US3576375A - Fluid pumping system - Google Patents

Fluid pumping system Download PDF

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Publication number
US3576375A
US3576375A US840752A US3576375DA US3576375A US 3576375 A US3576375 A US 3576375A US 840752 A US840752 A US 840752A US 3576375D A US3576375D A US 3576375DA US 3576375 A US3576375 A US 3576375A
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United States
Prior art keywords
fluid
pump
passage
pressure
pumping
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Expired - Lifetime
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US840752A
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English (en)
Inventor
Clive G B Jackson
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Bendix Corp
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Bendix Corp
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Publication date
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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
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more 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
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0072—Installation or systems with two or more pumps, wherein the flow path through the stages can be changed, e.g. series-parallel
    • 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
    • F04D29/20—Mounting rotors on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps

Definitions

  • ABSTRACT A pumping system for supplying fuel to the bur- Illtners of airc -laft jet engines
  • the syslem comprises a radially. Fold 13/00 vaned centnfugal pump and a perlpheral vortex pump ar- Fleld ofSearch ranged in parallel to cooperatively deliver fuel unde the 287; 415/53, 18, 143-147; 103/11 (A), 97 rect pressure for all ranges of operation.
  • the system includes sequential valving or clutching means so that at very low [56] Reta-films cued speeds (at ignition), the peripheral vortex pump supplies the 3 433 016 31:3 :3 SKATES PATENTS 60/241 ffiljel and at higher speeds, the radially vaned pump supplies the p q ore e 46 l 4 60 58 l 44 54. Q 66 6 o o o 77-7 so ⁇ //I4.
  • centrifugal pump designed to generate the correct fuel I pumping pressure at engine operating speeds will not generate sufficient fuel pumping pressure at the engine lightoff speed (which may be as low as 10 percent of the operating speed).
  • Centrifugal pumps are, however, extremely attractive in aircraft turbine fuel pumping applications because they are light in weight, sturdy, may be driven at very high speeds, and most importantly, they are insensitive to most contaminants carried by the fuel. It is, therefore, an object of this invention to provide a centrifugal pump or combination of centrifugal pumps as the main fluid pump in a system capable of supplying fuel to the burners of a turbine engine.
  • a positive displacement pump can be combined with a radially-vaned centrifugal pump to extend the lower range of operation of the pump system, but the positive displacement pumps are extremely sensitive to the presence of contaminants in the fluid being pumped. Furthermore, they require a gear and clutch connection to the drive of the pump so that they may operate at their optimum speed while the turbine is operating at low speed and may then be shut down after the radially-vaned centrifugal pump has reached its operated speed. It is, therefore, an object of this invention to provide a pumping system for pumping fluids which does not rely upon a positive displacement type of pump to supply pressurized fluid over the lower region of the operating speed range. It is a further object of this invention to provide a pumping system for a turbine engine which may be driven directly off of the same accessory drive shaft.
  • peripheral vortex pumps also known as side channel pumps, regenerative pumps and regenerative turbine pumps
  • head coefficient is inversely proportional to the normalized flow.
  • Head coefficient is a direct function of the pumping pressure or head, while normalized flow is the actual flow divided by the maximum flow.
  • a centrifugal pump for a given speed, demonstrates a pumping characteristic of essentially constant head coefficient for all flows.
  • centrifugal pumps Because of the desirable characteristics of centrifugal pumps in general, it is an object of this invention to provide a fluid pumping system which incorporates a plurality of pump impellers of different designs which may be coaxially mounted and which will be capable of supplying fuel under the proper pressure to the burner nozzles of turbine engines at all engine operating conditions. More specifically, it is an object of this invention to provide, in a fluid supply system, a centrifugal pump and a peripheral vortex pump cooperatively coupled to pump fuel at the necessary pressure to the burner of a turbine engine.
  • FIG. 1 shows comparative curves of pump head coefiicient plotted as a function of normalized flow.
  • FIG. 2 shows comparative curves as shown in FIG. 1 for three values of pump speed.
  • FIG. 3 shows a preferred embodiment of my invention in schematic form wherein the peripheral vortex or starting pump is disconnected from the pump circuit by suitable valving and is subsequently permitted to run dry.
  • FIG. 4 shows, in schematic form, an alternative embodiment of my invention in which the starting pump impeller is coupled to and decoupled from the from the power input shaft by suitable clutch means.
  • Gas turbine engines usually have a speed range of about 10:1 between the beginning of the starting cycle and the rated speed, with idle speed at about 50 percent of rated speed.
  • the fuel pressure required for the combustion system has a range of about 5:1 and the fuel pressure at idle is usually not much greater than that at the start.
  • a centrifugal pump designed to give the desired pressure at the start would, therefore, not only be very large because of its low head coefficient, but would generate about times the starting pressure at rated speed, or 10 times the required rated pressure.
  • the lines N N and N are the head curves of a centrifugal pump at cranking, lightoff and idle speeds respectively.
  • the lines N' N and N are the corresponding head curves of the peripheral vortex pump.
  • the dashed line denoted as N represents the curve of required pressure versus flow for increasing engine speed.
  • the peripheral vortex pump is designed so that, at point P it is able to supply fuel at the necessary pressure.
  • the centrifugal element which is generating a very low pressure at this speed, is shut ofi by means of a discharge check valve or the like.
  • the peripheral pump At point P, on the engine acceleration line, the peripheral pump has a head and flow capacity exceeding the requirement.
  • a bypass valve would, therefore, be required to direct excess fuel flow to the peripheral pump inlet, permitting the pump to operate at point P on its head curve N At this speed, the centrifugal element is still incapable of supplying sufficient pressure and remain shut off.
  • FIG. 3 my pump is shown in schematic fonn and is designated generally by 10.
  • the pumping action is provided by starting section 12 containing impeller 14 and main section 16 containing impeller 18.
  • the impellers l4 and 18 are attached to a shaft 20 for rotation therewith.
  • the impellers 14 and 18 are of unitary construction,
  • Shutoff valve 44 is a portion of the control valve, indicated generally by 46, and is positioned in response to the fluid pressure in the output channel or collector ring 48 of the main pumping section 16.
  • a pilot valve 50 is resiliently biased to close the outlet port of control passage 52 which intercommunicates control valve 46 and channel 48.
  • the fluid pressure in channel 48 is communicated to the piston end, indicated generally as 54, of control valve 46 and is operative to more control valve 46 and to thereby seal the inlet of passage 30 with shutoff valve 44.
  • the control valve 46 has, at the piston end 54, projecting abutment fingers 56 which allow the control valve 46 to be held away from the outlet of passage 52 so that fluid pressure in channel 48 can be communicated to the entire surface area of the piston portion.
  • the control valve 46 is biased toward the outlet of channel 52 by spring 58 and the pilot valve 50 is biased by spring 60 to close the aforementioned outlet of passage 52.
  • a passage 62 is arranged in the body of control valve 46 in order to communicate atmospheric pressure from channel 64 to the inlet of passage 30 when valve 44 has sealed passage 30 from communication with the pump inlet passage 26.
  • An annular recess 66 is also provided in the body of control valve 46 so that the passage 63 can communicate the delivery passage 38 of the starter pumping section 12 with the drain passage 70 whenever the shutoff valve 44 is seated so that when atmospheric pressure is being communicated to passage 30 by passage 64 through passage 62, the starter impeller can be drained of fluid.
  • passage 128 communicates the pump inlet passage 126 to the starting impeller 114, while passage 131 communicates additional flow from the outlet of the starting impeller 114 to the inlet of the starting impeller 114.
  • control clutch means 146 are operative to couple starting impeller 114 to the shaft 120 for rotation therewith and to decouple starting impeller 114 from the shaft 120 when its pumping action is no longer necessary.
  • my fluid pumping system is composed of four separately functioning elements, the fluid passage means to supply fluid to and receive fluid from the pump, a starting impeller and a main impeller and the impeller controlling means.
  • the impeller controlling means comprised various flow control valves and exhaust passages
  • the impeller controlling means comprised a clutch means to couple the impeller to and to decouple it from the power input shaft.
  • the clutch 146 utilized in the FIG. 4 embodiment may be a centrifugal clutch in which the interconnection of clutch input and output components is terminated above rotational speeds of a selected value and the interconnection is completed, as for instance, by a resilient or other biasing means below the selected speed.
  • the clutch 146 could also be electromagnetically actuated so that a friction connection exists whenever an electromagnetic coil is energized and energization of the coil could be controlled manually or automatically in response to the speed of shaft 120. Examples of both types of clutches, as well as further alternatives, are well known and further description is not considered necessary.
  • the spring constants of the springs controlling the pilot valve 50, control valve 46, and check valve 40 will be such that they will resist movement of the various valves until impeller 18 is generating sufficient pressure and capacity to supply all the fuel requirements of its associated turbine.
  • the pump according to the present invention, combines the advantages of almost complete insensitivity to contaminants with a lower weight and smaller possible envelope because it does not need the gear connection between main pump and starting pump.
  • the control valve means and fluid exhaust passage means need not be large or close to the impellers so that they do not impose a significant weight or envelope problem.
  • the arrangement of valves and passages herein described is not to be considered as the only method of achieving the desired functions, but is an example of my invention, the scope of which is defined by the claims which follow.
  • FIG. 4 embodiment of my invention achieves the sequential pumping by use of a control clutch 146 in place of the control valve 46.
  • control valve 46 permits my pump to become even less sensitive to fuel contaminants while the clutched connection between the starting impeller 114 and the main shaft permits the starting impeller to be nonrotating during most of the period of time the engine is operating.
  • the impellers provide substantially sequential pumping and are arranged in parallel fashion so as to remain substantially independent from one another. However, to provide a continuous range of pumping, there will be a region of overlap in which each impeller is providing a portion of the pressurized fluid.
  • a peripheral vortex impeller is the preferred form of impeller 14 for the starting section 12 of my fluid pump, taking into consideration envelope restrictions imtype of rotodynamic impeller, on the other hand, maintains a substantially-constant head coefficient over its entire flow range and is, therefore, my preferred form of main section impeller 18.
  • Fluid pumping apparatus having fluid inlet and fluid discharge passages comprising:
  • pump housing means including first and second chambers having fluid inlet means and fluid exhaust means;
  • said first and second chambers and said fluid inlet means and discharge means arranged in parallel and interconnecting the fluid inlet and fluid discharge passages;
  • first and second dissimilar rotodynamic impellers rotatably contained within said first and second chambers
  • control means responsive to fluid pressure in one of said chambers operative to control the flow of fluid from the fluid inlet passage, through the fluid inlet means and fluid exhaust means and out through the fluid discharge passage.
  • control means comprise:
  • flow controlling valve means operative to terminate fluid delivery to said first chamber means when the fluid pressure in said second chamber means reaches a predetermined level.
  • the apparatus as claimed in claim 2 including further venting means associated with said first chamber means operative to communicate the fluid inlet of said first chamber means to the atmosphere and the fluid outlet of the first chamber means to a fluid drain.

Landscapes

  • 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)
  • Control Of Positive-Displacement Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US840752A 1969-07-10 1969-07-10 Fluid pumping system Expired - Lifetime US3576375A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US84075269A 1969-07-10 1969-07-10

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US3576375A true US3576375A (en) 1971-04-27

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US840752A Expired - Lifetime US3576375A (en) 1969-07-10 1969-07-10 Fluid pumping system

Country Status (5)

Country Link
US (1) US3576375A (fr)
JP (1) JPS506361B1 (fr)
DE (1) DE2034427A1 (fr)
FR (1) FR2054134A5 (fr)
GB (1) GB1317164A (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3961859A (en) * 1975-04-17 1976-06-08 Chandler Evans Inc. Clutch connected multi-stage impeller pump
US4487548A (en) * 1983-05-19 1984-12-11 Chandler Evans Inc. Centrifugal main fuel pump having starting element
US4629394A (en) * 1983-07-25 1986-12-16 Chandler Evans Inc Centrifugal pump having low flow diffuser
US4643635A (en) * 1984-07-02 1987-02-17 Chandler Evans Inc. Vapor core centrifugal pump having main and low flow impellers
US4989411A (en) * 1988-12-22 1991-02-05 Allied-Signal Inc. Over the shaft fuel pumping system
US5456574A (en) * 1993-08-03 1995-10-10 United Technologies Corporation Centrifugal pump with starting stage
US20040079081A1 (en) * 2002-10-24 2004-04-29 Jevons Eric Edward Fuel system
WO2017079309A1 (fr) * 2015-11-03 2017-05-11 Eaton Corporation Étage de démarrage de pompe régénératrice pour pompe à carburant centrifuge à grande vitesse
FR3107935A1 (fr) * 2020-03-04 2021-09-10 Eaton Intelligent Power Limited Etage de démarrage et d'actionnement de pompe régénérative pour pompe à carburant centrifuge à grande vitesse
US20230011740A1 (en) * 2021-07-07 2023-01-12 Eaton Intelligent Power Limited Regenerative pump and methods
US20230034465A1 (en) * 2021-07-30 2023-02-02 Hamilton Sundstrand Corporation Fluid pump systems
US11821429B2 (en) 2020-03-04 2023-11-21 Eaton Intelligent Power Limited Single wheel multi-stage radially-layered regenerative pump

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5386034U (fr) * 1976-12-17 1978-07-15
GB8712575D0 (en) * 1987-05-28 1987-07-01 Powered Shower System Ltd Pump
GB9325029D0 (en) * 1993-12-07 1994-02-02 Lucas Ind Plc Pump

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2464144A (en) * 1945-04-02 1949-03-08 Ingersoll Rand Co Pumping mechanism
US2785634A (en) * 1950-08-18 1957-03-19 Bendix Aviat Corp Fluid pressurizing apparatus
US3147712A (en) * 1960-09-02 1964-09-08 Gen Motors Corp Fuel pumping system for gas turbines
US3433016A (en) * 1967-03-09 1969-03-18 Gen Electric Fuel delivery system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2464144A (en) * 1945-04-02 1949-03-08 Ingersoll Rand Co Pumping mechanism
US2785634A (en) * 1950-08-18 1957-03-19 Bendix Aviat Corp Fluid pressurizing apparatus
US3147712A (en) * 1960-09-02 1964-09-08 Gen Motors Corp Fuel pumping system for gas turbines
US3433016A (en) * 1967-03-09 1969-03-18 Gen Electric Fuel delivery system

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3961859A (en) * 1975-04-17 1976-06-08 Chandler Evans Inc. Clutch connected multi-stage impeller pump
US4487548A (en) * 1983-05-19 1984-12-11 Chandler Evans Inc. Centrifugal main fuel pump having starting element
US4629394A (en) * 1983-07-25 1986-12-16 Chandler Evans Inc Centrifugal pump having low flow diffuser
US4643635A (en) * 1984-07-02 1987-02-17 Chandler Evans Inc. Vapor core centrifugal pump having main and low flow impellers
US4989411A (en) * 1988-12-22 1991-02-05 Allied-Signal Inc. Over the shaft fuel pumping system
US5456574A (en) * 1993-08-03 1995-10-10 United Technologies Corporation Centrifugal pump with starting stage
US20040079081A1 (en) * 2002-10-24 2004-04-29 Jevons Eric Edward Fuel system
WO2017079309A1 (fr) * 2015-11-03 2017-05-11 Eaton Corporation Étage de démarrage de pompe régénératrice pour pompe à carburant centrifuge à grande vitesse
US10927837B2 (en) 2015-11-03 2021-02-23 Eaton Intelligent Power Limited Regenerative pump start stage for high speed centrifugal fuel pump
FR3107935A1 (fr) * 2020-03-04 2021-09-10 Eaton Intelligent Power Limited Etage de démarrage et d'actionnement de pompe régénérative pour pompe à carburant centrifuge à grande vitesse
GB2597563A (en) * 2020-03-04 2022-02-02 Eaton Intelligent Power Ltd Regenerative pump start and actuation stage for high-speed centrifugal fuel pump
US11821429B2 (en) 2020-03-04 2023-11-21 Eaton Intelligent Power Limited Single wheel multi-stage radially-layered regenerative pump
US20230011740A1 (en) * 2021-07-07 2023-01-12 Eaton Intelligent Power Limited Regenerative pump and methods
US20230034465A1 (en) * 2021-07-30 2023-02-02 Hamilton Sundstrand Corporation Fluid pump systems
US12071898B2 (en) * 2021-07-30 2024-08-27 Hamilton Sundstrand Corporation Fluid pump systems

Also Published As

Publication number Publication date
JPS506361B1 (fr) 1975-03-13
DE2034427A1 (de) 1971-01-14
FR2054134A5 (fr) 1971-04-16
GB1317164A (en) 1973-05-16

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