EP0240693A1 - Fuel injector for internal-combustion engines - Google Patents

Fuel injector for internal-combustion engines Download PDF

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Publication number
EP0240693A1
EP0240693A1 EP87102772A EP87102772A EP0240693A1 EP 0240693 A1 EP0240693 A1 EP 0240693A1 EP 87102772 A EP87102772 A EP 87102772A EP 87102772 A EP87102772 A EP 87102772A EP 0240693 A1 EP0240693 A1 EP 0240693A1
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EP
European Patent Office
Prior art keywords
piston
valve needle
injection nozzle
fuel
housing
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
EP87102772A
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German (de)
French (fr)
Other versions
EP0240693B1 (en
Inventor
Ewald Dr. Eblen
Paul Dipl.-Ing. Füssner
Karl Hofmann
Günter Kapolke
Edgar Schneider
Max Dr. Straubel
Werner Wagner
Klaus Wolf
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0240693A1 publication Critical patent/EP0240693A1/en
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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
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • 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
    • F02M61/161—Means for adjusting injection-valve lift

Definitions

  • the invention relates to a fuel injector according to the preamble of the main claim.
  • Injectors of this type are used for targeted pre-injection by means of pre-stroke control to reduce the combustion noise.
  • a known injection nozzle of the type mentioned (DE-A1 27 11 902)
  • the second pressure chamber and the piston which exerts an additional closing force on the valve needle after a forward stroke of the valve needle, between the chamber receiving the closing spring and the fuel connection piece in the holding body arranged.
  • the piston is firmly connected to a plunger, which is guided through the closing spring up to the pre-stroke dimension to a pressure piece, via which the closing spring acts on the valve needle.
  • This arrangement of the second pressure chamber and the piston requires an axial extension of the injection nozzle compared to a version without an additional piston for the pre-stroke control.
  • the actual values of the preliminary stroke and the total stroke are influenced by a large number of tolerances on different parts of the injection nozzle, so that the required close tolerance of the strokes necessitates an increased production outlay.
  • injection nozzles for pre-injection and main injection are known (DE-A1 25 55 019), in which pin-shaped pistons acted upon by fuel in the opening direction of the valve needle are displaceably mounted in the intermediate disc, which counteract the closing spring during the pre-stroke of the valve needle and at the end of the pre-stroke should be caught on shoulders fixed to the housing.
  • the closing spring must be dimensioned so strong that it applies the full closing force alone in the main injection phase.
  • the arrangement according to the invention with the characterizing features of the main claim has the advantage that conventional parts can be used for the holding body and the nozzle body without any modification and that the injection nozzle does not have to be extended or only insignificantly compared to a conventional design without an additional piston. Furthermore, fewer parts and dimensions are decisive for the size of the forward stroke and the total stroke of the valve needle in the embodiment according to the invention than in the case of an injection nozzle of the generic type, so that exact compliance with the prescribed stroke values poses fewer manufacturing problems than in the known embodiment.
  • the stop shoulder cooperating with the valve needle on the additional piston is particularly advantageous compared to that with the first stop fixed to the housing cooperating stop shoulder is set back by the amount of the forward stroke.
  • the upper, flat end face of the nozzle body can be finished in one operation with the flat, pinless top end face of the valve needle inserted into the nozzle body with one tool in one operation.
  • FIG. 1 shows a longitudinal section through the first exemplary embodiment
  • FIG. 2 enlarges a detail from FIG. 1
  • FIG. 3 shows a variant for the embodiment according to FIGS. 1 and 2
  • FIGS. 4 and 5 each show the second and third exemplary embodiment on the basis of a sectional diagram corresponding to FIG
  • FIG. 6 shows a variant of the third exemplary embodiment according to FIG. 5.
  • the injection nozzle according to FIGS. 1 and 2 has a nozzle body 10 which, together with an intermediate disk 12, is clamped to a holding body 16 by means of a union nut 14.
  • a valve needle 18 is slidably mounted in the nozzle body 10 and cooperates with an inward-facing valve seat in the nozzle body 10, which is arranged in front of a plurality of spray openings 20.
  • the guide bore of the valve needle 18 is, as usual, expanded at one point to a pressure chamber, in the area of which the valve needle 18 has a pressure shoulder and which is connected via a channel 22 and a filter body 23 to a connecting piece 24 on the holding body 16 for connecting a fuel line.
  • the fuel acting on the pressure shoulder of the valve needle 18 pushes the valve needle 18 upward against the graduated force curve of a closing force arrangement described below, the fuel being injected through the injection openings 20 in a pre-injection phase and a main injection phase.
  • a chamber 26 is formed for receiving a closing spring 28, which is supported by a washer 30 on the bottom of the chamber 26 and constantly acts on the valve needle 18 via a pressure piece 32 and a pressure bolt 34 passing through the washer 12.
  • a piston 36 is tightly but displaceably mounted in the intermediate disk 12 and has two sections 38, 40 of different diameters, between which an annular shoulder 42 is formed.
  • the correspondingly shaped bore in the intermediate disk 12 is provided with an annular shoulder 44 which delimits a second pressure chamber 46 with the annular shoulder 42 on the piston 36.
  • the piston 36 rests with its lower end face 48 on the upper end face 50 of the nozzle body 10.
  • the distance between the annular shoulders 42 and 44 corresponds to the total stroke h g reduced by a preliminary stroke h v and the distance between the end face 48 of the piston 36 and the flat, journalless end face 52 of the valve needle 18 in the closed position Forward stroke h v .
  • the pressure chamber 46 is connected to the channel 22 via a bore 54.
  • the valve needle 18 first performs the preliminary stroke h v , in which the fuel in the pressure chamber of the nozzle body 10 only has to overcome the counterforce of the closing spring 28.
  • the valve needle hits 18 on the piston 36, which stops the further movement of the valve needle 18 until the fuel pressure has risen so far that its force exerted on the valve needle in the opening direction exceeds the force of the closing spring 28 and the hydraulic closing force acting on the annular shoulder 42.
  • the valve needle 18 together with the piston 36 is moved upwards until the annular shoulders 42, 44 come into contact with one another on the piston 36 and on the intermediate disk 12.
  • the processes take place in reverse order.
  • the arrangement described has the advantage that the additional piston 36 does not require any additional space in the longitudinal direction of the injection nozzle and that the remaining stroke h g - h v of the valve needle 18 is influenced solely by the axial position tolerances of the annular shoulder 42, 44 on the piston 36 and the intermediate disk 12 becomes.
  • the valve needle 18a is designed such that in its closed position the upper end face 52a lies in the plane of the upper end face 50 of the nozzle body 10, so that both parts can be finished together by one tool.
  • the preliminary stroke play is obtained in this case in that an inner annular surface section 48a of the lower end face of the piston 36a is set back by the amount of the preliminary stroke h v compared to the remaining outer annular surface section 48b of this end face.
  • the actual dimension of the forward stroke is only influenced by tolerances on the piston 36a, which are tool-related and can therefore be kept extremely small.
  • the variant according to FIG. 3 differs from the embodiment according to FIGS. 1 and 2 in that the pressure pin 34a is integrally formed on the pressure element 32a.
  • an externally and internally smooth-cylindrical piston bushing 58 is displaceably guided in a correspondingly shaped annular cylindrical recess in the intermediate plate 56 in an intermediate plate 56.
  • a pressure chamber 62 is formed in this recess above the upper end face 60 of the piston bushing 58 and is connected to the channel 22 via a bore 64.
  • the fuel pressure in the pressure chamber 62 presses the piston bushing 58 against the upper end face 50 of the nozzle body 10, which lies above the upper end face 52 of the valve needle 18 by the amount of advance stroke h v .
  • the inner diameter of the piston bush 58 is smaller than the diameter of the valve needle 18, so that the valve needle 18 abuts the lower end face 66 of the piston bush 58 after the advance stroke h v and takes it upward according to the desired pressure level in the opening pressure curve of the fuel.
  • the total stroke h g of the valve needle 18 is limited by the inner collar 68 of the intermediate disk 56, which surrounds the pressure pin 34 and is correspondingly set back relative to the lower end face of the intermediate disk 56.
  • the injection nozzle according to FIG. 5 differs from that according to FIG. 4 essentially in that instead of the piston bushing 58, a ring of pin-like individual pistons 70 is provided, the guide bores of which open into an annular pressure chamber 72 at the top. This is formed by a corresponding recess in the upper end face of an intermediate disk 74, which is closed off by a cover plate 76 and is connected to the channel 22 via a groove 78.
  • the individual pistons 70 perform the same function as the piston bush 58 according to FIG. 4 and the total stroke h g of the valve needle 18 is also limited here by a recessed inner annular surface section 80 of the intermediate bush 74.
  • the upper end face 52a of the valve needle 18a lies in its closed position in the plane of the upper end face 50 of the nozzle body 10.
  • the individual pistons 70a with lugs 62 provided which in the lower end position of the individual pistons 70a rest on the end face 50 of the nozzle body 10 and hold the end face regions 84 of the individual pistons 70 projecting into the path of the valve needle 18a by the dimension h v above the end face 50.
  • the measure taken in the variant according to FIG. 6 could also be provided in an equivalent form for the piston bushing 58 according to FIG. 4, e.g. by turning them in at the lower end. It is thereby achieved that the upper end faces of nozzle body 10 and nozzle needle 18 can also be machined there. If only two diametrically opposed individual pistons 70 and 70a are provided, the arrangement of a cover plate 76 can be dispensed with if blind holes are provided for receiving the individual pistons 70 and 70a, which are each offset by 90 ° with respect to the channel 22 and over Single holes are connected to these.

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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

Fuel injector for internal combustion engines for preinjection and main injection with an inwards opening valve needle (18), which is loaded in the closing direction by a closing spring (28) and after one prelift (hv) also by a piston (36) to which fuel is admitted. The piston (36) is displaceably guided in a shim (12) clamped between nozzle bodies (10) and holders (16), on which shim there is also an integrally formed stop (44) to limit the overall lift (hg) of the valve needle. This arrangement has the advantage that the injector need not be made any longer or appreciably longer than an injector without additional pistons and that the dimensional tolerances of the prelift (hv) and overall lift (hg) of the valve needle (18) can be kept extremely small without undue manufacturing expense. <IMAGE>

Description

Stand der TechnikState of the art

Die Erfindung bezieht sich auf eine Kraftstoff-Einspritz­düse nach der Gattung des Hauptanspruchs. Einspritzdüsen dieser Gattung dienen der gezielten Voreinspritzung durch Vorhubsteuerung zur Senkung des Verbrennungsgeräusches. Bei einer bekannten Einspritzdüse der eingangs genannten Gattung (DE-A1 27 11 902) ist der zweite Druckraum und der Kolben, der nach einem Vorhub der Ventilnadel eine zusätzliche Schließkraft auf diese ausübt, zwischen der die Schließfeder aufnehmenden Kammer und dem Kraftstoff-­Anschlußstutzen im Haltekörper angeordnet. Der Kolben ist mit einem Stößel fest verbunden, welcher durch die Schließ­feder hindurch bis auf das Vorhubmaß an ein Druckstück heran­geführt ist, über welches die Schließfeder auf die Ventil­nadel einwirkt. Diese Anordnung des zweiten Druckraumes und des Kolbens bedingt eine axiale Verlängerung der Einspritz­düse gegenüber einer Ausführung ohne zusätzlichen Kol­ben zur Vorhubsteuerung. Außerdem sind die Istwerte von Vorhub und Gesamthub von einer Vielzahl von Toleranzen an verschiedenen Teilen der Einspritzdüse beeinflußt, so daß die geforderte enge Tolerierung der Hübe einen er­höhten Fertigungsaufwand bedingt.The invention relates to a fuel injector according to the preamble of the main claim. Injectors of this type are used for targeted pre-injection by means of pre-stroke control to reduce the combustion noise. In a known injection nozzle of the type mentioned (DE-A1 27 11 902), the second pressure chamber and the piston, which exerts an additional closing force on the valve needle after a forward stroke of the valve needle, between the chamber receiving the closing spring and the fuel connection piece in the holding body arranged. The piston is firmly connected to a plunger, which is guided through the closing spring up to the pre-stroke dimension to a pressure piece, via which the closing spring acts on the valve needle. This arrangement of the second pressure chamber and the piston requires an axial extension of the injection nozzle compared to a version without an additional piston for the pre-stroke control. In addition, the actual values of the preliminary stroke and the total stroke are influenced by a large number of tolerances on different parts of the injection nozzle, so that the required close tolerance of the strokes necessitates an increased production outlay.

Ferner sind Einspritzdüsen für Vor- und Haupteinspritzung bekannt (DE-A1 25 55 019), bei denen in der Zwischenschei­be vom Kraftstoff in Öffnungsrichtung der Ventilnadel be­aufschlagte stiftförmige Kolben verschiebbar gelagert sind, welche während des Vorhubes der Ventilnadel der Schließ­feder entgegenwirken und am Ende des Vorhubs an gehäuse­festen Schultern abgefangen werden. Bei dieser Ausführung muß die Schließfeder so stark bemessen sein, daß sie in der Haupteinspritzphase die volle Schließkraft allein auf­bringt.Furthermore, injection nozzles for pre-injection and main injection are known (DE-A1 25 55 019), in which pin-shaped pistons acted upon by fuel in the opening direction of the valve needle are displaceably mounted in the intermediate disc, which counteract the closing spring during the pre-stroke of the valve needle and at the end of the pre-stroke should be caught on shoulders fixed to the housing. In this version, the closing spring must be dimensioned so strong that it applies the full closing force alone in the main injection phase.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Anordnung mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß für den Haltekörper und den Düsenkörper herkömmliche Teile ohne jede Abänderung verwendet werden können und daß die Einspritzdüse nicht oder nur unwesentlich gegenüber einer herkömmlichen Ausführung ohne zusätzlichen Kolben verlängert werden muß. Ferner sind bei der erfindungsge­mäßen Ausführung weniger Teile und Abmessungen für die Größe des Vorhubs und des Gesamthubes der Ventilnadel maß­gebend als bei einer Einspritzdüse der gattungsmäßigen Art, so daß die exakte Einhaltung der vorgeschriebenen Hubwer­te geringere fertigungstechnische Probleme als bei der bekannten Ausführung aufwirft.The arrangement according to the invention with the characterizing features of the main claim has the advantage that conventional parts can be used for the holding body and the nozzle body without any modification and that the injection nozzle does not have to be extended or only insignificantly compared to a conventional design without an additional piston. Furthermore, fewer parts and dimensions are decisive for the size of the forward stroke and the total stroke of the valve needle in the embodiment according to the invention than in the case of an injection nozzle of the generic type, so that exact compliance with the prescribed stroke values poses fewer manufacturing problems than in the known embodiment.

Durch die in den Unteransprüchen enthaltenen Merkmale sind vorteilhafte Weiterbildungen der Anordnung nach dem Haupt­anspruch möglich.Advantageous developments of the arrangement according to the main claim are possible due to the features contained in the subclaims.

Besonders vorteilhaft ist es, wenn die mit der Ventilnadel zusammenarbeitende Anschlagschulter am zusätzlichen Kolben gegenüber dessen mit dem ersten gehäusefesten Anschlag zu­ sammenarbeitende Anschlagschulter um das Maß des Vorhubes zurückversetzt ist. In diesem Falle kann die obere, ebene Stirnseite des Düsenkörpers in einem Arbeitsgang mit der ebenen, zapfenlosen oberen Stirnseite der in den Düsen­körper eingesteckten Ventilnadel mit einem Werkzeug in einem Arbeitsgang fertigbearbeitet werden.It when the stop shoulder cooperating with the valve needle on the additional piston is particularly advantageous compared to that with the first stop fixed to the housing cooperating stop shoulder is set back by the amount of the forward stroke. In this case, the upper, flat end face of the nozzle body can be finished in one operation with the flat, pinless top end face of the valve needle inserted into the nozzle body with one tool in one operation.

Zeichnungdrawing

Drei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschrei­bung näher erläutert. Es zeigen Figur 1 einen Längsschnitt durch das erste Ausführungsbeispiel, Figur 2 vergrößert einen Ausschnitt aus Figur 1, Figur 3 eine Variante zur Ausführung nach den Figuren 1 und 2 die Figuren 4 und 5 das zweite und dritte Ausführungsbeispiel je anhand eines der Figur 2 entsprechenden Schnittbildes, und die Figur 6 eine Variante des dritten Ausführungsbeispiels nach Figur 5.Three embodiments of the invention are shown in the drawing and explained in more detail in the following description. FIG. 1 shows a longitudinal section through the first exemplary embodiment, FIG. 2 enlarges a detail from FIG. 1, FIG. 3 shows a variant for the embodiment according to FIGS. 1 and 2, FIGS. 4 and 5 each show the second and third exemplary embodiment on the basis of a sectional diagram corresponding to FIG , and FIG. 6 shows a variant of the third exemplary embodiment according to FIG. 5.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Die Einspritzdüse nach den Figuren 1 und 2 hat einen Düsen­körper 10, der zusammen mit einer Zwischenscheibe 12 durch eine Überwurfmutter 14 an einem Haltekörper 16 festge­spannt ist. Im Düsenkörper 10 ist eine Ventilnadel 18 ver­schiebbar gelagert, die mit einem nach innen gekehrten Ven­tilsitz im Düsenkörper 10 zusammenarbeitet, der mehreren Spritzöffnungen 20 vorgelagert ist. Die Führungsbohrung der Ventilnadel 18 ist wie üblich an einer Stelle zu einem Druckraum erweitert, in dessen Bereich die Ventilnadel 18 eine Druckschulter hat und der über einen Kanal 22 und einen Filterkörper 23 mit einem Stutzen 24 am Haltekörper 16 zum Anschließen einer Kraftstoffleitung verbunden ist. Der an der Druckschulter der Ventilnadel 18 angreifende Kraftstoff schiebt die Ventilnadel 18 entgegen dem abge­stuften Kraftverlauf einer im folgenden beschriebenen Schließkraftanordnung nach oben, wobei der Kraftstoff in einer Voreinspritzphase und einer Haupteinspritzphase durch die Spritzöffnungen 20 ausgespritzt wird.The injection nozzle according to FIGS. 1 and 2 has a nozzle body 10 which, together with an intermediate disk 12, is clamped to a holding body 16 by means of a union nut 14. A valve needle 18 is slidably mounted in the nozzle body 10 and cooperates with an inward-facing valve seat in the nozzle body 10, which is arranged in front of a plurality of spray openings 20. The guide bore of the valve needle 18 is, as usual, expanded at one point to a pressure chamber, in the area of which the valve needle 18 has a pressure shoulder and which is connected via a channel 22 and a filter body 23 to a connecting piece 24 on the holding body 16 for connecting a fuel line. The fuel acting on the pressure shoulder of the valve needle 18 pushes the valve needle 18 upward against the graduated force curve of a closing force arrangement described below, the fuel being injected through the injection openings 20 in a pre-injection phase and a main injection phase.

Im Haltekörper 16 ist eine Kammer 26 zur Aufnahme einer Schließfeder 28 gebildet, die sich über eine Scheibe 30 am Boden der Kammer 26 abstützt und über ein Druckstück 32 und einen die Zwischenscheibe 12 durchsetzenden Druck­bolzen 34 ständig auf die Ventilnadel 18 einwirkt. In der Zwischenscheibe 12 ist ein Kolben 36 dicht, jedoch ver­schiebbar gelagert, der zwei im Durchmesser unterschied­lich große Abschnitte 38, 40 hat, zwischen denen eine Ring­schulter 42 gebildet ist.In the holding body 16, a chamber 26 is formed for receiving a closing spring 28, which is supported by a washer 30 on the bottom of the chamber 26 and constantly acts on the valve needle 18 via a pressure piece 32 and a pressure bolt 34 passing through the washer 12. A piston 36 is tightly but displaceably mounted in the intermediate disk 12 and has two sections 38, 40 of different diameters, between which an annular shoulder 42 is formed.

Die entsprechend geformte Bohrung in der Zwischenscheibe 12 ist mit einer Ringschulter 44 versehen, die mit der Ringschulter 42 am Kolben 36 einen zweiten Druckraum 46 begrenzt. In seiner untersten Stellung liegt der Kolben 36 mit seiner unteren Stirn­seite 48 an der oberen Stirnseite 50 des Düsenkörpers 10 auf. In dieser Stellung des Kolbens 36 entspricht der Abstand zwi­schen den Ringschultern 42 und 44 dem Gesamthub hg vermindert um einen Vorhub hv und der Abstand zwischen der Stirnseite 48 des Kolbens 36 und der ebenen, zapfenlosen Stirnseite 52 der sich in Schließstellung befindenden Ventilnadel 18 dem Vorhub hv. Der Druckraum 46 ist über eine Bohrung 54 mit dem Kanal 22 verbunden.The correspondingly shaped bore in the intermediate disk 12 is provided with an annular shoulder 44 which delimits a second pressure chamber 46 with the annular shoulder 42 on the piston 36. In its lowest position, the piston 36 rests with its lower end face 48 on the upper end face 50 of the nozzle body 10. In this position of the piston 36, the distance between the annular shoulders 42 and 44 corresponds to the total stroke h g reduced by a preliminary stroke h v and the distance between the end face 48 of the piston 36 and the flat, journalless end face 52 of the valve needle 18 in the closed position Forward stroke h v . The pressure chamber 46 is connected to the channel 22 via a bore 54.

Beim Öffnungshub führt die Ventilnadel 18 zunächst den Vor­hub hv aus, bei welchem der Kraftstoff im Druckraum des Düsenkörpers 10 nur die Gegenkraft der Schließfeder 28 zu überwinden hat. Am Ende des Vorhubes stößt die Ventilnadel 18 am Kolben 36 an, der die Weiterbewegung der Ventilnadel 18 stoppt, bis der Kraftstoffdruck so weit angestiegen ist, daß seine in Öffnungsrichtung auf die Ventilnadel ausgeübte Kraft die Kraft der Schließfeder 28 und die auf die Ring­schulter 42 einwirkende hydraulische Schließkraft über­steigt. Danach wird die Ventilnadel 18 samt Kolben 36 nach oben bewegt, bis die Ringschultern 42, 44 am Kolben 36 und an der Zwischenscheibe 12 aneinander zur Anlage kommen. Beim Schließhub spielen sich die Vorgänge in umgekehrter Reihen­folge ab.During the opening stroke, the valve needle 18 first performs the preliminary stroke h v , in which the fuel in the pressure chamber of the nozzle body 10 only has to overcome the counterforce of the closing spring 28. At the end of the preliminary stroke, the valve needle hits 18 on the piston 36, which stops the further movement of the valve needle 18 until the fuel pressure has risen so far that its force exerted on the valve needle in the opening direction exceeds the force of the closing spring 28 and the hydraulic closing force acting on the annular shoulder 42. Thereafter, the valve needle 18 together with the piston 36 is moved upwards until the annular shoulders 42, 44 come into contact with one another on the piston 36 and on the intermediate disk 12. In the closing stroke, the processes take place in reverse order.

Die beschriebene Anordnung hat den Vorteil, daß der zusätz­liche Kolben 36 keinen zusätzlichen Platz in Längsrichtung der Einspritzdüse benötigt und daß der Resthub hg - hv der Ventilnadel 18 allein durch die axialen Lagetoleranzen der Ringschulter 42, 44 am Kolben 36 und der Zwischenscheibe 12 beeinflußt wird.The arrangement described has the advantage that the additional piston 36 does not require any additional space in the longitudinal direction of the injection nozzle and that the remaining stroke h g - h v of the valve needle 18 is influenced solely by the axial position tolerances of the annular shoulder 42, 44 on the piston 36 and the intermediate disk 12 becomes.

Bei der Variante nach Figur 3 ist die Ventilnadel 18a so ausgebildet, daß in ihrer Schließstellung die obere Stirn­seite 52a in der Ebene der oberen Stirnseite 50 des Düsen­körpers 10 liegt, so daß beide Teile durch ein Werkzeug gemeinsam fertigbearbeitet werden können. Das Vorhub­spiel wird in diesem Fall dadurch erhalten, daß ein innerer Ringflächenabschnitt 48a der unteren Stirnseite des Kolbens 36a gegenüber dem verbleibenden äußeren Ring­flächenabschnitt 48b dieser Stirnseite um das Maß des Vor­hubes hv zurückgesetzt ist. Bei dieser Ausbildung des Kol­bens 36a wird das Istmaß des Vorhubes lediglich durch Tole­ranzen am Kolben 36a beeinflußt, die werkzeuggebunden sind und daher extrem klein gehalten werden können. Ferner weicht die Variante nach Figur 3 von der Ausführung nach den Figuren 1 und 2 dadurch ab, daß der Druckbolzen 34a einstückig an das Druckstück 32a angeformt ist.In the variant according to FIG. 3, the valve needle 18a is designed such that in its closed position the upper end face 52a lies in the plane of the upper end face 50 of the nozzle body 10, so that both parts can be finished together by one tool. The preliminary stroke play is obtained in this case in that an inner annular surface section 48a of the lower end face of the piston 36a is set back by the amount of the preliminary stroke h v compared to the remaining outer annular surface section 48b of this end face. In this configuration of the piston 36a, the actual dimension of the forward stroke is only influenced by tolerances on the piston 36a, which are tool-related and can therefore be kept extremely small. Furthermore, the variant according to FIG. 3 differs from the embodiment according to FIGS. 1 and 2 in that the pressure pin 34a is integrally formed on the pressure element 32a.

Bei der Einspritzdüse nach Figur 4, deren grundsätzlicher Auf­bau mit jenem nach Figur 1 übereinstimmt, ist in einer Zwischen­scheibe 56 eine außen und innen glattzylindrisch ausgeführte Kolbenbuchse 58 in einer entsprechend geformten ringzylin­drischen Ausnehmung der Zwischenscheibe 56 verschiebbar ge­führt. In dieser Ausnehmung ist über der oberen Stirnseite 60 der Kolbenbuchse 58 ein Druckraum 62 gebildet, der über eine Bohrung 64 mit dem Kanal 22 verbunden ist. Der Kraftstoffdruck im Druckraum 62 drückt die Kolbenbuchse 58 an die obere Stirn­seite 50 des Düsenkörpers 10 an, die um das Vorhubmaß hv über der oberen Stirnseite 52 der Ventilnadel 18 liegt.In the injection nozzle according to FIG. 4, the basic structure of which corresponds to that according to FIG. 1, an externally and internally smooth-cylindrical piston bushing 58 is displaceably guided in a correspondingly shaped annular cylindrical recess in the intermediate plate 56 in an intermediate plate 56. A pressure chamber 62 is formed in this recess above the upper end face 60 of the piston bushing 58 and is connected to the channel 22 via a bore 64. The fuel pressure in the pressure chamber 62 presses the piston bushing 58 against the upper end face 50 of the nozzle body 10, which lies above the upper end face 52 of the valve needle 18 by the amount of advance stroke h v .

Der Innendurchmesser der Kolbenbuchse 58 ist kleiner als der Durchmeser der Ventilnadel 18, so daß die Ventilnadel 18 nach Zurücklegung des Vorhubes hv an die untere Stirn­seite 66 der Kolbenbuchse 58 anstößt und diese nach der ge­wünschten Druckstufe im Öffnungsdruckverlauf des Kraftstoffs nach oben mitnimmt. Der Gesamthub hg der Ventilnadel 18 wird durch den inneren Kragen 68 der Zwischenscheibe 56 begrenzt, der den Druckbolzen 34 umgibt und gegenüber der unteren Stirnseite der Zwischenscheibe 56 entsprechend zurückgesetzt ist.The inner diameter of the piston bush 58 is smaller than the diameter of the valve needle 18, so that the valve needle 18 abuts the lower end face 66 of the piston bush 58 after the advance stroke h v and takes it upward according to the desired pressure level in the opening pressure curve of the fuel. The total stroke h g of the valve needle 18 is limited by the inner collar 68 of the intermediate disk 56, which surrounds the pressure pin 34 and is correspondingly set back relative to the lower end face of the intermediate disk 56.

Die Einspritzdüse nach Figur 5 unterscheidet sich von jener nach Figur 4 im wesentlichen dadurch, daß anstelle der Kol­benbuchse 58 ein Kranz von stiftartigen Einzelkolben 70 vor­gesehen ist, deren Führungsbohrungen oben in einen ringför­migen Druckraum 72 einmünden. Dieser ist durch eine entsprech­ende Vertiefung in der oberen Stirnseite einer Zwischenscheibe 74 gebildet, welche durch eine Deckelplatte 76 abgeschlossen ist und über eine Nut 78 mit dem Kanal 22 in Verbindung steht. Die Einzelkolben 70 üben die gleiche Funktion wie die Kolben­buchse 58 nach Figur 4 aus und der Gesamthub hg der Ventil­nadel 18 wird auch hier durch einen zurückgesetzten inneren Ringflächenabschnitt 80 der Zwischenbuchse 74 begrenzt.The injection nozzle according to FIG. 5 differs from that according to FIG. 4 essentially in that instead of the piston bushing 58, a ring of pin-like individual pistons 70 is provided, the guide bores of which open into an annular pressure chamber 72 at the top. This is formed by a corresponding recess in the upper end face of an intermediate disk 74, which is closed off by a cover plate 76 and is connected to the channel 22 via a groove 78. The individual pistons 70 perform the same function as the piston bush 58 according to FIG. 4 and the total stroke h g of the valve needle 18 is also limited here by a recessed inner annular surface section 80 of the intermediate bush 74.

Bei der Variante nach Figur 6 liegt wie bei der Variante nach Figur 3 die obere Stirnseite 52a der Ventilnadel 18a in deren Schließstellung in der Ebene der oberen Stirnseite 50 des Düsenkörpers 10. Um den Vorhub hv zu erhalten, sind die Ein­zelkolben 70a mit Nasen 62 versehen, welche in der unteren End­stellung der Einzelkolben 70a auf der Stirnseite 50 des Düsen­körpers 10 aufliegen und die in den Weg der Ventilnadel 18a hineinragenden Stirnflächenbereiche 84 der Einzelkolben 70 um das Maß hv über der Stirnseite 50 halten.In the variant according to FIG. 6, as in the variant according to FIG. 3, the upper end face 52a of the valve needle 18a lies in its closed position in the plane of the upper end face 50 of the nozzle body 10. In order to maintain the preliminary stroke h v , the individual pistons 70a with lugs 62 provided, which in the lower end position of the individual pistons 70a rest on the end face 50 of the nozzle body 10 and hold the end face regions 84 of the individual pistons 70 projecting into the path of the valve needle 18a by the dimension h v above the end face 50.

Die bei der Variante nach Figur 6 getroffene Maßnahme könnte in äquivalenter Form auch bei der Kolbenbuchse 58 nach Figur 4 vorgesehen sein, z.B. durch eine Eindrehung an deren unterer Stirnseite. Dadurch ist erreicht, daß auch dort die oberen Stirnseiten von Düsenkörper 10 und Düsennadel 18 gemeinsam be­arbeitet werden können. Wenn nur zwei sich diametral gegenüber­liegende Einzelkolben 70 bzw. 70a vorgesehen werden, kann auf die Anordnung einer Deckelplatte 76 verzichtet werden, wenn zur Aufnahme der Einzelkolben 70 bzw. 70a Sackbohrungen vorge­sehen werden, die je um 90° gegenüber dem Kanal 22 versetzt angeordnet und über Einselbohrungen mit diesen verbunden werden.The measure taken in the variant according to FIG. 6 could also be provided in an equivalent form for the piston bushing 58 according to FIG. 4, e.g. by turning them in at the lower end. It is thereby achieved that the upper end faces of nozzle body 10 and nozzle needle 18 can also be machined there. If only two diametrically opposed individual pistons 70 and 70a are provided, the arrangement of a cover plate 76 can be dispensed with if blind holes are provided for receiving the individual pistons 70 and 70a, which are each offset by 90 ° with respect to the channel 22 and over Single holes are connected to these.

Claims (10)

1. Kraftstoff-Einspritzdüse für Brennkraftmaschinen, mit einem Düsenkörper, in welchem eine nach innen öffnende Ventilnadel verschiebbar gelagert ist und der über eine Zwischenscheibe an einem Haltekörper festgespannt ist, in welchem eine Kammer zur Aufnahme einer Schließfeder gebil­det ist, die über eine die Zwischenscheibe durchsetzende Druckübertragungseinrichtung auf die Ventilnadel im Schließsinn einwirkt, ferner mit einem ersten Druckraum, in welchem der Kraftstoff an einer Druckschulter der Ventilnadel im Öffnungssinn auf diese einwirkt, sowie mit einem zweiten Druckraum für einen vom Kraftstoff in Schließrichtung der Ventilnadel beaufschlagten und in deren Schließstellung gegen einen ersten gehäuse­festen Anschlag gedrückten Kolben, an welchem die Ven­tilnadel nach Zurücklegung eines Vorhubs zur Anlage kommt, wonach bei weiterem Ansteigen des Kraftstoffs­druckes um eine vorgegebene Druckstufe die Ventilnadel samt dem Kolben in Öffnungsrichtung bis zu einem zwei­ten gehäusefesten Anschlag weiterbewegt wird, dadurch gekennzeichnet, daß der nach Zurücklegung des Vorhubes (hv) der Ventilnadel (18) eine Zusatzkraft auf diese aus­übende Kolben (36, 58 70) in der Zwischenscheibe (12, 56, 74) verschiebbar gelagert und der zweite Druckraum (46, 62, 72) in der Zwischenscheibe (12, 56, 74) gebildet ist.1. Fuel injection nozzle for internal combustion engines, with a nozzle body, in which an inwardly opening valve needle is slidably mounted and which is clamped via an intermediate plate to a holding body, in which a chamber for receiving a closing spring is formed, which passes through a through the intermediate plate Pressure transmission device acts on the valve needle in the closing direction, further with a first pressure chamber in which the fuel acts on the pressure shoulder of the valve needle in the opening direction, as well as with a second pressure chamber for a fuel acting in the closing direction of the valve needle and in its closed position against a first one Piston fixed to the housing, on which the valve needle comes to rest after a forward stroke, after which, when the fuel pressure rises further by a predetermined pressure level, the valve needle together with the piston in the opening direction up to a second housing fixed to the housing chlag is further moved, characterized in that after the advance stroke (h v ) of the valve needle (18) has an additional force exerted on these pistons (36, 58 70) in the intermediate disc (12, 56, 74) and is displaceably mounted and the second pressure chamber (46, 62, 72) is formed in the intermediate disc (12, 56, 74). 2. Einspritzdüse nach Anspruch 1, dadurch gekennzeichnet, daß der erste gehäusefeste Anschlag, gegen welchen der Kolben (36, 58, 70) durch den Kraftstoff im zweiten Druck­raum (46, 62, 72) gedrückt ist, durch die obere Stirn­seite (50) des Düsenkörpers (10) gebildet ist.2. Injection nozzle according to claim 1, characterized in that the first housing-fixed stop against which the piston (36, 58, 70) is pressed by the fuel in the second pressure chamber (46, 62, 72), through the upper end face (50) of the nozzle body (10) is formed. 3. Einspritzdüse nach Anspruch 1 oder 2, dadurch gekenn­zeichnet, daß der zweite gehäusefeste Anschlag (46, 68, 80) an der Zwischenscheibe (12, 56, 74) gebildet ist.3. Injection nozzle according to claim 1 or 2, characterized in that the second housing-fixed stop (46, 68, 80) on the intermediate disc (12, 56, 74) is formed. 4. Einspritzdüse nach Anspruch 3, dadurch gekennzeichnet, daß der zweite gehäusefeste Anschlag (44, Figur 2 und 3) mit einer Druckschulter (42) am Kolben (36, 36a) zusammen­wirkend den zweiten Druckraum (46) in der Zwischenscheibe (12) begrenzt.4. Injection nozzle according to claim 3, characterized in that the second housing-fixed stop (44, Figures 2 and 3) with a pressure shoulder (42) on the piston (36, 36a) cooperating limits the second pressure chamber (46) in the intermediate disc (12) . 5. Einspritzdüse nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Kolben (36, 36a, 58, Figuren 2 bis 4) als Ringkörper ausgebildet ist, der den die Zwischen­scheibe (12, 56) durchsetzenden Teil (34, 34a) der Druck­übertragungseinrichtung (32, 34 bzw. 32a, 34a) der Schließ­feder (28) vorzugsweise konzentrisch umgibt.5. Injection nozzle according to one of claims 1 to 4, characterized in that the piston (36, 36a, 58, Figures 2 to 4) is designed as an annular body which the part (34, 34a) passing through the intermediate disc (12, 56) the pressure transmission device (32, 34 or 32a, 34a) of the closing spring (28) preferably surrounds concentrically. 6. Einspritzdüse nach Anspruch 5, dadurch gekennzeichnet, daß der Kolben (36, 36a, Figuren 2 und 3) und die ihn auf­nehmende Bohrung in der Zwischenscheibe (12) abgestuft sind und der zweite Druckraum (46) von den an den Stufen gebil­deten Ringschultern (42, 44) an Kolben (36, 36a) und Zwischen­scheibe (12) begrenzt ist.6. Injection nozzle according to claim 5, characterized in that the piston (36, 36a, Figures 2 and 3) and the bore receiving it in the intermediate plate (12) are graduated and the second pressure chamber (46) from the annular shoulders formed on the steps (42, 44) on the piston (36, 36a) and washer (12) is limited. 7. Einspritzdüse nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Kolben durch einen außermittig ange­ordneten Kolben oder durch die Gesamtheit mehrerer um die Düsenachse verteilter Einzelkolben (70, Figur 5) gebildet ist.7. Injection nozzle according to one of claims 1 to 4, characterized in that the piston is formed by an eccentrically arranged piston or by the entirety of several individual pistons (70, Figure 5) distributed around the nozzle axis. 8. Einspritzdüse nach Anspruch 7, dadurch gekennzeichnet, daß zur Bildung des zweiten Druckraums (72) die Zwischenscheibe (74) an der oberen Stirnseite mit einer durch eine Deckel­platte (76) nach außen abgeschlossenen Vertiefung versehen ist, in welche die die Einzelkolben (70) aufnehmenden Bohrungen sowie eine vom Kraftstoffkanal (72) abzweigende Nut (78) in der oberen Stirnseite der Zwischenplatte (74) einmünden.8. Injection nozzle according to claim 7, characterized in that to form the second pressure chamber (72), the intermediate plate (74) is provided on the upper end face with a through a cover plate (76) closed to the outside into which the individual pistons (70 ) opening bores and a groove (78) branching off from the fuel channel (72) in the upper end face of the intermediate plate (74). 9. Einspritzdüse nach Anspruch 7 oder 8, dadurch gekennzeich­net, daß der zweite gehäusefeste Anschlag an einem vertieft angeordneten inneren Ringflächenabschnitt (80) an der unteren Stirnseite der Zwischenscheibe (74) gebildet ist.9. Injection nozzle according to claim 7 or 8, characterized in that the second housing-fixed stop is formed on a recessed inner ring surface portion (80) on the lower end face of the intermediate plate (74). 10. Einspritzdüse nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die mit der Ventilnadel (18a) zusammenarbeitende Anschlagschulter (48a, 84, Figuren 3 und 6) am Kolben (36a, 70a) gegenüber dessen mit dem ersten ge­häusefesten Anschlag (50) zusammenarbeitenden Anschlag­schulter (48b, 82) um das Maß des Vorhubes (hv) nach oben zurückversetzt ist.10. Injection nozzle according to one of the preceding claims, characterized in that the stop shoulder (48a, 84, Figures 3 and 6) cooperating with the valve needle (18a) on the piston (36a, 70a) cooperates with the first stop fixed to the housing (50) Stop shoulder (48b, 82) is set back by the amount of the forward stroke (h v ).
EP87102772A 1986-04-04 1987-02-26 Fuel injector for internal-combustion engines Expired - Lifetime EP0240693B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863611316 DE3611316A1 (en) 1986-04-04 1986-04-04 FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES
DE3611316 1986-04-04

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EP0240693A1 true EP0240693A1 (en) 1987-10-14
EP0240693B1 EP0240693B1 (en) 1990-12-27

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JP (1) JPS62240466A (en)
DE (2) DE3611316A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0365143A1 (en) * 1988-10-19 1990-04-25 LUCAS INDUSTRIES public limited company Fuel injection nozzle
WO1994003720A1 (en) * 1992-08-05 1994-02-17 Robert Bosch Gmbh Fuel injection nozzle for internal combustion engines
WO1995024552A1 (en) * 1994-03-11 1995-09-14 Robert Bosch Gmbh Injection nozzle for internal combustion engines

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB8706757D0 (en) * 1987-03-21 1987-04-23 Lucas Ind Plc Fuel injection nozzles
JP2844742B2 (en) * 1989-11-13 1999-01-06 日産自動車株式会社 Diesel engine fuel injection nozzle
US9605639B2 (en) 2012-07-12 2017-03-28 Ford Global Technologies, Llc Fuel injector

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1110102A (en) * 1963-11-26 1968-04-18 Ruston & Hornsby Ltd Improvements in fuel injection equipment for internal combustion engines
DE2704688A1 (en) * 1976-02-05 1977-08-11 Nippon Denso Co FUEL INJECTION DEVICE
DE2711902A1 (en) * 1977-03-18 1978-09-21 Bosch Gmbh Robert FUEL INJECTOR
GB2086473A (en) * 1980-10-31 1982-05-12 Daimler Benz Ag Fuel injection valve for compression ignition engines

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1110102A (en) * 1963-11-26 1968-04-18 Ruston & Hornsby Ltd Improvements in fuel injection equipment for internal combustion engines
DE2704688A1 (en) * 1976-02-05 1977-08-11 Nippon Denso Co FUEL INJECTION DEVICE
DE2711902A1 (en) * 1977-03-18 1978-09-21 Bosch Gmbh Robert FUEL INJECTOR
GB2086473A (en) * 1980-10-31 1982-05-12 Daimler Benz Ag Fuel injection valve for compression ignition engines

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0365143A1 (en) * 1988-10-19 1990-04-25 LUCAS INDUSTRIES public limited company Fuel injection nozzle
WO1994003720A1 (en) * 1992-08-05 1994-02-17 Robert Bosch Gmbh Fuel injection nozzle for internal combustion engines
US5464158A (en) * 1992-08-05 1995-11-07 Robert Bosch Gmbh Fuel injection nozzle for internal combustion engines
WO1995024552A1 (en) * 1994-03-11 1995-09-14 Robert Bosch Gmbh Injection nozzle for internal combustion engines

Also Published As

Publication number Publication date
DE3767001D1 (en) 1991-02-07
JPS62240466A (en) 1987-10-21
EP0240693B1 (en) 1990-12-27
DE3611316A1 (en) 1987-10-08

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