WO2012024704A1 - Machine à pression de retenue hydraulique - Google Patents

Machine à pression de retenue hydraulique Download PDF

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Publication number
WO2012024704A1
WO2012024704A1 PCT/AT2011/000331 AT2011000331W WO2012024704A1 WO 2012024704 A1 WO2012024704 A1 WO 2012024704A1 AT 2011000331 W AT2011000331 W AT 2011000331W WO 2012024704 A1 WO2012024704 A1 WO 2012024704A1
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WO
WIPO (PCT)
Prior art keywords
machine
dynamic pressure
hub
modules
impeller
Prior art date
Application number
PCT/AT2011/000331
Other languages
German (de)
English (en)
Inventor
Andreas Sternecker
Original Assignee
Maschinenfabrik Kba-Mödling Aktiengesellschaft
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 Maschinenfabrik Kba-Mödling Aktiengesellschaft filed Critical Maschinenfabrik Kba-Mödling Aktiengesellschaft
Publication of WO2012024704A1 publication Critical patent/WO2012024704A1/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
    • F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
    • F03B13/08—Machine or engine aggregates in dams or the like; Conduits therefor, e.g. diffusors
    • 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
    • F03B7/00—Water wheels
    • 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
    • F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/18—Structural association of electric generators with mechanical driving motors, e.g. with turbines
    • H02K7/1807—Rotary generators
    • H02K7/1823—Rotary generators structurally associated with turbines or similar engines
    • 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
    • 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
    • F05B2250/00—Geometry
    • F05B2250/30—Arrangement of components
    • F05B2250/31—Arrangement of components according to the direction of their main axis or their axis of rotation
    • F05B2250/312—Arrangement of components according to the direction of their main axis or their axis of rotation the axes being parallel to each other
    • 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
    • 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 hydro-dynamic pressure machine with at least one rotatably mounted in a frame impeller having a hub and associated blades, and which defines a water level in operation as a difference between a head level and an underwater level, and with a with the impeller via a Gearbox coupled in a module with this combined electric motor-generator machine.
  • Hydropower dynamic pressure machines are known from AT 404 973 B and AT 501 575 AI.
  • the impeller is arranged transversely to the flow direction in a channel.
  • the hub of the impeller can replace a weir, which in hydraulic engineering is understood to mean a reservoir that closes off a flow region.
  • weirs can be overflowed or flowed through as needed, the section of the channel in the direction of flow above the weir as upper water and the section of the channel below the weir is referred to as underwater.
  • weirs with low stowage heights were only provided for damming water as required; Starting from this it was proposed in AT 404 973 B or AT 501 575 A1 to use the dynamic pressure for energy generation.
  • the inflowing water drives the blades of the impeller, which is connected to the motor-generator machine.
  • generator operation a braking torque is built up, and there is a conversion of the mechanical power into an electrical useful power, which is supplied to an energy storage ⁇ or fed into a power grid.
  • This type of hydro-electric machine has the advantage that the generator is driven by the pressure of the flowing water. Accordingly, in terms of high efficiency at large
  • Swallowing capacity used both the flow velocity of the channel and the potential level corresponding to the water level for energy production.
  • the output power and the achievable efficiency depend inter alia on the headwater level, ie on the upstream water level of the channel relative to the hub of the impeller.
  • the headwater level affects the impellers available to drive the impeller Amount of water. It has already been proposed (see http://de.wi-kipedia.org/wiki/Stauntzmaschine and the previously unpublished earlier application AT A 1195/2010) to regulate the upper water level to the current Oberwasserpegel continuously to the Oberwas ⁇ serpegel -Soll value to be adjusted.
  • the amount of water flowing from the upper water through the system into the underwater per unit of time depends on the speed of the impeller. Since the water flow is expediently not offered a possibility to avoid the impeller arranged across the entire channel, the entire water flows through the dynamic pressure machine.
  • the intake capacity depends on the speed of the impeller.
  • the impeller Since the water flow is expediently not offered a possibility to avoid the impeller arranged across the entire channel, the entire water flows through the dynamic pressure machine.
  • a high speed of the impeller is a high absorption capacity of the dynamic pressure machine, with a larger amount of water is transported by the blades to the underwater side and thus the head water level is reduced; conversely, reducing the speed of the impeller results in a lower one
  • the rotational speed of the impeller can be influenced, which can be accomplished via the braking torque of the motor-generator machine.
  • the braking torque of the generator can be increased; on the other hand, to achieve a higher speed of the impeller to achieve a greater absorption capacity of the dynamic pressure machine, the braking torque of the motor-generator machine can be reduced.
  • Such influencing is relatively expensive in a conventional dynamic pressure machine with a motor-generator machine control technology.
  • a single generator as usual, is provided, which is driven by a gear wheel driven by an impeller and thereby eccentrically relative to the axis of rotation of its own holder is arranged.
  • the invention provides a hydro-dynamic machine as characterized in the independent claim.
  • Advantageous embodiments and further developments of this dynamic pressure machine are specified in the dependent claims.
  • the present hydropower ram printing machine is thus provided primarily that adjacent at least one end ⁇ side of the hub of the impeller firmly connected to the frame support member with a plurality of slot-like, preferably underwater side arranged receptacles for each machine Ge ⁇ transmission module is arranged, opposite the impeller
  • the sprockets complement each other to a "matrix drive", for example, depending on the width of the impeller by attaching more or less machine gearbox modules with the matrix drive simplyylon ⁇ operating power (total generator power ) are adapted to the particular design of the impeller.
  • hydro-electric machine can continue to operate with the modules still operating, possibly with reduced power, i. it does not fail the entire system, as is the case in the prior art.
  • a wide water wheel delivers more power than a narrower impeller (with the same diameter).
  • a wheel that is twice as wide produces twice the torque and twice as much power.
  • the support part according to the invention for a plurality of machine-transmission modules can, depending on the width of the impeller, the number of modules to be used are determined, which are mounted in the desired receptacles of the support member. Unused recordings, ie free recordings, in which no machine-gearbox modules are inserted, are sealed in a suitable manner. This means that at a maximum wide wheels the maximum number of machine-Ge ⁇ gear modules is attached to the supporting part, whereas simply fewer machines gear modules can be attached to the support member at narrower wheels.
  • a generator with an integrated transmission e.g. a planetary gear or spur gear, in front; a drive pinion of this transmission is accessible from the outside, and this drive pinion is in engagement with the ring gear on the hub end face; via the gearbox, the relatively low speed of the impeller is converted into a suitably high speed of the generator.
  • the toothed rim on the hub end face is an internally toothed ring gear which is thus present on the outside (that is to say outside the pinions) and thus has a relatively large tooth area
  • Diameter and thus has a large number of teeth, so that the relatively small pinion, with a small number of teeth, can be driven in operation with a comparatively much higher speed from the sprocket.
  • the Support member preferably plate-shaped, for example as a side plate, out ⁇ forms.
  • the support member can be easily connected to the frame via at least one bracket projecting from the frame;
  • the machine-gearbox modules are preferably located on the underwater side of the dynamic pressure machine, and the console, preferably two consoles, project from the underbody side of frame supports and support the supporting part with the required strength.
  • the support member can also be used to support the impeller, i. the supporting part is part of the bearing frame via the console (s).
  • these modules are attached to the support part via flange connections.
  • these free receptacles of the support member are preferably closed by blind flanges.
  • the support member contains more than three shots for machine-gearbox modules. But it is also possible in principle to provide only two or three shots.
  • the switching means are connected to a control unit, eg with PLC module, which in turn is connected to a level sensor, preferably an upstream water level sensor, is connected to switch off at a comparatively low water level (for example, in the order of shutdown) switching means for switching off individual machine To control transmission modules.
  • a control unit eg with PLC module
  • a level sensor preferably an upstream water level sensor
  • Figure 1 is a perspective view of a hydro-dynamic pressure machine according to the invention, as seen from the underwater side, wherein the side of the impeller with the engine-transmission modules is visible.
  • Fig. 2 is a similar perspective view of the underwater side of the dynamic pressure machine of Figure 1, but now from the other side, opposite to the side where the machine transmission modules are mounted;
  • FIG. 3 shows an oblique view of the dynamic pressure machine according to FIGS. 1 and 2 from the upper water side;
  • Fig. 4 is a side view of the dynamic pressure machine according to Figures 1 to 3, wherein the side with the machine-gearbox modules is visible.
  • FIGS. 1 to 4 is an elevational view of the dynamic pressure machine according to FIGS. 1 to 4 seen from the upper water side;
  • FIG. 6 is a side view of the ram pressure machine similar to Fig. 4, but with the stationary frame and the storage frame of the ram pressure machine cut away, substantially along line VI-VI in Fig. 5;
  • FIGS. 7A and 7B show two embodiments with regard to the arrangement of the sprocket on the end face of the hub of the dynamic pressure machine, namely once with internal teeth (FIG. 7A) and once with external teeth (FIG. 7B);
  • Fig. 8 is a partial view, partially broken away, the dynamic pressure machine of FIG. 1 to 4, wherein in particular the bearing of the impeller and a formation of an externally toothed ring gear illustrated at the hub;
  • 9 and 10 are partial sectional views in the region of the seal between the module support member and the hub (detail IX in FIG. 9) or between the module support member and the impeller shaft (detail X in FIG. 10);
  • Fig. 11 is a block diagram illustrating an electric circuit including a control unit for turning on and off the electric machines (generators) depending on the water level.
  • a hydro-dynamic machine 1 with an impeller 2 is seen from the underside seen schematically illustrated.
  • Figs. 3 and 5 show this dynamic pressure machine 1 seen from the upper water side.
  • the impeller 2 has a cylindrical hub 3, whose axis is simultaneously the axis of rotation of the impeller 2, also called rotor.
  • annular end plates 4 are fixedly attached to the axial ends, which limit the width of the impeller 2.
  • shaped blades 9 are mounted, e.g. screwed and / or welded to form bags for water transport, i. to absorb the water pressure and to effect a torque around the wheel axle.
  • the vanes 9 of the impeller 1 may have, in addition to the V-shaped arrangement shown, other arrangements, such as simple oblique arrangements (see, for example, AT 404 973 B), and may also have a curvature depending on the objective.
  • the frame 5 supporting the impeller 2 has an overall rectangular shape with two vertical supports 10, 11 and a lower support 12 and an upper support 13 around the impeller 2 around.
  • the carriers 10 to 13 are preferably formed from rectangular in cross-section mold tubes, whereby a simple, lightweight, yet stable construction of the frame 5 is achieved, which also allows easy adaptation to different dimensions, in particular widths of wheels 2.
  • the vertical supports 10, 11 carry wheel bearings 14 (only one of these bearings is visible in Fig. 2, the other is concealed in Figs 1 to 3, but see also Fig. 8), wherein the wheel bearing 14 according to FIG is fastened to a bracket 15 projecting from the bracket 15, as shown in FIG. 2 can be seen.
  • This attachment of the bearing 14 is provided in the preferred embodiment on the downstream side (underwater side) of the dynamic pressure machine 1.
  • the vertical supports 10, 11 are on their outer sides, ie on the side facing away from the impeller 2, with not further apparent guide roller units (or other a low-friction displacement of the frame 5 in the stationary machine frame 6 ensuring guiding elements) equipped, see. 1 to 3, so as to raise or lower the frame 5 relative to the frame 6, for example for maintenance purposes or to adapt the impeller height to the respective underwater level, with the aid of a suitable,
  • the raising or lowering of the frame 5 is schematically illustrated in Fig. 3 with a double arrow 5 '.
  • a curved crop pan 17 which is arranged in the lower region of the rotor 2 and is shown by means of holders 18A attached to the vertical supports 10, 11, is shown.
  • 18B is attached to the frame 5 and has a curvature which is adapted to the path of movement of the impeller 2 and the blades 9 thereof.
  • the arrangement with the sealing lips 8 and further with the cropping plate 17 ensures that the water of the channel is optimally utilized for the generation of electrical energy, i. the efficiency of the dynamic pressure machine 1 shown is thereby additionally improved.
  • the described frame 5 for supporting the impeller 2 allows a modular principle for the dynamic pressure machine 1, wherein with the help of the carrier 10 to 12 in a simple manner to the respective size (width or diameter) of an impeller 2 adapted La ⁇ ger frame 5 assembled can be. Suitable for this purpose is then provided in the channel stationary arranged frame 6.
  • a matrix arrangement with several modules 20, each containing an electric machine (generator motor) and integrated with it a transmission vorgese ⁇ hen. From Fig. 1, three such modules 20, each with a gear 21 and a machine or a generator 21 ',
  • modules 20 are fixedly attached to a frame 5 fixed to the support member 22 which is disposed on the front side of the hub 3 of the impeller 2, but does not rotate with this hub 3, but with the aid of brackets 23, 24 with one of the vertical Support of the frame 5, as shown in FIG. 1 with the vertical support 11 shown there on the left, is rigidly connected.
  • the support member 22 is formed plate-shaped or disc-shaped in the embodiment shown, said disk-shaped support member 22 as shown in FIG. 1 is radially inside and adjacent to the circular on this page cover 4, which in turn firmly connected to the hub 3 of the impeller is as mentioned above.
  • the support member 22 also called circular disc, side plate or motor plate, has a plurality of slot-like receptacles 25 for each one machine-transmission module 20, wherein it is not necessary to install 25 corresponding modules 20 in all recordings.
  • the two intermediate free slot receptacles 25 that do not accommodate modules 20, s. 1, are tightly closed, for example with the aid of blind flanges 26.
  • the modules 20 in turn are connected in a corresponding manner via schematically shown in FIGS. 1 and 9 flange 27 with the support member 22.
  • Fig. 4 is a side view of the arrangement of the impeller 2 of the dynamic pressure machine 1 in the frame 6 (the frame 5 is not visible in Fig. 4) illustrated, wherein it is shown that the modules 20 and receptacles 25 in the support member 22 at the Underwater page 28 of the dynamic pressure machine 1 are present; the upper water side is indicated in Fig. 4 at 29, and further is the
  • FIGS. 7A and 7B the end face of the hub 3 can be seen, wherein it is shown that at these hub end faces a sprocket 33 (Fig. 7A) and 33 '(Fig. 7B) is fixedly mounted.
  • the ring gear 33 is an internally toothed ring gear with a relatively large diameter, and with this internally toothed ring gear ⁇ mesh ⁇ three drive pinion 34, which belong to the three machine-gearbox modules 20 as shown in FIG. 1, 2 and 4 , wherein the ring gear 33 with the respective drive pinion 34 already form a gear stage to increase the speed.
  • the resulting translation may already be sufficient to drive the generators 21 'of the modules 20 at a suitable rotational speed, so that further gear parts in the gears 21 of the modules 20 can be dispensed with.
  • the gear 21 is then formed in each case only by the ring gear 33 and the associated pinion 34.
  • further toothed wheels will be present in order to provide an additional (in the case of FIG. 7A, however, relatively small) ratio (secondary ratio) for driving the rotor of the generator 21 '.
  • the ring gear 33 ' is externally toothed, wherein the drive pinions 34 of the machine-gearbox modules 20 (see FIG. 1) are located radially outside this ring gear 33'.
  • the transmission ratio is smaller than in the case of FIG. 7A, so that here a comparatively larger secondary ratio in the transmission 21 of the respective module 20 is required.
  • the bearings 14, 31 for at the hub 3 of the impeller 2 frontally mounted stub shaft 35, 36 can be seen.
  • This can be a camp, namely the camp 14, on the side facing away from the modules 20 Stinseite, example ⁇ be designed as a pendulum bearing.
  • the opposite La ⁇ ger 31, for the other stub shaft 36, for example, via a rigid mounting plate 37 is connected to a provided as Na ⁇ ben end face 38 plate.
  • stiffeners 39 on the hub end faces can still be seen from FIG. 8. These stiffeners 39 can be provided for receiving bending moments, which originate from the distances between the bearings 14, 31 and the mounting plates 37 at the hub end faces 38.
  • Fig. 9 shows in a detail section corresponding to the detail IX in Fig. 8, the region of the seal between the support member 22 and the wheel hub 3. It is illustrated that between the hub 3 and the support member 22 (motor plate or side plate) a Oil space 40 is provided, said oil space 40 or space between the support member 22 and hub 3 is to seal accordingly. Specifically, here is a seal 41, in particular lip seal, provided to prevent ingress of water into the space 40, and another seal 42, in particular Lip ⁇ pendichtung, which lies axially further inside, serves to an oil leakage from the oil chamber 40 prevent. As can be seen further from FIG. 9, the respective toothed rim, for example the internally toothed ring gear 33 (see also FIG. 7A), can be fastened with the aid of bolts or similar fastening means 43
  • End face 38 or a fixedly connected flange 44 of the hub 3 may be connected.
  • Fig. 10 shows the detail X of FIG. 8 and concretely the area of a rolling bearing 45 for centering the support member or side plate 22 relative to the shaft 36 and further ent ⁇ speaking part of the oil chamber 40, with a seal 42 'against oil leakage on the one hand or a seal 41 'against Wasserein ⁇ occurs on the one hand between the support member 22 and the shaft or the stub shaft 36th
  • a plurality of strands 51, 52, 53, etc. are each shown with a generator 21 'of a module 20 as described above.
  • the generators 21 ' are preferably Asynchronous generators, even if synchronous generators could also be used.
  • the generators of the individual strands 51, 52 ... 53 provide their electrical power to inverter 54, which via switch PWR1, PWR2 ... PWRN with a sudspei ⁇ seumrichter 55 - in normal operation - are connected to current 55 about this to remindspeiseumrichter to deliver a network 56.
  • the switches PWR1, PWR2... PWRn form switching means 57 which belong to a control unit 58 with, for example, a PLC control module 59.
  • This PLC module 59 is connected to a level sensor 60 for water level determination, for example, (only) the upper water level is detected. If appropriate, however, it is also possible to detect the upper water level and the underwater level or the level difference, with a specific level difference leading to optimum operation of the dynamic pressure machine 1. At constant underwater level, it is sufficient to detect the head water level, then by raising the speed of the impeller 2 of the dynamic pressure machine 1 and thus the absorption capacity of the dynamic pressure machine 1, for example, a too deep sunken upper water level to raise again or too high
  • generators 21 ' Apart from the automatic activation or deactivation of generators 21 ', as described with reference to FIG. 11, it is naturally also conceivable to use individual generators 22 by hand Help switching means 57 on or off, such as when long-lasting changes in the water levels, in prolonged drought or prolonged periods of rain, given.
  • the described matrix arrangement with several machine-gearbox modules 20 also provides, apart from the above-described operational optimization, also the advantage that in the event that a generator module fails, the water engine 1 continues to work with the remaining modules 20, optionally with reduced power , can continue to operate.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)

Abstract

L'invention concerne une machine à pression de retenue hydraulique (1) comprenant au moins un rotor (2) monté rotatif sur un cadre, lequel rotor présente un moyeu (3) et des ailettes (9) reliées à ce moyeu, et qui définit pendant le fonctionnement une hauteur de niveau d'eau comme différence entre un niveau d'eau supérieur et un niveau d'eau inférieur, et une machine électrique à moteur-générateur (21') couplée au rotor (2) par un engrenage (21) et regroupée dans un module (20) avec celui-ci, une partie porteuse (22), reliée fixement au cadre (5) et étanchéifiée par rapport au rotor (2), comprenant plusieurs logements (25) de type emplacements d'affichage, disposés de préférence côté sous l'eau, pour respectivement un module (20) de machine (21')/d'engrenage (21) étant disposée à proximité d'au moins un côté avant du moyeu (3) du rotor, des modules de machine et d'engrenage (20) étant fixés dans au moins quelques logements (25), modules, un pignon d'entraînement (34) de chaque module s'engrenant avec une couronne crantée (33, 33') placée de façon fixe sur le côté avant du moyeu (3), et les interrupteurs (PWR1, PWR2,... PWRn) destinés à la connexion et à la déconnexion sélectives des modules de machine/d'engrenage (20) étant attribués aux modules de machine et d'engrenage (20).
PCT/AT2011/000331 2010-08-24 2011-08-03 Machine à pression de retenue hydraulique WO2012024704A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA1413/2010 2010-08-24
ATA1413/2010A AT510320B1 (de) 2010-08-24 2010-08-24 Wasserkraft-staudruckmaschine

Publications (1)

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WO2012024704A1 true WO2012024704A1 (fr) 2012-03-01

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT512973A1 (de) * 2012-05-22 2013-12-15 Berthiller Wasserradanlage
WO2018089324A1 (fr) * 2016-11-08 2018-05-17 TSENG, Chih-Shiang Dispositif générateur

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT521495B1 (de) * 2018-11-22 2020-02-15 Staudt Friedrich Wehranlage

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ATA501575A (de) 1974-07-08 1979-02-15 Cos Computer Systems Sa Desodorisierende wegwerf-einlegesohle
DE4313509A1 (de) 1992-08-10 1994-02-17 Thomas Dipl Ing Guenther Wasserkraftanlage
AT404973B (de) 1997-04-01 1999-04-26 Brinnich Adolf Wasserkraft - staudruckmaschine
US6616403B1 (en) * 2002-04-08 2003-09-09 Matt H. Smith Floating electric generator
AT501575A1 (de) * 2005-12-27 2006-09-15 Brinnich Adolf Wasserkraft-staudruckmaschine
EP1975404A1 (fr) * 2007-03-27 2008-10-01 de Jonghe d'Ardoye, Baldwin Système de récupération d'énergie hydraulique
WO2009121824A2 (fr) 2008-03-31 2009-10-08 Aweg Ag Für Wasser Und Energie Centrale hydroélectrique
US20090322093A1 (en) 2008-06-30 2009-12-31 Winius Henry C Paddle wheel electric generator
WO2010083590A1 (fr) * 2009-01-22 2010-07-29 Howard Harrison Système générateur modulaire pour éolienne
WO2010114496A2 (fr) * 2009-03-30 2010-10-07 Vladimir Mueller Roue hydraulique flottante agissant principalement comme génératrice d'énergie multifonctionnelle

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATA501575A (de) 1974-07-08 1979-02-15 Cos Computer Systems Sa Desodorisierende wegwerf-einlegesohle
DE4313509A1 (de) 1992-08-10 1994-02-17 Thomas Dipl Ing Guenther Wasserkraftanlage
AT404973B (de) 1997-04-01 1999-04-26 Brinnich Adolf Wasserkraft - staudruckmaschine
US6616403B1 (en) * 2002-04-08 2003-09-09 Matt H. Smith Floating electric generator
AT501575A1 (de) * 2005-12-27 2006-09-15 Brinnich Adolf Wasserkraft-staudruckmaschine
EP1975404A1 (fr) * 2007-03-27 2008-10-01 de Jonghe d'Ardoye, Baldwin Système de récupération d'énergie hydraulique
WO2009121824A2 (fr) 2008-03-31 2009-10-08 Aweg Ag Für Wasser Und Energie Centrale hydroélectrique
US20090322093A1 (en) 2008-06-30 2009-12-31 Winius Henry C Paddle wheel electric generator
WO2010083590A1 (fr) * 2009-01-22 2010-07-29 Howard Harrison Système générateur modulaire pour éolienne
WO2010114496A2 (fr) * 2009-03-30 2010-10-07 Vladimir Mueller Roue hydraulique flottante agissant principalement comme génératrice d'énergie multifonctionnelle

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT512973A1 (de) * 2012-05-22 2013-12-15 Berthiller Wasserradanlage
AT512973B1 (de) * 2012-05-22 2015-09-15 Franz Berthiller Wasserradanlage
WO2018089324A1 (fr) * 2016-11-08 2018-05-17 TSENG, Chih-Shiang Dispositif générateur

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AT510320A1 (de) 2012-03-15

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