EP2510220A1 - Fuel injector - Google Patents

Fuel injector

Info

Publication number
EP2510220A1
EP2510220A1 EP10767992A EP10767992A EP2510220A1 EP 2510220 A1 EP2510220 A1 EP 2510220A1 EP 10767992 A EP10767992 A EP 10767992A EP 10767992 A EP10767992 A EP 10767992A EP 2510220 A1 EP2510220 A1 EP 2510220A1
Authority
EP
European Patent Office
Prior art keywords
needle
nozzle needle
fuel injector
nozzle
magnetic
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
EP10767992A
Other languages
German (de)
French (fr)
Other versions
EP2510220B1 (en
Inventor
Walter Fuchs
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 EP2510220A1 publication Critical patent/EP2510220A1/en
Application granted granted Critical
Publication of EP2510220B1 publication Critical patent/EP2510220B1/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
    • 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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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.
  • a fuel injector comprises a solenoid actuator for actuating a nozzle needle in a bore of a nozzle body guided nozzle piston, on the lifting movement at least one injection port of the fuel injector is releasable or lockable.
  • magnetic actuators as a pressure plate in today's fuel injectors has proven itself insofar as magnetic actuators, for example, compared to piezo actuators, are physically small and inexpensive.
  • magnetic actuators have a comparatively small force, which is usually not sufficient to overcome in the closed position of the nozzle needle, the strong closing force on the nozzle needle seat and raise the nozzle needle. Therefore, the actuation of the nozzle needle when using a magnetic actuator as a pressure plate is usually indirectly by the nozzle needle is acted upon by a control valve with a variable control pressure, which then causes the opening or closing stroke of the nozzle needle.
  • the invention is now based on the object of providing a fuel injector of simple design with only one magnetic actuator or magnetic circuit, which nevertheless ensures reliable opening and closing operation of the nozzle needle.
  • the proposed fuel injector should further have improved efficiency.
  • the proposed fuel injector comprises a magnetic actuator for actuating the hub in a nozzle of a nozzle movable guided nozzle needle, which according to the invention has a hydraulically effective area Ai, which limits a control volume axially over which the nozzle needle with a preferably coaxially arranged magnetic needle is hydraulically coupled, in a central well of an intermediate piston is slidably guided and has a control volume axially delimiting hydraulically effective area A 2 , which is smaller than the area Ai of the nozzle needle, so that the hydraulic coupling during a first phase of the opening stroke of the nozzle needle causes a force boost.
  • the power amplification during the first phase of the opening stroke of the nozzle needle is thus achieved solely by the selected area ratio of the hydraulically active surfaces Ai and A 2 .
  • the strong closing force on the nozzle needle seat is overcome due to the power gain, so that a reliable opening operation is ensured.
  • no control quantities and no leakage return are required because the actuation of the nozzle needle takes place directly or via the existing control volume.
  • the efficiency is thus significantly improved over conventional solenoid-driven Injektor scholaren.
  • the return flow-free concept requires a lower high-pressure pump delivery rate, which means that fuel consumption and pollutant emissions are also reduced.
  • the nozzle needle during a second phase of its opening stroke with the intermediate piston which has a control volume axially delimiting hydraulically effective area A 3 and preferably also in the bore of the nozzle body hubbeweglich is guided, hydraulically coupled, wherein the hydraulic coupling during the second phase of the opening stroke compared to the first phase causes a Wegverstärkung.
  • the strong closing force at the nozzle needle is compensated by increasing pressure infiltration. Accordingly, in the second phase of the opening stroke of the nozzle needle, a force amplification is no longer required. Due to the largely pressure-balanced nozzle needle, therefore, the stroke reduction can be dispensed with in this second lifting phase, and path amplification can be achieved.
  • the path reinforcement is effected by the additional hydraulically effective area A 3 of the intermediate piston, which follows the lifting movement of the magnetic needle during the second phase of the opening stroke of the nozzle needle, so that the hydraulically active surfaces A 2 and A 3 complement each other.
  • the path reinforcement allows for a larger nozzle needle lift so that complete seat throttling is enabled or added. At least the seat throttling is very low. As a result, given a constant rail pressure, this reduces the pressure losses up to the injection opening, as a result of which the atomizing energy at the injection opening is improved in order to minimize emissions.
  • the hydraulically active surfaces A 2 and A 3 of the magnetic needle and the intermediate piston complement each other such that the sum of the areas A 2 and A 3 is greater than or equal to the area Ai. While opposing equal areas effect a 1/1 ratio in terms of force and stroke, actual path gain can only be achieved if the areas A 2 and A 3 together are greater than Ai. Compared to the first phase of the opening stroke of the nozzle needle, however, in each case a Wegverstärkung is effected, since the area A 3 is added.
  • the intermediate piston is designed as a stepped piston and has a collar region with a radially extending contact surface, by means of which the intermediate piston is preferably supported on the nozzle body.
  • the radially extending contact surface of the intermediate piston remains in contact with the nozzle body. Only in the second phase of the opening stroke of the intermediate piston lifts with its radially extending contact surface from the nozzle body after the sum of all forces on the contact surface of the intermediate piston to the nozzle body is zero.
  • the nozzle body serves as a stop which limits the path of the intermediate piston in its provision as soon as the radially extending contact surface of the intermediate piston comes into contact with the nozzle body again.
  • the intermediate piston is acted upon by a pressure force acting in the direction of the magnetic actuator of a spring, which is further preferably designed as a helical compression spring and surrounds the collar region of the intermediate piston.
  • the movement of the intermediate piston is thus spring assisted in the second phase of the opening stroke of the nozzle needle to reliably ensure a path gain compared to the first phase of the opening stroke of the nozzle needle.
  • the collar region of the intermediate piston has a radially extending shoulder for supporting the spring. The other end of the spring is supported against the nozzle body. The radially extending shoulder thus serves as a spring plate.
  • the intermediate piston is further supported by a spring relative to the magnetic needle, wherein the spring is preferably designed as a plate spring, which is preferably supported on a radially extending shoulder of the magnetic needle.
  • This disc spring can be used for tolerance compensation.
  • such a spring is dispensable, if, for example, the provision of the intermediate piston is ensured via a formed on the magnetic needle driver.
  • this plate spring can be used to compensate for tolerances.
  • the magnetic needle is acted upon by the pressure force of a spring, which causes a reliable return of the magnetic needle upon completion of the energization of the magnetic actuator and thus during the closing stroke of the nozzle needle.
  • the spring can also be designed as a helical compression spring, which is supported on the one hand on the actuator-side end of the magnetic needle, on the other hand on the housing of the injector.
  • the nozzle needle seals at the nozzle needle seat. Outside the sealing diameter of the nozzle needle is pressurized by high pressure, while within the sealing diameter of the significantly lower combustion chamber pressure is applied.
  • the nozzle needle seat facing away from the end of the nozzle needle is again subjected to high pressure.
  • the hydraulic force difference above and below the nozzle needle acts as a sealing force on the nozzle needle seat.
  • the spring-loaded magnetic needle is supported on the seat-remote end of the nozzle needle. In the narrow space of an injector, a magnetic actuator could not compensate for this high sealing force on the nozzle needle seat in order to lift the nozzle needle directly from the seat.
  • the fuel After first lifting the nozzle needle, the fuel also flows within the nozzle seat under the nozzle needle tip. The force under the needle is thereby increasingly raised, so that the force required to further raise the nozzle needle decreases. Because with increasing stroke, a pressure equalizing the rail pressure builds up below the nozzle needle.
  • the intermediate piston lifts from the nozzle body and thus causes a change in the area ratio of each relevant in relation to the control volume hydraulically active surfaces, wherein in comparison to the first phase of the opening stroke of the nozzle needle Wegverstärkung is achieved .
  • the magnetic needle would have to cover a larger path than the nozzle needle in order to fulfill the mass balance, in order to realize the nozzle needle stroke necessary for adequate seat throttling.
  • the magnetic circuit in this limited space is not able to allow such a large stroke to keep the seat throttling sufficiently low for larger nozzle hole cross-sections.
  • the intermediate piston moves in the direction of the magnetic actuator, so that complement the hydraulically effective surfaces of the magnetic needle and the intermediate piston, it is no longer necessary to meet the mass balance that the magnetic needle or Aktorhub a Many times the stroke of the nozzle needle amounts.
  • the nozzle needle is now more or less wegver fertil taken up.
  • the resulting larger nozzle needle stroke in turn leads to a maximization of the beam energy at the injection openings.
  • the closing process of the nozzle needle is initiated by the termination of the current supply of the magnetic actuator.
  • the magnetic force drops below the remaining resulting forces on the magnetic needle.
  • the magnetic needle and the subsequently applied intermediate piston move in the direction of the nozzle needle seat.
  • the pressure forces rise in the pressure chamber above the nozzle needle, which also, after conditioning the magnetic needle on the nozzle needle, is loaded by the spring force of the actuator side of the magnetic needle spring.
  • the result is the closing stroke of the nozzle needle.
  • the nozzle needle seat throttles the pressure in the seating area until combustion chamber pressure prevails within the sealing seat diameter. This again leads to the initially described high sealing forces on the nozzle needle seat and thus to the reliable sealing of the nozzle holes with respect to the rail pressure.
  • FIG. 1 shows a schematic longitudinal section through a fuel injector according to the invention.
  • the illustrated fuel injector has a solenoid actuator 1 for actuating a nozzle needle 4 that is guided in a lift-capable manner in a bore 2 of a nozzle body 3.
  • the nozzle body 3 can also be designed in two parts, preferably with a static sealing point at the level of a control volume 6.
  • By the lifting movement of the nozzle needle 4 is at least one injection port 5 of the fuel injector can be opened or closed, so that when released injection port under high pressure fuel is injected into the combustion chamber of the internal combustion engine.
  • the magnetic actuator 1 When the magnetic actuator 1 is energized, the magnetic needle 7 moves towards the magnetic actuator 1 against the force of a spring 16 arranged above the magnetic needle 7, wherein a control volume 6 via which the magnetic needle 7 is hydraulically coupled to the nozzle needle 4 undergoes an enlargement.
  • the pressure in which the control volume 6 defining pressure chamber decreases until the forces are balanced above and below the nozzle needle 4, so that finally the opening stroke of the nozzle needle 4 is initiated.
  • the intermediate piston 9 which is also guided in a liftable manner in the bore 2 of the one or two-part nozzle body 3, rests against the nozzle body 3 during the first phase of the opening stroke of the nozzle needle 4.
  • the intermediate piston 9 has a collar region 10, on which a radially extending contact surface che 11 is formed.
  • the counter surface on the nozzle body 3 also forms a stop surface for limiting the stroke of the intermediate piston 9 during its return.
  • the intermediate piston 9 is loaded by a first spring 12 whose spring force supports the movement of the intermediate piston 9 in the direction of the magnetic actuator 1. In this way, a reliable opening operation is ensured.
  • the spring 12 is supported on the one hand on the nozzle body 3, on the other hand on a radially extending shoulder 13 of the intermediate piston 9.
  • the spring 12 is designed as a helical compression spring, which is placed around the collar region 10 of the intermediate piston 9.
  • the intermediate piston 9 is supported via a second spring 14 in the form of a plate spring with respect to the magnetic needle 7, so that the movement of the intermediate piston 9 is inter alia also coupled to the movement of the magnetic needle 7.
  • the spring 14 is supported on a radially extending shoulder 15. The spring 14 is used here a tolerance compensation.
  • the magnetic needle 7 acting spring 16 which is presently designed as a helical compression spring and the actuator side abuts the magnetic needle 7, the spring 14 further ensures that all hubbeweglichen components are returned to their original position.
  • the spring force of the magnetic needle 7 acting spring 16 causes the nozzle needle 4 is returned to its seat. In this case, the magnetic needle 7 applies directly to the nozzle needle 4.
  • the proposed fuel injector can ensure a reliable opening and closing operation.
  • the magnetic field is also built up and dismantled faster.
  • the proposed fuel injector also has only a few components and few wear points. It is thus easy and inexpensive to manufacture. Furthermore, sufficient space within the fuel injector for generous high pressure volumes for pressure wave attenuation remains.

Landscapes

  • 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

The invention relates to a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine, having a magnetic actuator (1) for actuating a nozzle needle (4) guided so as to effect a lift movement in a bore (2) of a nozzle body (3), the lift movement of the nozzle needle causing at least one injection opening (5) of the fuel injector to be opened or closed. According to the invention, the nozzle needle (4) has a hydraulically effective surface A1, which axially limits a control volume (6) via which the nozzle needle (4) can be hydraulically coupled to a preferably coaxially arranged magnetic needle (7). The magnetic needle is guided so as to effect a lift movement in a central bore (8) in an intermediate piston (9) and has a hydraulically effective surface A2 axially limiting the control volume (6) and smaller than the surface A1 of the nozzle needle (4), so that the hydraulic coupling effects a power increase during a first phase of the opening lift of the nozzle needle (4).

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 Oberbegriffes des Anspruchs 1. Ein solcher Kraftstoffinjektor weist einen Magnetaktor zur Betätigung einer in einer Bohrung eines Düsenkörpers hubbeweglich geführten Düsennadel auf, über deren 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. Such a fuel injector comprises a solenoid actuator for actuating a nozzle needle in a bore of a nozzle body guided nozzle piston, on the lifting movement at least one injection port of the fuel injector is releasable or lockable.
Stand der Technik State of the art
Die Verwendung von Magnetaktoren als Drucksteller bei heutigen Kraftstoffinjektoren hat sich insoweit bewährt, da Magnetaktoren, beispielsweise im Vergleich zu Piezoak- toren, kleinbauend und kostengünstig sind. Magnetaktoren besitzen jedoch eine vergleichsweise geringe Kraft, die in der Regel nicht ausreicht, um in der Schließstellung der Düsennadel die stark schließende Kraft am Düsennadelsitz zu überwinden und die Düsennadel anzuheben. Daher erfolgt die Betätigung der Düsennadel bei Verwendung eines Magnetaktors als Drucksteller in der Regel indirekt, indem die Düsennadel über ein Steuerventil mit einem veränderbaren Steuerdruck beaufschlagt wird, der dann den Öffnungs- oder Schließhub der Düsennadel bewirkt. The use of magnetic actuators as a pressure plate in today's fuel injectors has proven itself insofar as magnetic actuators, for example, compared to piezo actuators, are physically small and inexpensive. However, magnetic actuators have a comparatively small force, which is usually not sufficient to overcome in the closed position of the nozzle needle, the strong closing force on the nozzle needle seat and raise the nozzle needle. Therefore, the actuation of the nozzle needle when using a magnetic actuator as a pressure plate is usually indirectly by the nozzle needle is acted upon by a control valve with a variable control pressure, which then causes the opening or closing stroke of the nozzle needle.
Um den Steuerdruck zu senken, wird eine Absteuermenge über einen im Kraftstoffinjektor ausgebildeten Niederdruckbereich einem Rücklauf zugeführt. Die rückgeführte Absteuermenge führt zum Einen zu einer unerwünschten Aufheizung des Kraftstoffniederdruckkreises, zum Anderen muss diese abgesteuerte Menge wieder auf Hochdruck gefördert werden, wodurch die Anforderungen an die Förderleistung der vorgeschalteten Hochdruckpumpe steigen. Leckageverluste führen zudem zu einer weiteren Verschlechterung des Wirkungsgrades eines solchen Kraftstoffinjektors. In order to reduce the control pressure, a Absteuermenge is fed via a formed in the fuel injector low pressure region to a return. The recirculated Absteuermenge leads on the one hand to an undesirable heating of the fuel low pressure circuit, on the other hand, this diverted quantity must be back to high pressure be promoted, whereby the demands on the delivery of the upstream high-pressure pump rise. Leakage losses also lead to a further deterioration of the efficiency of such a fuel injector.
In der DE 10 2007 029 969 AI wird daher ein gattungsgemäßer magnetbetätigter Kraftstoffinjektor mit einem Druckabbauventil vorgeschlagen, das nicht den Servokreis- lauf des Injektors schaltet, sondern einen sekundären Hydraulikkreislauf, der eine wesentlich geringere Steuermenge benötigt. Dem Druckabbauventil haftet zudem keine Leckage an, was bezüglich der Effizienz von Vorteil ist. In DE 10 2007 029 969 AI therefore a generic solenoid-operated fuel injector is proposed with a pressure reduction valve, which does not switch the Servokreis- run of the injector, but a secondary hydraulic circuit, which requires a much lower control amount. The pressure relief valve also adheres to no leakage, which is in terms of efficiency of advantage.
Darüber hinaus sind rücklaufmengen- bzw. rückführungsfreie Injektorkonzepte bekannt, bei denen die Düsennadel direkt betätigt wird. Ein solches Konzept geht beispielsweise aus der DE 102 60 825 AI hervor. Das hierin beschrieben Kraftstoffeinspritzventil weist hierzu zwei unabhängig voneinander steuerbare Magnetkreise auf, die einen zuverlässigen Öffnungs- und Schließbetrieb gewährleisten sollen. In addition, Rücklaufmengen- or recirculation-free Injektorkonzepte are known in which the nozzle needle is actuated directly. Such a concept is apparent, for example, from DE 102 60 825 AI. The fuel injection valve described herein has for this purpose two independently controllable magnetic circuits, which are to ensure a reliable opening and closing operation.
Ausgehend von der Idee eines rücklaufmengenfreien Injektorkonzeptes liegt der Erfindung nunmehr die Aufgabe zugrunde, einen einfach aufgebauten Kraftstoffinjektor mit nur einem Magnetaktor bzw. Magnetkreis bereit zu stellen, der dennoch einen zuverlässigen Öffnungs- und Schließbetrieb der Düsennadel gewährleistet. Gegenüber bekannten Injektorkonzepten mit nur einem Magnetaktor soll der vorgeschlagene Kraftstoffinjektor des Weiteren einen verbesserten Wirkungsgrad aufweisen. Based on the idea of a return-flow-free injector concept, the invention is now based on the object of providing a fuel injector of simple design with only one magnetic actuator or magnetic circuit, which nevertheless ensures reliable opening and closing operation of the nozzle needle. Compared with known Injektorkonzepten with only a magnetic actuator, the proposed fuel injector should further have improved efficiency.
Die Aufgabe wird gelöst durch einen Kraftstoffinjektor mit den Merkmalen des Anspruchs 1. Vorteilhafte Weiterbildungen der Erfindung werden 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 zur Betätigung der in einer Bohrung des Düsenkörpers hubbeweglichen geführten Düsennadel auf, die erfindungsgemäß eine hydraulisch wirksame Fläche Ai besitzt, die ein Steuervolumen axial begrenzt, über welches die Düsennadel mit einer vorzugsweise koaxial angeordneten Magnetnadel hydraulisch koppelbar ist, die in einer zentralen Bohrung eines Zwischen- kolbens hubbeweglich geführt ist und eine das Steuervolumen axial begrenzende hydraulisch wirksame Fläche A2 besitzt, die kleiner als die Fläche Ai der Düsennadel ist, so dass die hydraulische Kopplung während einer ersten Phase der Öffnungshubes der Düsennadel eine Kraftverstärkung bewirkt. The proposed fuel injector comprises a magnetic actuator for actuating the hub in a nozzle of a nozzle movable guided nozzle needle, which according to the invention has a hydraulically effective area Ai, which limits a control volume axially over which the nozzle needle with a preferably coaxially arranged magnetic needle is hydraulically coupled, in a central well of an intermediate piston is slidably guided and has a control volume axially delimiting hydraulically effective area A 2 , which is smaller than the area Ai of the nozzle needle, so that the hydraulic coupling during a first phase of the opening stroke of the nozzle needle causes a force boost.
Die Kraftverstärkung während der ersten Phase des Öffnungshubes der Düsennadel wird demnach allein durch das gewählte Flächenverhältnis der hydraulisch wirksamen Flächen Ai und A2 erzielt. Die stark schließende Kraft am Düsennadelsitz wird aufgrund der Kraftverstärkung überwunden, so dass ein zuverlässiger Öffnungsbetrieb gewährleistet ist. Es werden zudem keine Steuermengen und kein Leckagerücklauf benötigt, da die Betätigung der Düsennadel direkt bzw. über das vorhandene Steuervolumen erfolgt. Der Wirkungsgrad wird damit gegenüber herkömmlichen magnetbetriebenen Injektorkonzepten deutlich verbessert. Das rücklaufmengenfreie Konzept benötigt eine geringere Hochdruckpumpenförderleistung, so dass demzufolge auch der Kraftstoffverbrauch und die Schadstoffemissionen sinken. The power amplification during the first phase of the opening stroke of the nozzle needle is thus achieved solely by the selected area ratio of the hydraulically active surfaces Ai and A 2 . The strong closing force on the nozzle needle seat is overcome due to the power gain, so that a reliable opening operation is ensured. In addition, no control quantities and no leakage return are required because the actuation of the nozzle needle takes place directly or via the existing control volume. The efficiency is thus significantly improved over conventional solenoid-driven Injektorkonzepten. The return flow-free concept requires a lower high-pressure pump delivery rate, which means that fuel consumption and pollutant emissions are also reduced.
Um den zur Sitzentdrosselung erforderlichen Hub der Düsennadel zu bewirken wird als weitere Maßnahme vorgeschlagen, dass die Düsennadel während einer zweiten Phase ihres Öffnungshubes mit dem Zwischenkolben, der eine das Steuervolumen axial begrenzende hydraulisch wirksame Fläche A3 besitzt und vorzugsweise ebenfalls in der Bohrung des Düsenkörpers hubbeweglich geführt ist, hydraulisch koppelbar ist, wobei die hydraulische Kopplung während der zweiten Phase des Öffnungshubes im Vergleich zur ersten Phase eine Wegverstärkung bewirkt. Ab Beginn des Öffnungshubes wird durch zunehmende Druckunterwanderung die stark schließende Kraft an der Düsennadel kompensiert. In der zweiten Phase des Öffnungshubes der Düsennadel ist demnach eine Kraftverstärkung nicht mehr erforderlich. Durch die weitgehend druckausgeglichene Düsennadel ist daher in dieser zweiten Hubphase die Hubuntersetzung verzichtbar, eine Wegverstärkung ist realisierbar. In order to bring about the necessary for Sitzentdrosselung stroke of the nozzle needle is proposed as a further measure that the nozzle needle during a second phase of its opening stroke with the intermediate piston, which has a control volume axially delimiting hydraulically effective area A 3 and preferably also in the bore of the nozzle body hubbeweglich is guided, hydraulically coupled, wherein the hydraulic coupling during the second phase of the opening stroke compared to the first phase causes a Wegverstärkung. From the beginning of the opening stroke, the strong closing force at the nozzle needle is compensated by increasing pressure infiltration. Accordingly, in the second phase of the opening stroke of the nozzle needle, a force amplification is no longer required. Due to the largely pressure-balanced nozzle needle, therefore, the stroke reduction can be dispensed with in this second lifting phase, and path amplification can be achieved.
Die Wegverstärkung wird durch die zusätzliche hydraulisch wirksame Fläche A3 des Zwischenkolbens bewirkt, der während der zweiten Phase des Öffnungshubes der Düsennadel der Hubbewegung der Magnetnadel folgt, so dass sich die hydraulisch wirksamen Flächen A2 und A3 ergänzen. Die Wegverstärkung ermöglicht einen größeren Düsennadelhub, so dass eine vollständige Sitzentdrosselung ermöglicht wird oder zu- mindest die Sitzdrosselung sehr gering ist. Bei konstant gegebenem Raildruck verringern sich dadurch die Druckverluste bis zur Einspritzöffnung, so dass demzufolge die Zerstäubungsenergie an der Einspritzöffnung zur Minimierung der Emissionen verbessert wird. The path reinforcement is effected by the additional hydraulically effective area A 3 of the intermediate piston, which follows the lifting movement of the magnetic needle during the second phase of the opening stroke of the nozzle needle, so that the hydraulically active surfaces A 2 and A 3 complement each other. The path reinforcement allows for a larger nozzle needle lift so that complete seat throttling is enabled or added. At least the seat throttling is very low. As a result, given a constant rail pressure, this reduces the pressure losses up to the injection opening, as a result of which the atomizing energy at the injection opening is improved in order to minimize emissions.
Vorzugsweise ergänzen sich während der zweiten Phase des Öffnungshubes der Düsennadel die hydraulisch wirksamen Flächen A2 und A3 der Magnetnadel und des Zwischenkolbens derart, dass die Summe der Flächen A2 und A3 größer oder gleich der Fläche Ai ist. Während sich gegenüberliegende gleich große Flächen eine 1/1- Übersetzung im Hinblick auf Kraft und Hub bewirken, kann eine eigentliche Wegverstärkung nur dann erzielt werden, wenn die Flächen A2 und A3 gemeinsam größer als Ai sind. Im Vergleich zur ersten Phase des Öffnungshubes der Düsennadel wird jedoch in jedem Fall eine Wegverstärkung bewirkt, da die Fläche A3 hinzukommt. Preferably, during the second phase of the opening stroke of the nozzle needle, the hydraulically active surfaces A 2 and A 3 of the magnetic needle and the intermediate piston complement each other such that the sum of the areas A 2 and A 3 is greater than or equal to the area Ai. While opposing equal areas effect a 1/1 ratio in terms of force and stroke, actual path gain can only be achieved if the areas A 2 and A 3 together are greater than Ai. Compared to the first phase of the opening stroke of the nozzle needle, however, in each case a Wegverstärkung is effected, since the area A 3 is added.
Gemäß einer bevorzugten Ausführungsform ist der Zwischenkolben als Stufenkolben ausgebildet und besitzt einen Bundbereich mit einer radial verlaufenden Anlagefläche, mittels welcher der Zwischenkolben vorzugsweise am Düsenkörper abgestützt ist. Während der ersten Phase des Öffnungshubes der Düsennadel verbleibt die radial verlaufende Anlagefläche des Zwischenkolbens in Anlage mit dem Düsenkörper. Erst in der zweiten Phase des Öffnungshubes hebt der Zwischenkolben mit seiner radial verlaufenden Anlagefläche vom Düsenkörper ab, nachdem die Summe aller Kräfte an der Anlagefläche des Zwischenkolbens zum Düsenkörper Null wird. Darüber hinaus dient der Düsenkörper als Anschlag, der den Weg des Zwischenkolbens bei dessen Rückstellung begrenzt, sobald die radial verlaufende Anlagefläche des Zwischenkolbens wieder in Anlage mit dem Düsenkörper gelangt. According to a preferred embodiment, the intermediate piston is designed as a stepped piston and has a collar region with a radially extending contact surface, by means of which the intermediate piston is preferably supported on the nozzle body. During the first phase of the opening stroke of the nozzle needle, the radially extending contact surface of the intermediate piston remains in contact with the nozzle body. Only in the second phase of the opening stroke of the intermediate piston lifts with its radially extending contact surface from the nozzle body after the sum of all forces on the contact surface of the intermediate piston to the nozzle body is zero. In addition, the nozzle body serves as a stop which limits the path of the intermediate piston in its provision as soon as the radially extending contact surface of the intermediate piston comes into contact with the nozzle body again.
Vorzugsweise wird der Zwischenkolben mit einer in Richtung des Magnetaktors wirkenden Druckkraft einer Feder beaufschlagt, die weiterhin vorzugsweise als Schraubendruckfeder ausgebildet ist und den Bundbereich des Zwischenkolbens umgibt. Die Bewegung des Zwischenkolbens erfolgt in der zweiten Phase des Öffnungshubes der Düsennadel somit federunterstützt, um in zuverlässiger Weise eine Wegverstärkung im Vergleich zur ersten Phase des Öffnungshubes der Düsennadel zu gewährleisten. Bevorzugt weist der Bundbereich des Zwischenkolbens eine radial verlaufende Schulter zur Abstützung der Feder auf. Das andere Ende der Feder ist gegenüber dem Düsenkörper abgestützt. Die radial verlaufende Schulter dient somit als Federteller. Preferably, the intermediate piston is acted upon by a pressure force acting in the direction of the magnetic actuator of a spring, which is further preferably designed as a helical compression spring and surrounds the collar region of the intermediate piston. The movement of the intermediate piston is thus spring assisted in the second phase of the opening stroke of the nozzle needle to reliably ensure a path gain compared to the first phase of the opening stroke of the nozzle needle. Preferably, the collar region of the intermediate piston has a radially extending shoulder for supporting the spring. The other end of the spring is supported against the nozzle body. The radially extending shoulder thus serves as a spring plate.
Vorteilhafterweise ist der Zwischenkolben ferner über eine Feder gegenüber der Magnetnadel abgestützt, wobei die Feder vorzugsweise als Tellerfeder ausgebildet ist, die bevorzugt an einer radial verlaufenden Schulter der Magnetnadel abgestützt ist. Diese Tellerfeder kann zum Toleranzausgleich genutzt werden. Andererseits ist eine solche Feder verzichtbar, wenn beispielsweise die Rückstellung des Zwischenkolbens über einen an der Magnetnadel ausgebildeten Mitnehmer sichergestellt ist. Ferner kann diese Tellerfeder zum Toleranzausgleich genutzt werden. Advantageously, the intermediate piston is further supported by a spring relative to the magnetic needle, wherein the spring is preferably designed as a plate spring, which is preferably supported on a radially extending shoulder of the magnetic needle. This disc spring can be used for tolerance compensation. On the other hand, such a spring is dispensable, if, for example, the provision of the intermediate piston is ensured via a formed on the magnetic needle driver. Furthermore, this plate spring can be used to compensate for tolerances.
Bevorzugt wird auch die Magnetnadel von der Druckkraft einer Feder beaufschlagt, die eine zuverlässige Rückstellung der Magnetnadel bei Beendigung der Bestromung des Magnetaktors und damit während des Schließhubes der Düsennadel bewirkt. Die Feder kann ebenfalls als Schraubendruckfeder ausgebildet sein, die einerseits am aktor- seitigen Ende der Magnetnadel, andererseits am Gehäuse des Injektors abgestützt ist. Preferably, the magnetic needle is acted upon by the pressure force of a spring, which causes a reliable return of the magnetic needle upon completion of the energization of the magnetic actuator and thus during the closing stroke of the nozzle needle. The spring can also be designed as a helical compression spring, which is supported on the one hand on the actuator-side end of the magnetic needle, on the other hand on the housing of the injector.
Die Funktionsweise eines erfindungsgemäßen Kraftstoffinjektors ist wie folgt: The operation of a fuel injector according to the invention is as follows:
Initial bzw. in Schließstellung dichtet die Düsennadel am Düsennadelsitz. Außerhalb des Dichtdurchmessers wird die Düsennadel von Hochdruck beaufschlagt, während innerhalb des Dichtdurchmessers der deutlich niedrigere Brennraumdruck anliegt. Das dem Düsennadelsitz abgewandte Ende der Düsennadel ist wiederum hochdruckbeaufschlagt. Die hydraulische Kraftdifferenz oberhalb und unterhalb der Düsennadel lastet als Dichtkraft am Düsennadelsitz. Zudem ist die federbelastete Magnetnadel am sitz- abgewandten Ende der Düsennadel abgestützt. Im engen Bauraum eines Injektors könnte ein Magnetaktor diese hohe Dichtkraft am Düsennadelsitz nicht kompensieren, um die Düsennadel direkt angesteuert vom Sitz abzuheben. Erfolgt nun bei einem erfindungsgemäßen Kraftstoffinjektor eine Bestromung des Magnetaktors, wird die auf die Magnetnadel lastende Federkraft überwunden und die Magnetnadel beginnt sich in Richtung des Magnetaktors zu bewegen. Dabei wird komprimiertes Volumen aus einem oberhalb der Düsennadel angeordneten Druckraum abgesaugt. Dadurch sinkt der Druck in dem Druckraum solange ab, bis die Dichtkraft am Düsennadelsitz gleich Null wird. Ab diesem Zeitpunkt hebt die Düsennadel von ihrem Dichtsitz ab. Durch das ge- wählte Flächenverhältnis der hydraulisch wirksamen Flächen der Magnetnadel und der Düsennadel, die über das im Druckraum vorhandene Steuervolumen hydraulisch gekoppelt sind, wird eine Kraftverstärkung bewirkt, so dass zur Überwindung der Dichtkraft eine deutlich geringere Magnetkraft ausreicht. Initially or in the closed position, the nozzle needle seals at the nozzle needle seat. Outside the sealing diameter of the nozzle needle is pressurized by high pressure, while within the sealing diameter of the significantly lower combustion chamber pressure is applied. The nozzle needle seat facing away from the end of the nozzle needle is again subjected to high pressure. The hydraulic force difference above and below the nozzle needle acts as a sealing force on the nozzle needle seat. In addition, the spring-loaded magnetic needle is supported on the seat-remote end of the nozzle needle. In the narrow space of an injector, a magnetic actuator could not compensate for this high sealing force on the nozzle needle seat in order to lift the nozzle needle directly from the seat. If, in the case of a fuel injector according to the invention, current is applied to the magnet actuator, the spring force acting on the magnet needle is overcome and the magnet needle begins to move in the direction of the magnet actuator. In this case, compressed volume is sucked out of a pressure chamber arranged above the nozzle needle. As a result, the pressure in the pressure chamber decreases until the sealing force at the nozzle needle seat becomes zero. From this point, the nozzle needle lifts off from its sealing seat. Through the selected area ratio of the hydraulically active surfaces of the magnetic needle and the nozzle needle, which are hydraulically coupled via the control volume present in the pressure chamber, a force amplification is effected, so that sufficient to overcome the sealing force a significantly lower magnetic force.
Nach erstem Anheben der Düsennadel strömt der Kraftstoff auch innerhalb des Düsensitzes unter die Düsennadelspitze. Die Kraft unter der Nadel wird dadurch zunehmend angehoben, so dass der Kraftaufwand zum weiteren Heben der Düsennadel sinkt. Denn mit größer werdendem Hub baut sich unterhalb der Düsennadel ein dem Raildruck angleichender Druck auf. Es beginnt die zweite Phase des Öffnungshubes der Düsennadel, in welcher der Zwischenkolben vom Düsenkörper abhebt und somit eine Änderung des Flächenverhältnisses der jeweils in Bezug auf das Steuervolumen relevanten hydraulisch wirksamen Flächen bewirkt, wobei im Vergleich zur ersten Phase des Öffnungshubes der Düsennadel eine Wegverstärkung erzielt wird. Ohne Bewegung des Zwischenkolbens müsste die Magnetnadel zur Erfüllung der Mengenbilanz einen größeren Weg als die Düsennadel zurücklegen, um den für eine ausreichende Sitzentdrosselung notwendigen Düsennadelhub zu realisieren. Der Magnetkreis in diesem begrenzten Bauraum ist jedoch nicht in der Lage einen so großen Hub zu ermöglichen, um für größere Düsenlochquerschnitte die Sitzdrosselung ausreichend niedrig zu halten. Da nach Aufbrauch der Abstützkraft des Zwischenkolbens am Düsenkörper sich der Zwischenkolben in Richtung des Magnetaktors bewegt, so dass sich die hydraulisch wirksamen Flächen der Magnetnadel und des Zwischenkolbens ergänzen, ist es zur Erfüllung der Mengenbilanz nicht mehr notwendig, dass die Magnetnadel bzw. der Aktorhub ein Vielfaches des Hubes der Düsennadel beträgt. In Abhängigkeit vom äußeren Führungsdurchmesser des Zwischenkolbens wird nunmehr die Düsennadel mehr oder weniger wegverstärkt mit nach oben genommen. Der dadurch bewirkte größere Düsennadelhub wiederum führt zu einer Maximierung der Strahlenergie an den Einspritzöffnungen. After first lifting the nozzle needle, the fuel also flows within the nozzle seat under the nozzle needle tip. The force under the needle is thereby increasingly raised, so that the force required to further raise the nozzle needle decreases. Because with increasing stroke, a pressure equalizing the rail pressure builds up below the nozzle needle. It begins the second phase of the opening stroke of the nozzle needle, in which the intermediate piston lifts from the nozzle body and thus causes a change in the area ratio of each relevant in relation to the control volume hydraulically active surfaces, wherein in comparison to the first phase of the opening stroke of the nozzle needle Wegverstärkung is achieved , Without movement of the intermediate piston, the magnetic needle would have to cover a larger path than the nozzle needle in order to fulfill the mass balance, in order to realize the nozzle needle stroke necessary for adequate seat throttling. However, the magnetic circuit in this limited space is not able to allow such a large stroke to keep the seat throttling sufficiently low for larger nozzle hole cross-sections. Since after exhaustion of the supporting force of the intermediate piston on the nozzle body, the intermediate piston moves in the direction of the magnetic actuator, so that complement the hydraulically effective surfaces of the magnetic needle and the intermediate piston, it is no longer necessary to meet the mass balance that the magnetic needle or Aktorhub a Many times the stroke of the nozzle needle amounts. Depending on the outer guide diameter of the intermediate piston now the nozzle needle is now more or less wegverstärkt taken up. The resulting larger nozzle needle stroke in turn leads to a maximization of the beam energy at the injection openings.
Der Schließvorgang der Düsennadel wird durch die Beendigung der Bestromung des Magnetaktors eingeleitet. Die Magnetkraft sinkt unter die restlichen resultierenden Kräfte an der Magnetnadel. Die Magnetnadel und der im Folgenden daran angelegte Zwischenkolben bewegen sich in Richtung des Düsennadelsitzes. Dadurch steigen die Druckkräfte im Druckraum oberhalb der Düsennadel an, welche zudem, nach Anlage der Magnetnadel an der Düsennadel, durch die Federkraft der aktorseitig an der Magnetnadel anliegenden Feder belastet wird. Die Folge ist der Schließhub der Düsennadel. Gegen Bewegungsende drosselt der Düsennadelsitz den Druck im Sitzbereich, bis innerhalb des Dichtsitzdurchmessers wieder Brennraumdruck herrscht. Dadurch kommt es wieder zu den anfangs beschriebenen hohen Dichtkräften am Düsennadelsitz und damit zum sicheren Abdichten der Düsenlöcher gegenüber dem Raildruck. The closing process of the nozzle needle is initiated by the termination of the current supply of the magnetic actuator. The magnetic force drops below the remaining resulting forces on the magnetic needle. The magnetic needle and the subsequently applied intermediate piston move in the direction of the nozzle needle seat. As a result, the pressure forces rise in the pressure chamber above the nozzle needle, which also, after conditioning the magnetic needle on the nozzle needle, is loaded by the spring force of the actuator side of the magnetic needle spring. The result is the closing stroke of the nozzle needle. Towards the end of the movement, the nozzle needle seat throttles the pressure in the seating area until combustion chamber pressure prevails within the sealing seat diameter. This again leads to the initially described high sealing forces on the nozzle needle seat and thus to the reliable sealing of the nozzle holes with respect to the rail pressure.
Eine bevorzugte Ausführungsform der Erfindung wird nachfolgend anhand der einzigen Figur 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 figure. This shows a schematic longitudinal section through a fuel injector according to the invention.
Der dargestellte Kraftstoffinjektor weist einen Magnetaktor 1 zur Betätigung einer in einer Bohrung 2 eines Düsenkörpers 3 hubbeweglich geführten Düsennadel 4 auf. Der Düsenkörper 3 kann alternativ zur dargestellten einteiligen Ausführung auch zweiteilig, vorzugsweise mit einer statischen Dichtstelle auf Höhe eines Steuervolumens 6 ausgeführt sein. Durch die Hubbewegung der Düsennadel 4 ist wenigstens eine Einspritzöffnung 5 des Kraftstoffinjektors freigebbar oder verschließbar, so dass bei freigegebener Einspritzöffnung unter hohem Druck stehender Kraftstoff in den Brennraum der Brennkraftmaschine eingespritzt wird. The illustrated fuel injector has a solenoid actuator 1 for actuating a nozzle needle 4 that is guided in a lift-capable manner in a bore 2 of a nozzle body 3. As an alternative to the illustrated one-piece design, the nozzle body 3 can also be designed in two parts, preferably with a static sealing point at the level of a control volume 6. By the lifting movement of the nozzle needle 4 is at least one injection port 5 of the fuel injector can be opened or closed, so that when released injection port under high pressure fuel is injected into the combustion chamber of the internal combustion engine.
Der Magnetaktor lumfasst eine Magnetnadel 7, die in einer zentralen Bohrung 8 eines Zwischenkolbens 9 hubbeweglich geführt ist. Bei einer Bestromung des Magnetaktors 1 bewegt sich die Magnetnadel 7 entgegen der Kraft einer oberhalb der Magnetnadel 7 angeordneten Feder 16 zum Magnetaktor 1 hin, wobei ein Steuervolumen 6, über welches die Magnetnadel 7 mit der Düsennadel 4 hydraulisch gekoppelt ist eine Vergrößerung erfährt. Der Druck in dem das Steuervolumen 6 definierenden Druckraum sinkt, bis die Kräfte oberhalb und unterhalb der Düsennadel 4 ausgeglichen sind, so dass schließlich der Öffnungshub der Düsennadel 4 initiiert wird. The Magnetaktor lumfasst a magnetic needle 7, which is guided in a central bore 8 of an intermediate piston 9 liftable. When the magnetic actuator 1 is energized, the magnetic needle 7 moves towards the magnetic actuator 1 against the force of a spring 16 arranged above the magnetic needle 7, wherein a control volume 6 via which the magnetic needle 7 is hydraulically coupled to the nozzle needle 4 undergoes an enlargement. The pressure in which the control volume 6 defining pressure chamber decreases until the forces are balanced above and below the nozzle needle 4, so that finally the opening stroke of the nozzle needle 4 is initiated.
Der Zwischenkolben 9, der ebenfalls in der Bohrung 2 des ein- oder zweiteilig ausgeführten Düsenkörpers 3 hubbeweglich geführt ist, liegt während der ersten Phase des Öffnungshubes der Düsennadel 4 am Düsenkörper 3 an. Hierzu weist der Zwischenkolben 9 einen Bundbereich 10 auf, an welchem eine radial verlaufende Anlageflä- che 11 ausgebildet ist. Die Gegenfläche am Düsenkörper 3 bildet zugleich eine Anschlagfläche zur Hubbegrenzung des Zwischenkolbens 9 bei dessen Rückstellung aus. The intermediate piston 9, which is also guided in a liftable manner in the bore 2 of the one or two-part nozzle body 3, rests against the nozzle body 3 during the first phase of the opening stroke of the nozzle needle 4. For this purpose, the intermediate piston 9 has a collar region 10, on which a radially extending contact surface che 11 is formed. The counter surface on the nozzle body 3 also forms a stop surface for limiting the stroke of the intermediate piston 9 during its return.
Der Zwischenkolben 9 ist durch eine erste Feder 12 belastet, deren Federkraft die Bewegung des Zwischenkolbens 9 in Richtung des Magnetaktors 1 unterstützt. Auf diese Weise ist ein zuverlässiger Öffnungsbetrieb gewährleistet. Die Feder 12 ist einerseits am Düsenkörper 3, andererseits an einer radial verlaufenden Schulter 13 des Zwischenkolbens 9 abgestützt. Vorliegend ist die Feder 12 als Schraubendruckfeder ausgebildet, die um den Bundbereich 10 des Zwischenkolbens 9 gelegt ist. The intermediate piston 9 is loaded by a first spring 12 whose spring force supports the movement of the intermediate piston 9 in the direction of the magnetic actuator 1. In this way, a reliable opening operation is ensured. The spring 12 is supported on the one hand on the nozzle body 3, on the other hand on a radially extending shoulder 13 of the intermediate piston 9. In the present case, the spring 12 is designed as a helical compression spring, which is placed around the collar region 10 of the intermediate piston 9.
Des Weiteren ist der Zwischenkolben 9 über eine zweite Feder 14 in Form einer Tellerfeder gegenüber der Magnetnadel 7 abgestützt, so dass die Bewegung des Zwischenkolbens 9 unter anderem auch an die Bewegung der Magnetnadel 7 gekoppelt ist. Gegenüber der Magnetnadel 7 ist die Feder 14 an einer radial verlaufenden Schulter 15 abgestützt. Die Feder 14 dient vorliegend einem Toleranzausgleich. Furthermore, the intermediate piston 9 is supported via a second spring 14 in the form of a plate spring with respect to the magnetic needle 7, so that the movement of the intermediate piston 9 is inter alia also coupled to the movement of the magnetic needle 7. Opposite the magnetic needle 7, the spring 14 is supported on a radially extending shoulder 15. The spring 14 is used here a tolerance compensation.
Gemeinsam mit einer weiteren, die Magnetnadel 7 beaufschlagenden Feder 16, die vorliegend als Schraubendruckfeder ausgebildet ist und aktorseitig an der Magnetnadel 7 anliegt, gewährleistet die Feder 14 ferner, dass sämtliche hubbeweglichen Bauteile in ihre Ausgangslage zurückgestellt werden. So bewirkt insbesondere die Federkraft der die Magnetnadel 7 beaufschlagenden Feder 16, dass die Düsennadel 4 in ihren Sitz zurückgestellt wird. Dabei legt sich die Magnetnadel 7 direkt an die Düsennadel 4 an. Together with a further, the magnetic needle 7 acting spring 16 which is presently designed as a helical compression spring and the actuator side abuts the magnetic needle 7, the spring 14 further ensures that all hubbeweglichen components are returned to their original position. Thus, in particular, the spring force of the magnetic needle 7 acting spring 16 causes the nozzle needle 4 is returned to its seat. In this case, the magnetic needle 7 applies directly to the nozzle needle 4.
Bei einer Bestromung des Magnetaktors 1 bewegt sich die Magnetnadel 7entgegen der Druckkraft der Feder 16 nach oben, das heißt in Richtung des Elektromagneten des Magnetaktors 1. Das Steuervolumen 6 vergrößert sich, der Druck im Steuervolumen 6 fällt. Da die hydraulisch wirksame Fläche A2 der Magnetnadel 7 kleiner als die hydraulisch wirksame Fläche Ai der Düsennadel 4 ist, wird aufgrund des gewählten Flächenverhältnisses während einer ersten Phase des Öffnungshubes der Düsennadel 4 eine Kraftverstärkung bewirkt. Nach dem ersten Anheben der Düsennadel 4 strömt der Kraftstoff auch innerhalb des Düsensitzes unter die Düsennadelspitze. Die Kraft unter der Düsennadel 4 steigt dadurch zunehmend, so dass der Kraftaufwand zum weiteren Heben der Düsennadel 4 sinkt. Dadurch wird die Abstützkraft an der Anlagefläche 11 gleich Null und der Zwischenkolben 9 beginnt der Magnetnadel 7zu folgen. Durch die Ergänzung der Flächen A2 und A3 kommt es zur deutlichen Wegverstärkung gegenüber der ersten Nadelhubphase. When the magnet actuator 1 is energized, the magnet needle 7 moves upwards against the pressure force of the spring 16, that is to say in the direction of the electromagnet of the magnet actuator 1. The control volume 6 increases, the pressure in the control volume 6 drops. Since the hydraulically effective area A 2 of the magnetic needle 7 is smaller than the hydraulically effective area Ai of the nozzle needle 4, a force amplification is effected due to the selected area ratio during a first phase of the opening stroke of the nozzle needle 4. After the first lifting of the nozzle needle 4, the fuel also flows within the nozzle seat below the nozzle needle tip. The force under the nozzle needle 4 increases as a result, so that the force required for further lifting the nozzle needle 4 decreases. As a result, the supporting force on the contact surface 11th equal to zero and the intermediate piston 9 starts to follow the magnetic needle 7. By complementing the surfaces A 2 and A 3 , there is a clear path gain compared to the first Nadelhubphase.
Gleichwohl nur die vergleichsweise geringe Kraft eines einfachen Magnetkreises zur Verfügung steht, vermag der vorgeschlagene Kraftstoffinjektor einen zuverlässigen Öffnungs- und Schließbetrieb zu gewährleisten. In dem kleinen Magnetkreis ist das Magnetfeld zudem schneller auf- und abgebaut. However, only the comparatively low power of a simple magnetic circuit is available, the proposed fuel injector can ensure a reliable opening and closing operation. In the small magnetic circuit, the magnetic field is also built up and dismantled faster.
Der vorgeschlagene Kraftstoffinjektor weist zudem nur wenige Bauteile sowie wenige Verschleißstellen auf. Er ist somit einfach und kostengünstig herzustellen. Ferner verbleibt innerhalb des Kraftstoffinjektors ausreichend Bauraum für großzügige Hochdruckvolumina zur Druckwellenabschwächung. The proposed fuel injector also has only a few components and few wear points. It is thus easy and inexpensive to manufacture. Furthermore, sufficient space within the fuel injector for generous high pressure volumes for pressure wave attenuation remains.

Claims

Patentansprüche claims
1. Kraftstoffinjektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine mit einem Magnetaktor (1) zur Betätigung einer in einer Bohrung (2) eines Düsenkörpers (3) hubbeweglich geführten Düsennadel (4), über deren Hubbewegung wenigstens eine Einspritzöffnung (5) des Kraftstoffinjektors freigebbar oder verschließbar ist, 1. A fuel injector for injecting fuel into a combustion chamber of an internal combustion engine with a solenoid actuator (1) for actuating a in a bore (2) of a nozzle body (3) hubbeweglich guided nozzle needle (4) via the lifting movement at least one injection port (5) of the fuel injector is releasable or lockable,
dadurch gekennzeichnet, dass die Düsennadel (4) eine hydraulisch wirksame Fläche Ai besitzt, die ein Steuervolumen (6) axial begrenzt, über welches die Düsennadel (4) mit einer vorzugsweise koaxial angeordneten Magnetnadel (7) hydraulisch koppelbar ist, die in einer zentralen Bohrung (8) eines Zwischenkolbens (9) hubbeweglich geführt ist und eine das Steuervolumen (6) axial begrenzende hydraulisch wirksame Fläche A2 besitzt, die kleiner als die Fläche Ai der Düsennadel (4) ist, so dass die hydraulische Kopplung während einer ersten Phase des Öffnungshubes der Düsennadel (4) eine Kraftverstärkung bewirkt. characterized in that the nozzle needle (4) has a hydraulically effective area Ai, which axially limits a control volume (6), via which the nozzle needle (4) with a preferably coaxial magnetic needle (7) is hydraulically coupled, in a central bore (8) of an intermediate piston (9) is guided in a liftable manner and has a control volume (6) axially delimiting hydraulically effective area A 2 , which is smaller than the area Ai of the nozzle needle (4), so that the hydraulic coupling during a first phase of the Opening stroke of the nozzle needle (4) causes a force boost.
2. Kraftstoffinjektor nach Anspruch 1, 2. Fuel injector according to claim 1,
dadurch gekennzeichnet, dass die Düsennadel (4) während einer zweiten Phase ihres Öffnungshubes mit dem Zwischenkolben (9), der eine das Steuervolumen (6) axial begrenzende hydraulisch wirksame Fläche A3 besitzt und vorzugsweise ebenfalls in der Bohrung (2) des Düsenkörpers (3) hubbeweglich geführt ist, hydraulisch koppelbar ist, wobei die hydraulische Kopplung während der zweiten Phase des Öffnungshubes im Vergleich zur ersten Phase eine Wegverstärkung bewirkt. characterized in that the nozzle needle (4) during a second phase of its opening stroke with the intermediate piston (9) having a control volume (6) axially delimiting hydraulically effective area A 3 and preferably also in the bore (2) of the nozzle body (3 ) is hydraulically coupled, wherein the hydraulic coupling during the second phase of the opening stroke compared to the first phase causes a Wegverstärkung.
3. Kraftstoffinjektor nach Anspruch 1 oder 2, 3. Fuel injector according to claim 1 or 2,
dadurch gekennzeichnet, dass sich während der zweiten Phase des Öffnungshubes der Düsennadel (4) die hydraulisch wirksamen Flächen A2 und A3 der Magnetnadel (7) und des Zwischenkolbens (9) derart ergänzen, dass die Summe der Flächen A2 und A3 größer oder gleich der hydraulisch wirksamen Fläche Ai der Düsennadel (4) ist. characterized in that during the second phase of the opening stroke of the nozzle needle (4), the hydraulically active surfaces A 2 and A 3 of the magnetic needle (7) and the intermediate piston (9) complement each other such that the sum the areas A 2 and A 3 is greater than or equal to the hydraulically effective area Ai of the nozzle needle (4).
4. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, 4. Fuel injector according to one of the preceding claims,
dadurch gekennzeichnet, dass der Zwischenkolben (9) als Stufenkolben ausgebildet ist und einen Bundbereich (10) mit einer radial verlaufenden Anlagefläche (11) besitzt, mittels welcher der Zwischenkolben (9) vorzugsweise am Düsenkörper (3) abgestützt ist.  characterized in that the intermediate piston (9) is formed as a stepped piston and a collar portion (10) having a radially extending contact surface (11), by means of which the intermediate piston (9) is preferably supported on the nozzle body (3).
5. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, 5. Fuel injector according to one of the preceding claims,
dadurch gekennzeichnet, dass der Zwischenkolben (9) mit einer in Richtung des Magnetaktors (1) wirkenden Druckkraft einer Feder (12) beaufschlagt wird, die vorzugsweise als Schraubendruckfeder ausgebildet ist und den Bundbereich (10) des Zwischenkolbens (9) umgibt.  characterized in that the intermediate piston (9) is acted upon by a pressure force acting on a spring (12) in the direction of the magnetic actuator (1), which is preferably designed as a helical compression spring and surrounds the collar region (10) of the intermediate piston (9).
6. Kraftstoffinjektor nach Anspruch 5, 6. Fuel injector according to claim 5,
dadurch gekennzeichnet, dass zur Abstützung der Feder (12) der Bundbereich (10) eine radial verlaufende Schulter (13) aufweist.  characterized in that for supporting the spring (12) of the collar portion (10) has a radially extending shoulder (13).
7. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, 7. Fuel injector according to one of the preceding claims,
dadurch gekennzeichnet, dass der Zwischenkolben (9) über eine Feder (14) gegenüber der Magnetnadel (7) abgestützt ist, wobei die Feder (14) vorzugsweise als Tellerfeder ausgebildet ist, die an einer radial verlaufenden Schulter (15) der Magnetnadel (7) abgestützt ist.  characterized in that the intermediate piston (9) via a spring (14) relative to the magnetic needle (7) is supported, wherein the spring (14) is preferably designed as a plate spring, which at a radially extending shoulder (15) of the magnetic needle (7) is supported.
8. Kraftstoffinjektor nach einem der vorhergehenden Ansprüche, 8. Fuel injector according to one of the preceding claims,
dadurch gekennzeichnet, dass die Magnetnadel (7) von der Druckkraft einer Feder (16) beaufschlagt wird, die eine Rückstellung der Magnetnadel (7) während des Schließhubes der Düsennadel (4) bewirkt.  characterized in that the magnetic needle (7) is acted upon by the pressure force of a spring (16) which causes a return of the magnetic needle (7) during the closing stroke of the nozzle needle (4).
EP10767992.0A 2009-12-07 2010-10-07 Fuel injector Not-in-force EP2510220B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910047560 DE102009047560A1 (en) 2009-12-07 2009-12-07 fuel injector
PCT/EP2010/064968 WO2011069707A1 (en) 2009-12-07 2010-10-07 Fuel injector

Publications (2)

Publication Number Publication Date
EP2510220A1 true EP2510220A1 (en) 2012-10-17
EP2510220B1 EP2510220B1 (en) 2014-12-10

Family

ID=43265776

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10767992.0A Not-in-force EP2510220B1 (en) 2009-12-07 2010-10-07 Fuel injector

Country Status (3)

Country Link
EP (1) EP2510220B1 (en)
DE (1) DE102009047560A1 (en)
WO (1) WO2011069707A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010041013A1 (en) * 2010-09-20 2012-03-22 Robert Bosch Gmbh fuel injector
DE102012224387A1 (en) 2012-12-27 2014-07-03 Robert Bosch Gmbh Fuel injection valve for internal combustion engine, has control chamber limited by front end of nozzle needle, where total area of pressure exposed to front ends of control pistons is smaller than area of pressure exposed to end of needle
DE102013209304A1 (en) 2013-05-21 2014-11-27 Robert Bosch Gmbh Fuel injector with directly controlled nozzle needle

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19963568A1 (en) * 1999-12-29 2001-07-05 Bosch Gmbh Robert Fuel injector
US6910644B2 (en) 2001-12-26 2005-06-28 Toyota Jidosha Kabushiki Kaisha Solenoid-operated fuel injection valve
DE102004035280A1 (en) * 2004-07-21 2006-03-16 Robert Bosch Gmbh Fuel injector with direct multi-stage injection valve element control
DE102007002758A1 (en) * 2006-04-04 2007-10-11 Robert Bosch Gmbh fuel injector
DE102007029969A1 (en) 2007-06-28 2009-01-08 Robert Bosch Gmbh Fast-acting fuel injector for high injection pressures

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2011069707A1 *

Also Published As

Publication number Publication date
DE102009047560A1 (en) 2011-06-09
WO2011069707A1 (en) 2011-06-16
EP2510220B1 (en) 2014-12-10

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