Nothing Special   »   [go: up one dir, main page]

EP1623109A1 - Fuel injection valve - Google Patents

Fuel injection valve

Info

Publication number
EP1623109A1
EP1623109A1 EP04720841A EP04720841A EP1623109A1 EP 1623109 A1 EP1623109 A1 EP 1623109A1 EP 04720841 A EP04720841 A EP 04720841A EP 04720841 A EP04720841 A EP 04720841A EP 1623109 A1 EP1623109 A1 EP 1623109A1
Authority
EP
European Patent Office
Prior art keywords
valve seat
fuel injection
valve
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
EP04720841A
Other languages
German (de)
French (fr)
Other versions
EP1623109B1 (en
Inventor
Axel Heinstein
Axel Storch
Guido Pilgram
Detlef Nowak
Joerg Heyse
Robert Koehler
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 EP1623109A1 publication Critical patent/EP1623109A1/en
Application granted granted Critical
Publication of EP1623109B1 publication Critical patent/EP1623109B1/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
    • F02M61/1806—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
    • 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
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/1833—Discharge orifices having changing cross sections, e.g. being divergent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/188—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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/06—Fuel-injection apparatus having means for preventing coking, e.g. of fuel injector discharge orifices or valve needles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/90—Selection of particular materials
    • F02M2200/9038—Coatings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/90—Selection of particular materials
    • F02M2200/9053—Metals
    • F02M2200/9076—Non-ferrous metals

Definitions

  • the invention relates to a fuel injector according to the preamble of the main claim.
  • a fuel injection system for a mixture-compressing, spark-ignited internal combustion engine which comprises a fuel injector, 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 injector is provided with at least one row of injection holes distributed over the circumference of the fuel injector. Through a targeted injection of fuel through the injection holes, a jet-guided combustion process is implemented by forming a mixture cloud with at least one jet.
  • a disadvantage of the fuel injector known from the abovementioned publication is, in particular, the coking of the spray orifices, which thereby block and inadmissibly reduce the flow through the fuel injector. This leads to malfunction of the internal combustion engine.
  • the combustion chamber-side coating of the valve tip or the entire valve seat body is advantageously made from a highly thermally conductive material such as copper or aluminum.
  • Another advantage is that the widening in the mouth region of the spray openings can be carried out in any way, such as. B. funnel-shaped, conical or rectangular.
  • FIG. 1B shows a schematic section through the spray-side part of the exemplary embodiment of the fuel injector according to the invention shown in FIG. 1A in the area IB in FIG. 1,
  • FIGS. 2A-B show a highly schematic illustration of a second exemplary embodiment of a fuel injector designed according to the invention in the region of the valve seat body in two different views
  • 3A-B show schematic representations of possible forms of spray openings for the fuel injection valves designed according to the invention.
  • 4A-B are explanatory diagrams of the mode of action of various combinations of the measures according to the invention.
  • FIG. 1A shows an exemplary sectional view of an exemplary 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-compressing, spark-ignition internal combustion engines.
  • the fuel injection valve 1 is suitable for injecting fuel directly into a combustion chamber 36, 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 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 valve closing body is almost spherical and thereby contributes to an offset-free guidance in the valve seat body 5.
  • fuel injector 1 is an inward opening fuel injector 1 which has two spray orifices 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.
  • valve needle 3 is guided in a valve needle guide 14, which is disc-shaped.
  • a paired adjusting disk 15 is used for stroke adjustment.
  • An armature 20 is located on the other side of the adjusting disk 15. This armature is non-positively connected to the valve needle 3 via a first flange 21, which is connected to the first flange 21 by a weld seam 22.
  • a restoring spring 23 is supported on the first flange 21 and, in the present design of the fuel injector 1, is preloaded by a sleeve 24.
  • a second flange 31 is arranged on the downstream side of the armature 20 and serves as a lower armature stop. It is non-positively connected to the valve needle 3 via a weld 33. Between the armature 20 and the second flange 31 an elastic intermediate ring 32 is arranged for damping anchor bumpers when the fuel injector 1 closes.
  • Fuel channels 30 and 31 run in the valve needle guide 14 and in the armature 20.
  • bevels 32 are formed which guide the fuel to the sealing seat.
  • the fuel is supplied via a central fuel supply 16 and filtered by a filter element 25.
  • the fuel injector 1 is sealed by a seal 28 against a distribution line, not shown.
  • Another seal 39 seals against the cylinder head of the internal combustion engine, not shown.
  • the fuel injection valve 1 has a heat-dissipating coating 38 on an outer side 37 of the valve seat body 5 facing the combustion chamber 36 of the internal combustion engine (not shown further).
  • the spray openings 7 open out through the coating 38, for example in a funnel shape.
  • the coating 38 dissipates heat from the valve seat body 5, which makes it less hot and therefore reduces the buildup of fuel and coking of the spray openings 7.
  • the spray-side part of the fuel injector 1 with the coating 38 is shown in more detail in FIG. 1B. Together with other measures described in more detail below, the coking of the spray openings 7 can be effectively reduced.
  • the first flange 21 on the valve needle 3 is acted upon by the return spring 23 against its lifting direction in such a way that the valve closing body 4 on the valve seat 6 is held in sealing contact.
  • the armature 20 rests on the intermediate ring 32, which is supported on the second flange 31.
  • the magnet coil 10 When the magnet coil 10 is excited, it builds up a magnetic field which moves the armature 20 in the stroke direction against the spring force of the return spring 23.
  • the Armature 20 the first flange 21, which with the valve needle
  • valve needle 3 is welded, and thus the valve needle 3 also in
  • valve closing body 4 which is operatively connected to the valve needle 3, lifts off the valve seat surface 6, as a result of which the fuel led to the spray opening 7 is sprayed 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 first flange 21, as a result of which the valve needle 3 moves counter to the stroke direction.
  • the valve closing body 4 rests on the valve seat surface 6 and the fuel injection valve 1 is closed.
  • the armature 20 rests on the armature stop formed by the second flange 31.
  • FIG. 1B shows an excerpted sectional illustration of the section designated IB in FIG. 1 from the exemplary embodiment of a fuel injector 1 designed according to the invention shown in FIG. 1.
  • the valve seat body 5 has a coating 38 on its outside 37 facing the combustion chamber 36.
  • the temperature of the valve seat body 5 can be reduced by the coating 38, as a result of which the coking of fuel which deposits on this is reduced.
  • the spray openings 7 remain free of deposits, which would otherwise impermissibly reduce the flow through the fuel injection valve 1 and would make the operation of the internal combustion engine impossible.
  • the coating 38 can be formed over the entire surface 34 of the valve seat body 5 or can be applied only in the region of the spray openings 7.
  • the valve seat body 5 can also be thickened, since this measure improves the thermal conductivity of the valve seat body and thereby also for a cooler end face 37 cares.
  • the material thickness should be greater than or equal to 0.4 mm.
  • the coating 38 can be produced, for example, galvanically on the basis of copper or aluminum, alternatively the entire valve seat body 5 can also be produced from a highly thermally conductive material such as copper or aluminum.
  • the spray openings 7 can be provided at any points on the valve seat body 5. They are preferably arranged on a round or elliptical bolt circle, which can be concentric or eccentric to a longitudinal axis 40 of the valve seat body 5. The distance between the hole centers can be equidistant or different. The spatial orientation can be different for each hole axis, as indicated in FIG. 1B for two spray openings 7.
  • the fuel jets sprayed out of the spray openings 7 can have any desired opening angles, which only depend on the geometry of the spray opening 7.
  • IB shows, for example, funnel-shaped mouth areas 41 of the spray openings 7.
  • the shape of the mouth areas 41 of the spray openings 7 also has an effect on the coking behavior of the fuel injector 1.
  • a widened mouth area 41 as shown in FIGS. 1A and IB, can be conical, funnel-shaped or stepped, but also how 2A and 2B, shown in a highly schematic manner, can be produced by means of a groove 42 which is provided in the region of the spray openings 7 on the valve seat body 5.
  • the narrowest cross section of the spray openings 7 to be measured is protected from the high combustion temperature and the combustion particles by the expanded cross section. Deposits, which are instead formed in the enlarged cross section, do not interfere with the spraying process, since the toppings during Growing into the fuel jet can be carried away by it. Removal is possible because the covering is sufficiently thick and therefore rather brittle.
  • spray openings 7 and their widened mouth regions 41 are shown by way of example.
  • a shape, such as that shown in FIG. 3A, is possible, for example, in connection with the coating 38 described in FIGS. 1A and IB, while the shape shown in FIG. 3B, for example, by providing a groove 42, as in FIGS. 2A and 2B can be performed.
  • the mouth regions 41 can be introduced into the valve seat body 5 or the coating 38, for example by means of laser drilling, eroding and similar methods.
  • the spray openings 7 and their mouth areas 41 can be generally funnel-shaped, stepped or conical. It is also possible to produce the mouth regions 41 by means of two-stage eroding.
  • the shape of the sealing seat which is formed from the valve seat surface 6 formed on the valve seat body 5 and the valve closing body 4, also contributes to reducing the temperature in this area.
  • An important aspect here is the distance between the surface of the valve closing body 4 and each of the spray orifices ⁇ 7.
  • a preferred value for this distance is a maximum of 20 ⁇ . Good heat conduction can take place through a small distance, while a large distance would reduce the removal of heat into the cooler valve needle 3.
  • the fuel cannot evaporate below the valve closing body 4, so that the region remains protected from the high temperature of the combustion chamber and from deposits of combustion residues. In addition, no sticky evaporation residues can arise in this area.
  • Another factor which influences the deposits in the region of the spray openings 7 is the number of spray openings 7.
  • a large number of spray openings 7 leads to a thinning of the mixture cloud in the outer regions, but also produces a fat core, which has a high fuel concentration in the interior Has area of the mixture cloud and thus also on the valve closing body 5.
  • a number of a maximum of eight spray openings 7 is advantageous.
  • FIGS. 4A and 4B show the effect of different combinations of features in comparison with a fuel injector 1 without the features according to the invention.
  • the diagrams show the emaciation of the metered injection quantity for various of the measures mentioned and combinations thereof.
  • the x-axis shows the development progress that is achieved with these measures.
  • the top left point 50 in diagram 4A represents a fuel injector 1 without the measures according to the invention.
  • the emaciation of the mixture by coking the spray openings 7 is up to 40%.
  • valve seat body 5 is modified so that the distance between the valve closing body 4 and the valve seat body 5 is reduced, a significant improvement already occurs, as the second point 51 in diagram 4A shows at approx. 30%.
  • FIG. 4B shows a section of the diagram shown in FIG. 4A in the region below 10% thinning.
  • the third measuring point 52 from FIG. 4A in FIG. 4B is transferred with a sufficient leanness of 10%.
  • the invention is not limited to the exemplary embodiments shown and can be used, for example, for spray openings 7 arranged as desired and for any construction of multi-hole fuel injection valves 1 opening inwards.

Landscapes

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

Abstract

Disclosed is a fuel injection valve (1) for directly injecting fuel into a combustion chamber (39) of an internal combustion engine. Said fuel injection valve (1) comprises an excitable actuator (10), a valve needle (3) that is effectively connected to the actuator (10), is impinged upon by a return spring (23) in a closing direction, and actuates a valve closing member (4) which forms a sealing seat along with a valve seat area (6) embodied on a valve seat member (5), and at least two spray ports that are configured inside the valve seat member (5). A coating (38) is embodied on an external face (37) of the valve seat member (5), which faces the combustion chamber (36) of the internal combustion engine, and/or the maximum number of spray ports (7) provided is eight, and/or a distance between the valve closing member (4) and the valve seat member (5) is smaller than 20 µm, and/or the spray ports (7) expand in a fuel-spraying direction.

Description

Brennstoffeinspritzventil Fuel injector
Stand der TechnikState of the art
Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Hauptanspruchs .The invention relates to a fuel injector according to the preamble of the main claim.
Aus der DE 198 04 463 AI ist .ein Brennstoffeinspritzsystem für eine gemischverdichtende, fremdgezündete Brennkraf maschine 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 DE 198 04 463 AI. A fuel injection system for a mixture-compressing, spark-ignited internal combustion engine is known, which comprises a fuel injector, 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 injector is provided with at least one row of injection holes distributed over the circumference of the fuel injector. Through a targeted injection of fuel through the injection holes, a jet-guided combustion process is implemented by forming a mixture cloud with at least one jet.
Nachteilig an dem aus der obengenannten Druckschrift bekannten Brennstoffeinspritzventil ist insbesondere die Verkokung der Abspritzöffnungen, welche dadurch verstopfen und den Durchfluß durch das Brennstoffeinspritzventil unzulässig stark vermindern. Dies führt zu Fehlfunktionen der Brennkraftmaschine . Vorteile der ErfindungA disadvantage of the fuel injector known from the abovementioned publication is, in particular, the coking of the spray orifices, which thereby block and inadmissibly reduce the flow through the fuel injector. This leads to malfunction of the internal combustion engine. Advantages of the invention
Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber • den Vorteil, daß eine Kombination verschiedener Maßnahmen wie eine Auf eitung der Abspritzöffnungen in Abspritzrichtung des Brennstoffs, eine gute Wärmeleitfähigkeit des Ventilsitzkörpers, eine Reduktion der Anzahl der Abspritzöffnungen sowie eine Verringerung des Abstandes zwischen Ventilschließkörper und Ventilsitzkorper dafür sorgt, daß sich im Bereich der Austritte der Abspritzöffnungen in den Brennraum der Brennkra tmaschine keine Ablagerungen durch Verkokung bilden können. Einer Fehlfunktion des Brennstoffeinspritzventils bzw. einer unzulässigen Drosselung des Brennstoffflusses wird somit vorgebeugt .Has the fuel injection valve of the invention with the characterizing features of the main claim • the advantage that a combination of different measures such as on Zeitung of the ejection openings in the direction of injection of the fuel, good thermal conductivity of the valve seat body, a reduction in the number of the ejection openings as well as a reduction in the distance between the valve closing body and valve seat body ensures that no deposits can form due to coking in the area of the outlets of the spray openings in the combustion chamber of the internal combustion engine. A malfunction of the fuel injector or an impermissible throttling of the fuel flow is thus prevented.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen des im Hauptanspruch angegebenen Brennstoffeinspritzventils möglich.The measures listed in the subclaims allow advantageous developments of the fuel injector specified in the main claim.
Vorteilhafterweise ist die brennraumseitige Beschichtung der Ventilspitze oder der ganze Ventilsitzkorper aus einem hoch wärmeleitfähigen Material wie Kupfer oder Aluminium hergestellt .The combustion chamber-side coating of the valve tip or the entire valve seat body is advantageously made from a highly thermally conductive material such as copper or aluminum.
Weiterhin ist von Vorteil, daß die Aufweitung im Mündungsbereich der Abspritzöffnungen in beliebiger Weise ausgeführt sein kann, wie z. B. trichterförmig, konisch oder rechteckig.Another advantage is that the widening in the mouth region of the spray openings can be carried out in any way, such as. B. funnel-shaped, conical or rectangular.
Zeichnungdrawing
Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen: Fig. 1A einen schematischen ■ Schnitt durch einEmbodiments of the invention are shown in simplified form in the drawing and explained in more detail in the following description. Show it: 1A shows a schematic section through
Ausführungsbeispiel eines erfindungsgemäß ausgestalteten Brennstoffeinspritzventils in einer Gesamtansicht ,An embodiment of a fuel injector designed according to the invention in an overall view,
Fig. 1B einen schematischen Schnitt durch den abspritzseitigen Teil des in Fig. 1A dargestellten Ausführungsbeispiels des erfindungsgemäßen Brennstoffeinspritzventils im Bereich IB in Fig. 1,1B shows a schematic section through the spray-side part of the exemplary embodiment of the fuel injector according to the invention shown in FIG. 1A in the area IB in FIG. 1,
Fig. 2A-B eine stark schematisierte Darstellung eines zweiten Ausführungsbeispiels eines erfindungsgemäß ausgestalteten Brennstoffeinspritzventils im Bereich des Ventilsitzkörpers in zwei verschiedenen Ansichten,2A-B show a highly schematic illustration of a second exemplary embodiment of a fuel injector designed according to the invention in the region of the valve seat body in two different views,
Fig. 3A-B schematische Darstellungen von möglichen Formen von Abspritzöffnungen für die erfindungsgemäß ausgestalteten Brennstoffeinspritzventile, und3A-B show schematic representations of possible forms of spray openings for the fuel injection valves designed according to the invention, and
Fig. 4A-B erläuternde Diagramme der Wirkungsweise verschiedener Kombinationen der erfindungsgemäßen Maßnahmen .4A-B are explanatory diagrams of the mode of action of various combinations of the measures according to the invention.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Fig. 1A zeigt in einer auszugsweisen Schnittdarstellung ein 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 näher dargestellten Brennraum 36 einer Brennkraftmaschine.1A shows an exemplary sectional view of an exemplary 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-compressing, spark-ignition internal combustion engines. The fuel injection valve 1 is suitable for injecting fuel directly into a combustion chamber 36, 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 Ventilsitzkorper 5 angeordneten Ventilsitzfläche 6 zu einem Dichtsitz zusammenwirkt. Der Ventilschließkörper ist nahezu kugelförmig ausgebildet und trägt dadurch zu einer versatzfreien Führung im Ventilsitzkorper 5 bei. Bei dem Brennstoffeinspritzventil 1 handelt es sich im Ausführungsbeispiel um ein nach innen öffnendes Brennstoffeinspritzventil 1, welches über zwei Abspritzöffnungen 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 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 valve closing body is almost spherical and thereby contributes to an offset-free guidance in the valve seat body 5. In the exemplary embodiment, fuel injector 1 is an inward opening fuel injector 1 which has two spray orifices 7.
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 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 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 disc-shaped. A paired adjusting disk 15 is used for stroke adjustment. An armature 20 is located on the other side of the adjusting disk 15. This armature is non-positively connected to the valve needle 3 via a first flange 21, which is connected to the first flange 21 by a weld seam 22. A restoring spring 23 is supported on the first flange 21 and, in the present design of the fuel injector 1, is preloaded by a sleeve 24.
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 .A second flange 31 is arranged on the downstream side of the armature 20 and serves as a lower armature stop. It is non-positively connected to the valve needle 3 via a weld 33. Between the armature 20 and the second flange 31 an elastic intermediate ring 32 is arranged for damping anchor bumpers when the fuel injector 1 closes.
In der Ventilnadelführung 14 und im Anker 20 verlaufen Brennstoffkanäle 30 und 31. Am Ventilschließkörper 4 sind Anschliffe 32 ausgebildet, welche den Brennstoff zum Dichtsitz führen. 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. Eine weitere Dichtung 39 dichtet gegen den nicht weiter dargestellten Zylinderkopf der Brennkraftmaschine ab.Fuel channels 30 and 31 run in the valve needle guide 14 and in the armature 20. On the valve closing body 4, bevels 32 are formed which guide the fuel to the sealing seat. The fuel is supplied via a central fuel supply 16 and filtered by a filter element 25. The fuel injector 1 is sealed by a seal 28 against a distribution line, not shown. Another seal 39 seals against the cylinder head of the internal combustion engine, not shown.
Erfindungsgemäß weist das Brennstoffeinspritzventil 1 an einer dem nicht weiter dargestellten Brennraum 36 der Brennkraftmaschine zugewandten Außenseite 37 des Ventilsitzkörpers 5 eine wärmeableitende Beschichtung 38 auf. Die Abspritzöffnungen 7 münden durch die Beschichtung 38 beispielsweise trichterförmig aus. Durch die Beschichtung 38 wird Wärme vom Ventilsitzkorper 5 abgeleitet, wodurch dieser weniger heiß wird und daher die Anlagerung von Brennstoff und eine Verkokung der Abspritzöffnungen 7 vermindert wird. Der abspritzseitige Teil des Brennstoffeinspritzventils 1 mit der Beschichtung 38 ist in Fig. 1B näher dargestellt. Zusammen mit weiteren, im folgenden näher beschriebenen Maßnahmen kann die Verkokung der Abspritzöffnungen 7 wirkungsvoll reduziert werden.According to the invention, the fuel injection valve 1 has a heat-dissipating coating 38 on an outer side 37 of the valve seat body 5 facing the combustion chamber 36 of the internal combustion engine (not shown further). The spray openings 7 open out through the coating 38, for example in a funnel shape. The coating 38 dissipates heat from the valve seat body 5, which makes it less hot and therefore reduces the buildup of fuel and coking of the spray openings 7. The spray-side part of the fuel injector 1 with the coating 38 is shown in more detail in FIG. 1B. Together with other measures described in more detail below, the coking of the spray openings 7 can be effectively reduced.
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 VentilnadelIn the idle state of the fuel injector 1, the first flange 21 on the valve needle 3 is acted upon by the return spring 23 against its lifting direction in such a way that the valve closing body 4 on the valve seat 6 is held in sealing contact. The armature 20 rests on the intermediate ring 32, which is supported on the second flange 31. When the magnet coil 10 is excited, it builds up a magnetic field which moves the armature 20 in the stroke direction against the spring force of the return spring 23. The Armature 20 the first flange 21, which with the valve needle
3 verschweißt ist, und damit die Ventilnadel 3 ebenfalls in3 is welded, and thus the valve needle 3 also in
Hubrichtung mit. Der mit der Ventilnadel 3 in Wirkverbindung stehende Ventilschließkörper 4 hebt von der Ventilsitzfläche 6 ab, wodurch der zur Abspritzöffnung 7 geführte Brennstoff abgespritzt wird.Stroke direction with. The valve closing body 4, which is operatively connected to the valve needle 3, lifts off the valve seat surface 6, as a result of which the fuel led to the spray opening 7 is sprayed off.
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 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 first 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. The armature 20 rests on the armature stop formed by the second flange 31.
Fig. 1B zeigt in einer auszugsweisen Schnittdarstellung den in Fig. 1 mit IB bezeichneten Ausschnitt aus dem in Fig. 1 dargestellten Ausführungsbeispiel eines erfindungsgemäß ausgestalteten Brennstoffeinspritzventils 1.FIG. 1B shows an excerpted sectional illustration of the section designated IB in FIG. 1 from the exemplary embodiment of a fuel injector 1 designed according to the invention shown in FIG. 1.
Wie bereits in Fig. 1A angedeutet, weist der Ventilsitzkorper 5 an seiner dem Brennraum 36 zugewandten Außenseite 37 eine Beschichtung 38 auf. Durch die Beschichtung 38 kann die Temperatur des Ventilsitzkörpers 5 reduziert werden, wodurch die Verkokung von sich an diesem niederschlagendem Brennstoff reduziert wird. Dadurch bleiben die Abspritzöffnungen 7 frei von Ablagerungen, welche andernfalls den Durchfluß durch das Brennstoffeinspritzventil 1 unzulässig stark reduzieren und den Betrieb der Brennkraftmaschine unmöglich machen würden.As already indicated in FIG. 1A, the valve seat body 5 has a coating 38 on its outside 37 facing the combustion chamber 36. The temperature of the valve seat body 5 can be reduced by the coating 38, as a result of which the coking of fuel which deposits on this is reduced. As a result, the spray openings 7 remain free of deposits, which would otherwise impermissibly reduce the flow through the fuel injection valve 1 and would make the operation of the internal combustion engine impossible.
Die Beschichtung 38 kann dabei vollflächig auf der ganzen Fläche 34 des Ventilsitzkörpers 5 ausgebildet oder nur im Bereich der Abspritzöffnungen 7 angebracht sein. Alternativ oder zusätzlich kann statt einer Beschichtung 38 auch der Ventilsitzkorper 5 verdickt ausgebildet sein, da diese Maßnahme die Wärmeleitfähigkeit des Ventilsitzkörpers verbessert und dadurch ebenfalls für eine kühlere Stirnseite 37 sorgt. Die Materialstärke sollte dabei größer als oder gleich 0 , 4 mm sein.The coating 38 can be formed over the entire surface 34 of the valve seat body 5 or can be applied only in the region of the spray openings 7. As an alternative or in addition, instead of a coating 38, the valve seat body 5 can also be thickened, since this measure improves the thermal conductivity of the valve seat body and thereby also for a cooler end face 37 cares. The material thickness should be greater than or equal to 0.4 mm.
Die Herstellung der Beschichtung 38 kann dabei beispielsweise galvanisch auf Kupferbasis oder Aluminiumbasis erfolgen, es kann auch alternativ der ganze Ventilsitzkorper 5 aus einem hochwärmeleitfähigen Material wie Kupfer oder Aluminium hergestellt sein.The coating 38 can be produced, for example, galvanically on the basis of copper or aluminum, alternatively the entire valve seat body 5 can also be produced from a highly thermally conductive material such as copper or aluminum.
Die Abspritzöffnungen 7 können an beliebigen Punkten des Ventilsitzkörpers 5 angebracht sein. Vorzugsweise sind sie auf einem runden oder elliptischen Lochkreis, der konzentrisch oder exzentrisch zu einer Längsachse 40 des Ventilsitzkörpers 5 sein kann, angeordnet. Der Abstand zwischen den Lochmittelpunkten kann dabei äquidistant oder unterschiedlich sein. Die räumliche Orientierung kann für jede Lochachse unterschiedlich sein, wie in Fig. IB für zwei Abspritzöffnungen 7 angedeutet.The spray openings 7 can be provided at any points on the valve seat body 5. They are preferably arranged on a round or elliptical bolt circle, which can be concentric or eccentric to a longitudinal axis 40 of the valve seat body 5. The distance between the hole centers can be equidistant or different. The spatial orientation can be different for each hole axis, as indicated in FIG. 1B for two spray openings 7.
Die aus den Abspritzöffnungen 7 abgespritzten Brennstoffstrahlen können beliebige Öffnungswinkel aufweisen, welche nur von der Geometrie der Abspritzöffnung 7 abhängen. In Fig. IB sind beispielsweise trichterförmige Mündungsbereiche 41 der Abspritzöffnungen 7 dargestellt.The fuel jets sprayed out of the spray openings 7 can have any desired opening angles, which only depend on the geometry of the spray opening 7. IB shows, for example, funnel-shaped mouth areas 41 of the spray openings 7.
Neben der Beschichtung 38 hat auch die Form der Mündungsbereiche 41 der Abspritzoffnungen 7 Auswirkungen auf das Verkokungsverhalten des Brennstoffeinspritzventils 1. Ein aufgeweiteter Mündungsbereich 41, wie in den Fig. 1A und IB dargestellt, kann konisch, trichterförmig oder gestuft ausgeführt sein, aber auch, wie in den Fig. 2A und 2B stark schematisiert dargestellt, mittels einer Nut 42 hergestellt werden, welche im Bereich der Abspritzöffnungen 7 am Ventilsitzkorper 5 angebracht ist. Der zu messende, engste Querschnitt der Abspritzöffnungen 7 wird durch den erweiterten Querschnitt vor der hohen Verbrennungstemperatur und den Verbrennungspartikeln geschützt. Ablagerungen, die statt dessen im erweiterten Querschnitt gebildet werden, stören den Abspritzvorgang nicht, da die Beläge beim Hineinwachsen in den Brennstoffstrahl von diesem- abgetragen werden. Die Abtragung ist dabei deshalb möglich, weil der Belag ausreichend dick und daher eher brüchig ist .In addition to the coating 38, the shape of the mouth areas 41 of the spray openings 7 also has an effect on the coking behavior of the fuel injector 1. A widened mouth area 41, as shown in FIGS. 1A and IB, can be conical, funnel-shaped or stepped, but also how 2A and 2B, shown in a highly schematic manner, can be produced by means of a groove 42 which is provided in the region of the spray openings 7 on the valve seat body 5. The narrowest cross section of the spray openings 7 to be measured is protected from the high combustion temperature and the combustion particles by the expanded cross section. Deposits, which are instead formed in the enlarged cross section, do not interfere with the spraying process, since the toppings during Growing into the fuel jet can be carried away by it. Removal is possible because the covering is sufficiently thick and therefore rather brittle.
In den Fig. 3A und 3B sind Abspritzöffnungen 7 und deren aufgeweitete Mündungsbereiche 41 beispielhaft dargestellt. Eine Form, wie die in Fig. 3A dargestellte, ist beispielsweise in Verbindung mit der in Fig. 1A und IB beschriebenen Beschichtung 38 möglich, während die in Fig. 3B gezeigte Form beispielsweise durch das Anbringen einer Nut 42, wie in Fig. 2A und 2B gezeigt, ausgeführt werden kann.3A and 3B, spray openings 7 and their widened mouth regions 41 are shown by way of example. A shape, such as that shown in FIG. 3A, is possible, for example, in connection with the coating 38 described in FIGS. 1A and IB, while the shape shown in FIG. 3B, for example, by providing a groove 42, as in FIGS. 2A and 2B can be performed.
Die Mündungsbereiche 41 können dabei beispielsweise mittels Laserbohren, Erodieren und ähnliche Verfahren in den Ventilsitzkorper 5 bzw. die BeSchichtung 38 eingebracht werden. Die Abspritzöffnungen 7 und ihre Mündungsbereiche 41 können dabei allgemein trichterförmig, gestuft oder konisch ausgeführt sein. Auch eine Herstellung der Mündungsbereiche 41 mittels zweistufigen Erodierens ist möglich.The mouth regions 41 can be introduced into the valve seat body 5 or the coating 38, for example by means of laser drilling, eroding and similar methods. The spray openings 7 and their mouth areas 41 can be generally funnel-shaped, stepped or conical. It is also possible to produce the mouth regions 41 by means of two-stage eroding.
■ Auch die Form des Dichtsitzes, welcher aus der an dem Ventilsitzkorper 5 ausgebildeten Ventilsitzfläche 6 und dem Ventilschließkörper 4 gebildet wird, trägt zur Verringerung der Temperatur in diesem Bereich bei. Wesentlicher Gesichtspunkt ist dabei der Abstand zwischen der Oberfläche des Ventilschließkörpers 4 und jeder der Abspritzöffnungen ■7. Ein bevorzugter Wert für diesen Abstand liegt dabei bei maximal 20 μ . Durch einen kleinen Abstand kann eine gute Wärmeleitung stattfinden, während ein großer Abstand den Abtransport von Wärme in die kühlere Ventilnadel 3 vermindern würde. Zudem kann durch die so erzielten niedrigen Temperaturen der Brennstoff unterhalb des Ventilschließkörpers 4 nicht verdampfen, so daß der Bereich vor der hohen Temperatur des Brennraums und vor Ablagerung von Verbrennungsrückständen geschützt bleibt. Zudem können keine klebrigen Verdampfungsreste in diesem Bereich entstehen. Ein weiterer Faktor, welcher die Ablagerungen im Bereich der Abspritzoffnungen 7 beeinflußt, ist die Anzahl der Abspritzöffnungen 7. Eine große Anzahl Abspritzöffnungen 7 führt zwar zu einer Abmagerung der Gemischwolke in den Außenbereichen, erzeugt jedoch auch einen fetten Kern, welcher eine hohe Brennstoffkonzentration im inneren Bereich der Gemischwolke und damit auch am Ventilschließkörper 5 aufweist. Um die Ablagerungen im Bereich der Abspritzöffnungen 7 gering zu halten, ist eine Anzahl von maximal acht Abspritzöffnungen 7 vorteilhaft.The shape of the sealing seat, which is formed from the valve seat surface 6 formed on the valve seat body 5 and the valve closing body 4, also contributes to reducing the temperature in this area. An important aspect here is the distance between the surface of the valve closing body 4 and each of the spray orifices ■ 7. A preferred value for this distance is a maximum of 20 μ. Good heat conduction can take place through a small distance, while a large distance would reduce the removal of heat into the cooler valve needle 3. In addition, due to the low temperatures thus achieved, the fuel cannot evaporate below the valve closing body 4, so that the region remains protected from the high temperature of the combustion chamber and from deposits of combustion residues. In addition, no sticky evaporation residues can arise in this area. Another factor which influences the deposits in the region of the spray openings 7 is the number of spray openings 7. A large number of spray openings 7 leads to a thinning of the mixture cloud in the outer regions, but also produces a fat core, which has a high fuel concentration in the interior Has area of the mixture cloud and thus also on the valve closing body 5. In order to keep the deposits in the area of the spray openings 7 low, a number of a maximum of eight spray openings 7 is advantageous.
Jedes einzelne dieser Merkmale hat eine positive Wirkung auf die Verkokungsneigung, aber erst eine Kombination der verschiedenen Möglichkeiten ergibt eine signifikante Reduktion der Ablagerungen im Bereich der Abspritzöffnungen 7. Die Diagramme in Fig. 4A und 4B zeigen dabei die Wirkung verschiedener Merkmalskombinationen im Vergleich zu einem Brennstoffeinspritzventil 1 ohne die erfindungsgemäßen Merkmale. Die Diagramme zeigen dabei die Abmagerung der dosierten Einspritzmenge für verschiedene der erwähnten Maßnahmen und Kombinationen daraus . Die x-Achse zeigt den Entwicklungsfortschritt, der mit diesen Maßnahmen erzielt wird.Each of these features has a positive effect on the tendency to coke, but only a combination of the various possibilities results in a significant reduction in the deposits in the area of the spray openings 7. The diagrams in FIGS. 4A and 4B show the effect of different combinations of features in comparison with a fuel injector 1 without the features according to the invention. The diagrams show the emaciation of the metered injection quantity for various of the measures mentioned and combinations thereof. The x-axis shows the development progress that is achieved with these measures.
Der oberste linke Punkt 50 in Diagramm 4A repräsentiert dabei ein Brennstoffeinspritzventil 1 ohne die erfindungsgemäßen Maßnahmen. Die Abmagerung des Gemisches durch Verkokung der Abspritzöffnungen 7 liegt bei bis zu 40%.The top left point 50 in diagram 4A represents a fuel injector 1 without the measures according to the invention. The emaciation of the mixture by coking the spray openings 7 is up to 40%.
Wird der Ventilsitzkorper 5 so modifiziert, daß der Abstand zwischen Ventilschließkörper 4 und Ventilsitzkorper 5 verringert wird, tritt bereits eine deutliche Verbesserung ein, wie der zweite Punkt 51 in Diagramm 4A bei ca. 30% zeigt.If the valve seat body 5 is modified so that the distance between the valve closing body 4 and the valve seat body 5 is reduced, a significant improvement already occurs, as the second point 51 in diagram 4A shows at approx. 30%.
Kombiniert man das Merkmal des verringerten Abstandes am Dichtsitz mit den sich in Abspritzrichtung erweiternden Abspritzöffnungen 7, gelangt man zum dritten Punkt 52 in Diagramm 4A bei ca. 10%, was eine weitere deutliche Verbesserung bedeutet.Combining the feature of the reduced distance at the sealing seat with the spray openings 7 widening in the spray direction leads to the third point 52 in Diagram 4A at approx. 10%, which means a further significant improvement.
Die Kombination des verringerten Abstandes mit einer geringen Anzahl von Abspritzöffnungen 7 bringt eine weitere geringfügige Verbesserung der Verkokungsneigung, wie der Punkt 53 ganz rechts in Diagramm 4A zeigt.The combination of the reduced distance with a small number of spray openings 7 brings a further slight improvement in the tendency to coke, as point 53 on the far right in diagram 4A shows.
Fig. 4B zeigt einen Ausschnitt aus dem in Fig. 4A dargestellten Diagramm im Bereich unterhalb von 10% Abmagerung. Zur Verdeutlichung ist der dritte Meßpunkt 52 aus Fig. 4A in Fig. 4B bei reichlich 10% Abmagerung übertragen.FIG. 4B shows a section of the diagram shown in FIG. 4A in the region below 10% thinning. For the sake of clarity, the third measuring point 52 from FIG. 4A in FIG. 4B is transferred with a sufficient leanness of 10%.
Weitere Verbesserungen der Verkokungsneigung sind durch die Kombination der Merkmale des geringen Abstandes und der sich erweiternden Abspritzöffnungen 7 mit den wärmeleitenden Maßnahmen durch Erhöhung der Wandstärke des Ventilsitzkörpers 5 (Meßpunkt 54 bei knapp 4%) oder des Aufbringens einer Beschichtung auf die Stirnseite 37 des Ventilsitzkörpers 5 (Meßpunkt 55 bei gut 2%) erzielbar.Further improvements in the tendency to coking are due to the combination of the features of the short distance and the widening spray openings 7 with the heat-conducting measures by increasing the wall thickness of the valve seat body 5 (measuring point 54 at just under 4%) or by applying a coating to the end face 37 of the valve seat body 5 (Measuring point 55 at a good 2%) achievable.
Eine weitere Absenkung ist noch möglich, indem die Maßnahmen des geringen ' Abstandes und der sich erweiternden Abspritzoffnungen 7 mit der verringerten Anzahl von Abspritzöffnungen 7 kombiniert' wird. Dann kann die Verkokungsneigung auf einen Wert nahe 1% (Meßpunkt 56) reduziert werden.A further reduction is still possible by the action of the low 'is distance and the widening Abspritzoffnungen 7 combined with the reduced number of spray openings 7'. Then the coking tendency can be reduced to a value close to 1% (measuring point 56).
Die Erfindung ist nicht auf die dargestellten Ausführungsbeispiele beschränkt und z: B. für beliebig angeordnete Abspritzöffnungen 7 sowie für beliebige Bauweisen von nach innen öffnenden Mehrloch- Brennstoffeinspritzventilen 1 anwendbar. The invention is not limited to the exemplary embodiments shown and can be used, for example, for spray openings 7 arranged as desired and for any construction of multi-hole fuel injection valves 1 opening inwards.

Claims

Ansprüche Expectations
1. Brennstoffeinspritzventil (1) zum direkten Einspritzen von Brennstoff in einen Brennraum (39) einer Brennkraftmaschine mit einem erregbaren Aktuator (10) , einer mit dem Aktuator (10) in Wirkverbindung stehenden und in einer Schließrichtung von einer Rückstellfeder (23) beaufschlagten Ventilnadel (3) zur Betätigung eines Ventilschließkörpers (4) , der zusammen mit einer an einem Ventilsitzkorper (5) ausgebildeten Ventilsitzfläche (6) einen Dichtsitz bildet, und zumindest zwei Abspritzöffnungen (7), die in dem Ventilsitzkorper (5) ausgebildet sind, dadurch gekennzeichnet, daß an einer dem Brennraum (36) der Brennkraftmaschine zugewandten Außenseite (37) des Ventilsitzkörpers (5) eine wärmeleitende Beschichtung (38) ausgebildet ist und/oder daß die Anzahl der Abspritzöffnungen (7) maximal acht ist und/oder daß ein Abstand zwischen dem Ventilschließkörper (4) und einem Einströmquerschnitt der Abspritzöffnungen (7) im Ventilsitzkorper (5) kleiner als 20 μm ist und/oder daß sich die Abspritzöffnungen (7) in einer Abspritzrichtung des Brennstoffs erweitern.1. Fuel injection valve (1) for injecting fuel directly into a combustion chamber (39) of an internal combustion engine with an excitable actuator (10), a valve needle (which is operatively connected to the actuator (10) and acted upon in a closing direction by a return spring (23) 3) for actuating a valve closing body (4), which forms a sealing seat together with a valve seat surface (6) formed on a valve seat body (5), and at least two spray openings (7) which are formed in the valve seat body (5), characterized in that that a heat-conducting coating (38) is formed on an outer side (37) of the valve seat body (5) facing the internal combustion engine and / or that the number of spray openings (7) is a maximum of eight and / or that a distance between the Valve closing body (4) and an inflow cross section of the spray openings (7) in the valve seat body (5) is less than 20 μm and / or r that the spray openings (7) widen in a spray direction of the fuel.
2. Brennstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß die Beschichtung (38) aus Kupfer oder Aluminium besteht. 2. Fuel injection valve according to claim 1, characterized in that the coating (38) consists of copper or aluminum.
3. Brennstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, daß die Beschichtung mittels Galvanisierens auf dem Ventilsitzkorper (5) aufgebracht ist.3. Fuel injection valve according to claim 2, characterized in that the coating is applied by means of electroplating on the valve seat body (5).
4. Brennstoffeinspritzventil nach einem der Ansprüche 2 oder 3, dadurch gekennzeichnet, daß der Ventilsitzkorper (5) aus Kupfer oder Aluminium hergestellt ist.4. Fuel injection valve according to one of claims 2 or 3, characterized in that the valve seat body (5) is made of copper or aluminum.
5. Brennstoffeinspritzventil nach . einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, daß die Wandstärke des Ventilsitzkörpers (5) größer oder gleich 0,4 mm ist.5. Fuel injector after. one of claims 2 to 4, characterized in that the wall thickness of the valve seat body (5) is greater than or equal to 0.4 mm.
6. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß sich jeweils ein Mündungsbereich (41) der6. Fuel injection valve according to one of claims 1 to 5, characterized in that there is a respective mouth region (41)
Abspritzöffnungen (7) in einer Abspritzrichtung erweitert.Spray openings (7) expanded in a spray direction.
7. Brennstoffeinspritzventil nach Anspruch 6, dadurch gekennzeichnet, daß der Mündungsbereich (41) der Abspritzöffnungen (7) trichterförmig, konisch oder gestuft erweitert ist.7. Fuel injection valve according to claim 6, characterized in that the mouth region (41) of the spray openings (7) is funnel-shaped, conical or stepped.
8. Brennstoffeinspritzventil nach Anspruch 6, dadurch gekennzeichnet, daß die Abspritzöffnungen (7) in einer Nut (42) ausmünden.8. Fuel injection valve according to claim 6, characterized in that the spray openings (7) open out in a groove (42).
9. Brennstoffeinspritzventil nach Anspruch 8, dadurch gekennzeichnet, daß die Mündungsbereiche (41) in der Nut (42) einen rechteckigen Querschnitt haben. 9. Fuel injection valve according to claim 8, characterized in that the mouth regions (41) in the groove (42) have a rectangular cross section.
10. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis10. Fuel injection valve according to one of claims 1 to
9, dadurch gekennzeichnet, daß die Abspritzöffnungen (7) durch Erodieren, Laserbohren oder Stanzen in den Ventilsitzkorper (5) eingebracht sind. 9, characterized in that the spray openings (7) are introduced into the valve seat body (5) by eroding, laser drilling or punching.
EP04720841A 2003-05-02 2004-03-16 Fuel injection valve Expired - Lifetime EP1623109B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10319694A DE10319694A1 (en) 2003-05-02 2003-05-02 Fuel injector
PCT/DE2004/000523 WO2004097209A1 (en) 2003-05-02 2004-03-16 Fuel injection valve

Publications (2)

Publication Number Publication Date
EP1623109A1 true EP1623109A1 (en) 2006-02-08
EP1623109B1 EP1623109B1 (en) 2008-07-02

Family

ID=33394052

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04720841A Expired - Lifetime EP1623109B1 (en) 2003-05-02 2004-03-16 Fuel injection valve

Country Status (5)

Country Link
US (1) US20070095952A1 (en)
EP (1) EP1623109B1 (en)
JP (1) JP2006525461A (en)
DE (2) DE10319694A1 (en)
WO (1) WO2004097209A1 (en)

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7334746B2 (en) 2004-03-08 2008-02-26 Continental Automotive Systems Us, Inc. Seat-lower guide combination
EP1856404B8 (en) * 2005-03-07 2009-01-14 Continental Automotive Systems US, Inc. Seat-lower guide combination
JP4306710B2 (en) * 2006-09-26 2009-08-05 株式会社デンソー Fuel injection nozzle
DE102006049533A1 (en) * 2006-10-20 2008-04-24 Robert Bosch Gmbh Piezoelectrically actuated injector for injection system i.e. common rail fuel injection system, has actuator, and control valve with valve unit with ball and pressure pin, where ball is guided in guiding borehole of valve housing
DE102006057279A1 (en) * 2006-12-05 2008-06-12 Robert Bosch Gmbh Fuel injection valve and method for producing a valve seat for a fuel injection valve
JP4942508B2 (en) 2007-02-20 2012-05-30 アークレイ株式会社 Probe for detecting abl gene mutation and use thereof
JP4918080B2 (en) * 2008-12-25 2012-04-18 本田技研工業株式会社 Fuel injection device
US20110030635A1 (en) * 2009-08-04 2011-02-10 International Engine Intellectual Property Company, Llc Fuel injector nozzle for reduced coking
DE102011077268A1 (en) * 2011-06-09 2012-12-13 Robert Bosch Gmbh Injection valve for internal combustion engines
WO2013138673A1 (en) * 2012-03-14 2013-09-19 International Engine Intellectual Property Company, Llc Fuel injector nozzle
DE102012209326A1 (en) * 2012-06-01 2013-12-05 Robert Bosch Gmbh Fuel injector
DE102012214522B3 (en) * 2012-08-15 2014-03-27 Ford Global Technologies, Llc Injector
JP6186130B2 (en) * 2013-02-04 2017-08-23 日立オートモティブシステムズ株式会社 Fuel injection valve and fuel injection valve manufacturing method
JP5786875B2 (en) * 2013-02-05 2015-09-30 株式会社デンソー Fuel injection nozzle
DE102013010552A1 (en) * 2013-06-15 2014-12-18 Volkswagen Aktiengesellschaft Injector
JP6020380B2 (en) * 2013-08-02 2016-11-02 株式会社デンソー Fuel injection valve
DE102013225948A1 (en) * 2013-12-13 2015-06-18 Continental Automotive Gmbh Nozzle head and fluid injection valve
JP6311472B2 (en) * 2014-06-16 2018-04-18 株式会社デンソー Fuel injection valve
JP2016217245A (en) * 2015-05-20 2016-12-22 本田技研工業株式会社 Injector
US11242800B2 (en) * 2017-11-07 2022-02-08 General Electric Company Systems and methods for reducing coke formation of fuel supply systems
JP2019100208A (en) * 2017-11-29 2019-06-24 株式会社デンソー Fuel injection valve
DE102018200341A1 (en) * 2018-01-11 2019-07-11 Robert Bosch Gmbh Valve for metering a fluid, in particular fuel injection valve
GB2577251A (en) * 2018-09-18 2020-03-25 Ford Global Tech Llc Diesel injectors and method of manufacturing diesel injectors

Family Cites Families (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2833090A1 (en) * 1978-07-28 1980-02-07 Opel Adam Ag Fuel injection nozzle for IC engine - has conical thermally conducting outer jacket to reduce temp. variations at nozzle
DE3623221A1 (en) * 1986-07-10 1988-02-04 Daimler Benz Ag Fuel injection nozzle, especially hole-type nozzle for direct injection internal combustion engines
DE3843235A1 (en) * 1988-12-22 1990-06-28 Bosch Gmbh Robert FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES
JP2819702B2 (en) * 1989-12-12 1998-11-05 株式会社デンソー Fuel injection valve
US5449121A (en) * 1993-02-26 1995-09-12 Caterpillar Inc. Thin-walled valve-closed-orifice spray tip for fuel injection nozzle
WO1995004881A1 (en) * 1993-08-06 1995-02-16 Ford Motor Company A fuel injector
US5353992A (en) * 1993-08-30 1994-10-11 Chrysler Corporation Multi-hole injector nozzle tip with low hydraulic plume penetration and large cloud-forming properties
US5685491A (en) * 1995-01-11 1997-11-11 Amtx, Inc. Electroformed multilayer spray director and a process for the preparation thereof
JPH09222057A (en) * 1996-02-15 1997-08-26 Zexel Corp Carbon deposit preventing device for electromagnetic type fuel injection valve
DE19639506A1 (en) * 1996-09-26 1998-04-02 Bosch Gmbh Robert Perforated disc and valve with a perforated disc
JP3750768B2 (en) * 1996-10-25 2006-03-01 株式会社デンソー Fluid injection nozzle
DE19653832A1 (en) * 1996-12-21 1998-06-25 Bosch Gmbh Robert Valve with combined valve seat body and spray orifice plate
JPH10274134A (en) * 1997-03-28 1998-10-13 Zexel Corp Fuel injection valve
DE19804463B4 (en) 1998-02-05 2006-06-14 Daimlerchrysler Ag Fuel injection system for gasoline engines
DE19815800A1 (en) * 1998-04-08 1999-10-14 Bosch Gmbh Robert Fuel injector
US6102299A (en) * 1998-12-18 2000-08-15 Siemens Automotive Corporation Fuel injector with impinging jet atomizer
JP2001046919A (en) * 1999-08-06 2001-02-20 Denso Corp Fluid injection nozzle
EP1553287B1 (en) * 1999-09-03 2007-03-07 Delphi Technologies, Inc. Injection Nozzle
US6742727B1 (en) * 2000-05-10 2004-06-01 Siemens Automotive Corporation Injection valve with single disc turbulence generation
JP2002039036A (en) * 2000-07-24 2002-02-06 Mitsubishi Electric Corp Fuel injection valve
US6405945B1 (en) * 2000-09-06 2002-06-18 Visteon Global Tech., Inc. Nozzle for a fuel injector
JP3837283B2 (en) * 2000-10-24 2006-10-25 株式会社ケーヒン Fuel injection valve
JP3837282B2 (en) * 2000-10-24 2006-10-25 株式会社ケーヒン Fuel injection valve
JP3745232B2 (en) * 2001-01-17 2006-02-15 愛三工業株式会社 Fluid injection nozzle and fluid injection valve including the fluid injection nozzle
DE10116714A1 (en) * 2001-04-04 2002-10-10 Volkswagen Ag Fuel injection valve for internal combustion engine, preferably for high jet speeds, has spray channels with cross-sections that expand after jet hole
DE10118163B4 (en) * 2001-04-11 2007-04-19 Robert Bosch Gmbh Fuel injector
US6817545B2 (en) * 2002-01-09 2004-11-16 Visteon Global Technologies, Inc. Fuel injector nozzle assembly
US6783085B2 (en) * 2002-01-31 2004-08-31 Visteon Global Technologies, Inc. Fuel injector swirl nozzle assembly
US6848635B2 (en) * 2002-01-31 2005-02-01 Visteon Global Technologies, Inc. Fuel injector nozzle assembly with induced turbulence
JP3751264B2 (en) * 2002-06-19 2006-03-01 株式会社ケーヒン Fuel injection valve
JP3759918B2 (en) * 2002-10-16 2006-03-29 三菱電機株式会社 Fuel injection valve
DE10307931A1 (en) * 2003-02-25 2004-10-28 Robert Bosch Gmbh Fuel injector
US7093776B2 (en) * 2004-06-29 2006-08-22 Delphi Technologies, Inc Fuel injector nozzle atomizer having individual passages for inward directed accelerated cross-flow
US7051957B1 (en) * 2004-11-05 2006-05-30 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
US7137577B2 (en) * 2004-11-05 2006-11-21 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
US7168637B2 (en) * 2004-11-05 2007-01-30 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
US7124963B2 (en) * 2004-11-05 2006-10-24 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
US7185831B2 (en) * 2004-11-05 2007-03-06 Ford Motor Company Low pressure fuel injector nozzle
US7104475B2 (en) * 2004-11-05 2006-09-12 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
JP4610631B2 (en) * 2008-05-01 2011-01-12 三菱電機株式会社 Fuel injection valve

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004097209A1 *

Also Published As

Publication number Publication date
DE502004007496D1 (en) 2008-08-14
EP1623109B1 (en) 2008-07-02
US20070095952A1 (en) 2007-05-03
JP2006525461A (en) 2006-11-09
DE10319694A1 (en) 2004-12-02
WO2004097209A1 (en) 2004-11-11

Similar Documents

Publication Publication Date Title
EP1623109B1 (en) Fuel injection valve
EP1379773B1 (en) Fuel injection valve
EP1599669B1 (en) Fuel injection valve
DE10049518A1 (en) Fuel injector
EP1395749B1 (en) Fuel injection valve
EP1434941A1 (en) Fuel injection valve
EP1474604B1 (en) Fuel injection valve
EP1312796B1 (en) Fuel injection valve
DE10050751A1 (en) Fuel injection valve for IC engines has swirl-generating device formed by swirl channels in upstream side of valve seat body
DE10354467A1 (en) Fuel injector
EP1195516B1 (en) Fuel injection valve
EP1328721B1 (en) Fuel-injection valve
DE10124744A1 (en) Fuel injector
DE10307932A1 (en) Fuel injection valve for petrol engine, has valve plug with end surface facing valve seat with groove including array of spray openings
EP1260703B1 (en) Fuel injection valve
DE10130684A1 (en) Fuel injector
WO2005021957A1 (en) Fuel injection valve
DE102018221833A1 (en) Valve for metering a fluid, in particular a fuel injection valve
DE10142300A1 (en) Fuel injection valve, for an IC motor, has a flame protection capsule to shroud the fuel injection openings against the cylinder combustion zone to prevent a build-up of carbon deposits
DE10304866A1 (en) Motor vehicle internal combustion engine fuel injection valve has injection openings formed in valve seat with radial seating extending above them

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20051202

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 20060331

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 502004007496

Country of ref document: DE

Date of ref document: 20080814

Kind code of ref document: P

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20090403

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20150324

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20150324

Year of fee payment: 12

Ref country code: FR

Payment date: 20150319

Year of fee payment: 12

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20160316

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20161130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160316

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160316

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20170529

Year of fee payment: 14

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004007496

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181002