EP0946830B1 - Fuel injection system for an internal combustion engine - Google Patents

Fuel injection system for an internal combustion engine Download PDF

Info

Publication number
EP0946830B1
EP0946830B1 EP98954191A EP98954191A EP0946830B1 EP 0946830 B1 EP0946830 B1 EP 0946830B1 EP 98954191 A EP98954191 A EP 98954191A EP 98954191 A EP98954191 A EP 98954191A EP 0946830 B1 EP0946830 B1 EP 0946830B1
Authority
EP
European Patent Office
Prior art keywords
fuel
pressure
additional
injection system
line
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.)
Expired - Lifetime
Application number
EP98954191A
Other languages
German (de)
French (fr)
Other versions
EP0946830A1 (en
Inventor
Manfred Ruoff
Horst Harndorf
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0946830A1 publication Critical patent/EP0946830A1/en
Application granted granted Critical
Publication of EP0946830B1 publication Critical patent/EP0946830B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F02M43/00—Fuel-injection apparatus operating simultaneously on two or more fuels, or on a liquid fuel and another liquid, e.g. the other liquid being an anti-knock additive
    • F02M43/04—Injectors peculiar thereto
    • 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
    • F02M43/00—Fuel-injection apparatus operating simultaneously on two or more fuels, or on a liquid fuel and another liquid, e.g. the other liquid being an anti-knock additive
    • 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
    • F02M43/00—Fuel-injection apparatus operating simultaneously on two or more fuels, or on a liquid fuel and another liquid, e.g. the other liquid being an anti-knock additive
    • F02M43/02—Pumps peculiar thereto
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator

Definitions

  • the invention is based on a fuel injection system for an internal combustion engine according to the preamble of the claim 1.
  • Such fuel injection systems are, for example, from known from DE 4337 048 C2.
  • a two-component nozzle provided the stratified injection of Fuel and an additional liquid, such as diesel fuel and water serves to reduce pollutant emissions To reduce internal combustion engine and, if necessary, the efficiency to increase.
  • an additional liquid such as diesel fuel and water serves to reduce pollutant emissions To reduce internal combustion engine and, if necessary, the efficiency to increase.
  • the known Injection system also realizes the so-called common rail technology, in which all operating the internal combustion engine High pressure fuel injectors be fed from a common rail pressure accumulator.
  • a disadvantage of the known fuel injection system is that for each individual injector for metering the additional liquid a complex and relatively expensive 3/2-way valve as well as for the control of the diesel injection quantity another 3/2-way valve is required.
  • the additional liquid is the first 3/2-way valve Fuel supply from the common rail pressure accumulator to the injection nozzle interrupted and at the same time the injector surrounding pressure chamber, in the high pressure Fuel is stored through an appropriate position of the first 3/2-way valve to the fuel low pressure side drained out. Due to the pressure drop in the pressure chamber is additional liquid via a corresponding line conveyed into the pressure chamber, which is the corresponding fuel volume repressed.
  • the first 3/2-way valve brought back into a position that connects between the common rail pressure accumulator and the pressure chamber in the injection valve.
  • the amount of fuel to be injected that of the upstream Additional liquid in the through the next valve opening is to follow the injection burst caused
  • Another 3/2-way solenoid valve is provided, which is the rear the nozzle needle by a spring in the closed position is held, either with the common rail pressure accumulator or connects to the fuel low pressure side and thereby the stroke of the valve needle, the opening and Closing the valve and thus the desired injection quantity controls.
  • the known fuel injection system is required the two precisely working for each individual injector and thus complex 3/2-way solenoid valves to both the desired amount of fuel as well as the required amount to be able to precisely dose additional liquid.
  • the fuel injection system according to the invention has constructional simplification and thus for a cheaper manufacture the characteristic features of the claim 1 on.
  • This allows the two elaborate and expensive 3/2 solenoid control valves due to simpler and cheaper 2/2-way valves to be replaced, at the same time the possibility is opened for the quantity dosing Additional liquid on a single, precisely working metering valve to shift that a whole group of injectors can operate.
  • the second 2/2-way valve only the opening and closing times for the additional liquid pre-storage is determined, the quantity dosage for the amount of fuel to be injected by a corresponding Time control of the first 2/2-way valve in the injection line between the common rail pressure accumulator and the Pressure chamber.
  • the nozzle needle at the blunt end of their injector plunger in radial extension small piston that carries high pressure from the common rail pressure accumulator exposed space, which in turn protrudes pressure-tight against the space surrounding the nozzle needle is sealed.
  • Fuel injection system is used to promote the Additional liquid uses a membrane, one of which Side with the prevailing in the common rail pressure accumulator High pressure is applied, and the other side due the pressure pulses in the common rail pressure accumulator either directly or via a lever mechanism to promote the additional liquid into the additional liquid line leading to the two-substance nozzle causes.
  • the indirect delivery of additional liquid can, for example via a pump piston, which is carried out by a Lever mechanism is connected to the membrane and at Pressure changes in the common rail pressure accumulator that lead to a Membrane movement, a corresponding amount of additional liquid promotes.
  • a pump piston which is carried out by a Lever mechanism is connected to the membrane and at Pressure changes in the common rail pressure accumulator that lead to a Membrane movement, a corresponding amount of additional liquid promotes.
  • a massive partition wall also mass wall
  • the membrane at one end of the common rail pressure accumulator clamped, with an aperture hole in the bulk wall is provided, the damped pressure equalization between the common rail accumulator and the space between the mass wall and the membrane allows.
  • a low pass filter would correspond to the mass wall the inductance, the orifice hole the ohmic resistance and the membrane a capacitor.
  • An embodiment of the is also very particularly preferred Fuel injection system according to the invention, in which a additional common rail pressure accumulator to accommodate under Pressurized additional liquid is provided, which via a 2/2-way valve with the one leading to the two-component nozzle Auxiliary liquid line is connected and similar advantages has like the known common rail pressure accumulator for fuel.
  • a further common rail pressure accumulator of the above described delivery mechanism for the additional liquid considerably simplify by placing the diaphragm over a check valve directly and without interposing a pump piston driving lever mechanism by passing on corresponding Pressure surges on the other common rail pressure accumulators cause the pumping of additional liquid.
  • a particular advantage of using another common rail pressure accumulator for additional liquid is that the 2/2-way valve in the additional liquid line can supply whole group of injectors, whereby only It must be ensured that there is no overlap in time the metering processes for the individual injectors occur.
  • the fuel injection system according to the invention for a Internal combustion engine for bifluid fuel injection (usually diesel fuel) and an additional liquid (usually water) a high pressure pump 1 supplies one Common rail pressure accumulator 2 with fuel at a pressure level of around 1800 bar.
  • a high pressure pump 1 supplies one Common rail pressure accumulator 2 with fuel at a pressure level of around 1800 bar.
  • an injection line 6 pressure chamber 3.5 to be supplied with fuel which is the nozzle needle 3.1 surrounds a two-substance nozzle 3
  • must now be a metering Component can be arranged, since the earlier usual classic injection pump through the combination of Common rail pressure accumulator 2 and the simpler high pressure pump 1 was replaced and the rail pressure on a certain Level is constantly present.
  • This task takes over at the arrangement of the invention a first 2/2-way valve MV1.
  • the exact amount is metered over the known (measured or controlled) pressure drop between the commom rail pressure accumulator 2 and that of the two-substance nozzle 3 combustion chamber of the internal combustion engine to be supplied through an exact time window, the size of which is influenced by other factors depends on an electrical control that is not shown in the drawing.
  • a path for the fuel to be displaced by the additional liquid from the two-substance nozzle 3 must now be cleared, as is known per se in principle from the prior art.
  • This is done by suitably wiring a second 2/2-way valve MV2, the input of which is connected to the injection line 6 via a supply line 7 and the output of which is connected to the low-pressure fuel side via a discharge line 8.
  • the first 2/2-way valve MV1 is fired and the second 2/2-way valve is switched to passage.
  • fuel under high pressure escapes from the pressure chamber 3.5 via the injection line 6, the feed line 7, the discharge line 8 and a check valve 9 to the low-pressure fuel side, as a rule the fuel tank.
  • M pump 13 which has a working fluid at a pre-pressure level of about 2.5 bar in a separating piston adapter 10 with a Separating piston 11 and a constant pressure valve 12 promotes.
  • the Separating piston adapter 10 separates the operating fluid (in usually diesel fuel) of the M pump 13 to be introduced Additional liquid (usually water). there the water side of a barrel cylinder in the separating piston 11 from a filling pump 14 via a check valve 16 with additional liquid fed at low pressure (p ⁇ 2 bar).
  • the M pump 13 At the right time before the actual injection, between the injection cycles, the M pump 13 a desired amount of operating fluid with a higher Pressure than that with which the check valve 3.4 of the two-substance nozzle 3 is set on the separating piston 11 issued. This will increase the amount of makeup fluid that on the other side of the separating piston 11 the amount of operating fluid corresponds to the M pump 13, via the Constant pressure valve 12 to the additional liquid line 15 passed.
  • the constant pressure valve 12 is used for pressure relief or for the correct pre-pressure supply of the additional liquid line 15 between the separating piston adapter 11 and the two-substance nozzle 3.
  • the second 2/2-way valve MV2 can be a relatively simple one and cheaper valve than the first 2/2-way valve Be MV1 because the accuracy of the latter for the Function of fuel displacement from pressure chamber 3.5 to Purpose of storing additional liquid is not essential is required and otherwise only a clear yes / no behavior valve MV2 is required.
  • the second embodiment shown in FIG distinguishes fuel injection system according to the invention differs from that shown in Fig. 1 by a modification of the responsible for the pumping of the additional liquid Part of the facility.
  • a membrane 21.1 by means of a Mass wall 21.2 at one end of the common rail pressure accumulator 20 articulated, the mass wall 21.2 due to a slightly conical outer contour of the membrane 21.1 pressure-tight a high-pressure chamber 20.1 of the common rail pressure accumulator 20 clamps.
  • an aperture hole 21.3 provided by the fuel from the high pressure chamber 20.1 in a space 21.4, the membrane 21.1 and the Mass wall 21.2 is enclosed, depending on the pressure drop direction can penetrate or emerge from this.
  • a lever mechanism 22 is on the one hand with the space 21.4 opposite side of the membrane 21.1, on the other hand with a Pump piston 23.1 connected.
  • the lever mechanism 22 on a longitudinally movable slide 24.1 rotatably mounted. From pressure fluctuations in the high pressure room 20.1 due to jerky withdrawal of the injection quantity Fuel results in a movement of the membrane 21.1. By the diaphragm path becomes a reciprocating movement of the lever mechanism 22 causes, which in turn a corresponding Stroke of the pump piston 23.1 results.
  • the pump piston 23.1 is preloaded accordingly via a compression spring 23.2, so that there are no "lots" in any movement phase can arise.
  • the pump piston 23.1 sucks through a Line 29 supported with a check valve 27 by a pre-feed pump 20 a corresponding amount of additional liquid from a tank 25 Amount of water via the additional liquid line 15 and that Check valve 3.4 pushed into the two-fluid nozzle 3, if the second 2/2-way valve MV2 for directing the amount of water by a command of the not shown in the drawing Engine management was opened.
  • the slide 24.1 by an electric motor 24.3 which is a screwed into the slider 24.1 24.2 carries, according to a turning command from the engine management moved up or down.
  • the pump device can either from one injection to the other in the same injector Measure 3 different amounts of additional liquid or further connected to the additional liquid line 15 Injectors (indicated by a number in the drawing parallel arrows) can be customized with that for them respectively correct amount of additional liquid.
  • the current stroke of the pump piston can also be used 23.1 measured and with other important, currently available Data and the current change request compared and be offset to make an adjustment as quickly as possible new conditions (e.g. changing the accelerator pedal position by the driver of a motor-driven vehicle) to be able to.
  • Nervous reactions of membrane 21.1 caused by pressure peaks or other smaller pressure fluctuations with higher frequencies caused in the high pressure room 20.1 and one exact metering of the required additional liquid is detrimental are dimensioned appropriately and matching the mass wall 21.2 with the orifice bore 21.3 and the spring behavior of the membrane 21.1 damped.
  • a behavior that is hydraulic Low pass equals with the mass wall 21.2 in electrical analogue of an inductance, the aperture bore 21.3 an ohmic resistance and the membrane 21.1 one Capacitor corresponds.
  • a hydraulic low-pass filter also has an advantageous effect on the pressure conditions in the high pressure chamber 21.1 because this also dampens pressure fluctuations takes place.
  • FIG. 3 differs 2 essentially by the fact that for water supply the two-fluid nozzle 3 now another common rail pressure accumulator 32 to accommodate pressurized Additional liquid is provided via a further 2/2-way valve MV3 with the additional liquid line leading to the two-substance nozzle 3 15 and via a check valve 31 with the delivery side of the diaphragm driven pump piston 23.1 is connected.
  • the other can 2/2-way valve MV3 identical in construction to the first 2/2-way valve MV1 can be designed, whereby the 2/2-way valve MV3, however suitable for operation with the additional liquid have to be.
  • the further 2/2-way valve MV3 can supply entire group of two-substance nozzles 3, as long as none temporal overlaps of the metering processes for the different Injectors. In which injector each measured amount of additional liquid should go off, again determines a simply constructed second 2/2-way valve MV2, however, for every two-component nozzle in the group must be present.
  • a further pressure holding valve 43 is provided in the discharge line 8, which connects the second 2/2-way valve MV2 to the low-pressure fuel side.
  • Leakage line 35 attached to the reservoir 25 opens.
  • the delivery of the additional liquid from the additional container 25 is done via a check valve 34.
  • the fluid delivery can also be one in the drawing Pump not shown may be provided.
  • FIG. 4 shows a further development of the embodiment 3, in which on a lever mechanism 22 and an adjustment facial expression was dispensed with.
  • the promotion and metering is here directly from the to the high pressure room 40.1 of the common rail pressure accumulator 40 for fuel Membrane 41.1, which with appropriate Overpressure in the high pressure chamber 40.1 with a pressure surge Provides additional liquid charged space 43, which on the Check valve 31 in the other common rail pressure accumulator 42 is passed on.
  • the other functions are complete analogous to those of the exemplary embodiment according to FIG. 3.

Landscapes

  • 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)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzanlage für eine Brennkraftmaschine nach der Gattung des Patentanspruchs 1.The invention is based on a fuel injection system for an internal combustion engine according to the preamble of the claim 1.

Derartige Kraftstoffeinspritzanlagen sind beispielsweise aus der DE 4337 048 C2 bekannt. Dabei ist einerseits eine Zweistoffdüse vorgesehen, die der geschichteten Einspritzung von Kraftstoff und einer Zusatzflüssigkeit, beispielsweise Dieselkraftstoff und Wasser dient, um den Schadstoffausstoß der Brennkraftmaschine zu vermindern und gegebenenfalls den Wirkungsgrad zu erhöhen. Andererseits ist bei der bekannten Einspritzanlage auch die sogenannte Common-Rail-Technik verwirklicht, bei der sämtliche die Brennkraftmaschine bedienenden Einspritzdüsen mit unter Hochdruck stehendem Kraftstoff aus einem Common-Rail-Druckspeicher beschickt werden.Such fuel injection systems are, for example, from known from DE 4337 048 C2. On the one hand there is a two-component nozzle provided the stratified injection of Fuel and an additional liquid, such as diesel fuel and water serves to reduce pollutant emissions To reduce internal combustion engine and, if necessary, the efficiency to increase. On the other hand, in the known Injection system also realizes the so-called common rail technology, in which all operating the internal combustion engine High pressure fuel injectors be fed from a common rail pressure accumulator.

Nachteilig bei der bekannten Kraftstoffeinspritzanlage ist, daß für jeden einzelnen Injektor zur Mengendosierung der Zusatzflüssigkeit ein aufwendiges und relativ teures 3/2-Wegeventil sowie für die Steuerung der Dieseleinspritzmenge ein weiteres 3/2-Wegeventil benötigt wird. Zum Vorlagern der Zusatzflüssigkeit wird dabei mit dem ersten 3/2-Wegeventil die Kraftstoffzufuhr vom Common-Rail-Druckspeicher zur Einspritzdüse unterbrochen und gleichzeitig ein die Einspritzdüse umgebender Druckraum, in dem unter Hochdruck stehender Kraftstoff gelagert ist, durch eine entsprechende Stellung des ersten 3/2-Wegeventils zur Kraftstoff-Niederdruckseite hin abgelassen. Durch den entstehenden Druckabfall im Druckraum wird über eine entsprechende Leitung Zusatzflüssigkeit in den Druckraum gefördert, die das entsprechende Kraftstoffvolumen verdrängt. Anschließend wird das erste 3/2-Wegeventil wieder in eine Stellung gebracht, die eine Verbindung zwischen dem Common-Rail-Druckspeicher und dem Druckraum im Einspritzventil herstellt. Zur mengengenauen Dosierung der einzuspritzenden Kraftstoffmenge, die der vorgelagerten Zusatzflüssigkeit bei dem durch die nächste Ventilöffnung hervorgerufenen Einspritzstoß folgen soll, ist das weitere 3/2-Wege-Magnetventil vorgesehen, welches die Rückseite der Düsennadel, die von einer Feder in Schließstellung gehalten wird, wahlweise entweder mit dem Common-Rail-Druckspeicher oder mit der Kraftstoff-Niederdruckseite verbindet und dadurch zeitlich den Hub der Ventilnadel, das Öffnen und Schließen des Ventils und damit die gewünschte Einspritzmenge steuert.A disadvantage of the known fuel injection system is that for each individual injector for metering the additional liquid a complex and relatively expensive 3/2-way valve as well as for the control of the diesel injection quantity another 3/2-way valve is required. For storing the additional liquid is the first 3/2-way valve Fuel supply from the common rail pressure accumulator to the injection nozzle interrupted and at the same time the injector surrounding pressure chamber, in the high pressure Fuel is stored through an appropriate position of the first 3/2-way valve to the fuel low pressure side drained out. Due to the pressure drop in the pressure chamber is additional liquid via a corresponding line conveyed into the pressure chamber, which is the corresponding fuel volume repressed. Then the first 3/2-way valve brought back into a position that connects between the common rail pressure accumulator and the pressure chamber in the injection valve. For precise dosage the amount of fuel to be injected, that of the upstream Additional liquid in the through the next valve opening is to follow the injection burst caused Another 3/2-way solenoid valve is provided, which is the rear the nozzle needle by a spring in the closed position is held, either with the common rail pressure accumulator or connects to the fuel low pressure side and thereby the stroke of the valve needle, the opening and Closing the valve and thus the desired injection quantity controls.

Prinzipiell benötigt die bekannte Kraftstoffeinspritzanlage für jeden einzelnen Injektor die beiden genau arbeitenden und damit aufwendigen 3/2-Steuermagnetventile um sowohl die gewünschte Kraftstoffmenge als auch die erforderliche Menge an Zusatzflüssigkeit exakt dosieren zu können. In principle, the known fuel injection system is required the two precisely working for each individual injector and thus complex 3/2-way solenoid valves to both the desired amount of fuel as well as the required amount to be able to precisely dose additional liquid.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzanlage weist zur baulichen Vereinfachung und damit zur preisgünstigeren Herstellbarkeit die kennzeichnenden Merkmale des Patentanspruchs 1 auf. Dadurch können die beiden aufwendigen und teuren 3/2-Magnetsteuerventile durch einfachere und preiswertere 2/2-Wegeventile ersetzt werden, wobei gleichzeitig die Möglichkeit eröffnet wird, die Mengendosierung für die Zusatzflüssigkeit auf ein einziges, genau arbeitendes Dosierventil zu verlagern, das eine ganze Gruppe von Injektoren bedienen kann. Während das zweite 2/2-Wegeventil lediglich die Öffnungs- und Schließzeit für die Zusatzflüssigkeitsvorlagerung bestimmt, wird die Mengendosierung für die einzuspritzende Kraftstoffmenge durch eine entsprechende Zeitsteuerung des ersten 2/2-Wegeventils in der Einspritzleitung zwischen dem Common-Rail-Druckspeicher und dem Druckraum bewirkt.The fuel injection system according to the invention has constructional simplification and thus for a cheaper manufacture the characteristic features of the claim 1 on. This allows the two elaborate and expensive 3/2 solenoid control valves due to simpler and cheaper 2/2-way valves to be replaced, at the same time the possibility is opened for the quantity dosing Additional liquid on a single, precisely working metering valve to shift that a whole group of injectors can operate. While the second 2/2-way valve only the opening and closing times for the additional liquid pre-storage is determined, the quantity dosage for the amount of fuel to be injected by a corresponding Time control of the first 2/2-way valve in the injection line between the common rail pressure accumulator and the Pressure chamber.

Um gleichbleibende Druckverhältnisse im Leitungssystem zu gewährleisten und insbesondere auch bei hohen Temperaturen ein Ausgasen der Zusatzflüssigkeit, in der Regel Wasser, bei Überschreiten des Siedepunktes zu verhindern, empfiehlt sich der Einsatz eines Rückschlagventils zwischen dem zweiten 2/2-Wegeventil und der Kraftstoff-Niederdruckseite.To ensure constant pressure conditions in the pipe system ensure and especially at high temperatures outgassing the additional liquid, usually water It is advisable to prevent the boiling point from being exceeded the use of a check valve between the second 2/2-way valve and the fuel low pressure side.

Vorteilhaft ist es auch, wenn die Düsennadel am stumpfen Ende ihres Injektorstößels in radialer Verlängerung einen kleinen Kolben trägt, der in einen mit Hochdruck vom Common-Rail-Druckspeicher beaufschlagten Raum ragt, welcher seinerseits druckdicht gegen den die Düsennadel umgebenden Raum abgedichtet ist. Durch die Beaufschlagung der gleichbleibenden Kolbenfläche mit dem Common-Rail-Druck werden die Steuerbewegungen der Düsennadel beim Einspritzvorgang unabhängig von den Absolutdruckverhältnissen im Common-Rail-Druckspeicher, weil zur Bewegung des Injektorstößels stets der gleiche Widerstand, nämlich die Federkraft der Ventilfeder überwunden werden muß, so daß die Bewegungskräfte konstant bleiben. Dadurch ergeben sich regeltechnisch günstige konstante Schaltzeiten, die durch die jeweilige Bewegungszeit des Injektorstößels bestimmt werden.It is also advantageous if the nozzle needle at the blunt end of their injector plunger in radial extension small piston that carries high pressure from the common rail pressure accumulator exposed space, which in turn protrudes pressure-tight against the space surrounding the nozzle needle is sealed. By applying the constant Piston area with the common rail pressure are the control movements the nozzle needle during the injection process independently the absolute pressure conditions in the common rail pressure accumulator, because the same applies to the movement of the injector plunger Resistance, namely overcome the spring force of the valve spring must be so that the movement forces remain constant. This results in constant, which are favorable from a control standpoint Switching times by the respective movement time of the injector tappet be determined.

Bei der erfindungsgemäßen Kraftstoffeinspritzanlage wird zur Förderung der Zusatzflüssigkeit eine Membran verwendet, deren eine Seite mit dem im Common-Rail-Druckspeicher herrschenden Hochdruck beaufschlagt ist, und deren andere Seite aufgrund der Druckimpulse im Common-Rail-Druckspeicher entweder direkt oder über einen Hebelmechanismus eine Förderung der Zusatzflüssigkeit in die zur Zweistoffdüse führende Zusatzflüssigkeitsleitung bewirkt.In the case of the invention Fuel injection system is used to promote the Additional liquid uses a membrane, one of which Side with the prevailing in the common rail pressure accumulator High pressure is applied, and the other side due the pressure pulses in the common rail pressure accumulator either directly or via a lever mechanism to promote the additional liquid into the additional liquid line leading to the two-substance nozzle causes.

Die indirekte Förderung von Zusatzflüssigkeit kann beispielsweise über einen Pumpenkolben erfolgen, der durch einen Hebelmechanismus mit der Membran verbunden ist und bei Druckänderungen im Common-Rail-Druckspeicher, die zu einer Membranbewegung führen, eine entsprechende Menge an Zusatzflüssigkeit fördert. Zum Ausgleich für eine Membranwegtrift beispielsweise bei unterschiedlichen Common-Rail-Basisdrükken sowie zur genauen Regelung der Mengendosierung der geförderten Zusatzflüssigkeit kann das Hebelverhältnis und damit das Hubvolumen des Pumpenkolbens durch einen Verstellmechanismus beeinflußt werden, der beispielsweise mittels eines Elektromotors angetrieben werden kann. Aufgrund der Proportionalität der entnommenen Kraftstoffmenge zur geförderten Zusatzflüssigkeitsmenge dürften aber kaum Verstellungen erforderlich sein, so daß die erfindungsgemäße Anordnung eine hohe Betriebsstabilität aufweist.The indirect delivery of additional liquid can, for example via a pump piston, which is carried out by a Lever mechanism is connected to the membrane and at Pressure changes in the common rail pressure accumulator that lead to a Membrane movement, a corresponding amount of additional liquid promotes. To compensate for a membrane drift for example with different common rail base pressures as well as for precise regulation of the quantity metered of the funded Additional liquid can affect the leverage ratio and thus the stroke volume of the pump piston through an adjustment mechanism be influenced, for example by means of a Electric motor can be driven. Because of the proportionality the amount of fuel withdrawn to the amount delivered Additional liquid quantity is unlikely to make any adjustments be necessary so that the arrangement according to the invention a has high operational stability.

Zur Abdämpfung kleinerer Druckschwankungen mit höheren Frequenzen kann bei einer Weiterbildung das Fördersystem für die Zusatzflüssigkeit als eine Art "hydraulischer Tiefpaß" ausgebildet sein, bei dem eine massive Trennwand (auch Massenwand) die Membran an einem Ende des Common-Rail-Druckspeichers einspannt, wobei in der Massenwand eine Blendenbohrung vorgesehen ist, die einen gedämpften Druckausgleich zwischen dem Common-Rail-Druckspeicher und dem Raum zwischen der Massenwand und der Membran zuläßt. Im elektrischen Analogon eines Tiefpaßfilters entspräche dabei die Massenwand der Induktivität, die Blendenbohrung dem ohmschen Widerstand und die Membran einem Kondensator. Im Ergebnis können sich dadurch nur noch größere niederfrequente Druckschwankungen aufgrund von großen Volumenbewegungen des Kraftstoffes auf die Membranbewegung und damit auf die Förderung von Zusatzflüssigkeit auswirken.To dampen smaller pressure fluctuations with higher frequencies can the funding system for further training the additional liquid as a kind of "hydraulic low pass" be designed in which a massive partition wall (also mass wall) the membrane at one end of the common rail pressure accumulator clamped, with an aperture hole in the bulk wall is provided, the damped pressure equalization between the common rail accumulator and the space between the mass wall and the membrane allows. In the electrical analogue a low pass filter would correspond to the mass wall the inductance, the orifice hole the ohmic resistance and the membrane a capacitor. As a result, you can therefore only larger low-frequency pressure fluctuations due to large volume movements of the fuel the membrane movement and thus the delivery of additional liquid impact.

Ganz besonders bevorzugt ist auch eine Ausführungsform der erfindungsgemäßen Kraftstoffeinspritzanlage, bei der ein weiterer Common-Rail-Druckspeicher zur Aufnahme von unter Druck stehender Zusatzflüssigkeit vorgesehen ist, welcher über ein 2/2-Wegeventil mit der zur Zweistoffdüse führenden Zusatzflüssigkeitsleitung verbunden ist und ähnliche Vorteile aufweist wie der an sich bekannte Common-Rail-Druckspeicher für Kraftstoff. Insbesondere läßt sich bei Verwendung eines solchen weiteren Common-Rail-Druckspeichers der oben beschriebene Fördermechanismus für die Zusatzflüssigkeit erheblich vereinfachen, indem die Membran über ein Rückschlagventil direkt und ohne Zwischenschaltung eines einen Pumpenkolben antreibenden Hebelmechanismus durch Weitergabe entsprechender Druckstöße an den weiteren Common-Rail-Druckspeicher die Förderung von Zusatzflüssigkeit bewirken.An embodiment of the is also very particularly preferred Fuel injection system according to the invention, in which a additional common rail pressure accumulator to accommodate under Pressurized additional liquid is provided, which via a 2/2-way valve with the one leading to the two-component nozzle Auxiliary liquid line is connected and similar advantages has like the known common rail pressure accumulator for fuel. In particular, when used of such a further common rail pressure accumulator of the above described delivery mechanism for the additional liquid considerably simplify by placing the diaphragm over a check valve directly and without interposing a pump piston driving lever mechanism by passing on corresponding Pressure surges on the other common rail pressure accumulators cause the pumping of additional liquid.

Ein besonderer Vorteil der Verwendung eines weiteren Common-Rail-Druckspeichers für Zusatzflüssigkeit besteht darin, daß das 2/2-Wegeventil in der Zusatzflüssigkeitsleitung eine ganze Gruppe von Injektoren versorgen kann, wobei lediglich sichergestellt werden muß, daß keine zeitlichen Überschneidungen der Zumeßvorgänge für die einzelnen Injektoren auftreten.A particular advantage of using another common rail pressure accumulator for additional liquid is that the 2/2-way valve in the additional liquid line can supply whole group of injectors, whereby only It must be ensured that there is no overlap in time the metering processes for the individual injectors occur.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstands der Erfindung sind der Beschreibung, der Zeichnung und den Ansprüchen zu entnehmen.Further advantages and advantageous configurations of the object the invention are the description, the drawing and the claims.

Zeichnungdrawing

Vier Ausführungsbeispiele der erfindungsgemäßen Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen sind in der Zeichnung dargestellt und werden in der nachfolgenden Beschreibung erläutert.Four embodiments of the fuel injection device according to the invention for internal combustion engines are in the Drawing shown and are in the description below explained.

Es zeigen:

  • Fig. 1 eine schematische Beschaltung eines ersten Ausführungsbeispiels der erfindungsgemäßen Kraftstoffeinspritzanlage mit zwei 2/2-Wegeventilen zur Mengensteuerung der Förderung bzw. Einspritzung von Kraftstoff und Zusatzflüssigkeit durch eine schematisch im Längsschnitt dargestellte Zweistoffdüse, wobei die Zusatzflüssigkeitsleitung zur Zweistoffdüse von einem Trennkolbensystem mit Gleichdruckventilanordnung beschickt wird;
  • Fig. 2 ein zweites Ausführungsbeispiel mit membranbetriebener Zusatzflüssigkeitspumpe, wobei die Membran vom Druck im Common-Rail-Druckraum angesteuert wird und über einen Hebelmechanismus einen Förderpumpenkolben treibt;
  • Fig. 3 ein drittes Ausführungsbeispiel analog Fig. 2, allerdings mit einem weiteren Common-Rail-Druckspeicher für Zusatzflüssigkeit; und
  • Fig. 4 ein viertes Ausführungsbeispiel analog Fig. 3, das ebenfalls einen weiteren Common-Rail-Druckbehälter für die Zusatzflüssigkeit aufweist, wobei aber die Membran ohne Hebelmechanismus und ohne Pumpenkolben lediglich durch Druckstöße die Förderung der Zusatzflüssigkeit direkt bewirkt.
    • Show it:
  • Fig. 1 is a schematic circuit of a first embodiment of the fuel injection system according to the invention with two 2/2-way valves for quantity control of the delivery or injection of fuel and additional liquid through a two-component nozzle shown schematically in longitudinal section, wherein the additional liquid line to the two-component nozzle is fed by a separating piston system with a constant pressure valve arrangement ;
  • 2 shows a second exemplary embodiment with a diaphragm-operated auxiliary liquid pump, the diaphragm being controlled by the pressure in the common rail pressure chamber and driving a feed pump piston via a lever mechanism;
  • 3 shows a third exemplary embodiment analogous to FIG. 2, but with a further common rail pressure accumulator for additional liquid; and
  • Fig. 4 shows a fourth embodiment analogous to Fig. 3, which also has a further common rail pressure container for the additional liquid, but the membrane without lever mechanism and without pump piston only causes the delivery of the additional liquid directly by pressure surges.

    • Beschreibung der AusführungsbeispieleDescription of the embodiments

    Bei dem in Fig. 1 dargestellten ersten Ausführungsbeispiel der erfindungsgemäßen Kraftstoffeinspritzanlage für eine Brennkraftmaschine zur bifluiden Einspritzung von Kraftstoff (in der Regel Dieselkraftstoff) und einer Zusatzflüssigkeit (in der Regel Wasser) versorgt eine Hochdruckpumpe 1 einen Common-Rail-Druckspeicher 2 mit Kraftstoff auf einem Druckniveau von etwa 1800 bar. Zwischen dem Common-Rail-Druckspeicher 2 und einem von diesem über eine Einspritzleitung 6 mit Kraftstoff zu versorgenden Druckraum 3.5, der die Düsennadel 3.1 einer Zweistoffdüse 3 umgibt, muß nun ein mengendosierendes Bauelement angeordnet werden, da ja die früher übliche klassische Einspritzpumpe durch die Kombination aus Common-Rail-Druckspeicher 2 und der einfacheren Hochdruckpumpe 1 ersetzt wurde und der Raildruck auf einem gewissen Niveau ständig vorhanden ist. Diese Aufgabe übernimmt bei der erfindungsgemäßen Anordnung ein erstes 2/2-Wegeventil MV1. Dieses sollte als schnelles Magnetventil mit guter Reproduzierbarkeit und mehr oder weniger fließendem Übergang zwischen den beiden Extremstellungen ausgelegt sein, da eventuell ein zeitlich gestaltbarer Einspritzmengenverlauf benötigt wird. Die genaue Mengendosierung wird über den bekannten (gemessenen oder gesteuerten) Druckabfall zwischen dem Commom-Rail-Druckspeicher 2 und dem von der Zweistoffdüse 3 zu versorgenden Verbrennungsraum der Brennkraftmaschine durch ein genaues Zeitfenster, dessen Größe von anderen Einflußfaktoren abhängt, über eine elektrische Ansteuerung, die in der Zeichnung nicht dargestellt ist, ermöglicht.In the first embodiment shown in FIG. 1 the fuel injection system according to the invention for a Internal combustion engine for bifluid fuel injection (usually diesel fuel) and an additional liquid (usually water) a high pressure pump 1 supplies one Common rail pressure accumulator 2 with fuel at a pressure level of around 1800 bar. Between the common rail pressure accumulator 2 and one of these via an injection line 6 pressure chamber 3.5 to be supplied with fuel, which is the nozzle needle 3.1 surrounds a two-substance nozzle 3, must now be a metering Component can be arranged, since the earlier usual classic injection pump through the combination of Common rail pressure accumulator 2 and the simpler high pressure pump 1 was replaced and the rail pressure on a certain Level is constantly present. This task takes over at the arrangement of the invention a first 2/2-way valve MV1. This should be a fast solenoid valve with good reproducibility and more or less smooth transition be designed between the two extreme positions, because possibly a temporally configurable injection quantity curve is needed. The exact amount is metered over the known (measured or controlled) pressure drop between the commom rail pressure accumulator 2 and that of the two-substance nozzle 3 combustion chamber of the internal combustion engine to be supplied through an exact time window, the size of which is influenced by other factors depends on an electrical control that is not shown in the drawing.

    Der Aufbau und die wirkungsweise der verwendeten Zweistoffdüse 3 ist abgesehen von kleineren Details aus dem Stand der Technik bekannt. Beim erfindungsgemäßen System ist jedoch zusätzlich an dem der Düsennadelspitze abgewandten stumpfen axialen Ende der Düsennadel (Injektorstößel) 3.1 ein kleiner Kolben 3.3 vorgesehen, der mit seinem der Düsennadel 3.1 abgewandten Ende in einen Raum 3.6 ragt, welcher über eine Leitung 4 direkt mit dem Common-Rail-Druckspeicher 2 verbunden ist und mit dem dort herrschenden Hochdruck beaufschlagt wird. Dies hat zur Folge, daß zur Bewegung des Injektorstößels 3.1 stets die im wesentlichen gleiche Widerstandskraft überwunden werden muß, da nun bedingt durch die konstanten Kolbenflächenverhältnisse und das Ausschalten der Einflüsse des Absolutdrucks im Common-Rail-Druckspeicher 2 nur ein konstanter Federdruck von einem Druckimpuls aus dem (veränderlichen) Raildruck überwunden werden muß. Damit stellen sich regeltechnisch willkommenere, annähernd konstante Schaltzeiten (Bewegungszeit des Injektorstößels) ein. Zur Belüftung des Raumes 3.2, der das stumpfe axiale Ende der Düsennadel 3.1 aufnimmt, und der gegen den Raum 3.6 hochdruckmäßig abgedichtet ist, ist eine zur Kraftstoff-Niederdruckseite hin führende Belüftungsleitung 5 vorgesehen.The structure and the mode of operation of the two-component nozzle used 3 is, apart from minor details, from the prior art Technology known. However, in the system according to the invention additionally blunt on the nozzle needle tip axial end of the nozzle needle (injector plunger) 3.1 a small Piston 3.3 is provided, the one facing away from the nozzle needle 3.1 End protrudes into a room 3.6, which over a Line 4 connected directly to the common rail pressure accumulator 2 and the high pressure prevailing there becomes. As a result, the injector plunger moves 3.1 always the same resistance must be overcome, since now due to the constant Piston area ratios and switching off the influences of the absolute pressure in the common rail pressure accumulator 2 only one constant spring pressure from a pressure pulse from the (variable) Rail pressure must be overcome. With that pose more technically welcome, almost constant Switching times (movement time of the injector tappet) on. to Ventilation of the room 3.2, which is the blunt axial end of the Nozzle needle 3.1 takes up, and the high pressure against the room 3.6 is sealed, is to the fuel low pressure side leading ventilation line 5 provided.

    Für die Einbringung von Zusatzflüssigkeit muß nun, wie im Prinzip aus dem Stand der Technik an sich bekannt, ein Weg für den durch die Zusatzflüssigkeit zu verdrängenden Kraftstoff aus der Zweistoffdüse 3 freigegeben werden. Dies geschieht durch geeignetes Beschalten eines zweiten 2/2-Wegeventils MV2, dessen Eingang über eine Zufuhrleitung 7 mit der Einspritzleitung 6 und dessen Ausgang über eine Abfuhrleitung 8 mit der Kraftstoff-Niederdruckseite verbunden ist. Wenn Zusatzflüssigkeit zudosiert werden soll, ist das erste 2/2-Wegeventil MV1 geschossen und das zweite 2/2-Wegeventil wird auf Durchgang geschaltet. Dadurch entweicht unter Hochdruck stehender Kraftstoff aus dem Druckraum 3.5 über die Einspritzleitung 6, die Zufuhrleitung 7, die Abfuhrleitung 8 und ein Rückschlagventil 9 zur Kraftstoff-Niederdruckseite, in der Regel den Kraftstofftank. Dadurch kann Zusatzflüssigkeit von einer zur Zweistoffdüse 3 führenden Zusatzflüssigkeitsleitung 15 über ein Rückschlagventil 3.4 (mit p0 = 15 bar) in den Druckraum 3.5 nachströmen. Die fluidführenden Bohrungen der Zweistoffdüse 3 und die Leitungslängen müssen allerdings so dimensioniert werden und die Leitungen so angebracht sein, daß keine Zusatzflüssigkeit in den Kraftstofftank gelangen kann.For the introduction of additional liquid, a path for the fuel to be displaced by the additional liquid from the two-substance nozzle 3 must now be cleared, as is known per se in principle from the prior art. This is done by suitably wiring a second 2/2-way valve MV2, the input of which is connected to the injection line 6 via a supply line 7 and the output of which is connected to the low-pressure fuel side via a discharge line 8. If additional liquid is to be metered in, the first 2/2-way valve MV1 is fired and the second 2/2-way valve is switched to passage. As a result, fuel under high pressure escapes from the pressure chamber 3.5 via the injection line 6, the feed line 7, the discharge line 8 and a check valve 9 to the low-pressure fuel side, as a rule the fuel tank. As a result, additional liquid can flow into the pressure chamber 3.5 from an additional liquid line 15 leading to the two-substance nozzle 3 via a check valve 3.4 (with p 0 = 15 bar). The fluid-carrying bores of the two-fluid nozzle 3 and the line lengths must, however, be dimensioned and the lines must be installed in such a way that no additional liquid can get into the fuel tank.

    Vor dem eigentlichen Einspritzvorgang der Zusatzflüssigkeit muß die richtige Menge derselben zugemessen und bei noch niedrigem Systemdruck in die Zweistoffdüse 3 gefördert werden. Dies wird mittels einer sogenannten M-Pumpe 13 bewirkt, die eine Betriebsflüssigkeit auf einem Vordruckniveau von ungefähr 2,5 bar in einen Trennkolben-Adapter 10 mit einem Trennkolben 11 und einem Gleichdruckventil 12 fördert. Der Trennkolben-Adapter 10 separiert die Betriebsflüssigkeit (in der Regel Dieselkraftstoff) der M-Pumpe 13 von der einzubringenden Zusatzflüssigkeit (in der Regel wasser). Dabei wird die Wasserseite eines Laufzylinders im Trennkolben 11 von einer Füllpumpe 14 über ein Rückschlagventil 16 mit Zusatzflüssigkeit auf niedrigem Druck (p < 2 bar) beschickt. Zum richtigen Zeitpunkt vor der eigentlichen Einspritzung, also zwischen den Einspritztakten, wird von der M-Pumpe 13 eine gewünschte Menge an Betriebsflüssigkeit mit einem höheren Druck als demjenigen, mit dem das Rückschlagventil 3.4 der Zweistoffdüse 3 eingestellt ist, an den Trennkolben 11 abgegeben. Dadurch wird die Menge an Zusatzflüssigkeit, die auf der anderen Seite des Trennkolbens 11 der Menge an Betriebsflüssigkeit der M-Pumpe 13 entspricht, über das Gleichdruckventil 12 an die Zusatzflüssigkeitsleitung 15 weitergegeben. Das Gleichdruckventil 12 dient zur Druckentspannung bzw. zur richtigen Vordruckversorgung der Zusatzflüssigkeitsleitung 15 zwischen dem Trennkolben-Adapter 11 und der Zweistoffdüse 3.Before the additional liquid is actually injected the correct amount of it must be metered in and at still low system pressure in the two-fluid nozzle 3 are promoted. This is effected by means of a so-called M pump 13, which has a working fluid at a pre-pressure level of about 2.5 bar in a separating piston adapter 10 with a Separating piston 11 and a constant pressure valve 12 promotes. The Separating piston adapter 10 separates the operating fluid (in usually diesel fuel) of the M pump 13 to be introduced Additional liquid (usually water). there the water side of a barrel cylinder in the separating piston 11 from a filling pump 14 via a check valve 16 with additional liquid fed at low pressure (p <2 bar). At the right time before the actual injection, between the injection cycles, the M pump 13 a desired amount of operating fluid with a higher Pressure than that with which the check valve 3.4 of the two-substance nozzle 3 is set on the separating piston 11 issued. This will increase the amount of makeup fluid that on the other side of the separating piston 11 the amount of operating fluid corresponds to the M pump 13, via the Constant pressure valve 12 to the additional liquid line 15 passed. The constant pressure valve 12 is used for pressure relief or for the correct pre-pressure supply of the additional liquid line 15 between the separating piston adapter 11 and the two-substance nozzle 3.

    Das zweite 2/2-Wegeventil MV2 kann übrigens ein relativ einfaches und kostengünstigeres Ventil als das erste 2/2-Wegeventil MV1 sein, da die Exaktheit des letzteren für die Funktion der Kraftstoffverdrängung aus dem Druckraum 3.5 zum Zwecke der Vorlagerung von Zusatzflüssigkeit nicht unbedingt benötigt wird und im übrigen nur ein eindeutiges ja/nein-Verhalten des Ventils MV2 erforderlich ist.Incidentally, the second 2/2-way valve MV2 can be a relatively simple one and cheaper valve than the first 2/2-way valve Be MV1 because the accuracy of the latter for the Function of fuel displacement from pressure chamber 3.5 to Purpose of storing additional liquid is not essential is required and otherwise only a clear yes / no behavior valve MV2 is required.

    Das in Fig. 2 dargestellte zweite Ausführungsbeispiel der erfindungsgemäßen Kraftstoffeinspritzanlage unterscheidet sich von der in Fig. 1 gezeigten durch eine Modifikation des für die Förderung der Zusatzflüssigkeit verantwortlichen Teils der Anlage. Um die teure M-Pumpe 13 aus Fig. 1 durch preisgünstigere Aggregate zu ersetzen, ist nunmehr eine Pumpe für die Zusatzflüssigkeit mit dem Common-Rail-Druckspeicher 20 gekoppelt. Dazu ist eine Membran 21.1 mittels einer Massenwand 21.2 an einem Ende des Common-Rail-Druckspeichers 20 angelenkt, wobei die Massenwand 21.2 aufgrund einer leicht kegeligen Außenkontur die Membran 21.1 druckdicht in einen Hochdruckraum 20.1 des Common-Rail-Druckspeichers 20 einspannt. In der Massenwand 21.2 ist eine Blendenbohrung 21.3 vorgesehen, durch die Kraftstoff aus dem Hochdruckraum 20.1 in einen Raum 21.4, der von der Membran 21.1 und der Massenwand 21.2 umschlossen wird, je nach Druckgefällerichtung eindringen oder aus diesem austreten kann.The second embodiment shown in FIG distinguishes fuel injection system according to the invention differs from that shown in Fig. 1 by a modification of the responsible for the pumping of the additional liquid Part of the facility. Around the expensive M-pump 13 from FIG. 1 Replacing cheaper units is now a pump for the additional liquid with the common rail pressure accumulator 20 coupled. For this purpose, a membrane 21.1 by means of a Mass wall 21.2 at one end of the common rail pressure accumulator 20 articulated, the mass wall 21.2 due to a slightly conical outer contour of the membrane 21.1 pressure-tight a high-pressure chamber 20.1 of the common rail pressure accumulator 20 clamps. In the bulk wall 21.2 is an aperture hole 21.3 provided by the fuel from the high pressure chamber 20.1 in a space 21.4, the membrane 21.1 and the Mass wall 21.2 is enclosed, depending on the pressure drop direction can penetrate or emerge from this.

    Ein Hebelmechanismus 22 ist einerseits mit der dem Raum 21.4 abgewandten Seite der Membran 21.1, andererseits mit einem Pumpenkolben 23.1 verbunden. Außerdem ist der Hebelmechanismus 22 auf einem längsbeweglich geführten Schieber 24.1 drehbar gelagert. Aus Druckschwankungen im Hochdruckraum 20.1 aufgrund von ruckartiger Entnahme der Einspritzmenge an Kraftstoff ergibt sich eine Bewegung der Membran 21.1. Durch den Membranweg wird eine Hin- und Herbewegung des Hebelmechanismus 22 verursacht, welche wiederum einen entsprechenden Hub des Pumpenkolbens 23.1 zur Folge hat. Der Pumpenkolben 23.1 wird über eine Druckfeder 23.2 entsprechend vorgespannt, so daß in keiner Bewegungsphase irgendwelche "Lose" entstehen können.A lever mechanism 22 is on the one hand with the space 21.4 opposite side of the membrane 21.1, on the other hand with a Pump piston 23.1 connected. In addition, the lever mechanism 22 on a longitudinally movable slide 24.1 rotatably mounted. From pressure fluctuations in the high pressure room 20.1 due to jerky withdrawal of the injection quantity Fuel results in a movement of the membrane 21.1. By the diaphragm path becomes a reciprocating movement of the lever mechanism 22 causes, which in turn a corresponding Stroke of the pump piston 23.1 results. The pump piston 23.1 is preloaded accordingly via a compression spring 23.2, so that there are no "lots" in any movement phase can arise.

    Während der Ansaugphase saugt der Pumpenkolben 23.1 über eine Leitung 29 mit einem Rückschlagventil 27 unterstützt durch eine Vorförderpumpe 20 eine entsprechende Menge an Zusatzflüssigkeit aus einem Tank 25. Beim Ausschieben wird die Wassermenge über die Zusatzflüssigkeitsleitung 15 und das Rückschlagventil 3.4 in die Zweistoffdüse 3 geschoben, falls das zweite 2/2-Wegeventil MV2 zum Dirigieren der Wassermenge durch einen Befehl des in der Zeichnung nicht dargestellten Motor-Managements geöffnet wurde.During the suction phase, the pump piston 23.1 sucks through a Line 29 supported with a check valve 27 by a pre-feed pump 20 a corresponding amount of additional liquid from a tank 25 Amount of water via the additional liquid line 15 and that Check valve 3.4 pushed into the two-fluid nozzle 3, if the second 2/2-way valve MV2 for directing the amount of water by a command of the not shown in the drawing Engine management was opened.

    Zur Vermeidung von Gewaltbrüchen beispielsweise in Folge einer Fehlfunktion des 2/2-Wegeventils MV2 ist ein Überdruckrückschlagventil 28 in einer von der Zusatzflüssigkeitsleitung 15 abzweigenden, direkt in den Vorratsbehälter 25 mündenden Überdruckleitung angeordnet, welches bei Überschreiten eines entsprechenden Schwellendrucks aufmacht und eine Verbindung zwischen der Zusatzflüssigkeitsleitung 15 und dem Vorratsbehälter 25 herstellt.To avoid violent violations, for example as a result of a Malfunction of the 2/2-way valve MV2 is an overpressure check valve 28 in one of the auxiliary liquid line 15 branching, ending directly in the reservoir 25 Pressure line arranged, which when exceeded a corresponding threshold pressure and one Connection between the additional liquid line 15 and the Manufactures reservoir 25.

    Um die gewünschte Menge an Zusatzflüssigkeit richtig dosieren zu können, wird der Schieber 24.1 von einem Elektromotor 24.3, welcher eine im Schieber 24.1 eingeschraubte Spindel 24.2 trägt, entsprechend einem Drehbefehl des Motor-Managements auf- oder abbewegt. Dadurch verstellt sich das Hebelverhältnis der Hebelanordnung 22, so daß unterschiedliche Hubvolumina des Pumpenkolbens 23.1 eingestellt werden können. Auf diese Weise kann die Pumpeinrichtung entweder von einem Einspritzvorgang zum anderen in den gleichen Injektor 3 unterschiedliche Mengen an Zusatzflüssigkeit zumessen oder weitere an der Zusatzflüssigkeitsleitung 15 angeschlossene Injektoren (in der Zeichnung angedeutet durch eine Reihe paralleler Pfeile) können individuell mit der für sie jeweils richtigen Menge an Zusatzflüssigkeit beschickt werden.To dose the desired amount of additional liquid correctly to be able to, the slide 24.1 by an electric motor 24.3, which is a screwed into the slider 24.1 24.2 carries, according to a turning command from the engine management moved up or down. This changes the leverage ratio the lever assembly 22 so that different Stroke volumes of the pump piston 23.1 can be adjusted. In this way, the pump device can either from one injection to the other in the same injector Measure 3 different amounts of additional liquid or further connected to the additional liquid line 15 Injectors (indicated by a number in the drawing parallel arrows) can be customized with that for them respectively correct amount of additional liquid.

    Auf die Bewegungssteuerung des Schiebers 24.1 nimmt auch der Kraftstoffdruck im Hochdruckraum 20.1, der mit einem Drucksteuerventil 20.2 variierbar ist, über eine Membranwegtrift Einfluß. Um einigermaßen genaue Mengenzumessungen der einzuspritzenden Zusatzflüssigkeit vornehmen zu können, sollten entweder die Druckschwankungen im Hochdruckraum 20.1 gemessen und mit der Membrankennung durch das Motor-Management berechnet werden. Von diesem kann dann der entsprechende Drehbefehl an den Elektromotor 24.3 abgegeben werden, wobei auch eine Lageerkennung der Spindel 24.2 hilfreich ist.On the movement control of the slide 24.1 also takes Fuel pressure in the high pressure chamber 20.1, that with a pressure control valve 20.2 is variable, via a membrane path drift Influence. In order to measure the quantities of the injected to some extent To be able to make additional liquid either the pressure fluctuations in the high pressure space 20.1 are measured and with the membrane identification by the engine management be calculated. From this the corresponding one can then Rotation command are given to the electric motor 24.3, wherein a position detection of the spindle 24.2 is also helpful.

    Alternativ kann auch der momentane Hub des Pumpenkolbens 23.1 gemessen und mit anderen wichtigen, momentan vorliegenden Daten sowie dem aktuellen Änderungswunsch verglichen und verrechnet werden, um möglichst schnell eine Anpassung an neue Verhältnisse (beispielsweise Änderung der Gaspedalstellung durch den Fahrer eines motorbetriebenen Fahrzeugs) gewinnen zu können.Alternatively, the current stroke of the pump piston can also be used 23.1 measured and with other important, currently available Data and the current change request compared and be offset to make an adjustment as quickly as possible new conditions (e.g. changing the accelerator pedal position by the driver of a motor-driven vehicle) to be able to.

    Nervöse Reaktionen der Membran 21.1, die durch Druckspitzen oder sonstige kleinere Druckschwankungen mit höheren Frequenzen im Hochdruckraum 20.1 verursacht werden und einer genauen Zumessung der erforderlichen Zusatzflüssigkeit abträglich sind, werden durch eine geeignete Dimensionierung und Abstimmung der Massenwand 21.2 mit der Blendenbohrung 21.3 und dem Federverhalten der Membran 21.1 abgedämpft. Im dynamischen Zusammenwirken der drei genannten Elemente wird sich nämlich ein Verhalten einstellen, welches einem hydraulischen Tiefpaß gleichkommt, wobei die Massenwand 21.2 im elektrischen Analog einer Induktivität, die Blendenbohrung 21.3 einem ohmschen Widerstand und die Membran 21.1 einem Kondensator entspricht. Auf diese Weise können lediglich größere niederfrequente Druckschwankungen, die sich aus entsprechenden größeren Volumenbewegungen im Hochdruckraum 20.1 ergeben, Auswirkungen auf die Membranbewegungen haben. Ein derartiger hydraulischer Tiefpaß wirkt sich außerdem vorteilhaft auf die Druckverhältnisse im Hochdruckraum 21.1 aus, da hiervon auch eine Dämpfung von Druckschwankungen stattfindet.Nervous reactions of membrane 21.1 caused by pressure peaks or other smaller pressure fluctuations with higher frequencies caused in the high pressure room 20.1 and one exact metering of the required additional liquid is detrimental are dimensioned appropriately and matching the mass wall 21.2 with the orifice bore 21.3 and the spring behavior of the membrane 21.1 damped. in the dynamic interaction of the three elements mentioned namely, a behavior that is hydraulic Low pass equals, with the mass wall 21.2 in electrical analogue of an inductance, the aperture bore 21.3 an ohmic resistance and the membrane 21.1 one Capacitor corresponds. This way you can only larger low frequency pressure fluctuations resulting from corresponding larger volume movements in the high pressure room 20.1 result in effects on membrane movements. On Such a hydraulic low-pass filter also has an advantageous effect on the pressure conditions in the high pressure chamber 21.1 because this also dampens pressure fluctuations takes place.

    Die in Fig. 3 gezeigte Ausführungsform unterscheidet sich von der nach Fig. 2 im wesentlichen dadurch, daß zur Wasserversorgung der Zweistoffdüse 3 jetzt ein weiterer Common-Rail-Druckspeicher 32 zur Aufnahme von unter Druck stehender Zusatzflüssigkeit vorgesehen ist, der über ein weiteres 2/2-Wegeventil MV3 mit der zur Zweistoffdüse 3 führenden Zusatzflüssigkeitsleitung 15 sowie über ein Rückschlagventil 31 mit der Förderseite des membrangetriebenen Pumpenkolbens 23.1 verbunden ist.The embodiment shown in Fig. 3 differs 2 essentially by the fact that for water supply the two-fluid nozzle 3 now another common rail pressure accumulator 32 to accommodate pressurized Additional liquid is provided via a further 2/2-way valve MV3 with the additional liquid line leading to the two-substance nozzle 3 15 and via a check valve 31 with the delivery side of the diaphragm driven pump piston 23.1 is connected.

    Eine kompakte und raumsparende Gesamtanordnung ergibt sich, wenn, wie in Fig. 3 gezeigt, der weitere Common-Rail-Druckspeicher 32 für die Zusatzflüssigkeit mit dem Common-Rail-Speicher 30, der den Hochdruckraum 30.1 für den Kraftstoff umfaßt, einstückig verbunden ist.A compact and space-saving overall arrangement results, if, as shown in Fig. 3, the further common rail pressure accumulator 32 for the additional liquid with the common rail accumulator 30, the high pressure space 30.1 for the fuel includes, is integrally connected.

    Die Funktion der Mengenzumessung von Zusatzflüssigkeit wird bei dieser Ausführungsform unter anderem auch dadurch erleichtert, daß sie von der Funktion der Förderung von Zusatzflüssigkeit getrennt ist. Auf diese Weise kann die Mengenzumessung auch genauer erfolgen.The function of quantity metering of additional liquid is facilitated in this embodiment, inter alia, by that they depend on the function of pumping additional liquid is separated. In this way, the metering can also done more accurately.

    Zur Kosteneinsparung (höhere Stückzahlen) kann das weitere 2/2-Wegeventil MV3 baugleich mit dem ersten 2/2-Wegeventil MV1 gestaltet werden, wobei das 2/2-Wegeventil MV3 allerdings tauglich für den Betrieb mit der Zusatzflüssigkeit sein muß. Außerdem kann das weitere 2/2-Wegeventil MV3 eine ganze Gruppe von Zweistoffdüsen 3 versorgen, solange keine zeitlichen Überschneidungen der Zumeßvorgänge für die verschiedenen Injektoren vorliegen. In welchen Injektor die jeweils zugemessene Menge an Zusatzflüssigkeit abgehen soll, bestimmt wiederum ein einfach aufgebautes zweites 2/2-Wegeventil MV2, das allerdings für jede Zweistoffdüse der Gruppe vorhanden sein muß.To save costs (higher quantities), the other can 2/2-way valve MV3 identical in construction to the first 2/2-way valve MV1 can be designed, whereby the 2/2-way valve MV3, however suitable for operation with the additional liquid have to be. In addition, the further 2/2-way valve MV3 can supply entire group of two-substance nozzles 3, as long as none temporal overlaps of the metering processes for the different Injectors. In which injector each measured amount of additional liquid should go off, again determines a simply constructed second 2/2-way valve MV2, however, for every two-component nozzle in the group must be present.

    Um den steuerungstechnisch verwertbaren Druckabfall zwischen dem weiteren Common-Rail-Druckspeicher 32 mit Zusatzflüssigkeit und dem Rest der hydraulischen Widerstandskette konstant zu halten, ist der weitere Common-Rail-Druckspeicher 32 über ein Druckhalteventil 33 (p0 = const) mit dem Vorratsbehälter 25 für Zusatzflüssigkeit verbunden. Am Ende der hydraulischen Widerstandskette ist ein weiteres Druckhalteventil 43 in der Abfuhrleitung 8 vorgesehen, die das zweite 2/2-Wegeventil MV2 mit der Kraftstoff-Niederdruckseite verbindet.In order to keep the pressure drop between the further common rail pressure accumulator 32 with additional liquid and the rest of the hydraulic resistance chain usable in terms of control technology, the further common rail pressure accumulator 32 is connected to the reservoir 25 via a pressure maintaining valve 33 (p 0 = const) Additional liquid connected. At the end of the hydraulic resistance chain, a further pressure holding valve 43 is provided in the discharge line 8, which connects the second 2/2-way valve MV2 to the low-pressure fuel side.

    Zur Abführung einer möglichen Leckage von Zusatzflüssigkeit aus dem den Hebelmechanismus 22 einschließenden Raum ist eine Leckageleitung 35 angebracht, die in den Vorratsbehälter 25 mündet.To drain possible leakage of additional liquid from the space enclosing the lever mechanism 22 is one Leakage line 35 attached to the reservoir 25 opens.

    Die Förderung der Zusatzflüssigkeit aus dem Zusatzbehälter 25 erfolgt über ein Rückschlagventil 34. Zur Unterstützung des Fluidförderung kann auch noch eine in der Zeichnung nicht dargestellte Pumpe vorgesehen sein.The delivery of the additional liquid from the additional container 25 is done via a check valve 34. For support The fluid delivery can also be one in the drawing Pump not shown may be provided.

    Fig. 4 schließlich zeigt eine Weiterbildung der Ausführungsform nach Fig. 3, bei der auf einen Hebelmechanismus 22 sowie auf eine Verstellmimik verzichtet wurde. Die Förderung und Zumessung wird hier direkt von der an den Hochdruckraum 40.1 des Common-Rail-Druckspeichers 40 für Kraftstoff angelenkten Membran 41.1 bewirkt, welche bei entsprechendem Überdruck im Hochdruckraum 40.1 einen Druckstoß an einen mit Zusatzflüssigkeit beschickten Raum 43 abgibt, der über das Rückschlagventil 31 in den weiteren Common-Rail-Druckspeicher 42 weitergegeben wird. Die übrigen Funktionen sind ganz analog zu denen des Ausführungsbeispiels nach Fig. 3.4 shows a further development of the embodiment 3, in which on a lever mechanism 22 and an adjustment facial expression was dispensed with. The promotion and metering is here directly from the to the high pressure room 40.1 of the common rail pressure accumulator 40 for fuel Membrane 41.1, which with appropriate Overpressure in the high pressure chamber 40.1 with a pressure surge Provides additional liquid charged space 43, which on the Check valve 31 in the other common rail pressure accumulator 42 is passed on. The other functions are complete analogous to those of the exemplary embodiment according to FIG. 3.

    Claims (20)

    1. Fuel injection system for an internal combustion engine, with a high-pressure pump (1) for conveying the fuel, preferably diesel fuel, into a dual-fuel nozzle (3), and with a conveying device for conveying an additional liquid, preferably water, guided via a non-return valve (3.4), into an additional-liquid line (15) which leads to the dual-fuel nozzle (3) and which is connected to a pressure space (3.5) surrounding a nozzle needle (3.1) of the dual-fuel nozzle (3), furthermore with a valve arrangement for reserving the additional-liquid quantity in the dual-fuel nozzle (3), the opening and closing of the nozzle needle (3.1) taking place by means of the pressure of a common-rail pressure accumulator (2; 20; 30; 40) filled with fuel under high pressure, the valve arrangement being arranged at least partially in the injection line (6) and, during the reservation of the additional liquid, interrupting the fuel supply to the injection nozzle (3) and connecting the pressure space (3.5) to a fuel low-pressure side and otherwise interrupting the connection to the fuel low-pressure side and acting upon the pressure space (3.5) with high-pressure fuel, characterized in that a first 2/2-way valve (MV1) is provided in the injection line (6) between the common-rail pressure accumulator (2; 20; 30; 40) and the pressure space (3.5) and a second 2/2-way valve (MV2) is provided, the inlet of which is connected via a supply line (7) to the injection line (6) at a point between the first 2/2-way valve (MV1) and the pressure space (3.5) and the outlet of which is connected via a discharge line (8) to the fuel low-pressure side, there being articulated at a pressure-guiding end of the common-rail pressure accumulator (20; 30; 40) a diaphragm (21.1; 41.1), one side of which is acted upon by the high pressure prevailing in the common-rail pressure accumulator (20; 30; 40) and the other side of which, in the event of pressure fluctuations in the common-rail pressure accumulator (20; 30; 40), can convey additional liquid directly or indirectly out of a reservoir (25) and ultimately into the additional-liquid line (15) leading to the dual-fuel nozzle (3).
    2. Fuel injection system according to Claim 1, characterized in that the other side of the diaphragm (21.1) which faces away from the high pressure in the common-rail pressure accumulator (20; 30) is connected to a lever mechanism (22) which, in the event of a corresponding movement of the diaphragm (21.1), can drive a pump piston (23.1) which conveys additional liquid out of the reservoir (25).
    3. Fuel injection system according to Claim 2, characterized in that a prefeed pump (26) for conveying the additional liquid over greater distances and/or counter to a geodetic gradient is provided in a line (29) from the reservoir (25) to the pump piston (23.1), from which line the additional-liquid line (15) leading to the dual-fuel nozzle (3) branches off.
    4. Fuel injection system according to Claim 3, characterized in that a non-return valve (27) is arranged in the line (29) between the prefeed pump (26) and the branch-off point of the additional-liquid line (15) leading to the dual-fuel nozzle (3).
    5. Fuel injection system according to Claim 4, characterized in that, from the additional-liquid line (15) leading to the dual-fuel nozzle (3), an excess-pressure line leading to the reservoir (25) is provided, having an excess-pressure non-return valve (28) which, when a corresponding threshold pressure in the additional-liquid line (15) is exceeded, opens and connects the additional-liquid line (15) directly to the reservoir (25).
    6. Fuel injection system according to one of Claims 2 to 5, characterized in that an adjusting mechanism for adjusting the lever mechanism (22) and consequently the stroke volume moved by the pump piston (23.1) is provided.
    7. Fuel injection system according to Claim 6, characterized in that the adjusting mechanism is driven by an electric motor (24.3).
    8. Fuel injection system according to Claim 7, characterized in that the electric motor (24.3) drives a spindle (24.2) which is screwed into a longitudinally movable slide (24.1), on which a lever of the lever mechanism (22) is mounted rotatably.
    9. Fuel injection system according to one of Claims 1 to 8, characterized in that the diaphragm (21.1; 41.1) is clamped in a pressure-tight manner in the common-rail pressure accumulator (20; 30; 40) via a high-mass wall (21.2), the high-mass wall (21.2) having an aperture bore (21.3), through which fuel can penetrate into a space (21.4) between the diaphragm (21.1; 41.1) and the high-mass wall (21.2) or emerge from the said space, depending on the direction of the pressure gradient.
    10. Method for operating a fuel injection system according to one of Claims 6 to 9, characterized in that pressure fluctuations occurring in the common-rail pressure accumulator (20; 30; 40) are measured and control commands to the adjusting mechanism are derived from these according to the diaphragm characteristic and the current requirement for additional liquid to be conveyed.
    11. Method for operating a fuel injection system according to one of Claims 6 to 9, characterized in that the instantaneous stroke of the pump piston (23.1) is measured and control commands to the adjusting mechanism are derived from this according to the diaphragm characteristic and the current requirement for additional liquid to be conveyed.
    12. Fuel injection system according to one of Claims 2 to 9, characterized in that a further common-rail pressure accumulator (32) for the reception of additional liquid which is under pressure is provided, the said further common-rail pressure accumulator being connected via a 2/2-way valve (MV3) to the additional-liquid line (15) leading to the dual-fuel nozzle (3) and via a non-return valve (31) to the conveying side of the diaphragm-driven pump piston (23.1).
    13. Fuel injection system according to Claim 1, characterized in that a further common-rail pressure accumulator (42) for the reception of additional liquid which is under pressure is provided, the said further common-rail pressure accumulator being connected via a 2/2-way valve (MV3) to the additional-liquid line (15) leading to the dual-fuel nozzle (3) and via a non-return valve (31) to the conveying side of the diaphragm (41.1) conveying additional liquid.
    14. Fuel injection system according to Claim 12 or 13, characterized in that the further common-rail pressure accumulator (32; 42) for additional liquid is integrated preferably in one piece with the common-rail pressure accumulator (30; 40) for fuel.
    15. Fuel injection system according to one of Claims 12 to 14, characterized in that the 2/2-way valve (MV3) in the additional-liquid line (15) is structurally identical to the first 2/2-way valve (MV1) in the injection line (6).
    16. Fuel injection system according to one of Claims 12 to 15, characterized in that the 2/2-way valve (MV3) in the additional-liquid line (15) supplies a group of a plurality of dual-fuel nozzles (3) successively in time.
    17. Fuel injection system according to one of Claims 12 to 16, characterized in that the further common-rail pressure accumulator (32; 42) for additional liquid is connected via a pressure-holding valve (33) to the reservoir (25) for additional liquid and the second 2/2-way valve (MV2) is connected via a further pressure-holding valve (43) to the fuel low-pressure side.
    18. Fuel injection system according to one of the preceding claims, characterized in that a non-return valve (9) is provided in the discharge line (8) between the second 2/2-way valve (MV2) and the fuel low-pressure side.
    19. Fuel injection system according to Claim 18, characterized in that there is connected firmly, preferably in one piece with the nozzle needle (3.1), at the obtuse axial end, facing away from the nozzle-needle tip, of the nozzle needle (3.1), in the axial prolongation of the said nozzle needle, a piston (3.3) which, with its axial end facing away from the nozzle needle (3.1), projects into a space (3.6) which is sealed off in a pressure-tight manner against the space (3.2), receiving the obtuse axial end of the nozzle needle (3.1), of the dual-fuel nozzle (3) and which is acted upon by the high pressure prevailing in the common-rail pressure accumulator (2; 20; 30; 40).
    20. Fuel injection system according to Claim 19, characterized in that the space (3.2) receiving the obtuse axial end of the nozzle needle (3.1) is connected to the fuel low-pressure side via a ventilating line (5).
    EP98954191A 1997-10-22 1998-09-18 Fuel injection system for an internal combustion engine Expired - Lifetime EP0946830B1 (en)

    Applications Claiming Priority (3)

    Application Number Priority Date Filing Date Title
    DE19746492 1997-10-22
    DE19746492A DE19746492A1 (en) 1997-10-22 1997-10-22 Dual fluid injection system for IC engine
    PCT/DE1998/002771 WO1999020893A1 (en) 1997-10-22 1998-09-18 Fuel injection system for an internal combustion engine

    Publications (2)

    Publication Number Publication Date
    EP0946830A1 EP0946830A1 (en) 1999-10-06
    EP0946830B1 true EP0946830B1 (en) 2003-11-26

    Family

    ID=7846178

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP98954191A Expired - Lifetime EP0946830B1 (en) 1997-10-22 1998-09-18 Fuel injection system for an internal combustion engine

    Country Status (7)

    Country Link
    US (1) US6067964A (en)
    EP (1) EP0946830B1 (en)
    JP (1) JP2001507101A (en)
    KR (1) KR20000069569A (en)
    CN (1) CN1109193C (en)
    DE (2) DE19746492A1 (en)
    WO (1) WO1999020893A1 (en)

    Families Citing this family (34)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    AU7178698A (en) * 1996-11-15 1998-06-03 Advanced Bio Surfaces, Inc. Biomaterial system for in situ tissue repair
    DE19746490A1 (en) * 1997-10-22 1999-04-29 Bosch Gmbh Robert Dual fluid injection system for IC engine
    DE19747268A1 (en) * 1997-10-25 1999-04-29 Bosch Gmbh Robert Dual fluid injection system for internal combustion engine
    EP1061252B1 (en) * 1999-06-18 2003-08-06 Mitsubishi Fuso Truck and Bus Corporation Fuel injector
    DE19938169A1 (en) * 1999-08-16 2001-03-01 Bosch Gmbh Robert Fuel injector
    DE19939420B4 (en) * 1999-08-20 2004-12-09 Robert Bosch Gmbh Fuel injection method and system for an internal combustion engine
    DE10032923A1 (en) 2000-07-06 2002-01-24 Bosch Gmbh Robert Fuel injection device for internal combustion engines
    DE10146739A1 (en) * 2001-09-22 2003-04-10 Bosch Gmbh Robert Fuel injection device for an internal combustion engine
    US10569792B2 (en) 2006-03-20 2020-02-25 General Electric Company Vehicle control system and method
    US10308265B2 (en) 2006-03-20 2019-06-04 Ge Global Sourcing Llc Vehicle control system and method
    US9733625B2 (en) 2006-03-20 2017-08-15 General Electric Company Trip optimization system and method for a train
    KR20040015578A (en) * 2002-08-13 2004-02-19 현대자동차주식회사 Wiring connector
    US9950722B2 (en) 2003-01-06 2018-04-24 General Electric Company System and method for vehicle control
    DE102004053266A1 (en) * 2004-11-04 2006-05-11 Robert Bosch Gmbh Apparatus and method for correcting the injection behavior of an injector
    US9828010B2 (en) 2006-03-20 2017-11-28 General Electric Company System, method and computer software code for determining a mission plan for a powered system using signal aspect information
    US9156477B2 (en) 2006-03-20 2015-10-13 General Electric Company Control system and method for remotely isolating powered units in a vehicle system
    US7630823B2 (en) 2007-09-20 2009-12-08 General Electric Company System and method for controlling the fuel injection event in an internal combustion engine
    JP4595996B2 (en) * 2007-11-16 2010-12-08 トヨタ自動車株式会社 High pressure fuel supply device for internal combustion engine
    DE102008001444A1 (en) * 2008-04-29 2009-11-05 Robert Bosch Gmbh Method for determining an overpressure in a fuel accumulator of an injection system of an internal combustion engine
    CA2635410C (en) * 2008-06-19 2010-08-17 Westport Power Inc. Dual fuel connector
    US9834237B2 (en) 2012-11-21 2017-12-05 General Electric Company Route examining system and method
    US20110297125A1 (en) * 2010-06-03 2011-12-08 Caterpillar Inc. Reverse Flow Check Valve For Common Rail Fuel System
    US8919324B2 (en) 2010-12-08 2014-12-30 Robin B. Parsons Fuel rail for liquid injection of a two-phase fuel
    US20120255523A1 (en) * 2011-04-08 2012-10-11 Caterpillar Inc. Dual fuel injector and engine using same
    US20140373806A1 (en) * 2012-01-05 2014-12-25 Deyang Hou Fuel injector for multi-fuel injection with pressure intensification and a variable orifice
    US9669851B2 (en) 2012-11-21 2017-06-06 General Electric Company Route examination system and method
    SE537002C2 (en) 2013-03-22 2014-11-25 Scania Cv Ab Combustion engine fuel system and a method for regulating a fuel system
    US10202929B1 (en) 2014-09-22 2019-02-12 National Technology & Engineering Solutions Of Sandia, Llc Additive-mixing fuel-injection system for internal combustion engines
    BR112018008976B1 (en) 2015-11-20 2023-01-03 Mcearth Holdings Ltd EXTRATIFIED CHARGE COMBUSTION ENGINE, MECHANICAL ENERGY PRODUCTION PROCESS, CATALYST PRECURSOR AND CATALYTIC SUPPORT
    WO2018007865A1 (en) 2016-07-04 2018-01-11 Dominique Bosteels Stratified charge combustion engine
    CN109386420B (en) * 2018-10-15 2021-02-02 哈尔滨工程大学 Method for measuring multi-time fuel injection rule
    US11008957B2 (en) 2019-06-05 2021-05-18 Caterpillar Inc. Spill valve assembly for improved minimum delivery capability in fuel system
    DE102020116707A1 (en) * 2020-06-25 2021-12-30 Man Energy Solutions Se Fuel injector of a dual-fuel internal combustion engine and dual-fuel internal combustion engine
    DE102020116710A1 (en) * 2020-06-25 2021-12-30 Man Energy Solutions Se Dual-fuel internal combustion engine

    Family Cites Families (16)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    US4612905A (en) * 1980-01-26 1986-09-23 Motoren-Werke Mannheim Ag, Vorm. Benz Stat. Motorenba Fuel injection apparatus
    JPS5848771A (en) * 1981-09-04 1983-03-22 Toyota Motor Corp Fuel injecting device for diesel engine
    GB2126650B (en) * 1982-08-31 1988-02-10 George Stan Baranescu I c engine injection system providing a stratified charge of two fuels
    US4524033A (en) * 1983-03-31 1985-06-18 Elledge Jefferson D Multiple fuel carburetor
    DE3330772A1 (en) * 1983-08-26 1985-03-14 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION DEVICE
    DE3330774A1 (en) * 1983-08-26 1985-03-14 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION DEVICE WITH PRIMARY AND MAIN INJECTION IN INTERNAL COMBUSTION ENGINES
    US4693227A (en) * 1985-05-21 1987-09-15 Toyota Jidosha Kabushiki Kaisha Multi-fuel injection system for an internal combustion engine
    US5174247A (en) * 1992-01-22 1992-12-29 Mitsubishi Jukogyo Kabushiki Kaisha Water injection diesel engine
    DE4337048C2 (en) * 1993-10-29 1996-01-11 Daimler Benz Ag Fuel injection system for an internal combustion engine
    DE4341739C1 (en) * 1993-12-08 1995-03-30 Mtu Friedrichshafen Gmbh Injection system
    DE4407052C1 (en) * 1994-03-03 1995-03-09 Mtu Friedrichshafen Gmbh Injection system for the injection of a fuel and a liquid additive into the combustion chambers of an internal combustion engine
    US5732679A (en) * 1995-04-27 1998-03-31 Isuzu Motors Limited Accumulator-type fuel injection system
    DE19523878C2 (en) * 1995-06-30 1999-12-30 Mtu Friedrichshafen Gmbh Injection device for injecting fuel and a second fluid into a combustion chamber of a diesel engine
    EP0760425B1 (en) * 1995-08-30 2000-11-15 Robert Bosch Gmbh Injection device
    FI101739B (en) * 1996-08-16 1998-08-14 Waertsilae Nsd Oy Ab An injection valve
    DE19738397A1 (en) * 1997-09-03 1999-03-18 Bosch Gmbh Robert Fuel injection system for an internal combustion engine

    Also Published As

    Publication number Publication date
    DE59810274D1 (en) 2004-01-08
    WO1999020893A1 (en) 1999-04-29
    JP2001507101A (en) 2001-05-29
    US6067964A (en) 2000-05-30
    CN1109193C (en) 2003-05-21
    CN1242822A (en) 2000-01-26
    KR20000069569A (en) 2000-11-25
    EP0946830A1 (en) 1999-10-06
    DE19746492A1 (en) 1999-04-29

    Similar Documents

    Publication Publication Date Title
    EP0946830B1 (en) Fuel injection system for an internal combustion engine
    EP0954695B1 (en) Dual nozzle for injecting fuel and an additional fluid
    EP0873473A1 (en) Fuel injector
    EP1485609A1 (en) Device for injecting fuel to stationary internal combustion engines
    DE102008043217A1 (en) High-pressure fuel pump for an internal combustion engine
    EP0941400A1 (en) Liquid control valve
    EP1392966A1 (en) Fuel injection device with pressure amplification device and pressure amplification device
    EP0946828B1 (en) Fuel injection system for an internal combustion engine
    EP1141539A1 (en) Piston pump for high-pressure fuel generation
    EP0596054B1 (en) Fuel injection device for internal combustion engines
    EP1826396B1 (en) Common rail fuel injection system
    EP0982492B1 (en) Apparatus for injecting fuel in a reciprocating internal combustion engine
    WO2017174118A1 (en) Fuel exchange and fuel delivery system for fuel installations
    DE10139055A1 (en) Method, computer program, control and / or regulating device and fuel system for an internal combustion engine
    EP0946829B1 (en) Fuel injection system for an internal combustion engine
    DE102004008478A1 (en) Pump device for fuel injection system, has fuel tank connected to high pressure pump via feed pump with controllable fuel flow
    EP0974006A1 (en) Fuel injection system for an internal combustion engine
    DE19738502A1 (en) High pressure generation system
    DE3241266A1 (en) FUEL INJECTION PUMP DEVICE
    DE10139623A1 (en) Injection arrangement for fuel storage injection system has bypass channel from high-pressure chamber to valve chamber closed by valve closure element during injection process
    EP2807366B1 (en) Apparatus to inject fuel in the combustion chamber of a combustion engine
    DE2641203C2 (en) Fuel injection pump for an internal combustion engine
    DE3310030C2 (en) Fuel injection device for an internal combustion engine
    DE102016202916B4 (en) Method set up for controlling a fuel supply system for an internal combustion engine
    DE19834763C2 (en) Pump-line-nozzle system

    Legal Events

    Date Code Title Description
    PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

    Free format text: ORIGINAL CODE: 0009012

    AK Designated contracting states

    Kind code of ref document: A1

    Designated state(s): DE FR GB IT

    17P Request for examination filed

    Effective date: 19991029

    17Q First examination report despatched

    Effective date: 20020802

    GRAH Despatch of communication of intention to grant a patent

    Free format text: ORIGINAL CODE: EPIDOS IGRA

    GRAS Grant fee paid

    Free format text: ORIGINAL CODE: EPIDOSNIGR3

    GRAA (expected) grant

    Free format text: ORIGINAL CODE: 0009210

    AK Designated contracting states

    Kind code of ref document: B1

    Designated state(s): DE FR GB IT

    REG Reference to a national code

    Ref country code: GB

    Ref legal event code: FG4D

    Free format text: NOT ENGLISH

    REF Corresponds to:

    Ref document number: 59810274

    Country of ref document: DE

    Date of ref document: 20040108

    Kind code of ref document: P

    GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

    Effective date: 20040301

    ET Fr: translation filed
    PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

    Ref country code: GB

    Payment date: 20040906

    Year of fee payment: 7

    PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

    Ref country code: FR

    Payment date: 20040917

    Year of fee payment: 7

    PLBE No opposition filed within time limit

    Free format text: ORIGINAL CODE: 0009261

    STAA Information on the status of an ep patent application or granted ep patent

    Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

    26N No opposition filed

    Effective date: 20040827

    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: IT

    Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

    Effective date: 20050918

    Ref country code: GB

    Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

    Effective date: 20050918

    GBPC Gb: european patent ceased through non-payment of renewal fee

    Effective date: 20050918

    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: FR

    Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

    Effective date: 20060531

    REG Reference to a national code

    Ref country code: FR

    Ref legal event code: ST

    Effective date: 20060531

    PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

    Ref country code: DE

    Payment date: 20101126

    Year of fee payment: 13

    REG Reference to a national code

    Ref country code: DE

    Ref legal event code: R119

    Ref document number: 59810274

    Country of ref document: DE

    Effective date: 20130403

    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: DE

    Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

    Effective date: 20130403