US3416504A - Fuel injection systems - Google Patents

Fuel injection systems Download PDF

Info

Publication number
US3416504A
US3416504A US575010A US57501066A US3416504A US 3416504 A US3416504 A US 3416504A US 575010 A US575010 A US 575010A US 57501066 A US57501066 A US 57501066A US 3416504 A US3416504 A US 3416504A
Authority
US
United States
Prior art keywords
fuel
pressure
chamber
engine
valve
Prior art date
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
Application number
US575010A
Other languages
English (en)
Inventor
Jackson Harold Ernest
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Petrol Injection Ltd
Original Assignee
Petrol Injection Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Petrol Injection Ltd filed Critical Petrol Injection Ltd
Application granted granted Critical
Publication of US3416504A publication Critical patent/US3416504A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/02—Pumps peculiar thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/16—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by means for metering continuous fuel flow to injectors or means for varying fuel pressure upstream of continuously or intermittently operated injectors
    • F02M69/18—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by means for metering continuous fuel flow to injectors or means for varying fuel pressure upstream of continuously or intermittently operated injectors the means being metering valves throttling fuel passages to injectors or by-pass valves throttling overflow passages, the metering valves being actuated by a device responsive to the engine working parameters, e.g. engine load, speed, temperature or quantity of air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/46—Details, component parts or accessories not provided for in, or of interest apart from, the apparatus covered by groups F02M69/02 - F02M69/44
    • F02M69/50—Arrangement of fuel distributors, e.g. with means for supplying equal portion of metered fuel to injectors

Definitions

  • ABSTRACT OF THE DISCLOSURE A continuous circulation fuel injection system in which fuel supply to injector devices is pressurised in dependence on the square of engine speed by a rotary ring impeller and also controlled by a variable area orifice metering valve operated by engine air intake manifold vacuum.
  • the supply branch is connected to the impeller devices by a chamber having a first compartment having an upstanding tubular portion against which a diaphragm is seated by a predetermined, constant force sufiicient to ensure that fuel pressure in the supply branch does not fall below a predetermined value adequate to prevent fuel vaporisation.
  • the diaphragm has an aperture located within the confines of the annular seating so that when the diaphragm is unseated, fuel flows from the first compartment through the diaphragm aperture to a second compartment and hence to the injector devices, fuel flowing from the second compartment having removed therefrom the said predetermined pressure.
  • the first compartment is also connected to the fuel return branch which also includes a second diaphragm valve closed by the same predetermined force as the first mentioned diaphragm valve.
  • fuel flow from the second diaphragm valve is to a vapour separator which has an upstanding funnel member the lower, constricted end of which receives fuel from the second diaphragm valve.
  • the funnel member is disposed in a chamber having an upper vapour vent and a lower fuel outlet from which the fuel pressurising means is supplied.
  • This invention relates to continuous low-pressure fuelinpection systems for internal combustion engines and also to components for use in such systems.
  • the supply branch of the fuel circulation conduit system can contain a chamber from which the injector devices are fed and which also includes a pressure removing device for returning the fuel pressure to the lower pressure required by the injector devices.
  • the chamber can be divided into two parts by a resilient diaphragm loaded to a pressure equal to the added pressure to which the fuel is subjected to prevent or substantially reduce vaporization.
  • the diaphragm controls fuel flow to the injector devices and is lifted by the fuel pressure in the supply branch to admit fuel to the injector devices at the lower pressure.
  • the return branch of the fuel circulation conduit system extends from an outlet in the chamber via a pressure loading valvewhich raises the fuel pressure in the return branch to the increased valueand thence to the fuel tank.
  • a vapour separator is included in the return branch between the loading valve and the fuel tank to prevent any vapour which has formed being returned to the tank.
  • the fuel circulation conduit system includes an engine driven fuel pump mechanism which in conjunction with a variable orifice metering valve meters fuel to the injector devices in dependence on engine speed and engine loading. Fuel pressure is adjusted in accordance with engine speed by the pump mechanism whilst fuel flow is adjusted by the metering valve in dependence on engine loading.
  • FIG. 1 shows the embodiment in diagrammatic form only
  • FIGS. 2 and 3 are cross sections on the lines IIH and III-III respectively of FIGS. 3 and 2 of a component of the system of FIG. 1,
  • FIG. 4 is a section through another component of the system of FIG. 1, and
  • FIG. 5 is a section on the line VV in FIG. 1.
  • the system shown in FIG. 1 includes a fuel circulation conduit system comprising a fuel supply branch 1 and a fuel return branch 2.
  • the supply branch 1 contains a distribution chamber 3 with exit orifices 4 joined by conduits 50 to fuel injection devices 51 located in branch pipes leading from the engine intake manifold to the respective engine cylinders.
  • the injector devices each has a fuel tube 52 extending along an outer tube 53 terminating in an outlet orifice 54.
  • the fuel tube terminates in a capillary tube 55 (acting as a flow equalising restrictor) short of and aligned with the outlet orifice 54.
  • the outer tube 53 has a vent 56 to atmosphere.
  • the capillary tube 55 has a bore size relative to that of the orifice 54 such that fuel emergent from the capillary tube is discharged through the outlet orifice without contacting the walls of the orifice.
  • the injection devices shown are described in greater detail in the said copending application S.N. 527,221.
  • the return branch 2 extends from an exit orifice 5 in the chamber 3 containing a flow restrictor 6 via a pressure loading valve 7 and a vapour separator 8 to the fuel tank of the engine (not shown).
  • the pump mechanism 11 comprises a priming pump 12 which supplies fuel to a main pump 13 at a pressure determined by a pressure relieve valve 14 connected between the outlet of the priming pump 12 and the return branch '2.
  • the construction of the main pump 13 is shown in more detail in FIG. 5 which is a section on line V-V in FIG. 1.
  • the pump has a rotor 80 keyed to a shaft 81 connected to a gear 82 (FIG.
  • the rotor 80 has circumferential vanes or teeth 83 and is mounted for rotation in a closely fitting shallow cylindrical chamber one end face 84 of which has an arcuate groove 85, registering with the teeth 83, describing an arc of about 305 around the end face 84.
  • One end of the groove 85 communicates with an inlet port 86, fed from the priming pump 12, and the other end communicates with an outlet port 87 leading to the supply branch 1.
  • the rotor 80 is rotated at a speed determined by the engine speed and fuel entering the inlet port 86 is swept around the groove 85 by the teeth 83 as a speed dependent on engine speed.
  • the velocity energy of the fuel is converted to pressure energy, the fuel thereby being forced through the outlet port 87.
  • the pressure of fuel flowing through the outlet port is directly controlled by engine speed.
  • the output from the main pump 13 passes to the supply branch 1 which contains a fuel metering valve which is controlled by the engine inlet manifold vacuum or by the opening of the engine throttle to vary the area of a metering orifice in the supply branch 1 and thereby to adjust fuel flow to chamber 3 in dependence upon the inlet manifold vacuum or the throttle opening.
  • a fuel metering valve which is controlled by the engine inlet manifold vacuum or by the opening of the engine throttle to vary the area of a metering orifice in the supply branch 1 and thereby to adjust fuel flow to chamber 3 in dependence upon the inlet manifold vacuum or the throttle opening.
  • a suitable metering valve 15 is functionally illustrated and has upper and lower chambers 60, 61.
  • the former chamber has an inlet 62 for connection to the engine air intake manifold to communicate manifold vacuum changes to the interior of chamber 60, thereby causing movement of a piston 63 therein against a spring 64 in response to such changes.
  • the piston 63 is coupled by a linkage 65 to a pivoted cam 66 in the chamber 61 so that movement of the piston causes the cam to pivot and to rotate a cam follower 67. Rotation of the cam follower rotates a valve stem 68 in a sleeve 69.
  • the valve stem 68 is open at one end and closed at the other, the open end communicating with the supply branch 1 downstream of the valve 15.
  • the branch 1 Upstream of the valve 15, the branch 1 communicates via a rectangular aperture 70 in the sleeve 69 with the interior of the valve stem 68 under control of a transverse slot 71 in the wall of the stem.
  • the width of the slot 71 changes along its length so that rotation of the valve stem 68 in the sleeve 69 varies the area of the slot in registration with the rectangular aperture 70 and hence controls the flow of fuel through the metering valve 15.
  • This metering valve is described in greater detail in co-pending application S.N. 527,221.
  • FIGS. 2 and 3 show in more detail the chamber 3 and the valve contained therein.
  • the chamber 3 has an inlet 16 leading to an annular inlet chamber 17 separated from an outlet chamber 18 by a resilient diaphragm 19 carrying a diaphragm disc 20.
  • the diaphragm 19 acts as a closure valve and controls flow of fuel from chamber 17 to chamber 18 via a central chamber 21 and a central opening 22 in both diaphragm 19 and disc 20.
  • the wall of the central chamber 21 forms a seating for the diaphragm which is loaded by a spring 23 located by the disc and a spring plate 24.
  • the loading of the diaphragm 19 by the spring 23 is adjustable by an adjusting screw 25.
  • Also located in the chamber 17 is an annular shaped fuel filter 26.
  • the chamber 17 has an outlet passage 27 leading to a chamber 28 containing an orifice disc 29 and an axially adjustable rod 30 which passes through the disc 29 and has a portion 31 the cross sectional area of which transverse to the axis of the rod 30 changes along that axis and the position of which relative to the orifice disc 29 determines the rate of fuel flow through the latter.
  • the rod 30 and the orifice disc 29 perform the function of the restrictor 6 in FIG. 1.
  • the chamber 28 is connected to the outlet 5 leading to the return branch and which is located on that side of disc 29 remote from passage 27.
  • the position of rod 30, and hence the effective area of the orifice 29, is determined by the setting of an adjusting screw 32 against which the restrictor is held by a spring 33.
  • the pressure loading valve 7 and the relief valve 14 are contained in a common housing which is shown in more detail in FIG. 4.
  • the housing has fuel inlets 34, 35 separated from a common outlet chamber 36 by spring-loaded resilient diaphragms 37 and 38 respectively.
  • the inlet 34 communicates with an annular inlet chamber 39 the access of which to the outlet chamber 36 is controlled by the diaphragm 37 which coacts with a seating provided by the upper (as seen in FIG. 4) end of chamber 36.
  • the inlet 35 communicates with an annular inlet chamber 40 the access of which to the outlet chamber 36 is controlled by the diaphragm 38 which coacts with a seating provided by the lower (as seen in FIG. 4) end of chamber 36.
  • the diaphragms 37, 38 both have diaphragm discs 41.
  • each support loading springs 42, 43 adjustable by adjusting nuts 44 and adjusting screws 45 respectively.
  • the springs 42, 43 are relatively heavy and relatively light springs respectively, allowing very accurate adjustment of the pressure loading of the diaphragms 37, 38.
  • the inlets 34, 35 are joined respectively to the return branch 2 (FIG. 2) leading from the outlet 5 and to the output of the priming pump 12, whilst the outlet chamber 36 is joined by the return branch 2 to the vapour separator 8.
  • the vapour separator 8 (FIG. 1) is of known form and comprises an inverted cone 46 connected at its apex to the return branch 2 and to the fuel inlet 9. A restricted vapour venting connection 47 at the top of the separator permits the return of vapour from the separator to the fuel tank (not shown).
  • the pressure relief valve in the chamber 3 (as shown in FIGS. 2 and 3) is set so that the loading on diaphragm 19 is equal to the predetermined additional pressure to be applied to the fuel to prevent or substantially reduce fuel vaporization in the components of the system shown in FIG. 1 due to engine temperature.
  • the fuel pressure in chamber 18 is equal to the low pressure necessary for effective atomisation of the fuel in the injector devices.
  • the pressure loading valve 7 ensures that the fuel pressure in the return branch 2 is sufficient to stop or substantially prevent vaporization in that branch. A pressure of the order of 10 lbs. per square inch is satisfactory for most conditions. If, due to overheating, vapour does form, it is separated out in the separator 8.
  • the diaphragm 19 determines the minimum fuel pressure in the supply branch 1 and the valve 7 ensures that a similar pressure exists in the return branch 2.
  • Fuel is metered to the injector devices 51 by the engine driven pump mechanism 11 acting in conjunction with the metering valve 15.
  • the pump mechanism adjusts fuel pressure in the supply branch with changes in engine speed and the metering valve 15 is controlled by engine air intake manifold vacuum to adjust fuel flow to the chamber 3 in dependence on engine loading.
  • the fuel flow divides between the injector devices 51 and the return branch 2 in dependence upon the setting of the restrictor rod 30, the restriction offered by the flow equalising restrictors 55 in the actual injector devices and the spring loading on diaphragm 37.
  • Pressure in the return branch is maintained by the valve 7 at the value necessary to stop or substantially prevent vaporization of fuel in the return branch under normal conditions of engine temperature.
  • a low pressure continuous fuel injection system for an internal combustion engine including a plurality of fuel injector devices, a fuel circulation conduit system having supply and return branches; means connecting said supply branch to said injector devices for supplying fuel thereto; engine driven fuel pressurising means connected in said supply branch to circulate fuel through said conduit system and to deliver fuel to said supply branch at a pressure which increases with the square of engine speed and has a predetermined minimum pressure value sufficient substantially to prevent vaporisation of fuel in said supply branch during operation of the said engine; said circulation conduit system also including variable area orifice metering valve device responsive to changes in engine loading to adjust fuel flow from said supply branch to said injector devices in dependence on engine loading; a fuel distribution chamber having first and second compartments, means connecting the first compartment to the said supply and return branches; the said fuel distribution chamber including a first fuel pressure setting device comprising a first closure member movable between a first position in which it closes communication between the first and second compartments and a second position in which it communicates the first compartment with the second compartment, and resilient loading means urging said
  • said first compartment includes an upstanding annular seating and wherein said first and second closure members are respective first and second resilient diaphragms; said first diaphragm having an an aperture therein and said first position the said first diaphragm being urged by the said resilient loading means against said annular seating with the said seating surrounding said diaphragm seating.
  • said fixed flow restrictor comprises a member defining an orifice and an elongated member extending through said orifice to define together with said orifice an annular passage, and wherein said elongated member has a cross-sectional area which changes along part of the length thereof, and means operable to adjust the position of said elongated member relative to said orifice to set the flow resistance provided by said annular passage to a selected value.
  • said engine driven fuel pressurising means comprises a feed pump, a pressurising impeller and a relief valve, said pressurising impeller having an output connected to said supply branch and an inlet connected to receive fuel from said feed pump, and said relief valve being connected to said pressurising impeller input to maintain the pressure of fuel fed by the feed pump to said pressurising impeller approximately at said predetermined minimum pressure value.
  • said pressurising impeller comprises a housing, a surface defined internally of the housing, an arcuate groove in said surface, a disc disposed adjacent said surface and mounted on an engine driven shaft for rotation therewith, said disc having spaced peripheral portions registering with said groove, and in which the arcuate groove has ends which communicate with the pressurising impeller device inlet and outlet respectively, said disc being rotatable to sweep fuel from said pressurising impeller device input along said arcuate groove at a velocity increasing with rotary speed of said engine driven shaft and to expel said swept fuel through said pressurising impeller device outlet at a pressure which increases with the square of the rotary speed of said disc.
  • said fuel metering device comprises a metering orifice and a valve member rotatable to vary the area of said metering orifice, a chamber containing a member movable in response to changes in air intake manifold vacuum of said engine, means coupling said movable member to a cam member having a cam surface engaged by a cam follower carried by said valve member whereby movement of said movable member causes said cam to rotate said valve memto change the area of said metering orifice in response to changes in engine loading represented by changes in said manifold vacuum.
  • outlet of said sec-0nd fuel pressure setting device is connected to the fuel inlet of a fuel vapour separator comprising a chamber having an upper vent outlet and a lower fuel outlet, said fuel inlet being connected to the constricted end of a funnel shaped member disposed within said chamber, and wherein the funnel shaped member has a mouth disposed adjacent to vent outlet of said chamber.
  • said fuel pressurising means comprises a housing containing a disc mounted on an engine driven shaft, and having spaced peripheral portions, said disc being located adjacent a groove defined within said housing with said spaced peripheral portions registering with said groove.
  • a feed pump connected to feed fuel to one end of said groove and the other end to effect a corresponding variation in area of said metering orifice; and a fuel vapour separator device comprising a funnel shaped member disposed in a chamber having a lower fuel inlet, a lower fuel outlet and an upper vapour vent, the funnel shaped member being located in the chamber with the constricted end of the funnel shaped member beneath the mouth thereof, the said constricted end of the funnel shaped member being connected to the said fuel inlet of said chamber and said groove being connected to said supply branch whereby fuel fed to the groove by said feed pump is swept around said groove by rotation of said disc and expelled from the said other end of the groove to said supply branch at a pressure increasing with the square of engine speed, a relief valve connected to the outlet of said feedf pump to maintain the pressure of fuel fed by the feed pump to the said one end of said arcuate groove approximately at said predetermined minimum pressure value; wherein said fuel metering valve device comprises a member movable in response to air intake manif
  • the fuel metering valve device has a said movable member comprising a piston slidable in a chamber exposed to changes in said manifold vacuum, means coupling said piston to a cam having a cam surface engaged by a cam follower carried by said rotary valve member whereby sliding movement of said piston causes movement of said cam to rotate the said rotary valve member.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
US575010A 1965-09-08 1966-08-25 Fuel injection systems Expired - Lifetime US3416504A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB38394/65A GB1162513A (en) 1965-09-08 1965-09-08 Fuel Injection Systems for Internal Combustion Engines.

Publications (1)

Publication Number Publication Date
US3416504A true US3416504A (en) 1968-12-17

Family

ID=10403191

Family Applications (1)

Application Number Title Priority Date Filing Date
US575010A Expired - Lifetime US3416504A (en) 1965-09-08 1966-08-25 Fuel injection systems

Country Status (8)

Country Link
US (1) US3416504A (enrdf_load_stackoverflow)
BE (1) BE686629A (enrdf_load_stackoverflow)
CH (1) CH451596A (enrdf_load_stackoverflow)
DE (1) DE1526538C3 (enrdf_load_stackoverflow)
GB (1) GB1162513A (enrdf_load_stackoverflow)
IL (1) IL26393A (enrdf_load_stackoverflow)
NL (1) NL6612677A (enrdf_load_stackoverflow)
SE (1) SE330461B (enrdf_load_stackoverflow)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4211201A (en) * 1977-05-04 1980-07-08 Toyota Jidosha Kogyo Kabushiki Kaisha Fuel supply apparatus for internal combustion engines
US4404944A (en) * 1980-08-07 1983-09-20 Nissan Motor Co., Ltd. Fuel supply system for an injection-type internal combustion engine
US5101793A (en) * 1990-10-30 1992-04-07 Sample Larry A Manually adjustable override for fuel injection regulators

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3222000A1 (de) * 1982-06-11 1983-12-15 Volkswagenwerk Ag, 3180 Wolfsburg Kraftstoffeinspritzeinrichtung

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2566012A (en) * 1949-10-15 1951-08-28 Bendix Aviat Corp Carburetor
US2895463A (en) * 1957-01-16 1959-07-21 Continental Motors Corp Fuel metering valve
US2898899A (en) * 1955-12-05 1959-08-11 Holley Carburetor Co Fuel control for spark ingition internal combustion engines
US3006329A (en) * 1959-04-06 1961-10-31 Acf Ind Inc Fuel injection system
US3285233A (en) * 1962-12-21 1966-11-15 Petrol Injection Ltd Fuel injection systems
US3311099A (en) * 1965-10-22 1967-03-28 Wallace E Beaber Fuel injection systems

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2566012A (en) * 1949-10-15 1951-08-28 Bendix Aviat Corp Carburetor
US2898899A (en) * 1955-12-05 1959-08-11 Holley Carburetor Co Fuel control for spark ingition internal combustion engines
US2895463A (en) * 1957-01-16 1959-07-21 Continental Motors Corp Fuel metering valve
US3006329A (en) * 1959-04-06 1961-10-31 Acf Ind Inc Fuel injection system
US3285233A (en) * 1962-12-21 1966-11-15 Petrol Injection Ltd Fuel injection systems
US3311099A (en) * 1965-10-22 1967-03-28 Wallace E Beaber Fuel injection systems

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4211201A (en) * 1977-05-04 1980-07-08 Toyota Jidosha Kogyo Kabushiki Kaisha Fuel supply apparatus for internal combustion engines
US4404944A (en) * 1980-08-07 1983-09-20 Nissan Motor Co., Ltd. Fuel supply system for an injection-type internal combustion engine
US5101793A (en) * 1990-10-30 1992-04-07 Sample Larry A Manually adjustable override for fuel injection regulators

Also Published As

Publication number Publication date
DE1526538B2 (de) 1973-09-13
BE686629A (enrdf_load_stackoverflow) 1967-02-15
DE1526538A1 (de) 1970-09-10
NL6612677A (enrdf_load_stackoverflow) 1967-03-09
IL26393A (en) 1970-03-22
CH451596A (de) 1968-05-15
GB1162513A (en) 1969-08-27
SE330461B (enrdf_load_stackoverflow) 1970-11-16
DE1526538C3 (de) 1974-04-04

Similar Documents

Publication Publication Date Title
CA2119560A1 (en) Method and apparatus for metering fluid
US3285233A (en) Fuel injection systems
US3416504A (en) Fuel injection systems
US3404872A (en) Charge forming apparatus
US3330541A (en) Fuel injector devices and systems
US4393844A (en) Liquid fuel pumping apparatus
JPH0368232B2 (enrdf_load_stackoverflow)
US4196708A (en) Engine systems
US3395682A (en) Fuel injection systems
US2481334A (en) Hydraulic governor
US4284047A (en) Apparatus for controlling the air-fuel quantity ratio in internal combustion engines
US3672339A (en) Fuel injection apparatus
US2447268A (en) Charge forming device
US4245470A (en) Device to control a jet engine
US3431900A (en) Fuel injection systems
US2566012A (en) Carburetor
US2873956A (en) Fuel injection control valve
US2552056A (en) Carburetor priming means
US1978660A (en) Carburetor
US2536556A (en) Liquid fuel supply system for internal-combustion prime movers
US2893712A (en) Fuel injection apparatus
US2871844A (en) Low pressure, continuous flow fuel injection system
US2598202A (en) Speed controlled fuel system
US4462365A (en) Apparatus for supplying fuel to an internal combustion engine
US2880790A (en) Starting fuel control for gas turbine engines