US3728993A - Fuel injection apparatus including an air sensor and means for the direction-dependent damping of its movement - Google Patents

Fuel injection apparatus including an air sensor and means for the direction-dependent damping of its movement Download PDF

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Publication number
US3728993A
US3728993A US00208699A US3728993DA US3728993A US 3728993 A US3728993 A US 3728993A US 00208699 A US00208699 A US 00208699A US 3728993D A US3728993D A US 3728993DA US 3728993 A US3728993 A US 3728993A
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Prior art keywords
throttle
pressure
pressure chamber
air
fuel
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US00208699A
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English (en)
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K Eckert
H Knapp
W Sautter
V Stein
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • 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
    • F02M69/16—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
    • F02M69/26—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 varying fuel pressure in a fuel by-pass passage, the pressure acting on a throttle valve against the action of metered or throttled fuel pressure for variably throttling fuel flow to injection nozzles, e.g. to keep constant the pressure differential at the metering valve

Definitions

  • the air sensor is deflected by the flow of the intake air to an extent proportionate to the throughgoing air quantities against a constant return or resetting force.
  • the air sensor displaces the movable part (for example, a control plunger) of a quantity distributor valve disposed in the fuel line for metering the fuel in a manner proportionate to the intake air quantities.
  • the return force is derived from a pressurized liquid which is delivered continuously and under constant pressure in a pressure conduit and which affects a piston that reciprocates in a cylinder.
  • the latter communicates with the said pressure conduit by a connecting conduit containing a throttle, as shown in German Published Application 1,960,144.
  • the pressurized liquid that serves as a return force for the air sensor is forced through a throttle for the purpose of damping the oscillation of the air sensor. If a conventional throttle is used, air or sensor vibrations cause, in the lower rpm range, a mean value increase of the position of the control plunger in the metering valve; thus, an undesired increase in the metered fuel quantities occurs.
  • the aforenoted throttle is so designed that its throttling effect on the flow of the liquid supplying the resetting force is smaller in the direction of the pressure chamber (where the piston is located) than in the opposite, discharging direction.
  • FIG. 1 is a longitudinal sectional view of a fuel injection apparatus incorporating a first embodiment of the invention
  • FIG. 2 is a longitudinal sectional view of a second embodiment of the invention.
  • FIG. 2a is an end view of one component forming part of the second embodiment
  • FIG. 3 is a longitudinal sectional view of a third embodiment of the invention.
  • FIG. 3a is an end view of one component forming part of the third embodiment and FIG. 4 is a longitudinal sectional view of a fourth embodiment of the invention.
  • the intake air flows through an air filter (not shown) in the direction of the arrow A in an intake tube portion 1 having a flaring, conical portion 6 in which there is disposed an air sensor 2.
  • the intake air flows through a connecting hose portion 3 and an intake tube portion 4 in which there is disposed an arbitrarily operable butterfly valve 5.
  • the intake air is admitted to the cylinders 5 (not shown) of an internal combustion engine (also not shown).
  • the air sensor 2 is formed as a disc oriented normal to the direction of air flow and displaceable in the conical portion 6 linearly proportionately to the air quantities passing through the intake tube.
  • the pressure prevailing between the air sensor 2 and the butterfly valve 5 also remains constant.
  • the air sensor 2 directly controls a fuel metering and distributor valve 7.
  • a lever 8 which is pivotal and with low friction supported at 9 and which, upon its pivotal motion, displaces a movable valve component 11 (formed as a control plunger) of the metering valve 7 by means of a nose It) integral with the lever 8.
  • the frontal face 12 of the control plunger 1 1 disposed remote from the nose 10 is exposed to pressurized liquid which serves as the return force for the air sensor 2.
  • the fuel supply is effected by a fuel pump 15 which is driven by an electromotor l4 and which draws fuel from a tank 16 and forces the same through a conduit 17 to the metering valve 7. From the conduit 17 there extends, back into the tank 16, a conduit 18 in which there is disposed a pressure limiting valve 19.
  • the channel 22 leads to an annular groove 23 of the control plunger 11 and also to a plurality of chambers 24 in which the fuel under pressure exerts a force to one side of a diaphragm 25
  • the land 1121 forming part of the plunger and bounding the annular groove 23 covers to a greater or a lesser extent the control slots 26.
  • Each control slot 26, through an associated port 27, communicates with a chamber 28 separated from an adjacent chamber 24 by means of the diaphragm 25.
  • each chamber 28 the fuel is admitted through a channel 29 to the associated individual fuel injection valve (not shown) which is disposed in the air intake tube in the vicinity of an engine cylinder.
  • the diaphragm 25 serves as the movable part of a flat seat valve which is maintained in an open position by means of a spring 30 when the fuel injection apparatus is not operating. It is noted that the number of the flat seat valve assemblies formed of components 24, 25, 28, 30 is identical to the number of the control or metering slots 26 and thus the number of cylinders in the internal combustion engine.
  • Each flat seat valve assembly 24, 25, 28, 30 ensures that independently from the extent of overlap between the annular groove 23 and the control slots 26, thus independently from the fuel quantities flowing to the fuel injection valves, the pressure drop across the fuel metering valve 23, 26 is maintained substantially at a constant value. In this manner it is ensured that the extent of displacement of the control plunger 11 is proportionate to the metered fuel quantity.
  • the conical portion dot the air intake tube is so designed that the. annular flow passage section defined by the periphery of the disc 2 and the cone wall is proportionate to the displacement of the disc 2 which causes, through the pivotal motion of lever 8, a shift in the metering plunger 1 1. Consequently, there is a linear dependence between the motion of the air sensor 2 and the displacement of the control plunger 11, so that the fuel metered at 23, 26 will at any time be proportionate to the air quantities flowing through the intake tube.
  • the pressurized liquid serving as a constant return force and affecting the control plunger 11 is fuel.
  • a conduit 33 extending from the conduit 17 to the pressure chamber 34 into which extends that terminus of the control plunger 11 which is remote from the pivotal lever 8.
  • an advance throttle 35 which separates the supply circuit 17 of the fuel metering valve 7 from the control pressure circuit 33, 36 of the regulator assembly 37.
  • the regulator assembly 37 is formed as a flat seat valve 40 which has a diaphragm 41 serving as its movable valving member.
  • a very slight motion of the diaphragm 41 in a direction away from its seat is sufficient to fully open the valve 40.
  • the fuel flowing through the valve 40 from the conduit 36 returns depressurized to the fuel tank 16 through the return conduit 38.
  • the diaphragm 41 is loaded by a spring 42, the bias of which is changeable by magnitudes dependent upon operational engine variables.
  • a three-dimensional cam 43 which is rotatable as a unit with the butterfly valve I and is axially displaceable as a function of the vacuum prevailing in the air intake tube downstream of the butterfly valve 5.
  • the three-dimensional cam 43 is held axially slidably on a shaft 44 of the butterfly valve 5 which is arbitrarily turnable by a lever 45.
  • the three-dimensional cam 43 is rotatably coupled to the shaft 44 by a pin 46.
  • One end of the three-dimensional cam 43 is rotatably secured to a diaphragm 47 bounding a vacuum chamber 48 which is connected by means of a conduit 49 with the air intake tube at a location downstream of the butterfly valve .5.
  • the threedimensional cam 43 is axially displaced by the diaphragm 47 against the force of a return spring 50 disposed in the vacuum chamber 48.
  • the three-dimensional cam 43 is scanned by a follower pin 53, the motion of which is transmitted through a spring seat disc 54 to the spring 42, the bias of which determines the return force for the air sensor 2.
  • the fuel that pressurizes the chamber 34 passes through a throttle assembly 57 disposed in the inlet of the pressure chamber 34 and comprising a throttle plate 58 axially movable in a bore portion 62 of the housing of the valve 7 and a closure plate 60 held in said housing parallel and adjacent to the throttle plate 58.
  • the closure plate 60 has an aperture 59 coupled to the terminus of the pressure conduit 33.
  • the throttle plate 58 has a small throttle opening 63 aligned with the aperture 59 and a large throttle opening 64 facing a wall portion of the closure plate 60.
  • the operation of the throttle assembly 57 will be described in detail as the specification progresses.
  • the throttle assembly 57 effects a substantially temperature-independent damping of the motion of the air sensor 2 since fuel is used as the damping liquid.
  • the aforedescribed fuel injection apparatus operates as follows.
  • the constant resetting force affecting the air sensor 2 has to be changed.
  • the parameters for the load and rpm are the angular position of the butterfly valve 5 and the magnitude of the vacuum in the air intake tube.
  • the return force is expediently changed by these two variables.
  • the force of the spring 42 of the regulator assembly 37 is varied by axially and/or angularly displacing the three-dimensional cam 43 as a function, respectively, of said vacuum in the suction tube downstream of the butterfly valve 5 and of the position of the butterfly valve.
  • the follower pin 53 in engagement with the three-dimensional cam 43, determines the position of the spring seat disc 54 which, in turn determines the extent of compression (bias) of the spring 42. If, for example, during full load, the butterfly valve 5 is in a position in which the air intake tube is fully open, then a highest output, that is, a relatively rich air-fuel mixture is desired. Since the bias of the spring 42 of the regulator assembly 37 determines the pressure of the fuel which affects in the pressure chamber 34 the redial face 12 of the control plunger 11, the return force affecting the air sensor 2 has to be slightly decreased to cause the control plunger 11 to be shifted into a position in which the control slots 26 are opened to a greater extent.
  • the pressure of the fuel which affects the radial face 12 of the control plunger 11 and which acts as the return force for the air sensor 2, is thus maintained at a constant value and is varied only as a function of engine variables.
  • the control pressure circuit 33, 36 separated from the supply conduit 17 by means of the advance throttle 35 affects the radial face 12 of the control plunger 11 and thus acts as a return force on the air sensor 2 through the throttle assembly 57 as a function of the load and the rpm-dependent position of the regulator assembly 37.
  • the throttle assembly 57 is necessary as a damping means for preventing overshoots of the air sensor 2 during acceleration and to limit the effect of the suction thrusts of the engine. Such unrestrained oscillations of the air sensor 2 (and the lever 8) would cause a corresponding reciprocation of the control plunger 11 which, in turn, would lead to an undesired fluctuation in the fuel metering and to a jerky engine run.
  • the throttle assembly 57 is so designed that its throttling effect for damping the oscillations is dependent upon the flow direction. If the control plunger 11 moves in a direction out of the pressure chamber 34 (to the left, when viewed in FIG, 1) because of a drop in the force on the air sensor plate 2, the pressure in the chamber 34 decreases andfalls below the. control pressure of the liquid in the conduit 33. This pressure difference causes the movable throttle plate 58 to assume its position as shown in FIG. 1, in which the large throttle bore 64 of the throttle plate 58 is open. This is so because the throttle plate 58 is now positioned at a distance from the closure plate 60, defining therewith a space 61.
  • the pressurized liquid may flow rapidly from conduit 33 into the pressure chamber 34 because it may flow through both the small throttle opening 63 and the large throttle opening 64 provided in the throttle plate 58.
  • the air sensor 2 because of the pressure difference at the sensor, moves in the direction of air flow, the lever 8 seeks to push the control plunger 11 into the pressure chamber 34 (i.e. towards the right, as viewed in FIG. 1).
  • Such displacement of the control plunger 11 increases the pressure in the pressure chamber 34with respect to the pressure in the conduit 33, so that the throttle plate 58 is moved to the right and pressed against the closure plate 60 in a face-to-face engagement.
  • FIGS. 2, 2a, 3, 3a, and 4 show three other embodiments of the aforedescribed direction-dependent throttle assembly.
  • FIG. 2a illustrates an end view of the throttle plate 69 taken in the direction of arrow B.
  • a throttle plate or, more accurately, a tongue-shaped plate valve 76 having a small throttle opening 77, is clamped between a closure plate 78 and the housing of the valve 7.
  • the aperture 59a in the closure plate 78 merges into a counterbore 79 oriented towards the valve 76.
  • the plate valve 76 is in a faceto-face engagement with the closure plate 78.
  • FIG. 3a is an end view of the plate valve 76 taken in the direction of arrow C.
  • the throttle assembly 570 shown therein has a closure plate 82 which presses a throttle plate firmly against an annular shoulder 93 with the interposition of a spacer ring 92.
  • the closure plate 82 has an aperture 83 through which the pressurized liquid is admitted from the conduit 33 into an accumulator chamber 84 bounded by the closure plate 82 and the throttle plate 85.
  • the accumulator chamber 84 is in continuous communication with the pressure chamber 34 through a smaller throttle opening 86 of the throttle plate 85.
  • a second, larger throttle opening 87 provided in the throttle plate 85 is normally maintained in a closed position by means of a spherical valve formed of a ball 88, a spring seat disc 89 and a spring 90 bearing against an annular shoulder 91.
  • a fuel injection apparatus for introducing metered fuel in the air intake tube of an internal combustion engine, the improvement comprising A. a butterfly valve disposed in said air intake tube for controlling the flow of intake air therein,
  • a fuel metering valve having a movable valving member the position of which determining the fuel quantities to be injected
  • G a pressure conduit connected with said pressure chamber for carrying liquid under pressure thereto and therefrom,
  • a movable plunger having a work face disposed in said pressure chamber and exposed to the pressure therein, said pressure urging said plunger out of said pressure chamber, said plunger being connected to said means defined in (E) for exerting a return force on said air sensor by virtue of the pressurized liquid in said pressure chamber, said means defined in (E) urging said plunger into said pressure chamber in response to the deflecting forces exerted on said air sensor and J.
  • a throttle assembly arranged betweensaid pressure conduit and said pressure chamber to restrict the flow of said liquid to and from said pressure chamber, said throttle assembly including direction-dependent means for throttling the flow of said liquid to a smaller extent in a direction from said pressure conduit to said pressure chamber and to a greater extent in a direction from said pressure chamber to said pressure conduit.
  • said throt tle assembly including A. a movable throttle plate exposed to said liquid to assume a first position in response to the liquid flowin a direction from said pressure conduit to said pressure chamber and to assume a second position in response to the liquid flow in a opening and B. stationary wall means blocking said relatively large throttle opening in said second position of said movable throttle plate.
  • said throttle assembly including A. a chamber of circular cross section, B. a triangular throttle plate movable in said chamber and having a continuously open, relatively small throttle opening, the contour of said triangular throttle plate and said last-named chamber defining relatively large throttle openings,
  • said throttle assembly including A. a stationary component having 1. an aperture coupled to said pressure conduit, 2. a counterbore communicating with said aperture and Ba tongue valve plate having a throttle opening in registry with said counterbore, said tongue valve plate being resiliently urged against said stationary component over said counterbore, said tongue valve plate being adapted to move away from said counterbore by said liquid flowing from said pressure conduit to said pressure chamber.
  • said throttle assembly including A. means defining a continuously open, relatively small throttle opening,
  • valve ball means urging said valve ball into engagement with said means defining said relatively large throttle opening for closing the same, said valve ball being adapted to move away from the last-named means for opening said relatively large throttle opening by means of said liquid flowing from said pressur conduit to said pressure chamber.

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  • 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)
US00208699A 1970-12-17 1971-12-16 Fuel injection apparatus including an air sensor and means for the direction-dependent damping of its movement Expired - Lifetime US3728993A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2062078A DE2062078C3 (de) 1970-12-17 1970-12-17 Kraftstoffeinspritzanlage für gemischverdichtende fremdgezündete Brennkraftmaschinen

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US3728993A true US3728993A (en) 1973-04-24

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US00208699A Expired - Lifetime US3728993A (en) 1970-12-17 1971-12-16 Fuel injection apparatus including an air sensor and means for the direction-dependent damping of its movement

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US (1) US3728993A (de)
JP (1) JPS5421891B1 (de)
AU (1) AU449161B2 (de)
BE (1) BE776833R (de)
CS (1) CS157133B4 (de)
DE (1) DE2062078C3 (de)
ES (1) ES398040A2 (de)
FR (1) FR2131294A6 (de)
GB (1) GB1363740A (de)
IT (1) IT972069B (de)
NL (1) NL7117284A (de)
PL (1) PL83049B3 (de)
SE (1) SE365023B (de)
SU (1) SU512721A4 (de)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3796200A (en) * 1972-01-26 1974-03-12 Heinrich Knapp Fuel injection apparatus
US3809036A (en) * 1972-01-22 1974-05-07 Bosch Gmbh Robert Fuel injection apparatus
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
US3951119A (en) * 1973-06-09 1976-04-20 Robert Bosch G.M.B.H. Fuel injection system
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
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
US4007722A (en) * 1974-09-18 1977-02-15 Robert Bosch G.M.B.H. Fuel injection system
US4206735A (en) * 1978-08-04 1980-06-10 General Motors Corporation Mechanical throttle body injection apparatus
US4346589A (en) * 1979-11-03 1982-08-31 Robert Bosch Gmbh Flow rate meter
US4483298A (en) * 1979-12-15 1984-11-20 Robert Bosch Gmbh Valve

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2349631C2 (de) * 1973-10-03 1984-10-04 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzanlage
US4248188A (en) * 1978-12-29 1981-02-03 Cummins Engine Company, Inc. Hydraulic attenuator for air fuel control pump
DE2904496A1 (de) * 1979-02-07 1980-08-21 Audi Nsu Auto Union Ag Flachsitzventil fuer eine kraftstoff- einspritzanlage

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3015548A (en) * 1958-07-28 1962-01-02 Harry W Mcclain Carburetor of the pressure type
US3628515A (en) * 1969-12-01 1971-12-21 Bosch Gmbh Robert Measuring device for a fuel injection system
US3680535A (en) * 1969-12-01 1972-08-01 Bosch Gmbh Robert Fuel injection system for combustion engines

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3015548A (en) * 1958-07-28 1962-01-02 Harry W Mcclain Carburetor of the pressure type
US3628515A (en) * 1969-12-01 1971-12-21 Bosch Gmbh Robert Measuring device for a fuel injection system
US3680535A (en) * 1969-12-01 1972-08-01 Bosch Gmbh Robert Fuel injection system for combustion engines

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3809036A (en) * 1972-01-22 1974-05-07 Bosch Gmbh Robert Fuel injection apparatus
US3796200A (en) * 1972-01-26 1974-03-12 Heinrich Knapp Fuel injection apparatus
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
US4007722A (en) * 1974-09-18 1977-02-15 Robert Bosch G.M.B.H. Fuel injection system
US4206735A (en) * 1978-08-04 1980-06-10 General Motors Corporation Mechanical throttle body injection apparatus
US4346589A (en) * 1979-11-03 1982-08-31 Robert Bosch Gmbh Flow rate meter
US4483298A (en) * 1979-12-15 1984-11-20 Robert Bosch Gmbh Valve

Also Published As

Publication number Publication date
DE2062078A1 (de) 1972-06-22
DE2062078B2 (de) 1977-08-18
GB1363740A (en) 1974-08-14
PL83049B3 (de) 1975-12-31
SE365023B (de) 1974-03-11
JPS5421891B1 (de) 1979-08-02
IT972069B (it) 1974-05-20
FR2131294A6 (de) 1972-11-10
AU449161B2 (en) 1974-06-06
BE776833R (fr) 1972-04-17
CS157133B4 (de) 1974-08-23
DE2062078C3 (de) 1978-04-06
AU3695471A (en) 1973-06-21
NL7117284A (de) 1972-06-20
SU512721A4 (ru) 1976-04-30
ES398040A2 (es) 1974-07-16

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