WO1998040623A1 - Ventil zum steuern von flüssigkeiten - Google Patents
Ventil zum steuern von flüssigkeiten Download PDFInfo
- Publication number
- WO1998040623A1 WO1998040623A1 PCT/DE1997/002709 DE9702709W WO9840623A1 WO 1998040623 A1 WO1998040623 A1 WO 1998040623A1 DE 9702709 W DE9702709 W DE 9702709W WO 9840623 A1 WO9840623 A1 WO 9840623A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- valve
- pressure
- pressure chamber
- actuating piston
- valve member
- Prior art date
Links
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
-
- 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
-
- 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
- F02M47/025—Hydraulically 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
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
- F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
- F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions
-
- 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
- F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
- F02M2547/003—Valve inserts containing control chamber and valve piston
Definitions
- the invention relates to a valve for controlling liquids according to the preamble of claim 1.
- a valve for controlling liquids according to the preamble of claim 1.
- Such a valve is known from US Pat. No. 4,813,601.
- the actuating piston of the valve member is arranged in a part of a stepped bore that is smaller in diameter, whereas a piston with a larger diameter that is moved with the piezo actuator is arranged in a part of the stepped bore that is larger in diameter.
- a hydraulic space is clamped between the two pistons, such that when the larger piston is moved by the actuator by a certain distance, the actuating piston of the valve member is moved by a distance enlarged by the transmission ratio of the stepped bore diameter.
- valve member The valve member, the actuating piston, the piston with the larger diameter and the piezo actuator lie one behind the other on a common axis.
- This arrangement has the disadvantage that it takes up a large amount of space, particularly with regard to the length, taking into account the The fact that a piezo actuator is quite large for effective actuation.
- control valve according to the invention with the features of the characterizing part of claim 1 has the advantage over the fact that the position of the piezo actuator in front of the actual valve member with its actuating piston can be arranged separately, i.e. at a spatial lateral distance from the valve member. This creates space for accommodating this actuator in addition to the centrally arranged valve member in the large design of a piezo actuator required. Actuator and valve element can be parallel to one another in wide areas.
- FIG. 1 shows a first exemplary embodiment installed in an electrically controlled
- Fuel injection valve of which the part essential for control is shown - in the version as a 2/2 valve and FIG. 2 shows a second exemplary embodiment of the control valve as a 3/2 valve.
- the valve according to the invention is used in a fuel injection valve, the essential parts of which are shown in section in FIG. 1.
- This injection valve has a valve housing 1, in which a valve needle 3 is guided in a longitudinal bore 2.
- the valve needle is provided with a conical sealing surface 4, which cooperates with a seat on the tip 5 of the valve housing protruding into the combustion chamber, from which seat Remove injection openings that connect the interior of the injection valve, here the annular space 7 surrounding the valve needle 3 and filled with fuel under injection pressure, to the combustion chamber, so as to carry out an injection when the valve needle has lifted off its seat.
- the annular space is connected to a further pressure space 8, which is constantly in communication with a pressure line 10, via which fuel under injection pressure is fed to the fuel injection valve from a high-pressure fuel reservoir (not shown here).
- This high fuel pressure also acts in the pressure chamber 8 and there on a pressure shoulder 11, via which the nozzle needle can be lifted from its valve seat in a known manner under suitable conditions.
- valve needle At the other end of the valve needle, it is guided in a cylinder bore 12 and includes with its end face 14 a control pressure chamber 15 which is constantly connected via a throttle connection 16 to an annular chamber 17 which, like the annular chamber 8, is constantly connected to the high-pressure fuel reservoir in Connection is established.
- a throttle bore 19 leads axially from the control pressure chamber 15 to a valve seat 20 of a control valve 21 in the configuration according to the invention.
- a valve member 22 of the control valve 21 interacts with the valve seat 20 and, in the raised state, establishes a connection between the control pressure chamber 15 and a relief chamber.
- valve member 22 is acted upon by a compression spring 24 in the closing direction, ie towards the valve seat 20, so that this connection of the control pressure chamber 15 is closed in the normal position of the control valve. Since the face area of the valve needle in the area of the control pressure chamber is larger than the area of the pressure shoulder 11, the same fuel pressure holds in the control pressure chamber as in the annular chamber 8 now prevails the valve needle 3 in the closed position. However, if the valve member 22 is lifted off, the pressure in the control pressure chamber 15 is relieved due to the throttling effect of the throttle connection 16. When the closing force is now lacking, the valve needle opens quickly and, on the other hand, can be brought into the closed position as soon as the valve member 22 comes back into the closed position. From this point in time, the original high fuel pressure in the control pressure chamber 15 quickly builds up again via the throttle 16.
- the control valve has an actuating piston 25 which is fixedly connected to the valve member 22 and has a larger diameter than the shaft 27 guided in the housing 26.
- the piston 25 is guided tightly in a guide bore 28 and, with its annular shoulder 29, delimits a pressure chamber 31 of the control valve at the transition to the shaft 27, which pressure chamber 31 extends laterally to the axis of the actuating piston 25.
- This space is further delimited by an end face 32 of an actuator piston 33 such that the pressure space 31 is enclosed on all sides.
- the axis of the actuating piston is coaxial with the axis of the valve needle 3 and the axis of the actuator piston 33 is parallel to this axis.
- the actuator piston 33 is also guided tightly in the housing 26 and is moved by a piezo stack 30, which is only indicated here.
- expansion takes place in such a way that the actuator piston attempts to reduce the volume of the pressure chamber 31, which is immediately compensated for by the fact that the actuating piston 25 is raised.
- the diameter of the actuator piston has a larger area to the pressure chamber 31 than the annular shoulder 29 of the actuating piston, it executes a movement which is translated by area ratios and is displaced by a much greater distance against the restoring force of the compression spring 24, even with small changes in piezo length the control valve releases the throttle bore 19 to relieve the control pressure chamber 15.
- this embodiment offers the advantage that the actuator with piezo and actuator piston can be arranged next to the actuating piston 25 with an axis parallel to the axis of the fuel injection valve and that the overall length is reduced by the overlap of the parts with one another. Manufacturing is further simplified because there are no coaxial bores with different diameters in connection with the actuator that would require a double fit.
- the pressure chamber 31 can be designed so that a throttle section 34 can be realized in the area between the end faces of the actuator piston and the actuating piston, with which it can be achieved that vibration can be reduced on this throttle section due to the very fast actuator movement.
- the valve member 22 of the control valve can be brought quickly and safely into an open position or a closed position.
- the exemplary embodiment according to FIG. 2 differs from that according to FIG. 1 in that a 3/2 valve is implemented here instead of a 2/2 valve.
- the valve member has a valve head 35, which in turn is connected to the actuating piston 25 via the shaft 27.
- the stem 25 is guided in a guide bore 39 which opens into an enlarged space 40 in which the valve head 35 can be moved back and forth.
- This space is continuously connected via a channel 37 to the control pressure space 15, which is not shown here and which corresponds to that of FIG. 1.
- a first valve seat 41 is formed, which has a conical, for Actuating piston 25 facing sealing surface 42 of the valve head cooperates.
- the stem has an annular groove 36 which, together with the guide bore, forms an annular space 44 which is constantly connected to the high-pressure fuel reservoir via a high-pressure line 45 opening into the guide bore 39.
- fuel can get into the space 40 via the annular space 44 and from there via the channel 37 into the control pressure space 15, where this pressure holds the valve needle 3 in the closed position.
- the inflow provided in FIG. 1 via a throttle 16 into the control pressure chamber 15 is omitted in this case.
- the valve head also has a flat sealing surface 46 on its end face, with which it lies tightly against a plane seat 47 in the position shown under the action of the compression spring 24 '. In this position, the valve head closes a relief line 48, via which the space 40 and also the control pressure space 15 can be relieved when the valve head 35 is in contact with the first valve seat 41 and thus blocks the high-pressure inlet into the space 40.
- the valve head in turn reaches this position when the actuator piston 33 has displaced pressure medium, for example here also fuel, via the pressure chamber 31 and has lifted the latter via the shoulder 29 of the actuating piston 25. In this way, with this 3/2 valve, the control pressure chamber in one valve position is relieved in an exact assignment and high pressure is applied in the other valve position.
- the solution has the advantage that, when the piezo is not energized, the spring 24 'ensures that the control valve is brought into the rest position shown, in which the relief line 48 is closed and the control pressure chamber 15 is at high fuel pressure. The injection valve is thus also closed when the piezo is not excited.
- This is an essential security aspect because If the power supply part of the motor vehicle fails, an excessive fuel injection quantity is prevented.
- the energy requirement for the control of the control valve is also lower if it has to be energized only for the purpose of relief in the time of the short injection process and can in turn be de-energized during the long spray breaks.
- valve seat 2 also has a significant advantage, which is that one valve seat is a conical seat and the other valve seat is a flat seat. Because of the flat seat provided here, no special measures need to be taken for the assignment of the two seats to one another, which would be different if two cone seat valves had to be controlled with the valve head. With a corresponding design of the valve head it can be achieved in this embodiment that the balance of forces on the valve head 35, utilizing the high fuel pressure acting on it, acts on the valve member in the closed position.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP10539036A JP2000512360A (ja) | 1997-03-10 | 1997-11-19 | 液体を制御するための弁 |
US09/180,023 US6076800A (en) | 1997-03-10 | 1997-11-19 | Valve for controlling fluids |
EP97949954A EP0900332A1 (de) | 1997-03-10 | 1997-11-19 | Ventil zum steuern von flüssigkeiten |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19709794A DE19709794A1 (de) | 1997-03-10 | 1997-03-10 | Ventil zum Steuern von Flüssigkeiten |
DE19709794.4 | 1997-03-10 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1998040623A1 true WO1998040623A1 (de) | 1998-09-17 |
Family
ID=7822844
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE1997/002709 WO1998040623A1 (de) | 1997-03-10 | 1997-11-19 | Ventil zum steuern von flüssigkeiten |
Country Status (7)
Country | Link |
---|---|
US (1) | US6076800A (de) |
EP (1) | EP0900332A1 (de) |
JP (1) | JP2000512360A (de) |
KR (1) | KR20000010762A (de) |
DE (1) | DE19709794A1 (de) |
RU (1) | RU2193683C2 (de) |
WO (1) | WO1998040623A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1063418A3 (de) * | 1999-06-25 | 2002-12-11 | Delphi Technologies, Inc. | Brennstoffeinspritzventil |
Families Citing this family (29)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19821768C2 (de) * | 1998-05-14 | 2000-09-07 | Siemens Ag | Dosiervorrichtung und Dosierverfahren |
DE19835494C2 (de) * | 1998-08-06 | 2000-06-21 | Bosch Gmbh Robert | Pumpe-Düse-Einheit |
US6364282B1 (en) * | 1998-12-04 | 2002-04-02 | Caterpillar Inc. | Hydraulically actuated fuel injector with seated pin actuator |
DE19860476A1 (de) * | 1998-12-28 | 2000-07-06 | Bosch Gmbh Robert | Kraftstoffeinspritzanlage |
DE19921242C1 (de) * | 1999-05-07 | 2000-10-26 | Siemens Ag | Verfahren zum Positionieren des Stellantriebs in einem Kraftstoffinjektor und Vorrichtung zur Durchführung des Verfahrens |
DE19940300A1 (de) * | 1999-08-25 | 2001-03-01 | Bosch Gmbh Robert | Steuerventil für einen Injektor |
DE19946830A1 (de) * | 1999-09-30 | 2001-05-03 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE19946828C1 (de) * | 1999-09-30 | 2001-07-12 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE10002270C1 (de) * | 2000-01-20 | 2001-06-28 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE10019766A1 (de) * | 2000-04-20 | 2001-10-31 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE10031278A1 (de) * | 2000-06-27 | 2002-01-17 | Bosch Gmbh Robert | Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen |
DE10031579A1 (de) * | 2000-06-29 | 2002-01-17 | Bosch Gmbh Robert | Druckgesteuerter Injektor mit Vario-Register-Einspritzdüse |
DE10065221B4 (de) * | 2000-12-27 | 2007-11-29 | Robert Bosch Gmbh | Direkt gesteuertes 2-Sitzventil für Kraftstoffeinspritzsysteme |
DE10100392C1 (de) * | 2001-01-05 | 2002-06-13 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
DE10118053A1 (de) * | 2001-04-11 | 2002-10-24 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
JP3556921B2 (ja) * | 2001-04-27 | 2004-08-25 | 株式会社日本自動車部品総合研究所 | 燃料噴射弁 |
DE10132249A1 (de) * | 2001-07-04 | 2003-01-23 | Bosch Gmbh Robert | Kraftstoffinjektor mit kraftausgeglichenem Steuerventil |
DE10136595A1 (de) * | 2001-07-30 | 2002-09-19 | Orange Gmbh | Kraftstoff-Einspritzinjektor für Brennkraftmaschinen |
DE10162045B4 (de) * | 2001-12-17 | 2005-06-23 | Siemens Ag | Vorrichtung zum Übersetzen einer Auslenkung eines Aktors, insbesondere für ein Einspritzventil |
DE10250720A1 (de) * | 2002-10-31 | 2004-05-13 | Robert Bosch Gmbh | Einspritzventil |
JP4019934B2 (ja) * | 2002-12-26 | 2007-12-12 | 株式会社デンソー | 制御弁および燃料噴射弁 |
DE102004002088A1 (de) * | 2004-01-15 | 2005-08-04 | Robert Bosch Gmbh | Druckgesteuerter CR-Injektor zur Kraftstoff-Einspritzung in Brennräume von Brennkraftmaschinen, insbesondere Dieselmotoren |
JP2006257874A (ja) * | 2004-04-30 | 2006-09-28 | Denso Corp | インジェクタ |
US7100577B2 (en) * | 2004-06-14 | 2006-09-05 | Westport Research Inc. | Common rail directly actuated fuel injection valve with a pressurized hydraulic transmission device and a method of operating same |
DE102007044357A1 (de) * | 2007-06-21 | 2008-12-24 | Robert Bosch Gmbh | Steuerventil für ein Kraftstoffeinspritzventil |
DE102007035698A1 (de) * | 2007-07-30 | 2009-02-05 | Robert Bosch Gmbh | Kraftstoffeinspritzventil mit verbesserter Dichtheit am Dichtsitz eines druckausgeglichenen Steuerventils |
DE102008001647A1 (de) * | 2008-05-08 | 2009-11-12 | Zf Friedrichshafen Ag | Steuerventil |
EP3236123A1 (de) | 2016-04-19 | 2017-10-25 | Primetals Technologies Austria GmbH | Betätigungseinrichtung für einen steuerkolben eines hydraulikventils |
CN106762279B (zh) * | 2017-01-18 | 2023-03-21 | 哈尔滨工程大学 | 一种带液力反馈的谐振旁通式电控喷油器 |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4463727A (en) * | 1981-09-08 | 1984-08-07 | Robert Bosch Gmbh | Diesel engine fuel injection system |
US4813601A (en) | 1987-02-14 | 1989-03-21 | Daimler-Benz Aktiengesellschaft | Piezoelectric control valve for controlling fuel injection valve in internal-combustion engines |
US5237968A (en) * | 1992-11-04 | 1993-08-24 | Caterpillar Inc. | Apparatus for adjustably controlling valve movement and fuel injection |
EP0615064A1 (de) * | 1993-03-08 | 1994-09-14 | Ganser-Hydromag | Steueranordnung für ein Einspritzventil für Verbrennungskraftmaschinen |
DE4406522C1 (de) * | 1994-02-28 | 1995-07-13 | Siemens Ag | Elektrohydraulisches Antriebselement |
DE4406901A1 (de) * | 1994-03-03 | 1995-09-14 | Daimler Benz Ag | Magnetventilgesteuerter Injektor für eine Brennkraftmaschine |
US5452858A (en) * | 1993-03-24 | 1995-09-26 | Nippon Soken Inc. | Fuel injector for internal combustion engine having throttle portion |
DE19519762A1 (de) * | 1994-08-25 | 1996-02-29 | Mitsubishi Electric Corp | Kraftstoffeinspritzsystem |
DE19519192C1 (de) * | 1995-05-24 | 1996-06-05 | Siemens Ag | Einspritzventil |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0192241B1 (de) * | 1985-02-19 | 1988-09-21 | Nippondenso Co., Ltd. | Flüssigkeitsregelventil |
US4995587A (en) * | 1989-11-03 | 1991-02-26 | Martin Marietta Corporation | Motion amplifier employing a dual piston arrangement |
JPH03163280A (ja) * | 1989-11-20 | 1991-07-15 | Nippondenso Co Ltd | 積層型圧電体装置 |
JP3740733B2 (ja) * | 1996-02-13 | 2006-02-01 | いすゞ自動車株式会社 | 内燃機関の燃料噴射装置 |
-
1997
- 1997-03-10 DE DE19709794A patent/DE19709794A1/de not_active Withdrawn
- 1997-11-19 WO PCT/DE1997/002709 patent/WO1998040623A1/de not_active Application Discontinuation
- 1997-11-19 KR KR1019980708882A patent/KR20000010762A/ko not_active Application Discontinuation
- 1997-11-19 EP EP97949954A patent/EP0900332A1/de not_active Withdrawn
- 1997-11-19 RU RU98122114/06A patent/RU2193683C2/ru not_active IP Right Cessation
- 1997-11-19 JP JP10539036A patent/JP2000512360A/ja not_active Withdrawn
- 1997-11-19 US US09/180,023 patent/US6076800A/en not_active Expired - Fee Related
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4463727A (en) * | 1981-09-08 | 1984-08-07 | Robert Bosch Gmbh | Diesel engine fuel injection system |
US4813601A (en) | 1987-02-14 | 1989-03-21 | Daimler-Benz Aktiengesellschaft | Piezoelectric control valve for controlling fuel injection valve in internal-combustion engines |
US5237968A (en) * | 1992-11-04 | 1993-08-24 | Caterpillar Inc. | Apparatus for adjustably controlling valve movement and fuel injection |
EP0615064A1 (de) * | 1993-03-08 | 1994-09-14 | Ganser-Hydromag | Steueranordnung für ein Einspritzventil für Verbrennungskraftmaschinen |
US5452858A (en) * | 1993-03-24 | 1995-09-26 | Nippon Soken Inc. | Fuel injector for internal combustion engine having throttle portion |
DE4406522C1 (de) * | 1994-02-28 | 1995-07-13 | Siemens Ag | Elektrohydraulisches Antriebselement |
DE4406901A1 (de) * | 1994-03-03 | 1995-09-14 | Daimler Benz Ag | Magnetventilgesteuerter Injektor für eine Brennkraftmaschine |
DE19519762A1 (de) * | 1994-08-25 | 1996-02-29 | Mitsubishi Electric Corp | Kraftstoffeinspritzsystem |
DE19519192C1 (de) * | 1995-05-24 | 1996-06-05 | Siemens Ag | Einspritzventil |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1063418A3 (de) * | 1999-06-25 | 2002-12-11 | Delphi Technologies, Inc. | Brennstoffeinspritzventil |
Also Published As
Publication number | Publication date |
---|---|
JP2000512360A (ja) | 2000-09-19 |
RU2193683C2 (ru) | 2002-11-27 |
KR20000010762A (ko) | 2000-02-25 |
US6076800A (en) | 2000-06-20 |
DE19709794A1 (de) | 1998-09-17 |
EP0900332A1 (de) | 1999-03-10 |
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