EP1313945B1 - Injection valve for the injection of fuel in an internal combustion engine and method for control of the opening and closing process of a nozzle needle in an injection valve - Google Patents

Injection valve for the injection of fuel in an internal combustion engine and method for control of the opening and closing process of a nozzle needle in an injection valve Download PDF

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Publication number
EP1313945B1
EP1313945B1 EP01971616A EP01971616A EP1313945B1 EP 1313945 B1 EP1313945 B1 EP 1313945B1 EP 01971616 A EP01971616 A EP 01971616A EP 01971616 A EP01971616 A EP 01971616A EP 1313945 B1 EP1313945 B1 EP 1313945B1
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European Patent Office
Prior art keywords
pressure
control
control valve
injection
valve
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EP01971616A
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German (de)
French (fr)
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EP1313945A1 (en
Inventor
Wolfgang Bloching
Reda Rizk
Willibald SCHÜRZ
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Siemens AG
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Siemens 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
    • 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
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift

Definitions

  • the invention relates to a method for controlling the opening and closing operation of a nozzle needle of an injection valve according to the preamble of claim 1. Furthermore The invention relates to an injection valve for implementation this procedure.
  • injection systems are increasingly used, where with very high injection pressures.
  • Such injection systems are common rail systems (for diesel engines) and HPDI injection systems (for gasoline engines).
  • HPDI injection systems for gasoline engines.
  • injection systems use a high pressure pump to fuel the fuel in a common to all cylinders of the engine Pressure accumulator promoted from which the injectors the individual cylinders are supplied with fuel.
  • the Opening and closing the injection valves is done in the Usually controlled electromagnetically.
  • the injectors are in such systems equipped with control valves designed as servo valves, which hydraulically open and close the nozzle needle control the injection valve, that is, in particular the Schedule the start and end of the injection process.
  • the servo valve mainly affects the speed with which opens and closes the injector.
  • the fuel comes with System pressure from a high pressure accumulator, not shown via a high-pressure bore 1 to the injection valve housing 2.
  • a control valve 3 is arranged in the injection valve housing 2, via which the injector housing 2 is supplied Fuel via a line 4 of a nozzle pressure chamber 5 is feedable.
  • the present one acts in the nozzle pressure chamber 5 Pressure the front area of an axially movable in the injector housing 2 stored and guided nozzle body 6, which is used with one arranged at the foremost end Nozzle needle 7 injection holes 8 in the injector housing 2 to open and close the combustion chamber of an internal combustion engine to lead.
  • the injection bores 8 are thus when the injection valve is open with the nozzle pressure chamber 5 in connection, the in turn via line 4, control valve 3 and High pressure bore 1 is connected to the high pressure accumulator.
  • the control valve 3 serves as a switching element between the operating pressure (Rail pressure) in a valve chamber 9 of the control valve 3 and the nozzle pressure chamber 5.
  • the control valve 3 sits by the action of Rail pressure and the biasing force of a spring 10 sealing on a valve seat 11.
  • the control valve 3 switches via a Tappet 12, the one indicated by the arrow 13 Actuator is controlled.
  • the actuation of the plunger 12 leads from the in the Illustrated closed position of the control valves 3 to the fact that the control valves 3 against the rail pressure opened in the valve chamber 9 and the biasing force of the spring 10 become.
  • you open the control valves 3 plants the rail pressure into an annular chamber 14 and through line 4 up into the nozzle pressure chamber 5.
  • the rail pressure in the nozzle pressure chamber 5 causes a shift of the nozzle body 6 against the biasing force one in a control room 15 arranged, loading the nozzle body 6 Spring 16 so that the nozzle needle 7 the injection holes 8 releases and the injection of fuel into the combustion chamber of the internal combustion engine.
  • the control valve 3 a pressure compensation chamber 17.
  • the pressure compensation chamber 17 is formed in that the control valves 3 one with areas of different diameters provided step piston 18.
  • the control valve 3 is closed by deactivating the Actuator, which causes the control valve 3 under the biasing force the spring 10 closes.
  • the displacement of the step piston 18 causes a pressure build-up in the chamber 19 and in Control room 15. Since simultaneously with the closing of the control valve 3 the rail pressure in the nozzle pressure chamber 5 collapses, closes the nozzle needle 7 under the effect of the Nozzle body 6 acting biasing force of the spring 10 and the Pressure in the control room 15.
  • the pressure build-up in the chamber 19 and in the control room 15 is additionally regulated by a valve 20.
  • This configuration thus ensures that the closing the nozzle needle 7 with the participation of the additional pressure in Control room 15 is done quickly and without delay while when the nozzle needle 7 is opened, the pressure in the control chamber 15 is reduced is, so that the opening only against the biasing force of the Spring 10 takes place.
  • the short switching times and the fact that the pressure in chamber 19 and in control room 15 is not permanent contact ensures that permanent leakage does not occur and switching leaks are minimized as far as possible.
  • the stepped piston 18 is formed in two parts in this exemplary embodiment. As soon as fuel with rail pressure flows into line 4, fuel with rail pressure simultaneously flows via a bore 21 to the second part of the stepped piston 18 and displaces it against the biasing force of an additional spring 22.
  • the control valve 3 is closed by deactivating the Actuator, which causes the control valve 3 under the biasing force the spring 10 closes.
  • the displacement of the step piston 18 causes a pressure build-up in the chamber 19 and in Control room 15, since the control valve closes at the same time 3 the rail pressure in the nozzle pressure chamber 5 and above the bore 21 on the stepped piston 18 collapses.
  • the Nozzle needle 7 thus closes under the effect on the nozzle body 6 acting biasing force of the spring 10 and the Pressure in the control room 15.
  • This configuration also ensures that the closing the nozzle needle 7 with the participation of the additional pressure in the control room 15 takes place quickly and without delay
  • the pressure in the control room 15 is broken down so that the opening only against the biasing force the spring 10 takes place.
  • the short switching times and the fact that the pressure in the chamber 19 and in the control room 15th not permanently present ensure that permanent leakage does not occur occur and switching leaks are minimized as far as possible.

Description

Die Erfindung betrifft ein Verfahren zur Steuerung des Öffnungs- und Schließvorgangs einer Düsennadel eines Einspritzventils nach dem Oberbegriff des Patentanspruchs 1. Weiterhin betrifft die Erfindung ein Einspritzventil zur Durchführung dieses Verfahrens.The invention relates to a method for controlling the opening and closing operation of a nozzle needle of an injection valve according to the preamble of claim 1. Furthermore The invention relates to an injection valve for implementation this procedure.

Für die Kraftstoffversorgung von Verbrennungsmotoren werden zunehmend Speichereinspritzsysteme verwendet, bei denen mit sehr hohen Einspritzdrücken gearbeitet wird. Solche Einspritzsysteme sind als Common-Rail-Systeme (für Dieselmotoren) und HPDI-Einspritzsysteme (für Ottomotoren) bekannt. Bei diesen Einspritzsystemen wird der Kraftstoff mit einer Hochdruckpumpe in einen allen Zylindern des Motors gemeinsamen Druckspeicher gefördert, von dem aus die Einspritzventile an den einzelnen Zylindern mit Kraftstoff versorgt werden. Das Öffnen und Schließen der Einspritzventile wird dabei in der Regel elektromagnetisch gesteuert.For the fuel supply of internal combustion engines memory injection systems are increasingly used, where with very high injection pressures. Such injection systems are common rail systems (for diesel engines) and HPDI injection systems (for gasoline engines). at These injection systems use a high pressure pump to fuel the fuel in a common to all cylinders of the engine Pressure accumulator promoted from which the injectors the individual cylinders are supplied with fuel. The Opening and closing the injection valves is done in the Usually controlled electromagnetically.

Zu diesem Zweck sind die Einspritzventile bei solchen Systemen mit als Servoventilen ausgebildeten Steuerventilen ausgerüstet, die hydraulisch das Öffnen und Schließen der Düsennadel des Einspritzventils steuern, das heißt insbesondere den Beginn und das Ende des Einspritzvorgangs zeitlich festlegen. Das Servoventil beeinflußt vor allem die Geschwindigkeit, mit der das Einspritzventil öffnet und schließt.For this purpose the injectors are in such systems equipped with control valves designed as servo valves, which hydraulically open and close the nozzle needle control the injection valve, that is, in particular the Schedule the start and end of the injection process. The servo valve mainly affects the speed with which opens and closes the injector.

Da bei Dieselmotoren der Kraftstoff mit einem Druck von bis über 1500 bar in eine Brennkammer des Motors eingespritzt wird, werden an die Einspritzventile sehr hohe Anforderungen hinsichtlich der Dichtheit gestellt. Bei den aus der Praxis bekannten Common-Rail-Injektoren stellt die Leckage, sowohl die Dauerleckage als auch die Schaltleckage, einen deutlichen Leistungsverlust dar. Diese Leckagen treten insbesondere im Bereich des Steuerventils zur Steuerung der Kraftstoffeinspritzung und im Bereich des Steuerraums auf, in dem ein mit der Düsennadel in Wirkverbindung stehender Düsenkörper axialbeweglich gelagert ist. Eine Leckagestelle bildet hierbei die Düsennadelführung, deren Dichtspalt ständig dem Druckgefälle zwischen Raildruck und Leckagedruck ausgesetzt ist. Bei den bekannten Einspritzventile wurede versucht, die Dauerleckage durch Verkleinerung der Dichtspalte zu verringern.Since in diesel engines the fuel is at a pressure of up to over 1500 bar injected into a combustion chamber of the engine will place very high demands on the injection valves in terms of tightness. In practice known common rail injectors represents the leak, both the permanent leakage as well as the switching leakage, a clear one Loss of performance. These leaks occur particularly in the Area of the control valve for controlling the fuel injection and in the area of the control room, where a with the nozzle needle is operatively connected axially movable is stored. A leakage point forms here Nozzle needle guide, the sealing gap constantly the pressure drop between rail pressure and leakage pressure. Both Known fuel injectors have been tried to avoid permanent leakage by reducing the sealing gap.

Aus der US-A-5,299,919 ist ein Verfahren zur Steuerung des Öffnungs- und Schließvorgangs einer über eine Feder vorgespannten Düsennadel eines mit einem Steuerventil versehenen Einspritzventils für die Einspritzung von Kraftstoff in eine Verbrennungskraftmaschine bekannt, wobei über das Steuerventil der Druck in einem Steuerraum beeinflussbar ist, der mit der Düsennadel in Wirkverbindung steht. Zum Schließen der Düsennadel bei geschlossenem Steuerventil wird zusätzlich zur Vorspannkraft der Feder ein auf die Düsennadel wirkender Druck im Steuerraum erzeugt. Zum Öffnen der Düsennadel bei geöffnetem Steuerventil wird der zusätzliche auf die Düsennadel wirkende Druck aufgehoben. Über dies offenbart das genannte Dokument auch eine Vorrichtung zum Ausführen dieses Verfahrens. From US-A-5,299,919 a method for controlling the Opening and closing of a spring-loaded spring Nozzle needle one with a control valve Injector for injecting fuel into a Internal combustion engine known, being via the control valve the pressure in a control room can be influenced by using the nozzle needle is in operative connection. To close the nozzle needle when the control valve is closed, in addition to Preload force of the spring acting on the nozzle needle Pressure generated in the control room. To open the nozzle needle at Open control valve is the additional on the nozzle needle acting pressure released. The above reveals the above Document also a device for doing this Process.

Die vorrichtungsmäßigen Merkmale eines erfindungsgemäßen Einspritzventils werden in Patentanspruch 1 und 4 genannt.The device features of an injection valve according to the invention are mentioned in claims 1 and 4.

Durch die erfindungsgemäße Druckregulierung des Drucks im Steuerraum in Abhängigkeit von der Stellung des Steuerventils ist es möglich, einerseits den Schließvorgang der Düsennadel durch Druckbeaufschlagung zu beschleunigen und andererseits sicherzustellen, daß das Öffnen der Düsennadel nur gegen die Vorspannkraft der den Düsenkörper belastenden Feder erfolgt. By regulating the pressure according to the invention in the Control room depending on the position of the control valve it is possible, on the one hand, to close the nozzle needle accelerate by pressurizing and on the other hand ensure that the opening of the nozzle needle only against the Preload force of the spring loading the nozzle body takes place.

Da der Druck im Steuerraum nur zum Schließen der Düsennadel anliegt, nachfolgend bei geöffnetem Steuerventil aber wieder ganz abgebaut wird, ist es möglich, Dauerleckagen so gut wie ganz abzubauen und das Auftreten von Schaltleckagen stark zu verringern.Because the pressure in the control room only to close the nozzle needle is present, but again when the control valve is open is completely broken down, it is possible to prevent permanent leakage as well completely reduce and the occurrence of switching leaks greatly reduce.

Weitere Merkmale und Vorteile der Erfindung ergeben sich aus der nachfolgenden Beschreibung der zugehörigen Zeichnung, in der zwei Ausführungsbeispiele eines erfindungsgemäßen Einspritzventils schematisch dargestellt sind. In der Zeichnung zeigt:

Figur 1
einen Längsschnitt durch eine erste Ausführungsform eines erfindungsgemäßen Einspritzventils und
Figur 2
einen Längsschnitt durch eine zweite Ausführungsform eines erfindungsgemäßen Einspritzventils.
Further features and advantages of the invention result from the following description of the associated drawing, in which two exemplary embodiments of an injection valve according to the invention are shown schematically. The drawing shows:
Figure 1
a longitudinal section through a first embodiment of an injection valve according to the invention and
Figure 2
a longitudinal section through a second embodiment of an injection valve according to the invention.

Wie aus den Abbildungen ersichtlich, wird der Kraftstoff mit Systemdruck von einem nicht dargestellten Hochdruckspeicher über eine Hochdruckbohrung 1 dem Einspritzventilgehäuse 2 zugeführt.As can be seen from the pictures, the fuel comes with System pressure from a high pressure accumulator, not shown via a high-pressure bore 1 to the injection valve housing 2.

Im Einspritzventilgehäuse 2 ist ein Steuerventil 3 angeordnet, über das der dem Einspritzventilgehäuse 2 zugeführte Kraftstoff mittels einer Leitung 4 einer Düsendruckkammer 5 zuführbar ist. In der Düsendruckkammer 5 wirkt der vorliegende Druck den vorderen Bereich eines axial beweglich im Einspritzventilgehäuse 2 gelagerten und geführten Düsenkörpers 6, der dazu dient, mit einer am vordersten Ende angeordneten Düsennadel 7 Einspritzbohrungen 8 im Einspritzventilgehäuse 2 zu öffnen und zu schließen, die zum Brennraum eines Verbrennungsmotors führen.A control valve 3 is arranged in the injection valve housing 2, via which the injector housing 2 is supplied Fuel via a line 4 of a nozzle pressure chamber 5 is feedable. The present one acts in the nozzle pressure chamber 5 Pressure the front area of an axially movable in the injector housing 2 stored and guided nozzle body 6, which is used with one arranged at the foremost end Nozzle needle 7 injection holes 8 in the injector housing 2 to open and close the combustion chamber of an internal combustion engine to lead.

Die Einspritzbohrungen 8 stehen somit bei geöffnetem Einspritzventil mit der Düsendruckkammer 5 in Verbindung, die ihrerseits über die Leitung 4, das Steuerventil 3 und die Hochdruckbohrung 1 mit dem Hochdruckspeicher verbunden ist.The injection bores 8 are thus when the injection valve is open with the nozzle pressure chamber 5 in connection, the in turn via line 4, control valve 3 and High pressure bore 1 is connected to the high pressure accumulator.

Das Steuerventil 3 dient als Schaltorgan zwischen dem Betriebsdruck (Raildruck) in einer Ventilkammer 9 des Steuerventils 3 und der Düsendruckkammer 5. In der geschlossenen Stellung sitzt das Steuerventil 3 durch die Wirkung des Raildrucks und der Vorspannkraft einer Feder 10 abdichtend auf einem Ventilsitz 11. Das Steuerventil 3 schaltet über einen Stößel 12, der von einem durch den Pfeil 13 nur angedeuteten Aktor angesteuert wird.The control valve 3 serves as a switching element between the operating pressure (Rail pressure) in a valve chamber 9 of the control valve 3 and the nozzle pressure chamber 5. In the closed Position, the control valve 3 sits by the action of Rail pressure and the biasing force of a spring 10 sealing on a valve seat 11. The control valve 3 switches via a Tappet 12, the one indicated by the arrow 13 Actuator is controlled.

Das Ansteuern des Stößels 12 führt ausgehend von der in den Abbildungen dargestellten geschlossenen Stellung der Steuerventile 3 dazu, daß die Steuerventile 3 gegen den Raildruck in der Ventilkammer 9 und die Vorspannkraft der Feder 10 geöffnet werden. Beim Öffnen der Steuerventile 3 pflanzt sich der Raildruck in eine Ringkammer 14 und durch die Leitung 4 bis in die Düsendruckkammer 5 fort.The actuation of the plunger 12 leads from the in the Illustrated closed position of the control valves 3 to the fact that the control valves 3 against the rail pressure opened in the valve chamber 9 and the biasing force of the spring 10 become. When you open the control valves 3 plants the rail pressure into an annular chamber 14 and through line 4 up into the nozzle pressure chamber 5.

Der Raildruck in der Düsendruckkammer 5 bewirkt ein Verschieben des Düsenkörpers 6 entgegen der Vorspannkraft einer in einem Steuerraum 15 angeordneten, den Düsenkörper 6 belastenden Feder 16, so daß die Düsennadel 7 die Einspritzbohrungen 8 freigibt und das Einspritzen von Kraftstoff in die Brennkammer des Verbrennungsmotors ermöglicht.The rail pressure in the nozzle pressure chamber 5 causes a shift of the nozzle body 6 against the biasing force one in a control room 15 arranged, loading the nozzle body 6 Spring 16 so that the nozzle needle 7 the injection holes 8 releases and the injection of fuel into the combustion chamber of the internal combustion engine.

Um zu ermöglichen, daß das Öffnen des Düsenkörpers 6 nur gegen die Vorspannkraft der Feder 16 erfolgt und nicht auch noch gegen den in dem Steuerraum 15 herrschenden Druck, wird gleichzeitig mit dem Öffnen des Steuerventils 3 und somit der Einleitung des Raildrucks in die Düsendruckkammer 5 der Druck im Steuerraum 15 abgebaut. Zu diesem Zweck weist das Steuerventil 3 einen Druckausgleichsraum 17 auf. Bei den in den Abbildungen Figur 1 und 2 dargestellten Ausführungsformen ist der Druckausgleichsraum 17 dadurch ausgebildet, daß die Steuerventile 3 einen mit Bereichen unterschiedlichen Durchmessers versehenen Stufenkolben 18 aufweisen.To enable the opening of the nozzle body 6 only against the biasing force of the spring 16 takes place and not also against the pressure prevailing in the control chamber 15 simultaneously with the opening of the control valve 3 and thus the Introduction of the rail pressure into the nozzle pressure chamber 5 the pressure dismantled in the control room 15. For this purpose the control valve 3 a pressure compensation chamber 17. In the case of the figures Figures 1 and 2 are illustrated embodiments the pressure compensation chamber 17 is formed in that the control valves 3 one with areas of different diameters provided step piston 18.

Bei der in Figur 1 dargestellten ersten Ausführungsform erfolgt das Öffnen und Schließen der Düsennadel 7 wie folgt:In the first embodiment shown in Figure 1 takes place opening and closing the nozzle needle 7 as follows:

Sobald das Steuerventil 3 öffnet, gelangt Kraftstoff unter Raildruck über die Ringkammer 14 und die Leitung 4 in die Düsendruckkammer 5, wo der Raildruck auf den Düsenkörper 6 wirkt. Da der Durchmesser des D1 des Stufenkolbens 18 größer ist als der Durchmesser D2 des Stufenkolbens 18 entspannt sich mit dem Öffnen des Steuerventils 3 gleichzeitig der Druck im Steuerraum 15 sowie einer Kammer 19 des Steuerventils 3, so daß dem Öffnen der Düsennadel 7 ausschließlich die Vorspannkraft der im Steuerraum 15 angeordneten Feder 16 entgegenwirkt.As soon as the control valve 3 opens, fuel passes under rail pressure via the annular chamber 14 and the line 4 into the nozzle pressure chamber 5, where the rail pressure acts on the nozzle body 6. Since the diameter of the D 1 of the stepped piston 18 is larger than the diameter D 2 of the stepped piston 18, the pressure in the control chamber 15 and a chamber 19 of the control valve 3 simultaneously relax with the opening of the control valve 3, so that the opening of the nozzle needle 7 is exclusively the Pre-tensioning force of the spring 16 arranged in the control chamber 15 counteracts.

Das Schließen des Steuerventils 3 erfolgt durch Absteuern des Aktors, wodurch das Steuerventil 3 unter der Vorspannkraft der Feder 10 schließt. Die Verschiebung des Stufenkolbens 18 bewirkt dabei einen Druckaufbau in der Kammer 19 sowie im Steuerraum 15. Da gleichzeitig mit dem Schließen des Steuerventils 3 der Raildruck in der Düsendruckkammer 5 zusammenbricht, schließt die Düsennadel 7 unter Wirkung der auf den Düsenkörper 6 wirkenden Vorspannkraft der Feder 10 sowie des Drucks im Steuerraum 15. Der Druckaufbau in der Kammer 19 sowie im Steuerraum 15 wird zusätzlich über ein Ventil 20 geregelt.The control valve 3 is closed by deactivating the Actuator, which causes the control valve 3 under the biasing force the spring 10 closes. The displacement of the step piston 18 causes a pressure build-up in the chamber 19 and in Control room 15. Since simultaneously with the closing of the control valve 3 the rail pressure in the nozzle pressure chamber 5 collapses, closes the nozzle needle 7 under the effect of the Nozzle body 6 acting biasing force of the spring 10 and the Pressure in the control room 15. The pressure build-up in the chamber 19 and in the control room 15 is additionally regulated by a valve 20.

Diese Ausgestaltung stellt somit sicher, daß das Schließen der Düsennadel 7 unter Mitwirkung des zusätzlichen Drucks im Steuerraum 15 schnell und ohne Verzögerung erfolgt, während beim Öffnen der Düsennadel 7 der Druck im Steuerraum 15 abgebaut wird, so daß das Öffnen nur gegen die Vorspannkraft der Feder 10 erfolgt. Die kurzen Schaltzeiten sowie der Umstand, daß der Druck in der Kammer 19 sowie im Steuerraum 15 nicht permanent anliegt sorgen dafür, daß Dauerleckagen nicht auftreten und Schaltleckagen weitestgehend minimiert werden.This configuration thus ensures that the closing the nozzle needle 7 with the participation of the additional pressure in Control room 15 is done quickly and without delay while when the nozzle needle 7 is opened, the pressure in the control chamber 15 is reduced is, so that the opening only against the biasing force of the Spring 10 takes place. The short switching times and the fact that the pressure in chamber 19 and in control room 15 is not permanent contact ensures that permanent leakage does not occur and switching leaks are minimized as far as possible.

Bei der in Figur 2 dargestellten zweiten Ausführungsform erfolgt das Öffnen und Schließen der Düsennadel 7 wie folgt:In the second embodiment shown in Figure 2 takes place opening and closing the nozzle needle 7 as follows:

Sobald das Steuerventil 3 öffnet, gelangt Kraftstoff unter Raildruck über die Ringkammer 14 und die Leitung 4 in die Düsendruckkammer 5, wo der Raildruck auf den Düsenkörper 6 wirkt. Wie aus Figur 2 ersichtlich, ist bei diesem Ausführungsbeispiel der Stufenkolben 18 zweiteilig ausgebildet. Sobald Kraftstoff mit Raildruck in die Leitung 4 strömt, strömt gleichzeitig Kraftstoff mit Raildruck über eine Bohrung 21 zum zweiten Teil des Stufenkolbens 18 und verlagert diesen entgegen der Vorspannkraft einer zusätzlichen Feder 22. Da der Durchmesser des D1 des Stufenkolbens 18 größer ist als der Durchmesser D2 des Stufenkolbens 18 entspannt sich mit dem Öffnen des Steuerventils 3 gleichzeitig der Druck im Steuerraum 15 sowie in der Kammer 19 des Steuerventils 3, so daß dem Öffnen der Düsennadel 7 ausschließlich die Vorspannkraft der im Steuerraum 15 angeordneten Feder 16 entgegenwirkt.As soon as the control valve 3 opens, fuel passes under rail pressure via the annular chamber 14 and the line 4 into the nozzle pressure chamber 5, where the rail pressure acts on the nozzle body 6. As can be seen from FIG. 2, the stepped piston 18 is formed in two parts in this exemplary embodiment. As soon as fuel with rail pressure flows into line 4, fuel with rail pressure simultaneously flows via a bore 21 to the second part of the stepped piston 18 and displaces it against the biasing force of an additional spring 22. Since the diameter of the D 1 of the stepped piston 18 is larger than the diameter D 2 of the stepped piston 18 relaxes with the opening of the control valve 3, the pressure in the control chamber 15 and in the chamber 19 of the control valve 3, so that the opening of the nozzle needle 7 only counteracts the biasing force of the spring 16 arranged in the control chamber 15.

Das Schließen des Steuerventils 3 erfolgt durch Absteuern des Aktors, wodurch das Steuerventil 3 unter der Vorspannkraft der Feder 10 schließt. Die Verschiebung des Stufenkolbens 18 bewirkt dabei einen Druckaufbau in der Kammer 19 sowie im Steuerraum 15, da gleichzeitig mit dem Schließen des Steuerventils 3 der Raildruck in der Düsendruckkammer 5 sowie über die Bohrung 21 auf den Stufenkolben 18 zusammenbricht. Die Düsennadel 7 schließ somit unter Wirkung der auf den Düsenkörper 6 wirkenden Vorspannkraft der Feder 10 sowie des Drucks im Steuerraum 15.The control valve 3 is closed by deactivating the Actuator, which causes the control valve 3 under the biasing force the spring 10 closes. The displacement of the step piston 18 causes a pressure build-up in the chamber 19 and in Control room 15, since the control valve closes at the same time 3 the rail pressure in the nozzle pressure chamber 5 and above the bore 21 on the stepped piston 18 collapses. The Nozzle needle 7 thus closes under the effect on the nozzle body 6 acting biasing force of the spring 10 and the Pressure in the control room 15.

Auch diese Ausgestaltung stellt somit sicher, daß das Schließen der Düsennadel 7 unter Mitwirkung des zusätzlichen Drucks im Steuerraum 15 schnell und ohne Verzögerung erfolgt, während beim Öffnen der Düsennadel 7 der Druck im Steuerraum 15 abgebaut wird, so daß das Öffnen nur gegen die Vorspannkraft der Feder 10 erfolgt. Die kurzen Schaltzeiten sowie der Umstand, daß der Druck in der Kammer 19 sowie im Steuerraum 15 nicht permanent anliegt sorgen dafür, daß Dauerleckagen nicht auftreten und Schaltleckagen weitestgehend minimiert werden.This configuration also ensures that the closing the nozzle needle 7 with the participation of the additional pressure in the control room 15 takes place quickly and without delay When opening the nozzle needle 7, the pressure in the control room 15 is broken down so that the opening only against the biasing force the spring 10 takes place. The short switching times and the fact that the pressure in the chamber 19 and in the control room 15th not permanently present ensure that permanent leakage does not occur occur and switching leaks are minimized as far as possible.

Claims (6)

  1. Injection valve for injecting fuel into an internal combustion engine, having a control valve (3) for controlling fuel injection and having a control space (15) in which there is disposed an axially displaceable nozzle body (6) preloaded via a spring (10) and operatively connected to a valve needle (7) which, as the nozzle body (6) is displaced, frees or blocks injection bores (8), the pressure in the control space (15) being influenceable via the control valve (3),
    wherein the control valve (3) and the control space (15) are interlinked in such a way that closing of the control valve (3) causes the pressure in the control space (15) to increase and opening of the control valve (3) causes the pressure in the control space (15) to fall,
    characterised in that, when the control valve (3) is open, the control valve (3) has at least one pressure equalising chamber (17) to reduce the pressure in the control space (15).
  2. Injection valve according to Claim 1,
    characterised in that the control valve (3) has a differential spool (18) provided with regions of different diameter for forming the pressure equalisation chamber (17).
  3. Injection valve according to Claim 2,
    characterised in that the differential spool (18) of the control valve (3) is of multi-section design.
  4. Injection valve for injecting fuel into an internal combustion engine, having a control valve (3) for controlling fuel injection and having a control space (15) in which there is disposed an axially displaceable nozzle body (6) preloaded via a spring (10) and operatively connected to a valve needle (7) which, as the nozzle body (6) is displaced, frees or blocks injection bores (8), the pressure in the control space (15) being influenceable via the control valve (3), wherein the control valve (3) and the control space (15) are interlinked in such a way that closing of the control valve (3) causes the pressure in the control space (15) to increase and opening of the control valve (3) causes the pressure in the control space (15) to fall,
    characterised in that, when the control valve (3) is open, the control valve (3) is connected via a bore (21) to a differential spool (18) to reduce the pressure in the control space (15).
  5. Injection valve according to Claim 4, characterised in that the differential spool (18) is formed of two sections.
  6. Injection valve according to Claim 5, characterised in that the bore (21) is connected to the second section of the differential spool (18).
EP01971616A 2000-08-28 2001-08-16 Injection valve for the injection of fuel in an internal combustion engine and method for control of the opening and closing process of a nozzle needle in an injection valve Expired - Lifetime EP1313945B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10042231A DE10042231B4 (en) 2000-08-28 2000-08-28 Injection valve for injecting fuel into an internal combustion engine and method for controlling the opening and closing process of a nozzle needle of an injection valve
DE10042231 2000-08-28
PCT/DE2001/003122 WO2002018779A1 (en) 2000-08-28 2001-08-16 Injection valve for the injection of fuel in an internal combustion engine and method for control of the opening and closing process of a nozzle needle in an injection valve

Publications (2)

Publication Number Publication Date
EP1313945A1 EP1313945A1 (en) 2003-05-28
EP1313945B1 true EP1313945B1 (en) 2004-10-27

Family

ID=7654062

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Application Number Title Priority Date Filing Date
EP01971616A Expired - Lifetime EP1313945B1 (en) 2000-08-28 2001-08-16 Injection valve for the injection of fuel in an internal combustion engine and method for control of the opening and closing process of a nozzle needle in an injection valve

Country Status (3)

Country Link
EP (1) EP1313945B1 (en)
DE (2) DE10042231B4 (en)
WO (1) WO2002018779A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10326044A1 (en) * 2003-06-10 2004-12-30 Robert Bosch Gmbh Injection nozzle for internal combustion engines

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2558790A1 (en) * 1975-12-24 1977-07-14 Bosch Gmbh Robert FUEL INJECTION NOZZLE FOR COMBUSTION MACHINES
US5299919A (en) * 1991-11-01 1994-04-05 Paul Marius A Fuel injector system
US5397055A (en) * 1991-11-01 1995-03-14 Paul; Marius A. Fuel injector system
AT1626U1 (en) * 1995-04-05 1997-08-25 Avl Verbrennungskraft Messtech STORAGE INJECTION SYSTEM FOR INTERNAL COMBUSTION ENGINES
DE19519192C1 (en) * 1995-05-24 1996-06-05 Siemens Ag Injector
DE19519191C2 (en) * 1995-05-24 1997-04-10 Siemens Ag Injector
DE19734354A1 (en) * 1997-08-08 1999-02-11 Mtu Friedrichshafen Gmbh Internal combustion engine fuel injection system
DE19748999C2 (en) * 1997-11-06 2002-11-07 Daimler Chrysler Ag Solenoid valve controlled injector for a storage system of a multi-cylinder internal combustion engine
GB9905896D0 (en) * 1999-03-16 1999-05-05 Lucas Ind Plc Fuel injector arrangement
DE10033426B4 (en) * 2000-07-10 2004-10-14 Robert Bosch Gmbh Injector / nozzle needle combination with control room coupling

Also Published As

Publication number Publication date
DE10042231A1 (en) 2002-03-14
EP1313945A1 (en) 2003-05-28
DE10042231B4 (en) 2004-09-30
WO2002018779A1 (en) 2002-03-07
DE50104321D1 (en) 2004-12-02

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