EP0741244A2 - Injecteur - Google Patents

Injecteur Download PDF

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Publication number
EP0741244A2
EP0741244A2 EP96106549A EP96106549A EP0741244A2 EP 0741244 A2 EP0741244 A2 EP 0741244A2 EP 96106549 A EP96106549 A EP 96106549A EP 96106549 A EP96106549 A EP 96106549A EP 0741244 A2 EP0741244 A2 EP 0741244A2
Authority
EP
European Patent Office
Prior art keywords
valve
return
injection
injection nozzle
valve member
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
EP96106549A
Other languages
German (de)
English (en)
Other versions
EP0741244B1 (fr
EP0741244A3 (fr
Inventor
Gerd Dipl.-Ing. Huber
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.)
Mercedes Benz Group AG
Original Assignee
HUBER MOTORENBAU INST
Daimler Benz AG
Institut fur Motorenbau Prof Huber 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
Priority claimed from DE19516245A external-priority patent/DE19516245C2/de
Application filed by HUBER MOTORENBAU INST, Daimler Benz AG, Institut fur Motorenbau Prof Huber GmbH filed Critical HUBER MOTORENBAU INST
Publication of EP0741244A2 publication Critical patent/EP0741244A2/fr
Publication of EP0741244A3 publication Critical patent/EP0741244A3/xx
Application granted granted Critical
Publication of EP0741244B1 publication Critical patent/EP0741244B1/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
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • 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
    • F02M63/0056—Throttling valves, e.g. having variable opening positions throttling the flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/3809—Common rail control systems
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the invention relates to an injection nozzle for use in common rail systems according to the preamble of the main claim.
  • Common rail injection systems for diesel engines are described, for example, in the progress reports for the 15th Vienna Motor Symposium of the VDI Verlag, Series 12 / No. 205 (1994), pages 36 to 53.
  • the term "common rail” is used to summarize systems whose aim is on the one hand to make the injection pressure independent of the engine speed and the injection quantity, and on the other hand to increase the average injection pressure.
  • An essential feature of the Common Rail Systems (CR) is the decoupling of pressure generation and injection by means of a storage volume, which results from the volume of a common high-pressure distributor line (Common Rail) connected to the injection nozzles of a multi-cylinder engine, as well as the supply lines and in the The nozzle itself composes the available volumes.
  • Common Rail Common High-pressure distributor line
  • the injection process is controlled by an electromagnetic valve integrated in the injection nozzle.
  • a direct control of the nozzle body or the nozzle needle has so far not been possible with a magnetic valve or with piezoelectric or magnetostrictive actuators.
  • the return valve Due to its magnetic actuation, the return valve, which is designed as a solenoid valve, has two defined positions, a closed and a fully open position. So that the injection nozzle does not open too quickly when the return valve is opened by means of the magnet, a return throttle is provided downstream of the return valve. The timing characteristic of the injection nozzle is determined by suitable adjustment of the inlet throttle to the return throttle. A small cross section of the return throttle means when opening the return valve, a slow pressure drop across the working piston and thus a good small quantity capability of the injection nozzle, which is advantageous for a pre-injection.
  • a small return cross-section means a large minimum spray interval between two successive injections, since a relatively long time elapses between the opening of the return valve and the pressure drop across the actuator piston.
  • Systems with a small return throttle cross-section are therefore suitable for a small quantity pre-injection and a widely separated main or post-injection.
  • a large return throttle cross section leads to poorer small quantities due to the rapid full opening of the injection nozzle, but causes the nozzle body or the nozzle needle to open faster and thus enables shorter spraying intervals.
  • a large return throttle diameter is therefore suitable for one or more main injections.
  • the invention has for its object to provide an injection nozzle for use in common rail systems, which has both a good small quantity capability for a pre-injection and a rapid, following the pre-injection main injection or a timed main injection.
  • the valve member of the return valve can be opened analogously according to the invention, the return valve itself can form a variable return throttle cross section, so that the injection nozzle can be optimally adapted to the respective requirements.
  • the return valve by appropriately controlling the return valve, it is possible to carry out a good small quantity capability for a perfect pre-injection as well as a main injection which follows quickly and, if necessary, is clocked. This results in a soft combustion with low soot values and low nitrogen oxide values with a good overall efficiency.
  • the actuating device according to claim 2 is advantageously a piezoelectrically operating device. Because the actuating device does not directly actuate the nozzle body but the return valve, relatively small strokes are sufficient, as can be achieved with piezo actuators.
  • the claim 3 characterizes an advantageous embodiment of the injection nozzle, which is particularly precisely controllable.
  • valve member of the return valve for example a flat valve, must be kept in its closed position and thus with the injector closed against the high system pressure effective in the working area of the actuator piston in contact with the valve seat.
  • valve member is held in contact with the valve seat by the high system pressure acting from the working space, whereby the energy consumption is reduced and the operational safety is increased.
  • the valve member thus comes into increasingly firm contact with the seat when the system pressure builds up, as a result of which the injection valve remains reliably closed and no fuel is injected.
  • Claims 6 and 7 characterize advantageous embodiments of the valve according to claim 5.
  • Claims 8 and 9 are directed to two advantageous methods using an injection nozzle according to the invention. It is achieved with the features of claim 8 that the main injection can follow the pre-injection for a short time. With the features of claim 9 it is achieved that the injector closes extremely quickly, which is advantageous for the combustion.
  • a fuel tank 2 is connected to a common rail (CR) high-pressure pump 6 via a filter and a prefeed pump 4.
  • a line leads from the CR high-pressure pump to a distributor line (common rail) 8, which is connected via feed lines 10 to the injection nozzles 12 assigned to each cylinder of a multi-cylinder internal combustion engine.
  • the injection nozzles 12 are connected via return lines 14 to a return line 16 leading to the tank 2.
  • the system pressure is limited with the aid of a limiting valve 18 and can be up to 2000 bar.
  • the outputs of an electronic control unit 20 are connected to the high-pressure pump 6 and the injection nozzles 12.
  • the inputs 22 of the control unit are connected to a pressure sensor 24 of the distribution line 8 and further sensors, not shown, for example for the position of an accelerator pedal, driving speed, temperatures, boost pressure, air mass, speed, etc.
  • Fig. 2 shows the basic structure of an injection nozzle with the associated hydraulic diagram.
  • the injection nozzle 12 contains a nozzle body 26 which ends in a nozzle needle which, when the injection nozzle is closed, bears against a valve seat.
  • the nozzle body 26 extends through a nozzle chamber 28 which is connected to the feed line 10.
  • the nozzle body 26 is connected or formed in one piece to an actuator piston 30, which operates in a working space 32, which is connected to the supply line 10 via an inlet throttle 34.
  • the work space 32 is further connected to the return line 14 via a return valve 36.
  • valve member 38 To actuate the return valve 36, its valve member 38 is connected to an actuating device designed as a piezo actuator 40, which is connected to the control unit 20 via its connections 42.
  • actuating device designed as a piezo actuator 40
  • Such piezo actuators are known per se and are constructed like capacitors whose Dielectric consists of piezoelectric material, for example lead zirconate titanate ceramic. Modern actuators work with field strengths of up to 2000 V / mm and achieve relative changes in length of up to 1.5 ⁇ . In the example shown, a defined stroke of over 0.1 mm can thus be achieved with a length of the piezo actuator 40 of approximately 100 mm, which is completely sufficient for an analogous change in the opening cross section of the return valve 36 as a function of the voltage at the connections 42.
  • the piezo actuator 40 could also be a magnetostrictive actuator, in which magnetostrictive material is arranged within a current-carrying coil.
  • FIG. 3 shows a section through an executed example of an injection nozzle, the construction of the nozzle needle and its interaction with the seat being known per se, for example as described in the automotive paperback, Bosch, VDI Verlag 1991, on page 509.
  • the effective area with which the actuator piston 30 is acted upon in the working space 32 is larger than the effective area with which the nozzle body 26 in the nozzle space 28 or the nozzle needle is acted upstream of the valve seat, so that the pressure is the same in the working chamber 32 and nozzle chamber 28 the nozzle body 26 is pushed into the closed position.
  • the return valve 36 When the return valve 36 is closed, the pressure prevailing in the feed line is set in the working chamber 32 and nozzle chamber 28 and urges the nozzle body 26 into the closed position. If the valve member 38 is opened by applying voltage to the piezo actuator 40, the pressure escapes from the working space 32 if the return valve 36 is opened sufficiently quickly than fuel can flow in through the inlet throttle 34, so that when the pressure in the working space 32 decreases, the nozzle opens as a result of the pressure in the nozzle space 28. If the return valve 36 is closed, the high pressure in the working space 32 is restored, so that the injection nozzle closes.
  • the entire pressure level in the feed line 10 can be detected by the pressure sensor 24 depending on the operating conditions and, controlled by the control unit 20 by controlling the high-pressure pump 6, can be changed.
  • the diameter of the inlet throttle 34 was 0.30 mm and the bore diameter of the return valve 36 (FIG. 3) was 0.7 mm.
  • curves Ia and IIa correspond to curves I and II of FIG. 4.
  • the main injection is carried out in a clocked manner here, by actuating the return valve 36 in such a way that the nozzle body 26 always as soon as it has approximately reached its full stroke , closes again.
  • Curves Ib, IIb and Ic, IIc show a comparison of a stroke of a main injection, in which the return valve 36 is opened once with a constant amplitude (Ib) and the other time the opening amplitude of the return valve 36 is set to a reduced value as soon as the The opening of the injection nozzle has started or the nozzle body 26 has lifted substantially from its seat.
  • the control of the return valve 36 according to FIG. 1c leads to a more rapid closing of the injection nozzle after the return valve 36 has been closed, which is advantageous with regard to the combustion process.
  • FIG. 6 shows the hydraulic diagram of an embodiment of an injection nozzle that is somewhat modified compared to FIG. 2, the same reference numerals being used for functionally identical parts be used.
  • the main difference to Fig. 2 is that in the first example, the valve member 38 is arranged on the downstream side of the seat of the return valve 36 and thus must be constantly pressed in the closed position to close the valve against the high system pressure, whereas in the embodiment according to Fig. 6, the valve member 38 is arranged in the flow direction in front of the valve seat.
  • FIG. 7 shows the valve diagram of the return valve 36 according to FIG. 6.
  • a valve chamber 44 has a connection opening for connecting the connecting line 35 and a return opening 46, via which the valve chamber 44 merges into a space 48 which is connected to the return line 14.
  • the return opening is designed such that its edge forms a valve seat 50 for the valve member designed as a ball 38.
  • the ball 38 is pressed against the valve seat 50 by a spring 54.
  • an actuator 56 connected to the piezo actuator 40 projects through the space 48 and the return opening 46 and, as shown in FIG. 4, is guided in the space 48 downstream of the branch of the return line 14 with a seal.
  • FIG. 8 shows a section through an exemplary embodiment of an injection nozzle, the construction of the nozzle needle and its interaction with the seat being known per se, for example as described in the automotive paperback, Bosch, VDI Verlag 1991, on page 509.
  • a housing sleeve 60 ending in the injection nozzle 12 is screwed to a further housing part 62.
  • the piezo actuator 40 is received with the actuating element 56, which is sealed against the piezo actuator 40 by means of a seal 64 and works against a spring 66 by means of a flange.
  • the housing sleeve 60 and the housing part 62 span two further housing bodies 68 and 70 between them.
  • the actuator piston 30 works in the housing body 68.
  • the inlet throttle 34 is formed in the housing body 70.
  • the housing body 70 has a multiply stepped through hole which forms the connecting line 35, the valve chamber 44, the return opening 46 (FIG. 7) with the valve seat 50 and the space 48 (FIG. 7) from which the return line 14 branches off.
  • the actuating member 56 extends through the space 48 formed in the upper end of the through bore of the housing body 70 with a lug 72 with a smaller diameter or with grooves on its outer surface, which actuates the ball 38 through the rear opening.
  • the return line 14 branches off from an annular space which is formed by an enlarged bore step at the upper end of the through bore of the housing body 70 according to FIG. 8.
  • the actuator 56 protrudes so far into the return opening 46 that it is not in engagement with the ball 52 urged by the spring 54 into contact with the valve seat 50.
  • the ball 52 is additionally pushed into contact with the valve seat 50 by the system pressure, so that the return valve 36 is reliably closed and thus the entire injection valve is also reliably closed.

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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)
EP96106549A 1995-05-03 1996-04-25 Injecteur Expired - Lifetime EP0741244B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19516245A DE19516245C2 (de) 1995-05-03 1995-05-03 Verfahren zum Steuern einer mehrphasigen Einspritzung eines direkt einspritzenden Dieselmotors
DE19516245 1995-05-03
DE19541819 1995-11-09
DE19541819A DE19541819A1 (de) 1995-05-03 1995-11-09 Einspritzdüse

Publications (3)

Publication Number Publication Date
EP0741244A2 true EP0741244A2 (fr) 1996-11-06
EP0741244A3 EP0741244A3 (fr) 1996-11-27
EP0741244B1 EP0741244B1 (fr) 1999-07-07

Family

ID=26014848

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96106549A Expired - Lifetime EP0741244B1 (fr) 1995-05-03 1996-04-25 Injecteur

Country Status (5)

Country Link
US (1) US5713326A (fr)
EP (1) EP0741244B1 (fr)
JP (1) JP3944529B2 (fr)
CN (1) CN1067462C (fr)
ES (1) ES2135815T3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0911511A2 (fr) * 1997-10-25 1999-04-28 Robert Bosch Gmbh Procédé d'injection de carburant dans la chambre de combustion d'un moteur auto-allumage par compression d'air
EP0845077B1 (fr) * 1996-06-15 2003-01-22 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs a combustion interne
DE19929589C2 (de) * 1998-07-02 2003-01-23 Avl List Gmbh Einspritzeinrichtung für eine Brennkraftmaschine
DE19983014B4 (de) * 1998-03-02 2005-05-25 Cummins Inc., Columbus Vorrichtung zum Diagnostizieren von Störungen und Fehlerbedingungen in einer Kraftstoffanlage einer Verbrennungskraftmaschine
DE102004042189A1 (de) * 2004-08-31 2006-03-30 Siemens Ag Ventil

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DE19618932C2 (de) * 1996-05-10 2001-02-01 Siemens Ag Vorrichtung und Verfahren zur Regelung des Kraftstoffdruckes in einem Hochdruckspeicher
DE19706467C1 (de) * 1997-02-19 1998-03-26 Daimler Benz Ag Speichereinspritzsystem für eine mehrzylindrige Brennkraftmaschine
JP3834918B2 (ja) * 1997-03-04 2006-10-18 いすゞ自動車株式会社 エンジンの燃料噴射方法及びその装置
DE59806913D1 (de) * 1997-03-12 2003-02-20 Forsch Transferzentrum Ev An D Verfahren zur kraftstoffeinspritzung in mehrzylinder-kraftmaschinen und vorrichtung zur durchführung des verfahrens
DE19835340A1 (de) * 1997-11-03 2000-02-10 Guenter Slowik Verfahren und Einspritzdüse zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine
DE19821768C2 (de) * 1998-05-14 2000-09-07 Siemens Ag Dosiervorrichtung und Dosierverfahren
JP2000027725A (ja) * 1998-07-08 2000-01-25 Isuzu Motors Ltd コモンレール式燃料噴射装置
JP3695213B2 (ja) * 1999-04-02 2005-09-14 いすゞ自動車株式会社 コモンレール式燃料噴射装置
US6253736B1 (en) 1999-08-10 2001-07-03 Cummins Engine Company, Inc. Fuel injector nozzle assembly with feedback control
DE10003252A1 (de) * 2000-01-26 2001-08-09 Bosch Gmbh Robert Einspritzdüse
US6720684B2 (en) 2000-03-22 2004-04-13 Siemens Automotive Corporation Method of control for a self-sensing magnetostrictive actuator
US6345606B1 (en) * 2000-04-12 2002-02-12 Delphi Technologies, Inc Method for controlling fuel rail pressure using a piezoelectric actuated fuel injector
JP4178537B2 (ja) * 2000-07-12 2008-11-12 株式会社デンソー 燃料噴射装置
DE10035815A1 (de) * 2000-07-22 2002-01-31 Bosch Gmbh Robert Verfahren zur Steuerung eines Einspritzventils
DE10157886B4 (de) * 2000-11-27 2009-12-17 DENSO CORPORATION, Kariya-shi Kraftstoffeinspritzeinheit eines Verbrennungsmotors
DE10131631A1 (de) * 2001-06-29 2003-01-16 Bosch Gmbh Robert Kraftstoffinjektor mit hochdruckfestigkeitsoptimiertem Steuerraum
US6837221B2 (en) 2001-12-11 2005-01-04 Cummins Inc. Fuel injector with feedback control
US6792921B2 (en) * 2001-12-17 2004-09-21 Caterpillar Inc Electronically-controlled fuel injector
US6760212B2 (en) * 2002-09-23 2004-07-06 Delphi Technologies, Inc. Piezoelectric injector drive circuit
US7001158B2 (en) * 2003-01-24 2006-02-21 Sturman Industries, Inc. Digital fluid pump
DE102004001679B4 (de) * 2004-01-12 2009-01-08 Continental Automotive Gmbh Piezoaktor mit Mitteln zur Kompensation der thermischen Längenänderung und Kraftstoff-Einspritzventil mit Piezoaktor
DE102004018931A1 (de) * 2004-04-20 2005-11-17 Robert Bosch Gmbh Common-Rail-Injektor

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US4022166A (en) * 1975-04-03 1977-05-10 Teledyne Industries, Inc. Piezoelectric fuel injector valve
EP0199632A1 (fr) * 1985-04-19 1986-10-29 Societe Alsacienne De Constructions Mecaniques De Mulhouse Système d'injection de combustible pour moteur diesel
EP0647780A2 (fr) * 1993-10-08 1995-04-12 Lucas Industries Public Limited Company Buse d'injection de combustible
DE4434892A1 (de) * 1994-09-29 1996-04-11 Siemens Ag Einspritzventil

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US5467754A (en) * 1988-02-03 1995-11-21 Servojet Electronic Systems, Ltd. Accumulator fuel injection system
US5241935A (en) * 1988-02-03 1993-09-07 Servojet Electronic Systems, Ltd. Accumulator fuel injection system
DE4011782A1 (de) * 1989-04-11 1990-10-31 Toyota Motor Co Ltd Steuerschaltung fuer eine brennstoffeinspritzvorrichtung
DE4337048C2 (de) * 1993-10-29 1996-01-11 Daimler Benz Ag Kraftstoffeinspritzanlage für eine Brennkraftmaschine
US5605134A (en) * 1995-04-13 1997-02-25 Martin; Tiby M. High pressure electronic common rail fuel injector and method of controlling a fuel injection event
DE19516245C2 (de) * 1995-05-03 2002-12-05 Daimler Chrysler Ag Verfahren zum Steuern einer mehrphasigen Einspritzung eines direkt einspritzenden Dieselmotors

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2028442A1 (de) * 1970-06-10 1971-12-16 Daimler Benz Ag Kraftstoffeinspritzventil fur Ver brennungsmotoren
US4022166A (en) * 1975-04-03 1977-05-10 Teledyne Industries, Inc. Piezoelectric fuel injector valve
EP0199632A1 (fr) * 1985-04-19 1986-10-29 Societe Alsacienne De Constructions Mecaniques De Mulhouse Système d'injection de combustible pour moteur diesel
EP0647780A2 (fr) * 1993-10-08 1995-04-12 Lucas Industries Public Limited Company Buse d'injection de combustible
DE4434892A1 (de) * 1994-09-29 1996-04-11 Siemens Ag Einspritzventil

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0845077B1 (fr) * 1996-06-15 2003-01-22 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs a combustion interne
EP0911511A2 (fr) * 1997-10-25 1999-04-28 Robert Bosch Gmbh Procédé d'injection de carburant dans la chambre de combustion d'un moteur auto-allumage par compression d'air
EP0911511A3 (fr) * 1997-10-25 2002-10-30 Robert Bosch Gmbh Procédé d'injection de carburant dans la chambre de combustion d'un moteur auto-allumage par compression d'air
DE19983014B4 (de) * 1998-03-02 2005-05-25 Cummins Inc., Columbus Vorrichtung zum Diagnostizieren von Störungen und Fehlerbedingungen in einer Kraftstoffanlage einer Verbrennungskraftmaschine
DE19929589C2 (de) * 1998-07-02 2003-01-23 Avl List Gmbh Einspritzeinrichtung für eine Brennkraftmaschine
DE102004042189A1 (de) * 2004-08-31 2006-03-30 Siemens Ag Ventil
DE102004042189B4 (de) * 2004-08-31 2007-04-12 Siemens Ag Ventil

Also Published As

Publication number Publication date
CN1145451A (zh) 1997-03-19
CN1067462C (zh) 2001-06-20
EP0741244B1 (fr) 1999-07-07
JPH09100757A (ja) 1997-04-15
ES2135815T3 (es) 1999-11-01
EP0741244A3 (fr) 1996-11-27
US5713326A (en) 1998-02-03
JP3944529B2 (ja) 2007-07-11

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