EP1327066A2 - Fuel injection valve - Google Patents

Fuel injection valve

Info

Publication number
EP1327066A2
EP1327066A2 EP01986742A EP01986742A EP1327066A2 EP 1327066 A2 EP1327066 A2 EP 1327066A2 EP 01986742 A EP01986742 A EP 01986742A EP 01986742 A EP01986742 A EP 01986742A EP 1327066 A2 EP1327066 A2 EP 1327066A2
Authority
EP
European Patent Office
Prior art keywords
threaded rod
fuel injection
valve seat
injection valve
fuel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP01986742A
Other languages
German (de)
French (fr)
Other versions
EP1327066B1 (en
Inventor
Hubert Stier
Joerg Heyse
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1327066A2 publication Critical patent/EP1327066A2/en
Application granted granted Critical
Publication of EP1327066B1 publication Critical patent/EP1327066B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/1846—Dimensional characteristics of 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0671—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto
    • 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
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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
    • F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging 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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1853—Orifice plates

Definitions

  • the invention relates to a fuel injector according to the preamble of the main claim.
  • Fuel injection valves that have a swirl-generating element downstream of a sealing seat are e.g. known from DE 31 21 572 AI.
  • a cylindrical component is pressed into a bore which is arranged coaxially to the central axis of the fuel injection valve and which leads from a sealing seat to the spray opening and which has grooves in the cylinder jacket surface which connect the two cylinder faces to one another.
  • the grooves are arranged in a spiral and apply a swirl to the fuel flow when the fuel injector is open.
  • the grooves can be used to implement various spray patterns of the fuel jet. be adjusted in terms of their cross-section and their slope.
  • the metering of the injected fuel is also set via the grooves, which are supplemented by the valve seat body to form closed swirl channels.
  • Another fuel injector is known from US 4,520,962. Downstream of a ball valve is a rod, in 'the surface of which grooves are provided. These grooves are also arranged spirally to generate a swirl and are supplemented by the valve seat body to form closed swirl channels. Downstream there is a conically shaped spray opening.
  • a disadvantage of the fuel injectors mentioned is the complex production of the cylindrical swirl insert.
  • the introduction of individual swirl grooves is costly and time-consuming. Machining technologies are mostly used. which require reworking due to the formation of burrs when inserting the grooves.
  • the fuel injector according to the invention has the advantage that an inexpensive component can be used to generate a swirl flow through the formation of swirl channels through the threads of a threaded rod.
  • the swirl insert can be cut to length from long threaded rods with the required number of threads.
  • Threaded rods are usually manufactured without cutting using roll forming. A complex post-processing of the swirl insert is not necessary.
  • the central axis of the bore for receiving the swirl insert against the central axis of the fuel injector can include a non-zero angle. Due to the inclination of the entire swirl-generating unit with respect to the central axis of the fuel injection valve, there is no need to deflect the swirled fuel flow with the associated flow losses.
  • a swirl chamber arranged downstream of the swirl insert can influence the uniformity of the swirl in the fuel flow and thus a change in the spray pattern can be achieved. At the same time, the reduction in the flow cross-section causes the spray opening . an increase in swirl.
  • the swirl insert is formed a cavity upstream 'sung by the Zumes be sprayed the fuel takes place.
  • Figure 1 is a schematic partial section through a first embodiment of a fuel injector according to the invention.
  • Fig. 2 is a schematic partial section in section II of FIG. 1 through the first embodiment of a fuel injector according to the invention
  • the fuel injector 1 is in the form of a fuel injector 1 for fuel injection systems of mixture-compressing, spark-ignited
  • the fuel injection valve 1 is' in particular for the direct injection of fuel into an undepicted combustion chamber of an internal combustion engine.
  • the fuel injector 1 consists of . a nozzle body 2, in which a valve needle 3 is arranged.
  • the valve needle 3 is operatively connected to a valve closing body 4, which cooperates with a valve seat surface 6 arranged on a valve seat body 5 to form a sealing seat.
  • In the fuel injector 1 J in the exemplary embodiment is an electromagnetically actuated fuel injection valve 1 which has a spray opening 7.
  • the nozzle body 2 is sealed by 'a seal 8 from external pole 9 of a magnetic coil 10 degrees.
  • the magnet coil 10 is encapsulated in a coil housing 11 and wound on a coil carrier 12, which bears against an inner pole 13 of the magnet coil 10.
  • the inner pole 13 and the outer pole 9 are separated from one another by a gap 26 and are supported on a connecting component 29.
  • the magnet coil 10 is excited via a line 19 by an electrical current that can be supplied via an electrical plug contact 17.
  • the plug contact 17 is surrounded by a plastic sheath 18, which can be molded onto the inner pole 13.
  • valve needle 3 is guided in a valve needle guide 14, which is disc-shaped.
  • a paired adjusting disk 15 is used for stroke adjustment.
  • An armature 20 is located on the other side of the adjusting disk 15. This armature is non-positively connected to the valve needle 3 i via a flange 21. Connection which is connected to the flange 21, for example via a weld seam 22.
  • a restoring spring 23 is supported on the flange 21, which in the present design of the fuel injector 1 is preloaded by a sleeve 24.
  • Fuel channels 30a, 30b run in the valve needle guide 14 and in the armature 20.
  • the fuel is supplied via a central fuel supply 16 and filtered by a filter element 25.
  • the fuel is guided through fuel channels 30c, which run between the valve closing body 4 and the valve seat body 5 along flats 32 on the valve closing body 4, to the sealing seat.
  • the fuel injector 1 is sealed by a seal 28 against a distribution line, not shown.
  • the armature 20 is released by the return spring 23 via the flange 21 on the valve needle 3. acted against its stroke direction so that the valve closing body 4 is held in sealing contact with the valve seat surface 6 and the valve closing body 4 is in its stroke downward stroke-limiting end position.
  • the magnet coil 10 When the magnet coil 10 is excited, it builds up a magnetic field which moves the armature 20 in the stroke direction against the spring force of the return spring 23.
  • the armature 20 takes the flange 21, which is welded to the valve needle 3, and thus also the valve needle 3 in the lifting direction.
  • a fuel injection valve 1 according to the invention is shown in FIG. 2. Downstream of the sealing seat, a bore 35 is made in the valve seat body 5, into which a threaded rod 36 is pressed, downstream of which a conical taper 37 connects to the bore 35, which opens into the spray opening 7.
  • the central axis 38 of the bore 35 made in the valve seat body 5 is preferably inclined at an angle different from zero with respect to the central axis 39 of the fuel injection valve 1.
  • the diameter of the Bore 35 corresponds to the outside diameter of the threaded rod 36 to be pressed in.
  • the threads of the threaded rod 36 are closed through the bore 35 of the valve seat body 5 to swirl channels 33. At least one complete thread, preferably at least two complete threads, runs in the bore 35.
  • the use of threaded rods 36 of different pitches enables the twist generation to be changed with the same outer diameter of the threaded rod 36 and thus increases the proportion of components to be manufactured identically in the production of the fuel injection valve 1
  • the threaded rod 36 is pressed into the valve seat body 5 from the upstream side until its downstream end face 40b is in contact with the conical taper 37.
  • the conical taper 37 forms, upstream from the downstream end face 40b of the threaded rod 36, a swirl chamber 34 and opens downstream into the spray opening 7.
  • the swirl chamber 34 is connected by the swirl channels 33 to a cavity formed upstream of the threaded rod 36.
  • FIG 3 shows a second exemplary embodiment of a fuel injection valve 1 according to the invention.
  • the threaded rod 36 is pressed into the valve seat body 5 from the downstream side.
  • the spray opening 7 is arranged in a spray orifice plate 42, which e.g. is fixed by welding on the downstream side of the valve seat body 5.
  • the valve seat body 5 has, downstream of the sealing seat, an overflow bore 43, the diameter of which is smaller than the core diameter of the threaded rod 36 to be pressed in, and the central axis thereof preferably with the Center axis 38 of a downstream one
  • Hole 35 is identical and different from zero
  • the diameter of the bore 35 corresponds to the outer diameter of the threaded rod 36 to be pressed in.
  • the downstream end of the bore 35 emerges on the downstream side
  • Valve seat body 5 has a preferably flat surface 44 in the region of bore 35, the surface normal of which is identical to the central axis of bore 35.
  • the spray orifice plate 42 is on the valve seat body 5 e.g. attached by welding.
  • the upstream side 41 of the spray orifice plate 42 which is in contact with the surface 44 of the valve seat body 5 has a shape corresponding to the valve seat body 5.
  • the spray opening 7 is introduced in the spray orifice plate 42 in such a way that the central axis of the spray opening 7 is identical to the central axis 38 of the bore 35 in order to achieve a symmetrical spray pattern.
  • the diameter of the spray opening 7 is smaller than the diameter of the bore 35 and preferably also smaller than the core diameter of the threaded rod 36. be manufactured as a stamped part.
  • the pressed-in threaded rod 36 is shorter than the bore 35. Between the upstream end face 40a of the threaded rod 36 and the upstream end of the bore 35, a cavity 45 is formed, the height of which is determined by the distance between the upstream end face 40a of the threaded rod and the upstream end of the bore 35 is determined.
  • the swirl chamber 34 Downstream of the threaded rod -36, the swirl chamber 34 is arranged, which is formed between the downstream end face 40b of the threaded rod 36 and the upstream side 41 of the spray plate 42.
  • the swirl formed in the fuel flow is evened out in the swirl chamber 34 before the fuel flows through the spray opening 7 and is sprayed into the combustion chamber (not shown) of an internal combustion engine.
  • the center axes of the bores 35, 43 or the spray spray opening 7 can differ from one another with regard to their position and angle.
  • the preparation of the swirl of the fuel flow can be realized by using threaded rods 36, the threads of which differ with regard to the ratio of core and outer diameter and / or the pitch.
  • the influence of different lengths of the threaded rods 36 and the associated different number of twist-forming threads can also be used.

Abstract

The invention relates to a fuel injection valve (1) for fuel injection systems of internal combustion engines. Said fuel injection valve comprises a valve closing element (4) that is functionally linked with a valve needle (3) and that interacts with a valve face (6) of a valve seat (5) to give a sealing seat. The valve is further provided with a swirl-producing element that is located downstream of the sealing seat in the valve seat (5) and whose center axis (38) preferably includes an angle different from zero with the center axis (39) of the fuel injection valve (1). The swirl-producing element is a threaded rod (36) that is press-fitted into the valve seat (5).

Description

Brennstoffeinspritzvexitil Brennstoffeinspritzvexitil
Stand der TechnikState of the art
Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Hauptanspruchs .The invention relates to a fuel injector according to the preamble of the main claim.
Brennstoffeinspritzventile, die stromabwärts eines Dichtsitzes ein drallerzeugendes Element besitzen sind z.B. aus der DE 31 21 572 AI bekannt. Dabei ist in einer Bohrung, die koaxial zur Mittelachse des Brennstoffeinspritzventils angeordnet ist und die von einem Dichtsitz zur Abspritzöffnung führt, ein zylindrisches Bauteil eingepreßt, das in der Zylindermantelfläche Nuten aufweist, die die beiden Zylinderstirnseiten miteinander verbinden. Die Nuten sind spiralförmig angeordnet und beaufschlagen die BrennstoffStrömung bei geöffnetem Brennstoffeinspritzventil mit Drall. Zur Realisierung verschiedener Abspritzbilder des BrennstoffStrahls, können die Nuten . hinsichtlich ihres Querschnitts und ihrer Steigung angepaßt werden. Die Zu essung des eingespritzten Brennstoffs wird ebenfalls über die Nuten eingestellt, die von dem Ventilsitzkorper zu geschlossenen Drallkanälen ergänzt werden.Fuel injection valves that have a swirl-generating element downstream of a sealing seat are e.g. known from DE 31 21 572 AI. In this case, a cylindrical component is pressed into a bore which is arranged coaxially to the central axis of the fuel injection valve and which leads from a sealing seat to the spray opening and which has grooves in the cylinder jacket surface which connect the two cylinder faces to one another. The grooves are arranged in a spiral and apply a swirl to the fuel flow when the fuel injector is open. The grooves can be used to implement various spray patterns of the fuel jet. be adjusted in terms of their cross-section and their slope. The metering of the injected fuel is also set via the grooves, which are supplemented by the valve seat body to form closed swirl channels.
Ein weiteres Brennstoffeinspritzventil ist aus der US 4,520,962 bekannt. Stromabwärts eines Kugelventils befindet sich ein Stab, in "dessen Oberfläche Nuten eingebracht sind. Diese Nuten sind zur Erzeugung eines Dralls ebenfalls spiralförmig angeordnet und werden von dem Ventilsitzkorper zu geschlossenen Drallkanälen ergänzt. Stromabwärts schließt sich unmittelbar eine konusförmig erweiterte Abspritzöffnung an.Another fuel injector is known from US 4,520,962. Downstream of a ball valve is a rod, in 'the surface of which grooves are provided. These grooves are also arranged spirally to generate a swirl and are supplemented by the valve seat body to form closed swirl channels. Downstream there is a conically shaped spray opening.
Nachteilig bei den genannten Brennstoffeinspritzventilen ist die aufwendige Fertigung des zylinderförmigen Dralleinsatzes. Das Einbringen einzelner Drallnuten ist kosten- und zeitaufwendig. Dabei kommen meist spanende Bearbeitungstechnologien zum Einsatz. die aufgrund der Gratbildung beim Einbringen der Nuten eine Nachbearbeitung erfordern.A disadvantage of the fuel injectors mentioned is the complex production of the cylindrical swirl insert. The introduction of individual swirl grooves is costly and time-consuming. Machining technologies are mostly used. which require reworking due to the formation of burrs when inserting the grooves.
Weiterhin nachteilig auf die Kosten wirkt sich die hohe Präzision aus, die erforderlich ist, um die Ausbildung eines Nebenstromweges zu verhindern. Durch die Einhaltung einer Rundheitstoleranz hoher Güte wird die Abdichtung des Dralleinsatzes gegenüber dem Ventilsitzkorper erreicht. Dies hat eine vollständig durch die Drallkanäle geleitete BrennstoffStrömung zu Folge.The high precision that is required to prevent the formation of a bypass path also has a disadvantageous effect on the costs. By maintaining a roundness tolerance of high quality, the swirl insert is sealed off from the valve seat body. This results in a fuel flow completely directed through the swirl channels.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Brennstoffeinspritzventil gemäß dem kennzeichnenden Merkmal des Hauptanspruchs hat demgegenüber den Vorteil, daß durch die Ausbildung von Drallkanälen durch die Gewindegänge einer Gewindestange ein preiswertes Bauteil zur Erzeugung einer Drallströmung eingesetzt werden kann. Der Dralleinsatz kann von langen Gewindestangen mit der erforderlichen Anzahl an Gewindegängen abgelängt werden.The fuel injector according to the invention has the advantage that an inexpensive component can be used to generate a swirl flow through the formation of swirl channels through the threads of a threaded rod. The swirl insert can be cut to length from long threaded rods with the required number of threads.
Die Herstellung von GewindeStangen geschieht zumeist spanfrei durch Rollformen. Eine aufwendige Nachbearbeitung des Dralleinsatzes entfällt.Threaded rods are usually manufactured without cutting using roll forming. A complex post-processing of the swirl insert is not necessary.
Weiterhin von Vorteil ist, daß durch eine Mehrzahl von Gewindegängen, die in eine Bohrung eingepreßt sind, die Anforderungen an die Rundheit reduziert werden können. In axialer Richtung dichten mehrere Gewindegänge gegenüber dem Ventilsitzk rper ab. Durch die so ausgebildete' Labyrinthdichtung wird die Ausbildung eines axialen Nebenstromweges selbst bei großzügig tolerierten Bauteilen verhindert .Another advantage is that the roundness requirements can be reduced by a plurality of threads that are pressed into a bore. In In the axial direction, several threads seal against the valve seat body. The ' labyrinth seal designed in this way prevents the formation of an axial bypass path even with generously tolerated components.
Zum gezielten Abspritzen des Brennstoffs in eine durch die Geometrie des Zylinderkopfs vorgegebene Richtung kann die Mittelachse der Bohrung zur Aufnahme des Dralleinsatzes gegen Mittelachse des Brennstoffeinspritzventils einen von Null verschiedenen Winkel einschließen. Durch Neigung der ganzen drallerzeugenden Einheit gegenüber der Mittelachse des Brennstoffeinspritzventils entfällt eine Umlenkung der drallbehafteten BrennstoffStrömung mit den damit verbundenen Strömungsverlusten.For targeted spraying of the fuel in a direction predetermined by the geometry of the cylinder head, the central axis of the bore for receiving the swirl insert against the central axis of the fuel injector can include a non-zero angle. Due to the inclination of the entire swirl-generating unit with respect to the central axis of the fuel injection valve, there is no need to deflect the swirled fuel flow with the associated flow losses.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen des im Hauptanspruch angegebenen Brennstoffeinspritzventils möglich.The measures listed in the subclaims permit advantageous developments of the fuel injector specified in the main claim.
Durch eine stromabwärts an den Dralleinsatz anschließend angeordnete Drallkammer kann die Vergleichmäßigung des Dralls in der BrennstoffStrömung beeinflußt werden und so eine Veränderung des Abspritzbildes erreicht werden. Gleichzeitig bewirkt die Verringerung des Strömungsquerschnitts zu der Abspritzöffnung hin . eine Zunahme des Dralls.A swirl chamber arranged downstream of the swirl insert can influence the uniformity of the swirl in the fuel flow and thus a change in the spray pattern can be achieved. At the same time, the reduction in the flow cross-section causes the spray opening . an increase in swirl.
Weiterhin ist es möglich den Dralleinsatz von der stromabwärtigen Seite des Ventilsitzkörpers einzupressen. Dabei wird stromaufwärts des Dralleinsatzes ein Hohlraum erzeugt, durch den die Zumes'sung des abzuspritzenden Brennstoffs erfolgt.It is also possible to press in the swirl insert from the downstream side of the valve seat body. In this case, the swirl insert is formed a cavity upstream 'sung by the Zumes be sprayed the fuel takes place.
Zeichnungdrawing
Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen: Fig. 1 einen schematischen Teilschnitt durch ein erstes Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils;Embodiments of the invention are shown in simplified form in the drawing and explained in more detail in the following description. Show it: Figure 1 is a schematic partial section through a first embodiment of a fuel injector according to the invention.
Fig. 2 einen schematischen Teilschnitt im Ausschnitt II der Fig. 1 durch das erste Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils undFig. 2 is a schematic partial section in section II of FIG. 1 through the first embodiment of a fuel injector according to the invention and
Fig. 3 " einen schematischen Teilschnitt im Ausschnitt II der Fig. 1 durch ein zweites Ausführungsbeispiel eines erfindungsgemäßen3 "is a schematic partial section in section II of FIG. 1 through a second embodiment of an inventive
Brennstoffeinspritzventils .Fuel injector.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Bevor anhand der Figuren 2 und 3 zwei Ausführungsbeispiele eines erfindungsgemäßen Brennstoffeinspritzventils 1 näher beschrieben werden, soll zum besseren Verständnis der Erfindung zunächst anhand von Fig. 1 das erfindungsgemäße Brennstoffeinspritzventil 1 in einer Gesamtdarstellung bezüglich seiner wesentlichen Bauteile kurz erläutert werden.Before two exemplary embodiments of a fuel injector 1 according to the invention are described in more detail with reference to FIGS. 2 and 3, the fuel injector 1 according to the invention is first to be briefly explained in terms of its essential components with reference to FIG. 1, with reference to FIG. 1.
Das Brennstoffeinspritzventil 1 ist in der Form eines Brennstoffeinspritzventils 1 für Brennstoffeinspritzanlagen von gemischverdichtenden, fremdgezündetenThe fuel injector 1 is in the form of a fuel injector 1 for fuel injection systems of mixture-compressing, spark-ignited
Brennkraftmaschinen ausgeführt . Das Brennstoffeinspritzventil 1 eignet' sich insbesondere zum direkten Einspritzen von Brennstoff in einen nicht dargestellten Brennraum einer Brennkraftmaschine.Running internal combustion engines. The fuel injection valve 1 is' in particular for the direct injection of fuel into an undepicted combustion chamber of an internal combustion engine.
Das Brennstoffeinspritzventil 1 besteht aus . einem Düsenkörper 2, in welchem eine Ventilnadel 3 angeordnet ist. Die Ventilnadel 3 steht in Wirkverbindung mit einem Ventilschließkδrper 4, der mit einer auf einem Ventilsitzkorper 5 angeordneten Ventilsitzfläche 6 zu einem Dichtsitz zusammenwirkt. Bei dem Brennstoffeinspritzventil 1 J handelt es sich im Ausführungsbeispiel um ein elektromagnetisch betätigtes Brennstoffeinspritzventil 1, welches über eine Abspritzöffnung 7 verfügt. Der Düsenkörper 2 ist durch 'eine Dichtung 8 gegen den Außenpol 9 einer Magnetspule 10 abgedichtet. Die Magnetspule 10 ist in einem Spulengehäuse 11 gekapselt und auf einen Spulenträger 12 gewickelt, welcher an einem Innenpol 13 der Magnetspule 10 anliegt. Der Innenpol 13 und der Außenpol 9 sind durch einen Spalt 26 voneinander getrennt und stützen sich auf einem Verbindungsbauteil 29 ab. Die Magnetspule 10 wird über eine Leitung 19 von einem über einen elektrischen Steckkontakt 17 zuführbaren elektrischen Strom erregt. Der Steckkontakt 17 ist von einer Kunststoffummantelung 18 umgeben, die am Innenpol 13 angespritzt sein kann.The fuel injector 1 consists of . a nozzle body 2, in which a valve needle 3 is arranged. The valve needle 3 is operatively connected to a valve closing body 4, which cooperates with a valve seat surface 6 arranged on a valve seat body 5 to form a sealing seat. In the fuel injector 1 J in the exemplary embodiment is an electromagnetically actuated fuel injection valve 1 which has a spray opening 7. The nozzle body 2 is sealed by 'a seal 8 from external pole 9 of a magnetic coil 10 degrees. The magnet coil 10 is encapsulated in a coil housing 11 and wound on a coil carrier 12, which bears against an inner pole 13 of the magnet coil 10. The inner pole 13 and the outer pole 9 are separated from one another by a gap 26 and are supported on a connecting component 29. The magnet coil 10 is excited via a line 19 by an electrical current that can be supplied via an electrical plug contact 17. The plug contact 17 is surrounded by a plastic sheath 18, which can be molded onto the inner pole 13.
Die Ventilnadel 3 ist in einer Ventilnadelführung 14 geführt, welche scheibenförmig ausgeführt ist. Zur Hubeinstellung dient eine zugepaarte Einstellscheibe 15. An der anderen Seite der Einstellscheibe 15 befindet sich ein Anker 20. Dieser steht über einen Flansch 21 kraftschlüssig mit der Ventilnadel 3 i . Verbindung, welche beispielsweise über eine Schweißnaht 22 mit dem Flansch 21 verbunden ist. Auf dem Flansch 21 stützt sich eine Rückstellfeder 23 ab, welche in der- vorliegenden Bauform des Brennstoffeinspritzventils 1 durch eine Hülse 24 auf Vorspannung gebracht wird.The valve needle 3 is guided in a valve needle guide 14, which is disc-shaped. A paired adjusting disk 15 is used for stroke adjustment. An armature 20 is located on the other side of the adjusting disk 15. This armature is non-positively connected to the valve needle 3 i via a flange 21. Connection which is connected to the flange 21, for example via a weld seam 22. A restoring spring 23 is supported on the flange 21, which in the present design of the fuel injector 1 is preloaded by a sleeve 24.
In der Ventilnadelführung 14 und in dem Anker 20 verlaufen Brennsto fkanäle 30a, 30b. Der Brennstoff wird über eine zentrale Brennstoffzufuhr 16 zugeführt und durch ein Filterelement 25 gefiltert. Durch Brennstoffkanäle 30c, die zwischen dem Ventilschließkörper 4 und dem Ventilsitzkorper 5 entlang von Abflachungen 32 an dem Ventilschließkörper 4 verlaufen, wird der Brennstoff bis zu dem Dichtsitz geleitet. Das Brennstoffeinspritzventil 1 ist durch eine Dichtung 28 gegen eine nicht dargestellte Verteilerleitung abgedichtet . Im Ruhezustand des Brennstoffeinspritzventils 1 wird der Anker 20 über den Flansch 21 an der Ventilnadel 3 von der Rückstellfeder 23 . entgegen seiner Hubrichtung so beaufschlagt, daß der Ventilschließkδrper 4 an der Ventilsitzfläche 6 in dichtender Anlage gehalten wird und sich der Ventilschließkörper 4 in seiner stro abwärtig hubbegrenzenden Endposition befindet. Bei Erregung der Magnetspule 10 baut diese ein Magnetfeld auf, welches den Anker 20 entgegen der Federkraft der Rückstellfeder 23 in Hubrichtung bewegt. Der Anker 20 nimmt den Flansch 21, welcher mit der Ventilnadel 3 verschweißt ist, und damit die Ventilnadel 3 ebenfalls in Hubrichtung mit. Der mit der Ventilnadel 3 in Wirkverbindung stehende Ventilschließkörper 4 hebt von der Ventilsitzfläche 6 ab und der zu dem Ventildichtsitz gelangende Brennstoff strömt durch Drallkanäle 33 in eine Drallkammer 34, von dort zu der Abspritzöffnung 7 und wird abgespritzt.Fuel channels 30a, 30b run in the valve needle guide 14 and in the armature 20. The fuel is supplied via a central fuel supply 16 and filtered by a filter element 25. The fuel is guided through fuel channels 30c, which run between the valve closing body 4 and the valve seat body 5 along flats 32 on the valve closing body 4, to the sealing seat. The fuel injector 1 is sealed by a seal 28 against a distribution line, not shown. In the idle state of the fuel injection valve 1, the armature 20 is released by the return spring 23 via the flange 21 on the valve needle 3. acted against its stroke direction so that the valve closing body 4 is held in sealing contact with the valve seat surface 6 and the valve closing body 4 is in its stroke downward stroke-limiting end position. When the magnet coil 10 is excited, it builds up a magnetic field which moves the armature 20 in the stroke direction against the spring force of the return spring 23. The armature 20 takes the flange 21, which is welded to the valve needle 3, and thus also the valve needle 3 in the lifting direction. The valve closing body 4, which is operatively connected to the valve needle 3, lifts off the valve seat surface 6 and the fuel reaching the valve sealing seat flows through swirl channels 33 into a swirl chamber 34, from there to the spray opening 7 and is sprayed off.
Wird der Spulenstrom abgeschaltet, fällt der Anker 20 nach genügendem Abbau des Magnetfeldes durch den Druck der Rückstellfeder.23 auf den Flansch 21 vom Innenpol 13 ab, wodurch sich die Ventilnadel 3 entgegen der Hubrichtung bewegt. Dadurch setzt der Ventilschließkörper 4 auf der Ventilsitzfläche 6 auf, und das Brennstoffeinspritzventil 1 wird geschlossen.If the coil current is switched off, the armature 20 drops from the inner pole 13 after the magnetic field is sufficiently reduced by the pressure of the return spring 23 on the flange 21, as a result of which the valve needle 3 moves counter to the stroke direction. As a result, the valve closing body 4 rests on the valve seat surface 6 and the fuel injection valve 1 is closed.
In Fig. 2 ist ein erfindungsgemäßes Brennstoffeinspritzventil 1 dargestellt. Stromabwärts des Dichtsitzes ist eine Bohrung 35 in den Ventilsitzkorper 5 eingebracht, in die eine Gewindestange 36 eingepreßt ist, stromabwärts derer sich eine konusförmige Verjüngung 37 an die Bohrung 35 anschließt, die in die Abspritzöffnung 7 ausmündet .A fuel injection valve 1 according to the invention is shown in FIG. 2. Downstream of the sealing seat, a bore 35 is made in the valve seat body 5, into which a threaded rod 36 is pressed, downstream of which a conical taper 37 connects to the bore 35, which opens into the spray opening 7.
Die Mittelachse 38 der in dem Ventilsitzkorper 5 eingebrachten Bohrung 35 ist gegenüber der Mittelachse 39 des Brennstoffeinspritzventils 1 vorzugsweise um einen von Null verschiedenen Winkel geneigt. Der Durchmesser der Bohrung 35 korrespondiert mit dem Außendurchmesser der einzupressenden Gewindestange 36.The central axis 38 of the bore 35 made in the valve seat body 5 is preferably inclined at an angle different from zero with respect to the central axis 39 of the fuel injection valve 1. The diameter of the Bore 35 corresponds to the outside diameter of the threaded rod 36 to be pressed in.
Die Gewindegänge der Gewindestange 36 werden durch die Bohrung 35 des Ventilsitzkörpers 5 zu Drallkanälen 33 verschlossen. Es verläuft zumindest ein vollständiger Gewindegang, vorzugsweise zumindest zwei vollständige Gewindegänge in der Bohrung 35. Die Verwendung von Gewindestangen 36 verschiedener Steigungen ermöglicht eine Veränderung der Drallerzeugung bei gleichem Außendurchmesser der Gewindestange 36 und erhöht somit den Anteil identisch zu fertigender Bauteile bei der Herstellung des Brennstoffeinspritzventils 1. Die Gewindestange 36 ist von stromaufwärtiger Seite in den Ventilsitzkorper 5 so weit eingepreßt, bis ihre stromabwärtige Stirnfläche 40b mit der konusfδrmigen Verjüngung 37 in Kontakt ist.The threads of the threaded rod 36 are closed through the bore 35 of the valve seat body 5 to swirl channels 33. At least one complete thread, preferably at least two complete threads, runs in the bore 35. The use of threaded rods 36 of different pitches enables the twist generation to be changed with the same outer diameter of the threaded rod 36 and thus increases the proportion of components to be manufactured identically in the production of the fuel injection valve 1 The threaded rod 36 is pressed into the valve seat body 5 from the upstream side until its downstream end face 40b is in contact with the conical taper 37.
Die konusförmige Verjüngung 37 bildet, von der stromabwärtigen Stirnfläche 40b der Gewindestange 36 stromaufwärts begrenzt, eine Drallkammer 34 und mündet stromabwärts in die Abspritzöf nung 7. Die Drallkammmer 34 ist durch die Drallkanäle 33 mit einem stromaufwärts der Gewindestange 36 ausgebildeten Hohlraum verbunden. Bei geöffnetem Brennstoffeinspritzventil 1 tritt Brennstoff in die Drallkammer 34 ein, wo sich der Drall vergleichmäßigt und durch die Verengung des Querschnitts verstärkt .The conical taper 37 forms, upstream from the downstream end face 40b of the threaded rod 36, a swirl chamber 34 and opens downstream into the spray opening 7. The swirl chamber 34 is connected by the swirl channels 33 to a cavity formed upstream of the threaded rod 36. When the fuel injection valve 1 is open, fuel enters the swirl chamber 34, where the swirl is evened out and increased by the narrowing of the cross section.
In Fig. 3 ist ein zweites Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils 1 dargestellt . Die Gewindestange 36 ist von der stromabwärtigen Seite in den Ventilsitzkorper 5 eingepreßt. Die Abspritzö fnung 7 ist in einer Spritzlochscheibe 42 angeordnet,- die z.B. durch Schweißen an der stromabwärtigen Seite des Ventilsitzkörpers 5 befestigt ist.3 shows a second exemplary embodiment of a fuel injection valve 1 according to the invention. The threaded rod 36 is pressed into the valve seat body 5 from the downstream side. The spray opening 7 is arranged in a spray orifice plate 42, which e.g. is fixed by welding on the downstream side of the valve seat body 5.
Der Ventilsitzkorper 5 weist stromabwärts des Dichtsitzes eine Überströmbohrung 43 auf, deren Durchmesser kleiner ist, als der -Kerndurchmesser der einzupressenden Gewindestange 36, und deren Mittelachse vorzugsweise mit der Mittelachse 38 einer sich stromabwärts anschließendenThe valve seat body 5 has, downstream of the sealing seat, an overflow bore 43, the diameter of which is smaller than the core diameter of the threaded rod 36 to be pressed in, and the central axis thereof preferably with the Center axis 38 of a downstream one
Bohrung 35 identisch ist und einen von Null verschiedenenHole 35 is identical and different from zero
Winkel mit der Mittelachse 39 desAngle with the central axis 39 of the
Brennstoffeinspritzventils 1 einschließt. Der Durchmesser der Bohrung 35 korrespondiert mit dem Außendurchmesser der einzupressenden Gewindestange 36. Das stromabwärtige Ende der Bohrung 35 tritt an der stromabwärtigen Seite aus demIncludes fuel injector 1. The diameter of the bore 35 corresponds to the outer diameter of the threaded rod 36 to be pressed in. The downstream end of the bore 35 emerges on the downstream side
• Ventilsitzkorper 5 aus. Die stromabwärtige Seite des • Valve seat body 5 off. The downstream side of the
' Ventilsitzkörpers 5 weist im Bereich der Bohrung 35 eine vorzugsweise ebene Fläche 44 auf, deren Flächennormale mit der Mittelachse der Bohrung 35 identisch ist.Valve seat body 5 has a preferably flat surface 44 in the region of bore 35, the surface normal of which is identical to the central axis of bore 35.
Die Spritzlochscheibe 42 ist an dem Ventilsitzkorper 5 z.B. mittels Schweißverbindung befestigt. Die mit der Fläche 44 des Ventilsitzkörpers 5 in Kontakt stehende stromaufwärtige Seite 41 der Spritzlochscheibe 42 weist eine mit dem Ventilsitzkorper 5 korrespondierende Form auf. In der Spritzlochscheibe 42 ist die Abspritzöffnung 7 so eingebracht, daß die Mittelachse der Abspritzöffnung 7 identisch mit der Mittelachse 38 der Bohrung 35 ist, um ein symmetrisches Abspritzbild zu erreichen. Der Durchmesser der Abspritzöffnung 7 ist kleiner als der Durchmesser der Bohrung 35 und vorzugsweise auch kleiner als der Kerndurchmesser der Gewindestange 36. Die Spritzlochscheibe 42 kann kostengünstig z.B. als Stanzteil hergestellt werden.The spray orifice plate 42 is on the valve seat body 5 e.g. attached by welding. The upstream side 41 of the spray orifice plate 42 which is in contact with the surface 44 of the valve seat body 5 has a shape corresponding to the valve seat body 5. The spray opening 7 is introduced in the spray orifice plate 42 in such a way that the central axis of the spray opening 7 is identical to the central axis 38 of the bore 35 in order to achieve a symmetrical spray pattern. The diameter of the spray opening 7 is smaller than the diameter of the bore 35 and preferably also smaller than the core diameter of the threaded rod 36. be manufactured as a stamped part.
Die eingepreßte Gewindestange 36 ist kürzer als die Bohrung 35. Zwischen der stromaufwärtigen Stirnfläche 40a der Gewindestange 36 und dem stromaufwärtigen Ende der Bohrung 35 ist ein Hohlraum 45 ausgebildet, dessen Höhe durch den Abstand der stromaufwärtigen Stirnfläche 40a der Gewindestange und des stromaufwärtigen Endes der Bohrung 35 bestimmt ist. Die Zumessung der Brennstoffmenge bei geöffnetem Brennstoffeinspritzventil 1 erfolgt durch eine zu durchströmende Zylindermantelfläche der Fläche F=H*2Rπ, mit H als Höhe des Hohlraums 45 und R als Radius der Überströmbohrung 43. Die Einstellung der Zu eßmenge des Brennstoffs kann über die Einpreßtiefe der Gewindestange 36 vorgenommen werden, deren Position die Höhe H des Hohlraums 45 festlegt.The pressed-in threaded rod 36 is shorter than the bore 35. Between the upstream end face 40a of the threaded rod 36 and the upstream end of the bore 35, a cavity 45 is formed, the height of which is determined by the distance between the upstream end face 40a of the threaded rod and the upstream end of the bore 35 is determined. The metering of the amount of fuel when the fuel injector 1 is open takes place through a cylindrical jacket surface to be flowed through with the area F = H * 2Rπ, with H as the height of the cavity 45 and R as the radius of the overflow bore 43 36 be made, the position of which determines the height H of the cavity 45.
Stromabwärts der Gewindestange -36 ist die Drallkammer 34 angeordnet, die zwischen der stromabwärtigen Stirnfläche 40b der Gewindestange 36 und der stromaufwärtigen Seite 41 der Spritzlochscheibe 42 ausgebildet ist. Der in der BrennstoffStrömung ausgebildete Drall wird in der Drallkammer 34 vergleichmäßigt, bevor der Brennstoff durch die Abspritzöffnung 7 strömt und in den nicht dargestellten Brennraum einer Brennkraftmaschine abgespritzt wird.Downstream of the threaded rod -36, the swirl chamber 34 is arranged, which is formed between the downstream end face 40b of the threaded rod 36 and the upstream side 41 of the spray plate 42. The swirl formed in the fuel flow is evened out in the swirl chamber 34 before the fuel flows through the spray opening 7 and is sprayed into the combustion chamber (not shown) of an internal combustion engine.
Zur Ausbildung asymmetrischer Abspritzbilder können die Mittelachsen der Bohrungen 35, 43 bzw. der Abspritzöffnung 7 voneinander hinsichtlich Lage und Winkel verschieden sein. Die Aufbereitung des Dralls der BrennstoffStrömung läßt sich durch die Verwendung von Gewindestangen 36 realisieren, deren Gewinde sich hinsichtlich des Verhältnisses aus Kern- und Außendurchmesser und/oder der Steigung unterscheiden. Ebenso kann der Einfluß von verschiedenen Längen der Gewindestangen 36 .und der damit verbundenen unterschiedlichen Anzahl an drallbildenden Gewindegängen genutzt werden. In order to form asymmetrical spray patterns, the center axes of the bores 35, 43 or the spray spray opening 7 can differ from one another with regard to their position and angle. The preparation of the swirl of the fuel flow can be realized by using threaded rods 36, the threads of which differ with regard to the ratio of core and outer diameter and / or the pitch. The influence of different lengths of the threaded rods 36 and the associated different number of twist-forming threads can also be used.

Claims

Ansprüche Expectations
1. Brennstoffeinspritzventil (1) für1. Fuel injector (1) for
Brennstoffeinspritzanlagen von Brennkraftmaschinen mit einem Ventilschließkörper (4) , der mit einer Ventilnadel (3) in Wirkverbindung steht und der mit einer Ventilsitzfläche (6) eines 'Ventilsitzkörpers (5) zu einem Dichtsitz zusammenwirkt, mit einem drallerzeugenden Element, das stromabwärts des Dichtsitzes in dem Ventilsitzkorper (5) angeordnet ist, und mit einer Abspritzöffnung (7) , dadurch gekennzeichnet, daß das drallbildende Element eine Gewindestange (36) ist.Fuel injection systems of internal combustion engines with a valve closing body (4) which is operatively connected to a valve needle (3) and which interacts with a valve seat surface (6) of a ' valve seat body (5) to form a sealing seat, with a swirl-generating element which is located downstream of the sealing seat in the Valve seat body (5) is arranged, and with a spray opening (7), characterized in that the swirl-forming element is a threaded rod (36).
2. Brennstoffeinspritzventil nach Anspruch 1, dadurch, gekennzeichnet-. daß die Mittelachse (38) der Gewindestange (36) mit der Mittelachse (39) des Brennstoffeinspritzventils (1) einen von Null verschiedenen Winkel einschließt.2. Fuel injector according to claim 1, characterized, characterized. that the central axis (38) of the threaded rod (36) with the central axis (39) of the fuel injector (1) encloses a non-zero angle.
3. Brennstoffeinspritzventil nach Anspruch 1 oder 2 dadurch gekennzeichnet, daß sich an die Gewindestange (36) stromabwärts eine Drallkammer (34) anschließt, die in axialer Richtung von der stromabwärtigen Stirnfläche (40b) der Gewindestange (36) und dem Ventilsitzkorper (5) begrenzt ist.3. Fuel injection valve according to claim 1 or 2, characterized in that adjoining the threaded rod (36) downstream is a swirl chamber (34) which delimits in the axial direction from the downstream end face (40b) of the threaded rod (36) and the valve seat member (5) is.
4. Brennstoffeinspritzventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß sich an die Gewindestange (36) stromabwärts eine Drallkammer (34) anschließt, die in axialer Richtung von der stromabwärtigen Stirnfläche (40b) der Gewindestange (36) und der stromaufwärtigen Seite (47) einer Spritzlochscheibe (42) begrenzt ist.4. Fuel injection valve according to claim 1 or 2, characterized in that downstream of the threaded rod (36) there is a swirl chamber (34) which is axially delimited by the downstream end face (40b) of the threaded rod (36) and the upstream side (47) of a spray hole disc (42).
5. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die radiale Ausdehnung der Abspritzöffnung (7) kleiner ist als der Außendurchmesser der Gewindestange (36) .5. Fuel injection valve according to one of claims 1 to 4, characterized in that the radial extent of the spray opening (7) is smaller than the outer diameter of the threaded rod (36).
6. Brennstoffeinspritzventil nach Anspruch 4, dadurch gekennzeichnet, daß die Abspritzöffnung (7) in der Spritzlochscheibe (42) eingebracht ist .6. Fuel injection valve according to claim 4, characterized in that the spray opening (7) in the spray hole disc (42) is introduced.
7. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Gewindestange (36) von stromaufwärtiger Seite des Ventilsitzkörpers (5) in eine Bohrung (35) in dem Ventilsitzkorper (5) einpreßbar ist.7. Fuel injection valve according to one of claims 1 to 6, characterized in that the threaded rod (36) from the upstream side of the valve seat body (5) in a bore (35) in the valve seat body (5) can be pressed.
8. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Gewindestange (36) von strombwärtiger Seite des Ventilsitzkörpers (5) in eine Bohrung (35) in dem Ventilsitzkorper (5) einpreßbar ist.8. Fuel injection valve according to one of claims 1 to 6, characterized in that the threaded rod (36) from the upstream side of the valve seat body (5) in a bore (35) in the valve seat body (5) can be pressed.
9. Brennsto feinspritzventil nach Anspruch 8, dadurch gekennzeichnet, daß stromabwärts einer Überströmbohrung (43) , deren Durchmesser kleiner ist als der Kerndurchmesser der Gewindestange (36) , zwischen der stromaufwärtigen Stirnfläche (40a) der Gewindestange (36) und dem Ventilsitzkorper (5) ein Hohlraum (45) ausgebildet ist, dessen engster Strömungsquerschnitt die Zumessung der abzuspritzenden Brennsto fmenge definiert.9. Fuel fine injection valve according to claim 8, characterized in that downstream of an overflow bore (43), the diameter of which is smaller than the core diameter of the threaded rod (36), between the upstream end face (40a) of the threaded rod (36) and the valve seat member (5) a cavity (45) is formed, whose narrowest flow cross section defines the metering of the amount of fuel to be sprayed.
10. Brennstoffeinspritzventil nach Anspruch 9, dadurch gekennzeichnet, daß der engste Strömungsquerschnitt des Hohlraums durch die Fläche F eines Zylindermantels zu F=H*2Rπ bestimmt ist, mit H als dem • axialen Abstand zwischen stromaufwärtiger Stirnfläche (40a) und dem stromaufwärtigen Ende der Bohrung (35) und R als dem Radius der Überströmbohrung (43) .10. Fuel injection valve according to claim 9, characterized in that the narrowest flow cross section of the cavity through the surface F of a cylinder jacket is determined to F = H * 2Rπ, with H as the • axial distance between the upstream end face (40a) and the upstream end of the bore (35) and R as the radius of the overflow bore (43).
11. Brennstoffeinspritzventil nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß die Länge der eingepreßten Gewindestange (36) zumindest einen vollständigen Gewindegang umfaßt. 11. Fuel injection valve according to one of claims 1 to 10, characterized in that the length of the pressed-in threaded rod (36) comprises at least one complete thread.
EP01986742A 2000-10-10 2001-10-10 Fuel injection valve Expired - Lifetime EP1327066B1 (en)

Applications Claiming Priority (3)

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DE10050055A DE10050055A1 (en) 2000-10-10 2000-10-10 Fuel injection valve for internal combustion engine has threaded rod as spiral forming element
DE10050055 2000-10-10
PCT/DE2001/003846 WO2002031343A2 (en) 2000-10-10 2001-10-10 Fuel injection valve

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Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4528701B2 (en) * 2005-09-13 2010-08-18 日立オートモティブシステムズ株式会社 Injection valve and orifice machining method
US8225602B2 (en) * 2009-06-11 2012-07-24 Stanadyne Corporation Integrated pump and injector for exhaust after treatment
US20100314470A1 (en) * 2009-06-11 2010-12-16 Stanadyne Corporation Injector having swirl structure downstream of valve seat
CN102913310A (en) * 2011-08-05 2013-02-06 广西玉柴机器股份有限公司 SCR (selective catalytic reduction) post-processing nozzle for increasing conversion rate of NOx (nitrogen oxides)
JP5811979B2 (en) * 2012-09-24 2015-11-11 株式会社デンソー Fuel injection valve
CN109550607A (en) * 2019-01-30 2019-04-02 钱滋勒贸易(上海)有限公司 A kind of low-pressure nozzle
US20220056874A1 (en) * 2020-08-19 2022-02-24 Cummins Inc. Fuel injector having nozzle spray holes with grooves
CN115523313B (en) * 2022-09-06 2023-08-25 泗洪智工精密机械有限公司 Fuel control valve of electric control fuel injector

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB137134A (en) 1919-01-29 1920-01-08 Tom Latham Improvements in spray valves for diesel engines
US2981483A (en) * 1960-02-26 1961-04-25 Nord Aviation Injector having a high flow rate ratio
FR1358593A (en) 1963-03-07 1964-04-17 Tecalemit Advanced injector for supplying internal combustion engines
US4186883A (en) * 1978-05-08 1980-02-05 Essex Group, Inc. Electromagnetic fuel injection valve with swirl means
JPS57126554A (en) * 1981-01-30 1982-08-06 Hitachi Ltd Electro magnetic fuel jet valve
DE3121572A1 (en) 1981-05-30 1982-12-16 Robert Bosch Gmbh, 7000 Stuttgart "INJECTION VALVE"
US4487369A (en) * 1982-01-11 1984-12-11 Essex Group, Inc. Electromagnetic fuel injector with improved discharge structure
JPS5915668A (en) 1982-07-19 1984-01-26 Hitachi Ltd Electromagnetic fuel injection valve
SU1359463A1 (en) * 1986-05-20 1987-12-15 Запорожский индустриальный институт Carburetor for internal combustion engine
DE4200709A1 (en) 1992-01-14 1993-07-15 Bosch Gmbh Robert FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES
US5484108A (en) * 1994-03-31 1996-01-16 Siemens Automotive L.P. Fuel injector having novel multiple orifice disk members
JPH11267955A (en) * 1998-11-02 1999-10-05 Denso Corp Grinding method for needle for fluid injection valve
US6330981B1 (en) * 1999-03-01 2001-12-18 Siemens Automotive Corporation Fuel injector with turbulence generator for fuel orifice

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0231343A2 *

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US6851629B2 (en) 2005-02-08
WO2002031343A3 (en) 2002-07-18
US20030111562A1 (en) 2003-06-19
WO2002031343A2 (en) 2002-04-18
DE50110357D1 (en) 2006-08-10
DE10050055A1 (en) 2002-04-18
JP2004511699A (en) 2004-04-15
RU2002117416A (en) 2004-04-10
EP1327066B1 (en) 2006-06-28

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