EP0412075B1 - Device for introducing fuel into the combustion chamber of an internal combustion engine - Google Patents

Device for introducing fuel into the combustion chamber of an internal combustion engine Download PDF

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Publication number
EP0412075B1
EP0412075B1 EP90890208A EP90890208A EP0412075B1 EP 0412075 B1 EP0412075 B1 EP 0412075B1 EP 90890208 A EP90890208 A EP 90890208A EP 90890208 A EP90890208 A EP 90890208A EP 0412075 B1 EP0412075 B1 EP 0412075B1
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EP
European Patent Office
Prior art keywords
valve
gas
injection
annular
injection valve
Prior art date
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Expired - Lifetime
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EP90890208A
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German (de)
French (fr)
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EP0412075A1 (en
Inventor
Diethard Dipl.-Ing. Plohberger
Volker Dipl.-Ing. Pichl
Leopold Dr. Dipl.-Ing. Mikulic
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AVL List GmbH
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AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH
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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
    • 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
    • F02M67/10—Injectors peculiar thereto, e.g. valve less type
    • F02M67/12—Injectors peculiar thereto, e.g. valve less type having valves
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • 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
    • F02D41/3011—Controlling fuel injection according to or using specific or several modes of combustion
    • F02D41/3017—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used
    • F02D41/3023—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the stratified charge spark-ignited mode

Definitions

  • the invention relates to a device for introducing fuel into the combustion chamber of an internal combustion engine, an injection valve opening into the combustion chamber being provided, which is used for removing compressed gas from the cylinder and for blowing in the gas and the fuel provided by a metering device Gas storage is provided for receiving the compressed gas.
  • a device of this type has become known, for example, from EP-A 0 328 602, where a gas exchange chamber is controlled by an injection valve opening into the cylinder of an internal combustion engine. Compressed gases are removed from the cylinder during a work cycle, stored temporarily and, in the following cycle, blown into the cylinder of the internal combustion engine together with the fuel introduced into the valve-side gas chamber.
  • EP-A 0 328 602 has disclosed various design variants which allow control of the stroke speed of the valve needle or a change in the needle stroke. In comparison to the versions without a variable needle stroke, this results in advantages with regard to the operation of the engine at low loads or full load, the positive influence on the emission behavior of the internal combustion engine having to be mentioned above all.
  • any eccentricities of the injection valve with respect to the valve seat have a disadvantageous effect, which is particularly noticeable in the case of small valve strokes as a disruptive influence on the jet shape, as a result of which high demands must be placed on the quality of the valve guide and valve seat.
  • the mechanical and manufacturing technology Effort to control the valve lift is relatively large.
  • the object of the invention is to develop a device of the type mentioned in a mechanically simple manner so that optimal injection conditions prevail even for small injection quantities and low injection speeds in part-load and idling operation, any eccentricities in the area of the valve seat being acceptable.
  • variable throttle point is provided between the valve seat of the injection valve and the gas accumulator, the flow cross section of which can be controlled as a function of load and speed parameters of the internal combustion engine.
  • variable throttle point which is located downstream of the now constant throttle point of the valve seat, in contrast to the known device, in which this control was achieved by varying the stroke of the single-valve .
  • Connecting elements to the gas accumulator are designed so that they contain only a small volume and thus the majority of the stored gas passes through the variable throttle point both when charging the accumulator and when blowing the fuel-gas mixture into the combustion chamber.
  • the gas flow entering the gas storage device is more or less throttled, so that a more or less high pressure level is established in the gas storage device after the injection valve has been closed.
  • the difference between cylinder and accumulator pressure and thus the energy available for injection, depending on the throttle position, will vary depending on the start of injection.
  • the gas flow emerging from the gas storage unit during the injection is throttled to different extents, depending on the throttle position.
  • the injection jet can be adapted to the different requirements that arise in different operating states of the engine. For example, at low load, a weak charge jet in the combustion chamber can achieve a favorable charge stratification, while at full load, a high injection speed enables the desired homogenization of the combustion chamber charge.
  • the gas reservoir is designed as a rotatable or axially displaceable storage tube which is mounted in the housing of the injection valve and has an actuator and a wall opening which is connected via a feed line to an annular space adjoining the valve seat, the variable Throttle point is formed by the wall opening in the storage tube and the supply line to the storage tube which is swept therefrom, the metering device advantageously opening into the annular space adjoining the valve seat. For example, by rotating the storage tube, the coverage of the two openings is varied. This results in a different cross section available for the gas passage.
  • a particularly advantageous embodiment of the invention is given in that, in the case of a multi-cylinder burner, the individual injection valves have a common storage tube which is arranged parallel to the crankshaft axis and which is mounted in lateral formations of the housing of the individual injection valves and is divided into individual storage sections, each storage section is connected via a wall opening to a feed line of the corresponding injection valve.
  • the lateral, horizontal arrangement of the storage tube enables a low overall height of the blowing device, as is required above all in two-stroke engines.
  • the individual storage sections in the storage pipe are connected by throttle bores, so that the same medium pressure values are set in the individual storage sections.
  • a further improvement lies in the fact that the feed line arranged between the annular space adjoining the valve seat and the gas accumulator opens tangentially into the annular space, as a result of which a stabilizing swirl movement is forced on the injection jet.
  • Another embodiment variant of the invention which is particularly suitable for four-stroke engines, provides that a tubular throttle member enclosing the valve guide of the injection valve is provided, which comprises the valve guide of the injection valve axially displaceably, and that the throttle member at its end facing the valve seat has a cylindrical gap to the housing of the injection valve, which forms the variable throttle point between the valve seat and the gas accumulator. Since there is no space for a lateral, horizontal storage pipe due to the space required for the valve train, the gas storage is arranged concentrically to the injection valve.
  • the metering device can open into the annular gap between the injection valve and the valve guide.
  • the throttle element be on the valve seat opposite end has an annular plate which is movably sealed to the housing wall, that the annular plate separates two annular spaces arranged in the housing of the valve, one annular space which can be acted upon with a control pressure medium being separated from the gas reservoir by an annular shape in the valve housing and the other Annulus has an element or pressure medium acting in the closing direction of the throttle member.
  • the annular space having a pressure medium acting in the closing direction of the throttle element can have a flow connection to the gas reservoir. This enables the pressure in the gas reservoir to be regulated automatically.
  • FIGS. 1 and 2 on the one hand and FIG. 3 on the other hand are dealt with in detail below.
  • the device for introducing fuel into the combustion chamber of an internal combustion engine shown in FIG. 1 has an injection valve 2 guided in a housing 1. Between the valve seat 3 of the injection valve 2 and the gas storage 5 executed here as an axis 4 'rotatable storage tube 4, a supply line 7 to the gas storage 5 is provided starting from an annular space 6 adjoining the valve seat 3.
  • the wall opening 8 in the storage tube 4 and the feed line 7 swept therefrom together form the variable throttle point 9.
  • the storage tube 4 can be rotated and thus the coverage of the wall opening 8 with the feed line 7 can be varied, which results in the throttling point 9 different gas throughput results.
  • Space saving the storage tube 4 is mounted in a side molding 11 of the housing 1, which guarantees a compact design, in particular for two-stroke engines.
  • the fuel is supplied via the metering device 12 into the annular space 6 near the valve plate 13 of the injection valve 2, whereby the total amount of gas flowing in or out can be loaded with fuel in the various operating states of the internal combustion engine.
  • the type of actuation of the injection valve 2 is largely freely selectable; However, to ensure a low overall height, short opening and closing times and precise control with simultaneous variation of the blowing timing, it is advisable to open and close the valve using the pressure generated by a fuel pump, in accordance with the EP-A cited at the beginning 0 328 602.
  • the fuel pump also supplies the metering element 12 for fuel injection into the annular space 6.
  • an actuating piston 14 connected to the injection valve is subjected to high pressure (20 to 100 bar) on the side facing away from the valve seat 3, and is thereby pressed onto a stop 15 in the housing 1.
  • the distance traveled corresponds to the stroke of the injection valve 2.
  • a constant pressure of a pressure medium supplied via line 16, which is present on the opposite side of the actuating piston 14, is used to close the valve.
  • Opening and closing is accomplished by means of an electromagnetically actuated three-way valve 17, which releases the high-pressure line 18 from the beginning of the opening of the injection valve 2 until immediately before the closing time and thus acts on the actuating piston 14 on the side facing away from the valve.
  • the pressure on the opposite side of the piston is either lower than the high pressure from line 18, or different actuating forces on the piston are realized by differently sized pressure-effective surfaces on both sides of the piston, which can save a second pressure level.
  • the three-way valve 17 releases the return 19.
  • the pressure on the side of the piston facing away from the valve drops, the pressure present on the opposite side via line 16 closes the injection valve 2 and keeps it closed against the gas pressure in the gas accumulator.
  • the storage tube 4 is expediently arranged parallel to the crankshaft axis and thus connects the injection valves 2 arranged in series.
  • the storage tube 4 is mounted in the lateral projections 11 of the housing 1 of the individual injection valves 2 and divided into individual storage sections 5 '.
  • Each storage section 5 ' is connected via a wall opening 8 to a feed line 7 of the corresponding injection valve 2.
  • the wall openings 8 of the storage tube 4 at the variable throttle 9 can also be designed as elongated holes.
  • the feed line 7 to the storage section 5 ' is expediently designed such that the gas emerging from the storage section 5' when blowing in flows tangentially into the annular space 6 around the injection valve 2. As a result, a stabilizing swirl movement is forced on the blowing jet.
  • the gas accumulator 5 is arranged here coaxially with the injection valve 2 and delimited by the cylindrical housing wall 22.
  • the variable throttle point 9 between the valve seat 3 and the gas accumulator 5 is formed by the valve-side end of a throttle element 23, which forms a variable, cylindrical gap 24 with the housing 1 of the injection valve 2.
  • the tubular throttle member 23 encloses the valve guide 25 and is axially displaceable thereon, as a result of which the height of the cylindrical gap and thus the cross section of the throttle point 9 can be changed linearly.
  • the throttle point 9 closes in the form of a flat seat.
  • the design variant shown is particularly suitable for four-stroke engines due to its design and external dimensions.
  • the throttle point 9 which is rotationally symmetrical about the axis of the injection valve 2, together with the likewise symmetrical flow conditions in or in the gas reservoir 5 and a symmetrical fuel supply via the annular gap between the valve guide 25 and the injection valve 2, largely stratify the charge in the gas reservoir 5. This makes it possible, when the gas flows into the gas storage device, to load only that air mass which is introduced into the cylinder during the subsequent injection, which results in advantages in the transient operation of the internal combustion engine.
  • the supply of fuel from above via the valve guide 25 is further advantageous in that the fuel connection and the metering element 12 are located higher, which is generally desirable in the four-stroke engine with its large deck height.
  • its stem and the valve guide 25 are protected from the accumulation of contaminants.
  • the throttle element 23 is formed here at its upper end as an annular plate 26, which is movably sealed against the housing wall 22 of the injection valve 2.
  • the annular space 27 thus formed between the housing wall 22 and the throttle element 23 has a flow connection 28 to the gas accumulator 5.
  • the annular space 30 required for throttle control, which is acted upon by the variable control pressure via the connection 31, thus arises between the annular plate 26 and the projection 29.
  • the throttling effect of the flow connection 28 is to be coordinated in such a way that a medium pressure is established in the annular space 27 and the pressure changes in the gas accumulator 5 resulting during each blowing cycle do not have any effect.
  • An advantage of this system is that temperature-related changes in length and manufacturing tolerances on the throttle element and injection valve do not affect the pressure set in the gas reservoir 5, since this is continuously adjusted directly according to the specified control pressure. This also makes it possible to easily control and synchronize the blowing speed of several blowing devices by applying the same control pressure to them.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Die Erfindung betrifft eine Vorrichtung zum Einbringen von Kraftstoff in den Brennraum einer Brennkraftmaschine, wobei ein in den Brennraum öffnendes Einblaseventil vorgesehen ist, welches zur Entnahme von verdichtetem Gas aus dem Zylinder und zur Einblasung des Gases und des von einer Zumeßeinrichtung bereitgestellten Kraftstoffes dient, wobei ein Gaspeicher zur Aufnahme des verdichteten Gases vorgesehen ist.The invention relates to a device for introducing fuel into the combustion chamber of an internal combustion engine, an injection valve opening into the combustion chamber being provided, which is used for removing compressed gas from the cylinder and for blowing in the gas and the fuel provided by a metering device Gas storage is provided for receiving the compressed gas.

Eine Vorrichtung dieser Art ist beispielsweise aus der EP-A 0 328 602 bekannt geworden, wo durch ein in den Zylinder einer Brennkraftmaschine öffnendes Einblaseventil eine Gaswechselkammer gesteuert wird. Verdichtete Gase werden dabei während eines Arbeitszyklus aus dem Zylinder entnommen, zwischengespeichert und im darauffolgenden Zyklus zusammen mit dem in die ventilseitige Gaskammer eingebrachten Kraftstoff in den Zylinder der Brennkraftmaschine eingeblasen.A device of this type has become known, for example, from EP-A 0 328 602, where a gas exchange chamber is controlled by an injection valve opening into the cylinder of an internal combustion engine. Compressed gases are removed from the cylinder during a work cycle, stored temporarily and, in the following cycle, blown into the cylinder of the internal combustion engine together with the fuel introduced into the valve-side gas chamber.

Zur Anpassung der Steuerzeiten der Einblasevorrichtung an verschiedene Motorparameter wie Last- oder Drehzahl, sind aus der EP-A 0 328 602 verschiedene Ausführungsvarianten bekannt geworden, welche eine Steuerung der Hubgeschwindigkeit der Ventilnadel oder eine Änderung des Nadelhubes erlauben. Dies ergibt im Vergleich zu den Ausführungen ohne variablen Nadelhub Vorteile im Bezug auf den Betrieb des Motors bei geringen Lasten bzw. Vollast, wobei vor allem der positive Einfluß auf das Emissionsverhalten der Brennkraftmaschine zu erwähnen wäre.In order to adapt the control times of the blowing device to different engine parameters such as load or speed, EP-A 0 328 602 has disclosed various design variants which allow control of the stroke speed of the valve needle or a change in the needle stroke. In comparison to the versions without a variable needle stroke, this results in advantages with regard to the operation of the engine at low loads or full load, the positive influence on the emission behavior of the internal combustion engine having to be mentioned above all.

Nachteilig wirken sich bei der bekannten Vorrichtung etwaige Exzentrizitäten des Einblaseventils gegenüber dem Ventilsitz aus, der sich besonders bei kleinen Ventilhüben als störender Einfluß auf die Strahlform bemerkbar macht, wodurch an die Güte von Ventilführung und Ventilsitz hohe Ansprüche gestellt werden müssen. Weiters ist auch der mechanische und herstellungstechnische Aufwand zur Steuerung des Ventilhubes relativ groß.In the known device, any eccentricities of the injection valve with respect to the valve seat have a disadvantageous effect, which is particularly noticeable in the case of small valve strokes as a disruptive influence on the jet shape, as a result of which high demands must be placed on the quality of the valve guide and valve seat. Furthermore, the mechanical and manufacturing technology Effort to control the valve lift is relatively large.

Aufgabe der Erfindung ist es, eine Vorrichtung der eingangs genannten Art auf mechanisch einfache Weise so weiterzubilden, daß auch für kleine Einspritzmengen und kleine Einblasegeschwindigkeiten im Teillast- und Leerlaufbetrieb optimale Einblasebedingungen herrschen, wobei allfällige Exzentrizitäten im Bereich des Ventilsitzes in Kauf genommen werden können.The object of the invention is to develop a device of the type mentioned in a mechanically simple manner so that optimal injection conditions prevail even for small injection quantities and low injection speeds in part-load and idling operation, any eccentricities in the area of the valve seat being acceptable.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß zwischen dem Ventilsitz des Einblaseventiles und dem Gasspeicher eine variable Drosselstelle vorgesehen ist, deren Strömungsquerschnitt in Abhängigkeit von Last- und Drehzahlparametern der Brennkraftmaschine steuerbar ist. Durch die Steuerung des Einblasezeitpunktes und der Einblasegeschwindigkeit durch getrennte Bauelemente, nämlich einem Einblaseventil mit konstantem Nadelhub einerseits und einer variablen Drosselstelle andererseits, sind Funktionsverbesserungen und leichtere Anpassung an die bei verschiedenen Motoren und Einbausituationen vorhandenen unterschiedlichen Platzverhältnisse möglich. Durch den konstanten, verhältnismäßig großen Nadelhub wirken sich auch Fehler im Ventilsitz nicht störend auf die Strahlform aus.This object is achieved in that a variable throttle point is provided between the valve seat of the injection valve and the gas accumulator, the flow cross section of which can be controlled as a function of load and speed parameters of the internal combustion engine. By controlling the injection time and the injection speed through separate components, namely an injection valve with a constant needle stroke on the one hand and a variable throttle point on the other hand, functional improvements and easier adaptation to the different space conditions available in different engines and installation situations are possible. Due to the constant, relatively large needle stroke, errors in the valve seat do not have a disruptive effect on the jet shape.

Die Funktion die Steuerung der Einblasegeschwindigkeit bzw. der pro Zeiteinheit eingebrachten Gasmenge wird hier durch eine variable Drosselstelle, die der nunmehr konstanten Drosselstelle des Ventilsitzes nachgelagert ist erfüllt, im Gegensatz zur bekannten Vorrichtung, bei der diese Steuerung durch die Variation des Hubes des Einbalseventiles erreicht wurde. Verbindungselemente zum Gasspeicher sind dabei so ausgeführt, daß sie nur ein geringes Volumen beinhalten und somit der überwiegende Teil des gespeicherten Gases sowohl beim Aufladen des Speichers als auch beim Einblasen des Kraftstoff-Gasgemisches in den Brennraum die variable Drosselstelle passiert.The function of controlling the blowing speed or the amount of gas introduced per unit of time is here performed by a variable throttle point, which is located downstream of the now constant throttle point of the valve seat, in contrast to the known device, in which this control was achieved by varying the stroke of the single-valve . Connecting elements to the gas accumulator are designed so that they contain only a small volume and thus the majority of the stored gas passes through the variable throttle point both when charging the accumulator and when blowing the fuel-gas mixture into the combustion chamber.

Je nach dem an der variablen Drosselstelle freigegebenen Strömungsquerschnitt wird der beim Aufladen in den Gasspeicher eintretende Gasstrom mehr oder weniger gedrosselt, sodaß sich nach Schließen des Einblaseventiles im Gasspeicher ein mehr oder weniger hohes Druckniveau einstellt.Depending on the flow cross-section released at the variable throttle point, the gas flow entering the gas storage device is more or less throttled, so that a more or less high pressure level is established in the gas storage device after the injection valve has been closed.

Wird beim folgenden Einblasevorgang das Einblaseventil wieder geöffnet, so ist bei konstantem Einblasebeginn die Differenz zwischen Zylinder- und Speicherdruck und damit die zur Einblasung zur Verfügung stehende Energie ja nach Drosselstellung unterschiedlich hoch; zusätzlich wird der während der Einblasung aus dem Gasspeicher aus tretende Gasstrom je nach Drosselstellung unterschiedlich stark gedrosselt.If the injection valve is opened again during the following injection process, the difference between cylinder and accumulator pressure and thus the energy available for injection, depending on the throttle position, will vary depending on the start of injection. in addition, the gas flow emerging from the gas storage unit during the injection is throttled to different extents, depending on the throttle position.

Das Ergebnis ist, daß bei weitgehend geschlossener Drossel während des Einblasevorganges eine verhältnismäßig geringe Gasmenge ausgetauscht wird, wobei bei der Einblasung das im Gasspeicher gespeicherte Gas mit relativ kleiner Geschwindigkeit austritt. Bei offener Drossel verhält es sich dagegen umgekehrt. Es wird eine große Gasmenge ausgetauscht und die Einblasung erfolgt mit hoher Geschwindigkeit.The result is that when the throttle is largely closed, a relatively small amount of gas is exchanged during the blowing process, the gas stored in the gas reservoir escaping at a relatively low speed during blowing. With the throttle open it is the other way round. A large amount of gas is exchanged and the injection takes place at high speed.

Auf diese Weise kann der Einblasestrahl an die bei verschiedenen Betriebszuständen des Motors auftretenden unterschiedlichen Anforderungen angepaßt werden. So läßt sich beispielsweise bei Teillast durch einen schwachen Einblasestrahl im Brennraum eine günstige Ladungsschichtung erzielen, während bei Vollast eine hohe Einblasegeschwindigkeit die hier gewünschte weitgehende Homogenisierung der Brennraumladung ermöglicht.In this way, the injection jet can be adapted to the different requirements that arise in different operating states of the engine. For example, at low load, a weak charge jet in the combustion chamber can achieve a favorable charge stratification, while at full load, a high injection speed enables the desired homogenization of the combustion chamber charge.

Als weiterer Vorteil gegenüber bekannten Vorrichtungen sei angeführt, daß die Regelung eines Drosselorganes einen geringeren Aufwand erfordert, als die Steuerung des Ventilhubes.Another advantage over known devices is that the regulation of a throttle body requires less effort than the control of the valve lift.

Eine Ausführungsvariante der Erfindung sieht vor, daß der Gasspeicher als im Gehäuse des Einblaseventiles gelagertes, drehbares oder axial verschiebbares Speicherrohr ausgeführt ist, welches ein Stellorgan und eine Wandöffnung aufweist, die über eine Zuleitung mit einem an den Ventilsitz anschließenden Ringraum verbunden ist, wobei die variable Drosselstelle durch die Wandöffnung im Speicherrohr und die davon überstrichene Zuleitung zum Speicherrohr gebildet ist, wobei vorteilhafterweise die Zumeßeinrichtung in den an den Ventilsitz anschließenden Ringraum mündet. Beispielsweise durch Drehen des Speicherrohres wird dabei die Überdeckung der beiden Öffnungen variiert. Damit ergibt sich ein unterschiedlicher, für den Gasdurchlaß zur Verfügung stehender Querschnitt.An embodiment of the invention provides that the gas reservoir is designed as a rotatable or axially displaceable storage tube which is mounted in the housing of the injection valve and has an actuator and a wall opening which is connected via a feed line to an annular space adjoining the valve seat, the variable Throttle point is formed by the wall opening in the storage tube and the supply line to the storage tube which is swept therefrom, the metering device advantageously opening into the annular space adjoining the valve seat. For example, by rotating the storage tube, the coverage of the two openings is varied. This results in a different cross section available for the gas passage.

Eine besonders vorteilhafte Ausgestaltung der Erfindung ist dadurch gegeben, daß bei einer Mehrzylinder-Brenn die einzelnen Einblaseventile über ein gemeinsames, parallel zur Kurbelwellenachse angeordnetes Speicherrohr verfügen, welches in seitlichen Anformungen der Gehäuse der einzelnen Einblaseventile gelagert und in einzelne Speicherabschnitte unterteilt ist, wobei jeder Speicherabschnitt über eine Wandöffnung mit einer Zuleitung des entsprechenden Einblaseventiles verbunden ist. Die seitliche, horizontale Anordnung des Speicherrohres ermöglicht eine geringe Bauhöhe der Einblasevorrichtung, wie sie vor allem bei Zweitaktmotoren gefordert wird.A particularly advantageous embodiment of the invention is given in that, in the case of a multi-cylinder burner, the individual injection valves have a common storage tube which is arranged parallel to the crankshaft axis and which is mounted in lateral formations of the housing of the individual injection valves and is divided into individual storage sections, each storage section is connected via a wall opening to a feed line of the corresponding injection valve. The lateral, horizontal arrangement of the storage tube enables a low overall height of the blowing device, as is required above all in two-stroke engines.

Erfindungsgemäß kann dabei vorgesehen sein, daß die einzelnen Speicherabschnitte im Speicherrohr durch Drosselbohrungen verbunden sind, sodaß sich in den einzelnen Speicherabschnitten gleiche Mitteldruckwerte einstellen.According to the invention, it can be provided that the individual storage sections in the storage pipe are connected by throttle bores, so that the same medium pressure values are set in the individual storage sections.

Eine weitere Verbesserung liegt darin, daß die zwischen dem an den Ventilsitz anschließenden Ringraum und dem Gasspeicher angeordnete Zuleitung tangential in den Ringraum mündet, wodurch dem Einblasestrahl eine stabilisierende Drallbewegung aufgezwungen wird.A further improvement lies in the fact that the feed line arranged between the annular space adjoining the valve seat and the gas accumulator opens tangentially into the annular space, as a result of which a stabilizing swirl movement is forced on the injection jet.

Eine andere Ausführungsvariante der Erfindung, welche insbesondere für Viertakt-Motoren geeignet ist, sieht vor, daß ein die Ventilführung des Einblaseventiles umschließendes rohrförmiges Drosselorgan vorgesehen ist, welches die.Ventilführung des Einblaseventiles axial verschiebbar umfaßt, sowie daß das Drosselorgan an seinem dem Ventilsitz zugewandten Ende zum Gehäuse des Einblaseventiles einen zylindrischen Spalt aufweist, welcher die variable Drosselstelle zwischen Ventilstitz und Gasspeicher bildet. Da aufgrund des Platzbedarfes für den Ventiltrieb kein Raum für ein seitliches, horizontales Speicherrohr vorhanden ist, ist hier der Gasspeicher konzentrisch zum Einblaseventil angeordnet.Another embodiment variant of the invention, which is particularly suitable for four-stroke engines, provides that a tubular throttle member enclosing the valve guide of the injection valve is provided, which comprises the valve guide of the injection valve axially displaceably, and that the throttle member at its end facing the valve seat has a cylindrical gap to the housing of the injection valve, which forms the variable throttle point between the valve seat and the gas accumulator. Since there is no space for a lateral, horizontal storage pipe due to the space required for the valve train, the gas storage is arranged concentrically to the injection valve.

Gemäß einer Weiterbildung der Erfindung kann dabei die Zumeßeinrichtung in den Ringspalt zwischen Einblaseventil und Ventilführung münden.According to a development of the invention, the metering device can open into the annular gap between the injection valve and the valve guide.

Bei einem pneumatischen Antrieb des Drosselorganes, vorzugsweise mit dem von einer Pumpe erzeugten Kraftstoffdruck, wird vorgeschlagen, daß das Drosselorgan an seinem vom Ventilsitz abgewandten Ende eine kreisringförmige Platte aufweist, welche zur Gehäusewand beweglich abgedichtet ist, daß die kreisringförmige Platte zwei im Gehäuse des Ventiles angeordnete Ringräume trennt, wobei der eine mit einem Steuerdruckmedium beaufschlagbare Ringraum vom Gasspeicher durch eine kreisringförmige Anformung im Gehäuse des Ventiles getrennt ist und der andere Ringraum ein in Schließrichtung des Drosselorganes wirkendes Element bzw. Druckmedium aufweist.In the case of a pneumatic drive of the throttle element, preferably with the fuel pressure generated by a pump, it is proposed that the throttle element be on the valve seat opposite end has an annular plate which is movably sealed to the housing wall, that the annular plate separates two annular spaces arranged in the housing of the valve, one annular space which can be acted upon with a control pressure medium being separated from the gas reservoir by an annular shape in the valve housing and the other Annulus has an element or pressure medium acting in the closing direction of the throttle member.

Schließlich kann erfindungsgemäß der ein in Schließrichtung des Drosselorganes wirkendes Druckmedium aufweisende Ringraum eine Strömungsverbindung zum Gasspeicher aufweisen. Dadurch kann eine selbsttätige Einregelung des Druckes im Gasspeicher erreicht werden.Finally, according to the invention, the annular space having a pressure medium acting in the closing direction of the throttle element can have a flow connection to the gas reservoir. This enables the pressure in the gas reservoir to be regulated automatically.

Die Erfindung wird im folgenden anhand von Zeichnungen näher erläutert. Es zeigen:

  • Fig. 1 eine Vorrichtung gemäß der Erfindung in einer Schnittdarstellung entsprechend Linie I-I in Fig. 2,
  • Fig. 2 die Vorrichtung nach Fig. 1 geschnitten nach Linie II-II in Fig. 1 sowie
  • Fig. 3 eine andere erfindungsgemäße Vorrichtung.
The invention is explained in more detail below with reference to drawings. Show it:
  • 1 shows a device according to the invention in a sectional view along line II in Fig. 2,
  • Fig. 2 shows the device of Fig. 1 cut along line II-II in Fig. 1 and
  • Fig. 3 shows another device according to the invention.

Stellvertretend für die zahlreichen möglichen Ausführungsformen wird im folgenden auf zwei signifikante Varianten entsprechend Fig. 1 und 2 einerseits bzw. Fig. 3 anderseits detailliert eingegangen.As a representative of the numerous possible embodiments, two significant variants corresponding to FIGS. 1 and 2 on the one hand and FIG. 3 on the other hand are dealt with in detail below.

Die in Fig. 1 dargestellte Vorrichtung zum Einbringen von Kraftstoff in den Brennraum einer Brennkraftmaschine weist ein in einem Gehäuse 1 geführtes Einblaseventil 2 auf. Zwischen dem Ventilsitz 3 des Einblaseventiles 2 und dem hier als um seine Achse 4′ drehbares Speicherrohr 4 ausgeführten Gasspeichers 5 ist ausgehend von einem an den Ventilsitz 3 anschließenden Ringraum 6 eine Zuleitung 7 zum Gasspeicher 5 vorgesehen. Die Wandöffnung 8 im Speicherrohr 4 und die davon überstrichene Zuleitung 7 bilden zusammen die variable Drosselstelle 9. Mit einem Stellorgan 10 kann das Speicherrohr 4 verdreht werden und so die Überdeckung der Wandöffnung 8 mit der Zuleitung 7 variiert werden, womit sich an der Drosselstelle 9 ein unterschiedlicher Gasdurchsatz ergibt. Platzsparend ist das Speicherrohr 4 in einer seitlichen Anformung 11 des Gehäuses 1 gelagert, was insbesondere für Zweitakt-Motoren eine kompakte Ausführung garantiert.The device for introducing fuel into the combustion chamber of an internal combustion engine shown in FIG. 1 has an injection valve 2 guided in a housing 1. Between the valve seat 3 of the injection valve 2 and the gas storage 5 executed here as an axis 4 'rotatable storage tube 4, a supply line 7 to the gas storage 5 is provided starting from an annular space 6 adjoining the valve seat 3. The wall opening 8 in the storage tube 4 and the feed line 7 swept therefrom together form the variable throttle point 9. With an actuator 10, the storage tube 4 can be rotated and thus the coverage of the wall opening 8 with the feed line 7 can be varied, which results in the throttling point 9 different gas throughput results. Space saving the storage tube 4 is mounted in a side molding 11 of the housing 1, which guarantees a compact design, in particular for two-stroke engines.

Der Kraftstoff wird über die Zumeßeinrichtung 12 in den Ringraum 6 nahe dem Ventilteller 13 des Einblaseventiles 2 zugeführt, wodurch bei den verschiedenen Betriebszuständen der Brennkraftmaschine jeweils die gesamte ein- bzw. ausströmende Gasmenge mit Kraftstoff beladen werden kann.The fuel is supplied via the metering device 12 into the annular space 6 near the valve plate 13 of the injection valve 2, whereby the total amount of gas flowing in or out can be loaded with fuel in the various operating states of the internal combustion engine.

Die Art der Betätigung des Einblaseventiles 2 ist weitgehend frei wählbar; zur Gewährleistung einer geringen Bauhöhe, kurzer Öffnung- und Schließzeiten und einer exakten Steuerung bei gleichzeitiger Variationsmöglichkeit des Einblasetimings empfiehlt es sich jedoch, sowohl das Öffnen als auch das Schließen des Ventiles mittels des von einer Kraftstoffpumpe erzeugten Druckes vorzunehmen, entsprechend der eingangs zitierten EP-A 0 328 602. Die Kraftstoffpumpe versorgt zugleich das Zumeßorgan 12 für die Kraftstoffeinspritzung in den Ringraum 6.The type of actuation of the injection valve 2 is largely freely selectable; However, to ensure a low overall height, short opening and closing times and precise control with simultaneous variation of the blowing timing, it is advisable to open and close the valve using the pressure generated by a fuel pump, in accordance with the EP-A cited at the beginning 0 328 602. The fuel pump also supplies the metering element 12 for fuel injection into the annular space 6.

Zum Öffnen des Ventiles wird ein mit dem Einblaseventil verbundener Betätigungskolben 14 auf der dem Ventilsitz 3 abgewandten Seite mit Hochdruck (20 bis 100 bar) beaufschlagt und dadurch auf einen Anschlag 15 im Gehäuse 1 gedrückt. Der dabei zurückgelegte Weg entspricht dem Hub des Einblaseventiles 2. Zum Schließen des Ventiles dient ein auf der Gegenseite am Betätigungskolben 14 anliegender konstanter Druck eines über die Leitung 16 zugeführten Druckmediums.To open the valve, an actuating piston 14 connected to the injection valve is subjected to high pressure (20 to 100 bar) on the side facing away from the valve seat 3, and is thereby pressed onto a stop 15 in the housing 1. The distance traveled corresponds to the stroke of the injection valve 2. A constant pressure of a pressure medium supplied via line 16, which is present on the opposite side of the actuating piston 14, is used to close the valve.

Öffnen und Schließen wird mittels eines elektromagnetisch betätigbaren Dreiwegventiles 17 bewerkstelligt, das vom Beginn des Öffnens des Einblaseventiles 2 bis unmittelbar vor dem Schließzeitpunkt die Hochdruckleitung 18 freigibt und damit den Betätigungskolben 14 auf der vetilabgewandten Seite beaufschlagt. Der auf der Kolbengegenseite anliegende Druck ist dabei entweder geringer als der Hochdruck aus der Leitung 18, oder es werden unterschiedliche Stellkräfte am Kolben durch unterschiedlich große druckwirksame Flächen an beiden Kolbenseiten realisiert, wodurch man sich ein zweites Druckniveau ersparen kann.Opening and closing is accomplished by means of an electromagnetically actuated three-way valve 17, which releases the high-pressure line 18 from the beginning of the opening of the injection valve 2 until immediately before the closing time and thus acts on the actuating piston 14 on the side facing away from the valve. The pressure on the opposite side of the piston is either lower than the high pressure from line 18, or different actuating forces on the piston are realized by differently sized pressure-effective surfaces on both sides of the piston, which can save a second pressure level.

Zum Schließen des Einblaseventiles 2 gibt das Dreiwegventil 17 den Rücklauf 19 frei. Der Druck auf der ventilabgewandten Kolbenseite fällt ab, der über die Leitung 16 an der Gegenseite anliegende Druck schließt das Einblaseventil 2 und hält es gegen den Gasdruck im Gasspeicher geschlossen.To close the injection valve 2, the three-way valve 17 releases the return 19. The pressure on the side of the piston facing away from the valve drops, the pressure present on the opposite side via line 16 closes the injection valve 2 and keeps it closed against the gas pressure in the gas accumulator.

Bei Mehrzylinder-Motoren ist, wie in Fig. 2 dargestellt, in zweckmäßiger Weise das Speicherrohr 4 parallel zur Kurbelwellenachse angeordnet und verbindet so die in Reihe angeordneten Einblaseventile 2. Das Speicherrohr 4 ist in den seitlichen Anformungen 11 der Gehäuse 1 der einzelnen Einblaseventile 2 gelagert und in einzelne Speicherabschnitte 5′ unterteilt. Jeder Speicherabschnitt 5′ ist über eine Wandöffnung 8 mit einer Zuleitung 7 des entsprechenden Einblaseventiles 2 verbunden.In multi-cylinder engines, as shown in FIG. 2, the storage tube 4 is expediently arranged parallel to the crankshaft axis and thus connects the injection valves 2 arranged in series. The storage tube 4 is mounted in the lateral projections 11 of the housing 1 of the individual injection valves 2 and divided into individual storage sections 5 '. Each storage section 5 'is connected via a wall opening 8 to a feed line 7 of the corresponding injection valve 2.

Zwischen den einzelnen Speicherabschnitten 5′ befinden sich in Trennwänden 20 Drosselbohrungen 21, die so abgestimmt sind, daß sich in den den einzelnen Zylindern zugeordneten Speicherabschnitten 5′ gleiche Mitteldruckwerte einstellen, wobei aber die bei den einzelnen Einblaseventilen zeitlich versetzt stattfindenden Einblasevorgänge und die daraus resultierenden unterschiedlichen Momentandrücke in den einzelnen Speicherabschnitten 5′ einander nicht stören sollen. Die Anordnung der Gasspeicher sämtlicher Einblasevorrichtungen einer Zylinderreihe in einem gemeinsamen drehbaren Speicherrohr 4 bietet den Vorteil, daß zum Drehen des Speicherrohres und damit zur Steuerung der variablen Drosselstellen 9 nur ein einziges Stellorgan 10 erforderlich ist. Die rotatorische Bewegung des Speicherrohres 4 ist dabei ebenfalls vorteilhaft.Between the individual storage sections 5 'there are throttle bores 21 in the partition walls 20, which are coordinated such that the same mean pressure values are set in the storage sections 5' assigned to the individual cylinders, but with the blowing processes occurring at different times in the individual injection valves and the resulting different injection processes Instantaneous pressures in the individual memory sections 5 'should not interfere with each other. The arrangement of the gas accumulators of all the blowing devices of a cylinder bank in a common rotatable storage tube 4 offers the advantage that only a single actuator 10 is required for rotating the storage tube and thus for controlling the variable throttle points 9. The rotational movement of the storage tube 4 is also advantageous.

Zum Ausgleich von etwaigen Längenänderungen und Toleranzen in Richtung der Achse 4′ des Speicherrohres 4 können die Wandöffnungen 8 des Speicherrohres 4 an der variablen Drosselstelle 9 auch als Langlöcher ausgeführt werden.To compensate for any changes in length and tolerances in the direction of the axis 4 'of the storage tube 4, the wall openings 8 of the storage tube 4 at the variable throttle 9 can also be designed as elongated holes.

Die Zuleitung 7 zum Speicherabschnitt 5′ ist zweckmäßigerweise so ausgestaltet, daß das beim Einblasen aus dem Speicherabschnitt 5′ austretende Gas tangential in den Ringraum 6 um das Einblaseventil 2 einmündet. Dadurch wird dem Einblasestrahl eine stabilisierende Drallbewegung aufgezwungen.The feed line 7 to the storage section 5 'is expediently designed such that the gas emerging from the storage section 5' when blowing in flows tangentially into the annular space 6 around the injection valve 2. As a result, a stabilizing swirl movement is forced on the blowing jet.

Bei der in der Fig. 3 dargestellten Ausführungsvariante der Erfindung sind die der Ausführung nach Fig. 1 und 2 entsprechenden Teile mit gleichen Bezugszeichen versehen. Der Gasspeicher 5 ist hier koaxial zum Einblaseventil 2 angeordnet und von der zylindrischen Gehäusewand 22 begrenzt. Die variable Drosselstelle 9 zwischen Ventilsitz 3 und Gasspeicher 5 wird durch das ventilseitige Ende eines Drosselorganes 23 gebildet, welches mit dem Gehäuse 1 des Einblaseventiles 2 einen variablen, zylindrischen Spalt 24 formt. Das rohrförmige Drosselorgan 23 umschließt die Ventilführung 25 und ist auf dieser axial verschiebbar, wodurch die Höhe des zylindrischen Spaltes und damit der Querschnitt der Drosselstelle 9 linear geändert werden kann. Um die Auswirkungen von Unexaktheiten seitens der Führung des Drosselorganes 23 hintanzuhalten, schließt die Drosselstelle 9 in Form eines Flachsitzes.In the embodiment variant of the invention shown in FIG. 3, those corresponding to the embodiment according to FIGS. 1 and 2 are corresponding Provide parts with the same reference numerals. The gas accumulator 5 is arranged here coaxially with the injection valve 2 and delimited by the cylindrical housing wall 22. The variable throttle point 9 between the valve seat 3 and the gas accumulator 5 is formed by the valve-side end of a throttle element 23, which forms a variable, cylindrical gap 24 with the housing 1 of the injection valve 2. The tubular throttle member 23 encloses the valve guide 25 and is axially displaceable thereon, as a result of which the height of the cylindrical gap and thus the cross section of the throttle point 9 can be changed linearly. In order to prevent the effects of inaccuracies on the part of the guide of the throttle element 23, the throttle point 9 closes in the form of a flat seat.

Die dargestellte Ausführungsvariante ist aufgrund ihrer Bauform und ihrer Außenabmessungen vor allem für Viertakt-Motoren geeignet.The design variant shown is particularly suitable for four-stroke engines due to its design and external dimensions.

Die um die Achse des Einblaseventiles 2 rotationssymmetrische Drosselstelle 9 ermöglicht es zusammen mit den ebenfalls symmetrischen Strömungsbedingungen in den bzw. im Gasspeicher 5 und einer symmetrischen Kraftstoffzuführung über den Ringspalt zwischen Ventilführung 25 und Einblaseventil 2, die Ladung im Gasspeicher 5 weitgehend zu schichten. Dadurch ist es möglich, bereits beim Einströmen des Gases in den Gasspeicher nur jene Luftmasse mit Kraftstoff zu beladen, die während der darauffolgenden Einblasung in den Zylinder eingebracht wird, wodurch sich Vorteile im instationären Betrieb der Brennkraftmaschine ergeben.The throttle point 9, which is rotationally symmetrical about the axis of the injection valve 2, together with the likewise symmetrical flow conditions in or in the gas reservoir 5 and a symmetrical fuel supply via the annular gap between the valve guide 25 and the injection valve 2, largely stratify the charge in the gas reservoir 5. This makes it possible, when the gas flows into the gas storage device, to load only that air mass which is introduced into the cylinder during the subsequent injection, which results in advantages in the transient operation of the internal combustion engine.

Die Zuführung des Kraftstoffes von oben über die Ventilführung 25 ist weiters insoferne von Vorteil, als sich dadurch der Kraftstoffanschluß und das Zumeßorgan 12 lagemäßig höher befinden, was beim Viertaktmotor mit seiner großen Deckhöhe in der Regel wünschenswert ist. Außerdem ist bei einem Kraftstofffluß entlang des Einblaseventiles 2 dessen Schaft und die Ventilführung 25 vor der Anlagerung von Verunreinigungen geschützt.The supply of fuel from above via the valve guide 25 is further advantageous in that the fuel connection and the metering element 12 are located higher, which is generally desirable in the four-stroke engine with its large deck height. In addition, in the case of a fuel flow along the injection valve 2, its stem and the valve guide 25 are protected from the accumulation of contaminants.

Neben verschiedenen hier nicht näher ausgeführten mechanischen Betätigungsmöglichkeiten für das Drosselorgan 23 bietet sich die in Fig. 3 dargestellte selbsttätige Einregelung des Druckes im Gasspeicher 5 nach einem vorzugebenden variablen Druckniveau an, das seinerseits kennfeldabhängig gesteuert werden kann. Der Druck im Gasspeicher 5 ist, wie oben beschrieben, die entscheidende Größe für die Einblasegeschwindigkeit. Das Drosselorgan 23 ist hier an seinem oberen Ende als kreisringförmige Platte 26 ausgebildet, die gegen die Gehäusewand 22 des Einblaseventiles 2 beweglich abgedichtet ist. Der so zwischen Gehäusewand 22 und Drosselorgan 23 gebildete Ringraum 27 weist eine Strömungsverbindung 28 zum Gasspeicher 5 auf. Unterhalb der Platte 26 des Drosselorganes 23 befindet sich parallel dazu im Gehäuse 1 eine kreisringförmige Anformung 29, die gegen das rohrförmige Drosselorgan 23 beweglich abgedichtet ist. Zwischen der kreisringförmigen Platte 26 und der Anformung 29 entsteht so der zur Drosselregelung benötigte Ringraum 30, der über den Anschluß 31 mit dem variablen Steuerdruck beaufschlagt wird.In addition to various mechanical actuation options for the throttle element 23, which are not detailed here, there is the automatic adjustment of the pressure in the gas accumulator 5 shown in FIG. 3 according to a variable to be specified Pressure level that can be controlled depending on the map. As described above, the pressure in the gas reservoir 5 is the decisive variable for the blowing speed. The throttle element 23 is formed here at its upper end as an annular plate 26, which is movably sealed against the housing wall 22 of the injection valve 2. The annular space 27 thus formed between the housing wall 22 and the throttle element 23 has a flow connection 28 to the gas accumulator 5. Underneath the plate 26 of the throttle element 23 there is in parallel in the housing 1 an annular projection 29 which is movably sealed against the tubular throttle element 23. The annular space 30 required for throttle control, which is acted upon by the variable control pressure via the connection 31, thus arises between the annular plate 26 and the projection 29.

Wird nun ein Steuerdruck vorgegeben, so liegt dieser an der Unterseite der kreisringförmigen Platte 26 an, wobei als Gegenkraft auf der anderen Plattenseite der Gasdruck im Ringraum 27 wirkt. Überwiegt die Kraft durch den Steuerdruck, so wird das Drosselorgan 23 axial nach oben verschoeben. Dadurch wird der Strömungsquerschnitt an der variablen Drosselstelle 9 vergrößert und im Gasspeicher 5 stellt sich infolgedessen ein höherer Gasdruck ein. Ober die Strömungsverbindung 28 tritt Gas vom Gasspeicher 5 in den Ringraum 27 über, wodurch sich auch hier der erhöhte Speicherdruck einstellt. Der Einstellvorgang des Drosselorganes 23 und damit des Speicherdruckes ist beendet, wenn sich an der Oberseite und der Unterseite der Platte 26 des Drosselorganes 23 ein Kräftegleichgewicht einstellt. Wird der Steuerdruck im Ringraum 30 reduziert, so wird das Drosselorgan 23 durch den nun überwiegenden Druck im Ringraum 27 axial nach unten bewegt, der freigegebene Spalt 24 an der variablen Drosselstelle 9 verkleinert und der Druck im Gasspeicher sowie im Ringraum 27 abgesenkt. Auch hier wird der Einstellvorgang beendet, wenn am Drosselorgan 23 ein Kräftegleichgewicht herrscht.If a control pressure is now specified, it is applied to the underside of the annular plate 26, the gas pressure in the annular space 27 acting as counterforce on the other side of the plate. If the force prevails due to the control pressure, the throttle element 23 is displaced axially upwards. As a result, the flow cross section at the variable throttle point 9 is increased and, as a result, a higher gas pressure is established in the gas reservoir 5. Gas flows from the gas accumulator 5 into the annular space 27 via the flow connection 28, as a result of which the increased accumulator pressure also arises here. The adjustment process of the throttle element 23 and thus the accumulator pressure is ended when a force equilibrium is established on the top and the bottom of the plate 26 of the throttle element 23. If the control pressure in the annular space 30 is reduced, the throttle member 23 is moved axially downward by the now predominant pressure in the annular space 27, the released gap 24 at the variable throttle point 9 is reduced and the pressure in the gas accumulator and in the annular space 27 is reduced. Here, too, the adjustment process is ended when there is a balance of forces on the throttle element 23.

Die Drosselwirkung der Strömungsverbindung 28 ist so abzustimmen, daß sich im Ringraum 27 ein Mitteldruck einstellt und sich die während jedes Einblasezyklus ergebenden Druckänderungen im Gasspeicher 5 nicht auswirken.The throttling effect of the flow connection 28 is to be coordinated in such a way that a medium pressure is established in the annular space 27 and the pressure changes in the gas accumulator 5 resulting during each blowing cycle do not have any effect.

Anstelle der Strömungsverbindung 28 ist es auch möglich, die Verbindung zwischen dem Gasspeicher 5 und dem Ringraum 27 durch einen Spalt zwischen dem Drosselorgan 23 und der Ventilführung 25 herzustellen. In diesem Fall entfällt die bei der Strömungsverbindung 28 notwendige Abdichtung gegenüber dem Ringraum 20 zur Drosselregelung.Instead of the flow connection 28, it is also possible to establish the connection between the gas reservoir 5 and the annular space 27 through a gap between the throttle element 23 and the valve guide 25. In this case, the sealing with respect to the annular space 20 for throttle control, which is necessary for the flow connection 28, is omitted.

Bei Verwendung einer Flüssigkeit als Steuerdruckmedium können vom Motorbetrieb herrührende Schwingungen keine unkontrollierten Bewegungen des Drosselorganes 23 bewirken, da durch die weitgehende Inkompressibilität der Flüssigkeit jede Bewegung des Drosselorganes gegenüber dem Gehäuse des Einblaseventiles eine verhältnismäßig große Mengenänderung im Ringraum 30 erfordern würde, welcher die durch den verhältnismäßig kleinen Querschnitt des Anschlusses 31 entstehende Drosselkraft entgegenwirkt.When using a liquid as a control pressure medium, vibrations resulting from engine operation cannot cause uncontrolled movements of the throttle element 23, since due to the largely incompressible nature of the liquid, each movement of the throttle element relative to the housing of the injection valve would require a relatively large change in the volume in the annular space 30, which would be caused by the proportionately Small cross-section of the connection 31 counteracts throttling force.

Ein Vorteil dieses Systems ist, daß sich temperaturbedingte Längenänderungen und Herstellungstoleranzen an Drosselorgan und Einblaseventil nicht auf den eingestellten Druck im Gasspeicher 5 auswirken, da dieser kontinuierlich direkt nach dem vorgegebenen Steuerdruck eingeregelt wird. Dadurch ergibt sich auch die Möglichkeit, auf einfache Weise die Einblasegeschwindigkeit mehrerer Einblasevorrichtungen zu steuern und zu synchronisieren, indem man sie mit demselben Steuerdruck beaufschlagt.An advantage of this system is that temperature-related changes in length and manufacturing tolerances on the throttle element and injection valve do not affect the pressure set in the gas reservoir 5, since this is continuously adjusted directly according to the specified control pressure. This also makes it possible to easily control and synchronize the blowing speed of several blowing devices by applying the same control pressure to them.

Claims (10)

  1. A device for feeding fuel into the combustion chamber of an internal combustion engine, comprising an injection valve (2) opening into the combustion chamber, which is used for taking compressed gas from the cylinder and injecting the gas together with the fuel supplied by a metering device (12), and further comprising a gas storage cell (5) holding the compressed gas, wherein a variable throttle (9) is provided between the valve seat (3) of the injection valve (2) and the gas storage cell (5), whose flow cross-section can be controlled in accordance with load and speed parameters of the engine.
  2. A device as in claim 1, wherein the gas storage cell (5) is configured as a rotatable or axially movable storage tube (4), which is held in the housing (1) of the injection value (2) and is provided with an adjusting element (10) and a wall opening (8) connected via a feed line (7) to an annular chamber (6) adjoining the valve seat (3), the variable throttle (9) being formed by the wall opening (8) in the storage tube (4) and the corresponding feed line (7) into said tube (4) cooperating with said opening (8).
  3. A device as in claim 2, wherein the metering device (12) opens into the annular chamber (6) adjoining the valve seat (3).
  4. A device as in claim 2 or 3, wherein the individual injection valves (2) of a multi-cylinder engine have a joint storage tube (4) located parallel to the crankshaft axis, which is held by lateral projections (11) on the housings (1) of the individual injection valves (2) and is divided into individual storage sections (5′), each of which is connected via a wall opening (8) to a feed line (7) of the corresponding injection valve (2).
  5. A device as in claim 4, wherein the individual storage sections (5′) in the storage tube (4) are connected by throttling ports (21), thus establishing identical mean pressures in the individual sections (5′).
  6. A device as in any of claims 2 to 5, wherein the feed line (7) located between the annular chamber (6) adjoining the valve seat (3) and the gas storage cell (5;5′) opens tangentially into said annular chamber (6).
  7. A device as in claim 1, with the gas storage cell being positioned coaxially with the injection valve and being bounded by a cylindrical wall of the housing, wherein a tubular throttling element (23) is provided, with can be shifted axially and surrounds the valve guide (25) of the injection valve (2), and whose end facing the valve seat (3) has a cylindrical gap (24) towards the housing (1) of the injection valve (2), acting as the variable throttle (9) between valve seat (3) and gas storage cell (5).
  8. A device as in claim 7, wherein the metering device (12) opens into the annular gap between injection valve (2) and valve guide (25).
  9. A device as in claim 7 or 8, wherein the throttling element (23) carries an annular plate (26) at its far end away from the valve seat (3), which is movably sealed against the wall (22) of the housing, and wherein said annular plate (26) separates two annular chambers (27, 30) located in the valve housing (1), one of these annular chambers (30), which is subject to a control pressure medium, being separated from the gas storage cell (5) by means of an annular projection (29) in the valve housing (1), and the other annular chamber (27) being provided with an element or medium operating in closing direction of the throttling element (23).
  10. A device as in claim 9, wherein the annular chamber (27) containing a pressure medium which is effective in closing direction of the throttling element (23), has a flow-connection (28) into the gas storage cell (5).
EP90890208A 1989-07-31 1990-07-09 Device for introducing fuel into the combustion chamber of an internal combustion engine Expired - Lifetime EP0412075B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT1847/89 1989-07-31
AT0184789A AT408256B (en) 1989-07-31 1989-07-31 DEVICE FOR INPUTING FUEL INTO THE COMBUSTION CHAMBER OF AN INTERNAL COMBUSTION ENGINE

Publications (2)

Publication Number Publication Date
EP0412075A1 EP0412075A1 (en) 1991-02-06
EP0412075B1 true EP0412075B1 (en) 1992-12-23

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EP90890208A Expired - Lifetime EP0412075B1 (en) 1989-07-31 1990-07-09 Device for introducing fuel into the combustion chamber of an internal combustion engine

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US (1) US5025769A (en)
EP (1) EP0412075B1 (en)
JP (1) JPH0656141B2 (en)
AT (1) AT408256B (en)
DE (1) DE59000650D1 (en)

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US20030012985A1 (en) 1998-08-03 2003-01-16 Mcalister Roy E. Pressure energy conversion systems
US5201907A (en) * 1991-06-28 1993-04-13 Mazda Motor Corporation Internal combustion engine
US5390647A (en) * 1993-06-21 1995-02-21 Ford Motor Company Air charging valve for an air forced fuel injector
AT408137B (en) * 1995-02-27 2001-09-25 Avl Verbrennungskraft Messtech DEVICE FOR INPUTING FUEL INTO THE COMBUSTION CHAMBER OF AN INTERNAL COMBUSTION ENGINE
AUPN358595A0 (en) * 1995-06-15 1995-07-06 Orbital Engine Company (Australia) Proprietary Limited Improved fuel injected internal combustion engine
DE19618896A1 (en) * 1996-05-10 1997-11-20 Wtz Motoren & Maschforsch Gmbh Fuel air injector for internal combustion engine
JP3778319B2 (en) * 1997-05-24 2006-05-24 本田技研工業株式会社 2-cycle internal combustion engine
AUPO988597A0 (en) * 1997-10-20 1997-11-13 Orbital Engine Company (Australia) Proprietary Limited Start-up method for an internal combustion engine
DE10212439B4 (en) * 2002-03-21 2004-10-07 Kaibel, Jens, Dipl.-Ing. Device and method for producing fine drops
CA2798870C (en) 2012-12-17 2014-07-22 Westport Power Inc. Air-enriched gaseous fuel direct injection for an internal combustion engine
US9255560B2 (en) * 2013-03-15 2016-02-09 Mcalister Technologies, Llc Regenerative intensifier and associated systems and methods
US9091204B2 (en) 2013-03-15 2015-07-28 Mcalister Technologies, Llc Internal combustion engine having piston with piston valve and associated method

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Also Published As

Publication number Publication date
US5025769A (en) 1991-06-25
EP0412075A1 (en) 1991-02-06
ATA184789A (en) 2001-02-15
DE59000650D1 (en) 1993-02-04
JPH0370867A (en) 1991-03-26
JPH0656141B2 (en) 1994-07-27
AT408256B (en) 2001-10-25

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