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EP0853725B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP0853725B1
EP0853725B1 EP97918045A EP97918045A EP0853725B1 EP 0853725 B1 EP0853725 B1 EP 0853725B1 EP 97918045 A EP97918045 A EP 97918045A EP 97918045 A EP97918045 A EP 97918045A EP 0853725 B1 EP0853725 B1 EP 0853725B1
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EP
European Patent Office
Prior art keywords
valve seat
valve
seat body
opening
fuel injection
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP97918045A
Other languages
German (de)
French (fr)
Other versions
EP0853725A1 (en
Inventor
Hans-Dieter Schmid
Peter Romann
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0853725A1 publication Critical patent/EP0853725A1/en
Application granted granted Critical
Publication of EP0853725B1 publication Critical patent/EP0853725B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M51/0682—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 the body being hollow and its interior communicating with the fuel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1853—Orifice plates

Definitions

  • the invention is based on a fuel injector according to the genus of claim 1. It's already a Fuel injector known (DE 42 21 185 A1), in which after finishing in the valve seat body provided valve seat on an end face of the Valve seat body is welded an orifice plate. This creates stresses in the valve seat body, which among other things, the roundness of the valve seat surface deteriorate, causing the tightness of the Fuel injector in the closed state is influenced and unwanted from the closed Fuel injector fuel in small quantities leaks.
  • the fuel injector according to the invention with the characteristic features of claim 1 has in contrast the advantage that it is avoided in a simple manner, that the weld of the spray plate to the Valve seat body the roundness of the valve seat surface deteriorates, causing a when the valve is closed Leakage reduction is achieved.
  • the Valve seat surface Through the groove in the front of the valve seat body is the Valve seat surface mechanically and thermally decoupled and is thus no tension caused by welding exposed. Deformations caused by heat Valve seat bodies are from the area of the Valve seat body in which the weld he follows.
  • valve housing Provide longitudinal opening into which the valve seat body is inserted, and in the area of the lower end of the Valve seat body in the direction away from the valve seat body Extension opening with a larger cross section than that Provide longitudinal opening with the wall of the Spray plate connected by a second weld is.
  • Embodiments of the invention are in the drawing shown in simplified form and in the following Description explained in more detail.
  • 1 shows a first Embodiment of the invention using a schematic fuel injector shown in partial representation
  • Figure 2 shows a second embodiment of the invention partial representation of a fuel injector.
  • FIG. 1 shows an example of what is otherwise already known Fuel injection valve for fuel injection systems from mixture-compression-ignition internal combustion engines partially shown, as the first embodiment is designed according to the invention.
  • the fuel injector has a tubular valve housing 1 in which is concentric a longitudinal opening 3 is formed in a longitudinal valve axis 2. In the longitudinal opening 3 is a z.
  • tubular valve needle 5 arranged at its downstream end 6 with a spherical valve closing body 7, on the circumference for example five circular flats 8 are provided, connected is.
  • the fuel injector is actuated in known way, for example, electromagnetic.
  • electromagnetic For axial Movement of the valve needle 5 and thus to open against the Spring force of a return spring (not shown) or Closing the fuel injector serves an indicated electromagnetic circuit with a magnetic coil 10, an armature 11 and a core 12.
  • the anchor 11 is with the Valve closing body 7 facing away from the end of the valve needle 5 e.g. B. connected and welded by means of a laser the core 12 aligned.
  • valve seat body 16 To guide the valve closing body 7 during the axial movement serves a guide opening 15 of a valve seat body 16.
  • the circumference of the valve seat body 16 has one slightly smaller diameter than the longitudinal opening 3 of the Valve housing 1.
  • the valve closing body 7 Lower end face 17 facing away is valve seat body 16 provided with a circumferential groove 18.
  • a bottom part 20 of a z. B. cup-shaped spray plate 21 is located its upper end face 19 on the lower end face 17 of Valve seat body 16 and is concentric and fixed with this connected by a first weld 31.
  • Central area 24 has the bottom part 20 of the Spray plate 21 at least one spray hole 25, for example four formed by eroding or stamping Spray holes 25 on.
  • a circumferential holding edge 26 which is in extends axially away from the valve seat body 16 and is bent conically outwards until its end 27. Since the Circumferential diameter of the valve seat body 16 is smaller than that Diameter of the longitudinal opening 3 of the valve housing 1 is only between the longitudinal opening 3 and the slightly conical externally curved holding edge 26 of the spray plate 21 a radial pressure.
  • the insertion depth of the valve seat body 16 and cup-shaped Spray plate 21 existing valve seat part in the Longitudinal opening 3 determines the default stroke Valve needle 5, since the one end position of the valve needle 5 at non-excited solenoid 10 by the system of Valve closing body 7 on a valve seat surface 29 of the Valve seat body 16 is fixed.
  • the other end position of the Valve needle 5 is, for example, when solenoid 10 is excited fixed by the installation of the anchor 11 on the core 12.
  • the Path between these two end positions of the valve needle 5 thus represents the hub.
  • the holding edge 26 of the spray disk 21 tightly and firmly connected to the wall of the longitudinal opening 3.
  • a circumferential second weld seam 30 intended.
  • a welding edge 33 is formed, on the of the first circumferential weld 31 the bottom part 20 tightly the valve seat body 16 is connected.
  • valve seat body 16 and spray plate 21 and of Spray plate 21 and valve housing 1 A tight connection of valve seat body 16 and spray plate 21 and of Spray plate 21 and valve housing 1 is required the fuel is not between the longitudinal opening 3 of the Valve housing 1 and the circumference of the valve seat body 16 through to the spray holes 25 or between the Longitudinal opening 3 of the valve housing 1 and the retaining edge 26 of the pot-shaped spray perforated disk 21 directly into a Air intake line of the internal combustion engine can flow.
  • the spherical valve closing body 7 acts with the in Direction of flow tapering in the shape of a truncated cone Valve seat surface 29 of the valve seat body 16 together, which in axial direction between the guide opening 15 and one Outflow opening 32 in the lower end face 17 of the Valve seat body 16 is formed.
  • the valve seat body 16 has a valve seat body opening facing solenoid 10 34 on, which has a larger diameter than that Diameter of the guide opening 15 of the valve seat body 16.
  • the central area 24 of the bottom part 20 of the Spray plate 21 is downstream, for example Direction, ie in the direction pointing away from the valve closing body 7 Direction bent out of the plane of the bottom part 20, so that there is a bulge 36 in the central area.
  • the exact stroke setting for the valve closing body 7 takes place by bending the spray orifice plate 21 between the welds 30, 31 in the axial direction.
  • the circumferential groove 18 on the lower end face 17 of the Valve seat body 16 causes that when attaching the first weld 31 on the spray plate 21 and the Welding edge 33 throttling the heat transfer Valve seat surface 29 takes place so that tensions as a result the thermal and mechanical load only in Welding edge 33 occur and from the valve seat surface 29 in the same way as mechanical stresses are kept away become.
  • the roundness of the valve seat surface 29 thus remains which is a prerequisite for the tightness of the Forms fuel injector in the closed state, receive.
  • the thermal and mechanical decoupling of the Valve seat 29 from the first weld 31 is then especially large when the first weld 31 is nearby the circumference of the valve seat body 16 and the radial
  • the distance between the groove 18 and the first weld 31 is smaller than to the outflow opening 32, so that there is a possible narrow welding edge 33 results.
  • Deviating from the embodiment according to Figure 1 is in the embodiment of Figure 2 in Area of the lower end face 17 of the valve seat body 16 in the direction of the valve closing body 7 away from the Extension opening 40 adjoining longitudinal opening 3 provided that has a larger cross section than that Longitudinal opening 3.
  • the spray perforated disk 21 extends with their holding edge 26 up to the wall of the expansion opening 40 and is through with the wall of the extension opening 40 the circumferential second weld 30 is tightly connected.
  • the air ring gap 41 has, for example, a radial width of approximately 0.2 mm and an axial extension of, for example, about 1 mm.
  • the groove 21 has, for example, a radial width of approximately 0.6 mm and a depth of about 0.5 mm.

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

Description

Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Anspruchs 1. Es ist schon ein Brennstoffeinspritzventil bekannt (DE 42 21 185 A1), bei dem nach der Endbearbeitung der in dem Ventilsitzkörper vorgesehenen Ventilsitzfläche auf eine Stirnfläche des Ventilsitzkörpers eine Spritzlochscheibe geschweißt wird. Dabei entstehen Spannungen in dem Ventilsitzkörper, die unter anderem die Rundheit der Ventilsitzfläche verschlechtern, wodurch die Dichtheit des Brennstoffeinspritzventils im geschlossenen Zustand beeinflußt wird und ungewollterweise aus dem geschlossenen Brennstoffeinspritzventil Brennstoff in geringen Mengen ausleckt.The invention is based on a fuel injector according to the genus of claim 1. It's already a Fuel injector known (DE 42 21 185 A1), in which after finishing in the valve seat body provided valve seat on an end face of the Valve seat body is welded an orifice plate. This creates stresses in the valve seat body, which among other things, the roundness of the valve seat surface deteriorate, causing the tightness of the Fuel injector in the closed state is influenced and unwanted from the closed Fuel injector fuel in small quantities leaks.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Anspruches 1 hat demgegenüber den Vorteil, daß auf einfache Art und Weise vermieden wird, daß die Schweißung der Spritzlochscheibe an den Ventilsitzkörper die Rundheit der Ventilsitzfläche verschlechtert, wodurch bei geschlossenem Ventil eine Verringerung der Leckmenge erzielt wird. Durch die Nut in der Stirnseite des Ventilsitzkörpers wird die Ventilsitzfläche mechanisch und thermisch entkoppelt und ist damit keinen durch das Schweißen verursachten Spannungen ausgesetzt. Thermisch verursachte Verformungen am Ventilsitzkörper werden von dem Bereich des Ventilsitzkörpers aufgenommen, in dem die Schweißung erfolgt.The fuel injector according to the invention with the characteristic features of claim 1 has in contrast the advantage that it is avoided in a simple manner, that the weld of the spray plate to the Valve seat body the roundness of the valve seat surface deteriorates, causing a when the valve is closed Leakage reduction is achieved. Through the groove in the front of the valve seat body is the Valve seat surface mechanically and thermally decoupled and is thus no tension caused by welding exposed. Deformations caused by heat Valve seat bodies are from the area of the Valve seat body in which the weld he follows.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegebenen Brennstoffeinspritzventiles möglich.By the measures listed in the subclaims advantageous further developments and improvements of the Claim 1 specified fuel injector possible.

Vorteilhaft ist es, die erste Schweißnaht in der Nähe des Umfanges des Ventilsitzkörpers vorzusehen und den radialen Abstand der Nut zur ersten Schweißnaht geringer als zur Ausströmöffnung zu halten. Hierdurch ergibt sich ein großer Abstand der Schweißnaht zur Ventilsitzfläche und damit die geringstmögliche thermische Belastung der Ventilsitzfläche.It is advantageous to place the first weld near the Provide circumference of the valve seat body and the radial The distance between the groove and the first weld seam is smaller than the Keep outflow opening. This results in a big one Distance of the weld seam to the valve seat surface and thus the lowest possible thermal load on the valve seat surface.

Vorteilhaft ist es ebenfalls, das Ventilgehäuse mit einer Längsöffnung zu versehen, in die der Ventilsitzkörper eingeschoben ist, und im Bereich der unteren Stirnseite des Ventilsitzkörpers in Richtung vom Ventilsitzkörper weg eine Erweiterungsöffnung mit größerem Querschnitt als die Längsöffnung vorzusehen, mit deren Wandung die Spritzlochscheibe durch eine zweite Schweißnaht verbunden ist. Hierdurch wird erreicht, daß auch die Befestigung der Spritzlochscheibe im Ventilgehäuse mittels einer zweiten Schweißnaht zu keiner unerwünschten Verformung der Ventilsitzfläche durch thermische Belastung führt. Außerdem wird hierdurch eine Vergrößerung des radialen Abstandes der Schweißnähte erreicht, so daß eine leichtere Verbiegung der Spritzlochscheibe in diesem Bereich zur Ventilhubeinstellung möglich ist.It is also advantageous to use a valve housing Provide longitudinal opening into which the valve seat body is inserted, and in the area of the lower end of the Valve seat body in the direction away from the valve seat body Extension opening with a larger cross section than that Provide longitudinal opening with the wall of the Spray plate connected by a second weld is. This ensures that the attachment of the Orifice plate in the valve body using a second one No unwanted deformation of the weld Valve seat surface due to thermal stress. Moreover this will increase the radial distance of the Welding seams reached, so that an easier bending of the Spray plate in this area for valve stroke adjustment is possible.

Zeichnungdrawing

Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ein erstes Ausführungsbeispiel der Erfindung anhand eines schematisch in Teildarstellung gezeigten Brennstoffeinspritzventiles, Figur 2 ein zweites Ausführungsbeispiel der Erfindung mit teilweiser Darstellung eines Brennstoffeinspritzventiles.Embodiments of the invention are in the drawing shown in simplified form and in the following Description explained in more detail. 1 shows a first Embodiment of the invention using a schematic fuel injector shown in partial representation, Figure 2 shows a second embodiment of the invention partial representation of a fuel injector.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In der Figur 1 ist ein Beispiel eines sonst bereits bekannten Brennstoffeinspritzventils für Brennstoffeinspritzanlagen von gemischverdichtenden fremdgezündeten Brennkraftmaschinen teilweise dargestellt, das als erstes Ausführungsbeispiel erfindungsgemäß ausgebildet ist. Das Brennstoffeinspritzventil hat ein rohrförmiges Ventilgehäuse 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 kugelförmigen Ventilschließkörper 7, an dessen Umfang beispielsweise fünf kreisförmige Abflachungen 8 vorgesehen sind, verbunden ist.FIG. 1 shows an example of what is otherwise already known Fuel injection valve for fuel injection systems from mixture-compression-ignition internal combustion engines partially shown, as the first embodiment is designed according to the invention. The fuel injector has a tubular valve housing 1 in which is concentric a longitudinal opening 3 is formed in a longitudinal valve axis 2. In the longitudinal opening 3 is a z. B. tubular valve needle 5 arranged at its downstream end 6 with a spherical valve closing body 7, on the circumference for example five circular flats 8 are provided, connected is.

Die Betätigung des Brennstoffeinspritzventils erfolgt in bekannter Weise beispielsweise elektromagnetisch. Zur axialen Bewegung der Ventilnadel 5 und damit zum Öffnen entgegen der Federkraft einer nicht dargestellten Rückstellfeder 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 durch z. B. eine Schweißnaht mittels eines Lasers verbunden und auf den Kern 12 ausgerichtet.The fuel injector is actuated in known way, for example, electromagnetic. For axial Movement of the valve needle 5 and thus to open against the Spring force of a return spring (not shown) or Closing the fuel injector serves an indicated electromagnetic circuit with a magnetic coil 10, an armature 11 and a core 12. The anchor 11 is with the Valve closing body 7 facing away from the end of the valve needle 5 e.g. B. connected and welded by means of a laser the core 12 aligned.

Zur Führung des Ventilschließkörpers 7 während der Axialbewegung dient eine Führungsöffnung 15 eines Ventilsitzkörpers 16. In das stromabwärts liegende, dem Kern 12 abgewandte Ende des Ventilgehäuses 1 ist in die konzentrisch zur Ventillängsachse 2 verlaufende Längsöffnung 3 der zylinderförmige Ventilsitzkörper 16 eingeschoben. Der Umfang des Ventilsitzkörpers 16 weist einen geringfügig kleineren Durchmesser auf als die Längsöffnung 3 des Ventilgehäuses 1. An seiner einen, dem Ventilschließkörper 7 abgewandten, unteren Stirnseite 17 ist der Ventilsitzkörper 16 mit einer umlaufenden Nut 18 versehen. Ein Bodenteil 20 einer z. B. topfförmig ausgebildeten Spritzlochscheibe 21 liegt mit seiner oberen Stirnseite 19 an der unteren Stirnseite 17 des Ventilsitzkörpers 16 an und ist konzentrisch und fest mit dieser mittels einer ersten Schweißnaht 31 verbunden. In seinem zentralen Bereich 24 weist das Bodenteil 20 der Spritzlochscheibe 21 wenigstens ein Abspritzloch 25, beispielsweise vier durch Erodieren oder Stanzen ausgeformte Abspritzlöcher 25 auf.To guide the valve closing body 7 during the axial movement serves a guide opening 15 of a valve seat body 16. In the downstream end of the core 12 facing away from the core Valve housing 1 is concentric with the valve longitudinal axis 2 extending longitudinal opening 3 of the cylindrical valve seat body 16 inserted. The circumference of the valve seat body 16 has one slightly smaller diameter than the longitudinal opening 3 of the Valve housing 1. On its one, the valve closing body 7 Lower end face 17 facing away is valve seat body 16 provided with a circumferential groove 18. A bottom part 20 of a z. B. cup-shaped spray plate 21 is located its upper end face 19 on the lower end face 17 of Valve seat body 16 and is concentric and fixed with this connected by a first weld 31. In his Central area 24 has the bottom part 20 of the Spray plate 21 at least one spray hole 25, for example four formed by eroding or stamping Spray holes 25 on.

An das Bodenteil 20 der topfförmigen Spritzlochscheibe 21 schließt sich ein umlaufender Halterand 26 an, der sich in axialer Richtung dem Ventilsitzkörper 16 abgewandt erstreckt und bis zu seinem Ende 27 hin konisch nach außen gebogen ist. Da der Umfangsdurchmesser des Ventilsitzkörpers 16 kleiner als der Durchmesser der Längsöffnung 3 des Ventilgehäuses 1 ist, liegt nur zwischen der Längsöffnung 3 und dem leicht konisch nach außen gebogenen Halterand 26 der Spritzlochscheibe 21 eine radiale Pressung vor.On the bottom part 20 of the cup-shaped spray perforated disk 21 is followed by a circumferential holding edge 26, which is in extends axially away from the valve seat body 16 and is bent conically outwards until its end 27. Since the Circumferential diameter of the valve seat body 16 is smaller than that Diameter of the longitudinal opening 3 of the valve housing 1 is only between the longitudinal opening 3 and the slightly conical externally curved holding edge 26 of the spray plate 21 a radial pressure.

Die Einschubtiefe des aus Ventilsitzkörper 16 und topfförmiger Spritzlochscheibe 21 bestehenden Ventilsitzteils in die Längsöffnung 3 bestimmt die Voreinstellung des Hubes der Ventilnadel 5, da die eine Endstellung der Ventilnadel 5 bei nicht erregter Magnetspule 10 durch die Anlage des Ventilschließkörpers 7 an einer Ventilsitzfläche 29 des Ventilsitzkörpers 16 festgelegt ist. Die andere Endstellung der Ventilnadel 5 wird bei erregter Magnetspule 10 beispielsweise durch die Anlage des Ankers 11 an dem Kern 12 festgelegt. Der Weg zwischen diesen beiden Endstellungen der Ventilnadel 5 stellt somit den Hub dar.The insertion depth of the valve seat body 16 and cup-shaped Spray plate 21 existing valve seat part in the Longitudinal opening 3 determines the default stroke Valve needle 5, since the one end position of the valve needle 5 at non-excited solenoid 10 by the system of Valve closing body 7 on a valve seat surface 29 of the Valve seat body 16 is fixed. The other end position of the Valve needle 5 is, for example, when solenoid 10 is excited fixed by the installation of the anchor 11 on the core 12. The Path between these two end positions of the valve needle 5 thus represents the hub.

An seinem Ende 27 ist der Halterand 26 der Spritzlochscheibe 21 mit der Wandung der Längsöffnung 3 dicht und fest verbunden. Hierfür ist zwischen dem Ende 27 des Halterandes 26 und der Wandung der Längsöffnung 3 eine umlaufende zweite Schweißnaht 30 vorgesehen. Außerhalb des zentralen Bereiches 24 zwischen der Nut 18 und dem Umfang des Ventilsitzkörpers 16 ist an der unteren Stirnseite 17 ein Schweißrand 33 gebildet, an dem mit der ersten umlaufenden Schweißnaht 31 das Bodenteil 20 dicht mit dem Ventilsitzkörper 16 verbunden ist. Eine dichte Verbindung von Ventilsitzkörper 16 und Spritzlochscheibe 21 sowie von Spritzlochscheibe 21 und Ventilgehäuse 1 ist erforderlich, damit der Brennstoff nicht zwischen der Längsöffnung 3 des Ventilgehäuses 1 und dem Umfang des Ventilsitzkörpers 16 hindurch zu den Abspritzlöchern 25 oder zwischen der Längsöffnung 3 des Ventilgehäuses 1 und dem Halterand 26 der topfförmigen Spritzlochscheibe 21 hindurch unmittelbar in eine Luftansaugleitung der Brennkraftmaschine strömen kann.At its end 27 is the holding edge 26 of the spray disk 21 tightly and firmly connected to the wall of the longitudinal opening 3. For this is between the end 27 of the holding edge 26 and the Wall of the longitudinal opening 3 a circumferential second weld seam 30 intended. Outside the central area 24 between the Groove 18 and the circumference of the valve seat body 16 is on the lower end face 17, a welding edge 33 is formed, on the of the first circumferential weld 31 the bottom part 20 tightly the valve seat body 16 is connected. A tight connection of valve seat body 16 and spray plate 21 and of Spray plate 21 and valve housing 1 is required the fuel is not between the longitudinal opening 3 of the Valve housing 1 and the circumference of the valve seat body 16 through to the spray holes 25 or between the Longitudinal opening 3 of the valve housing 1 and the retaining edge 26 of the pot-shaped spray perforated disk 21 directly into a Air intake line of the internal combustion engine can flow.

Der kugelförmige Ventilschließkörper 7 wirkt mit der sich in Strömungsrichtung kegelstumpfförmig verjüngenden Ventilsitzfläche 29 des Ventilsitzkörpers 16 zusammen, die in axialer Richtung zwischen der Führungsöffnung 15 und einer Ausströmöffnung 32 in der unteren Stirnseite 17 des Ventilsitzkörpers 16 ausgebildet ist. Der Ventilsitzkörper 16 weist der Magnetspule 10 zugewandt eine Ventilsitzkörperöffnung 34 auf, die einen größeren Durchmesser besitzt als den Durchmesser der Führungsöffnung 15 des Ventilsitzkörpers 16.The spherical valve closing body 7 acts with the in Direction of flow tapering in the shape of a truncated cone Valve seat surface 29 of the valve seat body 16 together, which in axial direction between the guide opening 15 and one Outflow opening 32 in the lower end face 17 of the Valve seat body 16 is formed. The valve seat body 16 has a valve seat body opening facing solenoid 10 34 on, which has a larger diameter than that Diameter of the guide opening 15 of the valve seat body 16.

Zur exakten Führung des Ventilschließkörpers 7 und damit der Ventilnadel 5 während der Axialbewegung ist der Durchmesser der Führungsöffnung 15 so ausgebildet, daß der kugelförmige Ventilschließkörper 7 außerhalb seiner Abflachungen 8 die Führungsöffnung 15 mit geringem radialem Abstand durchragt. Der zentrale Bereich 24 des Bodenteils 20 der Spritzlochscheibe 21 ist beispielsweise in stromabwärtiger Richtung, also in von dem Ventilschließkörper 7 wegweisender Richtung aus der Ebene des Bodenteils 20 herausgebogen, so daß sich eine Ausbuchtung 36 im zentralen Bereich ergibt. Zwischen der Stirnseite 17 des Ventilschließkörpers 7, der Ventilsitzfläche 29 und der Wandung der Ausbuchtung 36 bzw. oberen Stirnseite 19 der Spritzlochscheibe 21 wird ein Sammelraum 37 gebildet, in den bei von der Ventilsitzfläche 29 abgehobenem Ventilschließkörper 7 der Brennstoff zunächst gelangt, bevor er durch die Abspritzlöcher 25 zugemessen und in die Luftansaugleitung der Brennkraftmaschine abgespritzt wird.For exact guidance of the valve closing body 7 and thus the Valve needle 5 during the axial movement is the diameter the guide opening 15 formed so that the spherical Valve closing body 7 outside of its flattenings 8 Passing through guide opening 15 with a small radial distance. The central area 24 of the bottom part 20 of the Spray plate 21 is downstream, for example Direction, ie in the direction pointing away from the valve closing body 7 Direction bent out of the plane of the bottom part 20, so that there is a bulge 36 in the central area. Between the end face 17 of the valve closing body 7, the Valve seat surface 29 and the wall of the bulge 36 or upper end face 19 of the spray orifice plate 21 is a Collection space 37 is formed, in the case of the valve seat surface 29 lifted valve closing body 7 the fuel initially arrives before it is metered through the spray holes 25 and hosed into the air intake line of the internal combustion engine becomes.

Die genaue Hubeinstellung für den Ventilschließkörper 7 erfolgt durch Verbiegen der Spritzlochscheibe 21 zwischen den Schweißnähten 30, 31 in axialer Richtung.The exact stroke setting for the valve closing body 7 takes place by bending the spray orifice plate 21 between the welds 30, 31 in the axial direction.

Die umlaufende Nut 18 an der unteren Stirnseite 17 des Ventilsitzkörpers 16 bewirkt, daß bei der Anbringung der ersten Schweißnaht 31 an der Spritzlochscheibe 21 und dem Schweißrand 33 eine Drosselung des Wärmeüberganges zur Ventilsitzfläche 29 hin erfolgt, so daß Spannungen infolge der thermischen und mechanischen Belastung nur im Schweißrand 33 auftreten und von der Ventilsitzfläche 29 in gleicher Weise wie mechanische Spannungen ferngehalten werden. Damit bleibt die Rundheit der Ventilsitzfläche 29, die eine Voraussetzung für die Dichtheit des Brennstoffeinspritzventiles im geschlossenen Zustand bildet, erhalten. Die thermische und mechanische Abkopplung der Ventilsitzfläche 29 von der ersten Schweißnaht 31 ist dann besonders groß, wenn die erste Schweißnaht 31 in der Nähe des Umfanges des Ventilsitzkörpers 16 liegt und der radiale Abstand der Nut 18 zur ersten Schweißnaht 31 geringer ist als zur Ausströmöffnung 32, so daß sich ein möglichst schmaler Schweißrand 33 ergibt.The circumferential groove 18 on the lower end face 17 of the Valve seat body 16 causes that when attaching the first weld 31 on the spray plate 21 and the Welding edge 33 throttling the heat transfer Valve seat surface 29 takes place so that tensions as a result the thermal and mechanical load only in Welding edge 33 occur and from the valve seat surface 29 in the same way as mechanical stresses are kept away become. The roundness of the valve seat surface 29 thus remains which is a prerequisite for the tightness of the Forms fuel injector in the closed state, receive. The thermal and mechanical decoupling of the Valve seat 29 from the first weld 31 is then especially large when the first weld 31 is nearby the circumference of the valve seat body 16 and the radial The distance between the groove 18 and the first weld 31 is smaller than to the outflow opening 32, so that there is a possible narrow welding edge 33 results.

Bei dem Ausführungsbeispiel nach Figur 2 sind die gegenüber dem Ausführungsbeispiel nach Figur 1 gleichbleibenden und gleichwirkenden Teile durch die gleichen Bezugszeichen gekennzeichnet. Abweichend von dem Ausführungsbeispiel nach Figur 1 ist bei dem Ausführungsbeispiel nach Figur 2 im Bereich der unteren Stirnseite 17 des Ventilsitzkörpers 16 in Richtung vom Ventilschließkörper 7 weg eine sich an die Längsöffnung 3 anschließende Erweiterungsöffnung 40 vorgesehen, die einen größeren Querschnitt hat, als die Längsöffnung 3. Die Spritzlochscheibe 21 erstreckt sich mit ihrem Halterand 26 bis zur Wandung der Erweiterungsöffnung 40 und ist mit der Wandung der Erweiterungsöffnung 40 durch die umlaufende zweite Schweißnaht 30 dicht verbunden. Hierdurch ergibt sich zwischen der Spritzlochscheibe 21, dem Umfang des Ventilsitzkörpers 16 und der Wandung der Erweiterungsöffnung 40 in diesem Bereich ein sich bis zum Übergang in die Längsöffnung 3 erstreckender Luftringspalt 41, der bewirkt, daß bei der Anbringung der zweiten Schweißnaht 30 ein Wärmeübergang vom Ventilgehäuse 1 auf den Ventilsitzkörper 16 nicht schon im Bereich der unteren Stirnseite 17 erfolgt, sondern erst nach einer um die axiale Erstreckung des Luftringspaltes 41 in Richtung der Ventillängsachse 2 verlängerten, die Wärmeleitung drosselnden Wärmeleitstrecke. Außerdem wird hierdurch der radiale Abstand zwischen den Schweißnähten 30, 31 vergrößert, so daß die Verbiegung der Spritzlochscheibe 21 in diesem Bereich zur Einstellung des Hubes des Ventilschließkörpers 7 erleichtert wird. Der Luftringspalt 41 hat beispielsweise eine radiale Breite von etwa 0,2 mm und eine axiale Erstreckung von beispielsweise etwa 1 mm. Die Nut 21 hat beispielsweise eine radiale Breite von etwa 0,6 mm und eine Tiefe von etwa 0,5 mm.In the exemplary embodiment according to FIG. 2, these are opposite the embodiment of Figure 1 constant and equivalent parts by the same reference numerals characterized. Deviating from the embodiment according to Figure 1 is in the embodiment of Figure 2 in Area of the lower end face 17 of the valve seat body 16 in the direction of the valve closing body 7 away from the Extension opening 40 adjoining longitudinal opening 3 provided that has a larger cross section than that Longitudinal opening 3. The spray perforated disk 21 extends with their holding edge 26 up to the wall of the expansion opening 40 and is through with the wall of the extension opening 40 the circumferential second weld 30 is tightly connected. This results in between the orifice plate 21, the Scope of the valve seat body 16 and the wall of the Extension opening 40 in this area up to Transition into the longitudinal opening 3 extending air ring gap 41, which causes the attachment of the second Weld 30 a heat transfer from the valve housing 1 to the Valve seat body 16 is not already in the lower area End face 17 takes place, but only after one around the axial Extension of the air ring gap 41 in the direction of Longitudinal valve axis 2 extended the heat conduction throttling heat conduction path. It will also make the radial distance between the weld seams 30, 31 enlarged so that the deflection of the spray plate 21st in this area to adjust the stroke of the Valve closing body 7 is facilitated. The air ring gap 41 has, for example, a radial width of approximately 0.2 mm and an axial extension of, for example, about 1 mm. The groove 21 has, for example, a radial width of approximately 0.6 mm and a depth of about 0.5 mm.

Claims (4)

  1. Fuel injection valve for internal combustion engines, having a valve housing, having a moveable valve closing body (7) which interacts with a valve seat surface which is formed on a valve seat body (16) and, at its downstream end, merges into an outflow opening (32), the outflow opening (32) extending as far as a lower end side of the valve seat body (16), and having a spray orifice plate (21) which is fastened to the lower endside of the valve seat body by a first weld seam and in which at least one spray hole is provided, characterized in that a groove (18) surrounding the outflow opening (32) at a radial distance is provided between the outflow opening (32) and the first weld seam (31) in the lower end side (17) of the valve seat body (16).
  2. Fuel injection valve according to Claim 1, characterized in that the first weld seam (31) lies in the vicinity of the circumference of the valve seat body (16) and the radial distance of the groove (18) from the first weld seam (31) is less than from the outflow opening (32).
  3. Fuel injection valve according to Claim 1 or 2, characterized in that the valve housing (1) has a longitudinal opening (3), into which the valve seat body (16) is inserted, and, in the region of the lower end side (17) of the valve seat body (16), an extension opening (40) having a relatively large cross section adjoins the longitudinal opening (3) in the direction away from the valve closing body (7).
  4. Fuel injection valve according to Claim 3, characterized in that the spray orifice plate (21) is connected to the wall of the extension opening (40) by a second weld seam (30).
EP97918045A 1996-07-05 1997-03-21 Fuel injection valve Expired - Lifetime EP0853725B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19627090 1996-07-05
DE19627090A DE19627090A1 (en) 1996-07-05 1996-07-05 Fuel injector
PCT/DE1997/000577 WO1998001665A1 (en) 1996-07-05 1997-03-21 Fuel injection valve

Publications (2)

Publication Number Publication Date
EP0853725A1 EP0853725A1 (en) 1998-07-22
EP0853725B1 true EP0853725B1 (en) 2001-08-29

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP97918045A Expired - Lifetime EP0853725B1 (en) 1996-07-05 1997-03-21 Fuel injection valve

Country Status (8)

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EP (1) EP0853725B1 (en)
JP (1) JPH11512167A (en)
KR (1) KR19990028585A (en)
BR (1) BR9706538A (en)
DE (2) DE19627090A1 (en)
ES (1) ES2163754T3 (en)
RU (1) RU2173788C2 (en)
WO (1) WO1998001665A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6378792B2 (en) * 1998-04-10 2002-04-30 Aisan Kogyo Kabushiki Kaisha Fuel injection nozzle
DE10118164B4 (en) * 2001-04-11 2007-02-08 Robert Bosch Gmbh Fuel injector
JP4077004B2 (en) 2005-10-27 2008-04-16 三菱電機株式会社 Fuel injection valve device
JP5921240B2 (en) * 2012-02-10 2016-05-24 日立オートモティブシステムズ株式会社 Fuel injection valve

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4026721A1 (en) * 1990-08-24 1992-02-27 Bosch Gmbh Robert INJECTION VALVE AND METHOD FOR PRODUCING AN INJECTION VALVE

Also Published As

Publication number Publication date
DE19627090A1 (en) 1998-01-08
BR9706538A (en) 1999-07-20
WO1998001665A1 (en) 1998-01-15
EP0853725A1 (en) 1998-07-22
RU2173788C2 (en) 2001-09-20
ES2163754T3 (en) 2002-02-01
DE59704441D1 (en) 2001-10-04
JPH11512167A (en) 1999-10-19
KR19990028585A (en) 1999-04-15

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