EP0976924A2 - Servovalve pour un injecteur et injecteur - Google Patents

Servovalve pour un injecteur et injecteur Download PDF

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Publication number
EP0976924A2
EP0976924A2 EP99112980A EP99112980A EP0976924A2 EP 0976924 A2 EP0976924 A2 EP 0976924A2 EP 99112980 A EP99112980 A EP 99112980A EP 99112980 A EP99112980 A EP 99112980A EP 0976924 A2 EP0976924 A2 EP 0976924A2
Authority
EP
European Patent Office
Prior art keywords
valve
injection
servo
servo valve
chamber
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
EP99112980A
Other languages
German (de)
English (en)
Other versions
EP0976924A3 (fr
EP0976924B1 (fr
Inventor
Heinz Lixl
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP0976924A2 publication Critical patent/EP0976924A2/fr
Publication of EP0976924A3 publication Critical patent/EP0976924A3/fr
Application granted granted Critical
Publication of EP0976924B1 publication Critical patent/EP0976924B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • 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
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves

Definitions

  • the invention relates to a servo valve from the EP-A-0 192 241 known type. Such a servo valve is used generally for the control of fluid flows. In the present Case the servo valve for fuel injectors for Internal combustion engines are applied.
  • Injection systems are increasingly used in which working with very high injection pressures.
  • Such Injection systems are common rail systems (for diesel engines) and HPDI injection systems (for gasoline engines).
  • the fuel is supplied with a High pressure pump in a common to all cylinders of the engine Pressure accumulator conveyed from which the injectors be supplied to the individual cylinders.
  • the opening and Closing the injection valves is usually electromagnetic controlled.
  • the injectors are common in such systems provided with servo valves that hydraulically open and Control the closing of the injector nozzle needle means in particular the beginning and the end of the injection process schedule.
  • the servo valve influences in Connection with control chokes especially the speed with which the injector opens and closes.
  • the injection valve is intended, for. B. in common rail systems for diesel engines at the start of injection for a controlled better mixing of the fuel with the air open slowly. In contrast, the injection valve must at the end of Close the injection process quickly to prevent soot formation prevent.
  • the injection of the smallest amounts of fuel is also intended for pre-injection (pilot injection) before the actual one Injection may be possible with which the combustion process can be optimized.
  • the injection valve is designed with a servo valve in the form of a 3/2-way valve, in which the inlet via an inlet throttle and an outlet throttle basically faster opening of the injection valve than with the 2/2-way valve. Furthermore, by the interpretation the inlet throttle also the closing process of the injection valve to be slowed down. For injection valves for internal combustion engines in contrast, however, one would like to Usually slow the opening of the injector while the closing should happen quickly.
  • a Servo valve for controlling fluid flows known in which the in a first fluid chamber on the valve body of the servo valve pressure applied opening and closing the servo valve causes.
  • the actuation of the servo valve has the opening or closing a separate fluid channel.
  • the fluid channel leads in the known arrangement of a master cylinder that applies pressure to the fluid, to secondary cylinders, actuated by the pressurized fluid become.
  • the master cylinder provides this arrangement the master brake cylinder of a motor vehicle and the secondary cylinders are the wheel brake cylinders.
  • the known Servo valve is intended for an anti-lock braking system, and the fluid channel should open without delay in rapid succession and be closed.
  • the invention is based on the object to design the servo valve so that it is relative simple way to open and close a Let the injector influence independently of each other. It should also be possible to use the smallest pilot injection Inject fuel quantities in a controlled manner.
  • the servo valve according to the invention which is a kind of 3/2-way valve to control the nozzle needle, in particular a common rail injector represents, united with regard to the defined Valve strokes and the control of the opening flanks the advantages of the nozzle needle stroke via inlet and outlet throttle of the known 3/2-way valve with those of the known 2/2-way valve.
  • the peculiarity of the servo valve according to the invention lies in the flow restrictor which flows through in both directions.
  • Another advantage of the servo valve according to the invention is the small stroke of the valve body of the servo valve, which can range from 20 to 40 ⁇ m. This contributes to rapid closing movement of the nozzle needle also.
  • 1 shows a conventional injection valve with a 2/2-way valve as a servo valve
  • Fig. 2 a conventional injection valve with a 3/2-way valve as Servo valve.
  • both versions the system pressure fuel from a high pressure accumulator (not shown) via a high pressure bore 1 and an inlet bore 2 with an inlet throttle 3 to a control room 4 out in the injection valve body 5.
  • the pressure there acts on the rear end of a axially movable nozzle body 6 with a nozzle needle on it front end, when the nozzle body 6
  • Injection holes 7 in the injector body 5 opens and closes, which lead to the combustion chamber of the internal combustion engine.
  • the injection holes 7 are when the injection valve is open with a nozzle chamber 8 in connection, which at the front end of the nozzle body 6 is formed in the injection valve body 5 and which in turn is connected to the high pressure accumulator. If both in the control room 4 and in the nozzle chamber 8 full system pressure is present, the nozzle body 6 is due the larger effective area in the control room 4 pressed down and closes the injection holes 7.
  • the conventional injection valve 1 When designing the conventional injection valve 1 leads a hole 9 in the injection valve body in the control chamber 4 5 with a flow restrictor 10 to an in the injector body 5 integrated servo valve 12 in in the form of a 2/2-way valve.
  • the servo valve 12 comes in unpressurized fuel return 14 to the fuel tank.
  • the Servo valve 12 is operated by a plunger 16 from an electromagnetic and / or piezoelectric actuator 18 and operated.
  • the servo valve 12 has the task of increasing the pressure control the in the control room 4 to close and open the Injection valve exerted on the movable nozzle body 6 becomes.
  • the servo valve 12 If the servo valve 12 is closed, is in the control room 4 essentially the full system pressure, so that the Nozzle needle at the front end of the nozzle body 6, the injection holes 7 closes, which lead into the combustion chamber. If the actuator 18 is controlled electrically, the plunger 16 exercises a force on the spring-loaded servo valve 12. As As a result, the servo valve 12 opens. With the servo valve open 12 stands between the high pressure accumulator and the control room 4, servo valve 12 and return 14 a steady flow on. This flow leads to the individual throttles, the Inlet throttle 3 and outlet throttle 10, to a defined Pressure drop. The inlet throttle 3 and the outlet throttle 10 are dimensioned so that the pressure in the control room 4 decreased.
  • This version with a known 2/2-way valve has the disadvantage that the opening and closing processes of the injection valve by the design of the inlet and Flow restrictors are independent only within very narrow limits be influenced.
  • the conventional one Execution of the injection valve with a servo valve 12 in the form of a 3/2-way valve, the inlet via the inlet throttle 3, the servo valve 12 and the flow restrictor 10 for Control room 4.
  • the discharge leads via the discharge throttle 10 and the servo valve 12 to the return 14.
  • the control room is at a closed injection valve 4 via the inlet throttle 3, the servo valve 12 and the Drain throttle 10 in connection with the high pressure bore 1.
  • the pressure in the control room 4 can without influence of the inlet throttle 3 on the Remove drain throttle 10. In principle, this is faster Opening of the injection valve is possible than with the 2/2-way valve. After closing the drain on the 3/2-way valve builds itself over the inlet throttle 3 and the outlet throttle 10 in Control room 4 again the system pressure.
  • FIG. 3 is an injection valve with the invention 3/2-way valve shown as servo valve 12.
  • servo valve 12 The same reference numerals as in Figs. 1 and 2 denote same or similar elements.
  • the in the embodiment of FIG. 3 from the high pressure bore 1 branching inlet hole 2 leads to a Space 20 in the injector body 5, via the inlet throttle 3 with the control room 4 at the rear end of the nozzle body 6 communicates.
  • the room 20, which is part or extension the inlet hole 2 can be viewed is in Injection valve body 5 arranged opposite the control chamber 4 and connected to it only by the inlet throttle 3.
  • the room 20 in turn expands on that of Nozzle body 6 facing away from a valve chamber 22, the with renewed narrowing into a bore 30, the one hand represents a guide for the plunger 16 of the actuator 18 and on the other hand the unpressurized fuel return 14 includes.
  • valve chamber 22 The expansion of the valve chamber 22 on the part of Room 20 is as a stop 24 for the bottom of one in the Valve chamber 22 formed valve body 26 is formed.
  • the valve chamber 22 On the opposite side, that is, at the transition to Bore 30, the valve chamber 22 has a valve seat 28 on to which the top of the valve body 26 to abut can come.
  • Bypassing room 20 leads from control room 4 the drain hole 9 with the drain throttle 10 directly to the valve chamber 22.
  • the servo valve according to the invention thus consists of the space 20 in the inlet bore 2 and the adjoining one Valve chamber 22 with the stop 24 and the valve seat 28 for the valve body 26.
  • the valve body 26 sealing by the system pressure in the space 20 pressed against the valve seat 28. This is the hole 30 closed and the connection to the return 14 interrupted.
  • the nozzle body 6 is the pressure in the control room 4, which is also essentially equal to the system pressure, pressed down and thus the nozzle needle into the nozzle needle seat, so that the injection holes 7 are closed.
  • valve body 26 To actuate the valve, the actuator 18 on the Ram 16 exerted a force.
  • the plunger 16 thus presses the Valve body 26 away from the valve seat 28 and sealing on the Stop 24. This is the connection from the valve chamber 22 to bore 30 with the return 14 opened and the connection interrupted between the space 20 and the valve chamber 22.
  • the valve lift ⁇ h of the valve body 26 is there very low, it is around 20 to 40 ⁇ m.
  • the pending in control room 4 under system pressure Fuel can thus via the drain hole 9, the drain throttle 10, the valve chamber 22 and the bore 30 drain. This reduces the pressure in the control room 4.
  • the pressure reduction In the control room 4, the inlet throttle 3 and the flow restrictor 10 determines. About the throttle ratio the smallest quantity capability and the minimum opening pressure the injector.
  • valve body 26 After the actuation of the actuator 5 has been completed the system pressure still present in the room 20 the valve body 26 again in the valve seat 28, the valve body 26 stands out from the stop 24. That is the connection restored between space 20 and valve chamber 22 and the return 14 to the hole 30 is interrupted.
  • Valve spring (not shown) can be provided which on the Valve body 26 exerts a force towards the valve seat 28.
  • the restored connection between the room 20 and the valve chamber 22 causes the control chamber 4 both via the inlet throttle 3 and the valve chamber 22, the flow restrictor 10 and the drain hole 9 again with Fuel is filled.
  • the pressure in the control room 4 thus increases quickly back to the system pressure.
  • the pressure in the control room 4 leads to a force in the direction on the nozzle body 6 to the seat of the nozzle needle, which the nozzle needle again in their Presses the seat and ends the injection process.
  • the speed at which the injector opens and closes is directly influenced by the speed, with which the pressure in the control room 4 goes off and on again is built up.
  • the closing process should be as possible happen quickly, which is why with the present Execution of the injection valve during the closing process
  • Fuel supply to the control room 4 also via the valve chamber 22 and the flow restrictor 10 takes place.
  • the effective flow cross section for the fuel during the closing process from the additive cross sections of inlet throttle 3 and outlet throttle 10 formed, so that the pressure build-up very going on quickly.
  • the valve body 26 is preferably in the form of a Partial ball 261 formed on the center of the cut surface 262 a guide pin 263 is attached.
  • the partial ball 261 is arranged in the valve chamber 22, the partial spherical surface of the partial ball the valve seat 28 is assigned.
  • the guide pin 263 is in a connecting bore introduced that the valve chamber 22 with the Room 20 connects. In this way, the guide pin adjusts 263 the partial ball 261 centered and symmetrical to the valve seat 28. This prevents the partial ball 261 from tilting.
  • the partial spherical shape of the partial sphere 261 offers the advantage that the valve chamber 22 is well adapted to the shape of the partial sphere and thus the volume of the valve chamber 22, that is not filled by the valve body 26 is small.
  • the dead volume is reduced and thus a exact switching behavior of the servo valve achieved.
  • the partial spherical shape has the advantage that the lower, plane Cutting surface 262, which is formed annularly around the guide pin is, seals the space 20 when the actuator 18 Valve body 26 with the flat cutting surface 262 on the stop 24 presses. In this way the outflow of fuel reduced from room 20. So that is the power loss of the injection system limited.
  • valve chamber 212 is preferably cylindrical formed, the cylindrical shape conical in the Hole 30 merges.
  • the conical transition area represents the Valve seat 30.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
EP99112980A 1998-07-31 1999-07-05 Injecteur avec une servovalve Expired - Lifetime EP0976924B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19834667 1998-07-31
DE19834667 1998-07-31

Publications (3)

Publication Number Publication Date
EP0976924A2 true EP0976924A2 (fr) 2000-02-02
EP0976924A3 EP0976924A3 (fr) 2001-06-13
EP0976924B1 EP0976924B1 (fr) 2003-09-17

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Family Applications (1)

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EP99112980A Expired - Lifetime EP0976924B1 (fr) 1998-07-31 1999-07-05 Injecteur avec une servovalve

Country Status (2)

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EP (1) EP0976924B1 (fr)
DE (1) DE59906995D1 (fr)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001014721A1 (fr) * 1999-08-20 2001-03-01 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs a combustion interne
DE10015268A1 (de) * 2000-03-28 2001-10-04 Siemens Ag Einspritzventil mit Bypaßdrossel
DE10024703A1 (de) * 2000-05-18 2001-11-22 Bosch Gmbh Robert Einspritzanordnung für ein Kraftstoff-Speichereinspritzsystem einer Verbrennungsmaschine
DE10024702A1 (de) * 2000-05-18 2001-11-22 Bosch Gmbh Robert Einspritzanordnung für ein Kraftstoff-Speichereinspritzsystem einer Verbrennungsmaschine
US6367453B1 (en) 1999-11-10 2002-04-09 Denso Corporation Fuel injection valve
WO2002050423A1 (fr) * 2000-12-20 2002-06-27 Siemens Aktiengesellschaft Systeme d'injection haute pression conçu sous la forme d'un papillon de commande sous forme de papillon en cascade
FR2824109A1 (fr) * 2001-04-27 2002-10-31 Denso Corp Structure simple d'injecteur de carburant concue pour maintenir un pointeau en position de levee intermediaire
WO2003004858A1 (fr) * 2001-06-29 2003-01-16 Robert Bosch Gmbh Injecteur de carburant a sollicitation en pression variable de la chambre de commande
WO2003004857A1 (fr) * 2001-06-29 2003-01-16 Robert Bosch Gmbh Injecteur de carburant a formation du cours de l'injection
DE10131640A1 (de) * 2001-06-29 2003-01-16 Bosch Gmbh Robert Kraftstoffinjektor mit Einspritzverlaufsformung durch schaltbare Drosselelemente
DE10132249A1 (de) * 2001-07-04 2003-01-23 Bosch Gmbh Robert Kraftstoffinjektor mit kraftausgeglichenem Steuerventil
DE10123775B4 (de) * 2001-05-16 2005-01-20 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung für Brennkraftmaschinen, insbesondere Common-Rail-Injektor, sowie Kraftstoffsystem und Brennkraftmaschine
DE102005046743B3 (de) * 2005-09-29 2007-05-16 Siemens Ag Verfahren zur Ermittlung des Zeitpunktes des Anschlags eines Ventilkörpers in einem von einem elektromechanischen Aktor betätigten Ablaufventil
WO2007098621A1 (fr) 2006-03-03 2007-09-07 Ganser-Hydromag Ag Soupape d'injection de carburant pour moteurs A combustion interne
EP1404964B1 (fr) * 2001-06-29 2008-02-13 Robert Bosch Gmbh Injecteur de carburant a amenee de chambre de commande commutable
DE10254466B4 (de) * 2001-11-22 2010-05-12 DENSO CORPORATION, Kariya-shi Kraftstoffeinspritzventil
WO2012130452A1 (fr) 2011-03-31 2012-10-04 Fuechslin Raphael Soupape d'injection
EP2354527A3 (fr) * 2010-02-05 2013-07-31 Robert Bosch GmbH Injecteur de carburant

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7331329B2 (en) 2002-07-15 2008-02-19 Caterpillar Inc. Fuel injector with directly controlled highly efficient nozzle assembly and fuel system using same

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0199632A1 (fr) * 1985-04-19 1986-10-29 Societe Alsacienne De Constructions Mecaniques De Mulhouse Système d'injection de combustible pour moteur diesel
EP0426205B1 (fr) * 1985-12-02 1993-07-21 Marco Alfredo Ganser Dispositif de commande d'injecteurs de combustible actionnés électro-hydrauliquement
EP0740067A2 (fr) * 1995-04-27 1996-10-30 Isuzu Motors Limited Système d'injection de combustible du type à accumulateur

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0199632A1 (fr) * 1985-04-19 1986-10-29 Societe Alsacienne De Constructions Mecaniques De Mulhouse Système d'injection de combustible pour moteur diesel
EP0426205B1 (fr) * 1985-12-02 1993-07-21 Marco Alfredo Ganser Dispositif de commande d'injecteurs de combustible actionnés électro-hydrauliquement
EP0740067A2 (fr) * 1995-04-27 1996-10-30 Isuzu Motors Limited Système d'injection de combustible du type à accumulateur

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001014721A1 (fr) * 1999-08-20 2001-03-01 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs a combustion interne
US6367453B1 (en) 1999-11-10 2002-04-09 Denso Corporation Fuel injection valve
DE10055714B4 (de) * 1999-11-10 2010-08-05 DENSO CORPORATION, Kariya-shi Kraftstoffeinspritzventil
DE10066299B8 (de) * 1999-11-10 2009-07-30 Denso Corporation, Kariya Kraftstoffeinspritzventil
DE10066299B4 (de) * 1999-11-10 2009-02-05 Denso Corp., Kariya-shi Kraftstoffeinspritzventil
DE10015268A1 (de) * 2000-03-28 2001-10-04 Siemens Ag Einspritzventil mit Bypaßdrossel
US7575180B2 (en) 2000-03-28 2009-08-18 Siemens Aktiengesellschaft Injection valve having a bypass throttle
US6789743B2 (en) 2000-03-28 2004-09-14 Siemens Aktiengesellschaft Injection valve having a bypass throttle
DE10024703A1 (de) * 2000-05-18 2001-11-22 Bosch Gmbh Robert Einspritzanordnung für ein Kraftstoff-Speichereinspritzsystem einer Verbrennungsmaschine
DE10024702A1 (de) * 2000-05-18 2001-11-22 Bosch Gmbh Robert Einspritzanordnung für ein Kraftstoff-Speichereinspritzsystem einer Verbrennungsmaschine
US7216629B2 (en) 2000-12-20 2007-05-15 Siemens Aktiengesellschaft High-pressure injection system with a control throttle embodied as a cascade throttle
WO2002050423A1 (fr) * 2000-12-20 2002-06-27 Siemens Aktiengesellschaft Systeme d'injection haute pression conçu sous la forme d'un papillon de commande sous forme de papillon en cascade
FR2824109A1 (fr) * 2001-04-27 2002-10-31 Denso Corp Structure simple d'injecteur de carburant concue pour maintenir un pointeau en position de levee intermediaire
DE10123775B4 (de) * 2001-05-16 2005-01-20 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung für Brennkraftmaschinen, insbesondere Common-Rail-Injektor, sowie Kraftstoffsystem und Brennkraftmaschine
WO2003004857A1 (fr) * 2001-06-29 2003-01-16 Robert Bosch Gmbh Injecteur de carburant a formation du cours de l'injection
EP1404964B1 (fr) * 2001-06-29 2008-02-13 Robert Bosch Gmbh Injecteur de carburant a amenee de chambre de commande commutable
DE10131640A1 (de) * 2001-06-29 2003-01-16 Bosch Gmbh Robert Kraftstoffinjektor mit Einspritzverlaufsformung durch schaltbare Drosselelemente
WO2003004858A1 (fr) * 2001-06-29 2003-01-16 Robert Bosch Gmbh Injecteur de carburant a sollicitation en pression variable de la chambre de commande
DE10132249A1 (de) * 2001-07-04 2003-01-23 Bosch Gmbh Robert Kraftstoffinjektor mit kraftausgeglichenem Steuerventil
DE10254466B4 (de) * 2001-11-22 2010-05-12 DENSO CORPORATION, Kariya-shi Kraftstoffeinspritzventil
DE102005046743B3 (de) * 2005-09-29 2007-05-16 Siemens Ag Verfahren zur Ermittlung des Zeitpunktes des Anschlags eines Ventilkörpers in einem von einem elektromechanischen Aktor betätigten Ablaufventil
WO2007098621A1 (fr) 2006-03-03 2007-09-07 Ganser-Hydromag Ag Soupape d'injection de carburant pour moteurs A combustion interne
US8544771B2 (en) 2006-03-03 2013-10-01 Ganser-Hydromag Ag Fuel injection valve for internal combustion engines
EP2354527A3 (fr) * 2010-02-05 2013-07-31 Robert Bosch GmbH Injecteur de carburant
WO2012130452A1 (fr) 2011-03-31 2012-10-04 Fuechslin Raphael Soupape d'injection
DE102011015753A1 (de) 2011-03-31 2012-10-04 Raphael Füchslin Einspritzventil

Also Published As

Publication number Publication date
DE59906995D1 (de) 2003-10-23
EP0976924A3 (fr) 2001-06-13
EP0976924B1 (fr) 2003-09-17

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