WO2003078825A1 - Kraftstoffeinspritzeinrichtung mit 3/2-wege-ventil - Google Patents
Kraftstoffeinspritzeinrichtung mit 3/2-wege-ventil Download PDFInfo
- Publication number
- WO2003078825A1 WO2003078825A1 PCT/DE2002/004542 DE0204542W WO03078825A1 WO 2003078825 A1 WO2003078825 A1 WO 2003078825A1 DE 0204542 W DE0204542 W DE 0204542W WO 03078825 A1 WO03078825 A1 WO 03078825A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- valve member
- valve
- chamber
- control
- 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
- 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
- F02M63/0031—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
- Pump-nozzle units are used for direct-injection ner internal combustion engines, or pump-line-nozzle systems (UPS) are used.
- the injection nozzles are connected to a high-pressure source via a short line or a bore.
- a very high peak pressure can be achieved at internal speed.
- switching valves are used on these injection systems, which can handle pressures of 300 to 500 times that of gasoline engines and switch much more frequently.
- a known K-fuel injection device has a fuel pump for each cylinder of the internal combustion engine, which has a pump piston driven by the internal combustion engine in a stroke movement. This delimits a pump work space, which is connected via a line to a fuel injection valve arranged separately from the fuel pump on the internal combustion engine.
- the fuel injection valve has an injection valve member, through which at least one injection opening is controlled. This can be moved in the opening direction against the closing force by the pressure generated in the pump work chamber.
- a first electrically controlled control valve is provided, by means of which a connection between the pump work chamber and a relief chamber is controlled and which is arranged close to the fuel pump.
- a second electrically controlled control valve is provided, which is arranged in the vicinity of the fuel injection valve and by which the pressure prevailing in a control pressure chamber of the fuel injection valve is controlled. This pressure acts on the injection valve member at least indirectly in the closing direction.
- a disadvantage of this solution is the fact that two electrically controlled control valves have to be provided, which increases the manufacturing effort and the complexity of this injection device.
- each cylinder of an internal combustion engine is assigned a high-pressure fuel pump and a fuel injection valve connected to it.
- a pump piston of the high pressure fuel pump is driven by the internal combustion engine, e.g. via the camshaft, driven in a stroke movement and delimits a pump work chamber which is connected to a pressure chamber of the fuel injection device.
- This comprises an injection valve member, through which at least one injection opening is controlled and which can be moved in an opening direction against the closing force by the pressure prevailing in the pressure chamber.
- a first control valve device controls an unthrottled connection and a connection via a throttling point of the pump work space to a relief space.
- a further, second control valve device controls a connection of a control pressure chamber of the fuel injection valve connected to the pump work chamber with the relief chamber. The injection valve member is acted upon by the pressure prevailing in the control pressure chamber in the closing direction.
- EP 0 957 261 AI also relates to a fuel injection device.
- This fuel injection device has a high-pressure fuel pump and a fuel injection valve connected to it for each cylinder of the internal combustion engine.
- the high-pressure fuel pump has a pump piston which is driven by the internal combustion engine in a stroke movement and delimits a pump working space.
- the fuel injection valve comprises a pressure chamber connected to the pump work chamber and an injection valve member, through which at least one injection opening is controlled and which can be moved in the opening direction to release the at least one injection opening by the pressure prevailing in the pressure chamber.
- a first control valve device consisting of a control valve, is provided, by means of which a connection of the pump work space to a relief space is controlled.
- a second control valve device consisting of a control valve, by means of which a connection between a control pressure chamber and a relief chamber is controlled.
- the injection valve member is acted upon by the pressure prevailing in the control pressure chamber at least indirectly in the closing direction and is the control pressure chamber connected to the pump work space.
- Both control valve devices are switched by a common electromagnetic actuator.
- a disadvantage of this fuel injection device is the fact that fuel injection is only possible in accordance with the pressure level generated by the fuel pump and the pressure at which the fuel injection device takes place cannot be varied.
- valve sections arranged one behind the other on the control valve member of a 3/3-way control valve proposed according to the invention short switching paths and thus short switching times can be achieved with the solution according to the invention, so that by switching several times an actuator designed as a solenoid valve, pre and post injections should be necessary be, can be displayed easily.
- a magnetic actuator, a piezo actuator or the like can be used to actuate the 3/3-way control valve proposed according to the invention in a pump-nozzle system or in a pump-line-nozzle system.
- the control valve member of the 3/3-way control valve can be provided in its head region with a plunger anchor, in the use of which the solenoid coil is embedded.
- control valve member of the 3/3-way control valve can also be actuated by means of a magnet coil fixedly arranged in the injector housing, it being possible to provide a flat anchor plate in the head region of the control valve member of the 3/3-way control valve.
- a pretensioning force can be generated, for example, by means of two spring elements arranged in parallel, one of which acts directly or with the interposition of a disc-shaped element on the lower end face of the control valve member, while the further spring element surrounding the first valve element is moved by a stop arranged movably in the housing of the injector body can be surrounded.
- a desired initial injection pressure can be preset, which can be overcome by a corresponding increase in the current supply to the actuator designed as a solenoid valve, so that the control valve member proposed according to the invention can be moved into a further switching position.
- FIG. 2 shows a pump-nozzle system with a 3/3-way control valve
- Figure 3.2 the 3/3-way control valve in a second switching position (seat valve
- FIG. 3.3 the 3/3-way control valve in a third switching position (both valve areas closed)
- FIG. 4 shows the curves of pump pressure, solenoid valve force, solenoid valve stroke and stroke path of the spring-loaded stop within the injector housing and plotted as a function of the camshaft angle 5 shows the curves of the nozzle pressure, nozzle needle lift, control chamber pressure and the course of the injection rate as a function of the camshaft angle.
- FIG. 1 shows a pump-nozzle system (UPS) with a controllable nozzle without reproducing a high-pressure source, for example a high-pressure pump.
- UPS pump-nozzle system
- FIG. 1 shows an injector 1 known from the prior art, in the injector body 2 of which an actuator 3 designed as a solenoid valve is arranged in the upper region.
- the actuator 3 is controlled via connections 4 and comprises a magnet coil 5.
- Opposite the magnet coil 5 of the actuator 3 is a flat-construction armature plate 6.1 of an armature arrangement 6.
- the anchor arrangement 6 has an anchor pin 6.2 almost in addition to the flat anchor plate 6.1.
- the magnet coil 5 of the actuator 3 is enclosed by a magnet sleeve 7.
- the actuator 3 is screwed into the head region of the injector body 2 by means of a clamping nut 8.
- the valve member 10 is enclosed within the injector housing 2 by an annular space 12, which in turn is connected to a high-pressure inlet 11 via a feed line.
- the high-pressure pump (not shown in FIG. 1) or its pump work space is connected to the high-pressure inlet 11.
- An inlet 13 branches off from the annular space 12 within the injector body 2 to a control space 14 within the injector body 2.
- the control chamber 14 acts on the upper end face of a push rod-shaped transmission element 15 which is enclosed by a closing spring 16 designed as a spiral spring.
- the closing spring 16 is supported on the one hand with its upper end face in the injector body 2 and with its lower end face on a pressure piece 17 which in turn acts on an injection valve member 18, for example in the form of a nozzle needle.
- the pressure piece 17 is received in a disc-shaped intermediate piece 19 which is centered on the injector body 2 by means of a centering pin 20.
- the injector body 2, the disc-shaped configured intermediate piece 19 and the injection valve member 18 are fixed to each other by means of a nozzle clamping nut 21 ⁇ .
- the injection valve member 18 is enclosed by a pressure chamber 22, which is connected to the high-pressure inlet 11 via a feed line 23 which extends through the injector body 2, the disk-shaped element 19 and the nozzle body.
- a pressure stage is formed on the injection valve member 18 within the pressure chamber 22, which enables the injection valve member 18 to be opened when the firing chamber 14 within the injector body 2 is relieved of pressure.
- injection openings 24 are indicated, via which fuel is injected into the combustion chamber of a direct injection internal combustion engine (not shown here) when the control chamber 14 is depressurized by actuating the control valve 9 and opening the injection valve member 18.
- the injection valve arrangement arranged at the end of the injector 1 on the combustion chamber side, comprising the injection valve member 18, the nozzle body, the pressure chamber 22 and the nozzle clamping nut 21, is identified by reference numeral 25.
- Figure 2 shows a pump-nozzle system with an actuator designed as a solenoid valve.
- FIG. 2 shows the structure of a pump-nozzle system according to the invention.
- an actuator 3 designed as a solenoid valve which is controlled via connections 4.
- the actuator 3 is enclosed by a sleeve-shaped jacket 7 and fastened in the head region of the injector body 2 by means of a clamping nut 8.
- the solenoid 5 of the actuator 3 designed as a solenoid valve is integrated in an insert 51 which is arranged in the head region of a control valve member 32 of a 3/3-way control valve 31.
- the armature formation 6.1 shown in FIG. 2 can also be formed in the head region of the control valve member 32 of the 3/3-way control valve 31, which is designed with such an embodiment variant in the magnetic core of the actuator 3 integrated magnetic coil 5 cooperates according to the representation of the injector in Figure 1.
- the injector body 2 or the injection valve 25 accommodated thereon is configured analogously to the injector already described in FIG. 1.
- the fuel under high pressure enters the inlet 23 to a pressure chamber 22 which is arranged in the injection valve 25 and surrounds the injection valve member 18 in the region of a pressure stage formed thereon.
- An inlet 41 extends from the high-pressure pump inlet 30 in the direction of the actuator 3, which can be embodied as a solenoid valve, to a first hydraulic chamber 34, which surrounds the control valve 32 of the 3/3-way control valve in the region of a first valve section 33.
- the first valve section 33 is designed as a seat valve.
- the first valve section 33 comprises a seat surface 35 which interacts with a corresponding surface of the housing surrounding the control valve member 32.
- a further, second valve section 36 which is designed as a slide valve section, is formed on the control valve member 32 of the 3/3-way control valve member 31.
- control edges 37 are formed which cooperate with the control edges 38 of the housing of the housing surrounding the control valve member 32. Furthermore, the second valve section 36 is enclosed by a second hydraulic chamber 39, from which a control chamber inlet line 40 branches off, which opens into the control chamber 14, which acts at least indirectly on the injection valve member 18.
- a piston section 43 which is enclosed by a third hydraulic space 42 on the low-pressure side.
- the end face 44 of the piston section 43 can, for example, be acted upon by a first spring element 48 accommodated in the cavity 50 with the interposition of a disk-shaped element 45.
- the first spring element 48 is enclosed in the cavity 50 below the control valve member 32 in the injector body 2 by a further, second spring element 49 designed as a spiral spring, which in turn acts upon a stop 46 movably received within the cavity 50 of the injector body 2.
- the upper end face of the second spring element 49 is overlapped by a collar surface 47 of the movably received stop 46.
- the first spring element 48 which acts directly on the control valve member 32 and the second spring element 49 acting on the resilient stop 46, are connected in parallel. Via the dimensioning of the first spring element 48 and the second spring element 49 acting on the resilient stop 46, the build-up of an initial injection pressure can be specified. This can be designed by setting the initial injection pressure accordingly by increasing the energization of the spring assembly 48 or 49, whereby the preload applied by the spring assembly 48 or 49 can be overcome by appropriate energization of the actuator 3 designed as a solenoid valve. In contrast to the embodiment variant of an injector 1 according to FIG.
- control chamber 14 according to the solution proposed according to the invention is connected on the one hand by a control chamber inlet line 40 to the second hydraulic chamber 39, which encloses the second valve section of the control valve member 32; on the other hand, the pressure relief controller 14 is connected via a relief line 52 to the cavity 50 and further to the third hydraulic space 42 on the low pressure side for pressure relief.
- Figure 3.1 shows the 3/2-way valve configured according to the invention in a first switching position (valve open).
- the first switching position 53 of the control valve member 32 of the 3/2-way control valve 31 according to FIG. 2 is shown in FIG. 3.1.
- this first switching state 53 i.e. in the de-energized state of the actuator 3, the first valve section 33 and the second valve section 36 are set into their open position by the action of the first spring element 48.
- the control valve member 32 is completely open and the fuel is diverted via the first valve section 33 and the second valve section 36.
- the fuel entering the first hydraulic chamber 34 from the inlet 41 (not shown in FIG.
- the part of the actuator 3 configured as plunger armature 5, 51 is energized by a small current and the position of the control valve member 32 by the resilient stop 46, which in the Cavity 50 is arranged below the control valve member 32, defined.
- the position of the resilient stop 46 is in turn dependent on the dimensioning of the second spring element 49 acting on the stop edge 47 within the cavity 50.
- Figure 3.3 shows the 3/3-way valve in a third switching position, the first and second valve sections closed.
- the third switching position of the control valve member 32 of the 3/3-way control valve 31, identified by reference numeral 55, is achieved if, starting from the second switching position 54 of the control valve member 32 shown in FIG. 3.2, further energization of the actuator 3 or the solenoid coil 5 of the plunger armature arrangement is achieved 5, 51 is made in the head region of the control valve member 32. Further energization of the plunger armature arrangement 5, 51 also moves the first valve section 33 of the control valve member 32 into its closed position, i.e. the pressure build-up from the first hydraulic space 34 via the control space feed line 40 into the control space 14 is ended.
- an injection phase is achieved in that the control valve member 32 of the 3/2-way Control valve 31 resumes its second switching position 54 and a pressure increase within the control chamber 14 occurs due to pressure build-up in the second hydraulic chamber 39 via the control chamber feed line 40.
- the injection valve member 18 moves back into its closed position.
- the first switching position 53 shown in FIG. 3.1 is switched, which relieves the high pressure system, since both valve sections 33 and 36 of the control valve member 32 assume their open position.
- Multiple actuations of the actuator 3 can be carried out to implement pre-and post-injection phases.
- the diagram according to FIG. 4 shows the curves of pump pressure, solenoid valve force, solenoid valve stroke and stroke of the stop 46, which are plotted as a function of the camshaft angle.
- the pump pressure curve is identified with reference number 60.
- the pump pressure reaches its maximum 61 towards the end of the injection.
- the pump pressure curve 60 is characterized by an essentially linear pressure rising edge 62.
- the stroke curve of the control valve member 32 is shown in dotted representation, which depending on the magnetic force either assumes a first stroke level 64 - for example to increase pressure - or assumes a second stroke level 65 if the magnetic force is further increased.
- the solenoid valve force 66 corresponding to the first stroke level 64 remains at a first level 67 (for example 50 Newtons) as long as the pressure increase continues without injection.
- a second magnetic force level 68 is set, which corresponds to a second stroke level 65 of the control valve member 32.
- the path of the movable stop 46, which is acted upon by the second spring element 49 on its collar 47, is represented by reference numeral 69.
- 5 shows the curves of nozzle pressure, nozzle needle lift, control chamber pressure and injection rate, which are plotted as a function of the camshaft angle.
- the course of the injected volume 70 is characterized by a linear increase 71 corresponding to the stroke 72 of the injection valve member 18.
- the injection valve member 18 After the injection valve member 18 has reached the closed position and the injection openings 24 have consequently closed at the end of the pump-nozzle system on the combustion chamber side, the injected volume changes to a constant profile, shown here by a straight line. As the camshaft angle increases, the pressure 73 at the injection valve member 18 rises steadily in order to reach its maximum towards the end of the injection, ie shortly before the injection valve member 18 closes in its seat for closing the injection openings 24. The rising phase of the injection pressure is indicated by the rising arrow 75.
- control chamber pressure 76 In parallel with the increase in the injection pressure at the injection valve member 18, the control chamber pressure 76 initially increases with increasing camshaft angle, which on the other hand leads to a pressure drop 77 there when the pressure in the control chamber 14 is released by opening the relief line 52, which results in an opening movement 78 of the injection valve member 18.
- the pressure 79 builds up within the control chamber 14 by acting on the control chamber 14 via the control chamber inlet line 40 (see illustration according to FIG. 2), the closing movement of the injection valve member 18 identified by reference numeral 80 occurs.
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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)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/478,182 US20040178283A1 (en) | 2002-03-20 | 2002-12-11 | Fuel injection device with a 3/2 way valve |
EP02792653A EP1488095A1 (de) | 2002-03-20 | 2002-12-11 | Kraftstoffeinspritzeinrichtung mit 3/2-wege-ventil |
JP2003576802A JP2005520966A (ja) | 2002-03-20 | 2002-12-11 | 3ポート3位置弁を備えた燃料噴射装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10212396.9 | 2002-03-20 | ||
DE10212396A DE10212396A1 (de) | 2002-03-20 | 2002-03-20 | Kraftstoffeinspritzeinrichtung mit 3/2-Wege-Ventil |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2003078825A1 true WO2003078825A1 (de) | 2003-09-25 |
Family
ID=27815810
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2002/004542 WO2003078825A1 (de) | 2002-03-20 | 2002-12-11 | Kraftstoffeinspritzeinrichtung mit 3/2-wege-ventil |
Country Status (5)
Country | Link |
---|---|
US (1) | US20040178283A1 (de) |
EP (1) | EP1488095A1 (de) |
JP (1) | JP2005520966A (de) |
DE (1) | DE10212396A1 (de) |
WO (1) | WO2003078825A1 (de) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4003770B2 (ja) * | 2004-10-01 | 2007-11-07 | トヨタ自動車株式会社 | 燃料噴射装置 |
DE102005033634A1 (de) * | 2005-07-19 | 2007-01-25 | Robert Bosch Gmbh | Hochdruck-Kraftstoffpumpe für ein Kraftstoff-Einspritzsystem einer Brennkraftmaschine |
US8443780B2 (en) | 2010-06-01 | 2013-05-21 | Caterpillar Inc. | Low leakage cam assisted common rail fuel system, fuel injector, and operating method therefor |
DE102017116367A1 (de) * | 2017-07-20 | 2019-01-24 | Liebherr-Components Deggendorf Gmbh | Vorrichtung zum Steuern eines Injektors |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1993023667A1 (en) * | 1992-05-18 | 1993-11-25 | Paul Marius A | Fuel injector system |
DE4236882C1 (de) * | 1992-10-31 | 1994-04-21 | Daimler Benz Ag | Kraftstoffeinspritzanlage mit einer Hochdruckpumpe und einer gemeinsamen Versorgungsleitung für alle Einspritzdüsen mit Magnetventilsteuerung |
DE19803910A1 (de) * | 1997-05-09 | 1998-11-12 | Fev Motorentech Gmbh & Co Kg | Steuerbares Einspritzventil für die Kraftstoffeinspritzung an Brennkraftmaschinen |
DE19729844A1 (de) * | 1997-07-11 | 1999-01-14 | Bosch Gmbh Robert | Kraftstoffeinspritzvorrichtung |
WO2001018381A1 (de) * | 1999-09-02 | 2001-03-15 | Robert Bosch Gmbh | Gebautes steuerventil für einen injektor eines kraftstoffeinspritzsystems für brennkraftmaschinen |
WO2001029395A2 (de) * | 1999-10-22 | 2001-04-26 | Robert Bosch Gmbh | Hydraulische steuervorrichtung, insbesondere für einen injektor |
DE19956598A1 (de) * | 1999-11-25 | 2001-06-13 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
WO2002048540A1 (de) * | 2000-12-16 | 2002-06-20 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4465231A (en) * | 1982-03-29 | 1984-08-14 | Deere & Company | Control device and method for activating a fuel injector nozzle |
GB9616521D0 (en) * | 1996-08-06 | 1996-09-25 | Lucas Ind Plc | Injector |
US5927614A (en) * | 1997-08-22 | 1999-07-27 | Touvelle; Matthew S. | Modular control valve for a fuel injector having magnetic isolation features |
US5897058A (en) * | 1997-09-25 | 1999-04-27 | Caterpillar Inc. | High pressure metal to metal sealing land in a control valve for a fuel injector |
US5915624A (en) * | 1997-11-03 | 1999-06-29 | Caterpillar Inc. | Fuel injector utilizing a biarmature solenoid |
DE10012552A1 (de) * | 2000-03-15 | 2001-09-27 | Bosch Gmbh Robert | Einspritzeinrichtung mit einem Aktor zur Nadelhubsteuerung |
-
2002
- 2002-03-20 DE DE10212396A patent/DE10212396A1/de not_active Ceased
- 2002-12-11 WO PCT/DE2002/004542 patent/WO2003078825A1/de not_active Application Discontinuation
- 2002-12-11 US US10/478,182 patent/US20040178283A1/en not_active Abandoned
- 2002-12-11 EP EP02792653A patent/EP1488095A1/de not_active Withdrawn
- 2002-12-11 JP JP2003576802A patent/JP2005520966A/ja active Pending
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1993023667A1 (en) * | 1992-05-18 | 1993-11-25 | Paul Marius A | Fuel injector system |
DE4236882C1 (de) * | 1992-10-31 | 1994-04-21 | Daimler Benz Ag | Kraftstoffeinspritzanlage mit einer Hochdruckpumpe und einer gemeinsamen Versorgungsleitung für alle Einspritzdüsen mit Magnetventilsteuerung |
DE19803910A1 (de) * | 1997-05-09 | 1998-11-12 | Fev Motorentech Gmbh & Co Kg | Steuerbares Einspritzventil für die Kraftstoffeinspritzung an Brennkraftmaschinen |
DE19729844A1 (de) * | 1997-07-11 | 1999-01-14 | Bosch Gmbh Robert | Kraftstoffeinspritzvorrichtung |
WO2001018381A1 (de) * | 1999-09-02 | 2001-03-15 | Robert Bosch Gmbh | Gebautes steuerventil für einen injektor eines kraftstoffeinspritzsystems für brennkraftmaschinen |
WO2001029395A2 (de) * | 1999-10-22 | 2001-04-26 | Robert Bosch Gmbh | Hydraulische steuervorrichtung, insbesondere für einen injektor |
DE19956598A1 (de) * | 1999-11-25 | 2001-06-13 | Bosch Gmbh Robert | Ventil zum Steuern von Flüssigkeiten |
WO2002048540A1 (de) * | 2000-12-16 | 2002-06-20 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine |
Also Published As
Publication number | Publication date |
---|---|
US20040178283A1 (en) | 2004-09-16 |
DE10212396A1 (de) | 2003-10-09 |
JP2005520966A (ja) | 2005-07-14 |
EP1488095A1 (de) | 2004-12-22 |
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