EP1260703B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP1260703B1
EP1260703B1 EP02010912A EP02010912A EP1260703B1 EP 1260703 B1 EP1260703 B1 EP 1260703B1 EP 02010912 A EP02010912 A EP 02010912A EP 02010912 A EP02010912 A EP 02010912A EP 1260703 B1 EP1260703 B1 EP 1260703B1
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EP
European Patent Office
Prior art keywords
fuel injection
injection valve
elevations
valve according
ejection openings
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
EP02010912A
Other languages
German (de)
French (fr)
Other versions
EP1260703A2 (en
EP1260703A3 (en
Inventor
Joerg Heyse
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP1260703A2 publication Critical patent/EP1260703A2/en
Publication of EP1260703A3 publication Critical patent/EP1260703A3/en
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Publication of EP1260703B1 publication Critical patent/EP1260703B1/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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • 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
    • 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
    • F02M61/188—Spherical or partly spherical shaped valve member ends
    • 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
    • F02M61/165—Filtering elements specially adapted in fuel inlets to injector

Definitions

  • the invention relates to a fuel injection valve according to the preamble of independent claim 1.
  • a fuel injection system for a mixture-compression spark-ignition internal combustion engine which comprises a fuel injection valve which injects fuel into a combustion chamber formed by a piston / cylinder construction and is provided with a spark plug projecting into the combustion chamber.
  • the fuel injection valve is provided with at least one row of injection holes distributed over the circumference of the fuel injection valve. Through a targeted injection of fuel through the injection holes, a spray-guided combustion process is achieved by forming a mixture cloud with at least one jet.
  • a disadvantage of the fuel injection valve known from the above publication is in particular the poor atomization of injected through the injection openings in the combustion chamber of the internal combustion engine fuel, which is adversely affected mainly by the cylindrical shape of the flow channels. This is especially at low fuel pressure, so for example when starting the internal combustion engine, disadvantageous, which is reflected, inter alia, in poor exhaust emissions.
  • the fuel injection valve according to the invention with the features of the independent claim 1 has the advantage that the injection orifices are designed so that bulge-shaped projections rise above the inner end face of the valve seat body, comprising the flow channels in which the fuel is passed to the ejection openings.
  • the spray openings open into the combustion chamber of the internal combustion engine.
  • the diameter of the flow channels widens to the ejection openings, so that there is a maximum flow separation in the flow channels.
  • the preparation of the injection orifices is easily possible by means of a mandrel, which is struck against the flow direction of the fuel through the valve seat body.
  • the shape of the flow channels is easily modeled by the shape of the mandrel.
  • the shape of the edge surrounding the inlet can be designed, in particular, a tapered edge is favorable because of the maximum internal jet peening.
  • the beam detachment is also favorably influenced by an extended catchment radius which arises in the production of the spray-discharge openings.
  • the fuel injection valve 1 shows in a partial sectional view a first embodiment of a fuel injection valve 1 according to the invention.
  • the fuel injection valve 1 is designed in the form of a fuel injection valve 1 for fuel injection systems of mixture-compression, spark-ignition internal combustion engines.
  • the fuel injection valve 1 is suitable for the direct injection of fuel into a combustion chamber, not shown, of an internal combustion engine.
  • the fuel injection valve 1 consists of a nozzle body 2, in which a valve needle 3 is arranged.
  • the valve needle 3 is in operative connection with a valve closing body 4, which cooperates with a arranged on a valve seat body 5 valve seat surface 6 to a sealing seat.
  • the fuel injection valve 1 in the exemplary embodiment is an inwardly opening fuel injection valve 1, which has at least one injection opening 7.
  • the valve closing body 4 of the inventively designed fuel injection valve 1 has a nearly spherical shape. As a result, an offset-free, gimbal valve needle guide is achieved, which ensures an exact functioning of the fuel injection valve 1.
  • the valve seat body 5 of the fuel injection valve 1 is formed almost pot-shaped and contributes by its shape to the valve needle guide.
  • the valve seat body 5 is inserted into a spray-side recess 34 of the nozzle body 2 and connected by a weld 35 to the nozzle body 2.
  • the nozzle body 2 is sealed by a seal 8 against an outer pole 9 of a magnetic coil 10.
  • the magnetic coil 10 is encapsulated in a coil housing 11 and wound on a bobbin 12, which rests against an inner pole 13 of the magnetic coil 10.
  • the inner pole 13 and the outer pole 9 are separated by a gap 26 and are based on a connecting member 29 from.
  • the magnetic coil 10 is energized via a line 19 from a via an electrical plug contact 17 can be supplied with electric current.
  • the plug contact 17 is surrounded by a plastic casing 18, which may be molded on the inner pole 13.
  • valve needle 3 is guided in a valve needle guide 14, which is designed disk-shaped.
  • a valve needle guide 14 which is designed disk-shaped.
  • a paired shim 15 On the other side of the dial 15 is a Anchor 20. This is connected via a first flange 21 frictionally with the valve needle 3 in connection, which is connected by a weld 22 with the first flange 21.
  • a return spring 23 On the first flange 21, a return spring 23 is supported, which is brought in the present design of the fuel injection valve 1 by a sleeve 24 to bias.
  • a second flange 31 is arranged, which serves as a lower anchor stop. He is connected via a weld 33 non-positively with the valve needle 3. Between the armature 20 and the second flange 31, an elastic intermediate ring 32 for damping armature bouncers when closing the fuel injection valve 1 is arranged.
  • the armature 20 and the valve seat body 5 run fuel channels 30a to 30c.
  • the fuel is supplied via a central fuel supply 16 and filtered by a filter element 25.
  • the fuel injection valve 1 is sealed by a seal 28 against a distribution line, not shown.
  • the fuel injection valve 1 on the valve seat body 5 which is arranged in a recess 34 of the nozzle body 2 and connected for example by means of a weld seam 35 with this, elevations 36, in which run into the ejection openings 7 flow channels 39 extend.
  • the elevations 36 are formed on an inner end face 37 of the valve seat body 5 and protrude into a volume 38 formed between the valve closing body 4 and the valve seat body 5. Due to their special shape and arrangement, they improve the detachment readiness of the flow by jet necking in the ejection openings 7.
  • the ejection-side part of the fuel injection valve 1 with the measures according to the invention is illustrated and explained in more detail in the following figures.
  • the first flange 21 is acted on the valve needle 3 by the return spring 23 counter to its stroke direction so that the valve closing body 4 is held on the valve seat 6 in sealing engagement.
  • the armature 20 rests on the intermediate ring 32, which is supported on the second flange 31.
  • this builds up a magnetic field, which moves the armature 20 against the spring force of the return spring 23 in the stroke direction.
  • the armature 20 takes the first flange 21, which is welded to the valve needle 3, and thus the valve needle 3 also in the stroke direction with.
  • the valve-closing body 4, which is in operative connection with the valve needle 3, lifts off from the valve seat surface 6, as a result of which the fuel is sprayed off at the spray-discharge openings 7.
  • the armature 20 drops after sufficient degradation of the magnetic field by the pressure of the return spring 23 on the first flange 21 from the inner pole 13, whereby the valve needle 3 moves against the stroke direction.
  • the valve closing body 4 is seated on the valve seat surface 6, and the fuel injection valve 1 is closed.
  • the armature 20 is seated on the anchor stop formed by the second flange 31.
  • FIG. 2A shows an excerpt from a sectional view of the detail of FIG. 1 labeled IIA from the first exemplary embodiment of a fuel injection valve 1 configured according to the invention.
  • valve seat body 5 in the first embodiment described on its the valve closing body 4 facing inner end face 37 elevations 36, in which flow channels 39 extend, which open into the ejection openings 7.
  • the ejection openings 7 are formed in the present embodiment on the inner end face 37 of the valve seat body 5 and protrude into the between the volume of the valve closing body 4 and the valve seat body 5 formed volume 38 inside.
  • the ejection openings 7 can be attached to any points of the valve seat body 5. Preferably, they are arranged on a plurality of round or elliptical hole circles, which may be concentric or eccentric to each other, or on a plurality of parallel, obliquely or staggered straight or curved rows of holes.
  • the distance between the hole centers may be equidistant or different, but should be at least one hole diameter for manufacturing reasons.
  • the spatial orientation may be different for each hole axis, as indicated in Fig. 2A for two ejection openings 7.
  • the elevations 36 are cupped to tubular above the inner end face 37 of the valve seat body 5 raised.
  • the production of the ejection openings 7 takes place z. B. by means of a hardened mandrel which is stung against the direction of flow of the fuel through the material of the valve seat body 5, whereby the ejection openings 7 surrounding elevations 36 arise.
  • various shapes and cross sections of injection orifices 7 can be generated by arbitrary shapes of the mandrel.
  • FIG. 2B shows a cross-sectional shape of the ejection opening 7, which widens trumpet-shaped in the outflow direction of the fuel, while in Fig. 2C a barrel-like cross-sectional shape is shown, which also extends in total also in the outflow direction.
  • the detachment of the fuel flow of the ejection openings 7 can be promoted. Since the diameter of the ejection openings 7 is typically about 100 ⁇ m, a continuous flow is formed in the flow channels 39, which shows little tendency to move away from the walls to dissolve the flow channels. This then happens relatively abruptly at the ejection openings 7, as a result of which the mixture cloud injected into the combustion chamber becomes stringy and exhibits inhomogeneities. Due to the widening shape of the flow channels 39 in the elevations 36 and by the intrusion of the elevations 36 into the inflowing fuel, a jet constriction can take place, whereby a detachment of the flow in the ejection opening 7 is favored. As a result, a homogeneous mixture cloud with low stringency and subsequently better evaporation and mixing of the fuel-air mixture in the combustion chamber can be achieved.
  • the jets associated with the individual ejection openings 7 can be fanned out better.
  • the exhaust values of the internal combustion engine can be realized by a more effective combustion, especially at low fuel pressures in the shift operation or at the start of the internal combustion engine. As a result, the fuel consumption also decreases.
  • the formation of the elevations 36 can be influenced by the use of a die, not further shown by the elevations 36 are clamped between the matrix and the mandrel and thereby an edge 41 of the projections 36 can be arbitrarily shaped.
  • the edge 41 is formed in each case tapered, which lends itself in the sense of improving the flow constriction and subsequent detachment of the flow.
  • the invention is not limited to the illustrated embodiments and z. B. for arbitrarily arranged spray openings 7, for conical or cylindrical flow channels 39 and for any construction of inwardly opening multi-hole fuel injectors 1 applicable.

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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)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Brennstoffeinspritzventil nach dem Oberbegriff des unabhängigen Anspruchs 1.The invention relates to a fuel injection valve according to the preamble of independent claim 1.

Aus der DE 198 04 463 A1 ist ein Brennstoffeinspritzsystem für eine gemischverdichtende, fremdgezündete Brennkraftmaschine bekannt, welches ein Brennstoffeinspritzventil umfaßt, das Brennstoff in einen von einer Kolben-/Zylinderkonstruktion gebildeten Brennraum einspritzt, und mit einer in den Brennraum ragenden Zündkerze versehen ist. Das Brennstoffeinspritzventil ist mit mindestens einer Reihe über den Umfang des Brennstoffeinspritzventils verteilt angeordneten Einspritzlöchern versehen. Durch eine gezielte Einspritzung von Brennstoff über die Einspritzlöcher wird eine strahlgeführtes Brennverfahren durch Bildung einer Gemischwolke mit mindestens einem Strahl realisiert.From the DE 198 04 463 A1 A fuel injection system for a mixture-compression spark-ignition internal combustion engine is known which comprises a fuel injection valve which injects fuel into a combustion chamber formed by a piston / cylinder construction and is provided with a spark plug projecting into the combustion chamber. The fuel injection valve is provided with at least one row of injection holes distributed over the circumference of the fuel injection valve. Through a targeted injection of fuel through the injection holes, a spray-guided combustion process is achieved by forming a mixture cloud with at least one jet.

Nachteilig an dem aus der obengenannten Druckschrift bekannten Brennstoffeinspritzventil ist insbesondere die mangelhafte Zerstäubung des durch die Abspritzöffnungen in den Brennraum der Brennkraftmaschine eingespritzten Brennstoffs, die vor allem durch die zylindrische Ausformung der Strömungskanäle ungünstig beeinflußt wird. Dies ist insbesondere bei geringem Brennstoffdruck, also beispielsweise beim Starten der Brennkraftmaschine, von Nachteil, was sich u. a. in schlechten Abgaswerten niederschlägt.A disadvantage of the fuel injection valve known from the above publication is in particular the poor atomization of injected through the injection openings in the combustion chamber of the internal combustion engine fuel, which is adversely affected mainly by the cylindrical shape of the flow channels. This is especially at low fuel pressure, so for example when starting the internal combustion engine, disadvantageous, which is reflected, inter alia, in poor exhaust emissions.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des unabhängigen Anspruchs 1 hat demgegenüber den Vorteil, daß die Abspritzöffnungen so gestaltet sind, daß sich wulstförmige Erhebungen über der inneren Stirnfläche des Ventilsitzkörpers erheben, die Strömungskanäle umfassen, in denen der Brennstoff zu den Abspritzöffnungen geleitet wird. Die Abspritzöffnungen münden in den Brennraum der Brennkraftmaschine aus.The fuel injection valve according to the invention with the features of the independent claim 1 has the advantage that the injection orifices are designed so that bulge-shaped projections rise above the inner end face of the valve seat body, comprising the flow channels in which the fuel is passed to the ejection openings. The spray openings open into the combustion chamber of the internal combustion engine.

Durch die in den abhängigen Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen des im Anspruch 1 angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous developments of the fuel injection valve specified in claim 1 are possible.

Vorteilhafterweise erweitert sich der Durchmesser der Strömungskanäle zu den Abspritzöffnungen, so daß eine maximale Strömungsablösung in den Strömungskanälen herrscht.Advantageously, the diameter of the flow channels widens to the ejection openings, so that there is a maximum flow separation in the flow channels.

Für die Form der Strömungskanäle ist neben einer trompetenoder konusförmigen Verjüngung auch eine tonnenartige Form, welche sich zunächst erweitert, dann verjüngt und dann wieder erweitert, von Vorteil.For the shape of the flow channels in addition to a trumpet or cone-shaped taper and a barrel-like shape, which initially expanded, then tapered and then expanded again, an advantage.

Die Herstellung der Abspritzöffnungen ist mittels eines Dorns, der entgegen der Strömungsrichtung des Brennstoffs durch den Ventilsitzkörper geschlagen wird, einfach möglich. Die Form der Strömungskanäle ist in einfacher Weise durch die Form des Dorns modellierbar.The preparation of the injection orifices is easily possible by means of a mandrel, which is struck against the flow direction of the fuel through the valve seat body. The shape of the flow channels is easily modeled by the shape of the mandrel.

Durch die Verwendung einer Matrize kann die Form der Kante, die den Zulauf umgibt, gestaltet werden, wobei besonders eine spitz zulaufende Kante wegen der maximalen spritzlochinternen Strahlablösung günstig ist.By using a die, the shape of the edge surrounding the inlet, can be designed, in particular, a tapered edge is favorable because of the maximum internal jet peening.

Die Strahlablösung wird auch durch einen erweiterten Einzugsradius, der bei der Herstellung der Abspritzöffnungen entsteht, vorteilhaft beeinflußt.The beam detachment is also favorably influenced by an extended catchment radius which arises in the production of the spray-discharge openings.

Zeichnungdrawing

Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
einen schematischen Schnitt durch ein erstes Ausführungsbeispiel eines erfindungsgemäß ausgestalteten Brennstoffeinspritzventils in einer Gesamtansicht,
Fig. 2A
einen schematischen Schnitt durch den abspritzseitigen Teil des in Fig. 1 dargestellten ersten Ausführungsbeispiels des erfindungsgemäßen Brennstoffeinspritzventils im Bereich IIA in Fig. 1, und
Fig. 2B-C
eine vergrößerte Ansicht zweier Ausführungsbeispiele von Abspritzöffnungen im Bereich IIB in Fig. 2A.
Embodiments of the invention are shown in simplified form in the drawing and explained in more detail in the following description. Show it:
Fig. 1
3 shows a schematic section through a first exemplary embodiment of a fuel injection valve designed according to the invention in an overall view,
Fig. 2A
a schematic section through the discharge-side part of the illustrated in Fig. 1 the first embodiment of the fuel injection valve according to the invention in the area IIA in Fig. 1, and
Fig. 2B-C
an enlarged view of two embodiments of spray openings in the area IIB in Fig. 2A.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Fig. 1 zeigt in einer auszugsweisen Schnittdarstellung ein erstes Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils 1. Das Brennstoffeinspritzventil 1 ist in der Form eines Brennstoffeinspritzventils 1 für Brennstoffeinspritzanlagen von gemischverdichtenden, fremdgezündeten Brennkraftmaschinen ausgeführt. Das Brennstoffeinspritzventil 1 eignet sich zum direkten Einspritzen von Brennstoff in einen nicht dargestellten Brennraum einer Brennkraftmaschine.1 shows in a partial sectional view a first embodiment of a fuel injection valve 1 according to the invention. The fuel injection valve 1 is designed in the form of a fuel injection valve 1 for fuel injection systems of mixture-compression, spark-ignition internal combustion engines. The fuel injection valve 1 is suitable for the direct injection of fuel into a combustion chamber, not shown, of an internal combustion engine.

Das Brennstoffeinspritzventil 1 besteht aus einem Düsenkörper 2, in welchem eine Ventilnadel 3 angeordnet ist. Die Ventilnadel 3 steht in Wirkverbindung mit einem Ventilschließkörper 4, 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 nach innen öffnendes Brennstoffeinspritzventil 1, welches über wenigstens eine Abspritzöffnung 7 verfügt.The fuel injection valve 1 consists of a nozzle body 2, in which a valve needle 3 is arranged. The valve needle 3 is in operative connection with a valve closing body 4, which cooperates with a arranged on a valve seat body 5 valve seat surface 6 to a sealing seat. The fuel injection valve 1 in the exemplary embodiment is an inwardly opening fuel injection valve 1, which has at least one injection opening 7.

Der Ventilschließkörper 4 des erfindungsgemäß ausgestalteten Brennstoffeinspritzventils 1 weist eine nahezu kugelförmige Form auf. Dadurch wird eine versatzfreie, kardanische Ventilnadelführung erzielt, die für eine exakte Funktionsweise des Brennstoffeinspritzventils 1 sorgt.The valve closing body 4 of the inventively designed fuel injection valve 1 has a nearly spherical shape. As a result, an offset-free, gimbal valve needle guide is achieved, which ensures an exact functioning of the fuel injection valve 1.

Der Ventilsitzkörper 5 des Brennstoffeinspritzventils 1 ist nahezu topfförmig ausgebildet und trägt durch seine Form zur Ventilnadelführung bei. Der Ventilsitzkörper 5 ist dabei in eine abspritzseitige Ausnehmung 34 des Düsenkörpers 2 eingesetzt und mittels einer Schweißnaht 35 mit dem Düsenkörper 2 verbunden.The valve seat body 5 of the fuel injection valve 1 is formed almost pot-shaped and contributes by its shape to the valve needle guide. The valve seat body 5 is inserted into a spray-side recess 34 of the nozzle body 2 and connected by a weld 35 to the nozzle body 2.

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.The nozzle body 2 is sealed by a seal 8 against an outer pole 9 of a magnetic coil 10. The magnetic coil 10 is encapsulated in a coil housing 11 and wound on a bobbin 12, which rests against an inner pole 13 of the magnetic coil 10. The inner pole 13 and the outer pole 9 are separated by a gap 26 and are based on a connecting member 29 from. The magnetic coil 10 is energized via a line 19 from a via an electrical plug contact 17 can be supplied with electric current. The plug contact 17 is surrounded by a plastic casing 18, which may be molded on the inner pole 13.

Die Ventilnadel 3 ist in einer Ventilnadelführung 14 geführt, welche scheibenförmig ausgeführt ist. Zur Hubeinstellung dient eine zugepaarte Einstellscheibe 15. An der anderen Seite der Einstellscheibe 15 befindet sich ein Anker 20. Dieser steht über einen ersten Flansch 21 kraftschlüssig mit der Ventilnadel 3 in Verbindung, welche durch eine Schweißnaht 22 mit dem ersten Flansch 21 verbunden ist. Auf dem ersten Flansch 21 stützt sich eine Rückstellfeder 23 ab, welche in der vorliegenden Bauform des Brennstoffeinspritzventils 1 durch eine Hülse 24 auf Vorspannung gebracht wird.The valve needle 3 is guided in a valve needle guide 14, which is designed disk-shaped. For stroke adjustment is a paired shim 15. On the other side of the dial 15 is a Anchor 20. This is connected via a first flange 21 frictionally with the valve needle 3 in connection, which is connected by a weld 22 with the first flange 21. On the first flange 21, a return spring 23 is supported, which is brought in the present design of the fuel injection valve 1 by a sleeve 24 to bias.

Abströmseitig des Ankers 20 ist ein zweiter Flansch 31 angeordnet, der als unterer Ankeranschlag dient. Er ist über eine Schweißnaht 33 kraftschlüssig mit der Ventilnadel 3 verbunden. Zwischen dem Anker 20 und dem zweiten Flansch 31 ist ein elastischer Zwischenring 32 zur Dämpfung von Ankerprellern beim Schließen des Brennstoffeinspritzventils 1 angeordnet.Downstream of the armature 20, a second flange 31 is arranged, which serves as a lower anchor stop. He is connected via a weld 33 non-positively with the valve needle 3. Between the armature 20 and the second flange 31, an elastic intermediate ring 32 for damping armature bouncers when closing the fuel injection valve 1 is arranged.

In der Ventilnadelführung 14, im Anker 20 und am Ventilsitzkörper 5 verlaufen Brennstoffkanäle 30a bis 30c. Der Brennstoff wird über eine zentrale Brennstoffzufuhr 16 zugeführt und durch ein Filterelement 25 gefiltert. Das Brennstoffeinspritzventil 1 ist durch eine Dichtung 28 gegen eine nicht weiter dargestellte Verteilerleitung abgedichtet.In the valve needle guide 14, the armature 20 and the valve seat body 5 run fuel channels 30a to 30c. The fuel is supplied via a central fuel supply 16 and filtered by a filter element 25. The fuel injection valve 1 is sealed by a seal 28 against a distribution line, not shown.

Erfindungsgemäß weist das Brennstoffeinspritzventil 1 an dem Ventilsitzkörper 5, der in einer Ausnehmung 34 des Düsenkörpers 2 angeordnet und beispielsweise mittels einer Schweißnaht 35 mit diesem verbunden ist, Erhebungen 36 auf, in welchen in die Abspritzöffnungen 7 ausmündende Strömungskanäle 39 verlaufen. Die Erhebungen 36 sind dabei an einer inneren Stirnseite 37 des Ventilsitzkörpers 5 ausgebildet und ragen in ein zwischen dem Ventilschließkörper 4 und dem Ventilsitzkörper 5 ausgebildetes Volumen 38 hinein. Sie verbessern durch ihre spezielle Form und Anordnung die Ablösungsbereitschaft der Strömung durch Strahleinschnürung in den Abspritzöffnungen 7. Der abspritzseitige Teil des Brennstoffeinspritzventils 1 mit den erfindungsgemäßen Maßnahmen ist in den folgenden Figuren näher dargestellt und erläutert.According to the invention, the fuel injection valve 1 on the valve seat body 5, which is arranged in a recess 34 of the nozzle body 2 and connected for example by means of a weld seam 35 with this, elevations 36, in which run into the ejection openings 7 flow channels 39 extend. The elevations 36 are formed on an inner end face 37 of the valve seat body 5 and protrude into a volume 38 formed between the valve closing body 4 and the valve seat body 5. Due to their special shape and arrangement, they improve the detachment readiness of the flow by jet necking in the ejection openings 7. The ejection-side part of the fuel injection valve 1 with the measures according to the invention is illustrated and explained in more detail in the following figures.

Im Ruhezustand des Brennstoffeinspritzventils 1 wird der erste Flansch 21 an der Ventilnadel 3 von der Rückstellfeder 23 entgegen seiner Hubrichtung so beaufschlagt, daß der Ventilschließkörper 4 am Ventilsitz 6 in dichtender Anlage gehalten wird. Der Anker 20 liegt auf dem Zwischenring 32 auf, der sich auf dem zweiten Flansch 31 abstützt. Bei Erregung der Magnetspule 10 baut diese ein Magnetfeld auf, welches den Anker 20 entgegen der Federkraft der Rückstellfeder 23 in Hubrichtung bewegt. Dabei nimmt der Anker 20 den ersten Flansch 21, welcher mit der Ventilnadel 3 verschweißt ist, und damit die Ventilnadel 3 ebenfalls in Hubrichtung mit. Der mit der Ventilnadel 3 in Wirkverbindung stehende Ventilschließkörper 4 hebt von der Ventilsitzfläche 6 ab, wodurch der Brennstoff an den Abspritzöffnungen 7 abgespritzt wird.In the idle state of the fuel injection valve 1, the first flange 21 is acted on the valve needle 3 by the return spring 23 counter to its stroke direction so that the valve closing body 4 is held on the valve seat 6 in sealing engagement. The armature 20 rests on the intermediate ring 32, which is supported on the second flange 31. Upon excitation of the magnetic coil 10, this builds up a magnetic field, which moves the armature 20 against the spring force of the return spring 23 in the stroke direction. In this case, the armature 20 takes the first flange 21, which is welded to the valve needle 3, and thus the valve needle 3 also in the stroke direction with. The valve-closing body 4, which is in operative connection with the valve needle 3, lifts off from the valve seat surface 6, as a result of which the fuel is sprayed off at the spray-discharge openings 7.

Wird der Spulenstrom abgeschaltet, fällt der Anker 20 nach genügendem Abbau des Magnetfeldes durch den Druck der Rückstellfeder 23 auf den ersten 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. Der Anker 20 setzt auf dem durch den zweiten Flansch 31 gebildeten Ankeranschlag auf.If the coil current is turned off, the armature 20 drops after sufficient degradation of the magnetic field by the pressure of the return spring 23 on the first flange 21 from the inner pole 13, whereby the valve needle 3 moves against the stroke direction. As a result, the valve closing body 4 is seated on the valve seat surface 6, and the fuel injection valve 1 is closed. The armature 20 is seated on the anchor stop formed by the second flange 31.

Fig. 2A zeigt in einer auszugsweisen Schnittdarstellung den in Fig. 1 mit IIA bezeichneten Ausschnitt aus dem in Fig. 1 dargestellten ersten Ausführungsbeispiel eines erfindungsgemäß ausgestalteten Brennstoffeinspritzventils 1.FIG. 2A shows an excerpt from a sectional view of the detail of FIG. 1 labeled IIA from the first exemplary embodiment of a fuel injection valve 1 configured according to the invention.

Wie bereits in Fig. 1 angedeutet, weist der Ventilsitzkörper 5 im beschriebenen ersten Ausführungsbeispiel an seiner dem Ventilschließkörper 4 zugewandten inneren Stirnseite 37 Erhebungen 36 auf, in denen Strömungskanäle 39 verlaufen, die in die Abspritzöffnungen 7 münden.As already indicated in Fig. 1, the valve seat body 5 in the first embodiment described on its the valve closing body 4 facing inner end face 37 elevations 36, in which flow channels 39 extend, which open into the ejection openings 7.

Die Abspritzöffnungen 7 sind im vorliegenden Ausführungsbeispiel an der inneren Stirnseite 37 des Ventilsitzkörpers 5 ausgebildet und ragen in das zwischen dem Ventilschließkörper 4 und dem Ventilsitzkörper 5 ausgebildete Volumen 38 hinein. Die Abspritzöffnungen 7 können an beliebigen Punkten des Ventilsitzkörpers 5 angebracht sein. Vorzugsweise sind sie auf mehreren runden oder elliptischen Lochkreisen, die zueinander konzentrisch oder exzentrisch sein können, oder auf mehreren parallelen, schräg oder versetzt zueinander angeordneten geraden oder gebogenen Lochreihen angeordnet. Der Abstand zwischen den Lochmittelpunkten kann dabei äquidistant oder unterschiedlich sein, sollte jedoch aus fertigungstechnischen Gründen zumindest einen Lochdurchmesser betragen. Die räumliche Orientierung kann für jede Lochachse unterschiedlich sein, wie in Fig. 2A für zwei Abspritzöffnungen 7 angedeutet.The ejection openings 7 are formed in the present embodiment on the inner end face 37 of the valve seat body 5 and protrude into the between the volume of the valve closing body 4 and the valve seat body 5 formed volume 38 inside. The ejection openings 7 can be attached to any points of the valve seat body 5. Preferably, they are arranged on a plurality of round or elliptical hole circles, which may be concentric or eccentric to each other, or on a plurality of parallel, obliquely or staggered straight or curved rows of holes. The distance between the hole centers may be equidistant or different, but should be at least one hole diameter for manufacturing reasons. The spatial orientation may be different for each hole axis, as indicated in Fig. 2A for two ejection openings 7.

Die Erhebungen 36 sind kuppen- bis röhrenförmig über der inneren Stirnseite 37 des Ventilsitzkörpers 5 erhaben. Die Herstellung der Abspritzöffnungen 7 erfolgt dabei z. B. mittels eines gehärteten Dorns, der entgegen der Strömungsrichtung des Brennstoffs durch das Material des Ventilsitzkörpers 5 gestochen wird, wodurch die die Abspritzöffnungen 7 umgebenden Erhebungen 36 entstehen. Durch beliebige Formen des Dorns können, wie in den Fig. 2B und 2C dargestellt, verschiedene Formen und Querschnitte von Abspritzöffnungen 7 erzeugt werden.The elevations 36 are cupped to tubular above the inner end face 37 of the valve seat body 5 raised. The production of the ejection openings 7 takes place z. B. by means of a hardened mandrel which is stung against the direction of flow of the fuel through the material of the valve seat body 5, whereby the ejection openings 7 surrounding elevations 36 arise. As shown in FIGS. 2B and 2C, various shapes and cross sections of injection orifices 7 can be generated by arbitrary shapes of the mandrel.

Fig. 2B zeigt dabei eine Querschnittsform der Abspritzöffnung 7, welche sich trompetenförmig in Abströmrichtung des Brennstoffs erweitert, während in Fig. 2C eine tonnenartige Querschnittsform dargestellt ist, welche sich insgesamt gesehen ebenfalls in Abströmrichtung erweitert.2B shows a cross-sectional shape of the ejection opening 7, which widens trumpet-shaped in the outflow direction of the fuel, while in Fig. 2C a barrel-like cross-sectional shape is shown, which also extends in total also in the outflow direction.

Durch die besondere Form und Anordnung der Abspritzöffnungen 7 kann die Ablösung der Brennstoffströmung der Abspritzöffnungen 7 begünstigt werden. Da der Durchmesser der Abspritzöffnungen 7 typischerweise ca. 100 µm beträgt, bildet sich in den Strömungskanälen 39 eine kontinuierliche Strömung aus, die wenig Neigung zeigt, sich von den Wänden der Strömungskanäle zu lösen. Dies geschieht dann erst relativ abrupt an den Abspritzöffnungen 7, wodurch die in den Brennraum eingespritzte Gemischwolke strähnig wird und Inhomogenitäten aufweist. Durch die sich erweiternde Form der Strömungskanäle 39 in den Erhebungen 36 sowie durch das Hineinragen der Erhebungen 36 in den anströmenden Brennstoff kann eine Strahleinschnürung erfolgen, wodurch eine Ablösung der Strömung in der Abspritzöffnung 7 begünstigt wird. Dadurch kann eine homogene Gemischwolke mit geringer Strähnigkeit und nachfolgend eine bessere Verdampfung und Durchmischung des Brennstoff-Luft-Gemisches im Brennraum erzielt werden.Due to the special shape and arrangement of the ejection openings 7, the detachment of the fuel flow of the ejection openings 7 can be promoted. Since the diameter of the ejection openings 7 is typically about 100 μm, a continuous flow is formed in the flow channels 39, which shows little tendency to move away from the walls to dissolve the flow channels. This then happens relatively abruptly at the ejection openings 7, as a result of which the mixture cloud injected into the combustion chamber becomes stringy and exhibits inhomogeneities. Due to the widening shape of the flow channels 39 in the elevations 36 and by the intrusion of the elevations 36 into the inflowing fuel, a jet constriction can take place, whereby a detachment of the flow in the ejection opening 7 is favored. As a result, a homogeneous mixture cloud with low stringency and subsequently better evaporation and mixing of the fuel-air mixture in the combustion chamber can be achieved.

Da die Abspritzöffnungen 7 erhaben über der inneren Stirnseite 37 des Ventilsitzkörpers 5 in das Volumen 38 ausmünden, aber bündig mit einer äußeren Stirnseite 42 des Ventilsitzkörpers 5 abschließen, können die den einzelnen Abspritzöffnungen 7 zugeordneten Strahlen besser aufgefächert werden.Since the ejection openings 7 open out above the inner end face 37 of the valve seat body 5 into the volume 38, but terminate flush with an outer end face 42 of the valve seat body 5, the jets associated with the individual ejection openings 7 can be fanned out better.

In der Folge können die Abgaswerte der Brennkraftmaschine durch eine effektivere Verbrennung insbesondere bei geringen Brennstoffdrücken im Schichtbetrieb oder beim Start der Brennkraftmaschine verwirklicht werden. In der Folge sinkt auch der Brennstoffverbrauch.As a result, the exhaust values of the internal combustion engine can be realized by a more effective combustion, especially at low fuel pressures in the shift operation or at the start of the internal combustion engine. As a result, the fuel consumption also decreases.

Im Bereich der Aufwölbung der Erhebungen 36 ergibt sich herstellungsbedingt ein Einzugsradius 40, der für die maximale Ablösung der Strömung im Strömungskanal 39 vorteilhaft ist.In the area of the bulge of the elevations 36 results in production due to a catchment radius 40, which is advantageous for the maximum separation of the flow in the flow channel 39.

Die Formung der Erhebungen 36 kann durch die Verwendung einer nicht weiter dargestellten Matrize beeinflußt werden, indem die Erhebungen 36 zwischen der Matrix und dem Dorn eingeklemmt werden und dadurch eine Kante 41 der Erhebungen 36 beliebig geformt werden kann. In den Fig. 2B und 2C ist die Kante 41 jeweils spitz zulaufend ausgeformt, was sich im Sinne der Verbesserung der Strömungseinschnürung und nachfolgenden Ablösung der Strömung anbietet.The formation of the elevations 36 can be influenced by the use of a die, not further shown by the elevations 36 are clamped between the matrix and the mandrel and thereby an edge 41 of the projections 36 can be arbitrarily shaped. In FIGS. 2B and 2C, the edge 41 is formed in each case tapered, which lends itself in the sense of improving the flow constriction and subsequent detachment of the flow.

Die Erfindung ist nicht auf die dargestellten Ausführungsbeispiele beschränkt und z. B. für beliebig angeordnete Abspritzöffnungen 7, für konische oder zylindrisch verlaufende Strömungskanäle 39 sowie für beliebige Bauweisen von nach innen öffnenden Mehrloch-Brennstoffeinspritzventilen 1 anwendbar.The invention is not limited to the illustrated embodiments and z. B. for arbitrarily arranged spray openings 7, for conical or cylindrical flow channels 39 and for any construction of inwardly opening multi-hole fuel injectors 1 applicable.

Claims (11)

  1. Fuel injection valve (1) for fuel injection systems of internal combustion engines, having an excitable actuator (10), having a valve needle (3), which is operatively connected to the actuator (10) and is acted on in a closing direction by a return spring (23), for actuating a valve closing body (4) which forms a sealing seat together with a valve seat face (6) formed on a valve seat body (5), and having at least one ejection opening (7) which is formed in the valve seat body (5), characterized in that each of the ejection openings (7) opens out from a separate elevation (36), with the elevations (36) projecting beyond an inner end side (37) of the valve seat body (5), and with the fuel being conducted through flow ducts (39) in the elevations (36).
  2. Fuel injection valve according to Claim 1,
    characterized
    in that the elevations (36) project into a volume (38) formed between the valve closing body (4) and the valve seat body (5).
  3. Fuel injection valve according to Claim 1 or 2,
    characterized
    in that the flow ducts (39) in the elevations (36) expand in an outflow direction of the fuel to the ejection openings (7).
  4. Fuel injection valve according to Claim 3, characterized in that the flow ducts (39) expand in a trumpet shape.
  5. Fuel injection valve according to Claim 3, characterized in that the flow ducts (39) initially expand in the shape of a barrel and expand more intensely to the ejection openings (7).
  6. Fuel injection valve according to Claim 3, characterized in that the flow ducts (39) expand conically to the ejection openings (7).
  7. Fuel injection valve according to Claim 1 or 2, characterized in that the flow ducts (39) run cylindrically through the elevations (36).
  8. Fuel injection valve according to one of Claims 1 to 7, characterized in that the elevations (36) are arched by means of a mandrel during the production of the ejection openings (7).
  9. Fuel injection valve according to one of Claims 1 to 8, characterized in that a draw-in radius (40) of the flow ducts (39) is formed at the ejection openings (7).
  10. Fuel injection valve according to one of Claims 1 to 9, characterized in that an edge (41) is formed on the elevations (36) in the region of the inflow-side end of the flow ducts (39).
  11. Fuel injection valve according to Claim 10, characterized in that the edge (41) is formed so as to taper to a point.
EP02010912A 2001-05-21 2002-05-16 Fuel injection valve Expired - Lifetime EP1260703B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10124745 2001-05-21
DE2001124745 DE10124745A1 (en) 2001-05-21 2001-05-21 Fuel injector

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EP1260703A2 EP1260703A2 (en) 2002-11-27
EP1260703A3 EP1260703A3 (en) 2004-01-28
EP1260703B1 true EP1260703B1 (en) 2007-07-04

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DE10341790A1 (en) * 2003-09-10 2005-04-21 Bosch Gmbh Robert Fuel injector valve and nozzle for internal combustion engine has electromagnetic coil moving valve needle with spherical end engaging nozzle lining with thickened portions round nozzle bores
DE102008041676A1 (en) * 2008-08-29 2010-03-04 Robert Bosch Gmbh Fuel injector

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GB736264A (en) * 1952-09-04 1955-09-07 Daimler Benz Ag Improvements in liquid fuel injection nozzle devices
DE2711350A1 (en) * 1977-03-16 1978-09-21 Bosch Gmbh Robert FUEL INJECTION NOZZLE FOR COMBUSTION MACHINES
GB2097471A (en) * 1981-04-23 1982-11-03 Lucas Ind Plc I.C. engine fuel injection nozzle
AT378244B (en) * 1982-12-14 1985-07-10 Steyr Daimler Puch Ag INJECTION NOZZLE FOR AIR COMPRESSING, SELF-IGNITIONING PISTON PISTON COMBUSTION ENGINES
FI88333C (en) * 1991-06-25 1993-04-26 Waertsilae Diesel Int FOERBAETTRAT INSPRUTNINGSVENTILARRANGEMANG FOER BRAENSLE
DE4202387C2 (en) * 1991-11-11 1999-09-09 Bosch Gmbh Robert Valve with a spray opening
DE4222137B4 (en) * 1992-07-06 2006-05-04 Robert Bosch Gmbh Fuel injector for diesel internal combustion engines
US5540200A (en) * 1993-12-28 1996-07-30 Nissan Motor Co., Ltd. Fuel injection valve
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JPH08232813A (en) * 1995-02-27 1996-09-10 Aisan Ind Co Ltd Injector
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JP3329239B2 (en) * 1997-09-05 2002-09-30 トヨタ自動車株式会社 Fuel injection valve
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JP2000291513A (en) * 1999-04-08 2000-10-17 Toyota Motor Corp Diesel engine
DE10056039A1 (en) * 2000-11-11 2002-05-16 Bosch Gmbh Robert Fuel injection valve, for an IC motor, has a disk at the injection openings with a bi-metal or shape memory alloy section which is distorted by a heater to free selected injection openings with the same sealed seat

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Also Published As

Publication number Publication date
DE10124745A1 (en) 2003-03-27
EP1260703A2 (en) 2002-11-27
EP1260703A3 (en) 2004-01-28
DE50210406D1 (en) 2007-08-16

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