WO1998057058A1 - Valve - Google Patents

Valve Download PDF

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Publication number
WO1998057058A1
WO1998057058A1 PCT/DE1998/000529 DE9800529W WO9857058A1 WO 1998057058 A1 WO1998057058 A1 WO 1998057058A1 DE 9800529 W DE9800529 W DE 9800529W WO 9857058 A1 WO9857058 A1 WO 9857058A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
valve seat
closing body
seat surface
circular edge
Prior art date
Application number
PCT/DE1998/000529
Other languages
German (de)
French (fr)
Inventor
Ferdinand Reiter
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
Priority to EP98914802A priority Critical patent/EP0917622A1/en
Priority to JP11501237A priority patent/JP2000517023A/en
Priority to BR9806041A priority patent/BR9806041A/en
Priority to AU69176/98A priority patent/AU6917698A/en
Publication of WO1998057058A1 publication Critical patent/WO1998057058A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
    • 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
    • F02M61/188—Spherical or partly spherical shaped valve member ends

Definitions

  • the invention relates to a valve, in particular a fuel injection valve for internal combustion engines, according to the preamble of the main claim. It's already a
  • Fuel injection valve known (DE 42 21 185 AI), in which a spherical valve closing body interacts with a conical valve seat surface and bears sealingly against a contact circle of the valve seat surface when the valve is closed. Due to the
  • valve closing body and valve seat surface or damage to their surfaces due to particles carried in the fuel there is a risk that a certain amount of fuel will escape from the valve in an undesirable manner despite the valve closing body being in contact with the valve seat surface.
  • the valve according to the invention with the characterizing features of the main claim has the advantage that the tightness is improved in the closed state of the valve and the durability is increased and the tightening times over the operating time in one change smaller dimensions.
  • the improvement of the tightness of the valve in the closed state results from the fact that the pressure drop prevailing between the inside and the outside of the valve is successively reduced at two throttle points, namely at the first circular edge between the
  • FIG. 1 shows it 2 shows a partial representation of the valve according to FIG. 1 on a different scale.
  • FIG. 1 partially shows an example of a valve based on an otherwise already known fuel injection valve for fuel injection systems of mixture-compressing spark-ignition internal combustion engines, which is designed 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.
  • 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.
  • 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 facing away from the valve closing body 7 End of the valve needle 5 by z. B. a weld seam connected by a laser and aligned with 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 In the downstream end of the valve housing 1 facing away from the core 12, the cylindrical valve seat body is in the longitudinal opening 3 which is concentric to the longitudinal axis 2 of the valve 16 inserted.
  • the circumference of the valve seat body 16 has a slightly smaller diameter than the longitudinal opening 3 of the valve housing 1.
  • a bottom part 20 of a z. B. cup-shaped spray plate 21 is located with its upper end face 19 on a lower end face 17 of
  • Valve seat body 16 and is concentrically and firmly connected to it 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.
  • 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
  • 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 conical 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 perforated 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.
  • valve seat body 16 and the spray orifice plate 21 and of the spray orifice plate 21 and the valve housing 1 is required so that the fuel does not pass between the longitudinal opening 3 of the valve housing 1 and the circumference of the valve seat body 16 to the spraying holes 25 or between the longitudinal opening 3 of the valve housing 1 and the
  • Holding edge 26 of the cup-shaped spray perforated disk 21 can flow directly into an air intake line of the internal combustion engine.
  • valve closing body 7 interacts with the valve seat surface 29 of the valve seat body 16 which tapers in the shape of a truncated cone and 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.
  • Valve seat body 16, facing solenoid 10 has a valve seat body opening 34 which has a larger diameter than the diameter of guide opening 15 of 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.
  • Spray plate 21 is bent out of the plane of the bottom part 20, for example in the downstream direction, ie in the direction pointing away from the valve closing body 7, so that a bulge 36 results in the central region.
  • a collecting space 37 is formed, into which the fuel first reaches when the valve closing body 7 is lifted from the valve seat surface 29, before it is metered through the spray holes 25 and into the air intake line of the internal combustion engine is hosed.
  • 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.
  • a circumferential recess 40 is provided in the valve seat surface 29, which merges into the valve seat surface 29 upstream at a first circular edge 41 and downstream at a second circular edge 42.
  • the spherical valve closing body 7 lies sealingly on the first circular edge 41 and on the second circular edge 42.
  • the first circular edge 41 and the second circular edge 42 lie symmetrically to a fictitious contact circle 44 on the valve seat surface 29, on which the valve closing body 7 would rest against a valve seat surface 29 without a recess.
  • the cross section of the depression can be triangular, semicircular, oval or the like, for example.
  • the depression 40 is produced by machining or by forming in the valve seat surface 29.
  • the valve seat body 16 is then hardened. After hardening, the circular edges 41, 42 are spherical in diameter
  • Valve closing body 7 corresponding ball machined by lapping or honing so that the edges have a width of about 5 to 100 microns.

Abstract

In existing valves with a spherical valve closing body and a spherical valve seat surface, the valve closing body is located in a contact circle on the valve seat surface. One possible danger is that the valve closing body no longer seals the valve seat surface after a given operating time of the valve, thereby causing the fluid leakage. The inventive valve seeks to improve the sealing capability of the valve. A recess (40) in the valve seat surface (29) forms a first circular edge (41) and a second circular edge (42). When the valve is closed, the spherical closing body (7) is placed on both circular edges (41, 42), thereby improving the sealing ability of the valve. The inventive valve is particularly useful in fuel injection valves for externally ignited mixture compressing internal combustion engines.

Description

VentilValve
Stand der TechnikState of the art
Die Erfindung geht aus von einem Ventil, insbesondere einem Brennstoffeinspritzventil für Brennkraftmaschinen, nach der Gattung des Hauptanspruchs. Es ist schon einThe invention relates to a valve, in particular a fuel injection valve for internal combustion engines, according to the preamble of the main claim. It's already a
Brennstoffeinspritzventil bekannt (DE 42 21 185 AI) , bei dem ein kugelförmiger Ventilschließkörper mit einer kegelförmigen Ventilsitzfläche zusammenwirkt und bei geschlossenem Ventil an einem Berührkreis der Ventilsitzfläche dichtend anliegt. Aufgrund derFuel injection valve known (DE 42 21 185 AI), in which a spherical valve closing body interacts with a conical valve seat surface and bears sealingly against a contact circle of the valve seat surface when the valve is closed. Due to the
Oberflächenrauhigkeit von Ventilschließkörper und Ventilsitzfläche bzw. von Beschädigungen deren Oberflächen aufgrund von im Brennstoff mitgeführten Partikeln besteht jedoch die Gefahr, daß trotz des Anliegens des Ventilschließkörpers an der Ventilsitzfläche in unerwünschter Weise eine gewisse Brennstoffmenge aus dem Ventil austritt.Surface roughness of the valve closing body and valve seat surface or damage to their surfaces due to particles carried in the fuel, however, there is a risk that a certain amount of fuel will escape from the valve in an undesirable manner despite the valve closing body being in contact with the valve seat surface.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Ventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß im geschlossenen Zustand des Ventiles die Dichtheit verbessert wird sowie die DauerlaufStabilität erhöht wird und sich die Anzugszeiten über die Betriebsdauer in einem kleineren Maße verändern. Die Verbesserung der Dichtheit des Ventiles im geschlossenen Zustand ergibt sich dadurch, daß das zwischen dem Inneren und dem Äußeren des Ventiles herrschende Druckgefälle an zwei Drosselstellen nacheinander abgebaut wird, nämlich am ersten Kreisrand zwischen demThe valve according to the invention with the characterizing features of the main claim has the advantage that the tightness is improved in the closed state of the valve and the durability is increased and the tightening times over the operating time in one change smaller dimensions. The improvement of the tightness of the valve in the closed state results from the fact that the pressure drop prevailing between the inside and the outside of the valve is successively reduced at two throttle points, namely at the first circular edge between the
Inneren des Ventiles und der Vertiefung sowie an dem zweiten Kreisrand, nämlich zwischen der Vertiefung und dem Äußeren des Ventiles, so daß für einen Leckstrom am ersten Kreisrand und am zweiten Kreisrand jeweils ein geringeres Druckgefälle zur Verfügung steht als bei dem bekannten Ventil nach dem Stand der Technik. Außerdem übt beim Aufsetzen des Ventilschließkörpers auf die beiden Kreisränder das in der Vertiefung eingeschlossene Flüssigkeitspolster eine dämpfende Wirkung auf den Ventilschließkörper aus, so daß es zu einer geringeren Verformung der Kreisränder während des Dauerbetriebes des Ventiles kommt, wodurch sich ebenfalls das sogenannte „hydraulische Kleben" auch bei längerer Betriebszeit kaum verstärkt, wodurch sich auch keine Erhöhung der erforderlichen Kraft zum Abheben des Ventilschließkörpers von der Ventilsitzfläche ergibt und damit gleichbleibende Anzugszeiten bei der Ventilöffnung erhalten bleiben.Inside of the valve and the recess and on the second circular edge, namely between the recess and the exterior of the valve, so that a lower pressure drop is available for a leakage current at the first circular edge and the second circular edge than in the known valve according to the prior art Technology. In addition, when the valve closing body is placed on the two circular edges, the liquid cushion enclosed in the recess exerts a damping effect on the valve closing body, so that there is less deformation of the circular edges during continuous operation of the valve, which also results in the so-called "hydraulic gluing" hardly increased in the case of a longer operating time, as a result of which there is also no increase in the force required to lift the valve closing body from the valve seat surface, and consequently constant tightening times are maintained when the valve is opened.
Durch die in dem Unteranspruch aufgeführte Maßnahme ist eine vorteilhafte Weiterbildung und Verbesserung des imThe measure listed in the subclaim provides an advantageous further development and improvement of the im
Hauptanspruch angegebenen Ventils möglich. Dadurch ergibt sich der Vorteil, daß ein dichtes Anliegen des Ventilschließkörpers an beiden Kreisrändern gewährleistet ist.Main claim specified valve possible. This has the advantage that a tight fit of the valve closing body is ensured on both circular edges.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ein erfindungsgemäß ausgestaltetes Ventil in Teildarstellung, Figur 2 eine Teildarstellung des Ventiles nach Figur 1 in geändertem Maßstab.An embodiment of the invention is shown in simplified form in the drawing and explained in more detail in the following description. 1 shows it 2 shows a partial representation of the valve according to FIG. 1 on a different scale.
Beschreibung des AusführungsbeispielesDescription of the embodiment
In der Figur 1 ist ein Beispiel für ein Ventil anhand eines sonst bereits bekannten Brennstoffeinspritzventils für Brennstoffeinspritzanlagen von gemischverdichtenden fremdgezündeten Brennkraftmaschinen teilweise dargestellt, das 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 s romabwärtigen 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 a valve based on an otherwise already known fuel injection valve for fuel injection systems of mixture-compressing spark-ignition internal combustion engines, which is designed 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 ausgerichtet.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 facing away from the valve closing body 7 End of the valve needle 5 by z. B. a weld seam connected by a laser and aligned with 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. Ein Bodenteil 20 einer z. B. topfförmig ausgebildeten Spritzlochscheibe 21 liegt mit seiner oberen Stirnseite 19 an einer unteren Stirnseite 17 desA guide opening 15 of a valve seat body 16 is used to guide the valve closing body 7 during the axial movement. In the downstream end of the valve housing 1 facing away from the core 12, the cylindrical valve seat body is in the longitudinal opening 3 which is concentric to the longitudinal axis 2 of the valve 16 inserted. The circumference of the valve seat body 16 has a slightly smaller diameter than the longitudinal opening 3 of the valve housing 1. A bottom part 20 of a z. B. cup-shaped spray plate 21 is located with its upper end face 19 on a lower end face 17 of
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.Valve seat body 16 and is concentrically and firmly connected to it 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 derThe 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
Ventilnadel 5, da die eine Endstellung der Ventilnadel 5 bei nicht erregter Magnetspule 10 durch die Anlage des Ventilschließkörpers 7 an einer kegelförmigen 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. 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. 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 demValve 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 conical 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. At its end 27, the holding edge 26 of the spray perforated 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. A tight connection of the valve seat body 16 and the spray orifice plate 21 and of the spray orifice plate 21 and the valve housing 1 is required so that the fuel does not pass between the longitudinal opening 3 of the valve housing 1 and the circumference of the valve seat body 16 to the spraying holes 25 or between the longitudinal opening 3 of the valve housing 1 and the
Halterand 26 der topfförmigen Spritzlochscheibe 21 hindurch unmittelbar in eine Luftansaugleitung der Brennkraftmaschine strömen kann.Holding edge 26 of the cup-shaped spray perforated disk 21 can flow directly into an air intake line of the internal combustion engine.
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 Ventilsitzkorpers 16.The spherical valve closing body 7 interacts with the valve seat surface 29 of the valve seat body 16 which tapers in the shape of a truncated cone and 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. Valve seat body 16, facing solenoid 10, has a valve seat body opening 34 which has a larger diameter than the diameter of guide opening 15 of 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 derFor 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 area 24 of the bottom part 20 of the
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.Spray plate 21 is bent out of the plane of the bottom part 20, for example in the downstream direction, ie in the direction pointing away from the valve closing body 7, 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 upper end face 19 of the spray orifice plate 21, a collecting space 37 is formed, into which the fuel first reaches when the valve closing body 7 is lifted from the valve seat surface 29, before it is metered through the spray holes 25 and into the air intake line of the internal combustion engine is hosed.
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.
Wie auch in Figur 2 dargestellt ist, ist in der Ventilsitzfläche 29 eine umlaufende Vertiefung 40 vorgesehen, die stromaufwärts an einem ersten Kreisrand 41 und stromabwärts an einem zweiten Kreisrand 42 in die Ventilsitzfläche 29 übergeht. Im geschlossenen Zustand des Brennstoffeinspritzventiles liegt der kugelförmige Ventilschließkörper 7 an dem ersten Kreisrand 41 und an dem zweiten Kreisrand 42 dichtend an. Der erste Kreisrand 41 und der zweite Kreisrand 42 liegen symmetrisch zu einem fiktiven Berührkreis 44 an der Ventilsitzfläche 29, an dem der Ventilschließkörper 7 an einer Ventilsitzfläche 29 ohne eine Vertiefung anliegen würde. Der Querschnitt der Vertiefung kann beispielsweise dreieckförmig, halbkreisförmig, oval oder ähnlich ausgebildet sein. Die Vertiefung 40 wird spanend oder durch Umformung in der Ventilsitzfläche 29 hergestellt. Anschließend wird der Ventilsitzkörper 16 gehärtet. Nach dem Härten werden die Kreisränder 41, 42 mittels einer im Durchmesser dem kugelförmigenAs is also shown in FIG. 2, a circumferential recess 40 is provided in the valve seat surface 29, which merges into the valve seat surface 29 upstream at a first circular edge 41 and downstream at a second circular edge 42. In the closed state of the fuel injector, the spherical valve closing body 7 lies sealingly on the first circular edge 41 and on the second circular edge 42. The first circular edge 41 and the second circular edge 42 lie symmetrically to a fictitious contact circle 44 on the valve seat surface 29, on which the valve closing body 7 would rest against a valve seat surface 29 without a recess. The cross section of the depression can be triangular, semicircular, oval or the like, for example. The depression 40 is produced by machining or by forming in the valve seat surface 29. The valve seat body 16 is then hardened. After hardening, the circular edges 41, 42 are spherical in diameter
Ventilschließkörper 7 entsprechenden Kugel durch Läppen oder Honen fein bearbeitet, so daß die Ränder etwa eine Breite von 5 bis 100 μm haben. Valve closing body 7 corresponding ball machined by lapping or honing so that the edges have a width of about 5 to 100 microns.

Claims

Patentansprüche claims
1. Ventil, insbesondere Brennstoffeinspritzventil für Brennkraftmaschinen, mit einem Ventilgehäuse und mit einem kugelförmigen Ventilschließkörper, der mit einer kegelförmigen Ventilsitzfläche zusammenwirkt, die in einem Ventilsitzkörper ausgebildet ist, dadurch gekennzeichnet, daß in der Ventilsitzfläche (29) eine Vertiefung (40) vorgesehen ist, die in die Ventilsitzfläche (29) an einem ersten Kreisrand (41) sowie an einem zweiten Kreisrand (42) übergeht und der Ventilschließkörper (7) im geschlossenen1.Valve, in particular fuel injection valve for internal combustion engines, with a valve housing and with a spherical valve closing body which interacts with a conical valve seat surface which is formed in a valve seat body, characterized in that a recess (40) is provided in the valve seat surface (29), which merges into the valve seat surface (29) at a first circular edge (41) and at a second circular edge (42) and the valve closing body (7) in the closed
Zustand des Ventiles an dem ersten Kreisrand (41) und an dem zweiten Kreisrand (42) anliegt.State of the valve on the first circular edge (41) and on the second circular edge (42).
2. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß der erste Kreisrand (41) und der zweite Kreisrand (42) symmetrisch zu einem fiktiven Berührkreis (44) an der Ventilsitzfläche (29) angeordnet sind, an dem der Ventilschließkörper (7) an der Ventilsitzfläche (29) ohne Vertiefung anliegen würde. 2. Valve according to claim 1, characterized in that the first circular edge (41) and the second circular edge (42) are arranged symmetrically to a fictitious contact circle (44) on the valve seat surface (29) on which the valve closing body (7) on the Valve seat surface (29) would lie without a recess.
PCT/DE1998/000529 1997-06-07 1998-02-21 Valve WO1998057058A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP98914802A EP0917622A1 (en) 1997-06-07 1998-02-21 Valve
JP11501237A JP2000517023A (en) 1997-06-07 1998-02-21 valve
BR9806041A BR9806041A (en) 1997-06-07 1998-02-21 valve
AU69176/98A AU6917698A (en) 1997-06-07 1998-02-21 Valve

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19724091.7 1997-06-07
DE19724091A DE19724091A1 (en) 1997-06-07 1997-06-07 Valve

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WO1998057058A1 true WO1998057058A1 (en) 1998-12-17

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Country Status (8)

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EP (1) EP0917622A1 (en)
JP (1) JP2000517023A (en)
KR (1) KR20000068066A (en)
CN (1) CN1228138A (en)
AU (1) AU6917698A (en)
BR (1) BR9806041A (en)
DE (1) DE19724091A1 (en)
WO (1) WO1998057058A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19935262A1 (en) * 1999-07-27 2001-02-01 Bosch Gmbh Robert Fuel injector
JP2004308603A (en) * 2003-04-09 2004-11-04 Denso Corp Fluid injection valve
WO2016075088A1 (en) * 2014-11-11 2016-05-19 Robert Bosch Gmbh An injection valve having movable valve member

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1952816A (en) * 1931-04-04 1934-03-27 Bendix Res Corp Fuel injector
GB2058466A (en) * 1979-09-08 1981-04-08 Bosch Gmbh Robert Electromagnetic fuel injection valve
WO1991008392A1 (en) * 1989-11-25 1991-06-13 Robert Bosch Gmbh Electromagnetically operated fuel-injection valve
DE4221185A1 (en) 1992-06-27 1994-01-05 Bosch Gmbh Robert Orifice plate for a valve and method of manufacture
WO1997028392A2 (en) * 1996-01-31 1997-08-07 Siemens Automotive Corporation Groove means in a fuel injector valve seat

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1952816A (en) * 1931-04-04 1934-03-27 Bendix Res Corp Fuel injector
GB2058466A (en) * 1979-09-08 1981-04-08 Bosch Gmbh Robert Electromagnetic fuel injection valve
WO1991008392A1 (en) * 1989-11-25 1991-06-13 Robert Bosch Gmbh Electromagnetically operated fuel-injection valve
DE4221185A1 (en) 1992-06-27 1994-01-05 Bosch Gmbh Robert Orifice plate for a valve and method of manufacture
WO1997028392A2 (en) * 1996-01-31 1997-08-07 Siemens Automotive Corporation Groove means in a fuel injector valve seat

Also Published As

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KR20000068066A (en) 2000-11-25
JP2000517023A (en) 2000-12-19
CN1228138A (en) 1999-09-08
BR9806041A (en) 1999-08-24
AU6917698A (en) 1998-12-30
EP0917622A1 (en) 1999-05-26
DE19724091A1 (en) 1998-12-10

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