US3680535A - Fuel injection system for combustion engines - Google Patents

Fuel injection system for combustion engines Download PDF

Info

Publication number
US3680535A
US3680535A US81221A US3680535DA US3680535A US 3680535 A US3680535 A US 3680535A US 81221 A US81221 A US 81221A US 3680535D A US3680535D A US 3680535DA US 3680535 A US3680535 A US 3680535A
Authority
US
United States
Prior art keywords
fuel
pressure
injection system
valve
control 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
US81221A
Other languages
English (en)
Inventor
Konrad Eckert
Heinrich Knapp
Reinhard Schwartz
Gregor Schuster
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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
Priority claimed from DE19691960144 external-priority patent/DE1960144C/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Application granted granted Critical
Publication of US3680535A publication Critical patent/US3680535A/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
    • F02M69/16—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
    • F02M69/22—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 the device comprising a member movably mounted in the air intake conduit and displaced according to the quantity of air admitted to the engine
    • 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
    • F02M69/30—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by means for facilitating the starting-up or idling of engines or by means for enriching fuel charge, e.g. below operational temperatures or upon high power demand of engines
    • F02M69/36—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by means for facilitating the starting-up or idling of engines or by means for enriching fuel charge, e.g. below operational temperatures or upon high power demand of engines having an enrichment mechanism modifying fuel flow to injectors, e.g. by acting on the fuel metering device or on the valves throttling fuel passages to injection nozzles or overflow passages
    • F02M69/38—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by means for facilitating the starting-up or idling of engines or by means for enriching fuel charge, e.g. below operational temperatures or upon high power demand of engines having an enrichment mechanism modifying fuel flow to injectors, e.g. by acting on the fuel metering device or on the valves throttling fuel passages to injection nozzles or overflow passages using fuel pressure, e.g. by varying fuel pressure in the control chambers of the fuel metering device
    • F02M69/386—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by means for facilitating the starting-up or idling of engines or by means for enriching fuel charge, e.g. below operational temperatures or upon high power demand of engines having an enrichment mechanism modifying fuel flow to injectors, e.g. by acting on the fuel metering device or on the valves throttling fuel passages to injection nozzles or overflow passages using fuel pressure, e.g. by varying fuel pressure in the control chambers of the fuel metering device variably controlling the pressure of the fuel by-passing the metering valves, e.g. by valves responsive to signals of temperature or oxygen sensors

Definitions

  • pressurecontrol valve may be sub ect to a spring bias which is varied by a surface cam in response to throttle posi- [56] References cued tion and to pressure downstream of the throttle in the UNITED STATES PATENTS suction ctluct.
  • the invention relates to a fuel-injection system for an external-ignition combustion engine operating with compression of the fuel mixture and continuous injec tion into the suction duct.
  • the spring must be comparatively long and weak in order to provide under normal operating conditions a substantially constant return force, but this, on the other hand, requires the displacement for varying the force of the spring to be correspondingly large.
  • the size of the arrangement becomes correspondingly large even at small energy levels.
  • the transmission of the engine characteristic to the spring requires complicated mechanical constructions.
  • At least one pressure control valve is provided downstream of the control member for varying the liquid pressure of the return force in response to operating characteristics of the engine.
  • Such an arrangement is advantageous in that the variation of the liquid pressure does not have to occur in the vicinity of the throttle but can be translated to any desired point by means of conduits. If it is desired to control in dependence on throttle position, the pressure control valve can be positioned close to the throttle without the latter having to be close to the sensor, which could lead to undesired aerodynamic interaction between these two units. Thus, it becomes possible to place the sensor with the measuring valve close to the air filter, which is practical in view of their appreciable size, whereas the throttle can be located immediately in front of the main part of the suction duct, from which connections are branched off to the cylinders. A further advantage is the incompressibility of the liquid, which makes for a more exact control.
  • the movable member is coupled at least indirectly to the movable member or slider of the fuel valve, the slider operating in a cylinder which is connected to the fuel line via a channel having a restriction provided therein. This damps the control movements of the slider and provides more uniform engine operation.
  • the liquid pressure is controlled in response to throttle position and/or suction duct pressure downstream of the throttle and/or at least one temperature characteristic.
  • a twoor three-dimensional cam or electric circuit may serve to transmit such characteristics to the fuel valve.
  • the liquid pressure may be derived from the fuel supplied to the fuel valve, preferably from a point longitudinally spaced therefrom.
  • -a pressure-reducing valve may be inserted between the fuel valve and the point in question, thereby providing a pair of hydraulic circuits, one for measuring and one for the return function.
  • a pressure fluctuation in one circuit, e.g. owing to fuel flow, then has little influence on the precision of the control action of the other circuit.
  • FIG. 1 shows an embodiment of the entire fuel injection system
  • FIGS. 2, 3 and 4 show different embodiments of pressure control valves
  • FIG. 5 shows the arrangement of a pressure-reducing valve in the fuel circuit
  • FIG. 6 shows an hydraulic damping means for the moveble member of the measuring valve
  • FIG. 7 is a section taken on line VII-VII of FIG. 8 through a pressure-reducing valve operating with a temperature-responsive member which simultaneously controls a bypass of the suction duct;
  • FIG. 8 is a section taken on line VIII-VIII of FIG. 7.
  • Sensor 4 immediately controls a measuring distributor valve 8.
  • an arm 10 attached thereto and pivoted with a minimum of friction on a pin 9.
  • arm 10 is a boss 11 for controlling the movable valve member or slider 12 of measuring valve 8.
  • the end face 13 of slider 12 remote from boss 11 is subject to the pressure of a liquid serving as a return force for the sensor 4.
  • the inoperative position of arm 10 is defined by an adjusting screw 14.
  • Fuel is supplied by a fuel pump 16 driven by an electric motor 17 and drawing fuel from a container 18 and supplying it through a fuel line 19 to measuring valve 8. From line 19 there branches off a return line 20 having a pressure-limiting valve 21 provided therein. The fuel flows from line 19 into a channel 22 in the housing of measuring valve 8. Channel 22 ends in an annular notch 220 provided in the housing and from which borings 22b lead to a cylinder 23 having a slider 12 fitting tightly therein. Borings 22b terminate at a point of cylinder 23 at which slider 12 has a peripheral notch 24 which is therefore connected without any intermediate restriction to annular notch 22a. Notch 24 partially overlaps a pair of control slots 25 to a greater or lesser extent depending on the position of slider 12.
  • Diaphragm 29 is biased by a spring 31, the force of which is adjustable in response to a control efl'ect derived in dependence on engine operation.
  • a surface carn 32 which is rotatable jointly with throttle 7 and axially displaceable in dependence on he degree of suction or subpressure downstream of throttle 7 in the suction duct;
  • Surface cam 32 is axially displaceable on the shaft 33 of throttle 7, which is arbitrarily adjustable with the aid of a bar 34. Rotation of shaft 33 is transferred by an angular catch member 35 to surface cam 32, which is journaled at one end thereof on a diaphragm 36 of a suction chamber 37. Chamber 37 is connected via a line 38 to a point in the suction duct downstream of the throttle. If sufficient subpressure is present, cam 32 is displaced axially by diaphragm 36 against the force of a return spring 39. The cam surface is sensed by a pin 40, the movement of which is transferred by a spring disc 41 on spring 31, the bias of which determines the pressure for the return force on sensor 4.
  • Branching ofi from line 27 is a further line 67 connecting with a second pressure control valve 68, from which it is returned without pressure via a line 69 to fuel container 18.
  • This valve controls the pressure for the return force of slider 12 and sensor 4 in dependence on engine temperature and comprises a flat-seat valve 70, the rate of flow of which is controlled by a diaphragm 71, which is biased in the closing direction by a spring 72.
  • the fuel therefore flows through line 67 and valve 70 into a space 73 and thence without pressure via return line 69 to container 18.
  • Container 18 is subject to atmospheric pressure and approximately the same pressure is therefore present also in space 73.
  • the space 74 separated from space 73 by diaphragm 71 and having spring 72 mounted therein forms part of a bypass 75, 75a for the throttle of the suction duct and of which only the junctions with the suction duct and with valve 68 have been shown.
  • a slider 76 for controlling the bypass area and also serving as a spring washer for spring 72.
  • Slider 76 is displaced by a temperature-responsive member, such as a thermalexpansion device, 78 causing spring 72 to be less compressed and bypass 75, 75a to be more open when the engine is cold than when it is warm. Therefore, in a cold engine more liquid flows through valve 70, the liquid pressure causing the return force to be correspondingly lower and the fuel-to-air ratio of the injected mixture higher.
  • a temperature-responsive member such as a thermalexpansion device
  • pump 16 With the engine running, pump 16 is driven by motor 17 to draw fuel from container 18 and supply it via line 19 to measuring valve 8. Simultaneously herewith, the engine draws air through suction duct 3, 5, 6 and causes sensor 4 to be deflected from its inoperative position.
  • slider 12 is displaced by arm and uncovers a larger area of control slots 25.
  • the quantity of fuel supplied to the engine therefore varies in dependence on the control effect derived from sensor 4. From annular notch 24 the remaining fuel flows to the terminal side of slider 12 and therefrom to pressure control valves 28 and 68.
  • the direct coupling of sensor 4 with slider 12 results in a constant fuel-to-air ratio if the characteristics of these two members are sufficiently linear, which is the desired type of operation.
  • the fuel-to-air ratio would then be constant over the entire operating range of the engine. As was indicated above, however, it is desirable to make the fuel mixture richer or thinner according to the section of the operating range of the engine. This is achieved, according to the invention, by varying of the return force acting on sensor 4.
  • pressure control valve 68 causes an enrichment of the fuel mixture, since the pressure from which the return force is derived is now lower. Owing to the fact that a portion of the air flows through bypass 75, 75a, sensor 4 is deflected more than what corresponds to the throttle position, so that already on account of this deflection a greater amount of fuel is measured ofi.
  • the pressure of the fuel acting on end face 13 of slider 12 and causing the return force on sensor 4 is therefore maintained inherently constant and is varied only in dependence on engine characteristics, such as in the embodiment shown, the position of the throttle, i.e. in dependence on the load, as well as the subpressure in the suction duct, i.e. in dependence on the rpm.
  • FIG. 2 shows the portion of the system comprising the pressure control valve.
  • the bias of spring 31 of control valve 28 is controlled by a cam 43, which is displaceable only axially in response to the pressure obtaining downstream of the throttle in the suction duct.
  • cam 43 is mounted on rollers 44.
  • the control movement is transferred in this case also to spring washer 41 by a pin 40.
  • the throttle therefore is now in no way coupled to the cam.
  • the adjustment of the bias of spring 31 and therefore the return force on sensor 4 is therefore dependent on rpm and load.
  • pin 40 is controlled by a cam 46 which is mounted on shaft 33 of throttle 7, whereby upon shaft 33 being rotated by operation of bar 34, pin 40 is displaced by cam 46.
  • cam 46 which is mounted on shaft 33 of throttle 7, whereby upon shaft 33 being rotated by operation of bar 34, pin 40 is displaced by cam 46.
  • the bias of spring 31 is varied by a surface cam 32, just as in FIG. 1.
  • a surface cam 32 there is provided in diaphragm 29' an aperture 48, through which fuel can flow from line 27 and the space 49 delimited by diaphragm 29 into the space 50 in which spring 31 is mounted and from there via line 30 back to container 18.
  • This causes the pressure of container 18 to be present on both sides of diaphragm 29, whereby a possible fluctuation in the pressure of the fuel container has no control effect on the diaphragm.
  • FIG. 5 embodiment of the measuring valve 8 in channel section 22c a pressure reducinG valve 52 shown as a simple diaphragm valve, the diaphragm 53 of which is subject on one side to the supplied fuel and on the other side to a spring 54 in combination with the atmospheric pressure entering through an aperture 55.
  • a pressure reducinG valve 52 shown as a simple diaphragm valve, the diaphragm 53 of which is subject on one side to the supplied fuel and on the other side to a spring 54 in combination with the atmospheric pressure entering through an aperture 55.
  • FIG. 6 shows an embodiment 8" of the measuring valve in which the movement of slider 12" and therefore also that of sensor 4 is braked and damped by means of a disc 57 placed on the end face of slider 12".
  • slider 12" extends with its end face 13 into a cylindrical space 58 of approximately the same diameter as disc 57 and which is divided thereby into spaces 58a and 58b connected with each other by means of damping borings 23a and 60 to channel 220. Since the surface of disc 57, which is subject to the fuel pressure in space 58a, is larger than the surface facing space 58b, borings 23a and 60 must be proportioned to have equal damping effects in both directions of slider 12".
  • pressure control valves 28 and 68 of FIG. 1 have been constructionally integrated into a pressure control system 28".
  • spring 31' can be controlled by means of a surface cam 32'.
  • a thermal expansion regulator 62 for controlling spring 31'.
  • Regulator 62 acts via slider 63 on one arm of a twoarmed lever 64, the pivot point 64a of which is coupled to spring 31', and the other arm of which is in engagement with surface cam 32'.
  • Lever 64 is guided by means of a link 65 attaching it to the housing.
  • Slider also controls an idling channel 66 which, similarly to FIG. 1, connects a point upstream of the throttle in the suction duct with a point downstream thereof. With increasing temperature, slider 63 is pushed towards a position in which the bias of spring 31' and therefore also the return force on sensor 4 increases.
  • the invention can be used in any type of system where a suction duct draws in an amount of air, to which there is to be admixed a corresponding amount of a liquid, for instance, in chemical apparatus, gasoline heating systems and power turbines.
  • a fuel injection system for an extemal-ignition combustion engine operating on fuel injected into the suction duct and including an arbitrarily operable butterfly valve disposed in said suction duct
  • said system being of the known type that includes (a) a fuel valve for metering the fuel quantities supplied to said engine, (b) a sensor member forming part of an air sensor means and being positioned in said suction duct spaced from said butterfly valve, said sensor member being movable by and as a function of the air flowing in said suction duct, (c) arm means forming part of said air sensor means and being attached to said sensor member and engaging said fuel valve for transmitting the motion of said sensor member to said fuel valve to ensure the metering of fuel quantities proportionate to the air quantities flowing in said suction duct and (d) means for applying a substantially constant return force to said sensor member, the improvement comprising A.
  • a movable member being in engagement with said air sensor means and following the movements thereof and B.
  • means including a pressure line, for continuously supplying liquid under constant pressure to said movable member for urging the latter against said air sensor means with a constant force having a magnitude independent from the position of said air sensor means and the position of said movable member, said means for continuously supplying liquid under constant pressure and said movable member constituting said means for applying a substantially constant return force to said sensor member.
  • a fuel-injection system accordinG to claim 1, comprising at least one pressure control valve responsive to an engine operating characteristic for controlling the pressure of said liquid.
  • a fuel-injection system in which said pressure control valve is disposed in said pressure line downstream of said movable member.
  • a fuel-injection system in which said movable member is coupled to said fuel valve.
  • a fuel-injection system in which said movable member comprises a slider operating in a cylinder in a fluid-tight manner, said cylinder 6.
  • a fuel-injection system according to claim 2, comprising means for controlling the pressure of said pressure control valve in response to deflection of said sensor-member.
  • a fuel-injection system comprising means for controlling the pressure of said pressure control valve in response to the pressure in said suction duct downstream of said sensor member.
  • a fuel-injection system comprising means for controlling the pressure of said pressure control valve in response to at least one temperature characteristic of said engine.
  • a fuel-injection system comprising a cam movable in response to an engine operating characteristic to control said pressure control valve.
  • a fuel-injection system comprising a surface cam movable in response to an engine operating characteristic for controlling said pressure control valve.
  • a fuel-injection system comprising electric circuit means for transmitting an engine operating characteristic to said pressure control valve.
  • a fuel-injection system comprising means for supplying fuel from said fuel valve as the liquid to said pressure line.
  • a fuel-injection system in which said movable member responds to fuel pressure in said pressure line at a point spaced in the direction of flow from said fuel valve.
  • a fuel-injection system in which a pressure-reducing means is provided between said fuel valve and said point.
  • said movable member is a slider movable in a cylinder of said fuel valve and having an annular notch cooperating with control slots provided in said cylinder for measuring off fuel, said slider having an end face extending into a chamber to respond to said liquid pressure and a disc on said end face for damping movements of said slider.
  • a fuel-injection system in which spaces are prOvided on both sides of said disc connected via individual restriction channels with said pressure line.
  • a fuel-injection system in which said pressure control valve is a flat-seat valve having a biasing spring, said biasing spring being responsive to an engine operating characteristic for varying the bias thereof.
  • a fuel-injection system in which the movable valve member of said pressure control valve is a diaphragm.
  • a fuel-injection system comprising: a bypass to said suction duct around said sensor member, a temperature-responsive control element coupled to a pressure control valve and to a closure member inserted in said bypass for closing the same in response to the normal operating temperature of said engine.
  • a fuel injection system comprising 9 10 a first pressure control valve responsive to the posiwith said first pressure control valve and respontion of said arbitrarily adjustable throttle member sive t th ng n t p ratur said first and said and to the pressure downstream thereof in said Second Pressure. Valves y the liquid suction duct and pressure generating said return force. a second pressure control valve connected parallel 5

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Control Of The Air-Fuel Ratio Of Carburetors (AREA)
  • Control Of Fluid Pressure (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
US81221A 1969-12-01 1970-10-16 Fuel injection system for combustion engines Expired - Lifetime US3680535A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19691960144 DE1960144C (de) 1969-12-01 Kraftstoffeinspritzanlage für gemisch verdichtende fremdgezündete Brennkraftma schinen mit kontinuierlicher Einspritzung in das Saugrohr

Publications (1)

Publication Number Publication Date
US3680535A true US3680535A (en) 1972-08-01

Family

ID=5752568

Family Applications (1)

Application Number Title Priority Date Filing Date
US81221A Expired - Lifetime US3680535A (en) 1969-12-01 1970-10-16 Fuel injection system for combustion engines

Country Status (13)

Country Link
US (1) US3680535A (nl)
JP (1) JPS4946669B1 (nl)
AT (1) AT306449B (nl)
BE (1) BE759677A (nl)
CH (1) CH524062A (nl)
CS (1) CS150645B2 (nl)
ES (1) ES386026A1 (nl)
FR (1) FR2072632A5 (nl)
GB (1) GB1336606A (nl)
NL (1) NL162993C (nl)
PL (2) PL73432B1 (nl)
SE (1) SE361335B (nl)
SU (1) SU491239A3 (nl)

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3728993A (en) * 1970-12-17 1973-04-24 Bosch Gmbh Robert Fuel injection apparatus including an air sensor and means for the direction-dependent damping of its movement
US3730155A (en) * 1971-01-11 1973-05-01 Bosch Gmbh Robert Fuel injection apparatus for spark plug-ignited internal combustion engines
US3739758A (en) * 1970-11-07 1973-06-19 Bosch Gmbh Robert Regulator mechanism for fuel injection apparatus
US3752454A (en) * 1971-08-06 1973-08-14 J Korponay Fuel injecting carburetor
US3791359A (en) * 1971-11-24 1974-02-12 Bosch Gmbh Robert Fuel injection apparatus for externally ignited internal combustion engines operating on continuously injected fuel
US3796200A (en) * 1972-01-26 1974-03-12 Heinrich Knapp Fuel injection apparatus
US3817229A (en) * 1971-05-18 1974-06-18 Bosch Gmbh Robert Fuel injection apparatus for externally ignited internal combustion engines operating on fuel continuously injected into the suction tube
US3835828A (en) * 1972-09-07 1974-09-17 Bosch Gmbh Robert Fuel supply system
US3867917A (en) * 1971-07-09 1975-02-25 Johannes Zeyns Combustion machines
US3894523A (en) * 1973-05-29 1975-07-15 Bosch Gmbh Robert Fuel supply system
US3915138A (en) * 1973-09-22 1975-10-28 Bosch Gmbh Robert Fuel injection system
US3916842A (en) * 1970-10-21 1975-11-04 Bosch Gmbh Robert Fuel injection apparatus for internal combustion engines
US3919992A (en) * 1973-09-28 1975-11-18 Bosch Gmbh Robert Fuel injection system
US3951121A (en) * 1973-08-03 1976-04-20 Robert Bosch G.M.B.H. Fuel injection system
US3951119A (en) * 1973-06-09 1976-04-20 Robert Bosch G.M.B.H. Fuel injection system
US3951120A (en) * 1973-08-10 1976-04-20 Robert Bosch G.M.B.H. Diaphragm-controlled pressure control valve assembly
US3963005A (en) * 1973-10-12 1976-06-15 Robert Bosch G.M.B.H. Fuel supply system
US3993032A (en) * 1974-05-13 1976-11-23 Robert Bosch G.M.B.H. Fuel injection systems
US3994267A (en) * 1973-06-30 1976-11-30 Robert Bosch G.M.B.H. Fuel injection system for mixture-compressing, externally ignited, stratified charge, internal combustion engines
US3996910A (en) * 1974-07-29 1976-12-14 Nippon Soken, Inc. Fuel injection system for internal combustion engine
US4058100A (en) * 1975-03-14 1977-11-15 Nippon Soken, Inc. Intake air flow rate measuring device for internal combustion engine
US4064854A (en) * 1975-11-15 1977-12-27 Robert Bosch Gmbh Air valve for a fuel injection system
DE2819477A1 (de) * 1977-05-04 1978-11-09 Aisan Ind Brennstoff-zufuehrungseinrichtung fuer brennkraftmaschinen
DE2818571A1 (de) * 1977-04-27 1978-11-16 Aisan Ind Brennstoff-zufuehrungseinrichtung fuer brennkraftmaschinen
DE2831593A1 (de) * 1977-07-20 1979-02-01 Aisan Ind Vorrichtung zur steuerung des luft- kraftstoff-verhaeltnisses fuer eine brennkraftmaschine
DE2831053A1 (de) * 1977-07-15 1979-02-08 Aisan Ind Brennstoff-zufuehrungseinrichtung fuer brennkraftmaschinen
US4206735A (en) * 1978-08-04 1980-06-10 General Motors Corporation Mechanical throttle body injection apparatus
US4207849A (en) * 1977-08-30 1980-06-17 Toyota Jidosha Kogyo Kabushiki Kaisha Air-fuel ratio control apparatus of a fuel supply system for an internal combustion engine
US4286562A (en) * 1979-03-07 1981-09-01 General Motors Corporation Engine charge forming apparatus
CN117780516A (zh) * 2024-02-23 2024-03-29 福鼎市福海化油器有限公司 可调节最大进气量的双腔节气门阀体

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2536317B2 (de) * 1975-08-14 1977-09-22 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart Gemischverdichtende, fremdgezuendete viertakt-brennkraftmaschine mit ladungsschichtung
DE3237963C2 (de) * 1982-10-13 1986-02-20 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart Kontinuierlich arbeitende Kraftstoffeinspritzanlage

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2318216A (en) * 1942-04-21 1943-05-04 Phillips Petroleum Co Variable fuel orifice carburetor
US2574670A (en) * 1945-11-23 1951-11-13 Ritter Co Inc Carburetor
US2591356A (en) * 1950-05-24 1952-04-01 Jr William L Howe Carbureting mechanism
US3182974A (en) * 1963-09-05 1965-05-11 Hill Raymond Roger Carburetor
US3284063A (en) * 1963-07-29 1966-11-08 Acf Ind Inc Carburetor
US3284062A (en) * 1964-05-13 1966-11-08 Ford Motor Co Fuel metering control for a constant metering force carburetor
US3301536A (en) * 1964-06-19 1967-01-31 Su Carburetter Co Ltd Carburetters for internal combustion engines
DE1281746B (de) * 1963-07-26 1968-10-31 Sibe Vergaser fuer Brennkraftmaschinen
US3539159A (en) * 1967-09-20 1970-11-10 Bosch Gmbh Robert Flow rate-responsive fuel mixture control device

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2318216A (en) * 1942-04-21 1943-05-04 Phillips Petroleum Co Variable fuel orifice carburetor
US2574670A (en) * 1945-11-23 1951-11-13 Ritter Co Inc Carburetor
US2591356A (en) * 1950-05-24 1952-04-01 Jr William L Howe Carbureting mechanism
DE1281746B (de) * 1963-07-26 1968-10-31 Sibe Vergaser fuer Brennkraftmaschinen
US3284063A (en) * 1963-07-29 1966-11-08 Acf Ind Inc Carburetor
US3182974A (en) * 1963-09-05 1965-05-11 Hill Raymond Roger Carburetor
US3284062A (en) * 1964-05-13 1966-11-08 Ford Motor Co Fuel metering control for a constant metering force carburetor
US3301536A (en) * 1964-06-19 1967-01-31 Su Carburetter Co Ltd Carburetters for internal combustion engines
US3539159A (en) * 1967-09-20 1970-11-10 Bosch Gmbh Robert Flow rate-responsive fuel mixture control device

Cited By (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3916842A (en) * 1970-10-21 1975-11-04 Bosch Gmbh Robert Fuel injection apparatus for internal combustion engines
US3739758A (en) * 1970-11-07 1973-06-19 Bosch Gmbh Robert Regulator mechanism for fuel injection apparatus
US3728993A (en) * 1970-12-17 1973-04-24 Bosch Gmbh Robert Fuel injection apparatus including an air sensor and means for the direction-dependent damping of its movement
US3730155A (en) * 1971-01-11 1973-05-01 Bosch Gmbh Robert Fuel injection apparatus for spark plug-ignited internal combustion engines
US3817229A (en) * 1971-05-18 1974-06-18 Bosch Gmbh Robert Fuel injection apparatus for externally ignited internal combustion engines operating on fuel continuously injected into the suction tube
US3867917A (en) * 1971-07-09 1975-02-25 Johannes Zeyns Combustion machines
US3752454A (en) * 1971-08-06 1973-08-14 J Korponay Fuel injecting carburetor
US3791359A (en) * 1971-11-24 1974-02-12 Bosch Gmbh Robert Fuel injection apparatus for externally ignited internal combustion engines operating on continuously injected fuel
US3796200A (en) * 1972-01-26 1974-03-12 Heinrich Knapp Fuel injection apparatus
US3835828A (en) * 1972-09-07 1974-09-17 Bosch Gmbh Robert Fuel supply system
US3894523A (en) * 1973-05-29 1975-07-15 Bosch Gmbh Robert Fuel supply system
US3951119A (en) * 1973-06-09 1976-04-20 Robert Bosch G.M.B.H. Fuel injection system
US3994267A (en) * 1973-06-30 1976-11-30 Robert Bosch G.M.B.H. Fuel injection system for mixture-compressing, externally ignited, stratified charge, internal combustion engines
US3951121A (en) * 1973-08-03 1976-04-20 Robert Bosch G.M.B.H. Fuel injection system
US3951120A (en) * 1973-08-10 1976-04-20 Robert Bosch G.M.B.H. Diaphragm-controlled pressure control valve assembly
US3915138A (en) * 1973-09-22 1975-10-28 Bosch Gmbh Robert Fuel injection system
US3919992A (en) * 1973-09-28 1975-11-18 Bosch Gmbh Robert Fuel injection system
US3963005A (en) * 1973-10-12 1976-06-15 Robert Bosch G.M.B.H. Fuel supply system
US3993032A (en) * 1974-05-13 1976-11-23 Robert Bosch G.M.B.H. Fuel injection systems
US3996910A (en) * 1974-07-29 1976-12-14 Nippon Soken, Inc. Fuel injection system for internal combustion engine
US4058100A (en) * 1975-03-14 1977-11-15 Nippon Soken, Inc. Intake air flow rate measuring device for internal combustion engine
US4064854A (en) * 1975-11-15 1977-12-27 Robert Bosch Gmbh Air valve for a fuel injection system
DE2818571A1 (de) * 1977-04-27 1978-11-16 Aisan Ind Brennstoff-zufuehrungseinrichtung fuer brennkraftmaschinen
DE2819477A1 (de) * 1977-05-04 1978-11-09 Aisan Ind Brennstoff-zufuehrungseinrichtung fuer brennkraftmaschinen
DE2831053A1 (de) * 1977-07-15 1979-02-08 Aisan Ind Brennstoff-zufuehrungseinrichtung fuer brennkraftmaschinen
DE2831593A1 (de) * 1977-07-20 1979-02-01 Aisan Ind Vorrichtung zur steuerung des luft- kraftstoff-verhaeltnisses fuer eine brennkraftmaschine
US4207849A (en) * 1977-08-30 1980-06-17 Toyota Jidosha Kogyo Kabushiki Kaisha Air-fuel ratio control apparatus of a fuel supply system for an internal combustion engine
US4206735A (en) * 1978-08-04 1980-06-10 General Motors Corporation Mechanical throttle body injection apparatus
US4286562A (en) * 1979-03-07 1981-09-01 General Motors Corporation Engine charge forming apparatus
CN117780516A (zh) * 2024-02-23 2024-03-29 福鼎市福海化油器有限公司 可调节最大进气量的双腔节气门阀体
CN117780516B (zh) * 2024-02-23 2024-05-03 福鼎市福海化油器有限公司 可调节最大进气量的双腔节气门阀体

Also Published As

Publication number Publication date
CS150645B2 (nl) 1973-09-04
DE1960144A1 (de) 1971-07-15
NL7017464A (nl) 1971-06-03
PL73432B1 (nl) 1974-08-30
AT306449B (de) 1973-04-10
NL162993C (nl) 1980-07-15
CH524062A (de) 1972-06-15
SU491239A1 (nl) 1975-11-05
SU491239A3 (ru) 1975-11-05
FR2072632A5 (nl) 1971-09-24
JPS4946669B1 (nl) 1974-12-11
SE361335B (nl) 1973-10-29
PL82919B3 (nl) 1975-10-31
GB1336606A (en) 1973-11-07
ES386026A1 (es) 1973-02-16
BE759677A (fr) 1971-04-30

Similar Documents

Publication Publication Date Title
US3680535A (en) Fuel injection system for combustion engines
US2785669A (en) Injection carburetion
US3791359A (en) Fuel injection apparatus for externally ignited internal combustion engines operating on continuously injected fuel
US4064854A (en) Air valve for a fuel injection system
US3628515A (en) Measuring device for a fuel injection system
US4090487A (en) Fuel injection system
US3739758A (en) Regulator mechanism for fuel injection apparatus
US3613650A (en) Fuel injection system for internal combustion engines
JPS6111469Y2 (nl)
US3835828A (en) Fuel supply system
US3983856A (en) Fuel injection system
US3993034A (en) Fuel injection system
US3170503A (en) Fuel viscosity responsive control
US3946714A (en) Fuel injection system
US3713430A (en) Fuel injection system
US4196708A (en) Engine systems
US2517501A (en) Overspeed prevention device for internal-combustion engines
US4075995A (en) Fuel injection system
US3999527A (en) Fuel injection system
US2957467A (en) Fuel metering system
US3817229A (en) Fuel injection apparatus for externally ignited internal combustion engines operating on fuel continuously injected into the suction tube
US2949102A (en) Cold enrichment device
US4214565A (en) Fuel injection apparatus
US3710769A (en) Fuel injection system for internal combustion engines
US4090486A (en) Fuel injection system