EP0853725A1 - Fuel injection valve - Google Patents

Fuel injection valve

Info

Publication number
EP0853725A1
EP0853725A1 EP97918045A EP97918045A EP0853725A1 EP 0853725 A1 EP0853725 A1 EP 0853725A1 EP 97918045 A EP97918045 A EP 97918045A EP 97918045 A EP97918045 A EP 97918045A EP 0853725 A1 EP0853725 A1 EP 0853725A1
Authority
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.)
Granted
Application number
EP97918045A
Other languages
German (de)
French (fr)
Other versions
EP0853725B1 (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
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 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

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
    • 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 preamble of claim 1.
  • a fuel injector is already known (DE 42 21 185 AI), in which, after the valve seat surface provided in the valve seat body has been finished, an injection orifice plate is welded onto an end face of the valve seat body. This creates tensions in the valve seat body, which among other things worsen the roundness of the valve seat surface, which causes the tightness of the
  • Fuel injector is affected in the closed state and unintentionally leaks fuel in small amounts from the closed fuel injector.
  • the fuel injector according to the invention with the characterizing features of claim 1 has the advantage that it is avoided in a simple manner that the welding of the spray disk to the valve seat body the roundness of the valve seat surface deteriorates, which results in a reduction in the amount of leakage when the valve is closed.
  • the groove in the end face of the valve seat body mechanically and thermally decouples the valve seat surface and is therefore not exposed to any stresses caused by welding. Deformations on the valve seat body caused by heat are absorbed by the area of the valve seat body in which the welding takes place.
  • valve housing with a longitudinal opening, into which the valve seat body is inserted, and in the region of the lower end face of the valve seat body in the direction away from the valve seat body to provide an expansion opening with a larger cross section than the longitudinal opening, with the wall of which the spray-perforated disk is penetrated by a second weld is connected.
  • This ensures that the attachment of the spray hole disk in the valve housing by means of a second weld seam does not lead to any undesired deformation of the valve seat surface due to thermal stress.
  • this increases the radial spacing of the weld seams, so that easier bending of the Spray plate in this area for valve stroke adjustment is possible.
  • FIG. 1 shows a first exemplary embodiment of the invention on the basis of a fuel injector shown schematically in partial representation
  • FIG. 2 shows a second exemplary embodiment of the invention with a partial representation of a fuel injector.
  • FIG. 1 partially shows an example of an otherwise already known fuel injection valve for fuel injection systems of mixture-compressing spark-ignition internal combustion engines, which is designed as a first exemplary embodiment according to the invention.
  • the fuel injector has a tubular valve housing 1, in which a longitudinal opening 3 is formed concentrically with a valve longitudinal axis 2. In the longitudinal opening 3 is a z.
  • 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 against the spring force of a return spring (not shown) or closing the fuel injector.
  • the armature 11 is connected to the Valve closing body 7 facing away from the valve needle 5 by z. B. connected a weld using a laser and aligned to the core 12.
  • a guide opening 15 of a valve seat body 16 is used to guide the valve closing body 7 during the axial movement.
  • the cylindrical valve seat body 16 is inserted into the downstream end of the valve housing 1 which faces away from the core 12 and into the longitudinal opening 3 which is concentric with the longitudinal axis 2 of the valve.
  • the circumference of the valve seat body 16 has a slightly smaller diameter than the longitudinal opening 3 of the valve housing 1.
  • On its one lower end face 17 facing away from the valve closing body 7, the valve seat body 16 is provided with a circumferential groove 18.
  • a bottom part 20 of a z. B. cup-shaped spray plate 21 rests with its upper end face 19 on the lower end face 17 of the valve seat body 16 and is concentrically and firmly connected to this by means of a first weld 31.
  • the bottom part 20 of the spray hole disk 21 has at least one spray hole 25, for example four spray holes 25 formed by erosion or stamping.
  • the insertion depth of the valve seat part consisting of valve seat body 16 and cup-shaped spray orifice plate 21 into the Longitudinal opening 3 determines the presetting of the stroke of the valve needle 5, since the one end position of the valve needle 5 is fixed when the solenoid 10 is not energized by the valve closing body 7 resting on a valve seat surface 29 of the valve seat body 16.
  • 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 of the valve needle 5 thus represents the stroke.
  • the holding edge 26 of the spray disk 21 is tightly and firmly connected to the wall of the longitudinal opening 3.
  • a circumferential second weld seam 30 is provided between the end 27 of the holding edge 26 and the wall of the longitudinal opening 3.
  • a welding edge 33 is formed on the lower end face 17, on which the bottom part 20 is tightly connected to the valve seat body 16 with the first circumferential weld seam 31.
  • Spray hole plate 21 and valve housing 1 is required so that the fuel does not flow directly between the longitudinal opening 3 of the valve housing 1 and the circumference of the valve seat body 16 to the spray holes 25 or between the longitudinal opening 3 of the valve housing 1 and the holding edge 26 of the cup-shaped spray hole plate 21 Air intake line of the internal combustion engine can flow.
  • the spherical valve closing body 7 acts with the frustoconical tapering in the direction of flow
  • Valve seat surface 29 of the valve seat body 16 together, which is formed in the axial direction between the guide opening 15 and an outflow opening 32 in the lower end face 17 of the valve seat body 16.
  • the valve seat body 16 has a valve seat body opening facing the solenoid 10 34, which has a larger diameter than the diameter of the guide opening 15 of the valve seat body 16.
  • the diameter of the guide opening 15 is designed such that the spherical valve closing body 7 projects through the guide opening 15 outside of its flattened portions 8 with a small radial distance.
  • the central region 24 of the base part 20 of the spray perforated disk 21 is downstream, for example
  • a bulge 36 results in the central region.
  • a collecting space 37 is formed, into which, when the valve closing body 7 is lifted from the valve seat surface 29, the fuel first reaches it before it passes through the Spray holes 25 are metered and sprayed into the air intake line of the internal combustion engine.
  • the precise stroke setting for the valve closing body 7 is carried out by bending the spray perforated disk 21 between the weld seams 30, 31 in the axial direction.
  • the circumferential groove 18 on the lower end face 17 of the valve seat body 16 has the effect that, when the first weld seam 31 is attached to the spray hole disk 21 and the weld rim 33, the heat transfer is restricted
  • Valve seat surface 29 takes place so that stresses due to the thermal and mechanical stress only occur in the welding edge 33 and are kept away from the valve seat surface 29 in the same way as mechanical stresses.
  • the roundness of the valve seat surface 29 thus remains which is a prerequisite for the tightness of the fuel injector in the closed state.
  • the thermal and mechanical decoupling of the valve seat surface 29 from the first weld seam 31 is particularly great when the first weld seam 31 is close to 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, so that the narrowest possible welding edge 33 results.
  • an extension opening 40 adjoining the longitudinal opening 3 is provided, which has a larger cross-section than the longitudinal opening 3.
  • the spraying hole disk 21 extends with its retaining edge 26 to the wall of the extension opening 40 and is tightly connected to the wall of the expansion opening 40 by the circumferential second weld 30. This results in between the spray orifice plate 21, the circumference of the valve seat body 16 and the wall of the
  • Extension opening 40 in this area an air ring gap 41 extending to the transition into the longitudinal opening 3, which causes heat transfer from the valve housing 1 to the valve seat body 16 not already in the area of the lower one when the second weld seam 30 is applied
  • End face 17 takes place, but only after a lengthened by the axial extension of the air ring gap 41 in the direction of the valve longitudinal axis 2, the heat conduction throttling heat conduction.
  • the radial distance between the weld seams 30, 31 enlarged so that the bending of the spray plate 21 is facilitated in this area for adjusting the stroke of the valve closing body 7.
  • the air ring gap 41 has, for example, a radial width of approximately 0.2 mm and an axial extent of, for example, approximately 1 mm.
  • the groove 21 has, for example, a radial width of approximately 0.6 mm and a depth of approximately 0.5 mm.

Abstract

In known valves, when the perforated injection disk is welded to the valve seat body, stresses are produced which affect the roundness of the valve seat surface, and so minor fuel leaks may occur in the closed state of the valve. The object of the invention therefore is to prevent such welding from affecting in an undesirable manner the roundness of the valve seat surface, and to improve the tightness of the valve in its closed state. A continuous groove (18) provided on the bottom front face (17) of the valve seat body (16) reduces heat transfer between the welding seam (31) between the perforated injection disk (21) and the valve seat body (16). Thermally and mechanically caused stresses are absorbed by a welding edge (33) and the valve seat surface (29) is kept free from such stresses. This fuel injection valve is particularly suitable for fuel injection systems of mixture-compressing, spark-ignited internal combustion engines.

Description

BrennstoffeinspritzventilFuel injector
Stand der TechnikState of the art
Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Anspruchs 1. Es ist schon ein Brennstoffeinspritzventil bekannt (DE 42 21 185 AI) , 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 desThe invention is based on a fuel injector according to the preamble of claim 1. A fuel injector is already known (DE 42 21 185 AI), in which, after the valve seat surface provided in the valve seat body has been finished, an injection orifice plate is welded onto an end face of the valve seat body. This creates tensions in the valve seat body, which among other things worsen the roundness of the valve seat surface, which causes the tightness of the
Brennstoffeinspritzventils im geschlossenen Zustand beeinflußt wird und ungewollterweise aus dem geschlossenen Brennstoffeinspritzventil Brennstoff in geringen Mengen ausleckt .Fuel injector is affected in the closed state and unintentionally leaks fuel in small amounts from the closed fuel injector.
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 erfolg .The fuel injector according to the invention with the characterizing features of claim 1 has the advantage that it is avoided in a simple manner that the welding of the spray disk to the valve seat body the roundness of the valve seat surface deteriorates, which results in a reduction in the amount of leakage when the valve is closed. The groove in the end face of the valve seat body mechanically and thermally decouples the valve seat surface and is therefore not exposed to any stresses caused by welding. Deformations on the valve seat body caused by heat are absorbed by the area of the valve seat body in which the welding takes place.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegebenen Brennstoffeinspritzventiles möglich.Advantageous further developments and improvements of the fuel injector specified in claim 1 are possible through the measures listed in the subclaims.
Vorteilhaft ist es, die erste Schweißnaht in der Nähe des Umfanges des Ventilsitzkδrpers 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 provide the first weld near the circumference of the valve seat body and to keep the radial distance of the groove from the first weld smaller than the outflow opening. This results in a large distance between the weld seam and 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 provide the valve housing with a longitudinal opening, into which the valve seat body is inserted, and in the region of the lower end face of the valve seat body in the direction away from the valve seat body to provide an expansion opening with a larger cross section than the longitudinal opening, with the wall of which the spray-perforated disk is penetrated by a second weld is connected. This ensures that the attachment of the spray hole disk in the valve housing by means of a second weld seam does not lead to any undesired deformation of the valve seat surface due to thermal stress. In addition, this increases the radial spacing of the weld seams, so that 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 l 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 shown in simplified form in the drawing and explained in more detail in the following description. FIG. 1 shows a first exemplary embodiment of the invention on the basis of a fuel injector shown schematically in partial representation, FIG. 2 shows a second exemplary embodiment of the invention with a 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 partially shows an example of an otherwise already known fuel injection valve for fuel injection systems of mixture-compressing spark-ignition internal combustion engines, which is designed as a first exemplary embodiment according to the invention. The fuel injector has a tubular valve housing 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, which is connected at its downstream end 6 with a spherical valve closing body 7, on the circumference of which, for example, five circular flats 8 are provided.
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 ausgerichte .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 against the spring force of a return spring (not shown) or closing the fuel injector. The armature 11 is connected to the Valve closing body 7 facing away from the valve needle 5 by z. B. connected a weld using a laser and aligned to the core 12.
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.A guide opening 15 of a valve seat body 16 is used to guide the valve closing body 7 during the axial movement. The cylindrical valve seat body 16 is inserted into the downstream end of the valve housing 1 which faces away from the core 12 and into the longitudinal opening 3 which is concentric with the longitudinal axis 2 of the valve. The circumference of the valve seat body 16 has a slightly smaller diameter than the longitudinal opening 3 of the valve housing 1. On its one lower end face 17 facing away from the valve closing body 7, the valve seat body 16 is provided with a circumferential groove 18. A bottom part 20 of a z. B. cup-shaped spray plate 21 rests with its upper end face 19 on the lower end face 17 of the valve seat body 16 and is concentrically and firmly connected to this by means of a first weld 31. In its central region 24, the bottom part 20 of the spray hole disk 21 has at least one spray hole 25, for example four spray holes 25 formed by erosion or stamping.
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.At the bottom part 20 of the cup-shaped spray perforated disk 21 there is a circumferential retaining edge 26 which extends in the axial direction away from the valve seat body 16 and is conically bent outwards up to its end 27. Since the circumferential diameter of the valve seat body 16 is smaller than the diameter of the longitudinal opening 3 of the valve housing 1, there is only a radial pressure between the longitudinal opening 3 and the slightly conically outwardly bent retaining edge 26 of the spray-disk 21.
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 part consisting of valve seat body 16 and cup-shaped spray orifice plate 21 into the Longitudinal opening 3 determines the presetting of the stroke of the valve needle 5, since the one end position of the valve needle 5 is fixed when the solenoid 10 is not energized by the valve closing body 7 resting on a valve seat surface 29 of the valve seat body 16. 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 of the valve needle 5 thus represents the stroke.
An seinem Ende 27 ist der Halterand 26 der Spritzlochscheibe 21 mit der Wandung der Längsδffnung 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 vonAt its end 27, the holding edge 26 of the spray disk 21 is tightly and firmly connected to the wall of the longitudinal opening 3. For this purpose, a circumferential second weld seam 30 is provided between the end 27 of the holding edge 26 and the wall of the longitudinal opening 3. Outside the central area 24 between the groove 18 and the circumference of the valve seat body 16, a welding edge 33 is formed on the lower end face 17, on which the bottom part 20 is tightly connected to the valve seat body 16 with the first circumferential weld seam 31. A tight connection of the valve seat body 16 and spray plate 21 and
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 Brennkraf maschine strömen kann.Spray hole plate 21 and valve housing 1 is required so that the fuel does not flow directly between the longitudinal opening 3 of the valve housing 1 and the circumference of the valve seat body 16 to the spray holes 25 or between the longitudinal opening 3 of the valve housing 1 and the holding edge 26 of the cup-shaped spray hole plate 21 Air intake line of the internal combustion engine can flow.
Der kugelförmige Ventilschließkörper 7 wirkt mit der sich in Strδmungsrichtung kegelstumpfförmig verjüngendenThe spherical valve closing body 7 acts with the frustoconical tapering in the direction of flow
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.Valve seat surface 29 of the valve seat body 16 together, which is formed in the axial direction between the guide opening 15 and an outflow opening 32 in the lower end face 17 of the valve seat body 16. The valve seat body 16 has a valve seat body opening facing the solenoid 10 34, which has a larger diameter than the 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 stromabwärtigerFor exact guidance of the valve closing body 7 and thus the valve needle 5 during the axial movement, the diameter of the guide opening 15 is designed such that the spherical valve closing body 7 projects through the guide opening 15 outside of its flattened portions 8 with a small radial distance. The central region 24 of the base part 20 of the spray perforated disk 21 is downstream, for example
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 Ventilschließkδrpers 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.Direction, ie in the direction pointing away from the valve closing body 7 out of the plane of the base part 20, so that a bulge 36 results in the central region. Between the end face 17 of the valve closing body 7, the valve seat surface 29 and the wall of the bulge 36 or the upper end face 19 of the spray orifice plate 21, a collecting space 37 is formed, into which, when the valve closing body 7 is lifted from the valve seat surface 29, the fuel first reaches it before it passes through the Spray holes 25 are metered and sprayed into the air intake line of the internal combustion engine.
Die genaue Hubeinstellung für den Ventilschließkörper 7 erfolgt durch Verbiegen der Spritzlochscheibe 21 zwischen den Schweißnähten 30, 31 in axialer Richtung.The precise stroke setting for the valve closing body 7 is carried out by bending the spray perforated disk 21 between the weld seams 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 zurThe circumferential groove 18 on the lower end face 17 of the valve seat body 16 has the effect that, when the first weld seam 31 is attached to the spray hole disk 21 and the weld rim 33, the heat transfer is restricted
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.Valve seat surface 29 takes place so that stresses due to the thermal and mechanical stress only occur in the welding edge 33 and are kept away from the valve seat surface 29 in the same way as mechanical stresses. The roundness of the valve seat surface 29 thus remains which is a prerequisite for the tightness of the fuel injector in the closed state. The thermal and mechanical decoupling of the valve seat surface 29 from the first weld seam 31 is particularly great when the first weld seam 31 is close to 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, so that the narrowest possible 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 imIn the exemplary embodiment according to FIG. 2, the parts which remain the same and have the same effect as in the exemplary embodiment according to FIG. 1 are identified by the same reference numerals. Deviating from the exemplary embodiment according to FIG. 1, in the exemplary embodiment according to FIG
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 derIn the area of the lower end face 17 of the valve seat body 16 in the direction away from the valve closing body 7, an extension opening 40 adjoining the longitudinal opening 3 is provided, which has a larger cross-section than the longitudinal opening 3. The spraying hole disk 21 extends with its retaining edge 26 to the wall of the extension opening 40 and is tightly connected to the wall of the expansion opening 40 by the circumferential second weld 30. This results in between the spray orifice plate 21, the circumference of the valve seat body 16 and the wall of the
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 unterenExtension opening 40 in this area an air ring gap 41 extending to the transition into the longitudinal opening 3, which causes heat transfer from the valve housing 1 to the valve seat body 16 not already in the area of the lower one when the second weld seam 30 is applied
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. End face 17 takes place, but only after a lengthened by the axial extension of the air ring gap 41 in the direction of the valve longitudinal axis 2, the heat conduction throttling heat conduction. In addition, the radial distance between the weld seams 30, 31 enlarged so that the bending of the spray plate 21 is facilitated in this area for adjusting the stroke of the valve closing body 7. The air ring gap 41 has, for example, a radial width of approximately 0.2 mm and an axial extent of, for example, approximately 1 mm. The groove 21 has, for example, a radial width of approximately 0.6 mm and a depth of approximately 0.5 mm.

Claims

Patentansprüche claims
1. Brennstoffeinspritzventil für Brennkraftmaschinen, mit einem Ventilgehäuse, mit einem bewegbaren1. Fuel injection valve for internal combustion engines, with a valve housing, with a movable
Ventilschließkörper, der mit einer Ventilsitzfläche zusammenwirkt, die an einem Ventilsitzkörper ausgebildet ist und an ihrem stromabwärtigen Ende in eine Ausströmöffnung übergeht, wobei die Ausströmöffnung sich bis zu einer unteren Stirnseite des Ventilsitzkörpers erstreckt, und mit einer an der unteren Stirnseite des Ventilsitzkörpers mit einer ersten Schweißnaht befestigten Spritzlochscheibe, in der wenigstens ein Abspritzloch vorgesehen ist, dadurch gekennzeichnet, daß in der unteren Stirnseite (17) des Ventilsitzkörpers (16) zwischen der Ausströmöffnung (32) und der ersten Schweißnaht (31) eine die Ausströmöffnung (32) mit radialem Abstand umgebende Nut (18) vorgesehen ist.Valve closing body which cooperates with a valve seat surface which is formed on a valve seat body and merges into an outflow opening at its downstream end, the outflow opening extending to a lower end face of the valve seat body, and with one on the lower end face of the valve seat body with a first weld attached spray hole disk, in which at least one spray hole is provided, characterized in that in the lower end face (17) of the valve seat body (16) between the outflow opening (32) and the first weld (31) surrounds the outflow opening (32) at a radial distance Groove (18) is provided.
2. Brennstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß 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 als zur Ausströmöffnung (32) ist. 2. Fuel injection valve according to claim 1, characterized in that the first weld seam (31) is in the vicinity of the circumference of the valve seat body (16) and the radial distance of the groove (18) to the first weld seam (31) less than to the outflow opening (32) is.
3. Brennstoffeinspritzventil nach Anspruch l oder 2, dadurch gekennzeichnet, daß das Ventilgehäuse (1) eine Längsöffnung (3) hat, in die der Ventilsitzkörper (16) eingeschoben ist, und im Bereich der unteren Stirnseite (17) des Ventilsitzkörpers (16) in Richtung vom Ventilschließkörper (7) weg sich an die Längsöffnung (3) eine Erweiterungsöffnung (40) mit größerem Querschnitt anschließt.3. Fuel injection valve according to claim l 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 face (17) of the valve seat body (16) in Direction away from the valve closing body (7), an extension opening (40) with a larger cross-section adjoins the longitudinal opening (3).
4. Brennstoffeinspritzventil nach Anspruch 3, dadurch gekennzeichnet, daß die Spritzlochscheibe (21) mit der Wandung der ErweiterungsÖffnung (40) durch eine zweite Schweißnaht (30) verbunden ist. 4. Fuel injection valve according to claim 3, characterized in that the spray orifice plate (21) is connected to the wall of the expansion 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
DE19627090A DE19627090A1 (en) 1996-07-05 1996-07-05 Fuel injector
DE19627090 1996-07-05
PCT/DE1997/000577 WO1998001665A1 (en) 1996-07-05 1997-03-21 Fuel injection valve

Publications (2)

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

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EP97918045A Expired - Lifetime EP0853725B1 (en) 1996-07-05 1997-03-21 Fuel injection valve

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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)

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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

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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

Non-Patent Citations (1)

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Title
See references of WO9801665A1 *

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BR9706538A (en) 1999-07-20
RU2173788C2 (en) 2001-09-20
EP0853725B1 (en) 2001-08-29
WO1998001665A1 (en) 1998-01-15
JPH11512167A (en) 1999-10-19
DE19627090A1 (en) 1998-01-08
ES2163754T3 (en) 2002-02-01
KR19990028585A (en) 1999-04-15
DE59704441D1 (en) 2001-10-04

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