EP1339972A1 - Fuel injection valve - Google Patents

Fuel injection valve

Info

Publication number
EP1339972A1
EP1339972A1 EP01995537A EP01995537A EP1339972A1 EP 1339972 A1 EP1339972 A1 EP 1339972A1 EP 01995537 A EP01995537 A EP 01995537A EP 01995537 A EP01995537 A EP 01995537A EP 1339972 A1 EP1339972 A1 EP 1339972A1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel injection
valve seat
seat body
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.)
Granted
Application number
EP01995537A
Other languages
German (de)
French (fr)
Other versions
EP1339972B1 (en
Inventor
Thomas Sebastian
Jens Pohlmann
Martin Maier
Guenter Dantes
Detlef Nowak
Joerg Heyse
Joerg Schlerfer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1339972A1 publication Critical patent/EP1339972A1/en
Application granted granted Critical
Publication of EP1339972B1 publication Critical patent/EP1339972B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M61/1853—Orifice plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0671—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto
    • 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

Definitions

  • the invention relates to a fuel injector according to the type of the main claim.
  • Fuel injectors with multiple spray orifices are known. Downstream of a sealing seat, formed from a valve needle and a valve seat surface, they have a plurality of spray openings, usually designed as bores, through which fuel is sprayed off when the valve needle is lifted off.
  • fuel injectors which have an orifice plate at the downstream end. Injection orifices are arranged in this orifice plate, which are distributed over several circles of holes. To form a specific spray geometry, the spray openings are made in the spray hole disk at different angles with respect to the central axis of the fuel injection valve. In the case of a flat spray perforated disk, it can thus be prevented that individual jets, which are sprayed, for example, from spray openings of the inner or outer hole circle, interfere with one another in their spreading. In order to achieve sufficient beam deflection, the thickness of the spray orifice plate is so large that the flow length along the spray opening is large compared to the diameter of the spray opening.
  • a fuel injection valve is known from DE 198 04 463 AI, in which a plurality of spray openings are made in the valve seat body. In the area of the spray openings, the fuel injector is shaped conically outwards. The spray openings are made directly in the valve seat body and downstream of the sealing seat e.g. arranged on several bolt circles.
  • a disadvantage of the fuel injectors specified are the thick-walled components into which the spray openings are to be made. These are necessary to withstand the high fuel pressure or combustion chamber pressure.
  • the radial extent of the spray openings cannot be chosen to be as small as desired, because the machining processes that can be used set limits due to the possible aspect ratio.
  • the only remedy is to reduce the number of spray openings, which increases the radial extent of the individual spray openings while maintaining the overall spray cross-section. However, this leads to undesirable concentration gradients of the fuel mixture in the combustion chamber.
  • the fuel injector according to the invention with the features of the main claim has the advantage that the flow orifice from a thin disc z. B. a thin membrane or a thin sheet can be produced. This makes it possible to introduce the smallest spray openings, even using cost-effective methods. If the spray openings are punched, for example, into the flow orifice, radial expansions in the region of the thickness of the flow orifice can be easily implemented.
  • the arrangement of the thin flow orifice downstream of the valve seat body also has the advantage that the flow orifice has no mechanically supporting functions.
  • the housing end at the downstream end of the fuel injector is formed by the valve seat body. A large number of small spray openings can therefore be introduced into the flow orifice for metering the fuel. This significantly improves the treatment of the sprayed fuel, the sprayed fuel forms a largely homogeneous mixture cloud.
  • the tolerances of the injection orifices to be introduced can be achieved using well reproducible methods, e.g. Punching, be kept low.
  • the resulting scatter of specimens is small and facilitates the design of the fuel injector.
  • the consumption of the internal combustion engine can be reduced.
  • valve seat body only a small number of recesses can be arranged in the valve seat body, which greatly simplifies machining.
  • the fuel is metered through a large number of small spray orifices in the flow orifice. The good preparation of the fuel spray can thus be maintained, although only a small number of recesses need to be made in the thick-walled valve seat body, which recesses can also be roughly tolerated.
  • valve seat body and flow orifice can have a spherical shape. On the one hand, this contributes to a lower tendency to coke, on the other hand, the spray openings can be introduced vertically into the thin flow orifice, which is only then brought into its final shape. This ensures that the fuel emerges vertically from the spray openings. Wetting of the flow orifice can thus be prevented, which further reduces the risk of coking.
  • the design of the flow orifice as a membrane is also advantageous.
  • the atomization process can be supported by vibrations that can be easily excited in a thin membrane. Improved atomization also reduces the time required to evaporate the fuel. In the case of direct-injection internal combustion engines in particular, this enables fuel-optimized injection since a later injection timing can be selected.
  • Figure 1 is a schematic overall section through an embodiment of a fuel injector according to the invention.
  • Fig. 2 is a schematic partial section in section II of Fig. 1 through the embodiment of the fuel injector according to the invention.
  • the fuel injector 1 is in the form of a fuel injector 1 for fuel injection systems of mixture-compressing, spark-ignited
  • Fuel injection valve 1 is particularly suitable for injecting fuel directly into a combustion chamber (not shown) of an internal combustion engine.
  • the fuel injection valve 1 comprises a nozzle body 2, in which a valve needle 3 is arranged.
  • the valve needle ' l 3 is operatively connected to a valve closing body 4, which cooperates with a valve seat surface 6 arranged on a valve seat body 5 to form a sealing seat.
  • the fuel injection valve 1 is an electromagnetically actuated fuel injection valve 1 which has a plurality of spray openings 7.
  • the nozzle body 2 is sealed by a seal 8 against an outer pole 9 of a solenoid 10.
  • the magnet coil 10 is encapsulated in a coil housing 11 and wound on a coil carrier 12, which bears against an inner pole 13 of the magnet coil 10.
  • the inner pole 13 and the outer pole 9 are separated from one another by a gap 26 and are supported on a connecting component 29.
  • the magnet coil 10 is excited via a line 19 by an electrical current that can be supplied via an electrical plug contact 17.
  • the plug contact 17 is surrounded by a plastic sheath 18, which can be molded onto the inner pole 13.
  • the valve needle 3 is guided in a disk-shaped valve needle guide 14. This is paired with a shim 15, which is used to adjust the valve needle stroke.
  • An armature 20 is located on the upstream side of the adjusting disk 15. This armature is non-positively connected to the valve needle 3 via a flange 21, which is connected to the flange 21 by a weld seam 22.
  • a restoring spring 23 is supported on the flange 21 and, in the present design of the fuel injector 1, is preloaded by a sleeve 24 pressed into the inner pole 13.
  • Fuel channels 30a, 30b run in the valve needle guide 14 and in the armature 20.
  • a filter element 25 is arranged in a central fuel supply 16.
  • the Fuel injector 1 is sealed by a seal 28 against a fuel line, not shown.
  • the armature 20 In the idle state of the fuel injection valve 1, the armature 20 is acted upon by the return spring 23 against the stroke direction via the flange 21 on the valve needle 3 in such a way that the valve closing body 4 is held in sealing contact with the valve seat surface 6.
  • the magnet coil 10 When the magnet coil 10 is excited, it builds up a magnetic field which moves the armature 20 against the spring force of the return spring 23 in the stroke direction, the stroke being predetermined by a working gap 27 which is in the rest position between the inner pole 13 and the armature 20.
  • the armature 20 takes the flange 21, which is welded to the valve needle 2, and thus also the valve needle 3 in the lifting direction.
  • the valve closing body 4 which is operatively connected to the valve needle 3 lifts from the
  • Valve seat surface 6 the fuel flows past the valve closing body 4, further through recesses 34, which are arranged in the valve seat body 5, to the spray openings 7 and is sprayed off.
  • Fig. 2 shows in section II of Fig. 1 a detailed partial section of an inventive
  • Fuel injector 1 Downstream of the valve seat body 5, a partially dome-shaped flow orifice 31 corresponding to the downstream geometry of the valve seat body 5 is fastened, for example by a welded connection 36.
  • a plurality of spray openings 7 are introduced, which are located downstream of the recesses 34 in the Connect valve seat body 5.
  • the spray openings 7 arranged in the flow orifice 31 represent the narrowest cross section to be flowed through, so that the total cross section of the spray openings 7 determines the amount of the metered fuel.
  • the valve seat body 5 has a central recess 32, the radial extent of which corresponds to the radial extent of the, for example, spherical valve closing body 4.
  • the central recess 32 tapers towards the downstream end and forms the valve seat surface 6.
  • a plurality of recesses 34 are made in the valve seat body 5 downstream. These can e.g. be introduced into the valve seat body 5 by drilling and connect the spray orifices 7 to the volume 33 between the valve closing body 4 and the valve seat body 5 which is pressurized with fuel when the fuel injection valve 1 is open.
  • the volume 33 is kept small by designing the valve seat body 5 with an internal geometry corresponding to the valve closing body 4.
  • the inside of the valve seat body 5 can, for example, have a spherical shape, the radius of which is slightly smaller than that of the valve closing body 4.
  • the central recess 32 of the valve seat body 5 guides the valve closing body 4 during the stroke.
  • flats 35 are attached to the valve closing body 4.
  • the flow path formed between the flats 35 and the valve seat body 5 has a larger cross section than all the spray openings 7 in FIG Flow orifice 31 together, so that even when the fuel injector 1 is fully open, the only orifice restricting the flow rate is the flow orifice 31 with the injection orifices 7 introduced therein.
  • the spray orifices 7 introduced in the flow orifice 31 are arranged on the flow orifice 31 such that the upstream end of each spray orifice 7 opens out from a recess 34 in the valve seat body 5.
  • the spray openings 7 can, for example, also be arranged in groups on the flow diaphragm 31, so that in each case one group of spray openings 7 opens out of a respective recess 34 in the valve seat body 5.
  • the spray openings 7 are preferably introduced into the flow orifice 31 before it is formed. This is done e.g. by exact punching, the punching direction being perpendicular to the surface of the still flat flow diaphragm 31. After the injection orifices 7 have been introduced, the flow orifice 31 is brought into its final shape. It is for this purpose according to the geometry of the valve seat body 5 z. B. deep-drawn so that e.g. Radially around the spherical area, a flat annular flange 37 remains, which is suitable for welding the flow diaphragm 31 to the valve seat body 5.
  • the thickness of the disc from which the flow orifice 31 is made is, for example, dimensioned such that the flow orifice 31 is excited to oscillate by the fuel flowing through the spray openings 7 when the fuel injection valve 1 is open. This creates pressure conditions in the individual emerging fuel jets, which promote finer atomization.

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

Abstract

The invention relates to a fuel injection valve for fuel injection systems of internal combustion engines, comprising a valve needle (3) and a valve closing body (4) functionally linked therewith that interacts with a valve face (6) disposed in a valve seat body (5) to give a sealing seat. A plurality of recesses (34) are provided downstream of the sealing seat in the valve seat body (5). An orifice plate (31) is disposed downstream of the valve seat body (5) and is provided with at least one spray orifice (7) per recess (34). The cross-section of said spray orifice is smaller than that of the recess (34) and disposed in such a manner that its inlet cross-section lies completely within the outlet cross-section of the respective recess (34).

Description

Brennstoffeinspritzventil Fuel injector
Stand der TechnikState of the art
Die Erfindung geht aus von einem Brennstoffeinspritzventil nach Gattung des Hauptanspruchs .The invention relates to a fuel injector according to the type of the main claim.
Brennstoffeinspritzventile mit mehreren Abspritzöffnungen sind bekannt. Sie besitzen stromabwärts eines Dichtsitzes, gebildet aus einer Ventilnadel und einer Ventilsitzfläche, mehrere meist als Bohrungen ausgeführte Abspritzöffnungen, durch die bei abgehobener Ventilnadel Brennstoff abgespritzt wird.Fuel injectors with multiple spray orifices are known. Downstream of a sealing seat, formed from a valve needle and a valve seat surface, they have a plurality of spray openings, usually designed as bores, through which fuel is sprayed off when the valve needle is lifted off.
Aus der DE 198 27 219 AI sind beispielsweise Brennstoffeinspritzventile bekannt, die am stromabwärtigen Ende eine Spritzlochscheibe aufweisen. In dieser Spritzlochscheibe sind Abspritzöffnungen angeordnet, die auf mehrere Lochkreise verteilt sind. Zur Ausbildung einer bestimmten Abspritzgeometrie sind die Abspritzöffnungen mit unterschiedlichen Winkeln gegenüber der Mittelachse des Brennstoffeinspritzventils in die Spritzlochscheibe eingebracht. So kann bei einer ebenen Spritzlochscheibe verhindert werden, daß sich Einzelstrahlen, die z.B. von Abspritzöffnungen des inneren bzw. äußeren Lochkreises abgespritzt werden, in ihrer Ausbreitung gegenseitig stören. Um eine ausreichende Strahlumlenkung zu erzielen, ist die Dicke der Spritzlochscheibe so groß, daß die Strömungslänge entlang der Abspritzöffnung groß gegenüber dem Durchmesser der Abspritzöffnung ist.From DE 198 27 219 AI, for example, fuel injectors are known which have an orifice plate at the downstream end. Injection orifices are arranged in this orifice plate, which are distributed over several circles of holes. To form a specific spray geometry, the spray openings are made in the spray hole disk at different angles with respect to the central axis of the fuel injection valve. In the case of a flat spray perforated disk, it can thus be prevented that individual jets, which are sprayed, for example, from spray openings of the inner or outer hole circle, interfere with one another in their spreading. In order to achieve sufficient beam deflection, the thickness of the spray orifice plate is so large that the flow length along the spray opening is large compared to the diameter of the spray opening.
Ferner ist aus der DE 198 04 463 AI ein Brennstoffeinspritzventil bekannt, -bei dem mehrere Abspritzöffnungen in den Ventilsitzkörper eingebracht sind. Im Bereich der Abspritzδffnungen ist das Brennstoffeinspritzventil kegelförmig nach außen geformt. Die Abspritzöffnungen sind direkt in den Ventilsitzkörper eingebracht und stromabwärts des Dichtsitzes z.B. auf mehreren Lochkreisen angeordnet.Furthermore, a fuel injection valve is known from DE 198 04 463 AI, in which a plurality of spray openings are made in the valve seat body. In the area of the spray openings, the fuel injector is shaped conically outwards. The spray openings are made directly in the valve seat body and downstream of the sealing seat e.g. arranged on several bolt circles.
Nachteilig bei den angegebenen Brennstoffeinspritzventilen sind die dickwandigen Bauteile, in die die Abspritzöffnungen einzubringen sind. Diese sind erforderlich, um dem hohen Brennstoffdruck bzw. Brennraumdruck standhalten zu können.A disadvantage of the fuel injectors specified are the thick-walled components into which the spray openings are to be made. These are necessary to withstand the high fuel pressure or combustion chamber pressure.
Die radiale Ausdehnung der Abspritzöffnungen kann aufgrund der dickwandigen Ausführung nicht beliebig klein gewählt werden, weil durch die einsetzbaren Bearbeitungsverfahren durch das mögliche Aspektverhältnis Grenzen gesetzt werden. Abhilfe kann lediglich durch eine Verringerung der Anzahl der Abspritzöffnungen geschaffen werden, wodurch bei gleichzeitiger Beibehaltung des Gesamtabspritzquerschnitts die radiale Ausdehnung der einzelnen Abspritzöffnungen vergrößert wird. Dies führt jedoch zu unerwünschten Konzentrationsgradienten des Brennstoffgemischs im Brennraum.Due to the thick-walled design, the radial extent of the spray openings cannot be chosen to be as small as desired, because the machining processes that can be used set limits due to the possible aspect ratio. The only remedy is to reduce the number of spray openings, which increases the radial extent of the individual spray openings while maintaining the overall spray cross-section. However, this leads to undesirable concentration gradients of the fuel mixture in the combustion chamber.
Konventionelle Bearbeitungsverfahren, wie z.B. spanendes Bohren, sind zwar bis in große Werkstücktiefen möglich, erhöhen aber die Maßtoleranzen. Als Folge ergibt sich eine größere Toleranz bei der Durchflußmenge. Dadurch wird eine optimierte Auslegung der Durchflußmenge erschwert, was letztlich in höherem Verbrauch der Brennkraftmaschine und in verschlechterten Abgaswerten resultiert. Weist das Brennstoffeinspritzventil eine nicht ebene Geometrie im Bereich der Abspritzöffnungen auf, so ist das Einbringen der Abspritzöffnungen zusätzlich erschwer/t.Conventional machining processes, such as cutting drilling, are possible down to large workpiece depths, but increase the dimensional tolerances. As a result, there is a greater tolerance in the flow rate. This makes an optimized design of the flow rate difficult, which ultimately results in higher consumption of the internal combustion engine and in deteriorated exhaust gas values. If the fuel injector has a non-planar geometry in the area of the spray openings, the introduction of the spray openings is additionally difficult.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß die Durchflußblende aus einer dünnen Scheibe z. B. einer dünnen Membran oder einem dünnen Blech herstellbar ist. Dadurch ist, auch unter Verwendung kostengünstiger Verfahren, das Einbringen kleinster Abspritzöffnungen möglich. Werden die Abspritzöffnungen beispielsweise in die Durchflußblende gestanzt, so sind radiale Ausdehnungen im Bereich der Dicke der Durchflußblende ohne weiteres realisierbar.The fuel injector according to the invention with the features of the main claim has the advantage that the flow orifice from a thin disc z. B. a thin membrane or a thin sheet can be produced. This makes it possible to introduce the smallest spray openings, even using cost-effective methods. If the spray openings are punched, for example, into the flow orifice, radial expansions in the region of the thickness of the flow orifice can be easily implemented.
Die Anordnung der dünnen Durchflußblende stromabwärts des Ventilsitzkörpers hat außerdem den Vorteil, daß der Durchflußblende keine mechanisch tragenden Funktionen zukommen. Der Gehäuseabschluß am stromabwärtigen Ende des Brennstoffeinspritzventils wird von dem Ventilsitzkörper gebildet. Zur Zumessung des Brennstoffs können deswegen eine Vielzahl kleine Abspritzöffnungen in die Durchflußblende eingebracht werden. Dadurch wird die Aufbereitung des abgespritzten Brennstoffs deutlich verbessert, der abgespritzte Brennstoff bildet eine weitgehend homogene Gemischwolke aus .The arrangement of the thin flow orifice downstream of the valve seat body also has the advantage that the flow orifice has no mechanically supporting functions. The housing end at the downstream end of the fuel injector is formed by the valve seat body. A large number of small spray openings can therefore be introduced into the flow orifice for metering the fuel. This significantly improves the treatment of the sprayed fuel, the sprayed fuel forms a largely homogeneous mixture cloud.
Die Toleranzen der einzubringenden Abspritzöffnungen können bei Verwendung von gut reproduzierbaren Verfahren, wie z.B. Stanzen, gering gehalten werden. Die sich somit ergebende Exemplarstreuung ist klein und erleichtert die Auslegung des Brennstoffeinspritzventils . Letztlich kann so der Verbrauch der Brennkraftmaschine verringert werden.The tolerances of the injection orifices to be introduced can be achieved using well reproducible methods, e.g. Punching, be kept low. The resulting scatter of specimens is small and facilitates the design of the fuel injector. Ultimately, the consumption of the internal combustion engine can be reduced.
Vorteilhafte Weiterbildungen des erfindungsgemäßen Brennstoffeinspritzventils mit den kennzeichnenden Merkmalen des Hauptanspruchs sind durch die in den kennzeichnenden Merkmalen der Unteransprüche aufgeführten Maßnahmen möglich.Advantageous developments of the fuel injector according to the invention with the characterizing features of the main claim are possible through the measures listed in the characterizing features of the subclaims.
So können z.B. in dem Ventilsitzkörper nur eine geringe Anzahl von Ausnehmungen angeordnet sein, wodurch sich die Bearbeitung stark vereinfacht . Die Zumessung des Brennstoffs erfolgt jedoch durch eine Vielzahl kleiner Abspritzöffnungen in der Durchflußblende. Damit kann die gute Aufbereitung des Brennstoffsprays beibehalten werden, obwohl in den dickwandigen Ventilsitzkörper nur eine geringe Anzahl von Ausnehmungen eingebracht werden muß, die darüber hinaus grob toleriert sein kann.For example, only a small number of recesses can be arranged in the valve seat body, which greatly simplifies machining. However, the fuel is metered through a large number of small spray orifices in the flow orifice. The good preparation of the fuel spray can thus be maintained, although only a small number of recesses need to be made in the thick-walled valve seat body, which recesses can also be roughly tolerated.
Ventilsitzkörper und Durchflußblende können eine kalottenförmige Geometrie aufweisen. Einerseits trägt dies zu einer geringeren Neigung zum Verkoken bei, andererseits können die Abspritzöffnungen senkrecht in die dünne Durchflußblende eingebracht werden, die erst- im Anschluß in ihre endgültige Form gebracht wird. Dadurch wird ein senkrechter Austritt des Brennstoffs aus den Abspritzöffnungen gewährleistet. Ein Benetzen der Durchflußblende kann somit verhindert werden, wodurch die Verkokungsgefahr weiter reduziert wird.The valve seat body and flow orifice can have a spherical shape. On the one hand, this contributes to a lower tendency to coke, on the other hand, the spray openings can be introduced vertically into the thin flow orifice, which is only then brought into its final shape. This ensures that the fuel emerges vertically from the spray openings. Wetting of the flow orifice can thus be prevented, which further reduces the risk of coking.
Ferner ist die Auslegung der Durchflußblende als Membran vorteilhaft. Durch Schwingungen, die in einer dünnen Membran leicht angeregt werden können, kann der Vorgang der Zerstäubung unterstützt werden. Bei einer verbesserten Zerstäubung verringert sich die zum Verdampfen des Brennstoffs erforderliche Zeit ebenfalls. Insbesondere bei direkteinspritzenden Brennkraftmaschinen wird dadurch eine verbrauchsoptimierte Einspritzung ermöglicht, da ein späterer Einspritzzeitpunkt gewählt werden kann.The design of the flow orifice as a membrane is also advantageous. The atomization process can be supported by vibrations that can be easily excited in a thin membrane. Improved atomization also reduces the time required to evaporate the fuel. In the case of direct-injection internal combustion engines in particular, this enables fuel-optimized injection since a later injection timing can be selected.
Durch die mit dem Ventilschließkörper korrespondierende Ausgestaltung der Innenseite des Ventilsitzkörpers ist nahezu kein Totvolumen vorhanden. Dadurch kommt es nach Abschluß des Abspritzvorgangs nicht zu einem Abdampfen von nicht abgespritzten Brennstoff am heißen Brennstoffeinspritzventil, was zu Emissionsspitzen führen würde. Zu Beginn des nachfolgenden Abspritzvorgangs wird ferner die Reaktionszeit verringert, da kein Volumen mit Brennstoff befüllt werden muß, bevor zum Ausbilden eines feinen Brennstoffsprays der erforderliche Brennstoffdruck an den Abspritzöffnungen anliegt.Due to the design of the inside of the valve seat body corresponding to the valve closing body, there is almost no dead volume. As a result, after the end of the spraying process, there is no evaporation of fuel that has not been sprayed out hot Fuel injector, which would lead to emission peaks. At the beginning of the subsequent spraying process, the reaction time is also reduced since no volume has to be filled with fuel before the fuel pressure required to form a fine fuel spray is present at the spraying openings.
Zeichnungdrawing
Ein Ausführungsbeispiel des erfindungsgemäßen Brennstoffeinspritzventils ist in der Zeichnung vereinfacht dargestellt und wird in der nachfolgenden Beschreibung näher erläutert. Es zeigen:An embodiment of the fuel injector according to the invention is shown in simplified form in the drawing and is explained in more detail in the following description. Show it:
Fig. 1 einen schematischen Gesamtschnitt durch ein Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils; undFigure 1 is a schematic overall section through an embodiment of a fuel injector according to the invention. and
Fig. 2 einen schematischen Teilschnitt im Ausschnitt II der Fig. 1 durch das Ausführungsbeispiel des erfindungsgemäßen Brennstoffeinspritzventils .Fig. 2 is a schematic partial section in section II of Fig. 1 through the embodiment of the fuel injector according to the invention.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Bevor anhand der Fig. 2 ein Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils 1 näher beschrieben wird, soll zum besseren Verständnis der Erfindung zunächst anhand von Fig. 1 das erfindungsgemäße Brennstoffeinspritzventil 1 in einer Gesamtdarstellung bezüglich seiner wesentlichen Bestandteile kurz erläutert werden.Before an exemplary embodiment of a fuel injector 1 according to the invention is described in more detail with reference to FIG. 2, the fuel injector 1 according to the invention is first to be briefly explained in terms of its essential components with reference to FIG.
Das Brennstoffeinspritzventil 1 ist in der Form eines Brennstoffeinspritzventils 1 für Brennstoffeinspritzanlagen von gemischverdichtenden, fremdgezündetenThe fuel injector 1 is in the form of a fuel injector 1 for fuel injection systems of mixture-compressing, spark-ignited
Brennkraftmaschinen ausgeführt . DasRunning internal combustion engines. The
Brennstoffeinspritzventil 1 eignet sich insbesondere zum direkten Einspritzen von Brennstoff in einen nicht dargestellten Brennraum einer Brennkraftmaschine. Das Brennstoffeinspritzventil 1 umfaßt einen Düsenkörper 2, in welchem eine Ventilnadel 3 angeordnet ist. Die Ventilnade'l 3 steht mit einem Ventilschließkörper 4 in Wirkverbindung, der mit einer auf einem Ventilsitzkörper 5 angeordneten Ventilsitzfläche 6 zu einem Dichtsitz zusammenwirkt. Bei dem Brennstoffeinspritzventil 1 handelt es sich im Ausführungsbeispiel um ein elektromagnetisch betätigtes Brennstoffeinspritzventil 1, welches über mehrere Abspritzöffnungen 7 verfügt. Der Düsenkörper 2 ist durch eine Dichtung 8 gegen einen Außenpol 9 einer Magnetspule 10 abgedichtet. Die Magnetspule 10 ist in einem Spulengehäuse 11 gekapselt und auf einen Spulenträger 12 gewickelt, welcher an einem Innenpol 13 der Magnetspule 10 anliegt. Der Innenpol 13 und der Außenpol 9 sind durch einen Spalt 26 voneinander getrennt und stützen sich auf einem Verbindungsbauteil 29 ab. Die Magnetspule 10 wird über eine Leitung 19 von einem über einen elektrischen Steckkontakt 17 zuführbaren elektrischen Strom erregt. Der Steckkontakt 17 ist von einer Kunststoffummantelung 18 umgeben, die am Innenpol 13 angespritzt sein kann.Fuel injection valve 1 is particularly suitable for injecting fuel directly into a combustion chamber (not shown) of an internal combustion engine. The fuel injection valve 1 comprises a nozzle body 2, in which a valve needle 3 is arranged. The valve needle ' l 3 is operatively connected to a valve closing body 4, which cooperates with a valve seat surface 6 arranged on a valve seat body 5 to form a sealing seat. In the exemplary embodiment, the fuel injection valve 1 is an electromagnetically actuated fuel injection valve 1 which has a plurality of spray openings 7. The nozzle body 2 is sealed by a seal 8 against an outer pole 9 of a solenoid 10. The magnet coil 10 is encapsulated in a coil housing 11 and wound on a coil carrier 12, which bears against an inner pole 13 of the magnet coil 10. The inner pole 13 and the outer pole 9 are separated from one another by a gap 26 and are supported on a connecting component 29. The magnet coil 10 is excited via a line 19 by an electrical current that can be supplied via an electrical plug contact 17. The plug contact 17 is surrounded by a plastic sheath 18, which can be molded onto the inner pole 13.
Die Ventilnadel 3 ist in einer scheibenförmig ausgeführten Ventilnadelführung 14 geführt. Dieser ist eine Einstellscheibe 15 zugepaart, welche zur Einstellung des Ventilnadelhubes dient. Auf der stromaufwärtigen Seite der Einstellscheibe 15 befindet sich ein Anker 20. Dieser steht über einen Flansch 21 kraftschlüssig mit der Ventilnadel 3 in Verbindung, welche durch eine Schweißnaht 22 mit dem Flansch 21 verbunden ist. Auf dem Flansch 21 stützt sich eine Rückstellfeder 23 ab, welche in der vorliegenden Bauform des Brennstoffeinspritzventils 1 durch eine in den Innenpol 13 eingepreßte Hülse 24 auf Vorspannung gebracht wird.The valve needle 3 is guided in a disk-shaped valve needle guide 14. This is paired with a shim 15, which is used to adjust the valve needle stroke. An armature 20 is located on the upstream side of the adjusting disk 15. This armature is non-positively connected to the valve needle 3 via a flange 21, which is connected to the flange 21 by a weld seam 22. A restoring spring 23 is supported on the flange 21 and, in the present design of the fuel injector 1, is preloaded by a sleeve 24 pressed into the inner pole 13.
In der Ventilnadelführung 14 und im Anker 20 verlaufen Brennsto fkanäle 30a, 30b. In einer zentralen Brennstoffzufuhr 16 ist ein Filterelement 25 angeordnet. Das Brennstoffeinspritzventil 1 ist durch eine Dichtung 28 gegen eine nicht dargestellte Brennstoffleitung abgedichtet.Fuel channels 30a, 30b run in the valve needle guide 14 and in the armature 20. A filter element 25 is arranged in a central fuel supply 16. The Fuel injector 1 is sealed by a seal 28 against a fuel line, not shown.
Im Ruhezustand des Brennstoffeinspritzventils 1 wird der Anker 20 über den Flansch 21 an der Ventilnadel 3 von der Rückstellfeder 23 entgegen seiner Hubrichtung so beaufschlagt, daß der Ventilschließkörper 4 an der Ventilsitzfläche 6 in dichtender Anlage gehalten wird. Bei Erregung der Magnetspule 10 baut diese ein Magnetfeld auf, welches den Anker 20 entgegen der Federkraft der Rückstellfeder 23 in Hubrichtung bewegt, wobei der Hub durch einen in der Ruhestellung zwischen dem Innenpol 13 und dem Anker 20 befindlichen Arbeitsspalt 27 vorgegeben ist. Der Anker 20 nimmt den Flansch 21, welcher mit der Ventilnadel 2 verschweißt ist, und damit die Ventilnadel 3 ebenfalls in Hubrichtung mit . Der mit der Ventilnadel 3 in Wirkverbindung stehende Ventilschließkörper 4 hebt von derIn the idle state of the fuel injection valve 1, the armature 20 is acted upon by the return spring 23 against the stroke direction via the flange 21 on the valve needle 3 in such a way that the valve closing body 4 is held in sealing contact with the valve seat surface 6. When the magnet coil 10 is excited, it builds up a magnetic field which moves the armature 20 against the spring force of the return spring 23 in the stroke direction, the stroke being predetermined by a working gap 27 which is in the rest position between the inner pole 13 and the armature 20. The armature 20 takes the flange 21, which is welded to the valve needle 2, and thus also the valve needle 3 in the lifting direction. The valve closing body 4 which is operatively connected to the valve needle 3 lifts from the
Ventilsitzfläche 6 ab, der Brennstoff strömt an dem Ventilschließkörper 4 vorbei, weiter durch Ausnehmungen 34, welche in dem Ventilsitzkörper 5 angeordnet sind, zu den Abspritzöffnungen 7 und wird abgespritzt.Valve seat surface 6, the fuel flows past the valve closing body 4, further through recesses 34, which are arranged in the valve seat body 5, to the spray openings 7 and is sprayed off.
Wird der Spulenstrom abgeschaltet, fällt der Anker 20 nach genügendem Abbau des Magnetfeldes durch den Druck der Rückstellfeder 23 auf den Flansch 21 vom Innenpol 13 ab, wodurch sich die Ventilnadel 3 entgegen der Hubrichtung bewegt. Dadurch setzt der Ventilschließkörper 4 auf der Ventilsitzfläche 6 auf, und das Brennstoffeinspritzventil 1 wird geschlossen.If the coil current is switched off, the armature 20 drops from the inner pole 13 after the magnetic field has been sufficiently reduced by the pressure of the return spring 23 on the flange 21, as a result of which the valve needle 3 moves counter to the stroke direction. As a result, the valve closing body 4 rests on the valve seat surface 6 and the fuel injection valve 1 is closed.
Fig. 2 zeigt im Ausschnitt II der Fig. 1 einen detaillierten Teilschnitt eines erfindungsgemäßenFig. 2 shows in section II of Fig. 1 a detailed partial section of an inventive
Brennstoffeinspritzventils 1. Stromabwärts des Ventilsitzkörpers 5 ist eine teilweise kalottenförmige, mit der stromabwärtigen Geometrie des Ventilsitzkörpers 5 korrespondierende Durchflußblende 31 z.B. durch eine Schweißverbindung 36 befestigt. In die Durchflußblende 31 sind mehrere Abspritzδffnungen 7 eingebracht, welche sich stromabwärts an die Ausnehmungen 34 in dem Ventilsitzkörper 5 anschließen. Die in der Durchflußblende 31 angeordneten Abspritzöffnungen 7 stellen den engsten zu durchströmenden Querschnitt dar, so daß durch den Gesamtquerschnitt der Abspritzöffnungen 7 die Menge des zugemessenen Brennstoffs festgelegt wird.Fuel injector 1. Downstream of the valve seat body 5, a partially dome-shaped flow orifice 31 corresponding to the downstream geometry of the valve seat body 5 is fastened, for example by a welded connection 36. In the flow diaphragm 31 a plurality of spray openings 7 are introduced, which are located downstream of the recesses 34 in the Connect valve seat body 5. The spray openings 7 arranged in the flow orifice 31 represent the narrowest cross section to be flowed through, so that the total cross section of the spray openings 7 determines the amount of the metered fuel.
Der Ventilsitzkörper 5 weist eine zentrale Ausnehmung 32 auf, deren radiale Ausdehnung mit der radialen Ausdehnung des beispielsweise kugelförmigen Ventilschließkörpers 4 korrespondiert. Zum stromabwärtigen Ende hin verjüngt sich die zentrale Ausnehmung 32 und bildet die Ventilsitzfläche 6 aus. Stromabwärts sind in den Ventilsitzkörper 5 mehrere Ausnehmungen 34 eingebracht. Diese können z.B. durch Bohren in den Ventilsitzkörper 5 eingebracht sein und verbinden die Abspritzöffnungen 7 mit dem bei geöffnetem Brennstoffeinspritzventil 1 mit Brennstoff bedrückten Volumen 33 zwischen Ventilschließkörper 4 und Ventilsitzkörper 5.The valve seat body 5 has a central recess 32, the radial extent of which corresponds to the radial extent of the, for example, spherical valve closing body 4. The central recess 32 tapers towards the downstream end and forms the valve seat surface 6. A plurality of recesses 34 are made in the valve seat body 5 downstream. These can e.g. be introduced into the valve seat body 5 by drilling and connect the spray orifices 7 to the volume 33 between the valve closing body 4 and the valve seat body 5 which is pressurized with fuel when the fuel injection valve 1 is open.
Das Volumen 33 wird durch Ausgestaltung des Ventilsitzkörpers 5 mit einer mit dem Ventilschließkörper 4 korrespondierenden Innengeometrie klein gehalten. Die Innenseite des Ventilsitzkörpers 5 kann beispielsweise eine Kugelform aufweisen, deren Radius geringfügig kleiner als der des Ventilschließkörpers 4 ist. Dadurch ist bei geschlossenem Brennstoffeinspritzventil 1 ein definierter Sitz des Ventilschließkörpers 4 auf der Ventilsitzfläche 6 sichergestellt, andererseits ein minimales Volumen 33 gewährleistet. Durch das kleine Volumen 33 wird das Abspritzbild zu Beginn und zu Ende des Abspritzvorgangs verbessert .The volume 33 is kept small by designing the valve seat body 5 with an internal geometry corresponding to the valve closing body 4. The inside of the valve seat body 5 can, for example, have a spherical shape, the radius of which is slightly smaller than that of the valve closing body 4. As a result, when the fuel injection valve 1 is closed, a defined fit of the valve closing body 4 on the valve seat surface 6 is ensured, and on the other hand a minimal volume 33 is ensured. The small volume 33 improves the spray pattern at the beginning and at the end of the spraying process.
Die zentrale Ausnehmung 32 des Ventilsitzkörpers 5 führt den Ventilschließkörper 4 während des Hubs. Zum Ausbilden eines Strömungswegs hin zu den Ausnehmungen 34 sind Abflachungen 35 an dem Ventilschließkörper 4 angebracht. Der zwischen den Abflachungen 35 und dem Ventilsitzkörper 5 gebildete Strömungsweg weist dabei einen größeren Querschnitt auf als alle Abspritzöffnungen 7 in der Durchflußblende 31 gemeinsam, so daß auch bei vollständig geöffnetem Brennstoffeinspritzventil 1 als einzige die Durchflußmenge begrenzende Drosselstelle die Durchflußblende 31 mit den darin eingebrachten Abspritzöffnungen 7 wirkt.The central recess 32 of the valve seat body 5 guides the valve closing body 4 during the stroke. To form a flow path to the recesses 34, flats 35 are attached to the valve closing body 4. The flow path formed between the flats 35 and the valve seat body 5 has a larger cross section than all the spray openings 7 in FIG Flow orifice 31 together, so that even when the fuel injector 1 is fully open, the only orifice restricting the flow rate is the flow orifice 31 with the injection orifices 7 introduced therein.
Die in der Durchflußblende 31 eingebrachten Abspritzδffnungen 7 sind so auf der Durchflußblende 31 angeordnet, daß das stromaufwärtige Ende jeder Abspritzöffnung 7 aus einer Ausnehmung 34 des Ventilsitzkörpers 5 ausmündet. Dabei können die Abspritzöffnungen 7 beispielsweise auch in Gruppen auf der Durchflußblende 31 angeordnet sein, so daß jeweils eine Gruppe von Abspritzöffnungen 7 aus jeweils einer Ausnehmung 34 des Ventilsitzkörpers 5 ausmündet.The spray orifices 7 introduced in the flow orifice 31 are arranged on the flow orifice 31 such that the upstream end of each spray orifice 7 opens out from a recess 34 in the valve seat body 5. The spray openings 7 can, for example, also be arranged in groups on the flow diaphragm 31, so that in each case one group of spray openings 7 opens out of a respective recess 34 in the valve seat body 5.
Die Abspritzöffnungen 7 werden vorzugsweise vor dem Umformen der Durchflußblende 31 in diese eingebracht. Dies erfolgt z.B. durch exaktes Stanzen, wobei die Stanzrichtung senkrecht zur Oberfläche der noch ebenen Durchflußblende 31 ist. Nach dem Einbringen der Abspritzöffnungen 7 wird die Durchflußblende 31 in ihre endgültige Form gebracht. Sie wird dazu entsprechend der Geometrie des Ventilsitzkörpers 5 z. B. tiefgezogen, so daß z.B. radial um den kalottenförmigen Bereich herum ein ebener ringförmiger Flansch 37 bleibt, der zum Verschweißen der Durchflußblende 31 an dem Ventilsitzkörper 5 geeignet ist.The spray openings 7 are preferably introduced into the flow orifice 31 before it is formed. This is done e.g. by exact punching, the punching direction being perpendicular to the surface of the still flat flow diaphragm 31. After the injection orifices 7 have been introduced, the flow orifice 31 is brought into its final shape. It is for this purpose according to the geometry of the valve seat body 5 z. B. deep-drawn so that e.g. Radially around the spherical area, a flat annular flange 37 remains, which is suitable for welding the flow diaphragm 31 to the valve seat body 5.
Die Dicke der Scheibe, aus der die Durchflußblende 31 gefertigt wird, ist beispielsweise so bemessen, daß durch den bei geöffnetem Brennstoffeinspritzventil 1 durch die Abspritzöffnungen 7 strömenden Brennstoff die Durchflußblende 31 zum Schwingen angeregt wird. Dadurch entstehen in den einzelnen austretenden Brennstoffstrahlen Druckverhältnisse, die eine feinere Zerstäubung begünstigen. The thickness of the disc from which the flow orifice 31 is made is, for example, dimensioned such that the flow orifice 31 is excited to oscillate by the fuel flowing through the spray openings 7 when the fuel injection valve 1 is open. This creates pressure conditions in the individual emerging fuel jets, which promote finer atomization.

Claims

Ansprüche Expectations
1. Brennstoffeinspritzventil für Brennstoffeinspritzanlagen von Brennkraftmaschinen mit einer Ventilnadel (3) und einem damit in Wirkverbindung stehenden Ventilschließkörper (4) , der mit einer in einem Ventilsitzkörper (5) angeordneten Ventilsitzfläche (6) zu einem Dichtsitz zusammenwirkt, und mehreren Ausnehmungen (34) , welche stromabwärts des Dichtsitzes, in den Ventilsitzkörper (5) eingebracht sind, dadurch gekennzeichnet, daß stromabwärts an dem Ventilsitzkörper (5) eine Durchflußblende (31) angeordnet ist, in welche für jeweils eine Ausnehmung (34) zumindest eine Abspritzöffnung (7) eingebracht ist, deren Querschnitt kleiner ist als der der jeweiligen Ausnehmung (34) und die so angeordnet ist, daß ihr Eintrittsquerschnitt vollständig innerhalb eines Austrittsquerschnitts der jeweiligen Ausnehmung (34) liegt.1. Fuel injection valve for fuel injection systems of internal combustion engines with a valve needle (3) and a valve closing body (4) that is operatively connected to it, which cooperates with a valve seat surface (6) arranged in a valve seat body (5) to form a sealing seat, and a plurality of recesses (34), which are introduced into the valve seat body (5) downstream of the sealing seat, characterized in that a flow orifice (31) is arranged downstream of the valve seat body (5), into which at least one spray opening (7) is made for each recess (34) , whose cross-section is smaller than that of the respective recess (34) and which is arranged such that its inlet cross-section lies completely within an outlet cross-section of the respective recess (34).
2. Brennstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß für jeweils eine Ausnehmung (34) des2. Fuel injection valve according to claim 1, characterized in that for one recess (34) of the
Ventilsitzkörpers (5) mehrere Abspritzöffnungen (7) in die Durchflußblende (31) eingebracht sind, wobei der Eintrittsquerschnitt aller stromabwärts jeweils einer Ausnehmung (34) angeordneter Abspritzöffnungen (7) innerhalb des Austrittsquerschnitts der jeweiligen Ausnehmung (34) liegt . '3. Brennstoffeinspritzventil nach Anspruch 1 oder 2, dadurc gekennzeichnet, daß der Ventilsitzkörper (5) und die Durchflußblende (31) in einem mittleren Bereich jeweils eine korrespondierende kalottenförmige Geometrie aufweisen.Valve seat body (5) a plurality of spray orifices (7) are introduced into the flow orifice (31), the inlet cross section of all spray orifices (7) arranged downstream of a respective recess (34) within the outlet cross section of the respective recess (34). ' 3. Fuel injection valve according to claim 1 or 2, characterized in that the valve seat body (5) and the flow orifice (31) each have a corresponding dome-shaped geometry in a central region.
4.Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 3 , dadurch gekennzeichnet, daß die Durchflußblende (31) aus einer dünnen Membran gefertigt ist und zu Schwingungen anregbar ist.4.Fuel injection valve according to one of claims 1 to 3, characterized in that the flow orifice (31) is made of a thin membrane and can be excited to vibrate.
5. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Ventilsitzkörper (5) stromabwärts des Dichtsitzes auf seiner Innenseite eine mit dem Ventilschließkörper (4) weitgehend korrespondierende Form aufweist .5. Fuel injection valve according to one of claims 1 to 4, characterized in that the valve seat body (5) downstream of the sealing seat on its inside has a largely corresponding shape with the valve closing body (4).
6. Brennstoffeinspritzventil nach einem der vorhergehenden Ansprüch , dadurch gekennzeichnet, daß die Ausnehmungen (34) in dem Ventilsitzkörper (5) mittels Bohren eingebracht sind.6. Fuel injection valve according to one of the preceding claims, characterized in that the recesses (34) in the valve seat body (5) are introduced by drilling.
7. Brennstoffeinspritzventil nach einem der vorhergehenden Ansprüche , dadurch gekennzeichnet, daß die Abspritzöffnungen (7) in der Durchflußblende (31) mittels Stanzen eingebracht sind. 7. Fuel injection valve according to one of the preceding claims, characterized in that the spray openings (7) in the flow orifice (31) are introduced by means of punching.
EP01995537A 2000-11-30 2001-11-29 Fuel injection valve Expired - Lifetime EP1339972B1 (en)

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DE10059420A DE10059420A1 (en) 2000-11-30 2000-11-30 Fuel injector
DE10059420 2000-11-30
PCT/DE2001/004462 WO2002044552A1 (en) 2000-11-30 2001-11-29 Fuel injection valve

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Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10130684A1 (en) * 2001-06-26 2003-02-06 Bosch Gmbh Robert Fuel injector
DE10150712A1 (en) * 2001-10-13 2003-04-17 Bosch Gmbh Robert Fuel injection valve has annular sealing seat as part of valve seat surface with gradual concave curve
ITBO20040560A1 (en) * 2004-09-10 2004-12-10 Magneti Marelli Powertrain Spa FUEL INJECTOR WITH INJECTION VALVE PROVIDED WITH SIDE FEED
ATE461363T1 (en) * 2006-07-27 2010-04-15 Magneti Marelli Spa FUEL INJECTION VALVE FOR A DIRECT INJECTION INTERNAL COMBUSTION ENGINE
KR101019324B1 (en) * 2007-01-29 2011-03-07 미쓰비시덴키 가부시키가이샤 Fuel injection valve
DE102012207406A1 (en) * 2012-05-04 2013-11-07 Robert Bosch Gmbh Valve for metering fluid
US20140116391A1 (en) * 2012-10-31 2014-05-01 Electro-Motive Diesel, Inc. Fuel system having an injector blocking member
EP3076004B1 (en) * 2015-04-02 2018-09-12 Continental Automotive GmbH Valve assembly with a particle retainer element and fluid injection valve
JP6451663B2 (en) * 2016-02-24 2019-01-16 株式会社デンソー Fuel injection device
JP6749148B2 (en) * 2016-06-10 2020-09-02 日立オートモティブシステムズ株式会社 Fuel injector
US20220143633A1 (en) * 2019-02-25 2022-05-12 Cummins Inc. Swirl seat nozzle

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4019752A1 (en) * 1990-06-21 1992-01-02 Bosch Gmbh Robert FUEL INJECTION VALVE
DE4025945C2 (en) * 1990-08-16 1998-10-08 Bosch Gmbh Robert Method of adjusting a fuel injector and fuel injector
DE4221185A1 (en) 1992-06-27 1994-01-05 Bosch Gmbh Robert Orifice plate for a valve and method of manufacture
DE4312756A1 (en) * 1993-04-20 1994-10-27 Bosch Gmbh Robert Device for injecting a fuel-gas mixture
US5570841A (en) * 1994-10-07 1996-11-05 Siemens Automotive Corporation Multiple disk swirl atomizer for fuel injector
WO1996030644A1 (en) * 1995-03-29 1996-10-03 Robert Bosch Gmbh Perforated disc, especially for injection valves, and process for producting it
JP3183156B2 (en) * 1995-04-27 2001-07-03 株式会社デンソー Fluid injection nozzle
DE19636396B4 (en) * 1996-09-07 2005-03-10 Bosch Gmbh Robert Fuel injector
JP3750768B2 (en) * 1996-10-25 2006-03-01 株式会社デンソー Fluid injection nozzle
JPH1172067A (en) 1997-06-24 1999-03-16 Toyota Motor Corp Fuel injection valve of internal combustion engine
JP3164023B2 (en) * 1997-06-25 2001-05-08 トヨタ自動車株式会社 Fuel injection valve for internal combustion engine
DE19804463B4 (en) 1998-02-05 2006-06-14 Daimlerchrysler Ag Fuel injection system for gasoline engines
DE19856920A1 (en) 1998-12-10 2000-06-15 Bosch Gmbh Robert Fuel injector
US6330981B1 (en) * 1999-03-01 2001-12-18 Siemens Automotive Corporation Fuel injector with turbulence generator for fuel orifice

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0244552A1 *

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EP1339972B1 (en) 2006-01-04
DE50108639D1 (en) 2006-03-30
US20030132320A1 (en) 2003-07-17
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JP2004514835A (en) 2004-05-20
DE10059420A1 (en) 2002-06-06
WO2002044552A1 (en) 2002-06-06

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