコーポレイテッド|Composite wind generator and method of operation|
    US8028604B2|2007-01-26|2011-10-04|General Electric Company|Methods and systems for turning rotary components within rotary machines|
    DE102007058746A1|2007-06-18|2008-12-24|Hanning & Kahl Gmbh & Co. Kg|Locking device for a wind turbine|
    DE102007040834A1|2007-08-29|2009-03-05|S.B. Patent Holding Aps|Wind energy plant operating method, involves changing operating parameter of wind energy plant corresponding to change in load, and operating brake system for changing operating parameter|
    US20110142626A1|2009-04-02|2011-06-16|Hanson Jesse M|Serviceable yaw brake disc segments without nacelle removal|
    US20110033291A1|2009-08-04|2011-02-10|Abundant Energy, LLC|Energy transfer system|ES2546266T3|2010-09-20|2015-09-22|Alstom Renewable Technologies|Rotor of a wind turbine with brake for the tilt of the blades|
    WO2013093124A1|2011-12-21|2013-06-27|Carpeno Velayos Angel|Tiltable wind turbine with rotor brake|
    DE102012101484A1|2012-02-24|2013-08-29|Setec Gmbh|Method and device for decelerating a wind turbine in an emergency|
    EP2669510B1|2012-05-30|2014-07-16|Siemens Aktiengesellschaft|A brake system for a wind turbine|
    CN103052824B|2012-07-24|2015-10-21|强海胜|The arrestment mechanism that the bi-directional braking method of disk type braker adopts and system|
    DE102012222637A1|2012-12-10|2014-06-12|Senvion Se|Turn drive for a wind turbine and method for rotating the rotor shaft of a wind turbine|
    GB2516668B|2013-07-29|2015-10-28|Andritz Hydro Hammerfest Uk Ltd|Improved underwater turbine brake|
    KR101768340B1|2015-12-07|2017-08-14|두산중공업 주식회사|System for yaw break having multi-disk|
    USD789854S1|2015-12-22|2017-06-20|Mahindra N.A. Tech Center|Disc brake rotor|
    CN105715702B|2016-04-01|2018-03-20|宁波彰星车辆有限公司|A kind of concealed double acting disc brake|
    USD787996S1|2016-04-29|2017-05-30|Eaton Corporation|Clutch cover|
    US10458206B2|2016-10-06|2019-10-29|Saudi Arabian Oil Company|Choke system for wellhead assembly having a turbine generator|
    ES2862724T3|2017-06-07|2021-10-07|Sb Patent Holding Aps|Multi-surface skid braking system for a wind turbine|
    USD852695S1|2017-10-03|2019-07-02|Winhere Automotive, Inc.|Brake disc|
    USD852694S1|2017-10-03|2019-07-02|Winhere Automotive, Inc.|Brake disc|
    EP3899255A1|2018-12-20|2021-10-27|Vestas Wind Systems A/S|A generator-gearbox assembly for a wind turbine|
    法律状态:
    2019-01-08| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-10-22| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2021-07-20| B06A| Patent application procedure suspended [chapter 6.1 patent gazette]|
    2021-10-26| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2022-01-11| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 26/01/2011, OBSERVADAS AS CONDICOES LEGAIS. PATENTE CONCEDIDA CONFORME ADI 5.529/DF, QUE DETERMINA A ALTERACAO DO PRAZO DE CONCESSAO. |
    优先权:
    申请号 | 申请日 | 专利标题
    ES201000131A|ES2384140B1|2010-02-04|2010-02-04|MECHANICAL BRAKE FOR AEROGENERATOR.|
    ESP201000131|2010-02-04|
    PCT/ES2011/000017|WO2011095655A1|2010-02-04|2011-01-26|Mechanical brake for a wind turbine|
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