EP0444053A1 - Fuel injection nozzle for internal combustion engines. - Google Patents

Fuel injection nozzle for internal combustion engines.

Info

Publication number
EP0444053A1
EP0444053A1 EP19890911536 EP89911536A EP0444053A1 EP 0444053 A1 EP0444053 A1 EP 0444053A1 EP 19890911536 EP19890911536 EP 19890911536 EP 89911536 A EP89911536 A EP 89911536A EP 0444053 A1 EP0444053 A1 EP 0444053A1
Authority
EP
European Patent Office
Prior art keywords
spring
valve needle
stroke
closing
spring chamber
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
EP19890911536
Other languages
German (de)
French (fr)
Other versions
EP0444053B1 (en
Inventor
Kurt Seifert
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 EP0444053A1 publication Critical patent/EP0444053A1/en
Application granted granted Critical
Publication of EP0444053B1 publication Critical patent/EP0444053B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/083—Having two or more closing springs acting on injection-valve

Definitions

  • the invention relates to a fuel injector for internal combustion engines of the type defined in the preamble of claim 1. Such an injector with
  • the intermediate disc and the intermediate bushing have the advantage that the tolerance range of the advance stroke of the valve needle, which is to be kept within narrow limits, is determined solely by the manufacturing tolerances on the pressure element and on the nozzle needle.
  • the forward stroke can therefore be measured precisely and by grinding the
  • Stop of the valve needle (which is generally formed by the free end of the valve needle can be adjusted. Measurement tolerances and / or changes occurring during operation or during assembly no longer affect the size of the advance stroke.
  • the shoulder fixed to the housing for supporting the second closing spring is created by a stepped design of the spring chamber, preferably as an axial stepped pocket bore.
  • the second closing spring rests on an annular disk against the annular shoulder formed between the bore sections with different bore diameters.
  • the pressure pin protrudes through a central opening in the ring disk and is acted upon by the first closing spring on the face side.
  • the two closing springs are graduated according to the two different diameters of the spring chamber.
  • the fuel injection nozzle according to the invention with the characterizing features of claim 1 has the advantage that the outer diameter of the nozzle holder can be made smaller without loss of strength.
  • the closing springs are identical in construction, the spring chamber has a constant diameter over the entire length, which can be kept relatively small.
  • the closing spring which is close to the nozzle body, is supported by means of a cross bolt crossing the spring chamber, so that the spring chamber available for the first closing spring can thus be fully used.
  • the cross bolt is inserted into a radial blind hole crossing the spring chamber and seals the spring chamber by means of an O-ring.
  • the transverse bolt is fixed in the radial blind bore by a centering piece designed as a spring plate, by means of which the second closing spring, which is close to the nozzle body, is supported on the transverse bolt.
  • the drawing shows a longitudinal section of a fuel injector for direct injection internal combustion engines.
  • the injection nozzle shown in longitudinal section in FIG. 1 has a nozzle body 10 which, together with an intermediate disk 11 lying on the end face, is guided by a nozzle
  • Union nut 12 is clamped to a nozzle holder 13.
  • a valve needle 14 is axially displaceably mounted in the nozzle body 10 and cooperates with an inward-facing valve seat in the nozzle body 10 and controls a plurality of spray openings 15 located upstream of the valve seat.
  • the guide bore 16 of the valve needle 14 in the nozzle body 10 is, as usual, expanded at one point to a pressure chamber, in the area of which the valve needle 14 has a pressure shoulder.
  • the pressure chamber is via a channel 17 running in the nozzle holder 13 and only partially shown, with a nozzle 18 Nozzle holder 13 for connecting a fuel delivery line leading to a fuel injection pump.
  • valve needle 14 The fuel pressure applied to the pressure shoulder of the valve needle 14 pushes the valve needle 14 upward against the graduated force curve of a closing spring arrangement described in the following, consisting of two helical compression springs, the valve needle 14 executing a preliminary stroke in a pre-injection phase and a residual stroke in a main injection phase, in which fuel via the Spray openings 15 is sprayed out.
  • a spring chamber 19 is arranged coaxially with the valve needle 14, which is designed as an axial blind bore and is closed on its open end face by the intermediate disk 11.
  • a "first closing spring 21 and a second closing spring 22 are arranged in series in the spring chamber 19.
  • the first closing spring 21, which is more distant from the nozzle body 10, acts continuously on the valve needle 14 in its closing direction via a pressure pin 23.
  • the first closing spring 21 is supported by a disk 20 on the base 30 of the spring chamber 19 and via a spring plate-like support element 31 on the end face of the pressure pin 23.
  • the support element 31 has on its end face a recess 32 which receives the end face of the pressure pin 23 in a form-fitting manner guided axially displaceably and abuts the free end of the valve needle 14.
  • the intermediate bush 24 is guided axially displaceably in the intermediate disk 11 coaxially to the valve needle 14 and bears a stop 25 and a counter-stop 26.
  • the stop 25 formed by a radial annular shoulder cooperates one of a same ichen shoulder formed on the intermediate plate 11 to limit the total stroke of the valve needle 14 together.
  • the from the end face of the intermediate bushing 24 Counter stop 26 formed interacts with a stop 28 formed by the end face of valve needle 14 to limit the forward stroke of valve needle 14.
  • the second closing spring 22, which is constructed identically to the first closing spring 21, is in the spring chamber 19 of the first closing spring
  • the second closing spring 22 is supported by a spring plate 29 on the intermediate bush 24, which is thereby placed in the closed position of the valve needle 14 on the end face of the nozzle body 10, and with its other end, the second closing spring 22 presses via a centering piece 33 designed as a spring plate against a cross bolt 34 crossing the spring chamber 19.
  • the cross bolt 34 which has a radial through opening 35 in the region of the spring chamber 19
  • Passage of the pressure pin 33 and a receptacle 36 for the centering piece 33 is inserted into a radial blind bore 37 which crosses the spring chamber 19.
  • a sealing ring 39 which is located in an annular groove 38 of the transverse bolt 34 and is designed as an O-ring, seals the spring chamber 19.
  • the transverse bolt 34 is fixed in the radial blind bore 37 by the contact pressure of the second closing spring 22, which secures the transverse bolt 34 in the spring chamber 19 against transverse displacement via the centering piece 33 and the receptacle 36.
  • the spring chamber 19 is still connected via a channel 40 to a connecting nipple 41 for a leak oil line.
  • the valve needle 14 performs a preliminary stroke h v , in which only the first closing spring 21 acts as a counterforce.
  • a limited pre-injection quantity is injected from the injection openings 15.
  • the preliminary stroke h v is ended when the stop 28 on the valve needle 14 comes to rest against the counter stop 26 of the intermediate bush 24.
  • the valve needle 14 remains in this position until the rising one Fuel pressure now overcomes the opposing forces of both closing springs 21, 22. Thereafter, the valve needle 14 together with the intermediate bush 24 is moved further in the opening direction until it has completed its total stroke after the remaining stroke h v . This is limited by the counter stop 27 on the
  • the invention is not limited to the exemplary embodiment described.
  • the intermediate disk 11 Juch can thus be formed from two individual disks, of which the lower individual disk has a larger inner diameter than the upper one.
  • the counter-stop 27 for limiting the total stroke of the valve needle 14 is formed by the area in the upper single disk not covered by the lower single disk.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

Un injecteur de carburant pour moteurs à combustion interne comporte un corps d'injecteur (10) fixé à une porte-injecteur (13) par un disque intermédiaire (11), et un pointeau de soupape (14) qui coulisse axialement dans le corps d'injecteur. Lorsque le carburant est injecté, la pression de carburant soulève ledit pointeau depuis un siège de soupape à l'encontre de l'action d'un agencement de ressorts de fermeture composé de deux ressorts hélicoïdaux (21, 22) disposés l'un derrière l'autre. La course totale du pointeau (14) est ainsi divisée en une course préalable et une course résiduelle. Pour permettre la réalisation d'un injecteur de diamètre extérieur minimal, les deux ressorts de fermeture (21, 22) sont de structure identique. Le premier ressort de fermeture (21), lequel agit pendant la course préalable, repose contre la base (30) d'une chambre de ressort (19) et contre un axe de pression (23) qui appuie sur le pointeau (14). Le deuxième ressort de fermeture (22), lequel agit pendant la course résiduelle, repose contre un boulon transversal (34) qui traverse la chambre de ressort (19) et contre une douille intermédiaire (24) qui coulisse axialement dans le disque intermédiaire (11) et est adjacente au corps d'injecteur (10). les paliers de la course et la course totale du pointeau (14) sont déterminés par des butées (25, 28) et des contre-butées (26, 27) sur la douille intermédiaire (24), le disque intermédiaire (11) et le pointeau (14).A fuel injector for internal combustion engines comprises an injector body (10) fixed to an injector holder (13) by an intermediate disc (11), and a valve needle (14) which slides axially in the body d 'injector. When fuel is injected, fuel pressure lifts said needle from a valve seat against the action of a closing spring arrangement consisting of two coil springs (21, 22) arranged one behind the valve. 'other. The total stroke of the needle (14) is thus divided into a preliminary stroke and a residual stroke. To allow an injector of minimum outside diameter to be produced, the two closing springs (21, 22) are of identical structure. The first closing spring (21), which acts during the preliminary stroke, rests against the base (30) of a spring chamber (19) and against a pressure pin (23) which presses on the needle (14). The second closing spring (22), which acts during the residual stroke, rests against a transverse bolt (34) which passes through the spring chamber (19) and against an intermediate sleeve (24) which slides axially in the intermediate disc (11 ) and is adjacent to the injector body (10). the bearings of the stroke and the total stroke of the needle (14) are determined by stops (25, 28) and counter-stops (26, 27) on the intermediate sleeve (24), the intermediate disc (11) and the needle (14).

Description

Kraftstoff-Einspritzdüse für Brennkraftic.ascl_.inenFuel injection nozzle for Brennkraftic.ascl_.inen
Stand der TechnikState of the art
Die Erfindung betrifft eine Kraftstoff-Einspritzdüse für Brennkraftmaschinen der im Oberbegriff des Anspruchs 1 definierten Gattung. Eine solche Einspritzdüse mitThe invention relates to a fuel injector for internal combustion engines of the type defined in the preamble of claim 1. Such an injector with
Zwischenscheibe und Zwischenbuchse hat den Vorteil, daß der in engen Grenzen zu haltende Toleranzbereich des Vorhubs der Ventilnadel allein durch die Fertigungstoleranzen am Druckkörper und an der Düsennadel bestimmt wird. Der Vorhub kann daher genau gemessen und durch Anschleifen desThe intermediate disc and the intermediate bushing have the advantage that the tolerance range of the advance stroke of the valve needle, which is to be kept within narrow limits, is determined solely by the manufacturing tolerances on the pressure element and on the nozzle needle. The forward stroke can therefore be measured precisely and by grinding the
Anschlags der Ventilnadel ( der im allgemeinen von dem freien Ende der Ventilnadel gebildet wird, eingestellt werden. Meßtoleranzen und/oder im Betrieb bzw. bei der Montage auftretende Veränderungen wirken sich danach nicht mehr auf die Größe des Vorhubs aus. Bei einer bekannten Kraftstoff-Einspritzdüse dieser Art (DE 35 41 131 AI) wird die gehäusefeste Schulter zur AbStützung der zweiten Schließfeder durch eine stufenförmige Ausbildung der Federkammer, vorzugsweise als axiale Stufensackbohrung, geschaffen. Die zweite Schließfeder liegt über eine Ringscheibe an der zwischen den Bohrungsabschnitten mit unterschiedlichem Bohrungsdurchmesser gebildeten Ringschulter an. Der Druckstift ragt durch eine zentrale Öffnung in der Ringscheibe hindurch und wird stirnseitig von der ersten Schließfeder beaufschlagt. Die beiden Schließfedern sind entsprechend den beiden unterschiedlichen Durchmessern des Federraums im Durchmesser abgestuft.Stop of the valve needle ( which is generally formed by the free end of the valve needle can be adjusted. Measurement tolerances and / or changes occurring during operation or during assembly no longer affect the size of the advance stroke. In a known fuel injection nozzle of this type (DE 35 41 131 AI), the shoulder fixed to the housing for supporting the second closing spring is created by a stepped design of the spring chamber, preferably as an axial stepped pocket bore. The second closing spring rests on an annular disk against the annular shoulder formed between the bore sections with different bore diameters. The pressure pin protrudes through a central opening in the ring disk and is acted upon by the first closing spring on the face side. The two closing springs are graduated according to the two different diameters of the spring chamber.
Für eine solche Durchmesserabstufung von Federraum und Schließfedern ist ein Mindestdurchmesser des Düsenhalters erforderlich, der aus Festigkeitsgründen nicht unterschritten werden kann.For such a graduated diameter of the spring chamber and closing springs, a minimum diameter of the nozzle holder is required, which, for reasons of strength, cannot be undercut.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Kraftstoff-Einspritzdüse mit den kennzeichnenden Merkmalen des Anspruchs 1 hat den Vorteil, daß der Außendurchmesser des Düsenhalters ohne Festigkeitsverlust kleiner gemacht werden kann. Die Schließfedern werden baugleich ausgeführt, die Federkammer hat einen über die gesamte Länge konstanten Durchmesser, der relativ klein gehalten werden kann. Die gehäusefesteThe fuel injection nozzle according to the invention with the characterizing features of claim 1 has the advantage that the outer diameter of the nozzle holder can be made smaller without loss of strength. The closing springs are identical in construction, the spring chamber has a constant diameter over the entire length, which can be kept relatively small. The housing-fixed
AbStützung der dem Düsenkörper naheliegenden Schließfeder ' erfolgt über einen den Federraum kreuzenden Querbolzen, so daß der für die erste Schließfeder zur Verfügung stehende Federraum damit voll genutzt werden kann.The closing spring, which is close to the nozzle body, is supported by means of a cross bolt crossing the spring chamber, so that the spring chamber available for the first closing spring can thus be fully used.
Durch die in den weiteren Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen Einspritzdüse möglich.The measures listed in the further claims are advantageous developments and improvements in Claim 1 specified injector possible.
Gemäß einer vorteilhaften Ausführungsform der Erfindung wird der Querbolzen in eine den Federraum kreuzende radiale Sackbohrung eingeschoben und dichtet den Federraum durch einen O-Ring ab. Die Fixierung des Querbolzens in der radialen Sackbohrung erfolgt gemäß einer weiteren Ausführungsform der Erfindung durch ein als Federteller ausgebildetes Zentrierstück, über das sich die dem Düsenkörper naheliegende zweite Schließfeder an dem Querbolzen abstützt.According to an advantageous embodiment of the invention, the cross bolt is inserted into a radial blind hole crossing the spring chamber and seals the spring chamber by means of an O-ring. According to a further embodiment of the invention, the transverse bolt is fixed in the radial blind bore by a centering piece designed as a spring plate, by means of which the second closing spring, which is close to the nozzle body, is supported on the transverse bolt.
Zeichnungdrawing
Die Erfindung ist anhand eines in der Zeichnung dargestellten Ausführungsbeispiels in der nachfolgenden Beschreibung näher erläutert. Dabei zeigt die Zeichnung einen Längsschnitt einer Kraftstoff-Einspritzdüse für direkt einspritzende Brennkraftmaschinen.The invention is explained in more detail in the following description with reference to an embodiment shown in the drawing. The drawing shows a longitudinal section of a fuel injector for direct injection internal combustion engines.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Die in Fig. 1 im Längsschnitt dargestellte Einspritzdüse besitzt einen Düsenkörper 10, der zusammen mit einer stirnseitig anliegenden Zwischenscheibe 11 durch eineThe injection nozzle shown in longitudinal section in FIG. 1 has a nozzle body 10 which, together with an intermediate disk 11 lying on the end face, is guided by a nozzle
Überwurfmutter 12 an einem Düsenhalter 13 festgespannt ist. Im Düsenkörper 10 ist eine Ventilnadel 14 axial verschieblich gelagert, die mit einem nach innen gekehrten Ventilsitz im Düsenkörper 10 zusammenarbeitet und mehrere, dem Ventilsitz vorgelagerte Spritzöffnungen 15 steuert. Wie nicht weiter dargestellt ist, ist die Führungsbohrung 16 der Ventilnadel 14 im Düsenkörper 10 wie üblich an einer Stelle zu einem Druckraum erweitert, in dessen Bereich die Ventilnadel 14 eine Druckschulter hat. Der Druckraum ist über einen im Düsenhalter 13 verlaufenden und nur teilweise dargestellten Kanal 17 mit einem Stutzen 18 am Düsenhalter 13 zum Anschließen einer zu einer Kraftstoff- Einspritzpumpe fü-hrenden Kraftstoff-Förderleitung verbunden. Der an der Druckschulter der Ventilnadel 14 anstehende Kraftstoffdruck schiebt die Ventilnadel 14 entgegen dem abgestuften Kraftverlauf einer im folgenden beschriebenen Schließfederanordnung aus zwei Schraubendruckfedern nach oben, wobei die Ventilnadel 14 in einer Voreinspritzphase einen Vorhub und in einer Haupteinspritzphase einen Resthub ausführt, in welchen Kraftstoff über die Spritzöffnungen 15 ausgespritzt wird.Union nut 12 is clamped to a nozzle holder 13. A valve needle 14 is axially displaceably mounted in the nozzle body 10 and cooperates with an inward-facing valve seat in the nozzle body 10 and controls a plurality of spray openings 15 located upstream of the valve seat. As is not further shown, the guide bore 16 of the valve needle 14 in the nozzle body 10 is, as usual, expanded at one point to a pressure chamber, in the area of which the valve needle 14 has a pressure shoulder. The pressure chamber is via a channel 17 running in the nozzle holder 13 and only partially shown, with a nozzle 18 Nozzle holder 13 for connecting a fuel delivery line leading to a fuel injection pump. The fuel pressure applied to the pressure shoulder of the valve needle 14 pushes the valve needle 14 upward against the graduated force curve of a closing spring arrangement described in the following, consisting of two helical compression springs, the valve needle 14 executing a preliminary stroke in a pre-injection phase and a residual stroke in a main injection phase, in which fuel via the Spray openings 15 is sprayed out.
Im Düsenhalter 13 ist eine Federkammer 19 koaxial zur Ventilnadel 14 angeordnet, die als axiale Sackbohrung ausgebildet und an ihrer offenen Stirnseite von der Zwischenscheibe 11 abgeschlossen ist. In der Federkammer 19 ist eine"erste Schließfeder 21 und eine zweite Schließfeder 22 hintereinandergereiht angeordnet. Die vom Düsenkörper 10 entferntere erste Schließfeder 21 wirkt über einen Druckstift 23 ständig auf die Ventilnadel 14 in deren Schließrichtung. Hierzu stützt sich die erste Schließfeder 21 über eine Scheibe 20 an dem Grund 30 der Federkammer 19 und über ein federtellerartiges Abstützelement 31 an der Stirnseite des Druckstifts 23 ab. Das Abstützelement 31 trägt auf seiner Stirnseite eine Ausnehmung 32, die das Stirnende des Druckstiftes 23 formschlüssig aufnimmt. Der Druckstift 23 ist in einer Zwischenbuchse 24 axial verschieblich geführt und liegt stirnseitig an dem freien Ende der Ventilnadel 14 an. Die Zwischenbuchse 24 ist koaxial zur Ventilnadel 14 in der Zwischenscheibe 11 axial verschieblich geführt und trägt einen Anschlag 25 und einen Gegenanschlag 26. Der von einer radialen Ringschulter gebildete Anschlag 25 wirkt mit einem von einer gleichen Schulter an der Zwischenscheibe 11 gebildeten Gegenanschlag 27 zur Begrenzung des Gesamthubs der Ventilnadel 14 zusammen. Der von der Stirnseite der Zwischenbuchse 24 gebildete Gegenanschlag 26 wirkt mit einem von der Stirnseite der Ventilnadel 14 gebildeten Anschlag 28 zur Begrenzung des Vorhubs der Ventilnadel 14 zusammen.In the nozzle holder 13, a spring chamber 19 is arranged coaxially with the valve needle 14, which is designed as an axial blind bore and is closed on its open end face by the intermediate disk 11. A " first closing spring 21 and a second closing spring 22 are arranged in series in the spring chamber 19. The first closing spring 21, which is more distant from the nozzle body 10, acts continuously on the valve needle 14 in its closing direction via a pressure pin 23. For this purpose, the first closing spring 21 is supported by a disk 20 on the base 30 of the spring chamber 19 and via a spring plate-like support element 31 on the end face of the pressure pin 23. The support element 31 has on its end face a recess 32 which receives the end face of the pressure pin 23 in a form-fitting manner guided axially displaceably and abuts the free end of the valve needle 14. The intermediate bush 24 is guided axially displaceably in the intermediate disk 11 coaxially to the valve needle 14 and bears a stop 25 and a counter-stop 26. The stop 25 formed by a radial annular shoulder cooperates one of a same ichen shoulder formed on the intermediate plate 11 to limit the total stroke of the valve needle 14 together. The from the end face of the intermediate bushing 24 Counter stop 26 formed interacts with a stop 28 formed by the end face of valve needle 14 to limit the forward stroke of valve needle 14.
Die zur ersten Schließfeder 21 baugleich ausgeführte zweite Schließfeder 22 ist in der Federkammer 19 der erstenThe second closing spring 22, which is constructed identically to the first closing spring 21, is in the spring chamber 19 of the first
Schließfeder 21 zum Düsenkörper 10 hin vorgeordnet und umgibt koaxial den Druckstift 23. Mit einem Stirnende stützt sich die zweite Schließfeder 22 über einen Federteller 29 an der Zwischenbuchse 24 ab, die dadurch in Schließlage der Ventilnadel 14 an die Stirnseite des Düsenkörpers 10 angelegt wird, und mit ihrem anderen Ende preßt sich die zweite Schließfeder 22 über ein als Federteller ausgebildetes Zentrierstück 33 an einen die Federkammer 19 kreuzenden Querbolzen 34. Der Querbolzen 34, der im Bereich der Federkammer 19 eine radiale Durchgangsöffnung 35 zumClosing spring 21 upstream of the nozzle body 10 and coaxially surrounds the pressure pin 23. With one end, the second closing spring 22 is supported by a spring plate 29 on the intermediate bush 24, which is thereby placed in the closed position of the valve needle 14 on the end face of the nozzle body 10, and with its other end, the second closing spring 22 presses via a centering piece 33 designed as a spring plate against a cross bolt 34 crossing the spring chamber 19. The cross bolt 34, which has a radial through opening 35 in the region of the spring chamber 19
Durchtritt des Druckstiftes 33 und eine Aufnahme 36 für das Zentrierstück 33 aufweist, ist in eine radiale, die Federkammer 19 querende Sackbohrung 37 eingeschoben. Ein in einer Ringnut 38 des Querbolzens 34 einliegender, als O-Ring ausgebildeter Dichtungsring 39 dichtet den Federkammer 19 ab. Die Fixierung des Querbolzens 34 in der radialen Sackbohrung 37 erfolgt durch die Anpreßkraft der zweiten Schließfeder 22, die über das Zentrierstück 33 und die Aufnahme 36 den Querbolzen 34 in der Federkammer 19 gegen Querverschiebung sichert. Die Federkammer 19 ist noch über einen Kanal 40 mit einem Anschlußnippel 41 für eine Leckölleitung verbunden.Passage of the pressure pin 33 and a receptacle 36 for the centering piece 33 is inserted into a radial blind bore 37 which crosses the spring chamber 19. A sealing ring 39, which is located in an annular groove 38 of the transverse bolt 34 and is designed as an O-ring, seals the spring chamber 19. The transverse bolt 34 is fixed in the radial blind bore 37 by the contact pressure of the second closing spring 22, which secures the transverse bolt 34 in the spring chamber 19 against transverse displacement via the centering piece 33 and the receptacle 36. The spring chamber 19 is still connected via a channel 40 to a connecting nipple 41 for a leak oil line.
Beim Einspritzvorgang führt die Ventilnadel 14 einen Vorhub hv aus, bei welchem nur die erste Schließfeder 21 als Gegenkraft wirksam ist. Bei diesem Vorhub wird eine begrenzte Voreinspritzmenge aus den Spritzöffnungen 15 ausgespritzt. Der Vorhub hv ist beendet, wenn der Anschlag 28 an der Ventilnadel 14 an dem Gegenanschlag 26 der Zwischenbuchse 24 zur Anlage kommt. In dieser Stellung verharrt die Ventinadel 14, bis der weiter ansteigende Kraftstoffdruck nunmehr die Gegenkräfte beider Schließfedern 21,22 überwindet. Danach wird die Ventilnadel 14 samt Zwischenbuchse 24 in Öffnungsrichtung weiterbewegt, bis sie nach dem Resthub hv ihren Gesamthub zurückgelegt hat. Dieser ist begrenzt durch den Gegenanschlag 27 an derDuring the injection process, the valve needle 14 performs a preliminary stroke h v , in which only the first closing spring 21 acts as a counterforce. During this preliminary stroke, a limited pre-injection quantity is injected from the injection openings 15. The preliminary stroke h v is ended when the stop 28 on the valve needle 14 comes to rest against the counter stop 26 of the intermediate bush 24. The valve needle 14 remains in this position until the rising one Fuel pressure now overcomes the opposing forces of both closing springs 21, 22. Thereafter, the valve needle 14 together with the intermediate bush 24 is moved further in the opening direction until it has completed its total stroke after the remaining stroke h v . This is limited by the counter stop 27 on the
Zwischenscheibe 11, an welcher der Anschlag 25 an der Zwischenbuchse 24 anschlägt. Durch die baugleiehe Ausführung der beiden Schließfedern 21,22 und die AbStützung der zweiten Schließfeder 22 an einem in dem Federraum 16 eingesetzten Querbolzen kann der Durchmesser der Federkammer 19 sehr klein gehalten und damit die Einspritzdüse insgesamt relativ schlank gemacht werden.Intermediate disc 11, on which the stop 25 strikes the intermediate bush 24. Due to the construction of the two closing springs 21, 22 and the support of the second closing spring 22 on a transverse bolt inserted in the spring chamber 16, the diameter of the spring chamber 19 can be kept very small and the injection nozzle can thus be made relatively slim overall.
Die Erfindung ist nicht auf das beschriebene Ausführungsbeispiel beschränkt. So kann die Zwischenscheibe 11 Juch aus zwei Einzelscheiben gebildet werden, von denen die untere Einzelscheibe einen größeren Innendurchmesser als die obere hat. Der Gegenanschlag 27 zur Begrenzung des Gesamthubs der Ventilnadel 14 wird durch den von der unteren Einzelscheibe nicht bedeckten Bereich in der oberen Einzelscheibe gebildet. Bei dieser Ausführung derThe invention is not limited to the exemplary embodiment described. The intermediate disk 11 Juch can thus be formed from two individual disks, of which the lower individual disk has a larger inner diameter than the upper one. The counter-stop 27 for limiting the total stroke of the valve needle 14 is formed by the area in the upper single disk not covered by the lower single disk. In this version of the
Zwischenscheibe 11 kann auch der Gesamthub der Ventilnadel 14 durch entsprechende Wahl der Scheibendicke der unteren Einzelscheibe leicht auf den gewünschten Wert eingestellt werden. Intermediate disc 11, the total stroke of valve needle 14 can be easily adjusted to the desired value by appropriate selection of the disc thickness of the lower individual disc.

Claims

Ansprüche Expectations
1. Kraftstoff-Einspritzdüse für Brennkraftmaschinen mit einem eine Ventilnadel axial verschieblich aufnehmenden Düsenkörper mit von der Ventilnadel gesteuerten Düsenöffnungen, der über eine Zwischenscheibe an einem Düsenhalter befestigt ist, mit einer in der Zwischenscheibe axial verschieblichen Zwischenbuchse, die einen mit einem Anschlag an der Ventilnadel zusammenwirkenden Gegenanschlag zur Begrenzung eines Vorhubs der Ventilnadel und einen mit einem1. Fuel injection nozzle for internal combustion engines with a nozzle body which axially displaceably accommodates a nozzle body with nozzle openings controlled by the valve needle and which is fastened to a nozzle holder via an intermediate disk, with an intermediate bush which is axially displaceable in the intermediate disk and which interacts with a stop on the valve needle Counterstop to limit a forward stroke of the valve needle and one with a
Gegenanschlag an der Zwischenscheibe zusammenwirkenden Anschlag zur Begrenzung des Gesamthubs der Ventilnadel aufweist, und mit zwei als Schraubendruckfedern in einer Federkammer im Düsenhalter hintereinandergereiht angeordneten Schließfedern, von denen die vomCounter-stop on the washer cooperating stop to limit the total stroke of the valve needle, and with two spring springs arranged in series in a spring chamber in the nozzle holder, of which the by
Düsenkörper entferntere erste Schließfeder über einen in der Zwischenbuchse geführten, zur Ventilnadel kaoxialen Druckstift ständig auf die Ventilnadel wirkt und die dem Druckkörper näherliegende zweite Schließfeder den Druckstift koaxial umgibt, sich an einer gehäusefesten Schulter in der Federkammer abstützt und über ein Druckstück auf die Zwischenbuchse wirkt und diese in Schließlage der Ventilnadel an dem Düsenkörper anlegt, dadurch gekennzeichnet, daß beide Schließfedern (21,22) baugleich ausgeführt sind und daß die gehäusefeste Schulter zur AbStützung der zweiten Schließfeder (22) von einem die Federkammer (19) durchdringenden Querbolzen (34) gebildet ist, der eine radiale Durchgangsöffnung (35) zum Durchtritt des Druckstiftes 5 (23) aufweist.The first closing spring, which is more distant from the nozzle, constantly acts on the valve needle via a pressure pin which is guided in the intermediate bush and is caoxial to the valve needle and the second closing spring which is closer to the pressure body surrounds the pressure pin coaxially, is supported on a shoulder fixed to the housing in the spring chamber and acts on the intermediate bush via a pressure piece and this engages the nozzle body in the closed position of the valve needle, characterized in that both closing springs (21, 22) are of identical construction and that the housing-fixed Shoulder for supporting the second closing spring (22) is formed by a cross bolt (34) penetrating the spring chamber (19) and having a radial through opening (35) for the push pin 5 (23) to pass through.
2. Einspritzdüse nach Anspruch 1, dadurch gekennzeichnet, daß der Querbolzen (34) in eine die Federkammer (19) durchdringende radiale Sackbohrung (37) eingeschoben ist.2. Injection nozzle according to claim 1, characterized in that the transverse bolt (34) is inserted into a radial blind bore (37) penetrating the spring chamber (19).
-1-0 3. Einspritzdüse nach Anspruch 2, dadurch gekennzeichnet, daß der Querbolzen (34) in einem in Einschieberichtung hinter der Durchgangsöffnung (35) liegenden Bereich eine Ringnut (38) trägt, in welcher ein sich an die Bohrungswand der Sackbohrung (37) anpressender- 1 - 0 3. Injection nozzle according to claim 2, characterized in that the transverse pin (34) in an area behind in the insertion opening (35) lies in an annular groove (38) in which an on the bore wall of the blind bore (37th ) more pressing
15 Dichtungsring (39) einliegt.15 Sealing ring (39) is inserted.
4. Einspritzdüse nach einem der Ansprüche 1 - 3, dadurch gekennzeichnet, daß der Querbolzen (34) im Kreuzungsbereich der Federkammer (19) eine Aufnahme (36) für ein als Federteller ausgebildetes Zentrierstück (33)4. Injection nozzle according to one of claims 1-3, characterized in that the cross bolt (34) in the crossing region of the spring chamber (19) has a receptacle (36) for a centering piece designed as a spring plate (33)
20 aufweist, an dem sich die zweite Schließfeder (22) abstützt.20, on which the second closing spring (22) is supported.
5. Einspritzdüse nach einem der Ansprüche 1 - 4, dadurch gekennzeichnet, daß die erste Schließfeder (21) sich am Grund (30) der. als axiale Sackbohrung ausgebildeten5. Injection nozzle according to one of claims 1-4, characterized in that the first closing spring (21) on the base (30) of the. trained as an axial blind bore
25 Federkammer (19) abstützt und über ein federtellerartiges Abstützelement (31) auf die Stirnseite des Druckstiftes (23) wirkt.25 spring chamber (19) is supported and acts on the end face of the pressure pin (23) via a spring plate-like support element (31).
6. Einspritzdüse nach Anspruch 5, dadurch gekennzeichnet, daß das Abstützelement das Stirnende des Druckstiftes6. Injection nozzle according to claim 5, characterized in that the supporting element is the front end of the pressure pin
30 (23) in einer stirnseitigen Ausnehmung (32) aufnimmt. 30 (23) in a front recess (32).
EP89911536A 1988-11-18 1989-10-19 Fuel injection nozzle for internal combustion engines Expired - Lifetime EP0444053B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3839038 1988-11-18
DE3839038A DE3839038A1 (en) 1988-11-18 1988-11-18 FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES

Publications (2)

Publication Number Publication Date
EP0444053A1 true EP0444053A1 (en) 1991-09-04
EP0444053B1 EP0444053B1 (en) 1993-03-03

Family

ID=6367434

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89911536A Expired - Lifetime EP0444053B1 (en) 1988-11-18 1989-10-19 Fuel injection nozzle for internal combustion engines

Country Status (4)

Country Link
EP (1) EP0444053B1 (en)
JP (1) JPH04501752A (en)
DE (2) DE3839038A1 (en)
WO (1) WO1990005844A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4005774A1 (en) * 1990-02-23 1991-08-29 Bosch Gmbh Robert IC engine fuel-injection nozzle - has coaxial thrust pins with fingers passing between each other and supporting springs
DE4101235C1 (en) * 1991-01-17 1992-06-04 Robert Bosch Gmbh, 7000 Stuttgart, De
GB9323236D0 (en) * 1993-11-11 1994-01-05 Lucas Ind Plc Fuel injection nozzle
DE19638339B4 (en) * 1996-09-19 2008-10-02 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2554987A1 (en) * 1975-12-06 1977-06-16 Bosch Gmbh Robert FUEL INJECTION NOZZLE FOR COMBUSTION MACHINES
DE3610658A1 (en) * 1985-11-21 1987-05-27 Bosch Gmbh Robert FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9005844A1 *

Also Published As

Publication number Publication date
DE3839038A1 (en) 1990-05-23
EP0444053B1 (en) 1993-03-03
JPH04501752A (en) 1992-03-26
WO1990005844A1 (en) 1990-05-31
DE58903686D1 (en) 1993-04-08

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