US3784318A - Variable diffuser centrifugal pump - Google Patents

Variable diffuser centrifugal pump Download PDF

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Publication number
US3784318A
US3784318A US00213417A US3784318DA US3784318A US 3784318 A US3784318 A US 3784318A US 00213417 A US00213417 A US 00213417A US 3784318D A US3784318D A US 3784318DA US 3784318 A US3784318 A US 3784318A
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United States
Prior art keywords
diffuser
centrifugal pump
pump
slots
passages
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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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US00213417A
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English (en)
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D Davis
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General Electric Co
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General Electric Co
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027—Varying behaviour or the very pump
    • F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/466—Fluid-guiding means, e.g. diffusers adjustable especially adapted for liquid fluid pumps
    • F04D29/468—Fluid-guiding means, e.g. diffusers adjustable especially adapted for liquid fluid pumps adjusting flow cross-section, otherwise than by using adjustable stator blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/60—Control system actuates means
    • F05D2270/64—Hydraulic actuators

Definitions

  • ABSTRACT A centrifugal pump is supplied with a discharge shutter valve which provides a variable diffuser for the pump.
  • the shutter valve includes a hollow, slotted cylinder positioned for movement into a variety of operative positions between the impeller and the diffuser vane passages. Each operative position completely closes one or more of the diffuser passages while leaving the remaining passages completely open, thereby providing a pump with high head rise over the complete operating range of the pump.
  • Centrifugal pumps while capable of providing the high output requirements of gas turbine engine and variable thrust liquid rocket engine systems, have historically been limited to relatively narrow flow ranges because of the excessive temperature rise and stability problems associated therewith at low percentages of rated flow.
  • Previous attempts at providing a centrifugal pump with a relatively wide flow range have met with various degrees of success.
  • variable speed drive centrifugal pumps can achieve the necessary high flow turndowns but the reduced speed results in substantial head dropoff from the pump.
  • Pump inlet throttling such as by using the inlet vapor core approach, or pump discharge throttling with a diffuser inlet shutter can each be utilized to provide the reduced temperature rise at low flow.
  • Each of these approaches also results in significant head rise dropoff at high flow turndown ratios.
  • One further proposed approach consists of providing a pump with a variable angle diffuser vane, which can successfully provide the low temperature rise without significantly causing head rise dropoff.
  • the complexity of such a pump however, in most cases far outweighs the advantages gained therefrom.
  • the slotted valve takes the form of a slotted cylindrical sleeve radially located between the pump impeller tip and the pump diffuser entry passages. Means are provided for moving the valve axially as a function of pumpdelivered flow in such a manner that selective diffuser vane entry passages are completely closed off while the desired flow is delivered through the remaining fully open diffuser vane entry passages. The net effect of the slotted valve is to increase overall efficiency at low delivered flows while maintaining near rated head rise of the pump throughout its range of operation.
  • FIG. 1 is a generally sectional view, with portions deleted, describing a centrifugal pump constructed in accordance with the prior art
  • FIG. 2 is an enlarged partial sectional view of a centrifugal pump, similar to FIG. 1, describing a pump constructed in accordance with the present invention
  • FIG. 3 is a sectional view, with portions deleted, showing the cross section of the pump of FIG. 2 with the slotted valve in one of its operative positions;
  • FIG. 4 is a perspective view of the slotted valve of FIGS. 2 and 3;
  • FIG. 5 is a graphical plot showing the outputs of the pumps illustrated in FIGS. 1 and 2.
  • FIG. 1 wherein a centrifugal pump constructed in accordance with the prior art is designated generally by the numeral 10.
  • the pump 10 is shown to include an axial inlet 12,. a rotating impeller wheel 14 which includes a plurality of impeller vanes 16, and a casing 18 which defines a radial outlet 20 sur-. rounding the tips of the impeller vanes 16.
  • a diffuser 22 surrounds the radial outlet 20 and includes a plurality of stationary diffuser vanes 24 at its inlet.
  • Each pair of the diffuser vanes 24 defines a diffuser entry passage 26 from the radial outlet of the pump 10 to a toroidalshaped collector 27.
  • the impeller wheel 14 extends from a rotatable shaft 28, which is journaled for rotation in bearings 30.
  • centrifugal pump 10 As previously mentioned, the elements described above are typical of prior art centrifugal pumps. For this reason, the structure of the centrifugal pump 10 is shown somewhat schematically in FIG. 1. As will become apparent from the following description, Applicants inventive concept may be applied to any type centrifugal pump and the structure shown in FIG. 1 is merely meant to be illustrativeand not limiting in any manner.
  • Centrifugal pumps such as that shown in FIG. 1, have been limited to relatively narrow flow ranges because of the excessive temperature rise and stability problems at low percentages of rated flow. These problems may be substantially reduced or eliminated by reducing low flow power loss. For this reason it is known to provide the centrifugal pump with a diffuser inlet shutter 32 which throttles the pump discharge by partially closing all of the diffuser entry passages 26.
  • the diffuser inlet shutter 32 takes the shape of a hollow cylinder positioned between the radial outlet of the pump 10 and the diffuser vanes 24 as shown in FIG. 1.
  • the cylinder 34 is provided with some actuating mechanism, such as a piston 36 formed integrally with one end of the cylinder 34.
  • the piston 36 is positioned within a chamber 38 which is supplied with actuating fluid by means of ports 40 and 42, respectively.
  • fluid is supplied to the centrifugal pump 10 at the inlet 12 in any known manner, while the shaft 28 and impeller wheel 14 are driven by some suitable driving mechanism (not shown).
  • the fluid is acted upon by the impeller vanes 16 and is delivered through the radial outlet 20 at a much higher pressure and velocity than its inlet pressure and velocity.
  • the fluid then passes through the diffuser entry passages 26 of the diffuser 22, where its velocity pressure is converted to static pressure. From the diffuser 22 the fluid is directed into collector 27.
  • the fluid may then be directed to a suitable control device (not shown) or to some other component, depending upon the use of the pump 10.
  • the centrifugal pump 10 Being a fluid dynamic device dependent upon fluid velocity and velocity vectors for adequate flow, pressure and pressure stability, the centrifugal pump 10 can only be designed to produce optimum effiency at a single value of output flow. This optimum or best efficiency point is usually obtained at or near the maximum flow point in order to satisfy the required pressure rise with minimum impeller size. This necessity of sizing the pump for high flow results in poor efficiency at low flows since the pump is grossly oversized in terms of fluid volume during low flows. In addition, the blade and diffuser shapes are mismatched for low flow operation. At these low flows, excessive power loss to the fuel can result in large fuel temperature rise, and numerous forms of pump and pump/system related pressure instabilities can occur.
  • FIGS. 2 through 4 Applicants inventive concept for diminishing the fluid temperature rise while maintaining near rated head rise throughout the range of operation ofa pump 10 will be described.
  • the basic construction of the pump 10' remains unchanged from that previously described. That is, the pump 10 still includes an inlet l2,'an impeller wheel 14, a diffuser 22, a plurality of diffuser vanes 24 which define diffuser inlet passages 26, and a collector 27.
  • the primary difference between the pump 10 described in connection with FIG. 1 and the improved pump 10', shown in FIGS. 2 through 4 lies in the fact that the diffuser inlet shutter 32 of the pump 10 is replaced with a variable diffuser valve 50.
  • variable diffuser valve 50 consists of a cylinder 52 having a plurality of various length slots 54, 56 and 58, located therein.
  • the cylinder 52 is further shown to include a piston member 60, similar to the piston 36 of FIG. 1, which may be formed integrally with the cylinder 52 or joined thereto in any known manner.
  • Each of the slots 54 58 begins in the end of the cylinder 52 opposite the piston 60 and extends axially toward the piston 60.
  • the slots 54 58 are of approximately equal width but are of varying axial lengths, with the slots 54 being the shortest and the slots 58 the longest, as shown in FIG. 4.
  • the slots 54 58 are spaced around the periphery of the cylinder 52 and positioned in such a manner that each of the slots lies between one of the diffuser inlet passages 26 and the tips of the impeller vanes 16. This arrangement is shown in the perspective view of FIG. 4 wherein the eight slots are positioned as if there were twelve equally spaced slots, i.e. the centerlines of the slots lie 30 apart. Since there are twelve diffuser passages 26 and only eight of the slots 54 58, there are four solid portions of the cylinder 52, generally designated by the numeral 59, which block four of the diffuser passages 26 as soon as the valve 50 is moved into a first operative position within the radial outlet 20.
  • the cylinder 52 is shown to include a total of eight slots of three various lengths, the total number of slots and the sizing thereof will, of course, depend upon the number of diffuser passages and the design of the centrifugal pump, as will become apparent from the following description of the operation of the variable diffuser centrifugal pump 10'.
  • the basic operation of the pump 10 is identical to that of the pump 10 with fluid being delivered through an inlet 12 to the impeller wheel 14 and being directed radially outwardly while being acted upon by the impeller vanes 16.
  • the fluid is then delivered through the radial outlet 20 to the diffuser entry passages 26, where its velocity pressure is converted to static pressure, and then it passes into the collector 27.
  • variable diffuser valve 50 When the pump 10' is operating near its rated maximum output, the variable diffuser valve 50 is held in an inoperative position such that all diffuser entry passages 26 are fully open to receive fluid from the radial outlet 20 and to deliver the same to the collector 27. As the desired output flow of the pump is decreased, the valve 50 is moved axially into a first operative position between the tips of the impeller vanes 14 and the diffuser vanes 24. The diffuser valve 50 is stopped in this first position in which each of the slots 54, 56 and 58 lies between the tips of the impeller vanes 14 and one of the diffuser inlet passages 26.
  • the diffuser valve 50 is moved further to the left (as shown in FIG. 2) to a second position in which the slots 54 are no longer positioned between the impeller tips and the diffuser vanes 24. That is, the diffuser valve 50 is moved to a second operative position in which that portion of the cylinder 52 which includes the slots 54 lies within a groove 62 (FIG. 2) formed in the casing 18. In this position, only the slots 56 and 58 are positioned between the impeller wheel 14 and the diffuser vanes 24, and thus only four of the diffuser vane passages 26 are fully open while the remaining eight are fully closed.
  • FIG. 3 is a sectional view of the pump with the diffuser valve 50 located in this second position. As clearly shown in this view, the slots 56 and 58 deliver fluid from the impeller vanes 16 to four of the diffuser vane passages 26, while the remaining eight passages are completely blocked.
  • the diffuser valve 50 is moved axially to a third operative position in which only the slots 58 lie between the impeller wheel 14 and the diffuser vanes 24. In this position, only two of the diffuser vane passages 26 receive fluid from the impeller wheel 14, while the remaining ten passages are completely blocked.
  • the output of a pump constructed as shown in FIGS. 2 through 4 is plotted as solid lines in FIG. 5.
  • the net effect of the variable diffuser is to increase overall efficiency at low delivered flows while maintaining near rated head rise. That is, the shaft power curves for the fully open and three alternative positions of the diffuser valve 50 are identical to those for the centrifugal pump 10.
  • the headrise curves show that the percent of rated head rise actually increases as the number of open diffuser inlet passages 26 decreases, as opposed to the dotted head rise curves which show significant decreases in head rise for the pump, 10 of FIG. 1 at low rated flow levels.
  • the increase in head rise is caused by the increasing pressure as the number of diffuser inlet passages is decreased.
  • centrifugal pump which has a number of basic advantages.
  • the primary advantage of this pump is the high head rise over the full operating range of the pump. This phenomenon, when combined with the further advantage of low fluid temperature rise due to low power loss at low flow rates, provides a centrifugal pump capable of usage in many areas heretofore thought impossible. Other advantages become readily apparent when one compares the simplicity of the described design with the complexity of previously known variable diffuser geometry-type pumps. Furthermore, the pump described above provides the potential of maintaining stable pump operation at lower delivered flow rates than pump 10.
  • the means for causing axial movement of the diffuser valve 50 could take many forms other than the piston 60 described above.
  • the diffuser valve 50 could be positioned mechanically by some linkage arrangement.
  • the shape and number of the slots within the cylinder 52 could vary substantially from those shown while still providing the basic function of completely closing a certain number of inlet diffuser passages while leaving the remaining passages completely open.
  • a centrifugal pump of the type including an impeller adapted to propel fluid through a radial outlet to a diffuser which includes a plurality of stationary diffuser vanes defining diffuser passages therebetween, the improvement comprising:
  • a discharge shutter valve positioned between said impeller and said diffuser vanes and capable of movement between an inoperative position and at least one operative position, said valve including meand for completely closing the inlets to individual diffuser passages when in an operative position while leaving the inlets to the remaining passages completely open.
  • valve comprises a hollow cylinder.
  • each of said slots is positioned opposite the inlet of one of said diffuser passages.
  • valve includes actuating means for moving said cylinder between its operative and inoperative positions. i l I 7.
  • actuating means includes a piston extend ing from one end of said cylinder, a chamber for receiving said piston, and means for delivering servo fluid to opposite sides of said piston.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Medicinal Preparation (AREA)
US00213417A 1971-12-29 1971-12-29 Variable diffuser centrifugal pump Expired - Lifetime US3784318A (en)

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US21341771A 1971-12-29 1971-12-29

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US (1) US3784318A (de)
JP (1) JPS5542277B2 (de)
BE (1) BE793550A (de)
CA (1) CA962894A (de)
CH (1) CH547956A (de)
DE (1) DE2262883C2 (de)
FR (1) FR2167163A5 (de)
GB (1) GB1412150A (de)
IL (1) IL40881A (de)
IT (1) IT973131B (de)
NL (1) NL7217857A (de)
SE (1) SE388251B (de)

Cited By (45)

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US4094613A (en) * 1976-05-07 1978-06-13 Sundstrand Corporation Variable output centrifugal pump
US4135850A (en) * 1975-09-16 1979-01-23 Mark Hot Inc. Ventilator system with adjustable damper fan
US4378194A (en) * 1980-10-02 1983-03-29 Carrier Corporation Centrifugal compressor
EP0081255A1 (de) * 1981-12-09 1983-06-15 BBC Brown Boveri AG Regulierbarer Abgasturbolader
DE3246623A1 (de) * 1982-04-21 1983-10-27 Gen Electric Verfahren und vorrichtung zum zersetzen von antivernebelungs-treibstoff
US4460310A (en) * 1982-06-28 1984-07-17 Carrier Corporation Diffuser throttle ring control
US4749332A (en) * 1982-04-21 1988-06-07 General Electric Company Method and apparatus for degrading antimisting fuel
US4802817A (en) * 1987-12-23 1989-02-07 Sundstrand Corporation Centrifugal pump with self-regulating impeller discharge shutter
US4824325A (en) * 1988-02-08 1989-04-25 Dresser-Rand Company Diffuser having split tandem low solidity vanes
US4850795A (en) * 1988-02-08 1989-07-25 Dresser-Rand Company Diffuser having ribbed vanes followed by full vanes
US4877373A (en) * 1988-02-08 1989-10-31 Dresser-Rand Company Vaned diffuser with small straightening vanes
US4877369A (en) * 1988-02-08 1989-10-31 Dresser-Rand Company Vaned diffuser control
US4902200A (en) * 1988-04-25 1990-02-20 Dresser-Rand Company Variable diffuser wall with ribbed vanes
US4932835A (en) * 1989-04-04 1990-06-12 Dresser-Rand Company Variable vane height diffuser
US5082428A (en) * 1990-08-16 1992-01-21 Oklejas Robert A Centrifugal pump
US5807071A (en) * 1996-06-07 1998-09-15 Brasz; Joost J. Variable pipe diffuser for centrifugal compressor
US6220031B1 (en) * 1998-08-26 2001-04-24 Daimlerchrysler Ag Exhaust gas turbocharger for an internal-combustion engine and method of operating same
US6431823B1 (en) * 2000-07-13 2002-08-13 Yudko Slepoy Centrifugal pump with variable capacity and pressure
US6619072B2 (en) 2000-08-02 2003-09-16 Mitsubishi Heavy Industries, Ltd. Turbocompressor and refrigerating machine
FR2871200A1 (fr) * 2004-06-02 2005-12-09 Mark Iv Systemes Moteurs Sa Dispositif de pompe a debit variable
US20060177305A1 (en) * 2005-02-07 2006-08-10 Hoang Khanh C Centrifugal volute pump with discontinuous vane-island diffuser
US20090049834A1 (en) * 2007-08-21 2009-02-26 Emmanuel Bouvier Turbocharger with sliding piston assembly
WO2009143832A3 (de) * 2008-05-30 2010-01-21 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare kühlmittelpumpe
US20110188987A1 (en) * 2008-05-10 2011-08-04 Geraete-Und Pumpenbau Gmbh Dr. Eugen Schmidt Regulatable coolant pump and method for its regulation
WO2011042695A3 (en) * 2009-10-06 2011-11-03 Cummins Ltd Variable geometry turbine
US20120111002A1 (en) * 2010-03-18 2012-05-10 Toyota Jidosha Kabushiki Kaisha Centrifugal compressor and turbo supercharger
US20120204818A1 (en) * 2011-02-15 2012-08-16 Schwabische Huttenwerke Automotive Gmbh Coolant pump which exhibits an adjustable delivery volume
US20120230817A1 (en) * 2009-11-17 2012-09-13 Toyota Jidosha Kabushiki Kaisha Centrifugal compressor and turbocharger
EP1657446A3 (de) * 2004-11-12 2013-05-01 Geräte- und Pumpenbau GmbH, Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
CN103122859A (zh) * 2013-03-18 2013-05-29 北京萃宝重工科技有限公司 高效双室离心式渣浆泵
US20140086725A1 (en) * 2011-08-15 2014-03-27 Wuxi Kaidi Supercharger Accessories Co., Ltd. Turbocharger with a double-vane nozzle system
EP1992824A3 (de) * 2007-05-09 2014-05-14 Honeywell International Inc. Verdichter mit diskreter variabler Geometrie
US20140328667A1 (en) * 2012-11-09 2014-11-06 Susan J. NENSTIEL Variable geometry diffuser having extended travel and control method thereof
CN104564302A (zh) * 2015-01-29 2015-04-29 浙江吉利控股集团有限公司 汽车发动机
US20150275917A1 (en) * 2014-03-26 2015-10-01 Kabushiki Kaisha Toyota Jidoshokki Centrifugal Compressor
US9188133B1 (en) * 2015-01-09 2015-11-17 Borgwarner Inc. Turbocharger compressor active diffuser
WO2016057262A1 (en) * 2014-10-08 2016-04-14 Borgwarner Inc. Variable turbine geometry turbocharger with a fixed vane flow control device
US20160208808A1 (en) * 2013-08-26 2016-07-21 Gree Electric Appliances, Inc. Of Zhuhai Regulator assembly and centrifugal compressor
US20180149171A1 (en) * 2015-04-29 2018-05-31 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pump having a plurality of adjustable outlet openings
US20180320694A1 (en) * 2015-11-06 2018-11-08 Pierburg Gmbh Control arrangement for a mechanically controllable coolant pump of an internal combustion engine
EP3431768A1 (de) * 2017-07-17 2019-01-23 Airtex Products, S.A. Verstellbare kühlmittelpumpe
US10690148B2 (en) 2015-07-22 2020-06-23 Carrier Corporation Diffuser restriction ring
US11085355B2 (en) * 2018-08-03 2021-08-10 Hyundai Motor Company Coolant pump, cooling system provided with the same for vehicle and control method for the same
US11708841B2 (en) 2019-09-18 2023-07-25 Massachusetts Institute Of Technology Adaptive volutes for centrifugal pumps
US12018690B2 (en) * 2020-10-06 2024-06-25 Pierburg Pump Technology Gmbh Variable mechanical automotive coolant pump

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US4770605A (en) * 1981-02-16 1988-09-13 Mitsubishi Jukogyo Kabushiki Kaisha Diffuser device in a centrifugal compressor and method for manufacturing the same
CH677956A5 (de) * 1986-07-02 1991-07-15 Carrier Corp
DE19854747B4 (de) * 1998-11-27 2008-02-28 Pierburg Gmbh Elektrisch angetriebenes Radialgebläse
AT506107B1 (de) 2007-12-03 2009-11-15 Tcg Unitech Systemtechnik Gmbh Radialpumpe
AT508076B1 (de) 2009-03-24 2011-07-15 Tcg Unitech Systemtechnik Gmbh Radialpumpe
AT508413A1 (de) 2009-06-29 2011-01-15 Tcg Unitech Systemtechnik Gmbh Radialpumpe
DE102011079897A1 (de) * 2011-07-27 2013-01-31 Mahle International Gmbh Pumpe
DE102011018240A1 (de) 2011-04-19 2011-11-24 Tcg Unitech Systemtechnik Gmbh Radialpumpe mit einem in einem Gehäuse drehbar gelagerten Laufrad
DE102011079898A1 (de) * 2011-07-27 2013-01-31 Mahle International Gmbh Pumpe
DE102012212410A1 (de) * 2012-07-16 2014-01-30 Siemens Aktiengesellschaft Paralleldiffusor für eine Fluidmaschine
AT513770B1 (de) 2013-01-09 2016-06-15 Tcg Unitech Systemtechnik Gmbh Radialpumpe
JP6582538B2 (ja) * 2015-05-14 2019-10-02 アイシン精機株式会社 流体圧ポンプ

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CH133892A (de) * 1928-07-18 1929-06-30 Sulzer Ag Zentrifugalpumpe.
FR706107A (fr) * 1930-01-11 1931-06-19 Escher Wyss & Cie Const Mec Machine hydraulique réversible à génératrice ou motrice
DE736266C (de) * 1940-03-26 1943-06-10 Escher Wyss Maschinenfabrik G Kreiselpumpe mit regulierbaren Leitschaufeln
US3236500A (en) * 1961-12-09 1966-02-22 Geratebau Eberspacher Ohg Turbine

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CH133892A (de) * 1928-07-18 1929-06-30 Sulzer Ag Zentrifugalpumpe.
FR706107A (fr) * 1930-01-11 1931-06-19 Escher Wyss & Cie Const Mec Machine hydraulique réversible à génératrice ou motrice
DE736266C (de) * 1940-03-26 1943-06-10 Escher Wyss Maschinenfabrik G Kreiselpumpe mit regulierbaren Leitschaufeln
US3236500A (en) * 1961-12-09 1966-02-22 Geratebau Eberspacher Ohg Turbine

Cited By (67)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4135850A (en) * 1975-09-16 1979-01-23 Mark Hot Inc. Ventilator system with adjustable damper fan
US4094613A (en) * 1976-05-07 1978-06-13 Sundstrand Corporation Variable output centrifugal pump
US4378194A (en) * 1980-10-02 1983-03-29 Carrier Corporation Centrifugal compressor
EP0081255A1 (de) * 1981-12-09 1983-06-15 BBC Brown Boveri AG Regulierbarer Abgasturbolader
US4749332A (en) * 1982-04-21 1988-06-07 General Electric Company Method and apparatus for degrading antimisting fuel
GB2119439A (en) * 1982-04-21 1983-11-16 Gen Electric Method and apparatus for degrading and antimisting fuel
US4474530A (en) * 1982-04-21 1984-10-02 General Electric Company Method and apparatus for degrading antimisting fuel
DE3246623A1 (de) * 1982-04-21 1983-10-27 Gen Electric Verfahren und vorrichtung zum zersetzen von antivernebelungs-treibstoff
US4460310A (en) * 1982-06-28 1984-07-17 Carrier Corporation Diffuser throttle ring control
GB2211246A (en) * 1987-12-23 1989-06-28 Sundstrand Corp Controlling fluid flow through centrifugal pump
US4802817A (en) * 1987-12-23 1989-02-07 Sundstrand Corporation Centrifugal pump with self-regulating impeller discharge shutter
US4824325A (en) * 1988-02-08 1989-04-25 Dresser-Rand Company Diffuser having split tandem low solidity vanes
US4850795A (en) * 1988-02-08 1989-07-25 Dresser-Rand Company Diffuser having ribbed vanes followed by full vanes
US4877373A (en) * 1988-02-08 1989-10-31 Dresser-Rand Company Vaned diffuser with small straightening vanes
US4877369A (en) * 1988-02-08 1989-10-31 Dresser-Rand Company Vaned diffuser control
US4902200A (en) * 1988-04-25 1990-02-20 Dresser-Rand Company Variable diffuser wall with ribbed vanes
US4932835A (en) * 1989-04-04 1990-06-12 Dresser-Rand Company Variable vane height diffuser
US5082428A (en) * 1990-08-16 1992-01-21 Oklejas Robert A Centrifugal pump
US5807071A (en) * 1996-06-07 1998-09-15 Brasz; Joost J. Variable pipe diffuser for centrifugal compressor
AU711217B2 (en) * 1996-06-07 1999-10-07 Carrier Corporation Variable pipe diffuser for centrifugal compressor
US6220031B1 (en) * 1998-08-26 2001-04-24 Daimlerchrysler Ag Exhaust gas turbocharger for an internal-combustion engine and method of operating same
US6431823B1 (en) * 2000-07-13 2002-08-13 Yudko Slepoy Centrifugal pump with variable capacity and pressure
US6619072B2 (en) 2000-08-02 2003-09-16 Mitsubishi Heavy Industries, Ltd. Turbocompressor and refrigerating machine
SG103836A1 (en) * 2000-08-02 2004-05-26 Mitsubishi Heavy Ind Ltd Turbocompressor and refrigerating machine
FR2871200A1 (fr) * 2004-06-02 2005-12-09 Mark Iv Systemes Moteurs Sa Dispositif de pompe a debit variable
EP1657446A3 (de) * 2004-11-12 2013-05-01 Geräte- und Pumpenbau GmbH, Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
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Also Published As

Publication number Publication date
JPS4881107A (de) 1973-10-30
IT973131B (it) 1974-06-10
DE2262883A1 (de) 1973-07-05
NL7217857A (de) 1973-07-03
JPS5542277B2 (de) 1980-10-29
IL40881A0 (en) 1973-01-30
SE388251B (sv) 1976-09-27
BE793550A (fr) 1973-04-16
DE2262883C2 (de) 1983-07-28
CH547956A (de) 1974-04-11
CA962894A (en) 1975-02-18
FR2167163A5 (de) 1973-08-17
IL40881A (en) 1976-02-29
GB1412150A (en) 1975-10-29

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