EP0898678B1 - Method for fuel injection in multicylinder engines and device for the implementation of said method - Google Patents
Method for fuel injection in multicylinder engines and device for the implementation of said method Download PDFInfo
- Publication number
- EP0898678B1 EP0898678B1 EP98923988A EP98923988A EP0898678B1 EP 0898678 B1 EP0898678 B1 EP 0898678B1 EP 98923988 A EP98923988 A EP 98923988A EP 98923988 A EP98923988 A EP 98923988A EP 0898678 B1 EP0898678 B1 EP 0898678B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- fuel
- common rail
- shutoff valve
- return
- 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
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
- F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
- F02M53/04—Injectors with heating, cooling, or thermally-insulating means
- F02M53/08—Injectors with heating, cooling, or thermally-insulating means with air cooling
-
- 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
- F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
- F02M53/04—Injectors with heating, cooling, or thermally-insulating means
- F02M53/043—Injectors with heating, cooling, or thermally-insulating means with cooling means other than air cooling
-
- 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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
- F02M55/025—Common rails
-
- 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
- F02M63/06—Use of pressure wave generated by fuel inertia to open injection valves
Definitions
- the invention relates to a method for fuel injection in multi-cylinder engines by generating a fuel admission pressure to deliver the fuel in a flywheel line for the purpose of using the pressure surge principle by means of a shutoff valve in the flywheel line, each injection nozzle assigned to a shutoff valve being supplied with the pressure surge and the fuel not passing the injection nozzle is fed back through the return line in front of the fuel pump via a return line, and a device for carrying out the method.
- Technical solutions of this type are required above all for fuel injection in internal combustion engines.
- Preferred areas of application are multi-cylinder gas engines with diesel pilot injection, multi-cylinder diesel engines, multi-cylinder gasoline engines and multi-cylinder engines for the use of alternative power.
- Multi-cylinder engines are predominantly equipped with fuel pumps that are driven by camshafts.
- the fuel dose supplied to the working cylinders has a marked speed dependency with regard to the droplet size and the length of the fuel jet.
- the required maximum pressure is always present in the rail or in the overall system up to the injection nozzles, but this pressure is only required temporarily when fuel is injected due to the opening of one or more electromagnetically controlled injection nozzles.
- the droplet size and the properties of the fuel jet remain the same regardless of the engine speed.
- the fuel pre-pressure realized by the pump or pumps with the corresponding adverse energy effects is only used to a small extent.
- the injection period 40 ms.
- the injection duration is only a maximum of 2 ms per injection period, which corresponds to an energetic utilization rate of at most 5%.
- the object of the invention is therefore to overcome the disadvantages of to overcome known prior art.
- One is aimed for technical solution with high energy efficiency and a low mechanical engineering requirements for a Improvement of the mass / performance and the price / performance ratio in the manufacture of multi-cylinder engines.
- the object is essentially achieved by the protective features of claims 1 and 10.
- the method for fuel injection in multi-cylinder engines is characterized in that essentially a single fuel pump delivers the fuel with a pre-pressure into a pre-pressure railchamber common to several engine cylinders, the pre-pressure corresponding to only a fraction of the required injection pressure. If the pre-pressure is exceeded, the fuel is transferred from the pre-pressure railchamber via pressure relief valves to the return railchamber common to several engine cylinders.
- each Shut-off valve a swing line between the pre-pressure Railchamber and Return railchamber is used.
- Each shut-off valve is in the each swing line actuated at least one injector.
- the pressure surge occurring when a shut-off valve is closed is used for the Dosing of the fuel used through the respective injection nozzle.
- the pressure conditions in the pre-pressure railchamber and in the return railchamber are kept constant with simple means, so that in the swing lines over the entire speed range optimal Flow conditions can be guaranteed. On this The basis is when the shut-off valves are actuated in the respective The pressure surge required for fuel injection via the injection nozzles connected to the respective swing line generated.
- the method is thereby characterized in that the energy of the in the return railchamber stored fuel is used for the fuel delivery system. This leads to an additional favorable influence on the Energy expenditure for providing the required fuel pressure in the pre-printed Railchamber.
- the flywheel can be used in conjunction with devices for Vibration damping are operated. This prevents unwanted ones Impairments to the fuel delivery system.
- swing line, Shut-off valve, vibration damper and injector in one High pressure unit can be summarized per cylinder.
- This High pressure unit can be covered with a jacket if necessary Engine operated thermally insulated and or by a in the jacket integrated cooling medium can be cooled.
- the technical solution is also characterized by a device consisting of fuel pumps, flywheel lines with shut-off valves and return lines to the fuel supply system.
- a pre-pressure railchamber common to at least one fuel pump and at least one flywheel line is arranged for a cylinder group or for all cylinders of the multi-cylinder engine.
- a return railchamber common to a cylinder group or to all cylinders of the multi-cylinder engine is arranged between the upstream and the return railchamber.
- each high pressure module you can choose between the pre-pressure Railchamber and Return railchamber one or more injection nozzles can be arranged.
- shut-off valve and the injection nozzles of a high-pressure unit can constructively in a common component or in several Lines connected components can be arranged.
- an embodiment of the device is thereby characterized in that one or more on the pre-printed Railchamber Fuel pumps are arranged.
- a cylinder group or for all cylinders of the multi-cylinder engine common pre-printed Railchamber and one for one Cylinder group or for all cylinders of the multi-cylinder engine common return railchamber as two chambers in one execute common structural unit. If necessary, the Execution of pre-pressure and return railchambers as two chambers a common railchamber in the partition between the Chamber one or more of the hysteresis and vibration free Pressure relief valves ensuring constant upstream pressure arranged.
- the arrangement of the high-pressure module in a thermal is advantageous insulating sleeve.
- This sleeve can also be used with a Coolant are operated and has a coolant inlet and a cooling medium drain.
- the invention makes it possible to combine the design and control of the fuel injection system according to the invention with the advantageous properties of a modern common rail.
- a common pre-pressure railchamber for all or for individual groups of working cylinders of a multi-cylinder engine as well as controlled valves are operated in a direct functional connection with injection nozzles.
- a decisive advantage of the solution found is that only a part of about a tenth of the required maximum pressure has to be constantly provided in the pre-pressure railchamber and that the maximum pressure is only a short-term pressure wave immediately before fuel metering via the injection nozzle by controlling the respective shut-off valve in front of one individual or a group of injection nozzles.
- the system is composed of a pre-pressure module, the pressure supply system, and high pressure modules.
- the high pressure required is generally 8 to 10 times the pre-pressure.
- the technical solution according to the invention is implemented in that a pressure accumulator is loaded by the admission pressure generated by a fuel pump, which prevents disruptive pressure fluctuations when the fuel is drawn from this pressure accumulator.
- the memory is designed as a common component in the form of a pre-pressure railchamber for several high-pressure modules connected to it. Defined opening of the controlled shut-off valves in one high-pressure module causes an acceleration of the fuel in the associated flywheel, which is returned to the return railchamber. The fuel is withdrawn from the fuel pump (s) primarily from the respective return railchamber using the available residual pressure, only the amount of fuel withdrawn from the system via the injection nozzles being withdrawn from the fuel tank. The abrupt closing of the shut-off valves in the respective high-pressure module results in a conversion of the predominant part of the kinetic energy of the fuel in the flow into pressure energy.
- the pressure increase brought about reaches a multiple of the static admission pressure in the admission pressure railchamber and propagates in the form of a pressure wave in the direction of the individual or more injection nozzles connected to the flywheel of the respective high pressure module, where it can be used for fuel injection.
- the pressure wave generated is reduced to the level of the pre-pressure generated in order to avoid undesirable reflections and impair the function of the injection system.
- This form arrives via a supply line in one for all cylinders of the machine common form Railchamber 4, which with an integrated additional fuel fine filter.
- the pre-pressure Railchamber 4 feeds the high pressure modules for the single working cylinder consisting of the flywheel 11, shut-off valve 10, Vibration damper 9, inclusion of the flywheel 12 and injection nozzle 13 exist.
- the pre-printed Railchamber 4 not only functions as a Fuel distribution system but because of its dimensions at the same time as Pressure fluctuations reducing pressure accumulator. When open Shut-off valves 10 in the high pressure modules will be under pressure standing fuel in the flywheel 11 accelerates and over a common return Railchamber 6 for all working cylinders Fuel pump 3 returned.
- the kinetic energy of the river located fuel is by suddenly closing the Electromagnetically operated shut-off valve 10 predominantly in Converted pressure energy, which takes the form of a pressure wave Injection nozzle 13 and the vibration damper 9 to the end of Flywheel 11 continues.
- Pressure of the pressure wave to avoid unwanted reflections steamed at least to the level of the form.
- the one in the blast The pressure level to be recorded is average or depends on the injection quantity is approximately 10 times the pre-set pressure and is used for fuel metering in the respective working cylinder the flywheel 11 connected injector 13 used.
- Between the pre-pressure railchamber 4 and the return railchamber 6 are one Short-circuit line arranged to keep constant vibration of the admission pressure is equipped with a pressure relief valve 5.
- the in the return railchamber 6 available fuel pressure directly to the fuel pump 3 to the pre-pressure system.
- an insulating sleeve 7 is arranged, which via a cooling medium inlet 8a and a cooling medium outlet 8b is flowed through with cooling liquid.
Abstract
Description
Die Erfindung betrifft ein Verfahren zur Kraftstoffeinspritzung in
Mehrzylinder-Kraftmaschinen durch Erzeugen eines Kraftstoffvordruckes
zur Förderung des Kraftstoffes in einer Schwungleitung zwecks
Nutzung des Druckstoßprinzips mittels Absperrventil in der
Schwungleitung, wobei jede einem Absperrventil zugeordnete
Einspritzdüse mit dem Druckstoß versorgt wird und der nicht die
Einspritzdüse passierende Kraftstoff durch das geöffnete Absperrventil
über eine Rücklaufleitung vor die Kraftstoffpumpe zurückgefördert wird,
sowie eine Vorrichtung zur Durchführung des Verfahrens.
Derartige technische Lösungen werden vor allem bei der
Kraftstoffeinspritzung in Verbrennungskraftmaschinen benötigt.
Bevorzugte Anwendungsgebiete sind Mehrzylinder-Gasmotoren mit
Diesel-Piloteinspritzung, Mehrzylinder-Dieselmotoren, Mehrzylinder-Ottomotoren
und Mehrzylinder-Motoren für den Einsatz von Alternativ-Kraftstorfen.The invention relates to a method for fuel injection in multi-cylinder engines by generating a fuel admission pressure to deliver the fuel in a flywheel line for the purpose of using the pressure surge principle by means of a shutoff valve in the flywheel line, each injection nozzle assigned to a shutoff valve being supplied with the pressure surge and the fuel not passing the injection nozzle is fed back through the return line in front of the fuel pump via a return line, and a device for carrying out the method.
Technical solutions of this type are required above all for fuel injection in internal combustion engines. Preferred areas of application are multi-cylinder gas engines with diesel pilot injection, multi-cylinder diesel engines, multi-cylinder gasoline engines and multi-cylinder engines for the use of alternative power.
Mehrzylinder-Kraftmaschinen sind überwiegend mit Kraftstoffpumpen
ausgestattet, die von Nockenwellen angetrieben werden. Die den
Arbeitszylindern zugeführte Kraftstoffdosis weist dabei bezüglich der
Tröpfchengröße und der Länge des Kraftstoffstrahls eine markante
Drehzahlabhängigkeit auf.
Bei sogenannten Common-Rail-Systemen herrscht im Rail bzw. im
Gesamtsystem bis zu den Einspritzdüsen stehts der erforderliche
Maximaldruck, der jedoch nur zeitweise beim Kraftstoffeinspritzen infolge
der Öffnung einer oder mehrerer elektromagnetisch gesteuerter
Einspritzdüsen benötigt wird. Multi-cylinder engines are predominantly equipped with fuel pumps that are driven by camshafts. The fuel dose supplied to the working cylinders has a marked speed dependency with regard to the droplet size and the length of the fuel jet.
In so-called common rail systems, the required maximum pressure is always present in the rail or in the overall system up to the injection nozzles, but this pressure is only required temporarily when fuel is injected due to the opening of one or more electromagnetically controlled injection nozzles.
In diesem Falle bleiben die Tröpfchengröße sowie die Eigenschaften des
Kraftstoffstrahles unabhängig von der Motordrehzahl gleich. Allerdings
wird der von der oder den Pumpen realisierte Kraftstoffvordruck mit den
entsprechend nachteiligen energetischen Auswirkungen nur zu einem
geringen Teil genutzt.
So beträgt beispielsweise bei einem Vierzylinder-Viertaktmotor mit einer
Drehzahl von 3000 1/Min. die Einspritzperiode 40 ms. Die Einspritzdauer
beträgt je Einspritzperiode dagegen lediglich maximal 2 ms, was einer
energetischen Nutzungsrate von höchstens 5 % entspricht.In this case, the droplet size and the properties of the fuel jet remain the same regardless of the engine speed. However, the fuel pre-pressure realized by the pump or pumps with the corresponding adverse energy effects is only used to a small extent.
By way of example, in a four-cylinder four-stroke engine with a speed of 3000 1 / min. the injection period 40 ms. The injection duration, on the other hand, is only a maximum of 2 ms per injection period, which corresponds to an energetic utilization rate of at most 5%.
Bekannt sind technische Lösungsvorschläge, die das Nutzen des
Druckstoßprinzips für die Bereitstellung des beim Vorgang des
Kraftstoffeinspritzens bei Einzylinder-Arbeitsmaschinen in den
Arbeitszylinder benötigten Drucks vorsehen. Hierbei kann der durch die
Kraftstoffpumpe bereitgestellte Vordruck auf einen Bruchteil des
benötigten Kraftstoffdrucks an der jeweiligen Einspritzdüse beschränkt
bleiben. Eine solche Lösung ist aus der WO-A-92/14925
bekannt.
Für die Nutzung dieses Prinzips bei Mehrzylinder-Arbeitsmaschinen
vervielfachen sich dabei die Anforderungen an Kraftstoffpumpen-Antriebe,
an die Kraftstoffpumpen sowie an die Kraftstoff-Vordruck- und Kraftstoff-Rücklaufförderleitungen.Technical solution proposals are known which provide for the use of the pressure surge principle for the provision of the pressure required in the working cylinder during the process of fuel injection in single-cylinder machines. In this case, the admission pressure provided by the fuel pump can remain limited to a fraction of the required fuel pressure at the respective injection nozzle. Such a solution is known from WO-A-92/14925.
In order to use this principle in multi-cylinder machines, the requirements for fuel pump drives, for fuel pumps and for the fuel pre-pressure and fuel return delivery lines are multiplied.
Die Nachteile der bekannten Lösungen für die Kraftstoffeinspritzung in
Mehrzylinder-Kraftmaschinen bestehen im wesentlichen im Falle des
Einsatzes von üblichen nocken- oder nockenwellenbetriebener
Kraftstoffpumpen in der Drehzahlabhängigkeit von Tröpfchengröße und
Eigenschaften des eingespritzten Kraftstoffstrahls.
Im Falle der Anwendung von Common-Rail-Systemen wird die
Drehzahlabhängigkeit der Qualität des Kraftstoffeinspritzens zwar
vermieden, jedoch um den Preis eines inakzeptablen energetischen
Wirkungsgrades, da der über die gesamte Einspritzperiode bereitgestellte
Vordruck nur während des unmittelbaren Einspritzvorgangs tatsächlich
benötigt wird. The disadvantages of the known solutions for fuel injection in multi-cylinder engines essentially exist in the case of the use of conventional cam- or camshaft-operated fuel pumps in the speed dependence of the droplet size and the properties of the injected fuel jet.
In the case of the use of common rail systems, the speed dependence of the quality of the fuel injection is avoided, but at the price of an unacceptable energy efficiency, since the pre-pressure provided over the entire injection period is actually only needed during the immediate injection process.
Im Falle der Nutzung des für Einzylinder-Kraftmaschinen bekannten Druckstoßprinzips an Mehrzylinder-Kraftmaschinen würden sich die maschinentechnischen und steuerungstechnischen Anforderungen wegen der erforderlichen Vielzahl der einzusetzenden Kraftstoffpumpen einschließlich Pumpenantriebe sowie der benötigten Kraftstoffzu- und -rückleitungen zu den Hochdruckeinheiten vervielfachen, was zu kostenseitigen Nachteilen sowie zu einer Beeinträchtigung des Masse-/Leistungsverhältnisses führt.In the case of using what is known for single-cylinder engines Pressure surge principles on multi-cylinder engines would be the same mechanical and control engineering requirements the required number of fuel pumps to be used including pump drives and the required fuel supply and - Return lines to the high pressure units multiply what to disadvantages in terms of costs and an impairment of the mass / performance ratio leads.
Die Aufgabe der Erfindung besteht deshalb darin, die Nachteile des bekannten Standes der Technik zu überwinden. Angestrebt wird eine technische Lösung, die mit hohem energetischen Wirkungsgrad und einem geringen maschinentechnischen Aufwand Voraussetzungen für eine Verbesserung des Masse-/Leistungs- und des Preis-/ Leistungsverhältnisses bei der Herstellung von Mehrzylinder-Kraftmaschinen bietet.The object of the invention is therefore to overcome the disadvantages of to overcome known prior art. One is aimed for technical solution with high energy efficiency and a low mechanical engineering requirements for a Improvement of the mass / performance and the price / performance ratio in the manufacture of multi-cylinder engines.
Die Aufgabe wird erfindungsgemäß im wesentlichen durch die
schutzbegründenden Merkmale der Ansprüche 1 und 10 gelöst.
Das Verfahren zur Kraftstoffeinspritzung in Mehrzylinder-Kraftmaschinen
ist dabei dadurch gekennzeichnet, daß im wesentlichen eine einzige
Kraftstoffpumpe den Kraftstoff mit einem Vordruck in eine für mehrere
Motorzylinder gemeinsame Vordruck-Railchamber fördert, wobei der
Vordruck lediglich einem Bruchteil des benötigten Einspritzdrucks
entspricht. Der Kraftstoff wird bei Überschreiten des eingestellten
Vordruckes aus der Vordruck-Railchamber über
Druckbegrenzungsventile in die für mehrere Motorzylinder gemeinsame
Rücklauf-Railchamber überführt. According to the invention, the object is essentially achieved by the protective features of
The method for fuel injection in multi-cylinder engines is characterized in that essentially a single fuel pump delivers the fuel with a pre-pressure into a pre-pressure railchamber common to several engine cylinders, the pre-pressure corresponding to only a fraction of the required injection pressure. If the pre-pressure is exceeded, the fuel is transferred from the pre-pressure railchamber via pressure relief valves to the return railchamber common to several engine cylinders.
Zwischen Vordruck-Railchamber und Rücklauf-Railchamber werden sogenannte Schwungleitungen mit Absperrventilen vorgesehen, wobei je Absperrventil eine Schwungleitung zwischen Vordruck-Railchamber und Rücklauf-Railchamber genutzt wird. Je Absperrventil wird in der jeweiligen Schwungleitung mindestens eine Einspritzdüse betätigt. Der beim Schließen eines Absperrventils entstehende Druckstoß wird für das Dosieren des Kraftstoffs über die jeweilige Einspritzdüse verwendet. Der bei geöffnetern Absperrventil rückströmende Kraftstoff wird in die für mehrere Motorzylinder gemeinsame Rücklauf-Railchamber gefördert. Die Druckverhältnisse in der Vordruck-Railchamber und in der Rücklauf-Railchamber werden mit einfachen Mitteln konstant gehalten, so daß in den Schwungleitungen über den gesamten Drehzahlbereich optimale Strömungsbedingungen gewährleistet werden können. Auf dieser Grundlage wird bei Betätigung der Absperrventile in den jeweiligen Schwungleitungen der benötigte Druckstoß für das Kraftstoffeinspritzen über die mit der jeweiligen Schwungleitung verbundenen Einspritzdüsen erzeugt.Between the pre-pressure railchamber and return railchamber So-called flywheels with shut-off valves are provided, each Shut-off valve a swing line between the pre-pressure Railchamber and Return railchamber is used. Each shut-off valve is in the each swing line actuated at least one injector. The pressure surge occurring when a shut-off valve is closed is used for the Dosing of the fuel used through the respective injection nozzle. The When the shut-off valve is open, the fuel flowing back into the for several engine cylinders promoted common return railchamber. The pressure conditions in the pre-pressure railchamber and in the return railchamber are kept constant with simple means, so that in the swing lines over the entire speed range optimal Flow conditions can be guaranteed. On this The basis is when the shut-off valves are actuated in the respective The pressure surge required for fuel injection via the injection nozzles connected to the respective swing line generated.
In einer besonderen Ausführungsform ist das Verfahren dadurch gekennzeichnet, daß die Energie des in der Rücklauf-Railchamber gespeicherten Kraftstoffs für das Kraftstoffördersystem genutzt wird. Dies führt zu einer zusätzlichen günstigen Beeinflussung des Energieaufwandes für das Bereitstellen des benötigten Kraftstoffvordrucks in der Vordruck-Railchamber.In a special embodiment, the method is thereby characterized in that the energy of the in the return railchamber stored fuel is used for the fuel delivery system. This leads to an additional favorable influence on the Energy expenditure for providing the required fuel pressure in the pre-printed Railchamber.
Die Schwungleitung kann in Verbindung mit Vorrichtungen zur Schwingungstilgung betrieben werden. Dies verhindert unerwünschte Beeinträchtigungen des Kraftstoffördersystems.The flywheel can be used in conjunction with devices for Vibration damping are operated. This prevents unwanted ones Impairments to the fuel delivery system.
Es ist auch möglich, für die Herstellung des Vordrucks in der Vordruck-Railchamber mehrere Kraftstoffpumpen zu nutzen. Dabei kann die Anzahl der zu betreibenden Kraftstoffpumpen entsprechend der jeweiligen Motorlastanforderungen gewählt werden. It is also possible for the production of the form in the form Railchamber to use multiple fuel pumps. The number of the fuel pumps to be operated according to the respective Engine load requirements can be selected.
In einer weiteren Ausführungsform der Erfindung können Schwungleitung, Absperrventil, Schwingungstilger und Einspritzdüse in einer Hochdruckeinheit je Arbeitszylinder zusammengefaßt sein. Diese Hochdruckeinheit kann bedarfsweise mit einem Mantel gegenüber der Kraftmaschine thermisch isoliert betrieben und oder durch ein im Mantel integriertes Kühlmedium gekühlt werden.In a further embodiment of the invention, swing line, Shut-off valve, vibration damper and injector in one High pressure unit can be summarized per cylinder. This High pressure unit can be covered with a jacket if necessary Engine operated thermally insulated and or by a in the jacket integrated cooling medium can be cooled.
Weiterhin ist es möglich, die Absperrventile in den Schwungleitungen des Einspritzsystems für Mehrzylinder-Kraftmaschinen elektro-magnetisch zu betreiben.It is also possible to cut the shut-off valves in the swing lines of the Injection system for multi-cylinder engines electro-magnetically too operate.
Die technische Lösung ist aufgabengemäß auch durch eine Vorrichtung
gekennzeichnet, die aus Kraftstoffpumpen, Schwungleitungen mit
Absperrventilen und Rücklaufleitungen zum Kraftstoffvorratssystem
besteht. In dieser Vorrichtung ist zwischen zumindest einer
Kraftstoffpumpe und zumindest einer Schwungleitung eine für eine
Zylindergruppe oder für alle Zylinder der Mehrzylinder-Kraftmaschine
gemeinsame Vordruck-Railchamber angeordnet.
Zwischen der zumindest einen Schwungleitung und dem Kraftstoffvorratssystem
ist eine für eine Zylindergruppe oder für alle Zylinder der
Mehrzylinder-Kraftmaschine gemeinsame Rücklauf-Railchamber
angeordnet. Außerdem sind ein oder mehrere Druckbegrenzungsventile
zwischen Vordruck- und Rücklauf-Railchamber angeordnet.According to the task, the technical solution is also characterized by a device consisting of fuel pumps, flywheel lines with shut-off valves and return lines to the fuel supply system. In this device, a pre-pressure railchamber common to at least one fuel pump and at least one flywheel line is arranged for a cylinder group or for all cylinders of the multi-cylinder engine.
Arranged between the at least one flywheel line and the fuel supply system is a return railchamber common to a cylinder group or to all cylinders of the multi-cylinder engine. In addition, one or more pressure relief valves are arranged between the upstream and the return railchamber.
In einer besonderen Ausführungsform der Vorrichtung sind Schwungleitung, Absperrventil, Einspritzdüse und bedarfsweise Schwingungstilger in einem gemeinsamen Hochdruckmodul angeordnet.In a special embodiment of the device Flywheel line, shut-off valve, injection nozzle and if necessary Vibration absorber arranged in a common high pressure module.
In jedem Hochdruckmodul können zwischen Vordruck-Railchamber und Rücklauf-Railchamber eine oder mehrere Einspritzdüsen angeordnet sein. In each high pressure module you can choose between the pre-pressure Railchamber and Return railchamber one or more injection nozzles can be arranged.
Das Absperrventil und die Einspritzdüsen einer Hochdruckeinheit können konstruktiv in einem gemeinsamen Bauteil oder in mehreren durch Leitungen verbundenen Bauteilen angeordnet sein.The shut-off valve and the injection nozzles of a high-pressure unit can constructively in a common component or in several Lines connected components can be arranged.
Weiterhin ist eine Ausführungsform der Vorrichtung dadurch gekennzeichnet, daß an der Vordruck-Railchamber eine oder mehrere Kraftstoffpumpen angeordnet sind.Furthermore, an embodiment of the device is thereby characterized in that one or more on the pre-printed Railchamber Fuel pumps are arranged.
Ebenso ist es möglich, an jedem Arbeitszylinder ein oder mehrere Hochdruckmodule anzuordnen.It is also possible to have one or more on each cylinder To arrange high pressure modules.
In einer weiteren Ausführungsform der Vorrichtung ist vorgesehen, die für eine Zylindergruppe oder für alle Zylinder der Mehrzylinder-Kraftmaschine gemeinsame Vordruck-Railchamber und die für eine Zylindergruppe oder für alle Zylinder der Mehrzylinder-Kraftmaschine gemeinsame Rücklauf-Railchamber als zwei Kammern in einer gemeinsamen Baueinheit auszuführen. Dabei werden bedarfsweise bei der Ausführung von Vordruck- und Rücklauf-Railchamber als zwei Kammern einer gemeinsamen Railchamber in der Trennwand zwischen den Kammern eine oder mehrere das hysterese- und schwingungsfreie Konstanthalten des Vordrucks sichernde Druckbegrenzungsventile angeordnet.In a further embodiment of the device it is provided that for a cylinder group or for all cylinders of the multi-cylinder engine common pre-printed Railchamber and one for one Cylinder group or for all cylinders of the multi-cylinder engine common return railchamber as two chambers in one execute common structural unit. If necessary, the Execution of pre-pressure and return railchambers as two chambers a common railchamber in the partition between the Chamber one or more of the hysteresis and vibration free Pressure relief valves ensuring constant upstream pressure arranged.
Vorteilhaft ist die Anordnung des Hochdruckmoduls in einer thermisch isolierenden Hülse. Diese Hülse kann bei Erfordernis auch mit einem Kühlmedium betrieben werden und weist dazu einen Kühlmediumzulauf und einen Kühlmediumablauf auf.The arrangement of the high-pressure module in a thermal is advantageous insulating sleeve. This sleeve can also be used with a Coolant are operated and has a coolant inlet and a cooling medium drain.
Die Vorteile der Erfindung bestehen darin, daß mit ihr ein drehzahlunabhängiger Hochdruck verfügbar ist, der jedoch nicht ständig sondern nur in Verbindung mit einem unmittelbaren Kraftstoffeinspritzvorgang erzeugt wird. The advantages of the invention are that with it a speed-independent High pressure is available, but not always, but only in Generated connection with an immediate fuel injection process becomes.
Die Erfindung erlaubt es, die konstruktive Ausführung und Steuerung des
erfindungsgemäßen Kraftstoffeinspritzsystems mit den vorteilhaften
Eigenschaften eines modernen Common-Rails zu verbinden. Dabei werden
ein gemeinsamer Vordruck-Railchamber für alle oder für einzelne Gruppen
von Arbeitszylindern einer Mehrzylinder-Kraftmaschine sowie gesteuerte
Ventile in direktem funktionalem Zusammenhang mit Einspritzdüsen
betrieben. Ein entscheidender Vorteil der gefundenen Lösung besteht
darin, daß in der Vordruck-Railchamber nur ein Teil von etwa einem
Zehntel des benötigten Maximaldruckes ständig bereitzustellen ist und daß
der Maximaldruck lediglich als kurzzeitige Druckwelle unmittelbar vor
dem Kraftstoffdosieren über die Einspritzdüse mittels Steuerung des
jeweiligen Absperrventils vor einer einzelnen oder einer Gruppe von
Einspritzdüsen entsteht. Dazu wird das System aus einem Vordruckmodul,
der Druckversorgungsanlage, und aus Hochdruckmodulen
zusammengesetzt. Der benötigte Hochdruck beträgt im allgemeinem das 8-bis
10-fache des Vordruckes. Praktisch wird die erfindungsgemäße
technische Lösung dadurch umgesetzt, daß durch den von einer
Kraftstoffpumpe erzeugten Vordruck ein Druckspeicher geladen wird, der
störende Druckschwankungen bei der aus diesem Druckspeicher
erfolgenden Kraftstoffentnahme verhindert. Der Speicher ist als
gemeinsames Bauteil in Form einer Vordruck-Railchamber für mehrere
daran angeschlossene Hochdruckmodule ausgeführt. Durch definiertes
Öffnen der gesteuerten Absperrventile in jeweils einem Hochdruckmodul
wird eine Beschleunigung des in der zugehörigen Schwungleitung
befindlichen Kraftstoffs bewirkt, der in die Rücklauf-Railchamber
zurückgeführt wird. Von der oder den Kraftstoffpumpen wird der
Kraftstoff in erster Linie der jeweiligen Rücklauf-Railchamber unter
Nutzung des verfügbaren Restdrucks entnommen, wobei dem
Kraftstofftank lediglich die dem System über die Einspritzdüsen entzogene
Kraftstoffmenge entnommen wird.
Durch schlagartiges Schließen der Absperrventile im jeweiligen
Hochdruckmodul erfolgt eine Umwandlung des überwiegenden Teils der
kinetischen Energie des im Fluß befindlichen Kraftstoffs in Druckenergie. The invention makes it possible to combine the design and control of the fuel injection system according to the invention with the advantageous properties of a modern common rail. A common pre-pressure railchamber for all or for individual groups of working cylinders of a multi-cylinder engine as well as controlled valves are operated in a direct functional connection with injection nozzles. A decisive advantage of the solution found is that only a part of about a tenth of the required maximum pressure has to be constantly provided in the pre-pressure railchamber and that the maximum pressure is only a short-term pressure wave immediately before fuel metering via the injection nozzle by controlling the respective shut-off valve in front of one individual or a group of injection nozzles. For this purpose, the system is composed of a pre-pressure module, the pressure supply system, and high pressure modules. The high pressure required is generally 8 to 10 times the pre-pressure. In practice, the technical solution according to the invention is implemented in that a pressure accumulator is loaded by the admission pressure generated by a fuel pump, which prevents disruptive pressure fluctuations when the fuel is drawn from this pressure accumulator. The memory is designed as a common component in the form of a pre-pressure railchamber for several high-pressure modules connected to it. Defined opening of the controlled shut-off valves in one high-pressure module causes an acceleration of the fuel in the associated flywheel, which is returned to the return railchamber. The fuel is withdrawn from the fuel pump (s) primarily from the respective return railchamber using the available residual pressure, only the amount of fuel withdrawn from the system via the injection nozzles being withdrawn from the fuel tank.
The abrupt closing of the shut-off valves in the respective high-pressure module results in a conversion of the predominant part of the kinetic energy of the fuel in the flow into pressure energy.
Die bewirkte Druckerhöhung erreicht ein Vielfaches des statischen
Vordrucks im Vordruck-Railchamber und pflanzt sich in Form einer
Druckwelle in Richtung der einzelnen oder mehrerer an die
Schwungleitung des jeweiligen Hochdruckmoduls angeschlossenen
Einspritzdüsen fort, wo diese zur Kraftstoffeinspritzung genutzt werden
kann.
Bei Einsatz von Schwingungstilgern wird durch diese die erzeugte
Druckwelle etwa auf das Niveau des erzeugten Vordrucks abgebaut, um
unerwünschte und die Funktion des Einspritzsystems beeinträchtigende
Reflexionen zu vermeiden.The pressure increase brought about reaches a multiple of the static admission pressure in the admission pressure railchamber and propagates in the form of a pressure wave in the direction of the individual or more injection nozzles connected to the flywheel of the respective high pressure module, where it can be used for fuel injection.
When using vibration absorbers, the pressure wave generated is reduced to the level of the pre-pressure generated in order to avoid undesirable reflections and impair the function of the injection system.
Die Erfindung soll nachstehend an einem Ausführungsbeispiel näher
erläutert werden.
In der beiliegenden Zeichnung zeigt die
- Fig. 1:
- die schematische Darstellung eines Krafstoffeinspritzsystems für eine Vierzylinder-Kraftmaschine.
In the accompanying drawing, the
- Fig. 1:
- the schematic representation of a fuel injection system for a four-cylinder engine.
Für ein Kraftstoffeinspritzsystem für eine Mehrzylinder-Kraftmaschine
wird gemäß Fig. 1 der bereitzustellende Vordruck in Abhängigkeit vom
Bedarfskennfeld der betreffenden Arbeitsmaschine über eine
Kraftstoffpumpe 3 realisiert, wobei im Kraftstoffbehälter 1 zum Schutz vor
Verunreinigungen ein Vorfilter 2 installiert ist. Dieser Vordruck gelangt
über eine Zuleitung in eine für alle Zylinder der Arbeitsmaschine
gemeinsame Vordruck-Railchamber 4, die mit einem integrierten
zusätzlichen Kraftstoff-Feinfilter ausgestattet ist. For a fuel injection system for a
Die Vordruck-Railchamber 4 speist die Hochdruckmodule für die
einzelnen Arbeitszylinder, die aus Schwungleitung 11, Absperrventil 10,
Schwingungstilger 9, Aufnahme der Schwungleitung 12 und Einspritzdüse
13 bestehen. Der Vordruck-Railchamber 4 fungiert nicht nur als
Kraftstoffverteilsystem sondern durch seine Dimensionierung zugleich als
Druckschwankungen vermindernder Druckspeicher. Bei geöffneten
Absperrventilen 10 in den Hochdruckmodulen wird der unter Vordruck
stehende Kraftstoff in der Schwungleitung 11 beschleunigt und über eine
für alle Arbeitszylinder gemeinsame Rücklauf-Railchamber 6 zur
Kraftstoffpumpe 3 zurückgeführt. Die kinetische Energie des sich im Fluß
befindlichen Kraftstoffs wird durch schlagartiges Schließen des
elektromagnetisch betätigten Absperrventils 10 überwiegend in
Druckenergie umgewandelt, die sich in Form einer Druckwelle zur
Einspritzdüse 13 sowie zum Schwingungstilger 9 bis an das Ende der
Schwungleitung 11 fortsetzt. Durch den Schwingungstilger 9 wird der
Druck der Druckwelle zur Vermeidung von unerwünschten Reflexionen
zumindest auf das Niveau des Vordrucks gedämpft. Die in der Druckwelle
zu verzeichnende Druckhöhe beträgt durchschnittlich bzw. abhängig von
der Einspritzmenge etwa das 10-fache des eingestellten Vordrucks und
wird zur Kraftstoffdosierung in den jeweiligen Arbeitszylinder über die mit
der Schwungleitung 11 verbundene Einspritzdüse 13 genutzt. Zwischen
der Vordruck-Railchamber 4 und der Rücklauf-Railchamber 6 ist eine
Kurzschlußleitung angeordnet, die zum schwingungsannen Konstanthalten
des Vordrucks mit einem Druckbegrenzungsventils 5 ausgestattet ist. Der
in der Rücklauf-Railchamber 6 verfügbare Kraftstoffüberdruck wird
unmittelbar an der Kraftstoffpumpe 3 dem Vordrucksystem zugeführt. Um
das Hochdruckmodul ist zur Geräuschdämmung und zum Wärmeschutz
eine Isolierhülse 7 angeordnet, die über einen Kühlmediumzulauf 8a und
einen Kühlmediumablauf 8b mit Kühlflüssigkeit durchströmt wird. The
- 1 -1 -
- KraftstoffbehälterFuel tank
- 2 -2 -
- Vorfilterprefilter
- 3 -3 -
- KraftstoffpumpeFuel pump
- 4 -4 -
- Vordruck-RailchamberForm rail Chamber
- 5 -5 -
- DruckbegrenzungsventilPressure relief valve
- 6 -6 -
- Rücklauf-RailchamberReturn rail Chamber
- 7 -7 -
- Isolierhülseinsulating sleeve
- 8a -8a -
- Kühlmedium-ZulaufCooling medium inlet
- 8b -8b -
- Kühlmedium-AblaufCooling medium flow
- 9 -9 -
- Schwingungstilgervibration absorber
- 10 -10 -
- Absperrventilshut-off valve
- 11 -11 -
- Schwungleitungacceleration line
- 12 -12 -
- Aufnahme der SchwungleitungInclusion of the swing line
- 13 -13 -
- Einspritzdüseinjection
Claims (19)
- A method of injecting fuel in multi-cylinder engines by generating a fuel pre-pressure for the fuel hauling into an acceleration pipe for the use of the water hammer principle by shutoff valves within acceleration pipes whereby any injector provided in relationship with a shutoff valve receives a high pressure wave which is generated by the water hammer principle, whereby the not injected fuel is fed back through the opened shutoff valve to the input of the pre-pressure pump,
wherein the pre-pressure fuel pump (3) feeds the pre-pressure into a pre-pressure common rail (4) which is common to several engine cylinders, whereby the pre-pressure is only a fraction of the required injection pressure,
wherein the fuel is fed back, when the pre-pressure is exceeded, from the pre-pressure common rail (4) via pressure-limiting valves (5) into a return common rail (6) which is common to several engine cylinders,
wherein to any shutoff valve (10) corresponds an acceleration pipe (11) which is connected between the pre-pressure common rail (4) and the return common rail (6),
wherein for any shutoff valve (10) in the corresponding acceleration pipe (11) is operated at least one injector (13),
wherein by shutting off a shutoff valve (10) the fuel high pressure wave generated by water hammer effect is captured by a corresponding injector (13) for injecting the fuel,
wherein the fuel which is fed back through a shut off valve (10) during their opening feeds into the return common rail (6) which is common for several engine cylinders - The method according to claim 1, wherein the energy of the fuel stored in the return common rail (6) is used to convey the fuel.
- The method according to claims 1 and 2, wherein the acceleration pipe (11) is operated in connection with wave dampers.
- The method according to claims 1 and 3, wherein several fuel pumps (3) are used for producing the pre-pressure in the pre-pressure common rail (4).
- The method according to claim 4, wherein the number to fuel pumps (3) to be operated is selected in accordance with the engine load requirements.
- The method according to claims 1 to 5, wherein acceleration pipe (11), shutoff valve (10), wave damper (9) and injector (13) are combined in one high-pressure unit.
- The method according to claim 6, wherein the high-pressure unit is thermally isolated versus the engine via a thermal isolator or is cooled by a cooling medium.
- The method according to claims 1 to 7, wherein the shutoff valve (10) is operated electromagnetically.
- The method according to claims 1 to 7, wherein the shutoff valve (10) is operated mechanically.
- Device for the implementation of the said method according to claims 1 to 9, consisting of fuel pumps, acceleration pipe with shutoff valve and return pipe to the fuel storage system,
wherein a pre-pressure common rail (4) for a group of engine cylinders or for all engine cylinders is provided between fuel pumps (3) and an acceleration pipes (11),
wherein a return common rail (6) for a group of engine cylinders or for all engine cylinders is provided between acceleration pipes (11) and the fuel storage system,
wherein, one or more pressure limiting valves (5) are provided between the pre-pressure common rail (4) and the return common rail (6). - Device according to claim 10, wherein acceleration pipe (11), shutoff valve (10), wave damper (9) and injector (13) are combined in one high-pressure unit.
- Device according to claims 10 and 11, wherein in every high-pressure unit between both pre-pressure common rail (4) and return common rail (6) are provided one or more injectors.
- Device according to claims 10 to 12, wherein the shutoff valve (10) and the injectors (13) of a high-pressure unit are combined in one common part or consist on several parts which are connected by pipes.
- Device according to the claims 10 to 13, wherein one or more fuel pumps (3) are connected to a pre-pressure common rail (4).
- Device according to the claims 10 to 14, wherein one or more high-pressure units are provided for one engine cylinder.
- Device according to claims 10 to 15, wherein the pre-pressure common rail (4) for a group of engine cylinders for all engine cylinders and the return common rail (6) for a group of engine cylinders or for all engine cylinders are arranged as two chambers in a common part.
- Device according to claim 16, wherein for the arrangement of pre-pressure common rail (4) and return common rail (6) as two chambers in a common part, one or more pressure limitation valves (5) for the maintenance of constant pre-pressure, free of oscillations and hysteresis are provided in the separation wall between both chambers.
- Device according to claim 11, wherein the high-pressure unit is wrapped in a thermal isolator (7).
- Device according to claims 11 and 18, wherein the high-pressure unit is wrapped in a socket with cooling circuit with coolant intake (8a) and coolant outlet (8b).
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19710128 | 1997-03-12 | ||
DE19710128 | 1997-03-12 | ||
DE19715355A DE19715355A1 (en) | 1997-03-12 | 1997-04-12 | Method for fuel injection in multi-cylinder engines and device for carrying out the method |
DE19715355 | 1997-04-12 | ||
PCT/DE1998/000716 WO1998040658A2 (en) | 1997-03-12 | 1998-03-09 | Method for fuel injection in multicylinder engines and device for the implementation of said method |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0898678A2 EP0898678A2 (en) | 1999-03-03 |
EP0898678B1 true EP0898678B1 (en) | 2003-01-15 |
Family
ID=26034760
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98923988A Expired - Lifetime EP0898678B1 (en) | 1997-03-12 | 1998-03-09 | Method for fuel injection in multicylinder engines and device for the implementation of said method |
Country Status (6)
Country | Link |
---|---|
US (1) | US6189508B1 (en) |
EP (1) | EP0898678B1 (en) |
JP (1) | JP2000516684A (en) |
AT (1) | ATE231227T1 (en) |
DE (1) | DE59806913D1 (en) |
WO (1) | WO1998040658A2 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6269804B1 (en) * | 2000-04-26 | 2001-08-07 | Delphi Technologies, Inc. | Coaxial liquid cooled fuel rail assembly |
US6591812B2 (en) * | 2000-12-14 | 2003-07-15 | Siemens Diesel Systems Technology | Rail connection with rate shaping behavior for a hydraulically actuated fuel injector |
DE102004055266A1 (en) * | 2004-11-17 | 2006-05-18 | Robert Bosch Gmbh | Fuel injection system with multiple accumulators |
JP2016114012A (en) * | 2014-12-17 | 2016-06-23 | 愛三工業株式会社 | Fuel supply unit |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1992014925A2 (en) * | 1991-02-26 | 1992-09-03 | Ficht Gmbh | Fuel injection device for internal combustion engines |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1046949B (en) * | 1954-02-01 | 1958-12-18 | Modag Motorenfabrik Darmstadt | Fuel injection system with pump and cooled injection valve |
US3945353A (en) * | 1974-11-29 | 1976-03-23 | Allis-Chalmers Corporation | Two phase nozzle cooling system |
US4539959A (en) * | 1984-02-27 | 1985-09-10 | General Motors Corporation | Fuel injection system with fuel flow limiting valve assembly |
US4860700A (en) * | 1988-10-20 | 1989-08-29 | General Motors Corporation | Tangent flow cylinder head |
US5035221A (en) * | 1989-01-11 | 1991-07-30 | Martin Tiby M | High pressure electronic common-rail fuel injection system for diesel engines |
JPH04113778U (en) * | 1991-03-22 | 1992-10-06 | 本田技研工業株式会社 | vehicle fuel cooling system |
US5423303A (en) * | 1993-05-28 | 1995-06-13 | Bennett; David E. | Fuel rail for internal combustion engine |
JP3293269B2 (en) * | 1993-10-06 | 2002-06-17 | 株式会社デンソー | Pressure supply device |
DE4344777C2 (en) * | 1993-12-28 | 1998-06-04 | Technoflow Tube Systems Gmbh | Fuel supply system for a motor vehicle with a gasoline engine |
DE4445586A1 (en) * | 1994-12-20 | 1996-06-27 | Bosch Gmbh Robert | Method for reducing fuel pressure in a fuel injector |
EP0741244B1 (en) * | 1995-05-03 | 1999-07-07 | DaimlerChrysler AG | Injection nozzle |
DE69619949T2 (en) * | 1995-12-19 | 2002-11-14 | Nippon Soken | Reservoir fuel injection device |
JP3228497B2 (en) * | 1996-03-27 | 2001-11-12 | 株式会社豊田中央研究所 | Fuel injection valve deposit reduction method and deposit reduction type fuel injection valve |
JPH09324712A (en) * | 1996-06-07 | 1997-12-16 | Sanshin Ind Co Ltd | Electronically controlled fuel supplier for outboard motor |
GB9614822D0 (en) * | 1996-07-13 | 1996-09-04 | Lucas Ind Plc | Injector |
GB9616521D0 (en) * | 1996-08-06 | 1996-09-25 | Lucas Ind Plc | Injector |
DE19639149C1 (en) * | 1996-09-24 | 1998-02-19 | Daimler Benz Ag | Fuel injection nozzle with nozzle needle axially movable in nozzle body |
US5852997A (en) * | 1997-05-20 | 1998-12-29 | Stanadyne Automotive Corp. | Common rail injector |
US5887555A (en) * | 1998-06-23 | 1999-03-30 | Thermo Power Corporation | Cooling device for a fuel pump and fuel in a marine combustion engine |
-
1998
- 1998-03-09 DE DE59806913T patent/DE59806913D1/en not_active Expired - Lifetime
- 1998-03-09 EP EP98923988A patent/EP0898678B1/en not_active Expired - Lifetime
- 1998-03-09 US US09/180,649 patent/US6189508B1/en not_active Expired - Fee Related
- 1998-03-09 AT AT98923988T patent/ATE231227T1/en not_active IP Right Cessation
- 1998-03-09 JP JP10539087A patent/JP2000516684A/en active Pending
- 1998-03-09 WO PCT/DE1998/000716 patent/WO1998040658A2/en active IP Right Grant
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1992014925A2 (en) * | 1991-02-26 | 1992-09-03 | Ficht Gmbh | Fuel injection device for internal combustion engines |
Also Published As
Publication number | Publication date |
---|---|
US6189508B1 (en) | 2001-02-20 |
ATE231227T1 (en) | 2003-02-15 |
EP0898678A2 (en) | 1999-03-03 |
JP2000516684A (en) | 2000-12-12 |
WO1998040658A3 (en) | 1999-07-08 |
DE59806913D1 (en) | 2003-02-20 |
WO1998040658A2 (en) | 1998-09-17 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2016177554A1 (en) | Device and method for injection of water for an internal combustion engine | |
DE10065103C1 (en) | Pressure-controlled fuel injection device has pressure cavity connected by line containing valve directly to pressure storage cavity | |
EP0966605A1 (en) | Fuel injection device for internal combustion engines | |
DE3907972A1 (en) | FUEL INJECTION SYSTEM FOR INTERNAL COMBUSTION ENGINES | |
DE3141154A1 (en) | FUEL INJECTION SYSTEM | |
WO2018233992A1 (en) | Water injection device of an internal combustion engine | |
DE2365106A1 (en) | FUEL INJECTION SYSTEM FOR COMBUSTION ENGINES | |
EP1123463B1 (en) | Fuel injection system for an internal combustion engine | |
DE112007000797T5 (en) | Common fuel system for engine and exhaust gas treatment | |
EP0925436B1 (en) | DRIVE ARRANGEMENT AND METHOD OF REDUCING THE AMOUNT OF NOx IN THE EXHAUST GASES FROM AN INTERNAL COMBUSTION ENGINE | |
EP0898678B1 (en) | Method for fuel injection in multicylinder engines and device for the implementation of said method | |
DE102008007349A1 (en) | Compact injection device with reduced steam bubble inclination | |
DE2424800A1 (en) | INJECTION UNIT FOR INJECTING AN ADDITIONAL LOW AMOUNT OF FUEL INTO AN EXTERNAL IGNITION ENGINE, WORKING ON THE STRATIFICATION PRINCIPLE | |
DE19823639A1 (en) | Fuel supply system of an internal combustion engine | |
DE4016055A1 (en) | FUEL SUPPLY SYSTEM FOR AN INTERNAL COMBUSTION ENGINE | |
DE102016203027A1 (en) | Internal combustion engine | |
WO2012089371A1 (en) | Injection pump for a fuel injection system | |
WO2002055868A1 (en) | Common rail unit | |
DE19715355A1 (en) | Method for fuel injection in multi-cylinder engines and device for carrying out the method | |
DE10057683B4 (en) | Fuel injection system | |
DE2713831A1 (en) | IC engine with steam injection - has vaporiser to produce steam pressure above that of combustion chamber pressure | |
DE102008038448B4 (en) | Apparatus and method for introducing fuel into an exhaust system | |
DE3630439A1 (en) | DOUBLE INJECTION METHOD FOR SELF-IGNITIONING INTERNAL COMBUSTION ENGINES | |
DE10004617C2 (en) | Common rail injection system with control valves integrated into the rail | |
DE636045C (en) | Device for injecting water into the exhaust gases of an internal combustion engine in order to generate a gas-steam mixture for operating an exhaust gas turbine |
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: A2 Designated state(s): AT DE DK ES FI FR GB IT SE |
|
17P | Request for examination filed |
Effective date: 19991217 |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
17Q | First examination report despatched |
Effective date: 20020417 |
|
PUAK | Availability of information related to the publication of the international search report |
Free format text: ORIGINAL CODE: 0009015 |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AT DE DK ES FI FR GB IT SE |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT DE DK ES FI FR GB IT SE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20030115 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20030115 |
|
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: 59806913 Country of ref document: DE Date of ref document: 20030220 Kind code of ref document: P |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20030415 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20030415 |
|
GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) | ||
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20030730 |
|
ET | Fr: translation filed | ||
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: 20031016 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20100325 Year of fee payment: 13 Ref country code: FR Payment date: 20100331 Year of fee payment: 13 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20100324 Year of fee payment: 13 Ref country code: AT Payment date: 20100322 Year of fee payment: 13 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20110309 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20110309 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20111130 |
|
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: 20110331 |
|
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 Effective date: 20110309 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20120228 Year of fee payment: 15 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20110309 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 59806913 Country of ref document: DE Effective date: 20131001 |
|
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: 20131001 |