WO2000017543A1 - Procede et dispositif permet de reguler la vitesse dans des transmissions a rapport d'engrenage eleve - Google Patents

Procede et dispositif permet de reguler la vitesse dans des transmissions a rapport d'engrenage eleve Download PDF

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Publication number
WO2000017543A1
WO2000017543A1 PCT/SE1999/001519 SE9901519W WO0017543A1 WO 2000017543 A1 WO2000017543 A1 WO 2000017543A1 SE 9901519 W SE9901519 W SE 9901519W WO 0017543 A1 WO0017543 A1 WO 0017543A1
Authority
WO
WIPO (PCT)
Prior art keywords
speed
transmission
generator
primary
shaft
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.)
Ceased
Application number
PCT/SE1999/001519
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English (en)
Inventor
Roland Davidson
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to AU63764/99A priority Critical patent/AU6376499A/en
Publication of WO2000017543A1 publication Critical patent/WO2000017543A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • 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
    • F03D15/00—Transmission of mechanical power
    • 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
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • F03D9/20—Wind motors characterised by the driven apparatus
    • F03D9/25—Wind motors characterised by the driven apparatus the apparatus being an 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
    • F05B2260/40—Transmission of power
    • F05B2260/403—Transmission of power through the shape of the drive components
    • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • F05B2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclic, planetary or differential type
    • 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 method and a device for rotational speed control and for achieving a high gear reduction, (from about 50:1 to 100:1) in transmissions, more particularly for such transmissions where the rotational speed at one side is very low and required, for various reasons, to be variable, whilst the speed at the other side is generally high and often preferably constant.
  • the most suitable gearbox for such a transmission is the epicyclical or planetary gearbox, and the present invention thus preferably relates to methods and devices for speed control and for achieving a high gear reduction in planetary gear transmissions.
  • a typical application for a transmission of the type mentioned above is a wind power generation plant, and the below description will therefore be made concrete using a wind power plant as an example.
  • Wind power plants today one of the world's most rapidly expanding trades, require transmissions with a high gear reduction.
  • a wind turbine typically works at a speed of about 15 - 20 rpm, whereas a generator, in order to become of standard design and thus be reasonably economical in manufacture, should run with at least 1500 rpm.
  • a transmission having such a gear ratio is commonly embodied as a planetary gear transmission having several stages, but will still be very large and heavy.
  • generators with two fixed speeds are today commonly used, making the transmission still larger and heavier.
  • As the transmission is located at the top of the tower of the wind power plant, this size and weight will create problems during assembly as well as maintenance work.
  • the generator In order then to reach the network frequency of 50 Hz, the generator must have a multitude of poles and/or a large diameter in order to reach a sufficient peripheral speed.
  • the generator As the generator is located at the top of the tower of the wind power plant, behind the actual wind turbine, there will be physical limitations to its size, for the same reasons as regarding the transmission. Furthermore, in this case the generator would have to be of special manufacture, making it expensive.
  • frequency converters are used to achieve the appropriate frequency.
  • the frequency converter may in this case further be used to allow the speed of the wind turbine to vary with the wind speed, whilst still delivering, via the frequency converter, 50 Hz to the network.
  • Fig. 1 shows a very schematical principle drawing of how known components could be interconnected, in accordance with the method of the invention, to form a device according to the invention.
  • Fig. 1 shows a planetary gear transmission having an input shaft 1, fixedly connected to the transmission ring gear 2.
  • the planetary gear transmission has, in a known manner, a number of planetary gears 3, mounted on a planet carrier 5 and rotating in constant mesh with the ring gear 2 and a sun gear 4.
  • the sun gear is, via a shaft 8, connected to an electrical primary generator 9.
  • the planet carrier 5 is, via a hollow shaft 6, connected to an electrical secondary generator 7.
  • the primary generator 9 is, as regards frequency, directly connected to a frequency-stable, three-phase electrical network 12, and may be of the novel high- tension type developing 10.000 Volts, allowing direct connection to the network as illustrated in Fig. 1.
  • the generator 9 may also be of the conventional type, developing a lower tension, in that case connected to the network via a transformer (not shown).
  • the secondary generator 7 is connected to the frequency-stable electrical network 12 via a frequency converter 10 and a transformer 11. However, the secondary generator may also be of the high-tension type, eliminating the need for the transformer 11.
  • the prime mover in this embodiment example would be a wind turbine
  • said turbine would, in a known manner, be connected to the input shaft 1 of the planetary gear transmission, which, in this embodiment example, is connected to the ring gear 2 of the transmission.
  • a brake arrangement for braking and locking the wind turbine an immobile position. The wind turbine and the braking arrangement are not shown.
  • the planetary gear transmission is assumed to have a gear ratio of 1 :3 between the rotational speed of the planet carrier 5 and that of the sun gear 4, if the ring gear 2 is immobile.
  • the primary generator 9 is assumed to have only one pair of poles, thus rotating at 3000 rpm when phased into a 50 Hz network.
  • the secondary generator 7 is assumed to have three pairs of poles and would then, if phased directly into a 50 Hz network, rotate at 1000 rpm. However, as the secondary generator is connected to the 50 Hz electrical network via a variable frequency converter, the rotational speed of the secondary generator, in the synchronised or phased-in state, can be made to vary within a range around these 1000 rpm.
  • the sun gear 1, being connected to the electrical primary generator 9, is forced by the stable network 12 and the synchronised primary generator 9 to rotate clockwise at 3000 rpm.
  • the frequency converter 10 is adjusted to a conversion factor of 1, i.e. no conversion, and that the planet carrier 5, being connected to the secondary generator 7, is forced by the stable network 12 and the synchronised secondary generator 7 to rotate clockwise at 1000 rpm.
  • the ring gear 2 will then, as the gear ratio between the planet carrier 5 and the sun gear 4 is 1 :3, and the ratio between their respective speeds are also 1:3, be standing completely still.
  • the synchronised rotational speed of the secondary generator will increase or decrease from 1000 rpm.
  • the ring gear 2 of the planetary gear transmission will begin to rotate at a speed varying with the difference between the speed of the primary generator 9 and the speed of the secondary generator 7, multiplied by the gear ratio between the planet carrier and the ring gear of the transmission.
  • the gear ratio between the ring gear 2 and the planet carrier 5 will be 2:3.
  • the extremely frequency-stable electrical network 12 is thus used for maintaining one of the three movable main components (sun wheel 4/primary output shaft 8) of the planetary gear transmission at a constant, relatively high speed, rather than, as in the conventional way, maintaining one main component immobile, that is at the constant speed of zero.
  • Another one of the transmission main components (planet carrier 5/secondary output shaft 6) is allowed to rotate at a speed that is also very stable (due to the electrical network 12) but adjustable (thanks to the frequency converter 10) about that nominal rotational speed where the speeds of the two transmission main components (4, 5) concerned, with regard to the gear ratios, cancel each other out, making the third main component (ring gear 2/input shaft 1) stand still.
  • the rotational speed of the input shaft 1 can be continuously controlled in both directions about zero rpm, through varying the setting of the frequency converter 10.
  • the setting of the frequency converter 10 can easily, and in a known manner, e.g. by a microprocessor-based control system, be controlled in response to an external parameter, in the described embodiment example e.g. in response to the wind speed, hereby allowing the rotational speed of the wind turbine to be continuously adjusted in relation to the wind speed.
  • an extremely high gear ratio between the input shaft 1 and the primary output generator shaft 8 in the demonstrated embodiment example no less than 3000:20 or 150:1, and between the input shaft 1 and the secondary output generator shaft 6 about 1030:20 or 51,5:1, on the other an elegant possibility of continuous speed control of the input drive shaft 1, in the clockwise as well as the anti-clockwise direction. Thanks to the stability of the electrical network 12, the control will be independent of changes in the input power on the input shaft 1; if the power increases, the two generators 7 and 9 will simply generate more power onto the electrical network 12. We assume, as a matter of course, that all components in the device are adapted to their required power, speed, torque, etc.
  • the device is started in the following manner: a.
  • the shaft 1 of the wind turbine is initially braked and immobile.
  • the secondary generator 7 is started unexcited (on idle) by regulating the frequency converter 10 from the frequency zero and upwards, and is phased into the net at its nominal speed, i.e. 1000 rpm.
  • the ring gear 2 of the transmission is standing still. This entails that when the secondary generator 7 starts to rotate, the rotation of the planet carrier 5 will also rotate the sun gear 4, and thereby the primary generator 9, which is also started and phased unexcited (on idle) into the network at its 3000 rpm.
  • both generators are phased-in or synchronised, they are excited, at the same time as the wind turbine brake is released and the frequency converter
  • the rotational speed of the wind turbine can now easily be adapted to the wind speed in an optimum way, by measuring the wind speed in a known manner and controlling the conversion factor of the frequency converter 10 in response thereof, for example via a microcomputer, making the wind turbine adapt its rotational speed continuously, in an optimum manner, to the wind speed.
  • the method and the device according to the invention could also be applied in a case where no shaft could be maintained at a stable and constant speed.
  • the speed of one of the transmission main components e.g. planet carrier 5/secondary output shaft 6
  • an external parameter e.g. the wind speed
  • another main component e.g. sun gear 4/primary output shaft 8
  • the speed of the secondary output shaft 6 to vary about a nominal speed that is a constant factor times the speed of the primary output shaft 8, the constant factor being equal to the transmission gear ratio between the two shafts 6 and 8.
  • a constant speed of the third transmission main component e.g. ring gear 2/input shaft 1 will still be maintained, even if the speed of the primary output shaft 8 is varied, as the speed of the secondary output shaft 6 is varied simultaneously, by the external parameter through the control system, with a corresponding amount, considering the transmission gear ratio.
  • the method and the device according to the invention thus provides among others a continuous speed control of the input shaft 1, as a function of an external parameter, said control being completely independent of the input power applied onto said shaft, whilst simultaneously providing an extremely high gear ratio between the input shaft 1 and the two output shafts 6 and 8, without requiring to that end a larger and heavier transmission.
  • This allows a large generator diameter and a high generator weight to be avoided, and the costs to be kept down.

Landscapes

  • 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)
  • Power Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

Cette invention concerne un procédé et un dispositif qui permettent de réguler la vitesse dans des transmission qui possèdent un rapport d'engrenage élevé, et dans lesquelles la vitesse de rotation d'un côté est très faible et doit devenir variable, tandis que la vitesse de rotation de l'autre côté est élevée. Ce procédé et ce dispositif permettent de réguler en continu la vitesse de rotation de l'arbre d'entrée (1) en fonction d'un paramètre externe, ceci tout en maintenant un rapport d'engrenage très élevé entre l'arbre d'entrée (1) et les deux arbres de sortie (6, 8). A cette fin, on dispose les trois arbres de manière qu'ils puissent entrer en rotation simultanément, et l'on régule la vitesse de rotation de l'arbre de sortie secondaire (6) de sorte qu'elle varie, en fonction d'un paramètre externe, par rapport à une vitesse nominale. Cette vitesse nominale est un facteur constant qui est égal au rapport d'engrenage de la transmission entre les deux arbres (6, 8) multiplié par la vitesse de rotation de l'arbre de sortie primaire (8). La vitesse de rotation de l'arbre d'entrée (1) est ainsi fonction de la différence entre les vitesses desdits arbres (6, 8).
PCT/SE1999/001519 1998-09-21 1999-09-03 Procede et dispositif permet de reguler la vitesse dans des transmissions a rapport d'engrenage eleve Ceased WO2000017543A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU63764/99A AU6376499A (en) 1998-09-21 1999-09-03 Method and device for rotational speed control in high gear ratio transmissions

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE9803182A SE512798C2 (sv) 1998-09-21 1998-09-21 Sätt och anordning för varvtalsreglering vid transmissioner med hög varvtalsutväxling
SE9803182-6 1998-09-21

Publications (1)

Publication Number Publication Date
WO2000017543A1 true WO2000017543A1 (fr) 2000-03-30

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ID=20412647

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE1999/001519 Ceased WO2000017543A1 (fr) 1998-09-21 1999-09-03 Procede et dispositif permet de reguler la vitesse dans des transmissions a rapport d'engrenage eleve

Country Status (3)

Country Link
AU (1) AU6376499A (fr)
SE (1) SE512798C2 (fr)
WO (1) WO2000017543A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003053782A1 (fr) * 2001-12-06 2003-07-03 Honeywell International Inc. Turbine a air a boitier d'engrenage multiplicateur
WO2010135754A2 (fr) 2009-05-25 2010-12-02 Gerald Hehenberger Installation de production d'énergie, en particulier éolienne
EP1985850A4 (fr) * 2005-12-23 2014-11-26 Dongfang Turbine Co Ltd Ensemble support planétaire destiné à une éolienne, transmission pour celle-ci et éolienne

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103967721A (zh) * 2014-05-23 2014-08-06 张东升 一种风力发电机组
SE2100126A1 (sv) * 2021-08-18 2023-02-19 Roland Davidsson Elektromekanisk drivlina för fordon

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4112311A (en) * 1975-12-18 1978-09-05 Stichting Energieonderzoek Centrum Nederland Windmill plant for generating energy
US4556801A (en) * 1981-07-07 1985-12-03 Snamprogetti S.P.A. Method for utilizing wind energy for autonomous electricity production
EP0635639A1 (fr) * 1993-07-21 1995-01-25 Ashot Ashkelon Industries Ltd. Transmission pour éoliènne
US5476293A (en) * 1993-02-22 1995-12-19 Yang; Tai-Her Electric energy storage and distribution system of differential distribution type

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4112311A (en) * 1975-12-18 1978-09-05 Stichting Energieonderzoek Centrum Nederland Windmill plant for generating energy
US4556801A (en) * 1981-07-07 1985-12-03 Snamprogetti S.P.A. Method for utilizing wind energy for autonomous electricity production
US5476293A (en) * 1993-02-22 1995-12-19 Yang; Tai-Her Electric energy storage and distribution system of differential distribution type
EP0635639A1 (fr) * 1993-07-21 1995-01-25 Ashot Ashkelon Industries Ltd. Transmission pour éoliènne

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003053782A1 (fr) * 2001-12-06 2003-07-03 Honeywell International Inc. Turbine a air a boitier d'engrenage multiplicateur
US6676379B2 (en) 2001-12-06 2004-01-13 Honeywell International Inc. Ram air turbine with speed increasing gearbox
US7077631B2 (en) 2001-12-06 2006-07-18 Honeywell International, Inc. Ram air turbine with speed increasing gearbox
EP1985850A4 (fr) * 2005-12-23 2014-11-26 Dongfang Turbine Co Ltd Ensemble support planétaire destiné à une éolienne, transmission pour celle-ci et éolienne
WO2010135754A2 (fr) 2009-05-25 2010-12-02 Gerald Hehenberger Installation de production d'énergie, en particulier éolienne
WO2010135754A3 (fr) * 2009-05-25 2011-03-03 Gerald Hehenberger Installation de production d'énergie, en particulier éolienne

Also Published As

Publication number Publication date
AU6376499A (en) 2000-04-10
SE9803182D0 (sv) 1998-09-21
SE9803182L (sv) 2000-03-22
SE512798C2 (sv) 2000-05-15

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