WO2017187472A1 - Turbine hydraulique du type à impulsion - Google Patents

Turbine hydraulique du type à impulsion Download PDF

Info

Publication number
WO2017187472A1
WO2017187472A1 PCT/JP2016/062863 JP2016062863W WO2017187472A1 WO 2017187472 A1 WO2017187472 A1 WO 2017187472A1 JP 2016062863 W JP2016062863 W JP 2016062863W WO 2017187472 A1 WO2017187472 A1 WO 2017187472A1
Authority
WO
WIPO (PCT)
Prior art keywords
runner
water
water flow
valve
energy
Prior art date
Application number
PCT/JP2016/062863
Other languages
English (en)
Japanese (ja)
Inventor
初雄 羽場
秋男 中山
智泰 落合
丈訓 羽場
賢 羽場
Original Assignee
初雄 羽場
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 初雄 羽場 filed Critical 初雄 羽場
Priority to CN201680084727.XA priority Critical patent/CN109072860B/zh
Priority to JP2018513947A priority patent/JP6425157B2/ja
Priority to PCT/JP2016/062863 priority patent/WO2017187472A1/fr
Priority to AU2016404873A priority patent/AU2016404873B2/en
Publication of WO2017187472A1 publication Critical patent/WO2017187472A1/fr
Priority to ZA2018/07925A priority patent/ZA201807925B/en

Links

Images

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
    • F03B11/00—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator
    • 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 present invention relates to an engine that obtains rotational power from water drop energy or kinetic energy of running water.
  • Francis turbines which are currently mainstream, mainly use anti-reaction turbines, and among other turbines, it is most efficient in optimal load operation, and the applicable head is 30 to 500 m, and the water volume is about 0.1 to 2000 cubic m / s.
  • the specific speed is 50 to 350 when the standard unit is (m, kW, rpm), and the results are the most.
  • the location where the water flow is divided by turbine main wings, guide vanes, etc. and the total length In many cases, slender and thin curtains can be entangled with abnormal vibrations, noise, efficiency and output degradation, and in the worst case, control can be lost, causing an emergency stop.
  • the Pelton turbine and the Targo impulse turbine are used for impulsive operation, and the efficiency is stable and high from small load to rated load. It is suitable for load following operation and water volume following operation by controlling the needle valve. 2000m, the amount of water is about 0.05 to 20 cubic m / s, the specific speed is 8 to 60 (6 shots) when the standard unit is (m, kW, rpm), and the amount of water is provided by providing multiple impulse jets.
  • the runner bucket that receives the high-speed jet water flow accompanying rotation can be reduced, and the installation record is the second most, and there are few places to divide the water flow and the dust does not get entangled and less maintenance work is required. Since the noise and impact force due to sequential movement change repeatedly from 0 to 100%, measures to suppress damage due to metal fatigue are required.
  • the cross-flow turbine is the same impulse turbine as the Belton turbine.
  • the wings are parallel to the axis and the water flow flows in a right angle direction and then goes to the inside of the blade row and then flows out in the opposite direction.
  • the amount of water is proportional to the length of the parallel blades.
  • High-strength design is difficult to secure an internal water flow space, making it unsuitable for large facilities.
  • the Provera turbine is a turbine that uses the reaction force generated when the water flow hits the wings, and it is possible to maintain high efficiency stably by changing the wing angle from a small load to a rated load.
  • the applicable head is 1 to 100 m
  • the water amount is 0.1 to 6000 cubic m / s
  • the specific speed is 100 to 900 when the standard unit is (m, kW, rpm).
  • Patent PR US-861A Patent Information : US-2599A Patent PR : US-236992 Patent PR : US-409865 Patent PR : DE-347271C Patent PR : JP-1760751 Patent PR : JP-4845550 Patent PR : JP-2002-000431 application published : JP-2013-007376 application published
  • Petroleum-coal-based fossil energy which is currently the mainstream, creates a tremendous burden on the global environment, and it is an urgent need to switch to natural energy use as a countermeasure.
  • the use of this energy in a myriad of undeveloped rivers, etc. Although promising, the response target is nature, and there are many difficult problems in terms of profitability, maintenance, and environmental measures such as noise countermeasures in residential areas.
  • the first point is that with small-scale water turbines, it is difficult to completely remove the incoming dust when taking water from natural lakes, rivers, etc. It has been a problem such as an increase in maintenance labor and an outage period due to the occurrence of an emergency stop.
  • the second point is that in the case of small-scale hydroelectric power generation facilities that do not have large-capacity water storage facilities such as dams, the amount of water taken from rivers can be changed according to changes in turbine water volume due to load following operation, emergency stop due to trouble, and resumption of operation. Changing the discharged water from time to time is likely to cause drastic changes in the water volume and speed of the original river, causing harm to swimmers, anglers, and other water users. It must be avoided by causing excessive pressure fluctuations, etc., and causing damage.
  • the third point is that river flow increases due to rainfall and snowfall, and changes naturally depending on the weather. Therefore, there is a demand for a water turbine that can easily follow a change in the amount of water and can easily follow the amount of water.
  • the fourth point is durability and environmental noise, but if it is made of expensive materials, it will increase the weight and construction costs, and if it tries to suppress construction costs, maintenance costs will increase.
  • the change in impact energy caused by the rotation of each runner braid specific to the impulse turbine is large and cannot be ignored as noise, and it has been difficult to overcome all of these problems with conventional turbines.
  • FIG. 1 is a main configuration diagram including a cross section including a central axis of a hydro turbine according to the present invention, a side surface of a runner, and a cross section perpendicular to the central axis.
  • FIG. 2 is an enlarged detail view of the runner blade, and is an explanatory view showing that a curved line is smoothly drawn according to each cross-sectional position of the blade.
  • FIG. 3 is an explanatory diagram for controlling the water flow and controlling the operation state by controlling the main valve and the subvalve of the turbine.
  • FIG. 4 is an explanatory view showing a state of water flow on the runner blade.
  • FIG. 5 is an explanatory diagram showing that the specification can be changed by changing the components of the hydro turbine according to the present invention.
  • FIG. 1 is a main configuration diagram including a cross section including a central axis of a hydro turbine according to the present invention, a side surface of a runner, and a cross section perpendicular to the central axis
  • FIG. 6 is an explanatory view showing that it can be applied to a horizontal axis hydro turbine.
  • FIG. 7 is a conceptual diagram showing energy conversion by vortex flow at each location in the hydro turbine.
  • FIG. 8 is a basic conceptual diagram for examining energy conversion specifications by a rotating disk-shaped inward radiating vortex acting on a turbine blade.
  • the vortex flow in the direction of rotation is similar to the runner from the same spiral tube as the conventional Francis turbine, but in the Francis turbine, pressure water mainly acts on the runner.
  • the water flow cross-sectional area is reduced by the vortex flow rate adjustment movable gate, about half of the energy is converted into velocity kinetic energy, and the vortex with half pressure and half kinetic energy is stored in the spiral tube.
  • the runner shaft core is used as a common core to surround the runner.
  • a ring-shaped sub-valve similar to the main valve is further radiated on the runner side of the spiral tube adjacent to the ring-shaped main valve that slides freely in parallel with the runner axial direction through the ring-shaped main valve sliding mechanism.
  • Annular sub-portion on the downstream side cylindrical substrate Provided via a sliding arm and a ring-shaped sub-valve sliding mechanism, the water flow at full load completely closes the valve structure on the ring-shaped sub-valve and radial ring-ring valve base material side, and the opening dimensions of the ring-shaped main valve and ring-shaped sub-valve
  • the maximum set flow rate it is converted into total kinetic inertia energy from the gap, and the rotating disk-shaped inward radiated vortex water flow is radiated toward the runner blade radiant vortex receiving port, and the runner rotational force generating blade water flow is followed.
  • variable guide vane used in Francis turbines is not provided to prevent entanglement of dust, and the partial load water flow is based on the sliding setting position of the two ring valves depending on the state of the full load water flow.
  • Rotating disk-shaped inwardly radiating vortex water flow required for loading to secure the required energy by sliding toward the ring main valve to narrow the opening size and at the same time the ring sub-valve and radial port ring valve base side
  • the valve components are partially opened with the same amount of movement, and the energy retention escape discharge water flow is released, and the load can be safely and widely tracked without changing the water flow in the water conduit, that is, the water intake of the water channel power plant.
  • Emergency avoidance damper that enables balanced control operation that shifts to load operation, and also prevents water hammer phenomenon in the waterway in the case of sudden operation at the time of emergency stop Combines ability, constitutes an outer shell portion of the hydro turbine to emit the rotating disk-shaped inward radiation vortex water flow having multiple functions essential to small hydropower.
  • Rotating disk-shaped inwardly radiating vortex water flow that reaches the runner blade radiant vortex receiving port radiates from an annular main valve sharing the shaft core and acts on all blades simultaneously and continuously without any breaks. Except for fluctuations caused by reaction due to load fluctuations, the impact force due to runner rotation unique to impulse turbines is eliminated, preventing damage due to noise and metal fatigue, and strong against the runner crown to prevent sudden reflection behavior
  • the runner rotates by gradually reducing the water speed by balancing the moving direction of the moving body and the centrifugal force in the water flow and blade relation so as to form a rectification that gradually converts the total kinetic inertia energy to mechanical power.
  • the bunt structure used in Francis turbines is not used because it causes entanglement of dust, and a runner blade water overflow rib is provided to prevent the water flow from splashing outside the blade due to rotational centrifugal force.
  • the runner blade radial vortex receiving port that receives the radial eddy current first and divides and distributes the water flow to each blade is a place where dust gets entangled.
  • the angle formed by the approaching direction of the radiating vortex and the cutting edge is set to about 120 degrees and the bevel to the downstream side, so that it gradually moves to the downstream side according to the fluctuation of the vortex, and finally reaches the runner blade water discharge gate.
  • a turpin runner with a runner blade designed and improved so that it is naturally excluded along with the water flow on the blade is used.
  • the runner blade water overflow prevention rib contributes to the improvement of the structural strength of the blade by combining the smooth curve of the blade and the smooth curve of the strong turbine crown.
  • the receiving source pressure water flow 9a led from the water guide pipe narrows the cross section of the water flow at the vortex flow rate adjusting movable gate 1a before flowing into the spiral pipe 1, and converts about half of the energy into velocity kinetic energy.
  • the spiral tube 1 is stored as a half-pressure and half-kinetic energy-bearing vortex, and is arranged in the runner axial direction as a main control valve between the radial outlet upstream cylindrical base material 1b and the radial outlet ring-shaped valve base side 1d on the runner side of the spiral pipe.
  • An annular main valve 2 that freely slides in parallel and an annular sub-valve 3 similar to the main valve 2 are provided adjacent to each other, and the distance between each is controlled and changed, so that the runner blade 6 has a rotating disk-shaped inward radiating vortex.
  • the water stream 9c is converted into total kinetic inertial energy and radiated into a runner rotational force generating blade water stream, which maintains a stable flow rate that prevents safe and stable rotation and water hammer in the waterway.
  • the amount can be freely controlled.
  • the main valve 2 is further provided with an annular main valve watertight mechanism 2b via an annular main valve sliding mechanism 2a.
  • the runner blade 6 is attached to the runner crown 5 in an orderly and firm manner, and the rotational energy is reliably transmitted to the runner shaft 4 via a hub and a fixed key to a turbine load 8 such as a generator.
  • a turbine load 8 such as a generator.
  • the runner blade radial vortex receiving port 6a, the runner blade water flow overflow rib 6b, and the runner blade water flow discharge gate 6c are clearly shown so that the position configuration and shape can be considered.
  • Fig. 5 shows how runner blades 6 are arranged in an orderly manner at regular intervals in the direction of rotation so that dust does not get entangled with the runner blade 6 as the base point, depending on the runner diameter.
  • the flow state of the vortex flow rate adjusting movable gate 1a before flowing into the spiral tube 1 of the original pressure water flow 9a is shown.
  • the shape of the runner blade is shown in detail from the upstream side to the downstream side using a perspective view of its cross-sectional position.
  • the runner blade 6 firmly supported by the runner crown 5 rectifies the blade.
  • the centrifuge by runner rotation for further efficiency improvement is shown. It shows a state in which the runner blade water flow overflow rib 6b is provided to suppress the phenomenon that the rectification on the blade jumps outward by force.
  • FIG. 3 four states of the water flow of the hydro turbine, which is a feature of the present invention, are shown by a cross-sectional view including the shaft core.
  • the structure is completely closed, and the opening degree of the annular main valve 2 and the annular sub-valve 3 is adjusted to the maximum set flow rate, and the rotating disc-shaped inward radiating vortex water flow 9c is directed toward the runner blade radiant vortex receiving port 6a through the clearance.
  • the runner blade water flow discharge gate is converted into inertial energy and radiated, and the runner blade 6 that smoothly curves as the runner rotational force generating blade water flow 9 maintains rectification without being affected by changes in the amount of water and sequentially converts it into mechanical rotational force.
  • 6c is shown as a discharge water flow 9e after rotating energy conversion to the runner.
  • the annular sub-valve 3 is designed so that the energy flow of the rotating disc-shaped inwardly radiating vortex water flow 9c required when the annular sub-valve 3 is partially loaded from the sliding setting position of the annular valve according to the state of the full-load water flow. Is required to secure the required energy by narrowing the opening dimension Lc by sliding the valve in the direction of the annular main valve 2, and at the same time, the opening dimension Ld of the valve component part of the ring-shaped sub-valve 3 and the radial ring-shaped valve base material side 1d is naturally the same distance.
  • the water flow at the time of no-load shut-off is to slide the ring sub-valve 3 further in the direction of the ring main valve 2 from the sliding setting position of the ring valve according to the state of the partial load water flow to seal the gap with the ring main valve 2
  • the flow rate of the rotating disc-shaped inward radiating vortex water flow 9c is completely eliminated, and at the same time, the valve components of the annular sub-valve 3 and the radiant-ring annular valve base 1d are fully opened with the same dimensions, and the energy holding escape discharge water flow 9d is discharged and guided. This shows that it is possible to safely proceed to no-load and stop the runner without changing the amount of water in the water channel, that is, the amount of water intake of the water channel power plant.
  • a rotating disk-shaped inward radiating vortex water flow 9c is divided into each blade by a runner blade radiating vortex receiving port 6a along the curve on the runner blade 6 with the rib of the hydro turbine which is a feature of the present invention. From the total kinetic inertial energy, the runner rotational force generating blade water flow 9 is guided to the runner crown 5 and the runner blade water flow overflow rib 6b, and the runner blade 6 that smoothly curves and maintains rectification without being affected by changes in the amount of water.
  • the flow cross-sectional area is gradually increased due to a decrease in flow velocity while gradually converting to a rotational force, reaching the runner blade water discharge gate 6c and discharging to the runner as the discharge water flow 9e after the rotation energy conversion.
  • the midstream cross-section is Jj
  • the downstream cross-section is Kk
  • the efficiency change due to load fluctuation is taken for one blade as an example It shows in detail that there is less to effect.
  • the runner blade radial vortex receiving port 6a is provided with an oblique angle of about 120 degrees with respect to the incoming direction of the radiant vortex, so that the dust gradually moves due to the fluctuation of the water flow, and finally the water flow on the blade while being entangled with the runner blade overflow rib 6b.
  • it shows that it is devised so that it will flow down naturally.
  • FIG. 5 shows two basic variations of the hydro turbine that is a feature of the present invention.
  • the state of the change of the shape of the runner blade 6 when introduced into a turbine for a high head is shown.
  • the runner blade radial vortex receiving port 6a is common, but from a high-kinetic inertial energy flow with high speed and high impact,
  • the runner rotational force generation blade water flow 9 is guided to the runner crown 5 and the runner blade water flow overflow rib 6b while maintaining smooth rectification in the runner blade 6 which is smoothly curved, and sequentially converting into mechanical rotational force and low kinetic inertia energy.
  • the capacity of the discharge water flow 9e after the rotation energy conversion is increased by increasing the ratio of the width of the runner blade water flow discharge gate 6c and increasing the rotation diameter Lb. It shows that it corresponds.
  • a power plant for the purpose of selling power through grid interconnection without the need for the second partial load operation only requires water volume follow-up operation, does not require hydroturbine equilibrium control operation to keep the water intake steady, and becomes a steady operation based on the amount of water that can be taken. If the consent of the relevant organization is obtained, it is possible to construct a plant that omits the ring-shaped secondary valve 3 for equilibrium control, and the water flow at the time of operation and shutdown of the hydroturbine As shown.
  • FIG. 6 is a representation that the vertical direction of the axial direction of the hydro turbine, which is a feature of the present invention, has been described so far.
  • Many of the facilities are of the horizontal axis type, and the discharge water housing 7 is also provided in the horizontal axis turbine in combination with the reason of workability such as maintenance management, so that the scale of the plant installation structure upper surface 7a becomes large and the spiral tube
  • the size of the structure that stops the bulge in the axial direction of 1 cannot be ignored, it is shown that this is advantageous in terms of total cost and can be handled in the case of a small-scale power plant.
  • FIG. 7 conceptually shows the vortex flow inside the turbine, and the incoming pressure water flow 9a introduced from the water conduit has a water flow cross-sectional area at the movable vortex flow adjusting gate 1a before flowing into the spiral tube 1.
  • About half of the energy of the throttle is converted into velocity kinetic energy and stored in the spiral tube 1 as a half-pressure half-kinetic energy-bearing vortex 9b, and passes through the radial base upstream side cylindrical substrate 1b on the runner side of the spiral tube. Is converted into total kinetic inertial energy to radiate a rotating disc-shaped inwardly radiating vortex water flow 9c, and is divided into blades by the runner blade radiant vortex flow receiving port 6a.
  • the runner blades 6 while being guided by the runoff blade rib 6b and smoothly curved, the runner blades 6 are maintained in rectification and are sequentially converted into mechanical rotational forces. Converted into rotational energy of the runner reaches the de water discharge gate 6c shows that to achieve the objective.
  • the solid arrow indicates that it is a pressure water flow
  • the white arrow indicates that it is a vortex with half pressure and half kinetic energy
  • the simple bar arrow indicates that the kinetic energy gradually increases depending on its size. It shows the situation of disappearing and converting into runner rotational energy.
  • FIG. 8 is a partially enlarged view, and the opening dimension Lc for radiating the rotating disc-shaped inward radiating vortex water flow 9c from the gap between the ring-shaped main valve 2 and the ring-shaped subvalve 3 is defined as 1d.
  • the arrangement of the valve component opening dimension Ld for discharging the energy holding escape discharge water flow 9d from the clearance between the ring main valve 2 and the ring sub valve 3 required for the impulse type hydro turbine design is described.
  • Equation (1) the radial discharge velocity V of the theoretical discharge rotating disc-shaped inward radiating vortex water flow 9c at the set head effective head H is obtained in the 1-1 column, and the runner rotation speed N is obtained in the 1-2 column. It should be noted that the signs and numerical values arranged in adjacent rows with respect to the columns in the frame correspond to each other.
  • Equation 2 The amount of water Q acting on all the runner blades per second is calculated by Equation 2, and the positions of the setting example value point A (in the circle) and other setting example value points B (in the circle) are shown in the horizontal axis of Table 2.
  • the flow rate is shown in Fig. 6 and the vertical axis indicates which position in the example of a compatible turbine is shown as an effective head. Note that the points A and B are all the same setting example values in the equations 3 and 4, and are the same points.
  • Table 2 shows an example of a characteristic constraint operation characteristic curve of this turbine.
  • N / Nr the ratio of the water quantity applied to the runner blade by control valve adjustment (control of kc) to the unit water quantity Qr on the vertical axis.
  • ⁇ efficiency
  • FIG. 8 Indicates that it has a curve of solid line display is improved by increasing the rotational velocity ratio radiation flow rate of the vortex 9b aperture eddy flow rate adjusting movable gate 1a.
  • Table 3 (graph) is a solid line that examines various materials, considers basic water wheel compatibility examples, and suits the impulse hydro turbine of the present invention based on various simulation calculations. It can be partially applied in the applicable range of conventional Francis turbines and Pelton turbines, and can be applied almost entirely in the compatible regions of crossflow turbines and targo turbines.
  • Table 4 shows the 20-year cash flow for small hydropower generation with weak profitability, so that the 20-year cash flow in the turbine construction business of this application and the conventional turbine can be easily distinguished.
  • This is a graph of the results of simulation considering all the assumptions. a is the case where the hydro turbine of the present application, which is easy to maintain and noise countermeasures, is adopted. b is an example of adopting a conventional hydro turbine that is efficient and has a proven record under specific conditions but requires consideration for maintenance and noise countermeasures. It is.
  • the horizontal axis shows the number of years from the construction completion date to the simulation period, and the vertical axis shows all the current funds.
  • the dotted line graph Mk shows the transition of construction funds and funds for equipment renewal by depreciation, and the solid line graph.
  • Ml indicates the cumulative amount of dividends paid to construction capital investors, Ma is the power sales revenue amount to Company A (example), and Mb is the power sales revenue to Company B (example)
  • the amount of money, Mc represents the amount of power sales revenue to company C (example), and the total amount of money is equivalent to the total amount of sales.
  • Md is the cost of various compensation money, right money, asset tax etc.
  • Me is the plant operator labor cost
  • Mf is the plant operation miscellaneous cost
  • Mg is the plant maintenance and repair cost
  • Mh is the investor dividend
  • Mi represents income tax, etc.
  • Mj represents depreciation expenses. If the total accumulated amount from Me to Mj corresponds to the total amount of expenses and protrudes from the upper limit of the accumulated band graph, it means deficit settlement.
  • a is for the case of adopting the hydro turbine of the present application, which is easy to maintain and noise countermeasures, and the cumulative total dividend Ml is about twice the total sales every two years.
  • b adopts a conventional hydro turbine, which is efficient and has a track record in specific conditions, but has many days of operation interruption due to maintenance and high efficiency. It is easy to see that the company is making good results. Note that this simulation shows a similar comparative example, and changes depending on the plant scale and site conditions, so that detailed display characters and amounts are reduced and no distinguishable notation is used.
  • the form in which the present invention can be most utilized overcomes the problems that must be solved in small hydropower plants and the like that are expected to spread in the future, and is efficient from low water to high water, from light load to rated load and emergency It can be easily and safely handled even when it stops, and it can be expanded and introduced as a power source for future hydropower brands with less noise and less maintenance.

Landscapes

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

Abstract

L'invention concerne une turbine hydraulique et traite du problème lié au développement d'une roue à aubes à usage général, dans laquelle le bruit de l'enchevêtrement des déchets et les changements soudains dans la quantité d'admission d'eau et d'eau déchargée sont évités, une efficacité élevée est maintenue même avec les changements de quantité d'eau et une opération de suivi de quantité d'eau est simplifiée pour réduire le coût total au minimum. L'invention concerne une turbine hydraulique du type à impulsion, dans laquelle une zone en section transversale du courant d'eau est rétrécie dans un passage mobile d'ajustement de vitesse à courant de Foucault (1a) et approximativement la moitié de l'énergie de pression est convertie en énergie cinétique à grande vitesse et stockée dans un tube hélicoïdal en tant que courant de Foucault retenant l'énergie à moitié de pression et à moitié cinétique (9b), une soupape principale annulaire (2) et une soupape auxiliaire annulaire (3) qui coulissent parallèlement à une direction d'axe de canal sont prévues sur une âme partagée de manière à enserrer un canal, un canal d'eau de décharge de libération retenant l'énergie, qui contourne en interne un canal de roue à aubes pour une opération de suivi de charge et pour un arrêt d'urgence, est conçu en déplaçant les positions de soupapes, l'impact d'aube qui se produit avec la rotation est éliminé à l'aide d'un courant d'eau de Foucault radial vers l'intérieur en forme de disque rotatif (9c) pour réduire le bruit au minimum et des aubes de canal nervurées empêchant la diffusion de l'eau et retenant l'énergie (6), qui sont de forme incurvée et qui amènent les déchets à s'écouler vers le bas en raison de l'action d'auto-nettoyage du courant d'eau, sont prévues pour réduire le débit lorsque l'énergie est convertie et pour maintenir un écoulement régulé.
PCT/JP2016/062863 2016-04-24 2016-04-24 Turbine hydraulique du type à impulsion WO2017187472A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN201680084727.XA CN109072860B (zh) 2016-04-24 2016-04-24 冲击式水力涡轮机
JP2018513947A JP6425157B2 (ja) 2016-04-24 2016-04-24 衝動型ハイドロタービン
PCT/JP2016/062863 WO2017187472A1 (fr) 2016-04-24 2016-04-24 Turbine hydraulique du type à impulsion
AU2016404873A AU2016404873B2 (en) 2016-04-24 2016-04-24 Impulse-type hydro turbine
ZA2018/07925A ZA201807925B (en) 2016-04-24 2018-11-23 Impulse-type hydro turbine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2016/062863 WO2017187472A1 (fr) 2016-04-24 2016-04-24 Turbine hydraulique du type à impulsion

Publications (1)

Publication Number Publication Date
WO2017187472A1 true WO2017187472A1 (fr) 2017-11-02

Family

ID=60161389

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2016/062863 WO2017187472A1 (fr) 2016-04-24 2016-04-24 Turbine hydraulique du type à impulsion

Country Status (5)

Country Link
JP (1) JP6425157B2 (fr)
CN (1) CN109072860B (fr)
AU (1) AU2016404873B2 (fr)
WO (1) WO2017187472A1 (fr)
ZA (1) ZA201807925B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020186327A1 (fr) * 2019-03-18 2020-09-24 Frangie Nabil H Turbine à impulsion électromagnétique assistée hydrauliquement

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113090435B (zh) * 2021-05-08 2023-02-03 重庆水轮机厂有限责任公司 一种水轮机
CN114477325B (zh) * 2022-01-26 2023-03-24 中国水利水电科学研究院 一种库湾水华的自适应调控装置及其方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5951164A (ja) * 1982-09-20 1984-03-24 Toshiba Corp 水力機械
JPS61157179U (fr) * 1985-03-22 1986-09-29
JPS63173U (fr) * 1986-06-17 1988-01-05
JP2001115941A (ja) * 1999-10-18 2001-04-27 Mitsubishi Heavy Ind Ltd 水車設備

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2139932A (en) * 1937-11-10 1938-12-13 Rodney Hunt Machine Co Turbine
JPS5692360A (en) * 1979-12-27 1981-07-27 Fuji Electric Co Ltd Water wheel
IE50310B1 (en) * 1980-06-11 1986-04-02 Patrick Belton Snr A water turbine
ATE155852T1 (de) * 1991-11-21 1997-08-15 Ente Naz Energia Elettrica Leitapparat für hydraulische reaktionsturbinen
CN101354004A (zh) * 2007-07-25 2009-01-28 黄国宏 全能水轮机
CN102878002B (zh) * 2012-10-10 2016-05-25 中国电建集团西北勘测设计研究院有限公司 一种防止水轮机引水系统水击压力升高的方法
FR3006717B1 (fr) * 2013-06-05 2019-05-17 Alstom Renewable Technologies Procede de rehabilitation d'une installation de conversion d'energie et installation de conversion d'energie rehabilitee

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5951164A (ja) * 1982-09-20 1984-03-24 Toshiba Corp 水力機械
JPS61157179U (fr) * 1985-03-22 1986-09-29
JPS63173U (fr) * 1986-06-17 1988-01-05
JP2001115941A (ja) * 1999-10-18 2001-04-27 Mitsubishi Heavy Ind Ltd 水車設備

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020186327A1 (fr) * 2019-03-18 2020-09-24 Frangie Nabil H Turbine à impulsion électromagnétique assistée hydrauliquement

Also Published As

Publication number Publication date
JPWO2017187472A1 (ja) 2018-06-14
AU2016404873B2 (en) 2021-12-02
CN109072860A (zh) 2018-12-21
ZA201807925B (en) 2019-07-31
JP6425157B2 (ja) 2018-11-21
AU2016404873A1 (en) 2019-01-03
CN109072860B (zh) 2019-11-12

Similar Documents

Publication Publication Date Title
Alatorre-Frenk Cost minimisation in micro-hydro systems using pumps-as-turbines
Okot Review of small hydropower technology
Kaunda et al. A technical discussion on microhydropower technology and its turbines
WO2017187472A1 (fr) Turbine hydraulique du type à impulsion
CN104471239A (zh) 具有流控制的垂直轴风力兼液力涡轮机
US11952976B2 (en) Hydraulic turbine
Arndt et al. Hydraulic turbines
Quaranta Investigation and optimization of the performance of gravity water wheels
Helmizar Turbine wheel-a hydropower converter for head differences between 2.5 and 5 m
Chattha et al. Design of a cross flow turbine for a micro-hydro power application
Muller The effect of using upper shroud on the performance of a breashoot water wheel
Chisale et al. Design of a pelton turbine for a specific site in Malawi
Wankhade et al. Automatic dam doors control centrifugal governor
Daugherty Hydraulic turbines: with a chapter on centrifugal pumps
Irie et al. Proposal of a new hydraulic turbine capable of high efficiency operation over a wide range of flow rate and effective head
Nielsen Hydropower and pumped storage
Beraki Effect of Surface roughness for Hydro Turbine Step-up Efficiency
PAMINN et al. Design and Numerical Simulation of Impeller Unsteady Interaction in Low Head Reaction Turbine
Hassan et al. Hydraulic Power Plants: A Textbook for Engineering Students
RU2653647C1 (ru) Способ регулирования мощности реактивных гидротурбин
Dewees Jr Streamlined Licensing of Small-Scale Hydroelectric Projects in Massachusetts
MAW et al. Design and Analysis of 30MW Pelton Turbine
Seewer Recent Developments in Hydro-Electric Engineering with Special Reference to British Practice
White Advances in the art of waterwheel designs and settings
Ramachandra Research on functionality of underpressure helical turbine

Legal Events

Date Code Title Description
ENP Entry into the national phase

Ref document number: 2018513947

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16900345

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2016404873

Country of ref document: AU

Date of ref document: 20160424

Kind code of ref document: A

122 Ep: pct application non-entry in european phase

Ref document number: 16900345

Country of ref document: EP

Kind code of ref document: A1