EP0553310B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP0553310B1
EP0553310B1 EP92911364A EP92911364A EP0553310B1 EP 0553310 B1 EP0553310 B1 EP 0553310B1 EP 92911364 A EP92911364 A EP 92911364A EP 92911364 A EP92911364 A EP 92911364A EP 0553310 B1 EP0553310 B1 EP 0553310B1
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EP
European Patent Office
Prior art keywords
valve
fuel
seat
valve seat
perforated
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Expired - Lifetime
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EP92911364A
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German (de)
French (fr)
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EP0553310A1 (en
Inventor
Peter Romann
Ferdinand Reiter
Martin Maier
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0553310A1 publication Critical patent/EP0553310A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—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
    • F02M61/1853—Orifice plates

Definitions

  • the invention is based on a fuel injection valve according to the preamble of claim 1.
  • a fuel injection valve is already known (US Pat. No. 4,971,254) in which the perforated disk is held on the valve seat body by means of a support disk. The perforated disk and the support disk are fixed by a flanged edge of the seat support engaging the support disk, a sealing ring being required between the seat support, valve seat body and perforated disk, which is intended to prevent fuel from escaping accidentally over the circumference of the perforated disk and support disk.
  • the sealing effect of the sealing ring will deteriorate, in particular also because of the constant temperature changes, and fuel will inadvertently emerge from the fuel injection valve.
  • the fuel injector according to the invention with the characterizing features of claim 1 has the advantage that a thin perforated disc can be used, which leads to an optimal fuel preparation with the finest fuel droplets without deterioration of the spray pattern of the sprayed fuel jet and still ensures the tightness of the fuel injector.
  • the support disk in a pot shape and to tightly connect its circumferential retaining edge to the seat support in its axial position after the adjustment of the valve seat body, so that this makes it possible to adjust the valve lift and thus the amount of fuel injected.
  • the holding edge of the support disk is bent outwards towards its free end and, with this free end, bears against the wall of a longitudinal opening of the seat support under radial tension, so that the valve seat body is in its axial direction during the adjustment process Position is held until the desired setting is reached and the retaining edge of the support plate is welded to the wall of the longitudinal opening of the seat support for final fixing.
  • the through-opening of the support disk encompasses as close as possible to the region of the perforated disk which is provided with the at least one spray opening and is curved in a dome shape downstream, in order to avoid undesirable deflection of the perforated disk due to the prevailing fuel pressure.
  • the fuel injector for fuel injection systems of mixture-compression-ignition Internal combustion engines partially shown.
  • the fuel injector has a tubular seat support 1, in which a longitudinal opening 3 is formed concentrically with a valve longitudinal axis 2.
  • a longitudinal opening 3 is formed concentrically with a valve longitudinal axis 2.
  • tubular valve needle 5 is arranged which is connected at its downstream end 6 with an example spherical valve closing body 7.
  • the fuel injector is actuated in a known manner, for example electromagnetically.
  • An indicated electromagnetic circuit with a magnet coil 10, an armature 11 and a core 12 is used for the axial movement of the valve needle 5 and thus for opening or closing the fuel injection valve.
  • the armature 11 is connected to the end of the valve needle 5 facing away from the valve closing body 7 and on the core 12 aligned.
  • a guide opening 16 of a valve seat body 18 serves to guide the valve closing body 7 during the axial movement.
  • the circumference of the valve seat body 18 has a slightly smaller diameter than the diameter of the longitudinal opening 3 of the seat carrier 1.
  • a metal perforated disk 22 is arranged concentrically on the valve seat body 18 and is firmly connected to it.
  • the perforated disc 22 has a thickness of 0.1 mm, for example.
  • the metal support disk 26 has a cup-shaped cross-sectional shape and has a thickness of 0.2 mm, for example.
  • a circumferential holding edge 28 adjoins a bottom part 27 of the support disk 26 which bears against the end face 25 of the perforated body 22 and extends in the axial direction away from the valve seat body 18 and is conically bent outwards up to one end 29.
  • the holding edge 28 has at its end 29 a slightly larger diameter than the diameter of the longitudinal opening 3 of the seat carrier 1.
  • the connection of the valve seat body 18, perforated disk 22 and support disk 26 is carried out, for example, by a circumferential and dense, e.g. B. first weld seam 24 formed by a laser. For this reason, good weldability should also be ensured in the material selection for the perforated disk 22 and the support disk 26.
  • valve seat body 18 with the perforated disk 22 and the support disk 26 attached to it is inserted into the longitudinal opening 3. Due to the somewhat smaller diameter of the circumference of the valve seat body 18 compared to the longitudinal opening 3 of the seat support 1, there is only radial pressure between the longitudinal opening 3 and the slightly conical outwardly bent retaining edge 28 of the support disk 26, the retaining edge 28 having a radial spring action exerts on the wall of the longitudinal opening 3. As a result, chip formation is avoided when the valve seat body 18 with the perforated disk 22 and the support disk 26 is inserted into the longitudinal opening 3 of the seat support 1.
  • valve seat body 18 In addition, in the manufacture of the valve seat body 18 it is not necessary to maintain a narrow dimensional tolerance on its circumference, since the valve seat body 18 has a slight play in the radial opening in the longitudinal opening 3 of the seat carrier 1, so that the manufacturing costs compared to a valve seat body pressed into the longitudinal opening 3 be significantly reduced.
  • the insertion depth of the valve seat body 18 into the longitudinal opening 3 of the seat support 1 determines the presetting of the stroke of the valve needle 5 guided radially through the guide opening 16, since the one end position of the valve needle 5 when the magnet coil 10 is not energized due to the valve closing body 7 resting against a downstream of the guide opening 16 formed valve seat surface 32 of the valve seat body 18 is fixed.
  • the other end position of the valve needle 5 is determined when the solenoid 10 is excited, for example by the armature 11 resting on the core 12. The path between these two end positions represents the stroke of the valve needle 5.
  • the holding edge 28 of the support disk 26 is connected to the wall of the longitudinal opening 3, for example by a circumferential and tight second weld seam 30.
  • the second weld 30 is just like the first weld 24 z. B. generated by a laser, so that there is a safe and reliable, easy to produce weld, in which the heating of the parts to be welded together is low.
  • valve seat body 18 and perforated disk 22 or support disk 26 and of support disk 26 and seat support 1 is required so that the medium used, for example a fuel, does not pass between the longitudinal opening 3 of the seat support 1 and the circumference of the valve seat body 18 or between the Longitudinal opening 3 of the seat support 1 and the holding edge 28 of the support plate 26 can flow directly into an intake line of the internal combustion engine.
  • medium used for example a fuel
  • the spherical valve closing body 7 interacts with the valve seat surface 32 of the valve seat body 18, which tapers conically in the flow direction, for example, and which is formed in the axial direction between the guide opening 16 and the end face 19 of the valve seat body 18, and has a plurality of flats 33, preferably five, which form a flow of the medium from the valve interior 35 delimited in the radial direction by the longitudinal opening 3 of the seat carrier 1 to the valve seat surface 32, from where the medium, in the opened state of the valve, reaches spray openings 37 of the perforated disk 22 via a short intermediate opening 36 formed downstream in the valve seat body 18.
  • the diameter of the guide opening 16 is designed such that the spherical valve closing body 7 projects into the guide opening 16 with a small radial distance.
  • the support disk 26 is used for the exact adjustment of the stroke of the valve needle 5 in the axial direction in the area between the second weld seam 30 and of the first weld seam 24 is stretched in this way by means of a tool 39 and, if necessary, is plastically deformed until the measured actual medium quantity matches the specified medium target quantity.
  • the exact setting of the stroke and the static flow quantity of a medium which is emitted during the stationary opening state of the injection valve is carried out in a simple manner on the fully assembled fuel injection valve.
  • a protective cap 45 is arranged on the circumference of the seat support 1 at its downstream end and is connected to the circumference of the seat support 1 by means of a latching connection 46.
  • the protective cap 45 rests with a first radial section 47 on an end face 48 of the seat support 1.
  • the first radial section 47 of the protective cap 45 is first adjoined by an axially extending parallel section 49 and a second radial section 50 pointing radially outward.
  • a sealing ring 51 is arranged in an annular groove 53, the side surfaces of which are formed by an end face 54 of the second radial section 50 of the protective cap 45 facing the magnetic coil 10 and by a radially outwardly facing contact surface 55 of the seat support 1 and the groove base 57 thereof by the circumference of the seat support 1 .
  • the sealing ring 51 serves to seal between the circumference of the fuel injection valve and a valve receptacle, not shown, for example the intake line of the internal combustion engine.
  • the intermediate opening 36 downstream of the valve seat surface 32 of the valve seat body 18 encompasses a central region 60 of the perforated disk 22, in which the at least one spray opening 37 is, but for example four spray openings 37 are formed.
  • a through-opening 61 is provided in the support disk 26 approximately concentrically to the valve longitudinal axis 2, which likewise encompasses the area 60 of the perforated disk 22 on the opposite side. The fuel sprayed through the spray openings 37 is thus sprayed through the through opening 61 of the support disk 26.
  • the area 60 of the perforated disk 22 which is encompassed by the through-opening 61 of the support disk 26 can be curved in the direction of flow such that it has the shape of a spherical cap.
  • the first weld 24 has a sufficiently large radial distance from the area 60 of the perforated disk 22 in order to avoid the formation of deformations in the area 60.
  • the axial distance between the area 60 of the perforated disk 22 and the lower end of the valve closing body 7 is kept as small as possible in order to form the smallest possible dead volume.

Abstract

A fuel injection valve with a thin perforated metal plate fitted on a valve seat member downstream of a valve seat surface is already known. Here, the perforated plate must be thick enough to prevent its bending as a result of the prevailing fuel pressure, but this adversely affects the preparation of the fuel which is injected through at least one aperture. The use of a thin perforated plate is therefore to be made possible in order to improve fuel preparation. The thin perforated plate (22) allocated to the valve seat member (18) is supported by a plate (26) with a through aperture (61) which is thicker than the perforated plate (22). This effectively prevents any undesirable bending of the perforated plate (22) and at the same time improves the fuel preparation at the injection apertures (37). The supporting plate (26) is pot shaped and is welded together with the perforated plate (22) to the valve seat member (18) by a circumferential weld seam (24). The fuel injection valve may be used in fuel injection systems of compressed-mixture spark-ignition internal combustion engines.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Patentanspruchs 1. Es ist bereits ein Brennstoffeinspritzventil bekannt (US-A-4,971,254), bei dem die Lochscheibe an dem Ventilsitzkörper mittels einer Stützscheibe gehalten wird. Dabei erfolgt die Fixierung von Lochscheibe und Stützscheibe durch einen an der Stützscheibe angreifenden Bördelrand des Sitzträgers, wobei zwischen Sitzträger, Ventilsitzkörper und Lochscheibe ein Dichtring erforderlich ist, der ein ungewolltes Austreten von Brennstoff über den Umfang von Lochscheibe und Stützscheibe verhindern soll. Dabei besteht jedoch die Gefahr, daß insbesondere auch wegen der ständigen Temperaturwechsel die Dichtwirkung des Dichtringes nachläßt und Brennstoff in ungewollter Weise aus dem Brennstoffeinspritzventil austritt.The invention is based on a fuel injection valve according to the preamble of claim 1. A fuel injection valve is already known (US Pat. No. 4,971,254) in which the perforated disk is held on the valve seat body by means of a support disk. The perforated disk and the support disk are fixed by a flanged edge of the seat support engaging the support disk, a sealing ring being required between the seat support, valve seat body and perforated disk, which is intended to prevent fuel from escaping accidentally over the circumference of the perforated disk and support disk. However, there is a risk that the sealing effect of the sealing ring will deteriorate, in particular also because of the constant temperature changes, and fuel will inadvertently emerge from the fuel injection valve.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß eine dünne Lochscheibe verwendet werden kann, die ohne Verschlechterung des Abspritzbildes des abgespritzten Brennstoffstrahles zu einer optimalen Brennstoffaufbereitung mit feinsten Brennstofftröpfchen führt und trotzdem die Dichtheit des Brennstoffeinspritzventiles gewährleistet ist.The fuel injector according to the invention with the characterizing features of claim 1 has the advantage that a thin perforated disc can be used, which leads to an optimal fuel preparation with the finest fuel droplets without deterioration of the spray pattern of the sprayed fuel jet and still ensures the tightness of the fuel injector.

Durch die in den abhängigen Patentansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Patentanspruch 1 angegebenen Brennstoffeinspritzventiles möglich.The measures listed in the dependent claims allow advantageous refinements and improvements of the fuel injector specified in claim 1.

Besonders vorteilhaft ist es, die Stützscheibe topfförmig auszubilden und deren umlaufenden Halterand nach der Einstellung des Ventilsitzkörpers in seiner axialen Lage mit dem Sitzträger dicht zu verbinden, so daß hierdurch die Einstellung des Ventilhubes und damit der eingespritzten Brennstoffmenge möglich ist. Für diese Einstellung ist es ebenfalls vorteilhaft, daß der Halterand der Stützscheibe zu seinem freien Ende hin nach außen gebogen ist und mit diesem freien Ende unter radialer Spannung an der Wandung einer Längsöffnung des Sitzträgers anliegt, so daß der Ventilsitzkörper bei dem Einstellvorgang jeweils in seiner axialen Lage gehalten wird, bis die gewünschte Einstellung erreicht und zur endgültigen Fixierung der Halterand der Stützscheibe mit der Wandung der Längsöffnung des Sitzträgers verschweißt ist.It is particularly advantageous to design the support disk in a pot shape and to tightly connect its circumferential retaining edge to the seat support in its axial position after the adjustment of the valve seat body, so that this makes it possible to adjust the valve lift and thus the amount of fuel injected. For this setting, it is also advantageous that the holding edge of the support disk is bent outwards towards its free end and, with this free end, bears against the wall of a longitudinal opening of the seat support under radial tension, so that the valve seat body is in its axial direction during the adjustment process Position is held until the desired setting is reached and the retaining edge of the support plate is welded to the wall of the longitudinal opening of the seat support for final fixing.

Vorteilhaft ist es ebenfalls, wenn die Durchgangsöffnung der Stützscheibe möglichst nahe den mit der wenigstens einen Abspritzöffnung versehenen und nach stromabwärts gewölbten kalottenförmig ausgebildeten Bereich der Lochscheibe umgreift, um eine unerwünschte Durchbiegung der Lochscheibe aufgrund des herrschenden Brennstoffdruckes zu vermeiden.It is also advantageous if the through-opening of the support disk encompasses as close as possible to the region of the perforated disk which is provided with the at least one spray opening and is curved in a dome shape downstream, in order to avoid undesirable deflection of the perforated disk due to the prevailing fuel pressure.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert.An embodiment of the invention is shown in simplified form in the drawing and explained in more detail in the following description.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In der Figur ist beispielsweise ein Brennstoffeinspritzventil für Brennstoffeinspritzanlagen von gemischverdichtenden fremdgezündeten Brennkraftmaschinen teilweise dargestellt. Das Brennstoffeinspritzventil hat einen rohrförmigen Sitzträger 1, in dem konzentrisch zu einer Ventillängsachse 2 eine Längsöffnung 3 ausgebildet ist. In der Längsöffnung 3 ist eine z. B. rohrförmige Ventilnadel 5 angeordnet die an ihrem stromabwärtigen Ende 6 mit einem beispielsweise kugelförmigen Ventilschließkörper 7 verbunden ist. Die Betätigung des Brennstoffeinspritzventils erfolgt in bekannter Weise beispielsweise elektromagnetisch. Zur axialen Bewegung der Ventilnadel 5 und damit zum Öffnen bzw. Schließen des Brennstoffeinspritzventils dient ein angedeuteter elektromagnetischer Kreis mit einer Magnetspule 10, einem Anker 11 und einem Kern 12. Der Anker 11 ist mit dem dem Ventilschließkörper 7 abgewandten Ende der Ventilnadel 5 verbunden und auf den Kern 12 ausgerichtet.In the figure is, for example, a fuel injector for fuel injection systems of mixture-compression-ignition Internal combustion engines partially shown. The fuel injector has a tubular seat support 1, in which a longitudinal opening 3 is formed concentrically with a valve longitudinal axis 2. In the longitudinal opening 3 is a z. B. tubular valve needle 5 is arranged which is connected at its downstream end 6 with an example spherical valve closing body 7. The fuel injector is actuated in a known manner, for example electromagnetically. An indicated electromagnetic circuit with a magnet coil 10, an armature 11 and a core 12 is used for the axial movement of the valve needle 5 and thus for opening or closing the fuel injection valve. The armature 11 is connected to the end of the valve needle 5 facing away from the valve closing body 7 and on the core 12 aligned.

Zur Führung des Ventilschließkörpers 7 während der Axialbewegung dient eine Führungsöffnung 16 eines Ventilsitzkörpers 18. Der Umfang des Ventilsitzkörpers 18 weist einen gering kleineren Durchmesser als den Durchmesser der Längsöffnung 3 des Sitzträgers 1 auf. An seiner einen, der Ventilnadel 5 abgewandten Stirnseite 19 ist an dem Ventilsitzkörper 18 eine metallene Lochscheibe 22 konzentrisch angeordnet und mit diesem fest verbunden. Die Lochscheibe 22 hat beispielsweise eine Dicke von 0,1 mm. An einer dem Ventilsitzkörper 18 abgewandten Stirnseite 25 der Lochscheibe 22 liegt eine dicker als die Lochscheibe 22 ausgebildete Stützscheibe 26 an. Die metallene Stützscheibe 26 weist eine topfförmige Querschnittsform auf und hat beispielsweise eine Dicke von 0,2 mm. An ein an der Stirnseite 25 des Lochkörpers 22 anliegendes Bodenteil 27 der Stützscheibe 26 schließt sich ein umlaufender Halterand 28 an, der sich in axialer Richtung dem Ventilsitzkörper 18 abgewandt erstreckt und bis zu einem Ende 29 hin konisch nach außen gebogen ist. Dabei weist der Halterand 28 an seinem Ende 29 einen gering größeren Durchmesser auf als den Durchmesser der Längsöffnung 3 des Sitzträgers 1. Die Verbindung von Ventilsitzkörper 18, Lochscheibe 22 und Stützscheibe 26 erfolgt beispielsweise durch eine umlaufende und dichte, z. B. mittels eines Lasers ausgebildete erste Schweißnaht 24. Bei der Werkstoffauswahl für die Lochscheibe 22 und die Stützscheibe 26 ist aus diesem Grund auch auf eine gute Schweißbarkeit zu achten.A guide opening 16 of a valve seat body 18 serves to guide the valve closing body 7 during the axial movement. The circumference of the valve seat body 18 has a slightly smaller diameter than the diameter of the longitudinal opening 3 of the seat carrier 1. On its one end face 19 facing away from the valve needle 5, a metal perforated disk 22 is arranged concentrically on the valve seat body 18 and is firmly connected to it. The perforated disc 22 has a thickness of 0.1 mm, for example. On an end face 25 of the perforated disk 22 facing away from the valve seat body 18, there is a support disk 26 which is thicker than the perforated disk 22. The metal support disk 26 has a cup-shaped cross-sectional shape and has a thickness of 0.2 mm, for example. A circumferential holding edge 28 adjoins a bottom part 27 of the support disk 26 which bears against the end face 25 of the perforated body 22 and extends in the axial direction away from the valve seat body 18 and is conically bent outwards up to one end 29. The holding edge 28 has at its end 29 a slightly larger diameter than the diameter of the longitudinal opening 3 of the seat carrier 1. The connection of the valve seat body 18, perforated disk 22 and support disk 26 is carried out, for example, by a circumferential and dense, e.g. B. first weld seam 24 formed by a laser. For this reason, good weldability should also be ensured in the material selection for the perforated disk 22 and the support disk 26.

Bei in die Längsöffnung 3 des Sitzträgers 1 eingeschobener Ventilnadel 5 wird in die Längsöffnung 3 der Ventilsitzkörper 18 mit daran befestigter Lochscheibe 22 und Stützscheibe 26 eingeschoben. Durch den im Vergleich zu der Längsöffnung 3 des Sitzträgers 1 etwas geringeren Durchmesser des Umfanges des Ventilsitzkörpers 18 liegt nur zwischen der Längsöffnung 3 und dem leicht konisch nach außen gebogen ausgebildeten Halterand 28 der Stützscheibe 26 eine radiale Pressung vor, wobei der Halterand 28 eine radiale Federwirkung auf die Wandung der Längsöffnung 3 ausübt. Dadurch wird beim Einschieben des Ventilsitzkörpers 18 mit Lochscheibe 22 und Stützscheibe 26 in die Längsöffnung 3 des Sitzträgers 1 eine Spanbildung vermieden. Zudem ist bei der Herstellung des Ventilsitzkörpers 18 nicht die Einhaltung einer engen Maßtoleranz an seinem Umfang erforderlich, da der Ventilsitzkörper 18 in radialer Richtung ein kleines Spiel in der Längsöffnung 3 des Sitzträgers 1 hat, so daß die Herstellkosten gegenüber einem in die Längsöffnung 3 eingepreßten Ventilsitzkörper wesentlich reduziert werden. Die Einschubtiefe des Ventilsitzkörpers 18 in die Längsöffnung 3 des Sitzträgers 1 bestimmt die Voreinstellung des Hubes der durch die Führungsöffnung 16 radial geführten Ventilnadel 5, da die eine Endstellung der Ventilnadel 5 bei nicht erregter Magnetspule 10 durch die Anlage des Ventilschließkörpers 7 an einer stromabwärts der Führungsöffnung 16 ausgebildeten Ventilsitzfläche 32 des Ventilsitzkörpers 18 festgelegt ist. Die andere Endstellung der Ventilnadel 5 wird bei erregter Magnetspule 10 beispielsweise durch die Anlage des Ankers 11 am Kern 12 festgelegt. Der Weg zwischen diesen beiden Endstellungen stellt den Hub der Ventilnadel 5 dar.When the valve needle 5 is inserted into the longitudinal opening 3 of the seat support 1, the valve seat body 18 with the perforated disk 22 and the support disk 26 attached to it is inserted into the longitudinal opening 3. Due to the somewhat smaller diameter of the circumference of the valve seat body 18 compared to the longitudinal opening 3 of the seat support 1, there is only radial pressure between the longitudinal opening 3 and the slightly conical outwardly bent retaining edge 28 of the support disk 26, the retaining edge 28 having a radial spring action exerts on the wall of the longitudinal opening 3. As a result, chip formation is avoided when the valve seat body 18 with the perforated disk 22 and the support disk 26 is inserted into the longitudinal opening 3 of the seat support 1. In addition, in the manufacture of the valve seat body 18 it is not necessary to maintain a narrow dimensional tolerance on its circumference, since the valve seat body 18 has a slight play in the radial opening in the longitudinal opening 3 of the seat carrier 1, so that the manufacturing costs compared to a valve seat body pressed into the longitudinal opening 3 be significantly reduced. The insertion depth of the valve seat body 18 into the longitudinal opening 3 of the seat support 1 determines the presetting of the stroke of the valve needle 5 guided radially through the guide opening 16, since the one end position of the valve needle 5 when the magnet coil 10 is not energized due to the valve closing body 7 resting against a downstream of the guide opening 16 formed valve seat surface 32 of the valve seat body 18 is fixed. The other end position of the valve needle 5 is determined when the solenoid 10 is excited, for example by the armature 11 resting on the core 12. The path between these two end positions represents the stroke of the valve needle 5.

An seinem Ende 29, das an der Längsöffnung 3 des Sitzträgers 1 anliegt, wird der Halterand 28 der Stützscheibe 26 mit der Wandung der Längsöffnung 3 beispielsweise durch eine umlaufende und dichte zweite Schweißnaht 30 verbunden. Die zweite Schweißnaht 30 wird genau wie die erste Schweißnaht 24 z. B. mittels eines Lasers erzeugt, so daß sich eine sichere und zuverlässige, auf einfache Art und Weise herstellbare Verschweißung ergibt, bei der die Erwärmung der miteinander zu verschweißenden Teile gering ist.At its end 29, which bears against the longitudinal opening 3 of the seat support 1, the holding edge 28 of the support disk 26 is connected to the wall of the longitudinal opening 3, for example by a circumferential and tight second weld seam 30. The second weld 30 is just like the first weld 24 z. B. generated by a laser, so that there is a safe and reliable, easy to produce weld, in which the heating of the parts to be welded together is low.

Eine dichte Verschweißung von Ventilsitzkörper 18 und Lochscheibe 22 bzw. Stützscheibe 26 sowie von Stützscheibe 26 und Sitzträger 1 ist erforderlich, damit das verwendete Medium, beispielsweise ein Brennstoff, nicht zwischen der Längsöffnung 3 des Sitzträgers 1 und dem Umfang des Ventilsitzkörpers 18 hindurch oder zwischen der Längsöffnung 3 des Sitzträgers 1 und dem Halterand 28 der Stützscheibe 26 hindurch unmittelbar in eine Ansaugleitung der Brennkraftmaschine strömen kann.A tight welding of valve seat body 18 and perforated disk 22 or support disk 26 and of support disk 26 and seat support 1 is required so that the medium used, for example a fuel, does not pass between the longitudinal opening 3 of the seat support 1 and the circumference of the valve seat body 18 or between the Longitudinal opening 3 of the seat support 1 and the holding edge 28 of the support plate 26 can flow directly into an intake line of the internal combustion engine.

Der kugelförmige Ventilschließkörper 7 wirkt mit der sich in Strömungsrichtung beispielsweise kegelförmig verjüngenden Ventilsitzfläche 32 des Ventilsitzkörpers 18 zusammen, die in axialer Richtung zwischen der Führungsöffnung 16 und der Stirnseite 19 des Ventilsitzkörpers 18 ausgebildet ist, und weist mehrere Abflachungen 33, vorzugsweise fünf, die eine Strömung des Mediums von dem in radialer Richtung durch die Längsöffnung 3 des Sitzträgers 1 begrenzten Ventilinnenraum 35 zur Ventilsitzfläche 32 ermöglichen, von wo das Medium im geöffneten Zustand des Ventils über eine stromabwärts im Ventilsitzkörper 18 ausgebildete kurze Zwischenöffnung 36 zu Abspritzöffnungen 37 der Lochscheibe 22 gelangt. Zur exakten Führung des Ventilschließkörpers 7 und damit der Ventilnadel 5 während der Axialbewegung ist der Durchmesser der Führungsöffnung 16 so ausgebildet, daß der kugelförmige Ventilschließkörper 7 in die Führungsöffnung 16 mit geringem radialen Abstand ragt.The spherical valve closing body 7 interacts with the valve seat surface 32 of the valve seat body 18, which tapers conically in the flow direction, for example, and which is formed in the axial direction between the guide opening 16 and the end face 19 of the valve seat body 18, and has a plurality of flats 33, preferably five, which form a flow of the medium from the valve interior 35 delimited in the radial direction by the longitudinal opening 3 of the seat carrier 1 to the valve seat surface 32, from where the medium, in the opened state of the valve, reaches spray openings 37 of the perforated disk 22 via a short intermediate opening 36 formed downstream in the valve seat body 18. For the exact guidance of the valve closing body 7 and thus the valve needle 5 during the axial movement, the diameter of the guide opening 16 is designed such that the spherical valve closing body 7 projects into the guide opening 16 with a small radial distance.

Die exakte Einstellung des Hubes der Ventilnadel 5 und damit der statischen, während des stationären Öffnungszustandes des Ventils abgegebenen Strömungsmenge des Mediums erfolgt an dem fertig montierten Brennstoffeinspritzventil, d.h. unter anderem, daß die mit dem Ventilsitzkörper 18 verschweißte Stützscheibe 26 an ihrem Halterand 28 mit dem Sitzträger 1 verschweißt ist. Stimmt die statische, von dem Ventil abgegebene und mittels eines Meßgefäßes 38 gemessene Istmenge des Mediums nicht mit der gewünschten, vorgegebenen Sollmenge überein, so wird die Stützscheibe 26 zur exakten Einstellung des Hubes der Ventilnadel 5 in axialer Richtung im Bereich zwischen der zweiten Schweißnaht 30 und der ersten Schweißnaht 24 mittels eines Werkzeuges 39 derart gestreckt und damit gegebenenfalls plastisch verformt, bis die gemessene Mediumistmenge mit der vorgegebenen Mediumsollmenge übereinstimmt. Hierdurch erfolgt auf einfache Art und Weise die exakte Einstellung des Hubes und der statischen, während des stationären Öffnungszustandes des Einspritzventils abgegebenen Strömungsmenge eines Mediums an dem fertig montierten Brennstoffeinspritzventil.The exact setting of the stroke of the valve needle 5 and thus the static flow quantity of the medium which is emitted during the stationary opening state of the valve takes place on the fully assembled fuel injection valve, i.e. among other things, that the support disk 26 welded to the valve seat body 18 is welded to the seat support 1 at its holding edge 28. If the static actual quantity of the medium emitted by the valve and measured by means of a measuring vessel 38 does not correspond to the desired, predetermined target quantity, then the support disk 26 is used for the exact adjustment of the stroke of the valve needle 5 in the axial direction in the area between the second weld seam 30 and of the first weld seam 24 is stretched in this way by means of a tool 39 and, if necessary, is plastically deformed until the measured actual medium quantity matches the specified medium target quantity. In this way, the exact setting of the stroke and the static flow quantity of a medium which is emitted during the stationary opening state of the injection valve is carried out in a simple manner on the fully assembled fuel injection valve.

An dem Umfang des Sitzträgers 1 ist an seinem stromabwärtigen Ende eine Schutzkappe 45 angeordnet und mittels einer Rastverbindung 46 mit dem Umfang des Sitzträgers 1 verbunden. Die Schutzkappe 45 liegt mit einem ersten stirnseitigen Radialabschnitt 47 an einer Stirnseite 48 des Sitzträgers 1 an. In der Magnetspule 10 zugewandter Richtung schließen sich an den ersten Radialabschnitt 47 der Schutzkappe 45 zunächst ein axial verlaufender Parallelabschnitt 49 und daran ein radial nach außen weisender zweiter Radialabschnitt 50 an. Ein Dichtring 51 ist in einer Ringnut 53 angeordnet deren Seitenflächen durch eine der Magnetspule 10 zugewandte Stirnseite 54 des zweiten Radialabschnittes 50 der Schutzkappe 45 und durch eine radial nach außen weisende Anlagefläche 55 des Sitzträgers 1 sowie deren Nutgrund 57 durch den Umfang des Sitzträgers 1 gebildet werden.A protective cap 45 is arranged on the circumference of the seat support 1 at its downstream end and is connected to the circumference of the seat support 1 by means of a latching connection 46. The protective cap 45 rests with a first radial section 47 on an end face 48 of the seat support 1. In the direction facing the magnet coil 10, the first radial section 47 of the protective cap 45 is first adjoined by an axially extending parallel section 49 and a second radial section 50 pointing radially outward. A sealing ring 51 is arranged in an annular groove 53, the side surfaces of which are formed by an end face 54 of the second radial section 50 of the protective cap 45 facing the magnetic coil 10 and by a radially outwardly facing contact surface 55 of the seat support 1 and the groove base 57 thereof by the circumference of the seat support 1 .

Der Dichtring 51 dient zur Abdichtung zwischen dem Umfang des Brennstoffeinspritzventils und einer nicht dargestellten Ventilaufnahme beispielsweise der Ansaugleitung der Brennkraftmaschine.The sealing ring 51 serves to seal between the circumference of the fuel injection valve and a valve receptacle, not shown, for example the intake line of the internal combustion engine.

Die Zwischenöffnung 36 stromabwärts der Ventilsitzfläche 32 des Ventilsitzkörpers 18 umgreift einen mittleren Bereich 60 der Lochscheibe 22, in dem die wenigstens eine Abspritzöffnung 37 ist, beispielsweise jedoch vier Abspritzöffnungen 37 ausgebildet sind. Andererseits ist in der Stützscheibe 26 etwa konzentrisch zur Ventillängsachse 2 eine Durchgangsöffnung 61 vorgesehen, die ebenfalls den Bereich 60 der Lochscheibe 22 auf der gegenüberliegenden Seite umgreift. Der durch die Abspritzöffnungen 37 abgespritzte Kraftstoff wird somit durch die Durchgangsöffnung 61 der Stützscheibe 26 hindurchgespritzt. Der mittels der Durchgangsöffnung 61 der Stützscheibe 26 umgriffene Bereich 60 der Lochscheibe 22 kann derart in Strömungsrichtung gewölbt sein, daß er die Form einer Kalotte hat. Die relativ dicke Stützscheibe 26 verhindert mit Ausnahme des Bereiches 60 ein Durchbiegen der Lochscheibe 22 infolge der Druckkraft des Brennstoffes, so daß die Dicke der Lochscheibe 22 geringer als bisher gewählt werden kann, wodurch sich die Aufbereitung des abgespritzten Brennstoffes an den Abspritzöffnungen 37 infolge der Bildung feinster Brennstofftröpfchen verbessert. Die erste Schweißnaht 24 hat einen ausreichend großen radialen Abstand zum Bereich 60 der Lochscheibe 22, um die Ausbildung von Verformungen im Bereich 60 zu vermeiden. Der axiale Abstand zwischen dem Bereich 60 der Lochscheibe 22 und dem unteren Ende des Ventilschließkörpers 7 wird möglichst gering gehalten, um ein möglichst geringes Totvolumen zu bilden.The intermediate opening 36 downstream of the valve seat surface 32 of the valve seat body 18 encompasses a central region 60 of the perforated disk 22, in which the at least one spray opening 37 is, but for example four spray openings 37 are formed. On the other hand, a through-opening 61 is provided in the support disk 26 approximately concentrically to the valve longitudinal axis 2, which likewise encompasses the area 60 of the perforated disk 22 on the opposite side. The fuel sprayed through the spray openings 37 is thus sprayed through the through opening 61 of the support disk 26. The area 60 of the perforated disk 22 which is encompassed by the through-opening 61 of the support disk 26 can be curved in the direction of flow such that it has the shape of a spherical cap. The relatively thick support disk 26, with the exception of the region 60, prevents the perforated disk 22 from bending due to the pressure force of the fuel, so that the thickness of the perforated disk 22 can be selected to be smaller than previously, as a result of which the treatment of the sprayed fuel at the spray openings 37 as a result of the formation finest fuel droplets improved. The first weld 24 has a sufficiently large radial distance from the area 60 of the perforated disk 22 in order to avoid the formation of deformations in the area 60. The axial distance between the area 60 of the perforated disk 22 and the lower end of the valve closing body 7 is kept as small as possible in order to form the smallest possible dead volume.

Claims (4)

  1. Fuel-injection valve for fuel-injection systems of internal-combustion engines, having a movable valve-closing body (7), having a valve-seat body (18) which is connected to a seat carrier (1) and which has a valve-seat face (32) cooperating with the valve-closing body (7), and having a thin metallic perforated disc (22) arranged on the valve-seat body (18) downstream of the valve-seat face (32) and having at least one spray orifice (37), a metallic supporting disc (26) made thicker than the perforated disc (22) being arranged on an end face (25) of the perforated disc (22) facing away from the valve-seat body (18) and the supporting disc (26) having a passage orifice (61) which surrounds a region (60) of the perforated disc (22) having the at least one spray orifice (37) characterised in that, together with the perforated disc (22), the supporting disc (26) is welded to the valve-seat body (18) by means of a continuous welding seam (24), and the supporting disc (26) is additionally sealingly welded at its circumference to the seat carrier (1).
  2. Fuel-injection valve according to Claim 1, characterised in that the supporting disc (26) is made pot-shaped and has a continuous holding edge (28) which extends in the axial direction so as to face away from the valve-seat body (18) and which is sealingly connected at its free end (29) to the wall of a longitudinal orifice (3) of the seat carrier (1).
  3. Fuel-injection valve according to Claim 2, characterised in that the holding edge (28) of the supporting disc (26) is bent outwards towards its free end (29) and at its free end (29) has a larger diameter than the diameter of the longitudinal orifice (3) of the seat carrier (1).
  4. Fuel-injection valve according to Claim 1, characterised in that the region (60) of the perforated disc (22) which is surrounded by the passage orifice (61) of the supporting disc (26) and which contains the at least one spray orifice (37) is arched downstream in the form of a dome.
EP92911364A 1991-07-17 1992-06-10 Fuel injection valve Expired - Lifetime EP0553310B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4123692A DE4123692C2 (en) 1991-07-17 1991-07-17 Fuel injector
DE4123692 1991-07-17
PCT/DE1992/000477 WO1993002285A1 (en) 1991-07-17 1992-06-10 Fuel injection valve

Publications (2)

Publication Number Publication Date
EP0553310A1 EP0553310A1 (en) 1993-08-04
EP0553310B1 true EP0553310B1 (en) 1995-09-13

Family

ID=6436375

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92911364A Expired - Lifetime EP0553310B1 (en) 1991-07-17 1992-06-10 Fuel injection valve

Country Status (7)

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US (1) US5335864A (en)
EP (1) EP0553310B1 (en)
JP (1) JP3107825B2 (en)
KR (1) KR100254305B1 (en)
DE (2) DE4123692C2 (en)
ES (1) ES2078745T3 (en)
WO (1) WO1993002285A1 (en)

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4141930B4 (en) * 1991-12-19 2007-02-08 Robert Bosch Gmbh Electromagnetically actuated injection valve
US5484108A (en) * 1994-03-31 1996-01-16 Siemens Automotive L.P. Fuel injector having novel multiple orifice disk members
WO1996012104A1 (en) * 1994-10-17 1996-04-25 Siemens Automotive Corporation Fuel injector having reduced stream dispersion, especially of an off-axis injected stream
DE4445358A1 (en) * 1994-12-20 1996-06-27 Bosch Gmbh Robert Valve and method of making a valve
DE4446241A1 (en) * 1994-12-23 1996-06-27 Bosch Gmbh Robert Fuel injector
EP0781917A1 (en) * 1995-12-26 1997-07-02 General Motors Corporation Fuel injector valve seat retention
JP3750126B2 (en) * 1996-03-26 2006-03-01 株式会社デンソー Fuel injection valve
DE19625059A1 (en) * 1996-06-22 1998-01-02 Bosch Gmbh Robert Injection valve, in particular for injecting fuel directly into a combustion chamber of an internal combustion engine
DE19724075A1 (en) 1997-06-07 1998-12-10 Bosch Gmbh Robert Method for producing a perforated disk for an injection valve and perforated disk for an injection valve and injection valve
DE19822896A1 (en) 1998-05-22 1999-11-25 Bosch Gmbh Robert Fuel injection valve for internal combustion engine
DE19855568A1 (en) * 1998-12-02 2000-06-08 Bosch Gmbh Robert Fuel injector
DE19856920A1 (en) 1998-12-10 2000-06-15 Bosch Gmbh Robert Fuel injector
DE19935262A1 (en) * 1999-07-27 2001-02-01 Bosch Gmbh Robert Fuel injector
DE10059007A1 (en) * 2000-11-28 2002-05-29 Bosch Gmbh Robert Fuel injector
DE10118164B4 (en) * 2001-04-11 2007-02-08 Robert Bosch Gmbh Fuel injector
WO2004063556A2 (en) * 2003-01-09 2004-07-29 Siemens Vdo Automotive Corporation Spray pattern control with non-angled orifices formed on a dimpled fuel injection metering disc having a sac volume reducer
US6948665B2 (en) * 2003-06-30 2005-09-27 Siemens Vdo Automotive Corporation Fuel injector including an orifice disc, and a method of forming the orifice disc with an asymmetrical punch
US7163159B2 (en) * 2003-07-15 2007-01-16 Siemens Vdo Automotive Corporation Fuel injector including a compound angle orifice disc
US7744020B2 (en) * 2003-07-21 2010-06-29 Continental Automotive Systems Us, Inc. Fuel injector including an orifice disc, and a method of forming the orifice disc including punching and shaving
US7159436B2 (en) * 2004-04-28 2007-01-09 Siemens Vdo Automotive Corporation Asymmetrical punch
US7201329B2 (en) * 2004-04-30 2007-04-10 Siemens Vdo Automotive Corporation Fuel injector including a compound angle orifice disc for adjusting spray targeting
US7086615B2 (en) 2004-05-19 2006-08-08 Siemens Vdo Automotive Corporation Fuel injector including an orifice disc and a method of forming an oblique spiral fuel flow
US20060157595A1 (en) * 2005-01-14 2006-07-20 Peterson William A Jr Fuel injector for high fuel flow rate applications
US20060192036A1 (en) * 2005-02-25 2006-08-31 Joseph J M Fuel injector including a multifaceted dimple for an orifice disc with a reduced footprint of the multifaceted dimple
US20060200988A1 (en) 2005-03-11 2006-09-14 Siemens Vdo Automotive Corporation Sandwich orifice disc
DE602005007856D1 (en) * 2005-04-14 2008-08-14 Siemens Ag Valve body and liquid injector with valve body
JP5161853B2 (en) * 2009-09-29 2013-03-13 三菱電機株式会社 Fuel injection valve
WO2017059237A1 (en) * 2015-09-30 2017-04-06 Nostrum Energy Pte. Ltd. Spray targeting and plume shaping for colliding jet atomizer with asymmetrical radial distribution

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1589247A (en) * 1926-01-07 1926-06-15 Super Diesel Tractor Corp Reed-type spray nozzle
US4030668A (en) * 1976-06-17 1977-06-21 The Bendix Corporation Electromagnetically operated fuel injection valve
US4934653A (en) * 1987-12-23 1990-06-19 Siemens-Bendix Automotive Electronics L.P. Multi-stream thin edge orifice disks for valves
DE3841142C2 (en) * 1988-12-07 1994-09-29 Bosch Gmbh Robert Injector
US4971254A (en) * 1989-11-28 1990-11-20 Siemens-Bendix Automotive Electronics L.P. Thin orifice swirl injector nozzle

Also Published As

Publication number Publication date
ES2078745T3 (en) 1995-12-16
KR930702610A (en) 1993-09-09
DE59203684D1 (en) 1995-10-19
DE4123692C2 (en) 1995-01-26
KR100254305B1 (en) 2000-06-01
JP3107825B2 (en) 2000-11-13
EP0553310A1 (en) 1993-08-04
WO1993002285A1 (en) 1993-02-04
US5335864A (en) 1994-08-09
DE4123692A1 (en) 1993-01-21
JPH06501087A (en) 1994-01-27

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