EP0028288B1 - Fuel injection nozzle for internal-combustion engines - Google Patents

Fuel injection nozzle for internal-combustion engines Download PDF

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Publication number
EP0028288B1
EP0028288B1 EP80104128A EP80104128A EP0028288B1 EP 0028288 B1 EP0028288 B1 EP 0028288B1 EP 80104128 A EP80104128 A EP 80104128A EP 80104128 A EP80104128 A EP 80104128A EP 0028288 B1 EP0028288 B1 EP 0028288B1
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EP
European Patent Office
Prior art keywords
nozzle
pressure
valve slide
inflow line
fuel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP80104128A
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German (de)
French (fr)
Other versions
EP0028288A1 (en
Inventor
Ewald Dr. Dipl.-Ing. Eblen
Odon Dipl.-Ing. Kopse
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
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to AT80104128T priority Critical patent/ATE10666T1/en
Publication of EP0028288A1 publication Critical patent/EP0028288A1/en
Application granted granted Critical
Publication of EP0028288B1 publication Critical patent/EP0028288B1/en
Expired 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/44—Valves, e.g. injectors, with valve bodies arranged side-by-side
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M45/086—Having more than one injection-valve controlling discharge orifices

Definitions

  • the invention relates to a fuel injector according to the preamble of the main claim.
  • the actuator which is movable by an external force, is designed as a rotatably mounted cam disk, which acts mechanically on the nozzle needle via tappets and blocks one of the nozzle needles in the closed position in the end positions.
  • the stroke of the nozzle needles is limited in the intermediate positions of the cam disk, which is not desirable in all cases.
  • the known mechanical solution is subject to a large number of tolerances, so that an increased production outlay is necessary if the cam disk is also to be adjustable into an exactly defined intermediate position.
  • the fuel is conveyed from the injection pump to the two pressure spaces in the injection nozzle via two separate pressure lines.
  • the actuator for controlling the two pressure lines is arranged in the injection pump and is designed as a rotary slide valve which is displaceably but non-rotatably coupled to the pump piston. This design is complex because of the two pressure lines and also does not provide an intermediate position of the actuator designed as a rotary slide valve, in which both pressure chambers of the nozzle needles are connected to the pump pressure chamber without throttling.
  • the fuel injection nozzle according to the invention with the characterizing features of the main claim has the advantage over a known injection nozzle of the generic type that an exact, fast closing of the nozzle needles is ensured by the pressure relief of the pressure chambers practically simultaneously with the blocking. It is also advantageous that the actuator designed as a valve slide can be assigned a defined intermediate position, so that the actuator can unthrottled connect the two pressure spaces to the fuel supply line in one of its three defined positions, both nozzle needles being able to carry out their full stroke.
  • a short design of the injection nozzle results if the axis of the valve slide is arranged perpendicular to the axes of the nozzle needles and a connection for the inflow line.
  • FIG. 1 shows a fuel injection nozzle with the usual structure of nozzle holder 1, intermediate plate 2, nozzle body 3, union nut 4 and nozzle needles 5.
  • the nozzle needles 5 are loaded via spring plates 6 by closing springs 7.
  • the space 8 accommodating the spring 7 is relieved of pressure via a channel 9.
  • the invention relates to an injection nozzle with two nozzle needles 5 and correspondingly two closing springs 7, but only one spring space 8.
  • pressure spaces 11 are provided in the area of the pressure shoulder 10 of the nozzle needle, which have inflow channels 12 and 13 in the nozzle holder 1 are connected, which can be connected via a slide valve 14 to an inflow line 15, via which the fuel under high pressure is fed to the injection nozzle.
  • the upper part of the nozzle holder 1 is drawn rotated by 90 ° with respect to the lower part, in order to be able to show the pressure chambers 11 in the nozzle body 3 or the closing springs 7 in section and the inflow channels 12 and 13.
  • the slide valve 14 works with a slide 16 which is displaceable against the force of a return spring 17 by pressure fluid located in a space 18.
  • the pressure fluid is controlled depending on the engine parameters by means not shown, for example a solenoid valve, and supplied to the space 18 via a nipple 19.
  • the slide 16 is displaced more or less against the spring 17 and thereby creates various connections between the inflow line 15 and the inflow channels 12 and 13.
  • the reference numbers of the parts corresponding to the first exemplary embodiment are provided with two dashes as an index.
  • the two nozzle needles are arranged coaxially with one another, one nozzle needle 31 being received by a hollow needle 32.
  • the nozzle needle 31 has a pressure space 33 arranged between the needles
  • the hollow needle 32 has a pressure space 34 arranged between the hollow needle and the nozzle body 3 ".
  • the pressure space 34 is connected directly to the inlet channel 12", it serves as a connection between the inlet channel 13 "and the pressure chamber 33 has an annular groove 35 ′′ arranged in the nozzle body 3 ′′ and radial bores 36 arranged in the hollow needle 32, which connect the ring groove 35 to the pressure chamber 33.
  • the compression springs acting on the nozzle needles 31 and 32 are connected in parallel as in the first embodiment.
  • the closing spring 37 of the hollow needle 32 has a much larger diameter than the closing spring 38 of the inner needle 31, since the surface acting on the hollow needle 32 in the opening direction, which is acted upon by the supplied fuel, is, by design, considerably larger than that on the inner needle 31.
  • the pressure chambers 33 and 34 or the inflow channels 12 ′′ and 13 ′′ are hydraulically completely separated from one another.
  • the slide valve 14 "works in principle like the valve shown in the first exemplary embodiment. In contrast to this, however, it is arranged coaxially to the injector axis, since the fuel pressure connection is connected to the fuel supply line 15" transversely to the nozzle axis. In addition to the advantage of the small diameter of this exemplary embodiment, fewer channels are required for the leakage drainage, since the space 25 "receiving the spring 17" of the slide 16 "is connected directly to the spring space 8" via a bore 39. In contrast to the first exemplary embodiment, after a first stroke has been covered, the slide 16 "encounters a stop 42 loaded by a spring 41. Only when the pressure in the chamber 18" increases further (force) is the force of the spring 41 overcome and the slide 16 "now counteracts the force of both springs 17 "and 41 shifted into its end position.

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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

A fuel injection nozzle is proposed having two nozzle needles in which the control of the fuel delivered via an inflow line is effected by means of a slide valve embodied as a 3-way valve, which in a preferred embodiment of the invention is simultaneously embodied as a 3-position valve and permits not only the alternative exertion of the fuel pressure upon one of the nozzle needles but also a common pressure exertion of both nozzle needles.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoff- Einspritzdüse nach der Gattung des Hauptanspruches. Bei bekannten Einspritzdüsen dieser Gattung (DE-B-2121 121) ist das durch eine äussere Krafteinwirkung bewegliche Stellglied als drehbar gelagerte Nockenscheibe ausgebildet, welche über Stössel mechanisch auf die Düsennadel einwirkt und in den Endstellungen jeweils eine der Düsennadeln in der Schliessstellung blockiert. Bei dieser Anordnung ist eine Entlastung des Druckraumes der jeweils blockierten Düsennadel nicht möglich. In den Zwischenstellungen der Nockenscheibe ist der Hub der Düsennadeln begrenzt, was nicht in allen Fällen erwünscht ist. Ausserdem ist die bekannte mechanische Lösung mit einer Vielzahl von Toleranzen behaftet, so dass ein erhöhter Fertigungsaufwand notwendig ist, wenn die Nockenscheibe auch in eine exakt definierte Zwischenstellung verstellbar sein soll.The invention relates to a fuel injector according to the preamble of the main claim. In known injection nozzles of this type (DE-B-2121 121), the actuator, which is movable by an external force, is designed as a rotatably mounted cam disk, which acts mechanically on the nozzle needle via tappets and blocks one of the nozzle needles in the closed position in the end positions. With this arrangement, it is not possible to relieve the pressure space of the respectively blocked nozzle needle. The stroke of the nozzle needles is limited in the intermediate positions of the cam disk, which is not desirable in all cases. In addition, the known mechanical solution is subject to a large number of tolerances, so that an increased production outlay is necessary if the cam disk is also to be adjustable into an exactly defined intermediate position.

Bei einer anderen bekannten Ausführung einer Einspritzdüse mit zwei Düsennadeln (DE-A-2 656 276) wird der Kraftstoff über zwei getrennte Druckleitungen von der Einspritzpumpe zu den beiden Druckräumen in der Einspritzdüse gefördert. Das Stellglied zur Steuerung der beiden Druckleitungen ist in der Einspritzpumpe angeordnet und als Drehschieber ausgebildet, welcher verschiebbar, jedoch unverdrehbar mit den Pumpenkolben gekoppelt ist. Diese Ausführung ist wegen der beiden Druckleitungen aufwendig und sieht ebenfalls keine Zwischenstellung des als Drehschieber ausgebildeten Stellgliedes vor, bei welcher beide Druckräume der Düsennadeln ungedrosselt mit dem Pumpendruckraum verbunden sind.In another known embodiment of an injection nozzle with two nozzle needles (DE-A-2 656 276), the fuel is conveyed from the injection pump to the two pressure spaces in the injection nozzle via two separate pressure lines. The actuator for controlling the two pressure lines is arranged in the injection pump and is designed as a rotary slide valve which is displaceably but non-rotatably coupled to the pump piston. This design is complex because of the two pressure lines and also does not provide an intermediate position of the actuator designed as a rotary slide valve, in which both pressure chambers of the nozzle needles are connected to the pump pressure chamber without throttling.

Ferner sind beispielsweise aus den Deutschen Normen DIN 24300, März 1966, Blatt 3, Nr. 1.1.2., sogenannte 3/2-Wegeventile bekannt, die in einer ersten Schaltstellung einen Zulauf sperren und einen Rücklauf öffnen und in einer zweiten Schaltstellung den Rücklauf sperren und den Zulauf öffnen.Furthermore, so-called 3 / 2-way valves are known, for example, from the German standards DIN 24300, March 1966, sheet 3, no. 1.1.2 lock and open the inlet.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemässe Kraftstoff-Einspritzdüse mit den kennzeichnenden Merkmalen des Hauptanspruchs hat gegenüber einer bekannten Einspritzdüse der gattungsmässigen Art den Vorteil, dass durch die praktisch gleichzeitig mit der Sperrung erfolgende Druckentlastung der Druckräume ein exaktes, schnelles Schliessen der Düsennadeln sichergestellt ist. Ferner ist vorteilhaft, dass dem als Ventilschieber ausgebildeten Stellglied eine definierte Zwischenstellung zugeordnet werden kann, so dass das Stellglied in einer seiner drei definierten Stellungen beide Druckräume ungedrosselt mit der Zuflussleitung des Kraftstoffs verbinden kann, wobei beide Düsennadeln ihren vollen Hub ausführen können. Eine kurz bauende Ausführung der Einspritzdüse ergibt sich, wenn die Achse des Ventilschiebers senkrecht zu den Achsen der Düsennadeln und eines Anschlusses für die Zuflussleitung angeordnet ist.The fuel injection nozzle according to the invention with the characterizing features of the main claim has the advantage over a known injection nozzle of the generic type that an exact, fast closing of the nozzle needles is ensured by the pressure relief of the pressure chambers practically simultaneously with the blocking. It is also advantageous that the actuator designed as a valve slide can be assigned a defined intermediate position, so that the actuator can unthrottled connect the two pressure spaces to the fuel supply line in one of its three defined positions, both nozzle needles being able to carry out their full stroke. A short design of the injection nozzle results if the axis of the valve slide is arranged perpendicular to the axes of the nozzle needles and a connection for the inflow line.

Zeichnungdrawing Zwei Ausführungsbeispiele des Gegenstandes der Erfindung sind in der Zeichnung vereinfacht dargestellt und im folgenden näher beschrieben. Es zeigen Figur 1 das erste Ausführungsbeispiel, Figur 2 eine Variante des Beispiels nach Figur 1 und Figur 3, 4 und 5 das zweite Ausführungsbeispiel.Two embodiments of the object of the invention are shown in simplified form in the drawing and described in more detail below. FIG. 1 shows the first exemplary embodiment, FIG. 2 shows a variant of the example according to FIG. 1, and FIGS. 3, 4 and 5 show the second exemplary embodiment. Beschreibung der ErfindungsbeispieleDescription of the invention examples

In Figur 1 ist eine Kraftstoffeinspritzdüse mit dem üblichen Aufbau Düsenhalter 1, Zwischenplatte 2, Düsenkörper 3, Überwurfmutter 4 und Düsennadeln 5 dargestellt. Die Düsennadeln 5 sind über Federteller 6 durch Schliessfedern 7 belastet. Der die Feder 7 aufnehmende Raum 8 ist über einen Kanal 9 druckentlastet. Die Erfindung betrifft eine Einspritzdüse mit zwei Düsennadeln 5 und entsprechend zwei Schliessfedern 7, jedoch nur einem Federraum 8. Zwischen den Düsennadein 5 und dem Düsenkörper 3 sind im Bereich der Druckschulter 10 der Düsennadel Druckräume 11 vorgesehen, die mit Zuflusskanälen 12 und 13 im Düsenhalter 1 verbunden sind, welche über ein Schiebeventil 14 mit einer Zuflussleitung 15 verbindbar sind, über welche der unter hohem Druck stehende Kraftstoff der Einspritzdüse zugeführt wird.FIG. 1 shows a fuel injection nozzle with the usual structure of nozzle holder 1, intermediate plate 2, nozzle body 3, union nut 4 and nozzle needles 5. The nozzle needles 5 are loaded via spring plates 6 by closing springs 7. The space 8 accommodating the spring 7 is relieved of pressure via a channel 9. The invention relates to an injection nozzle with two nozzle needles 5 and correspondingly two closing springs 7, but only one spring space 8. Between the nozzle needles 5 and the nozzle body 3, pressure spaces 11 are provided in the area of the pressure shoulder 10 of the nozzle needle, which have inflow channels 12 and 13 in the nozzle holder 1 are connected, which can be connected via a slide valve 14 to an inflow line 15, via which the fuel under high pressure is fed to the injection nozzle.

In Figur 1 ist der obere Teil des Düsenhalters 1 gegenüber dem unteren Teil um 90° verdreht gezeichnet, um dadurch jeweils einmal die Druckräume 11 im Düsenkörper 3 bzw. die Schliessfedern 7 im Schnitt zeigen zu können und zum anderen im oberen Teil die Zuflusskanäle 12 und 13. Das Schieberventil 14 arbeitet mit einem Schieber 16, der entgegen der Kraft einer Rückstellfeder 17 durch in einem Raum 18 befindliche Druckflüssigkeit verschiebbar ist. Die Druckflüssigkeit wird durch nicht dargestellte Mittel, beispielsweise ein Magnetventil, motorkenngrössenabhängig gesteuert und über einen Nippel 19 dem Raum 18 zugeführt. Je nach Druck dieser Druckflüssigkeit wird der Schieber 16 mehr oder weniger gegen die Feder 17 verschoben und stellt dabei verschiedene Verbindungen zwischen der Zuflussleitung 15 und den Zuflusskanälen 12 und 13 her. In der dargestellten Schaltstellung besteht eine Verbindung von der Leitung 15 zum Kanal 12. Der Kraftstoff strömt dabei entlang einer Ringnut 20 des Schiebers 16 in der den Schieber 16 aufnehmenden Bohrung 21, von einer mit der Zuflussleitung 15 verbundenen Ringnut 22 dieser Bohrung 21 zu einer mit dem Zuflusskanal 12 verbundenen Ringnut 23. In dem Schieber 16 ist ein Entlastungskanal 24 angeordnet, der in der dargestellten Stellung den Zuflusskanal 13 mit dem die Feder 17 aufnehmenden druckentlasteten Raum 25 verbindet. In diesen Raum 25 mündet auch die Entlastungsleitung 9 des Federraums 8. Der Raum 25 ist durch einen Anschlussnippel 26 mit einer nicht dargestellten Leckleitung verbunden.In Figure 1, the upper part of the nozzle holder 1 is drawn rotated by 90 ° with respect to the lower part, in order to be able to show the pressure chambers 11 in the nozzle body 3 or the closing springs 7 in section and the inflow channels 12 and 13. The slide valve 14 works with a slide 16 which is displaceable against the force of a return spring 17 by pressure fluid located in a space 18. The pressure fluid is controlled depending on the engine parameters by means not shown, for example a solenoid valve, and supplied to the space 18 via a nipple 19. Depending on the pressure of this pressure fluid, the slide 16 is displaced more or less against the spring 17 and thereby creates various connections between the inflow line 15 and the inflow channels 12 and 13. In the switching position shown there is a connection from the line 15 to the channel 12. The fuel flows along an annular groove 20 of the slide 16 in the bore 21 receiving the slide 16, from an annular groove 22 connected to the inflow line 15 of this bore 21 to one with the annular groove 23 connected to the inflow channel 12. A relief channel 24 is arranged in the slide 16 and, in the position shown, connects the inflow channel 13 to the pressure-relieved space 25 receiving the spring 17. The relief line 9 of the spring chamber 8 also opens into this space 25. The space 25 is connected by a connecting nipple 26 to a leak line, not shown.

Sobald aufgrund steigenden Druckes im Druckraum 18 der Schieber 16 nach rechts entgegen der Kraft der Feder 17 verschoben wird, werden die Ringnuten 22 und 23 über die Ringnut 20 mit einer Ringnut 27 verbunden, von der der Zuflusskanal 13 abzweigt. Nach Zurücklegung dieses Weges ist der Entlastungskanal 24 von der Ringnut 27 getrennt. Diese Verbindung entsteht in einer Zwischenstellung des Schiebers 16 und setzt voraus, dass die Ringnut 20 länger ist als der Abstand von Ringnut 23 zu Ringnut 27. In dieser Stellung werden beide Druckräume 11 mit Kraftstoff versorgt, wenn dieses so gewünscht ist und wenn eine Druckstufe, wie in Figur 3 dargestellt, vorgesehen wird. Bei dem dargestellten Beispiel überläuft der Schieber 16 diese Stellung, bis er an den hier als Anschlag dienenden Nippel 26 verschoben wird. In dieser Endstellung ist die Ringnut 20 von der Ringnut 23 getrennt, so dass lediglich noch die Verbindung der Ringnut 22 zur Ringnut 27 hin besteht. Der Kraftstoff gelangt also nur noch in den Zuflusskanal 13. Der Zuflusskanal 12 ist gesperrt und in dieser Stellung durch den Entlastungskanal 24 im Schieber 16 druckentlastet.As soon as the slide 16 is displaced to the right against the force of the spring 17 due to increasing pressure in the pressure chamber 18, the annular grooves 22 and 23 are connected via the annular groove 20 to an annular groove 27 from which the inflow channel 13 branches off. After covering this path, the relief channel 24 is separated from the annular groove 27. This connection is created in an intermediate position of the slide 16 and presupposes that the annular groove 20 is longer than the distance from the annular groove 23 to the annular groove 27. In this position, both pressure spaces 11 are supplied with fuel if this is so desired and if a pressure stage, as shown in Figure 3, is provided. In the example shown, the slide 16 overflows this position until it is moved to the nipple 26, which serves as a stop here. In this end position, the annular groove 20 is separated from the annular groove 23, so that there is only the connection of the annular groove 22 to the annular groove 27. The fuel therefore only reaches the inflow channel 13. The inflow channel 12 is blocked and in this position is relieved of pressure by the relief channel 24 in the slide 16.

Bei manchen Brennkraftmaschinen steht zur Aufnahme der Kraftstoffeinspritzdüse nur ein geringer Raum, also nur eine Bohrung geringen Durchmessers zur Verfügung. Bei der Verwendung von Kraftstoffeinspritzdüsen mit zwei parallel angeordneten Düsennadeln ist man deshalb darauf angewiesen, diese, wie in Figur 2 dargestellt, möglichst dicht nebeneinander anzuordnen. Der geringstmögliche Abstand wird jedoch bei parallel angeordneten Schliessfedern durch den Durchmesser dieser Federn bestimmt, der nicht in der erforderlichen Weise verringert werden kann. Bei der in Figur 2 dargestellten Variante des ersten Ausführungsbeispiels, bei der die entsprechenden Bezugszahlen lediglich mit einem Indexstrich versehen werden, ist die eine Feder 7' gegenüber der anderen zurückgesetzt, so dass neben der verbliebenen Feder 7'-lediglich eine verlängerte Druckstange 29 der einen Düsennadel 5' verläuft. Der Federraum 8' ist dadurch stufenförmig ausgebildet.In some internal combustion engines, only a small space, that is to say only a small diameter bore, is available for receiving the fuel injection nozzle. When using fuel injection nozzles with two nozzle needles arranged in parallel, it is therefore necessary to arrange them as closely as possible, as shown in FIG. The smallest possible distance, however, is determined in the case of closing springs arranged in parallel by the diameter of these springs, which cannot be reduced in the required manner. In the variant of the first exemplary embodiment shown in FIG. 2, in which the corresponding reference numbers are only provided with an index line, one spring 7 'is set back relative to the other, so that in addition to the remaining spring 7'-only one extended push rod 29 of the one Nozzle needle 5 'runs. The spring chamber 8 'is thereby designed in a step-like manner.

Bei dem in den Figuren 3 bis 5 dargestellten zweiten Ausführungsbeispiel sind die Bezugszahlen der dem ersten Ausführungsbeispiel entsprechenden Teile mit zwei Strichen als Index versehen. Wie in Figur 3 dargestellt, sind bei diesem Ausführungsbeispiel die beiden Düsennadeln koaxial zueinander angeordnet, wobei die eine Düsennadel 31 von einer Hohlnadel 32 aufgenommen wird. Die Düsennadel 31 hat einen zwischen den Nadeln angeordneten Druckraum 33, die Hohlnadel 32 weist einen zwischen Hohlnadel und Düsenkörper 3" angeordneten Druckraum 34 auf. Während der Druckraum 34 unmittelbar mit dem Zulaufkanal 12" verbunden ist, dient als Verbindung zwischen dem Zuflusskanal 13" und dem Druckraum 33 eine im Düsenkörper 3" angeordnete Ringnut 35 und in der Hohlnadel 32 angeordnete Radialbohrungen 36, die die Ringnut 35 mit dem Druckraum 33 verbinden. Die auf die Düsennadeln 31 und 32 wirkenden Druckfedern sind wie beim ersten Ausführungsbeispiel parallel geschaltet. Die Schliessfeder 37 der Hohlnadel 32 weist einen wesentlich grösseren Durchmesser auf als die Schliessfeder 38 der Innennadel 31, da die vom zugeführten Kraftstoff beaufschlagte in Öffnungsrichtung wirkende Fläche an der Hohlnadel 32 konstruktionsbedingt wesentlich grösser als die an der Innennadel 31 ist. Die Druckräume 33 und 34 bzw. die Zuflusskanäle 12" und 13" sind hydraulisch völlig voneinander getrennt. Das Schieberventil 14" arbeitet im Prinzip wie das im ersten Ausführungsbeispiel dargestellte Ventil. Im Gegensatz zu diesem ist es jedoch koaxial zur Einspritzdüsenachse angeordnet, da der Kraftstoffdruckanschluss mit der Kraftstoffzufiussleitung 15" quer zur Düsenachse angeschlossen ist. Ausser dem Vorteil des geringen Durchmessers dieses Ausführungsbeispiels sind für die Leckabführung auch weniger Kanäle erforderlich, da der die Feder 17" des Schiebers 16" aufnehmende Raum 25" über eine Bohrung 39 unmittelbar mit dem Federraum 8" verbunden ist. Im Unterschied zum ersten Ausführungsbeispiel stösst der Schieber 16" nach Zurücklegung eines ersten Hubes auf einen durch eine Feder 41 belasteten Anschlag 42. Erst bei weiterem Druckanstieg (Druckstufe) im Raum 18" wird die Kraft der Feder 41 überwunden und der Schieber 16" nun gegen die Kraft beider Federn 17" und 41 in seine Endlage verschoben.In the second exemplary embodiment shown in FIGS. 3 to 5, the reference numbers of the parts corresponding to the first exemplary embodiment are provided with two dashes as an index. As shown in FIG. 3, in this exemplary embodiment the two nozzle needles are arranged coaxially with one another, one nozzle needle 31 being received by a hollow needle 32. The nozzle needle 31 has a pressure space 33 arranged between the needles, the hollow needle 32 has a pressure space 34 arranged between the hollow needle and the nozzle body 3 ". While the pressure space 34 is connected directly to the inlet channel 12", it serves as a connection between the inlet channel 13 "and the pressure chamber 33 has an annular groove 35 ″ arranged in the nozzle body 3 ″ and radial bores 36 arranged in the hollow needle 32, which connect the ring groove 35 to the pressure chamber 33. The compression springs acting on the nozzle needles 31 and 32 are connected in parallel as in the first embodiment. The closing spring 37 of the hollow needle 32 has a much larger diameter than the closing spring 38 of the inner needle 31, since the surface acting on the hollow needle 32 in the opening direction, which is acted upon by the supplied fuel, is, by design, considerably larger than that on the inner needle 31. The pressure chambers 33 and 34 or the inflow channels 12 ″ and 13 ″ are hydraulically completely separated from one another. The slide valve 14 "works in principle like the valve shown in the first exemplary embodiment. In contrast to this, however, it is arranged coaxially to the injector axis, since the fuel pressure connection is connected to the fuel supply line 15" transversely to the nozzle axis. In addition to the advantage of the small diameter of this exemplary embodiment, fewer channels are required for the leakage drainage, since the space 25 "receiving the spring 17" of the slide 16 "is connected directly to the spring space 8" via a bore 39. In contrast to the first exemplary embodiment, after a first stroke has been covered, the slide 16 "encounters a stop 42 loaded by a spring 41. Only when the pressure in the chamber 18" increases further (force) is the force of the spring 41 overcome and the slide 16 "now counteracts the force of both springs 17 "and 41 shifted into its end position.

in der in der Figur 3 dargestellten Ausgangslage des Schiebers 16" verbindet dieser über die Ringnut 20" die Zuflussleitung 15" mit dem Zuflusskanal 13". Sobald dann der Schieber 16" entgegen der Feder 17" nach unten geschoben wird, besteht nach Zurücklegung des Weges bis an den Anschlag 42 eine Verbindung zwischen der Leitung 15" und dem Kanal 12", so dass Kraftstoff nur über die Hohlnadel 32 eingespritzt werden kann. Der Kanal 13" ist von der Leitung 15" dann getrennt, wie es in Figur 4 dargestellt ist. In Figur 5 ist dann der Schieber 16" in seiner Endstellung gezeigt nach Überwindung der Kraft der Feder 41, in der die Leitung 15" mit beiden Kanälen 12" und 13" verbunden ist. Die Verbindung zum Kanal 13" erfolgt dabei durch eine im Schieber 16" verlaufende Bohrung 43. Hierdurch ist es möglich, im folgenden Umsteuerreihenfolge erst einen der Kanäle dann alternativ den anderen Kanal und erst danach beide gleichzeitig aufzusteuern.in the starting position of the slide 16 "shown in FIG. 3, this connects the inflow line 15" to the inflow channel 13 "via the annular groove 20". As soon as the slide 16 "is pushed downward against the spring 17", there is a connection between the line 15 "and the channel 12" after covering the path up to the stop 42, so that fuel can only be injected via the hollow needle 32 . The channel 13 "is then separated from the line 15", as shown in Figure 4. In Figure 5, the slide 16 "is shown in its end position after overcoming the force of the spring 41, in which the line 15" is connected to both channels 12 "and 13". The connection to the channel 13 "is made through a bore 43 running in the slide 16". This makes it possible, in the following reversing order, to open one of the channels then alternatively the other channel and only then both at the same time.

Claims (3)

1. Fuel injection nozzle for internal-combustion engines, with two nozzle needles (5) which are arranged in the longitudinal direction of the nozzle body (3) and which each control at least one spray hole and are each provided with a pressure shoulder (10) which is located in a pressure space (11) and at which the fuel supplied via a common inflow line (15) causes a force displacing the nozzle needle in the opening direction, and also with an actuator (16) which is moveable as a result of the effect of an external force into a first and a second position and which, in the first position, prevents fuels from being sprayed out through the spray hole assigned to the one nozzle needle (5) and, in the second position, prevents fuel from being sprayed out through the spray hole assigned to the other nozzle needle (5), characterised in that the actuator (16) is designed in a way known per se as a valve slide, and the two nozzle needles (5) have assigned to them their own pressure spaces (11) which are each connected via a separate channel (12, 13) to a control bore (21) which receives the valve slide (16) and into which the single inflow line (15) also opens, and in that the valve slide (16) connects the particular channel (12 or 13) locked relative to the inflow line (15) to a low-pressure space (8, 25) in order to relieve the associated pressure space (11) of pressure.
2. Injection nozzle according to Claim 1, characterised in that, after covering a first part stroke, the valve slide (16") butts in a specific intermediate position against a stop (42) loaded by a spring (41) which yields only after the hydraulic pressure has increased a predetermined value (pressure step), and in that in one of its three specific positions the valve slide (16") connects the inflow line (15) to the two channels (12", 13").
3. Injection nozzle according to Claim 1 or 2, characterised in that the axis of the valve slide (16) is arranged perpendicularly to the axes of the nozzle needles (5) and of a connection for the inflow line (15).
EP80104128A 1979-10-31 1980-07-16 Fuel injection nozzle for internal-combustion engines Expired EP0028288B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80104128T ATE10666T1 (en) 1979-10-31 1980-07-16 FUEL INJECTION NOZZLE FOR COMBUSTION ENGINES.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19792943896 DE2943896A1 (en) 1979-10-31 1979-10-31 FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES
DE2943896 1979-10-31

Publications (2)

Publication Number Publication Date
EP0028288A1 EP0028288A1 (en) 1981-05-13
EP0028288B1 true EP0028288B1 (en) 1984-12-05

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EP80104128A Expired EP0028288B1 (en) 1979-10-31 1980-07-16 Fuel injection nozzle for internal-combustion engines

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US (1) US4356976A (en)
EP (1) EP0028288B1 (en)
JP (1) JPS5675960A (en)
AT (1) ATE10666T1 (en)
DE (2) DE2943896A1 (en)

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Also Published As

Publication number Publication date
US4356976A (en) 1982-11-02
EP0028288A1 (en) 1981-05-13
JPS5675960A (en) 1981-06-23
DE3069751D1 (en) 1985-01-17
JPH0154550B2 (en) 1989-11-20
DE2943896A1 (en) 1981-05-14
ATE10666T1 (en) 1984-12-15

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