EP1379776B1 - Injector nozzle with throttling action - Google Patents

Injector nozzle with throttling action Download PDF

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Publication number
EP1379776B1
EP1379776B1 EP02740226A EP02740226A EP1379776B1 EP 1379776 B1 EP1379776 B1 EP 1379776B1 EP 02740226 A EP02740226 A EP 02740226A EP 02740226 A EP02740226 A EP 02740226A EP 1379776 B1 EP1379776 B1 EP 1379776B1
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EP
European Patent Office
Prior art keywords
nozzle needle
nozzle
fuel
needle
fuel injector
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP02740226A
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German (de)
French (fr)
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EP1379776A2 (en
Inventor
Friedrich Boecking
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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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging orifices
    • F02M61/163—Means being injection-valves with helically or spirally shaped grooves
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies

Definitions

  • injectors For injecting fuel into the combustion chambers of an internal combustion engine injectors are used, at which the start of injection and the injection quantity are adjusted by electrical control by means of a solenoid valve or a piezoelectric actuator. Injectors injectors are included. The injectors hold the injectors, which are tuned to the respective conditions of the internal combustion engine on which they are used.
  • the design of the injection nozzle is crucial for the metered injection in terms of injection duration and injection quantity per degree crank angle and with regard to the preparation of the fuel with respect to injection jet shape and atomization of the fuel in the combustion chamber.
  • GB 2 335 000 refers to a fuel injector with a restricted fuel feed to a needle valve.
  • the fuel injector comprises a nozzle needle which is slidably received in a bore provided in a nozzle body.
  • the nozzle needle forms with the injector both a fuel reservoir and a fuel receiving chamber for the pending under high pressure fuel.
  • a flow channel system is provided for the fuel, which is the inlet limited to the fuel. If the nozzle needle is in an open position, fuel flows in the direction of the reservoir. On the other hand, if the nozzle needle moves upwards in the injector body, then a heightened volume of fuel flows in the direction of the injection nozzle
  • a fuel injector in which, within a gap surrounding the nozzle needle on the nozzle needle, a collar is formed, which forms, for example, an annular gap with the wall of the intermediate space.
  • the annular gap acts as a throttle. From the intermediate space, the fuel passes along flow surfaces on the nozzle needle either into a nozzle space and from there via a gap to the injection opening or else directly to the injection opening.
  • the solution according to the invention causes a faster closing of the nozzle needle, which can be avoided in particular by increased needle portions of hydrocarbon fractions in the exhaust gas of internal combustion engines.
  • the hitherto occurring higher HC components in the exhaust gas of an internal combustion engine touched last but not least that at a comparatively slow expiring needle closing through the still open injector fuel into the combustion chamber, but could not be burned because the combustion has already largely expired against needle closing is. If a faster needle closure is achieved by means of the solution according to the invention, the increase of the HC content in the exhaust gas of the internal combustion engine can be avoided.
  • a fast adjusting the nozzle needle forming the injection curve. i.e. its adaptation to the running in the combustion chamber combustion, in terms of Zündverznges, better reproducible.
  • the thrust bearing proposed according to the invention can be embodied both as a region of the nozzle needle which has a larger diameter and as a projection guided in the injector housing at a small distance at the nozzle needle circumference.
  • the throttle point - preferably designed as a throttle section - can be formed below a guide portion on the nozzle needle; Furthermore, the throttle section can be integrated in the guide section on the nozzle needle.
  • the arrangement of the thrust point below a guide portion or in the alternative integrated into this, has the advantageous effect that is avoided by the proximity of the thruster to the guide portion deflecting the nozzle needle from the centered position.
  • a deflection of the nozzle needle transversely to the nozzle needle axis would result in a large deviation of the flow rate, which however is ruled out due to the solution proposed according to the invention.
  • FIG. 1 is an injector of a Kraftstoffinjekiors removed, which can be controlled by a solenoid valve.
  • An injector 1 for injecting fuel into the combustion chambers of a combustion engine comprises an injector body 2 in which a nozzle needle 5 is received.
  • a high-pressure bore 3 is formed, via which a nozzle chamber 4 can be acted upon by high-pressure fuel.
  • the high-pressure bore 3 communicates with a high-pressure accumulation space (common rail), not shown here, in which a largely constant high pressure is generated.
  • the nozzle needle 5 comprises a first guide portion 6 and a second guide portion 7, with which it is guided in the injector body 2.
  • a pressure stage 8 is formed on the nozzle needle 5.
  • a feed ring 9 connects, which is designed in diameter 10.
  • the second guide section 7 is formed on the nozzle needle 5.
  • flow surfaces 20 may be integrated for the fuel to ensure flow of the fuel from the nozzle chamber 4 via the inlet ring 9 to the nozzle tip.
  • the injector body 2 is formed in the region of the second guide section 7 in a slightly reduced diameter 11.
  • the injector body 2 as shown in FIG. 1 goes over into a nozzle body 16.
  • the bore in the nozzle body 16, which encloses the nozzle needle 5, is designed in the region of the second guide section 7 with a smaller diameter, so that it is ensured that the nozzle needle 5 is guided in the nozzle-side region only within the second guide section 7.
  • the throttle point 17 is preferably designed as a throttle section, which extends in the axial direction of the nozzle needle 5 over a gap height h 1 (reference numeral 19). Between the nozzle body 16 and the throttling point 17, which, as shown in FIG. 1 is formed as a nozzle needle 5, a gap width 18, via which the throttling effect is adjustable depending on the design of the throttle point 17. Preferably, by means of the solution proposed according to the invention, throttle effects between 0.2 and 7% will be realized.
  • a conical seat 14 is formed on the latter.
  • the nozzle needle tip 12 In the lower region of the injection nozzle 12, which is preferably designed as a suction nozzle, a conical seat 14 is formed on the latter.
  • the nozzle needle tip 12 In the closed state of the nozzle needle 5 is the nozzle needle tip 12 with its seat 14 on the nozzle seat 13, which is formed on the nozzle needle 5 facing wall of the nozzle body 16.
  • the nozzle needle 5 is driven with its nozzle needle tip 12 into the nozzle seat 13, so that the injection port 15, which projects into the combustion chamber of an internal combustion engine, is closed by the nozzle tip 15.
  • the throttling action only occurs when the nozzle needle 5 is driven into the control chamber (not shown here), which results in a pressure drop at the nozzle needle tip 12, which can be advantageously utilized for rapid needle closure by pressurizing the control chamber associated with the nozzle needle 5.
  • the representation according to FIG. 2 is an embodiment of the present invention proposed solution with overflow can be seen above a thrust point.
  • a nozzle needle 30 is movably received in the vertical direction.
  • a first guide portion 6 and a second guide portion 7 is formed.
  • a high-pressure bore 3 is formed, which opens into a nozzle chamber 4.
  • the high-pressure bore 3 communicates with a high-pressure collecting chamber (common rail), not shown.
  • an overflow channel system 31 is formed, which is surrounded by a substantially pressurized fuel nozzle space 4.
  • Below the overflow channel system 31 is analogous to the representation of the nozzle needle 5 in FIG. 1 at the nozzle needle 30 a thrust point 17 is formed.
  • Throttling point 17 as shown in FIG. 2 is preferably carried out on the nozzle needle 30 as a throttle section, which extends in an axial gap height 19 in the axial direction of the nozzle needle 30. Between the second guide section 7 surrounding bore of the nozzle body 16 and the throttle point, a gap width 19, over which depending on the design, the throttle effect can be varied. Underneath the throttling point 17 is a nozzle needle 30 as shown in FIG FIG. 2 a seat diameter 14 is formed, which is retracted into a nozzle seat 13 in the nozzle body 16 of the injector body 2. Im in FIG. 2 reproduced state is the injection port 15, which projects into the combustion chamber of an internal combustion engine, closed by the nozzle needle tip 12, which has moved into its nozzle seat 13.
  • the overflow 31 with an inclination 32 resulting in a limitation of adjusting in the direction of the nozzle needle tip 12 fuel flow.
  • the Androsselstelle 17 causes a pressure drop in the nozzle needle tip 12, so that, taking into account the adjusting itself in the control chamber pressure levels a faster closing of the nozzle needle tip 12 into its nozzle seat 13 can achieve. This prevents fuel from being injected into the combustion chamber of an internal combustion engine towards the end of combustion, so that unburnt hydrocarbons can no longer be formed due to the largely completed combustion process.
  • FIG. 3 is a further embodiment of the solutions according to the invention with schematically illustrated pressure-relieved control chamber refer.
  • a nozzle body 16 is accommodated on an injector body 2.
  • injector body 2 and nozzle body 16 a nozzle needle 40 is movably received in the vertical direction.
  • this is surrounded by a ring 41, while the upper end face of the nozzle needle 40 is a boundary wall of a control space 42 shown here only schematically.
  • a closing filter element 43 is received between the end face of the ring 41 and a collar 44 of the nozzle needle 40.
  • flow relief surfaces 46 are received on the circumference of the nozzle needle 40, through which the fuel shoots into the nozzle body 16 in the direction of the nozzle needle tip 12.
  • the flow relief surfaces 46 are on the nozzle needle 40 as shown in FIG. 3 formed on a guide portion 45 which is guided in the bore of the nozzle body 16.
  • the guide portion 45 is formed in a diameter 49.
  • the throttle point 17 which is preferably designed as a throttle section and extending in the axial direction with the height h 1 (reference numeral 19).
  • An inlet chamber 47 in the nozzle body 16 serves to receive the volume of fuel flowing in via the flow rake surfaces 46 and the throttling point 17.
  • this comprises a seat surface diameter 14 which bears against the nozzle seat 13 of the nozzle body 16 and thus closes the injection opening 15 projecting into the combustion chamber of an internal combustion engine.
  • the configuration of the nozzle needle tip of the nozzle needle 40 is, for example, a blind-hole nozzle; In addition, the formation of the nozzle needle tip 12 would also be possible as a Weglochdüse.
  • the effect of the pressure drop at the nozzle needle tip 12 achievable by the throttle point 17 located near the nozzle allows a quicker closing of the nozzle needle 40 and therefore a precise termination of the injection phase, so that the occurrence of unburned hydrocarbons in the exhaust gas is considerably reduced when using the solution according to the invention, if not is completely excluded.
  • the arrangement of the throttling point 17 behind a second guide portion 7 of the nozzle needle 5 and the nozzle needle 30 and behind a guide portion 45 of the nozzle needle 40 or its integration therein prevents deflection of the nozzle needle 5, 30, 40 according to the illustrated embodiments such that the flow rate changed to the nozzle needle tip 12 by deflection thereof transversely to its axis and thus greatly changes the flow volume.

Description

Technisches GebietsTechnical field

Zur Einspritzung von Kraftstoff in die Brennräume einer Verbrennungskraftmaschine werden Injektoren eingesetzt, an welchen der Einspritzbeginn und die Einspritzmenge durch elektrische Ansteuerung mittels eines Magnetventils oder eines Piezoaktors eingestellt werden. In den Injektoren sind Einspritzdüsen aufgenommen. Die Injektoren halten die Einspritzdüsen, die auf die jeweiligen Verhältnisse der Verbrennungskraftmaschine, an der sie zum Einsatz kommen, abgestimmt sind. Die Auslegung der Einspritzdüse ist mit entscheidend für die dosierte Einspritzung hinsichtlich der Einspritzdauer und der Einspritzmenge je Grad Kurbelwinkel sowie hinsichtlich der Aufbereitung des Kraftstoffs im Hinblick auf Einspritzstrahlform und Zerstäubung des Kraftstoffs im Brennraum.For injecting fuel into the combustion chambers of an internal combustion engine injectors are used, at which the start of injection and the injection quantity are adjusted by electrical control by means of a solenoid valve or a piezoelectric actuator. Injectors injectors are included. The injectors hold the injectors, which are tuned to the respective conditions of the internal combustion engine on which they are used. The design of the injection nozzle is crucial for the metered injection in terms of injection duration and injection quantity per degree crank angle and with regard to the preparation of the fuel with respect to injection jet shape and atomization of the fuel in the combustion chamber.

Stand der TechnikState of the art

Aus DE 197 01 879 A1 geht eine Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen hervor. Diese umfaßt einen von einer Hochdruckpumpe mit Kraftstoff befüllbaren gemeinsamen Hochdrucksammelraum (Common Rail), der über Einspritzleitungen mit in den Brennraum der zu versorgenden Brennkraftmaschine ragenden Einspritzventilen verbunden ist. Deren Öffnungs- und Schließbewegungen werden jeweils von einem elektrisch angesteuerten Steuerventil gesteuert, wobei das Steuerventil zum Beispiel als 3/2-Wege-Ventil ausgebildet ist. Dieses verbindet einen an einer Einspritzöffnung des Einspritzventils mündenden Hochdruckkanal mit der Einspritzleitung oder einer Entlastungsleitung. Dabei ist am Steuerventilglied des Steuerventils ein mit Kraftstoffhochdruck befüllbarer hydraulischer Arbeitsraum vorgesehen, der zur Verstellung der Einstellposition des Steuerventilgliedes des Steuerventils in einen Entlastungskanal aufsteuerbar ist.Out DE 197 01 879 A1 goes out a fuel injection device for internal combustion engines. This includes a common by a high-pressure pump with fuel common high-pressure accumulator (common rail), which is connected via injection lines with projecting into the combustion chamber of the engine to be supplied injectors. Their opening and closing movements are each controlled by an electrically controlled control valve, wherein the control valve is formed, for example, as a 3/2-way valve. This connects a high pressure channel opening at an injection opening of the injection valve to the injection line or a discharge line. In this case, a fillable with high pressure hydraulic hydraulic working space is provided on the control valve member of the control valve, which is aufsteuerbar for adjusting the setting position of the control valve member of the control valve in a discharge channel.

GB 2 335 000 bezieht sich auf einen Kraftstoffinjektor mit einem verengten Kraftstoffzulauf an einem Nadelventil. Der Kraftstoffinjektor umfaßt eine Düsennadel, welche in einer in einem Düsenkörper vorgesehenen Bohrung verschiebbar aufgenommen ist. Die Düsennadel bildet mit dem Injektorkörper sowohl einen Kraftstoffvorratsraum als auch eine Kraftstoffaufnahmekammer für den unter hohem Druck anstehenden Kraftstoff. An der Düsennadel ist ein Strömungskanalsystem für den Kraftstoff vorgesehen, welches den Zulauf des Kraftstoffs begrenzt. Befindet sich die Düsennadel in einer geöffneten Position, strömt Kraftstoff in Richtung auf den Vorratsraum. Fährt die Düsennadel hingegen im Injektorkörper nach oben auf, so strömt ein verhöhtes Kraftstoffvolumen in Richtung zur Einspritzdüse GB 2 335 000 refers to a fuel injector with a restricted fuel feed to a needle valve. The fuel injector comprises a nozzle needle which is slidably received in a bore provided in a nozzle body. The nozzle needle forms with the injector both a fuel reservoir and a fuel receiving chamber for the pending under high pressure fuel. At the nozzle needle, a flow channel system is provided for the fuel, which is the inlet limited to the fuel. If the nozzle needle is in an open position, fuel flows in the direction of the reservoir. On the other hand, if the nozzle needle moves upwards in the injector body, then a heightened volume of fuel flows in the direction of the injection nozzle

Aus EP-A 0 971 118 ist ein Kraftstoffinjektor bekannt, bei dem innerhalb eines die Düsennadel umgebenden Zwischenraumes an der Düsennadel ein Bund ausgebildet ist, welcher zum Beispiel einen ringförmigen Spalt mit der Wand des Zwischenraumes ausbildet. Der ringförmige Spalt wirkt als Drossel. Aus dem Zwischenraum gelangt der Kraftstoff entlang von Strömungsflächen an der Düsennadel entweder in einen Düsenraum und von dort über einen Spalt zur Einspritzöffnung oder aber direkt zur Einspritzöffnung.Out EP-A 0 971 118 a fuel injector is known in which, within a gap surrounding the nozzle needle on the nozzle needle, a collar is formed, which forms, for example, an annular gap with the wall of the intermediate space. The annular gap acts as a throttle. From the intermediate space, the fuel passes along flow surfaces on the nozzle needle either into a nozzle space and from there via a gap to the injection opening or else directly to the injection opening.

Darstellung der ErfindungPresentation of the invention

Die erfindungsgemäße Lösung bewirkt ein schnelleres Schließen der Düsennadel, wodurch sich insbesondere erhöhte Kohlenwasserstoffanteile im Abgas von Brennkraftmaschinen durch verspätetes Nadelschließen vermeiden lassen. Die bisher auftretenden höheren HC-Anteile im Abgas einer Verbrennungskraftmaschine rührten nicht zuletzt daher, dass bei einem vergleichsweise langsam ablaufenden Nadelschließen durch die noch geöffnete Einspritzdüse Kraftstoff in den Brennraum gelangte, der jedoch nicht mehr verbrannt werden konnte, da die Verbrennung gegen Nadelschließen bereits weitestgehend abgelaufen ist. Wird mittels der erfindungsgemäßen Lösung ein schnelleres Nadelschließen erzielt, so kann die Zunahme des HC-Anteils im Abgas der Verbrennungskraftmaschine vermieden werden. Ferner ist durch ein sich schnell einstellendes Schließen der Düsennadel die Formung des Einspritzverlaufes. d.h. seine Anpassung an die im Brennraum ablaufende Verbrennung, hinsichtlich des Zündverznges, besser reproduzierbar.The solution according to the invention causes a faster closing of the nozzle needle, which can be avoided in particular by increased needle portions of hydrocarbon fractions in the exhaust gas of internal combustion engines. The hitherto occurring higher HC components in the exhaust gas of an internal combustion engine touched last but not least that at a comparatively slow expiring needle closing through the still open injector fuel into the combustion chamber, but could not be burned because the combustion has already largely expired against needle closing is. If a faster needle closure is achieved by means of the solution according to the invention, the increase of the HC content in the exhaust gas of the internal combustion engine can be avoided. Furthermore, by forming a fast adjusting the nozzle needle forming the injection curve. i.e. its adaptation to the running in the combustion chamber combustion, in terms of Zündverznges, better reproducible.

Die erfindungsgemäß vorgeschlagene Androsselstelle kann sowohl als ein im Durchmesser stärker ausgeführter Bereich der Düsennadel als auch als in geringem Abstand an dem Düsennadelumfang angeführter Vorsprung im Injektorgehäuse ausgeführt sein. Die Androsselstelle - vorzugsweise als eine Drosselstrecke ausgebildet - kann unterhalb eines Führungsabschnittes an der Düsennadel ausgebildet werden; ferner lässt sich die Drosselstrecke in dem Führungsabschnitt an der Düsennadel integrieren.The thrust bearing proposed according to the invention can be embodied both as a region of the nozzle needle which has a larger diameter and as a projection guided in the injector housing at a small distance at the nozzle needle circumference. The throttle point - preferably designed as a throttle section - can be formed below a guide portion on the nozzle needle; Furthermore, the throttle section can be integrated in the guide section on the nozzle needle.

Durch die Auslegung der Androsselstelle an Düsennadel oder Gehäuse hinsichtlich Axialerstreckung, d.h. hinsichtlich der Drosselspalthöhe sowie hinsichtlich der Spaltweite können Drosselungen im Bereich zwischen 0,2 und 7 % erzielt werden.Due to the design of the thrust point on the nozzle needle or housing with respect to axial extension, ie with respect to the throttle gap height and in terms of the gap width throttling in the range between 0.2 and 7% can be achieved.

Die Anordnung der Androsselstelle unterhalb eines Führungsabschnittes oder in der Alternative in diesen integriert, zieht den vorteilhaften Effekt nach sich, dass durch die Nähe der Androsselstelle zum Führungsabschnitt ein Auslenken der Düsennadel aus der zentrierten Lage vermieden wird. Eine Auslenkung der Düsennadel quer zur Düsennadelachse hätte eine starke Abweichung der Durchflussmenge zur Folge, was jedoch aufgrund der erfindungsgemäß vorgeschlagenen Lösung ausgeschlossen ist.The arrangement of the thrust point below a guide portion or in the alternative integrated into this, has the advantageous effect that is avoided by the proximity of the thruster to the guide portion deflecting the nozzle needle from the centered position. A deflection of the nozzle needle transversely to the nozzle needle axis would result in a large deviation of the flow rate, which however is ruled out due to the solution proposed according to the invention.

Die Androsselung des Durchflusses im Bereich der Nadelspitze der Düsennadel führt an dieser zu einem Druckabfall. Dadurch verschiebt sich das Druckverhältnis zum Steuerraum derart, daß das dortige Druckniveau höher liegt und somit ein schnelleres Einfahren der Düsennadel in die Sitzfläche des Injektorkörpers ermöglicht wird.The throttling of the flow in the region of the needle tip of the nozzle needle leads to a pressure drop at this point. As a result, the pressure ratio shifts to the control chamber such that the local pressure level is higher and thus a faster retraction of the nozzle needle is made possible in the seat of the injector body.

Zeichnungdrawing

Anhand der Zeichnung wird die Erfindung nachstehend eingehender erläutert.With reference to the drawing, the invention will be explained in more detail below.

Es zeigt:

Figur 1
eine Einspritzdüse eines Kraftstoffinjektors, der mittels eines Magnetventils ansteuerbar ist,
Figur 2
eine Ausführungsvariante einer Einspritzdüse mit Überströmltanälen oberhalb einer Androsselstelle und
Figur 3
eine weitere Ausführungsvariante mit schematisch dargestelltem druckentlast- baren Steuerraum.
It shows:
FIG. 1
an injection nozzle of a fuel injector, which can be activated by means of a solenoid valve,
FIG. 2
an embodiment of an injection nozzle with Überströmltanälen above an Androsselstelle and
FIG. 3
a further embodiment variant with schematically represented pressure-relieved control chamber.

Ausführungsvariantenvariants

Figur 1 ist eine Einspritzdüse eines Kraftstoffinjekiors entnehmbar, der über ein Magnetventil angesteuert werden kann. FIG. 1 is an injector of a Kraftstoffinjekiors removed, which can be controlled by a solenoid valve.

Ein Injektor 1 zum Einspritzen von Kraftstoff in die Brennräume einer Verbrennungkraftmaschine umfaßt einen Injelctorkcörper 2, in dem eine Düsennadel 5 aufgenommen ist. Im Injektorkörper 2 ist eine Hochdruckbohrung 3 ausgebildet, über welche ein Düsenraum 4 mit unter hohem Druck stehendem Kraftstoff beaufschlagbar ist. Die Hochdruckbohrung 3 steht mit einem hier nicht dargestellten Hochdrucksammelraum (Common Rail) in Verbindung, in welchem ein weitgehend konstanter hoher Druck erzeugt wird. In der Ausführungsvariante der erfindungsgemäßen Lösung gemäß Figur 1 umfaßt die Düsennadel 5 einen ersten Führungsabschnitt 6 sowie einen zweiten Führungsabschnitt 7, mit welchem sie im Injektorkörper 2 geführt ist.An injector 1 for injecting fuel into the combustion chambers of a combustion engine comprises an injector body 2 in which a nozzle needle 5 is received. In the injector body 2, a high-pressure bore 3 is formed, via which a nozzle chamber 4 can be acted upon by high-pressure fuel. The high-pressure bore 3 communicates with a high-pressure accumulation space (common rail), not shown here, in which a largely constant high pressure is generated. In the embodiment of the solution according to the invention according to FIG. 1 the nozzle needle 5 comprises a first guide portion 6 and a second guide portion 7, with which it is guided in the injector body 2.

Im Bereich der Düsennadel 5, in welchem diese vom Düsenraum 4 umgeben ist, ist an der Düsennadel 5 eine Druckstufe 8 ausgebildet. An den Düsenraum 4 im Injektorkörper 2 schließt sich ein Zulaufring 9 an, der im Durchmesser 10 ausgeführt ist. Unterhalb des Zulaufringes 9 zwischen Injektorkörper 2 und Düsennadel 5 ist an der Düsennadel 5 der zweite Führungsabschnitt 7 ausgebildet. In den zweiten Führungsabschnitt 7 können Strömungsflächen 20 für den Kraftstoff integriert sein, um ein Zuströmen des Kraftstoffes vom Düsenraum 4 über den Zulaufring 9 zur Düsenspitze zu gewährleisten.In the region of the nozzle needle 5, in which it is surrounded by the nozzle chamber 4, a pressure stage 8 is formed on the nozzle needle 5. To the nozzle chamber 4 in the injector body 2, a feed ring 9 connects, which is designed in diameter 10. Below the inlet ring 9 between the injector body 2 and the nozzle needle 5, the second guide section 7 is formed on the nozzle needle 5. In the second guide portion 7 flow surfaces 20 may be integrated for the fuel to ensure flow of the fuel from the nozzle chamber 4 via the inlet ring 9 to the nozzle tip.

Im Vergleich zum Durchmesser 10 des Zulaufringes 9 ist der Injektorkörper 2 im Bereich des zweiten Führungsabschnitts 7 in einem leicht reduzierten Durchmesser 11 ausgebildet. Der Injektorkörper 2 gemäß der Darstellung in Figur 1 geht in einen Düsenkörper 16 über. Die Bohrung im Düsenkörper 16, welche die Düsennadel 5 umschließt, ist in dem Bereich des zweiten Führungsabschnittes 7 mit einem kleineren Durchmesser ausgeführt, so daß sichergestellt ist, daß die Düsennadel 5 im düsenseitigen Bereich nur innerhalb des zweiten Führungsabschnittes 7 geführt ist.In comparison to the diameter 10 of the inlet ring 9, the injector body 2 is formed in the region of the second guide section 7 in a slightly reduced diameter 11. The injector body 2 as shown in FIG FIG. 1 goes over into a nozzle body 16. The bore in the nozzle body 16, which encloses the nozzle needle 5, is designed in the region of the second guide section 7 with a smaller diameter, so that it is ensured that the nozzle needle 5 is guided in the nozzle-side region only within the second guide section 7.

In axiale Richtung der Düsennadel 5 gemäß der Darstellung in Figur 1 gesehen, schließt sich am zweiten Führungsabschnitt 7 eine Androsselstelle 17 an. Die Androsselstelle 17 ist bevorzugt als eine Drosselstrecke ausgebildet, welche sich in axiale Richtung der Düsennadel 5 gesehen über eine Spalthöhe h1 (Bezugszeichen 19) erstreckt. Zwischen dem Düsenkörper 16 und der Androsselstelle 17, die gemäß der Darstellung in Figur 1 als eine Düsennadel 5 ausgebildet ist, stellt sich eine Spaltweite 18 ein, über welche die Drosselwirkung je nach Auslegung der Androsselstelle 17 einstellbar ist. Bevorzugt werde mittels der erfindungsgemäß vorgeschlagenen Lösung Drosselwirkungen zwischen 0,2 und 7% realisieit. Dadurch stellt sich an der Düsenspitze 12 ein Druckabfall ein, wodurch sich das Druckverhältnis zwischen der Düsenspitze 12 und einem hier nicht näher dargestellten Steuerraum zugunsten des Druckniveaus im Steuerraum verschiebt. Je höher der Druck im hier nicht dargestellten Steuerraum, welcher die Düsennadel beaufschlagt, desto kürzere Schließzeiten der Düsennadel 5 lassen sich erzielen.In the axial direction of the nozzle needle 5 as shown in FIG FIG. 1 seen, connects to the second guide section 7 an Androsselstelle 17. The throttle point 17 is preferably designed as a throttle section, which extends in the axial direction of the nozzle needle 5 over a gap height h 1 (reference numeral 19). Between the nozzle body 16 and the throttling point 17, which, as shown in FIG FIG. 1 is formed as a nozzle needle 5, a gap width 18, via which the throttling effect is adjustable depending on the design of the throttle point 17. Preferably, by means of the solution proposed according to the invention, throttle effects between 0.2 and 7% will be realized. As a result, a pressure drop occurs at the nozzle tip 12, as a result of which the pressure ratio between the nozzle tip 12 and a control chamber not shown here shifts in favor of the pressure level in the control chamber. The higher the pressure in the control chamber, not shown here, which acts on the nozzle needle, the shorter closing times of the nozzle needle 5 can be achieved.

Im unteren Bereich der vorzugsweise als Sacldochdüse beschaffenen Einspritzdüse 12 ist an dieser eine kegelförmige Sitzfläche 14 ausgebildet. Im geschlossenen Zustand der Düsennadel 5 liegt die Düsennadelspitze 12 mit ihrer Sitzfläche 14 am Düsensitz 13 an, der an der der Düsennadel 5 zuweisenden Wandung des Düsenkörpers 16 ausgebildet ist.In the lower region of the injection nozzle 12, which is preferably designed as a suction nozzle, a conical seat 14 is formed on the latter. In the closed state of the nozzle needle 5 is the nozzle needle tip 12 with its seat 14 on the nozzle seat 13, which is formed on the nozzle needle 5 facing wall of the nozzle body 16.

Im in Figur 1 wiedergegebenen Zustand ist die Düsennadel 5 mit ihrer Düsennadelspitze 12 in den Düsensitz 13 gefahren, so daß die Einspritzöffnung 15, welche in den Brennraum einer Verbrennungskraftmaschine hineinragt, durch die Düsenspitze 15 verschlossen ist.Im in FIG. 1 reproduced state, the nozzle needle 5 is driven with its nozzle needle tip 12 into the nozzle seat 13, so that the injection port 15, which projects into the combustion chamber of an internal combustion engine, is closed by the nozzle tip 15.

Die Androsselwirkung stellt sich erst beim Auffahren der Düsennadel 5 in den hier nicht näher dargestellten Steuerraum ein, wodurch es an der Düsennadelspitze 12 zu einem Druckabfall kommt, der für ein schnelles Nadelschließen durch Druckbeaufschlagung des der Düsennadel 5 zugeordneten Steuerraumes in vorteilhafter Weise ausgenutzt werden kann.The throttling action only occurs when the nozzle needle 5 is driven into the control chamber (not shown here), which results in a pressure drop at the nozzle needle tip 12, which can be advantageously utilized for rapid needle closure by pressurizing the control chamber associated with the nozzle needle 5.

Der Darstellung gemäß Figur 2 ist eine Ausführungsvariante der erfindungsgemäß vorgeschlagenen Lösung mit Überströmkanälen oberhalb einer Androsselstelle zu entnehmen.The representation according to FIG. 2 is an embodiment of the present invention proposed solution with overflow can be seen above a thrust point.

Im Injektorkörper 2 eines Injektors 1 zum Einspritzen von Kraftstoff ist analog zur Darstellung gemäß Figur 1 eine Düsennadel 30 in vertikale Richtung bewegbar aufgenommen. An der Düsennadel 30 ist ein erster Führungsabschnitt 6 sowie ein zweiter Führungsabschnitt 7 ausgebildet. Im Injektorgehäuse 2 ist eine Hochdruckbohrung 3 ausgebildet, die in einen Düsenraum 4 mündet. Zulaufseitig steht die Hochdruckbohrung 3 mit einem nicht dargestellten Hochdrucksammelraum (Common Rail) in Verbindung. Im Unterschied zur in Figur 1 dargestellten Ausführungsvariante ist an der Düsennadel 30 gemäß der Darstellung in Figur 2 ein Überstromkanalsystem 31 ausgebildet, welches im wesentlichen von einem mit unter hohem Druck stehenden Kraftstoffdüsenraum 4 umschlossen ist. Unterhalb des Überströmkanalsystems 31 ist analog zur Darstellung der Düsennadel 5 in Figur 1 an der Düsennadel 30 eine Androsselstelle 17 ausgebildet.In the injector 2 of an injector 1 for injecting fuel is analogous to the representation according to FIG. 1 a nozzle needle 30 is movably received in the vertical direction. At the nozzle needle 30, a first guide portion 6 and a second guide portion 7 is formed. In the injector 2, a high-pressure bore 3 is formed, which opens into a nozzle chamber 4. On the inlet side, the high-pressure bore 3 communicates with a high-pressure collecting chamber (common rail), not shown. Unlike in FIG. 1 illustrated embodiment is on the nozzle needle 30 as shown in FIG FIG. 2 an overflow channel system 31 is formed, which is surrounded by a substantially pressurized fuel nozzle space 4. Below the overflow channel system 31 is analogous to the representation of the nozzle needle 5 in FIG. 1 at the nozzle needle 30 a thrust point 17 is formed.

Die Androsselstelle 17 gemäß der Darstellung in Figur 2 ist bevorzugt an der Düsennadel 30 als eine Drosselstrecke ausgeführt, welche sich in einer axialen Spalthöhe 19 in Axialrichtung der Düsennadel 30 erstreckt. Zwischen der den zweiten Führungsabschnitt 7 umgebenden Bohrung des Düsenkörpers 16 und der Androsselstelle stellt sich eine Spaltweite 19 ein, über welche je nach Auslegung die Drosselwirkung variiert werden kann. Unterhalb der Androsselstelle 17 ist eine Düsennadel 30 gemäß der Darstellung in Figur 2 ein Sitzdurchmesser 14 ausgebildet, der in einen Düsensitz 13 im Düsenkörper 16 des Injektorkörpers 2 eingefahren ist. Im in Figur 2 wiedergegebenen Zustand ist die Einspritzöffnung 15, die in den Brennraum einer Verbrennungskraftmaschine hineinragt, durch die Düsennadelspitze 12, welche in ihren Düsensitz 13 gefahren ist, verschlossen.Throttling point 17 as shown in FIG. 2 is preferably carried out on the nozzle needle 30 as a throttle section, which extends in an axial gap height 19 in the axial direction of the nozzle needle 30. Between the second guide section 7 surrounding bore of the nozzle body 16 and the throttle point, a gap width 19, over which depending on the design, the throttle effect can be varied. Underneath the throttling point 17 is a nozzle needle 30 as shown in FIG FIG. 2 a seat diameter 14 is formed, which is retracted into a nozzle seat 13 in the nozzle body 16 of the injector body 2. Im in FIG. 2 reproduced state is the injection port 15, which projects into the combustion chamber of an internal combustion engine, closed by the nozzle needle tip 12, which has moved into its nozzle seat 13.

Gemäß der Darstellung in Figur 2 können am Umfang der Düsennadel 30 im Bereich des Düsenraumes 4 die Überströmkanäle 31 mit einer Neigung 32 aufgebracht werden, wodurch sich eine Begrenzung des in Richtung Düsennadelspitze 12 einstellenden Kraftstoffvolumenstroms ergibt. Die Androsselstelle 17 bewirkt einen Druckabfall im Bereich der Düsennadelspitze 12, so daß sich unter Berücksichtigung des sich im Steuerraum einstellenden Druckniveaus ein schnelleres Schließen der Düsennadelspitze 12 in ihren Düsensitz 13 erzielen läßt. Dadurch unterbleibt ein Einspritzen von Kraftstoff in den Brennraum einer Verbrennungskraftmaschine gegen Ende der Verbrennung, so daß keine unverbrannten Kohlenwasserstoffe aufgrund des weitestgehend abgeschlossenen Verbrennungsvorgangs mehr entstehen können.As shown in FIG. 2 can be applied to the circumference of the nozzle needle 30 in the region of the nozzle chamber 4, the overflow 31 with an inclination 32, resulting in a limitation of adjusting in the direction of the nozzle needle tip 12 fuel flow. The Androsselstelle 17 causes a pressure drop in the nozzle needle tip 12, so that, taking into account the adjusting itself in the control chamber pressure levels a faster closing of the nozzle needle tip 12 into its nozzle seat 13 can achieve. This prevents fuel from being injected into the combustion chamber of an internal combustion engine towards the end of combustion, so that unburnt hydrocarbons can no longer be formed due to the largely completed combustion process.

Der Darstellung gemäß Figur 3 ist eine weitere Ausführungsvariante der erfindungsgemäßen Lösungen mit schematisch dargestelltem druckentlastbaren Steuerraum zu entnehmen.The representation according to FIG. 3 is a further embodiment of the solutions according to the invention with schematically illustrated pressure-relieved control chamber refer.

Gemäß dieser Ausführungsvariante eines Kraftstoffinjektors 1 zum Einspritzen von Kraftstoff in die Brennräume von Verbrennungskraftmaschinen ist ein Düsenkörper 16 an einem Injektorkörper 2 aufgenommen. In Injektorkörper 2 bzw. Düsenkörper 16 ist eine Düsennadel 40 in vertikale Richtung bewegbar aufgenommen. Im oberen Bereich der Düsennadel 40 ist diese von einem Ring 41 umschlossen, während die obere Stirnfläche der Düsennadel 40 eine Begrenzungswand eines hier nur schematisch dargestellten Steuerraums 42 darstellt. Zwischen der Stirnseite des Rings 41 und einem Bund 44 der Düsennadel 40 ist ein Schließfilterelement 43 aufgenommen. Unterhalb des Bundes 44, an welchem die Schließfeder 43 anliegt, sind am Umfang der Düsennadel 40 Strömungsfreiflächen 46 aufgenommen, durch welche der Kraftstoff in Richtung auf die Düsennadelspitze 12 in den Düsenkörper 16 einschießt. Die Strömungsfreiflächen 46 sind an der Düsennadel 40 gemäß der Darstellung in Figur 3 an einem Führungsabschnitt 45 ausgebildet, der in der Bohrung des Düsenkörpers 16 geführt ist. Der Führungsabschnitt 45 ist in einem Durchmesser 49 ausgebildet. Gemäß der Darstellung in Figur 3 schließt sich an den Führungsabschnitt 45 der Düsennadel 40 die Androsselstelle 17 an welche bevorzugt als Drosselstrecke ausgebildet ist und sich in axiale Richtung mit der Höhe h1 (Bezugszeichen 19) erstreckt. Zwischen der Androsselstelle 17, die an der Düsennadel 40 ausgebildet ist, und der Bohrung des Düsenkörpers 16 stellt sich eine Spaltweite 18 ein, welche den Grad der Drosselung im wesentlichen bestimmt. Unterhalb der Androsselstelle 17 ist.die Bohrung, welche die Düsennadel 40 im Düsenkörper 16 umschließt, in einem erweiterten Durchmesser 50 ausgebildet. Ein Zulaufraum 47 im Düsenkörper 16 dient zur Aufnahme des über die Strömungsfreiflächen 46 und die Androsselstelle 17 einströmenden Kraftstoffvolumens.According to this embodiment variant of a fuel injector 1 for injecting fuel into the combustion chambers of internal combustion engines, a nozzle body 16 is accommodated on an injector body 2. In injector body 2 and nozzle body 16, a nozzle needle 40 is movably received in the vertical direction. In the upper region of the nozzle needle 40, this is surrounded by a ring 41, while the upper end face of the nozzle needle 40 is a boundary wall of a control space 42 shown here only schematically. Between the end face of the ring 41 and a collar 44 of the nozzle needle 40, a closing filter element 43 is received. Below the collar 44, against which the closing spring 43 abuts, flow relief surfaces 46 are received on the circumference of the nozzle needle 40, through which the fuel shoots into the nozzle body 16 in the direction of the nozzle needle tip 12. The flow relief surfaces 46 are on the nozzle needle 40 as shown in FIG FIG. 3 formed on a guide portion 45 which is guided in the bore of the nozzle body 16. The guide portion 45 is formed in a diameter 49. As shown in FIG. 3 closes at the guide portion 45 of the nozzle needle 40, the throttle point 17 which is preferably designed as a throttle section and extending in the axial direction with the height h 1 (reference numeral 19). Between the Anrosselstelle 17, which is formed on the nozzle needle 40, and the bore of the nozzle body 16 is a gap width 18, which determines the degree of throttling substantially. Underneath the throttling point 17, the bore which encloses the nozzle needle 40 in the nozzle body 16 is formed in an enlarged diameter 50. An inlet chamber 47 in the nozzle body 16 serves to receive the volume of fuel flowing in via the flow rake surfaces 46 and the throttling point 17.

Im Bereich der Düsennadelspitze 12 der Düsennadel 40 umfaßt diese einen Sitzflächendurchmesser 14, der am Düsensitz 13 des Düsenkörpers 16 anliegt und somit die in den Brennraum einer Verbrennungskraftmaschine hineinragende Einspritzöffnung 15 verschließt. Bei der Konfiguration der Düsennadelspitze der Düsennadel 40 handelt es sich beispielsweise um eine Sacklochdüse; daneben wäre die Ausbildung der Düsennadelspitze 12 auch als eine Sitzlochdüse möglich.In the area of the nozzle needle tip 12 of the nozzle needle 40, this comprises a seat surface diameter 14 which bears against the nozzle seat 13 of the nozzle body 16 and thus closes the injection opening 15 projecting into the combustion chamber of an internal combustion engine. The configuration of the nozzle needle tip of the nozzle needle 40 is, for example, a blind-hole nozzle; In addition, the formation of the nozzle needle tip 12 would also be possible as a Sitzlochdüse.

Neben der in Figur 1 und 3 wiedergegebenen Ausführungsmöglichkeit, die Androsselstelle 17 unterhalb des zweiten Führungsabschnittes 7 bzw. des Führungsabschnittes 45 vorzusehen, besteht in vereinfachter Ausführungsmöglichkeit der Düsennadeln 5 bzw. 40 auch die Möglichkeit, die Androsselstelle 17 unmittelbar in den zweiten Führungsabschnitt 7 bzw. den Führungsabschnitt 45 an der Düsennadel 40 zu integrieren. Damit könnte die entsprechende Düsennadel 5 bzw. 40, in axialer Länge gesehen, kürzergehalten werden.In addition to the in FIG. 1 and 3 reproduced execution possibility to provide the Anrosselstelle 17 below the second guide portion 7 and the guide portion 45, is in a simplified design possibility of the nozzle needles 5 and 40 also the possibility, the thrust point 17 directly into the second guide portion 7 and the guide portion 45 on the nozzle needle 40th to integrate. Thus, the corresponding nozzle needle 5 and 40, viewed in axial length, could be kept shorter.

Der durch die am düsennahen Bereich liegende Androsselstelle 17 erzielbare Effekt des Druckabfalls an der Düsennadelspitze 12 erlaubt ein schnelleres Schließen der Düsennadel 40 und damit eine präzise Beendigung der Einspritzphase, so daß das Auftreten unverbrannter Kohlenwasserstoffe im Abgas bei Einsatz der erfindungsgemäßen Lösung erheblich vermindert, wenn nicht völlig ausgeschlossen ist. Die Anordnung der Androsselstelle 17 hinter einem zweiten Führungsabschnitt 7 der Düsennadel 5 und der Düsennadel 30 bzw. hinter einem Führungsabschnitt 45 der Düsennadel 40 oder deren Integration darin verhindert eine Auslenkung der Düsennadel 5, 30, 40 gemäß der dargestellten Ausführungsvarianten derart, daß sich die Durchflußmenge zur Düsennadelspitze 12 durch Auslenkung derselben quer zu ihrer Achse verändert und somit sich das Durchflußvolumen stark verändert.The effect of the pressure drop at the nozzle needle tip 12 achievable by the throttle point 17 located near the nozzle allows a quicker closing of the nozzle needle 40 and therefore a precise termination of the injection phase, so that the occurrence of unburned hydrocarbons in the exhaust gas is considerably reduced when using the solution according to the invention, if not is completely excluded. The arrangement of the throttling point 17 behind a second guide portion 7 of the nozzle needle 5 and the nozzle needle 30 and behind a guide portion 45 of the nozzle needle 40 or its integration therein prevents deflection of the nozzle needle 5, 30, 40 according to the illustrated embodiments such that the flow rate changed to the nozzle needle tip 12 by deflection thereof transversely to its axis and thus greatly changes the flow volume.

Claims (7)

  1. Fuel injector for injecting fuel into the combustion chambers of an internal combustion engine, having an injector body (2, 16) in which a nozzle needle (5, 30, 40) is held in a movable manner, the nozzle needle tip (12) of which nozzle needle closes off or opens up an injection opening (15) into the combustion chamber, and the nozzle needle (5, 30, 40) has at least one guide section (6, 7, 45), characterized in that, in the region of the nozzle seat (13, 14) of the nozzle needle (5, 30, 40), a throttling point (17) is formed below a nozzle-body-side guide section (7, 45), with the throttling point (17) directly adjoining or being integrated in the nozzle-body-side guide section (7, 45).
  2. Fuel injector according to Claim 1, characterized in that the throttling point (17) is embodied as a throttle path which extends coaxially with respect to the nozzle needle (5, 30, 40).
  3. Fuel injector according to Claim 2, characterized in that the throttle path is formed at the throttling point (17) of the nozzle needle (5, 30, 40) at a gap level (19).
  4. Fuel injector according to Claim 2, characterized in that, between the throttling point (17) and the injector housing (2), a minimum gap width (18) is formed such that the throughflow of fuel is throttled by 0.2 to 7%.
  5. Fuel injector according to Claim 1, characterized in that the throttling point (17) is designed as a region of the nozzle needle (5, 30, 40) which is thickened in diameter.
  6. Fuel injector according to Claim 1, characterized in that the throttling point (17) is designed as a projection in the injector housing (2, 16).
  7. Fuel injector according to Claim 1, characterized in that the nozzle needle tip (12) of the nozzle needle (5, 30, 40) is a blind-hole nozzle (48).
EP02740226A 2001-04-10 2002-03-30 Injector nozzle with throttling action Expired - Lifetime EP1379776B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE2001117861 DE10117861A1 (en) 2001-04-10 2001-04-10 Fuel injector for injecting fuel into internal combustion engine combustion chambers has nozzle needle with at least one guide section and in form of choke point near nozzle seat
DE10117861 2001-04-10
PCT/DE2002/001163 WO2002084109A2 (en) 2001-04-10 2002-03-30 Injector nozzle with throttling action

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EP1379776A2 EP1379776A2 (en) 2004-01-14
EP1379776B1 true EP1379776B1 (en) 2009-10-21

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WO (1) WO2002084109A2 (en)

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DE10346212A1 (en) * 2003-10-06 2005-04-21 Bosch Gmbh Robert Fuel injection valve for IC engines has fuel feed channel with throttle to form smallest flow profile from the feed channel to injection apertures
DE602006012963D1 (en) 2006-07-27 2010-04-29 Magneti Marelli Spa Fuel injection valve for a direct injection internal combustion engine
US7690588B2 (en) 2007-07-31 2010-04-06 Caterpillar Inc. Fuel injector nozzle with flow restricting device
EP2568157A1 (en) * 2011-09-08 2013-03-13 Delphi Technologies Holding S.à.r.l. Injection Nozzle
CN109681360A (en) * 2019-02-28 2019-04-26 一汽解放汽车有限公司 A kind of long needle-valve for fuel injection valve

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EP0449763B1 (en) * 1990-03-28 1994-10-12 Stanadyne Automotive Corp. Fuel injector
JPH11200999A (en) * 1998-01-09 1999-07-27 Nissan Motor Co Ltd Fuel injection valve for internal combustion engine
GB2335000A (en) * 1998-03-05 1999-09-08 Lucas Ind Plc Fuel injector having a restricted fuel flow path provided by a needle valve
EP0971118A2 (en) * 1998-07-06 2000-01-12 Isuzu Motors Limited Fuel Injector

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JPS6052310B2 (en) * 1980-09-05 1985-11-18 日産自動車株式会社 Throttle type fuel injection valve
JPS61164068A (en) * 1985-01-14 1986-07-24 Nissan Motor Co Ltd Throttle type fuel injection nozzle
JPH07259704A (en) * 1994-03-24 1995-10-09 Nissan Diesel Motor Co Ltd Fuel injection nozzle for internal combustion engine
DE19701879A1 (en) 1997-01-21 1998-07-23 Bosch Gmbh Robert Fuel injection device for internal combustion engines
DE10054182A1 (en) * 2000-11-02 2002-05-29 Siemens Ag Fluid dosing device with a throttle point includes a metal bellows sealing a region around the leadthrough element of a needle valve passing through a chamber
DE10055651A1 (en) * 2000-11-10 2002-05-23 Bosch Gmbh Robert Fuel injector, for internal combustion engine, has annular volume, formed between needle and conical section of wall of case, just below narrowed section of needle.

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Publication number Priority date Publication date Assignee Title
EP0449763B1 (en) * 1990-03-28 1994-10-12 Stanadyne Automotive Corp. Fuel injector
JPH11200999A (en) * 1998-01-09 1999-07-27 Nissan Motor Co Ltd Fuel injection valve for internal combustion engine
GB2335000A (en) * 1998-03-05 1999-09-08 Lucas Ind Plc Fuel injector having a restricted fuel flow path provided by a needle valve
EP0971118A2 (en) * 1998-07-06 2000-01-12 Isuzu Motors Limited Fuel Injector

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EP1379776A2 (en) 2004-01-14
WO2002084109A3 (en) 2002-12-12
DE50213943D1 (en) 2009-12-03
WO2002084109A2 (en) 2002-10-24
DE10117861A1 (en) 2002-10-24

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