EP1239146A2 - Kraftstoffeinspritzsystem für Brennkraftmaschinen - Google Patents
Kraftstoffeinspritzsystem für Brennkraftmaschinen Download PDFInfo
- Publication number
- EP1239146A2 EP1239146A2 EP02001824A EP02001824A EP1239146A2 EP 1239146 A2 EP1239146 A2 EP 1239146A2 EP 02001824 A EP02001824 A EP 02001824A EP 02001824 A EP02001824 A EP 02001824A EP 1239146 A2 EP1239146 A2 EP 1239146A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- control
- pressure
- fuel injection
- 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.)
- Withdrawn
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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
- F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
- F02M63/0007—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using electrically actuated valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- 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
Definitions
- the invention relates to a fuel injection system the genus of claim 1.
- a fuel injection system is for example from DE 197 01 879 A1 known, in the case of a high-pressure fuel pump Fuel is pumped into a high pressure plenum is maintained in which a predetermined high fuel pressure becomes. High-pressure lines go from this high-pressure collecting space to each fuel injector, which Inject fuel into the combustion chambers of the internal combustion engine.
- a fuel injection valve has a piston-shaped one Valve member on that counter in a bore a closing force is arranged longitudinally displaceable and that has a printing area, which is located in a printing space and there is acted upon by fuel pressure.
- the known fuel injection system also includes a control valve which is designed as a 3/2-way valve and that the connection between the pressure room, the high pressure collection room and opens or interrupts a leak oil system.
- a control valve which is designed as a 3/2-way valve and that the connection between the pressure room, the high pressure collection room and opens or interrupts a leak oil system.
- the control valve opens the connection between the pressure chamber and the high-pressure collection chamber and fuel flows into the pressure chamber, so that at a corresponding Fuel pressure through the hydraulic force on the pressure surface the valve member is moved against the closing force and exposes the injection ports.
- To end the injection moves the control valve to the second position and the connection of the high-pressure collection chamber with the pressure chamber interrupted.
- the control valve Pressure chamber connected to the leak oil system so that the fuel pressure decreases rapidly in the pressure room and finally the Closing force is greater than the hydraulic force on the Pressure area, so that the valve member back into the Closed position.
- the fuel pressure in the pressure chamber is degraded very quickly due to the connection with the leak oil system, and the valve member closes the injection openings with very little time delay after switching the Control valve.
- the known fuel injection system the disadvantage that the closing of the valve member only indirectly via the decreasing fuel pressure controlled in the pressure chamber with a constant closing force becomes. With modern fuel injection systems that are very must be precisely controlled to ensure optimal combustion processes to ensure this locking mechanism under May not be determined precisely enough.
- the known fuel injection system has the disadvantage that the fuel pressure in the pressure chamber at the beginning Valve member closing movement has already dropped so much that the valve member, driven by the force of the Closing spring, almost unbraked with the valve sealing surface sits on the valve seat. With longer operation it can therefore excessive wear in the area of the valve seat come, which changes the injection characteristics of the Fuel injector adversely over time changes.
- the control valve opens the Connection of the high pressure line to the control room, so results a hydraulic closing force on the piston that over the push rod pushes the valve member into the closed position, so that it is accelerated by the hydraulic pressure in the Control room is moved to the closed position until the valve member rests on the valve seat. If an injection is to take place, so the connection of the high pressure line is through the control valve to the control room interrupted and the control room connected to a relief room. This reduces the hydraulic Force on the piston so that the hydraulic Force on the pressure surface of the valve member predominates and this is moved into an open position.
- This fuel injection system has the disadvantage, however, that the Valve element due to the high pressure in the control room for the closed position is strongly accelerated towards the valve seat hits at a high speed.
- the known fuel injection system Disadvantage that the piston is formed in a valve body is, in which very many holes and openings are formed have to be. For this reason, the valve body can only be made from a relatively soft steel, which is in the area of the moving piston lead to increased wear can and thus reduce the lifespan.
- valve member by the residual pressure in Pressure chamber only accelerated at the beginning of the closing movement and so the time of closing can be determined exactly is without excessive wear in the area of the Valve seat comes.
- the valve member is with a piston connected, a cylindrical at its opposite end End section and part of the total stroke of the valve member in a control section of the connection immersed between the control valve and the relief chamber.
- the pressure chamber of the Fuel injector via the control valve with the Piston connected so that the relatively high residual pressure in Pressure chamber acts on the piston and this makes it hydraulic Force experiences the piston and thus the valve member moved in the closing direction of the valve member.
- part of the closing movement is the cylindrical one End portion of the piston from the control section off, so that now the pressure chamber directly with the relief chamber is connected.
- the hydraulic force drops the piston so that the valve member is relatively gentle with its Valve sealing surface sits on the valve seat and there is none increased wear comes.
- the valve member is also with a hydraulic force after the closing movement has ended held in the closed position so that no combustion gases from the combustion chamber of the internal combustion engine into the injection openings can penetrate (blow back). Such combustion gases can lift the valve member and into the Penetrate pressure chamber, so that the subsequent injection is affected.
- the piston is arranged in a sleeve which in the connection from the control valve to the relief chamber is.
- the sleeve preferably consists of a hard one Steel that is harder than the steel that makes up the case of the control valve is made. This will reduce on the one hand the friction of the piston at its Longitudinal movement, which is the life of the fuel injector extended.
- the housing of the control valve made of a relatively soft steel be so that there are necessary bores and recesses can be trained easily and therefore inexpensively.
- the piston lateral recesses on the cylindrical end portion connect to the relief room.
- These recesses can be used advantageously in manufacturing form the piston on its outer surface, which is essential is easier and cheaper than corresponding recesses on the inner wall of the corresponding hole.
- a fuel injection system is shown that from a high-pressure fuel supply 2, a leak oil system 4 and a fuel injector 1.
- the Fuel injection valve 1 is shown in longitudinal section, while the high pressure fuel supply 2 and the leak oil system 4 are only shown schematically.
- a fuel tank 3 becomes a fuel line 5 fuel supplied to a high pressure pump 7, the High pressure fuel through a high pressure line 8 in a high-pressure plenum serving as a high-pressure fuel source 10 promotes.
- the high-pressure plenum 10 is by a a control device, not shown in the drawing maintain the specified high fuel pressure.
- From the high pressure collecting room 10 go a variety of high pressure lines 12, each with a fuel injection valve 1 are connected, of which only one is shown in FIG. 1 is.
- the fuel injection valve 1 has a valve holding body 15 on, with the interposition of a washer 17 by a clamping nut 22 in the axial direction is clamped against a valve body 20.
- valve holder body 15 In the valve holder body 15 is an inlet channel 25 which is formed with the high pressure line 12 is connected.
- the inlet channel 25 can be connected to an inlet bore 27 via a control valve 30, through the valve holding body 15 and the washer 17 extends into the valve body 20.
- a bore 62 In the valve body 20 is formed a bore 62 in which a piston-shaped valve member 60 is arranged to be longitudinally displaceable is.
- the valve member 60 is in a direction away from the combustion chamber Section in the bore 62 sealingly guided, tapers the combustion chamber to form a pressure surface 65 and goes at its end in a substantially conical valve sealing surface 66 over that with an at the combustion chamber end of Bore 62 trained valve seat 70 cooperates.
- Valve seat 70 in the Valve seat 70 is formed at least one injection opening 68, which bore 62 with the combustion chamber of the internal combustion engine combines.
- a pressure chamber 64 in the area of the pressure surface 65 formed as a surrounding the valve member 60 Ring channel continues up to valve seat 70.
- In the pressure room 64 opens the inlet bore 27, so that the pressure chamber 64 over the inlet bore 27 is filled with fuel under high pressure can be.
- a spring chamber 72 is formed in the valve holding body 15, which serves as a relief space and designed as a hole is which is arranged coaxially to the bore 62 and via a central opening 67 formed in the intermediate disk 17 is connected to the bore 62. Opens into the spring space 72 an outlet channel 24 formed in the valve holding body 15, which via a leak oil line 18 to the fuel tank 3rd is connected, so that in the spring chamber 72 always a lower There is fuel pressure. In the central opening 67 of the Between the washer 17, a spring plate 69 is arranged, the is connected to the valve member 60 and into the spring chamber 72 protrudes.
- FIG. 2 is an enlarged view in the area of the spring chamber 72 of Figure 1 shown.
- the central opening 67 instructs the contact surface of the intermediate disk 17 on the valve body 20 a diameter that is less than the diameter the bore 62 so that a stop surface on the washer 17 73 is formed.
- a Pressure pin 40 arranged, which is connected to the spring plate 69 and at its end facing away from the combustion chamber into one Piston 45 merges. 2 this area of the fuel injector 1 shown enlarged.
- the piston 45 is arranged in the guide bore 90 of a sleeve 42, arranged at the end of the spring chamber 72 facing away from the combustion chamber is.
- the sleeve 42 faces away from the valve member 60 End a collar so that there is a control section 48 is formed, the smaller diameter has as the guide bore 90.
- the closing spring 74 is supported with the interposition of a shim 29 the sleeve 42, so that the sleeve 42 by the force of Closing spring 74 against the end of the spring chamber facing away from the combustion chamber 72 is pressed.
- a cylindrical one End portion 44 formed, the diameter exactly the diameter of the control section 48 of the sleeve 42 equivalent.
- the cylindrical end portion 44 is one Limited control edge 93, which cooperates with a sealing edge 92, the end of the control section facing the valve member 48 is formed so that a valve is thereby formed becomes.
- the sealing edge 92 of the control edge 93 an axial distance u.
- a stop shoulder 96 At the transition of the cylindrical end portion 44 to the piston 45 is at Piston 45 formed a stop shoulder 96; that of the Stop surface 94 of the sleeve 42 has an axial distance h, which limits the total stroke of the valve member 60.
- the stop surface 94 at the transition of the control section 48 formed for the guide bore 90 is the stop surface 94 at the transition of the control section 48 formed for the guide bore 90.
- On the outer surface of the piston 45 are two recesses 43 formed, which face each other on the piston 45, so that only one recess 43 is visible in the drawing.
- the Recesses 43 connect the cylindrical end section 44 with the spring chamber 72. In the closed position of the valve member 60, that is when the valve sealing surface 66 on the valve seat 70 is present, the piston 45 has an axial distance of the shim 29 so that the control section 48th is connected to the spring chamber 72 via the recesses 43.
- the spring chamber 72 is controlled by a control connection from the guide bore 90, the control section 48 and one Connection bore 47 formed in the valve holding body 15 composed, with a formed in the valve holding body 15
- Control room 50 connected which is cylindrical and facing away from the valve member 60 into a control bore 38 transforms.
- the control bore 38 is parallel to the bore 62 formed, but it may also be provided can that both holes are coaxial with each other, one Include angles with each other or perpendicular to each other are.
- the control bore 38 is stepped in diameter. At the mouth of the control bore 38 in the control room 50 is the control bore 38 as a sliding section 138 educated. In the further course, the control borehole widens 38 radially to form a conical control valve seat 52 and then goes into a guide section 238 about.
- the control bore 38 is at the end via an intermediate bore 49 connected to a drain oil chamber 51, which with the drain channel 24 is connected and in which an electromagnet 34 is located, the one also arranged in the leak oil chamber 51 Magnetic armature 36 is operatively connected.
- a piston-shaped control valve member 32 which in the guide section 238 with a first section 132 is performed sealingly.
- the control valve member 32 tapers the control room 50 and goes into a smaller in diameter second section 232 so that between the second Section 232 of the control valve member 32 and the wall of the Guide portion 238 of the control valve bore 38 an annular first high pressure space 55 is formed, in which the Inlet channel 25 opens.
- control valve member 32 proceeds from the formation of a conical one Control valve sealing surface 54 in one opposite second section 232 reduced in diameter third Section 332 of the control valve member 32 via.
- This third Section 332 is arranged within the slide section 138, so that between the third portion 332 of the control valve member 32 and the wall of the control valve bore 38 a second high-pressure space 56 is formed, which is also is annular and from which the inlet bore 27 leads to the pressure chamber 64.
- the control valve sealing surface 54 forms a first valve together with the control valve seat 52, through which the inlet channel 25 with the inlet bore 27 is connectable.
- the end of the control chamber 50 facing Control valve member 32 is one against the third Section 332 of the control valve member 32 enlarged in diameter Slider head 39 formed which when the control valve sealing surface 54 rests on the control valve seat 52 in the Control room 50 protrudes.
- a slide edge 57 thereon trained with a at the transition of the control valve bore 38 to the control chamber 50 formed sealing edge 58 cooperates.
- the diameter of the slide head 39 is only slight smaller than the diameter of the slide bore 138 the control valve bore 38 so that the slide head 39 sealing can dip into the slide bore 138.
- control valve member 32 At the end facing away from the control chamber 50 is the control valve member 32 connected to the magnet armature 36 via a pin 53. If the electromagnet 34 is suitably energized, then the armature 36 and the pin 53 also the control valve member 32 moved away from the combustion chamber in the axial direction, so that the control valve sealing surface 54 from the control valve seat 52 lifts off and the first high-pressure chamber 55 with the second high-pressure chamber 56 connects. As soon as the slide edge 57 of the Slider head 39 and the sealing edge 58 on the combustion chamber side End of the slide bore 138 is formed, opposite, the slide head 39 closes the control chamber 50 against the second high-pressure chamber 56.
- the fuel injector works like follows:
- the high-pressure plenum 10 is via the high-pressure line 12 and the inlet channel 25 with the first high-pressure chamber 55 connected so that in the first high-pressure chamber 55 always on high fuel pressure is present. If an injection is to take place, so the electromagnet 34 is energized, so that the magnet armature 36 is moved and also about the pin 53 Control valve member 32.
- By lifting the control valve sealing surface 54 of the control valve seat 52 becomes the first pressure chamber 55 connected to the second pressure chamber 56 and thus also the inlet channel 25 with the inlet bore 27, so that the Pressure chamber 64 now inflows fuel under high pressure.
- valve member 60 Because the fuel in this room at the next Opening stroke movement of the valve member 60 is compressed is obtained in the further course of the opening stroke movement the valve member 60 a certain damping, so that the valve member 60 after passing through the total stroke h, that is when the stop shoulder 96 on the stop surface 94 comes to the system, somewhat slowed down in its opening stroke movement becomes.
- the valve member 60 does not come here Stop surface 73 of the washer 17 for contact. It can however, it can also be provided that the stroke of the valve member 60 is limited by the abutment on the stop surface 73, while between the stop surface 94 and the stop shoulder 96 a residual gap remains.
- the electromagnet 36 is suitably energized and the armature 36 moves the control valve member via the pin 53 32 in the axial direction towards the control room 50.
- the pressure chamber 64 via the inlet bore 27 with the control chamber 50 and over the connection hole 47 is connected to the control section 48.
- the cylindrical end portion 44 is also the still relatively high fuel pressure in the control chamber 50, so that on the piston 45 and over the Push pin 40 also on valve member 60 an additional hydraulic force in the closing direction results.
- valve member 60 Because now on the one hand the hydraulic pressure in the pressure chamber 64 decreases and on the other hand on the valve member 60 both the force of the Closing spring 74 as well as the hydraulic force on the piston 45 acts, the valve member 60 is accelerated in the closing direction emotional. After the valve member 60 the differential stroke h-u has passed, the cylindrical end section dips 44 from the control section 48. Does that move Valve member 60 continues in the closing direction, the control room 50 via the connecting bore 47 and the recesses 43 connected to the spring chamber 72 on the piston 45 and thus depressurized. As a result, the hydraulic pressure in the Control room 50 dismantled very quickly, and the hydraulic one Force on the cylindrical end portion 44 of the piston 45 omitted.
- valve member 60 The further closing movement of the valve member 60 is therefore only advanced by the force of the closing spring 74. As a result, the valve member 60 comes, also damped by the residual pressure in the pressure chamber 64, on the valve seat 70 to the system and closes the injection openings again 68.
- the control valve member 32 continues its closing movement long until the control valve sealing surface 54 on the control valve seat 52 is present and so the first high-pressure chamber 55 again closes against the second high-pressure chamber 56.
- the pressure room 64 is further relieved via the inlet bore 27 until it is completely depressurized.
- sleeve 42 is preferred made from a very hard steel that is extremely is low wear, so that between the sleeve 42 and the Piston 45, which is also made of a very hard steel may be little friction occurs.
- the hardness the steel of the sleeve 42 is significantly higher than that Hardness of the steel of the valve holding body 15.
- valve holding body 15 is constructed in several parts.
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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
- Figur 1 ein Kraftstoffeinspritzsystem im schematischen Aufbau zusammen mit einem Kraftstoffeinspritzventil im Längsschnitt,
- Figur 2 eine Vergrößerung von Figur 1 im Bereich des Entlastungsraums und
- Figur 3 eine Vergrößerung von Figur 1 im Bereich des Steuerventils.
Claims (7)
- Kraftstoffeinspritzsystem für Brennkraftmaschinen mit einem Kraftstoffeinspritzventil (1), das ein Gehäuse aufweist, in dem in einer Bohrung (62) ein Ventilglied (60) axial beweglich angeordnet ist, welches Ventilglied (60) hydraulisch gesteuert durch den Kraftstoffdruck in einem Druckraum (64) entgegen einer Schließkraft längsverschiebbar ist und dadurch wenigstens eine Einspritzöffnung (68) steuert, und mit einem Steuerventil (30), durch das die Verbindung des Druckraums (64) mit einer Kraftstoffhochdruckquelle (10) und/oder eines Entlastungsraums (72) gesteuert wird, dadurch gekennzeichnet, daß das Steuerventil (30) mit dem Entlastungsraum (72) über eine Steuerverbindung verbunden ist, die durch ein zusätzliches Ventil verschließbar ist, welches als Steuerglied einen Kolben (45) aufweist, der sich synchron mit dem Ventilglied (60) in Längsrichtung bewegt und der einen Endabschnitt (44) aufweist, an dem eine Steuerkante (93) ausgebildet ist, welche nach einem Teil des Gesamthubs des Kolbens (45) in einen Steuerabschnitt (48) der Steuerverbindung eintaucht und diese verschließt.
- Kraftstoffeinspritzsystem nach Anspruch 1, dadurch gekennzeichnet, daß der Endabschnitt (44) zylinderförmig ausgebildet ist und die Steuerkante (93) am Ende des Endabschnitts (44) ausgebildet ist.
- Kraftstoffeinspritzsystem nach Anspruch 1, dadurch gekennzeichnet, daβ das Steuerventil (30) zwei Schaltstellungen aufweist, wobei es in der ersten Schaltstellung zum Öffnen des Kraftstoffeinspritzventils (1) die Verbindung der Kraftstoffhochdruckquelle (10) zu dem Druckraum (64) öffnet und die Verbindung des Entlastungsraums (72) mit dem Druckraum (64) unterbricht und in der zweiten Schaltstellung zum Schließen des Kraftstoffeinspritzventils (1) den Druckraum (64) mit dem Entlastungsraum (72) verbindet und dabei die Verbindung des Druckraums (64) mit der Kraftstoffhochdruckquelle (10) unterbricht (3/2-Wegeventil).
- Kraftstoffeinspritzsystem nach Anspruch 1, dadurch gekennzeichnet, daß der Kolben (45) in einer Hülse (,42) angeordnet ist.
- Kraftstoffeinspritzsystem nach Anspruch 4, dadurch gekennzeichnet, daß die Hülse (42) aus einem härteren Stahl gefertigt ist als das Gehäuse des Kraftstoffeinspritzventils.
- Kraftstoffeinspritzsystem nach Anspruch 1, dadurch gekennzeichnet, daß der Kolben (45) seitliche Ausnehmungen (43) aufweist, die den zylinderförmigen Endabschnitt (43) mit dem Entlastungsraum (72) verbinden.
- Kraftstoffeinspritzsystem nach Anspruch 1, dadurch gekennzeichnet, daß der Kolben (45) koaxial zum Ventilglied (60) angeordnet ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10108719 | 2001-02-23 | ||
DE2001108719 DE10108719A1 (de) | 2001-02-23 | 2001-02-23 | Kraftstoffeinspritzsystem für Brennkraftmaschinen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1239146A2 true EP1239146A2 (de) | 2002-09-11 |
EP1239146A3 EP1239146A3 (de) | 2004-01-21 |
Family
ID=7675225
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02001824A Withdrawn EP1239146A3 (de) | 2001-02-23 | 2002-01-26 | Kraftstoffeinspritzsystem für Brennkraftmaschinen |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP1239146A3 (de) |
DE (1) | DE10108719A1 (de) |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5012982A (en) * | 1986-11-15 | 1991-05-07 | Hitachi, Ltd. | Electromagnetic fuel injector |
DE19701879A1 (de) * | 1997-01-21 | 1998-07-23 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen |
US6067955A (en) * | 1997-09-24 | 2000-05-30 | Robert Bosch Gmbh | Fuel injection device for internal combustion engines |
DE19923421A1 (de) * | 1999-05-21 | 2000-11-30 | Bosch Gmbh Robert | Injektor |
DE10033426A1 (de) * | 2000-07-10 | 2002-01-24 | Bosch Gmbh Robert | Injektor/Düsennadel-Kombination mit steuerraumseitiger Kopplung |
WO2002033250A1 (de) * | 2000-10-18 | 2002-04-25 | Robert Bosch Gmbh | Kraftstoffeinspritzsystem für brennkraftmaschinen |
-
2001
- 2001-02-23 DE DE2001108719 patent/DE10108719A1/de not_active Withdrawn
-
2002
- 2002-01-26 EP EP02001824A patent/EP1239146A3/de not_active Withdrawn
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5012982A (en) * | 1986-11-15 | 1991-05-07 | Hitachi, Ltd. | Electromagnetic fuel injector |
DE19701879A1 (de) * | 1997-01-21 | 1998-07-23 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen |
US6067955A (en) * | 1997-09-24 | 2000-05-30 | Robert Bosch Gmbh | Fuel injection device for internal combustion engines |
DE19923421A1 (de) * | 1999-05-21 | 2000-11-30 | Bosch Gmbh Robert | Injektor |
DE10033426A1 (de) * | 2000-07-10 | 2002-01-24 | Bosch Gmbh Robert | Injektor/Düsennadel-Kombination mit steuerraumseitiger Kopplung |
WO2002033250A1 (de) * | 2000-10-18 | 2002-04-25 | Robert Bosch Gmbh | Kraftstoffeinspritzsystem für brennkraftmaschinen |
Also Published As
Publication number | Publication date |
---|---|
EP1239146A3 (de) | 2004-01-21 |
DE10108719A1 (de) | 2002-09-05 |
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