[go: up one dir, main page]

EP0731271A2 - Arrangement for introducing fuel into the combustion chamber of an inertnal combustion engine - Google Patents

Arrangement for introducing fuel into the combustion chamber of an inertnal combustion engine Download PDF

Info

Publication number
EP0731271A2
EP0731271A2 EP96890011A EP96890011A EP0731271A2 EP 0731271 A2 EP0731271 A2 EP 0731271A2 EP 96890011 A EP96890011 A EP 96890011A EP 96890011 A EP96890011 A EP 96890011A EP 0731271 A2 EP0731271 A2 EP 0731271A2
Authority
EP
European Patent Office
Prior art keywords
valve
mixing chamber
fuel
cylinder
gas
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.)
Granted
Application number
EP96890011A
Other languages
German (de)
French (fr)
Other versions
EP0731271A3 (en
EP0731271B1 (en
Inventor
Walter Dr. Piock
Martin Dr. Ing. Dipl.-Ing. Wirth
Günther K Dipl.-Ing. Dr. Fraidl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
AVL List GmbH
Original Assignee
AVL List GmbH
AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by AVL List GmbH, AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH filed Critical AVL List GmbH
Publication of EP0731271A2 publication Critical patent/EP0731271A2/en
Publication of EP0731271A3 publication Critical patent/EP0731271A3/en
Application granted granted Critical
Publication of EP0731271B1 publication Critical patent/EP0731271B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D7/00—Other fuel-injection control
    • F02D7/02—Controlling fuel injection where fuel is injected by compressed air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/04—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure using fluid, other than fuel, for injection-valve actuation
    • F02M47/046—Fluid pressure acting on injection-valve in the period of injection to open it
    • 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
    • F02M67/00—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type
    • F02M67/02—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type the gas being compressed air, e.g. compressed in pumps
    • F02M67/04—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type the gas being compressed air, e.g. compressed in pumps the air being extracted from working cylinders of the engine

Definitions

  • the invention relates to a device for introducing fuel into the combustion chamber of an internal combustion engine with a delivery device for the fuel, an injection valve for removing compressed gas from the cylinder and for blowing the gas and the delivered fuel into the cylinder, with a valve-side mixing chamber for storage of the gas, the injection valve having a valve for controlling the gas exchange between the combustion chamber and the mixing chamber on the valve side.
  • a device of the type mentioned is known, with which compressed gas is removed from the cylinder during one working cycle, temporarily stored and blown into the cylinder together with the fuel in the following working cycle, the removal of a small amount being called Gas from the cylinder is timed via a valve opening into the combustion chamber of the cylinder. Fuel is injected into the extracted hot gas stored in the valve chamber of the valve, whereby an essentially homogeneous gas-fuel mixture is achieved. Finally, the stored fuel-gas mixture is blown into the cylinder through the valve opening into the cylinder in the subsequent working cycle. According to an embodiment variant of the known device, it is known to change the injection duration and the injection quantity, in particular independently of one another, as a function of engine operating parameters.
  • the injection valve With the same engine operating parameters, i.e. with the same load, speed, etc., the injection valve always opens and closes at a specific crankshaft position.
  • this has the disadvantage that the closing time of the valve must be selected so that even in the worst case no combustion can take place in the mixing room, since this would lead to coking.
  • it is desirable to close the valve late during the compression phase. Due to the spatial distance between the ignition source and the injection valve, a considerably later closing time than the ignition time is possible due to the flame spread.
  • the object of the present invention is to avoid these disadvantages and to enable constant, reproducible operating conditions in a device of the type mentioned.
  • the mixing chamber is in operative connection with at least one sensor element for measuring the pressure and / or the temperature of the mixing chamber and the valve is closed as a function of at least the physical variable measured by the at least one sensor element. It is preferably provided that the sensor element is connected to an electronic control unit which supplies a closing signal generated as a function of the measured size to a hydraulic, pneumatic or electromagnetic valve actuation device.
  • the closing time of the injection valve is determined directly by the physical conditions in the mixing room, such as temperature and / or pressure. As high a pressure as possible can be realized in the mixing room, which is subject to very small cyclical fluctuations.
  • the closing time is set so that there can be no combustion in the mixing chamber.
  • the reasonably possible closing time can be determined by a characteristic pressure or temperature specification. According to the present invention, this variable is used as a control or manipulated variable in order to realize the latest possible closing time of the valve without the flame entering the mixing chamber, similar to a knock control of the ignition timing, and thus to store the respective highest possible pressure in the mixing chamber.
  • an injection valve 1 of an internal combustion engine is shown schematically. With 2 it is Cylinder head, indicated by the reference numeral 3, a cylinder of the internal combustion engine.
  • a valve 5 is slidably mounted in the valve housing 4 of the injection valve 1.
  • the valve 5 is actuated by a hydraulic actuation device 6, for example.
  • the actuating device 6 can also be pneumatic or electrical.
  • an actuating piston 7 of the valve 5 is pressurized with hydraulic pressure in the pressure chamber 8 against the force of a spring 9, whereby the valve 5 is deflected into the open position. When the pressure is released, the valve 5 is brought into the closed position by the spring 9.
  • a hydraulic line 10 leads into the pressure chamber 8 and can be connected to a pump 12 or the like via a switching valve 11. In a second position of the switching valve 11, the pressure chamber 8 can be relieved via the relief line 13.
  • the switching valve 11 is actuated via an electronic control unit ECU.
  • a mixing chamber 14 Arranged within the valve housing 4 is a mixing chamber 14 which, in the open position of the valve 5, is flow-connected to the combustion chamber 21 of the internal combustion engine.
  • a fuel flow path 15 opens into the mixing chamber 14, via which fuel can be injected into the mixing chamber 14.
  • the fuel supply system is indicated by the fuel tank 16, the fuel delivery device 17, a fuel valve 18 and the line 15.
  • a temperature sensor 19 and / or a pressure sensor 20 is provided, the data of which are supplied to the control unit ECU.
  • the cylinder pressure p 1 indicated by the line A and the pressure p 2 symbolized by the line B in the mixing chamber 14 are plotted over the crank angle KW.
  • the arrow C indicates the ignition point in the area of the top dead center OT.
  • the reference symbol UT stands for bottom dead center.
  • the blowing-in phase of the blowing-in valve 1 is indicated by the reference symbol D, the reference symbol D 0 marking the opening point and E 0 the closing point of the blowing-in valve 1.
  • the valve 5 is opened and discharges the contents of the mixing chamber 14 into the combustion chamber 21 within the cylinder 3.
  • the recharging phase E of the blowing valve 1 follows, during which gas flows into the mixing chamber 14 as the combustion chamber pressure increases.
  • the recharging phase E must have ended before combustion takes place within the mixing space 14.
  • the mixing chamber 14 is discharged again in the following cycle during the blowing phase D.
  • the injection valve thus remains open during the injection phase D and the recharge phase E.
  • the closing time D 0 of the injection valve 4 is as late as possible.
  • the closing time D 0 must not take place too late in order to reliably exclude combustion in the mixing room 14.
  • at least one temperature sensor 19 and / or a pressure sensor 20 is provided for monitoring the temperature and / or the pressure within the mixing space 14, as shown in FIG. 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The fuel injection device has an injection valve (1) with a mixing space (14) for receiving compressed gas from the engine cylinder (3), before injecting the gas mixed with the supplied fuel to the cylinder. The gas exchange between the cylinder and the mixing space is controlled via a piston valve (5), with closure of the latter in dependence on the detected temp. and/or pressure within the mixing space, provided by a sensor element (19,20).

Description

Die Erfindung betrifft eine Einrichtung zum Einbringen von Kraftstoff in den Brennraum einer Brennkraftmaschine mit einer Fördereinrichtung für den Kraftstoff, einem Einblaseventil zum Entnehmen von verdichtetem Gas aus dem Zylinder und zum Einblasen des Gases und des geförderten Kraftstoffes in den Zylinder, mit einem ventilseitigen Mischraum zur Speicherung des Gases, wobei das Einblaseventil ein Ventil zur Steuerung des Gasaustausches zwischen dem Brennraum und dem ventilseitigen Mischraum aufweist.The invention relates to a device for introducing fuel into the combustion chamber of an internal combustion engine with a delivery device for the fuel, an injection valve for removing compressed gas from the cylinder and for blowing the gas and the delivered fuel into the cylinder, with a valve-side mixing chamber for storage of the gas, the injection valve having a valve for controlling the gas exchange between the combustion chamber and the mixing chamber on the valve side.

Aus der EP-PS 0 328 602 ist eine Einrichtung der genannten Art bekannt, mit der verdichtetes Gas während eines Arbeitszyklus aus dem Zylinder entnommen, zwischengespeichert und im darauffolgenden Arbeitszyklus zusammen mit dem Kraftstoff in den Zylinder eingeblasen wird, wobei die Entnahme einer kleinen Menge heißen Gases aus dem Zylinder zeitlich gesteuert über ein in den Brennraum des Zylinders öffnendes Ventil erfolgt. In das im Ventilraum des Ventils gespeicherte entnommene heiße Gas wird Kraftstoff eingespritzt, wodurch ein im wesentlichen homogenes Gas-Kraftstoff-Gemisch erreicht wird. Schließlich wird das gespeicherte Kraftstoff-Gas-Gemisch im darauffolgenden Arbeitszyklus durch das in den Zylinder öffnende Ventil in den Zylinder eingeblasen. Gemäß einer Ausführungsvariante der bekannten Einrichtung ist es bekannt, die EInblasedauer und die Einspritzmenge, insbesondere unabhängig voneinander, in Abhängigkeit von Motorbetriebsparametern zu verändern. Bei gleichen Motorbetriebsparametern, also bei gleicher Last, Drehzahl, etc., öffnet und schließt das Einblaseventil dabei stets bei einer bestimmten Kurbelwellenstellung. Dies hat allerdings den Nachteil, daß der Schließzeitpunkt des Ventiles so gewählt werden muß, daß auch im ungünstigsten Falle keine Verbrennung im Mischraum stattfinden kann, da dies zu Verkokungen führen würde. Um andererseits den Druck im ventilseitigen Mischraum möglichst hoch zu halten, ist ein spätes Schließen des Ventiles während der Kompressionsphase erwünscht. Durch den räumlichen Abstand der Zündquelle zum Einblaseventil ist infolge der Flammenausbreitung ein erheblich späterer Schließzeitpunkt als der Zündzeitpunkt möglich. Bei einer gemäß dem Stand der Technik unflexiblen Schließzeitpunktfestsetzung des Einblaseventiles kommt es infolge der für Ottomotoren charakteristischen zyklischen Schwankungen zu starken Schwankungen des Speicherdruckes im Mischraum und somit zu stark unterschiedlichen Einblasedrücken, weshalb das Druckverhältnis zwischen Mischkanal und Brennraum kaum reproduzierbar ist.From EP-PS 0 328 602, a device of the type mentioned is known, with which compressed gas is removed from the cylinder during one working cycle, temporarily stored and blown into the cylinder together with the fuel in the following working cycle, the removal of a small amount being called Gas from the cylinder is timed via a valve opening into the combustion chamber of the cylinder. Fuel is injected into the extracted hot gas stored in the valve chamber of the valve, whereby an essentially homogeneous gas-fuel mixture is achieved. Finally, the stored fuel-gas mixture is blown into the cylinder through the valve opening into the cylinder in the subsequent working cycle. According to an embodiment variant of the known device, it is known to change the injection duration and the injection quantity, in particular independently of one another, as a function of engine operating parameters. With the same engine operating parameters, i.e. with the same load, speed, etc., the injection valve always opens and closes at a specific crankshaft position. However, this has the disadvantage that the closing time of the valve must be selected so that even in the worst case no combustion can take place in the mixing room, since this would lead to coking. On the other hand, in order to keep the pressure in the valve-side mixing chamber as high as possible, it is desirable to close the valve late during the compression phase. Due to the spatial distance between the ignition source and the injection valve, a considerably later closing time than the ignition time is possible due to the flame spread. In accordance with According to the state of the art inflexible closing timing of the injection valve, the cyclical fluctuations characteristic of gasoline engines lead to large fluctuations in the storage pressure in the mixing chamber and thus to very different injection pressures, which is why the pressure ratio between the mixing duct and the combustion chamber is hardly reproducible.

Aufgabe der vorliegenden Erfindung ist es, diese Nachteile zu vermeiden und bei einer Einrichtung der genannten Art konstante, reproduzierbare Betriebsbedingungen zu ermöglichen.The object of the present invention is to avoid these disadvantages and to enable constant, reproducible operating conditions in a device of the type mentioned.

Erfindungsgemäß wird dies dadurch erreicht, daß der Mischraum mit zumindest einem Sensorelement zur Messung des Druckes und/oder der Temperatur des Mischraumes in Wirkverbindung steht und das Schließen des Ventiles in Abhängigkeit zumindest der durch das zumindest eine Sensorelement gemessenen physikalischen Größe erfolgt. Vorzugsweise ist vorgesehen, daß das Sensorelement mit einer elektronischen Steuereinheit verbunden ist, welche ein in Abhängigkeit der gemessenen Größe erzeugtes Schließsignal einer hydraulischen, pneumatischen oder elektromagnetischen Ventilbetätigungseinrichtung zuführt.According to the invention, this is achieved in that the mixing chamber is in operative connection with at least one sensor element for measuring the pressure and / or the temperature of the mixing chamber and the valve is closed as a function of at least the physical variable measured by the at least one sensor element. It is preferably provided that the sensor element is connected to an electronic control unit which supplies a closing signal generated as a function of the measured size to a hydraulic, pneumatic or electromagnetic valve actuation device.

Der Schließzeitpunkt des Einblaseventiles wird direkt von den physikalischen Bedingungen im Mischraum, wie Temperatur und/oder Druck bestimmt. Es kann somit ein möglichst hoher Druck im Mischraum realisiert werden, der sehr geringen zyklischen Schwankungen unterliegt. Der Schließzeitpunkt ist dabei so festgesetzt, daß keinesfalls eine Verbrennung in der Mischkammer stattfinden kann. Für einen gegebenen Betriebspunkt der Brennkraftmaschine kann der damit sinnvoll mögliche Schließzeitpunkt durch eine charakteristische Druck- oder Temperaturangabe bestimmt werden. Diese Größe wird gemäß der vorliegenden Erfindung als Regel- oder als Stellgröße verwendet, um ähnlich einer Klopfregelung des Zündzeitpunktes den spätestmöglichen Schließzeitpunkt des Ventiles ohne Eintritt der Flamme in die Mischkammer zu realisieren und damit den jeweiligen höchstmöglichen Druck im Mischraum zu speichern.The closing time of the injection valve is determined directly by the physical conditions in the mixing room, such as temperature and / or pressure. As high a pressure as possible can be realized in the mixing room, which is subject to very small cyclical fluctuations. The closing time is set so that there can be no combustion in the mixing chamber. For a given operating point of the internal combustion engine, the reasonably possible closing time can be determined by a characteristic pressure or temperature specification. According to the present invention, this variable is used as a control or manipulated variable in order to realize the latest possible closing time of the valve without the flame entering the mixing chamber, similar to a knock control of the ignition timing, and thus to store the respective highest possible pressure in the mixing chamber.

Die Erfindung wird anhand der Fig. näher erläutert. Es zeigen

  • Fig. 1 das erfindungsgemäße Einblaseventil im Längsschnitt,
  • Fig. 2 ein Druck-Kurbelwinkel-Diagramm.
The invention is explained in more detail with reference to the figure. Show it
  • 1 shows the injection valve according to the invention in longitudinal section,
  • Fig. 2 is a pressure-crank angle diagram.

In Fig. 1 ist schematisch ein Einblaseventil 1 einer nicht weiter dargestellten Brennkraftmaschine gezeigt. Mit 2 ist der Zylinderkopf, mit dem Bezugszeichen 3 ein Zylinder der Brennkraftmaschine angedeutet. Im Ventilgehäuse 4 des Einblaseventiles 1 ist ein Ventil 5 verschiebbar gelagert. Das Ventil 5 wird durch eine beispielsweise hydraulische Betätigungseinrichtung 6 betätigt. Genauso kann die Betätigungseinrichtung 6 auch pneumatisch oder elektrisch sein. Bei der in Fig. 1 dargestellten hydraulischen Betätigungseinrichtung 6 wird ein Betätigungskolben 7 des Ventils 5 mit hydraulischem Druck in der Druckkammer 8 entgegen der Kraft einer Feder 9 mit Druck beaufschlagt, wodurch das Ventil 5 in die Öffnungsstellung ausgelenkt wird. Bei Druckentlastung wird das Ventil 5 durch die Feder 9 in die Schließstellung gebracht. In den Druckraum 8 führt eine Hydraulikleitung 10, welche über ein Schaltventil 11 mit einer Pumpe 12 oder dgl. verbindbar ist. In einer zweiten Stellung des Schaltventiles 11 kann der Druckraum 8 über die Entlastungsleitung 13 entlastet werden. Das Schaltventil 11 wird über eine elektronische Steuereinheit ECU betätigt.In Fig. 1, an injection valve 1 of an internal combustion engine, not shown, is shown schematically. With 2 it is Cylinder head, indicated by the reference numeral 3, a cylinder of the internal combustion engine. A valve 5 is slidably mounted in the valve housing 4 of the injection valve 1. The valve 5 is actuated by a hydraulic actuation device 6, for example. The actuating device 6 can also be pneumatic or electrical. In the hydraulic actuating device 6 shown in FIG. 1, an actuating piston 7 of the valve 5 is pressurized with hydraulic pressure in the pressure chamber 8 against the force of a spring 9, whereby the valve 5 is deflected into the open position. When the pressure is released, the valve 5 is brought into the closed position by the spring 9. A hydraulic line 10 leads into the pressure chamber 8 and can be connected to a pump 12 or the like via a switching valve 11. In a second position of the switching valve 11, the pressure chamber 8 can be relieved via the relief line 13. The switching valve 11 is actuated via an electronic control unit ECU.

Innerhalb des Ventilgehäuses 4 ist ein Mischraum 14 angeordnet, welcher in der Öffnungsstellung des Ventils 5 mit dem Brennraum 21 der Brennkraftmaschine strömungsverbunden ist. In den Mischraum 14 mündet ein Kraftstoffströmungsweg 15, über welchen Kraftstoff in den Mischraum 14 eingespritzt werden kann. Das Kraftstoffversorgungssystem ist durch den Kraftstoffbehälter 16, die Kraftstoffördereinrichtung 17, ein Kraftstoffventil 18 und die Leitung 15 angedeutet. Zur Messung der Temperatur und/oder des Druckes im Mischraum 14 ist ein Temperatursensor 19 und/oder ein Drucksensor 20 vorgesehen, dessen bzw. deren Daten der Steuereinheit ECU zugeführt werden.Arranged within the valve housing 4 is a mixing chamber 14 which, in the open position of the valve 5, is flow-connected to the combustion chamber 21 of the internal combustion engine. A fuel flow path 15 opens into the mixing chamber 14, via which fuel can be injected into the mixing chamber 14. The fuel supply system is indicated by the fuel tank 16, the fuel delivery device 17, a fuel valve 18 and the line 15. To measure the temperature and / or the pressure in the mixing chamber 14, a temperature sensor 19 and / or a pressure sensor 20 is provided, the data of which are supplied to the control unit ECU.

In dem in Fig. 2 gezeigten Druck-Kurbelwinkelschaubild ist der durch die Linie A angedeutete Zylinderdruck p1 und der durch die Linie B symbolisierte Druck p2 im Mischraum 14 über dem Kurbelwinkel KW aufgetragen. Der Pfeil C deutet den Zündzeitpunkt im Bereich des oberen Totpunktes OT an. Das Bezugszeichen UT steht für den unteren Totpunkt. Die Einblasephase des Einblaseventiles 1 ist durch das Bezugszeichen D angedeutet, wobei das Bezugszeichen D0 den Öffnungspunkt und E0 den Schließpunkt des Einblaseventils 1 markieren. Während der Einblasephase D ist das Ventil 5 geöffnet und entlädt den Inhalt des Mischraumes 14 in den Brennraum 21 innerhalb des Zylinders 3. Unmittelbar an die Einblasephase D schließt bei Einrichtungen der eingangs genannten Art die Wiederaufladephase E des Einblaseventils 1 an, während der bei steigendem Brennraumdruck Gas in den Mischraum 14 strömt. Die Wiederaufladephase E muß beendet sein, bevor eine Verbrennung innerhalb des Mischraumes 14 stattfindet. Nach darauffolgender Einspritzung von Kraftstoff in das heiße gespeicherte Gas im Mischraum 14 wird im darauffolgenden Zyklus während der Einblasephase D der Mischraum 14 wieder entladen. Das Einblaseventil bleibt somit während der Einblasephase D und der Wiederaufladephase E geöffnet.In the pressure-crank angle diagram shown in FIG. 2, the cylinder pressure p 1 indicated by the line A and the pressure p 2 symbolized by the line B in the mixing chamber 14 are plotted over the crank angle KW. The arrow C indicates the ignition point in the area of the top dead center OT. The reference symbol UT stands for bottom dead center. The blowing-in phase of the blowing-in valve 1 is indicated by the reference symbol D, the reference symbol D 0 marking the opening point and E 0 the closing point of the blowing-in valve 1. During the blowing phase D, the valve 5 is opened and discharges the contents of the mixing chamber 14 into the combustion chamber 21 within the cylinder 3. Immediately after the blowing phase D in devices of the type mentioned, the recharging phase E of the blowing valve 1 follows, during which gas flows into the mixing chamber 14 as the combustion chamber pressure increases. The recharging phase E must have ended before combustion takes place within the mixing space 14. After the subsequent injection of fuel into the hot stored gas in the mixing chamber 14, the mixing chamber 14 is discharged again in the following cycle during the blowing phase D. The injection valve thus remains open during the injection phase D and the recharge phase E.

Zur Erzielung hoher Einblasedrücke während der Einblasephase D ist es vorteilhaft, wenn der Schließzeitpunkt D0 des Einblaseventiles 4 möglichst spät erfolgt. Allerdings darf der Schließzeitpunkt D0 auch nicht zu spät erfolgen, um eine Verbrennung im Mischraum 14 sicher auszuschließen. Um den optimalen Schließzeitpunkt D0 des Einblaseventiles 1 zu bestimmen, ist erfindungsgemäß zumindest ein Temperatursensor 19 und/oder ein Drucksensor 20 zur Überwachung der Temperatur und/oder des Druckes innerhalb des Mischraumes 14 vorgesehen, wie in Fig. 1 gezeigt ist.To achieve high injection pressures during the injection phase D, it is advantageous if the closing time D 0 of the injection valve 4 is as late as possible. However, the closing time D 0 must not take place too late in order to reliably exclude combustion in the mixing room 14. In order to determine the optimum closing time D 0 of the injection valve 1, according to the invention at least one temperature sensor 19 and / or a pressure sensor 20 is provided for monitoring the temperature and / or the pressure within the mixing space 14, as shown in FIG. 1.

Claims (2)

Einrichtung zum Einbringen von Kraftstoff in den Brennraum einer Brennkraftmaschine mit einer Fördereinrichtung für den Kraftstoff, einem Einblaseventil zum Entnehmen von verdichtetem Gas aus dem Zylinder und zum Einblasen des Gases und des geförderten Kraftstoffes in den Zylinder, mit einem ventilseitigen Mischraum zur Speicherung des Gases, wobei das Einblaseventil ein Ventil zur Steuerung des Gasaustausches zwischen dem Brennraum und dem ventilseitigen Mischraum aufweist, dadurch gekennzeichnet , daß der Mischraum (14) mit zumindest einem Sensorelement (19; 20) zur Messung des Druckes und/oder der Temperatur des Mischraumes (14) in Wirkverbindung steht und das Schließen des Ventiles (5) in Abhängigkeit zumindest der durch das zumindest eine Sensorelement (19; 20) gemessenen physikalischen Größe erfolgt.Device for introducing fuel into the combustion chamber of an internal combustion engine with a delivery device for the fuel, an injection valve for removing compressed gas from the cylinder and for injecting the gas and the delivered fuel into the cylinder, with a valve-side mixing chamber for storing the gas, wherein the injection valve has a valve for controlling the gas exchange between the combustion chamber and the mixing chamber on the valve side, characterized in that the mixing chamber (14) with at least one sensor element (19; 20) for measuring the pressure and / or the temperature of the mixing chamber (14) in There is an operative connection and the valve (5) is closed as a function of at least the physical variable measured by the at least one sensor element (19; 20). Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß das Sensorelement (19; 20) mit einer elektronischen Steuereinheit (ECU) verbunden ist, welche ein in Abhängigkeit der gemessenen physikalischen Größe(n) erzeugtes Schließsignal einer hydraulischen, pneumatischen oder elektromagnetischen Ventilbetätigungseinrichtung (6) zuführt.Device according to claim 1, characterized in that the sensor element (19; 20) is connected to an electronic control unit (ECU) which supplies a closing signal generated as a function of the measured physical quantity (s) to a hydraulic, pneumatic or electromagnetic valve actuating device (6) .
EP96890011A 1995-02-27 1996-01-23 Arrangement for introducing fuel into the combustion chamber of an internal combustion engine Expired - Lifetime EP0731271B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT353/95 1995-02-27
AT0035395A AT408137B (en) 1995-02-27 1995-02-27 DEVICE FOR INPUTING FUEL INTO THE COMBUSTION CHAMBER OF AN INTERNAL COMBUSTION ENGINE

Publications (3)

Publication Number Publication Date
EP0731271A2 true EP0731271A2 (en) 1996-09-11
EP0731271A3 EP0731271A3 (en) 1996-10-30
EP0731271B1 EP0731271B1 (en) 1998-03-25

Family

ID=3488370

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96890011A Expired - Lifetime EP0731271B1 (en) 1995-02-27 1996-01-23 Arrangement for introducing fuel into the combustion chamber of an internal combustion engine

Country Status (4)

Country Link
US (1) US5647336A (en)
EP (1) EP0731271B1 (en)
AT (1) AT408137B (en)
DE (1) DE59600120D1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030012985A1 (en) 1998-08-03 2003-01-16 Mcalister Roy E. Pressure energy conversion systems
AT7202U1 (en) * 2002-12-19 2004-11-25 Avl List Gmbh METHOD FOR OPERATING A GAS INTERNAL COMBUSTION ENGINE
CA2798870C (en) 2012-12-17 2014-07-22 Westport Power Inc. Air-enriched gaseous fuel direct injection for an internal combustion engine
WO2014144581A1 (en) 2013-03-15 2014-09-18 Mcalister Technologies, Llc Internal combustion engine and associated systems and methods
US9255560B2 (en) * 2013-03-15 2016-02-09 Mcalister Technologies, Llc Regenerative intensifier and associated systems and methods

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989001568A1 (en) * 1987-08-12 1989-02-23 Avl Gesellschaft Für Verbrennungskraftmaschinen Un Process and device for introducing fuel into the combustion chamber of an internal combustion engine
US4944277A (en) * 1989-03-03 1990-07-31 Outboard Marine Corporation Cylinder entrapment system with an air spring
WO1994025742A1 (en) * 1993-04-29 1994-11-10 Orbital Engine Company (Australia) Pty. Limited Fuel injected internal combustion engine

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT407428B (en) * 1989-04-12 2001-03-26 Avl Verbrennungskraft Messtech HYDRAULICALLY ACTUATED VALVE WITH CONTROLLED LIFT
AT408256B (en) * 1989-07-31 2001-10-25 Avl Verbrennungskraft Messtech DEVICE FOR INPUTING FUEL INTO THE COMBUSTION CHAMBER OF AN INTERNAL COMBUSTION ENGINE
AT408138B (en) * 1995-02-23 2001-09-25 Avl Verbrennungskraft Messtech DEVICE FOR INPUTING FUEL INTO THE COMBUSTION CHAMBER OF AN INTERNAL COMBUSTION ENGINE

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989001568A1 (en) * 1987-08-12 1989-02-23 Avl Gesellschaft Für Verbrennungskraftmaschinen Un Process and device for introducing fuel into the combustion chamber of an internal combustion engine
US4944277A (en) * 1989-03-03 1990-07-31 Outboard Marine Corporation Cylinder entrapment system with an air spring
WO1994025742A1 (en) * 1993-04-29 1994-11-10 Orbital Engine Company (Australia) Pty. Limited Fuel injected internal combustion engine

Also Published As

Publication number Publication date
DE59600120D1 (en) 1998-04-30
EP0731271A3 (en) 1996-10-30
ATA35395A (en) 2001-01-15
US5647336A (en) 1997-07-15
EP0731271B1 (en) 1998-03-25
AT408137B (en) 2001-09-25

Similar Documents

Publication Publication Date Title
DE69612045T2 (en) Direct injection system for gaseous fuel for internal combustion engines
DE4313852A1 (en) Fuel injection device for internal combustion engines
DE69605075T2 (en) Fuel injection device of the accumulator type
WO1999022133A1 (en) Dual nozzle for injecting fuel and an additional fluid
DE2558699A1 (en) PUMP JET FOR FUEL INJECTION IN COMBUSTION ENGINE
DE19720731A1 (en) Fuel injector with vibration damper for directly injected petrol engine
DE19738397A1 (en) Fuel injection system for an internal combustion engine
DE10024268A1 (en) Petrol fuel injection system is pressurized by converter connected to hydraulic oil system controlling engine valves
EP2876275B1 (en) Reciprocating piston combustion engine and method for operating same
DE69728270T2 (en) FUEL-GAS MIXTURE INJECTION SYSTEM
EP0946828B1 (en) Fuel injection system for an internal combustion engine
EP0731271B1 (en) Arrangement for introducing fuel into the combustion chamber of an internal combustion engine
EP1704316B1 (en) Method and device for controlling a valve and method and device for controlling a pump-nozzle device with a valve
EP0982492B1 (en) Apparatus for injecting fuel in a reciprocating internal combustion engine
WO2007042386A1 (en) Method for operating an internal combustion engine
DE19709446C1 (en) Conveyor for fuel
DE19909955A1 (en) Transient operating method for automobile engine uses mathematical model for calculating fuel pressure during transition between two fuel pressures for corresponding regulation of engine operating point
DE10148221A1 (en) Method, computer program and control and / or regulating device for operating an internal combustion engine, and internal combustion engine
DE69415140T2 (en) CONTROL SYSTEM FOR A HIGH PRESSURE FUEL INJECTION SYSTEM FOR AN INTERNAL COMBUSTION ENGINE
EP0561740B1 (en) Method of operation of a Diesel engine and such Diesel engine
DE19529826C1 (en) Injector for common-rail system
DE102004035301B4 (en) diesel engine
CH660401A5 (en) Fuel injection in an internal combustion engine.
EP1464819A2 (en) Method for operating a combustion engine
DE4030890A1 (en) Fuel injector for two=stroke IC engine - includes mixing chamber with piston valve controlled by pressure of fuel introduced into hot exhaust gas

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): DE ES FR GB IT SE

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE ES FR GB IT SE

17P Request for examination filed

Effective date: 19961102

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: AVL LIST GMBH

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

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

17Q First examination report despatched

Effective date: 19970901

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): DE ES FR GB IT SE

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

Ref country code: ES

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19980325

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

Effective date: 19980402

REF Corresponds to:

Ref document number: 59600120

Country of ref document: DE

Date of ref document: 19980430

ITF It: translation for a ep patent filed
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: 19980625

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

Ref country code: DE

Payment date: 19990116

Year of fee payment: 4

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

Ref country code: FR

Payment date: 19990128

Year of fee payment: 4

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
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 NON-PAYMENT OF DUE FEES

Effective date: 20000123

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

Effective date: 20000123

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: 20000929

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: 20001101

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

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

Ref country code: IT

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

Effective date: 20050123