EP0615064B1 - Injection valve control system for internal combustion engines - Google Patents

Injection valve control system for internal combustion engines Download PDF

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Publication number
EP0615064B1
EP0615064B1 EP19940102943 EP94102943A EP0615064B1 EP 0615064 B1 EP0615064 B1 EP 0615064B1 EP 19940102943 EP19940102943 EP 19940102943 EP 94102943 A EP94102943 A EP 94102943A EP 0615064 B1 EP0615064 B1 EP 0615064B1
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EP
European Patent Office
Prior art keywords
valve
closing
control system
housing
insert
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EP19940102943
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German (de)
French (fr)
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EP0615064A1 (en
Inventor
Marco A. Ganser
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Ganser Hydromag AG
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Ganser Hydromag AG
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    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure

Definitions

  • the present invention relates to a control arrangement known from DE-B-1 290 010 for an injection valve for internal combustion engines according to the preamble of Claim 1.
  • a control arrangement with the additional characterizing features of claim 1 points over known control arrangements thereof kind, as in particular in FR-A-2,543,647, however also described in DE-A-26 47 744 or US-A-3,680,782 are lower leakage losses and is also of much simpler construction.
  • the fuel injector shown in the drawings in the State between two injection processes is shown is via a high pressure fuel connection 10 and Fuel return connection 12 with a high-pressure delivery device for the fuel and via electrical connections 14 connected to an electronic control.
  • the high pressure conveyor and the electronic Controls are not shown in the drawings.
  • the high-pressure delivery device pumps the fuel over the high-pressure fuel connection 10 in a fuel supply bore 16, which is in a valve housing 18 of the Injector is located. Part of the fuel will practically depressurized via the fuel return connection 12 returned to the high pressure conveyor, such as is explained in more detail below.
  • the fuel is supplied via the fuel supply bore 16 on the one hand to a room 20 and on the other hand to the control section passed, which is shown enlarged in Fig.2.
  • the space 20 is formed in a nozzle body 22 which by means of a retaining part designed as a union nut 24 is screwed onto the valve housing 18.
  • a retaining part designed as a union nut 24 is screwed onto the valve housing 18.
  • the space 20 is formed in a nozzle body 22 with the fuel supply bore 16 connecting bore 25 available.
  • a nozzle needle 26 is slidably guided in the nozzle body 22, which rests with its lower end on a nozzle needle seat 28 and closes injection bores 30 which are in a nozzle tip 32 forming part of the nozzle body 22 are trained.
  • the nozzle needle 26 is closed on the one hand by a nozzle needle spring 34 and the other by the on manner to be described acting on its rear end Fuel pressure maintained on its nozzle needle seat 28. in the In the area of the space 20, the nozzle needle 26 has a shoulder 36 on.
  • the control part shown enlarged in FIGS. 2 and 3 has a 3/2-way valve 37, which by means of an electromagnet 38 is switched.
  • the 3/2-way valve 37 has a closure member 40 which by means of a guide shaft 42 and one built into the valve housing 18, fixed insert 44, between which a Sliding surface 45 is formed, is guided.
  • the Insert part 44 and a further insert part 46 are of this type installed in the valve housing 18 and by a Lock nut 48 fixed that none or none significant leakage between the high pressure part and the Low pressure part of the injection valve can take place.
  • This z. B. with a press fit or a narrow sliding fit between the valve housing 18 and the insert parts 44 and 46 reached.
  • Other fuel-tight connections are but conceivable, e.g.
  • the two insert parts 44.46 are pressed into the valve housing 18 by means of a or inserted spacer ring 50 at a distance kept apart.
  • the closure member 40 forms with the Insert part 44 a first valve 52 and with the other Insert part 46, a second valve 54 (Fig. 3).
  • closure 40 has a first Closing surface 56 and a second closing surface 58, with a valve seat 60 or 62 in the insert part 44 or 46 cooperate.
  • Both closing surfaces 56.58 are as Shell surfaces formed by circular cones.
  • Valve seats 60, 62 in the form of annular edges are in the insert parts 44, 46 formed surfaces 64,66, the are also circular cone surfaces.
  • the annular groove 78 could also be formed in the valve housing 18.
  • the valve room 72 is via an existing connection bore in the insert part 46 82 connected to a control room 84, on the one hand by the insert part 46 and on the other hand by a Control piston 86 is complete, which slides in the valve housing 18 is performed. Between the control piston 86 and a connecting rod 87 is arranged in the nozzle needle 26. The fuel pressure in the control room 84 thus acts on the Control piston 86 and the connecting rod 87 on the rear end of the nozzle needle 26.
  • the guide shaft integral with the closure member 40 42 is the one shown in FIGS. 1 and 2 Embodiment fixed with an anchor 104 of the Electromagnet 38 connected, the excitation coil 106 over the electrical connections 14 from the electronic Control receives control impulses.
  • a transmission pin 108 is passed through pressed against the armature 104 by means of a compression spring 110 becomes.
  • the force that the compression spring 110 exerts on the Uebertragungsw 108 exercises can be by means of a Adjust adjusting screw 112 (Fig. 1).
  • the Armature 104 of the electromagnet 38 instead of that Guide shaft 42 with the transmission pin 108 firmly connected.
  • the transmission pin 108 is in this case in the de-energized state of the electromagnet 38 from the Compression spring 110 pressed against the guide shaft 42.
  • This can e.g. in a manner known per se by a suitable one Design of the valve seat 60 can be realized that there is no complete hydraulic compensation and thus the hydraulic pressure force on the guide shaft 42 presses on and moves up.
  • a compression spring which on the Side of the valve 54 on the closure member 40 and thus also on the guide shaft 42 in the direction of Anchor movement works.
  • valve 52 of the Directional control valve 37 which serves as an inlet valve, as in the Figures shown essentially under the effect of Compression spring 110 kept open while the valve 54, the forms an outlet valve is closed.
  • valve room 72 and also in the control room 84 there is a fuel pressure that Can exceed 1000 bar. This fuel pressure works via the control piston 86 and the connecting rod 87 the nozzle needle 26, which is pressed against the nozzle needle seat 28 is and the injection bores 30 closes.
  • the directional valve 37 is leaking from the high-pressure part to the low pressure part between the injection processes small because only the leadership shaft 42 for the closure member 40 by means of the sliding surface 45 in Insert part 44 is slidably guided together with the insert part 46 in the manner described in the Valve housing 18 is inserted.
  • the leakage can be small being held.
  • FIG. 4 is a representation corresponding to FIG. 3 another embodiment shown, which differs from the embodiment according to FIGS. 1-3 only by one different design of the closure member 40, which is designated in Fig. 4 with 140. For the rest are in 3 and 4 corresponding parts for themselves the same Reference numerals used.
  • Closure member 140 In contrast to the closure member shown in FIGS. 1-3 40 with circular conical closing surfaces 56, 58 are at Closure member 140, the two designated 156, 158 Closing surfaces arched and preferably as spherical jacket surfaces educated.

Description

Die vorliegende Erfindung betrifft eine aus der DE-B-1 290 010 bekannte Steueranordnung für ein Einspritzventil für Verbrennungskraftmaschinen gemäss Oberbegriff von Anspruch 1. Eine Steueranordnung mit den zusätzlichen kennzeichnenden Merkmalen von Anspruch 1 weist gegenüber bekannten Steueranordnungen dieser Art, wie sie insbesondere in der FR-A-2,543,647, aber auch in der DE-A-26 47 744 oder der US-A-3,680,782 beschrieben sind, geringere Leckverluste auf und ist zudem von wesentlich einfacherem Aufbau.The present invention relates to a control arrangement known from DE-B-1 290 010 for an injection valve for internal combustion engines according to the preamble of Claim 1. A control arrangement with the additional characterizing features of claim 1 points over known control arrangements thereof Kind, as in particular in FR-A-2,543,647, however also described in DE-A-26 47 744 or US-A-3,680,782 are lower leakage losses and is also of much simpler construction.

Anhand der Zeichnungen wird nachfolgend ein Ausführungsbeispiel der Erfindung näher erläutert. Es zeigen:

Fig.1
im Längsschnitt ein Brennstoffeinspritzventil,
Fig.2
im Längsschnitt den Steuerteil des Einspritzventils gemäss Fig.1 in vergrössertem Massstab,
Fig.3
im Längsschnitt einen Bereich des Steuerteils gemäss Fig.2 in vergrössertem Massstab und
Fig.4
in einer der Fig.3 entsprechenden Darstellung eine andere Ausführungsform des Steuerteils
An exemplary embodiment of the invention is explained in more detail below with reference to the drawings. Show it:
Fig. 1
in longitudinal section a fuel injector,
Fig. 2
in longitudinal section the control part of the injection valve according to FIG. 1 on an enlarged scale,
Fig. 3
in longitudinal section an area of the control part according to Figure 2 on an enlarged scale and
Fig. 4
3 shows another embodiment of the control part

Das Brennstoff-Einspritzventil, das in den Zeichnungen im Zustand zwischen zwei Einspritzvorgängen dargestellt ist, ist über einen Brennstoffhochdruckanschluss 10 und einen Brennstoffrücklaufanschluss 12 mit einer Hochdruck-Fördereinrichtung für den Brennstoff und über elektrische Anschlüsse 14 mit einer elektronischen Steuerung verbunden. Die Hochdruck-Fördereinrichtung und die elektronische Steuerung sind in den Zeichnungen nicht gezeigt. The fuel injector shown in the drawings in the State between two injection processes is shown is via a high pressure fuel connection 10 and Fuel return connection 12 with a high-pressure delivery device for the fuel and via electrical connections 14 connected to an electronic control. The high pressure conveyor and the electronic Controls are not shown in the drawings.

Die Hochdruck-Fördereinrichtung pumpt den Brennstoff über den Brennstoffhochdruckanschluss 10 in eine Brennstoffzuführbohrung 16, die sich in einem Ventilgehäuse 18 des Einpritzventils befindet. Ein Teil des Brennstoffes wird praktisch drucklos über den Brennstoffrücklaufanschluss 12 an die Hochdruck-Fördereinrichtung zurückgeführt, wie untenstehend näher erläutert wird.The high-pressure delivery device pumps the fuel over the high-pressure fuel connection 10 in a fuel supply bore 16, which is in a valve housing 18 of the Injector is located. Part of the fuel will practically depressurized via the fuel return connection 12 returned to the high pressure conveyor, such as is explained in more detail below.

Der Brennstoff wird über die Brennstoffzuführbohrung 16 einerseits zu einem Raum 20 und anderseits zum Steuerteil geleitet, der in Fig.2 vergrössert dargestellt ist.The fuel is supplied via the fuel supply bore 16 on the one hand to a room 20 and on the other hand to the control section passed, which is shown enlarged in Fig.2.

Der Raum 20 ist in einem Düsenkörper 22 ausgebildet, der mittels eines als Ueberwurfmutter ausgebildeten Halteteils 24 am Ventilgehäuse 18 festgeschraubt ist. Im Düsenkörper 22 ist eine den Raum 20 mit der Brennstoffzuführbohrung 16 verbindende Bohrung 25 vorhanden.The space 20 is formed in a nozzle body 22 which by means of a retaining part designed as a union nut 24 is screwed onto the valve housing 18. In the nozzle body 22 is the space 20 with the fuel supply bore 16 connecting bore 25 available.

Im Düsenkörper 22 ist gleitend eine Düsennadel 26 geführt, die mit ihrem unteren Ende an einem Düsennadelsitz 28 anliegt und Einspritzbohrungen 30 abschliesst, die in einer, einen Teil des Düsenkörpers 22 bildenden Düsenspitze 32 ausgebildet sind. In dieser in den Figuren gezeigten Schliessstellung wird die Düsennadel 26 einerseits durch eine Düsennadelfeder 34 und andererseits durch den auf noch zu beschreibende Weise auf ihr rückseitiges Ende wirkenden Brennstoffdruck auf ihrem Düsennadelsitz 28 gehalten. Im Bereich des Raumes 20 weist die Düsennadel 26 einen Absatz 36 auf. A nozzle needle 26 is slidably guided in the nozzle body 22, which rests with its lower end on a nozzle needle seat 28 and closes injection bores 30 which are in a nozzle tip 32 forming part of the nozzle body 22 are trained. In this shown in the figures The nozzle needle 26 is closed on the one hand by a nozzle needle spring 34 and the other by the on manner to be described acting on its rear end Fuel pressure maintained on its nozzle needle seat 28. in the In the area of the space 20, the nozzle needle 26 has a shoulder 36 on.

Der in den Fig. 2 und 3 vergrössert dargestellte Steuerteil weist ein 3/2-Wegeventil 37 auf, das mittels eines Elektromagneten 38 geschaltet wird. Das 3/2-Wegeventil 37 weist ein Verschlussorgan 40 auf, das mittels eines Führungsschaftes 42 und eines in das Ventilgehäuse 18 eingebauten, gehäusefesten Einsatzteils 44, zwischen welchen eine Gleitfläche 45 ausgebildet ist, geführt ist. Das Einsatzteil 44 und ein weiteres Einsatzteil 46 sind derart in das Ventilgehäuse 18 eingebaut und durch eine Sicherungsmutter 48 fixiert, dass keine oder keine nennenswerte Leckage zwischen dem Hochdruckteil und dem Niederdruckteil des Einspritzventils stattfinden kann. Dies wird z. B. mit einem Pressitz oder einem engen Schiebesitz zwischen dem Ventilgehäuse 18 und den Einsatzteilen 44 und 46 erreicht. Weitere brennstoffdichte Verbindungen sind aber denkbar, z.B. unter Verwendung von geeigneten Dichtungsringen (O-Ringen). Die beiden Einsatzteile 44,46 sind mittels eines in das Ventilgehäuse 18 eingepressten oder eingeschobenen Distanzringes 50 in einem Abstand voneinander gehalten. Das Verschlussorgan 40 bildet mit dem Einsatzteil 44 ein erstes Ventil 52 und mit dem andern Einsatzteil 46 ein zweites Ventil 54 (Fig. 3). Zu diesem Zwecke weist das Verschlussorgan 40 eine erste Schliessfläche 56 und eine zweite Schliessfläche 58 auf, die mit einem Ventilsitz 60 bzw. 62 im Einsatzteil 44 bzw. 46 zusammenwirken. Beide Schliessflächen 56,58 sind als Mantelflächen von Kreiskegeln ausgebildet. Zur Bildung von Ventilsitzen 60,62 in Form von ringförmigen Kanten sind in den Einsatzteilen 44, 46 Flächen 64,66 ausgebildet, die ebenfalls Kreiskegelflächen sind. Dabei sind die Oeffnungswinkel der Kreiskegel, die die Schliessfläche 56 und die zugeordnete Fläche 64 bzw. die Schliessfläche 58 und die zugeordnete Fläche 66 festlegen, verschieden gross. Entsprechende Differenzwinkel sind in Fig. 3 mit 68 und 70 bezeichnet und übertrieben gross dargestellt. In Wirklichkeit betragen diese Differenzwinkel wenige Grade, nämlich in der Regel höchstens 3 Grad. Zwischen den Einsatzteilen 44,46 befindet sich ein Ventilraum 72. Dieser steht über das erste Ventil 52 mit einem Zweig 73, der oben durch einen Stopfen 74 abgeschlossen ist, mit der Brennstoffzuführbohrung 16 in Verbindung. Diese Verbindung wird durch eine im Ventilgehäuse 18 ausgebildeten Querbohrung 76 gebildet, die in eine nach aussen offene Ringnut 78 im hohlzylindrischen Einsatzteil 44 mündet. Diese Ringnut 78 steht über Einlassbohrungen 80 in Verbindung mit einem Innenraum 81 des Einsatzteiles 44. Die Ringnut 78 könnte auch im Ventilgehäuse 18 ausgebildet werden. Der Ventilraum 72 ist über eine im Einsatzteil 46 vorhandene Verbindungsbohrung 82 mit einem Steuerraum 84 verbunden, der einerseits durch den Einsatzteil 46 und andererseits durch einen Steuerkolben 86 abgeschlossen ist, der gleitend im Ventilgehäuse 18 geführt ist. Zwischen dem Steuerkolben 86 und der Düsennadel 26 ist eine Verbindungsstange 87 angeordnet. Der Brennstoffdruck im Steuerraum 84 wirkt somit über den Steuerkolben 86 und die Verbindungsstange 87 auf das rückseitige Ende der Düsennadel 26.The control part shown enlarged in FIGS. 2 and 3 has a 3/2-way valve 37, which by means of an electromagnet 38 is switched. The 3/2-way valve 37 has a closure member 40 which by means of a guide shaft 42 and one built into the valve housing 18, fixed insert 44, between which a Sliding surface 45 is formed, is guided. The Insert part 44 and a further insert part 46 are of this type installed in the valve housing 18 and by a Lock nut 48 fixed that none or none significant leakage between the high pressure part and the Low pressure part of the injection valve can take place. This z. B. with a press fit or a narrow sliding fit between the valve housing 18 and the insert parts 44 and 46 reached. Other fuel-tight connections are but conceivable, e.g. using appropriate Sealing rings (O-rings). The two insert parts 44.46 are pressed into the valve housing 18 by means of a or inserted spacer ring 50 at a distance kept apart. The closure member 40 forms with the Insert part 44 a first valve 52 and with the other Insert part 46, a second valve 54 (Fig. 3). To this For purposes of closure 40 has a first Closing surface 56 and a second closing surface 58, with a valve seat 60 or 62 in the insert part 44 or 46 cooperate. Both closing surfaces 56.58 are as Shell surfaces formed by circular cones. For the formation of Valve seats 60, 62 in the form of annular edges are in the insert parts 44, 46 formed surfaces 64,66, the are also circular cone surfaces. Here are the opening angles the circular cone, the closing surface 56 and the assigned surface 64 or the closing surface 58 and the Define assigned area 66, different sizes. Corresponding difference angles are 68 and 70 in FIG. 3 labeled and exaggerated. In reality these difference angles are a few degrees, namely usually at most 3 degrees. Between the insert parts 44,46 there is a valve space 72. This protrudes the first valve 52 with a branch 73 passing through the top a plug 74 is completed with the Fuel feed hole 16 in connection. This connection is through a transverse bore formed in the valve housing 18 76 formed in an annular groove 78 open to the outside opens into the hollow cylindrical insert part 44. This ring groove 78 communicates with one via inlet bores 80 Interior 81 of the insert part 44. The annular groove 78 could also be formed in the valve housing 18. The valve room 72 is via an existing connection bore in the insert part 46 82 connected to a control room 84, on the one hand by the insert part 46 and on the other hand by a Control piston 86 is complete, which slides in the valve housing 18 is performed. Between the control piston 86 and a connecting rod 87 is arranged in the nozzle needle 26. The fuel pressure in the control room 84 thus acts on the Control piston 86 and the connecting rod 87 on the rear end of the nozzle needle 26.

Im unteren Einsatzteil 46 ist weiter ein Sackloch 88 vorhanden, das über eine Querbohrung 90 mit einer im Ventilgehäuse 18 ausgebildeten Entlastungsbohrung 92 in Verbindung steht. In diese Entlastungsbohrung 92 mündet eine weitere Querbohrung 94 (Fig. 1), die mit einem Entlastungsraum 96 in Verbindung steht, der durch die Ventilnadel 26, die Verbindungsstange 87 und das Ventilgehäuse 18 gebildet ist. Die Entlastungsbohrung 92 mündet in einen Abflussraum 98, der zwischen dem oberen Ende des Ventilgehäuses 18 und einer auf dieses Ende aufgeschraubten Haltemutter 100 für den Elektromagneten 38 gebildet wird. Dieser Abflussraum 98 ist über eine Abflussbohrung 102 in der Haltemutter 100 mit dem Brennstoffrücklaufanschluss 12 verbunden.In the lower insert part 46 there is also a blind hole 88, that via a cross bore 90 with a Valve housing 18 formed relief bore 92 in Connection is established. In this relief bore 92 opens a further transverse bore 94 (Fig. 1), with a Relief chamber 96 communicates through the Valve needle 26, the connecting rod 87 and that Valve housing 18 is formed. Relief bore 92 opens into a drainage space 98, which is between the upper End of the valve housing 18 and one on this end screwed-on retaining nut 100 for the electromagnet 38 is formed. This drainage space 98 is over a Drain hole 102 in the retaining nut 100 with the Fuel return connection 12 connected.

Der mit dem Verschlussorgan 40 einstückige Führungsschaft 42 ist bei der in den Fig. 1 und 2 gezeigten Ausführungsform fest mit einem Anker 104 des Elektromagneten 38 verbunden, dessen Erregerspule 106 über die elektrischen Anschlüsse 14 von der elektronischen Steuerung Steuerimpulse erhält. Durch den Elektromagneten 38 ist ein Uebertragungsstift 108 hindurchgeführt, der mittels einer Druckfeder 110 gegen den Anker 104 gedrückt wird. Die Kraft, die die Druckfeder 110 auf den Uebertragungsstift 108 ausübt, lässt sich mittels einer Einstellschraube 112 einstellen (Fig. 1).The guide shaft integral with the closure member 40 42 is the one shown in FIGS. 1 and 2 Embodiment fixed with an anchor 104 of the Electromagnet 38 connected, the excitation coil 106 over the electrical connections 14 from the electronic Control receives control impulses. Through the electromagnet 38, a transmission pin 108 is passed through pressed against the armature 104 by means of a compression spring 110 becomes. The force that the compression spring 110 exerts on the Uebertragungsstift 108 exercises can be by means of a Adjust adjusting screw 112 (Fig. 1).

In einer nicht gezeigten, andern Ausführungsform ist der Anker 104 des Elektromagneten 38 anstatt mit dem Führungsschaft 42 mit dem Uebertragungsstift 108 fest verbunden. Der Uebertragungsstift 108 wird in diesem Fall im stromlosen Zustand des Elektromagnets 38 von der Druckfeder 110 an den Führungsschaft 42 angedrückt. Wird der Elektromagnet 38 erregt und demzufolge der Anker 104 angezogen, so muss sichergestellt werden, dass sich der mit dem Verschlussorgan 40 einstückige Führungsschaft 42 ebenfalls in Richtung der Ankerbewegung verschiebt. Dies kann z.B. auf an sich bekannte Weise durch eine geeignete Ausgestaltung des Ventilsitzes 60 so realisiert werden, dass kein vollständiger hydraulischer Ausgleich stattfindet und somit die hydraulische Druckkraft den Führungsschaft 42 aufdrückt und nach oben bewegt. Eine weitere Möglichkeit besteht darin, eine Druckfeder zu verwenden, welche auf der Seite des Ventils 54 auf das Verschlussorgan 40 und damit auch auf den Führungsschaft 42 in Richtung der Ankerbewegung wirkt.In another embodiment, not shown, the Armature 104 of the electromagnet 38 instead of that Guide shaft 42 with the transmission pin 108 firmly connected. The transmission pin 108 is in this case in the de-energized state of the electromagnet 38 from the Compression spring 110 pressed against the guide shaft 42. Becomes the electromagnet 38 is energized and consequently the armature 104 tightened, it must be ensured that the with the locking member 40 is a one-piece guide shaft 42 also moves in the direction of the anchor movement. This can e.g. in a manner known per se by a suitable one Design of the valve seat 60 can be realized that there is no complete hydraulic compensation and thus the hydraulic pressure force on the guide shaft 42 presses on and moves up. One more way is to use a compression spring, which on the Side of the valve 54 on the closure member 40 and thus also on the guide shaft 42 in the direction of Anchor movement works.

Die Funktionsweise des vorstehend beschriebenen Einspritzventils ist wie folgt:The operation of the injection valve described above is as follows:

Bei stromlosem Elektromagneten 38 wird das Ventil 52 des Wegeventils 37, das als Einlassventil dient, wie in den Figuren gezeigt, im wesentlichen unter der Wirkung der Druckfeder 110 offengehalten, während das Ventil 54, das ein Auslassventil bildet, geschlossen ist. Im Ventilraum 72 und auch im Steuerraum 84 herrscht ein Brennstoffdruck, der 1000 bar übersteigen kann. Dieser Brennstoffdruck wirkt über den Steuerkolben 86 und die Verbindungsstange 87 auf die Düsennadel 26, die gegen den Düsennadelsitz 28 gedrückt wird und die Einspritzbohrungen 30 abschliesst.When the electromagnet 38 is de-energized, the valve 52 of the Directional control valve 37, which serves as an inlet valve, as in the Figures shown essentially under the effect of Compression spring 110 kept open while the valve 54, the forms an outlet valve is closed. In the valve room 72 and also in the control room 84 there is a fuel pressure that Can exceed 1000 bar. This fuel pressure works via the control piston 86 and the connecting rod 87 the nozzle needle 26, which is pressed against the nozzle needle seat 28 is and the injection bores 30 closes.

Beim Einschalten des Elektromagneten 38 wird dessen Anker 104 angezogen und damit das Verschlussorgan 40 angehoben. Das Einlassventil 52 wird geschlossen, während das Auslassventil 54 geöffnet wird. Dadurch wird der Steuerraum 84 über die Verbindungsbohrung 82, das Sackloch 88 und die Querbohrung 90 mit der Entlastungsbohrung 92 verbunden. Der Druck im Steuerraum 84 fällt. Die Düsennadel 26 wird durch den im Raum 20 herrschenden und auf den Absatz 36 der Düsennadel 26 wirkenden Brennstoffdruck angehoben. Die Einspritzbohrungen 30 werden freigegeben und es wird auf an sich bekannte Weise Brennstoff in den Verbrennungsraum der Verbrennungskraftmaschine eingespritzt. When the electromagnet 38 is switched on, its armature becomes 104 attracted and thus the closure member 40 is raised. The inlet valve 52 is closed while the outlet valve 54 is opened. This will make the control room 84 via the connecting bore 82, the blind hole 88 and the Cross bore 90 connected to the relief bore 92. Of the Pressure in control room 84 drops. The nozzle needle 26 is through the prevailing in room 20 and on paragraph 36 of the Nozzle needle 26 acting fuel pressure raised. The Injection holes 30 are released and it is on known fuel in the combustion chamber Internal combustion engine injected.

Zur Beendigung des Einspritzvorganges wird der Elektromagnet 38 ausgeschaltet. Das Wegeventil 37 wird dadurch umgesteuert, d.h. das Auslassventil 54 wird geschlossen und das Einlassventil 52 geöffnet. Im Ventilraum 72 und im Steuerraum 84 kann sich nun der Druck wieder aufbauen, was zur Folge hat, dass die Düsennadel 26 wieder gegen den Düsennadelsitz 28 gedrückt wird, womit die Einspritzung beendet wird.To end the injection process, the electromagnet 38 switched off. The directional valve 37 is thereby reversed, i.e. exhaust valve 54 is closed and inlet valve 52 opened. In the valve space 72 and Control room 84 can now build up the pressure again, what has the consequence that the nozzle needle 26 again against the Nozzle needle seat 28 is pressed, with which the injection is ended.

Da während des Einspritzvorganges, während dem der Ventilraum 72 des Wegeventils 37 über das offene Auslassventil 54 mit der Entlastungsbohrung 92 verbunden ist, das Einlassventil 52 geschlossen bleibt, ist während dieser Zeit der Ventilraum 52 gegenüber der Brennstoffzuführbohrung 16 abgeschlossen. Anders ausgedrückt ist der Hochdruckteil des Einspritzventils während des Einspritzvorganges vom Niederdruckteil getrennt. Es fliesst somit nur während des kurzen Umschaltens des Wegeventiles 37 eine gewisse Brennstoffmenge vom Hochdruckteil direkt zum Niederdruckteil.Because during the injection process, during which the valve chamber 72 of the directional control valve 37 via the open outlet valve 54 is connected to the relief bore 92, the inlet valve 52 remains closed during this time Valve space 52 opposite the fuel supply bore 16 completed. In other words, the high pressure part of the Injection valve during the injection process from the low pressure part Cut. It only flows during the short one Switching the directional valve 37 a certain amount of fuel from the high pressure part directly to the low pressure part.

Im weiteren ist die Leckage des Wegeventiles 37 vom Hochdruckteil zum Niederdruckteil zwischen den Einspritzvorgängen deswegen klein gehalten, weil nur der Führungsschaft 42 für das Verschlussorgan 40 mittels der Gleitfläche 45 im Einsatzteil 44 gleitend geführt ist, welcher zusammen mit dem Einsatzteil 46 auf die beschriebene Weise in das Ventilgehäuse 18 eingesetzt ist. Dadurch, dass nur eine Gleitfläche 45 vorhanden ist, kann die Leckage klein gehalten werden. Furthermore, the directional valve 37 is leaking from the high-pressure part to the low pressure part between the injection processes small because only the leadership shaft 42 for the closure member 40 by means of the sliding surface 45 in Insert part 44 is slidably guided together with the insert part 46 in the manner described in the Valve housing 18 is inserted. By having only one Sliding surface 45 is present, the leakage can be small being held.

Diese Massnahmen zur Verringerung der vom Hochdruckteil in den Niederdruckteil dringenden Leckmenge wirken sich vor allem bei Einspritzsystemen vorteilhaft aus, die mit hohen Brennstoffdrücken arbeiten, d.h. mit Drücken von 500 bis 1000 bar und höher.These measures to reduce the high pressure part in the low-pressure part urgent leakage act especially advantageous for injection systems with high Fuel pressures work, i.e. with presses from 500 to 1000 bar and higher.

Durch die beschriebene Ausgestaltung der Schliessflächen 56 und 58 am Verschlussorgan 40 und der dazugehörigen Ventilsitze 60 und 62 wird ein einwandfreies Schliessen der Ventile 52, 54 während einer langen Betriebsdauer sichergestellt, d.h. die auftretende Abnützung vermag auch bei einer sehr grossen Zahl von Schaltvorgängen die Funktionsweise nicht nachteilig zu beeinflussen.Due to the described configuration of the closing surfaces 56 and 58 on the closure member 40 and the associated valve seats 60 and 62 will close the valves properly 52, 54 ensured over a long period of operation, i.e. the wear and tear that occurs can also a very large number of switching operations not adversely affect.

In der Fig. 4 ist in einer der Fig. 3 entsprechenden Darstellung eine andere Ausführungsform gezeigt, die sich von der Ausführungsform gemäss den Fig. 1-3 nur durch eine andere Gestaltung des Verschlussorganes 40 unterscheidet, das in Fig. 4 mit 140 bezeichnet ist. Im übrigen sind in den Fig. 3 und 4 für sich entsprechende Teile dieselben Bezugszeichen verwendet.4 is a representation corresponding to FIG. 3 another embodiment shown, which differs from the embodiment according to FIGS. 1-3 only by one different design of the closure member 40, which is designated in Fig. 4 with 140. For the rest are in 3 and 4 corresponding parts for themselves the same Reference numerals used.

Im Gegensatz zum in den Fig. 1-3 gezeigten Verschlussorgan 40 mit kreiskegelförmigen Schliessflächen 56, 58 sind beim Verschlussorgan 140 die beiden mit 156, 158 bezeichneten Schliessflächen gewölbt und vorzugsweise als Kugelmantelflächen ausgebildet.In contrast to the closure member shown in FIGS. 1-3 40 with circular conical closing surfaces 56, 58 are at Closure member 140, the two designated 156, 158 Closing surfaces arched and preferably as spherical jacket surfaces educated.

Claims (9)

  1. Control system for an injection valve for internal combustion engines for controlling the opening and closing movement of the valve element of the injection valve, having a directional control valve (37) which can be switched by means of an electromagnet (38) and whose closing element (40, 140), which can be moved backwards and forwards in a translatory fashion, has a first and a second closing face (56, 58, 156, 158) and, depending on the switched position of the directional control valve (37), either comes into contact, by means of the first closing face (56, 156), with a first valve seat (60) which is fixed to the housing and is arranged on the side of an inflow line (16) for pressurized fuel, or comes into contact, by means of the second closing face (58, 158), with a second valve seat (62) which is fixed to the housing and is arranged on the side of a pressure relief line (92), and having a control space (84) which, by means of the directional control valve (37), can be connected either to the fuel inflow line (16) via a passage which is defined by the first valve seat (60) which is fixed to the housing, or can be connected to the pressure relief line (92) via a passage which is defined by the second valve seat (62) which is fixed to the housing, the fuel pressure in the control space (84) acting on the rear end of the valve element (26) and pressing the latter against the valve seat (28) of the injection valve, characterized in that the closing element (40, 140), arranged at a distance from the electromagnet (38), of the directional control valve (37) is guided by means of a single sliding face (45) in an insert (44) which is fixed to the housing and is arranged between the closing element (40, 140) and the electromagnet (38), for which purpose the closing element (40, 140) is permanently connected to a guide element (42) on the side of its first closing face (56, 156), said guide element (42) being guided in the insert (44) and being operatively connected to an armature (104) of the electromagnet (38).
  2. Control system according to Claim 1, characterized in that the closing faces (56, 58) of the closing element (40) are formed as outer faces of circular cones.
  3. Control system according to Claim 1, characterized in that the closing faces (156, 158) of the closing element (140) are curved and are preferably formed as spherical outer faces.
  4. Control system according to one of Claims 1 - 3, characterized in that the valve seats (60, 62) are formed as edges.
  5. Control system according to Claims 2 and 4, characterized in that, in order to form the valve seats (60, 62), circular conical faces (64, 66) are provided, the angle of aperture of the circular cones defining the circular conical faces (64, 66) differing by a few degrees, preferably at most 3 degrees, from the angle of aperture of the circular cones which define the associated closing faces (56, 58).
  6. Control system according to one of Claims 1 - 5, characterized in that the first valve seat (60) and a connection (80, 81) to the fuel inflow line (16) are formed in the insert (44), and there is a second insert (46) which is seated in the valve housing (18) and in which the second valve seat (62) is formed, a valve space (72) being formed between the inserts (44, 46).
  7. Control system according to Claim 6, characterized in that the valve space (72) is connected to the control space (84) via at least one connecting opening (82).
  8. Control system according to Claim 6 or 7, characterized in that a spacer element (50) is arranged between the inserts (44, 46).
  9. Control system according to one of Claims 6 - 8, characterized in that in the second insert (46) there is an outflow connection (88, 90) which leads from the valve space (72) to a return flow line (92).
EP19940102943 1993-03-08 1994-02-26 Injection valve control system for internal combustion engines Expired - Lifetime EP0615064B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH696/93 1993-03-08
CH00696/93A CH686845A5 (en) 1993-03-08 1993-03-08 Control arrangement for an injection valve for internal combustion engines.

Publications (2)

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EP0615064A1 EP0615064A1 (en) 1994-09-14
EP0615064B1 true EP0615064B1 (en) 1998-08-26

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CH (1) CH686845A5 (en)
DE (1) DE59406752D1 (en)

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DE4404050C1 (en) * 1994-02-09 1994-12-01 Daimler Benz Ag Injector with solenoid-valve control for an internal combustion engine
DE4434892A1 (en) * 1994-09-29 1996-04-11 Siemens Ag Injector
DE19634105A1 (en) * 1996-08-23 1998-01-15 Daimler Benz Ag Injection valve for internal combustion engines
DE19709794A1 (en) * 1997-03-10 1998-09-17 Bosch Gmbh Robert Valve for controlling liquids
DE19729844A1 (en) * 1997-07-11 1999-01-14 Bosch Gmbh Robert Fuel injector
DE19744723A1 (en) * 1997-10-10 1999-04-15 Bosch Gmbh Robert Fuel injector
GB9805854D0 (en) 1998-03-20 1998-05-13 Lucas France Fuel injector
EP1000240B1 (en) 1998-05-28 2004-03-24 Siemens Aktiengesellschaft Fuel injection valve for internal combustion engines
GB9823134D0 (en) 1998-10-23 1998-12-16 Lucas Ind Plc Valve
DE19907544C2 (en) * 1999-02-22 2002-12-05 Siemens Ag Injector for an injection system of an internal combustion engine
DE10024703A1 (en) * 2000-05-18 2001-11-22 Bosch Gmbh Robert Injection arrangement for fuel storage injection system has valve unit blocking auxiliary channel and outlet path in alternation
JP2006257874A (en) * 2004-04-30 2006-09-28 Denso Corp Injector
CN112943499B (en) * 2021-02-25 2022-05-03 山东菏泽华星油泵油嘴有限公司 Novel orifice mechanism of fuel sprayer

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US2927737A (en) * 1952-04-12 1960-03-08 Bosch Gmbh Robert Fuel injection valves
GB1097752A (en) * 1963-09-09 1968-01-03 Ass Eng Ltd Fuel injection valves for internal combustion engines
FR2068857A5 (en) * 1969-10-24 1971-09-03 Sofredi
FR2145081A5 (en) * 1971-07-08 1973-02-16 Peugeot & Renault
IT1217260B (en) * 1987-08-25 1990-03-22 Weber Srl ELECTROMAGNETICALLY OPERATED FUEL INJECTION VALVE FOR DIESEL CYCLE ENGINES
DE3814156A1 (en) * 1988-04-27 1989-11-09 Mesenich Gerhard PULSE-MODULATED HYDRAULIC VALVE
JP2712760B2 (en) * 1990-05-29 1998-02-16 トヨタ自動車株式会社 Fuel injection valve

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EP0615064A1 (en) 1994-09-14
DE59406752D1 (en) 1998-10-01
CH686845A5 (en) 1996-07-15

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