US3689205A - Pump-and-nozzle assembly for injecting fuel into internal combustion engines - Google Patents

Pump-and-nozzle assembly for injecting fuel into internal combustion engines Download PDF

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Publication number
US3689205A
US3689205A US116804A US3689205DA US3689205A US 3689205 A US3689205 A US 3689205A US 116804 A US116804 A US 116804A US 3689205D A US3689205D A US 3689205DA US 3689205 A US3689205 A US 3689205A
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United States
Prior art keywords
pump
fuel
piston
pressure
servo
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Expired - Lifetime
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US116804A
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English (en)
Inventor
Heinz Links
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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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
    • 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
    • F02M2700/00—Supplying, feeding or preparing air, fuel, fuel air mixtures or auxiliary fluids for a combustion engine; Use of exhaust gas; Compressors for piston engines
    • F02M2700/13—Special devices for making an explosive mixture; Fuel pumps
    • F02M2700/1317—Fuel pumpo for internal combustion engines
    • F02M2700/1358—Fuel pump with control of fuel inlet to the pumping chamber

Definitions

  • a pump and nozzle assembly for injecting fuel into internal combustion engines includes a servo piston I A which operates a smaller pump piston in response to pressurized fuel periodically admitted to and removed from said servo piston by virtue of a respective first and second position of a solenoid valve also forming 5 Claims, 4 Drawing Figures PATENTEUSEP 5:912
  • This invention relates to a fuel injection pump and nozzle assembly associated with internal combustion engines, particularly diesel engines operating on directly injected fuel.
  • the assembly is of the type which has a pump piston driven by a servo piston having a larger diameter than the pump piston and which is connected to a pressure source. The latter supplies fuel under pressure to the pump piston through a supply valve and to the servo piston.
  • the assembly further includes a solenoid valve which is operated synchronously with the engine operation and the movable valve member of which may assume two positions. In the first position the flow of fuel is directed to the servo piston and in the second position the flow of fuel is directed from the servo piston to a return conduit. In the first position the solenoid valve triggers the beginning of injection while in the second position it controls the start of the return stroke.
  • the aforeoutlined pump and nozzle assembly has the disadvantage that due to the hydraulic abutment affecting the servo piston, the pump piston and the servo piston remain in their end position until the beginning of the return stroke. As a result, an effective timely depressurization of the pump work chamber necessary for closing the injection nozzle does not take place.
  • the terminal moment of the injection is controlled by an oblique control edge which is provided on the pump piston and which cooperates with a bypass bore in the pump cylinder in a known manner.
  • the servo piston and the pump piston both execute their entire stroke; the effective delivery stroke which is variable by the oblique control edge, and thus determined by the angular position of the piston, determines the injected fuel quantities
  • the fuel is admitted to the servo piston at its side adjacent the pump piston, whereupon the servo piston is returned into its initial position.
  • the fuel admitted to the servo piston in the first position of the control plunger is forced into a return conduit.
  • the terminal moment of the injection is controllable by means of the second position of the solenoid valve simultaneously with the beginning of the return stroke of the servo piston, whereupon the charging stroke of the pump piston begins and further, between the pump work chamber and the injection nozzle there is provided a continuously open connection.
  • This results in a sudden depressurization of the pump work chamber and the pressure conduit and thus results in a desired rapid termination of the injection.
  • the pump nozzle according to the invention, has further the advantage that the pressure prevailing prior to the beginning of each injection in the channel leading to the injection nozzle is equal to the servo pressure.
  • FIGS. 1 and 2 the pump and nozzle assembly 10 composed of two structural groups is held together as a single unit by'means of a threaded clamping sleeve 11.
  • the first structural group forming part of the assembly 10 comprises a hydraulically driven pump device 13 controlled by a solenoid valve 12, while the second structural group is formed of an injection nozzle device 17 comprising a spring housing 14, an intermediate disc 15 and a nozzle member 16.
  • the latter has a nozzle body 18 and includes a valve needle 19 disposed therein for axial reciprocal motion.
  • the contact face 21 between the pump device 13 and the spring housing 14, as well as the contact face 22 between the intermediate disc 15 and the spring housing 14 and the contact face 23 between the nozzle body 18 and the intermediate disc 15 are machined planar and, by means of the clamping force of the sleeve 11, provide fluid-tight seals for the channels and chambers passing through said contact faces. Further, the structural group 13 and the components 14, 15 and 16 are conventionally secured against rotation by means of securing pins 24, 24a and 24b.
  • the housing 26 of the pump device 13 has a supply bore 27 which extends transversely to the longitudinal axis of the assembly and which is provided with a coupling thread 28 connected to a supply conduit 29 which, in turn, delivers fuel under a servo pressure p, to the assembly 10 from a pressure source, not shown.
  • This pressure source may be formed, for example, by an engine driven gear pump, the delivery pressure of which may be maintained at the desired servo pressure (for example, 100 kglcm by means of a pressure regulating valve.
  • the solenoid valve 12 is inserted into a stepped continuation 31 of the supply bore 27 and controls the fuel flow from or to a pressure chamber 32 situated above a servo piston 34 reciprocating in a bore 33 of the pump housing 26.
  • the servo piston 34 engages an upper abutment 35.
  • the fuel returns from the pressure chamber 32 into a fuel tank, not shown, through a return conduit 36.
  • the pump piston 37 is slidably held in a cylinder bore 38 of the pump housing 26; it has a frontal radial face 39 which delimits the pump work chamber 41 from one side.
  • the pump work chamber 41 is connected through a port 42 with a chamber 43 of the check valve 44 functioning as a supply valve to control the admission of fuel to the pump work chamber 41 through a charging channel 46.
  • the chamber 43 also serves as a housing for a valve spring 47 urging the check valve 44 into its closed position.
  • the valve spring 47 is preloaded to a charging pressure which is substantially below the servo pressure and which may have a magnitude of approximately 10 kglcm If the pressure in the pump work chamber 41 is approximately equal to the servo pressure in the charging channel 46, the spring 47 closes the valve 44.
  • the charging channel 46 branches off from the supply bore 27 between the coupling thread 28 and the solenoid valve 12 and has in the vicinity of the branch-off a throttle 51.
  • the supply valve 44 is located at the downstream end of the charging channel 46.
  • valve 44 the periphery of its movable valve member 52 and wall 53 of the spring chamber 43 define a gap 54 which may be so designed that it forms a constricted flow passage section and functions as an additional throttle besides the throttle 51.
  • the fuel which leaks into the spring chamber 62 from the annular chamber 57 through the valve needle 19, is returned to the fuel tank through a leakage port 63 extending from the spring chamber 62 and indicated in broken lines in FIGS. 1 and 2 and through a leakage conduit 64 (FIG. 2) adjoining the leakage port 63.
  • the fuel leaking through servo piston 34 and pump piston 37 is collected in an annular groove 66 which is located at the end of the cylinder bore 33 adjacent the end of the servo piston 34 remote from pressure chamber 32.
  • the annular groove 66 communicates with the return conduit 36 by means of a channel 67 containing a check valve 68.
  • the purpose of the latter is to prevent fuel from being drawn from the return conduit 36 into the chamber 69 delimited by the annular groove 66 and the pump piston 37 during the return stroke of the servo piston 34.
  • the occurrence of an aforenoted drawing of fuel would prevent a subsequent downward motion of the servo piston 34 during the delivery stroke.
  • the solenoid valve 12 inserted into the enlarged extension 31 of the supply bore 27 is formed of a pressure-equalized 3/2-way valve operated by an electromagnet 71, a valve housing 72 and a sphere 73 constituting the movable valve member.
  • the sphere 73 in its position shown in FIG. 1, closes the valve seat 74 at the mouth of a bore 75 communicating with the supply bore 27 and thus prevents the admission of fuel from the supply bore 27 to a control chamber 76 in the valve housing 72.
  • the control chamber 76 is connected by means of a bore 77 and a channel 78 with the return conduit 36.
  • the mouth of the bore 77 at the control chamber 76 is formed as a second valve seat 79 for the sphere 73.
  • the control chamber 76 and the pressure chamber 32 of the servo piston 34 are interconnected by means of a bore 81.
  • the electromagnet 71 is provided with an armature 82 which is movably held in an extension of the bore 77 in the valve housing 72 and which, by means of a pin 83, urges the sphere 73 against valve seat 74 under the effect of spring 84 when the electromagnet 71 is in a de-energized condition.
  • the solenoid valve 12 is pressure-equalized by communicating the pressure prevailing in the supply bore 27 through a channel 85 to the chamber 86 which receives the spring 84 and which is located behind the armature 82.
  • the electromagnet 71 is provided with a sole control winding 87. As soon as the latter is energized, for example, by means of an electronic control apparatus (not shown), the force of the spring 84 is overcome and the armature 82 is drawn thereagainst. Thus, the sphere 73 is lifted from valve seat 74. This results in a flow of pressurized fuel from supply bore 27 through bore 75 into the control chamber 76. The force of this fuel flow presses the sphere 73 to the second valve seat 79 closing off the bore 77 leading to the return conduit 36. Thus the fuel flows through bores 27, 75 and 81 into the pressure chamber 32.
  • valve housing 72 Portions of the valve housing 72 which are under different pressures, are, in the stepped extension 31 of the supply bore 27, sealed from one another by means of packing rings 88, 88a and 88b. Because of the small moving masses of the solenoid valve 12, its switching occurs practically without delay and its switching period is very short.
  • the servo piston 34 and the pump piston 37 are in their upper position of rest (also shown in FIG. 1), but the solenoid valve 12 is shown in its position in which it allows the flow of fuel from the pressure source to the pressure chamber 32.
  • the delivery stroke of the pump device 13 begins in this position of the solenoid valve 12.
  • FIG. 4 the servo piston 34 and the pump piston 37 are shown in a position in which they have terminated their delivery stroke H and the solenoid valve 12 is deenergized, whereupon the armature 82 and the valve sphere 73 reassume their position shown in FIG. 1. As a result, the pressure chamber 32 is depressurized through the return conduit 36.
  • the solenoid valve 12 When the solenoid valve 12 is in its position shown in FIG. 1, in the pump work chamber 41 and in the pressure channel 56 there prevails the servo pressure p, the magnitude of which may be, for example, 100 kg/cm. In this position, the supply valve 44 is closed. When the solenoid valve 12 switches over to a position shown in FIG. 3 under the effect of a control signal, the fuel, which is under servo pressure, is admitted from the supply bore 27 into the pressure chamber 32 above the servo piston 34.
  • the closing spring 61 of the injection nozzle 17 is in the present example preloaded to 150 kg/cm nozzle opening pressure.
  • the injection stroke H is terminated when, due to the discontinuation of the control signal to the solenoid valve 12, the latter is switched over into its position shown in FIG. 4.
  • the pressure chamber. 32 is suddenly depressurized, the fuel which is under injection pressure and which prevails in the pump work chamber 41 and in the pressure channel 56 moves the pistons 34 and 37 slightly upwardly, whereby the pressure in the channel 56 falls under the nozzle opening pressure.
  • the valve needle 19 returns into its closed position and the fuel injection is terminated.
  • the supply valve opens and fuel flows into the charging bore 46 and, through port 42, into the pump work chamber 41 and moves the pump piston 34 and the servo piston 37 upwardly.
  • throttle 51 By virtue of the effect of throttle 51, a pressure drop of such a magnitude results, that the servo piston 34 is dampened in its motion as it reaches the upper abutment 35.
  • Such a braking of the servo piston is advantageous since it extends the life expectancy of the pump and nozzle assembly and diminishes the operating noise.
  • the charging stroke may be extended until shortly before the beginning of the subsequent injection stroke. The charging stroke which occurs immediately after depressurization of the pressure channel 56, prevents a highly undesirable cavitation which normally would occur at rapid depressurization and vacuum.
  • a further advantage of the above-described pump and nozzle assembly resides in the fact that the change in difference between the actually injected fuel quanti-' ties and the desired injected fuel quantities (quantity scattering) of subsequent injection steps is substantially decreased because of the down-stepped surface ratio between the servo piston 34 and the pump piston 37.
  • solenoid valves operate with time scatter, that is, the opening moments and the closing moments are not always exactly the same in case of identical control periods. Such a time scatter results in a quantity scattering of the output of the pump and nozzle assembly. Since, according to the invention, the fuel quantities controlled by the solenoid valve are admitted to the servo piston, the quantity scattering in the pump piston is decreased by the surface ratio between the servo piston and the pump piston.
  • a pump and nozzle assembly for injecting fuel into internal combustion engines, wherein said assembly is of the known type that includes (a) a reciprocating pump piston associated with a pump work chamber, (b) a servo piston driving said pump piston and having a diameter larger than that of said pump piston, (c) means for supplying fuel under servo pressure for driving said servo piston, (d) means for supplying fuel under said servo pressure to the pump work chamber of said pump piston, (e) a solenoid valve actuated synchronously with the operation of said engine and adapted to assume a first position in which it directs said fuel to said servo piston causing a forward stroke thereof, thereby triggering the start of fuel injection into said engine and a second position in which it causes said servo piston to be relieved of the servo pressure of said fuel to permit its return stroke to begin and (f) a nozzle through which fuel is injected into said engine, the improvement comprising,
  • said means defined in ((1) includes a fuel supply channel; said improvement comprises a throttle means to extend the period of fuel supply to said pump work chamber until the start of the fuel injection of a successive work cycle.
  • said solenoid valve is formed of a pressure-equalized, 3/2-way valve including a displaceable sphere as a movable valve member and an electromagnet including a sole control winding and a movable armature operatively connected to said sphere.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
US116804A 1970-03-14 1971-02-19 Pump-and-nozzle assembly for injecting fuel into internal combustion engines Expired - Lifetime US3689205A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19702012202 DE2012202A1 (de) 1970-03-14 1970-03-14 Pumpe Düse zur Kraftstoffeinspritzung für Brennkraftmaschinen

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US (1) US3689205A (de)
AT (1) AT307163B (de)
DE (1) DE2012202A1 (de)
FR (1) FR2084575A5 (de)
GB (1) GB1314115A (de)

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4046112A (en) * 1975-10-20 1977-09-06 General Motors Corporation Electromagnetic fuel injector
US4182492A (en) * 1978-01-16 1980-01-08 Combustion Research & Technology, Inc. Hydraulically operated pressure amplification system for fuel injectors
EP0054483A1 (de) * 1980-12-17 1982-06-23 The Bendix Corporation Fördersystem zur Kraftstoffeinspritzung für einen Dieselmotor
DE3151942A1 (de) * 1980-12-31 1982-07-08 Cummins Engine Co., Inc., 47201 Columbus, Ind. "einspritzung fuer dieselmotor"
US5121730A (en) * 1991-10-11 1992-06-16 Caterpillar Inc. Methods of conditioning fluid in an electronically-controlled unit injector for starting
US5168855A (en) * 1991-10-11 1992-12-08 Caterpillar Inc. Hydraulically-actuated fuel injection system having Helmholtz resonance controlling device
US5176115A (en) * 1991-10-11 1993-01-05 Caterpillar Inc. Methods of operating a hydraulically-actuated electronically-controlled fuel injection system adapted for starting an engine
US5181494A (en) * 1991-10-11 1993-01-26 Caterpillar, Inc. Hydraulically-actuated electronically-controlled unit injector having stroke-controlled piston and methods of operation
US5191867A (en) * 1991-10-11 1993-03-09 Caterpillar Inc. Hydraulically-actuated electronically-controlled unit injector fuel system having variable control of actuating fluid pressure
WO1993007382A1 (en) * 1991-10-11 1993-04-15 Caterpillar Inc. Damped actuator and valve assembly for an electronically-controlled unit injector
WO1993007379A1 (en) * 1991-10-11 1993-04-15 Caterpillar Inc. Actuator and valve assembly for a hydraulically-actuated electronically-controlled unit injector
US5245970A (en) * 1992-09-04 1993-09-21 Navistar International Transportation Corp. Priming reservoir and volume compensation device for hydraulic unit injector fuel system
US5271371A (en) * 1991-10-11 1993-12-21 Caterpillar Inc. Actuator and valve assembly for a hydraulically-actuated electronically-controlled injector
US5499608A (en) * 1995-06-19 1996-03-19 Caterpillar Inc. Method of staged activation for electronically actuated fuel injectors
US5566660A (en) * 1995-04-13 1996-10-22 Caterpillar Inc. Fuel injection rate shaping apparatus for a unit fuel injector
US5632444A (en) * 1995-04-13 1997-05-27 Caterpillar Inc. Fuel injection rate shaping apparatus for a unit injector
US5740782A (en) * 1996-05-20 1998-04-21 Lowi, Jr.; Alvin Positive-displacement-metering, electro-hydraulic fuel injection system
US6085991A (en) * 1998-05-14 2000-07-11 Sturman; Oded E. Intensified fuel injector having a lateral drain passage
US6126412A (en) * 1997-12-10 2000-10-03 Caterpillar Inc. Fluid driven piston assembly and fuel injector using same
US6148778A (en) * 1995-05-17 2000-11-21 Sturman Industries, Inc. Air-fuel module adapted for an internal combustion engine
US6161770A (en) * 1994-06-06 2000-12-19 Sturman; Oded E. Hydraulically driven springless fuel injector
US6257499B1 (en) 1994-06-06 2001-07-10 Oded E. Sturman High speed fuel injector

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1470166A (en) * 1973-05-12 1977-04-14 Cav Ltd Fuel injection pumping apparatus
GB1599649A (en) * 1977-12-09 1981-10-07 Lucas Industries Ltd Fuel injection system
DE3039972A1 (de) * 1980-10-23 1982-05-27 Robert Bosch Gmbh, 7000 Stuttgart Elektrisch steuerbare kraftstoff-einspritz-vorrichtung
DE3133288A1 (de) * 1981-08-22 1983-03-03 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8900 Augsburg "brennstoffeinspritzsystem an einer brennkraftmaschine"
US4485969A (en) * 1982-02-19 1984-12-04 General Motors Corporation Electromagnetic unit fuel injector with cartridge type solenoid actuated valve
US5297523A (en) * 1993-02-26 1994-03-29 Caterpillar Inc. Tuned actuating fluid inlet manifold for a hydraulically-actuated fuel injection system
RU2273762C2 (ru) * 2001-09-03 2006-04-10 Военный автомобильный институт Форсунка двигателя внутреннего сгорания

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2537748A (en) * 1947-03-10 1951-01-09 Evans Arthur Frederick Fuel injection pump for internalcombustion engines
US2598528A (en) * 1948-12-20 1952-05-27 Louis O French Fuel injection apparatus

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2537748A (en) * 1947-03-10 1951-01-09 Evans Arthur Frederick Fuel injection pump for internalcombustion engines
US2598528A (en) * 1948-12-20 1952-05-27 Louis O French Fuel injection apparatus

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4046112A (en) * 1975-10-20 1977-09-06 General Motors Corporation Electromagnetic fuel injector
US4182492A (en) * 1978-01-16 1980-01-08 Combustion Research & Technology, Inc. Hydraulically operated pressure amplification system for fuel injectors
EP0054483A1 (de) * 1980-12-17 1982-06-23 The Bendix Corporation Fördersystem zur Kraftstoffeinspritzung für einen Dieselmotor
DE3151942A1 (de) * 1980-12-31 1982-07-08 Cummins Engine Co., Inc., 47201 Columbus, Ind. "einspritzung fuer dieselmotor"
US4448169A (en) * 1980-12-31 1984-05-15 Cummins Engine Company, Inc. Injector for diesel engine
WO1993007379A1 (en) * 1991-10-11 1993-04-15 Caterpillar Inc. Actuator and valve assembly for a hydraulically-actuated electronically-controlled unit injector
US5168855A (en) * 1991-10-11 1992-12-08 Caterpillar Inc. Hydraulically-actuated fuel injection system having Helmholtz resonance controlling device
US5176115A (en) * 1991-10-11 1993-01-05 Caterpillar Inc. Methods of operating a hydraulically-actuated electronically-controlled fuel injection system adapted for starting an engine
US5181494A (en) * 1991-10-11 1993-01-26 Caterpillar, Inc. Hydraulically-actuated electronically-controlled unit injector having stroke-controlled piston and methods of operation
US5191867A (en) * 1991-10-11 1993-03-09 Caterpillar Inc. Hydraulically-actuated electronically-controlled unit injector fuel system having variable control of actuating fluid pressure
WO1993007382A1 (en) * 1991-10-11 1993-04-15 Caterpillar Inc. Damped actuator and valve assembly for an electronically-controlled unit injector
WO1993007378A1 (en) * 1991-10-11 1993-04-15 Caterpillar Inc. Hydraulically-actuated electronically-controlled unit injector having stroke-controlled piston and methods of operation
US5121730A (en) * 1991-10-11 1992-06-16 Caterpillar Inc. Methods of conditioning fluid in an electronically-controlled unit injector for starting
WO1993007384A1 (en) * 1991-10-11 1993-04-15 Caterpillar Inc. Methods of conditioning fluid in an electronically-controlled unit injector for starting
RU2101547C1 (ru) * 1991-10-11 1998-01-10 Катерпиллар Инк. Приводной и клапанный узел для форсунки с гидравлическим приводом и электронным управлением
US5271371A (en) * 1991-10-11 1993-12-21 Caterpillar Inc. Actuator and valve assembly for a hydraulically-actuated electronically-controlled injector
US5245970A (en) * 1992-09-04 1993-09-21 Navistar International Transportation Corp. Priming reservoir and volume compensation device for hydraulic unit injector fuel system
US6257499B1 (en) 1994-06-06 2001-07-10 Oded E. Sturman High speed fuel injector
US6161770A (en) * 1994-06-06 2000-12-19 Sturman; Oded E. Hydraulically driven springless fuel injector
US5566660A (en) * 1995-04-13 1996-10-22 Caterpillar Inc. Fuel injection rate shaping apparatus for a unit fuel injector
US5632444A (en) * 1995-04-13 1997-05-27 Caterpillar Inc. Fuel injection rate shaping apparatus for a unit injector
US6148778A (en) * 1995-05-17 2000-11-21 Sturman Industries, Inc. Air-fuel module adapted for an internal combustion engine
US6173685B1 (en) 1995-05-17 2001-01-16 Oded E. Sturman Air-fuel module adapted for an internal combustion engine
US5499608A (en) * 1995-06-19 1996-03-19 Caterpillar Inc. Method of staged activation for electronically actuated fuel injectors
US5740782A (en) * 1996-05-20 1998-04-21 Lowi, Jr.; Alvin Positive-displacement-metering, electro-hydraulic fuel injection system
US6126412A (en) * 1997-12-10 2000-10-03 Caterpillar Inc. Fluid driven piston assembly and fuel injector using same
US6085991A (en) * 1998-05-14 2000-07-11 Sturman; Oded E. Intensified fuel injector having a lateral drain passage

Also Published As

Publication number Publication date
FR2084575A5 (de) 1971-12-17
AT307163B (de) 1973-05-10
GB1314115A (en) 1973-04-18
DE2012202A1 (de) 1971-10-07

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