WO1987000578A1 - Injection directe de carburant par gas comprime - Google Patents

Injection directe de carburant par gas comprime Download PDF

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Publication number
WO1987000578A1
WO1987000578A1 PCT/AU1986/000203 AU8600203W WO8700578A1 WO 1987000578 A1 WO1987000578 A1 WO 1987000578A1 AU 8600203 W AU8600203 W AU 8600203W WO 8700578 A1 WO8700578 A1 WO 8700578A1
Authority
WO
WIPO (PCT)
Prior art keywords
fuel
pressure
gas
chamber
engine
Prior art date
Application number
PCT/AU1986/000203
Other languages
English (en)
Inventor
Michael Leonard Mckay
Steven Ross Ahern
Original Assignee
Orbital Engine Company Proprietary Limited
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 Orbital Engine Company Proprietary Limited filed Critical Orbital Engine Company Proprietary Limited
Priority to NL8620298A priority Critical patent/NL8620298A/nl
Priority to IN644/DEL/86A priority patent/IN167833B/en
Priority to KR1019870700241A priority patent/KR940001927B1/ko
Priority to BR8606798A priority patent/BR8606798A/pt
Priority to GB8706101A priority patent/GB2188369B/en
Publication of WO1987000578A1 publication Critical patent/WO1987000578A1/fr
Priority to SE8701143A priority patent/SE466864B/sv

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D3/00—Controlling low-pressure fuel injection, i.e. where the fuel-air mixture containing fuel thus injected will be substantially compressed by the compression stroke of the engine, by means other than controlling only an injection pump
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D7/00—Other fuel-injection control
    • F02D7/02—Controlling fuel injection where fuel is injected by compressed 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0635—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding
    • F02M51/0642—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding the armature having a valve attached thereto
    • F02M51/0653—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding the armature having a valve attached thereto the valve being an elongated body, e.g. a needle valve
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/08—Injectors peculiar thereto with means directly operating the valve needle specially for low-pressure fuel-injection
    • 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
    • F02M69/08—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by the fuel being carried by compressed air into main stream of combustion-air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/12—Other methods of operation
    • F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B61/00—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing
    • F02B61/04—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving propellers
    • F02B61/045—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving propellers for marine engines
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • This invention relates to the injection of etered quantities of fuel into the combustion chamber of an internal combustion engine.
  • the principal object of the present invention is to provide a method of control of the fuelling of an engine so that the position of the fuel cloud may be varied to assist in the more efficient combustion of the fuel.
  • a method of controlling fuel distribution in an internal combustion engine comprising directly injecting fuel into the combustion chamber through a nozzle under conditions so the fuel penetrates a first distance into the combustion chamber, and varying said conditions in response to the engine load demand being above a predetermined value to increase the distance of penetration of the fuel into the combustion chamber.
  • the pressure effecting delivery of the fuel through the nozzle may be increased in a stepwise manner at one or more selected levels of engine load demand or the pressure increases may be progressive over one or more ranges of engine speed or load to vary the degree of penetration of the fuel. More specifically there is provided a method of controlling fuel distribution in the combustion chamber of an internal combustion engine comprising combining a metered quantity of fuel delivered at delivery pressure and a gas mass, delivering the fuel-gas mixture so formed at a mixture delivery pressure through a nozzle into the combustion chamber, regulating the pressure differential between the fuel and gas mass to maintain a substantially uniform pressure differential over the engine load demand, and controlling the pressure of the fuel-gas mixture during delivery to the combustion chamber so said pressure is increased in response to the engine load demand above a predetermined value, whereby the extent of penetration of the fuel into the chamber is increased.
  • control of the fuel penetration is achieved by varying the fuel pressure with engine speed and consequently varying the gas pressure to maintain a steady pressure differential. Accordingly the variation of the fuel pressure will have the end result of varying the pressure available to deliver the fuel-gas mixture through the nozzle to the combustion chamber.
  • the increases in pressure are preferably effected at one or more selected engine speeds within the normal operating speed range, and it has been found that one increase in the mid-speed range is sufficient in many engine applications.
  • specific advantages arise from the regulations being based on varying the pressure of the fuel as the control function, and effecting a consequential variation int he gas pressure to maintain the selected pressure differential.
  • the gas is less viscous than a liquid fuel and so, in a regulation situation, the controlled gas pressure will not be as affected by flow rate variations through the pressure regulator. This results in the pressure differential being less sensitive to flow rate variation of either the fuel or gas.
  • This feature is of particular significance where the pumps providing the fuel and gas are engine driven and have outputs that are significantly speed related. Accordingly it is another object of the present invention to provide a fuel-gas regulation system that is particularly suitable for incorporation in a fuel injection system employing pressurised fuel and gas supplies.
  • fuel injection system for internal combustion engines wherein a metered quantity of fuel under pressure is delivered into a gas to form a fuel-gas charge, characterised in that the fuel pressure is regulated to a reselected value and the gas pressure is regulated relative to the fuel pressure to maintain a predetermined pressure differential between the fuel and gas during metering of th fuel.
  • the regulated pressure of the fuel i selectable between at least two predetermined values.
  • the variation in the regulated fuel pressure is effected at a selected speed, within the normal operating speed range of the engine, and the variation is preferably an increase as the engine speed exceeds the selected value. A corresponding decrease is effected as the engine speed falls below that selected value.
  • the fuel pressure is regulated to a preselected value relative to atmospheric pressure.
  • a fuel pressure regulator set to provide a predetermined fuel output pressure, and means adapted to vary said pressure a predetermined amount in response to a selected engine condition.
  • the predetermined fuel output pressure is set by a resilient means prestressed to a set degree, and the means to vary the output pressure adjust the degree of stress on the resilient means.
  • the resilient means is a spring tensioned or compressed to a degree to provide a load necessary to set the required base fuel pressure. The degree of compression or tension of the spring is increased to increase the fuel output pressure upon the engine reaching a predetermined load and is subsequently reduced upon the engine speed falling below the selected load.
  • Figure 1 is an axial section view of a two stroke cycle engine having a direct in-cylinder fuel injection system.
  • Figure 2 is an elevational view, partly in section of a fuel metering and injection unit suitable for use with the engine shown in Figure 1.
  • Figure 3 is a sectional view of a combined fuel and air pressure regulator suitable for use with the metering and injection unit shown in Figure 2, shown in conjunction diagrammatically with other components of a fuel injection system.
  • the engine 109 is a single cylinder two stroke cycle engine, of generally conventional construction, having a cylinder 110, crankcase 111 and piston 112 that reciprocates in the cylinder 110.
  • the piston 112 is coupled by the connecting rod 113 to the crankshaft 114.
  • the crankcase is provided with air induction ports 115, incorporating conventional reed valves 119 and three transfer passages 116 (only one shown) communicate the crankcase with respective transfer ports, two of which are shown at 117 and 118, the third being the equivalent to 117 on the opposite side of port 118.
  • the transfer ports are each formed in the wall of the cylinder 110 with their respective upper edge located in the same diametral plane of the cylinder.
  • An exhaust port 120 is formed in the wall of the cylinder generally opposite the central transfer port 118.
  • the detachable cylinder head 121 has a combustion cavity 122 into which the spark plug 123 projects, the cavity 122 is located substantially symmetrically with respect to the axis of the cylinder, and the spark plug is located on that axis.
  • the fuel injector 124 is located in the wall of the cylinder 110 between the transfer ports and the cylinder head. In the configuration shown the injection nozzle 124 is directly above the central transfer port 118.
  • the injector 124 is an integral part of a fuel metering and injection system whereby fuel entrained in air is injected directly into the combustion chamber of the engine by the pressure of the air supply.
  • a fuel metering and injection unit is illustrated in Figure 2 of the drawings which is representative of a type of metering and injection unit that the fuel and air pressure regulating system of the present invention is applicable to.
  • the fuel metering and injection unit in Figure 2 incorporates a suitable metering device 130, such as an automotive type throttle body injector, coupled to an injector body 131 having a holding chamber 132 therein.
  • Fuel is delivered from a fuel pump (not shown) through fuel inlet port 133 to the metering device 130 which meters an amount of fuel into the holding chamber 132 in accordance with the engine fuel demand. Excess fuel supplied to the metering device is returned to a fuel reservoir via fuel return port 134.
  • the particular construction of the fuel metering device 130 is not critical to the present invention and any suitable device may be used.
  • the holding chamber 132 is pressurised by air supplied supplied through an air inlet port 145 in the body 131.
  • An injection valve 143 is actuated to permit the pressurised air to discharge the metered amount of fuel from the chamber 132 through injector nozzle 142 into a combustion chamber of the engine.
  • Injection valve 143 of the injector nozzle is of the poppet valve construction opening inwardly to the combustion chamber, that is, outwardly from the holding chamber.
  • the injection valve 143 is coupled, via a valve stem 144, which passes through the holding chamber 132, to the armature 141 of solenoid 147 located within the injector body 131.
  • the valve 143 is biased into the closed position by the disc spring 140 and is opened by energising the solenoid 147.
  • Energising of the solenoid 147 is controlled in time relation to the engine cycle to effect delivery of the fuel from the holding chamber 132 to the engine combustion chamber.
  • the fuel is delivered into the holding chamber 132 by the metering device 130 against the pressure of the air existing in the chamber. Accordingly, the difference in pressure between the fuel supply at the metering device and the air in the holding chamber is relevant to the quantity of fuel that will be delivered into the holding chamber. In view of the need for accuracy in the fuel metering, both from the aspect of fuel economy and exhaust emission control, it is important to effectively control this presure difference.
  • Figure 3 illustrates a fuel injection system incorporating a combined fuel and air regulator which is suitable for use with the fuel metering and injection unit as described above with reference to Figure 2.
  • the regulator hereinafter described with reference to Figure 3 may be used in other fuel metering and injection systems and is not limited to use in the system described with reference to Figure 2.
  • the fuel injection system comprises a fuel metering and injecting unit 5 to which air and fuel are provided from the compressor 2 and fuel reservoir 6 respectively via the regulator 10.
  • the fuel is delivered from the reservoir 6 by the low pressure lift pump 3 to the high pressure pump 7 via the through passage 18 in the regulator 10.
  • the regulator 10 comprises a fuel pressure regulation portion 9 and an air pressure regulation portion 11 incorporated in an integral construction.
  • the fuel regulation chamber 12 has one wall thereof formed by the flexible diaphragm 13 which is secured around its marginal perimeter.
  • the diaphragm 13 has secured thereto a valve element 14 which co-operates with the port 15 provided in the wall 17 of the fuel regulation chamber opposite the diaphragm 13.
  • the port 15 communicates with the low pressure fuel passage 18 which in turn communicates with the delivery side of the low pressure pump 3 and the suction side of the high pressure pump 7.
  • the high pressure fuel inlet passage 20 communicates the fuel regulation chamber 12 with the delivery side of the high pressure fuel pump 7.
  • the one way valve 21 between the passage 18 and the chamber 12 is only lightly pre-loaded, so that during start up the lower pressure fuel may flow from the passage 18 through the fuel chamber 12 to purge the high pressure fuel circuit and injector 5 of air.
  • the diaphragm 13 is located by the spring 25 so as to normally position the valve 14 to close the port 15.
  • the spring backing plate 24 normally abuts the stop 19 provided on the end wall 26 of the regulator body.
  • the spring backing plate 24 is attached to the diaphragm 27 which divides the control cavity 28.
  • the portion 29 of the control cavity on the spring side of the diaphragm 27 is subject to atmospheric air via the port 22 whilst the portion 30 on the opposite side of the diaphragm 27 may be selectively communicated with the regulated air source via the port 31 and solenoid valve 49.
  • the diaphragm 27 and the spring backing plate 24 will be moved to the right as seen in the drawing, to apply further compression to the spring 25.
  • the extent of movement of the backing plate 24 to the right is limited by the edge band 32 of the backing plate 24 contacting the annular should 33 on the regulator body.
  • a spring (not shown) may be provided between the backing plate 24 and the end wall 26 to partially counteract the spring 25.
  • the actuation of the solenoid valve 49, to increase in fuel delivery pressure may be effected by a suitable engine speed sensor being provided to activate a switch when the engine speed reaches a selected value.
  • the switch when activated energises the solenoid valve 49 so that air from the regulated air supply to the injector unit 5 is admitted to the portion 30 of the control cavity 28.
  • the application of pressure by this air to the diaphragm 27 will move the backing plate 24 so that the edge band 32 will abut the shoulder 33, thus increasing the load applied by the spring 25 to the diaphragm 13 by a set amount.
  • chamber 37 and the action of the spring 45 together is sufficient to overcome the force created by the fuel presure in the chamber 36 on the diaphragm 38. Accordingly it will be appreciated that the air pressure will always be less than the fuel pressure by the amount represented by the force applied to the diaphragm 38 by the spring 45.
  • the regulator as above described will in use regulate, relative to atmospheric pressure, the pressure of the fuel supplied to a fuel injection unit 5 by the pump 7, and regulate relative to the fuel pressure, the pressure of the air the air supply to the fuel injector unit, so that during operation of the fuel injection unit there is a predetermined pressure differential between the fuel and air supplies.
  • the regulated fuel pressure can be increased by a preset amount, and the air pressure will consequently be correspondingly increased by the same amount so that the same pressure differential is maintained between the fuel and the air supplies to the fuel metering and injection unit.
  • the fuel spray penetration may thus be altered without other adjustments or corrections to the metering of the fuel.
  • the degree of change in the pressure of the air provided to effect delivery of the fuel-air mixture to the combustion chamber is selected by experiment for each engine depending on the geometry of the engine, and the required degree of fuel penetration with varying load or speed conditions.
  • the air pressure is increased from 250 to 500 KPA at an engine speed of 2500 RPM which is in the mid-speed range of the engine.
  • the above described fuel pressure regulator, and the integrated fuel and air pressure differential regulator may be used in combination with the fuel metering and delivery system described with reference to Figure 2 and as
  • the operation of the solenoid valve 49 and control cavity 28 to increase the fuel pressure may be adapted to provide more than one increase in the regulated fuel pressure.
  • an electrically operated device may be used to effect the adjustment.
  • the current supplied to the device may be varied to effect the adjustment of the movement of the diaphragm.
  • the fuel pressure regulation portion 9, of the composite fuel and air pressure regulation portion 11 so far described with reference to Figure 3, nay be constructed as an individual fuel pressure regulator wherein the regulated pressure is variable during operation.
  • the desirability of an adjustable injection pressure has previously been discussed as a means of varying the penetration of the fuel into the combustion chamber, and this is equally applicable to injection system where liquid fuel alone is injected as to systems wherein liquid fuel is entrained in air or other suitable gas. Accordingly the fuel pressure regulator portion 9 may be used as a variable pressure regulator in injection systems injecting liquid alone.
  • the fuel chamber 12 is in communication, via the passage 35, with the chamber 36 in the air regulation portion 11 and is separated from the air pressure chamber 37 by the diaphragm 38.
  • the air pressure chamber 37 is in communication with the air from the compressor 2 via the passage 39, and air outlet passage 40 leads from chamber 37 to the injector unit 5.
  • the diaphragm 38 carries the valve 41 which co-operates with the port 42 which communicates with the air bypass passage 43.
  • the spring 45 applies presure to the diaphragm 38 to normally hold the valve 41 open. Accordingly the valve 41 will open the port 42 when the air pressure in the disclosed in our co-pending Australian Patent Application No. 32132/84 and, may be used in the fuelling of a two stroke cycle engine as described in our co-pending Australian Patent Application Nos. PH01559, PH1991 and PH3344 entitled "Improvements Relating to Direct Fuel

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

Dans un moteur à allumage par bougie, du carburant est injecté directement dans le volume du cylindre. Afin d'obtenir une meilleure efficacité de la combustion et une réduction des émissions la position du nuage de carburant à l'intérieur du volume du cylindre est amenée à varier avec la charge du moteur par commande de la variation de la pression d'injection du carburant. La présente invention décrit plus particulièrement un procédé et un appareil destinés à l'injection du carburant par air comprimé, la position du nuage de carburant à l'intérieur du volume de cylindre étant réglée par commande jointe de la pression d'injection du carburant et de l'air. La présente invention trouve des applications en particulier dans les moteurs à deux temps.
PCT/AU1986/000203 1985-07-19 1986-07-18 Injection directe de carburant par gas comprime WO1987000578A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
NL8620298A NL8620298A (nl) 1985-07-19 1986-07-18 Directe brandstofinspuiting door middel van samengeperst gas.
IN644/DEL/86A IN167833B (fr) 1985-07-19 1986-07-18
KR1019870700241A KR940001927B1 (ko) 1985-07-19 1986-07-18 내연기관 연료분사 방법
BR8606798A BR8606798A (pt) 1985-07-19 1986-07-18 Aperfeicoamentos relativos a injecao de combustivel em motores de combustao interna
GB8706101A GB2188369B (en) 1985-07-19 1986-07-18 Improvements relating to fuel injection to internal combustion engines
SE8701143A SE466864B (sv) 1985-07-19 1987-03-19 Foerfarande och anordning foer braensleinsprutning med hjaelp av tryckluft vid foerbraenningsmotor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AUPH156085 1985-07-19
AUPH1560 1985-07-19

Publications (1)

Publication Number Publication Date
WO1987000578A1 true WO1987000578A1 (fr) 1987-01-29

Family

ID=3771186

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AU1986/000203 WO1987000578A1 (fr) 1985-07-19 1986-07-18 Injection directe de carburant par gas comprime

Country Status (18)

Country Link
JP (1) JP2669820B2 (fr)
KR (1) KR940001927B1 (fr)
CN (1) CN1015277B (fr)
AU (1) AU594357B2 (fr)
BE (1) BE905149A (fr)
BR (1) BR8606798A (fr)
CA (1) CA1271948A (fr)
DE (1) DE3690389C2 (fr)
ES (1) ES2000700A6 (fr)
FR (1) FR2585079B1 (fr)
GB (1) GB2188369B (fr)
IN (1) IN167833B (fr)
IT (1) IT1197786B (fr)
MX (1) MX174369B (fr)
NL (1) NL8620298A (fr)
PH (1) PH26109A (fr)
SE (1) SE466864B (fr)
WO (1) WO1987000578A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0392550A2 (fr) * 1989-04-13 1990-10-17 Yamaha Hatsudoki Kabushiki Kaisha Moteur à combustion interne et procédé pour commander son injection de combustible
EP0404347A1 (fr) * 1989-06-21 1990-12-27 General Motors Corporation Regulateur de pression
US5062395A (en) * 1988-07-01 1991-11-05 Toyota Jidosha Kabushiki Kaisha Two-stroke internal combustion engine
EP0609311A1 (fr) * 1991-10-21 1994-08-10 Orbital Engine Company (Australia) Pty. Ltd. Procede et appareil permettant de mesurer des carburants
US6092502A (en) * 1997-02-12 2000-07-25 Hitachi, Ltd. Direct injection engine controller

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1149321A (en) * 1912-03-30 1915-08-10 Charles Whiting Baker Method of and apparatus for delivering liquid fuel to oil-engines.
US1166937A (en) * 1912-06-01 1916-01-04 Busch Sulzer Bros Diesel Engine Co Means for regulating combustion-engines.
US2753217A (en) * 1952-11-08 1956-07-03 Texas Co Fuel injection nozzle for internal combustion engine
JPS59206672A (ja) * 1983-05-11 1984-11-22 Toyota Motor Corp 内燃機関の燃料噴射弁

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE867327C (de) * 1940-10-31 1953-02-16 Nsu Werke Ag Gemischverdichtender Zweitaktmotor mit innerer Gemischbildung und Fremdzuendung
DE916365C (de) * 1943-02-06 1954-08-09 Daimler Benz Ag Druckluft-Einspritzbrennkraftmaschine mit Fremdzuendung
JPS58155269A (ja) * 1981-12-31 1983-09-14 オ−ビタル・エンジン・カンパニイ・プロプライエタリ・リミテイツド エンジンにガス圧により液体燃料を供給する方法及びその装置
JPS5960069A (ja) * 1982-09-30 1984-04-05 Mitsubishi Motors Corp エンジンの燃料供給装置
US4685432A (en) * 1983-10-31 1987-08-11 Kabushiki Kaisha Toyota Chuo Kenkyusho Method and device for forming mixture gas in direct injection type internal combustion engine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1149321A (en) * 1912-03-30 1915-08-10 Charles Whiting Baker Method of and apparatus for delivering liquid fuel to oil-engines.
US1166937A (en) * 1912-06-01 1916-01-04 Busch Sulzer Bros Diesel Engine Co Means for regulating combustion-engines.
US2753217A (en) * 1952-11-08 1956-07-03 Texas Co Fuel injection nozzle for internal combustion engine
JPS59206672A (ja) * 1983-05-11 1984-11-22 Toyota Motor Corp 内燃機関の燃料噴射弁

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5062395A (en) * 1988-07-01 1991-11-05 Toyota Jidosha Kabushiki Kaisha Two-stroke internal combustion engine
EP0392550A2 (fr) * 1989-04-13 1990-10-17 Yamaha Hatsudoki Kabushiki Kaisha Moteur à combustion interne et procédé pour commander son injection de combustible
EP0392550A3 (fr) * 1989-04-13 1991-05-08 Yamaha Hatsudoki Kabushiki Kaisha Moteur à combustion interne et procédé pour commander son injection de combustible
EP0404347A1 (fr) * 1989-06-21 1990-12-27 General Motors Corporation Regulateur de pression
EP0609311A1 (fr) * 1991-10-21 1994-08-10 Orbital Engine Company (Australia) Pty. Ltd. Procede et appareil permettant de mesurer des carburants
EP0609311A4 (fr) * 1991-10-21 1994-08-31 Orbital Engine Company (Australia) Pty. Ltd.
US6092502A (en) * 1997-02-12 2000-07-25 Hitachi, Ltd. Direct injection engine controller

Also Published As

Publication number Publication date
SE8701143D0 (sv) 1987-03-19
MX174369B (es) 1994-05-11
KR880700153A (ko) 1988-02-20
IN167833B (fr) 1990-12-29
AU594357B2 (en) 1990-03-08
JPS63500324A (ja) 1988-02-04
DE3690389C2 (de) 1996-08-29
PH26109A (en) 1992-02-06
GB2188369A (en) 1987-09-30
ES2000700A6 (es) 1988-03-16
IT8621181A1 (it) 1988-01-18
GB8706101D0 (en) 1987-04-15
SE466864B (sv) 1992-04-13
FR2585079B1 (fr) 1991-06-21
IT8621181A0 (it) 1986-07-18
GB2188369B (en) 1990-02-21
SE8701143L (sv) 1987-03-19
DE3690389T1 (fr) 1987-07-16
NL8620298A (nl) 1987-06-01
BR8606798A (pt) 1987-10-13
AU6147686A (en) 1987-02-10
CN1015277B (zh) 1992-01-01
CA1271948A (fr) 1990-07-24
JP2669820B2 (ja) 1997-10-29
KR940001927B1 (ko) 1994-03-11
BE905149A (fr) 1986-11-17
CN86105113A (zh) 1987-03-18
FR2585079A1 (fr) 1987-01-23
IT1197786B (it) 1988-12-06

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