EP1518049B1 - Fuel injection valve for an internal combustion engine - Google Patents

Fuel injection valve for an internal combustion engine Download PDF

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Publication number
EP1518049B1
EP1518049B1 EP03718631A EP03718631A EP1518049B1 EP 1518049 B1 EP1518049 B1 EP 1518049B1 EP 03718631 A EP03718631 A EP 03718631A EP 03718631 A EP03718631 A EP 03718631A EP 1518049 B1 EP1518049 B1 EP 1518049B1
Authority
EP
European Patent Office
Prior art keywords
valve
needle
combustion chamber
hollow
chamber end
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
EP03718631A
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German (de)
French (fr)
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EP1518049A1 (en
Inventor
Detlev Di Potz
Thomas Kuegler
Predrag Nunic
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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 EP1518049A1 publication Critical patent/EP1518049A1/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
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
    • 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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/1833—Discharge orifices having changing cross sections, e.g. being divergent
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1866—Valve seats or member ends having multiple cones
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
    • 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 is based on a fuel injection valve for internal combustion engine, as it corresponds to the preamble of patent claim 1.
  • a fuel injection valve for example from the published patent application DE 27 11 391 and has a valve body in which a valve hollow needle is arranged to be longitudinally displaceable in a bore.
  • the valve hollow needle has at its combustion chamber end a conical valve sealing surface, with which it cooperates with a conical valve seat which forms the combustion chamber end of the bore.
  • a valve needle is arranged longitudinally displaceable, which also has a conical valve contact surface and cooperates with the valve seat. Both the valve hollow needle and the valve needle control the flow of fuel to at least one injection opening, through which fuel is injected into the combustion chamber of the internal combustion engine.
  • valve needle In the known fuel injection valve from DE 27 11 391, the tip of the valve hollow needle is flattened, so that an end face is formed, which lies in a radial plane of the valve hollow needle.
  • this valve needle has the disadvantage that between the valve hollow needle, the valve needle and the valve seat forms a relatively large dead volume, which has an adverse effect on the hydrocarbon emissions of the fuel injection valve.
  • a fuel injection valve in which the hollow valve needle has no flattening, but expires pointed. Although this reduces the dead volume and thus has a favorable effect on the hydrocarbon emissions of the internal combustion engine, but here there is the disadvantage that the inner needle can easily pinch in the outer needle. Due to the installation of the valve hollow needle on the conical valve seat, the valve hollow needle deforms slightly radially inwards, so that the already very small annular gap between the valve needle and the valve hollow needle is further reduced. This can lead to increased wear between these two slidably mounted components, which leads to a reduction in the life of the fuel injection valve.
  • a hollow valve needle which has a flattening at its combustion chamber end.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that a clamping of the valve needle is effectively prevented in the hollow valve needle with simultaneously reduced hydrocarbon emissions of the fuel injection valve.
  • the hollow valve needle at its tip a chamfer, which connects directly to the conical valve sealing surface. Since the outermost valve tip is no longer directly influenced by the force generated by the pressing of the hollow valve needle on the conical valve seat, results in a much lower indentation of the valve needle, and thus a jamming or excessive wear during movement prevents the valve needle in the valve hollow needle.
  • the volume between the valve hollow needle, the valve needle and the valve seat, when both the valve needle and the valve hollow needle abut the valve seat remains so low that there is no significant increase in the hydrocarbon emissions of the internal combustion engine.
  • FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention.
  • a valve body 1 In a valve body 1, a bore 3 is formed, at the combustion chamber end of which a conical valve seat 18 is formed.
  • a piston-shaped valve hollow needle 5 In the bore 3, which has a longitudinal axis 8, a piston-shaped valve hollow needle 5 is arranged longitudinally displaceable.
  • the valve hollow needle 5 is sealingly guided in a bore away from the combustion chamber in the bore 3 and tapers the valve seat 18 to form a pressure shoulder 14.
  • the hollow valve needle 5 has a conical valve sealing surface 24 which in the closed position of the valve hollow needle 5 on the valve seat 18th comes to the plant.
  • a pressure chamber 10 is formed, which is radially expanded at the level of the pressure shoulder 14. In the radial extension of the pressure chamber 10 opens a formed in the valve body 1 Inlet channel 12, via which the pressure chamber 10 can be filled with fuel under high pressure.
  • the valve hollow needle 5 has a longitudinal bore 6, whose longitudinal axis coincides with the longitudinal axis 8 of the valve hollow needle 5.
  • a valve needle 7 is arranged longitudinally displaceable, which has a conical valve contact surface 26 at its combustion chamber end, which likewise comes into contact with the valve seat 18 in the closed position of the valve needle 7.
  • a brennraumabgewandter, first guide portion 16 and a combustion chamber facing, second guide portion 17 is formed, in which it is guided relatively tight in the hollow valve needle 5.
  • the clearance between the second guide portion 17 and the wall of the longitudinal bore 6 is very small, preferably less than 10 microns. Between these two guide portions 16, 17, a relatively large annular gap between the valve needle 7 and the wall of the longitudinal bore 6 is formed, so that the valve needle 7 is actually guided only at the two guide portions 16, 17.
  • FIG. 1 shows this an enlargement of Figure 1 in the region of the valve seat 18 and Figure 3 again the same section as Figure 2, wherein the valve hollow needle 5 is not shown cut here.
  • the valve hollow needle 5 is in its closed position on the valve seat 18, wherein the valve sealing surface 24, the outer injection ports 20 closes.
  • the valve needle 7 closes with its valve contact surface 26, the inner injection openings 22.
  • annular groove 32 is formed, which is bounded on the one hand by the cylindrical portion of the valve needle 7 and on the other hand by the valve contact surface 26. Through this Ring groove 32 results in an attack surface for the fuel pressure of the pressure chamber 10 when the pressure acts on the valve needle 7.
  • Both the valve hollow needle 5 and the valve needle 7 are acted upon by a device, such as a spring, not shown in the drawing, with a closing force in the direction of the valve seat 18, so that they remain in their closed position in the absence of further forces.
  • a device such as a spring, not shown in the drawing
  • a closing force in the direction of the valve seat 18, so that they remain in their closed position in the absence of further forces.
  • a hydraulic force results on the pressure shoulder 14, which is opposite to the closing force on the valve hollow needle 5. If this hydraulic force exceeds the closing force, the valve hollow needle 5 lifts off from the valve seat 18 and releases the outer injection openings 20, through which fuel is injected into the combustion chamber of the internal combustion engine.
  • the valve needle 7 remains in its closed position until the now acting hydraulic pressure on the pressure shoulder, which is formed by the annular groove 32, sufficient to overcome the closing force on the valve needle 7.
  • valve needle 7 also moves out of its closed position, the fuel is injected in addition to the outer injection openings 20 also through the inner injection openings 22. If, however, only injected through the outer injection openings 20, the closing force on the valve needle 7 becomes so high held that they are not moved by the hydraulic pressure from its closed position. In this way, only a part of the entire injection cross section or the entire injection cross section can be controlled for the injection of fuel into the combustion chamber of the internal combustion engine.
  • a further conical surface 124 is formed, which adjoins the valve sealing surface 24 and extends to the cylindrical portion of the valve hollow needle 5.
  • a chamfer 30 connects to the valve seat 18, which forms a conical surface.
  • the chamfer 30 is inclined relative to the radial plane of the longitudinal axis 8.
  • the cone forming the conical surface of the chamfer 30 has a larger opening angle than the valve sealing surface 24.
  • the chamfer 30 prevents, on the one hand, that the valve hollow needle 5 experiences a radially inwardly directed force on its combustion-chamber-side end as a result of its contact with the conical valve seat 18 it may come to a pinching of the valve needle 7 in the valve hollow needle 5.
  • the valve hollow needle 5 has a sufficient wall thickness, so that only a very small indentation in the radial direction occurs due to the closing force on the valve hollow needle 5 and the valve needle 7 retains sufficient mobility in the longitudinal bore 6.
  • valve sealing surface 24 Since the angles of inclination of the valve sealing surface 24, the valve abutment surface 26 and the valve seat 18 are optimized so that a sealing of the injection openings 20, 22 is ensured against the pressure chamber 10, it may happen that fuel from between the valve seat 18 and the valve pins 5, 7 formed cavity in the injection breaks through the injection ports 20, 22 passes into the combustion chamber of the internal combustion engine and there leads to increased hydrocarbon emissions.
  • this volume By a corresponding inclination angle of the chamfers 30, this volume can be minimized without affecting the reduction in wear.

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

Abstract

The invention relates to a fuel injection valve for an internal combustion engine, comprising a valve base (1) in which, in a bore (3), a valve hollow needle (5) is disposed so as to be longitudinally displaced. The valve hollow needle (5), at its combustion chamber end, is provided with a conical valve stem (24) that interacts with a conical valve seat (18) disposed at the combustion chamber end of the bore (3). In the valve hollow needle (5) a longitudinal bore (6) is configured in which a valve needle (7) is disposed which, with a valve locating face (26) configured at its combustion chamber end, likewise interacts with the valve seat (18). The combustion chamber end tip of the valve hollow needle (5) is formed by a chamfered element (30).

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschine aus, wie es dem Oberbegriff des Patentanspruchs 1 entspricht. Ein derartiges Kraftstoffeinspritzventil ist beispielsweise aus der Offenlegungsschrift DE 27 11 391 bekannt und weist einen Ventilkörper auf, in dem in einer Bohrung eine Ventilhohlnadel längsverschiebbar angeordnet ist. Die Ventilhohlnadel weist an ihrem brennraumseitigen Ende eine konische Ventildichtfläche auf, mit der sie mit einem konischen Ventilsitz zusammenwirkt, der das brennraumseitige Ende der Bohrung bildet. In der Ventilhohlnadel ist eine Ventilnadel längsverschiebbar angeordnet, die ebenfalls eine konische Ventilanlagefläche aufweist und mit dem Ventilsitz zusammenwirkt. Sowohl die Ventilhohlnadel, als auch die Ventilnadel steuern den Kraftstofffluss zu jeweils wenigstens einer Einspritzöffnung, durch die Kraftstoff in den Brennraum der Brennkraftmaschine eingespritzt wird.The invention is based on a fuel injection valve for internal combustion engine, as it corresponds to the preamble of patent claim 1. Such a fuel injection valve is known for example from the published patent application DE 27 11 391 and has a valve body in which a valve hollow needle is arranged to be longitudinally displaceable in a bore. The valve hollow needle has at its combustion chamber end a conical valve sealing surface, with which it cooperates with a conical valve seat which forms the combustion chamber end of the bore. In the valve hollow needle, a valve needle is arranged longitudinally displaceable, which also has a conical valve contact surface and cooperates with the valve seat. Both the valve hollow needle and the valve needle control the flow of fuel to at least one injection opening, through which fuel is injected into the combustion chamber of the internal combustion engine.

Bei dem bekannten Kraftstoffeinspritzventil aus der DE 27 11 391 ist die Spitze der Ventilhohlnadel abgeflacht, so dass eine Stirnfläche gebildet wird, die in einer Radialebene der Ventilhohlnadel liegt. Diese Ventilnadel weist hierbei jedoch den Nachteil auf, dass sich zwischen der Ventilhohlnadel, der Ventilnadel und dem Ventilsitz ein relativ großes Totvolumen bildet, was sich ungünstig auf die Kohlenwasserstoff-Emissionen des Kraftstoffeinspritzventils auswirkt.In the known fuel injection valve from DE 27 11 391, the tip of the valve hollow needle is flattened, so that an end face is formed, which lies in a radial plane of the valve hollow needle. However, this valve needle has the disadvantage that between the valve hollow needle, the valve needle and the valve seat forms a relatively large dead volume, which has an adverse effect on the hydrocarbon emissions of the fuel injection valve.

Darüber hinaus ist aus der Offenlegungsschrift DE 27 11 390 ein Kraftstoffeinspritzventil bekannt, bei dem die Ventilhohlnadel keine Abflachung aufweist, sondern spitz ausläuft. Dies verringert zwar das Totvolumen und wirkt sich damit günstig auf die Kohlenwasserstoff-Emissionen der Brennkraftmaschine aus, jedoch ergibt sich hier der Nachteil, dass die Innennadel leicht in der Außennadel klemmen kann. Durch die Anlage der Ventilhohlnadel am konischen Ventilsitz kommt es zu einem leichten Verformen der Ventilhohlnadel radial nach innen, so dass sich der ohnehin nur sehr kleine Ringspalt zwischen der Ventilnadel und der Ventilhohlnadel weiter verringert. Dadurch kann es zu einem erhöhten Verschleiß zwischen diesen beiden gleitverschiebbar gegeneinander gelagerten Bauteilen kommen, was zu einer Verminderung der Lebensdauer des Kraftstoffeinspritzventil führt.In addition, from the published patent application DE 27 11 390 a fuel injection valve is known in which the hollow valve needle has no flattening, but expires pointed. Although this reduces the dead volume and thus has a favorable effect on the hydrocarbon emissions of the internal combustion engine, but here there is the disadvantage that the inner needle can easily pinch in the outer needle. Due to the installation of the valve hollow needle on the conical valve seat, the valve hollow needle deforms slightly radially inwards, so that the already very small annular gap between the valve needle and the valve hollow needle is further reduced. This can lead to increased wear between these two slidably mounted components, which leads to a reduction in the life of the fuel injection valve.

Aus der EP 967 382 A ist ebenfalls eine Ventilhohlnadel bekannt, die an ihrem brennraumseitigen Ende eine Abflachung aufweist.From EP 967 382 A, a hollow valve needle is also known which has a flattening at its combustion chamber end.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass ein Klemmen der Ventilnadel in der Ventilhohlnadel wirksam unterbunden wird bei gleichzeitig verminderten Kohlenwasserstoff-Emissionen des Kraftstoffeinspritzventils. Hierzu weist die Ventilhohlnadel an ihrer Spitze eine Anfasung auf, die sich direkt an die konische Ventildichtfläche anschließt. Da die äußerste Ventilspitze nun nicht mehr direkt von der Kraft, die durch das Anpressen der Ventilhohlnadel am konischen Ventilsitz erzeugt wird, beeinflusst wird, ergibt sich eine deutlich geringere Einformung der Ventilhohlnadel, und damit wird ein Klemmen oder ein übermäßiger Verschleiß bei der Bewegung der Ventilnadel in der Ventilhohlnadel verhindert. Gleichzeitig bleibt das Volumen zwischen der Ventilhohlnadel, der Ventilnadel und dem Ventilsitz, wenn sowohl die Ventilnadel als auch die Ventilhohlnadel am Ventilsitz anliegen, so gering, dass es zu keinem bedeutenden Anstieg der Kohlenwasserstoff-Emissionen der Brennkraftmaschine kommt.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that a clamping of the valve needle is effectively prevented in the hollow valve needle with simultaneously reduced hydrocarbon emissions of the fuel injection valve. For this purpose, the hollow valve needle at its tip a chamfer, which connects directly to the conical valve sealing surface. Since the outermost valve tip is no longer directly influenced by the force generated by the pressing of the hollow valve needle on the conical valve seat, results in a much lower indentation of the valve needle, and thus a jamming or excessive wear during movement prevents the valve needle in the valve hollow needle. At the same time, the volume between the valve hollow needle, the valve needle and the valve seat, when both the valve needle and the valve hollow needle abut the valve seat, remains so low that there is no significant increase in the hydrocarbon emissions of the internal combustion engine.

Zeichnungdrawing

In der Zeichnung ist ein Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Es zeigt

Figur 1
einen Ventilkörper im Längsschnitt,
Figur 2
eine Vergrößerung von Figur 1 im Bereich des Ventilsitzes, wobei die Ventilhohlnadel geschnitten dargestellt ist und
Figur 3
denselben Ausschnitt wie Figur 2, wobei hier die Ventilhohlnadel ungeschnitten gezeigt ist.
In the drawing, an embodiment of the fuel injection valve according to the invention is shown. It shows
FIG. 1
a valve body in longitudinal section,
FIG. 2
an enlargement of Figure 1 in the region of the valve seat, wherein the valve hollow needle is shown in section and
FIG. 3
the same section as Figure 2, in which case the valve hollow needle is shown uncut.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Figur 1 ist ein Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil dargestellt. In einem Ventilkörper 1 ist eine Bohrung 3 ausgebildet, an deren brennraumseitigen Ende ein konischer Ventilsitz 18 ausgebildet ist. In der Bohrung 3, die eine Längsachse 8 aufweist, ist eine kolbenförmige Ventilhohlnadel 5 längsverschiebbar angeordnet. Die Ventilhohlnadel 5 wird in einem brennraumabgewandten Abschnitt in der Bohrung 3 dichtend geführt und verjüngt sich dem Ventilsitz 18 zu unter Bildung einer Druckschulter 14. An ihrem brennraumseitigen Ende weist die Ventilhohlnadel 5 eine konische Ventildichtfläche 24 auf, die in Schließstellung der Ventilhohlnadel 5 am Ventilsitz 18 zur Anlage kommt. Zwischen der Ventilhohlnadel 5 und der Wand der Bohrung 3 ist ein Druckraum 10 ausgebildet, der auf Höhe der Druckschulter 14 radial erweitert ist. In die radiale Erweiterung des Druckraums 10 mündet ein im Ventilkörper 1 ausgebildeter Zulaufkanal 12, über den der Druckraum 10 mit Kraftstoff unter hohem Druck befüllt werden kann.FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention. In a valve body 1, a bore 3 is formed, at the combustion chamber end of which a conical valve seat 18 is formed. In the bore 3, which has a longitudinal axis 8, a piston-shaped valve hollow needle 5 is arranged longitudinally displaceable. The valve hollow needle 5 is sealingly guided in a bore away from the combustion chamber in the bore 3 and tapers the valve seat 18 to form a pressure shoulder 14. At its combustion chamber end, the hollow valve needle 5 has a conical valve sealing surface 24 which in the closed position of the valve hollow needle 5 on the valve seat 18th comes to the plant. Between the valve hollow needle 5 and the wall of the bore 3, a pressure chamber 10 is formed, which is radially expanded at the level of the pressure shoulder 14. In the radial extension of the pressure chamber 10 opens a formed in the valve body 1 Inlet channel 12, via which the pressure chamber 10 can be filled with fuel under high pressure.

Die Ventilhohlnadel 5 weist eine Längsbohrung 6 auf, deren Längsachse mit der Längsachse 8 der Ventilhohlnadel 5 zusammenfällt. In der Längsbohrung 6 ist eine Ventilnadel 7 längsverschiebbar angeordnet, die an ihrem brennraumseitigen Ende eine konische Ventilanlagefläche 26 aufweist, die in Schließstellung der Ventilnadel 7 ebenfalls am Ventilsitz 18 zur Anlage kommt. An der Ventilnadel 7 ist ein brennraumabgewandter, erster Führungsabschnitt 16 und ein brennraumzugewandter, zweiter Führungsabschnitt 17 ausgebildet, in denen sie relativ eng in der Ventilhohlnadel 5 geführt ist. Das Spiel zwischen dem zweiten Führungsabschnitt 17 und der Wand der Längsbohrung 6 ist dabei sehr gering, vorzugsweise weniger als 10 µm. Zwischen diesen beiden Führungsabschnitten 16, 17 ist ein relativ großer Ringspalt zwischen der Ventilnadel 7 und der Wand der Längsbohrung 6 ausgebildet, so dass die Ventilnadel 7 nur an den beiden Führungsabschnitten 16, 17 tatsächlich geführt wird.The valve hollow needle 5 has a longitudinal bore 6, whose longitudinal axis coincides with the longitudinal axis 8 of the valve hollow needle 5. In the longitudinal bore 6, a valve needle 7 is arranged longitudinally displaceable, which has a conical valve contact surface 26 at its combustion chamber end, which likewise comes into contact with the valve seat 18 in the closed position of the valve needle 7. At the valve needle 7 a brennraumabgewandter, first guide portion 16 and a combustion chamber facing, second guide portion 17 is formed, in which it is guided relatively tight in the hollow valve needle 5. The clearance between the second guide portion 17 and the wall of the longitudinal bore 6 is very small, preferably less than 10 microns. Between these two guide portions 16, 17, a relatively large annular gap between the valve needle 7 and the wall of the longitudinal bore 6 is formed, so that the valve needle 7 is actually guided only at the two guide portions 16, 17.

Ausgehend vom Ventilsitz 18 sind im Ventilkörper 1 äußere Einspritzöffnungen 20 und innere Einspritzöffnungen 22 ausgebildet, von denen vorzugsweise mehrere über den Umfang des Ventilkörpers 1 verteilt angeordnet sind. Figur 2 zeigt hierzu eine Vergrößerung von Figur 1 im Bereich des Ventilsitzes 18 und Figur 3 nochmals denselben Ausschnitt wie Figur 2, wobei die Ventilhohlnadel 5 hier nicht geschnitten dargestellt ist. Die Ventilhohlnadel 5 liegt in ihrer Schließstellung am Ventilsitz 18 an, wobei die Ventildichtfläche 24 die äußeren Einspritzöffnungen 20 verschließt. Ebenso verschließt die Ventilnadel 7 mit ihrer Ventilanlagefläche 26 die inneren Einspritzöffnungen 22. An der Ventilnadel 7 ist eine Ringnut 32 ausgebildet, die einerseits vom zylindrischen Abschnitt der Ventilnadel 7 begrenzt wird und andererseits von der Ventilanlagefläche 26. Durch diese Ringnut 32 ergibt sich eine Angriffsfläche für den Kraftstoffdruck des Druckraums 10, wenn der Druck die Ventilnadel 7 beaufschlagt.Starting from the valve seat 18, outer injection openings 20 and inner injection openings 22 are formed in the valve body 1, of which a plurality are preferably distributed over the circumference of the valve body 1. Figure 2 shows this an enlargement of Figure 1 in the region of the valve seat 18 and Figure 3 again the same section as Figure 2, wherein the valve hollow needle 5 is not shown cut here. The valve hollow needle 5 is in its closed position on the valve seat 18, wherein the valve sealing surface 24, the outer injection ports 20 closes. Likewise, the valve needle 7 closes with its valve contact surface 26, the inner injection openings 22. On the valve needle 7, an annular groove 32 is formed, which is bounded on the one hand by the cylindrical portion of the valve needle 7 and on the other hand by the valve contact surface 26. Through this Ring groove 32 results in an attack surface for the fuel pressure of the pressure chamber 10 when the pressure acts on the valve needle 7.

Sowohl die Ventilhohlnadel 5 als auch die Ventilnadel 7 werden von einer in der Zeichnung nicht dargestellten Vorrichtung, beispielsweise einer Feder, mit einer Schließkraft in Richtung des Ventilsitzes 18 beaufschlagt, so dass sie bei Fehlen weiterer Kräfte in ihrer Schließstellung bleiben. Durch Einleitung von Kraftstoff unter entsprechendem Einspritzdruck in den Druckraum 10 des Ventilkörpers 1 ergibt sich eine hydraulische Kraft auf die Druckschulter 14, die der Schließkraft auf die Ventilhohlnadel 5 entgegengerichtet ist. Übersteigt diese hydraulische Kraft die Schließkraft, so hebt die Ventilhohlnadel 5 vom Ventilsitz 18 ab und gibt die äußeren Einspritzöffnungen 20 frei, durch welche Kraftstoff in den Brennraum der Brennkraftmaschine eingespritzt wird. Die Ventilnadel 7 verbleibt vorerst in ihrer Schließstellung, bis der jetzt wirkende hydraulischen Druck auf die Druckschulter, die durch die Ringnut 32 gebildet wird, ausreicht, die Schließkraft auf die Ventilnadel 7 zu überwinden. Bewegt sich auch die Ventilnadel 7 aus ihrer Schließstellung, so erfolgt die Einspritzung von Kraftstoff zusätzlich zu den äußeren Einspritzöffnungen 20 auch durch die inneren Einspritzöffnungen 22. Soll hingegen nur durch die äußeren Einspritzöffnungen 20 eingespritzt werden, so wird die Schließkraft auf die Ventilnadel 7 so hoch gehalten, dass sie sich durch den hydraulischen Druck nicht aus ihrer Schließstellung bewegt. Auf diese Weise lässt sich für die Einspritzung von Kraftstoff in den Brennraum der Brennkraftmaschine nur ein Teil des gesamten Einspritzquerschnitts oder der gesamte Einspritzquerschnitt aufsteuern.Both the valve hollow needle 5 and the valve needle 7 are acted upon by a device, such as a spring, not shown in the drawing, with a closing force in the direction of the valve seat 18, so that they remain in their closed position in the absence of further forces. By introducing fuel under a corresponding injection pressure into the pressure chamber 10 of the valve body 1, a hydraulic force results on the pressure shoulder 14, which is opposite to the closing force on the valve hollow needle 5. If this hydraulic force exceeds the closing force, the valve hollow needle 5 lifts off from the valve seat 18 and releases the outer injection openings 20, through which fuel is injected into the combustion chamber of the internal combustion engine. The valve needle 7 remains in its closed position until the now acting hydraulic pressure on the pressure shoulder, which is formed by the annular groove 32, sufficient to overcome the closing force on the valve needle 7. If the valve needle 7 also moves out of its closed position, the fuel is injected in addition to the outer injection openings 20 also through the inner injection openings 22. If, however, only injected through the outer injection openings 20, the closing force on the valve needle 7 becomes so high held that they are not moved by the hydraulic pressure from its closed position. In this way, only a part of the entire injection cross section or the entire injection cross section can be controlled for the injection of fuel into the combustion chamber of the internal combustion engine.

Am brennraumseitigen Ende der Ventilhohlnadel 5 ist neben der Ventildichtfläche 24, die am Ventilsitz 18 in Schließstellung der Ventilhohlnadel 5 zur Anlage kommt, in diesem Ausführungsbeispiel eine weitere Konusfläche 124 ausgebildet, die an die Ventildichtfläche 24 grenzt und bis zum zylindrischen Bereich der Ventilhohlnadel 5 reicht. An die Ventildichtfläche 24 schließt sich zum Ventilsitz 18 hin eine Anfasung 30 an, die eine Konusfläche bildet. Dadurch ist die Anfasung 30 gegenüber der Radialebene der Längsachse 8 geneigt. Der die Konusfläche der Anfasung 30 bildende Kegel weist jedoch einen größeren Öffnungswinkel auf als die Ventildichtfläche 24. Die Anfasung 30 verhindert zum einen, dass die Ventilhohlnadel 5 durch ihre Anlage am konischen Ventilsitz 18 eine radial nach innen gerichtete Kraft auf ihr brennraumseitiges Ende erfährt, wodurch es zu einem Klemmen der Ventilnadel 7 in der Ventilhohlnadel 5 kommen kann. Die Ventilhohlnadel 5 weist im Bereich der Ventildichtfläche 24 jedoch eine ausreichende Wandstärke auf, so dass es durch die Schließkraft auf die Ventilhohlnadel 5 nur zu einer sehr geringen Einformung in radialer Richtung kommt und die Ventilnadel 7 eine ausreichende Beweglichkeit in der Längsbohrung 6 behält. Durch die Anfasung 30 ist im Gegensatz zu einer Abflachung aber auch sichergestellt, dass der Raum zwischen der Ventilhohlnadel 7, der Ventilnadel 5 und dem Ventilsitz 18 nicht zu groß wird. Da die Neigungswinkel der Ventildichtfläche 24, der Ventilanlagefläche 26 und des Ventilsitzes 18 so optimiert sind, dass eine Abdichtung der Einspritzöffnungen 20, 22 gegen den Druckraum 10 sichergestellt ist, kann es vorkommen, dass Kraftstoff aus dem zwischen dem Ventilsitz 18 und den Ventilnadeln 5, 7 gebildeten Hohlraum in den Einspritzpausen durch die Einspritzöffnungen 20, 22 in den Brennraum der Brennkraftmaschine gelangt und dort zu erhöhten Kohlenwasserstoff-Emissionen führt. Durch einen entsprechenden Neigungswinkel der Anfasungen 30 lässt sich dieses Volumen minimieren, ohne die Verschleißminderung zu beeinträchtigen.At the combustion chamber end of the hollow valve needle 5 is next to the valve sealing surface 24, which comes to rest on the valve seat 18 in the closed position of the hollow valve needle 5 in this Embodiment, a further conical surface 124 is formed, which adjoins the valve sealing surface 24 and extends to the cylindrical portion of the valve hollow needle 5. At the valve sealing surface 24, a chamfer 30 connects to the valve seat 18, which forms a conical surface. As a result, the chamfer 30 is inclined relative to the radial plane of the longitudinal axis 8. However, the cone forming the conical surface of the chamfer 30 has a larger opening angle than the valve sealing surface 24. The chamfer 30 prevents, on the one hand, that the valve hollow needle 5 experiences a radially inwardly directed force on its combustion-chamber-side end as a result of its contact with the conical valve seat 18 it may come to a pinching of the valve needle 7 in the valve hollow needle 5. However, in the region of the valve sealing surface 24, the valve hollow needle 5 has a sufficient wall thickness, so that only a very small indentation in the radial direction occurs due to the closing force on the valve hollow needle 5 and the valve needle 7 retains sufficient mobility in the longitudinal bore 6. By chamfering 30 but in contrast to a flattening but also ensures that the space between the hollow valve needle 7, the valve needle 5 and the valve seat 18 is not too large. Since the angles of inclination of the valve sealing surface 24, the valve abutment surface 26 and the valve seat 18 are optimized so that a sealing of the injection openings 20, 22 is ensured against the pressure chamber 10, it may happen that fuel from between the valve seat 18 and the valve pins 5, 7 formed cavity in the injection breaks through the injection ports 20, 22 passes into the combustion chamber of the internal combustion engine and there leads to increased hydrocarbon emissions. By a corresponding inclination angle of the chamfers 30, this volume can be minimized without affecting the reduction in wear.

Claims (3)

  1. Fuel injection valve for internal combustion engines having a valve body (1) in which a hollow valve needle (5) is arranged in a longitudinally displaceable fashion in a bore (3) and has, at its combustion chamber end, a conical valve sealing face (24) which interacts with a conical valve seat (18) which is arranged at the combustion chamber end of the bore (3), and having a longitudinal bore (6) which is formed in the hollow valve needle (5) and in which a valve needle (7) is arranged, said valve needle (7) also interacting with the valve seat (18) with a valve bearing face (26) which is formed at the combustion chamber end of said valve needle (7), with a chamfer (30) being formed at the combustion chamber end tip of the hollow valve needle (5), characterized in that the chamfer (30) of the hollow valve needle (5) forms a conical face which directly adjoins the conical valve sealing face (24).
  2. Fuel injection valve according to Claim 1, characterized in that at the inner, combustion chamber end edge of the chamfer (30) it directly adjoins the inner lateral surface of the longitudinal bore (6) of the hollow valve needle (5).
  3. Fuel injection valve according to Claim 1, characterized in that the valve needle (7) is guided in its combustion chamber end region with little play in the hollow valve needle (5), with the play being less than 10 µm.
EP03718631A 2002-06-19 2003-03-26 Fuel injection valve for an internal combustion engine Expired - Lifetime EP1518049B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10227277A DE10227277A1 (en) 2002-06-19 2002-06-19 Fuel injection valve for internal combustion engines
DE10227277 2002-06-19
PCT/DE2003/000991 WO2004001219A1 (en) 2002-06-19 2003-03-26 Fuel injection valve for an internal combustion engine

Publications (2)

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EP1518049A1 EP1518049A1 (en) 2005-03-30
EP1518049B1 true EP1518049B1 (en) 2006-05-10

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EP03718631A Expired - Lifetime EP1518049B1 (en) 2002-06-19 2003-03-26 Fuel injection valve for an internal combustion engine

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EP (1) EP1518049B1 (en)
JP (1) JP2005530091A (en)
CN (1) CN100370132C (en)
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WO (1) WO2004001219A1 (en)

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DE10351881A1 (en) * 2003-10-30 2005-06-02 Robert Bosch Gmbh Injector with structures for limiting wear-related changes of an opening course
TR200402050A2 (en) * 2004-08-18 2006-03-21 Robert Bosch Gmbh Dual seating diameter injector with coaxial areal contact
CN101268273B (en) * 2005-04-06 2012-01-18 通用汽车环球科技运作公司 Injector double row cluster configuration for reduced soot emissions
CN104919173A (en) * 2013-01-11 2015-09-16 Kw技术有限两合公司 Device for spraying liquid into an operating space
JP5716788B2 (en) * 2013-04-25 2015-05-13 株式会社デンソー Fuel injection valve
GB201309122D0 (en) * 2013-05-21 2013-07-03 Delphi Tech Holding Sarl Fuel Injector
DE102014224348A1 (en) * 2014-11-28 2016-06-02 Robert Bosch Gmbh Direct injection gas injector with improved opening and closing behavior
JP2017008861A (en) * 2015-06-24 2017-01-12 株式会社デンソー Fuel injection nozzle
JP6507890B2 (en) * 2015-07-02 2019-05-08 株式会社デンソー Fuel injection valve
US10453490B2 (en) 2017-12-19 2019-10-22 Panasonic Intellectual Property Management Co., Ltd. Optical disc device
DE102019210142A1 (en) * 2019-07-10 2021-01-14 Robert Bosch Gmbh Injection valve for a water injection system of an internal combustion engine and water injection system with such an injection valve

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DE2711391A1 (en) * 1977-03-16 1978-09-21 Bosch Gmbh Robert FUEL INJECTOR
DE3236046C2 (en) * 1982-09-29 1986-03-20 Daimler-Benz Ag, 7000 Stuttgart Fuel injector for internal combustion engines
DE3429471C2 (en) * 1984-08-10 1987-04-30 L'Orange GmbH, 7000 Stuttgart Fuel injection nozzle for an internal combustion engine
DE3938551A1 (en) * 1989-11-21 1991-05-23 Bosch Gmbh Robert IC engine fuel injection nozzle - has longitudinal groove in needle valve stem, delivering fuel to seat
EP0967382B1 (en) * 1998-06-24 2004-11-24 Delphi Technologies, Inc. Fuel injector
GB9903496D0 (en) * 1999-02-16 1999-04-07 Lucas Ind Plc Fuel injector
DE10122241A1 (en) * 2001-05-08 2002-12-05 Bosch Gmbh Robert Fuel injection valve for internal combustion engines

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DE10227277A1 (en) 2004-01-08
DE50303303D1 (en) 2006-06-14
US20050139698A1 (en) 2005-06-30
CN1662742A (en) 2005-08-31
CN100370132C (en) 2008-02-20
WO2004001219A1 (en) 2003-12-31
JP2005530091A (en) 2005-10-06
EP1518049A1 (en) 2005-03-30
US7044406B2 (en) 2006-05-16

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