EP2643581A1 - Fuel injector - Google Patents

Fuel injector

Info

Publication number
EP2643581A1
EP2643581A1 EP11788109.4A EP11788109A EP2643581A1 EP 2643581 A1 EP2643581 A1 EP 2643581A1 EP 11788109 A EP11788109 A EP 11788109A EP 2643581 A1 EP2643581 A1 EP 2643581A1
Authority
EP
European Patent Office
Prior art keywords
valve member
injection valve
hydraulic
fuel injector
stroke
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP11788109.4A
Other languages
German (de)
French (fr)
Other versions
EP2643581B1 (en
Inventor
Armin Schuelke
Olaf Ohlhafer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2643581A1 publication Critical patent/EP2643581A1/en
Application granted granted Critical
Publication of EP2643581B1 publication Critical patent/EP2643581B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0635—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding
    • F02M51/066—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding the armature and the valve being allowed to move relatively to each other or not being attached to each other
    • 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
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0635—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention relates to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine having the features of the preamble of claim 1.
  • the fuel injector comprises a magnetic actuator for direct control of a preferably needle-shaped injection valve member, via the stroke movement at least one injection port of the fuel injector is releasable or closable.
  • the control of an injection valve member of a fuel substance with an electromagnetic actuator as the actuating means is generally indirect.
  • the magnetic actuator comprises a solenoid valve, by means of which a control pressure acting on the injection valve member in a control chamber is variable, so that opening or closing of the injection valve member is effected with change of the control pressure.
  • the indirect control proves to be disadvantageous because the required to reduce the control pressure control amount must be fed to a return and then again promoted to high pressure.
  • indirectly actuated injection valve members have a delayed response as compared to directly actuated principles. In order to realize a direct control of the injection valve member but so far almost exclusively injector concepts are known which provide for the use of piezoelectric actuators.
  • DE 10 2006 015 745 A1 discloses a fuel injector with a directly controlled injection valve member and a magnetic actuator in the form of a solenoid valve.
  • a flow channel of a first control chamber can be opened or closed, which is acted upon by an inlet throttle system pressure.
  • the injector concept disclosed herein also requires the discharge of a certain amount of purge via a low-pressure end.
  • the object of the present invention is to provide a fuel injector with a solenoid actuator that allows direct control of the injection valve member and thus can be operated without backflow.
  • the proposed fuel injector should be simple and inexpensive to produce.
  • the proposed fuel injector has a magnetic actuator with a liftable anchor element for the direct control of a preferably needle-shaped injection valve member.
  • the injection valve member during a first phase of its opening stroke with a hydraulic translator mechanically coupled, which has a control volume limiting hydraulic active surface Ai, which in total with a formed on the injection valve member hydraulic active surface A 2 greater than a formed on the anchor element, the control volume limiting hydraulic Active surface A 3 is, so that due to the area ratio of the relevant in relation to the control volume hydraulic active surfaces Ai, A 2 and A 3, a force gain is effected.
  • the injection valve member is mechanically coupled during its closing stroke with the anchor element, the is acted upon in the closing direction of the injection valve member by an armature spring, so that the closing stroke of the injection valve member by means of the armature spring is effected.
  • a separate closing spring which acts on the injection valve member in the closing direction with a closing force, is thus unnecessary.
  • the elimination of a separate closing spring has the advantage of a reduced manufacturing and voting effort.
  • the control volume can be minimized, which has a favorable effect on the response of the input signal.
  • the force amplification makes it possible to realize a direct actuation of the injection valve member using a magnetic actuator. The control is therefore carried out without backflow.
  • the hydraulic effective area A 2 formed on the injection valve member is selected smaller than the hydraulic effective area A 3 formed on the anchor element.
  • the mechanical coupling of the injection stroke is canceled by the hydraulic booster, so that the area ratio of the hydraulic active surfaces relevant in relation to the control volume is now A 2 / A 3 1 amounts to.
  • a stop surface on the injection valve member is formed with the hydraulic booster for the mechanical coupling of the egg n p ritzve nti I. The stop surface causes the injection valve member to be entrained during a stroke movement of the hydraulic booster.
  • the lifting movement of the hydraulic booster is in turn realized by a lifting movement of the anchor element in the direction of the magnetic actuator and a concomitant lowering of the control pressure in the control volume. Since during this phase of the opening stroke of the injection stroke, the hydraulic active surfaces Ai and A 2 add up and in total are larger than the hydraulic active surface A 3 of the armature element, a force amplification is effected, by means of which the initial high closing force can be overcome.
  • a stop is formed on a housing part of the fuel injector.
  • the stop serves to unilaterally limit the stroke of the hydraulic translator. This means that the opening stroke of the hydraulic booster is limited in contrast to the opening stroke of the injection valve member.
  • the hydraulic booster rests against the stop of the housing part, so that not only the mechanical coupling of the hydraulic booster with the injection valve member but also the hydraulic coupling of the hydraulic booster with the anchor element is released. Only the hydraulic coupling of the injection valve member remains, so that over a surface ratio A 2 / A 3 ⁇ 1, a path gain can be effected.
  • the hydraulic booster is disc-shaped or piston-shaped and has a central bore in which the injection valve member is received.
  • the stop formed on the injection valve member may be formed, for example, as a radial shoulder in the region of an increase in diameter of the injection valve member.
  • the hydraulic booster, the injection valve member and the anchor member arranged coaxially, wherein the armature formed on the hydraulic active surface A 3 is the active surfaces Ai and A 2 opposite.
  • the hydraulic booster is acted upon by the pressure force of a spring, by means of which it is ensured that the hydraulic booster rests in the closed position of the injector against the stop of the injection valve member. Therefore, the spring has only to ensure that the hydraulic translator resumes its initial position after an injection process. As a result, a relatively soft spring can be used. At least the spring force is less than that of the armature spring chosen to effect the complete closing stroke of the injection valve member.
  • the illustrated fuel injector has a magnetic actuator 1 for actuating an injection valve member 2.
  • the injection valve member 2 is guided for releasing and closing at least one injection opening 3 in a liftable manner in a nozzle body 13.
  • the solenoid actuator 1 has a likewise liftable anchor element 4, which limits a control volume 5 with a hydraulic active surface A 3 in the axial direction.
  • the armature element 4 moves in the direction of the actuator and thus causes a pressure drop in the control volume 5.
  • control volume 5 further formed by a formed on a hydraulic translator 6 hydraulic effective area Ai and a formed on the injection valve member 2 hydraulic Impact surface A 2 is limited, there is a hydraulic coupling of this with the anchor element 4. That is, the hydraulic booster 6 and the injection valve member 2 follow the movement of the anchor member 4. Since the sum of the hydraulic effective areas A [and A 2 is greater than the area A 3 , an increase of the force is effected via the area ratio during this first phase of the opening stroke of the opening stroke of the electric drive. To ensure that both the hydraulic transmission 6 and the injection valve member 2 follow the movement of the armature element 4, the hydraulic booster 6 and the injection valve member 2 via a formed on the injection valve member 2 stop surface 8 are mechanically coupled.
  • a stop 10 is formed on a housing part 9. If the hydraulic booster 6 comes into abutment with the stopper 10, the mechanical coupling with the injection valve member 2 is released and the injection valve member 2 continues the movement alone.
  • the mechanical coupling takes place in the present case in a simple manner, namely by the injection valve member 2 is received in a central bore 11 of the hydraulic booster 6 and to form the stop surface 8 has a region with increased outer diameter, wherein the outer diameter greater than the inner diameter of the central bore 11 is selected is.
  • a spring 12 which applies a compressive force to the hydraulic translator 6 in the direction of the abutment surface 8, places the abutment of the hydraulic translator 6 against the abutment surface 8 during the first phase of the opening stroke of the eccentric injection valve 2 or in the closed position of the injector safely.
  • the energization of the magnetic actuator 1 is terminated.
  • An anchor element 4 in the closing direction with a pressure force acting anchor spring 7 ensures the return of the anchor element 4.
  • the return of the spring 10 is also effected via the pressure force of the armature spring 7.
  • the spring force of the armature spring 7 is therefore chosen to be relatively high. In any case, the spring force of the armature spring 7 is selected higher than the spring force of the spring 12, which acts on the hydraulic booster in the opening direction of the injection valve member 2.
  • a separate closing spring for returning the injection valve member 2 is dispensable, whereby the manufacturing and tuning effort is reduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

The invention relates to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine, comprising a magnetic actuator (1) for directly controlling a preferably needle-shaped injection valve member (2), by means of the stroke movement of which at least one injection opening (3) of the fuel injector can be released or closed. The magnetic actuator (1) comprises an armature element (4) that can carry out a stroke movement in order to control the control pressure in a control volume (5). According to the invention, the injection valve member (2) can be mechanically coupled to a hydraulic intensifier (6) during a first phase of the injection valve member opening stroke, said intensifier having a hydraulic active surface A1 which delimits the control volume (5) and which together with a hydraulic active surface A2 that is formed on the injection valve member (2) is larger than a hydraulic active surface A3 that is formed on the armature element (4) and delimits the control volume (5) so that a force amplification is caused on the basis of the surface area ratio of the hydraulic active surfaces A1, A2, and A3 that are relevant to the control volume (5). Furthermore, according to the invention the injection valve member (2) can be mechanically coupled to the armature element (4) during the injection valve member closing stroke, the pressing force of an armature spring (7) being applied to said armature element in the closing direction of the injection valve member (2) such that the closing stroke of the injection valve member (2) can be caused by means of the armature spring (7).

Description

Beschreibung  description
Titel title
Kraftstoffinjektor  fuel injector
Die Erfindung betrifft einen Kraftstoffinjektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine mit den Merkmalen des Oberbegriffs des Anspruchs 1. Der Kraftstoffinjektor umfasst einen Magnetaktor zur direkten Ansteuerung eines vorzugsweise nadeiförmigen Einspritzventilgliedes, über dessen Hubbewegung wenigstens eine Einspritzöffnung des Kraftstoffinjektors freigebbar oder verschließbar ist. The invention relates to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine having the features of the preamble of claim 1. The fuel injector comprises a magnetic actuator for direct control of a preferably needle-shaped injection valve member, via the stroke movement at least one injection port of the fuel injector is releasable or closable.
Stand der Technik State of the art
Die Ansteuerung eines Einspritzventilgliedes eines K raftstoff i nj e kto rs mit einem Magnetaktor als Betätigungsmittel erfolgt in der Regel indirekt. Hierzu umfasst der Magnetaktor ein Magnetventil, mittels dessen ein das Einspritzventilglied beaufschlagender Steuerdruck in einem Steuerraum veränderbar ist, so dass mit Veränderung des Steuerdrucks ein Öffnen oder Schließen des Einspritzventilgliedes bewirkt wird. Die indirekte Ansteuerung erweist sich jedoch als nachteilig, da die zur Absenkung des Steuerdrucks erforderliche Steuermenge einem Rücklauf zugeführt und danach erneut auf Hochdruck gefördert werden muss. Außerdem weisen indirekt angesteuerte Einspritzventilglieder gegenüber direkt angesteuerten prinzipbedingt ein verzögertes Ansprechverhalten auf. Um eine direkte Ansteuerung des Einspritzventilgliedes zu realisieren sind bislang jedoch fast ausschließlich Injektorkonzepte bekannt, die den Einsatz von Piezoaktoren vorsehen. Denn der Einsatz eines Magnetaktors würde bei Systemdrücken von über 2000 bar einen zu großen Magnetaktor erfordern, um die zum Öffnen des E i ns p ritzve nti I g I ied es notwendige Kraft zu realisieren. Darüber hinaus ist aus der DE 10 2006 015 745 AI ein Kraftstoffinjektor mit einem direktgesteuerten Einspritzventilglied und einem magnetischen Steller in Form eines Magnetventils bekannt. Über das Magnetventil kann ein Ablaufkanal eines ersten Steuerraumes geöffnet oder geschlossen werden, der über eine Zulaufdrossel mit Systemdruck beaufschlagt ist. Um die prinzipbedingten langen Öffnungs- und Schließzyklen in Bezug auf das Einspritzventilglied zu verkürzen, wird vorgeschlagen, das Magnetventil durch einen zusätzlichen Bypass, der den Ablaufkanal mit einem Hochdruck- anschluss verbindet, zu umgehen. Dennoch bedingt auch das hierin offenbarte Injektorkonzept das Abführen einer bestimmten Absteuermenge über einen niederdrucksei- tigen Ablauf. The control of an injection valve member of a fuel substance with an electromagnetic actuator as the actuating means is generally indirect. For this purpose, the magnetic actuator comprises a solenoid valve, by means of which a control pressure acting on the injection valve member in a control chamber is variable, so that opening or closing of the injection valve member is effected with change of the control pressure. However, the indirect control proves to be disadvantageous because the required to reduce the control pressure control amount must be fed to a return and then again promoted to high pressure. In addition, indirectly actuated injection valve members have a delayed response as compared to directly actuated principles. In order to realize a direct control of the injection valve member but so far almost exclusively injector concepts are known which provide for the use of piezoelectric actuators. The use of a magnetic actuator would require a magnet actuator that is too large at system pressures of more than 2000 bar in order to realize the necessary force to open the electrical contact. Furthermore, DE 10 2006 015 745 A1 discloses a fuel injector with a directly controlled injection valve member and a magnetic actuator in the form of a solenoid valve. About the solenoid valve, a flow channel of a first control chamber can be opened or closed, which is acted upon by an inlet throttle system pressure. In order to shorten the principle of long opening and closing cycles with respect to the injection valve member, it is proposed to bypass the solenoid valve by means of an additional bypass which connects the discharge channel to a high-pressure connection. Nevertheless, the injector concept disclosed herein also requires the discharge of a certain amount of purge via a low-pressure end.
Ausgehend von dem vorstehend genannten Stand der Technik besteht die Aufgabe der vorliegenden Erfindung darin, einen Kraftstoffinjektor mit einem Magnetaktor bereit zu stellen, der eine direkte Ansteuerung des Einspritzventilgliedes ermöglicht und somit rücklaufmengenfrei betrieben werden kann. Zugleich soll der vorgeschlagene Kraftstoffinjektor einfach und kostengünstig herstellbar sein. Based on the above-mentioned prior art, the object of the present invention is to provide a fuel injector with a solenoid actuator that allows direct control of the injection valve member and thus can be operated without backflow. At the same time, the proposed fuel injector should be simple and inexpensive to produce.
Die Aufgabe wird gelöst durch einen Kraftstoffinjektor mit den Merkmalen des Anspruchs 1. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben. The object is achieved by a fuel injector with the features of claim 1. Advantageous developments of the invention are specified in the subclaims.
Offenbarung der Erfindung Disclosure of the invention
Der vorgeschlagene Kraftstoffinjektor weist einen Magnetaktor mit einem hubbeweglichen Ankerelement zur direkten Ansteuerung eines vorzugsweise nadeiförmigen Einspritzventilgliedes auf. Erfindungsgemäß ist das Einspritzventilglied während einer ersten Phase seines Öffnungshubes mit einem hydraulischen Übersetzer mechanisch koppelbar, der eine ein Steuervolumen begrenzende hydraulische Wirkfläche Ai besitzt, welche in Summe mit einer am Einspritzventilglied ausgebildeten hydraulischen Wirkfläche A2 größer als eine am Ankerelement ausgebildete, das Steuervolumen begrenzende hydraulische Wirkfläche A3 ist, so dass aufgrund des Flächenverhältnisses der in Bezug auf das Steuervolumen relevanten hydraulischen Wirkflächen Ai, A2 und A3 eine Kraftverstärkung bewirkt wird. Ferner erfindungsgemäß ist das Einspritzventilglied während seines Schließhubes mit dem Ankerelement mechanisch koppelbar, das in Schließrichtung des Einspritzventilgliedes von einer Ankerfeder beaufschlagt wird, so dass der Schließhub des Einspritzventilgliedes mittels der Ankerfeder bewirkbar ist. Eine separate Schließfeder, welche das Einspritzventilglied in Schließrichtung mit einer Schließkraft beaufschlagt, ist somit entbehrlich. Der Entfall einer separaten Schließfeder weist den Vorteil eines verminderten Fertigungs- und Abstimmungsaufwands auf. Ferner kann das Steuervolumen minimiert werden, was sich günstig auf das Ansprechverhalten des E i ns p ritz ve nti I g I ied es auswirkt. Darüber hinaus ermöglicht die Kraftverstärkung während der ersten Phase des Öffnungshubes des Einspritzventilgliedes eine direkte Ansteuerung des Einspritzventilgliedes unter Verwendung eines Magnetaktors zu realisieren. Die Ansteuerung erfolgt demnach rücklaufmengenfrei. The proposed fuel injector has a magnetic actuator with a liftable anchor element for the direct control of a preferably needle-shaped injection valve member. According to the invention, the injection valve member during a first phase of its opening stroke with a hydraulic translator mechanically coupled, which has a control volume limiting hydraulic active surface Ai, which in total with a formed on the injection valve member hydraulic active surface A 2 greater than a formed on the anchor element, the control volume limiting hydraulic Active surface A 3 is, so that due to the area ratio of the relevant in relation to the control volume hydraulic active surfaces Ai, A 2 and A 3, a force gain is effected. Further, according to the invention, the injection valve member is mechanically coupled during its closing stroke with the anchor element, the is acted upon in the closing direction of the injection valve member by an armature spring, so that the closing stroke of the injection valve member by means of the armature spring is effected. A separate closing spring, which acts on the injection valve member in the closing direction with a closing force, is thus unnecessary. The elimination of a separate closing spring has the advantage of a reduced manufacturing and voting effort. In addition, the control volume can be minimized, which has a favorable effect on the response of the input signal. In addition, during the first phase of the opening stroke of the injection valve member, the force amplification makes it possible to realize a direct actuation of the injection valve member using a magnetic actuator. The control is therefore carried out without backflow.
Während der ersten Phase des Öffnungshubes gilt es den Druckunterschied am geschlossenen Einspritzventilglied zu überwinden, der anfänglich sehr groß ist. Um das Einspritzventilglied aus seinem Sitz zu heben, bedarf es daher der Kraftverstärkung. Die mit der Kraftverstärkung einhergehende Wegminderung ist in dieser Phase des Öffnungshubes des Einspritzventilgliedes unerheblich. Zur vollständigen Sitzentdrosselung wird daher während einer zweiten Phase von einer Kraftverstärkung auf eine Wegverstärkung umgeschaltet. Die mit der Wegverstärkung einhergehende Kraftminderung ist wiederum unerheblich, da sich mit fortschreitendem Hub des Einspritzventilgliedes unterhalb des Einspritzventilgliedes ein dem System druck angleichender Druck aufbaut, so dass die zum weiteren Anheben des Einspritzventilgliedes erforderliche Kraft sinkt. Die Umschaltung von einer Kraftverstärkung auf eine Wergverstärkung erfolgt durch eine Änderung des Flächenverhältnisses der jeweils in Bezug auf das Steu- ervolumen relevanten hydraulischen Wirkflächen. During the first phase of the opening stroke, it is necessary to overcome the pressure difference at the closed injection valve member, which is initially very large. In order to lift the injection valve member from its seat, it therefore requires the power boost. The associated with the power amplification Wegminderung is irrelevant in this phase of the opening stroke of the injection valve member. For complete seat throttling is therefore switched over during a second phase of a power gain to a path gain. The power reduction associated with the Wegverstärkung is again irrelevant, since with the progressive stroke of the injection valve member below the injection valve member, a system pressure equalizing pressure builds up, so that the force required to further increase the injection valve member decreases. The switchover from a force amplification to a drag gain is effected by a change in the area ratio of the hydraulic active surfaces relevant in each case in relation to the control volume.
Vorzugsweise ist zur Realisierung einer Wegverstärkung während der zweiten Phase des Öffnungshubes des Einspritzventilgliedes die am Einspritzventilglied ausgebildete hydraulische Wirkfläche A2 kleiner als die am Ankerelement ausgebildete hydraulische Wirkfläche A3 gewählt. Zudem wird während der zweiten Phase des Öffnungshubes die mechanische Kopplung des E i ns p ritz ve nti I gl i ed es mit dem hydraulischen Übersetzer aufgehoben, so dass das Flächenverhältnis der in Bezug auf das Steuervolumen relevanten hydraulischen Wirkflächen nunmehr A2/ A 3 < 1 beträgt. Gemäß einer bevorzugten Ausführungsform der Erfindung ist zur mechanischen Kopplung des E i ns p ritzve nti I g I ied es mit dem hydraulischen Übersetzer eine Anschlagfläche am Einspritzventilglied ausgebildet. Die Anschlagfläche bewirkt, dass bei einer Hubbe- wegung des hydraulischen Übersetzers das Einspritzventilglied mitgenommen wird. Die Hubbewegung des hydraulischen Übersetzers wird wiederum durch eine Hubbe- wegung des Ankerelementes in Richtung des Magnetaktors und einer damit einhergehenden Absenkung des Steuerdrucks im Steuervolumen realisiert. Da sich während dieser Phase des Öffnungshubes des E i ns p ritzve nti I gl ied es die hydraulischen Wirkflächen Ai und A2 addieren und in der Summe größer als die hydraulische Wirkfläche A3 des Ankerelements sind, wird eine Kraftverstärkung bewirkt, mittels welcher die anfänglich hohe Schließkraft überwunden werden kann. Preferably, in order to realize a travel gain during the second phase of the opening stroke of the injection valve member, the hydraulic effective area A 2 formed on the injection valve member is selected smaller than the hydraulic effective area A 3 formed on the anchor element. In addition, during the second phase of the opening stroke, the mechanical coupling of the injection stroke is canceled by the hydraulic booster, so that the area ratio of the hydraulic active surfaces relevant in relation to the control volume is now A 2 / A 3 1 amounts to. According to a preferred embodiment of the invention, a stop surface on the injection valve member is formed with the hydraulic booster for the mechanical coupling of the egg n p ritzve nti I. The stop surface causes the injection valve member to be entrained during a stroke movement of the hydraulic booster. The lifting movement of the hydraulic booster is in turn realized by a lifting movement of the anchor element in the direction of the magnetic actuator and a concomitant lowering of the control pressure in the control volume. Since during this phase of the opening stroke of the injection stroke, the hydraulic active surfaces Ai and A 2 add up and in total are larger than the hydraulic active surface A 3 of the armature element, a force amplification is effected, by means of which the initial high closing force can be overcome.
Um die Entkopplung des Einspritzventilgliedes vom hydraulischen Übersetzer und damit ein Umschalten von einer Kraftverstärkung auf eine Wegverstärkung zu bewirken, ist vorzugsweise an einem Gehäuseteil des Kraftstoff injektors ein Anschlag ausgebildet. Der Anschlag dient der einseitig wirksamen Hubbegrenzung des hydraulischen Übersetzers. Das heißt, dass der Öffnungshub des hydraulischen Übersetzers im Unterschied zum Öffnungshub des Einspritzventilgliedes begrenzt ist. Während der zweiten Phase des Öffnungshubes des Einspritzventilgliedes liegt der hydraulische Übersetzer am Anschlag des Gehäuseteils an, so dass nicht nur die mechanische Kopplung des hydraulischen Übersetzers mit dem Einspritzventilglied sondern auch die hydraulische Kopplung des hydraulischen Übersetzers mit dem Ankerelement aufgehoben wird. Lediglich die hydraulische Kopplung des Einspritzventilgliedes bleibt bestehen, so dass über ein Flächenverhältnis A2/ A3 < 1 eine Wegverstärkung bewirkbar ist. In order to effect the decoupling of the injection valve member from the hydraulic booster and thus switching from a power gain to a path gain, preferably a stop is formed on a housing part of the fuel injector. The stop serves to unilaterally limit the stroke of the hydraulic translator. This means that the opening stroke of the hydraulic booster is limited in contrast to the opening stroke of the injection valve member. During the second phase of the opening stroke of the injection valve member, the hydraulic booster rests against the stop of the housing part, so that not only the mechanical coupling of the hydraulic booster with the injection valve member but also the hydraulic coupling of the hydraulic booster with the anchor element is released. Only the hydraulic coupling of the injection valve member remains, so that over a surface ratio A 2 / A 3 <1, a path gain can be effected.
Gemäß einer weiteren bevorzugten Ausführungsform der Erfindung ist der hydraulische Übersetzer Scheiben- oder kolbenförmig ausgebildet und besitzt eine zentrale Bohrung, in welcher das Einspritzventilglied aufgenommen ist. Auf diese Weise lassen sich am einfachsten die vorstehend beschriebenen Flächenverhältnisse während der ersten und der zweiten Phase des Öffnungshubes des E i ns p ritzve nti I g I ied es realisieren. Der am Einspritzventilglied ausgebildete Anschlag kann beispielsweise als radialer Absatz im Bereich einer Durchmesservergrößerung des Einspritzventilgliedes ausgebildet sein. Weiterhin bevorzugt sind der hydraulische Übersetzer, das Einspritzventil- glied und das Ankerelement koaxial angeordnet, wobei die am Ankerelement ausgebildete hydraulische Wirkfläche A3 den Wirkflächen Ai und A2 gegenüber liegt. According to a further preferred embodiment of the invention, the hydraulic booster is disc-shaped or piston-shaped and has a central bore in which the injection valve member is received. In this way, it is easiest to realize the area ratios described above during the first and the second phase of the opening stroke of the opening stroke. The stop formed on the injection valve member may be formed, for example, as a radial shoulder in the region of an increase in diameter of the injection valve member. Further preferred are the hydraulic booster, the injection valve member and the anchor member arranged coaxially, wherein the armature formed on the hydraulic active surface A 3 is the active surfaces Ai and A 2 opposite.
Vorteilhafterweise wird der hydraulische Übersetzer von der Druckkraft einer Feder beaufschlagt, mittels welcher sichergestellt ist, dass der hydraulische Übersetzer in Schließstellung des Injektors am Anschlag des Einspritzventilgliedes anliegt. Die Feder hat demnach lediglich zu gewährleisten, dass der hydraulische Übersetzer nach einem Einspritzvorgang wieder seine Ausgangsposition einnimmt. Demzufolge kann eine relativ weiche Feder eingesetzt werden. Zumindest ist die Federkraft geringer als die der Ankerfeder gewählt, um den vollständigen Schließhub des Einspritzventilgliedes zu bewirken. Advantageously, the hydraulic booster is acted upon by the pressure force of a spring, by means of which it is ensured that the hydraulic booster rests in the closed position of the injector against the stop of the injection valve member. Therefore, the spring has only to ensure that the hydraulic translator resumes its initial position after an injection process. As a result, a relatively soft spring can be used. At least the spring force is less than that of the armature spring chosen to effect the complete closing stroke of the injection valve member.
Eine bevorzugte Ausführungsform der Erfindung wird nachfolgend anhand der einzigen Zeichnung näher beschrieben. Diese zeigt einen schematischen Längsschnitt durch einen erfindungsgemäßen Kraftstoffinjektor. A preferred embodiment of the invention will be described below with reference to the single drawing. This shows a schematic longitudinal section through a fuel injector according to the invention.
Ausführliche Beschreibung der Zeichnung Detailed description of the drawing
Der dargestellte erfindungsgemäße Kraftstoffinjektor weist einen Magnetaktor 1 zur Betätigung eines Einspritzventilgliedes 2 auf. Das Einspritzventilglied 2 ist zum Freigeben und Verschließen wenigstens einer Einspritzöffnung 3 hubbeweglich in einem Düsenkörper 13 geführt. Zur Betätigung des Einspritzventilgliedes 2 weist der Magnetaktor 1 ein ebenfalls hubbewegliches Ankerelement 4 auf, das in axialer Richtung ein Steuervolumen 5 mit einer hydraulischen Wirkfläche A3 begrenzt. Bei einer Bestromung des Magnetaktors 1 bewegt sich das Ankerelement 4 in Richtung des Aktors und bewirkt auf diese Weise einen Druckabfall im Steuervolumen 5. Da das Steuervolumen 5 ferner von einer an einem hydraulischen Übersetzer 6 ausgebildeten hydraulischen Wirkfläche Ai und von einer am Einspritzventilglied 2 ausgebildeten hydraulischen Wirkfläche A2 begrenzt wird, erfolgt eine hydraulische Kopplung dieser mit dem Ankerelement 4. Das heißt, dass der hydraulische Übersetzer 6 und das Einspritzventilglied 2 der Bewegung des Ankerelementes 4 folgen. Da die Summe der hydraulischen Wirkflächen A[ und A2 größer als die Fläche A3 gewählt ist, wird über das Flächenverhältnis während dieser ersten Phase des Öffnungshubes des E i ns p ritzve nti I g I ied es 2 eine Kraftverstärkung bewirkt. Um sicherzustellen, dass sowohl der hydraulische Überset- zer 6 als auch das Einspritzventilglied 2 der Bewegung des Ankerelementes 4 folgen, sind der hydraulische Übersetzer 6 und das Einspritzventilglied 2 über eine am Einspritzventilglied 2 ausgebildete Anschlagfläche 8 mechanisch koppelbar. Während der ersten Phase des Öffnungshubes liegt der hydraulische Übersetzer 6 an dieser Anschlagfläche 8 des Einspritzventilgliedes 2 an. Einen Teil des Öffnungshubes des Einspritzventilgliedes 2 bewältigen der hydraulische Übersetzer 6 und das Einspritzventil- glied 2 demnach gemeinsam. Strömt nach anfänglichem Öffnen der Kraftstoff unter das Einspritzventilglied 2 sinken die Kraftanforderungen zum weiteren Anheben des Einspritzventilgliedes. Demnach kann nunmehr von einer Kraftverstärkung auf eine Wegverstärkung umgeschaltet werden. Das Umschalten erfolgt, indem der hydraulische Übersetzer 6 an einer weiteren Bewegung gehindert wird. Das heißt, dass die mechanische Kopplung des hydraulischen Übersetzers 6 mit dem Einspritzventilglied 2 während dieser zweiten Phase des Öffnungshubes des Einspritzventilgliedes 2 gelöst wird. Als wirksame hydraulische Flächen liegen sich demnach nur noch die Wirkflächen A2 und A3 gegenüber. Da die am Einspritzventilglied 2 ausgebildete hydraulische Wirkfläche A2 kleiner als die am Ankerelement 4 ausgebildete hydraulische Wirkfläche A3 gewählt ist, wird nunmehr eine Wegverstärkung erzielt. The illustrated fuel injector according to the invention has a magnetic actuator 1 for actuating an injection valve member 2. The injection valve member 2 is guided for releasing and closing at least one injection opening 3 in a liftable manner in a nozzle body 13. For actuation of the injection valve member 2, the solenoid actuator 1 has a likewise liftable anchor element 4, which limits a control volume 5 with a hydraulic active surface A 3 in the axial direction. When energizing the solenoid actuator 1, the armature element 4 moves in the direction of the actuator and thus causes a pressure drop in the control volume 5. Since the control volume 5 further formed by a formed on a hydraulic translator 6 hydraulic effective area Ai and a formed on the injection valve member 2 hydraulic Impact surface A 2 is limited, there is a hydraulic coupling of this with the anchor element 4. That is, the hydraulic booster 6 and the injection valve member 2 follow the movement of the anchor member 4. Since the sum of the hydraulic effective areas A [and A 2 is greater than the area A 3 , an increase of the force is effected via the area ratio during this first phase of the opening stroke of the opening stroke of the electric drive. To ensure that both the hydraulic transmission 6 and the injection valve member 2 follow the movement of the armature element 4, the hydraulic booster 6 and the injection valve member 2 via a formed on the injection valve member 2 stop surface 8 are mechanically coupled. During the first phase of the opening stroke of the hydraulic booster 6 abuts against this stop surface 8 of the injection valve member 2. A part of the opening stroke of the injection valve member 2, the hydraulic translator 6 and the injection valve member 2 accordingly master together. After initially opening the fuel flows under the injection valve member 2, the force requirements for further raising the injection valve member decrease. Accordingly, it is now possible to switch from a power amplification to a path gain. The switching occurs by preventing the hydraulic booster 6 from further movement. That is, the mechanical coupling of the hydraulic booster 6 with the injection valve member 2 is released during this second phase of the opening stroke of the injection valve member 2. As effective hydraulic surfaces are therefore only the active surfaces A 2 and A 3 against. Since the formed on the injection valve member 2 hydraulic effective area A 2 is selected to be smaller than that formed on the anchor member 4 hydraulic effective area A 3, a path gain will now be achieved.
Zur Hubbegrenzung des hydraulischen Übersetzers 6 ist an einem Gehäuseteil 9 ein Anschlag 10 ausgebildet. Gelangt der hydraulische Übersetzer 6 in Anlage mit dem Anschlag 10, wird die mechanische Kopplung mit dem Einspritzventilglied 2 gelöst und das Einspritzventilglied 2 setzt die Bewegung alleine fort. Die mechanische Kopplung erfolgt vorliegend in einfacher Weise, nämlich indem das Einspritzventilglied 2 in einer zentralen Bohrung 11 des hydraulischen Übersetzers 6 aufgenommen ist und zur Ausbildung der Anschlagfläche 8 einen Bereich mit vergrößertem Außendurchmesser besitzt, wobei der Außendurchmesser größer als der Innendurchmesser der zentralen Bohrung 11 gewählt ist. Eine Feder 12, welche den hydraulischen Übersetzer 6 in Richtung der Anschlagfläche 8 mit einer Druckkraft beaufschlagt, stellt die Anlage des hydraulischen Übersetzers 6 an der Anschlagfläche 8 während der ersten Phase des Öffnungshubes des E i ns p ritz ve nti I g I ied es 2 bzw. in Schließstellung des Injektors sicher. To limit the stroke of the hydraulic booster 6, a stop 10 is formed on a housing part 9. If the hydraulic booster 6 comes into abutment with the stopper 10, the mechanical coupling with the injection valve member 2 is released and the injection valve member 2 continues the movement alone. The mechanical coupling takes place in the present case in a simple manner, namely by the injection valve member 2 is received in a central bore 11 of the hydraulic booster 6 and to form the stop surface 8 has a region with increased outer diameter, wherein the outer diameter greater than the inner diameter of the central bore 11 is selected is. A spring 12, which applies a compressive force to the hydraulic translator 6 in the direction of the abutment surface 8, places the abutment of the hydraulic translator 6 against the abutment surface 8 during the first phase of the opening stroke of the eccentric injection valve 2 or in the closed position of the injector safely.
Zum Schließen der wenigstens einen Einspritzöffnung 3 wird die Bestromung des Magnetaktors 1 beendet. Eine das Ankerelement 4 in Schließrichtung mit einer Druck- kraft beaufschlagende Ankerfeder 7 stellt die Rückstellung des Ankerelementes 4 sicher. Bei der Rückstellung gelangt das Ankerelement 4 in Anlage mit dem Einspritzventilglied 2 und drückt dieses in seinen Sitz zurück. Aufgrund der mechanischen Kopplung des Einspritzventilgliedes 2 mit dem Ankerelement 4 während der Schließphase wird die Rückstellung des E i ns p ritz ve nti I g I ied es 2 ebenfalls über die Druckkraft der Ankerfeder 7 bewirkt. Die Federkraft der Ankerfeder 7 ist dementsprechend relativ hoch gewählt. In jedem Fall ist die Federkraft der Ankerfeder 7 höher als die Federkraft der Feder 12 gewählt, welche den hydraulischen Übersetzer in Öffnungsrichtung des Einspritzventilgliedes 2 beaufschlagt. Eine separate Schließfeder zur Rückstellung des Einspritzventilgliedes 2 ist verzichtbar, wodurch der Fertigungs- und Abstimmungsaufwand verringert wird. For closing the at least one injection opening 3, the energization of the magnetic actuator 1 is terminated. An anchor element 4 in the closing direction with a pressure force acting anchor spring 7 ensures the return of the anchor element 4. When returning the anchor element 4 comes into contact with the injection valve member 2 and pushes this back into its seat. Due to the mechanical coupling of the injection valve member 2 with the armature element 4 during the closing phase, the return of the spring 10 is also effected via the pressure force of the armature spring 7. The spring force of the armature spring 7 is therefore chosen to be relatively high. In any case, the spring force of the armature spring 7 is selected higher than the spring force of the spring 12, which acts on the hydraulic booster in the opening direction of the injection valve member 2. A separate closing spring for returning the injection valve member 2 is dispensable, whereby the manufacturing and tuning effort is reduced.
Die Erfindung ist nicht auf das dargestellte Ausführungsbeispiel begrenzt. Darüber hinaus sind Abwandlungen, insbesondere im Hinblick auf die Ausführung des Ankerelementes 4, des hydraulischen Übersetzers 6 und/oder des E i ns p ritz ve nti I gl ied es 2, realisierbar. The invention is not limited to the illustrated embodiment. In addition, modifications, in particular with regard to the design of the anchor element 4, of the hydraulic booster 6 and / or of the electrical connector 2, can be realized.

Claims

Patentansprüche claims
1. Kraftstoffinjektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine mit einem Magnetaktor (1) zur direkten Ansteuerung eines vorzugsweise nadeiförmigen Einspritzventilgliedes (2), über dessen Hubbewegung wenigstens eine Einspritzöffnung (3) des Kraftstoffinjektors freigebbar oder verschließbar ist, wobei der Magnetaktor (1) ein hubbewegliches Ankerelement (4) zur Steuerung des Steuerdrucks in einem Steuervolumen (5) umfasst, 1. A fuel injector for injecting fuel into a combustion chamber of an internal combustion engine with a magnetic actuator (1) for direct control of a preferably needle-shaped injection valve member (2), via the lifting movement at least one injection port (3) of the fuel injector is releasable or closable, wherein the magnetic actuator (1 ) comprises a lifting armature element (4) for controlling the control pressure in a control volume (5),
dadurch gekennzeichnet, dass das Einspritzventilglied (2) während einer ersten Phase seines Öffnungshubes mit einem hydraulischen Übersetzer (6) mechanisch koppelbar ist, der eine das Steuervolumen (5) begrenzende hydraulische Wirkfläche Aj besitzt, welche in Summe mit einer am Einspritzventilglied (2) ausgebildeten hydraulischen Wirkfläche A2 größer als eine am Ankerelement (4) ausgebildete und das Steuervolumen (5) begrenzende hydraulische Wirkfläche A3 ist, so dass aufgrund des Flächenverhältnisses der in Bezug auf das Steuervolumen (5) relevanten hydraulischen Wirkflächen Aj, A2 und A3 eine Kraftverstärkung bewirkt wird, ferner, dass das Einspritzventilglied (2) während seines Schließhubes mit dem Ankerelement (4) mechanisch koppelbar ist, das in Schließrichtung des Einspritzventilgliedes (2) von der Druckkraft einer Ankerfeder (7) beaufschlagt wird, so dass der Schließhub des Einspritzventilgliedes (2) mittels der Ankerfeder (7) bewirkbar ist. characterized in that the injection valve member (2) during a first phase of its opening stroke with a hydraulic booster (6) is mechanically coupled, which has a control volume (5) limiting hydraulic effective area Aj, which in total with one of the injection valve member (2) formed Hydraulic effective area A 2 is greater than an armature element (4) formed and the control volume (5) limiting hydraulic effective area A 3 , so that due to the area ratio of the relevant in relation to the control volume (5) hydraulic active surfaces Aj, A 2 and A third a force amplification is effected, further that the injection valve member (2) during its closing stroke with the armature element (4) is mechanically coupled, which is acted upon in the closing direction of the injection valve member (2) by the pressure force of an armature spring (7), so that the closing stroke of Injection valve member (2) by means of the armature spring (7) is effected.
2. Kraftstoffinjektor nach Anspruch 1, 2. Fuel injector according to claim 1,
dadurch gekennzeichnet, dass am Einspritzventilglied (2) eine Anschlagfläche (8) zur mechanischen Kopplung mit dem hydraulischen Übersetzer (6) ausgebildet ist.  characterized in that on the injection valve member (2) a stop surface (8) for mechanical coupling with the hydraulic booster (6) is formed.
3. Kraftstoffinjektor nach Anspruch 1 oder 2, 3. Fuel injector according to claim 1 or 2,
dadurch gekennzeichnet, dass die am Einspritzventilglied (2) ausgebildete Anschlagfläche (8) eine Mitnahme des Einspritzventilgliedes (2) bei einer Hubbewe- gung des hydraulischen Übersetzers (6) zur Umsetzung einer Kraftverstärkung während der ersten Phase der Hubbewegung des E i ns ritz ve nti I g I ied es (2) bewirkt. characterized in that on the injection valve member (2) formed stop surface (8) entrainment of the injection valve member (2) in a Hubbewe- movement of the hydraulic translator (6) to implement a force amplification during the first phase of the lifting movement of the electric drive (2).
4. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, 4. Fuel injector according to one of the preceding claims,
dadurch gekennzeichnet, dass an einem Gehäuseteil (9) des Kraftstoffinjektors ein Anschlag (10) zur einseitig wirksamen Hubbegrenzung des hydraulischen Übersetzers (6) ausgebildet ist.  characterized in that on a housing part (9) of the fuel injector, a stop (10) for unilaterally effective stroke limitation of the hydraulic booster (6) is formed.
5. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, 5. Fuel injector according to one of the preceding claims,
dadurch gekennzeichnet, dass der hydraulische Übersetzer (6) Scheiben- oder kolbenförmig ausgebildet ist und eine zentrale Bohrung (11) zur Aufnahme des Einspritzventilgliedes (2) besitzt.  characterized in that the hydraulic booster (6) is disc-shaped or piston-shaped and has a central bore (11) for receiving the injection valve member (2).
6. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, 6. Fuel injector according to one of the preceding claims,
dadurch gekennzeichnet, dass der hydraulische Übersetzer (6) von der Druckkraft einer Feder (12) beaufschlagt wird.  characterized in that the hydraulic booster (6) is acted upon by the pressure force of a spring (12).
EP11788109.4A 2010-11-22 2011-11-21 Fuel injector Not-in-force EP2643581B1 (en)

Applications Claiming Priority (2)

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DE201010044205 DE102010044205A1 (en) 2010-11-22 2010-11-22 fuel injector
PCT/EP2011/070513 WO2012069393A1 (en) 2010-11-22 2011-11-21 Fuel injector

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DE102014205910A1 (en) * 2014-03-31 2015-10-01 Robert Bosch Gmbh Fuel injector
CN109312735A (en) * 2016-05-12 2019-02-05 布里格斯斯特拉顿公司 Fuel delivery injector

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JP2001522140A (en) * 1997-11-03 2001-11-13 ディーゼル エンジン リターダーズ，インコーポレイテッド Cascade electromagnetic armature
DE102004035280A1 (en) * 2004-07-21 2006-03-16 Robert Bosch Gmbh Fuel injector with direct multi-stage injection valve element control
DE102006015745A1 (en) 2006-04-04 2007-10-11 Robert Bosch Gmbh Fuel injector especially for diesel engine has a solenoid operated valve with a bypass for enhanced switching speed
DE102007002758A1 (en) * 2006-04-04 2007-10-11 Robert Bosch Gmbh fuel injector
DE102007028490A1 (en) * 2007-06-21 2008-12-24 Robert Bosch Gmbh Hydraulic coupler for injector, has coupler element which is connected with stationary component, where another coupler element is provided
DE102008042227A1 (en) * 2008-09-19 2010-04-01 Robert Bosch Gmbh Fuel injector, particularly common rail injector for injecting fuel into combustion chamber of internal-combustion engine, comprises injection valve element, which is adjustable between closing position and opening position
DE102009047559A1 (en) * 2009-12-07 2011-06-09 Robert Bosch Gmbh fuel injector
DE102010028835A1 (en) * 2010-05-11 2011-11-17 Robert Bosch Gmbh fuel injector

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CN103221677A (en) 2013-07-24

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