EP1597473B1 - Fuel-injection device, in particular for internal combustion engines with direct fuel-injection - Google Patents

Fuel-injection device, in particular for internal combustion engines with direct fuel-injection Download PDF

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Publication number
EP1597473B1
EP1597473B1 EP03769230A EP03769230A EP1597473B1 EP 1597473 B1 EP1597473 B1 EP 1597473B1 EP 03769230 A EP03769230 A EP 03769230A EP 03769230 A EP03769230 A EP 03769230A EP 1597473 B1 EP1597473 B1 EP 1597473B1
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EP
European Patent Office
Prior art keywords
valve element
inner valve
injection device
fuel injection
fuel
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
Application number
EP03769230A
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German (de)
French (fr)
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EP1597473A1 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1597473A1 publication Critical patent/EP1597473A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the invention relates to a fuel injection device according to the preamble of claim 1.
  • Such a fuel injection device is known from DE 41 15 477 A1.
  • This shows an injection valve with two coaxially arranged valve elements.
  • An elongate and comparatively thin actuating portion of the inner valve member carries at its end a comparatively thick and adjacent to the valve seat sealing portion.
  • the recess in the outer valve element, in which the inner valve element is arranged, is stepped. Between the sealing portion and the recess in the outer valve element is a gap.
  • Object of the present invention is to develop a fuel injection device of the type mentioned so that it works as effectively as possible.
  • the outer diameter of the inner valve element and the inner diameter of the recess in the outer valve element are stepped and matched to one another.
  • the wall thicknesses or cross-sectional areas of the sealing sections and the actuating sections of the valve elements can be optimally adapted to the desired functions. This is particularly advantageous in view of the extremely small overall dimensions (diameter of a valve element of at most a few millimeters, sometimes significantly less).
  • the sealing section of the inner valve element has a smaller diameter than its actuating section.
  • the outer valve member may have a relatively large sealing portion, so that there existing pressure surface is also relatively large, which simplifies the hydraulic actuation of the outer valve member, especially at low pressures.
  • the operating portion of the inner valve element has a nevertheless sufficiently large in diameter that it has a high rigidity.
  • the sealing portion of the inner valve member may also have a larger diameter than the actuating portion of the inner valve member.
  • This has advantages if the inner valve element relatively large amounts of fuel to be injected, which makes fuel outlet channels with correspondingly large diameters required. Their arrangement is facilitated if, as in the present case, the sealing portion of the inner valve element and, as a result, also the associated valve seat have a comparatively large diameter.
  • the operating portion of the outer valve member may have a comparatively high wall thickness, so that in this case the outer valve member has a high rigidity as a whole.
  • the outer valve element has an upper guide region, in which the actuating portion of the inner valve element is guided at least in regions (the term "top” here is not absolute, but relative to the fuel injection device to understand). This also benefits the centering of the inner valve element in the outer valve element and the lowering of the actuating pressures and thus ultimately the quality of the fuel injection.
  • the fuel injection device forms an existing between the sealing portion and the actuating portion of the inner valve member Paragraph a printing surface. This allows a uniform distribution of the forces acting on the inner valve element hydraulic forces.
  • longitudinally extending recesses be present in the lateral surface of the region of the inner valve element guided by the upper guide region and / or in the lateral surface of the upper guide region of the outer valve element.
  • a fuel system bears the overall reference numeral 10. It is used in an internal combustion engine 12, which is not shown in detail in FIG.
  • the fuel system 10 includes a fuel tank 14 from which an electric fuel pump 16 delivers the fuel to a high pressure fuel pump 18. This compresses the fuel to a very high pressure and conveys it into a fuel rail ("rail") 20. To these are connected via high-pressure lines 22 a plurality of fuel injectors 24, which Inject the fuel directly into them associated combustion chambers 26. The fuel injectors 24 are connected via a low pressure return line 28 to the fuel tank 14 again.
  • FIG. 2 An area of one of the fuel injection devices 24 facing the combustion chamber 26 is shown in detail in FIG. 2:
  • the fuel injector 24 includes a housing 30 in which a stepped blind bore 32 is present. This is connected via a channel 34 to the high-pressure line 22.
  • the lower region of the stepped blind bore 32 in FIG. 2 tapers conically. It is limited by a conical valve seat surface 36.
  • In the valve seat surface 36 open distributed over the circumference of the housing 30 arranged radially outer fuel outlet channels 38 and radially inner fuel outlet channels 40, which respectively pass through the housing wall.
  • two mutually coaxial valve elements are arranged, namely an outer valve element 42 and an inner valve element 44.
  • the outer valve element 42 is guided in a guide region 46 from the housing 30 in a fluid-tight manner.
  • An annular space 48 present in FIG. 2 below the guide region 46 between the outer valve element 42 and the wall of the stepped blind bore 32 is connected to the high-pressure line 22 via the high-pressure passage 34.
  • the annular space 48 has a bulge 50, at the level of which on the outer valve element 42 there is a pressure surface 52 acting in the opening direction of the outer valve element 42.
  • the lower end of the outer valve element 42 in FIG. 2 is also conical with two conical surfaces 54 and 56 of different conicity. Between these a sealing edge 58 is present.
  • the two conical surfaces 54 and 56 with the sealing edge 58 are provided on a sealing portion 60 of the outer valve member 42, whereas the pressure surface 52 is provided on an actuating portion 62 of the outer valve member 42.
  • the inner valve member 44 is received in a stepped bore 64 of the outer valve member 42.
  • the stepped bore 64 in this case has a portion 66 with a smaller and a portion 68 with a larger diameter.
  • the inner valve element 44 has in the section 68 of the stepped bore 64 a sealing section 70 which has a larger diameter than an actuating section 72 of the inner valve element 44, which is arranged in the section 66 of the stepped bore 64 of the outer valve element 42. Between the two sections 70 and 72 of the inner valve member 44, a shoulder is present, which forms an annular pressure surface 74.
  • the sealing portion 70 of the inner valve member 44 includes a cylinder portion 76 which is fluid-tightly guided in the portion 68 of the stepped bore 64.
  • the section 68 is therefore also referred to as "lower guide area".
  • the sealing section 70 comprises two regions of different conicity. These are delimited by an outer conical surface 78 or an inner conical surface 80, between which a sealing edge 82 is present.
  • the operating portion 72 of the inner valve member 44 has two regions 84 and 86 of different diameters.
  • the immediately adjacent to the sealing portion 70 region 84 has a slightly smaller diameter than the portion 66 of the stepped bore 64 in the outer valve member 42.
  • the outer diameter of the region 86 of the actuating portions 72 corresponds approximately to the inner diameter of the portion 66 of the stepped bore 64 in the outer valve member 42.
  • This region of the stepped bore 62 therefore forms an upper guide portion 88, in which the actuating portion 72 of the inner valve member 44 is guided.
  • the region 86 of the actuating portion 72 of the inner valve member 44 extending in the axial direction grooves 90 are introduced.
  • the fuel injection device 24 shown in Figure 2 can be operated stroke or pressure controlled or in a combination of two control principles. It is conceivable, for example, that the outer valve element 42 operates under pressure control, that an opening movement of the outer valve element 42 is thus effected by an increase in pressure in the annular space 48. As a result, the hydraulic force acting on the pressure surface 52 and on the outer conical surface 54 increases, which finally leads, contrary to a constant closing force, to a lifting of the sealing edge 58 from the valve seat surface 36.
  • the inner valve member 44 may be stroke controlled. This means that its sealing edge 82 only lifts off from the valve seat surface 36 due to a constant opening force when the hydraulic force acting on the annular pressure surface 74 in the closing direction is at least is lowered briefly. This is possible by the annular space present between the region 84 of the actuating section 72 and the inner wall of the stepped bore 64 and by the grooves 90 which pass through the region 86 of the actuating section 72 of the inner valve element 44. It is also conceivable, however, for the inner valve element 44 to be pressure-controlled, so that for an opening movement of the inner valve element 44, a corresponding, briefly increased, hydraulic force must act on the outer conical surface 78. In this case, the annular space between the region 84 of the actuating portion 72 and the stepped bore 64 and the grooves 90 in the region 86 for depressurization of the pressure surface 74 formed between the actuating portion 72 and the sealing portion 70 is used.
  • the inner fuel outlet channels 40 have a comparatively large diameter. This requires a comparatively large diameter in the region of the valve seat or, in other words, a large diameter of the sealing section 70 in the region of the sealing edge 82. Nevertheless, a high rigidity of the outer valve element 42 can be realized by the stepped bore 64 in the outer valve element 42.
  • FIG. 3 shows an alternative fuel injection device 24.
  • elements and areas which have equivalent functions to elements and areas of the fuel injection device 24 shown in Figure 2, the same reference numerals. They are not explained again in detail.
  • the sealing portion 70 of the inner valve member 44 has a smaller diameter than its operating portion 72.
  • the portion 66 of the stepped bore 64 in the outer valve member 42 has a larger diameter than the portion 68.
  • the diameter of the inner fuel Exit channels 40 significantly smaller than in the previous embodiment.
  • the sealing portion 60 of the outer valve member 42 may be larger overall, so that the inner cone surface 56 may be larger.
  • a secure opening of the outer valve element 42 is ensured even at low pressures in the annular space 48.
  • high pressures are required to generate at the comparatively small outer conical surface 78 of the inner valve element 44 that hydraulic force acting in the opening direction, which finally leads to a lifting of the sealing edge 82 from the valve seat surface 36.
  • the high forces can be well absorbed by the comparatively thick actuating portion 72 of the inner valve member 44, so this has sufficient rigidity. Due to the grooves 90 and the gap between the region 84 of the actuating portion 72 of the inner valve member 44 and the inner wall of the stepped bore 64, the pressure surface 74 can still be relieved sufficiently.

Abstract

A fuel injection device having a housing and an outer valve element contained in the housing and having a recess containing an inner valve element that has at least one sealing section cooperating with a valve seat and an actuation section connected to sealing section. The sealing section and the actuation section have different diameters. The recess disposed in the outer valve element and containing the inner valve element has sections with different diameters, which are at least approximately matched to the diameters of the sections of the inner valve element.

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Kraftstoff-Einspritzvorrichtung nach dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injection device according to the preamble of claim 1.

Eine derartige Kraftstoff-Einspritzvorrichtung ist aus der DE 41 15 477 A1 bekannt. Diese zeigt ein Einspritzventil mit zwei koaxial zueinander angeordneten Ventilelementen. Ein länglicher und vergleichsweise dünner Betätigungsabschnitt des inneren Ventilelements trägt an seinem Ende einen vergleichsweise dicken und zum Ventilsitz benachbarten Dichtabschnitt. Die Ausnehmung im äußeren Ventilelement, in welcher das innere Ventilelement angeordnet ist, ist gestuft. Zwischen Dichtabschnitt und der Ausnehmung im äußeren Ventilelement ist ein Spalt.Such a fuel injection device is known from DE 41 15 477 A1. This shows an injection valve with two coaxially arranged valve elements. An elongate and comparatively thin actuating portion of the inner valve member carries at its end a comparatively thick and adjacent to the valve seat sealing portion. The recess in the outer valve element, in which the inner valve element is arranged, is stepped. Between the sealing portion and the recess in the outer valve element is a gap.

Aufgabe der vorliegenden Erfindung ist es, eine Kraftstoff-Einspritzvorrichtung der eingangs genannten Art so weiterzubilden, dass sie möglichst effektiv arbeitet.Object of the present invention is to develop a fuel injection device of the type mentioned so that it works as effectively as possible.

Diese Aufgabe wird durch eine Kraftstoff-Einspritzvorrichtung mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved by a fuel injection device having the features of claim 1.

Vorteile der ErfindungAdvantages of the invention

Bei der erfindungsgemäßen Kraftstoff-Einspritzvorrichtung wird eine besonders gute Zentrierung des inneren Ventilelements erreicht, was zu optimalen und reproduzierbaren Strömungsverhältnissen bei einer Einspritzung von Kraftstoff führt. Dabei sei darauf hingewiesen, dass der Begriff "unten" nicht absolut, sondern relativ zur Kraftstoff-Einspritzvorrichtung zu verstehen ist.In the fuel injection device according to the invention, a particularly good centering of the inner valve element is achieved, which leads to optimal and reproducible flow conditions in an injection of fuel. It should be noted that the term "bottom" is not absolute, but relative to the fuel injection device to understand.

Bei der erfindungsgemäßen Kraftstoff-Einspritzvorrichtung sind einerseits der Außendurchmesser des inneren Ventilelements und der Innendurchmesser der Ausnehmung im äußeren Ventilelement gestuft und aufeinander abgestimmt. Hierdurch können die Wandstärken beziehungsweise Querschnittsflächen der Dichtabschnitte und der Betätigungsabschnitte der Ventilelemente optimal an die gewünschten Funktionen angepasst werden. Dies ist vor allem in Anbetracht der äußerst kleinen Gesamtabmessungen (Durchmesser eines Ventilelements von höchstens ein paar Millimetern, bisweilen auch deutlich weniger) vorteilhaft.In the fuel injection device according to the invention, on the one hand, the outer diameter of the inner valve element and the inner diameter of the recess in the outer valve element are stepped and matched to one another. As a result, the wall thicknesses or cross-sectional areas of the sealing sections and the actuating sections of the valve elements can be optimally adapted to the desired functions. This is particularly advantageous in view of the extremely small overall dimensions (diameter of a valve element of at most a few millimeters, sometimes significantly less).

Vorteilhafte Weiterbildungen der Erfindung sind in Unteransprüchen angegeben.Advantageous developments of the invention are specified in subclaims.

In einer ersten Weiterbildung wird vorgeschlagen, dass der Dichtabschnitt des inneren Ventilelements einen kleineren Durchmesser aufweist als dessen Betätigungsabschnitt. Somit kann das äußere Ventilelement einen relativ großen Dichtabschnitt aufweisen, so dass eine dort vorhandene Druckfläche ebenfalls vergleichsweise groß ist, was die hydraulische Betätigung des äußeren Ventilelements vor allem bei kleinen Drücken vereinfacht. Gleichzeitig weist der Betätigungsabschnitt des inneren Ventilelements einen dennoch so ausreichend großen Durchmesser auf, dass er eine hohe Steifigkeit besitzt.In a first development, it is proposed that the sealing section of the inner valve element has a smaller diameter than its actuating section. Thus, the outer valve member may have a relatively large sealing portion, so that there existing pressure surface is also relatively large, which simplifies the hydraulic actuation of the outer valve member, especially at low pressures. At the same time, the operating portion of the inner valve element has a nevertheless sufficiently large in diameter that it has a high rigidity.

Alternativ kann der Dichtabschnitt des inneren ventilelements aber auch einen größeren Durchmesser aufweisen als der Betätigungsabschnitt des inneren Ventilelements. Dies hat dann Vorteile, wenn vom inneren ventilelement relativ große Kraftstoffmengen eingespritzt werden sollen, was Kraftstoff-Austrittskanäle mit entsprechend großen Durchmessern erforderlich macht. Deren Anordnung wird erleichtert, wenn, wie vorliegend, der Dichtabschnitt des inneren ventilelements und, in der Folge, auch der zugehörige Ventilsitz einen vergleichsweise großen Durchmesser haben. Aufgrund des vergleichsweise dünnen Betätigungsabschnitts des inneren Ventilelements kann der Betätigungsabschnitt des äußeren Ventilelements eine vergleichsweise hohe Wandstärke haben, so dass in diesem Falle das äußere Ventilelement insgesamt eine hohe Steifigkeit aufweist.Alternatively, however, the sealing portion of the inner valve member may also have a larger diameter than the actuating portion of the inner valve member. This has advantages if the inner valve element relatively large amounts of fuel to be injected, which makes fuel outlet channels with correspondingly large diameters required. Their arrangement is facilitated if, as in the present case, the sealing portion of the inner valve element and, as a result, also the associated valve seat have a comparatively large diameter. Due to the comparatively thin actuating portion of the inner valve member, the operating portion of the outer valve member may have a comparatively high wall thickness, so that in this case the outer valve member has a high rigidity as a whole.

Ferner wird vorgeschlagen, dass das äußere Ventilelement einen oberen Führungsbereich aufweist, in dem der Betätigungsabschnitt des inneren Ventilelements wenigstens bereichsweise geführt ist (der Begriff "oben" ist hier nicht absolut, sondern relativ zur Kraftstoff-Einspritzvorrichtung zu verstehen). Auch dies kommt der Zentrierung des inneren Ventilelements im äußeren Ventilelement sowie der Absenkung der Betätigungsdrücke und somit letztlich der Qualität der Kraftstoffeinspritzung zugute.It is also proposed that the outer valve element has an upper guide region, in which the actuating portion of the inner valve element is guided at least in regions (the term "top" here is not absolute, but relative to the fuel injection device to understand). This also benefits the centering of the inner valve element in the outer valve element and the lowering of the actuating pressures and thus ultimately the quality of the fuel injection.

In einer besonders vorteilhaften Ausgestaltung der erfindungsgemäßen Kraftstoff-Einspritzvorrichtung bildet ein zwischen dem Dichtabschnitt und dem Betätigungsabschnitt des inneren Ventilelements vorhandener Absatz eine Druckfläche. Dies gestattet eine gleichmäßige Verteilung der am inneren Ventilelement angreifenden hydraulischen Kräfte.In a particularly advantageous embodiment of the fuel injection device according to the invention forms an existing between the sealing portion and the actuating portion of the inner valve member Paragraph a printing surface. This allows a uniform distribution of the forces acting on the inner valve element hydraulic forces.

In Weiterbildung hierzu wird vorgeschlagen, dass in der Mantelfläche des vom oberen Führungsbereich geführten Bereichs des inneren ventilelements und/oder in der Mantelfläche des oberen Führungsbereichs des äußeren Ventilelements in Längsrichtung verlaufende Ausnehmungen vorhanden sind. Hierdurch wird eine Druckbeaufschlagung der Druckfläche durch den Spalt zwischen dem inneren Ventilelement und dem äußeren Ventilelement und durch die Ausnehmungen im Führungsbereich ermöglicht. Auf einen separaten zusätzlichen Druckkanal kann in diesem Falle also verzichtet werden.In a further development, it is proposed that longitudinally extending recesses be present in the lateral surface of the region of the inner valve element guided by the upper guide region and / or in the lateral surface of the upper guide region of the outer valve element. As a result, pressurization of the pressure surface is made possible by the gap between the inner valve element and the outer valve element and by the recesses in the guide region. On a separate additional pressure channel can therefore be omitted in this case.

Zeichnungdrawing

Nachfolgend werden besonders bevorzugte Ausführungsbeispiele der vorliegenden Erfindung unter Bezugnahme auf die beiliegende Zeichnung im Detail erläutert. In der Zeichnung zeigen:

Figur 1
eine schematische Darstellung eines Kraftstoffsystems mit mehreren Kraftstoff-Einspritzvorrichtungen;
Figur 2
einen teilweisen Schnitt durch einen Bereich eines ersten Ausführungsbeispiels einer der Kraftstoff-Einspritzvorrichtungen von Figur 1; und
Figur 3
eine Darstellung ähnlich Figur 2 eines zweiten Ausführungsbeispiels einer der Kraftstoff-Einspritzvorrichtungen von Figur 1.
Hereinafter, particularly preferred embodiments of the present invention will be explained in detail with reference to the accompanying drawings. In the drawing show:
FIG. 1
a schematic representation of a fuel system with multiple fuel injectors;
FIG. 2
a partial section through a portion of a first embodiment of one of the fuel injectors of Figure 1; and
FIG. 3
2 shows a representation similar to FIG. 2 of a second exemplary embodiment of one of the fuel injection devices of FIG. 1.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Ein Kraftstoffsystem trägt in Figur 1 insgesamt das Bezugszeichen 10. Es kommt in einer Brennkraftmaschine 12 zum Einsatz, welche in Figur 1 nicht im Detail dargestellt ist.In FIG. 1, a fuel system bears the overall reference numeral 10. It is used in an internal combustion engine 12, which is not shown in detail in FIG.

Das Kraftstoffsystem 10 umfasst einen Kraftstoffbehälter 14, aus dem eine elektrische Kraftstoffpumpe 16 den Kraftstoff zu einer Hochdruck-Kraftstoffpumpe 18 fördert. Diese komprimiert den Kraftstoff auf einen sehr hohen Druck und fördert ihn in eine Kraftstoff-Sammelleitung ("Rail") 20. An diese sind über Hochdruckleitungen 22 mehrere Kraftstoff-Einspritzvorrichtungen 24 angeschlossen, welche den Kraftstoff direkt in ihnen zugeordnete Brennräume 26 einspritzen. Die Kraftstoff-Einspritzvorrichtungen 24 sind über eine Niederdruck-Rücklaufleitung 28 wieder mit dem Kraftstoffbehälter 14 verbunden.The fuel system 10 includes a fuel tank 14 from which an electric fuel pump 16 delivers the fuel to a high pressure fuel pump 18. This compresses the fuel to a very high pressure and conveys it into a fuel rail ("rail") 20. To these are connected via high-pressure lines 22 a plurality of fuel injectors 24, which Inject the fuel directly into them associated combustion chambers 26. The fuel injectors 24 are connected via a low pressure return line 28 to the fuel tank 14 again.

Ein dem Brennraum 26 zugewandter Bereich einer der Kraftstoff-Einspritzvorrichtungen 24 ist in Figur 2 im Detail dargestellt:An area of one of the fuel injection devices 24 facing the combustion chamber 26 is shown in detail in FIG. 2:

Danach umfasst die Kraftstoff-Einspritzvorrichtung 24 ein Gehäuse 30, in dem eine Stufen-Sackbohrung 32 vorhanden ist. Diese ist über einen Kanal 34 mit der Hochdruck-Leitung 22 verbunden. Der in Figur 2 untere Bereich der Stufen-Sackbohrung 32 verjüngt sich konisch. Er wird durch eine konische Ventilsitzfläche 36 begrenzt. In die Ventilsitzfläche 36 münden über den Umfang des Gehäuses 30 verteilt angeordnete radial äußere Kraftstoff-Austrittskanäle 38 sowie radial innere Kraftstoff-Austrittskanäle 40, welche jeweils die Gehäusewand durchsetzen.Thereafter, the fuel injector 24 includes a housing 30 in which a stepped blind bore 32 is present. This is connected via a channel 34 to the high-pressure line 22. The lower region of the stepped blind bore 32 in FIG. 2 tapers conically. It is limited by a conical valve seat surface 36. In the valve seat surface 36 open distributed over the circumference of the housing 30 arranged radially outer fuel outlet channels 38 and radially inner fuel outlet channels 40, which respectively pass through the housing wall.

In der Stufen-Sackbohrung 32 des Gehäuses 30 sind zwei zueinander koaxiale Ventilelemente angeordnet, nämlich ein äußeres Ventilelement 42 und ein inneres Ventilelement 44. Das äußere Ventilelement 42 wird in einem Führungsbereich 46 vom Gehäuse 30 fluiddicht geführt. Ein in Figur 2 unterhalb des Führungsbereichs 46 vorhandener Ringraum 48 zwischen dem äußeren Ventilelement 42 und der Wand der Stufen-Sackbohrung 32 ist über den Hochdruck-Kanal 34 mit der Hochdruck-Leitung 22 verbunden. Unmittelbar unterhalb vom Führungsbereich 46 weist der Ringraum 48 eine Ausbuchtung 50 auf, auf deren Höhe am äußeren Ventilelement 42 eine in Öffnungsrichtung des äußeren Ventilelements 42 wirkende Druckfläche 52 vorhanden ist.In the stepped blind bore 32 of the housing 30, two mutually coaxial valve elements are arranged, namely an outer valve element 42 and an inner valve element 44. The outer valve element 42 is guided in a guide region 46 from the housing 30 in a fluid-tight manner. An annular space 48 present in FIG. 2 below the guide region 46 between the outer valve element 42 and the wall of the stepped blind bore 32 is connected to the high-pressure line 22 via the high-pressure passage 34. Immediately below the guide region 46, the annular space 48 has a bulge 50, at the level of which on the outer valve element 42 there is a pressure surface 52 acting in the opening direction of the outer valve element 42.

Das in Figur 2 untere Ende des äußeren Ventilelements 42 ist ebenfalls konisch ausgebildet mit zwei Konusflächen 54 und 56 unterschiedlicher Konizität. Zwischen diesen ist eine Dichtkante 58 vorhanden. Die beiden Konusflächen 54 und 56 mit der Dichtkante 58 sind an einem Dichtabschnitt 60 des äußeren Ventilelements 42 vorhanden, wohingegen die Druckfläche 52 an einem Betätigungsabschnitt 62 des äußeren Ventilelements 42 vorhanden ist.The lower end of the outer valve element 42 in FIG. 2 is also conical with two conical surfaces 54 and 56 of different conicity. Between these a sealing edge 58 is present. The two conical surfaces 54 and 56 with the sealing edge 58 are provided on a sealing portion 60 of the outer valve member 42, whereas the pressure surface 52 is provided on an actuating portion 62 of the outer valve member 42.

Das innere Ventilelement 44 ist in einer Stufenbohrung 64 des äußeren Ventilelements 42 aufgenommen. Die Stufenbohrung 64 weist dabei einen Abschnitt 66 mit kleinerem und einen Abschnitt 68 mit größerem Durchmesser auf. Das innere Ventilelement 44 weist im Abschnitt 68 der Stufenbohrung 64 einen Dichtabschnitt 70 auf, der einen größeren Durchmesser hat als ein Betätigungsabschnitt 72 des inneren Ventilelements 44, der im Abschnitt 66 der Stufenbohrung 64 des äußeren Ventilelements 42 angeordnet ist. Zwischen den beiden Abschnitten 70 und 72 des inneren Ventilelements 44 ist ein Absatz vorhanden, der eine ringförmige Druckfläche 74 bildet.The inner valve member 44 is received in a stepped bore 64 of the outer valve member 42. The stepped bore 64 in this case has a portion 66 with a smaller and a portion 68 with a larger diameter. The inner valve element 44 has in the section 68 of the stepped bore 64 a sealing section 70 which has a larger diameter than an actuating section 72 of the inner valve element 44, which is arranged in the section 66 of the stepped bore 64 of the outer valve element 42. Between the two sections 70 and 72 of the inner valve member 44, a shoulder is present, which forms an annular pressure surface 74.

Der Dichtabschnitt 70 des inneren Ventilelements 44 umfasst einen Zylinderabschnitt 76, der im Abschnitt 68 der Stufenbohrung 64 fluiddicht geführt ist. Der Abschnitt 68 wird daher auch als "unterer Führungsbereich" bezeichnet. In Figur 2 unterhalb des Zylinderabschnitts 76 umfasst der Dichtabschnitt 70 zwei Bereiche unterschiedlicher Konizität. Diese werden von einer äußeren Konusfläche 78 beziehungsweise einer inneren Konusfläche 80 begrenzt, zwischen denen eine Dichtkante 82 vorhanden ist. Bei geschlossenem inneren Ventilelement 44 liegt die Dichtkante 82 an der Ventilsitzfläche 36 des Gehäuses 30 an. Analog hierzu liegt bei geschlossenem äußeren Ventilelement 42 dessen Dichtkante 48 an der gleichen Ventilsitzfläche 36 an.The sealing portion 70 of the inner valve member 44 includes a cylinder portion 76 which is fluid-tightly guided in the portion 68 of the stepped bore 64. The section 68 is therefore also referred to as "lower guide area". In FIG. 2, below the cylinder section 76, the sealing section 70 comprises two regions of different conicity. These are delimited by an outer conical surface 78 or an inner conical surface 80, between which a sealing edge 82 is present. When the inner valve element 44 is closed, the sealing edge 82 bears against the valve seat surface 36 of the housing 30. By analogy, when the outer valve element 42 is closed its sealing edge 48 on the same valve seat surface 36 at.

Der Betätigungsabschnitt 72 des inneren Ventilelements 44 hat zwei Bereiche 84 und 86 mit unterschiedlichen Durchmessern. Der unmittelbar an den Dichtabschnitt 70 anschließende Bereich 84 weist einen etwas kleineren Durchmesser als der Abschnitt 66 der Stufenbohrung 64 im äußeren Ventilelement 42 auf. Der Außendurchmesser des Bereichs 86 des Betätigungsabschnitte 72 entspricht dagegen in etwa dem Innendurchmesser des Abschnitts 66 der Stufenbohrung 64 im äußeren Ventilelement 42. Dieser Bereich der Stufenbohrung 62 bildet daher einen oberen Führungsbereich 88, in dem der Betätigungsabschnitt 72 des inneren Ventilelements 44 geführt ist. In den Bereich 86 des Betätigungsabschnitts 72 des inneren Ventilelements 44 sind in axialer Richtung verlaufende Nuten 90 eingebracht.The operating portion 72 of the inner valve member 44 has two regions 84 and 86 of different diameters. The immediately adjacent to the sealing portion 70 region 84 has a slightly smaller diameter than the portion 66 of the stepped bore 64 in the outer valve member 42. The outer diameter of the region 86 of the actuating portions 72, however, corresponds approximately to the inner diameter of the portion 66 of the stepped bore 64 in the outer valve member 42. This region of the stepped bore 62 therefore forms an upper guide portion 88, in which the actuating portion 72 of the inner valve member 44 is guided. In the region 86 of the actuating portion 72 of the inner valve member 44 extending in the axial direction grooves 90 are introduced.

Die in Figur 2 dargestellte Kraftstoff-Einspritzvorrichtung 24 kann hub- oder druckgesteuert oder in einer Kombination aus beiden Ansteuerprinzipien betrieben werden. Denkbar ist beispielsweise, dass das äußere Ventilelement 42 druckgesteuert arbeitet, dass eine Öffnungsbewegung des äußeren Ventilelements 42 also durch eine Druckerhöhung im Ringraum 48 bewirkt wird. Hierdurch erhöht sich die an der Druckfläche 52 und an der äußeren Konusfläche 54 angreifende hydraulische Kraft, welche schließlich entgegen einer konstanten Schließkraft zu einem Abheben der Dichtkante 58 von der Ventilsitzfläche 36 führt.The fuel injection device 24 shown in Figure 2 can be operated stroke or pressure controlled or in a combination of two control principles. It is conceivable, for example, that the outer valve element 42 operates under pressure control, that an opening movement of the outer valve element 42 is thus effected by an increase in pressure in the annular space 48. As a result, the hydraulic force acting on the pressure surface 52 and on the outer conical surface 54 increases, which finally leads, contrary to a constant closing force, to a lifting of the sealing edge 58 from the valve seat surface 36.

Das innere Ventilelement 44 kann hubgesteuert sein. Dies bedeutet, dass dessen Dichtkante 82 nur dann aufgrund einer konstanten Öffnungskraft von der Ventilsitzfläche 36 abhebt, wenn die an der ringförmigen Druckfläche 74 in Schließrichtung wirkende hydraulische Kraft wenigstens kurzzeitig abgesenkt wird. Dies ist möglich durch den zwischen dem Bereich 84 des Betätigungsabschnitts 72 und der Innenwand der Stufenbohrung 64 vorhandenen Ringraum und durch die Nuten 90, welche den Bereich 86 des Betätigungsabschnitts 72 des inneren Ventilelements 44 durchsetzen. Denkbar ist aber auch, dass das innere Ventilelement 44 druckgesteuert wird, dass zu einer Öffnungsbewegung des inneren Ventilelements 44 also eine entsprechende kurzzeitig erhöhte hydraulische Kraft an der äußeren Konusfläche 78 angreifen muss. In diesem Fall dient der Ringraum zwischen dem Bereich 84 des Betätigungsabschnitts 72 und der Stufenbohrung 64 sowie die Nuten 90 in dem Bereich 86 zur Druckentlastung der zwischen dem Betätigungsabschnitt 72 und dem Dichtabschnitt 70 gebildeten Druckfläche 74.The inner valve member 44 may be stroke controlled. This means that its sealing edge 82 only lifts off from the valve seat surface 36 due to a constant opening force when the hydraulic force acting on the annular pressure surface 74 in the closing direction is at least is lowered briefly. This is possible by the annular space present between the region 84 of the actuating section 72 and the inner wall of the stepped bore 64 and by the grooves 90 which pass through the region 86 of the actuating section 72 of the inner valve element 44. It is also conceivable, however, for the inner valve element 44 to be pressure-controlled, so that for an opening movement of the inner valve element 44, a corresponding, briefly increased, hydraulic force must act on the outer conical surface 78. In this case, the annular space between the region 84 of the actuating portion 72 and the stepped bore 64 and the grooves 90 in the region 86 for depressurization of the pressure surface 74 formed between the actuating portion 72 and the sealing portion 70 is used.

Bei dem in Figur 2 dargestellten Ausführungsbeispiel einer Kraftstoff-Einspritzvorrichtung 24 weisen die inneren Kraftstoff-Austrittskanäle 40 einen vergleichsweise großen Durchmesser auf. Dies erfordert einen vergleichsweise großen Durchmesser im Bereich des Ventilsitzes oder, mit anderen Worten, einen großen Durchmesser des Dichtabschnitts 70 im Bereich der Dichtkante 82. Durch die gestufte Bohrung 64 im äußeren Ventilelement 42 kann dennoch eine hohe Steifigkeit des äußeren Ventilelements 42 realisiert werden.In the exemplary embodiment of a fuel injection device 24 shown in FIG. 2, the inner fuel outlet channels 40 have a comparatively large diameter. This requires a comparatively large diameter in the region of the valve seat or, in other words, a large diameter of the sealing section 70 in the region of the sealing edge 82. Nevertheless, a high rigidity of the outer valve element 42 can be realized by the stepped bore 64 in the outer valve element 42.

In Figur 3 ist eine alternative Kraftstoff-Einspritzvorrichtung 24 dargestellt. Dabei tragen solche Elemente und Bereiche, welche äquivalente Funktionen zu Elementen und Bereichen der in Figur 2 dargestellten Kraftstoff-Einspritzvorrichtung 24 aufweisen, die gleichen Bezugszeichen. Sie sind nicht nochmals im Detail erläutert.FIG. 3 shows an alternative fuel injection device 24. In this case, bear such elements and areas which have equivalent functions to elements and areas of the fuel injection device 24 shown in Figure 2, the same reference numerals. They are not explained again in detail.

Im Gegensatz zu dem vorhergehenden Ausführungsbeispiel hat der Dichtabschnitt 70 des inneren Ventilelements 44 einen kleineren Durchmesser als sein Betätigungsabschnitt 72. Entsprechend hat auch der Abschnitt 66 der Stufenbohrung 64 im äußeren Ventilelement 42 einen größeren Durchmesser als der Abschnitt 68. Ferner ist der Durchmesser der inneren Kraftstoff-Austrittskanäle 40 deutlich kleiner als bei dem vorhergehenden Ausführungsbeispiel.In contrast to the previous embodiment, the sealing portion 70 of the inner valve member 44 has a smaller diameter than its operating portion 72. Similarly, the portion 66 of the stepped bore 64 in the outer valve member 42 has a larger diameter than the portion 68. Further, the diameter of the inner fuel Exit channels 40 significantly smaller than in the previous embodiment.

Auf diese Weise kann der Dichtabschnitt 60 des äußeren Ventilelements 42 insgesamt größer sein, so dass auch die innere Konusfläche 56 größer sein kann. Hierdurch wird auch bei geringen Drücken im Ringraum 48 ein sicheres Öffnen des äußeren Ventilelements 42 gewährleistet. Gleichzeitig sind hohe Drücke erforderlich, um an der vergleichsweise kleinen äußeren Konusfläche 78 des inneren Ventilelements 44 jene in Öffnungsrichtung wirkende hydraulische Kraft zu erzeugen, die schließlich zu einem Abheben der Dichtkante 82 von der Ventilsitzfläche 36 führt. Die hohen Kräfte können durch den vergleichsweise dicken Betätigungsabschnitt 72 des inneren Ventilelements 44 gut aufgenommen werden, dieses weist also eine ausreichende Steifigkeit aus. Durch die Nuten 90 und den Spalt zwischen dem Bereich 84 des Betätigungsabschnitts 72 des inneren Ventilelements 44 und der Innenwand der Stufenbohrung 64 kann die Druckfläche 74 dennoch in ausreichender Weise entlastet werden.In this way, the sealing portion 60 of the outer valve member 42 may be larger overall, so that the inner cone surface 56 may be larger. As a result, a secure opening of the outer valve element 42 is ensured even at low pressures in the annular space 48. At the same time, high pressures are required to generate at the comparatively small outer conical surface 78 of the inner valve element 44 that hydraulic force acting in the opening direction, which finally leads to a lifting of the sealing edge 82 from the valve seat surface 36. The high forces can be well absorbed by the comparatively thick actuating portion 72 of the inner valve member 44, so this has sufficient rigidity. Due to the grooves 90 and the gap between the region 84 of the actuating portion 72 of the inner valve member 44 and the inner wall of the stepped bore 64, the pressure surface 74 can still be relieved sufficiently.

Claims (6)

  1. Fuel injection device (24), in particular for internal combustion engines (12) having direct fuel injection, with a housing (30), with an outer valve element (42) which is arranged in said housing (30) and has a recess (64) in which an inner valve element (44) is arranged at least in regions, said inner valve element (44) having at least one sealing section (70) which interacts with a valve seat (36) by means of a sealing edge (82) and is arranged adjacent to said valve seat (36), and having an actuating section (72) which is connected to said sealing section (70) and is arranged at a distance from the valve seat (36), said sealing section (70) and actuating section (72) having different diameters, wherein the recess (64), in which the inner valve element (44) is arranged, in the outer valve element (42) has sections (66, 68) which are of different diameters which are at least approximately matched to the diameters of the sections (70, 72) of the inner valve element (44), and wherein the outer valve element (42) has a lower guide region (68) in which the sealing section (70) of the inner valve element (44) is guided at least in regions.
  2. Fuel injection device (24) according to Claim 1, characterized in that the sealing section (70) of the inner valve element (44) has a smaller diameter than the actuating section (72) of said inner valve element (44).
  3. Fuel injection device (24) according to Claim 1, characterized in that the sealing section (70) of the inner valve element (44) has a larger diameter than the actuating section (72) of said inner valve element (44).
  4. Fuel injection device (24) according to one of the preceding claims, characterized in that the outer valve element (42) has an upper guide region (88) in which the actuating section (72) of the inner valve element (44) is guided at least in regions.
  5. Fuel injection device (24) according to one of the preceding claims, characterized in that a shoulder which is provided between the sealing section (70) and the actuating section (72) of the inner valve element (44) forms a pressure face (74).
  6. Fuel injection device (24) according to Claims 4 and 5, characterized in that recesses (90) which run in the longitudinal direction are provided in the lateral surface of that region of the inner valve element (44) which is guided by the upper guide region (88) and/or in the lateral surface of the upper guide region of the outer valve element as a whole.
EP03769230A 2003-02-08 2003-10-08 Fuel-injection device, in particular for internal combustion engines with direct fuel-injection Expired - Lifetime EP1597473B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10305187A DE10305187A1 (en) 2003-02-08 2003-02-08 Fuel injection device, in particular for internal combustion engines with direct fuel injection
DE10305187 2003-02-08
PCT/DE2003/003329 WO2004070191A1 (en) 2003-02-08 2003-10-08 Fuel-injection device, in particular for internal combustion engines with direct fuel-injection

Publications (2)

Publication Number Publication Date
EP1597473A1 EP1597473A1 (en) 2005-11-23
EP1597473B1 true EP1597473B1 (en) 2006-12-20

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Application Number Title Priority Date Filing Date
EP03769230A Expired - Lifetime EP1597473B1 (en) 2003-02-08 2003-10-08 Fuel-injection device, in particular for internal combustion engines with direct fuel-injection

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US (1) US20060151638A1 (en)
EP (1) EP1597473B1 (en)
JP (1) JP2006521484A (en)
CN (1) CN1745241A (en)
AT (1) ATE348951T1 (en)
DE (2) DE10305187A1 (en)
WO (1) WO2004070191A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE406515T1 (en) * 2005-05-03 2008-09-15 Delphi Tech Inc DEVICE FOR A FUEL INJECTION VALVE WITH SWITCHABLE OPERATION MODES
JP4535037B2 (en) * 2006-02-08 2010-09-01 株式会社デンソー Injector and fuel injection device
JP4226011B2 (en) * 2006-02-16 2009-02-18 株式会社デンソー Fuel injection device
JP6488134B2 (en) * 2015-01-26 2019-03-20 日立オートモティブシステムズ株式会社 Fuel injection valve

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DE3433710A1 (en) * 1984-09-14 1986-03-27 Robert Bosch Gmbh, 7000 Stuttgart ELECTRICALLY CONTROLLED PUMPEDUESE FOR FUEL INJECTION IN DIESEL INTERNAL COMBUSTION ENGINES
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US6776358B2 (en) * 1998-10-09 2004-08-17 Jun Arimoto Fuel injection nozzle for a diesel engine
GB9904938D0 (en) * 1999-03-04 1999-04-28 Lucas Ind Plc Fuel injector
GB9913314D0 (en) * 1999-06-09 1999-08-11 Lucas Ind Plc Fuel injector
GB9914644D0 (en) * 1999-06-24 1999-08-25 Lucas Ind Plc Fuel injector
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EP1637730B1 (en) * 2004-09-17 2014-04-16 Delphi International Operations Luxembourg S.à r.l. Fuel injection nozzle and method of manufacture

Also Published As

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CN1745241A (en) 2006-03-08
US20060151638A1 (en) 2006-07-13
DE50306076D1 (en) 2007-02-01
DE10305187A1 (en) 2004-08-19
EP1597473A1 (en) 2005-11-23
WO2004070191A1 (en) 2004-08-19
ATE348951T1 (en) 2007-01-15
JP2006521484A (en) 2006-09-21

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