EP2103802B1 - Injector - Google Patents

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Publication number
EP2103802B1
EP2103802B1 EP09100059A EP09100059A EP2103802B1 EP 2103802 B1 EP2103802 B1 EP 2103802B1 EP 09100059 A EP09100059 A EP 09100059A EP 09100059 A EP09100059 A EP 09100059A EP 2103802 B1 EP2103802 B1 EP 2103802B1
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EP
European Patent Office
Prior art keywords
pressure
nozzle needle
nozzle
nozzles
injector according
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Not-in-force
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EP09100059A
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German (de)
French (fr)
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EP2103802A1 (en
Inventor
Olaf Ohlhafer
Sebastian Jansen
Sergey Solovyev
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2103802A1 publication Critical patent/EP2103802A1/en
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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
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0614—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of electromagnets or fixed armature
    • F02M51/0617—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of electromagnets or fixed armature having two or more electromagnets

Definitions

  • the invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • a low pressure port in addition to a high pressure port of the injector, a low pressure port must be provided, can run back through the fuel in a substantially pressure-free tank when the control chamber to open the nozzle needle is to be relieved of pressure.
  • Injectors of this type therefore inherently have a required for the realization of the Düsennadelhubs control flow and optionally a leakage volume flow, which on the one hand, additional system overhead for return lines and on the other hand, an increased flow of the high pressure pump for the fuel are necessary.
  • the WO 99/30029 shows a fuel injector, wherein the injectors are controlled by a small valve member with low mass. This valve member is arranged in a valve member holder in the immediate vicinity of the associated valve seat on the injection nozzles.
  • a control chamber is arranged, the pressure of which acts on the valve member in the closing direction.
  • This control chamber is constantly connected via a throttle with a high pressure fuel source and is connected at the beginning of the injection phase via a pressure actuated by an actuator pressure control valve with a low pressure region, so that the pending on the valve seat high pressure can lift the valve member in the open position.
  • the object of the invention is therefore to reduce the forces required to open an injector, so that the nozzle needle can be actuated directly with the help of comparatively weak actuators.
  • the invention is based on the general idea to provide the nozzle needle for a switchable pressure equalization, such that the hydraulically generated forces on the nozzle needle cancel each other with the appropriate circuit of the pressure compensation valve of the order of magnitude and the nozzle needle their nozzle blocking the closed position can be lifted with correspondingly small forces to inject fuel into the respective combustion chamber.
  • the opening stroke of the nozzle needle can then be effected with weak and only a small volume requiring actuators. Due to the pressure equalization effected with appropriate switching of the pressure compensation valve, the opening stroke of the valve needle is thus "prepared".
  • the opening stroke or the termination of the open position of the nozzle needle is effected by appropriate control of the actuator.
  • the additional space, the pressure of which is controlled by means of the pressure compensation valve, arranged on the input side of the nozzle and in the closed position located nozzle needle or the like via a remaining between the nozzle needle and the inlet side of the nozzle throttle gap is vented into the combustion chamber.
  • Closing the pressure relief valve ensures that a discharge of very small amounts of fuel through the throttle gap and the nozzles in the combustion chamber is sufficient to relieve the additional space from the pressure.
  • the nozzle needle can be configured as a hollow needle with an axial bore communicating with the high-pressure source (common rail) and the pressure compensation valve can be arranged at the nozzle-near end of the axial bore, wherein the valve body of the pressure-compensating valve then expediently controls an outlet which continues the axial bore, which opens into the additional space arranged between the nozzles.
  • the high-pressure source common rail
  • the pressure compensation valve can be arranged at the nozzle-near end of the axial bore, wherein the valve body of the pressure-compensating valve then expediently controls an outlet which continues the axial bore, which opens into the additional space arranged between the nozzles.
  • an electromagnet arrangement is preferably provided which cooperates magnetically with an armature arrangement associated with the nozzle needle and with an armature arrangement assigned to the valve body of the pressure compensation valve.
  • the armature arrangements of the nozzle needle and the pressure compensating valve can be combined with separate electromagnet arrangements, with the possibility in principle of energizing the electromagnet arrangements independently of one another electrically. This increases the flexibility of the injection system. In addition, if necessary, small amounts can be injected in special injection phases by opening only the pressure compensation valve.
  • the electromagnet arrangements can be arranged electrically in series.
  • the injector has an injector body 1, the interior of which is constantly connected to a high-pressure source (common rail) for fuel.
  • the injector body 1 continues downwards into a nozzle body 2, the interior of which communicates with the interior of the injector body 1.
  • the nozzle body 2 has substantially the shape of a tube whose free end is formed by a nozzle tip 3 provided with a cone. These nozzles open into a combustion chamber, not shown, of an internal combustion engine.
  • a nozzle needle 4 which is designed here as a hollow needle and similar to the nozzle body has the shape of a tube whose lower end in the drawing is formed by a conical tip.
  • the seat 5 is arranged radially outside the entrance sides of the nozzles 3. Accordingly, the input sides of the nozzles 3 are shut off from the annular space between the outside of the nozzle needle 4 and the inner periphery of the nozzle body 2 when the nozzle needle 4 is seated on the seat 5.
  • the seat 5 may also be formed as an annular bead, which cooperates sealingly with the apex of the nozzle needle 4.
  • This additional space 6 communicates with the interior of the nozzle needle 4 via a bore 7 which continues the axial bore of the nozzle needle 4 and is controlled by a small, spherical valve body 8 of a pressure compensation valve 7, 8 in the illustrated example.
  • the nozzle needle 4 controlling solenoid assembly 10 cooperates with an arranged at the opposite end of the nozzle needle 4 armature assembly 12, i. the armature assembly 12 is acted upon electrical energization of the solenoid assembly 10 with a force that seeks to lift the nozzle needle 4 from the seat 5.
  • valve body 8 is connected to its associated armature assembly 13 via a central bore of the solenoid assembly 10 passing through rod 14, which is formed by a trained example as a helical compression spring closing spring 15 which is clamped between a flange on the rod 14 and an abutment surface on the solenoid assembly 10, after is biased downward, such that the valve body 8 is brought into the closed position on the associated seat on the bore 7.
  • rod 14 is formed by a trained example as a helical compression spring closing spring 15 which is clamped between a flange on the rod 14 and an abutment surface on the solenoid assembly 10, after is biased downward, such that the valve body 8 is brought into the closed position on the associated seat on the bore 7.
  • the remaining in the closed position of the nozzle needle 4 throttle gap 18 at the input side of the nozzle 3 has, as shown above, on the one hand the function that the additional space 6 can vent with closed pressure compensation valve 9 in the combustion chamber. Furthermore, this throttle gap 18 at the opening pressure compensation valve 7.8 the effect that in the additional space 6 can follow a rapid increase in pressure, because initially due to the throttling effect of the throttle gap 18, only a small proportion of the flowing through the bore 7 and high pressure fuel on the Nozzles 3 flows out. As a result, therefore, a fast opening of the nozzle needle 4 at the beginning of the injection phase is achieved by a very narrow throttle gap 18.
  • the armature assemblies 12 and 13 according to Fig. 3 be actuated by a single solenoid assembly 19.
  • the armature assemblies 12 and 13 according to Fig. 3 arranged coaxially with each other.
  • the closing spring 15 of the pressure compensating valve 7, 8 above the solenoid assembly 19 between a bottom of the injector body 1 and a flange on the rod 14, which passes through a central bore of the solenoid assembly 19, be clamped.
  • the armature assembly 13 of the pressure compensation valve 7.8 in the upper end position (open position) of the nozzle needle 4 and the associated armature assembly 12 has a sufficient axial mobility to open the pressure compensation valve 7.8 or close.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The injector has an inner chamber which is permanently connected with a high pressure source for fuel. The inner chamber is connected with an assigned combustion chamber by a nozzle (3) for fuel injection. A nozzle needle (4) is lifted from the closing position by an assigned actuator and by opening a pressure compensating valve. The nozzle needle is pushed into the inner chamber in its closing position for locking the nozzle by the pressure. The pressure compensating valve is connected with a normal depressurized auxiliary chamber (6) in its opened condition.

Description

Technisches GebietTechnical area

Die Erfindung bezieht sich auf einen Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine entsprechend dem Oberbegriff des Anspruches 1.The invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.

Stand der TechnikState of the art

Es ist bekannt, zur Einbringung von Kraftstoff in direkt einspritzende Dieselmotoren hubgesteuerte Kraftstoffinjektoren einzusetzen. Dies bietet den Vorteil, dass der Einspritzdruck an Last und Drehzahl angepasst werden kann. Die Ansteuerung erfolgt oftmals unter Zwischenschaltung eines Servosteuerraumes, der bei entsprechender Betätigung eines Steuerventils auf sehr hohen Druck, insbesondere den Einspritzdruck des Einspritzsystems, bzw. auf verschwindenden Druck gebracht werden kann. Dieser Druck wirkt auf ein plungerartiges Teil einer die Einspritzdüsen steuernden Düsennadel, wobei die Düsennadel bei hohem Druck die die Einspritzdüsen verschließende Schließlage und bei verschwindendem Druck die die Einspritzdüsen mit einer Hochdruckquelle (Common-Rail) für den einzuspritzenden Kraftstoff verbindende Offenlage einnimmt.It is known to use stroke-controlled fuel injectors for introducing fuel into direct-injection diesel engines. This offers the advantage that the injection pressure can be adapted to load and speed. The control is often carried out with the interposition of a servo control room, which can be brought to a very high pressure, in particular the injection pressure of the injection system, or to vanishing pressure with appropriate actuation of a control valve. This pressure acts on a plunger-like part of a nozzle needle controlling the injectors, wherein the nozzle needle at high pressure occupies the closed position closing the injectors and at vanishing pressure occupies the open nozzle connecting the injectors with a high pressure source (common rail) for the fuel to be injected.

Bei derartigen Injektoren muss neben einem Hochdruckanschluss des Injektors ein Niederdruckanschluss vorhanden sein, über den Kraftstoff in einen im wesentlichen druckfreien Tank zurücklaufen kann, wenn der Steuerraum zur Öffnung der Düsennadel vom Druck entlastet werden soll. Injektoren dieser Art besitzen daher prinzipbedingt einen zur Realisierung des Düsennadelhubs erforderlichen Steuervolumenstrom sowie gegebenenfalls einen Leckvolumenstrom, womit einerseits ein zusätzlicher Systemaufwand für Rückleitungen und andererseits eine erhöhte Förderleistung der Hochdruckpumpe für den Kraftstoff notwendig werden. Die WO 99/30029 zeigt einen Kraftstoffinjektor, bei dem die Einspritzdüsen von einem kleinen Ventilglied mit geringer Masse gesteuert werden. Dieses Ventilglied ist in einem Ventilgliedhalter in unmittelbarer Nähe des zugeordneten Ventilsitzes an den Einspritzdüsen angeordnet. Innerhalb des Ventilgliedhalters ist ein Steuerraum angeordnet, dessen Druck das Ventilglied in Schließrichtung beaufschlagt. Dieser Steuerraum ist ständig über eine Drossel mit einer Kraftstoff-Hochdruckquelle verbunden und wird bei Beginn der Einspritzphase über ein von einem Aktor betätigtes Drucksteuerventil mit einem Niederdruckbereich verbunden, so dass der am Ventilsitz anstehende Hochdruck das Ventilglied in die Offenlage ausheben kann.In such injectors, in addition to a high pressure port of the injector, a low pressure port must be provided, can run back through the fuel in a substantially pressure-free tank when the control chamber to open the nozzle needle is to be relieved of pressure. Injectors of this type therefore inherently have a required for the realization of the Düsennadelhubs control flow and optionally a leakage volume flow, which on the one hand, additional system overhead for return lines and on the other hand, an increased flow of the high pressure pump for the fuel are necessary. The WO 99/30029 shows a fuel injector, wherein the injectors are controlled by a small valve member with low mass. This valve member is arranged in a valve member holder in the immediate vicinity of the associated valve seat on the injection nozzles. Within the valve member holder, a control chamber is arranged, the pressure of which acts on the valve member in the closing direction. This control chamber is constantly connected via a throttle with a high pressure fuel source and is connected at the beginning of the injection phase via a pressure actuated by an actuator pressure control valve with a low pressure region, so that the pending on the valve seat high pressure can lift the valve member in the open position.

Bisher ist es bei Injektoren der eingangs genannten Art nicht möglich, die Düsennadel direkt mit einem elektromagnetischen Aktor zu betätigen. Denn dabei müssen extreme Drücke überwunden werden, so dass der notwendige Bauraum für entsprechend starke Aktoren zu groß wäre.So far it is not possible with injectors of the type mentioned, to actuate the nozzle needle directly with an electromagnetic actuator. Because extreme pressures must be overcome, so that the necessary space for correspondingly strong actuators would be too large.

Offenbarung der ErfindungDisclosure of the invention

Aufgabe der Erfindung ist es nun, die zum Öffnen eines Injektors erforderlichen Kräfte zu reduzieren, so dass die Düsennadel direkt mit Hilfe vergleichsweise schwacher Aktoren betätigt werden kann.The object of the invention is therefore to reduce the forces required to open an injector, so that the nozzle needle can be actuated directly with the help of comparatively weak actuators.

Dies wird durch die kennzeichnenden Merkmale des Anspruches 1 erreicht. Im Ergebnis können auf diese Weise Injektoren hergestellt werden, die ohne Kraftstoffrücklaufleitung auskommen.This is achieved by the characterizing features of claim 1. As a result, injectors can be produced in this way, which manage without fuel return line.

Die Erfindung beruht auf dem allgemeinen Gedanken, an der Düsennadel für einen schaltbaren Druckausgleich zu sorgen, derart, dass die an der Düsennadel hydraulisch erzeugten Kräfte einander bei entsprechender Schaltung des Druckausgleichsventils größenordnungsmäßig aufheben und die Düsennadel aus ihrer die Düsen versperrenden Schließlage mit entsprechend geringen Kräften ausgehoben werden kann, um Kraftstoff in den jeweiligen Brennraum einzuspritzen. Damit kann dann der Öffnungshub der Düsennadel mit schwachen und nur ein geringes Bauvolumen erfordernden Aktoren bewirkt werden. Durch den bei entsprechender Schaltung des Druckausgleichsventils bewirkten Druckausgleich wird also der Öffnungshub der Ventilnadel "vorbereitet". Der Öffnungshub bzw. die Beendigung der Offenstellung der Düsennadel wird durch entsprechende Ansteuerung des Aktors bewirkt.The invention is based on the general idea to provide the nozzle needle for a switchable pressure equalization, such that the hydraulically generated forces on the nozzle needle cancel each other with the appropriate circuit of the pressure compensation valve of the order of magnitude and the nozzle needle their nozzle blocking the closed position can be lifted with correspondingly small forces to inject fuel into the respective combustion chamber. Thus, the opening stroke of the nozzle needle can then be effected with weak and only a small volume requiring actuators. Due to the pressure equalization effected with appropriate switching of the pressure compensation valve, the opening stroke of the valve needle is thus "prepared". The opening stroke or the termination of the open position of the nozzle needle is effected by appropriate control of the actuator.

Gemäß der Erfindung ist vorgesehen, dass der Zusatzraum, dessen Druck mittels des Druckausgleichsventils gesteuert wird, an der Eingangsseite der Düsen angeordnet und bei in Schließlage befindlicher Düsennadel oder dergleichen über einen zwischen Düsennadel und Eingangsseite der Düsen verbleibenden Drosselspalt in den Brennraum entlüftbar ist. Hier wird die Tatsache ausgenutzt, dass zwischen den Einspritzdüsen ein vergleichsweise großer Querschnitt der Düsennadel bei Öffnung des Druckausgleichsventils mit hohem kraftststoffdruck beaufschlagt werden kann. Andererseits ist beimAccording to the invention, it is provided that the additional space, the pressure of which is controlled by means of the pressure compensation valve, arranged on the input side of the nozzle and in the closed position located nozzle needle or the like via a remaining between the nozzle needle and the inlet side of the nozzle throttle gap is vented into the combustion chamber. Here, the fact is exploited that between the injectors a comparatively large cross-section of the nozzle needle can be acted upon opening of the pressure compensation valve with high fuel pressure. On the other hand, at

Schließen des Druckentlastungsventils gewährleistet, dass ein Austritt geringster Kraftstoffmengen über den Drosselspalt und die Düsen in den Brennraum genügt, um den Zusatzraum vom Druck zu entlasten.Closing the pressure relief valve ensures that a discharge of very small amounts of fuel through the throttle gap and the nozzles in the combustion chamber is sufficient to relieve the additional space from the pressure.

Gemäß einer konstruktiv bevorzugten Ausführungsform der Erfindung kann die Düsennadel als Hohlnadel mit einer mit der Hochdruckquelle (Common-Rail) kommunizierenden Axialbohrung ausgebildet und das Druckausgleichsventil am düsennahen Ende der Axialbohrung angeordnet sein, wobei dann der Ventilkörper des Druckausgleichsventils zweckmäßig einen die Axialbohrung fortsetzenden Auslass steuert, der in den zwischen den Düsen angeordneten Zusatzraum mündet. Auf diese Weise wird eine besonders kompakte Bauform des Injektors erreicht.According to a constructively preferred embodiment of the invention, the nozzle needle can be configured as a hollow needle with an axial bore communicating with the high-pressure source (common rail) and the pressure compensation valve can be arranged at the nozzle-near end of the axial bore, wherein the valve body of the pressure-compensating valve then expediently controls an outlet which continues the axial bore, which opens into the additional space arranged between the nozzles. In this way, a particularly compact design of the injector is achieved.

Als Aktor ist vorzugsweise eine Elektromagnetanordnung vorgesehen, die mit einer der Düsennadel zugeordneten Ankeranordnung sowie einer dem Ventilkörper des Druckausgleichsventils zugeordneten Ankeranordnung magnetisch zur Betätigung zusammenwirkt.As an actuator, an electromagnet arrangement is preferably provided which cooperates magnetically with an armature arrangement associated with the nozzle needle and with an armature arrangement assigned to the valve body of the pressure compensation valve.

Dabei besteht einerseits die Möglichkeit, eine einzige Elektromagnetanordnung gemeinsam für Druckausgleichsventil und Düsennadel vorzusehen.On the one hand there is the possibility to provide a single solenoid assembly together for pressure compensation valve and nozzle needle.

Andererseits können die Ankeranordnungen von Düsennadel und Druckausgleichsventil mit gesonderten Elektromagnetanordnungen kombiniert sein, wobei grundsätzlich die Möglichkeit besteht, die Elektromagnetanordnungen unabhängig voneinander elektrisch zu bestromen. Damit wird die Flexibilität des Einspritzsystems erhöht. Außerdem können gegebenenfalls in besonderen Einspritzphasen Kleinstmengen eingespritzt werden, indem nur das Druckausgleichsventil geöffnet wird.On the other hand, the armature arrangements of the nozzle needle and the pressure compensating valve can be combined with separate electromagnet arrangements, with the possibility in principle of energizing the electromagnet arrangements independently of one another electrically. This increases the flexibility of the injection system. In addition, if necessary, small amounts can be injected in special injection phases by opening only the pressure compensation valve.

Bei einer weiteren Variante können die Elektromagnetanordnungen elektrisch in Reihe liegen.In a further variant, the electromagnet arrangements can be arranged electrically in series.

Im übrigen wird hinsichtlich bevorzugter Merkmale der Erfindung auf die Ansprüche und die nachfolgende Erläuterung der Zeichnung verwiesen, anhand der bevorzugte Ausführungen der Erfindung näher beschrieben werden.Moreover, with regard to preferred features of the invention to the claims and the following explanation of the drawing, reference is made to the preferred embodiments of the invention.

Erläuterung der ZeichnungExplanation of the drawing

In der Zeichnung zeigt:

Fig. 1
eine Serie von Schnittbildern A bis E verschiedener Betriebszustände eines erfindungsgemäßen Injektors,
Fig. 2
die Einzelheit II in Fig. 1 und
Fig. 3
ein Schnittbild einer gegenüber Fig. 1 abgewandelten Ausführungsform des erfindungsgemäßen Injektors.
In the drawing shows:
Fig. 1
a series of sectional images A to E of different operating states of an injector according to the invention,
Fig. 2
the detail II in Fig. 1 and
Fig. 3
a cross-sectional view of one opposite Fig. 1 modified embodiment of the injector according to the invention.

Gemäß Fig. 1 besitzt der Injektor einen Injektorkörper 1, dessen Innenraum ständig mit einer Hochdruckquelle (Common-Rail) für Kraftstoff verbunden ist. Der Injektorkörper 1 setzt sich in der Zeichnung nach unten in einen Düsenkörper 2 fort, dessen Innenraum mit dem Innenraum des Injektorkörpers 1 kommuniziert. Der Düsenkörper 2 hat im wesentlichen die Form eines Rohres, dessen freies Ende durch eine mit Düsen 3 versehene Kegelspitze gebildet wird. Diese Düsen münden in einen nicht dargestellten Brennraum einer Brennkraftmaschine.According to Fig. 1 the injector has an injector body 1, the interior of which is constantly connected to a high-pressure source (common rail) for fuel. In the drawing, the injector body 1 continues downwards into a nozzle body 2, the interior of which communicates with the interior of the injector body 1. The nozzle body 2 has substantially the shape of a tube whose free end is formed by a nozzle tip 3 provided with a cone. These nozzles open into a combustion chamber, not shown, of an internal combustion engine.

Zur Steuerung der Düsen dient eine Düsennadel 4, die hier als Hohlnadel ausgebildet ist und ähnlich wie der Düsenkörper die Form eines Rohres aufweist, dessen in der Zeichnung unteres Ende durch eine Kegelspitze gebildet wird. Wenn die Düsennadel 4 ihre untere Endlage einnimmt, sitzt sie mit einer ringförmigen Kante am Übergang zur unteren Kegelspitze auf einem ringförmigen Sitz 5 auf der Innenseite der Kegelspitze des Düsenkörpers 2 dicht auf. Der Sitz 5 ist radial außerhalb der Eingangsseiten der Düsen 3 angeordnet. Dementsprechend sind die Eingangsseiten der Düsen 3 vom Ringraum zwischen der Außenseite der Düsennadel 4 und dem Innenumfang des Düsenkörpers 2 abgesperrt, wenn die Düsennadel 4 auf dem Sitz 5 aufsitzt. Gegebenenfalls kann der Sitz 5 auch als Ringwulst ausgebildet sein, der mit der Kegelspitze der Düsennadel 4 dichtend zusammenwirkt.To control the nozzle is a nozzle needle 4, which is designed here as a hollow needle and similar to the nozzle body has the shape of a tube whose lower end in the drawing is formed by a conical tip. When the nozzle needle 4 assumes its lower end position, it sits tightly with an annular edge at the transition to the lower cone tip on an annular seat 5 on the inside of the apex of the nozzle body 2. The seat 5 is arranged radially outside the entrance sides of the nozzles 3. Accordingly, the input sides of the nozzles 3 are shut off from the annular space between the outside of the nozzle needle 4 and the inner periphery of the nozzle body 2 when the nozzle needle 4 is seated on the seat 5. Optionally, the seat 5 may also be formed as an annular bead, which cooperates sealingly with the apex of the nozzle needle 4.

Zwischen der Außenseite der Kegelspitze der Düsennadel 4 und der Innenseite der Kegelspitze des Düsenkörpers 2 verbleibt ein Zusatzraum 6, dessen Zweck weiter unten erläutert wird. Dieser Zusatzraum 6 kommuniziert mit dem Innenraum der Düsennadel 4 über eine die Axialbohrung der Düsennadel 4 fortsetzende Bohrung 7, die durch einen im dargestellten Beispiel kleinen, kugelförmigen Ventilkörper 8 eines Druckausgleichsventils 7,8 gesteuert wird.Between the outside of the apex of the nozzle needle 4 and the inside of the apex of the nozzle body 2 remains an additional space 6, the purpose of which will be explained below. This additional space 6 communicates with the interior of the nozzle needle 4 via a bore 7 which continues the axial bore of the nozzle needle 4 and is controlled by a small, spherical valve body 8 of a pressure compensation valve 7, 8 in the illustrated example.

Zur Betätigung der Düsennadel 4 bzw. des Ventilkörpers 8 dienen im Injektorkörper 1 axial hintereinander angeordnete ringförmige Elektromagnetanordnungen 10 und 11. Die die Düsennadel 4 steuernde Elektromagnetanordnung 10 wirkt mit einem am zugewandten Ende der Düsennadel 4 angeordneten Ankeranordnung 12 zusammen, d.h. die Ankeranordnung 12 wird bei elektrischer Bestromung der Elektromagnetanordnung 10 mit einer Kraft beaufschlagt, die die Düsennadel 4 vom Sitz 5 abzuheben sucht. Der Ventilkörper 8 ist mit seiner zugeordneten Ankeranordnung 13 über eine die Zentralbohrung der Elektromagnetanordnung 10 durchsetzende Stange 14 verbunden, die von einer beispielsweise als Schraubendruckfeder ausgebildeten Schließfeder 15, die zwischen einem Flansch an der Stange 14 und einer Widerlagerfläche an der Elektromagnetanordnung 10 eingespannt ist, nach abwärts gespannt wird, derart, dass der Ventilkörper 8 in Schließlage auf dem zugeordneten Sitz an der Bohrung 7 gebracht wird.For actuating the nozzle needle 4 and the valve body 8 are used in the injector 1 axially successively arranged annular electromagnet assemblies 10 and 11. The nozzle needle 4 controlling solenoid assembly 10 cooperates with an arranged at the opposite end of the nozzle needle 4 armature assembly 12, i. the armature assembly 12 is acted upon electrical energization of the solenoid assembly 10 with a force that seeks to lift the nozzle needle 4 from the seat 5. The valve body 8 is connected to its associated armature assembly 13 via a central bore of the solenoid assembly 10 passing through rod 14, which is formed by a trained example as a helical compression spring closing spring 15 which is clamped between a flange on the rod 14 and an abutment surface on the solenoid assembly 10, after is biased downward, such that the valve body 8 is brought into the closed position on the associated seat on the bore 7.

Wird die Elektromagnetanordnung 11 bestromt, wird die Ankeranordnung 13 in Fig. 1 nach aufwärts gezogen, und der Ventilkörper 8 des Druckausgleichsventils 7,8 gibt die Bohrung 7 frei, so dass der Zusatzraum 6 mit dem Innenraum der Düsennadel 4 und damit mit dem unter Hochdruck stehenden Innenraum des Injektorkörpers 1 Verbindung hat.If the solenoid assembly 11 is energized, the armature assembly 13 in Fig. 1 pulled upwards, and the valve body 8 of the pressure compensating valve 7.8 are the bore 7 free, so that the additional space 6 with the interior of the nozzle needle 4 and thus with the high pressure inside the injector body 1 has connection.

Der dargestellte Injektor der Fig. 1 funktioniert wie folgt:

  • Die Elektromagnetanordnungen 10 und 11 sind elektrisch in Reihe geschaltet und können dementsprechend gemeinsam mittels einer elektrischen Spannungsquelle 16 bestromt werden, wenn ein Schalter 17 geschlossen wird. Zunächst möge dieser Schalter gemäß Bild A offen sein, d.h. die Elektromagnetanordnungen 10 und 11 sind ohne elektrischen Strom, und die Düsennadel 4 sowie der Ventilkörper 8 des Druckausgleichsventils 7,8 werden vom hydraulischen Druck im Injektorkörper 1 bzw. im Düsenkörper 2 auf ihre jeweiligen Sitze gedrängt. In dieser Phase ist der Zusatzraum 6 in den am Düsenausgang angeschlossenen Brennraum entlüftet, da gemäß Fig. 2 zwischen der Außenseite des Kegels der Düsennadel 4 und der ringwulstförmigen Eingangsseite der Düsen 3 ein schmaler Drosselspalt 18 offen bleibt. Zu Beginn einer gewünschten Einspritzphase werden die Elektromagnetanordnungen 10 und 11 durch Schließen des Schalters 17 elektrisch bestromt. Aufgrund seines kleinen Querschnittes kann der Ventilkörper 8 des Druckausgleichsventils 7,8 sofort von den zwischen der Elektromagnetanordnung 11 und der Ankeranordnung 13 wirksamen Magnetkräften aus seinem Sitz ausgehoben werden. Damit wird der Zusatzraum 6 über die Bohrung 7 mit hohem Druck aufgeladen, derart, dass die zwischen der Ankeranordnung 12 und der Elektromagnetanordnung 10 wirkenden magnetischen Kräfte in Verbindung mit den hydraulischen Druckkräften im Zusatzraum 6 ausreichen, die Düsennadel 4 aus ihren Sitz 5 auszuheben. Dieser Zustand ist im Bild C dargestellt. Damit kommuniziert die Eingangsseite der Düsen 3 über den Innenraum des Düsenkörpers 2 mit dem Innenraum des Injektorkörpers 1, und Kraftstoff wird über die Düsen 3 in den angeschlossenen Brennraum eingespritzt.
The injector shown Fig. 1 works as follows:
  • The electromagnet assemblies 10 and 11 are electrically connected in series and can accordingly be energized together by means of an electrical voltage source 16 when a switch 17 is closed. First of all, this switch should be open according to picture A, ie the solenoid assemblies 10 and 11 are without electric current, and the nozzle needle 4 and the valve body 8 of the pressure compensating valve 7, 8 are actuated by the hydraulic pressure in the injector body 1 and in the nozzle body 2, respectively crowded. In this phase, the additional space 6 is in the combustion chamber connected to the nozzle outlet vented, according to Fig. 2 between the outside of the cone of the nozzle needle 4 and the annular bulge-shaped input side of the nozzle 3, a narrow throttle gap 18 remains open. At the beginning of a desired injection phase, the electromagnet assemblies 10 and 11 are electrically energized by closing the switch 17. Due to its small cross section, the valve body 8 of the pressure compensating valve 7,8 can be immediately lifted out of its seat by the magnetic forces acting between the electromagnet assembly 11 and the armature assembly 13. Thus, the additional space 6 is charged via the bore 7 at high pressure, such that the forces acting between the armature assembly 12 and the solenoid assembly 10 magnetic forces in conjunction with the hydraulic pressure forces in the additional space 6 sufficient to lift the nozzle needle 4 from its seat 5. This condition is shown in Figure C. Thus, the input side of the nozzles 3 communicates with the interior of the injector body 1 via the interior of the nozzle body 2, and fuel is injected via the nozzles 3 into the connected combustion chamber.

Zur Beendigung der Einspritzphase wird der Schalter 17 wieder geöffnet, so dass die Bestromung der Elektromagnetanordnungen 10 und 11 beendet wird. Dies führt gemäß Bild D zunächst dazu, dass der Ventilkörper 8 des Druckausgleichsventils 7,8 wieder seine Schließlage einnimmt und die Bohrung 7 zum Zusatzraum 6 absperrt. Dies hat des weiteren zur Folge, dass die Düsennadel 4 vom hydraulischen Druck im Injektorkörper 1 bzw. im Düsenkörper 2 sowie durch die Kraft der Schließfeder 15 in Schließrichtung belastet wird und auf dem Sitz 5 aufsetzt, sobald sich der Zusatzraum 6 über die Düsen 3 hinreichend entleert hat. Damit wird der Zustand des Bildes E bzw. A erreicht.To end the injection phase of the switch 17 is opened again, so that the energization of the solenoid assemblies 10 and 11 is terminated. This leads according to Figure D initially to the fact that the valve body 8 of the pressure compensating valve 7,8 again assumes its closed position and the hole 7 to the additional space 6 shuts off. This also has the consequence that the nozzle needle 4 is loaded by the hydraulic pressure in the injector 1 and the nozzle body 2 and by the force of the closing spring 15 in the closing direction and touches on the seat 5, as soon as the additional space 6 on the nozzles 3 sufficient has emptied. Thus, the state of the image E or A is achieved.

Der in Schließlage der Düsennadel 4 verbleibende Drosselspalt 18 an der Eingangsseite der Düsen 3 hat, wie oben dargestellt wurde, einerseits die Funktion, dass sich der Zusatzraum 6 bei geschlossenem Druckausgleichsventil 9 in den Brennraum entlüften kann. Des Weiteren hat dieser Drosselspalt 18 bei öffnendem Druckausgleichsventil 7,8 die Wirkung, dass im Zusatzraum 6 ein schneller Druckanstieg folgen kann, weil zunächst aufgrund der Drosselwirkung des Drosselspaltes 18 nur ein geringer Anteil des durch die Bohrung 7 zuströmenden und unter Hochdruck stehenden Kraftstoffes über die Düsen 3 abströmt. Im Ergebnis wird also durch einen sehr engen Drosselspalt 18 ein schnelles Öffnen der Düsennadel 4 zu Beginn der Einspritzphase erreicht.The remaining in the closed position of the nozzle needle 4 throttle gap 18 at the input side of the nozzle 3 has, as shown above, on the one hand the function that the additional space 6 can vent with closed pressure compensation valve 9 in the combustion chamber. Furthermore, this throttle gap 18 at the opening pressure compensation valve 7.8 the effect that in the additional space 6 can follow a rapid increase in pressure, because initially due to the throttling effect of the throttle gap 18, only a small proportion of the flowing through the bore 7 and high pressure fuel on the Nozzles 3 flows out. As a result, therefore, a fast opening of the nozzle needle 4 at the beginning of the injection phase is achieved by a very narrow throttle gap 18.

Bei der vorangegangenen Funktionsbeschreibung wurde davon ausgegangen, dass die Elektromagnetanordnungen 10 und 11 simultan bestromt bzw. simultan vom elektrischen Strom abgeschaltet werden. Dies ist nicht zwingend notwendig. Vielmehr ist es auch möglich und vorteilhaft, die Elektromagnetanordnungen 10 und 11 separat voneinander elektrisch bestromen zu können.In the previous functional description, it was assumed that the electromagnet arrangements 10 and 11 are simultaneously energized or simultaneously disconnected from the electrical current. This is not mandatory. Rather, it is also possible and advantageous to be able to energize the electromagnet assemblies 10 and 11 separately from each other electrically.

Beispielsweise besteht die Möglichkeit, in bestimmten Phasen nur die Elektromagnetanordnung 11 zur Betätigung des Druckausgleichsventils 7,8 zu bestromen. Damit öffnet nur das Druckausgleichsventil 7,8, so dass die Düsen 3 nur über die Bohrung 7, den Zusatzraum 6 und den Drosselspalt 18 mit Kraftstoff beliefert werden. Auf diese Weise besteht die Möglichkeit, in besonderen Einspritzphasen ganz geringe Kraftstoffmengen reproduzierbar einzuspritzen.For example, it is possible to energize in certain phases only the solenoid assembly 11 for actuating the pressure compensation valve 7.8. This only opens the pressure compensation valve 7.8, so that the nozzles 3 are supplied with fuel only via the bore 7, the additional space 6 and the throttle gap 18. In this way, it is possible to inject very small amounts of fuel reproducibly in special injection phases.

Gegebenenfalls können die Ankeranordnungen 12 und 13 gemäß Fig. 3 auch von einer einzigen Elektromagnetanordnung 19 betätigt werden. Dazu sind die Ankeranordnungen 12 und 13 gemäß Fig. 3 koaxial zueinander angeordnet. In diesem Fall kann die Schließfeder 15 des Druckausgleichsventils 7,8 oberhalb der Elektromagnetanordnung 19 zwischen einem Boden des Injektorkörpers 1 und einem Flansch an der Stange 14, die eine Zentralbohrung der Elektromagnetanordnung 19 durchsetzt, eingespannt sein. Wichtig ist, dass die Ankeranordnung 13 des Druckausgleichsventils 7,8 auch in der oberen Endlage (Offenlage) der Düsennadel 4 und der zugeordneten Ankeranordnung 12 eine hinreichende axiale Beweglichkeit hat, um das Druckausgleichsventil 7,8 öffnen bzw. schließen zu können.Optionally, the armature assemblies 12 and 13 according to Fig. 3 be actuated by a single solenoid assembly 19. For this purpose, the armature assemblies 12 and 13 according to Fig. 3 arranged coaxially with each other. In this case, the closing spring 15 of the pressure compensating valve 7, 8 above the solenoid assembly 19 between a bottom of the injector body 1 and a flange on the rod 14, which passes through a central bore of the solenoid assembly 19, be clamped. It is important that the armature assembly 13 of the pressure compensation valve 7.8 in the upper end position (open position) of the nozzle needle 4 and the associated armature assembly 12 has a sufficient axial mobility to open the pressure compensation valve 7.8 or close.

Claims (8)

  1. Injector for injecting fuel into a combustion chamber of an internal combustion engine, having an interior space which is permanently connected to a high-pressure source for fuel and which can be connected to the associated combustion chamber, for the purpose of injecting fuel, via nozzles (3) which are controlled by a nozzle needle (4) or the like, with it being possible for the nozzle needle (4) or the like, which is forced by the pressure in the interior space into its closed position in which it shuts off the nozzles (3), to be raised out of the closed position by means of an associated actuator (10) and by means of the opening, effected initially by the actuator (10), of a pressure compensating valve (7, 8) which, in its open state, connects the interior space to a secondary chamber (6) which is normally substantially unpressurized when the pressure compensating valve (7, 8) is closed and whose pressure seeks to raise the nozzle needle (4) or the like out of its closed position, characterized in that the secondary chamber (6) is arranged at the inlet side of the nozzles (3) and, when the nozzle needle (4) or the like is situated in the closed position, can be ventilated into the combustion chamber via a throttle gap (18) which remains between the nozzle needle (4) and the inlet side of the nozzles (3).
  2. Injector according to Claim 1,
    characterized in that the nozzle needle (4) is designed as a hollow needle with an axial bore which communicates with the high-pressure source, and the pressure compensating valve (7, 8) is arranged at the nozzle-side end of the axial bore.
  3. Injector according to Claim 2,
    characterized in that the valve body (8) of the pressure compensating valve (7, 8) controls an outlet (7) which forms a continuation of the axial bore and which opens out into the secondary chamber (6) arranged between the inlets of the nozzles (3).
  4. Injector according to one of Claims 1 to 3, characterized in that an electromagnet arrangement (10,11) is arranged in the interior space, which electromagnet arrangement interacts with an armature arrangement (12) arranged on the nozzle needle (4) and with an armature arrangement (13) assigned to the pressure compensating valve (7, 8).
  5. Injector according to Claim 4,
    characterized in that separate electromagnets (10,11) which can be separately supplied with electrical current are provided for the armature arrangements (12, 13).
  6. Injector according to Claim 4,
    characterized in that a single electromagnet (19) interacts with both armature arrangements (12, 13).
  7. Injector according to one of Claims 1 to 6, characterized in that the valve body (8) of the pressure compensating valve (7, 8) is formed with a small cross section which is loaded in the closing direction by hydraulic pressure, and said cross section is smaller in terms of order of magnitude than the cross section of the nozzle needle (4).
  8. Injector according to one of Claims 1 to 7, characterized in that the interior space is connected to a common rail which forms the high-pressure source.
EP09100059A 2008-03-17 2009-01-22 Injector Not-in-force EP2103802B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008000702A DE102008000702A1 (en) 2008-03-17 2008-03-17 injector

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EP2103802A1 EP2103802A1 (en) 2009-09-23
EP2103802B1 true EP2103802B1 (en) 2011-01-19

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EP09100059A Not-in-force EP2103802B1 (en) 2008-03-17 2009-01-22 Injector

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EP (1) EP2103802B1 (en)
AT (1) ATE496216T1 (en)
DE (2) DE102008000702A1 (en)
ES (1) ES2358869T3 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008042227A1 (en) 2008-09-19 2010-04-01 Robert Bosch Gmbh Fuel injector, particularly common rail injector for injecting fuel into combustion chamber of internal-combustion engine, comprises injection valve element, which is adjustable between closing position and opening position
DE102010030037A1 (en) 2010-06-14 2011-12-15 Robert Bosch Gmbh Injector
DE102010030385A1 (en) 2010-06-23 2011-12-29 Robert Bosch Gmbh Injection valve for injecting fuel into combustion chamber of combustion engine, has axially movable pressure equalization piston included within hollow needle such that combustion and pressure chambers are axially limited
DE102014203640A1 (en) * 2014-02-28 2015-09-03 Robert Bosch Gmbh fluid injector
DE102018219311A1 (en) 2018-11-13 2020-05-14 Robert Bosch Gmbh Injector with a hollow needle

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3344229A1 (en) * 1983-12-07 1985-06-20 Pierburg Gmbh & Co Kg, 4040 Neuss ELECTROMAGNETIC FUEL INJECTION VALVE
DE19754050A1 (en) 1997-12-05 1999-07-15 Orange Gmbh Injector for intermittent fuel injection
EP1612401B1 (en) * 2004-06-30 2008-11-05 C.R.F. Società Consortile per Azioni An injection system for an internal combustion engine
DE102006055792A1 (en) * 2006-11-27 2008-05-29 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

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EP2103802A1 (en) 2009-09-23
DE102008000702A1 (en) 2009-09-24
ES2358869T3 (en) 2011-05-16
ATE496216T1 (en) 2011-02-15
DE502009000293D1 (en) 2011-03-03

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