EP0440674A1 - A fuel injection nozzle for internal combustion engines. - Google Patents

A fuel injection nozzle for internal combustion engines.

Info

Publication number
EP0440674A1
EP0440674A1 EP19890910836 EP89910836A EP0440674A1 EP 0440674 A1 EP0440674 A1 EP 0440674A1 EP 19890910836 EP19890910836 EP 19890910836 EP 89910836 A EP89910836 A EP 89910836A EP 0440674 A1 EP0440674 A1 EP 0440674A1
Authority
EP
European Patent Office
Prior art keywords
nozzle
nozzle body
injection nozzle
opening
collar
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
EP19890910836
Other languages
German (de)
French (fr)
Other versions
EP0440674B1 (en
Inventor
Karl Hofmann
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 EP0440674A1 publication Critical patent/EP0440674A1/en
Application granted granted Critical
Publication of EP0440674B1 publication Critical patent/EP0440674B1/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
    • F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
    • F02M53/04—Injectors with heating, cooling, or thermally-insulating means
    • 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
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention is based on a fuel injection nozzle according to the preamble of claim 1.
  • a known injection nozzle of this type DE-OS 30 00 061
  • the inner support area of the heat shield lying against the bottom of the nozzle body is directly affected by the forms the inner disk edge adjoining the annular fold, which leaves a relatively large central area of the nozzle bottom uncovered.
  • this embodiment is not sufficient to cool the nozzle base so much that the tendency of the nozzle bore to coke remains within the desired limits.
  • the injectors of the generic type the so-called throttle dispensing nozzle, the temperature should not exceed the nozzle plate 200 ⁇ C.
  • the thin-walled heat shields of the known type owing to their relatively narrow contact area with the ring flange at the attachment of the clamping nut, burn out or burn at all.
  • the arrangement according to the invention with the characterizing features of claim 1 has the advantage, in comparison, that a larger area of the nozzle base is covered by the heat protection disk and thus the nozzle body is better protected from the heat radiation. At the same time, better heat dissipation to the cylinder head of the machine is achieved due to the larger contact area of the heat shield with the ring flange at the attachment of the clamping nut.
  • the heat protection disk is provided with a hub part which forms the collar and has a greater wall thickness than the other disk areas, which on the front side forms the inner support area which bears against the nozzle base and which expands in the direction of flow of the fuel ⁇ nicden central through opening contains.
  • the thickening in the hub area reduces the risk of damage to the heat shield with extremely high thermal loads.
  • Figures 1 to 3 show, on an enlarged scale, partial longitudinal sections through injection nozzles according to the first, second and third exemplary embodiment.
  • nozzle body 10 which, together with an intermediate disk 12, is fastened to a nozzle holder (not shown in the drawing) by means of a clamping nut 14.
  • the clamping nut 14 is provided with an inner annular shoulder 16 , which engages an outer annular shoulder 18 of the nozzle holder 10.
  • the clamping nut 14 is also provided in the region of the annular shoulder 15 with an external thread 20 which engages in a thread in an installation bore 22 in the cylinder head 24 of the machine
  • a support shoulder 28 is formed on the outside on a cylindrical extension 26 of the clamping nut 14 which surrounds the nozzle body 10 below the annular shoulder 18 and which, when the injection nozzle is installed, is pressed against a support shoulder 32 in the installation bore 22 via a sealing ring 30.
  • the injection nozzle is a so-called throttle pin nozzle, in which the valve needle opening inwards is provided with a throttle pin 34 which, during a forward stroke of the valve needle, plunges into a nozzle bore opening on the combustion chamber side and narrows it down to a narrow throttle gap.
  • the Nozzle base 36 of the nozzle body 10 can be cooled particularly well in order to keep the coking of the throttle gap within limits.
  • a heat shield 40 is axially clamped under resilient deformation between the nozzle base 36 and an inwardly directed annular flange 38 of the shoulder 26 of the clamping nut 14.
  • the heat protection disk 40 protects a partial area of the nozzle base 36 from heat radiation and dissipates heat to the clamping nut 14, from where the heat passes over a short distance into the cylinder head 24.
  • the heat protection pane 40 has a flat, thin-walled outer edge area 42 which bears against the nozzle base 36.
  • a thin-walled annular fold 44 adjoins the outer edge region 42, the apex region 46 of which rests on the annular flange 38 of the clamping nut 14.
  • the annular fold 44 merges on the inside via a thin-walled intermediate area 48 into a hub part 50, the wall thickness of which is considerably greater than that of the other disk areas.
  • the hub part 50 fits appropriately into a central through opening 52 of the clamping nut 14 surrounded by the ring flange 38 and itself contains a through opening 54 which tapers conically towards the nozzle body 10.
  • the tapered opening of the passage opening 54 in the hub part 50 is surrounded by an annular edge 56 which rests on the nozzle base 36 and forms the inner support region of the heat protection disk 40.
  • This design of the heat shield 40 covers a larger area of the nozzle base 36 than in the known designs of heat shield discs, in which a hub part is not provided.
  • good heat dissipation is achieved due to the enlarged contact area between the heat protection disk 40 and the ring flange 38, so that the thin-walled outer disk area of the heat protective pane 40 is protected from overheating damage. Soot and dirt particles from combustion gases are deposited on the conically tapering wall of the passage opening 54 in the hub part 50 and flow against the nozzle base 36 during the injection breaks, whereby the coking of the throttle gap in the nozzle bore is further counteracted.
  • a heat protection disk 40a is provided, which has the same basic structure as the heat protection disk 40 according to FIG. 1 and differs from it only in another manufacturing process.
  • the heat protection disk 40a is extruded and accordingly provided with strongly rounded edges, so that there is a through opening 54 with a section 54a constricting on the nozzle side.
  • the rest of the structure of the injection nozzle corresponds to that according to FIG. 1.
  • the injection nozzle according to Figure 3 has a heat shield 60, which is made entirely of a thin-walled sheet metal part.
  • the outer ring area of the heat shield 60 and the basic structure of the injection nozzle correspond to the above-described embodiments, so that the same parts and the same features are provided with the same reference numbers.
  • the difference is that an inner support area 62 of the heat shield 60 resting against the nozzle base 36 connects directly to its annular fold 44 and merges into a collar section 64 which fits into the through opening 52 of the tension nut 14.
  • the collar section 64 is adjoined by a wall section 66 bent back against the nozzle body 10, one wall section facing the nozzle floor 36 encloses tapering through opening 68.
  • the wall section 66 does not reach all the way to the nozzle base 36, so that there is a free edge 70 on which dirt and soot particles carried in the combustion gases settle.
  • the bent-back wall section 66 the nozzle base 36 is covered to the same extent and extent against heat radiation as in the exemplary embodiments according to FIGS. 1 and 2, despite the support area 52 located further outside.

Abstract

Dans les injecteurs appartenant à la technique connue, il est nécessaire d'avoir un refroidissement efficace à la base du gicleur (36), afin de limiter la cokéfaction qui se produit au niveau de la fente d'étranglement. L'invention a pour but d'agencer le disque protecteur thermique (40, 60) de manière à protéger de la chambre d'explosion du moteur, une zone de base du gicleur (36) plus grande que dans les formes d'exécution connues, et d'éviter, grâce à une bon contact thermique du disque protecteur thermique (40, 60) avec les parties dissipant la chaleur (14, 26), une surcharge thermique du disque protecteur thermique (40, 60). Ce but est atteint grâce au fait que le disque protecteur thermique (40, 60) est muni d'un collet (50, 64) entourant son ouverture interne (54) et monté en étant ajusté de façon appropriée dans l'ouverture (52) du manchon de serrage (14) entourée par la bride annulaire (38). Un domaine d'application préféré est celui des moteurs diesel.In injectors belonging to the known technique, it is necessary to have effective cooling at the base of the nozzle (36) in order to limit the coking which occurs at the level of the throttle slot. The object of the invention is to arrange the thermal protective disc (40, 60) in such a way as to protect from the explosion chamber of the engine, a base area of the nozzle (36) which is larger than in the known embodiments. , and by means of good thermal contact of the thermal protective disc (40, 60) with the heat-dissipating parts (14, 26), of preventing thermal overload of the thermal protective disc (40, 60). This object is achieved by the fact that the thermal protective disc (40, 60) is provided with a collar (50, 64) surrounding its internal opening (54) and mounted with a suitable fit in the opening (52). of the clamping sleeve (14) surrounded by the annular flange (38). A preferred field of application is that of diesel engines.

Description

Kraftstoff-Einspritzdüse für BrennkraftmaschinenFuel injection nozzle for internal combustion engines
Stand der TechnikState of the art
Die Erfindung geht aus von einer Kra tstoff-Einspritzdüse nach der Gattung des Anspruchs 1. Bei einer bekannten Einspritzdüse dieser Gattung (DE-OS 30 00 061) ist der am Boden des Düsenkörpers anlie¬ gende innere Stützbereich der Wärmeschutzscheibe durch den sich un¬ mittelbar an die Ringfalte anschließenden inneren Scheibenrand ge¬ bildet, der einen verhältnismäßig großen Zentralbereich des Düsenbo¬ dens unbedeckt läßt. Diese Ausführung reicht in manchen Anwendungs¬ fällen nicht aus, um den Düsenboden so stark zu kühlen, daß die Ver¬ kokungsneigung der Düsenbohrung in den gewünschten Grenzen bleibt. Bei den Einspritzdüsen der gattungsmäßigen Art, den sogenannten Drosselzapfendüsen, soll die Temperatur am Düsenboden 200 βC nicht überschreiten. Auch besteht die Gefahr, daß in Fällen mit extrem . hoher Wärmebelastung die dünnwandigen Wärmeschutzscheiben der be¬ kannten Bauart wegen ihrer verhältnismäßig schmalen Berührungsfläche mit dem Ringflansch am Ansatz der Spannmutter ausglühen oder über¬ haupt verbrennen. Vorteile der ErfindungThe invention is based on a fuel injection nozzle according to the preamble of claim 1. In a known injection nozzle of this type (DE-OS 30 00 061), the inner support area of the heat shield lying against the bottom of the nozzle body is directly affected by the forms the inner disk edge adjoining the annular fold, which leaves a relatively large central area of the nozzle bottom uncovered. In some applications, this embodiment is not sufficient to cool the nozzle base so much that the tendency of the nozzle bore to coke remains within the desired limits. With the injectors of the generic type, the so-called throttle dispensing nozzle, the temperature should not exceed the nozzle plate 200 β C. There is also a risk that in cases with extreme. high thermal load, the thin-walled heat shields of the known type, owing to their relatively narrow contact area with the ring flange at the attachment of the clamping nut, burn out or burn at all. Advantages of the invention
Die erfindungsgemäße Anordnung mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß eine größere Fläche des Düsenbodens durch die W rmeschutzscheibe abgedeckt wird und so¬ mit der Düsenkörper besser vor der Wärmeeinstrahlung geschützt ist. Gleichzeitig wird durch die größere Berührungsfläche der Warme¬ schutzscheibe mit dem Ringflansch am Ansatz der Spannmutter eine bessere Wärmeableitung zum Zylinderkopf der Maschine erreicht.The arrangement according to the invention with the characterizing features of claim 1 has the advantage, in comparison, that a larger area of the nozzle base is covered by the heat protection disk and thus the nozzle body is better protected from the heat radiation. At the same time, better heat dissipation to the cylinder head of the machine is achieved due to the larger contact area of the heat shield with the ring flange at the attachment of the clamping nut.
Durch die in den Unter nsprüchen aufgeführten Merkmale sind vorteil¬ hafte Weiterbildungen der Erfindung möglich.Advantageous developments of the invention are possible through the features listed in the subclaims.
Besonders vorteilhaft ist es, wenn die Warmeschutzscheibe mit einem den Kragen bildenden, eine größere Wändstärke als die übrigen Schei¬ benbereiche aufweisenden Nabenteil versehen ist, welcher an der ei¬ nen Stirnseite den am Dusenboden anliegenden inneren Stützbereich bildet und eine sich in Strömungsrichtung des Kraftstoffs erwei¬ ternde zentrale Durchgangsöffnung enthält. Durch die Verdickung im Nabenbereich wird die Gefahr der Beschädigung der Warmeschutzscheibe bei extrem hoher Wärmebelastung vermindert. Durch die Abstimmung der Warmeschutzscheibe zur Spannmutter im Bereich der zentralen Durch¬ gangsöffnung wird eine Überdeckung erreicht und damit eine Abschir¬ mung der Innenpartie der Warmeschutzscheibe. Die sich zum Dusenboden hin verjüngende Durchgangsöffnung hat den weiteren Vorteil, daß ge¬ gen den Dusenboden strömende Verbrennungsgase mitgeführte Schmutz¬ partikel an der Wand der Durchgangsöffnung absetzen, wodurch der Verkokung der Düsenbohrung ebenfalls entgegengewirkt wird. ZeichnungIt is particularly advantageous if the heat protection disk is provided with a hub part which forms the collar and has a greater wall thickness than the other disk areas, which on the front side forms the inner support area which bears against the nozzle base and which expands in the direction of flow of the fuel ¬ terenden central through opening contains. The thickening in the hub area reduces the risk of damage to the heat shield with extremely high thermal loads. By coordinating the heat shield with the clamping nut in the area of the central through opening, an overlap is achieved and thus shielding the inner part of the heat shield. The passage opening tapering towards the nozzle floor has the further advantage that combustion gases flowing against the shower floor deposit dirt particles carried along on the wall of the passage opening, which also counteracts the coking of the nozzle bore. drawing
Drei Ausführungsbeispiele der Erfindung sind in der Zeichnung darge¬ stellt und in der nachfolgenden Beschreibung näher erläutert. Die . Figuren 1 bis 3 zeigen in vergrößertem Maßstab Teil-Längsschnitte durch Einspritzdüsen nach dem ersten, zweiten und dritten Ausfüh¬ rungsbeispiel.Three exemplary embodiments of the invention are shown in the drawing and explained in more detail in the following description. The . Figures 1 to 3 show, on an enlarged scale, partial longitudinal sections through injection nozzles according to the first, second and third exemplary embodiment.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Die Einspritzdüse nach Figur 1 hat einen Düsenkörper 10, der zusam¬ men mit einer Zwischenscheibe 12 durch eine Spannmutter 14 an einem" in der Zeichnung nicht mehr dargestellten Düsenhalter befestigt ist. Zu diesem Zweck ist die Spannmutter 14 mit einer inneren Ringschul¬ ter 16 versehen, die an einer äußeren Ringschulter 18 des Düsenhal¬ ters 10 angreift. Die Spannmutter 14 ist ferner im Bereich der Ring¬ schulter 15 mit einem Außengewinde 20 versehen, welches in ein Ge¬ winde in einer Einbaubohrung 22 im Zylinderkopf 24 der Maschine ein¬ greift. An einem den Düsenkörper 10 unterhalb der Ringschulter 18 umgreifenden zylindrischen Ansatz 26 der Spannmutter 14 ist außen eine Stützschulter 28 gebildet, die bei eingebauter Einspritzdüse über einen Dichtring 30 gegen eine Stützschulter 32 in der Einbau¬ bohrung 22 gepreßt ist.1 has a nozzle body 10 which, together with an intermediate disk 12, is fastened to a nozzle holder (not shown in the drawing) by means of a clamping nut 14. For this purpose, the clamping nut 14 is provided with an inner annular shoulder 16 , which engages an outer annular shoulder 18 of the nozzle holder 10. The clamping nut 14 is also provided in the region of the annular shoulder 15 with an external thread 20 which engages in a thread in an installation bore 22 in the cylinder head 24 of the machine A support shoulder 28 is formed on the outside on a cylindrical extension 26 of the clamping nut 14 which surrounds the nozzle body 10 below the annular shoulder 18 and which, when the injection nozzle is installed, is pressed against a support shoulder 32 in the installation bore 22 via a sealing ring 30.
Die Einspritzdüse ist eine sogenannte Drosselzapfenduse, bei welcher die nach innen öffnende Ventilnadel mit einem Drosselzapfen 34 ver¬ sehen ist, der während eines Vorhubs der Ventilnadel in eine brenn- raumseitig ausmündende Düsenbohrung taucht und diese bis auf einen schmalen Drosselspalt verengt. Bei derartigen Einspritzdüsen muß der Düsenboden 36 des Düsenkörpers 10 besonders gut gekühlt werden, um die Verkokung des Drosselspaltes in Grenzen zu halten. Zu die¬ sem Zweck ist zwischen dem Düsenboden 36 und einem nach innen ge¬ kehrten Ringflansch 38 des Ansatzes 26 der Spannmutter 14 eine Wär*- meschutzscheibe 40 unter federnder Verformung axial eingespannt. Die W rmeschutzscheibe 40 schützt einen Teilbereich des Düsenbodens 36 vor Wärmestrahlung und leitet Wärme auf die Spannmutter 14 ab, von wo die Wärme auf kurzem Wege in den Zylinderkopf 24 übergeht.The injection nozzle is a so-called throttle pin nozzle, in which the valve needle opening inwards is provided with a throttle pin 34 which, during a forward stroke of the valve needle, plunges into a nozzle bore opening on the combustion chamber side and narrows it down to a narrow throttle gap. With such injectors, the Nozzle base 36 of the nozzle body 10 can be cooled particularly well in order to keep the coking of the throttle gap within limits. For this purpose, a heat shield 40 is axially clamped under resilient deformation between the nozzle base 36 and an inwardly directed annular flange 38 of the shoulder 26 of the clamping nut 14. The heat protection disk 40 protects a partial area of the nozzle base 36 from heat radiation and dissipates heat to the clamping nut 14, from where the heat passes over a short distance into the cylinder head 24.
Die W rmeschutzscheibe 40 hat einen ebenen, dünnwandigen Außenrand- bereich 42, der am Düsenboden 36 anliegt. An den Außenrandbereich 42 schließt sich eine ebenfalls dünnwandige Ringfalte 44 an, deren Scheitelbereich 46 am Ringflansch 38 der Spannmutter 14 anliegt. Die Ringfalte 44 geht innen über einen dünnwandigen Zwischenbereich 48 in ein Nabenteil 50 über, dessen Wandstärke erheblich größer als jene der übrigen Scheibenbereiche ist. Der Nabenteil 50 greift pas¬ send in eine vom Ringflansch 38 umgebene zentrale Durchgangsöffnung 52 der Spannmutter 14 ein und enthält selbst eine Durchgangsöffnung 54, die sich zum Düsenkörper 10 hin konisch verjüngt.The heat protection pane 40 has a flat, thin-walled outer edge area 42 which bears against the nozzle base 36. A thin-walled annular fold 44 adjoins the outer edge region 42, the apex region 46 of which rests on the annular flange 38 of the clamping nut 14. The annular fold 44 merges on the inside via a thin-walled intermediate area 48 into a hub part 50, the wall thickness of which is considerably greater than that of the other disk areas. The hub part 50 fits appropriately into a central through opening 52 of the clamping nut 14 surrounded by the ring flange 38 and itself contains a through opening 54 which tapers conically towards the nozzle body 10.
Die verjüngte Ausmündung der Durchgangsöffnung 54 im Nabenteil 50 ist von einem Ringrand 56 umgeben, der am Dusenboden 36 aufliegt und den inneren Stützbereich der Warmeschutzscheibe 40 bildet. Durch diese Ausbildung der Warmeschutzscheibe 40 ist ein größerer Bereich des Düsenbodens 36 abgedeckt als bei den bekannten Ausführungen von WärmeschützScheiben, bei denen ein Nabenteil nicht vorgesehen ist. Außerdem ist durch die vergrößerte Berührungsfläche zwischen W rme¬ schutzscheibe 40 und Ringflansch 38 eine gute Wärmeableitung er¬ reicht, so daß der dünnwandige äußere Scheibenbereich der Wärme- schutzscheibe 40 vor Überhitzungsschäden geschützt ist. An der sich konisch verjüngenden Wand der Durchgangsöffnung 54 im Nabenteil 50 werden Ruß- und Schmutzpartikel aus Verbrennungsgasen abgesetzt, die in den Spritzpausen gegen den Düsenboden 36 strömen, wodurch der Verkokung des Drosselspaltes in der Düsenbohrung weiter entgegenge¬ wirkt wird.The tapered opening of the passage opening 54 in the hub part 50 is surrounded by an annular edge 56 which rests on the nozzle base 36 and forms the inner support region of the heat protection disk 40. This design of the heat shield 40 covers a larger area of the nozzle base 36 than in the known designs of heat shield discs, in which a hub part is not provided. In addition, good heat dissipation is achieved due to the enlarged contact area between the heat protection disk 40 and the ring flange 38, so that the thin-walled outer disk area of the heat protective pane 40 is protected from overheating damage. Soot and dirt particles from combustion gases are deposited on the conically tapering wall of the passage opening 54 in the hub part 50 and flow against the nozzle base 36 during the injection breaks, whereby the coking of the throttle gap in the nozzle bore is further counteracted.
Bei der Einspritzdüse nach Figur 2 ist eine Warmeschutzscheibe 40a vorgesehen, die im grundsätzlichen Aufbau mit der Warmeschutzscheibe 40 nach Figur 1 übereinstimmt und sich von dieser nur durch ein an¬ deres Fertigungsverfahren unterscheidet. Die W rmeschutzscheibe 40a ist fließgepreßt und demgemäß mit stark ausgerundeten Kanten verse¬ hen, so daß sich eine Durchgangsöffnung 54 mit einem düsenseitig sich diffusorartig einschnürenden Abschnitt 54a ergibt. Der übrige Aufbau der Einspritzdüse stimmt mit jenem nach Figur 1 überein.In the injection nozzle according to FIG. 2, a heat protection disk 40a is provided, which has the same basic structure as the heat protection disk 40 according to FIG. 1 and differs from it only in another manufacturing process. The heat protection disk 40a is extruded and accordingly provided with strongly rounded edges, so that there is a through opening 54 with a section 54a constricting on the nozzle side. The rest of the structure of the injection nozzle corresponds to that according to FIG. 1.
Die Einspritzdüse nach Figur 3 hat eine Warmeschutzscheibe 60, die vollständig aus einem dünnwandigen Blechteil hergestellt ist. Der äußere Ringbereich der Warmeschutzscheibe 60 und der grundsätzliche Aufbau der Einspritzdüse stimmen mit den vorbeschriebenen Ausfüh¬ rungen überein, so daß gleiche Teile und gleiche Merkmale mit den gleichen Bezugszahlen versehen sind. Unterschiedlich ist, daß sich ein am Dusenboden 36 anliegender innerer Stützbereich 62 der Warme¬ schutzscheibe 60 unmittelbar an deren Ringfalte 44 anscnließt und in einen passend in die Durchgangsöffnung 52 der Spannmutter 14 ein¬ greifenden Kragenabschnitt 64 übergeht.The injection nozzle according to Figure 3 has a heat shield 60, which is made entirely of a thin-walled sheet metal part. The outer ring area of the heat shield 60 and the basic structure of the injection nozzle correspond to the above-described embodiments, so that the same parts and the same features are provided with the same reference numbers. The difference is that an inner support area 62 of the heat shield 60 resting against the nozzle base 36 connects directly to its annular fold 44 and merges into a collar section 64 which fits into the through opening 52 of the tension nut 14.
An den Kragenabschnitt 64 schließt sich ein gegen den Düsenkörper 10 zurückgebogener Wandabschnitt 66 an, der eine sich zum Dusenboden 36 hin verjüngende Durchgangsöffnung 68 umschließt. Der Wandabschnitt 66 reicht nicht ganz bis an den Düsenboden 36 heran, so daß sich eine freie Kante 70 ergibt, an welcher sich in den Verbrennungsgasen mitgeführte Schmutz- und Rußpartikel absetzen. Durch den zurückgebo¬ genen Wandabschnitt 66 wird der Düsenboden 36 trotz des sich weiter außen befindenden Stützbereiches 52 in gleichem Maß und Umfang gegen Wärmestrahlung abgedeckt wie bei den Ausführungsbeispielen nach den Figuren 1 und 2. The collar section 64 is adjoined by a wall section 66 bent back against the nozzle body 10, one wall section facing the nozzle floor 36 encloses tapering through opening 68. The wall section 66 does not reach all the way to the nozzle base 36, so that there is a free edge 70 on which dirt and soot particles carried in the combustion gases settle. By means of the bent-back wall section 66, the nozzle base 36 is covered to the same extent and extent against heat radiation as in the exemplary embodiments according to FIGS. 1 and 2, despite the support area 52 located further outside.

Claims

Ansprüche Expectations
1. Kraftstoff-Einspritzdüse für Brennkraftmaschinen, mit einem Dü¬ senkörper, in welchem ein Ventilsitz an einer Düsenbohrung gebildet und eine Ventilnadel verschiebbar gelagert ist, die mit einem min¬ destens während eines Vorhubs in die Düsenbohrung eintauchenden Drosselzapfen versehen ist, ferner mit einer Spannmutter, die den Düsenkörper gegen einen Düsenhalter spannt und die mit einem den Dü¬ senkörper stromab einer Spannschulter umgreifenden hülsenförmigen Ansatz verbunden ist, welcher am brennrau seitigen Stirnende einen nach innen gekehrten Ringflansch hat, der eine zentrale Durchgangs¬ öffnung für die Spritzstrahlen umgibt und eine ringförmige Warme¬ schutzscheibe unter elastischer Verformung gegen den Boden des Dü¬ senkörpers spannt, die sowohl mit einem eine zentrale Durchgangs¬ öffnung umgebenden inneren Stützbereich als auch mit einem äußeren Ringrandbereich am Boden des Düsenkörpers anliegt und dazwischen mit einer Ringfalte versehen ist, deren Scheitelbereich am Ringflansch des Ansatzes der Spannmutter anliegt, dadurch gekennzeichnet, daß die Warmeschutzscheibe (40, 60) mit einem von der Ringfalte (44) um¬ gebenen, auf der gleichen Seite wie diese aus der Ebene des äußeren Scheibenrandes (42) heraustretenden Kragen (50, 64) versehen ist, der passend in die vom Ringflansch (38) umgebene zentrale Durchgangs¬ öffnung (52) der Spannmutter (14) eingreift.1. Fuel injection nozzle for internal combustion engines, with a nozzle body, in which a valve seat is formed on a nozzle bore and a valve needle is displaceably mounted, which is provided with a throttle pin which plunges into the nozzle bore at least during a forward stroke, and also with a tension nut , which clamps the nozzle body against a nozzle holder and which is connected to a sleeve-shaped attachment encompassing the nozzle body downstream of a clamping shoulder, which has an inward-facing ring flange on the firing-gray end that surrounds a central through-opening for the spray jets and an annular one The heat protection disk clamps against the bottom of the nozzle body with elastic deformation, which rests both with an inner support area surrounding a central passage opening and with an outer ring edge area on the bottom of the nozzle body and is provided with an annular fold therebetween Eren apex area on the ring flange of the approach of the clamping nut, characterized in that the heat shield (40, 60) with a collar surrounded by the annular fold (44) on the same side as this coming out of the plane of the outer disc edge (42) (50, 64) is provided, the suitably engages in the central through opening (52) of the clamping nut (14) surrounded by the ring flange (38).
2. Einspritzdüse nach Anspruch 1, dadurch gekennzeichnet, daß die Warmeschutzscheibe (40) mit einem den Kragen bildenden, eine größere Wandstärke als die übrigen Scheibenbereiche aufweisenden Nabenteil (50) versehen ist, welcher an einer Stirnseite den am Boden (36) des Düsenkörpers (10) anliegenden inneren Stützbereich (56) bildet und eine .sich in Strömungsrichtung des Kraftstoffs erweiternde zentrale Durchgangsöffnung (54) enthält (Figuren 1 und 2).2. Injection nozzle according to claim 1, characterized in that the heat shield (40) with a collar forming a larger wall thickness than the other disc areas having hub part (50) is provided, which on one end face the bottom (36) of the nozzle body ( 10) forms adjacent inner support area (56) and contains a central through opening (54) which widens in the direction of flow of the fuel (FIGS. 1 and 2).
3. Einspritzdüse nach Anspruch 1, dadurch gekennzeichnet, daß ein Kragenabschnitt (64) der aus einem Blechteil bestehenden Warme¬ schutzscheibe (60) sich unmittelbar an deren am Boden (36) des Dü¬ senkörpers (10) anliegenden inneren Stützbereich (62) anschließt und daß ein am Kragenabschnitt (64) sich anschließender Wandabschnitt (66) gegen den Düsenkörper (10) schräg zurückgefaltet ist (Figuren 3).3. Injection nozzle according to claim 1, characterized in that a collar portion (64) of the heat shield made of a sheet metal part (60) directly adjoins the inner support region (62) which bears against the bottom (36) of the nozzle body (10) and that a wall section (66) adjoining the collar section (64) is folded back obliquely against the nozzle body (10) (FIGS. 3).
4. Einspritzdüse nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der den Düsenkörper (10) umgebende hulsenformige Ansatz (26) der Spannmutter (14) außen eine Ringschulter (28) hat, welche durch die die Einspritzdüse in der Einbaulage festhaltenden Spannmittel gegebenenfalls unter Zwischenlage eines Dichtrings (30) gegen eine Ringschulter (32) in der Einbaubohrung (22) für die Ein¬ spritzdüse gespannt ist. 4. Injection nozzle according to one of the preceding claims, characterized in that the sleeve-shaped projection (26) surrounding the nozzle body (10) of the clamping nut (14) has an annular shoulder (28) on the outside, which, if necessary, is held by the clamping means holding the injection nozzle in the installed position Intermediate position of a sealing ring (30) against an annular shoulder (32) in the mounting hole (22) for the injection nozzle is clamped.
EP89910836A 1988-10-26 1989-10-04 A fuel injection nozzle for internal combustion engines Expired - Lifetime EP0440674B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3836413 1988-10-26
DE3836413A DE3836413A1 (en) 1988-10-26 1988-10-26 FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES

Publications (2)

Publication Number Publication Date
EP0440674A1 true EP0440674A1 (en) 1991-08-14
EP0440674B1 EP0440674B1 (en) 1992-06-17

Family

ID=6365931

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89910836A Expired - Lifetime EP0440674B1 (en) 1988-10-26 1989-10-04 A fuel injection nozzle for internal combustion engines

Country Status (4)

Country Link
EP (1) EP0440674B1 (en)
JP (1) JP2768522B2 (en)
DE (2) DE3836413A1 (en)
WO (1) WO1990004716A1 (en)

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US10605213B2 (en) 2015-08-21 2020-03-31 Cummins Inc. Nozzle combustion shield and sealing member with improved heat transfer capabilities

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DE4019752A1 (en) * 1990-06-21 1992-01-02 Bosch Gmbh Robert FUEL INJECTION VALVE
DE4209837A1 (en) * 1992-03-26 1993-09-30 Bosch Gmbh Robert Fuel injection nozzle for internal combustion engines
DE4443861A1 (en) * 1994-12-09 1996-06-13 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
JP2001132582A (en) 1999-11-10 2001-05-15 Mitsubishi Electric Corp Fuel injection valve for cylinder injection
DE10017113B4 (en) * 2000-04-06 2006-02-09 Ina-Schaeffler Kg locknut
DE10142299A1 (en) * 2001-08-29 2003-04-17 Bosch Gmbh Robert fuel injection system
US9410520B2 (en) 2013-08-08 2016-08-09 Cummins Inc. Internal combustion engine including an injector combustion seal positioned between a fuel injector and an engine body
US10036355B2 (en) 2013-08-08 2018-07-31 Cummins Inc. Heat transferring fuel injector combustion seal with load bearing capability
JP6757145B2 (en) 2016-02-24 2020-09-16 本田技研工業株式会社 Fuel gas circulation device
JP6666745B2 (en) * 2016-02-24 2020-03-18 本田技研工業株式会社 Hydrogen injection device

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US10605213B2 (en) 2015-08-21 2020-03-31 Cummins Inc. Nozzle combustion shield and sealing member with improved heat transfer capabilities

Also Published As

Publication number Publication date
JPH04501292A (en) 1992-03-05
JP2768522B2 (en) 1998-06-25
WO1990004716A1 (en) 1990-05-03
DE3836413A1 (en) 1990-05-03
EP0440674B1 (en) 1992-06-17
DE58901717D1 (en) 1992-07-23

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