US3238534A - Hydraulic pumps and reversible pump turbines - Google Patents

Hydraulic pumps and reversible pump turbines Download PDF

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Publication number
US3238534A
US3238534A US314463A US31446363A US3238534A US 3238534 A US3238534 A US 3238534A US 314463 A US314463 A US 314463A US 31446363 A US31446363 A US 31446363A US 3238534 A US3238534 A US 3238534A
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United States
Prior art keywords
impeller
water
suction tube
valve
casing
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Expired - Lifetime
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US314463A
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English (en)
Inventor
Hartland Derek
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English Electric Co Ltd
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English Electric Co Ltd
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    • 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
    • F03B15/00—Controlling
    • F03B15/005—Starting, also of pump-turbines
    • 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
    • F03B11/002—Injecting air or other fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
    • F03B3/10—Machines or engines of reaction type; Parts or details peculiar thereto characterised by having means for functioning alternatively as pumps or turbines
    • F03B3/103—Machines or engines of reaction type; Parts or details peculiar thereto characterised by having means for functioning alternatively as pumps or turbines the same wheel acting as turbine wheel and as pump wheel
    • 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
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y10S415/91—Reversible between pump and motor use

Definitions

  • a hydraulic pump or reversible pump turbine includes means for injecting water into the draft tube with a substantial tangential component adjacent the Wall of the suction tube below and adjacent to the impeller of the pump or reversible pump turbine, so as to generate a vortex having a substantial peripheral velocity, during priming of the pump, or of the reversible pump turbine in operation as a pump.
  • FIG. 1 shows generally a first embodiment of hydraulic pump or reversible pump turbine in accordance with the invention
  • FIGS. 2 and 3 show details of the arrangement of FIG. 1 on a larger scale
  • FIG. 4 is a graph plotting power absorbed against time
  • FIG. 5 shows another embodiment of hydraulic pump or reversible pump turbine in accordance with the invention
  • FIG. 6 shows a further modification of hydraulic pump or reversible pump turbine in accordance with the invention.
  • FIG. 7 shows yet another modification, on a larger scale than FIG. 1.
  • a large hydraulic pump i.e., a pump having an input power greater than one megawatt
  • the pump also includes a shaft 15, through which the impeller is driven by a motor 16.
  • the stationary structure of the pump includes a spiral casing 17, which surrounds the impeller and is connected to a delivery pipe 18 incorporating a valve 19.
  • the delivery pipe is connected to a reservoir (not shown) to which water is to be delivered during pump operation.
  • a suction tube Zil vertically below and symmetrical with the impeller Immediately below the eye of the impeller 11 is provided a suction tube Zil vertically below and symmetrical with the impeller. At the lower end of the suction tube there is provided an inlet bend tube 21 which communicates through a passage 22 with a lower reservoir (not shown) from which water is to be pumped.
  • the passage 23 surrounding the impeller 11 may be provided with adjustable guide vanes 24 and a ring of fixed vanes 25 as shown, through which water is delivered by the impeller 11 into the spiral casing 17, or alternatively in certain cases only a ring of fixed diffuser vanes may be provided.
  • the centre of the crown 12 is formed with a cavity 26 connected by a bore 27 with an annular space 28 between the stationary structure and the rotating parts of the pump, sealing rings 29, 30 between the stationary structure and the rotating parts Patented Mar. 1, 1966 and the stationary structure, and a further labyrinth seal 34 is provided between the skirt 13 and the stationary structure at the top of the suction tube 20.
  • a drain pipe 35 is provided between the sealing ring 30 and the labyrinth seal 33 through which any leakage is drained off.
  • annular structure 36 defining a chamber 37 surrounding the suction tube 20, and the suction tube wall is provided with baffles 38 defining slots 39 opening to the interior of the suction tube.
  • elongated slots 39 there may be provided circular or other orifices, and instead of the annular chamber 37 there may be a series of short circumferential chambers, or the slots or orifices may be fed direct from pipes connected for example to a manifold. A single orifice of appropriate size and supplied with water of the appropriate head would be adequate.
  • a pipe 50 is connected to a source of water under pressure, such as may be afforded by the spiral casing 17, and is connected at its other end to the chamber 37.
  • a valve 51 is provided in the pipe 50.
  • the impeller 11 In starting operation of a pump or of a reversible pump turbine in the pumping sense, the impeller 11 is first accelerated by any known or convenient means such as an auxiliary motor from rest to synchronous speed in air, the water being depressed down the suction tube by the introduction of compressed air through pipe 31. A small amount of water may be admitted to the impeller seals during this phase, to reduce the risk of the fine clearances, with which the impeller runs, being taken up and seizing occurring.
  • the valve 19 is closed, and the adjustable guide vanes 24 are in the closed position (as shown in FIG. 1) at this stage.
  • the method of operation described with relation to the first embodiment is probably impractical in machines only fitted with fixed diffuser vanes.
  • the motor 16 is connected to the power supply, e.g., to the grid, and synchronised and the auxiliary motor may be disconnected.
  • the power absorbed in these two phases rises from zero to about 3 percent of the normal full load, and they may be completed, for example, in two minutes (see FIG. 4).
  • valve 19 is then opened to allow pressure water from the delivery pipe 18 into the spiral casing 17, the adjustable guide vanes 24 remaining shut.
  • the valve 51 is then opened partially and slowing to allow pressure being provided at the top and bottom of the space 28.
  • a labyrinth seal 33 is provided between the crown 12 water into chamber 37 to produce a vortex in the suction tube 20.
  • Some of the water, which owing to the centrifugal effect tends to remain against the wall of the suction tube 20, will travel downwards and some upwards into the passages between the vanes 14 of the impeller 11, and in this way the impeller will be slowly filled and the motor 16 will slowly take on load (phase 3, FIG. 4).
  • Some of the water in the impeller leaks from the periphery through the space between the skirt 13 and the casing, and through seal 34, into the suction tube 20, but additional water is continuously flowing in from chamber 37.
  • Valve 51 is then fully opened, and the remaining air is allowed to escape in a controlled manner from the suction tube 20 through cavity 26, bore 27, bore 31 and valve 32. By this means additional load is taken on by the motor 16 relatively slowly (phase 4, FIG. 4).
  • This phase has hitherto produced a sudden rise in the power absorbed, caused by a rapid change in the flow regime in the suction tube. Once this phase was initiated, it was extremely difficult to arrest or reverse. Hitherto this sudden change, caused by circulation of the water both circumferentially and axially of the suc tion tube, has caused the power absorbed to rise from about 17 percent to about 27 percent of normal full load for pumps with adjustable guide vanes, and from about 40 percent to about 60 percent for pumps with fixed guide vanes, in a fraction of a second (see FIG. 4).
  • the air may be exhausted slowly through pipe 31 and the impeller filled without causing a sudden rise in the power which must be supplied by the motor 16. This is because the vortex generated by the jets of water issuing from chamber 37 artificially produces the final flow regime and there can be no sudden change which requires energy to be supplied by the motor 16.
  • the air from the centre of the suction tube can be exhausted at a slow, controlled rate, and the motor will take on load at a steady rate.
  • the energy required to maintain the vortex is derived from the supply of water from the delivery pipe 18, flowing through valve 19, spiral casing 17, and pipe 50, rather than being derived entirely from the impeller, as hitherto.
  • valve 51 When all the air has been exhausted from the impeller 11, the valve 51 may be progressively closed, so that the load on the motor is gradually further increased.
  • the adjustable guide vanes 24 are gradually opened so that the power absorbed is increased in a controllable manner up to full load.
  • the valve 51 is closed for normal operation.
  • FIG. 5 there is shown an modification of the arrangement of FIGS. 13 in which instead of pipe 50 and valve 51, there is provided a pipe 60 fitted with a valve 61, leading from the delivery pipe 18 to the chamber 37.
  • This modification is suitable both for machines with adjustable guide vanes 24 and for machines having only fixed diffuser vanes 25.
  • valve 19 is operated as described for valve 51.
  • the valve 19 need not be opened until the end of the fifth phase.
  • FIG. 6 there is shown a further modification of the arrangement of FIGS. 1-3; in the modification intended for use with machines having adjustable guide vanes 24 there is provided a pipe 70 fitted with a valve 71, as shown; however in machines having only the fixed diffuser vanes 25 there may be provided a pipe 50 connected to the casing 17 and fitted with a valve 51, as shown in FIG. 1. (The latter arrangement is identical with that described with relation to FIGS. 1-3 except for the omission of the guide vanes, but the operation is different.)
  • Air is gradually released from the suction tube through pipe 31, allowing the water level in the suction tube 20 to rise slowly into the impeller inlet.
  • the water picked up by the vanes 14 is centrifuged to the outer periphery and displaces the air in the impeller radially inward.
  • the air/water boundary in the initial stage is shown by the chain-dashed line 72 (right-hand side of FIG. 6).
  • the valve 71 (or 51 as appropriate) is then opened so that pressure water from the impeller periphery or from the spiral casing passes through the pipe into chamber 37, emerging through slots 39 into the suction tube 20 and imparting a rotational velocity to the water in the suction tube.
  • the adjustable guide vanes 24 (or in pumps with only fixed diffuser vanes 25, the delivery valve 19) are gradually opened so that the power absorbed is increased in a controllable manner up to full load, as described above.
  • the means for injecting water into the suction tube 20 may be provided by arranging for the part of the stationary casing including part 34a of the lower runner seal 34 to be made retractable with a short downward stroke, providing a path for pressure water from the passage 23 to the suction tube 21 A number of small fixed vanes a set at an angle (as described in relation to baffles 38) on the retractable member 80 impart the required swirl to this water.
  • the retractable element 80 may be annular, as shown, and may be retracted by means of pistons 81 set in a series of cylinders 82 within the outer stationary casing 83 which forms a pressure-retaining wall.
  • Operation in this case is substantially as described with reference to FIG. 6, except that instead of opening valve 71 the element 80 is moved down.
  • the air/water boundary 84 shown corresponds to that at 73 in FIG. 6.
  • a large pressure difference exists between passage 23 and suction tube 20, and water flows as indicated by the arrows.
  • the circumferential velocity of water entering the passage 85 between the skirt 13 and element 80 from passage 23 is almost equal to the circumferential velocity at exit from the impeller. This velocity will increase at exit from passage 85 proportionally to the decrease in radius of the vortex, and thus a very intense vortex may be set up in the suction tube 20.
  • the pressure water from between the impeller skirt 13 and the stationary casing may be admitted to chamber 37 to emerge into the suction tube as jets by means of a rotatable ported ring which can be rotated between a position in which its ports register with corresponding ports in the stationary structure and a position in which the ports are closed.
  • a hydraulic machine comprising a casing
  • a suction tube mounted on said casing upstream of said impeller for connection to a liquid reservoir, means for introducing gas into said impeller,
  • said means for injecting liquid into said suction tube comprises,
  • control means selectively operable to move said plate away from said impeller whereby to define a channel between said plate and said impeller and create a flow path for liquid circulating through said impeller back into said suction tube.
  • a hydraulic machine comprising a spirally-wound tube connected to said casing downstream of said impeller, and wherein said means for injecting liquid into said suction tube comprises,
  • valve means mounted in said liquid flow tube and selectively operable to permit the passage of said liquid from said spirally-Wound tube into said suction tube through the said outer casing.
  • a hydraulic machine comprising,
  • an inlet tube mounted on said casing upstream of said impeller, said tube having one end for receiving Water from a reservoir and another end connected adjacent to said impeller for feeding the water thereto,
  • first valve means mounted on said casing and selectively operable to introduce air into said impeller and control the rate at which air is subsequently exhausted from said impeller whereby the advance of water along said inlet tube is controlled during the period in which the said machine is started,
  • second valve means mounted in said water flow pipe and selectively operable to introduce water from said source into said inlet tube during the said period whereby to cause said Water advancing along the inlet tube to describe a vortex during the said period.
  • a hydraulic machine comprising a casing
  • a suction tube mounted on said casing upstream of said impeller for connection to a liquid reservoir
  • valve means for controlling the rate at which air is exhausted from said impeller during the period in which the machine is started whereby to control the advance of said liquid along the suction tube towards the impeller,

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US314463A 1962-10-15 1963-10-07 Hydraulic pumps and reversible pump turbines Expired - Lifetime US3238534A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB38853/62A GB1006365A (en) 1962-10-15 1962-10-15 Improvements in or relating to hydraulic pumps and reversible pump turbines

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US (1) US3238534A (de)
AT (1) AT243621B (de)
CH (1) CH405939A (de)
DE (1) DE1528821A1 (de)
ES (1) ES292503A1 (de)
GB (1) GB1006365A (de)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3307828A (en) * 1966-06-29 1967-03-07 Baldwin Lima Hamilton Corp Torque reducing means
US3309057A (en) * 1964-03-11 1967-03-14 Hitachi Ltd Method of starting operation of pumps and pump turbines
US3372645A (en) * 1966-03-16 1968-03-12 Baldwin Lima Hamilton Corp Power-accumulation system
US3403888A (en) * 1966-05-20 1968-10-01 English Electric Co Ltd Reversible pump turbines
US3507603A (en) * 1966-03-10 1970-04-21 Escher Wyss Ltd Filling a two-stage or multi-stage hydraulic turbomachine with water
US3724966A (en) * 1970-07-29 1973-04-03 Dominion Eng Works Ltd Hydraulic machine crown aeration
US3923417A (en) * 1974-12-30 1975-12-02 Allis Chalmers Hydraulic turbine spiral case drain
US3927951A (en) * 1973-09-08 1975-12-23 Tokyo Shibaura Electric Co Water turbine
US3945754A (en) * 1973-08-06 1976-03-23 Hitachi, Ltd. Hydraulic machines and operating method thereof
US4014624A (en) * 1974-08-16 1977-03-29 Hitachi, Ltd. Method and device for starting pump
US4025228A (en) * 1974-07-09 1977-05-24 Ateliers Des Charmilles S.A. Hydraulic plant
US4142825A (en) * 1976-11-26 1979-03-06 Dominion Engineering Works Limited Draft tube aeration with eductor
US4179237A (en) * 1976-10-08 1979-12-18 Hitachi, Ltd. Method for controlling the operation of a fluid machine in spinning reserve
US4412779A (en) * 1981-02-03 1983-11-01 Tokyo Shibaura Denki Kabushiki Kaisha Control method for multi-stage hydraulic machine
US4514138A (en) * 1982-02-26 1985-04-30 Tokyo Shibaura Denki Kabushiki Kaisha Leakage water discharge method and apparatus in a reversible hydraulic machine
US4898512A (en) * 1989-03-27 1990-02-06 Geffs John J Apparatus and method for reducing effects of draft tube pressure fluctuations
US4948336A (en) * 1987-12-10 1990-08-14 Sundstrand Corporation Mechanical shaft seal
US4964783A (en) * 1988-04-20 1990-10-23 Hanning Electro-Werke Gmbh & Co. Device for emptying a liquid-collection tank in a water-conducting household appliance
US5941682A (en) * 1997-07-24 1999-08-24 Voith Hydro, Inc. Draft tube peripheral plenum
US7094016B1 (en) * 1999-07-21 2006-08-22 Unitec Institute Of Technology Multi-phase flow pumping means and related methods
US20110158795A1 (en) * 2008-05-27 2011-06-30 Kevin Edward Burgess Centrifugal pump impellers
CN103228908A (zh) * 2010-11-02 2013-07-31 沃依特专利有限责任公司 用于水力发电站的混流式泵
DE102013019652A1 (de) * 2013-09-30 2015-04-02 Dieter Mühlenbruch Wasserkraftwerk
CN109092580A (zh) * 2018-10-15 2018-12-28 厦门英仕卫浴有限公司 一种高效节能的出水组件
US11378084B2 (en) * 2013-09-12 2022-07-05 Ebara Corporation Apparatus and method for alleviating and preventing cavitation surge of water supply conduit system

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AU769473B2 (en) * 1998-03-13 2004-01-29 Unitec Institute Of Technology Improved pumping apparatus and methods
WO1999046513A1 (en) * 1998-03-13 1999-09-16 Unitec Institute Of Technology Improved pumping apparatus and methods
DE50303864D1 (de) * 2003-12-04 2006-07-27 Tcg Unitech Systemtechnik Gmbh Radialpumpe
NO20044391D0 (no) * 2004-10-18 2004-10-18 Troms Kraft Produksjon As Anordning og fremgangsmate ved sugeror
BE1017069A3 (nl) * 2006-04-25 2008-01-08 Atlas Copco Airpower Nv Verbeterde turbocompressor met leischoepen.
FR2919353B1 (fr) 2007-07-23 2014-02-14 Alstom Power Hydraulique Machine hydraulique comprenant des moyens d'injection d'un ecoulement preleve d'un ecoulement principal
CN110173444B (zh) * 2019-04-30 2021-03-26 中国科学院工程热物理研究所 分体式超临界二氧化碳闭式叶轮及制造方法

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US820779A (en) * 1905-04-03 1906-05-15 Laval Steam Turbine Co Pumping apparatus.
FR562881A (fr) * 1922-04-28 1923-11-21 Dispositif pour moto-pompe centrifuge
US1787655A (en) * 1929-05-18 1931-01-06 American Blower Corp Apparatus and method of controlling fans
GB343385A (de) * 1929-04-23 1931-02-19 Georg Weyland
FR935340A (fr) * 1946-10-28 1948-06-16 Augmenteur de flux pour réacteurs et compresseurs
US2444100A (en) * 1944-02-28 1948-06-29 Marison Company Pump
US2656096A (en) * 1946-01-04 1953-10-20 Rateau Soc Centrifugal pump and compressor
US2690293A (en) * 1951-01-20 1954-09-28 Westinghouse Electric Corp Fan
US2786420A (en) * 1952-03-27 1957-03-26 Stanley G Harwood Pressure controlled pump
US2798658A (en) * 1955-03-01 1957-07-09 Westinghouse Electric Corp Volume controls for centrifugal fans
US2865297A (en) * 1952-12-22 1958-12-23 Thompson Prod Inc Injector cover for pumps
US2874642A (en) * 1955-10-05 1959-02-24 Allis Chalmers Mfg Co Adjustable bypass valve
CA571575A (en) * 1959-03-03 General Motors Corporation Pump inlet fitting
US3019963A (en) * 1955-07-08 1962-02-06 Eck Bruno Christian Radial blower for gases with high dust content
US3041848A (en) * 1959-06-01 1962-07-03 Garrett Corp Variable head compressor
US3070025A (en) * 1958-03-03 1962-12-25 Thompson Ramo Wooldridge Inc Injector discharge pressure regulator for pumps

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Publication number Priority date Publication date Assignee Title
CA571575A (en) * 1959-03-03 General Motors Corporation Pump inlet fitting
US820779A (en) * 1905-04-03 1906-05-15 Laval Steam Turbine Co Pumping apparatus.
FR562881A (fr) * 1922-04-28 1923-11-21 Dispositif pour moto-pompe centrifuge
GB343385A (de) * 1929-04-23 1931-02-19 Georg Weyland
US1787655A (en) * 1929-05-18 1931-01-06 American Blower Corp Apparatus and method of controlling fans
US2444100A (en) * 1944-02-28 1948-06-29 Marison Company Pump
US2656096A (en) * 1946-01-04 1953-10-20 Rateau Soc Centrifugal pump and compressor
FR935340A (fr) * 1946-10-28 1948-06-16 Augmenteur de flux pour réacteurs et compresseurs
US2690293A (en) * 1951-01-20 1954-09-28 Westinghouse Electric Corp Fan
US2786420A (en) * 1952-03-27 1957-03-26 Stanley G Harwood Pressure controlled pump
US2865297A (en) * 1952-12-22 1958-12-23 Thompson Prod Inc Injector cover for pumps
US2798658A (en) * 1955-03-01 1957-07-09 Westinghouse Electric Corp Volume controls for centrifugal fans
US3019963A (en) * 1955-07-08 1962-02-06 Eck Bruno Christian Radial blower for gases with high dust content
US2874642A (en) * 1955-10-05 1959-02-24 Allis Chalmers Mfg Co Adjustable bypass valve
US3070025A (en) * 1958-03-03 1962-12-25 Thompson Ramo Wooldridge Inc Injector discharge pressure regulator for pumps
US3041848A (en) * 1959-06-01 1962-07-03 Garrett Corp Variable head compressor

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3309057A (en) * 1964-03-11 1967-03-14 Hitachi Ltd Method of starting operation of pumps and pump turbines
US3507603A (en) * 1966-03-10 1970-04-21 Escher Wyss Ltd Filling a two-stage or multi-stage hydraulic turbomachine with water
US3372645A (en) * 1966-03-16 1968-03-12 Baldwin Lima Hamilton Corp Power-accumulation system
US3403888A (en) * 1966-05-20 1968-10-01 English Electric Co Ltd Reversible pump turbines
US3307828A (en) * 1966-06-29 1967-03-07 Baldwin Lima Hamilton Corp Torque reducing means
US3724966A (en) * 1970-07-29 1973-04-03 Dominion Eng Works Ltd Hydraulic machine crown aeration
US3945754A (en) * 1973-08-06 1976-03-23 Hitachi, Ltd. Hydraulic machines and operating method thereof
US3927951A (en) * 1973-09-08 1975-12-23 Tokyo Shibaura Electric Co Water turbine
US4025228A (en) * 1974-07-09 1977-05-24 Ateliers Des Charmilles S.A. Hydraulic plant
US4014624A (en) * 1974-08-16 1977-03-29 Hitachi, Ltd. Method and device for starting pump
US3923417A (en) * 1974-12-30 1975-12-02 Allis Chalmers Hydraulic turbine spiral case drain
US4179237A (en) * 1976-10-08 1979-12-18 Hitachi, Ltd. Method for controlling the operation of a fluid machine in spinning reserve
US4142825A (en) * 1976-11-26 1979-03-06 Dominion Engineering Works Limited Draft tube aeration with eductor
US4412779A (en) * 1981-02-03 1983-11-01 Tokyo Shibaura Denki Kabushiki Kaisha Control method for multi-stage hydraulic machine
US4514138A (en) * 1982-02-26 1985-04-30 Tokyo Shibaura Denki Kabushiki Kaisha Leakage water discharge method and apparatus in a reversible hydraulic machine
US4948336A (en) * 1987-12-10 1990-08-14 Sundstrand Corporation Mechanical shaft seal
US4964783A (en) * 1988-04-20 1990-10-23 Hanning Electro-Werke Gmbh & Co. Device for emptying a liquid-collection tank in a water-conducting household appliance
US4898512A (en) * 1989-03-27 1990-02-06 Geffs John J Apparatus and method for reducing effects of draft tube pressure fluctuations
US5941682A (en) * 1997-07-24 1999-08-24 Voith Hydro, Inc. Draft tube peripheral plenum
US7094016B1 (en) * 1999-07-21 2006-08-22 Unitec Institute Of Technology Multi-phase flow pumping means and related methods
US20140105747A1 (en) * 2008-05-27 2014-04-17 Weir Minerals Australia, Ltd. Centrifugal pump impellers
US8608445B2 (en) * 2008-05-27 2013-12-17 Weir Minerals Australia, Ltd. Centrifugal pump impellers
US20110158795A1 (en) * 2008-05-27 2011-06-30 Kevin Edward Burgess Centrifugal pump impellers
US9004869B2 (en) * 2008-05-27 2015-04-14 Weir Minerals Australia, Ltd. Centrifugal pump impellers
US9422938B2 (en) 2008-05-27 2016-08-23 Weir Minerals Australia Ltd. Relating to centrifugal pump impellers
CN103228908A (zh) * 2010-11-02 2013-07-31 沃依特专利有限责任公司 用于水力发电站的混流式泵
JP2013543074A (ja) * 2010-11-02 2013-11-28 フォイト パテント ゲーエムベーハー 水力発電所用のフランシス構造のポンプ
US11378084B2 (en) * 2013-09-12 2022-07-05 Ebara Corporation Apparatus and method for alleviating and preventing cavitation surge of water supply conduit system
DE102013019652A1 (de) * 2013-09-30 2015-04-02 Dieter Mühlenbruch Wasserkraftwerk
CN109092580A (zh) * 2018-10-15 2018-12-28 厦门英仕卫浴有限公司 一种高效节能的出水组件

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Publication number Publication date
DE1528821A1 (de) 1969-10-16
GB1006365A (en) 1965-09-29
ES292503A1 (es) 1964-01-16
CH405939A (de) 1966-01-15
AT243621B (de) 1965-11-25

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