EP0812391B1 - Fuel injection valve for internal combustion engines - Google Patents
Fuel injection valve for internal combustion engines Download PDFInfo
- Publication number
- EP0812391B1 EP0812391B1 EP96924779A EP96924779A EP0812391B1 EP 0812391 B1 EP0812391 B1 EP 0812391B1 EP 96924779 A EP96924779 A EP 96924779A EP 96924779 A EP96924779 A EP 96924779A EP 0812391 B1 EP0812391 B1 EP 0812391B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- valve body
- head piece
- fuel injection
- sealing surface
- 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
- F02M61/04—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
- F02M61/047—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 being formed by deformable nozzle parts, e.g. flexible plates or discs 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
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.
- known fuel injector is the valve member fixed to the valve body and lies with a Valve sealing surface under axial preload on one Valve seat of the valve body.
- a membrane trained valve member is in the known Fuel injection valve is disc-shaped, wherein the radially outer area between a spacer sleeve and a clamping nut clamped against the valve body is.
- the membrane disc also has a central bore on whose ring edge facing the valve body Forms valve sealing surface with which the valve membrane on one conical valve seat surface, which rests on an axial Pin of the valve body is formed.
- a Pressure channel provided in the valve body with a Injection line of a fuel injection pump connected GB 100 445 also discloses a fuel injection valve known in which a membrane-shaped, circular valve member in the form of a head piece limits a pressure space, connected to a central inlet channel running in the valve body and can be filled with fuel under pressure.
- the head piece is resilient and rests under tension a valve sealing surface. The head piece becomes due to the fuel pressure lifted against its internal stress from the valve sealing surface and releases an injection cross section.
- the membrane-shaped head piece is fixed at its edge to the valve body by a clamping nut and formed in one piece without openings. and that in a limited by the valve membrane Pressure chamber opens.
- valve sealing surface on the valve seat of the Valve body adjacent valve member is during the Injection phase due to the high fuel pressure from the valve seat lifted off and gives an injection cross section in the Combustion chamber of the internal combustion engine to be supplied is free.
- the known fuel injection valve the disadvantage that due to the relatively complicated Construction and use of a variety of components Manufacture of the known fuel injection valve is complex and costly. It also needs that known fuel injector due to the variety of Components an increased space, especially on his end near the combustion chamber, which shows the installation flexibility at the Restricts internal combustion engine.
- Another disadvantage is the shape of the injection opening in the combustion chamber of the internal combustion engine to be supplied, the is ring-shaped in the known injection valve, which is an exact jet alignment of the injection jet difficult.
- the fuel injection valve according to the invention for internal combustion engines with the characterizing features of claim 1 has in contrast the advantage that by directly attaching the as Head piece trained valve member on the valve body by a Welded connection only two components are required. Through this the manufacturing and assembly costs can be very simple the fuel injector significantly reduce, so that the manufacturing cost over the known injector can be reduced. It’s not another fastener, for example a clamping nut, necessary to the valve member in the the intended location.
- the weld on the outer radial Edge of the head piece advantageously causes the valve member is resilient in the middle. To do the axial preload To reach the valve member, it is under high axial Contact pressure welded to the valve body.
- Another advantageous way of securing the axial preload is achieved by thermal treatment during assembly, at which the valve body heats up to a high temperature becomes. Now weld the cold head piece to the heated valve body at the lower end of the valve sealing surface facing away Head piece, turns up after cooling or temperature compensation between the components due to the contraction of the valve body the axial preload between the head piece and valve body on. This can be done either via the axial contact pressure or the Degree of thermal treatment during the assembly of the components adjust the axial preload force with which the head piece formed valve member bears on the valve seat of the valve body, what in turn directly determines the opening pressure at the injection valve. A further possibility of setting the opening pressure and the course the opening movement of the acting as a resilient membrane End face of the head piece is through the formation of this end face possible.
- the cone angle of the conical Valve seat surface and the conical valve sealing surface slightly deviate from each other so that a sealing edge seat is formed.
- the head piece is particularly advantageous to design the head piece as a pot-shaped one Form hollow body, the closed, the valve body facing End face forms the resilient membrane and that at its radial outer area is non-detachably connected to the valve body.
- Another advantage of the fuel injection valve according to the invention represents the provision of freely selectable injection openings, through which the jet position of the injected fuel is adjustable is.
- the head piece its radially outer area facing the valve body Face is welded to the valve body, the beam path by the cone angle of the valve sealing surface and the locations of the Interruptions in the circumferential weld seam determined.
- the cup-shaped Head piece is inserted into a receiving opening of the valve body, are the injection openings through freely selectable recesses in the Wall of the valve body in the area of the overlap with the valve sealing surface educated.
- Fuel injection valves for internal combustion engines are in of the drawing and are shown in the following Description explained in more detail.
- FIG. 1 shows a first exemplary embodiment in FIG 2 shows a longitudinal section through the injection valve
- FIG. 2 shows an enlarged section from FIG. 1 a section through the injection valve of Figure 2 along the valve seat surface of the valve body
- the figure 4 a second embodiment analogous to the representation of the figure 2
- Figure 5 shows a section through the valve body of the Figure 4 along the injection openings and Figures 6A up to 6F different design options for the head piece of the two embodiments.
- the first embodiment shown in Figure 1 has a preferably rotationally symmetrical valve body 1 on which in the combustion chamber of the to be supplied Internal combustion engine protruding lower end one Valve member forming head 3 is attached.
- Valve body 1 On his Valve body 1 has an upper end remote from the combustion chamber Pipe connection 5 to which one, the valve body 1 in Longitudinal penetrating pressure channel 7 connects at the end of the valve body 1 near the combustion chamber at its lower end End face opens.
- valve seat surface 9 which is conical is trained.
- valve seat surface 9 acts upper end face of the valve body 1 Head piece 3 together, which has a valve sealing surface 11 forms, which is also conical.
- valve sealing surface 11 forms, which is also conical.
- the head piece 3 In order to form a resilient valve member, the head piece 3 on its outer radial edge of the valve body 1 facing end face 11 forming the valve sealing face with the lower end of the valve body on the combustion chamber side 1 welded.
- the head 3 is during the Welding at high pressure axially against the valve body 1 pressed so that the valve sealing surface 11 under tension rests on valve seat 9.
- the two components are welded together not over the entire scope, but as in the Figure 3 shown on several, four in the embodiment Areas interrupted.
- These recesses 15 the circumferential weld 17 form the Injection ports through which the fuel enters the combustion chamber the internal combustion engine emerges.
- the injection jet angle is determined by the cone angle of the conical valve seat and valve sealing surface 9, 11 and the jet width through the Width of the recesses 15 predetermined.
- Exemplary embodiment has the valve body 1 on its lower receiving end projecting into the combustion chamber 21, in which the head piece 3 is fully inserted.
- the upper end face of the head piece 3 forms again a valve sealing surface 11 and the lower ring end face of the Valve body 1 a valve seat 9, which also are conical and slightly different have a different cone angle.
- the educated can Sealing edge 13 in the second embodiment both inside as well as being located outside.
- valve body 1 is heated to a high temperature, then the cold head piece 3 in the receiving opening 21 of the Valve body 1 used and when the Valve sealing surface 11 on the valve seat 9 on the lower, end facing the combustion chamber with the wall of the receiving opening 21 of the valve body 1 welded. After this Temperature compensation of the two components 1, 3 results due to the contraction of the valve body 1 when Cooling an axial bracing of the head piece 3 against the Valve body 1.
- the injection openings are, as in FIG. 5 removable, in the second embodiment as Recesses 23 formed in the wall of the valve body 1, over the coverage area with the Extend valve sealing surface 11 and their arrangement and geometric shape shape the injection jet.
- Head piece 3 as shown in Figures 6A to 6F as Hollow body formed. Only FIG. 6B shows one Design variant of the head piece 3 as a funnel-shaped Disc, the use of which however only in the first, in the Figures 1 to 3 embodiment shown advantageous is.
- the fuel injection valve for internal combustion engines works in the following way: At the beginning of the injection phase, fuel under high pressure flows via the injection line into the pressure channel 7 and acts on the valve sealing surface 11 of the head piece 3 in the opening direction. From a certain fuel pressure, the compressive force acting in the opening direction exceeds the pretensioning force on the head piece 3, with which the valve sealing surface 11 is braced axially against the valve seat 9, and the valve sealing surface 11 lifts resiliently from the valve seat 9.
- the fuel flows in the first exemplary embodiment into the annular gap between the valve seat surface 9 and the valve sealing surface 11 and exits at the cutouts 15 of the weld seam 17 into the combustion chamber of the internal combustion engine.
- the fuel flows to the recesses 23 in the wall of the valve body 1 and from there into the combustion chamber.
- the inventive works Fuel injector very quickly and reliably because almost no moving masses occur.
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. Bei einem derartigen, aus dem DE-Gbm. 93 204 337 bekannten Kraftstoffeinspritzventil ist das Ventilglied ortsfest am Ventilkörper befestigt und liegt mit einer Ventildichtfläche unter axialer Vorspannung an einem Ventilsitz des Ventilkörpers an. Das als Membran ausgebildete Ventilglied ist dabei beim bekannten Kraftstoffeinspritzventil scheibenförmig ausgebildet, wobei der radial äußere Bereich zwischen einer Distanzhülse und einer Spannmutter ortsfest gegen den Ventilkörper verspannt ist. Die Membranscheibe weist ferner eine zentrale Bohrung auf, deren dem Ventilkörper zugewandte Ringkante die Ventildichtfläche bildet, mit der die Ventilmembran an einer konischen Ventilsitzfläche anliegt, die an einem axialen Zapfen des Ventilkörpers gebildet ist. Zur Druckzuführung des Kraftstoffhochdruckes an die Ventilmembran ist ein Druckkanal im Ventilkörper vorgesehen, der mit einer Einspritzleitung einer Kraftstoffeinspritzpumpe verbunden Aus der Schrift GB 100 445 ist darüber hinaus ein Kraftstoffeinspritzventil bekannt, bei dem ein membranförmiges, kreisrundes Ventilglied in Form eines Kopfstücks einen Druckraum begrenzt, der mit einem im Ventilkörper verlaufenden, zentralen Zulaufkanal verbunden ist und über diesen mit Kraftstoff unter Druck befüllt werden kann. Das Kopfstück ist federnd ausgebildet und liegt unter Vorspannung an einer Ventildichtfläche an. Durch den Kraftstoffdruck wird das Kopfstück gegen seine Eigenspannung von der Ventildichtfläche abgehoben und gibt einen Einspritzquerschnitt frei. Das membranförmige Kopfstück ist an seinem Rand durch eine Spannmutter am Ventilkörper fixiert und einstückig ohne Öffnungen ausgebildet. ist und der in einen von der Ventilmembran begrenzten Druckraum mündet.The invention relates to a fuel injection valve for Internal combustion engines according to the preamble of claim 1 out. In such a, from DE-Gbm. 93 204 337 known fuel injector is the valve member fixed to the valve body and lies with a Valve sealing surface under axial preload on one Valve seat of the valve body. That as a membrane trained valve member is in the known Fuel injection valve is disc-shaped, wherein the radially outer area between a spacer sleeve and a clamping nut clamped against the valve body is. The membrane disc also has a central bore on whose ring edge facing the valve body Forms valve sealing surface with which the valve membrane on one conical valve seat surface, which rests on an axial Pin of the valve body is formed. For pressure supply of the high fuel pressure on the valve membrane is a Pressure channel provided in the valve body with a Injection line of a fuel injection pump connected GB 100 445 also discloses a fuel injection valve known in which a membrane-shaped, circular valve member in the form of a head piece limits a pressure space, connected to a central inlet channel running in the valve body and can be filled with fuel under pressure. The head piece is resilient and rests under tension a valve sealing surface. The head piece becomes due to the fuel pressure lifted against its internal stress from the valve sealing surface and releases an injection cross section. The membrane-shaped head piece is fixed at its edge to the valve body by a clamping nut and formed in one piece without openings. and that in a limited by the valve membrane Pressure chamber opens.
Das mit der Ventildichtfläche am Ventilsitz des Ventilkörpers anliegende Ventilglied wird dabei während der Einspritzphase durch den Kraftstoffhochdruck vom Ventilsitz abgehoben und gibt einen Einspritzquerschnitt in den Brennraum der zu versorgenden Brennkraftmaschine frei.That with the valve sealing surface on the valve seat of the Valve body adjacent valve member is during the Injection phase due to the high fuel pressure from the valve seat lifted off and gives an injection cross section in the Combustion chamber of the internal combustion engine to be supplied is free.
Dabei weist das bekannte Kraftstoffeinspritzventil jedoch den Nachteil auf, daß infolge des relativ komplizierten Aufbaus und der Verwendung einer Vielzahl von Bauteilen die Herstellung des bekannten Kraftstoffeinspritzventils aufwendig und kostenintensiv ist. Zudem benötigt das bekannte Kraftstoffeinspritzventil aufgrund der Vielzahl der Bauteile einen erhöhten Bauraum, insbesondere an seinem brennraumnahen Ende, was die Einbauflexibilität an der Brennkraftmaschine einschränkt.However, the known fuel injection valve the disadvantage that due to the relatively complicated Construction and use of a variety of components Manufacture of the known fuel injection valve is complex and costly. It also needs that known fuel injector due to the variety of Components an increased space, especially on his end near the combustion chamber, which shows the installation flexibility at the Restricts internal combustion engine.
Ein weiterer Nachteil ist die Form der Einspritzöffnung in den Brennraum der zu versorgenden Brennkraftmaschine, die beim bekannten Einspritzventil ringförmig ausgebildet ist, was eine exakte Strahlausrichtung des Einspritzstrahls erschwert. Another disadvantage is the shape of the injection opening in the combustion chamber of the internal combustion engine to be supplied, the is ring-shaped in the known injection valve, which is an exact jet alignment of the injection jet difficult.
Das erfindungsgemäße Kraftstoffeinspritzventil für Brennkraftmaschinen mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß durch die direkte Befestigung des als Kopfstück ausgebildeten Ventilgliedes am Ventilkörper durch eine Schweißverbindung nur noch zwei Bauteile benötigt werden. Durch diesen sehr einfachen Aufbau läßt sich der Herstellungs- und Montageaufwand des Kraftstoffeinspritzventils erheblich reduzieren, so daß die Fertigungskosten gegenüber dem bekannten Einspritzventil verringert werden können. Es ist kein weiteres Befestigungselement, beispielsweise eine Spannmutter, nötig, um das Ventilglied in der vorgesehenen Lage zu halten. Die Verschweißung am äußeren radialen Rand des Kopfstücks bewirkt in vorteilhafter Weise, daß das Ventilglied in der Mitte federnd ausgebildet ist. Um dabei die axiale Vorspannung des Ventilgliedes zu erreichen, wird es unter hohem axialen Anpreßdruck am Ventilkörper verschweißt.The fuel injection valve according to the invention for internal combustion engines with the characterizing features of claim 1 has in contrast the advantage that by directly attaching the as Head piece trained valve member on the valve body by a Welded connection only two components are required. Through this the manufacturing and assembly costs can be very simple the fuel injector significantly reduce, so that the manufacturing cost over the known injector can be reduced. It’s not another fastener, for example a clamping nut, necessary to the valve member in the the intended location. The weld on the outer radial Edge of the head piece advantageously causes the valve member is resilient in the middle. To do the axial preload To reach the valve member, it is under high axial Contact pressure welded to the valve body.
Eine weitere vorteilhafte Möglichkeit der Sicherung der axialen Vorspannkraft wird durch eine Thermobehandlung während der Montage erreicht, bei der der Ventilkörper auf eine hohe Temperatur erhitzt wird. Verschweißt man nun das kalte Kopfstück am erhitzten Ventilkörper an dem der Ventildichtfläche abgewandten unteren Ende des Kopfstückes, stellt sich nach dem Abkühlen bzw. dem Temperaturausgleich zwischen den Bauteilen aufgrund des Zusammenziehens des Ventilkörpers die axiale Vorspannung zwischen Kopfstück und Ventilkörper ein. Dabei läßt sich sowohl über die axiale Anpreßkraft oder den Grad der Thermobehandlung während des Zusammenfügens der Bauteile die axiale Vorspannkraft einstellen, mit der das durch das Kopfstück gebildete Ventilglied am Ventilsitz des Ventilkörpers anliegt, was wiederum direkt den Öffnungsdruck am Einspritzventil bestimmt. Eine weitere Möglichkeit des Einstellens des Öffnungsdruckes und des Verlaufs der Öffnungsbewegung der als federnde Membran wirkenden Stirnfläche des Kopfstückes ist durch die Ausbildung dieser Stirnfläche möglich.Another advantageous way of securing the axial preload is achieved by thermal treatment during assembly, at which the valve body heats up to a high temperature becomes. Now weld the cold head piece to the heated valve body at the lower end of the valve sealing surface facing away Head piece, turns up after cooling or temperature compensation between the components due to the contraction of the valve body the axial preload between the head piece and valve body on. This can be done either via the axial contact pressure or the Degree of thermal treatment during the assembly of the components adjust the axial preload force with which the head piece formed valve member bears on the valve seat of the valve body, what in turn directly determines the opening pressure at the injection valve. A further possibility of setting the opening pressure and the course the opening movement of the acting as a resilient membrane End face of the head piece is through the formation of this end face possible.
Um einen sicheren Dichtsitz am Einspritzventil zu gewährleisten ist dieser zudem konisch ausgeführt, wobei die Kegelwinkel der konischen Ventilsitzfläche und der konischen Ventildichtfläche geringfügig voneinander abweichen, so daß ein Dichtkantensitz gebildet ist. Dabei ist es besonders vorteilhaft, das Kopfstück als topfförmigen Hohlkörper auszubilden, dessen geschlossene, dem Ventilkörper zugewandte Stirnfläche die federnde Membran bildet und das an seinem radial äußeren Bereich unlösbar mit dem Ventilkörper verbunden ist.To ensure a secure seal on the injection valve this is also conical, the cone angle of the conical Valve seat surface and the conical valve sealing surface slightly deviate from each other so that a sealing edge seat is formed. there it is particularly advantageous to design the head piece as a pot-shaped one Form hollow body, the closed, the valve body facing End face forms the resilient membrane and that at its radial outer area is non-detachably connected to the valve body.
Ein weiterer Vorteil des erfindungsgemäßen Kraftstoffeinspritzventils stellt das Vorsehen von frei wählbaren Einspritzöffnungen dar, durch die die Strahllage des eingespritzten Kraftstoffes einstellbar ist. In einem ersten Ausführungsbeispiel, bei dem das Kopfstück an seinem radial äußeren Bereich der dem Ventilkörper zugewandten Stirnfläche mit dem Ventilkörper verschweißt ist, wird der Strahlverlauf durch den Kegelwinkel der Ventildichtfläche und die Orte der Unterbrechungen der umlaufenden Schweißnaht bestimmt. Bei einem zweiten beschriebenen Ausführungsbeispiel, bei dem das topfförmige Kopfstück in eine Aufnahmeöffnung des Ventilkörpers eingesetzt ist, sind die Einspritzöffnungen durch frei wählbare Aussparungen in der Wand des Ventilkörpers im Bereich der Überdeckung mit der Ventildichtfläche gebildet.Another advantage of the fuel injection valve according to the invention represents the provision of freely selectable injection openings, through which the jet position of the injected fuel is adjustable is. In a first embodiment, in which the head piece its radially outer area facing the valve body Face is welded to the valve body, the beam path by the cone angle of the valve sealing surface and the locations of the Interruptions in the circumferential weld seam determined. At a second described embodiment, in which the cup-shaped Head piece is inserted into a receiving opening of the valve body, are the injection openings through freely selectable recesses in the Wall of the valve body in the area of the overlap with the valve sealing surface educated.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung der Ausführungsbeispiele, der Zeichnung und den Ansprüchen entnehmbar. Further advantages and advantageous configurations of the object the invention are the description of the embodiments, the Drawing and the claims can be removed.
Zwei Ausführungsbeispiele des erfindungsgemäßen Kraftstoffeinspritzventils für Brennkraftmaschinen sind in der Zeichnung dargestellt und werden in der folgenden Beschreibung näher erläutert.Two embodiments of the invention Fuel injection valves for internal combustion engines are in of the drawing and are shown in the following Description explained in more detail.
Es zeigen die Figur 1 ein erstes Ausführungsbeispiel in einem Längsschnitt durch das Einspritzventil, die Figur 2 einen vergrößerten Ausschnitt aus der Figur 1, die Figur 3 einen Schnitt durch das Einspritzventil nach Figur 2 entlang der Ventilsitzfläche des Ventilkörpers, die Figur 4 ein zweites Ausführungsbeispiel analog zur Darstellung der Figur 2, die Figur 5 einen Schnitt durch den Ventilkörper der Figur 4 entlang der Einspritzöffnungen und die Figuren 6A bis 6F verschiedene Ausführungsmöglichkeiten des Kopfstückes der beiden Ausführungsbeispiele.1 shows a first exemplary embodiment in FIG 2 shows a longitudinal section through the injection valve, FIG. 2 FIG. 3 shows an enlarged section from FIG. 1 a section through the injection valve of Figure 2 along the valve seat surface of the valve body, the figure 4 a second embodiment analogous to the representation of the figure 2, Figure 5 shows a section through the valve body of the Figure 4 along the injection openings and Figures 6A up to 6F different design options for the head piece of the two embodiments.
Das in der Figur 1 dargestellte erste Ausführungsbeispiel
weist einen vorzugsweise rotationssymmetrischen Ventilkörper
1 auf, an dessen in den Brennraum der zu versorgenden
Brennkraftmaschine ragenden, unteren Ende ein ein
Ventilglied bildendes Kopfstück 3 befestigt ist. An seinem
oberen, brennraumfernen Ende weist der Ventilkörper 1 einen
Rohranschluß 5 auf, an den sich ein, den Ventilkörper 1 in
Längsrichtung durchdringender Druckkanal 7 anschließt, der
am brennraumnahen Ende des Ventilkörpers 1 an dessen untere
Stirnfläche mündet. An den Rohranschluß 5 ist eine nicht
näher dargestellte Kraftstoffeinspritzleitung zu einer
Kraftstoffeinspritzpumpe angeschlossen, die das
Einspritzventil mit unter hohem Druck stehenden Kraftstoff
beliefert.The first embodiment shown in Figure 1
has a preferably rotationally symmetrical valve body
1 on which in the combustion chamber of the to be supplied
Internal combustion engine protruding lower end one
Valve
Die untere, brennraumseitige Ringstirnfläche des
Ventilkörpers 1 bildet, wie in der Figur 2 vergrößert
dargestellt, eine Ventilsitzfläche 9, die konisch
ausgebildet ist. Mit dieser Ventilsitzfläche 9 wirkt eine
obere, dem Ventilkörper 1 zugewandte Stirnfläche des
Kopfstückes 3 zusammen, die eine Ventildichtfläche 11
bildet, die ebenfalls konisch ausgebildet ist. Dabei sind
die Kegelwinkel der Ventilsitzfläche 9 und der
Ventildichtfläche 11 derart geringfügig unterschiedlich
ausgebildet, daß eine Dichtkante an an der inneren Ringkante
der Ventilsitzfläche 9 gebildet wird.The lower ring face of the combustion chamber
Valve body 1 forms, as enlarged in Figure 2
shown, a valve seat surface 9 which is conical
is trained. With this valve seat surface 9 acts
upper end face of the valve body 1
Um ein federndes Ventilglied zu bilden, ist das Kopfstück 3
an seinem äußeren radialen Rand der dem Ventilkörper 1
zugewandten, die Ventildichtfläche bildenden Stirnfläche 11
mit dem unteren, brennraumseitigen Ende des Ventilkörpers 1
verschweißt. Dabei wird das Kopfstück 3 während des
Verschweißens mit hohem Druck axial gegen den Ventilkörper 1
gedrückt, so daß die Ventildichtfläche 11 unter Vorspannung
am Ventilsitz 9 anliegt.In order to form a resilient valve member, the
Die Verschweißung der beiden Bauteile miteinander erfolgt
dabei nicht über den gesamten Umfang, sondern ist wie in der
Figur 3 dargestellt an mehreren, im Ausführungsbeispiel vier
Bereichen unterbrochen. Diese Aussparungen 15 der
umlaufenden Schweißnaht 17 bilden dabei die
Einspritzöffnungen, an denen der Kraftstoff in den Brennraum
der Brennkraftmaschine austritt. Der Einspritzstrahlwinkel
ist dabei durch die Kegelwinkel der konischen Ventilsitz-
und Ventildichtfläche 9, 11 und die Strahlbreite durch die
Breite der Aussparungen 15 vorgegeben.The two components are welded together
not over the entire scope, but as in the
Figure 3 shown on several, four in the embodiment
Areas interrupted. These recesses 15 the
Bei dem in der Figur 4 dargestellten zweiten
Ausführungsbeispiel weist der Ventilkörper 1 an seinem
unteren, in den Brennraum ragenden Ende eine Aufnahmeöffnung
21 auf, in die das Kopfstück 3 vollständig eingesetzt ist.
Dabei bilden die obere Stirnfläche des Kopfstückes 3 wieder
eine Ventildichtfläche 11 und die untere Ringstirnfläche des
Ventilkörpers 1 eine Ventilsitzfläche 9, die ebenfalls
konisch ausgebildet sind und einen geringfügig voneinander
abweichenden Kegelwinkel aufweisen. Dabei kann die gebildete
Dichtkante 13 beim zweiten Ausführungsbeispiel sowohl innen
als auch außenliegend angeordnet sein.In the second shown in Figure 4
Exemplary embodiment has the valve body 1 on its
lower receiving end projecting into the
Die Erzeugung der Vorspannung der Ventildichtfläche 11 am
Ventilsitz 9 erfolgt beim zweiten Ausführungsbeispiel durch
eine Thermobehandlung bei der Montage. Dabei wird zunächst
der Ventilkörper 1 auf eine hohe Temperatur erhitzt, dann
wird das kalte Kopfstück 3 in die Aufnahmeöffnung 21 des
Ventilkörpers 1 eingesetzt und bei Anlage der
Ventildichtfläche 11 am Ventilsitz 9 am unteren,
brennraumzugewandten Ende mit der Wand der Aufnahmeöffnung
21 des Ventilkörpers 1 verschweißt. Nach dem
Temperaturausgleich der beiden Bauteile 1, 3 ergibt sich
infolge des Zusammenziehens des Ventilkörpers 1 beim
Abkühlen eine axiale Verspannung des Kopfstückes 3 gegen den
Ventilkörper 1.The generation of the bias of the
Die Einspritzöffnungen sind, wie auch der Figur 5
entnehmbar, beim zweiten Ausführungsbeispiel als
Ausnehmungen 23 in der Wand des Ventilkörpers 1 ausgebildet,
die sich über den Überdeckungsbereich mit der
Ventildichtfläche 11 erstrecken und deren Anordnung und
geometrische Form den Einspritzstrahl formen.The injection openings are, as in FIG. 5
removable, in the second embodiment as
Um eine möglichst gute federnde Membranwirkung an der
Ventildichtfläche des Kopfstückes 3 zu erzielen ist das
Kopfstück 3 wie in den Figuren 6A bis 6F dargestellt als
Hohlkörper ausgebildet. Lediglich die Figur 6B zeigt eine
Ausführungsvariante des Kopfstückes 3 als trichterförmige
Scheibe, deren Verwendung jedoch nur beim ersten, in den
Figuren 1 bis 3 gezeigten Ausführungsbeispiel vorteilhaft
ist.To achieve the best possible resilient membrane effect on the
To achieve valve sealing surface of the
Bei den in den übrigen Ausführungsbeispielen der Figur 6
gezeigten Hohlkörperformen des Kopfstückes 3 ist es
besonders wichtig, daß die obere, die Ventildichtfläche
bildende Stirnfläche 11 gut nach innen einfederbar ist,
wobei diese Federfunktion neben dem verwendeten Werkstoff
durch die Formgebung der oberen Stirnfläche 11 einstellbar
ist.In the case of the other exemplary embodiments in FIG. 6
It is shown hollow body shapes of the
Das erfindungsgemäße Kraftstoffeinspritzventil für
Brennkraftmaschinen arbeitet in folgender Weise:
Am Beginn der Einspritzphase strömt unter hohem Druck
stehender Kraftstoff über die Einspritzleitung in den
Druckkanal 7 und beaufschlagt die Ventildichtfläche 11 des
Kopfstückes 3 in Öffnungsrichtung. Dabei übersteigt ab einem
bestimmten Kraftstoffdruck die in Öffnungsrichtung wirkende
Druckkraft die Vorspannkraft am Kopfstück 3, mit der die
Ventildichtfläche 11 axial gegen den Ventilsitz 9 verspannt
ist und die Ventildichtfläche 11 hebt federnd vom Ventilsitz
9 ab. In Folge des geöffneten Querschnitts am Dichtsitz
strömt der Kraftstoff im ersten Ausführungsbeispiel in den
Ringspalt zwischen der Ventilsitzfläche 9 und der
Ventildichtfläche 11 und tritt an den Aussparungen 15 der
Schweißnaht 17 in den Brennraum der Brennkraftmaschine aus.
Im zweiten Ausführungsbeispiel strömt der Kraftstoff nach
Passieren des geöffneten Dichtquerschnitts zu den
Ausnehmungen 23 in der Wand des Ventilkörpers 1 und gelangt
von dort in den Brennraum.The fuel injection valve for internal combustion engines works in the following way:
At the beginning of the injection phase, fuel under high pressure flows via the injection line into the
Das Einspritzende erfolgt in bekannter Weise durch die
Beendigung der Hochdruckzufuhr zum Einspritzventil, in
dessen Folge der am Ventilglied anliegende Öffnungsdruck
wieder unter die notwendige Öffnungskraft sinkt, so daß die
federnde Ventildichtfläche 11 von der diese in
Schließrichtung beaufschlagenden Vorspannkraft erneut in
Anlage an den Ventilsitz 9 gebracht wird.The injection ends in a known manner by the
End of high pressure supply to the injection valve, in
the result of which is the opening pressure applied to the valve member
again falls below the necessary opening force, so that the
resilient
Dabei arbeitet das erfindungsgemäße Kraftstoffeinspritzventil sehr schnell und zuverlässig, da nahezu keine bewegten Massen auftreten.The inventive works Fuel injector very quickly and reliably because almost no moving masses occur.
Claims (9)
- Fuel injection valve for internal combustion engines, having a valve body (1) with, at its combustion-chamber end, a valve seat surface (9) being provided against which a valve element, which is arranged in a fixed position with respect to the valve body (1) and is designed as a head piece (3), bears under axial prestress by means of a valve-sealing surface (11), that end surface of the head piece (3) which faces the valve body (1) forming the valve-sealing surface (11), the valve furthermore having a pressure channel (7) which penetrates the valve body (1) in the longitudinal direction and opens into a pressure chamber which is bounded by the valve seat (9) and acts upon the end surface of the head piece (3) in the opening direction, and also having at least one injection opening, adjoining the valve seat surface (9) in the downstream direction, into the combustion chamber of the internal combustion engine to be supplied, characterized in that the head piece (3) is fastened directly to the combustion-chamber end of the valve body (1) in a nonreleasable manner by means of a welded connection at its outer, radial border.
- Fuel injection valve according to Claim 1, characterized in that the head piece (3) is designed in the region of the valve-sealing surface (11) as a resilient membrane which can be raised from the valve seat (9) by being subjected to fuel which is under high pressure.
- Fuel injection valve according to Claim 2, characterized in that the head piece (3) is designed as a hollow body whose closed end surface, which faces the valve body (1), forms the valve-sealing surface (11).
- Fuel injection valve according to Claim 1, characterized in that the valve seat surface (9) on the valve body (1) and the valve-sealing surface (11) on the head piece (3) are of conical design.
- Fuel injection valve according to Claim 1, characterized in that on the radially outer region of its end surface (11) facing the valve body (1), the head piece (3) is welded to that end surface of the valve body (1) which is at the combustion-chamber end and forms the valve seat surface (9).
- Fuel injection valve according to Claim 5, characterized in that the peripheral weld seam (17) has a multiplicity of cutouts (15) which form an injection opening when the valve-sealing surface (11) is raised from the valve seat (9).
- Fuel injection valve according to Claim 1, characterized in that the head piece (3) is inserted into a receiving opening (21) at the combustion-chamber end of the valve body (1), recesses (23), which form the injection openings, being provided in the wall of the valve body (1) in the region of overlap with the valve-sealing surface (11) of the head piece (3).
- Fuel injection valve according to Claim 7, characterized in that at its lower edge at the combustion-chamber end, between the circumferential surface and the lower annular end surface, the head piece (3) is welded to the wall of the receiving opening (21) of the valve body (1).
- Method for producing a fuel injection valve according to Claim 7, characterized by the following method steps:heating the valve body (1) to a high temperatureinserting the cold head piece (3) into the receiving opening (21) of the valve body (1)welding the head piece (3) in the receiving opening (21) of the valve body (1).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19547169A DE19547169A1 (en) | 1995-12-16 | 1995-12-16 | Fuel injection valve for internal combustion engines |
| DE19547169 | 1995-12-16 | ||
| PCT/DE1996/001409 WO1997022800A1 (en) | 1995-12-16 | 1996-07-30 | Fuel injection valve for internal combustion engines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0812391A1 EP0812391A1 (en) | 1997-12-17 |
| EP0812391B1 true EP0812391B1 (en) | 2001-11-07 |
Family
ID=7780409
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP96924779A Expired - Lifetime EP0812391B1 (en) | 1995-12-16 | 1996-07-30 | Fuel injection valve for internal combustion engines |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP0812391B1 (en) |
| JP (1) | JPH11501101A (en) |
| KR (1) | KR19980702177A (en) |
| BR (1) | BR9607297A (en) |
| DE (2) | DE19547169A1 (en) |
| WO (1) | WO1997022800A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006003668A1 (en) * | 2006-01-26 | 2007-08-02 | Bayerische Motoren Werke Ag | Fuel injection valve with outward opening nozzle needle e.g. for fuel injection valves, has longitudinal hole nozzle body and outward opening having nozzle needle which is movably provided in longitudinal hole |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB100445A (en) * | 1915-05-07 | 1917-01-25 | Oscar Robert Groenkwist | Means for Injecting Liquid Fuel, and other Liquids into Explosions Motors, Furnaces, and the like. |
| GB565999A (en) * | 1943-06-03 | 1944-12-07 | Henry Franz Pulitzer | Improvements in or relating to atomising nozzles for liquids |
| JPS62255571A (en) * | 1986-04-30 | 1987-11-07 | Nippon Denso Co Ltd | Fuel injection nozzle |
| DE9320433U1 (en) * | 1993-04-10 | 1994-09-29 | Bosch Gmbh Robert | Fuel injection nozzle for internal combustion engines |
-
1995
- 1995-12-16 DE DE19547169A patent/DE19547169A1/en not_active Withdrawn
-
1996
- 1996-07-30 DE DE59608147T patent/DE59608147D1/en not_active Expired - Fee Related
- 1996-07-30 WO PCT/DE1996/001409 patent/WO1997022800A1/en active IP Right Grant
- 1996-07-30 BR BR9607297A patent/BR9607297A/en not_active IP Right Cessation
- 1996-07-30 EP EP96924779A patent/EP0812391B1/en not_active Expired - Lifetime
- 1996-07-30 JP JP9522401A patent/JPH11501101A/en not_active Ceased
- 1996-07-30 KR KR1019970705572A patent/KR19980702177A/en active IP Right Grant
Also Published As
| Publication number | Publication date |
|---|---|
| DE19547169A1 (en) | 1997-06-19 |
| EP0812391A1 (en) | 1997-12-17 |
| KR19980702177A (en) | 1998-07-15 |
| JPH11501101A (en) | 1999-01-26 |
| BR9607297A (en) | 1997-11-25 |
| WO1997022800A1 (en) | 1997-06-26 |
| DE59608147D1 (en) | 2001-12-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| DE19547423B4 (en) | Fuel injection valve for internal combustion engines | |
| EP1119703B1 (en) | Fuel injection valve | |
| EP0937201A1 (en) | Electromagnetically operated valve | |
| EP1370765B1 (en) | Fuel injection valve | |
| DE19623713A1 (en) | Fuel injection valve for internal combustion engine | |
| DE10055483B4 (en) | Fuel injector | |
| DE19634933A1 (en) | Fuel injection valve for internal combustion engines | |
| DE3412625A1 (en) | METHOD FOR CONTROLLING THE DRAIN CROSS-SECTION OF INJECTION NOZZLES FOR DIRECTLY INJECTING INTERNAL COMBUSTION ENGINES AND INJECTION NOZZLE FOR CARRYING OUT THE METHOD | |
| DE19536330A1 (en) | Fuel injection valve for IC engines | |
| EP0812391B1 (en) | Fuel injection valve for internal combustion engines | |
| DE10027669A1 (en) | Fixing device for fuel injection valve has at least one sealing element in region of step in bush | |
| EP3034857A1 (en) | Fuel injector valve | |
| DE10063260A1 (en) | Fuel injector | |
| DE10063261B4 (en) | Fuel injector | |
| EP0811119B1 (en) | Fuel injection valve for internal combustion engines | |
| EP0927303B1 (en) | Fuel injection valve | |
| EP1209353B1 (en) | Fuel injection valve | |
| DE10059263B4 (en) | Process for the production or assembly of a fuel injection valve | |
| DE602004003212T3 (en) | Injector with means to prevent valve needle rotation | |
| DE10052146A1 (en) | Fuel injector | |
| WO2002029243A1 (en) | Fuel-injection valve | |
| AT500011B1 (en) | INJECTION ENGINE FOR INTERNAL COMBUSTION ENGINES | |
| DE19638339A1 (en) | Fuel injection valve for internal combustion engines | |
| DE102020215215A1 (en) | fuel injector | |
| DE102020214154A1 (en) | fuel injector |
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 |
|
| 17P | Request for examination filed |
Effective date: 19971229 |
|
| 17Q | First examination report despatched |
Effective date: 20000119 |
|
| 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 |
|
| REF | Corresponds to: |
Ref document number: 59608147 Country of ref document: DE Date of ref document: 20011213 |
|
| REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
| ET | Fr: translation filed | ||
| GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 20020208 |
|
| 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 | ||
| 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: 8 |
|
| 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: 20040730 |
|
| GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20040730 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20050916 Year of fee payment: 10 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20060719 Year of fee payment: 11 |
|
| 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: 20070201 |
|
| REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20080331 |
|
| 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: 20070731 |