EP1062423B1 - Fuel injection valve - Google Patents
Fuel injection valve Download PDFInfo
- Publication number
- EP1062423B1 EP1062423B1 EP99964369A EP99964369A EP1062423B1 EP 1062423 B1 EP1062423 B1 EP 1062423B1 EP 99964369 A EP99964369 A EP 99964369A EP 99964369 A EP99964369 A EP 99964369A EP 1062423 B1 EP1062423 B1 EP 1062423B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- transition region
- fuel injection
- upstream
- sealing
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
-
- 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
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
- F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
Definitions
- the invention relates to a fuel injection valve for internal combustion engines according to the preamble of the patent claim 1.
- fuel injectors are for example from DE 195 47 423 A1 and DE 196 34 133 A1 known.
- valves In such fuel injection valves is a piston-shaped one Valve member axially displaceable in one Drilled bore of a valve body.
- the valve member has a conical end on the combustion chamber side Valve sealing surface with which it is conical Valve seat surface cooperates on the valve body, at the inwardly projecting end of the closed valve bore is formed.
- the valve sealing surface on the valve member is in several, preferably two areas divided different cone angles, one Transition area between the two valve sealing surface areas is provided by a downstream side and an upstream valve sealing edge is limited.
- the valve member is elastically equal under the valve closing force to the nozzle body.
- the resulting one hydraulically effective seat diameter is in in this case arranged undefined in the transition area, as shown schematically in Fig. 1. Due to the inverse seat angle difference Pressure distribution at the offset from the axial direction A valve member, which the valve member back into the centric, axial position pushes back. In contrast to would look at a fuel injector without an inverse Seat angle difference set a pressure distribution, through which the valve member further from the centric, axial position would be moved.
- the invention has for its object a fuel injection itzventil of the generic type such further that it by axial alignment of the Valve member a symmetrical spray pattern and above a defined hydraulically effective seat diameter, a high damping of the valve member and enables the lowest possible risk of cavitation.
- the distance between the upstream valve sealing edge and the downstream valve sealing edge the transition area is chosen so that the upstream valve sealing edge of the transition area forms the hydraulically effective seat diameter.
- the distance can be determined by test measurements and / or Bills can be determined.
- a fuel injector shown in FIGS. 1 to 3 for internal combustion engines has a cylindrical valve body 1 on with its free lower End in a combustion chamber, not shown protrudes with fuel to be supplied to the internal combustion engine.
- An axial blind bore 3 is provided in the valve body 1, in which a piston-shaped valve member 5 axially is slidably guided.
- the valve member 5 instructs a conical valve sealing surface at its lower end near the combustion chamber 7 with which it is used to control a Injection cross section with a conical valve seat 9 at the combustion chamber end of the valve body 1 interacts with the closed cantilever End of the bore 3 is formed and from the injection openings 6 in the combustion chamber of the internal combustion engine out.
- the valve sealing surface 7 is like 3, in particular, in an upper region 71 and divided into a lower area. Between the upper area 71 and the lower area 72 a transition region 73 is formed. The angle that from the difference between transition area 73 and Valve seat surface 9 results must be smaller than that Angle resulting from the difference between valve seat area 9 and the lower area 72 results (inverse Seat angle difference). Adjacent to the downstream side Area 72 are injection openings in the valve body 1 20 provided.
- the upstream side Area 71 of the valve sealing surface has a radial, undercut-shaped recess 74. This forms a space formed by one on the valve body 1 Edge 75 is limited upstream.
- the transition region 73 is marked by an upstream Valve sealing edge 73a and a downstream side Valve sealing edge 73b limited, which is adjacent are arranged to each other that the hydraulic effective seat diameter during a closing process the upstream valve sealing edge 73a coincides. Because of this defined hydraulically effective Seat diameter becomes a resulting radial Prevents force on the valve member, which in the Fig. 1 shown undefined hydraulic effective seat diameter 90 occurs.
- the design of the distance between the two valve sealing edges 73a and 73b will be experimental and based determined by bills. With a maximum closing force of 1250 N, which are determined experimentally can result, for example, in a difference in diameter of approximately 0.15 mm with a geometric seat diameter of 2 mm. With this minimal transition area, i.e. with this minimal seating area is in any case guaranteed that the hydraulic effective seat diameter exactly with the valve sealing edge 73a coincides.
- the angle that the Damping room includes, chosen so that it is larger is than the body seat angle. In this way it is created in the closed state a damping room that one Effect similar to that of a sail Pressure cushion generated when the valve member 5 is closed, that increases the damping of the valve member 5.
- the fuel injector will close the fuel arranged in the damping space displaces and flows over between the valve member 5 and the edge 75 formed upstream gap from the damping room. The damping effect is due to the flow resistance generated by the gap generated during the closing process.
- the upstream side Edge 75 is designed so that it in Extreme case with complete deformation of the valve member has no distance from the valve body 5. Out this damping results in a lower tip load.
- Such a fuel injection valve also has the advantage that the bladder collapse of the cavitation bubbles preferably in the area upstream of the edge 75 takes place because the originating from the injection pump Pressure waves through edge 75 from the transition area be kept away. This does not cause damage the seating area.
- valve holding body (not shown) tends to an opening pressure drop, whereas the valve member 5 due to the inverse seat angle difference to an increase in opening pressure tends. Opposing effects occur that partially cancel each other out. hereby the service life of the fuel injector increases.
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 betrifft ein Kraftstoffeinspritzventil für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1. Derartige Kraftstoffeinspritzventile sind beispielsweise aus der DE 195 47 423 A1 sowie der DE 196 34 133 A1 bekannt.The invention relates to a fuel injection valve for internal combustion engines according to the preamble of the patent claim 1. Such fuel injectors are for example from DE 195 47 423 A1 and DE 196 34 133 A1 known.
Bei derartigen Kraftstoffeinspritzventilen ist ein kolbenförmiges Ventilglied axial verschiebbar in einer Bohrung eines Ventilkörpers geführt. Das Ventilglied weist dabei an seinem brennraumseitigen Ende eine konische Ventildichtfläche auf, mit der es mit einer konischen Ventilsitzfläche am Ventilkörper zusammenwirkt, die am nach innen kragenden Ende der geschlossenen Ventilbohrung gebildet ist. Die Ventildichtfläche am Ventilglied ist in mehrere, vorzugsweise zwei Bereiche mit unterschiedlichen Kegelwinkeln unterteilt, wobei ein Übergangsbereich zwischen den beiden Ventildichtflächenbereichen vorgesehen ist, der von einer stromabwärtsseitigen und einer stromaufwärtsseitigen Ventildichtkante begrenzt wird.In such fuel injection valves is a piston-shaped one Valve member axially displaceable in one Drilled bore of a valve body. The valve member has a conical end on the combustion chamber side Valve sealing surface with which it is conical Valve seat surface cooperates on the valve body, at the inwardly projecting end of the closed valve bore is formed. The valve sealing surface on the valve member is in several, preferably two areas divided different cone angles, one Transition area between the two valve sealing surface areas is provided by a downstream side and an upstream valve sealing edge is limited.
Aufgrund der hohen Ventilschließkräfte, die besonders bei diesen Kraftstoffeinspritzventilen der "Lochdüsen-Bauart" auftreten, tritt insbesondere bei sehr geringen Hüben des Ventilglieds oder beim Vorhub bei zwei Federhaltern ein unsymmetrisches Strahlbild auf, das zur Erhöhung der Emission der Brennkraftmaschine führt. Das Ventilglied gleicht sich dabei elastisch unter der Ventilschließkraft an den Düsenkörper an. Der dabei entstehende hydraulisch wirksame Sitzdurchmesser ist in diesem Falle undefiniert in dem Übergangsbereich angeordnet, wie es in Fig. 1 schematisch dargestellt ist. Durch die inverse Sitzwinkeldifferenz stellt sich eine Druckverteilung an dem aus der Axialrichtung versetzten Ventilglied ein, welche das Ventilglied wieder in die zentrische, axiale Lage zurückdrückt. Im Gegensatz dazu würde sich bei einem Kraftstoffeinspritzventil ohne inverse Sitzwinkeldifferenz eine Druckverteilung einstellen, durch welche das Ventilglied noch weiter aus der zentrischen, axialen Lage bewegt würde.Due to the high valve closing forces, the particular with these fuel injection valves of the "perforated nozzle type" occur, especially occurs at very low Lifting the valve member or during the preliminary stroke with two spring holders an asymmetrical beam pattern that increases the emission of the internal combustion engine leads. The The valve member is elastically equal under the valve closing force to the nozzle body. The resulting one hydraulically effective seat diameter is in in this case arranged undefined in the transition area, as shown schematically in Fig. 1. Due to the inverse seat angle difference Pressure distribution at the offset from the axial direction A valve member, which the valve member back into the centric, axial position pushes back. In contrast to would look at a fuel injector without an inverse Seat angle difference set a pressure distribution, through which the valve member further from the centric, axial position would be moved.
Der Erfindung liegt die Aufgabe zugrunde, ein Kraftstoffeinspr itzventil der gattungsgemäßen Art derart weiterzubilden, daß es durch axiale Ausrichtung des Ventilglieds ein symmetrisches Strahlbild und darüber hinaus einen definierten hydraulisch wirksamen Sitzdurchmesser, eine hohe Dämpfung des Ventilglieds und eine möglichst geringe Kavitationsgefährdung ermöglicht.The invention has for its object a fuel injection itzventil of the generic type such further that it by axial alignment of the Valve member a symmetrical spray pattern and above a defined hydraulically effective seat diameter, a high damping of the valve member and enables the lowest possible risk of cavitation.
Diese Aufgabe wird bei einem Kraftstoffeinspritzventil der eingangs beschriebenen Art erfindungsgemäß durch die Merkmale des Anspruchs 1 gelöst und hat den Vorteil, daß der hydraulisch wirksame Sitzdurchmesser insbesondere bei zunehmendem Verschleiß des Kraftstoffeinspritzventils durch die an den Übergangsbereich stromaufwärts im dem Ventilglied ausgebildete radiale, hinterschnittförmige Ausnehmung und die inverse Sitzwinkeldifferenz maximal bis zu der strömaufwärtsseitigen ventildichtkante "wandern" kann. Auf diese weise wird ein präzise definierter hydraulisch wirksamer Sitzdurchmesser an der stromaufwärtsseitigen Ventildichtkante erzielt.This task is done with a fuel injector of the type described above according to the invention solved the features of claim 1 and has the advantage that the hydraulically effective seat diameter in particular with increasing wear of the fuel injector through upstream to the transition area radial, undercut-shaped in the valve member Recess and the inverse seat angle difference up to the upstream side valve sealing edge can "wander". This way a precisely defined hydraulically effective seat diameter on the upstream valve sealing edge achieved.
Der Abstand zwischen der stromaufwärtsseitigen Ventildichtkante und der stromabwärtsseitigen Ventildichtkante des Übergangsbereichs wird dabei so gewählt, daß die stromaufwärtsseitige Ventildichtkante des Übergangsbereichs den hydraulisch wirksamen Sitzdurchmesser bildet. Der Abstand kann durch versuchsmessungen und/oder Rechnungen bestimmt werden.The distance between the upstream valve sealing edge and the downstream valve sealing edge the transition area is chosen so that the upstream valve sealing edge of the transition area forms the hydraulically effective seat diameter. The distance can be determined by test measurements and / or Bills can be determined.
Ein Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils für Brennkraftmaschinen sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.An embodiment of the fuel injection valve according to the invention for internal combustion engines are in shown in the drawing and in the description below explained in more detail.
In der Zeichnung zeigen:
- Fig. 1
- schematisch den hydraulisch wirksamen Sitzdurchmesser bei einem aus dem Stand der Technik bekannten Ventil;
- Fig. 2
- ein von der Erfindung Gebrauch machendes Kraftstoffeinspritzventil und
- Fig. 3
- eine vergrößerte Ausschnittdarstellung des in Fig. 2 dargestellten Kraftstoffeinspritzventils.
- Fig. 1
- schematically the hydraulically effective seat diameter in a valve known from the prior art;
- Fig. 2
- a fuel injector making use of the invention; and
- Fig. 3
- an enlarged sectional view of the fuel injector shown in Fig. 2.
Ein in Fig. 1 bis Fig. 3 dargestelltes Kraftstoffeinspritzventil
für Brennkraftmaschinen weist einen zylindrischen
ventilkörper 1 auf, der mit seinem freien unteren
Ende in einem nicht dargestellten Brennraum der
mit Kraftstoff zu versorgenden Brennkraftmaschine ragt.
Im Ventilkörper 1 ist eine axiale Sackbohrung 3 vorgesehen,
in der ein kolbenförmiges Ventilglied 5 axial
verschiebbar geführt ist. Das Ventilglied 5 weist an
seinem unteren, brennraumnahen Ende eine konische Ventildichtfläche
7 auf, mit der es zur Steuerung eines
Einspritzquerschnitts mit einer konischen Ventilsitzfläche
9 am brennraumseitigen Ende des Ventilkörpers 1
zusammenwirkt, die am nach innen kragenden geschlossenen
Ende der Bohrung 3 gebildet ist und von der Einspritzöffnungen
6 in den Brennraum der Brennkraftmaschine
ausgehen. Die ventildichtfläche 7 ist dabei wie
insbesondere aus Fig. 3 hervorgeht, in einen oberen Bereich
71 und in einen unteren Bereich geteilt. zwischen
dem oberen Bereich 71 und dem unteren Bereich 72 ist
ein Übergangsbereich 73 ausgebildet. Der Winkel, der
sich aus der Differenz zwischen Übergangsbereich 73 und
Ventilsitzfläche 9 ergibt, muß kleiner sein als der
Winkel, der sich aus der Differenz zwischen Ventilsitzfläche
9 und dem unteren Bereich 72 ergibt (inverse
Sitzwinkeldifferenz). Benachbart zu dem stromabwärtsseitigen
Bereich 72 sind in dem Ventilkörper 1 Einspritzöffnungen
20 vorgesehen. Der stromaufwärtsseitige
Bereich 71 der Ventildichtfläche weist eine radiale,
hinterschnittförmige Ausnehmung 74 auf. Diese bildet
einen Raum, der von einer an dem Ventilkörper 1 ausgebildeten
Kante 75 stromaufwärtsseitig begrenzt wird.
Der Übergangsbereich 73 wird durch eine stromaufwärtsseitige
Ventildichtkante 73a und eine stromabwärtsseitige
Ventildichtkante 73b begrenzt, die derart benachbart
zueinander angeordnet sind, daß der hydraulisch
wirksame Sitzdurchmesser bei einem Schließvorgang mit
der stromaufwärtsseitigen Ventildichtkante 73a zusammenfällt.
Aufgrund dieses definierten hydraulisch wirksamen
Sitzdurchmesser wird eine resultierende radiale
Kraft auf das Ventilglied verhindert, die bei dem in
Fig. 1 dargestellten undefiniert verlaufenden hydraulisch
wirksamen Sitzdurchmesser 90 auftritt.A fuel injector shown in FIGS. 1 to 3
for internal combustion engines has a cylindrical
valve body 1 on with its free lower
End in a combustion chamber, not shown
protrudes with fuel to be supplied to the internal combustion engine.
An axial
Die Auslegung des Abstands der beiden Ventildichtkanten
73a und 73b wird experimentell und auf der Grundlage
von Rechnungen ermittelt. Bei einer maximalen Schließkraft
von 1250 N, die experimentell bestimmt werden
kann, ergibt sich beispielsweise eine Durchmesserdifferenz
von ungefähr 0,15 mm bei einem geometrischen Sitzdurchmesser
von 2 mm. Bei diesem minimalen Übergangsbereich,
d.h. bei dieser minimalen Sitzangleichsfläche
ist auf jeden Fall gewährleistet, daß der hydraulisch
wirksame Sitzdurchmesser genau mit der Ventildichtkante
73a zusammenfällt.The design of the distance between the two
Durch die radiale Ausnehmung 74 im Ventilglied 5 wird
ein Dämpfungsraum geschaffen, der eine sehr hohe Dämpfung
des Ventilglieds 5 bei einem Schließvorgang ermöglicht.
Dabei wird vorzugsweise der Winkel, der den
Dämpfungsraum einschließt, so gewählt, daß er größer
ist als der Körpersitzwinkel. Auf diese Weise entsteht
im geschlossenen Zustand ein Dämpfungsraum, der einen
Effekt ähnlich dem eines Segels hervorruft und ein
Druckpolster beim Schließen des Ventilglieds 5 erzeugt,
das die Dämpfung des Ventilglieds 5 verstärkt. Bei einem
Schließvorgang des Kraftstoffeinspritzventils wird
der in dem Dämpfungsraum angeordnete Brennstoff verdrängt
und strömt über den zwischen dem Ventilglied 5
und der Kante 75 gebildeten Spalt stromaufwärtsseitig
aus dem Dämpfungsraum. Der Dämpfungseffekt wird aufgrund
des durch den Spalt erzeugten Strömungswiderstands
beim Schließvorgang erzeugt. Die stromaufwärtsseitige
Kante 75 wird dabei so ausgelegt, daß sie im
Extremfall bei vollständiger Deformation des Ventilglieds
keinen Abstand zum Ventilkörper 5 aufweist. Aus
dieser Dämpfung resultiert eine geringere Kuppenbelastung. Through the
Ein derartiges Kraftstoffeinspritzventil weist ferner
den Vorteil auf, daß der Blasenkollaps der Kavitationsblasen
vorzugsweise im Bereich stromaufwärts der Kante
75 erfolgt, da die von der Einspritzpumpe herrührenden
Druckwellen durch die Kante 75 von dem Übergangsbereich
ferngehalten werden. Dadurch kommt es nicht zur Schädigung
des Sitzbereichs.Such a fuel injection valve also has
the advantage that the bladder collapse of the cavitation bubbles
preferably in the area upstream of the
Der (nicht dargestellte) Ventilhaltekörper tendiert zu
einem Öffnungsdruckabfall, wohingegen das Ventilglied 5
wegen der inversen Sitzwinkeldifferenz zu einem Öffnungsdruckanstieg
tendiert. Es treten gegenläufige Effekte
auf, die sich zum Teil wieder aufheben. Hierdurch
steigt die Lebensdauer des Kraftstoffeinspritzventils.The valve holding body (not shown) tends to
an opening pressure drop, whereas the
Claims (2)
- Fuel injection valve for internal combustion engines, having a valve element (5) which can be displaced axially in a bore (3) of a valve body (1) and, at its end which faces the combustion space of the internal combustion engine, has a conical valve-sealing surface (7) with which it interacts with a conical valve seat surface (9) at that end of the bore (3) of the valve body (1) which is closed on the combustion-space side, the conical valve-sealing surface (7) on the valve element (5) being divided into two regions (71, 72) which have different cone angles and at the transition of which a transition region (73) bounded by a valve-sealing edge (73a) on the upstream side and a valve-sealing edge (73b) on the downstream side is formed, the difference of the cone angles of the transition region (73) and of the valve seat surface (9) being smaller than the difference of the cone angles of the region (72) on the downstream side and of the valve seat surface (9), characterized in that a radial recess (74) which is formed in the valve element (5) adjoins the transition region (73) upstream and is bounded by that sealing edge (73a) of the transition region (73) which is on the upstream side and by an edge (75) formed with respect to the valve body (1).
- Fuel injection valve according to Claim 1, characterized in that the valve-sealing edges (73a, 73b) which bound the transition region (73) are arranged so closely adjacent to each other that the valve-sealing edge (73a) on the upstream side forms a hydraulically effective seat diameter.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19901057A DE19901057A1 (en) | 1999-01-14 | 1999-01-14 | Fuel injection valve for internal combustion engines |
| DE19901057 | 1999-01-14 | ||
| PCT/DE1999/003723 WO2000042316A1 (en) | 1999-01-14 | 1999-11-24 | Fuel injection valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1062423A1 EP1062423A1 (en) | 2000-12-27 |
| EP1062423B1 true EP1062423B1 (en) | 2004-08-11 |
Family
ID=7894152
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP99964369A Expired - Lifetime EP1062423B1 (en) | 1999-01-14 | 1999-11-24 | Fuel injection valve |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US6502554B1 (en) |
| EP (1) | EP1062423B1 (en) |
| JP (1) | JP4587248B2 (en) |
| KR (1) | KR100631298B1 (en) |
| DE (2) | DE19901057A1 (en) |
| WO (1) | WO2000042316A1 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10050600A1 (en) * | 2000-10-12 | 2002-04-25 | Siemens Ag | Injector for a fuel injection system |
| DE10105681A1 (en) * | 2001-02-08 | 2002-08-29 | Siemens Ag | Fuel injection valve for an internal combustion engine |
| EP1522721B1 (en) | 2003-10-06 | 2006-05-03 | Delphi Technologies, Inc. | Injection nozzle |
| DE10359302A1 (en) * | 2003-12-17 | 2005-07-21 | Robert Bosch Gmbh | Valve body with multi-cone geometry at the valve seat |
| JP2006307678A (en) * | 2005-04-26 | 2006-11-09 | Denso Corp | Fuel injection nozzle |
| US20070200011A1 (en) * | 2006-02-28 | 2007-08-30 | Caterpillar Inc. | Fuel injector having nozzle member with annular groove |
| EP2969318B1 (en) * | 2013-03-15 | 2018-07-25 | Schott Corporation | Glass-metal composites |
Family Cites Families (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1952816A (en) * | 1931-04-04 | 1934-03-27 | Bendix Res Corp | Fuel injector |
| JPS6058868U (en) * | 1983-09-30 | 1985-04-24 | いすゞ自動車株式会社 | Valve seat type fuel injection nozzle |
| JPS60169664A (en) * | 1984-02-14 | 1985-09-03 | Mitsui Eng & Shipbuild Co Ltd | Extra-high pressure fuel injection valve |
| SE448828B (en) * | 1985-06-07 | 1987-03-23 | Ingemanssons Ingenjorsbyra Ab | NOZZLE |
| JPH0158770U (en) * | 1987-10-07 | 1989-04-12 | ||
| JP2819702B2 (en) * | 1989-12-12 | 1998-11-05 | 株式会社デンソー | Fuel injection valve |
| US5020500A (en) * | 1990-03-28 | 1991-06-04 | Stanadyne Automotive Corp. | Hole type fuel injector and injection method |
| US5159911A (en) * | 1991-06-21 | 1992-11-03 | Cummins Engine Company, Inc. | Hot start open nozzle fuel injection systems |
| FI88333C (en) * | 1991-06-25 | 1993-04-26 | Waertsilae Diesel Int | FOERBAETTRAT INSPRUTNINGSVENTILARRANGEMANG FOER BRAENSLE |
| US5288025A (en) * | 1992-12-18 | 1994-02-22 | Chrysler Corporation | Fuel injector with a hydraulically cushioned valve |
| US5449121A (en) * | 1993-02-26 | 1995-09-12 | Caterpillar Inc. | Thin-walled valve-closed-orifice spray tip for fuel injection nozzle |
| US5647536A (en) * | 1995-01-23 | 1997-07-15 | Cummins Engine Company, Inc. | Injection rate shaping nozzle assembly for a fuel injector |
| EP0789142B1 (en) * | 1995-08-29 | 2003-02-05 | Isuzu Motors Limited | Storage type fuel injection device |
| DE19547423B4 (en) * | 1995-12-19 | 2008-09-18 | Robert Bosch Gmbh | Fuel injection valve for internal combustion engines |
| DE19634133C2 (en) | 1996-08-23 | 1999-03-11 | Siemens Ag | Microprocessor, in particular for use in a chip card, and chip card with such a microprocessor |
| DE19822503C1 (en) * | 1998-05-19 | 1999-11-25 | Siemens Ag | Control valve for fuel injector |
| GB9823028D0 (en) * | 1998-10-22 | 1998-12-16 | Lucas Ind Plc | Fuel injector |
-
1999
- 1999-01-14 DE DE19901057A patent/DE19901057A1/en not_active Withdrawn
- 1999-11-24 WO PCT/DE1999/003723 patent/WO2000042316A1/en active IP Right Grant
- 1999-11-24 DE DE59910205T patent/DE59910205D1/en not_active Expired - Lifetime
- 1999-11-24 EP EP99964369A patent/EP1062423B1/en not_active Expired - Lifetime
- 1999-11-24 JP JP2000593859A patent/JP4587248B2/en not_active Expired - Fee Related
- 1999-11-24 KR KR1020007009967A patent/KR100631298B1/en not_active IP Right Cessation
- 1999-11-24 US US09/646,189 patent/US6502554B1/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JP2002535537A (en) | 2002-10-22 |
| US6502554B1 (en) | 2003-01-07 |
| KR20010041733A (en) | 2001-05-25 |
| DE59910205D1 (en) | 2004-09-16 |
| WO2000042316A1 (en) | 2000-07-20 |
| JP4587248B2 (en) | 2010-11-24 |
| KR100631298B1 (en) | 2006-10-09 |
| EP1062423A1 (en) | 2000-12-27 |
| DE19901057A1 (en) | 2000-07-27 |
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