US3841786A - Method and cooling system for cooling centrifugal pumps - Google Patents

Method and cooling system for cooling centrifugal pumps Download PDF

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Publication number
US3841786A
US3841786A US00157438A US15743871A US3841786A US 3841786 A US3841786 A US 3841786A US 00157438 A US00157438 A US 00157438A US 15743871 A US15743871 A US 15743871A US 3841786 A US3841786 A US 3841786A
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United States
Prior art keywords
blade
pump
zone
cooling
casing
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Expired - Lifetime
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US00157438A
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English (en)
Inventor
D Florjancic
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Sulzer AG
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Sulzer AG
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Classifications

    • G—PHYSICS
    • G21—NUCLEAR PHYSICS; NUCLEAR ENGINEERING
    • G21C—NUCLEAR REACTORS
    • G21C15/00—Cooling arrangements within the pressure vessel containing the core; Selection of specific coolants
    • G21C15/24—Promoting flow of the coolant
    • G21C15/243—Promoting flow of the coolant for liquids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D3/00—Axial-flow pumps
    • F04D3/005—Axial-flow pumps with a conventional single stage rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D9/00—Priming; Preventing vapour lock
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
    • F22D11/00—Feed-water supply not provided for in other main groups
    • F22D11/02—Arrangements of feed-water pumps
    • 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
    • Y02E30/00—Energy generation of nuclear origin
    • Y02E30/30—Nuclear fission reactors

Definitions

  • This invention relates to centrifugal pumps and more particularly to a method of improving the suction performance of centrifugal pumps.
  • the invention provides a method and a cooling system by which a pump zone ofa centrifugal pump exposed to the risk of vapor bubbles is cooled.
  • the method of the invention resides in the improvement of the suction performance of a centrifugal pump by cooling the pump zone at an impeller blade in which there is a risk of vapor bubble formation.
  • the method cools the surfaces of the impeller blades exposed to the risk by passing a cooling medium through the interior of the blade.
  • the cooling medium can either be discharged out of the blades for recirculation or can be discharged into the pump zone to flow over the external surfaces of the blades.
  • the cooling medium can be injected into the pump zone from the exterior of the pump casing to admix with the heated medium being conveyed through the zone so as to cool the conveyed medium.
  • the medium being conveyed can be used for cooling purposes. For example, a portion of the medium can be extracted from the medium flow upstream of the pumpv and then injected into the flow in the pump zone while at a lower temperature.
  • the cooling system in one embodiment, utilizes cooling elements such as a plurality of ducts which pass through the impeller blades and carry a cooling medium supplied from any suitable means. These ducts can be connected with return means for recirculation of the cooling medium or can be connected to discharge ducts in the blades for discharging the cooling medium in the pump zone over the external blade surfaces.
  • the cooling elements can be in the form of passages which pass through the pump casing to inject the cooling medium into the pump zone from outsidethe pump.
  • the cooling elements can be connected in parallel by-pass relation with the ducts for directing a medium to be conveyed through the pump. These elements then direct a portion of the conveyed medium through a separate path wherein this portion is maintained at a cooler'tempera'ture than the remainder of the flow and inject the cooled portion back into the flow in the pump zone.
  • FIG. 1 illustrates a cross-sectionalview of an axial flow pump with a duct cooling system for the blades according to the invention
  • FIG. 2 illustrates a cross-sectional view of a radialflow pump with film cooling according to the invention
  • FIG. 3 illustrates a cross-sectional view of a pump with provision for cooling the fluid which flows through the hazardous zone according to the invention
  • FIG. 4 illustrates another embodiment of a pump according to FIG. 3 modified in accordance with the invention
  • FIG. 5 illustrates a partial section of a leading blade edge of a blade with film cooling according to the invention
  • FIG. 6 illustrates a partial section, corresponding to FIG. 5 and relating to a blade with duct cooling according to the invention
  • FIG. 7 illustrates a section of a leading blade edge in which the fluid required for forming the film flows outwardly through porous material from the interior of the blade according to the invention.
  • FIG. 8 diagrammatically illustrates the circuit of a boiler feed pump constructed in accordance with the invention.
  • centrifugal pumps refers to all pumps having blades over which delivered fluid flows, for example, axial-flow pumps, radial-flow pumps and diagonal pumps.
  • axial-flow pumps for example, axial-flow pumps, radial-flow pumps and diagonal pumps.
  • an axial-flow pump which may,
  • function as the circulating pump for a boiling-water reactor is provided with a tubular casing l defining a central inlet for flow of a fluid therethrough, a suction branch 2 adjoining the casing and a bearing 3 in which a drive shaft 4 is journalled.
  • a boss 5 of an impeller having blades 6 extending therefrom is mounted on the end of the drive shaft 4 within the suction branch 2.
  • a cooling system is pro- I vided.
  • This system has cooling ducts 7 formed in the connection may be obtained, for example, in the illustrated manner, by circumferential grooves 12.
  • the ports 10, 11, in turn, communicate with longitudinal bores 13, 14 in the shaft 4 which are connected, in a manner not shown, to ducts for the supply and discharge of a coolant, for example a cooling fluid.
  • the ducts 7 on the leading edge or forward flow impinging edge of the blade 6, against which the flow impinges, can alternatively be constructed by being milled into the surface of the blade 6.
  • the ducts 7 are covered with metallic closure strips 15, afiixed by soldering.
  • a coolant for example water
  • the coolant flows from the bore 13 through the port 11 and the port 9 into the ducts 7 and is discharged from the ports 8, 10 and the bore 14.
  • the coolant thus serves to cool the blade 6 via a heat exchange along and adjacent the path of the ducts 7.
  • a radial-flow pump for example, the feed pump of a boiler installation, has a pump casing with a suction branch 21, a casing cover 22 with a shaft seal 23, integral casing parts 24, 25, 26 with the first casing part 24 defining a central inlet and a shaft 27 with radial flow impellers 28 and 29.
  • the impellers of further stages may adjoin the impeller 29 but would not normally require any cooling.
  • each impeller 28, 29 carries a plurality of blades as is known.
  • the cooling system for this pump cooperates with the shaft seal 23 in that the shaft seal 23 is formed of two parts which define a chamber 30 therebetween.
  • This chamber 30 connects to a supply line 31 for coolant.
  • the chamber 30 also communicates through bores 32, formed in a shroud bush 33 of the shaft 27, with a circumferential groove 34 of the shaft 27.
  • Radial bores 35 extend from the groove 34 into an axial bore 36 of the shaft 27
  • the axial bore 36 communicates through a radial bore 37 with a circumferential groove 38 in the first impeller 28.
  • the flow-receiving leading blade edges of the impeller 28 are provided with bores 39 which ad join on the circumferential groove 38.
  • bores or ducts 40 extend outwardly from each bore 39 to the tip edge of the impeller 28. This is more clearly shown in FIG. 5 wherein a section through a leading blade edge is taken to disclose the construction of the bores 39 and 40. This illustration also shows further bores 41 which extend rearwardly into the zone which is hazarded by the formation of vapor bubbles.
  • the coolant is preferably the same fluid as the pump fluid but at a lower temperature.
  • the coolant supplied through the duct 31 and the bores 35, 36, 37 to the bore 39 to be feed water at a temperature lower than that delivered by the pump.
  • the coolant is intermixed with the delivered fluid by emerging outwardly through the bores 40 and 41 from the blade and flowing in the form of a fluid film, indicated by arrows in FIG. 5, along the surface of the blade before being intermixed with the pumped fluid.
  • the zone, hazarded by the formation of gas bubbles may also be cooled.
  • film cooling can also be obtained by means of the coolant.
  • the coolant forming the coolant film can flow through the pores of a sintered material of which the leading edge of the blade 6 is constructed.
  • the sintered material may form a strip which extends along at least part of the leading edge of the blade 6 and is provided with a bore 39, corresponding to the above described bore 39, for supplying the coolant.
  • the external circumferential zones of the flow can be supplied from stationary sources to achieve the cooling effect.
  • the zones in which there is a risk of vapor bubble formation are disposed mainly on the external circumference of the inlet cross section of the impeller.
  • FIG. 3 shows a vapor bubble G of this kind.
  • the pump has a casing 50 and an impeller 51 as well as a labyrinth seal 53 and a restrictor ring 54 on that side of the impeller 51 which is nearest to the inlet socket 52.
  • the coolant in this case also preferably the same liquid which is being conveyed but having a lower temperature, flows from' the chamber 55 past the restrictor ring 54 and is then entrained by the flow delivered by the pump. Under these conditions the coolant will move in a film along the outer wall of the duct of the impeller 51 to cool the zone in which there is a risk of a vapor bubble G being formed.
  • the pump shown in FIG. 4 differs from the pump illustrated in FIG. 3 solely by the fact that the coolant is supplied through circumferentially disposed ducts 60 which are formed in a suction branch 61 of the pump. In this case, there is no need to provide two seals or one seal and one restrictor position at the front of the impeller 51 of the pump. In use, the coolant supplied by the system to the pump cools the outer zone of the suction eye of the impeller 51, which correponds to the .hazard zone G in FIG. 3.
  • the circuit of a feed pump which is, for example, constructed as illustrated in FIG. 2, and is disposed in a boiler plant connects with a cooling system so that cooling medium is supplied to the pump impeller of the first stage.
  • the feed pump 100 is provided with feed water from a feed water tank 101 to which the feed water is supplied by a condensate pump 102.
  • a low-pressure preheater 103 is disposed between the condensate pump 102 and the feed water tank 101 in order to preheat the condensate as is known.
  • the feed pump 100 delivers feed water through a high-pressure preheater 104 into a steam boiler 105 in which the water is evaporated and super-heated.
  • the steam passes from the steam boiler into a turbine 106, is expanded and then finally passes into a condenser 107.
  • the condensate formed in the condenser 107 is returned by the condensate pump 102 into the feed water tank 101.
  • the cooling system utilizes a duct 109 which branches from a condensate duct 108 connecting the condensate pump 102 to the feed water tank 101 upstream of the low pressure preheater 103. Accordingly, the duct 109 conveys cool condensate which may be used for cooling the first stage of the feed pump in the manner described by reference to FIG. 2. If blade cooling is to be provided in accordance with FIGS. 1 or 6 respectively, a duct 110 may be employed for returning the heated coolant. This duct 110 would then extend into the condensate duct 108 upstream of the condensate pump 102 as shown in dash-dot lines.
  • At least one radial flow impeller mounted on said drive shaft, said impeller having at least one blade extending radially of said shaft and transversely of the fluid flow, said blade having a forward flow impinging edge and surfaces within a pump zone adjacent said blade in which vapor bubbles formation can raise, said edge extending at an angle to said axis of rotation;
  • a cooling system for cooling said zone said system including at least one bore extending through said blade, a plurality of discharge ducts disposed in said blade in communication with said bore and extending to the surface of said forward flow impinging edge, and means for supplying coolant to said bore and said ducts to discharge the coolant out of said blade over said blade surface in a fluid film into said zone.
  • impeller mounted on said drive shaft, said impeller having at least one radial pumping blade extending therefrom within a pump zone adjacent said blade in which vapor bubble formation can arise, said blade having a forward flow inclined leading impinging edge and surfaces adjacent said pump zone;
  • a cooling system for cooling said zone, said system including a plurality of ducts disposed in said blade at said forward flow inclined leading impinging edge, means connected to at least one of said bores in said shaft for supplying a coolant to said ducts to cool said blade surfaces in said zone, and means connected to said ducts for receiving the coolant from said blade and for discharging the received coolant into at least one other of said bores of said shaft.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Plasma & Fusion (AREA)
  • High Energy & Nuclear Physics (AREA)
  • Water Supply & Treatment (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US00157438A 1970-07-01 1971-06-28 Method and cooling system for cooling centrifugal pumps Expired - Lifetime US3841786A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH996070A CH526048A (de) 1970-07-01 1970-07-01 Verfahren zur Verbesserung der Saugfähigkeit von Kreiselpumpen sowie Pumpe zur Ausführung des Verfahrens

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US00157438A Expired - Lifetime US3841786A (en) 1970-07-01 1971-06-28 Method and cooling system for cooling centrifugal pumps

Country Status (10)

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US (1) US3841786A (OSRAM)
AT (1) AT305776B (OSRAM)
BE (1) BE769076A (OSRAM)
CA (1) CA948922A (OSRAM)
CH (1) CH526048A (OSRAM)
DE (1) DE2033711A1 (OSRAM)
FR (1) FR2097998A5 (OSRAM)
GB (1) GB1332251A (OSRAM)
NL (1) NL143657B (OSRAM)
SE (1) SE371868B (OSRAM)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4260336A (en) * 1978-12-21 1981-04-07 United Technologies Corporation Coolant flow control apparatus for rotating heat exchangers with supercritical fluids
US4416581A (en) * 1982-02-16 1983-11-22 Elliott Turbomachinery Co., Inc. Method and apparatus for cooling an expander
US4478553A (en) * 1982-03-29 1984-10-23 Mechanical Technology Incorporated Isothermal compression
EP0257140A1 (en) * 1985-08-01 1988-03-02 Westinghouse Electric Corporation Nuclear reactor coolant pump impeller/shaft assembly
DE3802763A1 (de) * 1988-01-30 1989-08-10 Kloeckner Humboldt Deutz Ag Radialturbine
US5957657A (en) * 1996-02-26 1999-09-28 Mitisubishi Heavy Industries, Ltd. Method of forming a cooling air passage in a gas turbine stationary blade shroud
US6179554B1 (en) * 1999-10-29 2001-01-30 Elvin A. Stafford Low friction fluid bearing and turbine using same
US6564874B2 (en) * 2001-07-11 2003-05-20 Schlumberger Technology Corporation Technique for facilitating the pumping of fluids by lowering fluid viscosity
CN103939381A (zh) * 2013-12-31 2014-07-23 江苏大学 一种核主泵泵体的设计方法
CN109854515A (zh) * 2018-12-27 2019-06-07 枞阳县中邦科技信息咨询有限公司 一种耐高温的工程塑料泵

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3523495A1 (de) * 1985-07-01 1987-01-08 Sihi Gmbh & Co Kg Pumpenanlage zur foerderung von leicht siedenden medien im saugbetrieb
GB2239491B (en) * 1989-11-28 1993-09-29 Copermill Ltd Hot gas blower
GB2422003A (en) * 2005-01-06 2006-07-12 Ford Global Tech Llc Combined fan and heat exchanger
CN104613001B (zh) * 2015-01-07 2017-02-22 江苏大学 一种可通过鱼类的生态友好型轴流泵结构
CN112648235B (zh) * 2021-01-19 2024-05-07 大连海事大学 一种带有鼓包和凹缝结构的跨声速压气机转子叶片
CN113027780A (zh) * 2021-04-21 2021-06-25 黄飞 一种静音潜水管道泵

Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE475711C (de) * 1928-05-13 1929-05-02 Aeg Kreiselpumpe fuer Abwasserfoerderung mit unter Druck eingefuehrtem Spuelmittel
GB319020A (OSRAM) * 1928-09-14 1930-02-27 International General Electric Company Incorporated
US2018144A (en) * 1933-04-29 1935-10-22 Linde Air Prod Co Method and apparatus for transferring gas material
US2149510A (en) * 1934-01-29 1939-03-07 Cem Comp Electro Mec Method and means for preventing deterioration of turbo-machines
US2292617A (en) * 1940-06-15 1942-08-11 Linde Air Prod Co Apparatus for pumping volatile liquids
US2576814A (en) * 1946-05-28 1951-11-27 Edward A Stalker Cooling means for turbines
GB673393A (en) * 1950-02-14 1952-06-04 Burmeister & Wains Mot Mask Improvements in or relating to gas turbine rotors
DE920234C (de) * 1952-11-06 1954-11-15 Kuehnle Ag Verfahren und Vorrichtung zum Schutz der stroemungsfuehrenden Wandungen rotierender Teile gegen Verschleiss durch feste Teile
US2720356A (en) * 1952-06-12 1955-10-11 John R Erwin Continuous boundary layer control in compressors
CH350836A (de) * 1957-05-22 1960-12-15 Oerlikon Maschf Verfahren zur Kühlung eines Gasturbinenrotors
US2988325A (en) * 1957-07-18 1961-06-13 Rolls Royce Rotary fluid machine with means supplying fluid to rotor blade passages
US2990779A (en) * 1956-12-27 1961-07-04 Obermaier & Cie High speed propeller pump
US3237564A (en) * 1962-10-15 1966-03-01 English Electric Co Ltd Hydraulic pumps and reversible pump turbines
US3240468A (en) * 1964-12-28 1966-03-15 Curtiss Wright Corp Transpiration cooled blades for turbines, compressors, and the like
US3600890A (en) * 1968-11-29 1971-08-24 United Aircraft Corp Turbine cooling construction
US3623825A (en) * 1969-11-13 1971-11-30 Avco Corp Liquid-metal-filled rotor blade

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE475711C (de) * 1928-05-13 1929-05-02 Aeg Kreiselpumpe fuer Abwasserfoerderung mit unter Druck eingefuehrtem Spuelmittel
GB319020A (OSRAM) * 1928-09-14 1930-02-27 International General Electric Company Incorporated
US2018144A (en) * 1933-04-29 1935-10-22 Linde Air Prod Co Method and apparatus for transferring gas material
US2149510A (en) * 1934-01-29 1939-03-07 Cem Comp Electro Mec Method and means for preventing deterioration of turbo-machines
US2292617A (en) * 1940-06-15 1942-08-11 Linde Air Prod Co Apparatus for pumping volatile liquids
US2576814A (en) * 1946-05-28 1951-11-27 Edward A Stalker Cooling means for turbines
GB673393A (en) * 1950-02-14 1952-06-04 Burmeister & Wains Mot Mask Improvements in or relating to gas turbine rotors
US2720356A (en) * 1952-06-12 1955-10-11 John R Erwin Continuous boundary layer control in compressors
DE920234C (de) * 1952-11-06 1954-11-15 Kuehnle Ag Verfahren und Vorrichtung zum Schutz der stroemungsfuehrenden Wandungen rotierender Teile gegen Verschleiss durch feste Teile
US2990779A (en) * 1956-12-27 1961-07-04 Obermaier & Cie High speed propeller pump
CH350836A (de) * 1957-05-22 1960-12-15 Oerlikon Maschf Verfahren zur Kühlung eines Gasturbinenrotors
US2988325A (en) * 1957-07-18 1961-06-13 Rolls Royce Rotary fluid machine with means supplying fluid to rotor blade passages
US3237564A (en) * 1962-10-15 1966-03-01 English Electric Co Ltd Hydraulic pumps and reversible pump turbines
US3240468A (en) * 1964-12-28 1966-03-15 Curtiss Wright Corp Transpiration cooled blades for turbines, compressors, and the like
US3600890A (en) * 1968-11-29 1971-08-24 United Aircraft Corp Turbine cooling construction
US3623825A (en) * 1969-11-13 1971-11-30 Avco Corp Liquid-metal-filled rotor blade

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* Cited by examiner, † Cited by third party
Title
Flight; Mar. 16, 1956; Vol. 69, No. 2460; p. 293 294. *
The Gas Turbine; R. Hodge et al.; A Review of Blade Cooling Systems; Feb. 1958; p. 396 398. *

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4260336A (en) * 1978-12-21 1981-04-07 United Technologies Corporation Coolant flow control apparatus for rotating heat exchangers with supercritical fluids
US4416581A (en) * 1982-02-16 1983-11-22 Elliott Turbomachinery Co., Inc. Method and apparatus for cooling an expander
US4478553A (en) * 1982-03-29 1984-10-23 Mechanical Technology Incorporated Isothermal compression
EP0257140A1 (en) * 1985-08-01 1988-03-02 Westinghouse Electric Corporation Nuclear reactor coolant pump impeller/shaft assembly
DE3802763A1 (de) * 1988-01-30 1989-08-10 Kloeckner Humboldt Deutz Ag Radialturbine
US5957657A (en) * 1996-02-26 1999-09-28 Mitisubishi Heavy Industries, Ltd. Method of forming a cooling air passage in a gas turbine stationary blade shroud
US6179554B1 (en) * 1999-10-29 2001-01-30 Elvin A. Stafford Low friction fluid bearing and turbine using same
US6564874B2 (en) * 2001-07-11 2003-05-20 Schlumberger Technology Corporation Technique for facilitating the pumping of fluids by lowering fluid viscosity
CN103939381A (zh) * 2013-12-31 2014-07-23 江苏大学 一种核主泵泵体的设计方法
CN103939381B (zh) * 2013-12-31 2018-08-10 江苏大学 一种核主泵泵体的设计方法
CN109854515A (zh) * 2018-12-27 2019-06-07 枞阳县中邦科技信息咨询有限公司 一种耐高温的工程塑料泵

Also Published As

Publication number Publication date
NL143657B (nl) 1974-10-15
BE769076A (fr) 1971-12-27
DE2033711A1 (de) 1972-01-13
AT305776B (de) 1973-03-12
CA948922A (en) 1974-06-11
SE371868B (OSRAM) 1974-12-02
FR2097998A5 (OSRAM) 1972-03-03
NL7011154A (OSRAM) 1972-01-04
GB1332251A (en) 1973-10-03
CH526048A (de) 1972-07-31

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