EP1298316B1 - Fuel injection system - Google Patents

Fuel injection system Download PDF

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Publication number
EP1298316B1
EP1298316B1 EP02021072A EP02021072A EP1298316B1 EP 1298316 B1 EP1298316 B1 EP 1298316B1 EP 02021072 A EP02021072 A EP 02021072A EP 02021072 A EP02021072 A EP 02021072A EP 1298316 B1 EP1298316 B1 EP 1298316B1
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EP
European Patent Office
Prior art keywords
pump
internal combustion
combustion engine
pressure
injection
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Revoked
Application number
EP02021072A
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German (de)
French (fr)
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EP1298316A2 (en
EP1298316A3 (en
Inventor
Kai-Uwe Dr. Münch
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Deutz AG
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Deutz AG
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Publication of EP1298316A2 publication Critical patent/EP1298316A2/en
Publication of EP1298316A3 publication Critical patent/EP1298316A3/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding 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
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • 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
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • F02M39/02—Arrangements of fuel-injection apparatus to facilitate the driving of pumps; Arrangements of fuel-injection pumps; Pump drives
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/0265—Pumps feeding common rails
    • F02M63/027—More than one high pressure pump feeding a single common rail
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/06—Fuel or fuel supply system parameters
    • F02D2200/0602—Fuel pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/3809—Common rail control systems

Definitions

  • the invention relates to an internal combustion engine with a fuel injection system having an uncontrolled high pressure pump, in the fuel supply line a fore pump and a control device are turned on and wherein the high pressure pump via a high pressure line to a high pressure storage device and this via an injection line and a control valve with an injection valve are connected.
  • the illustrated fuel injection pump assembly includes two high pressure pumps that fill independent high pressure accumulator devices with fuel.
  • the two high-pressure pumps each have a housing with an associated camshaft for actuating the bucket tappets.
  • This housing must be attached to a suitable point of the internal combustion engine and the camshaft be driven in a suitable manner.
  • a toothed belt with corresponding gears or meshing gears when driving the camshaft of the crankshaft of the internal combustion engine is required.
  • Another internal combustion engine with a fuel injection device for a self-igniting internal combustion engine is known from DE 195 08 445 A1 known.
  • This internal combustion engine has a high-pressure pump from which fuel is conveyed into a supply reservoir.
  • Fuel quantity the high pressure pump on a pump piston with a bevel for quantity control.
  • This pump piston is rotated by a control rod, wherein the adjustment of the control rod is effected by an adjusting device which evaluates the pressure prevailing in the supply reservoir pressure.
  • the invention has for its object to provide an air-compressing internal combustion engine with a fuel injection system designed as a common rail system, in particular with regard to the high-pressure pump and the drive is simple and with a conventional system has the same parts.
  • the high-pressure pump is a single pump element which has a pump housing which can be inserted into the crankcase of the internal combustion engine and the single pump element has an injection cam of a gas exchange camshaft having rolling roller tappet, which is connected to the pump plunger.
  • the control device is an electromagnetically actuated hydraulic valve.
  • This hydraulic valve or the hydraulic valve having a pressure control valve and a zero-delivery throttle is switched on at a suitable point in the supply line, which in a further embodiment is integrated directly in the crankcase or adapted to the crankcase.
  • the hydraulic valve preferably outside of the crankcase in the area is arranged adjacent to a single pump element, controls the fuel flow to the single pump element.
  • a comprehensive control or regulation of the fuel quantity to be fed into the high-pressure storage device is possible with a simple construction of the single pump element. It can also be provided two single pump elements, in which case the hydraulic valve is arranged between the individual pump elements.
  • the control device in addition to the electromagnetically operated hydraulic valve on a pressure control valve and a zero feed throttle.
  • excess fuel is again discharged into the fuel tank, in particular in the case of a constant delivery of fuel through a backing pump.
  • the backing pump is advantageously adjusted so that it delivers a quantity of fuel that is greater in each case than the maximum amount of fuel injected by the injection valves into the combustion chambers.
  • the delivery pressure in the low-pressure system is for example set to a value between 5 and 10 bar, preferably 7 bar.
  • the supply line between the hydraulic valve and the individual pump elements is relieved via the zero-feed throttle and discharged through the hydraulic valve leakage fuel flowing through.
  • the amount of fuel flowing out via the zero-delivery throttle is so small that there is no impairment of the fuel supply to the individual pump elements.
  • the hydraulic valve is in a further embodiment of the invention, a pulse width modulating hydraulic valve or a proportional horrndes hydraulic valve. Both variants allow accurate and reliable quantity control of the fuel to be supplied to the single pump elements, thus ensuring overall reliable and accurate fuel supply and pressure adjustment in the high pressure storage device.
  • Fig. 1 shows a schematically illustrated crankcase 3 of a self-igniting internal combustion engine 1 with a total of six cylinders.
  • the internal combustion engine has a crankshaft 2 mounted in the crankcase 3, which drives the camshaft 4 via a single meshing engagement, that is to say via a camshaft gearwheel 5b meshing with a crankshaft gearwheel 5a.
  • the camshaft 4 has each cylinder associated bearing points 8a, 8b, between which gas exchange cam 6a and 6b and an injection cam 7 are arranged.
  • the injection cam 7 can also be arranged between the gas exchange cam 6a and the gas exchange cam 6b.
  • the bearings 8a, 8b, the gas exchange cams 6a, 6b and the injection cam 7 go directly, so without punctures, into each other. As a result, a very stiff camshaft 4 is formed.
  • the crankcase 3 are recessed in accordance with the number of cylinders close to the cylinder head, into which a corresponding number of high-pressure pumps can be used.
  • these high-pressure pumps are connected via short injection lines directly to the injection valves.
  • the high-pressure pump is designed as a single pump element 10 that has a pump housing 19 which can be directly inserted into the crankcase 3.
  • a Zylinderplunger 13 is guided without control edge, the Zylinderplunger 13 cooperates with a roller tappet 9, which rolls on the injection cam 7.
  • a supply line 14 is further admitted for fuel, which is connected to the fuel supply to the injection pump element 10.
  • a second or further single pump element may be present if required by the corresponding design of the injection system for filling the high-pressure storage device 11. Otherwise, the recesses in the crankcase 3 for receiving the (conventional) high-pressure pumps with closure lids 18 are closed.
  • an electromagnetically actuated hydraulic valve 16 is switched on, which controls the fuel flow to the single pump element 10.
  • the single pump element 10 is connected via a high-pressure line 12 to the high-pressure accumulator device 11 and fills this quantity regulated by the hydraulic valve 16 with fuel.
  • injection pipes 17 which are connected to the injection valves 15 are exhausted.
  • control valves are installed, which control the amount of fuel delivered by the respective injection valve 15 into the combustion chamber.
  • Fig. 2 the fuel injection system is shown without reference to the internal combustion engine.
  • the fuel is supplied from a fore-pump 20 from a fuel tank 21 via a filter device 22 to the hydraulic valve 16.
  • the hydraulic valve 16 is connected via a supply line 14 with one or more individual pump elements 10, wherein the individual pump elements 10 via check valves 23 promote the fuel via high pressure lines 12 into the high pressure storage device 11.
  • the fuel is supplied to the injection valves 15 via injection lines 17.
  • the entire system, so in particular the hydraulic valve 16 and the control valves of the injectors 15 is controlled, the necessary parameters for controlling, for example, the pressure in the high-pressure accumulator device 11 are supplied as measured data to the control unit 24.
  • the detail enlargement A of the hydraulic valve 16 shows the preferred construction of this hydraulic valve 16, which additionally has a pressure regulating valve 25 and a zero feed throttle 26. In this case, the discharged from the pressure control valve 25 and the zero feed throttle 26 amount of fuel is returned to the fuel tank 26.

Abstract

The IC engine has the fuel supplied to the common-rail fuel injection system via an unregulated high pressure pump with a control device (24) inserted in the fuel feed line. The high pressure pump has a single pump element (10) within a pump housing incorporated in the crank housing of the engine, with an operating rod having a roller cooperating with an injection cam of a valve camshaft (4) and coupled to a pump plunger.

Description

Die Erfindung betrifft eine Brennkraftmaschine mit einem Kraftstoff-Einspritzsystem, das eine ungeregelte Hochdruckpumpe aufweist, in deren Kraftstoff-Zuführleitung eine Vorpumpe und eine Steuervorrichtung eingeschaltet sind und wobei die Hochdruckpumpe über eine Hochdruckleitung mit einer Hochdruckspeichervorrichtung und diese über eine Einspritzleitung sowie ein Steuerventil mit einem Einspritzventil verbunden sind.The invention relates to an internal combustion engine with a fuel injection system having an uncontrolled high pressure pump, in the fuel supply line a fore pump and a control device are turned on and wherein the high pressure pump via a high pressure line to a high pressure storage device and this via an injection line and a control valve with an injection valve are connected.

Eine derartige Brennkraftmaschine ist aus der DE 42 33 273 A1 bekannt. Die dargestellte Kraftstoff-Einspritzpumpenanordnung weist zwei Hochdruckpumpen auf, die unabhängige Hochdruckspeichervorrichtungen mit Kraftstoff befüllen. Die beiden Hochdruckpumpen weisen jeweils ein Gehäuse mit einer zugeordneten Nockenwelle zur Betätigung der Tassenstößel auf. Dieses Gehäuse muss an geeigneter Stelle der Brennkraftmaschine befestigt und die Nockenwelle in geeigneter Weise angetrieben werden. Hierzu sind beispielsweise ein Zahnriemen mit entsprechenden Zahnrädern oder ineinandergreifende Zahnräder bei Antrieb der Nockenwelle von der Kurbelwelle der Brennkraftmaschine erforderlich.Such an internal combustion engine is from the DE 42 33 273 A1 known. The illustrated fuel injection pump assembly includes two high pressure pumps that fill independent high pressure accumulator devices with fuel. The two high-pressure pumps each have a housing with an associated camshaft for actuating the bucket tappets. This housing must be attached to a suitable point of the internal combustion engine and the camshaft be driven in a suitable manner. For this purpose, for example, a toothed belt with corresponding gears or meshing gears when driving the camshaft of the crankshaft of the internal combustion engine is required.

Eine weitere Brennkraftmaschine mit einer Kraftstoffeinspritzvorrichtung für eine selbstzündende Brennkraftmaschine ist aus der DE 195 08 445 A1 bekannt. Diese Brennkraftmaschine weist eine Hochdruckpumpe auf, von der Kraftstoff in einen Versorgungsspeicher gefördert wird. Zur Steuerung der in den Versorgungsspeicher geförderten Kraftstoffmenge weist die Hochdruckpumpe einen Pumpenkolben mit einer Schrägkante zur Mengensteuerung auf. Dieser Pumpenkolben wird von einer Regelstange verdreht, wobei die Verstellung der Regelstange von einer Stelleinrichtung erfolgt, die den in dem Versorgungsspeicher herrschenden Druck auswertet.Another internal combustion engine with a fuel injection device for a self-igniting internal combustion engine is known from DE 195 08 445 A1 known. This internal combustion engine has a high-pressure pump from which fuel is conveyed into a supply reservoir. To control the pumped into the supply memory Fuel quantity, the high pressure pump on a pump piston with a bevel for quantity control. This pump piston is rotated by a control rod, wherein the adjustment of the control rod is effected by an adjusting device which evaluates the pressure prevailing in the supply reservoir pressure.

Der Erfindung liegt die Aufgabe zugrunde, eine luftverdichtende Brennkraftmaschine mit einem Kraftstoff-Einspritzsystem bereitzustellen, das als Common-Rail-System ausgelegt insbesondere hinsichtlich der Hochdruckpumpe und deren Antrieb einfach aufgebaut ist und mit einem herkömmlichen System Gleichteile aufweist.The invention has for its object to provide an air-compressing internal combustion engine with a fuel injection system designed as a common rail system, in particular with regard to the high-pressure pump and the drive is simple and with a conventional system has the same parts.

Diese Aufgabe wird dadurch gelöst, dass strömungsmäßig hinter der Vorpumpe und vor der Steuervorrichtung eine Filtervorrichtung in die Zuführleitung eingeschaltet ist, dass die Hochdruckpumpe ein Einzelpumpenelement ist, das ein in das Kurbelgehäuse der Brennkraftmaschine einsetzbares Pumpengehäuse aufweist und dass das Einzelpumpenelement einen auf einem Einspritznocken einer Gaswechselnockenwelle abrollenden Rollenstößel aufweist, der mit dem Pumpenplunger verbunden ist. Ein Vorteil dieser Ausbildung ist die Vereinheitlichung wesentlicher Einspritzkomponenten zumindest für eine Baureihe einer derart ausgestalteten Brennkraftmaschine. Hierbei sind das Kurbelgehäuse der Brennkraftmaschine, die Gaswechselnockenwelle und auch wesentliche Teile des Einspritzpumpenelementes, insbesondere das Pumpengehäuse und der Rollenstößel gegenüber einer mit einem herkömmlichen Einspitzsystem ausgestatteten Brennkraftmaschine unverändert ausgebildet. Lediglich der Pumpenplunger, der bei dem herkömmlichen Einspritzsystem mit einer Steuerkante versehen ist, ist bei der erfindungsgemäßen Ausgestaltung in bevorzugter Ausführung als Zylinderplunger ohne Steuerkante ausgebildet. Somit wird bei beiden Einspritzsystemvarianten eine große Zahl von Gleichteilen, die gegebenenfalls auch bei mehreren Baureihen von Brennkraftmaschinen zur Anwendung kommen können, verwendet und die Grundkonzeption der Brennkraftmaschine mit Einbau und Antrieb des Einspritzsystems ist unverändert. Im Ergebnis wird eine kostengünstige, technisch zuverlässige Lösung durch hohe Stückzahlen einheitlicher Komponenten erreicht. Dabei weist dieses Konzept ein hohes Zukunftspotential auf, da eine Ausbaufähigkeit für steigende Anforderungen gegeben ist.This object is achieved in that, downstream of the backing pump and upstream of the control device, a filter device is switched into the supply line, that the high-pressure pump is a single pump element which has a pump housing which can be inserted into the crankcase of the internal combustion engine and the single pump element has an injection cam of a gas exchange camshaft having rolling roller tappet, which is connected to the pump plunger. An advantage of this design is the standardization of essential injection components, at least for a series of such a designed internal combustion engine. In this case, the crankcase of the internal combustion engine, the gas exchange camshaft and also essential parts of the injection pump element, in particular the pump housing and the roller tappet with respect to a equipped with a conventional Einspitzsystem internal combustion engine are unchanged. Only the pump plunger, which is provided with a control edge in the conventional injection system, is formed in the embodiment according to the invention in a preferred embodiment as Zylinderplunger without control edge. Thus, in both injection system variants, a large number of identical parts, which optionally also come with several series of internal combustion engines for use can, used and the basic concept of the internal combustion engine with installation and drive of the injection system is unchanged. As a result, a cost-effective, technically reliable solution is achieved by high volumes of uniform components. This concept has a high potential for the future, since it can be upgraded to meet increasing requirements.

In weiterer Ausgestaltung der Erfindung ist die Steuervorrichtung ein elektromagnetisch betätigtes Hydraulikventil. Dieses Hydraulikventil beziehungsweise das ein Druckregelventil und eine Nullförderdrossel aufweisende Hydraulikventil ist an geeigneter Stelle in die Zuführleitung, die in weiterer Ausgestaltung direkt in das Kurbelgehäuse integriert oder an das Kurbelgehäuse adaptiert ist, eingeschaltet. Das Hydraulikventil, das bevorzugt außerhalb des Kurbelgehäuses im Bereich neben einem Einzelpumpenelement angeordnet ist, steuert den Kraftstoffzufluss zu dem Einzelpumpenelement. Somit ist eine umfassende Steuerung bzw. Regelung der in die Hochdruckspeichervorrichtung einzuspeisenden Kraftstoffmenge bei einem einfachen Aufbau des Einzelpumpenelementes möglich. Es können auch zwei Einzelpumpenelemente vorgesehen sein, wobei dann das Hydraulikventil zwischen den Einzelpumpenelementen angeordnet ist.In a further embodiment of the invention, the control device is an electromagnetically actuated hydraulic valve. This hydraulic valve or the hydraulic valve having a pressure control valve and a zero-delivery throttle is switched on at a suitable point in the supply line, which in a further embodiment is integrated directly in the crankcase or adapted to the crankcase. The hydraulic valve, preferably outside of the crankcase in the area is arranged adjacent to a single pump element, controls the fuel flow to the single pump element. Thus, a comprehensive control or regulation of the fuel quantity to be fed into the high-pressure storage device is possible with a simple construction of the single pump element. It can also be provided two single pump elements, in which case the hydraulic valve is arranged between the individual pump elements.

In weiterer Ausgestaltung der Erfindung weist die Steuervorrichtung neben dem elektromagnetisch betätigten Hydraulikventil ein Druckregelventil und eine Nullförderdrossel auf. Über das Druckregelventil wird insbesondere bei einer konstanten Kraftstoffförderung durch eine Vorpumpe überschüssig geförderter Kraftstoff wieder in den Kraftstofftank abgeführt. Dabei ist vorteilhaft die Vorpumpe so eingestellt, dass diese eine Kraftstoffmenge fördert, die in jedem Falle größer ist als die von den Einspritzventilen maximal in die Brennräume eingespritzte Kraftstoffmenge. Der Förderdruck in dem Niederdrucksystem ist beispielsweise auf einen Wert zwischen 5 und 10 bar, vorzugsweise 7 bar, eingestellt. Über die Nullförderdrossel wird die Zuführleitung zwischen dem Hydraulikventil und den Einzelpumpenelementen entlastet und durch das Hydraulkventil hindurchströmender Leckagekraftstoff abgeführt. Dabei ist die über die Nullförderdrossel abströmende Kraftstoffmenge aber so gering, dass eine Beeinträchtigung der Kraftstoffzufuhr zu den Einzelpumpenelementen nicht gegeben ist.In a further embodiment of the invention, the control device in addition to the electromagnetically operated hydraulic valve on a pressure control valve and a zero feed throttle. By means of the pressure regulating valve, excess fuel is again discharged into the fuel tank, in particular in the case of a constant delivery of fuel through a backing pump. In this case, the backing pump is advantageously adjusted so that it delivers a quantity of fuel that is greater in each case than the maximum amount of fuel injected by the injection valves into the combustion chambers. The delivery pressure in the low-pressure system is for example set to a value between 5 and 10 bar, preferably 7 bar. The supply line between the hydraulic valve and the individual pump elements is relieved via the zero-feed throttle and discharged through the hydraulic valve leakage fuel flowing through. However, the amount of fuel flowing out via the zero-delivery throttle is so small that there is no impairment of the fuel supply to the individual pump elements.

Das Hydraulikventil ist in weiterer Ausgestaltung der Erfindung ein pulsweitenmodulierendes Hydraulikventil oder ein proportionalsteuerndes Hydraulikventil. Beide Varianten ermöglichen eine genaue und zuverlässige Mengensteuerung des den Einzelpumpenelementen zuzuführenden Kraftstoffs, sodass insgesamt eine zuverlässige und genaue Kraftstoffversorgung und Druckeinstellung in der Hochdruckspeichervorrichtung sichergestellt ist.The hydraulic valve is in a further embodiment of the invention, a pulse width modulating hydraulic valve or a proportionalsteuerndes hydraulic valve. Both variants allow accurate and reliable quantity control of the fuel to be supplied to the single pump elements, thus ensuring overall reliable and accurate fuel supply and pressure adjustment in the high pressure storage device.

Dabei ist in weiterer Ausgestaltung vorgesehen, in die Einspritzleitung und/oder das Einspritzventil einen Druckverstärker einzuschalten. Mit diesem Druckverstärker wird der an der Düsennadel des Einspritzventils anstehende Kraftstoffdruck weiter erhöht. Damit sind weitere Verringerungen der Abgasemissionen möglich und es können auch zukünftige Generationen eines solchen Einspritzsystems mit diesem Konzept bedient werden.It is provided in a further embodiment, turn on a pressure booster in the injection line and / or the injection valve. With this pressure amplifier, the pending on the nozzle needle of the injector fuel pressure is further increased. Thus, further reductions in exhaust emissions are possible and future generations of such an injection system can be served with this concept.

Weitere vorteilhafte Ausgestaltungen der Erfindung sind der Beschreibung zu entnehmen, in der ein in den Figuren dargestelltes Ausführungsbeispiel der Erfindung näher beschrieben ist.Further advantageous embodiments of the invention are described in the description, in which an illustrated in the figures embodiment of the invention is described in detail.

Es zeigen:

Fig. 1:
das an die Brennkraftmaschine adaptierte Einspritzsystem und
Fig. 2:
ein Schaltschema des Einspritzsystems.
Show it:
Fig. 1:
the adapted to the internal combustion engine injection system and
Fig. 2:
a schematic diagram of the injection system.

Fig. 1 zeigt ein schematisch dargestelltes Kurbelgehäuse 3 einer selbstzündenden Brennkraftmaschine 1 mit insgesamt sechs Zylindern. Die Brennkraftmaschine weist 1 eine in dem Kurbelgehäuse 3 gelagerte Kurbelwelle 2 auf, die über einen einzigen Zahneingriff, also über ein mit einem Kurbelwellenzahnrad 5a kämmenden Nockenwellenzahnrad 5b die Nockenwelle 4 antreibt. Die Nockenwelle 4 weist jedem Zylinder zugeordnete Lagerstellen 8a, 8b auf, zwischen denen Gaswechselnocken 6a und 6b sowie ein Einspritznocken 7 angeordnet sind. Der Einspritznocken 7 kann dabei selbstverständlich auch zwischen dem Gaswechselnocken 6a und dem Gaswechselnocken 6b angeordnet sein. Die Lagerstellen 8a, 8b, die Gaswechselnocken 6a, 6b und der Einspritznocken 7 gehen direkt, also ohne Einstiche, ineinander über. Dadurch ist eine sehr steife Nockenwelle 4 gebildet. Fig. 1 shows a schematically illustrated crankcase 3 of a self-igniting internal combustion engine 1 with a total of six cylinders. The internal combustion engine has a crankshaft 2 mounted in the crankcase 3, which drives the camshaft 4 via a single meshing engagement, that is to say via a camshaft gearwheel 5b meshing with a crankshaft gearwheel 5a. The camshaft 4 has each cylinder associated bearing points 8a, 8b, between which gas exchange cam 6a and 6b and an injection cam 7 are arranged. Of course, the injection cam 7 can also be arranged between the gas exchange cam 6a and the gas exchange cam 6b. The bearings 8a, 8b, the gas exchange cams 6a, 6b and the injection cam 7 go directly, so without punctures, into each other. As a result, a very stiff camshaft 4 is formed.

In das Kurbelgehäuse 3 sind entsprechend der Anzahl der Zylinder zylinderkopfnah Ausnehmungen eingearbeitet, in die eine entsprechende Anzahl von Hockdruckpumpen eingesetzt werden können. In einer konventionellen Ausführungsform sind diese Hochdruckpumpen über kurze Einspritzleitungen direkt mit den Einspritzventilen verbunden. Bei der vorliegenden Erfindung ist die Hockdruckpumpe als ein Einzelpumpenelement 10 ausgebildet, dass ein in das in das Kurbelgehäuse 3 direkt einsetzbares Pumpengehäuse 19 aufweist. In dem Pumpengehäuse 19 ist ein Zylinderplunger 13 ohne Steuerkante geführt, wobei der Zylinderplunger 13 mit einem Rollenstößel 9 zusammenwirkt, der auf dem Einspritznocken 7 abrollt. In das Kurbelgehäuse 3 ist weiterhin eine Zuführleitung 14 für Kraftstoff eingelassen, die mit der Kraftstoffzufuhr zu dem Einspritzpumpenelement 10 verbunden ist. Zu bemerken ist, dass gegebenenfalls ein zweites oder weitere Einzelpumpenelement(e) vorhanden sein kann (können), wenn dies durch die entsprechende Auslegung des Einspritzsystems zur Befüllung der Hochdruckspeichervorrichtung 11 erforderlich ist. Ansonsten sind die Ausnehmungen in dem Kurbelgehäuse 3 zur Aufnahme der (konventionellen) Hochdruckpumpen mit Verschlussdeckeln 18 verschlossen.In the crankcase 3 are recessed in accordance with the number of cylinders close to the cylinder head, into which a corresponding number of high-pressure pumps can be used. In a conventional embodiment, these high-pressure pumps are connected via short injection lines directly to the injection valves. In the present invention, the high-pressure pump is designed as a single pump element 10 that has a pump housing 19 which can be directly inserted into the crankcase 3. In the pump housing 19, a Zylinderplunger 13 is guided without control edge, the Zylinderplunger 13 cooperates with a roller tappet 9, which rolls on the injection cam 7. In the crankcase 3, a supply line 14 is further admitted for fuel, which is connected to the fuel supply to the injection pump element 10. It should be noted that, if necessary, a second or further single pump element (s) may be present if required by the corresponding design of the injection system for filling the high-pressure storage device 11. Otherwise, the recesses in the crankcase 3 for receiving the (conventional) high-pressure pumps with closure lids 18 are closed.

An geeigneter Stelle der Zuführleitung 14 ist ein elektromagnetisch betätigtes Hydraulikventil 16 eingeschaltet, das den Kraftstoffzufluss zu dem Einzelpumpenelement 10 steuert. Das Einzelpumpenelement 10 ist über eine Hochdruckleitung 12 mit der Hochdruckspeichervorrichtung 11 verbunden und befüllt diese mengenmäßig durch das Hydraulikventil 16 geregelt mit Kraftstoff. Von der Hochdruckspeichervorrichtung 11 gehen Einspritzleitungen 17 ab, die mit den Einspritzventilen 15 verbunden sind. In die Einspritzventile 15 sind Steuerventile eingebaut, die die von dem jeweiligen Einspritzventil 15 in den Brennraum abgegebene Kraftstoffmenge steuern.At a suitable point of the supply line 14, an electromagnetically actuated hydraulic valve 16 is switched on, which controls the fuel flow to the single pump element 10. The single pump element 10 is connected via a high-pressure line 12 to the high-pressure accumulator device 11 and fills this quantity regulated by the hydraulic valve 16 with fuel. From the high-pressure accumulator device 11, injection pipes 17 which are connected to the injection valves 15 are exhausted. In the injection valves 15 control valves are installed, which control the amount of fuel delivered by the respective injection valve 15 into the combustion chamber.

In Fig. 2 ist das Kraftstoff-Einspritzsystem ohne Bezug zu der Brennkraftmaschine dargestellt. Der Kraftstoff wird von einer Vorpumpe 20 aus einem Kraftstofftank 21 über eine Filtereinrichtung 22 dem Hydraulikventil 16 zugeführt. Das Hydraulikventil 16 ist über eine Zuführleitung 14 mit einem oder mehreren Einzelpumpenelementen 10 verschaltet, wobei die Einzelpumpenelemente 10 über Rückschlagventile 23 den Kraftstoff über Hochdruckleitungen 12 in die Hochdruckspeichervorrichtung 11 fördern. Von der Hochdruckspeichervorrichtung 11 wird der Kraftstoff über Einspritzleitungen 17 den Einspritzventilen 15 zugeführt. Von einem Steuergerät 24 wird das gesamte System, also insbesondere das Hydraulikventil 16 und die Steuerventile der Einspritzventile 15 gesteuert, wobei die notwendigen Parameter zur Steuerung, beispielsweise der Druck in der Hochdruckspeichervorrichtung 11 als Messdaten dem Steuergerät 24 zugeführt werden.In Fig. 2 the fuel injection system is shown without reference to the internal combustion engine. The fuel is supplied from a fore-pump 20 from a fuel tank 21 via a filter device 22 to the hydraulic valve 16. The hydraulic valve 16 is connected via a supply line 14 with one or more individual pump elements 10, wherein the individual pump elements 10 via check valves 23 promote the fuel via high pressure lines 12 into the high pressure storage device 11. From the high-pressure accumulator device 11, the fuel is supplied to the injection valves 15 via injection lines 17. From a control unit 24, the entire system, so in particular the hydraulic valve 16 and the control valves of the injectors 15 is controlled, the necessary parameters for controlling, for example, the pressure in the high-pressure accumulator device 11 are supplied as measured data to the control unit 24.

Die Ausschnittsvergrößerung A des Hydraulikventils 16 zeigt den bevorzugten Aufbau dieses Hydraulikventils 16, das zusätzlich ein Druckregelventil 25 und eine Nullförderdrossel 26 aufweist. Dabei wird die von dem Druckregelventil 25 und der Nullförderdrossel 26 abgeführte Kraftstoffmenge in den Kraftstofftank 26 zurückgeführt.The detail enlargement A of the hydraulic valve 16 shows the preferred construction of this hydraulic valve 16, which additionally has a pressure regulating valve 25 and a zero feed throttle 26. In this case, the discharged from the pressure control valve 25 and the zero feed throttle 26 amount of fuel is returned to the fuel tank 26.

Claims (9)

  1. Internal combustion engine having a fuel injection system which has an unregulated high-pressure pump, connected into the fuel supply line (14) of which are a fore-pump (20) and a control device (16), and with the high-pressure pump being connected via a high-pressure line (12) to a high-pressure accumulator device (11) and the latter being connected via an injection line (17) and a control valve to an injection valve,
    characterized in that a filter device (22) is connected into the supply line (14) downstream of the fore-pump (20) and upstream of the control device in terms of flow, in that the high-pressure pump is a single pump element (10) which has a pump housing (19) which is inserted into the crankcase (3) of the internal combustion engine, and in that the single pump element (10) has a roller tappet (9) which rolls on an injection cam (7) of a gas exchange camshaft (4) and which is connected to the pump plunger.
  2. Internal combustion engine according to Claim 1,
    characterized in that the pump plunger is a cylindrical plunger (13) without a control edge.
  3. Internal combustion engine according to one of the preceding claims,
    characterized in that the control device is an electromagnetically actuated hydraulic valve (16).
  4. Internal combustion engine according to one of Claims 1 or 2,
    characterized in that the control device has an electromagnetically actuated hydraulic valve (16) and a pressure regulating valve (25) and a zero feed throttle (26) .
  5. Internal combustion engine according to one of the preceding claims,
    characterized in that the hydraulic valve (16) is a pulse-width-modulated hydraulic valve (16).
  6. Internal combustion engine according to one of Claims 1 to 4,
    characterized in that the hydraulic valve (16) is a proportionally-controlled hydraulic valve (16).
  7. Internal combustion engine according to one of the preceding claims,
    characterized in that the supply line (14) is integrated into the crankcase (3).
  8. Internal combustion engine according to one of Claims 1 to 6,
    characterized in that the supply line (14) is adapted to the crankcase (3).
  9. Internal combustion engine according to one of the preceding claims,
    characterized in that a pressure booster is connected into the injection line (17) and/or the injection valve (15).
EP02021072A 2001-09-26 2002-09-21 Fuel injection system Revoked EP1298316B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10147534A DE10147534A1 (en) 2001-09-26 2001-09-26 A fuel injection system
DE10147534 2001-09-26

Publications (3)

Publication Number Publication Date
EP1298316A2 EP1298316A2 (en) 2003-04-02
EP1298316A3 EP1298316A3 (en) 2005-02-02
EP1298316B1 true EP1298316B1 (en) 2008-05-07

Family

ID=7700403

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02021072A Revoked EP1298316B1 (en) 2001-09-26 2002-09-21 Fuel injection system

Country Status (6)

Country Link
EP (1) EP1298316B1 (en)
AT (1) ATE394594T1 (en)
DE (2) DE10147534A1 (en)
DK (1) DK1298316T3 (en)
ES (1) ES2305166T3 (en)
PT (1) PT1298316E (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2172634A2 (en) 2008-10-02 2010-04-07 DEUTZ Aktiengesellschaft Rail pressure regulation concept for rail pressure regulators with several actuators
CN101086242B (en) * 2006-06-09 2011-04-20 C.R.F.索奇埃塔·孔索尔蒂莱·佩尔·阿齐奥尼 Fuel-injection system for an internal -combustion engine

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10237586A1 (en) † 2002-08-16 2004-02-26 Robert Bosch Gmbh Fuel injection installation for IC engine, such as diesel engine with high pressure pump for fuel delivery to buffer container, whose piston is driven from engine camshaft
JP2004316518A (en) * 2003-04-15 2004-11-11 Denso Corp High-pressure fuel feeder
DE602004005051T2 (en) * 2004-11-12 2007-11-22 C.R.F. S.C.P.A. High-pressure pump with a device for controlling the flow for a fuel injection system
DE102008008259A1 (en) * 2008-02-08 2009-08-13 Deutz Ag Internal combustion engine with a common rail injection system

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5230613A (en) 1990-07-16 1993-07-27 Diesel Technology Company Common rail fuel injection system
MX9403372A (en) * 1993-05-06 1995-01-31 Cummins Engine Co Inc HIGH PRESSURE VARIABLE DISPLACEMENT PUMP FOR COMMON FUEL INJECTION SYSTEMS.
JP3077738B2 (en) * 1994-04-28 2000-08-14 株式会社デンソー High pressure supply pump
DE19508445B4 (en) * 1995-03-09 2004-07-08 Deutz Ag Fuel injection device for a self-igniting internal combustion engine
DE19716513C2 (en) * 1997-04-19 1999-02-11 Mtu Friedrichshafen Gmbh Fuel injection system for an internal combustion engine with a common rail
DE19719265A1 (en) * 1997-05-07 1998-11-12 Deutz Ag Internal combustion engine with fuel pump in the crankcase
EP0915252A3 (en) * 1997-11-05 2000-03-15 SIG Schweizerische Industrie-Gesellschaft Common rail fuel injection system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101086242B (en) * 2006-06-09 2011-04-20 C.R.F.索奇埃塔·孔索尔蒂莱·佩尔·阿齐奥尼 Fuel-injection system for an internal -combustion engine
EP2172634A2 (en) 2008-10-02 2010-04-07 DEUTZ Aktiengesellschaft Rail pressure regulation concept for rail pressure regulators with several actuators
DE102008049964A1 (en) 2008-10-02 2010-04-08 Deutz Ag Rail pressure control concept for rail pressure regulators with multiple actuators

Also Published As

Publication number Publication date
EP1298316A2 (en) 2003-04-02
ATE394594T1 (en) 2008-05-15
EP1298316A3 (en) 2005-02-02
DE10147534A1 (en) 2003-04-30
DK1298316T3 (en) 2008-08-11
DE50212211D1 (en) 2008-06-19
ES2305166T3 (en) 2008-11-01
PT1298316E (en) 2008-07-29

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