US2539484A - Vapor removing system for rotary fuel metering devices - Google Patents

Vapor removing system for rotary fuel metering devices Download PDF

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Publication number
US2539484A
US2539484A US586224A US58622445A US2539484A US 2539484 A US2539484 A US 2539484A US 586224 A US586224 A US 586224A US 58622445 A US58622445 A US 58622445A US 2539484 A US2539484 A US 2539484A
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United States
Prior art keywords
fuel
chamber
valve
pressure
vapor
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Expired - Lifetime
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US586224A
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English (en)
Inventor
Albert P Schnaible
Willard F Blakeway
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Bendix Aviation Corp
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Bendix Aviation Corp
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Publication date
Priority to IT454462D priority Critical patent/IT454462A/it
Application filed by Bendix Aviation Corp filed Critical Bendix Aviation Corp
Priority to US586224A priority patent/US2539484A/en
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Publication of US2539484A publication Critical patent/US2539484A/en
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Expired - Lifetime legal-status Critical Current

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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F9/00—Measuring volume flow relative to another variable, e.g. of liquid fuel for an engine
    • G01F9/006—Measuring volume flow relative to another variable, e.g. of liquid fuel for an engine with mechanic means

Definitions

  • This invention relates primarily to fuel-feeding devices of that type wherein the fuel supplied to a power plant or engine is measured or metered on the basis of engine speed which may be modified by one or more operating functions or characteristics indicative of mass air flow to the engine, or air consumption.
  • a device is illustrated in the copending application of Frank C. Mock, Serial No. 586,223, filed of even date herewith (common assignee), and now Patent No. 2,531,780 granted Nov. 28, 1950.
  • the fuel is conducted under pressure to a chamber embodying rotating parts which tend to impart a whirling motion to theY fuel in the chamber.
  • Such parts in the device selected for the purposes of illustration in the present, instance comprise a pump rotor which draws fuel into the pump chamber, a fuel valve controlled by a centrifugal governor rotating in synchronism with the engine, and a cup-shaped member connected to the rotor and having a driving connection with the governor and functioning among other things to limit the throw of the governor weights.
  • an object of the present invention is to provide a vapor elimination system for speed metering pumps which is highly effective in operation and at the same time tends towards simplicity in overall pump construction.
  • Another object is to generally improve fuelfeeding devices of the type specified.
  • Fig. 1 is a schematic diagram of a speed metering pump in accordance with the invention
  • Fig. 2 is a section taken substantially on the line 2 2, Figure 1;
  • Figure 3 is an enlarged section of part of Figure 1.
  • a main pump housing I has a portion shaped to define a fuel pump chamber II to which fuel may be supplied from a tank or other suitable source, not shown, through conduit I2.
  • a fuel pump I3 has a rotor I4 formed with a center bore mounting a cam pin I5 and a series of radial slots mounting blades I6.
  • the rotor is supported for rotation in an open sleeve or cage I'l terminating at its opposite ends in rings Ila which cam the blades radially inwardly against the cam pin I5.
  • the right-hand end of the rotor is reduced to provide a drive shaft Ida which has a pinion gear I8 secured thereon to facilitate a driving connection with the power plant or engine to be supplied With fuel.
  • the pump I3 takes fuel from chamber II and forces it under pressure into chamber I9 dened by a wall 20- shown as formed integral with the housing I0 and having portions 20a and 20h which are contoured to receive the rotor cage Il.
  • removably secured to the housing I0 supports the sealing and bearing assembly for shaft Ida to which oil may be supplied through duct 22.
  • the left end of the rotor is rotatable in a stepped bearing and sealing ring 23 mounted in a boss 24 formed integral with the housing or casing I0, a bushing 25 serving to lock the bearing in place.
  • the left end of the rotor is hollow to permit insertion of the cam pin I5, the latter being held against endwise displacement by an abutment member 26 provided with a sealing ring to prevent escape of fue1 from the rotor bore, said member being removably held in place by a snap ring 21.
  • the pump rotor I4 has a driving connection with a governor assembly which, as will be more fully described hereinafter, is arranged to operate a poppet valve comprising an elongated valve or valve member 28 formed with a reduced stem 28a.
  • the valve member 28 is mounted to slide in a bushing 29 having an attaching flange 29a secured to a flange 30 forming part of the wall of an unmetered fuel chamber to be described, said bushing being formed with a valve seat defining a valve port 3 I.
  • valve stem 28 is encircled by a spring 32 which at its left end abuts a shoulder formed on the valve stem and at its opposite end bears against the inner race of a thrust bearing 33 held in adjusted position by end nut 34, the latter serving to adjust and correlate the governor and poppet valve assemblies.
  • the governor weights are indicated at 35; they are each secured on a shaft 36 and have formed integrally therewith clutch fingers 3l adapted to engage the thrust bearing 33 and urge the valve 28 toward open position, or to the right as viewed@ in Figure l, with a force depending uponthe speed of rotation and the resulting centrifugal effect of the weights 35.
  • the shafts or pins 36 are anchored in yokes 38 forming part of a' hub 39 carrying the outer races of a bearing assembly 40, the inner races of the bearing assembly being mounted on the bushing 29 and held in place by endnutor collar 4 I.
  • a cup or cup-shaped member 42 is secured on the left end of the rotor I4 by means of a fitting 43 and'endnutor collar 44;'it functions among other things to reduce turbulence of the fuel in the chamber I9 and to limit the throw of the governor weights under certain conditions, as for instance, when there is no appreciable differential pressure across the metering head diaphragm, to be described.
  • a fuel baille or shield 42a is preferably mounted on the bushing 29 adjacent the valve port 3
  • a driving connection between the rotor I4 and governor is provided by means of lugs 45 projecting radially from the ange of the hub 39 and engaging in open slots 46 formed in the edge of the cup 42. This construction tends toward simplicity and it also facilitates assembly.
  • a governor head diaphragm is indicated at 41, Figure 1; it is clamped between the radial portions or flanges of bushings 48 and 49.
  • Bushing 48 is slidingly mounted in a guide sleeve 50 supported by hub I, while bushing 49 has connected thereto a stem 52 adjustably locked in position by end nut 53.
  • a cable 64 connects at one end with the member 52 and at its opposite end with the stem 28a of valve 28, note Figure 3.
  • a bushing 55 steadies the cable 54, and to stiffen the cable sufficiently to prevent buckling due to idle spring thrust, a relatively light wire spring encircles the cable.
  • An idle spring 51 engages the outer side of the diaphragm bushing 49 and applies predetermined pressure in an opening direction on the poppet valve 28 at low idling speeds to ensure suflicient metering head pressure for idling purposes, said spring being backed by an end plug 58 which is threaded into end cap 59 and is maintained in adjusted position by spring-pressed detent members 69. Since the spring 5l may require delicate adjustment, it
  • the plug 58 be capable of easy adjustment while at the same time it should be held stable when once set or adjusted; and the detent members function advantageously in this respect.
  • a by-pass chamber 6I communicates with the fuel-intake chamber II; and controlling passage of fuel from the pressure chamber I9 to the bypass 6I is a relief valve 62 which seats on a valve cage 63 mounted in the upper transverse portion of the wall 20 and provided with ports 63a.
  • the valve has a depending stem carrying a piston member 65 which slides in a vented cylinder 65a, said members 65 and 65a functioning as a dashpot to stabilize the action of the valve 62.
  • a spring 66 is seated in a cup-shaped member 61 secured to the valve 62.
  • a diaphragm 68 of substantially the same mean effective area as the seat of valve 62 is clamped between the member 61 and valve 62 and forms a movable wall of a balancing chamber 10. The spring 66 urges valve 62 onto its seat and allows it to open when the pressure in chamber I9 exceeds the pressure in chamber 19 by some predetermined amount dependent upon the strength of spring 66.
  • a constant drop across the valve 26 is brought about by connecting the balancing chamber 10 through duct or channel 1I, 1Ia with unmetered fuel chamber 12 into which the port 3
  • the chamber 10 communicates with by-pass chamber 6I through restricted orifice or bleed 16 to permit complete filling of chamber 10 and to relieve vapor or excess pressure developed in said chamber by engine heat when the engine is stopped.
  • valve 62 When the pump is initially placed in operation and suiicientv pressure is built up in the chamber I9 the valve 62 will open. When this valve opens, fuel is admitted to the chamber 6I, and after this chamber lls, fuel will pass through slaughter 15 into chamber 10. Since this latter chamber is in communication with the unmetered fuel chamber 12, the pressure on the top side of diaphragm 68 will be metering head pressure while that on the lower side of valve 62 will be equivalent to that in the governor chamber I9, and the differential between these chambers 10 and I9 or across the diaphragm and valve assembly 68, 62, and hence the drop across the valve 28 will therefore be maintained at a substantially constant predetermined value as determined by spring A66, irrespective of the volume of fuel delivered by the unit.
  • the valve indicated at BI, Figure 1 is an idle cut-off valve; it is used to completely cut off flow of fuel to the engine to stop the latter.
  • the valve is provided with a stem 82 and a lever 83. In the position shown, the valve is open and fuel may flow through conduit 89, the latter being provided with a coupling member 65 for attachment of a suitable tube or fuel line leading to a spray nozzle, injection pump, burner ring or the like, depending upon what type of power unit is being supplied with fuel.
  • conduit or duct 1l connects with its continuation 1Ia through a valve port 186 controlled by rotary valve 61 mounted on and rotatable with valve stem 82 and cut-off valve 8l.
  • valve 81 is likewise closed and communication between the chamber 12 and the chamber 10 is broken.
  • the by-pass valve 62 would require so much pressure to unseat it as to produce dangerously high, pressures in the chamber I9.
  • a metering needle controls a metering orifice 9
  • Needle 96 is regulated by an automatic control unit including a bellows 93 mounted in a housing 94 defining a chamber 95 to which charging pressure may be communicated through passage 96.
  • the bellows 93 maybe evacuated to render it responsive to changes in pressure only, temperature compensation being had through a separate control element, subsequently referred to.
  • An exhaust back pressure capsule or bellows 91 coacts with the latter to effect movement of the needle 90 as a function of manifold pressure modified by a certain increment of exhaust back pressure.
  • the bellows 91 is vented to the atmosphere, since atmospheric pressure may be taken as an index of exhaust back pressure.
  • metering or feed of fuel is regulated by correlating certain variable factors of engine operation, namely, engine speed or R. P. M., manifold or boost pressure modified by a certain predetermined percentage of exhaust back pressure, for example one-sixth, and manifold temperature, to fulfill the following formula:
  • Rotation of the pump rotor I4 causes fuel to be drawn in through conduit I2 from a suitable source of supply, such as a conventional fuel tank, and into the chamber I I, from which it is forced by the rotor blades or varies into the chamber I9.
  • the relief valve 82 is set to maintain the fuel in chamber I9 at a predetermined pressure, over and above the pressure in unmetered fuel chamber 12. When this pressure is exceeded, the excess fuel is by-passed back to the chamber I
  • variable pressure regulator control chamber 98 A small portion of the fuel fiows from chamber 12 through destriction 99 into regulator control chamber 98, thence through the variable orifice,
  • the pressure in the variable pressure regulator control chamber 98 will be of a value intermediate the unmetered fuel pressure in chamber 12 and the metered fuel pressure in chamber 92, and will tend to approach the pressure in chamber 12 as the effective area of orifice
  • the differential between the pressures in chambers 12 and 98 will remain a constant percentage of the differential between the pressures in chambers 12 and 92, the latter differential being the metering differential pressure effective across the metering orifice 9
  • the governor head thatis, the differential between the pressures in chambers 12 and 98, is effective on the governor head diaphragm 41 tending to move the diaphragm to the left and tending through cable 54 to move the valve 28 to the left in opposition to the force thereon of the governor weights '35.
  • the valve 28 will float toward open or closed position until the governor head acting on diaphragm 41 balances the force of the governor weights 35. Since the governor rotates in direct relation to engine ⁇ speed, the thrust of the governor weights is proportional to speed squared and therefore the balancing differential across diaphragm 41 is maintained proportional to speed squared and the metering head across the metering orifice 92 is also maintained proportional to speed squared. Assuming that the area of the metering orifice 9
  • the mass rate of air now to the engine in addition to being dependent upon the engine speed is also dependent upon the manifold orl charging pressure modified by a predetermined increment or portion of the exhaust back pressure.
  • is controlled by the needle 90 and the latter is actuated in direct relation to manifold pressure modified by a predetermined increment of back pressure or atmospheric pressure.
  • Aweights 35 will open the valve 28 an additional amount to increase the fuel now until the differential pressure across diaphragm 41 is restored to its former value to balance the force of weights 35. This will result in a percentage increase in the fuel ow through metering horr 9
  • the rate of fuel ow will be at a minimum, and when the area of said orifice is at a minimum, the rate of fuel flow will be at a maximum, for any given engine speed and a fixed position of needle
  • 5 When there is little or no vapor or air in the float chamber the valve port
  • the vapor elimination system will operate in any fuel metering device where the fuel is centrifuged due to a whirling action or movement irrespective of the particular means which causes such movement; hence the inventive concept is not limited to any specific type of fuel-feeding or charge-forming device or parts thereof but only by the scope of the appended claims.
  • a vapor-collecting chamber said rotor being provided with an axial passage adapted to receive fuel and entrained Vapor, and a vapor-removing conduit communicating said passage with said vapor-collecting chamber.
  • a vapor-collecting chamber said cup-shaped member having a plurality of holes in the Wall thereof to expedite flow of vapor toward the axis of the governor chamber and said rotor having an axial passage adapted to receive fuel and entrained vapor. and a vapor-removing conduit communicating said axial passage with said vapor-collecting chamber.
  • a metering device for use in a fuel-feeding system for an engine wherein fuel is metered as a function of engine speed, a metering device provided with a pressure chamber, a by-pass and a relief valve controlling passage of fuel from the pressure chamber to the by-pass, a.
  • vapor-removing passage communicating at its inlet with the axial portion of said pressure chamber and at its outlet with the vapor-collecting chamber to conduct fuel and entrained vapor from said pressure chamber ⁇ to said vapor-collecting chamber, and a restricted ow passage communicating the vapor-collecting chamber with said by-pass to maintain the liquid fuel in said latter chamber at a predetermined level.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Fuel-Injection Apparatus (AREA)
US586224A 1945-04-02 1945-04-02 Vapor removing system for rotary fuel metering devices Expired - Lifetime US2539484A (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
IT454462D IT454462A (enrdf_load_stackoverflow) 1945-04-02
US586224A US2539484A (en) 1945-04-02 1945-04-02 Vapor removing system for rotary fuel metering devices

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3135220A (en) * 1962-11-20 1964-06-02 Richard H Haynes Portable self-priming floor drainer pump assembly
US3144832A (en) * 1961-07-10 1964-08-18 Richard H Haynes Portable self-priming floor drainer pump assembly

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1345895A (en) * 1920-03-29 1920-07-06 Gnome Et Rhone Moteurs Centrifugal pump
US1906334A (en) * 1930-06-13 1933-05-02 Rathbun Edward Fuel control system for oil engines
DE630932C (de) * 1935-03-27 1936-06-09 Carl Schmieske Kreiselpumpe, insbesondere fuer Schmieroel, mit Entlueftungsvorrichtung
GB526988A (en) * 1938-03-30 1940-09-30 Marconi Wireless Telegraph Co Improvements in or relating to printing telegraph receiving apparatus
US2238502A (en) * 1939-01-16 1941-04-15 Muir Neil Shaw Pumping apparatus
US2275355A (en) * 1938-04-28 1942-03-03 Bjournulf Johnsen Pump and air separator
US2368529A (en) * 1942-09-08 1945-01-30 Edwards Miles Lowell Pump
US2368528A (en) * 1941-02-01 1945-01-30 Edwards Miles Lowell Pump
US2368530A (en) * 1943-04-19 1945-01-30 Edwards Miles Lowell Vapor expelling pump
US2412289A (en) * 1941-04-07 1946-12-10 Plessey Co Ltd Pump having bypass with speed-sensitive and pressure-responsive control

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1345895A (en) * 1920-03-29 1920-07-06 Gnome Et Rhone Moteurs Centrifugal pump
US1906334A (en) * 1930-06-13 1933-05-02 Rathbun Edward Fuel control system for oil engines
DE630932C (de) * 1935-03-27 1936-06-09 Carl Schmieske Kreiselpumpe, insbesondere fuer Schmieroel, mit Entlueftungsvorrichtung
GB526988A (en) * 1938-03-30 1940-09-30 Marconi Wireless Telegraph Co Improvements in or relating to printing telegraph receiving apparatus
US2275355A (en) * 1938-04-28 1942-03-03 Bjournulf Johnsen Pump and air separator
US2238502A (en) * 1939-01-16 1941-04-15 Muir Neil Shaw Pumping apparatus
US2368528A (en) * 1941-02-01 1945-01-30 Edwards Miles Lowell Pump
US2412289A (en) * 1941-04-07 1946-12-10 Plessey Co Ltd Pump having bypass with speed-sensitive and pressure-responsive control
US2368529A (en) * 1942-09-08 1945-01-30 Edwards Miles Lowell Pump
US2368530A (en) * 1943-04-19 1945-01-30 Edwards Miles Lowell Vapor expelling pump

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3144832A (en) * 1961-07-10 1964-08-18 Richard H Haynes Portable self-priming floor drainer pump assembly
US3135220A (en) * 1962-11-20 1964-06-02 Richard H Haynes Portable self-priming floor drainer pump assembly

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