EP2510220B1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP2510220B1
EP2510220B1 EP10767992.0A EP10767992A EP2510220B1 EP 2510220 B1 EP2510220 B1 EP 2510220B1 EP 10767992 A EP10767992 A EP 10767992A EP 2510220 B1 EP2510220 B1 EP 2510220B1
Authority
EP
European Patent Office
Prior art keywords
needle
nozzle needle
fuel injector
intermediate piston
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.)
Not-in-force
Application number
EP10767992.0A
Other languages
German (de)
English (en)
Other versions
EP2510220A1 (fr
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2510220A1 publication Critical patent/EP2510220A1/fr
Application granted granted Critical
Publication of EP2510220B1 publication Critical patent/EP2510220B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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 with the features of the preamble of claim 1 such as in the DE 10 2007 002 758 shown.
  • a fuel injector has a magnetic actuator for actuating a nozzle needle, which is guided in a liftable manner in a bore of a nozzle body, via the lifting movement of which at least one injection opening of the fuel injector can be opened or closed.
  • magnetic actuators as a pressure plate in today's fuel injectors has been proven to the extent that 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 has 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 A 1 , which limits a control volume axially, via which the nozzle needle with a preferably coaxially arranged magnetic needle is hydraulically coupled, the in a central bore of an intermediate piston is guided in a stroke and has a control volume axially delimiting hydraulically effective area A 2 , which is smaller than the area A 1 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 force 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 A 1 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 Injektortownen.
  • 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 a larger nozzle needle stroke, so that a complete seat throttling is possible or 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 atomization 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 A 1 . While opposing equal areas cause a 1/1 translation 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 A 1 . 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 may also be formed as a helical compression spring which is supported on the one hand on the actuator end of the magnetic needle, on the other hand on the housing of the injector.
  • 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 active surfaces of the magnetic needle and the intermediate piston, it is no longer necessary to meet the mass balance that the 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 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 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.

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

Claims (8)

  1. Injecteur de carburant pour l'injection de carburant dans une chambre de combustion d'un moteur à combustion interne comprenant un actionneur magnétique (1) pour l'actionnement d'une aiguille d'injecteur (4) guidée de manière à pouvoir effectuer un mouvement de va-et-vient dans un alésage (2) d'un corps d'injecteur (3), par le biais du mouvement de va-et-vient de laquelle aiguille d'injecteur au moins une ouverture d'injection (5) de l'injecteur de carburant peut être libérée ou peut être fermée,
    l'aiguille d'injecteur (4) présentant une surface hydrauliquement active A1 qui limite axialement un volume de commande (6) par le biais duquel l'aiguille d'injecteur (4) peut être accouplée hydrauliquement à une aiguille magnétique (7) disposée de préférence de manière coaxiale, laquelle aiguille magnétique est guidée de manière à pouvoir effectuer un mouvement de va-et-vient dans un alésage central (8) d'un piston intermédiaire (9) et présente une surface hydrauliquement active A2 limitant axialement le volume de commande (6), laquelle est plus petite que la surface A1 de l'aiguille d'injecteur (4), de telle sorte que l'accouplement hydraulique provoque une amplification de force pendant une première phase de la course d'ouverture de l'aiguille d'injecteur (4), le piston intermédiaire (9) étant guidé de manière à pouvoir effectuer un mouvement de va-et-vient dans l'alésage (2).
  2. Injecteur de carburant selon la revendication 1, caractérisé en ce que l'aiguille d'injecteur (4) peut être accouplée hydrauliquement, pendant une deuxième phase de sa course d'ouverture, au piston intermédiaire (9) qui présente une surface hydrauliquement active A3 limitant axialement le volume de commande (6), l'accouplement hydraulique provoquant une amplification de course pendant la deuxième phase de la course d'ouverture par comparaison avec la première phase.
  3. Injecteur de carburant selon la revendication 2, caractérisé en ce que, pendant la deuxième phase de la course d'ouverture de l'aiguille d'injecteur (4), les surfaces hydrauliquement actives A2 et A3 de l'aiguille magnétique (7) et du piston intermédiaire (9) se complètent de telle sorte que la somme des surfaces A2 et A3 soit supérieure ou égale à la surface hydrauliquement active A1 de l'aiguille d'injecteur (4).
  4. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que le piston intermédiaire (9) est réalisé sous forme de piston étagé et présente une région de collet (10) comprenant une surface d'appui (11) s'étendant radialement, au moyen de laquelle le piston intermédiaire (9) s'appuie de préférence contre le corps d'injecteur (3).
  5. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que le piston intermédiaire (9) est sollicité par une force de pression d'un ressort (12) agissant en direction de l'actionneur magnétique (1), lequel ressort est réalisé de préférence sous forme de ressort hélicoïdal de compression et entoure la région de collet (10) du piston intermédiaire (9).
  6. Injecteur de carburant selon la revendication 5, caractérisé en ce que la région de collet (10) comprend un épaulement (13) s'étendant radialement pour l'appui du ressort (12).
  7. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que le piston intermédiaire (9) est supporté par le biais d'un ressort (14) par rapport à l'aiguille magnétique (7), le ressort (14) étant réalisé de préférence sous forme de ressort diaphragme qui s'appuie contre un épaulement (15) s'étendant radialement de l'aiguille magnétique (7).
  8. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que l'aiguille magnétique (7) est sollicitée par la force de pression d'un ressort (16) qui provoque un rappel de l'aiguille magnétique (7) pendant la course de fermeture de l'aiguille d'injecteur (4).
EP10767992.0A 2009-12-07 2010-10-07 Injecteur de carburant Not-in-force EP2510220B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910047560 DE102009047560A1 (de) 2009-12-07 2009-12-07 Kraftstoffinjektor
PCT/EP2010/064968 WO2011069707A1 (fr) 2009-12-07 2010-10-07 Injecteur de carburant

Publications (2)

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

Family

ID=43265776

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10767992.0A Not-in-force EP2510220B1 (fr) 2009-12-07 2010-10-07 Injecteur de carburant

Country Status (3)

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

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010041013A1 (de) * 2010-09-20 2012-03-22 Robert Bosch Gmbh Kraftstoffinjektor
DE102012224387A1 (de) 2012-12-27 2014-07-03 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102013209304A1 (de) 2013-05-21 2014-11-27 Robert Bosch Gmbh Kraftstoffinjektor mit direkt gesteuerter Düsennadel

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19963568A1 (de) * 1999-12-29 2001-07-05 Bosch Gmbh Robert Brennstoffeinspritzventil
US6910644B2 (en) 2001-12-26 2005-06-28 Toyota Jidosha Kabushiki Kaisha Solenoid-operated fuel injection valve
DE102004035280A1 (de) * 2004-07-21 2006-03-16 Robert Bosch Gmbh Kraftstoffinjektor mit direkter mehrstufiger Einspritzventilgliedansteuerung
DE102007002758A1 (de) * 2006-04-04 2007-10-11 Robert Bosch Gmbh Kraftstoffinjektor
DE102007029969A1 (de) 2007-06-28 2009-01-08 Robert Bosch Gmbh Schnellschaltender Kraftstoffinjektor für hohe Einspritzdrücke

Also Published As

Publication number Publication date
DE102009047560A1 (de) 2011-06-09
EP2510220A1 (fr) 2012-10-17
WO2011069707A1 (fr) 2011-06-16

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