EP1045977B1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP1045977B1
EP1045977B1 EP99938137A EP99938137A EP1045977B1 EP 1045977 B1 EP1045977 B1 EP 1045977B1 EP 99938137 A EP99938137 A EP 99938137A EP 99938137 A EP99938137 A EP 99938137A EP 1045977 B1 EP1045977 B1 EP 1045977B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
space
fuel injection
valve member
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
EP99938137A
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German (de)
French (fr)
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EP1045977A1 (en
Inventor
Roger Potschin
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1045977A1 publication Critical patent/EP1045977A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M61/08—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 the valves opening in direction of fuel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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

Definitions

  • the invention relates to a fuel injection valve for Internal combustion engines according to the preamble of the claim 1.
  • Such an injector goes for example from the DE 43 25 904 C2 and from the unpublished DE 197 16 226.6-13.
  • the fuel injector according to the invention with the Features of claim 1, however, has the Advantage that the leadership and sealing against the fuel injection valves known from the prior art is improved for internal combustion engines.
  • the order the one pressure shoulder on the distant combustion chamber End of the valve body in a fluid with the pressure chamber connected compensation room, the front through completed an axially displaceable pressure sleeve has the particularly great advantage that the compensation space is always connected to the pressure chamber. hereby it is ensured that the pressure shoulder on the one hand is always pressurized, on the other ensures that pressure differences, for example when opening the fuel injector, between the Pressure chamber and the compensation room compensated directly become.
  • the valve member is advantageously between the two Pressure shoulders needle-shaped and has one constant diameter.
  • the pressure sleeve is preferred to avoid leaks pressed onto the valve member.
  • the compensation space can be designed in any way his.
  • One particularly with regard to a simple one Manufacturing advantageous embodiment sees that the compensation chamber the pressure shoulder remote from the combustion chamber surrounds in a ring.
  • the high pressure fuel supply to the fuel injector preferably takes place from one for all fuel injection valves common high pressure storage space, which in turn can be filled using a high-pressure fuel pump is.
  • the actuator for actuating the valve member is advantageous an electromechanical actuator. It is designed in particular as a piezo actuator or electromagnet.
  • FIG. 1 An embodiment of a fuel injector for internal combustion engines, the lower, combustion chamber side Part in Fig. 1 in a schematic sectional view is shown has a valve body 10 which by means of a union nut 30 on a valve holding body 20 is axially clamped.
  • the valve body 10 has an axial guide bore 40 in which a needle-shaped valve member 50 is axially displaceable which is led to his in one (not shown) combustion chamber of the fuel to be supplied Internal combustion engine protruding lower end has valve head 52 acting as a valve closing member.
  • This valve head 52 protruding from the bore has one conical sealing surface 53 facing valve body 10 on by in the illustrated embodiment formed on the valve head 52 seat ring and that with a corresponding valve seat surface 11 on the end face of the valve body on the combustion chamber side 10 cooperates.
  • valve member 50 Between the wall of the bore 40 and part of the Shaft of the valve member 50 is a pressure chamber 12 in the valve body 10 formed, the axially each of a Valve member 50 formed pressure shoulder 54 and 55 limited is.
  • This pressure chamber 12 opens into a pressure chamber 13 enlarged volume of the pressure chamber 12 itself a supply bore 60 in a known manner.
  • the one located at the end of the pressure chamber 12 remote from the combustion chamber Pressure shoulder 55 has the same pressure application area on how that formed on the valve member head 52 pressure shoulder 54 near the combustion chamber, so that the valve member 50 is pressure balanced. This prevents that the fuel injector due to the applied Common rail pressure opens automatically.
  • the fuel injector has another additional one Attack surface acted upon by high-pressure fuel through which the pending at the injector High fuel pressure in the closing direction on the valve member 50 works.
  • This additional pressure application area is by a lower end face 71 on the combustion chamber side a pressure sleeve 70 is formed, which a compensation space 80, the pressure shoulder 55 distant from the combustion chamber in the shape of a ring surrounds and fluidly connected to the pressure chamber 12 is on its side facing away from the combustion chamber.
  • the compensation space 80 forms in this way the combustion chamber distant end of the pressure chamber 12.
  • the sleeve 70 is axially displaceable in an annular body 90 led.
  • valve member 56 As can also be seen from Fig. 1, follows the Valve member 56 another stem portion 57, the into a spring chamber provided in the valve holding body 20 22 protrudes.
  • an electromechanical actuator for example a piezo actuator or an electromagnet, an axial displacement of the valve member 50 and thus an opening of those provided in the valve member head 52 Injection opening (not shown).
  • the area between the two pressure shoulders 54 or 55 of the valve member 50 is needle-shaped with a constant Diameter formed.
  • the elasticity that this enables of the valve member 50 in particular perpendicular to Valve member axis advantageously enables Compensate for an offset between the guides of the Valve member 50 through the pressure sleeve 70 and the Valve member head 52 are formed in the central region of the needle-shaped area.

Description

Beschreibung und Stand der TechnikDescription and state of the art

Die Erfindung betrifft ein Kraftstoffeinspritzventil für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1.The invention relates to a fuel injection valve for Internal combustion engines according to the preamble of the claim 1.

Ein solches Einspritzventil geht beispielsweise aus der DE 43 25 904 C2 sowie aus der nicht vorveröffentlichten DE 197 16 226.6-13 hervor.Such an injector goes for example from the DE 43 25 904 C2 and from the unpublished DE 197 16 226.6-13.

Problematisch bei derartigen Kraftstoffeinspritzventilen ist die Führung und Abdichtung des Ventilglieds im Ventilkörper 1. So kommt es insbesondere bei nicht exakt ausgerichteten Bohrungen oder dann, wenn das Ventilglied geringfügige Knicks aufweist, zu Führungs- und Dichtheitsproblemen. Problematic with such fuel injection valves is the guiding and sealing of the valve member in the valve body 1. This is especially the case with not exactly aligned holes or when the valve member shows slight kinks, problems with guidance and tightness.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß die Führung und Abdichtung gegenüber den aus dem Stand der Technik bekannten Kraftstoffeinspritzventilen für Brennkraftmaschinen verbessert ist. Die Anordnung der einen Druckschulter an dem brennraumfernen Ende des Ventilkörpers in einem mit dem Druckraum fluidisch verbundenen Ausgleichsraum, der stirnseitig durch eine axial verschieblich geführte Druckhülse abgeschlossen ist, hat den besonders großen Vorteil, daß der Ausgleichsraum immer mit dem Druckraum verbunden ist. Hierdurch ist sichergestellt, daß die Druckschulter zum einen immer mit einem Druck beaufschlagt wird, zum anderen ist sichergestellt, daß Druckunterschiede, zum Beispiel beim Öffnen des Kraftstoffeinspritzventils, zwischen dem Druckraum und dem Ausgleichsraum direkt ausgeglichen werden. Auf diese Weise ist immer eine Rückstellung in die Schließposition des Kraftstoffeinspritzventils - auch dann, wenn beispielsweise aufgrund eines brennraumseitigen Lecks aufgrund einer hierdurch bewirkten Druckdifferenz zwischen den Druckschultern eine in Öffnungsrichtung wirkende Kraft an dem Ventilglied wirkt - gegeben.The fuel injector according to the invention with the Features of claim 1, however, has the Advantage that the leadership and sealing against the fuel injection valves known from the prior art is improved for internal combustion engines. The order the one pressure shoulder on the distant combustion chamber End of the valve body in a fluid with the pressure chamber connected compensation room, the front through completed an axially displaceable pressure sleeve has the particularly great advantage that the compensation space is always connected to the pressure chamber. hereby it is ensured that the pressure shoulder on the one hand is always pressurized, on the other ensures that pressure differences, for example when opening the fuel injector, between the Pressure chamber and the compensation room compensated directly become. This way there is always a provision in the closed position of the fuel injector - even if, for example, due to a combustion chamber Leaks due to a pressure difference caused thereby one in the opening direction between the pressure shoulders acting force on the valve member acts - given.

Vorteilhafterweise ist das Ventilglied zwischen den beiden Druckschultern nadeiförmig ausgebildet und weist einen konstanten Durchmesser auf. Durch diese Ausbildung des Ventilglieds zwischen den beiden Druckschultern als dünne Nadel mit konstantem Durchmesser kann ein geringfügiger Versatz zwischen den Führungen, die einerseits durch den Ventilgliedkopf, andererseits durch die Druckhülse gebildet werden, auf einfache und vorteilhafte Weise ausgeglichen werden.The valve member is advantageously between the two Pressure shoulders needle-shaped and has one constant diameter. Through this training of the valve member between the two pressure shoulders as thin needle with constant diameter can be a minor Offset between the guides on the one hand through the valve member head, on the other hand through the pressure sleeve be formed on simple and beneficial Be balanced.

Die Druckhülse ist zur Vermeidung von Leckagen vorzugsweise auf das Ventilglied aufgepreßt. Rein prinzipiell kann der Ausgleichsraum auf beliebige Art und Weise ausgebildet sein. Eine insbesondere hinsichtlich einer einfachen Herstellung vorteilhafte Ausführungsform sieht vor, daß der Ausgleichsraum die brennraumferne Druckschulter ringförmig umgibt.The pressure sleeve is preferred to avoid leaks pressed onto the valve member. In principle the compensation space can be designed in any way his. One particularly with regard to a simple one Manufacturing advantageous embodiment sees that the compensation chamber the pressure shoulder remote from the combustion chamber surrounds in a ring.

Die Kraftstoffhochdruckzufuhr des Kraftstoffeinspritzventils erfolgt vorzugsweise aus einem für alle Kraftstoffeinspritzventile gemeinsamen Hochdruckspeicherraum, der seinerseits über eine Kraftstoffhochdruckpumpe befüllbar ist.The high pressure fuel supply to the fuel injector preferably takes place from one for all fuel injection valves common high pressure storage space, which in turn can be filled using a high-pressure fuel pump is.

Das Stellglied zur Betätigung des Ventilsglieds ist vorteilhafterweise ein elektromechanisches Stellglied. Es ist insbesondere als Piezoaktor oder Elektromagnet ausgebildet.The actuator for actuating the valve member is advantageous an electromechanical actuator. It is designed in particular as a piezo actuator or electromagnet.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstands der Erfindung sind der Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar.Further advantages and advantageous configurations of the The invention relates to the description of the Drawing and the claims can be found.

Zeichnungdrawing

In der Zeichnung zeigen:

Fig. 1
schematisch geschnitten den unteren Bereich eines von der Erfindung Gebrauch machenden Kraftstoffeinspritzventils für Brennkraftmaschinen und
Fig. 2
schematisch geschnitten in vergrößerter Darstellung das brennraumferne Ende des Ventilkörpers des in Fig. 1 dargestellten Kraftstoffeinspritzventils für Brennkraftmaschinen.
The drawing shows:
Fig. 1
schematically cut the lower portion of a fuel injection valve for internal combustion engines and the invention
Fig. 2
schematically sectioned in an enlarged view, the end remote from the combustion chamber of the valve body of the fuel injector shown in FIG. 1 for internal combustion engines.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Ein Ausführungsbeispiel eines Kraftstoffeinspritzventils für Brennkraftmaschinen, dessen unterer, brennraumseitiger Teil in Fig. 1 in Schnittdarstellung schematisch dargestellt ist, weist einen Ventilkörper 10 auf, der mittels einer Überwurfmutter 30 an einem Ventilhaltekörper 20 axial festgespannt ist.An embodiment of a fuel injector for internal combustion engines, the lower, combustion chamber side Part in Fig. 1 in a schematic sectional view is shown has a valve body 10 which by means of a union nut 30 on a valve holding body 20 is axially clamped.

Der Ventilkörper 10 weist eine axiale Führungsbohrung 40 auf, in der ein nadelförmiges Ventilglied 50 axial verschieblich geführt ist, das an seinem in einen (nicht dargestellten) Brennraum der mit Kraftstoff zu versorgenden Brennkraftmaschine ragenden unteren Ende einen als Ventilschließglied wirkenden Ventilkopf 52 aufweist. Dieser aus der Bohrung ragende Ventilkopf 52 weist eine dem Ventilkörper 10 zugewandte konische Dichtfläche 53 auf, die bei dem dargestellten Ausführungsbeispiel durch einen auf den Ventilkopf 52 aufgesetzten Sitzring gebildet ist und die mit einer entsprechenden Ventilsitzfläche 11 an der brennraumseitigen Stirnseite des Ventilkörpers 10 zusammenwirkt.The valve body 10 has an axial guide bore 40 in which a needle-shaped valve member 50 is axially displaceable which is led to his in one (not shown) combustion chamber of the fuel to be supplied Internal combustion engine protruding lower end has valve head 52 acting as a valve closing member. This valve head 52 protruding from the bore has one conical sealing surface 53 facing valve body 10 on by in the illustrated embodiment formed on the valve head 52 seat ring and that with a corresponding valve seat surface 11 on the end face of the valve body on the combustion chamber side 10 cooperates.

Zwischen der Wand der Bohrung 40 und einem Teil des Schafts des Ventilglieds 50 ist ein Druckraum 12 im Ventilkörper 10 gebildet, der axial jeweils von einer am Ventilglied 50 ausgebildeten Druckschulter 54 und 55 begrenzt ist.Between the wall of the bore 40 and part of the Shaft of the valve member 50 is a pressure chamber 12 in the valve body 10 formed, the axially each of a Valve member 50 formed pressure shoulder 54 and 55 limited is.

In diesen Druckraum 12 mündet in einem als Druckkammer 13 vergrößerten Volumen des Druckraums 12 auf an sich bekannte Weise eine Zulaufbohrung 60.This pressure chamber 12 opens into a pressure chamber 13 enlarged volume of the pressure chamber 12 itself a supply bore 60 in a known manner.

Die am brennraumfernen Ende des Druckraums 12 angeordnete Druckschulter 55 weist die gleiche Druckangriffsfläche auf, wie die an dem Ventilgliedkopf 52 ausgebildete brennraumnahe Druckschulter 54, so daß das Ventilglied 50 druckausgeglichen ist. Auf diese Weise wird verhindert, daß das Kraftstoffeinspritzventil aufgrund des anliegenden Common-Rail-Drucks selbsttätig öffnet.The one located at the end of the pressure chamber 12 remote from the combustion chamber Pressure shoulder 55 has the same pressure application area on how that formed on the valve member head 52 pressure shoulder 54 near the combustion chamber, so that the valve member 50 is pressure balanced. This prevents that the fuel injector due to the applied Common rail pressure opens automatically.

Wie aus Fig. 1 und insbesondere aus Fig. 2 hervorgeht, weist das Kraftstoffeinspritzventil eine weitere zusätzliche vom Kraftstoffhochdruck beaufschlagte Angriffsfläche auf, über die der am Einspritzventil anstehende Kraftstoffhochdruck in Schließrichtung auf das Ventilglied 50 wirkt. Diese zusätzliche Druckangriffsfläche wird durch eine untere brennraumseitige Stirnfläche 71 einer Druckhülse 70 gebildet, welche einen Ausgleichsraum 80, der die brennraumferne Druckschulter 55 ringförmig umgibt und fluidisch mit dem Druckraum 12 verbunden ist, auf seiner dem Brennraum abgewandten Seite abschließt. Der Ausgleichsraum 80 bildet auf diese Weise den brennraumfernen Abschluß des Druckraums 12. Die Hülse 70 ist axial verschieblich in einem ringförmigen Körper 90 geführt. Sie ist zur Vermeidung von Leckagen auf den oberen Schaftteil 56 des Ventilglieds 50 aufgepreßt. Da die durch die Stirnfläche 71 gebildete Druckangriffsfläche geringfügig größer ist als die Druckangriffsfläche der Schultern 54 bzw. 55, wird eine Rückstellung des Kraftstoffeinspritzventils in Schließstellung auch dann gewährleistet, wenn beispielsweise aufgrund der hohen Beanspruchung des Kraftstoffeinspritzventils im Bereich des Ventilgliedkopfs 52 eine geringfügige Undichtigkeit entstanden ist, die zu einer unerwünschten Öffnung des Kraftstoffeinspritzventils führt.As can be seen from FIG. 1 and in particular from FIG. 2, the fuel injector has another additional one Attack surface acted upon by high-pressure fuel through which the pending at the injector High fuel pressure in the closing direction on the valve member 50 works. This additional pressure application area is by a lower end face 71 on the combustion chamber side a pressure sleeve 70 is formed, which a compensation space 80, the pressure shoulder 55 distant from the combustion chamber in the shape of a ring surrounds and fluidly connected to the pressure chamber 12 is on its side facing away from the combustion chamber. The compensation space 80 forms in this way the combustion chamber distant end of the pressure chamber 12. The sleeve 70 is axially displaceable in an annular body 90 led. It is open to avoid leakage the upper shaft part 56 of the valve member 50 is pressed on. Since the pressure application surface formed by the end face 71 is slightly larger than the pressure application area the shoulders 54 and 55, respectively, is a provision of the Fuel injector in the closed position even then guaranteed if, for example, due to the high Stress on the fuel injector in the area the valve member head 52 has a slight leak has arisen, which leads to an undesirable opening of the Fuel injector leads.

Wie ferner aus Fig. 1 hervorgeht, schließt sich an den Ventilgliedschaft 56 ein weiterer Schaftteil 57 an, der in einen in dem Ventilhaltekörper 20 vorgesehenen Federraum 22 ragt. Zum Öffnen des Kraftstoffeinspritzventils wird entgegen der Rückstellkraft einer Ventilfeder 24 durch Ansteuerung eines elektromechanischen Stellglieds, beispielsweise eines Piezoaktors oder eines Elektromagneten, eine Axialverschiebung des Ventilglieds 50 und damit eine Öffnung der in dem Ventilgliedkopf 52 vorgesehenen (nicht dargestellten) Einspritzöffnung hervorgerufen.As can also be seen from Fig. 1, follows the Valve member 56 another stem portion 57, the into a spring chamber provided in the valve holding body 20 22 protrudes. To open the fuel injector becomes against the restoring force of a valve spring 24 by controlling an electromechanical actuator, for example a piezo actuator or an electromagnet, an axial displacement of the valve member 50 and thus an opening of those provided in the valve member head 52 Injection opening (not shown).

Der Bereich zwischen den beiden Druckschultern 54 bzw. 55 des Ventilglieds 50 ist nadelförmig mit konstantem Durchmesser ausgebildet. Die hierdurch ermöglichte Elastizität des Ventilglieds 50 insbesondere senkrecht zur Ventilgliedachse ermöglicht auf vorteilhafte Weise den Ausgleich eines Versatzes zwischen den Führungen des Ventilglieds 50, die durch die Druckhülse 70 und den Ventilgliedkopf 52 gebildet werden, im Mittelbereich des nadelförmigen Bereichs.The area between the two pressure shoulders 54 or 55 of the valve member 50 is needle-shaped with a constant Diameter formed. The elasticity that this enables of the valve member 50 in particular perpendicular to Valve member axis advantageously enables Compensate for an offset between the guides of the Valve member 50 through the pressure sleeve 70 and the Valve member head 52 are formed in the central region of the needle-shaped area.

Durch die direkte Verbindung des Ausgleichsraums über den Zulauf 12a mit dem Druckraum 12 werden Druckunterschiede, zum Beispiel beim Öffnen des Kraftstoffeinspritzventils zwischen dem Druckraum 12 und dem Ausgleichsraum 80 direkt ausgeglichen.Through the direct connection of the compensation room via the inlet 12a with the pressure chamber 12 are pressure differences, for example when opening the fuel injector between the pressure chamber 12 and the compensation chamber 80 directly balanced.

Claims (6)

  1. Fuel injection valve for internal combustion engines, with a valve member (50) which is displaced axially in a bore (40) of a valve body (10) and which, at its end located on the combustion-space side, has a valve-member head (52) which forms a valve-closing member and which, on its side facing the valve body (10) has a sealing surface (53), by which it cooperates with a valve-seat surface (11) provided on that end face of the valve body (10) which is located on the combustion-space side, and with injection orifices in the valve-member head (52), which emerge from a pressure space (12) formed between the valve member (50) and the wall of the bore (40), so as to lead away on the circumferential wall of the valve-member head (52), injection orifices being closed by the wall of the bore (40) when the valve member (50) comes to bear on the valve seat (11) and being opened as a result of an outwardly directed opening-stroke movement of the valve member (50), the valve member being actuable by an externally controllable actuator independently of the fuel high pressure in the pressure space (12), and there being provided on the needle-shaped valve member (50) two mutually facing pressure shoulders (54, 55) which axially delimit the pressure space and which have essentially in each case identical pressure application surfaces, characterized in that one of the pressure shoulders (55) is arranged, at that end of the valve body (10) which is remote from the combustion space, in a compensating space (80) which is fluidically connected to the pressure space (12) and which is closed off on the end face by means of an axially displaceably guided pressure sleeve (70).
  2. Fuel injection valve according to Claim 1, characterized in that, between the two pressure shoulders (54, 55), the valve member (50) is of needle-shaped design and has a constant diameter.
  3. Fuel injection valve according to Claim 1 or 2, characterized in that the pressure sleeve (70) is pressed onto the valve member (50).
  4. Fuel injection valve according to one of Claims 1 to 3, characterized in that the compensating space (80) annularly surrounds the pressure shoulder (55) remote from the combustion space.
  5. Fuel injection valve according to one of Claims 1 to 4, characterized in that the pressure space (12) is connectable to a high-pressure accumulator space which, in turn, is capable of being filled via a fuel higher pressure pump.
  6. Fuel injection valve according to one of Claims 1 to 5, characterized in that the actuator is designed as an electromechanical actuator, preferably as a piezoelectric actuator or electromagnet.
EP99938137A 1998-08-20 1999-06-08 Fuel injection valve for internal combustion engines Expired - Lifetime EP1045977B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19837813 1998-08-20
DE19837813A DE19837813A1 (en) 1998-08-20 1998-08-20 Fuel injection valve for internal combustion engine has pressure shoulder on valve body in compensation chamber fluidically connected to pressure chamber and closed by pressure sleeve
PCT/DE1999/001660 WO2000011341A1 (en) 1998-08-20 1999-06-08 Fuel injection valve for internal combustion engines

Publications (2)

Publication Number Publication Date
EP1045977A1 EP1045977A1 (en) 2000-10-25
EP1045977B1 true EP1045977B1 (en) 2003-09-03

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ID=7878158

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99938137A Expired - Lifetime EP1045977B1 (en) 1998-08-20 1999-06-08 Fuel injection valve for internal combustion engines

Country Status (5)

Country Link
US (1) US6247453B1 (en)
EP (1) EP1045977B1 (en)
JP (1) JP2002523672A (en)
DE (2) DE19837813A1 (en)
WO (1) WO2000011341A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19953562A1 (en) * 1999-11-08 2001-05-23 Bosch Gmbh Robert Fuel injector
US6343587B1 (en) * 2000-06-28 2002-02-05 Siemens Automotive Corporation Fuel injector armature permitting fluid and vapor flow
DE10204655A1 (en) * 2002-02-05 2003-08-28 Bosch Gmbh Robert Fuel injector
EP1561942B1 (en) * 2004-01-29 2006-12-27 Siemens VDO Automotive S.p.A. Fluid injector and its method of manufacture

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3734737A1 (en) * 1986-10-14 1988-04-21 Orbital Eng Pty FUEL INJECTION SYSTEM AND COMBUSTION ENGINE EQUIPPED WITH THIS
GB2219627B (en) * 1988-06-10 1992-10-28 Orbital Eng Pty Improvements relating to nozzles for in-cylinder fuel injection systems
US5024385A (en) * 1990-01-11 1991-06-18 Outboard Marine Corporation Internal combustion engine fuel supply system
DE4325904C2 (en) * 1993-08-02 1995-07-20 Daimler Benz Ag Fuel injection system provided for a diesel internal combustion engine with a high-pressure pump delivering the fuel into a common supply line (common rail) for all injection nozzles
DE19504849A1 (en) * 1995-02-15 1996-08-22 Bosch Gmbh Robert Fuel injection device for internal combustion engines
US5752656A (en) * 1996-07-10 1998-05-19 Outboard Marine Corporation Nozzle assembly and method of fabrication thereof
DE19642440A1 (en) * 1996-10-15 1998-04-16 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE19701288C2 (en) * 1997-01-16 1999-10-14 Daimler Benz Ag Valve for dispensing fluids

Also Published As

Publication number Publication date
EP1045977A1 (en) 2000-10-25
DE19837813A1 (en) 2000-02-24
US6247453B1 (en) 2001-06-19
WO2000011341A1 (en) 2000-03-02
JP2002523672A (en) 2002-07-30
DE59906859D1 (en) 2003-10-09

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