EP0028288A1 - Fuel injection nozzle for internal-combustion engines - Google Patents

Fuel injection nozzle for internal-combustion engines Download PDF

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Publication number
EP0028288A1
EP0028288A1 EP80104128A EP80104128A EP0028288A1 EP 0028288 A1 EP0028288 A1 EP 0028288A1 EP 80104128 A EP80104128 A EP 80104128A EP 80104128 A EP80104128 A EP 80104128A EP 0028288 A1 EP0028288 A1 EP 0028288A1
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EP
European Patent Office
Prior art keywords
nozzle
fuel injection
pressure
needle
slide
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
EP80104128A
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German (de)
French (fr)
Other versions
EP0028288B1 (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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Publication date
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Priority to AT80104128T priority Critical patent/ATE10666T1/en
Publication of EP0028288A1 publication Critical patent/EP0028288A1/en
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Publication of EP0028288B1 publication Critical patent/EP0028288B1/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
    • F02M61/04—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.
  • a fuel injection nozzle of this type the pressure spaces are supplied with fuel by either two pumps or two independent pump work spaces, with supply of only one space enabling the second to be activated via the slide valve. It is therefore a special fuel injection system, which is relatively complex due to the two required cubic capacity and is also only of limited use.
  • the fuel injection pump according to the invention with the characterizing features of the main claim has the advantage that the fuel injection nozzle can also be supplied with a conventional injection pump, for example a distributor pump, with only one pump working space. There is also the possibility of an alternative switching or switching as well as a common on circuit of the injection nozzles. Additional important embodiments of the invention can be found in the drawing and the following description.
  • FIG. 1 shows the first exemplary embodiment
  • FIG. 2 shows a variant of the example according to FIG. 1
  • FIGS. 3, 4 and 5 show the second exemplary embodiment.
  • 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 receiving 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 chamber 8.
  • pressure spaces 11 are provided in the area of the pressure shoulder 10 of the nozzle needle, which with inflow channels 12 and 13 in Nozzle holders 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.
  • FIG. 1 the upper part of the nozzle holder 1 is shown rotated by 90 ° with respect to the lower part, because there to be able to show the pressure chambers 11 in the nozzle body 3 or the closing springs 7 in section by one time and the inflow channels 12 and 13 in the upper part on the other.
  • the slide valve 14 works with a slide 16 which counteracts the force of a return spring 17 in one Room 18 hydraulic fluid is displaceable.
  • the pressure fluid is controlled as a function of the engine parameters by means not shown, for example a solenoid valve, and is supplied to the space 18 via a nipple 19.
  • the slide 16 is displaced more or less against the spring 17 and in doing so makes various connections between the inflow line 15 and the inflow channels 12 and 13.
  • 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 inflow channel 12 connected annular groove 23.
  • a relief channel 24 is arranged, which connects the inflow channel 13 in the position shown with the pressure-relieving space 25 accommodating 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.
  • 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 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 substantially larger diameter than the closing spring 38 of the inner needle 31, since the area on the hollow needle 32 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 separate 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 embodiment, fewer channels are required for leakage removal, since the spring 17 "of the Slider 16 "receiving space 25" is directly connected to the spring space 8 "via a bore 39. In contrast to the first exemplary embodiment, the slide 1 6" encounters a stop 42 loaded by a spring 41 after covering a first stroke. Only when the pressure increases further (Pressure stage) in space 18 ", the force of spring 41 is overcome and slide 16" is now moved against the force of both springs 17 "and 41 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 Kraftstoffeinspritzdüse nach der Gattung des Hauptanspruchs. Bei einer bekannten Kraftstoffeinspritzdüse dieser Art werden die Druckräume von entweder zwei Pumpen oder zwei unabhängigen Pumpenarbeitsräumen mit Kraftstoff versorgt, wobei bei Versorgung nur des einen Raumes eine Zuschaltung des zweiten über das Schieberventil möglich ist. Es handelt sich also um eine spezielle Kraftstoffeinspritzanlage, die durch die zwei erforderlichen Hubräume verhältnismäßig aufwendig und außerdem nur begrenzt einsetzbar ist.The invention relates to a fuel injector according to the preamble of the main claim. In a known fuel injection nozzle of this type, the pressure spaces are supplied with fuel by either two pumps or two independent pump work spaces, with supply of only one space enabling the second to be activated via the slide valve. It is therefore a special fuel injection system, which is relatively complex due to the two required cubic capacity and is also only of limited use.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzpumpe mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß auch mit einer gewöhnlichen Einspritzpumpe z.B. Verteilerpumpe mit nur einem Pumpenarbeitsraum die Kraftstoffeinspritzdüse versorgt werden kann. Außerdem besteht die Möglichkeit der Alternativschaltung bzw. Umschaltung sowie der gemeinsamen Einschaltung der Einspritzdüsen. Zusätzliche wichtige Ausgestaltungen der Erfindung sind der Zeichnung sowie der folgenden Beschreibung zu entnehmen.The fuel injection pump according to the invention with the characterizing features of the main claim has the advantage that the fuel injection nozzle can also be supplied with a conventional injection pump, for example a distributor pump, with only one pump working space. There is also the possibility of an alternative switching or switching as well as a common on circuit of the injection nozzles. Additional important embodiments of the invention can be found in the drawing and the following description.

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 Federraüm 8. Zwischen den Düsennadeln 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 Einspitzdüse 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 receiving 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 chamber 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 with inflow channels 12 and 13 in Nozzle holders 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 shown rotated by 90 ° with respect to the lower part, because there to be able to show the pressure chambers 11 in the nozzle body 3 or the closing springs 7 in section by one time and the inflow channels 12 and 13 in the upper part on the other. The slide valve 14 works with a slide 16 which counteracts the force of a return spring 17 in one Room 18 hydraulic fluid is displaceable. The pressure fluid is controlled as a function of the engine parameters by means not shown, for example a solenoid valve, and is 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 in doing so makes 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 inflow channel 12 connected annular groove 23. In the slide 16, a relief channel 24 is arranged, which connects the inflow channel 13 in the position shown with the pressure-relieving space 25 accommodating 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 occurs in an intermediate position of the slide 16 and assumes 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. 2. 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 as required. 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 reset 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.

den Bei dem in Figuren3 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 Kraftstoffzuflußleitung 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", 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 substantially larger diameter than the closing spring 38 of the inner needle 31, since the area on the hollow needle 32 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 separate 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 embodiment, fewer channels are required for leakage removal, since the spring 17 "of the Slider 16 "receiving space 25" is directly connected to the spring space 8 "via a bore 39. In contrast to the first exemplary embodiment, the slide 1 6" encounters a stop 42 loaded by a spring 41 after covering a first stroke. Only when the pressure increases further (Pressure stage) in space 18 ", the force of spring 41 is overcome and slide 16" is now moved against the force of both springs 17 "and 41 into its end position.

In der in der Figur 3 dargestellten Ausgangslage des. Schie- bers 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 möglicn, im folgenden Ümsteuerreihenfolge erst einen der Kanäle dann alternativ den anderen Kanal und erst danach beide gleichzeitig aufzusteuern.In the embodiment illustrated in the Figure 3 initial position of the. B rail ers 16 "connects this via the annular groove 20", the supply line 15 "to the inlet duct 13". As soon as the slide 16 "against the spring 17" is pushed down, 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" 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 (7)

1. Kraftstoffeinspritzdüse für Brennkraftmaschinen mit zwei in Längsrichtung des Düsenkörpers angeordneten den Zufluß des Einspritzkraftstoffes zu jeweils wenigstens einem Spritzloch steuernden Düsennadeln, deren im Bereich von Druckschultern jeweils angeordneten Druckräume getrennte Zuflußkanäle aufweisen, die über ein Schieberventil miteinander verbindbar sind, dadurch gekennzeichnet, daß das Schieberventil (14) als 3-Wegeventil ausgebildet ist, durch welches eine Kraftstoffzuflußleitung (15) mitmindestens einem der \Zuflußkanäle (12, 13) verbindbar ist.1. Fuel injection nozzle for internal combustion engines with two in the longitudinal direction of the nozzle body arranged the inflow of the injection fuel to at least one spray hole controlling nozzle needles, the pressure chambers arranged in the area of pressure shoulders each have separate inflow channels that can be connected to each other via a slide valve, characterized in that the slide valve (14) is designed as a 3-way valve, through which a fuel inflow line (15) can be connected to at least one of the \ inflow channels (12, 13). 2. Kraftstoffeinspritzdüse, nach Anspruch 1, dadurch gekennzeichnet, daß der von der Zuflußleitung (15) getrennte Zuflußkanal (12, 13) über den Schieber (16) zu einem Raum (8, 25) niederen Druckes druckentlastbar ist.2. Fuel injection nozzle, according to claim 1, characterized in that the inlet channel (15) separate inlet channel (12, 13) via the slide (16) to a space (8, 25) of low pressure can be depressurized. 3. Kraftstoffeinspritzdüse nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Schieber (16") hydraulisch betätigt ist und nach Zurücklegung eines ersten Hubes auf einen Anschlag (42) stößt, der durch eine Feder (41) belastet ist, die erst nach Ansteigen des hydraulischen Druk-(14") kes (Druckstufe) nachgibt, so daß das Schieberventil als 3-Stellungsventil arbeitet und die Zuflußleitung (15") auch mit beiden Zuflußkanälen (12", 13') verbindbar ist.3. Fuel injection nozzle according to claim 1 or 2, characterized in that the slide (16 ") is hydraulic is actuated and, after covering a first stroke, encounters a stop (42) which is loaded by a spring (41) which only gives way after the hydraulic pressure (14 ") pressure (pressure stage) has risen, so that the slide valve as the third -Position valve works and the inflow line (15 ") can also be connected to both inflow channels (12", 13 '). 4. Kraftstoffeinspritzdüse nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Schieberachse senkrecht zu der Achse des Druckanschlusses (15) der Düse angeordnet ist.4. Fuel injection nozzle according to one of the preceding claims, characterized in that the slide axis is arranged perpendicular to the axis of the pressure connection (15) of the nozzle. 5. Kraftstoffeinspritzdüse nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Schließfedern (7, 7', 37,38) der Düsennadeln (5,5', 31,32) parallel zueinander geschaltet sind.5. Fuel injection nozzle according to one of the preceding claims, characterized in that the closing springs ( 7 , 7 ', 37,38) of the nozzle needles (5,5', 31 , 32 ) are connected in parallel to one another. 6. Kraftstoffeinspritzdüse nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Düsennadeln(5') parallel zueinander und möglichst dicht nebeneinander angeordnet sind und der eine Federraum (8') mit Feder (7') gegenüber den anderen zurückgesetzt ist, wofür der Druckbolzen (29) der einen Düsennadel (5') entsprechend verlängert ist (Figur 2).6. Fuel injection nozzle according to one of the preceding claims, characterized in that the nozzle needle n (5 ') are arranged parallel to one another and as close as possible to one another and the one spring chamber (8') with spring (7 ') is reset relative to the other, for which the Push pin (29) of a nozzle needle (5 ') is extended accordingly (Figure 2). 7. Kraftstoffeinspritzdüse nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Düsennadeln (31, 32) koaxial zueinander angeordnet sind, wobei die eine Nadel als Hohlnadel (32) ausgebildet ist und die zweite Nadel (31) aufnimmt, und daß die Innennadeldüse als Lochdüse und die Hohlnadeldüse als Zapfendüse wirken.7. Fuel injection nozzle according to one of claims 1 to 5, characterized in that the nozzle needles (31, 32) are arranged coaxially to one another, wherein the one needle is designed as a hollow needle (32) and the second needle (31), and that The inner needle nozzle acts as a perforated nozzle and the hollow needle nozzle acts as a pin nozzle.
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
DE2943896 1979-10-31
DE19792943896 DE2943896A1 (en) 1979-10-31 1979-10-31 FUEL INJECTION NOZZLE FOR INTERNAL COMBUSTION ENGINES

Publications (2)

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

Family

ID=6084777

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80104128A Expired EP0028288B1 (en) 1979-10-31 1980-07-16 Fuel injection nozzle for internal-combustion engines

Country Status (5)

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

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0065282B1 (en) * 1981-05-20 1985-10-09 Robert Bosch Gmbh Fuel injection nozzle for internal-combustion engines
US4570853A (en) * 1982-09-29 1986-02-18 Daimler-Benz Aktiengesellschaft Self-cleaning fuel injection valve
FR2582121A1 (en) * 1985-02-07 1986-11-21 Philips Nv METHOD AND INTERACTIVE SYSTEM FOR IDENTIFYING AN ORDER APPLIED TO THIS SYSTEM BY ITS USER
EP0083001B1 (en) * 1981-12-24 1988-04-20 Robert Bosch Gmbh Fuel injection system for direct fuel injection in internal-combustion engines
DE4115478A1 (en) * 1990-05-17 1991-11-21 Avl Verbrennungskraft Messtech Injection nozzle for IC engine - has at least two adjacent valve needles which are operable alternatively
DE19630204A1 (en) * 1996-07-26 1998-01-29 Man B & W Diesel Ag Stationary or marine engine fuel injection
DE4115477C2 (en) * 1990-05-17 2003-02-06 Avl Verbrennungskraft Messtech Injection nozzle for an internal combustion engine
WO2005057003A1 (en) 2003-12-10 2005-06-23 Siemens Aktiengesellschaft Fuel injection valve
CN104040161A (en) * 2012-01-19 2014-09-10 瓦锡兰芬兰有限公司 Fuel injection system

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DE3214040A1 (en) * 1982-04-16 1983-10-20 Volkswagenwerk Ag, 3180 Wolfsburg Fuel injection nozzle, especially for a high-speed vehicle diesel engine
DE3330774A1 (en) * 1983-08-26 1985-03-14 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION DEVICE WITH PRIMARY AND MAIN INJECTION IN INTERNAL COMBUSTION ENGINES
DE3425460A1 (en) * 1983-08-26 1985-03-07 Robert Bosch Gmbh, 7000 Stuttgart FUEL INJECTION DEVICE FOR DEFINED PRELIMINARY AND MAIN INJECTION IN INTERNAL COMBUSTION ENGINES
DE4432686C2 (en) * 1994-09-14 1996-09-05 Man B & W Diesel Ag Cross-section controlled injection nozzle
AT408132B (en) * 1995-09-14 2001-09-25 Avl Verbrennungskraft Messtech STORAGE INJECTION SYSTEM FOR AN INTERNAL COMBUSTION ENGINE
DE10040738B4 (en) * 1999-08-19 2012-12-13 Avl List Gmbh Injection device for an internal combustion engine with an injection nozzle designed as a double needle nozzle
GB9920144D0 (en) 1999-08-26 1999-10-27 Lucas Industries Ltd Fuel injector
DE10141678A1 (en) * 2001-08-25 2003-05-08 Bosch Gmbh Robert Fuel injection device for an internal combustion engine
US8069835B2 (en) * 2005-03-09 2011-12-06 Caterpillar Inc. Internal combustion engine and operating method therefor
FI119030B (en) * 2005-04-28 2008-06-30 Waertsilae Finland Oy Control arrangement for fuel input device for an internal combustion engine
US7556017B2 (en) * 2006-03-31 2009-07-07 Caterpillar Inc. Twin needle valve dual mode injector
FR2913465B1 (en) * 2007-03-07 2009-11-20 Peugeot Citroen Automobiles Sa FUEL INJECTOR AND METHOD FOR OPERATING THE INJECTOR.
FI20115418A0 (en) * 2011-05-03 2011-05-03 Waertsilae Finland Oy FUEL INJECTION UNIT AND SYSTEM
US9046067B2 (en) * 2012-09-28 2015-06-02 Caterpillar Inc. Dual fuel injector with off set check biasing springs
US9175651B2 (en) * 2013-08-19 2015-11-03 Caterpillar Inc. Dual fuel system for internal combustion engine and leakage limiting seal strategy for same
US20140346254A1 (en) * 2014-08-07 2014-11-27 Caterpillar Inc. Fuel injector for gaseous injection

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DE2656276A1 (en) * 1976-12-11 1978-06-15 Orange Gmbh & Co Kg L INJECTION SYSTEM FOR SELF-IGNING COMBUSTION MACHINERY

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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0065282B1 (en) * 1981-05-20 1985-10-09 Robert Bosch Gmbh Fuel injection nozzle for internal-combustion engines
EP0083001B1 (en) * 1981-12-24 1988-04-20 Robert Bosch Gmbh Fuel injection system for direct fuel injection in internal-combustion engines
US4570853A (en) * 1982-09-29 1986-02-18 Daimler-Benz Aktiengesellschaft Self-cleaning fuel injection valve
FR2582121A1 (en) * 1985-02-07 1986-11-21 Philips Nv METHOD AND INTERACTIVE SYSTEM FOR IDENTIFYING AN ORDER APPLIED TO THIS SYSTEM BY ITS USER
DE4115478C2 (en) * 1990-05-17 1999-05-12 Avl Verbrennungskraft Messtech Injection nozzle for an internal combustion engine
DE4115478A1 (en) * 1990-05-17 1991-11-21 Avl Verbrennungskraft Messtech Injection nozzle for IC engine - has at least two adjacent valve needles which are operable alternatively
DE4115477C2 (en) * 1990-05-17 2003-02-06 Avl Verbrennungskraft Messtech Injection nozzle for an internal combustion engine
DE19630204A1 (en) * 1996-07-26 1998-01-29 Man B & W Diesel Ag Stationary or marine engine fuel injection
DE19630204B4 (en) * 1996-07-26 2005-04-14 Man B & W Diesel Ag Fuel injector
WO2005057003A1 (en) 2003-12-10 2005-06-23 Siemens Aktiengesellschaft Fuel injection valve
DE10357769B4 (en) * 2003-12-10 2007-06-21 Siemens Ag Fuel injection valve
CN104040161A (en) * 2012-01-19 2014-09-10 瓦锡兰芬兰有限公司 Fuel injection system
CN104040161B (en) * 2012-01-19 2016-08-10 瓦锡兰芬兰有限公司 Fuel injection system

Also Published As

Publication number Publication date
JPH0154550B2 (en) 1989-11-20
DE2943896A1 (en) 1981-05-14
DE3069751D1 (en) 1985-01-17
JPS5675960A (en) 1981-06-23
EP0028288B1 (en) 1984-12-05
US4356976A (en) 1982-11-02
ATE10666T1 (en) 1984-12-15

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