WO2003081027A1 - Aube entretoise et aube directrice d'une turbine francis - Google Patents

Aube entretoise et aube directrice d'une turbine francis Download PDF

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Publication number
WO2003081027A1
WO2003081027A1 PCT/EP2003/003007 EP0303007W WO03081027A1 WO 2003081027 A1 WO2003081027 A1 WO 2003081027A1 EP 0303007 W EP0303007 W EP 0303007W WO 03081027 A1 WO03081027 A1 WO 03081027A1
Authority
WO
WIPO (PCT)
Prior art keywords
blade
blades
guide
ring
fixed support
Prior art date
Application number
PCT/EP2003/003007
Other languages
German (de)
English (en)
Inventor
Ernst-Ulrich Jaeger
Gerhard Wengert
Armin Otto
Ulrich Seidel
Original Assignee
Voith Siemens Hydro Power Generation Gmbh & Co. Kg
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 Voith Siemens Hydro Power Generation Gmbh & Co. Kg filed Critical Voith Siemens Hydro Power Generation Gmbh & Co. Kg
Publication of WO2003081027A1 publication Critical patent/WO2003081027A1/fr

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
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
    • F03B3/16—Stators
    • F03B3/18—Stator blades; Guide conduits or vanes, e.g. adjustable
    • F03B3/183—Adjustable vanes, e.g. wicket gates
    • 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
    • F05B2240/00—Components
    • F05B2240/20—Rotors
    • F05B2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05B2240/31—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor of changeable form or shape
    • F05B2240/312—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor of changeable form or shape capable of being reefed
    • 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
    • Y02E10/20—Hydro energy

Definitions

  • the invention relates to a Francis turbine or pump or pump turbine, in particular the diffuser of such a turbine, which serves to supply the water to the impeller.
  • Water turbines such as Francis turbines are subject to increasingly higher requirements with regard to efficiency and the largest possible working area.
  • a variable use with regard to the water flow rate from extreme part-load operation to overload operation is desirable. In all load ranges, the highest possible efficiency with vibration-free running of the turbine should be achieved.
  • Francis turbines are adapted to different operating conditions by adjusting the guide vanes. Nevertheless, unsteady flow conditions occur, especially under partial load, which lead to strong vibrations on the machine. Material damage as a result can occur in particular if the natural frequencies of components match these vibrations.
  • Another negative consequence of turbine vibrations, especially for large machines, is the impact that these vibrations have on the power grid. Synchronous unrest is coupled into the power grid via the generator and there is unpleasantly noticeable as power fluctuations. This results in disadvantageous restrictions on the turbine operating range.
  • Critical partial load areas can be passed through particularly quickly when the turbine is started up and avoided in continuous operation. In addition, there is an undesirable mutual influence of water-bearing systems.
  • Baffles can be designed as fins, which are oriented in the axial direction. This shape leads to suppression of the swirl in the intake manifold, but this is associated with the disadvantage of reduced efficiency.
  • variable baffles have been developed that can be swiveled around an axis parallel to the machine axis depending on the operating conditions. Further designs of baffles are oriented parallel to the wall surfaces of the intake manifold and thus prevent flow areas from becoming detached by stabilizing the flow between baffle and intake manifold wall. Like the aforementioned fin-like structures, this construction also reduces the energy yield of the turbines. Furthermore, such static or variable designs increase the effort for the manufacture and maintenance of turbines and are therefore a cost-relevant factor.
  • the invention has for its object to design a machine of the type mentioned in such a way that pressure fluctuations at any point in the machine are minimized under different operating conditions.
  • the inventor has recognized the following: If the direction of flow of the water to the moving blade is changed when the guide blades are adjusted about their pivot axes, shock losses and deflection losses occur at certain angular positions of the guide blades. This means that the machine has only one certain operating area has the necessary smoothness, but vibrates in other operating areas.
  • the support blades or the guide blades are not made stationary, but are displaceable, and preferably also during operation.
  • the individual guide vane can still be pivoted in order to be able to adapt the operation to given conditions at any time, for example to a given surface water level.
  • the individual guide vane can be moved to counteract undesirable pressure fluctuations. It may be sufficient for only a few guide vanes of a guide vane ring to be displaceable, and in extreme cases only a single guide vane. By moving guide vanes, a vibration in the machine can be impaired or disturbed or superimposed by other vibrations so that it no longer appears.
  • a second alternative consists of at least one support blade and / or
  • the blade is divided into two parts, which are connected to one another in an articulated manner and which can be brought into specific angular positions relative to one another via the joint.
  • the second alternative can also be realized in that at least one blade can be changed in volume, for example in that it is at least partially hollow and at least partially consists of an elastic material. For example, it can be inflated so that it changes its total volume. However, it can also be designed in such a way that only part of its wall consists of elastic material which bulges outwards when an overpressure is introduced into the hollow interior of the blade or pulls into the cavity when an underpressure is applied.
  • a third alternative is to equip the machine with irregularities from the outset. Such irregularities can consist in the irregular arrangement of fixed or movable guide vanes. For example, the mutual distance between two adjacent ones
  • Guide vanes are chosen differently than between another pair of adjacent guide vanes.
  • the geometry of certain guide vanes can also be different from the outset than that of the other guide vanes. Such irregularities can be determined constructively from the outset, without which they can be changed later.
  • the machine is preferably equipped with a sensor and regulating or control device.
  • the sensor device detects the vibration level of the machine or individual elements of the machine, for example in the blade-free space between the guide vane and the impeller. The measured value is then compared to a target value. If the vibration level deviates from a setpoint, a central process unit initiates it
  • CPU an intervention in the sense of a change in the guide vane designed according to the invention.
  • the first alternative can also be realized, for example, by making the swivel axis tiltable so that it can also take any course relative to the machine axis, thus inclined towards the machine axis.
  • One way of realizing the first alternative can also be to place one or more support blades or guide vanes happens finely in the form of an oscillation or vibration. The deflections of the deplacement can thus be minimal and at high frequency.
  • the second alternative can be realized, for example, in that the guide vane has a telescopic structure. Accordingly, it consists of two or more parts which are telescopically fitted into one another and which can thus be moved into one another or moved away from one another.
  • the first alternative can also be realized in that the entire guide vane ring can be rotated in the radial direction about its own axis, or in that individual segments of the guide vane ring can be rotated around the axis of rotation.
  • An interesting variant of the first alternative is to set at least one guide vane to vibrate. Dislocation also takes place, albeit to a minimal extent.
  • the idea of applying a vibration to guide vanes is known, but for a different purpose and not in conjunction with the other features mentioned here, namely a sensor system for detecting the actual vibration state and a CPU for initiating countermeasures against excessive vibrations.
  • the blades of the truss ring can thus also be dislocated according to the invention - first alternative - or change in shape - second alternative.
  • the invention is explained in more detail with reference to the drawing. The following is shown in detail:
  • Figure 1 shows a Francis turbine in an axial section.
  • FIGS. 2-7 show support blades and pivotable guide blades of a Francis turbine each in a meridian section.
  • FIG. 8 shows a first embodiment of a guide vane with a changeable outer contour.
  • FIG. 9 shows a second embodiment of a guide vane with a variable outer contour.
  • FIG. 10 contains a diagram which illustrates the possibilities of compensating for undesired pressure pulsations by forced vibrations from rotatable guide vanes.
  • the Francis turbine shown in FIG. 1 is constructed as follows:
  • An impeller 1 comprises a plurality of blades 1.1. It is rotatable about an impeller axis 1.2.
  • the impeller 1 with its blades 1.1 is surrounded by a spiral housing 2.
  • the impeller 1 is preceded by a ring of fixed support blades 3, followed by a ring of pivotable guide blades 4.
  • the turbine has a suction pipe 5.
  • This includes an inlet diffuser 5.1 with an axis 5.1.1, an adjoining manifold 5.2, and an adjoining suction box 5.3.
  • FIG. 2 shows a ring of fixed support blades 3, also called a “traverse ring”.
  • Radially inside the crossbar ring is a ring of guide vanes 4. These can be rotated about an axis 4.1 in order to adjust the width between two respectively adjacent guide vanes 4, and thus at the same time the throughput of the incoming water flow.
  • each guide vane can perform a rotary movement about the associated axis of rotation 4.1.
  • the rotatable guide vanes 4 are again displaceable, but not in the circumferential direction but in the radial direction.
  • the size of the displacement path can be freely selected. This applies to all of the examples shown here, in which a displacement of guide vanes is provided (first alternative). This applies to Figures 2 to 4.
  • FIG. 3 uses one of the rotatable guide vanes 4 to illustrate a displacement possibility that differs from that of FIGS. 2 and 3. See the blade 4 shown on the far left in FIG. 4.
  • the double arrow A indicates the possibility of rotating this blade about its axis of rotation 4.1
  • double arrow B indicates the displacement of the blade.
  • double arrow B essentially runs in the direction of the longitudinal axis 4.2 of the blade profile.
  • FIG. 5 again shows fixed support blades 3 and rotatable guide blades 4.
  • a special structure can be seen from the fixed guide blade 3 shown on the left.
  • This blade 3 is constructed from two components, namely from blade part 3.3 and from blade part 3.4.
  • Blade part 3.3 forms a sleeve into which blade part 3.4 is inserted.
  • Blade part 3.4 can be telescopically extended and retracted from blade part 3.3, in the direction of the double arrow B. This extends essentially in the direction of the longitudinal axis 3.2 of the blade profile. Bucket part 3.3 remains stationary during the sliding movement of bucket part 3.4.
  • the embodiment shown here differs from that according to FIGS. 2 to 4.
  • the outer contour of the blade 3 can be changed. This measure can be carried out with all fixed guide vanes 3, but also only with some or with a single one.
  • FIG. 6 shows guide vanes in which the outer contour can also be changed. This is the case, for example, with one of the fixed support blades 3.
  • This consists of two parts, namely a fixed part 3.3 and a pivotable part 3.4. The two parts are articulated to one another by an axis of rotation 3.1.
  • the rotatable guide vane 4 shown on the left thus comprises two parts 4.3, 4.4. These can be pivoted in different ways - see the double arrows C and D. While, for example, blade part 4.3 can execute a certain pivot angle, blade part 4.4 can execute a different pivot angle.
  • the tail region 4.4 of the vane profile can be bent such that it is pivoted out of the longitudinal axis 4.2.
  • the rotatable guide vanes 4 are in turn divided into a front part 4.3 and a rear part 4.4.
  • the entire blade 4 can be pivoted about an axis of rotation 4.1 in the manner shown above, but the rear part 4.4 of the rotatable guide blade can be pivoted through a different angle than the front part 4.3.
  • the guide vane 3 shown in Figure 8 is made of an elastic material and is hollow.
  • the cavity has a compressed air connection. If compressed air is admitted into the cavity, the outer contour 3.8 of the blade 3 is changed to the outer contour 3.9.
  • the head part 3.10 consists of elastic material, while the main part 3.11 consists of steel.
  • the head part 3.10 is attached to the main part 3.11. There is a cavity in the area of the head part. This in turn has a compressed air connection.
  • the outer contour 3.8 is changed to the outer contour 3.9.
  • Pressure pulsations are plotted on the ordinate, time on the abscissa. Three curves I, II and III can be seen. Curve I illustrates the pressure pulsations that the machine has.
  • Curve II illustrates vibrations that are applied in the area of the guide apparatus, for example in the case of one or more rotatable guide vanes.
  • Curve III illustrates the resulting pressure pulsations from the machine. As can be seen, the amplitudes of these pressure pulsations are greatly minimized compared to the amplitudes of curve I.
  • curve I will be determined by measurements at critical points on the machine, for example in the intake manifold, in the vane-free space, in the spiral, or at other locations.
  • Curve II can be generated, for example, by rotating one or more rotatable guide vanes, i. H. closed and opened again, namely by a minimum angle of, for example, 1 °.
  • the opening and closing can take place at relatively high frequencies, for example at a frequency of 0.1-100 Hz, thus at a frequency somewhere between these two limit values. Deviations upwards and downwards are also possible.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Turbines (AREA)

Abstract

L'invention concerne une turbine Francis ou une machine spéciale conçue selon le principe Francis. La turbine Francis selon l'invention est équipé d'une roue à aubes présentant des aubes mobiles et d'un carter en spirale qui entoure la roue à aubes. Une couronne d'aubes entretoises fixes est montée en aval du carter en spirale. Une couronne d'aubes directrices rotatives est montée en aval de la couronne d'aubes directrices fixes. Au moins une aube directrice peut être déplacée ou son contour externe peut être modifié. Un dispositif détecteur permet de détecter le comportement vibratoire ou autres paramètres de la machine dans son ensemble ou de certaines pièces de la machine. L'invention concerne une unité processeur centrale (CPU) qui, lors du dépassement de valeurs théoriques des paramètres, commande un déplacement des aubes directrices ou une modification de leur contour externe.
PCT/EP2003/003007 2002-03-27 2003-03-22 Aube entretoise et aube directrice d'une turbine francis WO2003081027A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10213774.9 2002-03-27
DE10213774A DE10213774A1 (de) 2002-03-27 2002-03-27 Francis-Turbine oder Francis-Pumpe oder Francis-Pumpturbine

Publications (1)

Publication Number Publication Date
WO2003081027A1 true WO2003081027A1 (fr) 2003-10-02

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ID=28050918

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2003/003007 WO2003081027A1 (fr) 2002-03-27 2003-03-22 Aube entretoise et aube directrice d'une turbine francis

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DE (1) DE10213774A1 (fr)
WO (1) WO2003081027A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102011672A (zh) * 2010-12-08 2011-04-13 清华大学 一种采用新型导叶和转轮叶片型线的混流式水轮机
CN102072074A (zh) * 2010-12-28 2011-05-25 华东宜兴抽水蓄能有限公司 水泵工况导叶预开建压方法
CN107143458A (zh) * 2017-05-15 2017-09-08 中国水利水电科学研究院 一种减轻水泵水轮机动静干涉及厂房振动的方法
CN108915931A (zh) * 2018-07-09 2018-11-30 中国水利水电科学研究院 减轻抽水蓄能电站机组和厂房振动的水泵水轮机设计方法
NO20211453A1 (no) * 2021-01-29 2022-08-01 Ec Utvikling As Reguleringsanordning for ledeskovler til Francisturbin

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100427753C (zh) * 2005-11-18 2008-10-22 清华大学 一种h型流道转轮的混流式水轮机
DE102011112521A1 (de) 2011-09-07 2013-03-07 Voith Patent Gmbh Francis-Turbine oder Francis-Pumpe oder Francis-Pumpturbine
WO2013182210A1 (fr) * 2012-06-05 2013-12-12 Ferme Jean-Marc Distributeur mobile a deux degres de liberte

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1256170B (de) * 1961-12-28 1967-12-07 Voith Gmbh J M Leitapparat fuer Stroemungsmaschinen
FR2492007A2 (fr) * 1980-08-05 1982-04-16 Joly Michel Panneau deflecteur telescopique pour grande eolienne
US5029440A (en) * 1990-01-26 1991-07-09 The United States Of America As Represented By The Secretary Of The Air Force Acoustical anti-icing system
DE19803390C1 (de) * 1998-01-29 1999-02-11 Voith Hydro Gmbh & Co Kg Laufrad für eine Strömungsmaschine, insbesondere für eine Francisturbine
DE19741992A1 (de) * 1997-09-24 1999-03-25 Voith Hydro Gmbh & Co Kg Strömungsmaschine, insbesondere Wasserturbine
US6139268A (en) * 1999-03-19 2000-10-31 The United States Of America As Represented By The Secretary Of The Air Force Turbine blade having an extensible tail

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE224977C (fr) *
DE22311C (de) * M. & J. FEDER in Eupen Mechanismus zum Reguliren des Wasserefn/auis bei Tangentia/turbinen
DE19531789C2 (de) * 1995-08-30 2000-05-11 Gerhard Fink Elastische Leitschaufel für Turbinenregelung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1256170B (de) * 1961-12-28 1967-12-07 Voith Gmbh J M Leitapparat fuer Stroemungsmaschinen
FR2492007A2 (fr) * 1980-08-05 1982-04-16 Joly Michel Panneau deflecteur telescopique pour grande eolienne
US5029440A (en) * 1990-01-26 1991-07-09 The United States Of America As Represented By The Secretary Of The Air Force Acoustical anti-icing system
DE19741992A1 (de) * 1997-09-24 1999-03-25 Voith Hydro Gmbh & Co Kg Strömungsmaschine, insbesondere Wasserturbine
DE19803390C1 (de) * 1998-01-29 1999-02-11 Voith Hydro Gmbh & Co Kg Laufrad für eine Strömungsmaschine, insbesondere für eine Francisturbine
US6139268A (en) * 1999-03-19 2000-10-31 The United States Of America As Represented By The Secretary Of The Air Force Turbine blade having an extensible tail

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102011672A (zh) * 2010-12-08 2011-04-13 清华大学 一种采用新型导叶和转轮叶片型线的混流式水轮机
CN102072074A (zh) * 2010-12-28 2011-05-25 华东宜兴抽水蓄能有限公司 水泵工况导叶预开建压方法
CN102072074B (zh) * 2010-12-28 2013-03-20 国家电网公司 水泵工况导叶预开建压方法
CN107143458A (zh) * 2017-05-15 2017-09-08 中国水利水电科学研究院 一种减轻水泵水轮机动静干涉及厂房振动的方法
CN107143458B (zh) * 2017-05-15 2019-08-09 中国水利水电科学研究院 一种减轻水泵水轮机动静干涉及厂房振动的方法
CN108915931A (zh) * 2018-07-09 2018-11-30 中国水利水电科学研究院 减轻抽水蓄能电站机组和厂房振动的水泵水轮机设计方法
CN108915931B (zh) * 2018-07-09 2020-08-21 中国水利水电科学研究院 减轻抽水蓄能电站机组和厂房振动的水泵水轮机设计方法
NO20211453A1 (no) * 2021-01-29 2022-08-01 Ec Utvikling As Reguleringsanordning for ledeskovler til Francisturbin
NO20210111A1 (no) * 2021-01-29 2022-08-01 Ec Utvikling As Reguleringsanordning for ledeskovler til Francisturbin
NO347411B1 (no) * 2021-01-29 2023-10-23 Weis As Reguleringsanordning for ledeskovler til Francisturbin

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