US3810453A - Fuel injection system - Google Patents

Fuel injection system Download PDF

Info

Publication number
US3810453A
US3810453A US00190142A US19014271A US3810453A US 3810453 A US3810453 A US 3810453A US 00190142 A US00190142 A US 00190142A US 19014271 A US19014271 A US 19014271A US 3810453 A US3810453 A US 3810453A
Authority
US
United States
Prior art keywords
chamber
pressure
valve
pump
fuel
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
US00190142A
Other languages
English (en)
Inventor
G Wolfe
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.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to US00190142A priority Critical patent/US3810453A/en
Priority to JP47103711A priority patent/JPS515132B2/ja
Priority to DE2251125A priority patent/DE2251125A1/de
Application granted granted Critical
Publication of US3810453A publication Critical patent/US3810453A/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
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift

Definitions

  • Fuel is pumped in cyclic pressure pulses the opposite side of the valve to augment the spring force urging the valve to its closed position.
  • the entire pulse is conducted at full pump pressure to the discharge chamber, thereby opening the valve and discharging fuel from the nozzle to the firing chamber of the engine.
  • the second chamber in the nozzle is connected to the pump chamber so that the two chambers at opposite sides of the valve are in fluid communication with the pump.
  • a positive pressure wave travels to the second chamber from the pump, thus temporarily dropping the pump output pressure until the system can become equalized.
  • control of the discharge of fuel from the injection nozzle is accomplished by means of a spring loaded valve which is unseated when the fuel pressure in the valve discharge chamber is high enough to open the valve against the biasing action of the valve spring.
  • the relatively high pressures employed are such that during the injecting cycle, the forces exerted on the valve by the fuel pressure substantially exceed the biasing force developed by the valve spring.
  • the fuel pressure must decrease substantially before the spring can drive the valve to its closed position.
  • a fuel pump having a reciprocatory piston driven by the engine is employed to pump fuel in cyclic pulses to an injection nozzle.
  • the nozzle is provided with .a spring loaded valve having one shoulder exposed to the pressure existing within the fuel discharge chamber from which fuel is expelled, when the valve is open, through conventional nozzle orifices.
  • the fuel discharge chamber communicates directly with the fuel pump output chambenA second chamber is formed in the nozzle with the opposite end of the valve exposed to pressure in the second chamber.
  • any pressure existing within the second chamber augments the biasing force of the valve spring to urge the valve toward its closed position.
  • a reduced diameter section is formed on the piston and isin constant communication with the pump chamber via an internal passage through the piston.
  • a port in the side of the cylinder in which the piston slides comes into communication with the reduced diameter section of the piston, thus permitting some of the fuel being compressed by the piston to leave the pump chamber via the internal passage through the piston and the reduced diameter section and the port.
  • This latter port is connected by a conduit to the second chamber in the injection nozzle.
  • the port is closed by the side of the piston and hence, the entire first portion of each pressure pulse generated by the piston is conducted from the pump chamber to the fuel discharge chamber in the nozzle.
  • uncovering of the port transmits a positive pressure pulse from-the pump chamber through the port and to the second chamber of the nozzle.
  • the pressure thus developed augments the spring force urging the valve to its closed position and, depending upon the spring setting, may immediately close the valve upon its arrival while full pump pressure still exists in the discharge chamber.
  • Full pump pressure will still exist in the discharge chamber at the time the positive pulse arrives in the second chamber due to the fact that the fluid path from the pump chamber to the discharge chamber is longer than the fluid path from the pump chamber to the second chamber of the injection nozzle.
  • a pressure increase is initiated in the newly connected portion of the system and this portion becomes pressurized.
  • This increase will, of course, arrive at the second nozzle chamber before the change in pressure is felt in the nozzle discharge chamber, hence a situation is created where the pressure in the second chamber, augmenting the spring force, is building up prior to the belated arrival of the negative pressure pulse from the pump chamber.
  • the system is so regulated that the pressure augmented spring force urging the valve to its closed position will overcome the opposing pressure force in the discharge chamber while the pressure in the discharge chamber is at or substantially at the full fuel injection pressure. This action results in a rapid closing of the valve while injection is still continuing at full pressure.
  • FIG. 1 is a schematic diagram, partially in crosssection, of one form of fuel injection system embodying the present invention.
  • a fuel injection system embodying the invention is shown as including a pump designated generally and an injection nozzle designated generally 12.
  • Pump 10 includes a casing 14 having an internal bore 16 within which a pump piston 18 is mounted for reciprocatory movement. Piston 18 is driven in reciprocatory movement by conventional means such as a cam 20 mounted on a rotary shaft 22 driven by the engine which is supplied with fuel by the present system.
  • the piston is just beginning its upward or pressure delivering stroke and pump chamber 24 is still in communciation with a constantly filled fuel supply chamber 26 via fuel inlet passage 28.
  • valve 32 As piston 18 moves upwardly beyond passage 28, pressure is developed in the fuel in chamber 24 above the piston and the fuel is discharged under pressure through a main outlet port 30 when the pressure developed in the fuel is sufficient to overcome the biasing action on a spring loaded differential valve 32. Upon opening of valve 32, fuel is discharged through a passage 34 in the pump casing to a main outlet conduit 36 connected to injection nozzle 12.
  • Piston 18 is formed with a reduced diameter section or groove 38, the forward wall of which is inclined to the piston axis as at 40.
  • An axially extending passage 42 and a communicating cross passage 44 place piston chamber 24 in constant communication with groove 38.
  • groove 38 moves into communication with a second discharge port 46 which communicates via an internal passage 50 through the pump casing with a secondary conduit 52 which is likewise connected to nozzle 12.
  • piston 18 is driven in continuous reciprocatory movement to discharge fuel from the pump in cyclic pressure pulses offinite time duration, each pressure pulse commencing at the moment piston 18 moves upwardly beyond fuel inlet passage 28 and terminating when piston 18 reaches the upward end of its stroke (assuming that groove 38 will not uncover port 28 as will be the case in some systems).
  • the sole outlet of chamber 24 is main outlet port 30.
  • the nozzle is provided with discharge orifices 56 which communicate via a bore 58 with a first internal chamber 60 formed within the nozzle.
  • a reciprocatory valve member 62 is slidably mounted within a bore 64 in nozzle 12 and is resiliently biased by a spring 66 to a closed position in which the valve head 68 is engaged with a valve seat 70 to block communication between chamber 60 and orifices 56.
  • Chamber 60 is in constant communication with conduit 36 via an inlet passage 72.
  • valve member 62 A downwardly facing shoulder 74 on valve member 62 is exposed to chamber 60 so that when the pressure of fuel in chamber 60 acting on shoulder 74 is sufficient to overcome the biasing action of spring 66, valve member 62 is driven upwardly to an open position in which head 68 is lifted clear of valve seat 70 to permit the discharge of fuel from chamber 60 through orifices 56.
  • valve spring 66 The internal bore 76 within which valve spring 66 is mounted is placed in fluid communication with conduit 52 via passage 78 in nozzle 12.
  • An upwardly facing surface 80 on valve member 62 is exposed to chamber 76 so that any fluid pressure developed in chamber 76 will act against surface 80 to apply a force urging valve member 62 downwardly toward its closed position.
  • the system shown in FIG. 1 is especially designed to provide a sharp cut off or termination of each pulse injected into the engine firing chamber from nozzle orifices 56.
  • Fuel injection systems of the type with which the present invention is concerned operate at very high injection pressures, in some cases as high as 10,000 PSI or more.
  • closing of the nozzle valve is accomplished solely by the spring loading of the valve which drives the valve back to its seat as the fuel pressure diminishes at the end of the injection cycle.
  • a sharp cutoff at the end of the injection cycle is achieved in the system of FIG. 1 by splitting the pressure pulse of fuel during the final portion of the pulse to apply a positive pressure to the upper side of injection valve 62 to augment the valve closing biasing force of spring 66, while continuing to supply fuel under pressure to chamber 60.
  • valve 62 may or may not close immediately upon the arrival of the pressure wave at surface 80, because the opposing pressure in chamber 60 at this instant is still at the original full pump pressure. Chamber 60 is still at full pump pressure because the path of travel from pump chamber 24 to injection chamber 60 via passage 34, conduit 36 and passage 72 is deliberately made longer than the fluid path from chamber 24 to surface 80 via passages 42, 44, groove 38, passage 50 and conduit 52.
  • the positive pressure pulse generated by the uncovering of port 46 arrives at surface 30, the corresponding negative pressure pulse traveling toward chamber 60 via conduit 36 and passage 72 has not yet arrived at chamber 60.
  • the magnitude of the pressure against surface 80 at the time of the arrival of the positive pressure pulse is inherently lower than the pressure in chamber 60 because of the pressure reduction in chamber 24 occasioned, in effect, by the extraction of the positive pressure pulse from chamber 24 by the uncovering of port 46.
  • the pressure against surface 80 will increase further as the system moves toward equalization and at some point in time the pressure exerted against surface 80 will reach a point at which this pressure, augmented by the force of spring 66, will act to close valve 62 against the pressure force in chamber 60.
  • valve 62 may be closed and injection terminated without any substantial drop in the injection pressure.
  • The. point in time at which valve 62 begins to close is the moment at which the combined force of spring 66 and the force developed by the pressure acting on surface 80 exceeds the opposing force exerted on the valve by the pressure in chamber '80.
  • closing of the valve may be accomplished either before the arrival of the negative pressure wave at chamber 60 or in response to the arrival of the negative pulse.
  • Chamber 76 is dimensioned such that together with the rest of the system and due to the compressibility of the fluid it can absorb the fluid displaced by piston 18 after the termination of injection. Pressure is relieved in the system during the return or downward stroke of piston 18 by exposing conduit 52 and passage 50 to the fuel supply pressure or sump via passage 82, uncovered when the piston is at its lower end of stroke. Excess pressure from chamber 76 and conduit 52 can also be vented from conduit 52 across ball check valve 84 into conduit 36 as piston 18 moves'downward prior to uncovering port 82.
  • a fuel injection system comprising an injection nozzle having an inlet passage, an internal chamber, and a discharge orifice, a valve member mounted in said nozzle for movement between an open position wherein said inlet passage is in communication with said discharge orifice and a closed position wherein said valve member blocks communication between said inlet passage and said orifice, biassing means biassing said valve member toward said closed position, said valve member having opposed surfaces thereon respectively exposed to said inlet passage and to said chamber for urging said valve member toward said open position in response to pressure in said inlet passage and for urging said valve member toward said closed position.
  • pump means for pumping fuel in cyclically generated pressure pulses
  • conduit means for conducting a first portion of each pressure pulse generated by said pump means to said inlet passage to move said valve member to an open position and for conducting a subsequent portion of each pressure pulse generated by said pump means to said inlet passage and said chamber to move said valve member to its closed position.
  • said pump means comprises a piston reciprocable within a pump chamber
  • said conduit means comprises a first conduit connecting said pump chamber to said inlet passage, a second conduit in constant communication with said chamber in said nozzle, and passage means in said pump piston for placing said second conduit in commu- I nication with said pump chamber during a selected portion of the cyclic movement of said piston.
  • a system as defined in claim 3 further comprising means for adjustably selecting the range of movement of said piston over which said second conduit is in communication with said pump chamber.
  • a system as defined in claim 3 having passage means for venting said second conduit cyclically, said passage means being connected with an area of lower pressure during a selected portion of the cyclic movement of said piston.
  • a system as defined in claim 3 further comprising means to store the fuel displaced by said piston after the end of injection, and means to vent said fuel during a selected portion of the cyclic movement of said piston.
  • valve means for venting said first conduit, said valve means determining the pressure remaining in said first conduit after the end of the injection.
  • valve means being adjustable in respect to the pressure at which said venting is terminated.
  • a system as defined in claim 1 having passage means connecting said inlet passage and said internal .chamber, and valve means normally preventing flow through said passage means from said inlet passage to said internal chamber.
  • step of pumping fuel is performed by a cyclically operable positive displacement pump having an outlet chamber in constant communication with said one side of said valve, and the step of splitting the final portion of said pulse comprises the step of placing said outlet chamber in communication with said other side of said valve during the final portion of each pulse generating cycle of said pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
US00190142A 1971-10-18 1971-10-18 Fuel injection system Expired - Lifetime US3810453A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US00190142A US3810453A (en) 1971-10-18 1971-10-18 Fuel injection system
JP47103711A JPS515132B2 (de) 1971-10-18 1972-10-18
DE2251125A DE2251125A1 (de) 1971-10-18 1972-10-18 Brennstoffeinspritzsystem und verfahren zur zyklischen erzeugung eines hochdruckstosses innerhalb eines derartigen systems

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00190142A US3810453A (en) 1971-10-18 1971-10-18 Fuel injection system

Publications (1)

Publication Number Publication Date
US3810453A true US3810453A (en) 1974-05-14

Family

ID=22700175

Family Applications (1)

Application Number Title Priority Date Filing Date
US00190142A Expired - Lifetime US3810453A (en) 1971-10-18 1971-10-18 Fuel injection system

Country Status (3)

Country Link
US (1) US3810453A (de)
JP (1) JPS515132B2 (de)
DE (1) DE2251125A1 (de)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3952711A (en) * 1975-03-04 1976-04-27 Ambac Industries, Inc. Diesel injection nozzle with independent opening and closing control
US3965875A (en) * 1973-07-02 1976-06-29 Cummins Engine Company, Inc. Fuel injection system for diesel engines
US4036192A (en) * 1974-02-08 1977-07-19 Diesel Kiki Co. Engine fuel injection system
US4069800A (en) * 1975-01-24 1978-01-24 Diesel Kiki Co., Ltd. Fuel injection apparatus
US4141329A (en) * 1976-04-30 1979-02-27 Foster-Miller Associates, Inc. Internal combustion engine fuel injection system
US4165724A (en) * 1976-07-01 1979-08-28 Nippondenso Co., Ltd. Fuel injection system for internal combustion engine
US4167168A (en) * 1976-02-05 1979-09-11 Nippondenso Co., Ltd. Fuel injection apparatus
USRE30189E (en) * 1973-07-02 1980-01-15 Cummins Engine Company Fuel injection system for diesel engines
US4475515A (en) * 1981-09-05 1984-10-09 Lucas Industries Public Limited Company Fuel systems for compression ignition engines
US4545352A (en) * 1983-02-21 1985-10-08 Regie Nationale Des Usines Renault Electromagnetic control injection systems for diesel engines of the pressure-time type where the injector needle is controlled by the charging and discharging of a chamber
EP0178427A2 (de) * 1984-09-14 1986-04-23 Robert Bosch Gmbh Elektrisch gesteuerte Kraftstoffeinspritzpumpe für Brennkraftmaschinen
US4598863A (en) * 1983-01-20 1986-07-08 Usui Kokusai Sangyo Kabushiki Kaisha Fuel injector
EP0204982A2 (de) * 1985-06-14 1986-12-17 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
US4711216A (en) * 1985-05-16 1987-12-08 Nippon Soken, Inc. Fuel supply device for an internal combustion engine
US4712528A (en) * 1979-02-24 1987-12-15 Institut fur Motorenbau Professor Huber e.V. Fuel injection system
US5012786A (en) * 1990-03-08 1991-05-07 Voss James R Diesel engine fuel injection system
US5076239A (en) * 1987-04-15 1991-12-31 Perkins Engines Group Limited Fuel injection system
US5315978A (en) * 1992-03-25 1994-05-31 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Fuel injection system
US5339786A (en) * 1989-01-11 1994-08-23 Martin Tiby M High pressure electronic common-rail fuel injection system for diesel engines
US5551391A (en) * 1988-02-03 1996-09-03 Servojet Electronic Systems, Ltd. Accumulator fuel injection system
US5950600A (en) * 1997-11-18 1999-09-14 Elasis Sistema Ricerca Fiat Nel Mezzogiorno Societa Consortile Per Azioni Device for controlling an internal combustion engine fuel injector
US6269795B1 (en) * 1997-11-27 2001-08-07 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
US6360727B1 (en) 2000-03-14 2002-03-26 Alfred J. Buescher Reduce initial feed rate injector with fuel storage chamber
US20070272199A1 (en) * 2003-10-28 2007-11-29 Yanmar Co., Ltd. Reverse Rotation Preventing Mechanism For Diesel Engine
CN102239327A (zh) * 2008-10-27 2011-11-09 现代重工业株式会社 一种用于柴油机的燃油喷射泵的防气蚀损伤装置

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5321047B2 (de) * 1973-08-07 1978-06-30
DE2742870C2 (de) * 1977-09-23 1979-11-15 Kloeckner-Humboldt-Deutz Ag, 5000 Koeln Kraftstoff einspritzvorrichtung
JPS559854U (de) * 1978-07-06 1980-01-22
JPS5515384A (en) * 1978-07-20 1980-02-02 Kubota Ltd Operation car
JPS6015709Y2 (ja) * 1979-01-16 1985-05-17 ヤンマーディーゼル株式会社 農用トラクタの４輪駆動切換装置
JPS5637090Y2 (de) * 1980-02-21 1981-08-31
JPS601369A (ja) * 1983-06-16 1985-01-07 Nippon Soken Inc 燃料噴射弁
DE3523536A1 (de) * 1984-09-14 1986-03-27 Robert Bosch Gmbh, 7000 Stuttgart Elektrisch gesteuerte kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3521427A1 (de) * 1985-06-14 1986-12-18 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzvorrichtung
DE3912106C2 (de) * 1988-05-02 1996-05-02 Volkswagen Ag Kraftstoffeinspritzvorrichtung

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1802933A (en) * 1928-08-10 1931-04-28 Sulzer Ag Fuel-injection device for internal-combustion engines
US2916028A (en) * 1955-01-14 1959-12-08 British Internal Combust Eng Fuel injection systems
US3625192A (en) * 1969-12-12 1971-12-07 Allis Chalmers Mfg Co Fuel injection nozzle with hydraulic valve-closing means

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1802933A (en) * 1928-08-10 1931-04-28 Sulzer Ag Fuel-injection device for internal-combustion engines
US2916028A (en) * 1955-01-14 1959-12-08 British Internal Combust Eng Fuel injection systems
US3625192A (en) * 1969-12-12 1971-12-07 Allis Chalmers Mfg Co Fuel injection nozzle with hydraulic valve-closing means

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3965875A (en) * 1973-07-02 1976-06-29 Cummins Engine Company, Inc. Fuel injection system for diesel engines
USRE30189E (en) * 1973-07-02 1980-01-15 Cummins Engine Company Fuel injection system for diesel engines
US4036192A (en) * 1974-02-08 1977-07-19 Diesel Kiki Co. Engine fuel injection system
US4069800A (en) * 1975-01-24 1978-01-24 Diesel Kiki Co., Ltd. Fuel injection apparatus
US3952711A (en) * 1975-03-04 1976-04-27 Ambac Industries, Inc. Diesel injection nozzle with independent opening and closing control
US4167168A (en) * 1976-02-05 1979-09-11 Nippondenso Co., Ltd. Fuel injection apparatus
US4141329A (en) * 1976-04-30 1979-02-27 Foster-Miller Associates, Inc. Internal combustion engine fuel injection system
US4165724A (en) * 1976-07-01 1979-08-28 Nippondenso Co., Ltd. Fuel injection system for internal combustion engine
US4712528A (en) * 1979-02-24 1987-12-15 Institut fur Motorenbau Professor Huber e.V. Fuel injection system
US4475515A (en) * 1981-09-05 1984-10-09 Lucas Industries Public Limited Company Fuel systems for compression ignition engines
US4598863A (en) * 1983-01-20 1986-07-08 Usui Kokusai Sangyo Kabushiki Kaisha Fuel injector
US4545352A (en) * 1983-02-21 1985-10-08 Regie Nationale Des Usines Renault Electromagnetic control injection systems for diesel engines of the pressure-time type where the injector needle is controlled by the charging and discharging of a chamber
EP0178427A3 (en) * 1984-09-14 1987-12-09 Robert Bosch Gmbh Electrically controlled fuel injection pump for internalelectrically controlled fuel injection pump for internal combustion engines combustion engines
EP0178427A2 (de) * 1984-09-14 1986-04-23 Robert Bosch Gmbh Elektrisch gesteuerte Kraftstoffeinspritzpumpe für Brennkraftmaschinen
US4711216A (en) * 1985-05-16 1987-12-08 Nippon Soken, Inc. Fuel supply device for an internal combustion engine
EP0204982A2 (de) * 1985-06-14 1986-12-17 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
US4750462A (en) * 1985-06-14 1988-06-14 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
EP0204982A3 (en) * 1985-06-14 1989-02-22 Robert Bosch Gmbh Fuel injection for internal-combustion engines
US5076239A (en) * 1987-04-15 1991-12-31 Perkins Engines Group Limited Fuel injection system
US5551391A (en) * 1988-02-03 1996-09-03 Servojet Electronic Systems, Ltd. Accumulator fuel injection system
US5339786A (en) * 1989-01-11 1994-08-23 Martin Tiby M High pressure electronic common-rail fuel injection system for diesel engines
US5012786A (en) * 1990-03-08 1991-05-07 Voss James R Diesel engine fuel injection system
US5315978A (en) * 1992-03-25 1994-05-31 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Fuel injection system
US5950600A (en) * 1997-11-18 1999-09-14 Elasis Sistema Ricerca Fiat Nel Mezzogiorno Societa Consortile Per Azioni Device for controlling an internal combustion engine fuel injector
US6269795B1 (en) * 1997-11-27 2001-08-07 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
US6360727B1 (en) 2000-03-14 2002-03-26 Alfred J. Buescher Reduce initial feed rate injector with fuel storage chamber
US20070272199A1 (en) * 2003-10-28 2007-11-29 Yanmar Co., Ltd. Reverse Rotation Preventing Mechanism For Diesel Engine
US7441531B2 (en) * 2003-10-28 2008-10-28 Yanmar Co., Ltd. Reverse rotation preventing mechanism for diesel engine
CN102239327A (zh) * 2008-10-27 2011-11-09 现代重工业株式会社 一种用于柴油机的燃油喷射泵的防气蚀损伤装置
CN102239327B (zh) * 2008-10-27 2013-06-05 现代重工业株式会社 一种用于柴油机的燃油喷射泵的防气蚀损伤装置

Also Published As

Publication number Publication date
DE2251125A1 (de) 1973-04-26
JPS4848826A (de) 1973-07-10
JPS515132B2 (de) 1976-02-17

Similar Documents

Publication Publication Date Title
US3810453A (en) Fuel injection system
US4396151A (en) Fuel injection system for internal combustion engines
US4069800A (en) Fuel injection apparatus
US2090781A (en) Fuel pump for internal combustion engines
GB1577092A (en) Pumping nozzle for internal combustion engines
GB1390422A (en) Fuel injection systems for internal combustion engines
GB1391327A (en) Fuel injection devices for internal combustion engines
JPS6339790B2 (de)
JPH06510581A (ja) 噴射装置
US2055578A (en) Fuel supply and regulating system for internal combustion engines
GB1512134A (en) Fuel injection pump
US3625192A (en) Fuel injection nozzle with hydraulic valve-closing means
US3342422A (en) Fuel injection apparatus for internal combustion engines
GB1314017A (en) Fuel injection nozzles
US3456629A (en) Fuel injection devices for compression ignited internal combustion engines
JPS63295854A (ja) 燃料噴射ポンプ
US2537087A (en) Fuel injection apparatus
GB1306422A (en) Fuel injection pumps for internal combustion engines
US2612842A (en) Fuel injection pump
US3893629A (en) Fuel injection device for diesel engines
US4082481A (en) Fuel injection pumping apparatus
US3667438A (en) Fuel injecting device for an internal combustion engine
US2513883A (en) Fuel pump for engines
JPS6120303Y2 (de)
JPS6134347A (ja) 燃料ポンプ装置