EP2503138B1 - Injecteur de carburant commandé électriquement pour grands moteurs diesel - Google Patents

Injecteur de carburant commandé électriquement pour grands moteurs diesel Download PDF

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Publication number
EP2503138B1
EP2503138B1 EP11159584.9A EP11159584A EP2503138B1 EP 2503138 B1 EP2503138 B1 EP 2503138B1 EP 11159584 A EP11159584 A EP 11159584A EP 2503138 B1 EP2503138 B1 EP 2503138B1
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EP
European Patent Office
Prior art keywords
needle
fuel injector
flow restrictor
injector according
control chamber
Prior art date
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Application number
EP11159584.9A
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German (de)
English (en)
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EP2503138A1 (fr
Inventor
Marco Coppo
Claudio Negri
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OMT Officine Meccaniche Torino SpA
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OMT Officine Meccaniche Torino SpA
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Application filed by OMT Officine Meccaniche Torino SpA filed Critical OMT Officine Meccaniche Torino SpA
Priority to EP11159584.9A priority Critical patent/EP2503138B1/fr
Priority to PL11159584T priority patent/PL2503138T3/pl
Priority to DK11159584.9T priority patent/DK2503138T3/da
Priority to KR1020120020238A priority patent/KR101557521B1/ko
Priority to JP2012067071A priority patent/JP5890714B2/ja
Priority to CN201210078775.1A priority patent/CN102691605B/zh
Publication of EP2503138A1 publication Critical patent/EP2503138A1/fr
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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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • the present invention relates to an electrically-controlled fuel injector for large diesel engines.
  • the invention relates in particular to a fuel injector for common-rail injection systems for large two-stroke diesel engines, such as diesel engines for marine propulsion.
  • a common-rail high-pressure injection system comprises a pump, usually with a fixed displacement, designed to pressurize the fuel in a high-pressure accumulator (common-rail), which supplies the injectors.
  • the injectors are equipped with a valve seat and with a needle which can move in the injector body between a closed position and an open position. The position of the needle is determined by the intensity of two hydraulic forces, which are generated by the action of pressurized fluid on appropriate surfaces of influence.
  • the pressurized fuel in a delivery chamber upstream of the valve seat acts in the direction of raising the needle from its seat and hence in the opening direction.
  • An electrically-operated control valve modulates the hydraulic pressure in a control chamber, which generates a force acting in the direction of closing the injector.
  • the activation of the control valve causes a reduction of the pressure in the control chamber to the point where the force acting to open the injector seat prevails over the force acting to close the injector seat, causing the needle to rise from the valve seat and hence fuel injection.
  • control chamber is connected to the high-pressure line by means of an inlet flow restrictor and to a discharge line by means of an outlet flow restrictor.
  • the sizes of the inlet and outlet flow restrictors must be chosen so that, when the control valve is opened, the pressure in the control chamber can drop to values low enough to make sure that the force in the closing direction becomes smaller than the one in the opening direction. Once this happens, the needle opens the injector seat, thus enabling fuel passage to the chamber downstream of the injector seat (the so-called sac), from which fuel is injected in the combustion chamber through the injection holes.
  • control valve position When the injector needs to be closed the control valve position is reset, thereby disabling the connection between the control chamber and the low pressure fuel line.
  • the control chamber pressure rises again but, for the reasons explained above, it needs to reach a much higher value than the one necessary to initiate the opening phase before the needle starts moving again towards its seat.
  • the needle speed during the closing phase is constrained by technical requirements, and the desired value can be achieved with the right sizing of the inlet flow restrictor in relation to the cross section area of the needle in the control chamber.
  • a larger outlet flow restrictor poses more problems in terms of control valve design and injector efficiency because in two-way poppet valves commonly used in these applications the control chamber pressure acts in the direction of opening the valve.
  • a larger outlet flow restrictor requires a larger poppet (otherwise the passage through the valve becomes the main restriction), and this leads to larger surfaces of influence of the control chamber pressure. In the end, this increases the force demands on the spring (to keep the valve closed in absence of the command signal) and on the actuator that needs to overcome the spring force. This also implies that larger components must be used, and this is not always acceptable due to geometrical constraints on the engine, and control valve speed requirements (for example, larger and stronger solenoids are usually slower).
  • the object of the present invention is to provide a solution to the problems described above.
  • the present invention allows to optimise the performance of electronic injectors for large diesel engines.
  • the invention allows to minimise the control flow rate that the electronic control valve needs to discharge to keep the injector open during the injection cycle.
  • an injection system for a diesel engine is indicated by the reference number 10.
  • the injection system comprises a feed pump 12 which intakes fuel from a low pressure fuel tank 14 and delivers pressurized fuel to a high-pressure common rail 16.
  • the common rail 16 is connected to a plurality of high-pressure pipes 18 (only one of which is shown in figure 1 ), each of which is connected to a respective injector 20.
  • the injector 20 comprises a body 22 having a delivery chamber 24 connected to the high-pressure pipe 18 through a fuel supply line 26.
  • the delivery chamber 24 is provided with a conical valve seat 28.
  • the injector 20 comprises a needle 30 extending through the delivery chamber 24 and having a conical sealing surface 32 cooperating with the valve seat 28.
  • the needle 30 is movable along a longitudinal axis A between a closed position and an open position. In the closed position the sealing surface 32 abuts against the valve seat 28 and in the open position the sealing surface 32 is spaced apart from the valve seat 28.
  • a spring 34 pushes the injector needle 30 towards the closed position.
  • the hydraulic pressure of the fuel contained in the delivery chamber 24 generates a first hydraulic force pushing the injector needle 30 towards its open position.
  • the body 22 comprises an atomizer 36 having a longitudinal bore or sac 38 in fluid communication with the delivery chamber 24 through the valve seat 28.
  • the atomizer has one or more injection holes 40.
  • the needle 30 has a slide valve 42 which extends into the sac 38.
  • the injector 20 has a control chamber 44 sealed from the delivery chamber 24.
  • the control chamber 44 is connected to the fuel supply line 26 through an inlet line 46 including an inlet flow restrictor 48.
  • the control chamber 44 is also connected to a discharge line 50 including an outlet flow restrictor 52.
  • the hydraulic pressure into the control chamber 44 generates a second hydraulic force pushing the injector needle 30 towards its closed position.
  • An electrically-operated two-way control valve 54 selectively opens and closes hydraulic communication between the control chamber 44 and a low pressure volume, for instance formed by the tank reservoir 14.
  • the control valve 54 is controlled by an electric actuator 56, which receives control signals by an electronic control unit 58.
  • the pressure in the control chamber 44 and in the delivery chamber 24 is equal to the rail pressure. Given that the surface of influence of the pressure in the control chamber 44 is larger than the one in the delivery chamber 24, the force pushing the needle 30 towards its closed position is greater than the force pushing the needle 30 towards its open position.
  • the control valve 54 is open, the pressure in the control chamber 44 is reduced and the force pushing the needle 30 towards its open position becomes greater than the force pushing the needle 30 towards its closed position.
  • the needle 30 moves away from the valve seat 28, the pressurized fuel contained in the delivery chamber 24 is admitted into the sac 38 of the atomizer 36 and it is injected through the injection holes 40 once the needle has been lifted enough for the slide valve to uncover them.
  • the present invention provides a design in which the inlet flow restrictor 48 includes a variable choking section, movable between a choked position corresponding to a fully closed position of the injection needle 30 an un-choked position corresponding to a position of initial opening of the needle 30. Therefore, the inlet flow restrictor 48 is considerably choked when the needle 30 abuts against the valve seat 28. The choking is then reduced and eventually eliminated in the first stage of the needle stroke.
  • the arrow 60 schematically represents the variable choking section of the inlet flow restrictor 48 and the dotted line 62 represents the fact that the variable choking section 60 is controlled by the movement of the needle 30.
  • the inlet flow restrictor 48 comprises at least one orifice movable with the needle 30 and the variable choking section 60 comprises a gap formed between a first surface movable with the needle 30 and a second surface fixed with respect to the body 22.
  • a smaller outlet flow restrictor 52 is enough to bring the pressure in the control chamber 52 to a level sufficient to trigger the injector opening.
  • any size of the outlet flow restrictor 52 would be sufficient to completely discharge the control chamber 44 (it would only be a matter of time). Then, when the needle 30 lifts and the opening force increases due to sac pressurisation, the inlet flow restrictor 48 opens fully and the pressure of the control chamber 44 stabilises at a value closer to the level at which the closing phase would begin.
  • the solution according to the present invention has the additional benefit of reducing the injector switching time, because the pressure level in the control chamber 44 during the injection is kept close to the level necessary to trigger injector closure, which is important in multi-shot and ultra low load operation.
  • a first embodiment of the present invention is shown in Figure 2 .
  • the body 22 comprises a locking nut 64, a lower body portion 66, an intermediate body portion 68 and an upper body portion 70.
  • the body portions 66 and 68 are fixed to the upper body portion 70 by means of the locking nut 64.
  • the atomizer 36 is fixed to the lower body portion 66 by means of a threaded bush 72.
  • the needle 30 is slidably guided into a bushing 74 carried by the lower body portion 66.
  • the spring 34 is housed into the delivery chamber 24 and is compressed between the bushing 74 and a radial shoulder of the needle 30.
  • the control chamber 44 is contoured by a top front surface of the needle 30, a cylindrical wall portion of the bushing 74 and a front surface of the intermediate portion 68.
  • the outlet flow restrictor is formed by an orifice 52 formed in the intermediate body portion.
  • the control valve 54 comprises an axially movable stem 76 which is slidable into a guide bore 78 of the intermediate body portion 68.
  • the electric actuator 56 includes a magnetic core 80 and a coil 82.
  • the inlet flow restrictor 48 comprises one or more orifices 84 formed in the area of the needle 30 bearing the conical sealing surface 32.
  • the or each orifice 84 has a radially inner end communicating with an elongated bore 86 formed into the needle 30.
  • the upper end of the elongated bore 86 opens into the control chamber 44.
  • the radially outer end of the or each orifice 84 is open on the conical sealing surface 32 of the needle 30, immediately above the area where the sealing surface 32 abuts the valve seat 28.
  • variable choking section 60 is formed by a gap 88 formed between the sealing surface 32 of the needle 30 and the valve seat 28.
  • the size of the gap 88 is minimum when the needle 30 is closed and increases as the needle moves away from the valve seat 28. Accordingly, the or each orifice 84 is choked when the needle is closed and becomes un-choked after an initial opening of the needle 30.
  • the elongated bore that connects the inlet flow restrictor 48 to the control chamber 44 plays an active role in ensuring the proper functionality of the invention by delaying the response of the inlet flow restrictor 48 to a drop of pressure in the control chamber 44 by the time it takes for the depression wavefront to travel from the control chamber 44 to the inlet flow restrictor 48 outlet and back. This allows enough time for pressurisation of the sac 38, thereby managing to open the needle 30 with the smallest possible size of the outlet flow restrictor 52.
  • a remarkable advantage of this solution is that its cost of implementation is negligible as it uses a seat that is already present in the injector.
  • an injector using the present invention can operate with up to 60% less control flow rate which, in terms of overall engine efficiency, is equivalent to a 0.26% increase.
  • the main benefit to be gained by such optimisation is the reduction of the forces needed to seal and operate the control valve 44, which allows to use fast and compact actuators that can be integrated in the injector body. This is essential for obtaining an injector that can operate with the fast switching times required in multi-shot mode.
  • FIG. 4 A second embodiment of the present invention is shown in figure 4 .
  • the elements corresponding to the ones previously disclosed are indicated by the same reference numbers.
  • the solution shown in figure 4 is a more conventional common rail injector arrangement in which a separate control piston 90 is used to keep the needle 30 closed.
  • the lower end of the control piston 90 abuts against the upper end of the needle 30.
  • the control piston 90 moves axially together with the needle 30.
  • the body 22 comprises a sleeve 92 set between the lower body portion 66 and the intermediate body portion 68.
  • the spring 34 is set in a low pressure chamber formed between the sleeve 92 and the control piston 90.
  • the control chamber 44 is contoured by a top front surface of the control piston 90, a cylindrical wall portion of the sleeve 92 and a front surface of the intermediate portion 68.
  • the outlet flow restrictor is formed by an orifice 52 formed in the intermediate body portion 68.
  • the control valve 54 remains unchanged with respect to the first embodiment.
  • the inlet flow restrictor 48 comprises a first annular groove 94 formed on a cylindrical inner surface 96 of the sleeve 92 and a second annular groove 98 formed on a cylindrical outer surface 100 of the control piston 90.
  • the first annular groove 94 is connected to the fuel supply line 26 by a first orifice 102 formed in the sleeve 92.
  • the second annular groove 98 is connected to the control chamber 44 by means of second and third orifices 104 and 106 formed in the control piston 90.
  • variable choking section 60 is formed by an annular gap 108 formed between the cylindrical inner surface 96 of the sleeve 92 and the cylindrical outer surface 100 of the control piston 90.
  • the control chamber 44 communicates with the fuel supply line 26 through two paths: one including the annular gap 108, the first annular groove 94 and the first orifice 102, the other including the third and second orifices 106 and 104, the second annular groove 98, the annular gap 108, the first annular groove 94 and the first orifice 102.
  • the annular gap 108 chokes the inlet flow restrictor 48 in the closed position of the needle 30. During the initial opening of the needle 30 the choking of the inlet flow restrictor is eliminated as the first and second annular grooves 94, 98 overlap.
  • the size of the annular gap 108 and the length of overlap between the first and second annular grooves 94, 98 are conveniently chosen to allow the pressurisation of the sac 38 before a significant flow rate through the inlet flow restrictor 48 is established.
  • the second embodiment is simpler in construction and offers the additional flexibility of choosing different diameters for needle 30 and control chamber 44.
  • the second embodiment has the disadvantage that high pressure fuel leakages occur when the injector is closed, due to the fuel flow within the clearances between needle, control piston and their respective sleeves, that ends up in the spring chamber and, from there, it is discharged to tank.

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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)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (11)

  1. Injecteur de carburant commandé électriquement pour gros moteurs diesels, comprenant :
    un corps (22) ayant une chambre de distribution (24) raccordée à une conduite d'alimentation en carburant (26) et doté d'un siège de soupape conique (28) ;
    une aiguille (30) s'étendant à travers ladite chambre de distribution (24) et ayant une surface d'étanchéité conique (32) coopérant avec ledit siège de soupape (28), l'aiguille (30) étant mobile le long d'un axe longitudinal (A) entre une position fermée dans laquelle ladite surface d'étanchéité conique (32) vient en butée contre ledit siège de soupape conique (28) et une position ouverte dans laquelle ladite surface d'étanchéité conique (32) est éloignée dudit siège de soupape conique (28), dans lequel la pression hydraulique dans ladite chambre de distribution (24) génère une première force hydraulique poussant l'aiguille (30) vers sa position ouverte ;
    une chambre de commande (44) raccordée à ladite conduite d'alimentation en carburant (26) par un limiteur d'écoulement d'entrée (48) et raccordée à une conduite de décharge (50) par un limiteur d'écoulement de sortie (52), dans lequel la pression hydraulique dans ladite chambre de commande (44) génère une seconde force hydraulique poussant l'aiguille (30) vers sa position fermée ;
    une soupape de commande actionnée électriquement (54) pour ouvrir et fermer sélectivement la communication hydraulique entre ladite chambre de commande (44) et un volume à basse pression (14) par la conduite de décharge (50) ;
    caractérisé en ce que ledit limiteur d'écoulement d'entrée (48) comprend une section d'étranglement variable (60), mobile entre une position étranglée correspondant à une position complètement fermée de l'aiguille (30) et une position non étranglée correspondant à une ouverture initiale de l'aiguille (30).
  2. Injecteur de carburant selon la revendication 1, caractérisé en ce que ledit limiteur d'écoulement d'entrée (48) comprend au moins un orifice (84 ; 104, 106) mobile avec l'aiguille (30) et en ce que ladite section d'étranglement variable (60) comprend un espace (88 ; 108) formé entre une surface (32 ; 100) mobile avec l'aiguille (30) et une surface (28 ; 96) fixe par rapport au corps (22).
  3. Injecteur de carburant selon la revendication 2, caractérisé en ce que ledit limiteur d'écoulement d'entrée (48) comprend au moins un orifice (84) formé dans une zone de l'aiguille (30) supportant ladite surface d'étanchéité conique (32).
  4. Injecteur de carburant selon la revendication 3, caractérisé en ce que ledit orifice (84) a une extrémité radialement interne communiquant avec un alésage allongé (86) formé dans l'aiguille (30), l'alésage allongé (86) ayant une extrémité supérieure ouverte dans ladite chambre de commande (44).
  5. Injecteur de carburant selon la revendication 3, caractérisé en ce que ledit orifice (84) a une extrémité radialement externe ouverte sur la surface d'étanchéité conique (32) de l'aiguille (30), immédiatement au-dessus de la zone où la surface d'étanchéité (32) vient en butée contre le siège de soupape (28).
  6. Injecteur de carburant selon l'une quelconque des revendications 2 à 5, caractérisé en ce que ladite section d'étranglement variable (60) est formée par un espace (88) formé entre la surface d'étanchéité conique (32) de l'aiguille (30) et le siège de soupape conique (28).
  7. Injecteur de carburant selon la revendication 2, caractérisé en ce qu'un piston de commande (90) est guidé de manière coulissante dans un manchon (92) et est mobile avec l'aiguille (30), le piston de commande (90) étant placé entre la chambre de commande (44) et l'aiguille (30).
  8. Injecteur de carburant selon la revendication 7, caractérisé en ce que le limiteur d'écoulement d'entrée (48) comprend une première rainure annulaire (94) formée sur une surface interne cylindrique (96) dudit manchon (92) et une seconde rainure annulaire (98) formée sur une surface externe cylindrique (100) du piston de commande (90).
  9. Injecteur de carburant selon la revendication 8, caractérisé en ce que la première rainure annulaire (94) est raccordée à la conduite d'alimentation en carburant (26) par un premier orifice (102) formé dans le manchon (92) et la seconde rainure annulaire (98) est raccordée à la chambre de commande (44) au moyen de deuxième et troisième orifices (104, 106) formés dans le piston de commande (90).
  10. Injecteur de carburant selon la revendication 9, caractérisé en ce que, dans la position fermée de l'aiguille (30), les première et seconde rainures annulaires (94, 98) sont décalées l'une de l'autre, et dans une position d'ouverture initiale de l'aiguille (30), les première et seconde rainures annulaires (94, 98) se chevauchent au moins partiellement.
  11. Injecteur de carburant selon l'une quelconque des revendications 8 à 10, caractérisé en ce que la section d'étranglement variable (60) est formée par un espace annulaire (108) formé entre la surface interne cylindrique (96) du manchon (92) et la surface externe cylindrique (100) du piston de commande (90).
EP11159584.9A 2011-03-24 2011-03-24 Injecteur de carburant commandé électriquement pour grands moteurs diesel Active EP2503138B1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP11159584.9A EP2503138B1 (fr) 2011-03-24 2011-03-24 Injecteur de carburant commandé électriquement pour grands moteurs diesel
PL11159584T PL2503138T3 (pl) 2011-03-24 2011-03-24 Sterowany elektrycznie wtryskiwacz paliwa do dużych silników wysokoprężnych
DK11159584.9T DK2503138T3 (da) 2011-03-24 2011-03-24 Elektrisk styret brændstofindsprøjtningsindretning til store dieselmotorer
KR1020120020238A KR101557521B1 (ko) 2011-03-24 2012-02-28 대형 디젤엔진용 전기제어식 연료인젝터
JP2012067071A JP5890714B2 (ja) 2011-03-24 2012-03-23 大型ディーゼルエンジンのための電子制御式燃料噴射装置
CN201210078775.1A CN102691605B (zh) 2011-03-24 2012-03-23 用于大型柴油发动机的电控燃料喷射器

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP11159584.9A EP2503138B1 (fr) 2011-03-24 2011-03-24 Injecteur de carburant commandé électriquement pour grands moteurs diesel

Publications (2)

Publication Number Publication Date
EP2503138A1 EP2503138A1 (fr) 2012-09-26
EP2503138B1 true EP2503138B1 (fr) 2013-05-08

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EP (1) EP2503138B1 (fr)
JP (1) JP5890714B2 (fr)
KR (1) KR101557521B1 (fr)
CN (1) CN102691605B (fr)
DK (1) DK2503138T3 (fr)
PL (1) PL2503138T3 (fr)

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KR101821228B1 (ko) 2015-04-22 2018-01-23 맨 디젤 앤드 터보 필리얼 아프 맨 디젤 앤드 터보 에스이 티스크랜드 대형 2행정 자체점화 내연기관용 연료 밸브

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DE102012220610B4 (de) 2012-11-13 2015-04-02 Continental Automotive Gmbh Injektor
CN104196665B (zh) * 2014-08-29 2017-06-23 龙口龙泵燃油喷射有限公司 一种高压共轨喷油器
KR101695092B1 (ko) 2015-06-04 2017-01-10 주식회사 현대케피코 니들 흔들림 방지구조를 가지는 인젝터
EP3181889A1 (fr) * 2015-12-15 2017-06-21 Winterthur Gas & Diesel AG Procédé pour injecter un carburant dans un moteur diesel de grande dimension, grand moteur diesel et dispositif d'injection
EP3486475A1 (fr) * 2017-11-15 2019-05-22 Winterthur Gas & Diesel AG Dispositif d'injection et procédé pour injecter un carburant dans un cylindre et moteur diesel de grande dimension
DE102018217761A1 (de) * 2018-10-17 2020-04-23 Robert Bosch Gmbh Kraftstoffinjektor
DE102018217723A1 (de) * 2018-10-17 2020-04-23 Robert Bosch Gmbh Kraftstoffinjektor, Verfahren zum Betreiben eines Kraftstoffinjektors

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JP3729239B2 (ja) * 1999-02-18 2005-12-21 三菱ふそうトラック・バス株式会社 蓄圧式燃料噴射制御装置
JP4188539B2 (ja) * 1999-09-22 2008-11-26 三菱ふそうトラック・バス株式会社 蓄圧式燃料噴射装置
DE10160262A1 (de) * 2001-12-07 2003-06-18 Bosch Gmbh Robert Injektor, insbesondere für Common-Rail-Einspritzsysteme von Dieselmotoren
DE10160490B4 (de) * 2001-12-08 2005-10-06 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung, Kraftstoffsystem sowie Brennkraftmaschine
JP4241601B2 (ja) * 2004-12-20 2009-03-18 株式会社デンソー 燃料噴射装置および燃料噴射方法
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JP4772016B2 (ja) 2007-09-07 2011-09-14 トヨタ自動車株式会社 内燃機関の燃料噴射制御装置
DE102008014251A1 (de) * 2008-03-13 2009-09-17 Man Diesel Se Einspritzventil für Direkteinspritzung
DK2239451T3 (da) * 2009-03-30 2011-10-10 Waertsilae Switzerland Ltd Brændstofindsprøjtningsindretning til interne forbrændingsmotorer
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KR101821228B1 (ko) 2015-04-22 2018-01-23 맨 디젤 앤드 터보 필리얼 아프 맨 디젤 앤드 터보 에스이 티스크랜드 대형 2행정 자체점화 내연기관용 연료 밸브

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CN102691605B (zh) 2014-12-17
KR101557521B1 (ko) 2015-10-06
PL2503138T3 (pl) 2013-10-31
DK2503138T3 (da) 2013-06-03
CN102691605A (zh) 2012-09-26
JP2012202408A (ja) 2012-10-22
EP2503138A1 (fr) 2012-09-26
JP5890714B2 (ja) 2016-03-22
KR20120109296A (ko) 2012-10-08

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