EP2138709A1 - Directly actuated fuel injector - Google Patents
Directly actuated fuel injector Download PDFInfo
- Publication number
- EP2138709A1 EP2138709A1 EP09100250A EP09100250A EP2138709A1 EP 2138709 A1 EP2138709 A1 EP 2138709A1 EP 09100250 A EP09100250 A EP 09100250A EP 09100250 A EP09100250 A EP 09100250A EP 2138709 A1 EP2138709 A1 EP 2138709A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- pressure
- fuel injector
- fuel
- sleeve
- 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
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Classifications
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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
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
- F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
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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
- 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
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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
- 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
- DE 10 2006 050 810 refers to a fuel injector for internal combustion engines with a control room connected to a high-pressure side. About the pressure and the change in pressure, the movement of a nozzle needle is controlled.
- a control valve locks or opens the connection of the control chamber to a low pressure side.
- the control valve comprises a fixed valve pin which has an inner relief channel coming from the control chamber and opening into an annular groove of the valve pin. Further, a displaceably guided on the free end of the valve pin, force balanced control sleeve is provided which closes the annular groove in its closed valve position to the outside and opens in their direction towards the free end of the valve pin open valve position, the compound of the annular groove to the low pressure side.
- Fuel injectors of this type therefore inherently have a necessary for the realization of the needle stroke control flow and, where appropriate, a leakage volume flow, which leads to an increased required delivery capacity of the high-pressure pump.
- a delayed response of the injection valve member which can also be influenced by unintentionally occurring pressure fluctuations.
- a direct actuation of the usually needle-shaped injection valve member with an electromagnetic actuator has not been possible because the required force due to the non-pressure balanced formed injection valve member at system pressures of over 2000 bar resulted in too large a magnetic actuator.
- a concept of a fuel injector is proposed, with which the force required to open a needle-shaped injection valve member is lowered so far that the injection valve member can be lifted directly and directly via a magnetic actuator.
- the proposed injector concept is characterized by low applied forces for opening the injection valve member, so that a direct actuation of the same by means of an electromagnet is possible.
- the proposed solution according to the invention realizes a tax-free principle. There is no return of a controlled from a control room volume of fuel required, which on the one hand represents a reduced system overhead and on the other hand leads to smaller pump delivery in terms of high-pressure pumping unit through which the high-pressure accumulator chamber (common rail) is acted upon.
- the proposed solution according to the invention represents a very cost-effective solution, since a simple construction can be achieved.
- a control valve with associated inlet and outlet throttles can be omitted, as well as a push rod with respect to the injection valve member and any required leakage lines.
- the proposed solution according to the invention realizes a concept which requires little installation space.
- the magnetic armature cooperating with a magnetic actuator is designed as a valve sleeve.
- a spring presses the valve sleeve into the sealing seat, which is formed, for example, on a valve piece embedded in the injector body.
- the spring force is preset when mounting a shim, for example.
- the valve piece is pressed via the shim into the sealing seat, so that no leakage can occur on the sealing seat. Any leakage that may occur is led out through the guide of the valve sleeve via a return line. It is important to avoid leaking into the high pressure area.
- the leakage described here occurs between the guide the valve body and the valve sleeve in the return.
- the return flow flows due to the pressure conditions through a laterally mounted hole upwards in the direction of a return.
- the valve sleeve at the top of which the anchor plate is formed, is external, top and bottom of the system pressure, i. surrounded by the pressure prevailing in the high-pressure accumulator body. It is therefore pressure-balanced with respect to its axial movement and thus balanced with respect to the pressure prevailing in the high pressure reservoir body (common rail) system pressure.
- To open the valve sleeve only the spring force must be overcome by means of a magnetic actuator.
- the force required for opening is independent of the pressure prevailing in the high-pressure accumulator body system pressure (which is also referred to as rail pressure) and thus over the entire pressure range that occurs in the high-pressure accumulator body, constant.
- valve sleeve which also represents the armature, pulled by the magnetic actuator upwards.
- fuel now flows from the outside to the at least one injection port at the combustion chamber end of the fuel injector.
- the injection openings may be embodied, for example, at the combustion chamber end in the wall of the fuel injector.
- the energization of the magnetic actuator is interrupted.
- the valve sleeve is urged back down into its sealing seat on the valve member by the spring force acting on it so that supply of system pressurized fuel to the at least one injection port formed at the combustion chamber end of the fuel injector is discontinued.
- FIG. 1 is a longitudinal section through the inventively proposed fuel injector with directly actuated valve sleeve refer.
- a fuel injector 10 as shown in FIG. 1 comprises an injector body 12, which in the illustration according to FIG. 1 is guided symmetrically to a Injektorachse 14.
- a high pressure supply line 16 is under system pressure pending fuel.
- the pressure level is designated, which within a in the illustration according to FIG. 1 unplayed high-pressure accumulator body (common rail) prevails. This pressure level is in the illustration according to FIG. 1 indicated by p Rail .
- the fuel which is present at the high-pressure port 16 of the injector body 12, flows into the interior of the injector body 12 and supplies it with fuel.
- valve piece 20 Inside the injector body 12 is a valve piece 20 which is fixed to the combustion chamber end of the injector body 12 of the fuel injector 10.
- the valve piece 20 comprises a leakage bore 22 extending coaxially with the injector axis 14.
- the leakage bore 22 has no direct connection to the supply line 26 or 28.
- the fuel flows during the injection through the inlet bore 28 or the transverse bore 26.
- the leakage bore 22 is intended to remove leakage from the blind hole, which flows through the lower guide of the valve piece with the sleeve, and the leakage from the high-pressure region passes through the guide above the transverse bore 26 into the return line (FIG.
- valve piece 20 is installed with the aid of a dial 40 in the injector 12 and forms at the combustion chamber end a seal 32, below which extends a blind hole configured cavity. From this extend, as shown in the illustration FIG. 1 reproduced, at least two injection openings 30, via which fuel in the in FIG. 1 not shown combustion chamber of an internal combustion engine can be injected.
- a further dial 46 is added below the dial 40.
- This further shim 46 serves to adjust the spring force of a closing spring 44.
- This closing spring 44 surrounds a magnetic actuator 38.
- the magnetic actuator 38 is received in the interior of the injector body 12 and surrounded by the fuel under system pressure p rail .
- the solenoid actuator 38 further encloses the valve member 20 which extends coaxially with the injector axis 14 through the injector body 12 of the fuel injector 10.
- the magnetic actuator 38 acts on an armature plate 36, which is formed on the upper plan side of the axially movable in the injector body 12 valve sleeve 42.
- the valve sleeve 42 is also enclosed on the inside of the injector body 12 by the system pressure fuel on all sides, i. pressure-balanced.
- the adjusting washer 40, the further adjusting washer 46 for adjusting the force acting on the closing spring 44 are supported by an adjusting sleeve 48 which is arranged in the interior of the injector body 12, the valve sleeve 42 enclosing.
- valve sleeve 42 which surrounds the valve member 20 forms at the lower end a sealing seat 24, which is formed for example as a conical seat. From the illustration according to FIG. 1 shows that even at the sealing seat 24, the in FIG. 1 is shown closed, standing under high pressure fuel from the outside.
- the blind hole 34 is acted upon only via the concentric, ie coaxially to the injector 14 extending inlet bore 28 under system pressure p rail standing fuel.
- the solenoid actuator 38 applies only the force required to actuate the pressure balanced valve sleeve 42.
- the magnet armature 38 When the magnet armature 38 is energized, it pulls the armature plate 36 of the valve sleeve 42 against the force of the closing spring 44. Accordingly, the magnetic actuator 38 has only the closing force, ie the spring force which applies the closing spring 44, to overcome and can be designed accordingly.
- the inventively proposed, directly operated fuel injector 10 is also constructed much simpler compared to previously known from the prior art fuel injectors whose operation is done indirectly via the pressure relief or pressurization of a control room.
- the inventively proposed fuel injector 10 realizes a tax-free fuel injector, in which no return of a controlled from a control room volume in the direction of the low pressure region is required. This requires a reduced compared to previous solutions system overhead and a smaller dimensioning capacity of a delivery unit.
- drain and inlet throttle can be omitted, as well as the control chamber and the push rod, which was previously used in generally needle-shaped injection valve members.
- the inventively proposed fuel injector 10 is characterized by a shorter overall length compared to known from the prior art fuel injectors.
- the representation according to FIG. 2 is to refer to the connection of the leakage hole 22 in an enlarged scale.
- FIG. 2 puts the in FIG. 1 Circled area on an enlarged scale.
- the return flow flows due to suitable pressure conditions and possibly to generate a negative pressure in the leakage bore 22 by the in FIG. 2 illustrated transverse holes upwards in the direction of the return.
- the return flow occurs as soon as a leakage pressure p leakage as a function of the system pressure p rail plus a combustion chamber pressure p cylinder is greater than the pressure prevailing in the return pressure level p RL .
- valve sleeve 42 is surrounded outside on its lateral surface at the top and at the bottom of system pressure p rail . This means that the valve sleeve 42 is pressure-balanced with respect to its axial movement and is force-balanced with respect to the system pressure p Rail .
- the spring force which is applied by the closing spring 44, must be overcome by means of the magnet armature 38.
- the required magnetic force is independent of the system pressure p rail and thus constant over the entire pressure range of the system pressure p rail .
- this or its armature plate 36 is attracted by the magnetic actuator 38 upwards.
- the fuel which is present at the valve seat 42 under system pressure p rail flows via the open valve seat 24 in the direction of the blind hole 34 and from there to the injection openings 30.
- the energization of the magnetic actuator 38 is interrupted and the force-balanced valve sleeve 42 is pressed by the action of the spring force of the closing spring 44 back down into the valve seat 24.
- the pressurization of the blind hole-like cavity 34 is interrupted at the combustion chamber end of the injector body 12 of the fuel injector 10 and the injection is completed.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Bei heute verfügbaren, magnetisch betätigten Kraftstoffinjektoren, insbesondere für selbstzündende Verbrennungskraftmaschinen, die über Hochdruckspeichersysteme (Common-Rail) mit Kraftstoff versorgt werden, erfolgt die Betätigung eines nadelförmig ausgebildeten Einspritzventilgliedes indirekt, indem eine Druckabsenkung in einem Steuerraum erfolgt. Die Differenz zwischen dem Systemdruck, d.h. dem Druckniveau, welches im Hochdruckspeicherkörper herrscht, und dem im Steuerraum jeweils herrschenden Druck bewirkt in Verbindung mit dem Größenverhältnis der druckbeaufschlagten Flächen die Bewegung des in der Regel nadelförmig ausgebildeten Einspritzventilgliedes. Dieses Prinzip kommt zum Beispiel bei heute eingesetzten Kraftstoffinjektoren zum Einsatz. Von Nachteil bei diesen Injektorkonzepten ist die Notwendigkeit, die aus dem Steuerraum jeweils abgesteuerte Steuermenge in einen Niederdruckkraftstoffrücklauf abführen zu müssen. Kraftstoffinjektoren dieser Bauart besitzen daher prinzipbedingt einen zur Realisierung des Nadelhubs erforderlichen Steuervolumenstrom sowie gegebenenfalls einen Leckagevolumenstrom, was zu einer erhöhten erforderlichen Förderleistung der Hochdruckpumpe führt. Außerdem erfolgt aus der indirekten Steuerung des in der Regel nadelförmig ausgebildeten Einspritzventilgliedes ein verspätetes Ansprechverhalten des Einspritzventilgliedes, welches auch zusätzlich durch ungewollt auftretende Druckschwankungen beeinflusst werden kann.In today available, magnetically actuated fuel injectors, especially for self-igniting internal combustion engines, which are supplied via high-pressure storage systems (common rail) with fuel, the actuation of a needle-shaped injection valve member takes place indirectly by a pressure reduction takes place in a control room. The difference between the system pressure, ie the pressure level which prevails in the high-pressure accumulator body, and the prevailing pressure in the control chamber in conjunction with the size ratio of the pressurized surfaces causes the movement of the usually needle-shaped injection valve member. This principle is used, for example, in fuel injectors used today. A disadvantage of these Injektorkonzepten is the need to dissipate each of the control room diverted control amount in a low-pressure fuel return. Fuel injectors of this type therefore inherently have a necessary for the realization of the needle stroke control flow and, where appropriate, a leakage volume flow, which leads to an increased required delivery capacity of the high-pressure pump. In addition, from the indirect control of the usually needle-shaped injection valve member a delayed response of the injection valve member, which can also be influenced by unintentionally occurring pressure fluctuations.
Eine direkte Betätigung des in der Regel nadelförmig ausgebildeten Einspritzventilgliedes mit einem elektromagnetischen Aktor ist bisher nicht möglich, da die hierzu erforderliche Kraft aufgrund des nicht druckausgeglichenen ausgebildeten Einspritzventilgliedes bei Systemdrücken von über 2000 bar zu einem zu großen Magnetaktor führte.A direct actuation of the usually needle-shaped injection valve member with an electromagnetic actuator has not been possible because the required force due to the non-pressure balanced formed injection valve member at system pressures of over 2000 bar resulted in too large a magnetic actuator.
Erfindungsgemäß wird eine Konzeption eines Kraftstoffinjektors vorgeschlagen, mit der die zum Öffnen eines nadelförmig ausgebildeten Einspritzventilgliedes erforderliche Kraft so weit herabgesenkt ist, dass das Einspritzventilglied direkt und unmittelbar über einen Magnetaktor angehoben werden kann. Das vorgeschlagene Injektorkonzept zeichnet sich durch geringe aufzubringende Kräfte zum Öffnen des Einspritzventilgliedes aus, so dass eine direkte Betätigung desselben mittels eines Elektromagneten möglich ist. Die erfindungsgemäß vorgeschlagene Lösung verwirklicht ein steuermengenfreies Prinzip. Es ist keine Rückführung eines aus einem Steuerraum abgesteuerten Kraftstoffvolumens erforderlich, was einerseits einen verringerten Systemaufwand darstellt und andererseits zu kleineren Pumpenförderleistungen im Hinblick auf das Hochdruckförderaggregat führt, durch welches der Hochdruckspeicherraum (Common-Rail) beaufschlagt ist.According to the invention, a concept of a fuel injector is proposed, with which the force required to open a needle-shaped injection valve member is lowered so far that the injection valve member can be lifted directly and directly via a magnetic actuator. The proposed injector concept is characterized by low applied forces for opening the injection valve member, so that a direct actuation of the same by means of an electromagnet is possible. The proposed solution according to the invention realizes a tax-free principle. There is no return of a controlled from a control room volume of fuel required, which on the one hand represents a reduced system overhead and on the other hand leads to smaller pump delivery in terms of high-pressure pumping unit through which the high-pressure accumulator chamber (common rail) is acted upon.
Des Weiteren stellt die erfindungsgemäß vorgeschlagene Lösung eine sehr kostengünstige Lösung dar, da ein einfacher Aufbau erreicht werden kann. Ein Steuerventil mit dazugehörigen Zulauf- und Ablaufdrosseln kann entfallen, ebenso wie eine Druckstange in Bezug auf das Einspritzventilglied sowie eventuell erforderliche Leckageleitungen. Schließlich verwirklicht die erfindungsgemäß vorgeschlagene Lösung ein Konzept, welches geringen Bauraum beansprucht.Furthermore, the proposed solution according to the invention represents a very cost-effective solution, since a simple construction can be achieved. A control valve with associated inlet and outlet throttles can be omitted, as well as a push rod with respect to the injection valve member and any required leakage lines. Finally, the proposed solution according to the invention realizes a concept which requires little installation space.
Der erfindungsgemäß vorgeschlagenen Lösung folgend, ist der mit einem Magnetaktor zusammenwirkende Magnetanker als Ventilhülse ausgeführt. Im geschlossenen Zustand drückt eine Feder die Ventilhülse in den Dichtsitz, der zum Beispiel an einem in den Injektorkörper eingelassenen Ventilstück ausgebildet ist. Die Federkraft wird bei der Montage einer Einstellscheibe, um ein Beispiel zu nennen, voreingestellt. Das Ventilstück wird über die Einstellscheibe in den Dichtsitz eingepresst, derart, dass keine Leckage am Dichtsitz auftreten kann. Eine möglicherweise auftretende Leckage wird durch die Führung der Ventilhülse über eine Rücklaufleitung herausgeführt. Es ist unbedingt zu vermeiden, dass Leckage in den Hochdruckbereich gelangt. Die hier beschriebene Leckage tritt durch die Führung zwischen dem Ventilkörper und der Ventilhülse in den Rücklauf. Die Rücklaufmenge fließt aufgrund der Druckverhältnisse durch eine seitlich angebrachte Bohrung nach oben in Richtung eines Rücklaufes.Following the solution proposed by the invention, the magnetic armature cooperating with a magnetic actuator is designed as a valve sleeve. In the closed state, a spring presses the valve sleeve into the sealing seat, which is formed, for example, on a valve piece embedded in the injector body. The spring force is preset when mounting a shim, for example. The valve piece is pressed via the shim into the sealing seat, so that no leakage can occur on the sealing seat. Any leakage that may occur is led out through the guide of the valve sleeve via a return line. It is important to avoid leaking into the high pressure area. The leakage described here occurs between the guide the valve body and the valve sleeve in the return. The return flow flows due to the pressure conditions through a laterally mounted hole upwards in the direction of a return.
Die Ventilhülse, an deren Oberseite die Ankerplatte ausgebildet ist, ist außen, oben und unten vom Systemdruck, d.h. dem im Hochdruckspeicherkörper herrschenden Druck, umgeben. Sie ist daher im Hinblick auf ihre axiale Bewegung druckausgeglichen und damit bezüglich des im Hochdruckspeicherkörper (Common-Rail) herrschenden Systemdrucks kraftausgeglichen. Zum Öffnen der Ventilhülse muss lediglich die Federkraft mittels eines Magnetaktors überwunden werden. Die zum Öffnen benötigte Kraft ist unabhängig vom im Hochdruckspeicherkörper herrschenden Systemdruck (der auch als Raildruck bezeichnet wird) und damit über den gesamten Druckbereich, der im Hochdruckspeicherkörper auftritt, konstant. Zum Öffnen der Einspritzöffnungen am brennraumseitigen Ende des erfindungsgemäß vorgeschlagenen Kraftstoffinjektors wird die Ventilhülse, die gleichzeitig den Magnetanker darstellt, durch den Magnetaktor nach oben gezogen. Unter Systemdruck stehender Kraftstoff fließt nun von außen zu der mindestens einen Einspritzöffnung am brennraumseitigen Ende des Kraftstoffinjektors. Die Einspritzöffnungen können zum Beispiel am brennraumseitigen Ende in der Wand des Kraftstoffinjektors ausgeführt sein.The valve sleeve, at the top of which the anchor plate is formed, is external, top and bottom of the system pressure, i. surrounded by the pressure prevailing in the high-pressure accumulator body. It is therefore pressure-balanced with respect to its axial movement and thus balanced with respect to the pressure prevailing in the high pressure reservoir body (common rail) system pressure. To open the valve sleeve, only the spring force must be overcome by means of a magnetic actuator. The force required for opening is independent of the pressure prevailing in the high-pressure accumulator body system pressure (which is also referred to as rail pressure) and thus over the entire pressure range that occurs in the high-pressure accumulator body, constant. To open the injection openings at the combustion chamber end of the inventively proposed fuel injector, the valve sleeve, which also represents the armature, pulled by the magnetic actuator upwards. Under system pressure fuel now flows from the outside to the at least one injection port at the combustion chamber end of the fuel injector. The injection openings may be embodied, for example, at the combustion chamber end in the wall of the fuel injector.
Zum Schließen des Ventilstückes und zum Beenden der Einspritzung von Kraftstoff in den Brennraum der Verbrennungskraftmaschine wird die Bestromung des Magnetaktors unterbrochen. Die Ventilhülse wird durch die auf sie wirkende Federkraft wieder nach unten in ihren Dichtsitz am Ventilstück gedrückt, so dass die Zufuhr von unter Systemdruck stehendem Kraftstoff zu der mindestens einen am brennraumseitigen Ende des Kraftstoffinjektors ausgeführten Einspritzöffnung unterbrochen wird.To close the valve piece and to terminate the injection of fuel into the combustion chamber of the internal combustion engine, the energization of the magnetic actuator is interrupted. The valve sleeve is urged back down into its sealing seat on the valve member by the spring force acting on it so that supply of system pressurized fuel to the at least one injection port formed at the combustion chamber end of the fuel injector is discontinued.
Anhand der Zeichnungen wird die Erfindung nachstehend eingehender beschrieben.With reference to the drawings, the invention will be described in more detail below.
Es zeigt:
- Figur 1
- einen Schnitt durch den erfindungsgemäß vorgeschlagenen Kraftstoffinjektor mit direkt betätigter Ventilhülse und
- Figur 2
- eine Darstellung der Anbindung einer Leckagebohrung am Ventilstück.
- FIG. 1
- a section through the inventively proposed fuel injector with directly actuated valve sleeve and
- FIG. 2
- a representation of the connection of a leakage hole on the valve piece.
Der Darstellung gemäß
Ein Kraftstoffinjektor 10 gemäß der Darstellung in
Im Inneren des Injektorkörpers 12 befindet sich ein Ventilstück 20, welches am brennraumseitigen Ende des Injektorkörpers 12 des Kraftstoffinjektors 10 fixiert ist. Das Ventilstück 20 umfasst eine sich koaxial zur Injektorachse 14 erstreckende Leckagebohrung 22. Die Leckagebohrung 22 hat keine direkte Verbindung zu der Versorgungsleitung 26 bzw. 28. Durch die Zulaufbohrung 28 bzw. die Querbohrung 26 fließt der Kraftstoff während der Einspritzung. Die Leckagebohrung 22 soll Leckage aus dem Sackloch, die durch die untere Führung des Ventilstücks mit der Hülse strömt, und die Leckage aus dem Hochdruckbereich durch die Führung oberhalb der Querbohrung 26 in den Rücklauf gelangt, abführen (??). Das Ventilstück 20 ist mit Hilfe einer Einstellscheibe 40 im Injektorkörper 12 verbaut und bildet am brennraumseitigen Ende eine Abdichtung 32, unterhalb der sich ein sacklochförmig konfigurierter Hohlraum erstreckt. Von diesem erstrecken sich, wie in der Darstellung gemäß
Aus der Schnittdarstellung gemäß
Der Magnetaktor 38 wirkt auf eine Ankerplatte 36, die an der oberen Planseite der axial im Injektorkörper 12 beweglichen Ventilhülse 42 ausgebildet ist. Auch die Ventilhülse 42 ist im Inneren des Injektorkörpers 12 von dem unter Systemdruck stehenden Kraftstoff allseits umschlossen, d.h. druckausgeglichen.The
Die Einstellscheibe 40, die weitere Einstellscheibe 46 zur Einstellung der auf die Schließfeder 44 wirkenden Kraft sind von einer Einstellhülse 48 abgestützt, die in das Innere des Injektorkörpers 12, die Ventilhülse 42 umschließend, angeordnet ist.The adjusting
Wie aus der Schnittdarstellung gemäß
Bei einer Bestromung des Magnetaktors 38 bewegt sich die Ankerplatte 36, die an der Ventilhülse 42 aufgenommen ist, entgegen der Wirkung der Schließfeder 44 nach oben. Dadurch wird der Dichtsitz 24 oberhalb des verbreiterten Bereiches des Ventilstücks 20 geöffnet, so dass von der Außenseite in Bezug auf den Dichtsitz 24 gesehen, unter Systemdruck PRail stehender Kraftstoff 18 über die Querbohrung 26 in die Zulaufbohrung 28 innerhalb des Ventilstücks 20 in das Sackloch 34 einströmt. Der im Sackloch 34 unter Systemdruck stehende Kraftstoff wird dann über die in
Das Sackloch 34 wird nur über die zentrisch, d.h. koaxial zur Injektorachse 14 verlaufende Zulaufbohrung 28 mit unter Systemdruck pRail stehendem Kraftstoff beaufschlagt. Die Außenseite, d.h. die Innenseite des Ventilkörpers 12 und die Außenseite des Ventilstücks 20, bilden die Abdichtung 32, so dass das Sackloch 34 am brennraumseitigen Ende des Injektorkörpers 12 des Kraftstoffinjektors 10 gegen den unter Systemdruck stehenden Kraftstoff abgedichtet ist.The
Bei dem im Längsschnitt gemäß
Der erfindungsgemäß vorgeschlagene, direkt betätigte Kraftstoffinjektor 10 ist darüber hinaus wesentlich einfacher aufgebaut im Vergleich zu bisher aus dem Stand der Technik bekannten Kraftstoffinjektoren, deren Betätigung indirekt über die Druckentlastung bzw. Druckbeaufschlagung eines Steuerraums erfolgt. Der erfindungsgemäß vorgeschlagene Kraftstoffinjektor 10 verwirklicht einen steuermengenfreien Kraftstoffinjektor, bei dem keine Rückführung eines aus einem Steuerraum abgesteuerten Volumens in Richtung des Niederdruckbereiches erforderlich ist. Dies bedingt einen im Vergleich zu bisherigen Lösungen verringerten Systemaufwand sowie eine kleiner zu dimensionierende Förderleistung eines Förderaggregates. Des Weiteren können Ablauf- und Zulaufdrossel entfallen, ebenso wie der Steuerraum sowie die Druckstange, die bei im Allgemeinen nadelförmig ausgebildeten Einspritzventilgliedern bisher eingesetzt wurde. Der erfindungsgemäß vorgeschlagene Kraftstoffinjektor 10 zeichnet sich durch eine kürzere Baulänge aus im Vergleich zu aus dem Stand der Technik bekannten Kraftstoffinjektoren.The inventively proposed, directly operated
Aus dem Längsschnitt gemäß der Darstellung in
Der Darstellung gemäß
Die Darstellung gemäß
Wie den Darstellungen gemäß der
Zum Schließen der Kraftstoffzufuhr in den Brennraum der Verbrennungskraftmaschine wird die Bestromung des Magnetaktors 38 unterbrochen und die kraftausgeglichene Ventilhülse 42 durch die Wirkung der Federkraft der Schließfeder 44 wieder nach unten in den Ventilsitz 24 gedrückt. Damit ist die Druckbeaufschlagung des sacklochartigen Hohlraums 34 am brennraumseitigen Ende des Injektorkörpers 12 des Kraftstoffinjektors 10 unterbrochen und die Einspritzung beendet.To close the fuel supply in the combustion chamber of the internal combustion engine, the energization of the
Claims (10)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008002605A DE102008002605A1 (en) | 2008-06-24 | 2008-06-24 | Direct operated fuel injector |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2138709A1 true EP2138709A1 (en) | 2009-12-30 |
EP2138709B1 EP2138709B1 (en) | 2011-10-26 |
Family
ID=41202348
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09100250A Not-in-force EP2138709B1 (en) | 2008-06-24 | 2009-04-24 | Directly actuated fuel injector |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2138709B1 (en) |
AT (1) | ATE530760T1 (en) |
DE (1) | DE102008002605A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2395227A3 (en) * | 2010-06-14 | 2015-04-22 | Robert Bosch GmbH | Injection valve |
SE1951116A1 (en) * | 2019-10-01 | 2021-04-02 | Scania Cv Ab | Fuel injector arrangement, high pressure injection system comprising the injector arrangement, fuel system comprising the high pressure injection system, vehicle comprising the fuel system, and a meth |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5645226A (en) * | 1995-02-13 | 1997-07-08 | Siemens Automotive Corporation | Solenoid motion initiator |
DE19754112A1 (en) * | 1996-12-06 | 1998-06-10 | Hyundai Motor Co Ltd | Automotive fuel injection system for diesel engines |
DE10111293A1 (en) * | 2001-03-09 | 2002-09-19 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
DE102006050810A1 (en) | 2006-10-27 | 2008-04-30 | Robert Bosch Gmbh | Fuel injector for internal combustion engines, comprises control valve with stationary valve pin which has internal relief duct that extends from control chamber to annular groove of valve pin |
-
2008
- 2008-06-24 DE DE102008002605A patent/DE102008002605A1/en not_active Withdrawn
-
2009
- 2009-04-24 EP EP09100250A patent/EP2138709B1/en not_active Not-in-force
- 2009-04-24 AT AT09100250T patent/ATE530760T1/en active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5645226A (en) * | 1995-02-13 | 1997-07-08 | Siemens Automotive Corporation | Solenoid motion initiator |
DE19754112A1 (en) * | 1996-12-06 | 1998-06-10 | Hyundai Motor Co Ltd | Automotive fuel injection system for diesel engines |
DE10111293A1 (en) * | 2001-03-09 | 2002-09-19 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
DE102006050810A1 (en) | 2006-10-27 | 2008-04-30 | Robert Bosch Gmbh | Fuel injector for internal combustion engines, comprises control valve with stationary valve pin which has internal relief duct that extends from control chamber to annular groove of valve pin |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2395227A3 (en) * | 2010-06-14 | 2015-04-22 | Robert Bosch GmbH | Injection valve |
SE1951116A1 (en) * | 2019-10-01 | 2021-04-02 | Scania Cv Ab | Fuel injector arrangement, high pressure injection system comprising the injector arrangement, fuel system comprising the high pressure injection system, vehicle comprising the fuel system, and a meth |
SE545024C2 (en) * | 2019-10-01 | 2023-02-28 | Scania Cv Ab | Fuel injector arrangement for an internal combustion engine and method for operating said arrangement |
Also Published As
Publication number | Publication date |
---|---|
DE102008002605A1 (en) | 2009-12-31 |
ATE530760T1 (en) | 2011-11-15 |
EP2138709B1 (en) | 2011-10-26 |
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