EP1299642B1 - Turbomachine hydraulique - Google Patents

Turbomachine hydraulique Download PDF

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Publication number
EP1299642B1
EP1299642B1 EP01967133A EP01967133A EP1299642B1 EP 1299642 B1 EP1299642 B1 EP 1299642B1 EP 01967133 A EP01967133 A EP 01967133A EP 01967133 A EP01967133 A EP 01967133A EP 1299642 B1 EP1299642 B1 EP 1299642B1
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EP
European Patent Office
Prior art keywords
energy
water
guide
generator
chamber
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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.)
Expired - Lifetime
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EP01967133A
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German (de)
English (en)
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EP1299642A1 (fr
Inventor
Johannes Van Berkum
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Individual
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Individual
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Priority claimed from DE10129830A external-priority patent/DE10129830A1/de
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Publication of EP1299642A1 publication Critical patent/EP1299642A1/fr
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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
    • F03B17/00—Other machines or engines
    • F03B17/005—Installations wherein the liquid circulates in a closed loop ; Alleged perpetua mobilia of this or similar kind
    • 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
    • F05B2200/00—Mathematical features
    • F05B2200/10—Basic functions
    • F05B2200/11—Sum

Definitions

  • the invention relates to a hydraulic flow machine for Energy conversion for the energy supply of energy consumers of any kind.
  • the drive power of a pump is needed to set the impeller in rotation, the atmospheric Air pressure the water column in the suction pipe and from there into the impeller suppressed.
  • the water from the flow direction in the suction pipe in the direction of flow in the impeller are deflected.
  • the Torque on the impeller and the centrifugal force must be the water within the blade channels of the impeller from that in the center of the Impeller existing smaller rotational speed on the am Outer diameter required circulation and exit velocity accelerated and transported.
  • the required Acceleration forces must be provided by the drive of the pump Will be provided.
  • the water is going out the spiral housing into a discharge nozzle, in which it on his Drive power of the impeller from the delivery and the Delivery volume of the water / per unit time and of the Energy losses determined.
  • An essential feature of conventional centrifugal pump is that for in the impeller inflowing flow, the drive power of the engine is not in Claimed.
  • the drive motor accelerates this into the Impeller inflowing water on the exit velocity of the the impeller flowing water. Due to the centrifugal force of the impeller circulating water creates a negative pressure compared to the pressure of prevails at the suction tube entrance.
  • the resulting overpressure on the Intake manifold inlet lets the water rise in the intake manifold and into the Impeller flow. Part of the total head of the centrifugal pump However, not from the performance of the drive motor, but from the Overpressure on the intake manifold.
  • the influence of the supplied flow energy on the impeller blades causes a torque on the turbine shaft. This is the working capacity of a water flow driving the turbine wheel.
  • the described hydropower plants are localized and require considerable investment costs. Due to the seasonal water supply of different sizes, the available amount of water can fluctuate very strongly, which in turn has a great influence on the amount of energy available or to be dispensed to the consumer.
  • EP 0 545 280 A1 also discloses a drive device with a turbine fixedly arranged on a rotatable shaft, which can be acted upon by a liquid, in particular water, and set into rotary motion together with the shaft, characterized in that the shaft is vertical is arranged that on the shaft this concentrically surrounding a conically upwardly flared tube is fixed and which has an overflow in the upper edge with an underneath, fixed collecting container for overflowing liquid, and that the turbine via at least one outgoing from the collecting container Downpipe is acted upon from below with the liquid.
  • DE 196 47 476 A1 discloses a pneumatic hydraulic centrifugal drive for all types of energy movement and power generation, characterized in that record by a rotor with one or more integrated chambers / tanks water, oil or other liquids and centrifuged by acceleration / compacted and in a pressurized housing presses, wherein the housing in which the rotor is driven is under atmospheric pressure or gas pressure and filled with water or other liquids.
  • the chambers of the rotor are filled via the rotor axis with liquid and thrown by the rotational movement of the rotor to the outside, whereby centrifugal forces arise, which throw the water through the arranged on the chambers nozzles from the rotor in the pressurized housing, at the bottom itself collects the water and a turbine is supplied, which returns the water to a power generator and at the same time in the rotor axis.
  • the above-described solutions are based on the basic principle of buoyancy of a water column in the center about a rotating axis, from where the liquid is guided radially in a turbine wheel and forced by centrifugal forces to the outside, the disadvantages described above occur.
  • the hydraulic turbomachine described in WO 00/29747 can not eliminate these disadvantages, since in this solution, the water is not supplied to the suction chamber with a trough-shaped guide, the centrifugal force does not form a balance of forces with the atmospheric pressure at the exit of the hub and the engine Water in the hub must accelerate to exit velocity.
  • the invention is therefore an object of the invention to provide a hydraulic fluid flow machine that uses only due to the atmospheric air pressure acceleration of the flow circuit of a rising in a suction chamber to an impeller water column and provides as final energy to a consumer.
  • the object is achieved by a hydraulic turbomachine with the characterizing features of claim 1.
  • the trough-shaped flow space according to the invention of the hydraulic fluid machine inside a closed container which at the same time contains the water supply required for the function of the machine has the great advantage, in contrast to previous solutions, that only the pressure energy of the atmospheric air pressure, reduced by all losses, is delivered as final energy to a consumer.
  • can act through an opening between the two inner guide walls in front of the inlet of the suction chamber within the trough-shaped flow space of the atmospheric pressure on the water level and arranged between the flow space and container compensating pipe allows the adjustability of the water level in the trough-shaped flow space.
  • the height of the water level in the container by known methods such as manually through a window or appropriately arranged float or sensors that trigger a signal upon reaching a determinable level and optimally determined by a the application conditions adapted water inlet and outlet system.
  • the atmospheric air pressure exerts a pressure on the water level in the trough-shaped flow space and causes, due to the force balance generated by the impeller, the water is accelerated in the suction chamber, via the guide vanes in the horizontally about the axis of the generator rotating impeller and from this is passed into the Leitraum, where it can be deflected and fed back to the suction chamber.
  • the speed energy of the exit velocity of the water from the impeller adds to the pressure energy of the atmospheric Lucasrucks and by cross-sectional constriction in the vane area, the water is accelerated again to the required inlet velocity into the impeller.
  • the drive motor, the impeller in a certain speed which exceeds the speed of rotation of the Water in the impeller generated centrifugal force at the outlet openings of the Impeller generates a pressure that the back pressure to the Outlets corresponds and this is directed against, whereby an equilibrium of forces arises at the impeller outlet.
  • the structural design of the trough-shaped flow space coaxial about the axis of the Generator in a container with a required water supply is arranged.
  • the outer guide wall of the trough-shaped Flow space forms together with two inner guide walls a suction chamber and a Leitraum, between which on the axis of the generator and horizontally rotating about this axis Impeller is guided with impeller blades, taking all components together form the annular water cycle.
  • a second variant of the hydraulic according to the invention Turbomachine provides that at one, by a desired lower flow velocity in the guide and suction chamber conditional, reduced exit velocity of the water from the Impeller in place of the vanes one with the impeller horizontally around the Axis of the generator rotating accelerating wheel is provided which the missing speed energy for the Entry speed of water into the impeller with the Drive motor compensates and the ingress of atmospheric air prevented in the suction chamber.
  • the amount of energy to be delivered is the inventive hydraulic turbomachine of the constructive sizes of individual components and by measuring the drive power for the energy supply in the start phase of the plant and to compensate for the determined conditional losses, the yield of final energy in the hydraulic turbomachine with guide vanes is greater than when using the accelerator, because by the accelerator additional energy losses are recorded.
  • the advantages of the hydraulic turbomachine according to the invention exist, due to the structural design and the so guaranteed optimization of space requirements in the absolute Adaptability to local conditions and Performance requirements, associated low investment and Maintenance costs and a long service life.
  • the machine works absolutely independent of day or seasons, allows one Cost-effective energy storage, is through the use of the atmospheric pressure as secondary energy absolute environmentally friendly and produces no waste. It does not need any Water gradient, no natural and / or jammed water source and is thus not localized.
  • Fig.1 and Fig.3 show an embodiment of the invention Hydraulic fluid machine with vanes 2, which with a annular water circuit according to the invention with a radial, to a Axle 6 'of a generator 6, extending flow direction is equipped.
  • the annular water circuit consists of the suction chamber 1 with Suction chamber inlet 1 'and suction chamber outlet 1 ", in the area of Saugraumausgangs 1 "arranged vanes 2, the impeller 3 with Impeller blades 3 ', arranged on the inner diameter D1 Inlet openings 3 "and arranged on the outer diameter D2 Outlet openings 3 '”and a Leitraum 7 with inlet opening 7' and Outlet opening 7 ", within a trough-shaped Flow space 8 coaxially about the axis 6 'of the generator 6 in one Container 9 is arranged, wherein the impeller 3 between the suction chamber 1 and the Leitraum 7 horizontally to the axis 6 'rotates and the transition from the guide vanes 2 to the impeller 3 preferably by a non-contact seal 24 is sealed according to Figure 4.
  • the trough-shaped flow space 8 consists of a, in a container. 9 arranged non-positively, outer guide wall 8 ', with a inner guide wall 8 "forms the suction chamber 1 and over in the Suction chamber 1 arranged vanes 2 with the outer Guide wall 8 'is connected and with an inner guide wall 8 "'forms the Leitraum 7 and guide webs 17 with the outer Guide wall 8 'is connected. Between the two inner ones Guide walls 8 "and 8 '" is in the inner bottom area of the trough-shaped flow space 8 an opening arranged. Furthermore is located in this floor area, a water level 4 ', the for example, via a compensating pipe 10 to the container 9 is adjustable.
  • the container 9 is preferably with two container chambers 12 and 13 equipped.
  • the container 9 When starting the machine is from the For example, higher arranged container chamber 13 preferably via a directional control valve 14, water 4 filled in the container 9, whereby the Air from the suction chamber 1 and the Leitraum 7 and from the impeller. 3 is displaced. After reaching the required speed or after Completion of the startup process is now in the container 9 excess Water 4 via the preferably second directional control valve 14 in the Container chamber 12 passed.
  • the water level is too low 4 'in the Container 9 or in the flow chamber 8 is 4 of the water Container chamber 12 via, for example, a check valve 15 and a Pump 16 pumped into the container chamber 13 and from there via the first Directional valve 14 back to the container 9 back to the water level 4 'back to the level required for the function of the machine was reduced.
  • a check valve 15 and a Pump 16 pumped into the container chamber 13 and from there via the first Directional valve 14 back to the container 9 back to the water level 4 'back to the level required for the function of the machine was reduced.
  • For the detection and regulation of the water level 4 ' in the container 9 conventionally known methods are provided as the manual detection through a viewing window and its manual Regulation or detection via a float or sensor and by these triggered electrical signals to the directional control valves 14.
  • the Generator 6 is arranged outside of the container 9 so that he for example via a coupling 22 and a bearing 23 with the axis 6 ' is connected, wherein on the, in the container 9 vertically protruding Axial part as a transmission element 20, 21 preferably one Pulley 20 is arranged via a belt 21 with a second pulley 20 on the axis of the also outside the Container 9 arranged drive motor 5 are interconnected.
  • the impeller 3 is arranged on another bearing 23 so that it can rotate horizontally about the axis 6 '.
  • the axis 6 'of the flow space 8 is arranged, in which the circular Water circulation is installed, whereby the the floor area of the Flow space 8 opposite opening between the suction chamber. 1 and Leitraum 7 through the horizontally about the axis 6 'rotating impeller. 3 is covered.
  • the drive motor 5, which requires for the starting process is, drives the impeller 3 and compensates for part of the losses of Energy conversion into the impeller 3.
  • About the impeller 3 is the Generator 6 driven. This generates the circulating in the impeller 3 Water 4 a centrifugal force Fz.
  • the centrifugal force Fz in turn creates a Pressure pz at the outlet openings 3 '"of the impeller 3, the atmospheric pressure equals pL and this counteracted is, whereby the entry of air into the impeller 3 is prevented. to same time arises due to the centrifugal force Fz at the inlet openings 3 " of the impeller 3, a negative pressure.
  • the emerging from the impeller 3 Water 4 flows at a defined speed c2 in the Leitraum 7, is deflected by the shape and again the suction chamber. 1 fed.
  • c2 the degree of the maintenance of centrifugal force Fz in the impeller 3 required entry speed c1 of the water.
  • the Circulation speeds cu1 and cu2 are in turn determined by the Centrifugal force Fz of the water 4 in the impeller 3 determined.
  • the Entry speed c1 the water 4 in the impeller 3 must be in the suction chamber 1 can be accelerated back to the required size.
  • the energy difference between supplied Energy at the inlet openings 3 "and dissipated energy to the Outlet openings 3 '"of the impeller 3 corresponds to the of atmospheric air pressure pL and that of the drive motor 5 introduced energy EM.
  • the pressure energy of the atmospheric air pressure pL converted in to the occurring Energy losses of the turbine Etv, the propulsion engine Emv and the Generator's EGV reduced, final energy EN.
  • Figure 5 shows a scheme of the resulting energy balance for a Hydraulic turbomachine according to the invention with guide vanes 2 according to the first embodiment, wherein in addition to the already the factors influencing the water density, p, the efficiencies ⁇ the drive motor 5 and the generator 6, the suction chamber 1 and the Impeller 3 are taken into account.
  • FIGS. 6 and 8 show a second embodiment of the invention inventive hydraulic fluid machine with a Accelerator 11 and without vanes 2, which with a annular water circuit according to the invention with a radial, to a Axle 6 'of a generator 6, extending flow direction is equipped.
  • the annular water cycle is different from that of the first one Embodiment in that instead of the guide vanes.
  • an accelerator 11 is arranged with the impeller 3 about the axis 6 'of the generator 6, wherein the bottom of the flow area 8 opposite lying opening between the suction chamber 1 and Leitraum 7 through the horizontally about the axis 6 'rotating accelerator 11 and the Impeller 3 is covered and the transition from the Saugraumausgang 1 "to the acceleration wheel 11 according to Figure 9 by a non-contact Seal 24 is sealed.
  • This embodiment is preferred then used when the water in the Leitraum 7 and the suction chamber. 1 should have a low flow rate. The circulation speed cu2 of the water 4 in the impeller 3 is then too low to prevent penetration of the atmospheric air pressure pL in the suction chamber 1 to avoid.
  • the acceleration wheel 11 with inlet openings 11 'on Inner diameter D3 and outlet openings 11 "on the outer diameter D4 takes over in this case the additional acceleration of the Suction chamber 1 leaking water 4 from the inlet velocity c3 on the exit velocity c4 and the required Entry speed c1 of the water 4 in the impeller 3.
  • this additional acceleration of the water 4 in the accelerator 11th also increases a circulation speed cu3 at the inner diameter D3 to a peripheral speed cu4 at the outer diameter D4 of Acceleration wheel 11.
  • the orbital velocities cu3 and cu4 of the Water 4 in the accelerator 11 generate in this case, the Centrifugal force Fz, which by the apparent from Fig.7 blade assembly and Form in the accelerator wheel 11 and the impeller 3 is supported.
  • the Energy required for this is supplied by the drive motor 5. Of the Energy amount is, however, by the larger torque output of the Impeller 3 to the generator 6 the drive motor 5 again for Provided. As a result, the services to be transferred in Drive motor 5, in the impeller 3 and in the generator 6 larger. Furthermore the power transmission of the acceleration wheel 11 still comes added. The energy losses increase significantly, causing the final energy EN to be given off from the atmospheric air pressure pL introduced and from the generator 6 a consumer available can be made is less than when running with Guide vanes 2.
  • FIG. 10 shows a schematic of the resulting energy balance for a inventive hydraulic fluid machine without vanes 2 with an accelerator 11 after the second Embodiment, in addition to those already listed Influence factors the water density p, the efficiencies ⁇ of the Drive motor 5 and the generator 6 of the suction chamber 1, the impeller 3, and the accelerator 11 are taken into account.

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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)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Cyclones (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Claims (5)

  1. Turbomachine hydraulique se composant d'un arbre (6'), d'une chambre d'aspiration (1), d'aubes directrices (2) et d'une roue mobile rotative (3) à aubes (3') qui sont remplies d'eau (4), d'un moteur d'entraínement (5) et d'un générateur (6), d'un cycle d'eau annulaire ayant un sens d'écoulement dirigé radialement vers un axe (6') du générateur (6), d'une chambre directrice (7), d'une chambre d'écoulement (8) qui sont disposées de façon coaxiale autour de l'axe (6') du générateur (6) dans un réservoir (9), caractérisée par le fait que ladite chambre d'écoulement (8) est réalisée en forme de cuve et est équipée, devant une entrée d'espace d'aspiration (1') de l'espace d'aspiration (1), d'une ouverture par laquelle il est possible de régler un niveau d'eau (4') dans le réservoir (9),
    que, dans la chambre directrice (7), l'eau (4) sortant de la roue mobile (3) peut être dirigée à travers une sortie de chambre directrice (7") de la chambre directrice (7) vers l'entrée (1') de la chambre d'aspiration et peut être ramenée à la chambre d'aspiration (1),
    que ledit moteur d'entraínement (5) maintient la roue mobile (3) à une vitesse de rotation déterminée afin d'obtenir sur des orifices de sortie (3"') de la roue mobile (3) un équilibre de forces entre la pression d'air atmosphérique en tant que force centripète et la force centrifuge, et
    qu'entre l'énergie amenée sur des orifices d'entrée (3") et l'énergie évacuée sur les orifices de sortie (3"') de la roue mobile (3) est créée une différence d'énergie qui correspond à la somme d'une énergie de pression de la pression d'air atmosphérique (pL), introduite sur l'entrée de chambre d'aspiration (1') et d'une énergie introduite (EM) du moteur d'entraínement (5), et qui peut être transmise, en tant que couple, de la roue mobile (3) au générateur (6).
  2. Turbomachine hydraulique selon la revendication 1, caractérisée par le fait que ladite chambre d'écoulement (8) en forme de cuve se compose d'une paroi extérieure de guidage (8') qui comprend, avec une paroi intérieure de guidage (8"), la chambre d'aspiration (1) avec les aubes directrices (2) et, avec une paroi intérieure de guidage (8"'), la chambre directrice (7), entre ladite chambre d'aspiration (1) avec les aubes directrices (2) et ladite chambre directrice (7) étant disposée à rotation la roue mobile (3) qui forment ensemble le cycle d'eau annulaire.
  3. Turbomachine hydraulique selon la revendication 2, caractérisée par le fait que ladite paroi intérieure de guidage (8") est reliée par les aubes directrices (2) à la paroi extérieure de guidage (8') et la paroi intérieure de guidage (8"') est reliée par des entretoises de guidage (17) à la paroi extérieure de guidage (8'), ou que ladite paroi intérieure de guidage (8") est reliée par des entretoises de guidage (18) à la paroi extérieure de guidage (8') et la paroi intérieure de guidage (8"') est reliée par des entretoises de guidage (19) à la paroi extérieure de guidage (8').
  4. Turbomachine hydraulique selon la revendication 1, caractérisée par le fait que, lorsque l'eau (4) sort de la roue mobile (3) à une vitesse réduite de sortie (c2), c'est au lieu des aubes directrices (2) une roue d'accélération (11) qui compense avec le moteur d'entraínement (5) l'énergie manquante de vitesse pour la vitesse d'entrée (c1) de l'eau (4) dans la roue mobile (3), ladite roue d'accélération (11) tournant avec la roue mobile (3) horizontalement autour de l'axe (6') du générateur (6).
  5. Turbomachine hydraulique selon la revendication 1, caractérisée par le fait que l'énergie (EM) amenée par le moteur d'entraínement (5) peut être ramenée par le générateur (6) au moteur d'entraínement (5) et qu'exclusivement l'énergie de pression de la pression d'air atmosphérique (pL), réduite de toutes les pertes d'énergie se produisant, qui est introduite dans la chambre d'aspiration (1) peut être amenée comme énergie finale (EN) par le générateur (6) à un appareil consommateur.
EP01967133A 2000-07-13 2001-07-09 Turbomachine hydraulique Expired - Lifetime EP1299642B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10034219 2000-07-13
DE10034219 2000-07-13
DE10129830 2001-06-25
DE10129830A DE10129830A1 (de) 2000-07-13 2001-06-25 Hydraulische Strömungsmaschine
PCT/EP2001/007849 WO2002006666A1 (fr) 2000-07-13 2001-07-09 Turbomachine hydraulique

Publications (2)

Publication Number Publication Date
EP1299642A1 EP1299642A1 (fr) 2003-04-09
EP1299642B1 true EP1299642B1 (fr) 2005-12-07

Family

ID=26006384

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01967133A Expired - Lifetime EP1299642B1 (fr) 2000-07-13 2001-07-09 Turbomachine hydraulique

Country Status (6)

Country Link
EP (1) EP1299642B1 (fr)
AT (1) ATE312283T1 (fr)
AU (1) AU2001287588A1 (fr)
DE (1) DE50108325D1 (fr)
ES (1) ES2254479T3 (fr)
WO (1) WO2002006666A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021256924A1 (fr) * 2020-06-18 2021-12-23 Arnbarg Beheer B.V. Moteur à vortex
NL2025860B1 (nl) * 2020-06-18 2022-02-17 Arnbarg Beheer B V Vortex motor

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE414415C (de) 1925-05-30 Hermann Schnaidt Mehroktavige diatonische Harmonika
DE260261C (fr)
DE195199C (fr)
BE337974A (fr) *
FR2395407A2 (fr) * 1977-02-11 1979-01-19 Commins Eric Moteur d'energie mecanique (a action hydraulique)
JPS56118566A (en) * 1980-02-22 1981-09-17 Kiyotatsu Fukai Rotary hydraulic machine
DE4139633A1 (de) * 1991-12-02 1993-08-12 Willi Maurer Antriebsvorrichtung
DE19647476A1 (de) * 1996-11-16 1998-05-20 Manfred Klenk Pneumatisch hydraulischer Zentrifugalantrieb
WO2000029747A2 (fr) * 1998-11-10 2000-05-25 Johannes Van Berkum Turbomachine hydraulique

Also Published As

Publication number Publication date
WO2002006666A1 (fr) 2002-01-24
ATE312283T1 (de) 2005-12-15
EP1299642A1 (fr) 2003-04-09
DE50108325D1 (de) 2006-01-12
ES2254479T3 (es) 2006-06-16
AU2001287588A1 (en) 2002-01-30

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