EP0657642A2 - Dispositif d'injection de combustible pour moteurs à combustion interne - Google Patents

Dispositif d'injection de combustible pour moteurs à combustion interne Download PDF

Info

Publication number
EP0657642A2
EP0657642A2 EP94113010A EP94113010A EP0657642A2 EP 0657642 A2 EP0657642 A2 EP 0657642A2 EP 94113010 A EP94113010 A EP 94113010A EP 94113010 A EP94113010 A EP 94113010A EP 0657642 A2 EP0657642 A2 EP 0657642A2
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
chamber
injection
injection device
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.)
Granted
Application number
EP94113010A
Other languages
German (de)
English (en)
Other versions
EP0657642B1 (fr
EP0657642A3 (fr
Inventor
Peter Dipl.-Ing. Müller
Jaroslaw Dipl.-Ing. Hlousek
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0657642A2 publication Critical patent/EP0657642A2/fr
Publication of EP0657642A3 publication Critical patent/EP0657642A3/fr
Application granted granted Critical
Publication of EP0657642B1 publication Critical patent/EP0657642B1/fr
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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention is based on a fuel injection device for internal combustion engines according to the preamble of claim 1.
  • a high-pressure fuel pump delivers fuel from a low-pressure chamber to a high-pressure collecting chamber, which is connected via high-pressure lines to the individual injection valves projecting into the combustion chamber of the internal combustion engine to be supplied, this common pressure storage system being operated by a pressure control device is kept at a certain pressure.
  • an electrically controlled control valve is inserted into the high-pressure lines, which controls the opening and closing of the high-pressure fuel injection at the injection valve.
  • each injection valve which is filled by the common pressure storage system and which, in addition to the high-pressure line leading away from the high-pressure collection space, also with the Injector is connected.
  • the injection process can be optimally adapted to the requirements of the respective internal combustion engine in connection with a throttled outflow of fuel from a pressure chamber acting on the valve member of the injection valve become, in particular a slow pressure increase at the beginning and a high pressure increase at the end of the injection can be achieved.
  • the quantity of fuel supplied directly to the injection valve from the common high-pressure accumulation chamber is used only as a control means for controlling the lifting movement of the valve member of the injection valve, while the injection quantity is completely removed from the respective smaller pressure storage chamber.
  • the known fuel injection device has the disadvantage that the high system pressure is constantly applied to the injection valve member due to the hydraulic connection between the pressure storage chamber and the pressure chamber on the injection valve member, which results in a high mechanical load on the injection valve.
  • the control of the injection process by means of the hydraulic blocking or relief of a pressure chamber on the valve member of the injection valve by the fuel in the pressure storage system causes pressure fluctuations in the system, as a result of which the control processes on the individual injection valves connected via the high-pressure lines can influence one another, which results in inaccuracies .
  • the arrangement of two high-pressure lines per injection valve and the associated pressure connections increases the manufacturing outlay, so that the known fuel injection device does not meet the current high requirements with regard to a structurally simple structure, high injection accuracy over a long operating time and high operational reliability.
  • the fuel injection device according to the invention with the characterizing features of claim 1 has the advantage that the injection valve is separated from the pressure system by the control valve during the injection breaks, so that the high system pressure is not constantly applied to the injection valve. In addition to a lower mechanical load on the injection valve, this also results in the valve member of the injection valve being closed by its valve spring and being able to be kept in the closed state, which makes high pressurization of the valve member in the closing direction superfluous and thus contributes to simplifying the entire injection device .
  • Another advantage is achieved by the through hole in the piston-shaped valve member of the control valve, via which the fuel under high pressure flows out of the high-pressure area within the control valve during the injection pauses into a relief chamber and via which pressure equalization at both valve member end faces, or at the latter, is constant adjoining rooms.
  • the volume of the pressure storage spaces assigned to the injection valves is 5 to 20 times larger than the maximum injection quantity at the injection valve executed, the fuel pressure reflected at the injection valve at the start of the injection in the pressure storage space being used to increase the pressure to a value above the system pressure.
  • This pressure increase can be adjusted via the afterflow into the pressure accumulator, which can be adjusted by the dimensioning of the high-pressure line and a pressure valve in the inlet, in such a way that the highest fuel pressure in the system is built up towards the end of the injection.
  • a flow restrictor inserted in the pressure connection of the pressure accumulator prevents the pressure fluctuations from propagating into the system.
  • FIG. 1 shows a schematic illustration of the fuel injection device with a longitudinal section through the control valve and the injection valve
  • FIG. 2 shows the design of the valve seats and sealing surfaces of the control valve in an enlarged detail from FIG. 1.
  • a high-pressure fuel pump 1 is connected on the suction side via a fuel supply line 3 to a fuel-filled low-pressure chamber 5 and on the pressure side via a delivery line 7 to a high-pressure collecting chamber 9, the delivery rate of the High-pressure fuel pump 1 can be controlled by an electrical control unit 11.
  • High-pressure lines 13 lead from the high-pressure plenum 9 to the individual injection valves 15 projecting into the combustion chamber of the internal combustion engine to be supplied, an electric control valve 17 being inserted in each injection valve 15 into the respective high-pressure line 13 to control the injection process.
  • a further pressure storage chamber 19 is provided in each high-pressure line 13 between the high-pressure collection chamber 9 and the control valve 17, the volume of which is approximately 5 to 20 times larger than the maximum injection quantity at the injection valve 15 per injection process and which has two parallel pressure connections with the one leading to the high-pressure collection chamber 9 Part of the high pressure line 13 is connected.
  • a first pressure connection 21 has a pressure valve 23 opening in the direction of the pressure storage space 19 and designed as a check valve
  • a second pressure connection 25 has a throttle point 27, with an uncontrolled backflow of fuel into the part of the high pressure line 13 leading to the high pressure collection space 9 via the throttle 27 and one Influencing of the pressure in the pressure storage spaces of the other injection valves is to be avoided, while the pressure valve 23 enables rapid refilling of the pressure storage space 19. It can be adjusted via the design of the throttle 27 and the pressure valve 23 depending on the dimensioning of the high pressure line 13, the inflow and outflow into the pressure storage chamber 19, in particular during high pressure injection, throttle 27 and pressure valve 23 also in a common pressure connection, in series can be arranged switched.
  • the control valve 17 is designed as a 3/2-way valve, the piston-shaped valve member 29 of which acts on its one end against a compression spring 35 which is supported between the housing 31 and a spring plate 33 on the valve member 29 Actuating magnet 37 is actuated, the energization of which is controlled by control unit 11.
  • the valve member 29 has an annular web 39 on its shaft, the lower transition surface of the piston shaft facing away from the actuating magnet 37 is conical and thereby forms a first conical sealing surface 41 on the valve member 29, which cooperates with a conical valve seat 43.
  • This conical valve seat 43 shown enlarged in FIG.
  • valve member 29 is formed by a conical diameter widening of a guide bore 49, which receives a guide piston part 45 on the valve member 29, within the housing 31 of the control valve 17.
  • annular groove 47 is provided on the valve member 29, which forms a pressure chamber 51 with the wall of the guide bore 49, which is separated from the guide piston part 45 and the conical valve sealing surface 41 on the annular web 39 is limited and in which a part of the high-pressure line 13 leading away from the pressure storage chamber 19 to the control valve 17 opens in such a way that the opening cannot be closed by the valve member 29 during the lifting movement of the valve member 29.
  • the transition from the ring web 39 to the piston skirt facing the actuating magnet 37 takes place via a ring shoulder 53, the resulting axially directed ring surface on the ring shoulder 53 forming a second flat sealing surface 55 which, with a flat valve seat 59 surrounding a bore 57, on the axial end face of an intermediate piece 61 cooperates, the piston shaft continuing through the bore 57 to the actuating magnet 37 and thereby protruding with its end into a spring space 63 receiving the compression spring 35 of the valve member 29.
  • the outer diameter of the ring shoulder 53 carrying the flat axial sealing surface 55 on the ring web 39 is equal to the diameter of the guide piston part 45 for pressure equalization at the open control valve 17.
  • the stroke movement of the valve member 29 is in each case by contact the sealing surfaces 41, 55 limited to one of the valve seats 43, 59.
  • the annular web 39 is arranged in an annular space bounded by the respective valve seats 43, 59 and forming an antechamber 65, from which a pressure line 67 leads to the injection valve 15 and a relief channel 69.
  • This relief channel 69 is partially formed by a remaining annular gap between the piston skirt and the bore 57 in the intermediate piece 61, which is formed with its outer diameter smaller than the sealing surface 55 and can thus be closed by it.
  • the bore 57 opens into the spring chamber 63, which acts as the return spring 35 of the valve member 29, and is provided with transverse bores 73 that intersect an axial through-bore 71 in the valve member 29 with a boundary of the end face of the guide piston 45 of the valve member 29 facing away from the actuating magnet 37 Relief chamber 75 connected.
  • This relief space 75 formed within the guide bore 49 continues axially in the direction facing away from the actuating magnet 37 into a spring space 77 of the injection valve 15, in which a valve spring 81 acting on a valve member 79 of the injection valve 15 in the closing direction is arranged and from which a return line 83 into the Low pressure space 5 leads away.
  • the valve member 79 of the injection valve 15 is provided in a known manner with a conical pressure shoulder 85 which projects into a pressure chamber 87 connected to the pressure line 67 such that the pressure in the pressure chamber 87 acts on the valve member 79 in the opening direction. Furthermore, an injection channel 89 leads from the pressure chamber 87 along the valve member 79 to one or more injection openings 91 of the injection valve 15, which are controlled by the sealing surface at the tip of the valve member 79, into the combustion chamber, not shown, of the internal combustion engine to be supplied.
  • the fuel injection device according to the invention works in the following way.
  • the high-pressure fuel pump 1 delivers the fuel from the Low-pressure chamber 5 in the high-pressure collection chamber 9 and thus builds up a high-pressure fuel in this, which is adjustable via the control of the high-pressure pump 1.
  • This high fuel pressure continues via the high-pressure lines 13 into the pressure chamber 51 of the individual control valves 17 on the injection valves 15 and also fills the respective pressure storage chambers 19 via the pressure valves 23.
  • the actuating magnet 37 is energized and moves the valve member 29 of the control valve 17 against the restoring force of the spring 35 until its flat valve sealing surface 55 abuts the flat valve seat 59.
  • the connection of the antechamber 65 to the relief channel 69 is closed and opened to the pressure line 67, so that the high fuel pressure now continues from the pressure chamber 51 via the antechamber 65 and the pressure line 67 to the pressure chamber 87 of the injection valve 15 and there, in a known manner, by lifting the valve member 79 from its valve seat, the injection at the injection openings 91 he follows.
  • a pressure increase over the system pressure can be achieved in the following manner in the pressure line 67 during the injection phase.
  • the pressure chamber 51 is connected to the antechamber 65 and a flow begins in the direction of the transverse bore 73 and through bore 71 up to the pressure-free return line 83.
  • This flow caused in a further consequence is a flow in the line connection from the pressure storage space 19 to the pressure space 51 and in the line 13 between the pressure storage space 19 and the high pressure collection space 9.
  • the fuel flow is directed in the direction of the pressure line 67.
  • the build-up effect of the fuel flow in motion creates an excess pressure there.
  • This pressure increase can be influenced by a suitable choice of the influencing variables line length, line diameter, storage volume, throttle cross-section, etc.
  • a pressure increase in the injection pressure above the value of the system pressure can be achieved by partially reflecting the fuel pressure wave running to the injection valve 15 at the injection valve, returning to the pressure accumulator 19 and causing a pressure increase in this, which is caused by the flow energy of the fuel flowing in from the high-pressure collecting chamber 9 and the dimensioning of the throttle 27, which prevents rapid pressure reduction, can be set.
  • This increased fuel pressure then reaches the injection valve 15 again and increases its injection rate towards the end of the injection.
  • the course of injection at the injection valve 15 can also be shaped via the opening cross section on the valve member 29 (diameter / stroke), the volume of the antechamber 65 and the pressure line 67 and the volume of the pressure accumulator 19.
  • the actuating magnet 37 is again de-energized and the compression spring 35 brings the valve member 29 of the control valve 17, which is pressure-compensated by the ring shoulder 53, into contact with the conical valve seat 43 again in the open state.
  • the opening cross section on the flat valve seat 59 is opened and the fuel under high pressure relaxes via the relief channel 69, the spring chamber 63, the transverse and longitudinal bores 73, 71 in the valve member 29 in the relief chamber 75, from where the fuel flows through the spring chamber 77 and the return line 83 into the low-pressure chamber 5, so that the valve member 79 of the injection valve 15 is depressurized under the action of the valve spring 81 in the closed position and the valve member 29 is pressure-balanced again.
  • the cross section of the relief channel 69 is designed so that it ensures a rapid pressure drop in the pressure line 67 below the closing pressure of the injection valve 15, but on the other hand throttles the outflow from the pressure line 67 so that a residual pressure in the pressure line 67 and the injection valve 15 remains.
  • the volume of the pressure accumulator space 19 and the cross section of the throttle 27 in the pressure connection 25 serving as the return line must be coordinated such that the pressure peaks within the pressure accumulator space 19 and be dismantled to the high-pressure plenum 9.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP94113010A 1993-12-07 1994-08-20 Dispositif d'injection de combustible pour moteurs à combustion interne Expired - Lifetime EP0657642B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4341543A DE4341543A1 (de) 1993-12-07 1993-12-07 Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE4341543 1993-12-07

Publications (3)

Publication Number Publication Date
EP0657642A2 true EP0657642A2 (fr) 1995-06-14
EP0657642A3 EP0657642A3 (fr) 1995-12-06
EP0657642B1 EP0657642B1 (fr) 1999-01-13

Family

ID=6504295

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94113010A Expired - Lifetime EP0657642B1 (fr) 1993-12-07 1994-08-20 Dispositif d'injection de combustible pour moteurs à combustion interne

Country Status (4)

Country Link
US (1) US5497750A (fr)
EP (1) EP0657642B1 (fr)
JP (1) JP3655938B2 (fr)
DE (2) DE4341543A1 (fr)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998031933A1 (fr) 1997-01-21 1998-07-23 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs a combustion interne
WO1999015783A1 (fr) 1997-09-24 1999-04-01 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs a combustion interne
EP0915254A2 (fr) * 1997-11-06 1999-05-12 DaimlerChrysler AG Injecteur commandé par une vanne magnétique pour un système d' accumulation d'un moteur à combustion interne à plusieurs cylindres
WO2001031193A2 (fr) 1999-10-26 2001-05-03 Robert Bosch Gmbh Injecteur de carburant a limitation de debit integree
WO2002025098A1 (fr) * 2000-09-20 2002-03-28 L'orange Gmbh Soupape de commande pour injecteurs
FR2816367A1 (fr) 2000-11-07 2002-05-10 Bosch Gmbh Robert Injecteur commande en pression pour injecter du carburant avec une double soupape
FR2816368A1 (fr) 2000-11-08 2002-05-10 Bosch Gmbh Robert Injecteur commande en pression dans un systeme d'injection a haute pression de vehicules automobiles
FR2816665A1 (fr) 2000-11-13 2002-05-17 Bosch Gmbh Robert Injecteur a dispositif de commande en cascade et alimente a partir d'une rampe commune
FR2817297A1 (fr) 2000-11-29 2002-05-31 Bosch Gmbh Robert Systeme d'injection de carburant dans un moteur a combustion interne
FR2817918A1 (fr) 2000-12-07 2002-06-14 Bosch Gmbh Robert Injecteur de carburant a haute pression commande en pression avec un comportement d'ouverture et de fermeture etage
DE10114252A1 (de) * 2001-03-22 2002-09-26 Mtu Friedrichshafen Gmbh Verfahren zum Einspritzen von Kraftstoff in die Brennräume einer Brennkraftmaschine, sowie Kraftstoffeinspritzsystem für eine solche
DE10149868C1 (de) * 2001-10-10 2002-12-05 Orange Gmbh Einspritzinjektor für Brennkraftmaschinen
US6561768B2 (en) 2000-11-30 2003-05-13 Robert Bosch Gmbh Device for supplying liquids, in particular, fuel
US6816050B2 (en) 2001-10-22 2004-11-09 Robert Bosch Gmbh Size-reduced magnet coil carrier
DE10055269B4 (de) * 2000-11-08 2005-10-27 Robert Bosch Gmbh Druckgesteuerter Injektor mit Druckübersetzung
WO2007009279A1 (fr) * 2005-07-18 2007-01-25 Ganser-Hydromag Ag Systeme d'injection d'accumulateur pour moteur a combustion interne
DE102017201262A1 (de) 2016-03-18 2017-09-21 Ganser Crs Ag Speichereinspritzsystem für Verbrennungskraftmaschinen

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5669355A (en) * 1994-07-29 1997-09-23 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5687693A (en) 1994-07-29 1997-11-18 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5526791A (en) * 1995-06-07 1996-06-18 Diesel Technology Company High-pressure electromagnetic fuel injector
DE19712135C1 (de) 1997-03-22 1998-08-13 Mtu Friedrichshafen Gmbh Kraftstoffeinspritzsystem für eine Brennkraftmaschine
DE19715234A1 (de) * 1997-04-12 1998-06-25 Daimler Benz Ag Magnetventilgesteuertes direkteinspritzendes Kraftstoffeinspritzventil für Speichereinspritzsysteme von mehrzylindrigen Brennkraftmaschinen
DE19720913C1 (de) * 1997-05-16 1998-08-20 Mtu Friedrichshafen Gmbh Kraftstoffeinspritzsystem mit gemeinsamem Vorspeicher
DE19732070C2 (de) * 1997-07-25 2001-02-01 Daimler Chrysler Ag Direkteinspritzendes Kraftstoffeinspritzventil mit Magnetventilsteuerung für eine mehrzylindrige Brennkraftmaschine
DE19753072C2 (de) * 1997-11-29 1999-11-18 Bosch Gmbh Robert Kraftstoffversorgungssystem für eine Brennkraftmaschine insbesondere eines Kraftfahrzeugs
US6026785A (en) * 1998-05-08 2000-02-22 Caterpillar Inc. Hydraulically-actuated fuel injector with hydraulically assisted closure of needle valve
US6364282B1 (en) 1998-12-04 2002-04-02 Caterpillar Inc. Hydraulically actuated fuel injector with seated pin actuator
DE19859175A1 (de) * 1998-12-21 2000-06-29 Siemens Ag Verfahren zum Entlüften eines Kraftstoffversorgungssystems
DE19860678A1 (de) * 1998-12-29 2000-07-06 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE19910970A1 (de) * 1999-03-12 2000-09-28 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung
DE19919665A1 (de) * 1999-04-29 2000-11-02 Volkswagen Ag Kraftstoffeinspritzvorrichtung
DE19928906A1 (de) * 1999-06-24 2001-01-11 Bosch Gmbh Robert Common-Rail-Injektor
DE19928846A1 (de) * 1999-06-24 2001-03-08 Bosch Gmbh Robert Common-Rail-Injektor
DE19939428A1 (de) * 1999-08-20 2001-03-01 Bosch Gmbh Robert Verfahren und Vorrichtung zur Durchführung einer Kraftstoffeinspritzung
DE19942990A1 (de) 1999-09-09 2001-03-22 Bosch Gmbh Robert Common-Rail-Injektor
DE10032923A1 (de) * 2000-07-06 2002-01-24 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE10060811A1 (de) * 2000-12-07 2002-06-13 Bosch Gmbh Robert Kraftstoffeinspritzsystem für Brennkraftmaschinen
DE10105031A1 (de) * 2001-02-05 2002-08-14 Bosch Gmbh Robert Vorrichtung zur Dämpfung von Druckpulsationen in Hochdruckeinspritzsystemen
DE10143423A1 (de) * 2001-09-05 2003-05-08 Bosch Gmbh Robert Kraftstoffeinspritzsystem mit hydraulisch von der Zuleitung entkoppeltem Injektor
US7124746B2 (en) 2002-07-16 2006-10-24 Brocco Douglas S Method and apparatus for controlling a fuel injector
US7021565B2 (en) * 2004-02-10 2006-04-04 Caterpillar Inc. Pressure modulated common rail injector and system
EP1584815A1 (fr) * 2004-04-05 2005-10-12 Tiby M. Martin Soupape d'injection par accumulation
WO2009033304A1 (fr) * 2007-09-13 2009-03-19 Ganser-Hydromag Ag Dispositif d'injection de carburant
US20110297125A1 (en) * 2010-06-03 2011-12-08 Caterpillar Inc. Reverse Flow Check Valve For Common Rail Fuel System
DE102021200154A1 (de) * 2021-01-11 2022-07-14 Robert Bosch Gesellschaft mit beschränkter Haftung Kraftstoffeinspritzvorrichtung

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2449795A1 (fr) * 1979-02-24 1980-09-19 Huber Motorenbau Inst Systeme d'injection pour moteur a combustion interne
US4360163A (en) * 1981-01-19 1982-11-23 General Motors Corporation Electromagnetic diesel fuel 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

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS51101628A (fr) * 1975-01-24 1976-09-08 Diesel Kiki Co
JPS5939963A (ja) * 1982-08-27 1984-03-05 Nippon Denso Co Ltd 燃料噴射装置
JPS5941658A (ja) * 1982-08-31 1984-03-07 Yanmar Diesel Engine Co Ltd 低重質油燃料噴射装置
USRE33270E (en) * 1982-09-16 1990-07-24 Bkm, Inc. Pressure-controlled fuel injection for internal combustion engines
JPS6111447A (ja) * 1984-06-27 1986-01-18 Nippon Denso Co Ltd 燃料噴射弁
ATE98340T1 (de) * 1986-09-25 1993-12-15 Ganser Hydromag Elektronisch gesteuertes einspritzsystem.
JP2712760B2 (ja) * 1990-05-29 1998-02-16 トヨタ自動車株式会社 燃料噴射弁
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

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2449795A1 (fr) * 1979-02-24 1980-09-19 Huber Motorenbau Inst Systeme d'injection pour moteur a combustion interne
US4360163A (en) * 1981-01-19 1982-11-23 General Motors Corporation Electromagnetic diesel fuel 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

Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998031933A1 (fr) 1997-01-21 1998-07-23 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs a combustion interne
WO1999015783A1 (fr) 1997-09-24 1999-04-01 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs a combustion interne
EP0915254A3 (fr) * 1997-11-06 2002-07-17 DaimlerChrysler AG Injecteur commandé par une vanne magnétique pour un système d' accumulation d'un moteur à combustion interne à plusieurs cylindres
EP0915254A2 (fr) * 1997-11-06 1999-05-12 DaimlerChrysler AG Injecteur commandé par une vanne magnétique pour un système d' accumulation d'un moteur à combustion interne à plusieurs cylindres
WO2001031193A2 (fr) 1999-10-26 2001-05-03 Robert Bosch Gmbh Injecteur de carburant a limitation de debit integree
DE19951554A1 (de) * 1999-10-26 2001-05-10 Bosch Gmbh Robert Kraftstoffinjektor mit integrierter Durchflussbegrenzung
DE10066102B4 (de) * 2000-09-20 2004-12-16 L'orange Gmbh Steuerventil für einen Einspritzinjektor
DE10046829C2 (de) * 2000-09-20 2003-01-09 Orange Gmbh Steuerventil für Einspritzinjektoren von Brennkraftmaschinen
WO2002025098A1 (fr) * 2000-09-20 2002-03-28 L'orange Gmbh Soupape de commande pour injecteurs
DE10046829A1 (de) * 2000-09-20 2002-04-04 Orange Gmbh Steuerventil für Einspritzinjektoren
US6669108B2 (en) 2000-11-07 2003-12-30 Robert Bosch Gmbh Pressure-control injector for injecting fuel with a double valve
FR2816367A1 (fr) 2000-11-07 2002-05-10 Bosch Gmbh Robert Injecteur commande en pression pour injecter du carburant avec une double soupape
FR2816368A1 (fr) 2000-11-08 2002-05-10 Bosch Gmbh Robert Injecteur commande en pression dans un systeme d'injection a haute pression de vehicules automobiles
DE10055269B4 (de) * 2000-11-08 2005-10-27 Robert Bosch Gmbh Druckgesteuerter Injektor mit Druckübersetzung
DE10055268A1 (de) * 2000-11-08 2002-05-23 Bosch Gmbh Robert Druckgesteuerter Injektor eines Hochdruckspeichereinspritzsystems
DE10056165C2 (de) * 2000-11-13 2003-06-12 Bosch Gmbh Robert Sammelraumbeaufschlagter Injektor mit kaskadenförmiger Steuerungsanordnung
DE10056165A1 (de) * 2000-11-13 2002-05-23 Bosch Gmbh Robert Sammelraumbeaufschlagter Injektor mit kaskadenförmiger Steuerungsanordnung
FR2816665A1 (fr) 2000-11-13 2002-05-17 Bosch Gmbh Robert Injecteur a dispositif de commande en cascade et alimente a partir d'une rampe commune
US6688537B2 (en) 2000-11-13 2004-02-10 Robert Bosch Gmbh Injector loaded from collecting chamber and provided with cascade-shaped control device
DE10059124B4 (de) * 2000-11-29 2005-09-15 Robert Bosch Gmbh Druckgesteuerter Injektor für Einspritzsysteme mit Hochdrucksammelraum
US6644278B2 (en) 2000-11-29 2003-11-11 Robert Bosch Gmbh Pressure controlled injector for injection systems with high pressure collecting area
FR2817297A1 (fr) 2000-11-29 2002-05-31 Bosch Gmbh Robert Systeme d'injection de carburant dans un moteur a combustion interne
US6561768B2 (en) 2000-11-30 2003-05-13 Robert Bosch Gmbh Device for supplying liquids, in particular, fuel
DE10060836C1 (de) * 2000-12-07 2002-07-25 Bosch Gmbh Robert Druckgesteuerter CR Injektor mit gestuftem Öffnungs- und Schließverhalten
FR2817918A1 (fr) 2000-12-07 2002-06-14 Bosch Gmbh Robert Injecteur de carburant a haute pression commande en pression avec un comportement d'ouverture et de fermeture etage
DE10114252C2 (de) * 2001-03-22 2003-01-30 Mtu Friedrichshafen Gmbh Verfahren zum Einspritzen von Kraftstoff in die Brennräume einer Brennkraftmaschine, sowie Kraftstoffeinspritzsystem für eine solche
DE10114252A1 (de) * 2001-03-22 2002-09-26 Mtu Friedrichshafen Gmbh Verfahren zum Einspritzen von Kraftstoff in die Brennräume einer Brennkraftmaschine, sowie Kraftstoffeinspritzsystem für eine solche
US6805102B2 (en) 2001-03-22 2004-10-19 Mtu Friedrichshafen Gmbh Method of injecting fuel into the combustion chambers of an internal combustion engine, and fuel injection system for said engine
DE10149868C1 (de) * 2001-10-10 2002-12-05 Orange Gmbh Einspritzinjektor für Brennkraftmaschinen
US6816050B2 (en) 2001-10-22 2004-11-09 Robert Bosch Gmbh Size-reduced magnet coil carrier
WO2007009279A1 (fr) * 2005-07-18 2007-01-25 Ganser-Hydromag Ag Systeme d'injection d'accumulateur pour moteur a combustion interne
US7603984B2 (en) 2005-07-18 2009-10-20 Ganser-Hydromag Ag Accumulator injection system for an internal combustion engine
CN101223352B (zh) * 2005-07-18 2010-12-08 甘瑟-许德罗玛格股份公司 用于内燃机的蓄压式喷射系统
DE102017201262A1 (de) 2016-03-18 2017-09-21 Ganser Crs Ag Speichereinspritzsystem für Verbrennungskraftmaschinen
AT518510A3 (de) * 2016-03-18 2018-07-15 Ganser Hydromag Speichereinspritzsystem für Verbrennungskraftmaschinen
AT518510B1 (de) * 2016-03-18 2018-07-15 Ganser Hydromag Speichereinspritzsystem für Verbrennungskraftmaschinen

Also Published As

Publication number Publication date
JPH07189849A (ja) 1995-07-28
US5497750A (en) 1996-03-12
DE59407645D1 (de) 1999-02-25
EP0657642B1 (fr) 1999-01-13
EP0657642A3 (fr) 1995-12-06
DE4341543A1 (de) 1995-06-08
JP3655938B2 (ja) 2005-06-02

Similar Documents

Publication Publication Date Title
EP0657642B1 (fr) Dispositif d'injection de combustible pour moteurs à combustion interne
EP0898650B1 (fr) Dispositif d'injection de carburant pour moteurs a combustion interne
EP0779949B1 (fr) Systeme d'injection de carburant pour moteurs a combustion interne
DE4311627B4 (de) Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
EP0657644B1 (fr) Dispositif d'injection de combustible pour moteurs à combustion interne
DE19910970A1 (de) Kraftstoffeinspritzeinrichtung
DE19816316A1 (de) Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE10229417A1 (de) Speichereinspritzsystem mit Variodüse und Druckübersetzungseinrichtung
WO2002092998A1 (fr) Systeme d'injection de carburant pourvu d'un dispositif multiplicateur de pression et dispositif multiplicateur de pression
WO2002084106A1 (fr) Soupape pour commander le passage de fluides
DE19910589C2 (de) Einspritzventil für eine Brennkraftmaschine
DE10221384A1 (de) Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
WO2008061844A1 (fr) Injecteur de carburant
DE19844891A1 (de) Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102004024527A1 (de) Kraftstoffeinspritzeinrichtung
EP1151192B1 (fr) Soupape d'injection de carburant pour moteurs a combustion interne
DE19921878A1 (de) Kraftstoffeinspritzsystem für eine Brennkraftmaschine
DE10160264A1 (de) Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE19623211A1 (de) Kraftstoffeinspritzventil für Brennkraftmaschinen
WO2008061842A1 (fr) Injecteur de carburant
WO2003004863A1 (fr) Injecteur de carburant a commande de distributeur a 2 voies
DE19947196A1 (de) Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE10233574B4 (de) Ventil zum Steuern von Flüssigkeiten
DE10032924A1 (de) Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE10065221B4 (de) Direkt gesteuertes 2-Sitzventil für Kraftstoffeinspritzsysteme

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19960607

17Q First examination report despatched

Effective date: 19971007

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REF Corresponds to:

Ref document number: 59407645

Country of ref document: DE

Date of ref document: 19990225

ET Fr: translation filed
ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN P. & C. S.N.C.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19990318

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20071024

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20080826

Year of fee payment: 15

Ref country code: FR

Payment date: 20080818

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20080822

Year of fee payment: 15

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090303

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20090820

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20100430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090820

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090820