• 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:
    An energy production plant, in particular a wind power plant, has a drive shaft, a generator (8) and a differential gear (4, 11 to 13) with three inputs and outputs, wherein a first drive with the drive shaft, an output with a generator (8) and a second drive is connected to a differential drive (6) and wherein the differential gear (4; 11 to 13) is a planetary gear. There are two differential drives (6) and possibly also two frequency converter (7) are provided, which are connected to the second drive. The differential drives (6) are connected to a sun gear (11) of the differential gear (4, 11 to 13) and arranged on the side remote from the differential gear (4; 11 to 13) of the generator (8).
    公开号:AT511720A4
    申请号:T1252/2011
    申请日:2011-09-01
    公开日:2013-02-15
    发明作者:
    申请人:Hehenberger Gerald；
    IPC主号:
    专利说明:

    The invention relates to an energy generation plant, in particular a wind power plant, having a drive shaft, a generator and a differential gearbox with three drives, wherein a first drive with the drive shaft, an output with a generator and a second drive with a differential Drive is connected and wherein the differential gear is a planetary gear.
    Wind power plants are becoming increasingly important
    Electricity generation plants. As a result, the percentage of electricity generated by wind is continuously increasing. This, in turn, requires new standards of power quality on the one hand and a trend towards even larger wind turbines on the other. At the same time, more and more offshore wind farms are being built, requiring plant sizes of at least 5 MW of installed capacity. Due to the high costs for infrastructure and maintenance of the wind turbines in the offshore sector, the availability of the turbines is of particular importance here.
    Common to all systems is the need for a variable rotor speed, on the one hand to increase the aerodynamic efficiency in Teiilastbereich and on the other hand to control the torque in the drive train of the wind turbine. The latter for the purpose of speed control of the rotor in combination with the rotor blade adjustment. Currently, therefore, wind turbines are in use, which increasingly meet this requirement by using variable-speed generator solutions in the form of so-called permanent magnet-excited low-voltage synchronous generators in combination with IGBT frequency converters. However, this solution has the disadvantage that (a) the wind turbines can only be connected to the medium-voltage grid by means of transformers and (b) the frequency inverters required for the variable speed are correspondingly powerful and therefore a source of unwanted failures and efficiency losses. Alternatively, therefore, so-called differential drives are used recently, which directly to the medium-voltage network connected externally-excited medium-voltage synchronous generators in combination with a differential gear and an auxiliary drive, which preferably provides a permanent magnet synchronous machine in combination with an IGBT frequency converter small power use. • »« «• • · · * * * * · < ·» ««
    The '507 395' shows a diode of the type mentioned at the outset with an electric servo drive with a permanent magnet synchronous machine in combination with an IGBT frequency converter.
    Due to the particularly exposed position of e.g. Off-shore equipment is a high system availability of particular importance. The invention is therefore based on the task of taking appropriate precautions, so that even if a differential drive system fails, the system can continue to operate.
    This object is achieved with a differential gear with the features of claim 1 and with an energy recovery system, in particular wind turbine, with the features of claim 1.
    In the invention, the power plant can continue to operate in case of failure of a differential drive and / or a frequency converter with at least half the rated power of the system.
    Preferred embodiments of the invention are subject-matter of the subclaims.
    Hereinafter, preferred embodiments of the invention will be described in detail with reference to the accompanying drawings.
    It shows:
    Fig. 1 shows the principle of a differential gear with an electric differential drive according to the prior art, Fig. 2 shows a first embodiment according to the invention of a redundant structure of an electric differential drive and
    Fig. 3 shows another embodiment of a redundant differential drive according to the invention.
    The power of the rotor of a wind turbine is calculated from the formula
    Rotor power = Rotor area * Power coefficient * Air density / 2 * Wind speed3, the power factor depending on the speed factor (= ratio of blade tip speed to wind speed) of: 3 • · t · * »·» · • · · · * · · * · »·« «« * · * # * · Φ |
    Wind power day * is rotor. A red wind turbine is designed for an optimum power coefficient based on a fast-running number (usually a value between 7 and 9) to be determined during development. For this reason, when operating the wind turbine in the partial load range, a correspondingly low speed must be set in order to ensure optimum aerodynamic efficiency.
    Fig. 1 shows a possible principle of a differential system for a wind turbine with a differential stage 4 or 11 to 13, an adjustment gear stage 5 and an electric differential drive 6. A rotor 1 of the wind turbine, on a drive shaft 2 for a main transmission sits, drives the main gearbox 3. The main transmission 3 is a 3-stage transmission with two planetary stages and a spur gear. Between the main gear 3 and a generator 8 is a differential stage 4, which is driven by the main gear 3 via a planet carrier 12 of the differential stage 4. A generator 8, preferably a third-excited medium-voltage synchronous generator, is connected to a ring gear 13 of the differential stage 4 and is driven by the latter. A pinion 11 of the differential stage 4 is connected to a differential drive 6. The speed of the differential drive 6 is controlled to ensure a variable speed of the rotor 1, a constant speed of the generator 8 and on the other hand to regulate the torque in the drive train of the wind turbine.
    In order to increase the input speed for the differential drive 6, in the case shown a multi-stage differential gear is selected, which has a matching gear stage 5, e.g. in the form of a spur gear, between the differential stage 4 and the differential drive 6 provides. Since in the range of the differential drive 6 and a massive clutch 14 as a connecting element between the main transmission 3 and the differential stage 6, a correspondingly large axial offset for the differential drive 6 is required. This can be done for the adaptation gear stage 5 e.g. be realized by large gear diameter or a multi-stage version of this adaptation gear stage 5.
    The differential drive 6 is preferably a three-phase machine, in particular a permanent magnet synchronous three-phase machine, which via a frequency converter 7 and a transformer 9 ans
    Net connected wirtf. Alternatively, the differential drive may also be used as e.g. hydrostatic pumps / motor combination are performed. In this case, the second pump is preferably connected to the drive shaft of the generator 8 via a further adaptation gear stage.
    The speed equation for the differential gear is:
    SpeedGenerator = x * SpeedRotor + y * SpeedDrive.drive, where the generator speed is constant, and factors x and y can be derived from the selected transmission ratios of the main and differential gears. The torque on the rotor is determined by the upcoming wind supply and the aerodynamic efficiency of the rotor. The ratio between the torque at the rotor shaft and that at the differential drive is constant, whereby the torque in the drive train can be controlled by the differential drive. The torque equation for the differential drive is:
    Dre hmomentDi (external drive = torque rotor * y / x, where the size factor y / x is a measure of the required design torque of the differential drive The power of the differential drive is essentially proportional to the product of the percentage deviation of the rotor speed Accordingly, a large speed range generally requires a correspondingly large dimensioning of the differential drive, that is, the smaller the required speed range on the drive shaft, the smaller the required differential drive and consequently also the expense for its production and operation be Turbomachines of any kind such as
    Wind turbines, water turbines or pumps, systems for the extraction of energy from ocean currents, or any type of industrial plants, which operate at a limited speed range, are therefore the ideal application areas for differential systems.
    FIG. 2 shows an extension according to the invention of the system described by way of example with reference to FIG. 1. It is understood that the inventive redundant system can also be used in other embodiments of energy production plants. The pinion 11 5 ······ · j »· drives in this AusfüMrufi ^ sfc3rm * ^ wei preferably identical matching gear stages 5 and differential drives 6 at. The differential drives 6 are each driven by a frequency converter 7. Alternatively, one could drive both differential drives 6 with a common frequency converter 7 (as shown in FIG. 3), whereby, however, only the differential drive 6 would be redundant.
    Also, the transformer 9 could be arranged redundantly.
    Due to the redundant design of the differential drive 6 or frequency converter 7 shown in FIG. 2, if one of these components fails, at least 50% of the rated torque is still available, which may also be temporarily exceeded in accordance with the thermal design. In addition, a possible reduction of the IGBT clock frequency also helps.
    As e.g. Wind turbines are operated over long periods of time in the partial load range, there is an energy yield loss only in the operating range with more than 50% of the nominal torque. Here you can make adjustments in order to temporarily achieve a higher output with higher operating speed, in this case to 50% limited torque. At a mean annual wind speed at hub height of 7.5 m / s with Rayleigh distribution (this covers a large part of the world's commercially exploitable wind areas) is statistically the energy yield loss only about 30% of the energy yield achievable with fully functional plant.
    3 shows a further embodiment according to the invention with redundant differential drives 6. In this alternative embodiment, a shaft 15 guided through a hollow shaft of the generator 8 connects the pinion 11 with two adaptation gear stages 5 and subsequently two differential drives 6 resulting advantages are that (a) the planetary stage 4 is easier and less expensive to produce and (b) no large center distance is to be bridged by the adjustment gear stages 5, since the input clutch 14 is not between the differential drives 6. : e * · ♦ * · · »··· * ·· * ·· ♦ f I #
    In order to be able to realize lower wind speeds and an optimum characteristic curve for the rotor 1 at a lower power requirement, it is generally possible in the invention to connect one or both differential drives 6 and / or one or both adaptation gear stages 5 as adjusting, such as described in WO 2008/061263 A to execute. In this case, for example, a differential drive 6 could be switched off and the second differential drive 6 can be operated further in a favorable speed range.
    权利要求:
    Claims (5)
    [1]
    ♦ ··· ··· I. The invention relates to a power generation plant, in particular a wind power plant, comprising a drive shaft, a generator (8) and a differential gear (4, 11 to 13) with three drives, a first drive with the drive shaft, an output with a generator (8) and a second drive with a differential drive (6) is connected and wherein the differential gear (4; 11 to 13) is a planetary gear, characterized in that two differential drives (6) are provided with are connected to the second drive. Power generation plant according to claim 1, characterized in that the differential drives (6) are electrical machines which are connected via a frequency converter (7) and optionally a transformer (9) to a network. Power generation plant according to claim 2, characterized in that the differential drives (6) via a common frequency converter (7) and optionally a transformer (9) are connected to a network. Power generation plant according to claim 2, characterized in that each differential drive (6) via its own frequency converter (7) and optionally a transformer (9) is connected to a network. Power generation plant according to one of claims 1 to 4, characterized in that the differential drives (6) with a sun gear (11) of the differential gear (4; 11 to 13) are connected and facing away from the differential gear (4, 11 to 13) Side of the generator (8) are arranged. Power generation plant according to one of claims 1 to 5, characterized in that the differential drives (6) via adaptation gear stages (5) with the differential gear (4, 11 to 13) are connected. • »· *« «« I 1 * * '♦ * * * * ft · »*« · * ·· · ·
    [2]
    7. Energiegewinnungäctnla§e * rtach · Ansprtrcrh 6, characterized in that at least one adjustment gear stage (5) is an adjusting gear.
    [3]
    8. Power generation plant according to one of claims 1 to 7, characterized in that at least one differential drive {6} is a pole-changing electric machine.
    [4]
    9. Power generation plant according to one of claims 1 to 7, characterized in that the differential drives (6) are hydraulic drives.
    [5]
    10. Energy production plant according to one of claims 1 to 9, characterized in that the drive shaft is the rotor shaft of a wind turbine.
    类似技术:
    公开号 | 公开日 | 专利标题
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    DE202012101708U1|2012-06-13|Differential gearbox for power generation plant
    AT508155B1|2010-11-15|ENERGY EQUIPMENT, IN PARTICULAR WIND POWER PLANT
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    EP2342455B1|2014-09-17|Wind power station
    AT13294U1|2013-10-15|Differential gear for an energy recovery plant
    WO2019030300A1|2019-02-14|Generator for a wind turbine, and wind turbine having same
    同族专利:
    公开号 | 公开日
    AT511720B1|2013-02-15|
    DE202012102872U1|2012-08-22|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    CH297231A|1951-09-17|1954-03-15|Foerderanlagen Heckel|Drive arrangement for cable cars and cable crane systems.|
    CH449362A|1965-04-24|1967-12-31|Renk Ag Zahnraeder|Planetary gear|
    WO2002040862A1|2000-11-14|2002-05-23|Aloys Wobben|Wind energy turbine|
    WO2010063052A2|2008-12-03|2010-06-10|Gerald Hehenberger|Energy production plant and method for operating the same|WO2016172742A1|2015-04-27|2016-11-03|Set Sustainable Energy Technologies Gmbh|Power train for pumps, energy generation systems or similar and method for starting up a power train of this type|AT504395B1|2006-11-21|2009-05-15|Amsc Windtec Gmbh|COMPENSATION GEAR OF A WIND POWER PLANT AND METHOD FOR MODIFYING OR SWITCHING THE PERFORMANCE OF THIS BALANCE TRANSMISSION|CN103277252B|2013-04-10|2015-01-14|浙江大学|Control method of grid connected wind turbine|
    AT514239B1|2013-04-18|2015-02-15|Set Sustainable Energy Technologies Gmbh|Drive and method for operating such a drive|
    CN103986278B|2013-08-01|2017-12-22|威海戥同测试设备有限公司|Different motor|
    AT15388U1|2015-07-13|2017-07-15|Ing Gerald Hehenberger Dipl|Drive train and method for operating a drive train|
    CN106194594A|2016-07-11|2016-12-07|上海电力学院|A kind of sustainable work and the low offshore wind farm speeder of maintenance cost|
    CN109209784B|2018-09-30|2020-09-01|浙江大学|Control method of wind power generation system|
    法律状态:
    2020-08-15| MM01| Lapse because of not paying annual fees|Effective date: 20190901 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA1252/2011A|AT511720B1|2011-09-01|2011-09-01|ENERGY RECOVERY SYSTEM|ATA1252/2011A| AT511720B1|2011-09-01|2011-09-01|ENERGY RECOVERY SYSTEM|
    DE202012102872U| DE202012102872U1|2011-09-01|2012-07-31|Energy recovery plant|
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