EP2807366B1 - Apparatus to inject fuel in the combustion chamber of a combustion engine - Google Patents

Apparatus to inject fuel in the combustion chamber of a combustion engine Download PDF

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Publication number
EP2807366B1
EP2807366B1 EP13714682.5A EP13714682A EP2807366B1 EP 2807366 B1 EP2807366 B1 EP 2807366B1 EP 13714682 A EP13714682 A EP 13714682A EP 2807366 B1 EP2807366 B1 EP 2807366B1
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Prior art keywords
pressure
bore
nozzle
fuel
pressure accumulator
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EP13714682.5A
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German (de)
French (fr)
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EP2807366A1 (en
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Johannes Schnedt
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/04—Injectors peculiar thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10L—SPEECH ANALYSIS OR SYNTHESIS; SPEECH RECOGNITION; SPEECH OR VOICE PROCESSING; SPEECH OR AUDIO CODING OR DECODING
    • G10L15/00—Speech recognition
    • G10L15/02—Feature extraction for speech recognition; Selection of recognition unit
    • G10L2015/025—Phonemes, fenemes or fenones being the recognition units
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10L—SPEECH ANALYSIS OR SYNTHESIS; SPEECH RECOGNITION; SPEECH OR VOICE PROCESSING; SPEECH OR AUDIO CODING OR DECODING
    • G10L19/00—Speech or audio signals analysis-synthesis techniques for redundancy reduction, e.g. in vocoders; Coding or decoding of speech or audio signals, using source filter models or psychoacoustic analysis
    • G10L2019/0001—Codebooks
    • G10L2019/0004—Design or structure of the codebook
    • G10L2019/0005—Multi-stage vector quantisation

Definitions

  • the invention relates to a device for injecting fuel into the combustion chamber of an internal combustion engine having at least one injector, which includes a high-pressure accumulator integrated in the injector body, an injection nozzle comprising an axially displaceable nozzle needle, which is surrounded by a nozzle chamber, a high-pressure accumulator and the nozzle chamber connecting high-pressure bore and an inlet bore in order to supply the high-pressure accumulator high-pressure fuel, wherein the inlet bore has a laterally arranged on the injector body lance connection.
  • Injection injectors of this type are used in modular common rail systems, which are characterized in that a part of the existing storage volume in the system is present in the injector itself.
  • Modular common-rail systems are used in particularly large engines, in which the individual injectors may be mounted at a considerable distance from each other.
  • the sole use of a common rail for all injectors is not useful in such engines, as it would come to a massive slump in injection pressure due to the long lines during injection, so with prolonged injection duration, the injection rate would noticeably break.
  • it is therefore intended to arrange a high-pressure accumulator inside each injector.
  • Such a design is referred to as a modular structure, since each injector has its own high-pressure accumulator and thus can be used as a stand-alone module.
  • a high-pressure accumulator is not a common line to understand, but it is a pressure-resistant vessel with an inlet and outlet, whose Diameter is significantly increased compared to the high pressure lines, so that from the high-pressure accumulator a certain amount of injection can be delivered without causing an immediate pressure drop.
  • High-pressure fuel is supplied from a high-pressure pump, wherein the supply takes place either via a high-pressure port of the injector at the top of the high-pressure accumulator (so-called top feed) or via a laterally contacting the injector lance (so-called Sidefeed).
  • top feed a high-pressure port of the injector at the top of the high-pressure accumulator
  • Sidefeed a laterally contacting the injector lance
  • Sidefeed the lance opens via a lance connection of the injector in an inlet bore, which opens into the high-pressure accumulator connecting the high-pressure reservoir with the nozzle antechamber high pressure bore.
  • the Sidefeed has a number of advantages, especially in large-scale engines, since it allows the leadership of the fuel flow to the injector across the cylinder, whereby the length of the feed can be shortened compared to a pot feed in the rule.
  • the Sidefeed in the conventional design has the disadvantage that the high-pressure fuel flows directly from the lance connection to the injection nozzle during the injection, which leads to an insufficient replacement of the fuel in the high-pressure accumulator. Replacing the fuel is important, however, so that it does not lead to deposits or the emergence of residues. The risk of deposits or residues exists especially when using high-viscosity fuels, such as heavy oil in large diesel engines.
  • Another disadvantage of the above-described type Sidefeed is that the mouth of the inlet hole in the high-pressure bore, which is usually carried out in the form of a T-connection, is unfavorable strength.
  • the invention therefore aims to avoid the above-mentioned disadvantages, in particular to prevent the formation of deposits and residues in the high pressure accumulator of a modular common rail injector.
  • the invention provides, starting from a device of the type mentioned in essence, that the inlet bore is formed as a separate hole from the high pressure bore, which connects the lance connection with the high-pressure accumulator directly. This ensures that the entire amount of fuel supplied to the injector is passed through the high-pressure accumulator, so that a sufficient replacement of the fuel in the high-pressure accumulator can take place.
  • This fuel guide also promotes the creation of turbulence, resulting in a better ventilation of the high-pressure accumulator.
  • a particularly preferred construction provides that the lance connection is formed on a holding body which is connected, in particular screwed, to the end face of the storage tube forming the high-pressure accumulator.
  • pressure oscillations also lead to strong fluctuations in the injection rate in fast successive injection events. If, for example, a pressure oscillation at the nozzle seat is induced by a pre-injection, then with a constant opening time of the nozzle needle for the second, subsequent injection, the injected quantity depends on whether the second injection occurred earlier in a maximum or in a minimum of the pressure oscillation. The lowest possible pressure oscillation at the injection nozzle in all operating states of the hydraulic system is therefore desirable.
  • WO 2007/143768 A1 One way of reducing pressure pulsations is the WO 2007/143768 A1 can be seen, wherein a parallel to the high-pressure line between the injection nozzle and high-pressure accumulator switched resonator is provided, which has a high-pressure accumulator side Resonatordrossel.
  • the resonator throttle is preferably arranged at the inlet of the resonator line into the high-pressure accumulator.
  • the inventive design is particularly advantageous for injectors to bear, in which the nozzle needle for controlling its opening and closing movement of the prevailing in a fuel-pressurized control chamber pressure in the axial direction can be acted upon, wherein the control chamber with an inlet throttle having inlet channel and a flow channel having an outlet throttle is in communication and at least one inlet or outlet channel opening or closing control valve is provided with which the pressure in the control chamber is controllable.
  • Fig.1 schematically a cross section of an equipped with a high-pressure accumulator injector according to the prior art
  • Fig.2 a schematic representation of the inventive design of the injector.
  • an injector 1 having an injector 2, a throttle plate 3, a valve plate 4, a holding body 5 and a high-pressure accumulator 6, wherein a screwed to the holding body 5 nozzle retaining nut 7, the injection nozzle 2, the throttle plate 3 and the valve plate 4 together.
  • the solenoid valve 13 is closed, so that the high-pressure fuel from the high pressure accumulator 6 via the high pressure line 8, the cross connection 9 and the inlet throttle 10 flows into the control chamber 11 of the injection nozzle 2, the Outflow from the control chamber 11 via the outlet throttle 12 but is blocked at the valve seat of the solenoid valve 13.
  • a resonator is used. This consists of a resonator 20, which is the same length and the same Diameter as the high-pressure line 8, and a resonator 21, which is attached to the memory-side end of the resonator 20 and connects them to the memory 6.
  • the solenoid valve 13 When closing the solenoid valve 13, the pressure pulse generated at the nozzle seat 16 is propagated via the nozzle chamber 19 into the high-pressure line 8 and the resonator line 20.
  • the supply of high-pressure fuel to the high-pressure accumulator 6 takes place at the in Fig. 1 illustrated embodiment of the prior art from the side of the injector 1, via a sidefeed 24.
  • the Sidefeed 24 includes a laterally screwed into the injector 1 lance or a lance connector 25 (only in Fig. 2 shown).
  • the inlet bore is designated 22 and opens at 23 in the high-pressure bore 8.
  • Fig. 2 shows a highly schematic representation of the injector 1, wherein the in Fig.1 Functional components described in more detail, namely the memory 6, the holding body 5, the valve plate 4, the throttle plate 3 and the injection nozzle 2 are only outlined without their individual components, as they are based on the Fig. 1 described individually.
  • Fig. 2 shows the construction according to the invention, in which the inlet bore 22 connects the lance connection 25 directly to the high-pressure accumulator 6. This leads to the fact that with each injection the entire injection quantity is taken from the high-pressure accumulator 6, so that over the running time there is sufficient circulation of the accumulator contents.

Description

Die Erfindung betrifft eine Vorrichtung zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine mit wenigstens einem Injektor, der einen im Injektorkörper integrierten Hochdruckspeicher, eine Einspritzdüse, die eine axial verschieblich geführte Düsennadel umfasst, die von einem Düsenraum umgeben ist, eine den Hochdruckspeicher und den Düsenraum verbindende Hochdruckbohrung und eine Zulaufbohrung, um dem Hochdruckspeicher Hochdruckkraftstoff zuzuführen, umfasst, wobei die Zulaufbohrung einen seitlich am Injektorkörper angeordneten Lanzenanschluss aufweist.The invention relates to a device for injecting fuel into the combustion chamber of an internal combustion engine having at least one injector, which includes a high-pressure accumulator integrated in the injector body, an injection nozzle comprising an axially displaceable nozzle needle, which is surrounded by a nozzle chamber, a high-pressure accumulator and the nozzle chamber connecting high-pressure bore and an inlet bore in order to supply the high-pressure accumulator high-pressure fuel, wherein the inlet bore has a laterally arranged on the injector body lance connection.

Einspritzinjektoren dieser Art werden in modularen Common-Rail-Systemen verwendet, die dadurch gekennzeichnet sind, dass ein Teil des im System vorhandenen Speichervolumens im Injektor selbst vorhanden ist. Modulare Common-Rail-Systeme kommen bei besonders großen Motoren zum Einsatz, bei welchen die einzelnen Injektoren unter Umständen in erheblichem Abstand voneinander angebracht sind. Die alleinige Verwendung eines gemeinsamen Rails für alle Injektoren ist bei solchen Motoren nicht sinnvoll, da es aufgrund der langen Leitungen während der Einspritzung zu einem massiven Einbruch im Einspritzdruck kommen würde, sodass bei längerer Spritzdauer die Einspritzrate merklich einbrechen würde. Bei solchen Motoren ist es daher vorgesehen, einen Hochdruckspeicher im Inneren eines jeden Injektors anzuordnen. Eine solche Bauweise wird als modularer Aufbau bezeichnet, da jeder einzelne Injektor über seinen eigenen Hochdruckspeicher verfügt und somit als eigenständiges Modul eingesetzt werden kann. Unter einem Hochdruckspeicher ist hierbei nicht eine gewöhnliche Leitung zu verstehen, sondern es handelt sich um ein druckfestes Gefäß mit einer Zu- bzw. Ableitung, dessen Durchmesser im Vergleich zu den Hochdruckleitungen deutlich vergrößert ist, damit aus dem Hochdruckspeicher eine gewisse Einspritzmenge abgegeben werden kann, ohne dass es zu einem sofortigen Druckabfall kommt.Injection injectors of this type are used in modular common rail systems, which are characterized in that a part of the existing storage volume in the system is present in the injector itself. Modular common-rail systems are used in particularly large engines, in which the individual injectors may be mounted at a considerable distance from each other. The sole use of a common rail for all injectors is not useful in such engines, as it would come to a massive slump in injection pressure due to the long lines during injection, so with prolonged injection duration, the injection rate would noticeably break. In such engines, it is therefore intended to arrange a high-pressure accumulator inside each injector. Such a design is referred to as a modular structure, since each injector has its own high-pressure accumulator and thus can be used as a stand-alone module. Under a high-pressure accumulator is not a common line to understand, but it is a pressure-resistant vessel with an inlet and outlet, whose Diameter is significantly increased compared to the high pressure lines, so that from the high-pressure accumulator a certain amount of injection can be delivered without causing an immediate pressure drop.

Injektoren von modularen Common-Rail-Systemen wie in der WO 03/076794 wird Hochdruckkraftstoff aus einer Hochdruckpumpe zugeführt, wobei die Zuführung entweder über einen Hochdruckanschluss des Injektors an der Oberseite des Hochdruckspeichers (sogenannter Topfeed) oder über eine den Injektor seitlich kontaktierende Lanze (sogenannter Sidefeed) erfolgt. Beim Sidefeed mündet die Lanze über einen Lanzenanschluss des Injektors in eine Zulaufbohrung, die in die den Hochdruckspeicher mit dem Düsenvorraum verbindende Hochdruckbohrung mündet. Grundsätzlich hat der Sidefeed eine Reihe von Vorteilen, insbesondere bei großbauenden Motoren, da er die Führung des Kraftstofflaufs zum Injektor quer durch den Zylinder erlaubt, wodurch die Länge der Zuführung gegenüber einem Topfeed in der Regel verkürzt werden kann. Allerdings ist der Sidefeed in der herkömmlichen Bauart mit dem Nachteil verbunden, dass der Hochdruckkraftstoff während der Einspritzung direkt vom Lanzenanschluss zur Einspritzdüse fließt, was zu einem unzureichenden Austausch des Kraftstoffs im Hochdruckspeicher führt. Ein Austausch des Kraftstoffs ist jedoch wichtig, damit es nicht zu Ablagerungen oder dem Entstehen von Rückständen kommt. Die Gefahr von Ablagerungen oder Rückständen besteht besonders bei Verwendung von hochviskosen Kraftstoffen, wie z.B. Schweröl in Großdieselmotoren. Ein weiterer Nachteil der oben beschriebenen Bauart mittels Sidefeed ist, dass die Mündungsstelle der Zulaufbohrung in die Hochdruckbohrung, die meist in der Form einer T-Verbindung ausgeführt ist, festigkeitstechnisch ungünstig ist.Injectors of modular common rail systems as in WO 03/076794 High-pressure fuel is supplied from a high-pressure pump, wherein the supply takes place either via a high-pressure port of the injector at the top of the high-pressure accumulator (so-called top feed) or via a laterally contacting the injector lance (so-called Sidefeed). When Sidefeed the lance opens via a lance connection of the injector in an inlet bore, which opens into the high-pressure accumulator connecting the high-pressure reservoir with the nozzle antechamber high pressure bore. Basically, the Sidefeed has a number of advantages, especially in large-scale engines, since it allows the leadership of the fuel flow to the injector across the cylinder, whereby the length of the feed can be shortened compared to a pot feed in the rule. However, the Sidefeed in the conventional design has the disadvantage that the high-pressure fuel flows directly from the lance connection to the injection nozzle during the injection, which leads to an insufficient replacement of the fuel in the high-pressure accumulator. Replacing the fuel is important, however, so that it does not lead to deposits or the emergence of residues. The risk of deposits or residues exists especially when using high-viscosity fuels, such as heavy oil in large diesel engines. Another disadvantage of the above-described type Sidefeed is that the mouth of the inlet hole in the high-pressure bore, which is usually carried out in the form of a T-connection, is unfavorable strength.

Die Erfindung zielt daher darauf ab, die oben genannten Nachteile zu vermeiden, insbesondere die Entstehung von Ablagerungen und Rückständen im Hochdruckspeicher eines modularen Common-Rail-Injektors zu verhindern.The invention therefore aims to avoid the above-mentioned disadvantages, in particular to prevent the formation of deposits and residues in the high pressure accumulator of a modular common rail injector.

Zur Lösung dieser Aufgabe sieht die Erfindung ausgehend von einer Vorrichtung der eingangs genannten Art im Wesentlichen vor, dass die Zulaufbohrung als von der Hochdruckbohrung gesonderte Bohrung ausgebildet ist, die den Lanzenanschluss mit dem Hochdruckspeicher direkt verbindet. Dadurch wird gewährleistet, dass die gesamte Menge des dem Injektor zugeführten Kraftstoffes durch den Hochdruckspeicher geleitet wird, sodass ein ausreichender Austausch des Kraftstoffes im Hochdruckspeicher stattfinden kann. Diese Kraftstoffführung fördert außerdem das Entstehen von Verwirbelungen, wodurch es zu einer besseren Entlüftung des Hochdruckspeichers kommt.To achieve this object, the invention provides, starting from a device of the type mentioned in essence, that the inlet bore is formed as a separate hole from the high pressure bore, which connects the lance connection with the high-pressure accumulator directly. This ensures that the entire amount of fuel supplied to the injector is passed through the high-pressure accumulator, so that a sufficient replacement of the fuel in the high-pressure accumulator can take place. This fuel guide also promotes the creation of turbulence, resulting in a better ventilation of the high-pressure accumulator.

Eine besonders bevorzugte Konstruktion sieht vor, dass der Lanzenanschluss an einem Haltekörper ausgebildet ist, der stirnseitig mit dem den Hochdruckspeicher bildenden Speicherrohr verbunden, insbesondere verschraubt ist.A particularly preferred construction provides that the lance connection is formed on a holding body which is connected, in particular screwed, to the end face of the storage tube forming the high-pressure accumulator.

In einem Common-Rail-System werden elektronisch gesteuerte Einspritzinjektoren zum Einspritzen des Kraftstoffs in den Motorbrennraum verwendet. Die in diesen Injektoren verwendeten Servoventile bewirken ein sehr schnelles Schließen der Einspritzdüse. Beim Schließen der Einspritzdüse läuft der Kraftstoff gegen ein geschlossenes Leitungsende, wobei auf Grund der Trägheit des Kraftstoffes der Druck vor der Einspritzdüse deutlich ansteigt. Diese Druckspitze läuft in der Folge in der Hochdruckbohrung zwischen Einspritzdüse und dem Hochdruckspeicher hin und her, wobei am Düsensitz starke Druckpulsationen entstehen, die hier zu starkem Verschleiß führen. Die dabei auftretenden Druckspitzen liegen in ungünstigen Fällen um bis zu 500 bar über dem Raildruck.In a common rail system, electronically controlled injection injectors are used to inject the fuel into the engine combustion chamber. The servo valves used in these injectors cause a very fast closing of the injector. When closing the injector, the fuel runs against a closed line end, wherein due to the inertia of the fuel, the pressure in front of the injector increases significantly. As a result, this pressure peak reciprocates in the high-pressure bore between the injection nozzle and the high-pressure accumulator, with strong pressure pulsations occurring at the nozzle seat, which lead to excessive wear here. The occurring Pressure peaks are in unfavorable cases up to 500 bar above the rail pressure.

Diese Druckschwingungen führen bei schnell aufeinander folgenden Einspritzvorgängen überdies zu starken Schwankungen der Einspritzrate. Wird zum Beispiel durch eine Voreinspritzung eine Druckschwingung am Düsensitz induziert, so ist bei konstanter Öffnungszeit der Düsennadel für die zweite, nachfolgende Einspritzung die eingespritzte Menge davon abhängig, ob die zweite Einspritzung eher in einem Maximum oder in einem Minimum der Druckschwingung erfolgt ist. Eine möglichst geringe Druckschwingung an der Einspritzdüse in allen Betriebszuständen des hydraulischen Systems ist daher erstrebenswert.These pressure oscillations also lead to strong fluctuations in the injection rate in fast successive injection events. If, for example, a pressure oscillation at the nozzle seat is induced by a pre-injection, then with a constant opening time of the nozzle needle for the second, subsequent injection, the injected quantity depends on whether the second injection occurred earlier in a maximum or in a minimum of the pressure oscillation. The lowest possible pressure oscillation at the injection nozzle in all operating states of the hydraulic system is therefore desirable.

Eine Möglichkeit der Reduktion von Druckpulsationen ist der WO 2007/143768 A1 zu entnehmen, wobei eine parallel zur Hochdruckleitung zwischen Einspritzdüse und Hochruckspeicher geschaltene Resonatorleitung vorgesehen ist, die hochdruckspeicherseitig eine Resonatordrossel aufweist. Bevorzugt ist die Resonatordrossel am Eintritt der Resonatorleitung in den Hochdruckspeicher angeordnet. Die aus der WO 2007/143768 A1 bekannte Ausbildung sieht somit vor, dass die Hochdruckleitung in zwei voneinander unabhängige Bereiche geteilt wird, von denen einer mit einer Drossel ausgestattet ist, sodass die Druckschwingungen, die am Düsensitz entstehen, in beiden Bereichen unterschiedlich reflektiert werden und sich die reflektierten Schwingungen aufgrund ihres Phasenversatzes nahezu auslöschen. Diese Art der Reduktion von Druckpulsen funktioniert bei einer herkömmlichen Kraftstoffzuführung mittels Sidefeed nicht optimal, da hier die seitliche Kraftstoffzufuhr in die Hochdruckbohrung mündet, wobei es an der Einmündungsstelle zu Reflexionen und Überlagerungen von Druckwellen kommt, welche die mit dem beschriebenen Resonatorsystem beabsichtigte Auslöschung von Druckwellen stört. Mit der erfindungsgemäßen Ausbildung, bei der die Zuführung des Kraftstoffes vom Lanzenanschluss direkt in den Hochdruckspeicher erfolgt, wird der störende Einfluss der Mündungsstelle eliminiert, sodass das Resonatorsystem die Druckpulse wesentlich wirksamer reduzieren kann.One way of reducing pressure pulsations is the WO 2007/143768 A1 can be seen, wherein a parallel to the high-pressure line between the injection nozzle and high-pressure accumulator switched resonator is provided, which has a high-pressure accumulator side Resonatordrossel. The resonator throttle is preferably arranged at the inlet of the resonator line into the high-pressure accumulator. The from the WO 2007/143768 A1 known training provides that the high pressure line is divided into two independent areas, one of which is equipped with a throttle, so that the pressure oscillations that arise at the nozzle seat are reflected differently in both areas and the reflected vibrations due to their phase offset almost extinguish. This type of reduction of pressure pulses does not work optimally in a conventional fuel supply by means of Sidefeed, since the lateral fuel supply opens into the high-pressure bore, which comes at the confluence to reflections and superpositions of pressure waves, which interferes with the described resonator system intended extinction of pressure waves , With the invention Training in which the supply of fuel from the lance connection takes place directly into the high pressure accumulator, the disturbing influence of the discharge point is eliminated, so that the resonator system can reduce the pressure pulses much more effective.

Die erfindungsgemäße Ausbildung kommt besonders vorteilhaft bei Injektoren zum Tragen, bei denen die Düsennadel zur Steuerung ihrer Öffnungs- und Schließbewegung von dem in einem mit Kraftstoff unter Druck speisbaren Steuerraum herrschenden Druck in axialer Richtung beaufschlagbar ist, wobei der Steuerraum mit einem eine Zulaufdrossel aufweisenden Zulaufkanal und einem eine Ablaufdrossel aufweisenden Ablaufkanal in Verbindung steht und wenigstens ein den Zu- oder Ablaufkanal öffnendes oder schließendes Steuerventil vorgesehen ist, mit dem der Druck im Steuerraum steuerbar ist.The inventive design is particularly advantageous for injectors to bear, in which the nozzle needle for controlling its opening and closing movement of the prevailing in a fuel-pressurized control chamber pressure in the axial direction can be acted upon, wherein the control chamber with an inlet throttle having inlet channel and a flow channel having an outlet throttle is in communication and at least one inlet or outlet channel opening or closing control valve is provided with which the pressure in the control chamber is controllable.

Die Erfindung wird nachfolgend anhand eines in der Zeichnung schematisch dargestellten Ausführungsbeispiels näher erläutert. In dieser zeigen Fig.1 schematisch einen Querschnitt eines mit einem Hochdruckspeicher ausgestatteten Injektors gemäß dem Stand der Technik und Fig.2 eine schematische Darstellung der erfindungsgemäßen Ausbildung des Injektors.The invention will be explained in more detail with reference to an embodiment schematically illustrated in the drawing. In this show Fig.1 schematically a cross section of an equipped with a high-pressure accumulator injector according to the prior art and Fig.2 a schematic representation of the inventive design of the injector.

In Fig.. 1 ist ein Injektor 1 dargestellt, der eine Einspritzdüse 2, eine Drosselplatte 3, eine Ventilplatte 4, einen Haltekörper 5 und einen Hochdruckspeicher 6 aufweist, wobei eine mit dem Haltekörper 5 verschraubte Düsenspannmutter 7 die Einspritzdüse 2, die Drosselplatte 3 und die Ventilplatte 4 zusammenhält. Im Ruhezustand ist das Magnetventil 13 geschlossen, sodass der Hochdruckkraftstoff aus dem Hochdruckspeicher 6 über die Hochdruckleitung 8, die Querverbindung 9 und die Zulaufdrossel 10 in den Steuerraum 11 der Einspritzdüse 2 strömt, der Abfluss aus dem Steuerraum 11 über die Ablaufdrossel 12 aber am Ventilsitz des Magnetventils 13 blockiert ist. Der im Steuerraum 11 anliegende Systemdruck drückt gemeinsam mit der Kraft der Düsenfeder 14 die Düsennadel 15 in den Düsennadelsitz 16, sodass die Spritzlöcher 17 verschlossen sind. Wird das Magnetventil 13 betätigt, gibt es den Durchfluss über den Magnetventilsitz frei, und Kraftstoff strömt aus dem Steuerraum 11 durch die Ablaufdrossel 12, den Magnetventilankerraum und die Niederdruckbohrung 18 zurück in den nicht dargestellten Kraftstofftank. Es stellt sich ein durch die Strömungsquerschnitte von Zulaufdrossel 10 und Ablaufdrossel 12 definierter Gleichgewichtsdruck im Steuerraum 11 ein, der so gering ist, dass der im Düsenraum 19 anliegende Systemdruck die im Düsenkörper längs verschieblich geführte Düsennadel 15 zu öffnen vermag, sodass die Spritzlöcher 17 freigegeben werden und eine Einspritzung erfolgt.In Fig. 1 an injector 1 is shown having an injector 2, a throttle plate 3, a valve plate 4, a holding body 5 and a high-pressure accumulator 6, wherein a screwed to the holding body 5 nozzle retaining nut 7, the injection nozzle 2, the throttle plate 3 and the valve plate 4 together. In the idle state, the solenoid valve 13 is closed, so that the high-pressure fuel from the high pressure accumulator 6 via the high pressure line 8, the cross connection 9 and the inlet throttle 10 flows into the control chamber 11 of the injection nozzle 2, the Outflow from the control chamber 11 via the outlet throttle 12 but is blocked at the valve seat of the solenoid valve 13. The voltage applied in the control chamber 11 system pressure presses together with the force of the nozzle spring 14, the nozzle needle 15 in the nozzle needle seat 16, so that the injection holes 17 are closed. If the solenoid valve 13 is actuated, it releases the flow through the solenoid valve seat, and fuel flows from the control chamber 11 through the outlet throttle 12, the solenoid valve armature chamber and the low-pressure bore 18 back into the fuel tank, not shown. A equilibrium pressure defined in the control chamber 11 by the flow cross-sections of inlet throttle 10 and outlet throttle 12 is so small that the system pressure applied in the nozzle chamber 19 is able to open the nozzle needle 15, which is displaceable longitudinally in the nozzle body, so that the spray holes 17 are released and an injection takes place.

Sobald das Magnetventil 13 geschlossen wird, wird der Ablaufweg des Kraftstoffes durch die Ablaufdrossel 12 gesperrt. Über die Zulaufdrossel 10 wird im Steuerraum 11 wieder Kraftstoffdruck aufgebaut, was eine zusätzliche Schließkraft erzeugt, welche die hydraulische Kraft auf die Druckschulter der Düsennadel 15 vermindert und die Kraft der Düsenfeder 14 übersteigt. Die Düsennadel 15 verschließt den Weg zu den Einspritzöffnungen 17, wobei der Einspritzvorgang beendet wird.As soon as the solenoid valve 13 is closed, the drainage path of the fuel is blocked by the outlet throttle 12. Via the inlet throttle 10, fuel pressure is again built up in the control chamber 11, which generates an additional closing force which reduces the hydraulic force on the pressure shoulder of the nozzle needle 15 and exceeds the force of the nozzle spring 14. The nozzle needle 15 closes the way to the injection openings 17, wherein the injection process is terminated.

Aufgrund der Massenträgheit des Kraftstoffs in Speicher 6, Hochdruckleitung 8 und Düsenraum 19 kommt es direkt nach dem Schließen der Düsennadel 15 zu starken Druckschwingungen am Düsensitz 16, da der fließende Kraftstoff in sehr kurzer Zeit abgebremst werden muss. Zur Reduktion der Druckschwingungen kommt ein Resonator zum Einsatz. Dieser besteht aus einer Resonatorleitung 20, welche die gleiche Länge und den gleichen Durchmesser wie die Hochdruckleitung 8 aufweist, sowie einer Resonatordrossel 21, die am speicherseitigen Ende der Resonatorleitung 20 angebracht ist und diese mit dem Speicher 6 verbindet. Beim Schließen des Magnetventils 13 pflanzt sich der am Düsensitz 16 entstehende Druckpuls über den Düsenraum 19 in die Hochdruckleitung 8 und die Resonatorleitung 20 fort. Am Ende der Hochdruckleitung 8 erfolgt eine Reflexion des Druckpulses am offenen Ende am Übergang in den Speicher 6. Gleichzeitig wird der in der Resonatorleitung 20 laufende Druckpuls am geschlossenen Ende an der Resonatordrossel 21 reflektiert. Die beiden reflektierten Druckpulse sind aufgrund der unterschiedlichen Reflexionsart (offenes bzw. geschlossenes Ende) um 180° phasenverschoben, sodass sie sich beim Aufeinandertreffen im Düsenraum 19 auslöschen. Dadurch kommt es zu keinen weiteren Druckpulsen am Düsensitz 16, sodass hier deutlich weniger Verschleiß auftritt.Due to the inertia of the fuel in memory 6, high-pressure line 8 and nozzle chamber 19, there are strong pressure oscillations on the nozzle seat 16 directly after closing the nozzle needle 15, since the flowing fuel has to be braked in a very short time. To reduce the pressure oscillations, a resonator is used. This consists of a resonator 20, which is the same length and the same Diameter as the high-pressure line 8, and a resonator 21, which is attached to the memory-side end of the resonator 20 and connects them to the memory 6. When closing the solenoid valve 13, the pressure pulse generated at the nozzle seat 16 is propagated via the nozzle chamber 19 into the high-pressure line 8 and the resonator line 20. At the end of the high pressure line 8, a reflection of the pressure pulse at the open end takes place at the transition into the memory 6. At the same time, the pressure pulse running in the resonator line 20 is reflected at the closed end on the resonator throttle 21. Due to the different reflection modes (open or closed end), the two reflected pressure pulses are phase-shifted by 180 °, so that they cancel each other out when they meet in the nozzle chamber 19. As a result, there are no further pressure pulses on the nozzle seat 16, so that significantly less wear occurs here.

Die Zufuhr von Hochdruckkraftstoff zum Hochdruckspeicher 6 erfolgt bei der in Fig. 1 dargestellten Ausführung gemäß dem Stand der Technik von der Seite des Injektors 1, und zwar über einen Sidefeed 24. Der Sidefeed 24 umfasst eine seitlich in den Injektor 1 eingeschraubte Lanze bzw. einen Lanzenanschluss 25 (nur in Fig. 2 dargestellt). Die Zulaufbohrung ist mit 22 bezeichnet und mündet bei 23 in die Hochdruckbohrung 8. So fließt der Kraftstoff während der Einspritzung des Injektors 1 nicht nur aus dem Hochdruckspeicher 6 zur Einspritzdüse 2, sondern auf Grund des Druckabfalls auch von der Zulaufbohrung 22 direkt zur Einspritzdüse 2. Nach Beendigung der Einspritzung wird der Hochdruckspeicher 6 über den aus der Lanze nachfließenden Kraftstoff wieder aufgefüllt. Somit erfolgt mit dieser nachfließenden Menge lediglich ein kleiner Kraftstoffaustausch im Speicher.The supply of high-pressure fuel to the high-pressure accumulator 6 takes place at the in Fig. 1 illustrated embodiment of the prior art from the side of the injector 1, via a sidefeed 24. The Sidefeed 24 includes a laterally screwed into the injector 1 lance or a lance connector 25 (only in Fig. 2 shown). The inlet bore is designated 22 and opens at 23 in the high-pressure bore 8. Thus, the fuel flows during the injection of the injector 1 not only from the high-pressure accumulator 6 to the injection nozzle 2, but due to the pressure drop from the inlet bore 22 directly to the injection nozzle. 2 After completion of the injection, the high-pressure accumulator 6 is refilled via the fuel flowing from the lance. Thus, with this nachfließenden amount only a small fuel exchange in the memory.

Fig. 2 zeigt eine stark schematisierte Darstellung des Injektors 1, wobei die in Fig.1 näher beschriebenen Funktionskomponenten, nämlich der Speicher 6, der Haltekörper 5, die Ventilplatte 4, die Drosselplatte 3 und die Einspritzdüse 2 nur umrissen sind, ohne deren einzelne Bauteile, wie sie anhand der Fig. 1 beschrieben wurden, einzeln darzustellen. Fig. 2 zeigt die erfindungsgemäße Ausbildung, bei welcher die Zulaufbohrung 22 den Lanzenanschluss 25 direkt mit dem Hochdruckspeicher 6 verbindet. Dies führt dazu, dass bei jeder Einspritzung die gesamte Einspritzmenge aus dem Hochdruckspeicher 6 entnommen wird, sodass es über die Laufzeit zu einer ausreichenden Umwälzung des Speicherinhalts kommt. Fig. 2 shows a highly schematic representation of the injector 1, wherein the in Fig.1 Functional components described in more detail, namely the memory 6, the holding body 5, the valve plate 4, the throttle plate 3 and the injection nozzle 2 are only outlined without their individual components, as they are based on the Fig. 1 described individually. Fig. 2 shows the construction according to the invention, in which the inlet bore 22 connects the lance connection 25 directly to the high-pressure accumulator 6. This leads to the fact that with each injection the entire injection quantity is taken from the high-pressure accumulator 6, so that over the running time there is sufficient circulation of the accumulator contents.

Claims (3)

  1. Device for injecting fuel into the combustion chamber of an internal combustion engine, having at least one injector (1), which has a high-pressure accumulator (6) integrated into the injector body, an injection nozzle (2) that has a nozzle needle (15) which is guided in an axially movable manner and which is surrounded by a nozzle chamber (19), a high-pressure bore (8) connecting the high-pressure accumulator (6) and the nozzle chamber (19), and a feed bore (22) for feeding high-pressure fuel to the high-pressure accumulator (6), wherein the feed bore (22) has a lance connection (25) arranged laterally on the injector body, characterized in that the feed bore (22) is designed as a bore which is separate from the high-pressure bore (8) and connects the lance connection (25) directly to the high-pressure accumulator (6), wherein the lance connection (25) is formed on a holding body (5), which is connected, in particular screwed, at the end to the accumulator tube forming the high-pressure accumulator (6).
  2. Device according to Claim 1, characterized in that a resonator bore (20) is provided, which is arranged in parallel with the high-pressure bore (8), is connected to the injection nozzle (2) and opens into the high-pressure accumulator (6) via a resonator restrictor (21).
  3. Device according to either of Claims 1 and 2, characterized in that, in order to control the opening and closing movement of the nozzle needle (15), said needle can be acted upon in an axial direction by the pressure prevailing in a control space (11) that can be fed with fuel under pressure, wherein the control space (11) is connected to a feed channel (9) having a feed restrictor (10) and to a drain channel having a drain restrictor (12), and at least one control valve (13) that opens or closes the feed or drain channel is provided, by means of which the pressure in the control space (11) can be controlled.
EP13714682.5A 2012-01-26 2013-01-17 Apparatus to inject fuel in the combustion chamber of a combustion engine Active EP2807366B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA105/2012A AT512437B1 (en) 2012-01-26 2012-01-26 DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE
PCT/IB2013/000212 WO2013111008A1 (en) 2012-01-26 2013-01-17 Device for injecting fuel into the combustion chamber of an internal combustion engine

Publications (2)

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EP2807366A1 EP2807366A1 (en) 2014-12-03
EP2807366B1 true EP2807366B1 (en) 2016-01-13

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US (1) US10371111B2 (en)
EP (1) EP2807366B1 (en)
KR (1) KR102009766B1 (en)
AT (1) AT512437B1 (en)
WO (1) WO2013111008A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013013234A1 (en) * 2013-08-08 2015-02-12 Man Diesel & Turbo Se Injector for a fuel supply system of an internal combustion engine and fuel supply system
CN114151251B (en) * 2021-11-19 2023-10-13 哈尔滨工程大学 Liquid ammonia-diesel oil dual-fuel integrated injector

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Publication number Priority date Publication date Assignee Title
US3187733A (en) * 1963-08-23 1965-06-08 Int Harvester Co Fuel injection system for internal combustion engines
DE3119050A1 (en) * 1981-05-05 1982-11-18 Gebrüder Sulzer AG, 8401 Winterthur "FUEL INJECTION DEVICE WITH ELECTROMAGNETICALLY ACTUATED SWITCHING VALVE"
DE3505229A1 (en) * 1985-02-05 1986-08-07 Gebrüder Sulzer AG, Winterthur Device for the injection of a fine particulate, solid fuel suspended in a liquid into the combustion chamber of a reciprocating piston internal combustion engine
US5012786A (en) * 1990-03-08 1991-05-07 Voss James R Diesel engine fuel injection system
JP2000205081A (en) * 1999-01-06 2000-07-25 Usui Internatl Ind Co Ltd Accumulated fuel injection system for diesel internal combustion engine
DE10136157A1 (en) * 2001-05-04 2002-08-29 Mtu Friedrichshafen Gmbh Fuel injector for IC engines of motor vehicles has fuel reservoir of one-piece precision-cast component of hardened steel, fastened to rear of injector housing
DE10210282A1 (en) * 2002-03-08 2003-09-25 Bosch Gmbh Robert Device for injecting fuel into stationary internal combustion engines
DE602004017593D1 (en) * 2004-06-30 2008-12-18 Fiat Ricerche Fuel injection device for an internal combustion engine
ATE488690T1 (en) 2005-07-18 2010-12-15 Ganser Hydromag STORAGE INJECTION SYSTEM FOR INTERNAL COMBUSTION ENGINE
AT503660B1 (en) 2006-06-13 2007-12-15 Bosch Gmbh Robert DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE
DE102006027614B4 (en) * 2006-06-13 2009-02-05 L'orange Gmbh Injection injector for internal combustion engines
AT509405A1 (en) * 2010-01-19 2011-08-15 Bosch Gmbh Robert METHOD FOR TEMPERATING AN INJECTOR OF INJECTION FOR THE INJECTION OF FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE
AT509877B1 (en) * 2010-11-02 2011-12-15 Bosch Gmbh Robert DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE

Also Published As

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EP2807366A1 (en) 2014-12-03
US10371111B2 (en) 2019-08-06
KR20140108581A (en) 2014-09-11
AT512437A1 (en) 2013-08-15
WO2013111008A1 (en) 2013-08-01
AT512437B1 (en) 2014-03-15
KR102009766B1 (en) 2019-08-12
US20140345569A1 (en) 2014-11-27

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