EP0826878B1 - Fuel injector for internal combustion engines - Google Patents
Fuel injector for internal combustion engines Download PDFInfo
- Publication number
- EP0826878B1 EP0826878B1 EP97110726A EP97110726A EP0826878B1 EP 0826878 B1 EP0826878 B1 EP 0826878B1 EP 97110726 A EP97110726 A EP 97110726A EP 97110726 A EP97110726 A EP 97110726A EP 0826878 B1 EP0826878 B1 EP 0826878B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- valve member
- fuel injection
- stroke
- conical
- 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
Links
Images
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
-
- 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
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/042—The valves being provided with fuel passages
- F02M61/045—The valves being provided with fuel discharge orifices
-
- 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
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
Definitions
- the invention relates to a fuel injection valve for Internal combustion engines according to the preamble of claim 1 out.
- a fuel injection valve for Internal combustion engines according to the preamble of claim 1 out.
- Such a known from DE-OS 42 28 359 A1 Fuel injection valve has a valve body with a axial bore in which a piston-shaped valve member is led to control an injection cross section by the high fuel pressure against the force of one Closing spring can be moved outwards.
- the valve member has one at the end of the combustion chamber Bore of the valve body protruding closing head, the one Forms valve closing member and the valve body thereof facing a valve sealing surface is arranged with the closing head with one on the combustion chamber side End face of the valve body arranged valve seat surface interacts.
- At least one Injection opening on the valve member at the level of the closing head provided by a between the valve member and the Bore formed pressure chamber.
- the exit opening the injection opening is in the closed position of the Valve member covered by the valve body and is only in Course of the outward opening stroke of the Valve member released by dipping out of the hole.
- valve member With its end facing away from the closing head and away from the combustion chamber the valve member protrudes into a spring chamber which is axially aligned is formed with the valve body clamped holding body.
- the valve member points to its distant combustion chamber Shaft a spring plate between, and one on Valve body attached to the housing-fixed stop Closing spring is clamped.
- the fuel injection takes place at the beginning of the High pressure fuel supply in the pressure chamber of the Injector, the high pressure fuel that Valve member acted in the opening direction and counter the restoring force of the closing spring from the valve seat stands out on the outside. After a short Opening stroke of the valve member the injection opening turned on so that the fuel in the combustion chamber too supplying internal combustion engine is injected.
- the maximum opening stroke movement of the valve member is thereby by the creation of a federal government on Valve member formed contact surface on a fixed stroke stop limited, on the location itself the maximum opening stroke can be set.
- the known fuel injection valve has the Disadvantage on that at the contact surfaces of the stroke stop very high due to the strong valve link stroke delay Surface pressure forces at the contact points and, conditionally due to the inertial forces of the valve member, very high dynamic tensile forces occur on the valve member that breakage of the valve member and thus total failure of the entire fuel injection system.
- the fuel injector according to the invention for Internal combustion engines with the characteristic features of the Claim 1 has the advantage that means a conical formation of the contact surfaces of the Ventilgliedhubanschlag the supporting cross section of the Valve member can be increased without losing the Surface pressure on the contact surface of the valve member to increase disproportionately. To do this point the stationary conical stroke stop surface and the one with this cooperating conical valve member contact surface same angle of inclination to the largest possible To provide force application area.
- this cross-sectional transition is in advantageously rounded with a large radius educated.
- the conical stroke stop surface is advantageously on the end face of a stop ring provided, the Transition from the conical stop surface to the cylindrical one Inner wall over different angles of inclination of the oblique Inner wall surfaces are made.
- the stop ring is made of two half shells formed in the installed state by a support ring are enclosed, which fixes the half-shells in their position and secures, the support ring also by the conical force application surface due to spreading forces the half shells.
- the two half-shells will be more advantageous Way by cutting a finished ring produced, alternatively also a division into three or more stop ring segments is possible.
- Fuel injection valve for internal combustion engines is in of the drawing and is shown in the following Description explained in more detail.
- FIG. 1 shows a known one Fuel injection valve in a longitudinal section
- FIG. 2 the inventive design of the stroke stop in one Detail from a fuel injection valve according to FIG. 1
- FIG. 3 shows an enlarged partial illustration of the Inner cross section of a half shell of the stroke stop ring of Figure 2.
- Fuel injector for internal combustion engines has a valve body 1, which by means of a union nut 3 is axially clamped against a valve holding body 5.
- the one with its free end in the combustion chamber of the internal combustion engine projecting valve body 1 has an axial guide bore 7 on, in which a piston-shaped valve member 8 axially is slidably mounted on the lower, in the End of the combustion chamber projecting a valve closing head 9 is arranged is.
- This valve closing head 9 has one of the valve body 1 facing conical valve sealing surface 11 with a corresponding conical valve seat 13 on the Front side of the valve body on the combustion chamber side 1 interacts.
- the protruding into the guide bore 7 radial with respect to the part having the sealing surface 11 offset section of the valve closing head 9 is as Piston spool designed with its distant combustion chamber Ring face 15 a pressure chamber 17 within the Guide bore 7 limited, of which a variety of axial inlet channels 19 in the valve closing head 9, of which a radial injection opening 21 leads away.
- the outlet openings of the injection openings 21 arranged so that when the injector is closed, with valve member 8 resting against valve seat 13, from the wall the guide hole 7 are closed and only in the course the outward opening stroke of the valve member 8 Dive out of the overlap with the valve body 1.
- the high-pressure fuel supply takes place in the pressure chamber 17 via a high-pressure channel 23, which the valve body 1 and the Valve holder body 5 penetrates axially and to the one of a fuel injection pump, not shown Injection line is connected.
- Valve member 8 With its valve member facing away from the combustion chamber, this protrudes Valve member 8 provided in a valve holding body 5 Spring chamber 25, in which the valve member 8 in Closing direction towards the valve seat 13 Valve spring 27 is inserted. It is on the far side of the combustion A spring plate 29 is arranged at the end of the valve member 8, between the and a housing-fixed ring insert 31 die Valve spring 27 is clamped.
- the ring insert 31 lies with its spring facing away End face on a stop ring 33, with its other face on the face of the Valve body 1 is applied.
- the inside diameter of the Stop ring 33 formed smaller than that Inner diameter of the ring insert 31, so that on the Contact surface between ring insert 31 and stop ring 33 an annular stroke stop surface 35 is formed. With this stroke stop surface 35 acts to limit the after outward valve member opening stroke movement Contact surface 37 together on the valve member 8, the one combustion chamber side shoulder of a collar 39 am Valve member 8 is formed and the closed Injector one, the maximum opening stroke has a defining distance from the stroke stop surface 35.
- the stop ring 33 is shown in FIG Embodiment according to the invention from two half shells 41 formed by cutting a finished Stop ring are made.
- a support ring 43 is used, which is also on the Front surface of the valve body 1 distant from the combustion chamber.
- FIG. 3 shows the inner wall course of the half-shells 41 shown enlarged, the conical stroke stop surface 35 over differently inclined conical surfaces 45 in the cylindrical inner wall area 47 merges.
- the fuel injection valve according to the invention works in the following way.
- the valve spring 27 holds the valve member 8 with its sealing surface 11 in contact with the valve seat surface 13 on the valve body 1, the injection openings 21 being covered by the wall of the guide bore 7, so that the injector is closed.
- the maximum opening stroke movement of the valve member 8 is thereby by the contact of the valve member contact surface 37 on the fixed stroke stop surface 35, being limited by the conical formation of these two contact surfaces of the load-bearing cross section on the valve member 8, without an increase the surface pressure can be increased such that Fractures of the valve member 8 due to the hard impact can be safely avoided at the stroke stop.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Die Erfindung geht von einem Kraftstoffeinspritzventil für
Brennkraftmaschinen nach der Gattung des Patentanspruchs 1
aus. Ein derartiges aus der DE-OS 42 28 359 A1 bekanntes
Kraftstoffeinspritzventil weist einen Ventilkörper mit einer
axialen Bohrung auf, in der ein kolbenförmiges Ventilglied
geführt ist, das zur Steuerung eines Einspritzquerschnitts
durch den Kraftstoffhochdruck entgegen der Kraft einer
Schließfeder nach außen verschiebbar ist. Das Ventilglied
weist dabei an seinem brennraumseitigen Ende einen aus der
Bohrung des Ventilkörpers ragenden Schließkopf auf, der ein
Ventilschließglied bildet und an dessen dem Ventilkörper
zugewandter Seite eine Ventildichtfläche angeordnet ist, mit
der der Schließkopf mit einer an der brennraumseitigen
Stirnseite des Ventilkörpers angeordneten Ventilsitzfläche
zusammenwirkt. Dabei ist weiterhin wenigstens eine
Einspritzöffnung am Ventilglied in Höhe des Schließkopfes
vorgesehen, die von einem zwischen dem Ventilglied und der
Bohrung gebildeten Druckraum ausgeht. Die Austrittsöffnung
der Einspritzöffnung ist in Schließstellung des
Ventilgliedes vom Ventilkörper abgedeckt und wird erst im
Verlauf des nach außen gerichteten Öffnungshubes des
Ventilgliedes durch Austauchen aus der Bohrung freigegeben. The invention relates to a fuel injection valve for
Internal combustion engines according to the preamble of
Mit seinem dem Schließkopf abgewandten, brennraumfernen Ende ragt das Ventilglied in einen Federraum, der in einem axial mit dem Ventilkörper verspannten Haltekörper gebildet ist. Dabei weist das Ventilglied an seinem brennraumfernen Schaftende einen Federteller auf, zwischen dem und einem am Ventilkörper anliegenden gehäusefesten Anschlag die Schließfeder eingespannt ist.With its end facing away from the closing head and away from the combustion chamber the valve member protrudes into a spring chamber which is axially aligned is formed with the valve body clamped holding body. The valve member points to its distant combustion chamber Shaft a spring plate between, and one on Valve body attached to the housing-fixed stop Closing spring is clamped.
Die Kraftstoffeinspritzung erfolgt mit Beginn der Kraftstoffhochdruckzufuhr in den Druckraum des Einspritzventils, wobei der Kraftstoffhochdruck das Ventilglied in Öffnungsrichtung beaufschlagt und entgegen der Rückstellkraft der Schließfeder vom Ventilsitz nach außen abhebt. Dabei wird bereits nach einem kurzen Öffnungshubweg des Ventilgliedes die Einspritzöffnung aufgesteuert, so daß der Kraftstoff in den Brennraum der zu versorgenden Brennkraftmaschine eingespritzt wird.The fuel injection takes place at the beginning of the High pressure fuel supply in the pressure chamber of the Injector, the high pressure fuel that Valve member acted in the opening direction and counter the restoring force of the closing spring from the valve seat stands out on the outside. After a short Opening stroke of the valve member the injection opening turned on so that the fuel in the combustion chamber too supplying internal combustion engine is injected.
Die maximale Öffnungshubbewegung des Ventilgliedes wird dabei durch die Anlage einer durch einen Bund am Ventilgliedschaft gebildeten Anlagefläche an einem gehäusefesten Hubanschlag begrenzt, über dessen Lage sich der maximale Öffnungshub einstellen läßt.The maximum opening stroke movement of the valve member is thereby by the creation of a federal government on Valve member formed contact surface on a fixed stroke stop limited, on the location itself the maximum opening stroke can be set.
Dabei weist das bekannte Kraftstoffeinspritzventil den Nachteil auf, daß an den Kontaktflächen des Hubanschlages infolge der starken Ventilgliedhubverzögerung sehr hohe Flächenpressungskräfte an den Kontaktstellen und, bedingt durch die Massenkräfte des Ventilgliedes,sehr hohe dynamische Zugspannungskräfte am Ventilglied auftreten, die zu einem Bruch des Ventilgliedes und somit zum Totalausfall des gesamten Kraftstoffeinspritzsystems führen können. The known fuel injection valve has the Disadvantage on that at the contact surfaces of the stroke stop very high due to the strong valve link stroke delay Surface pressure forces at the contact points and, conditionally due to the inertial forces of the valve member, very high dynamic tensile forces occur on the valve member that breakage of the valve member and thus total failure of the entire fuel injection system.
Dabei tritt bei den bekannten Kraftstoffeinspritzventilen der Zielkonflikt auf, daß das Absenken der Flächenpressungskräfte durch eine Vergrößerung der waagerechten Auflagefläche am Ventilglied zu einer Erhöhung der Zugspannungen im verbleibenden Ventilgliedquerschnitt führt und umgekehrt.This occurs in the known fuel injection valves the conflict of goals on that lowering the Surface pressure forces by increasing the horizontal contact surface on the valve member for an increase the tensile stresses in the remaining valve member cross-section leads and vice versa.
Da zudem der maximale Ventilglieddurchmesser im Bereich der Anlagefläche montagebedingt auf das Maß des kleinsten Führungsquerschnittes beschränkt ist, ist eine einfache Vergrößerung des Anschlagquerschnittes am Ventilglied nicht möglich, so daß bisher keine Lösung des beschriebenen Zielkonfliktes bekannt ist.Since the maximum valve member diameter in the area of Installation area to the smallest possible due to assembly Guide cross-section is a simple one Not increase the cross section of the stop on the valve member possible so that so far no solution of the described Conflicting goals is known.
Das erfindungsgemäße Kraftstoffeinspritzventil für
Brennkraftmaschinen mit den kennzeichnenden Merkmalen des
Patentanspruchs 1 hat demgegenüber den Vorteil, daß mittels
einer konischen Ausbildung der Kontaktflächen des
Ventilgliedhubanschlages der tragende Querschnitt des
Ventilgliedes gesteigert werden kann, ohne dabei die
Flächenpressung an der Anlagefläche des Ventilgliedes
überproportional zu erhöhen. Dazu weisen die ortsfeste
konische Hubanschlagfläche und die mit dieser
zusammenwirkende konische Ventilgliedanlagefläche den
gleichen Neigungswinkel auf, um eine möglichst große
Krafteinleitungsfläche bereitzustellen.The fuel injector according to the invention for
Internal combustion engines with the characteristic features of the
Um die Kerbwirkung im kritischen Übergangsbereich zwischen der Anlagefläche am Ventilglied zu dessen zylindrischen Schaft zu reduzieren, ist dieser Querschnittsübergang in vorteilhafter Weise mit einem großen Radius abgerundet ausgebildet.To the notch effect in the critical transition area between the contact surface on the valve member to its cylindrical To reduce shaft, this cross-sectional transition is in advantageously rounded with a large radius educated.
Die konische Hubanschlagfläche ist in vorteilhafter Weise an der Stirnseite eines Anschlagringes vorgesehen, wobei der Übergang von der konischen Anschlagfläche zur zylindrischen Innenwand über verschiedene Neigungswinkel der schrägen Innenwandflächen erfolgt.The conical stroke stop surface is advantageously on the end face of a stop ring provided, the Transition from the conical stop surface to the cylindrical one Inner wall over different angles of inclination of the oblique Inner wall surfaces are made.
Für die Montage ist der Anschlagring aus zwei Halbschalen gebildet, die in eingebautem Zustand von einem Stützring umschlossen sind, der die Halbschalen in ihrer Lage fixiert und sichert, wobei der Stützring zudem die durch die konische Krafteinleitungsfläche bedingten Spreizkräfte an den Halbschalen aufnimmt.For the assembly the stop ring is made of two half shells formed in the installed state by a support ring are enclosed, which fixes the half-shells in their position and secures, the support ring also by the conical force application surface due to spreading forces the half shells.
Um Fertigungstoleranzen innerhalb der beiden Halbschalen zu verringern, werden die beiden Halbschalen in vorteilhafter Weise durch Auftrennen eines fertig bearbeiteten Ringes hergestellt, wobei alternativ auch eine Aufteilung in drei oder mehr Anschlagringsegmente möglich ist.To allow for manufacturing tolerances within the two half shells decrease, the two half-shells will be more advantageous Way by cutting a finished ring produced, alternatively also a division into three or more stop ring segments is possible.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar.Further advantages and advantageous configurations of the The invention relates to the description of Drawing and the claims can be found.
Ein Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils für Brennkraftmaschinen ist in der Zeichnung dargestellt und wird in der folgenden Beschreibung näher erläutert.An embodiment of the invention Fuel injection valve for internal combustion engines is in of the drawing and is shown in the following Description explained in more detail.
Es zeigen die Figur 1 ein bekanntes Kraftstoffeinspritzventil in einem Längsschnitt, die Figur 2 die erfindungsgemäße Ausbildung des Hubanschlages in einem Ausschnitt aus einem Kraftstoffeinspritzventil gemäß Figur 1 und die Figur 3 eine vergrößerte Einzelteildarstellung des Innenquerschnitts einer Halbschale des Hubanschlagrings aus der Figur 2.FIG. 1 shows a known one Fuel injection valve in a longitudinal section, FIG. 2 the inventive design of the stroke stop in one Detail from a fuel injection valve according to FIG. 1 and FIG. 3 shows an enlarged partial illustration of the Inner cross section of a half shell of the stroke stop ring of Figure 2.
Das in der Figur 1 dargestellte bekannte
Kraftstoffeinspritzventil für Brennkraftmaschinen weist
einen Ventilkörper 1 auf, der mittels einer Überwurfmutter 3
axial gegen einen Ventilhaltekörper 5 verspannt ist. Der mit
seinem freien Ende in den Brennraum der Brennkraftmaschine
ragende Ventilkörper 1 weist eine axiale Führungsbohrung 7
auf, in der ein kolbenförmiges Ventilglied 8 axial
verschiebbar gelagert ist, an dessen unterem, in den
Brennraum ragenden Ende ein Ventilschließkopf 9 angeordnet
ist. Dieser Ventilschließkopf 9 weist eine dem Ventilkörper
1 zugewandte konische Ventildichtfläche 11 auf, die mit
einer entsprechenden konischen Ventilsitzfläche 13 an der
brennraumseitigen Stirnseite des Ventilkörpers 1
zusammenwirkt. Der in die Führungsbohrung 7 ragende,
gegenüber dem die Dichtfläche 11 aufweisenden Teil radial
abgesetzte Abschnitt des Ventilschließkopfes 9 ist dabei als
Kolbenschieber ausgebildet, der mit seiner brennraumfernen
Ringstirnfläche 15 einen Druckraum 17 innerhalb der
Führungsbohrung 7 begrenzt, von dem eine Vielzahl von
axialen Zulaufkanälen 19 im Ventilschließkopf 9 ausgehen,
von denen jeweils eine radiale Einspritzöffnung 21 abführt.
Dabei sind die Austrittsöffnungen der Einspritzöffnungen 21
so angeordnet, daß sie bei geschlossenem Einspritzventil,
bei am Ventilsitz 13 anliegendem Ventilglied 8, von der Wand
der Führungsbohrung 7 verschlossen sind und erst im Verlauf
des nach außen gerichteten Öffnungshubs des Ventilgliedes 8
aus der Überdeckung mit dem Ventilkörper 1 austauchen.The known known in Figure 1
Fuel injector for internal combustion engines has
a
Die Kraftstoffhochdruckzufuhr in den Druckraum 17 erfolgt
über einen Hochdruckkanal 23, der den Ventilkörper 1 und den
Ventilhaltekörper 5 axial durchdringt und an den eine von
einer nicht gezeigten Kraftstoffeinspritzpumpe abführende
Einspritzleitung angeschlossen ist.The high-pressure fuel supply takes place in the
Mit seinem brennraumabgewandten Ventilgliedschaft ragt das
Ventilglied 8 in einen im Ventilhaltekörper 5 vorgesehenen
Federraum 25, in den eine das Ventilglied 8 in
Schließrichtung zum Ventilsitz 13 hin beaufschlagende
Ventilfeder 27 eingesetzt ist. Dabei ist am brennraumfernen
Ende des Ventilgliedes 8 ein Federteller 29 angeordnet,
zwischen dem und einem gehäusefesten Ringeinsatz 31 die
Ventilfeder 27 eingespannt ist.With its valve member facing away from the combustion chamber, this protrudes
Valve
Der Ringeinsatz 31 liegt dabei mit seiner federabgewandten
Stirnfläche an einem Anschlagring 33 an, der mit seiner
anderen Stirnfläche an der brennraumfernen Stirnfläche des
Ventilkörpers 1 anliegt. Dabei ist der Innendurchmesser des
Anschlagringes 33 kleiner ausgebildet, als der
Innendurchmesser des Ringeinsatzes 31, so daß an der
Kontaktfläche zwischen Ringeinsatz 31 und Anschlagring 33
eine ringförmige Hubanschlagfläche 35 gebildet ist. Mit
dieser Hubanschlagfläche 35 wirkt zur Begrenzung der nach
außen gerichteten Ventilgliedöffnungshubbewegung eine
Anlagefläche 37 am Ventilglied 8 zusammen, die an einer
brennraumseitigen Schulter eines Ringbundes 39 am
Ventilgliedschaft 8 gebildet ist und die bei geschlossenem
Einspritzventil einen, den maximalen Öffnungshubweg
definierenden Abstand zur Hubanschlagfläche 35 aufweist.The ring insert 31 lies with its spring facing away
End face on a
Bei der in der Figur 2 dargestellten erfindungsgemäßen
Ausgestaltung der Kontaktflächen des die Öffnungshubbewegung
des Ventilgliedes 8 begrenzenden Hubanschlags, ist die sich
an den Ringbund 39 brennraumseitig anschließende
Anlagefläche 37 am Ventilglied 8 konisch ausgebildet und
geht über einen großen Radius in die zylindrische
Mantelfläche des Ventilgliedschaftes über. Analog dazu ist
die Hubanschlagfläche 35 am Anschlagring 33 konisch
ausgebildet, wobei die beiden konischen Kontaktflächen den
gleichen Neigungswinkel aufweisen, um so eine möglichst
großflächige Anlage- und Krafteinleitungsfläche
bereitzustellen.In the invention shown in Figure 2
Design of the contact surfaces of the opening stroke movement
of the
Der Anschlagring 33 ist im in der Figur 2 dargestellten
erfindungsgemäßen Ausführungsbeispiel aus zwei Halbschalen
41 gebildet, die durch Auftrennen eines fertig bearbeiteten
Anschlagringes hergestellt sind.The
Zur Fixierung der Halbschalen 41 und zur Aufnahme der auf
diese eingeleiteten Spreizkräfte sind die Halbschalen 41 in
einen Stützring 43 eingesetzt, der ebenfalls an der
brennraumfernen Stirnfläche des Ventilkörpers 1 anliegt. To fix the half-
In der Figur 3 ist der Innenwandverlauf der Halbschalen 41
vergrößert dargestellt, wobei die konische Hubanschlagfläche
35 über verschieden geneigte konische Flächen 45 in den
zylindrischen Innenwandbereich 47 übergeht.FIG. 3 shows the inner wall course of the half-
Das erfindungsgemäße Kraftstoffeinspritzventil arbeitet in
folgender Weise.
Im Ruhezustand, d.h. wenn keine Hochdruckförderung an der
dem Einspritzventil zugeordneten Hochdruckeinspritzpumpe
erfolgt, hält die Ventilfeder 27 das Ventilglied 8 mit
seiner Dichtfläche 11 in Anlage an der Ventilsitzfläche 13
am Ventilkörper 1, wobei die Einspritzöffnungen 21 durch die
Wand der Führungsbohrung 7 abgedeckt sind, so daß das
Einspritzventil geschlossen ist.The fuel injection valve according to the invention works in the following way.
In the idle state, ie when there is no high-pressure delivery at the high-pressure injection pump assigned to the injection valve, the
Beim Einspritzvorgang gelangt der von der
Hochdruckeinspritzpumpe geförderte Kraftstoff in bekannter
Weise über den Druckkanal 23 und den Ringspalt zwischen
Führungsbohrung 7 und Ventilglied 8 in den Druckraum 17.
Dort greift der Kraftstoffhochdruck an der Ringstirnfläche
15 des Ventilschließkopfes 9 in Öffnungsrichtung des
Ventilgliedes 8 an und hebt nach Erreichen eines bestimmten
Öffnungsdrucks das Ventilglied 8 entgegen der Rückstellkraft
der Ventilfeder 27 nach außen vom Ventilsitz 13 ab. Dabei
tauchen nach einem kurzen Leerhub die Einspritzöffnungen 21
aus der Überdeckung mit der Wand der Führungsbohrung 7 aus,
so daß der Kraftstoff aus dem Druckraum 17 über den
Zulaufkanal 19 und die Einspritzöffnungen 21 zur
Einspritzung in den Brennraum der Brennkraftmaschine
gelangt. During the injection process it gets from the
High-pressure injection pump delivered fuel in known
Way over the
Die maximale Öffnungshubbewegung des Ventilgliedes 8 wird
dabei durch die Anlage der Ventilgliedanlagefläche 37 an der
ortsfesten Hubanschlagfläche 35 begrenzt, wobei durch die
konische Ausbildung dieser beiden Kontaktflächen der
tragende Querschnitt am Ventilglied 8, ohne eine Erhöhung
der Flächenpressung, derart gesteigert werden kann, daß
Brüche des Ventilgliedes 8 infolge des harten Aufschlagens
am Hubanschlag sicher vermieden werden können.The maximum opening stroke movement of the
Das Ende der Kraftstoffeinspritzung erfolgt durch die
Beendigung der Zufuhr von Kraftstoffhochdruck, so daß der
Druck im Druckraum 17 wieder unter den Einspritzdruck sinkt
und die Ventilfeder 27 das Ventilglied 8 in Anlage an den
Ventilsitz 13 zurückbewegt.The end of fuel injection takes place through the
Cessation of the supply of high pressure fuel so that the
Pressure in the
Claims (7)
- Fuel injection valve for internal combustion engines with a valve member (8), which is guided in an axially displaceable manner in a bore (7) of a valve body (1) and, at its combustion-chamber end, has a valve-sealing surface (11), by means of which it interacts with a valve seat surface (13) on the valve body (1) to control an injection aperture cross section, and with a stroke stop surface (35), the location of which is fixed relative to the valve body (1) and against which the valve member (8) comes to rest by means of a contact surface (37) after traversing a maximum outward opening-stroke travel, characterized in that the fixed-location stroke stop surface (35) and the valve member's contact surface (37) interacting with the latter are of conical design.
- Fuel injection valve according to Claim 1, characterized in that the transition between the conical contact surface (37) on the valve member (8) and its cylindrical stem is of arched design and has a large radius.
- Fuel injection valve according to Claim 1, characterized in that the conical stroke stop surface (35) merges into a cylindrical inside diameter (47) by way of different angles of inclination.
- Fuel injection valve according to Claim 1, characterized in that the fixed-location stroke stop surface (35) is provided on the end faces of two half-shells (41), which form a continuous stop ring (33) and are surrounded by a supporting ring (43).
- Fuel injection valve according to Claim 1, characterized in that the conical contact surface (37) of the valve member (8) is formed on a cross-sectional transition of the valve member's stem to an annular collar (39), this transition forming a pressure shoulder.
- Fuel injection valve according to Claim 1, characterized in that, at its combustion-chamber end, the valve member (8) has a valve-closing head (9), which projects from the bore (7) of the valve body (1), which incorporates the valve-sealing surface (11) and in which is provided at least one injection aperture (21), which is closed by the wall of the bore (7) when the valve member (8) is resting on the valve seat (13) and emerges from overlap with the bore (7) during the outward opening stroke of the valve member.
- Fuel injection valve according to Claim 4, characterized in that the two half-shells (41) are produced by dividing a finished continuous stop ring (33).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19634716 | 1996-08-28 | ||
DE19634716A DE19634716A1 (en) | 1996-08-28 | 1996-08-28 | Fuel injection valve for internal combustion engines |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0826878A1 EP0826878A1 (en) | 1998-03-04 |
EP0826878B1 true EP0826878B1 (en) | 2002-05-15 |
Family
ID=7803891
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97110726A Expired - Lifetime EP0826878B1 (en) | 1996-08-28 | 1997-07-01 | Fuel injector for internal combustion engines |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0826878B1 (en) |
JP (1) | JPH1089196A (en) |
DE (2) | DE19634716A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19753162A1 (en) * | 1997-11-29 | 1999-06-02 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
CN110344979B (en) * | 2019-07-19 | 2020-12-25 | 北京中康增材科技有限公司 | Design method of oil way of oil injector |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE750183C (en) * | 1941-12-03 | 1944-12-16 | Liquid-controlled injection valve especially designed for internal combustion engines | |
US2756106A (en) * | 1954-03-18 | 1956-07-24 | Schenk Rudolf | Fuel injection valve |
US5522550A (en) | 1992-06-10 | 1996-06-04 | Robert Bosch Gmbh | Injection nozzle for internal combustion engines |
-
1996
- 1996-08-28 DE DE19634716A patent/DE19634716A1/en not_active Withdrawn
-
1997
- 1997-07-01 DE DE59707262T patent/DE59707262D1/en not_active Expired - Fee Related
- 1997-07-01 EP EP97110726A patent/EP0826878B1/en not_active Expired - Lifetime
- 1997-08-27 JP JP9230752A patent/JPH1089196A/en active Pending
Also Published As
Publication number | Publication date |
---|---|
EP0826878A1 (en) | 1998-03-04 |
DE19634716A1 (en) | 1998-03-05 |
DE59707262D1 (en) | 2002-06-20 |
JPH1089196A (en) | 1998-04-07 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE19820513A1 (en) | Fuel injection nozzle for internal combustion engine | |
EP0142008A2 (en) | Delivery valve for fuel injection pumps | |
DE102007002445A1 (en) | Check valve and injector with hydraulic interrupter and check valve | |
DE19706591A1 (en) | Pressure valve | |
DE19618698A1 (en) | Fuel injection valve for internal combustion engines | |
DE19523243A1 (en) | Fuel injection valve for internal combustion engines | |
DE10122256A1 (en) | Fuel injection device for internal combustion engines, in particular common rail injector, and fuel system and internal combustion engine | |
DE19634933B4 (en) | Fuel injection valve for internal combustion engines | |
DE19645900A1 (en) | Fuel injection valve for internal combustion engine | |
EP0890735B2 (en) | Fuel injection valve | |
WO2000001936A2 (en) | Pressure valve | |
DE2458940A1 (en) | INJECTION DEVICE FOR COMBUSTION ENGINES | |
EP2084391B1 (en) | Fuel injection valve device | |
DE10062959A1 (en) | Fuel injection valve for internal combustion engines | |
WO2003004856A1 (en) | Fuel injector having injection curve shaping carried out by switchable throttling elements | |
EP0826878B1 (en) | Fuel injector for internal combustion engines | |
EP1296054A1 (en) | Injection valve for a combustion engine | |
EP1373710A1 (en) | Fuel-injection valve for internal combustion engines | |
DE3811885A1 (en) | FUEL INJECTION DEVICE WITH PRIMARY AND MAIN INJECTION FOR AN INTERNAL COMBUSTION ENGINE, IN PART. SUCH WITH AIR COMPRESSION AND AUTO IGNITION | |
EP1043496B1 (en) | Injector for fuel injection in an internal combustion engine | |
DE19753162A1 (en) | Fuel injection valve for internal combustion engines | |
EP1483499A1 (en) | Installation for the pressure-modulated formation of the injection behavior | |
DE102006050033A1 (en) | Injector, in particular common rail injector | |
DE10121340A1 (en) | Common rail injector for internal combustion engine fuel injection system has casing and intermediate plate bounding control chamber implemented in one piece with inlet and outlet choke | |
DE9301992U1 (en) | Fuel injection nozzle for internal combustion engines |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE FR GB IT |
|
17P | Request for examination filed |
Effective date: 19980904 |
|
AKX | Designation fees paid |
Free format text: DE FR GB IT |
|
RBV | Designated contracting states (corrected) |
Designated state(s): DE FR GB IT |
|
17Q | First examination report despatched |
Effective date: 20010201 |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB IT |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REF | Corresponds to: |
Ref document number: 59707262 Country of ref document: DE Date of ref document: 20020620 |
|
GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 20020731 |
|
ET | Fr: translation filed | ||
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20030218 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20030625 Year of fee payment: 7 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20030716 Year of fee payment: 7 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20030825 Year of fee payment: 7 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20040701 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050201 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20040701 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050331 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED. Effective date: 20050701 |