EP1651862A1 - Soupape de commande pour un injecteur de carburant comprenant un dispositif multiplicateur de pression - Google Patents

Soupape de commande pour un injecteur de carburant comprenant un dispositif multiplicateur de pression

Info

Publication number
EP1651862A1
EP1651862A1 EP04738706A EP04738706A EP1651862A1 EP 1651862 A1 EP1651862 A1 EP 1651862A1 EP 04738706 A EP04738706 A EP 04738706A EP 04738706 A EP04738706 A EP 04738706A EP 1651862 A1 EP1651862 A1 EP 1651862A1
Authority
EP
European Patent Office
Prior art keywords
servo valve
piston
pressure
sealing seat
seat
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
EP04738706A
Other languages
German (de)
English (en)
Other versions
EP1651862B1 (fr
Inventor
Hans-Christoph Magel
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 EP1651862A1 publication Critical patent/EP1651862A1/fr
Application granted granted Critical
Publication of EP1651862B1 publication Critical patent/EP1651862B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • 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
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0045—Three-way valves
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • Stroke-controlled high-pressure accumulator injection systems can be used to inject fuel into direct-injection ner internal combustion engines. These fuel injection systems are characterized by the fact that the injection pressure can be adapted to the load and speed of the ner internal combustion engine. A high injection pressure is required to reduce emissions and achieve high specific outputs. Since the achievable pressure level in high-pressure fuel pumps is limited for reasons of strength, a further increase in pressure in high-pressure injection systems (common rail) can be achieved via pressure intensifiers on injectors.
  • DE 101 23 913 discloses a fuel injection device for internal combustion engines with a fuel injector that can be supplied by a high-pressure fuel source.
  • a pressure transmission device having a movable pressure booster piston is connected between the fuel injector and the high-pressure fuel source.
  • the pressure booster piston separates a space that can be connected to the high-pressure fuel source from a high-pressure space that is connected to the fuel injector.
  • the fuel pressure in the high-pressure chamber can be varied by infecting a rear space of the pressure booster device with fuel or by emptying the rear space of fuel.
  • the fuel injector has a movable closing piston for opening and closing injection openings, the closing piston protruding into a closing pressure chamber.
  • Fuel pressure can be applied to the closing piston to achieve a force acting on the closing piston in the closing direction.
  • the closing pressure chamber and the rear chamber are formed by a common closing pressure rear chamber, all partial areas of the closing pressure rear chamber being permanently connected to one another for the exchange of fuel.
  • a pressure chamber is provided for supplying fuel to the injection opening and for applying a force acting in the opening direction to the closing piston.
  • the high-pressure chamber is connected to the high-pressure fuel source in such a way that, apart from pressure vibrations, at least the fuel pressure of the high-pressure fuel source can be constantly present in the high-pressure chamber.
  • the pressure- The space and the high-pressure space are formed by a common injection space, the partial areas of which are permanently connected to one another for the exchange of fuel.
  • servo valves can be used as switching valves which have a one-piece servo valve piston in the seat-slide design of the control cross sections.
  • servo valves in the form of seat slide valve designs used as switching valves high wear on the slide edges can occur, since only small overlap lengths can be achieved.
  • servo valves designed in a seat-slide design place high demands on the manufacturing accuracy, particularly with regard to the position of the control edges of the servo valve piston relative to one another.
  • the embodiment proposed according to the invention of a switching valve designed as a servo valve in a 3/2-seat design for controlling a fuel injector comprises a valve needle on which a first needle piston is formed, which has a first sealing seat. On the first needle piston there is another, second needle piston, which has the function of a sealing sleeve. A second sealing seat is formed on the second needle piston, the second needle piston being designed against a valve housing by means of a spring supported on the first needle piston, and forming the second sealing seat with the latter. Due to this design of the valve needle of the 3/2-seat valve proposed according to the invention, the second sealing seat closes after a substantially smaller partial valve stroke.
  • the first sealing seat opens regardless of the closing of the second sealing seat up to a much larger stroke.
  • the solution proposed according to the invention of designing a switching valve controlling a fuel injector as a 3/2-seat seat valve enables an optimal injector coordination without large losses.
  • the proposed two-part servo valve according to the invention can advantageously be used in fuel injectors that include a pressure intensifier, be it integrated into or attached to the fuel injector, which are controlled by pressure relief or pressurization of the differential pressure chamber (rear space) of the pressure intensifier.
  • Figure 1 shows an embodiment of a valve designed as a 3/2-seat switch valve for a fuel injector with pressure booster in the deactivated state
  • FIG 2 shows the 3/2-seat switch valve shown in Figure 1 in the activated state.
  • FIG. 1 shows an exemplary embodiment of a 3/2-seat seat switching valve for a fuel injector, this fuel injector comprising a pressure booster.
  • a fuel injector 1 comprises a pressure intensifier 2 and a switching valve which is designed as a servo valve 3.
  • the servo valve 3 can be actuated via an actuator 4.
  • the actuator 4 can be designed on the one hand as a solenoid valve or as a piezo actuator, optionally with the interposition of a hydraulic coupling space.
  • the fuel injector 1 is supplied with fuel under high pressure via a pressure accumulator 5 (common rail).
  • the system pressure is present within the pressure accumulator 5 at the pressure intensifier 2 in its working space 7 via a high-pressure line 6.
  • the pressure booster 2 also includes a differential pressure space 8 (rear space), which is separated from the working space 7 via a booster piston 10, 11.
  • the two-part booster piston comprises a first booster piston part 10 and a second booster piston part 11.
  • the second booster piston part 11 is acted upon by a spring element 12 supported on the bottom of the differential pressure chamber 8, via which the booster piston 10, 11 returns to its rest position against one in the working chamber 7 arranged stop ring 13 are placed.
  • a compression space 9 of the pressure booster 2 is acted upon with increased pressure in accordance with the gear ratio of the pressure booster 2.
  • a nozzle chamber inlet 14 extends from the compression chamber 9 to a nozzle chamber 17 of the fuel injector 1.
  • the compression chamber 9 is refilled when the pressure intensifier 2 is deactivated via a filling valve 16, which in the illustration according to FIG. 1 is designed as a check valve.
  • the translation piston, 1, which is formed in two parts (see reference numerals 10, 11), can also be made in one part.
  • the nozzle chamber 17 encloses an injection valve member 18 designed as a nozzle needle, which has a pressure stage 19.
  • An annular gap 20 extends from the nozzle chamber 17 to a seat 21 of the injection valve member 8.
  • Below the seat 21 there are injection openings 22, via which fuel is injected into the combustion chamber of an internal combustion engine when the injection valve member 18 is lifted out of the seat 21.
  • the end face of the injection valve member 18 is acted upon by a closing piston 23, the spherical end face of which contacts the end face of the needle-shaped injection valve member 18.
  • An overflow throttle 24 is received in the closing piston 23, via which a through bore 27 of the closing piston 23 communicates with a space receiving a spring element 25.
  • the closing piston 23 is acted upon in the closing direction by the spring element 25.
  • a control chamber line 15, into which a first throttle point 26 is formed, extends from the hydraulic chamber receiving the spring element 25 to the differential pressure chamber 8 (rear chamber) of the pressurizer 2.
  • the pressure relief of the differential pressure chamber 8 of the pressure booster 2 takes place via a relief line 28. This ends in a valve housing 29 of the servo valve 3 at an orifice point 40.
  • a servo valve piston 30 is accommodated in the valve housing 29 of the servo valve 3.
  • the servo valve piston 30 comprises a through channel 31, which has a second throttle point 32.
  • the second throttle point 32 lies at the mouth of the through-channel 31 into a control chamber 33 of the servo valve 3.
  • From the control chamber 33 a line branches off into the first low-pressure side return 35, in which a discharge throttle 34 is received.
  • the control chamber 33 of the servo valve 3 can be depressurized by actuating the actuator 4, wherein the actuator 4 can be designed either as a solenoid valve or as a piezo actuator.
  • the servo valve piston 30 is surrounded by a servo valve chamber 36, from which branches off a second low-pressure-side return 37 for controlling control volumes.
  • the two returns 35, 37 can also be brought together within the injector and connected to a common return system.
  • a first sealing seat 38 is formed, which cooperates with an annular surface of a first shaft region 46 of the servo valve piston 30.
  • a second, reduced diameter second shaft area 47 follows, which is enclosed by an annular space 39 within the servo valve housing 29.
  • the second shaft area 47 of the servo valve piston has a stop surface 49 for one on the first servo valve piston 30 second servo valve piston 41 movably received.
  • the second servo valve piston 41 is movably mounted on the first servo valve piston 30 within a third sheep area 48 and is acted upon by a spring element 42, which is supported on a spring element support 43 at the lower end of the third shaft area 48.
  • the third shaft area 48 of the first servo valve piston 30 has an end face 45 on the working space side, which is acted upon by the pressure prevailing in the working space 7 of the pressure booster 2.
  • the second movably received servo valve piston 41 has a contoured piston surface 44, which forms a further, second sealing seat 50 with the valve housing 29.
  • the system pressure prevailing in the working space 7 of the pressure intensifier 2 is present via the opened second sealing seat 50 below the servo valve housing 29 via the outlet point 40, the relief line 28 in the differential pressure space 8 (rear space) of the pressure intensifier 2.
  • the pressure booster 2 is thus compensated for by the identical pressure prevailing in the working space 7 and in the differential pressure space 8 (rear space) and there is no pressure amplification.
  • the second return 37 on the low-pressure side is closed by the first stem region 46 of the first servo valve piston 30 placed in the first sealing seat 38;
  • the first return 35 on the low-pressure side is likewise closed via the actuator 4, which is also moved into its closed position.
  • the differential pressure chamber 8 of the pressure booster 2 is depressurized via the relief line 28.
  • the actuator 4 designed as a solenoid valve or a piezo actuator is activated in such a way that the first low-pressure return 35 is opened.
  • fuel flows out of the control chamber 33 of the servo valve 3 into the first return 35 on the low pressure side, so that the end face of the first servo valve piston 30 moves into the control chamber 33 of the servo valve 3.
  • the second sealing seat 50 is closed earlier than the first sealing seat 38 is fully opened.
  • the second sealing seat 50 can be closed completely after a small valve stroke, the first of which being independent of this Sealing seat 38 opens in accordance with a further stroke of the first servo valve piston 30.
  • This contributes significantly to an improvement in the injector dynamics of the fuel injector 1. Furthermore, the losses that occur when the pressure intensifier 2 is activated can be considerably reduced by the inventive design of the servo valve 3.
  • the actuator 4 is activated such that the first return 35 on the low-pressure side is closed again.
  • the pressure in the control chamber 33 of the servo valve 3 rises again owing to the fuel flowing in through the through channel 31 and flowing in from the working chamber 7.
  • the first servo valve piston 30 moves into the first sealing seat 38 and closes it.
  • the stop 49 on the piston side, formed on the second shaft area 47 of the first servo valve piston 30 strikes the second servo valve piston 41 and thus opens the second sealing seat 50 the relief line 28, fuel under system pressure, flows into the differential pressure chamber 8 of the pressure booster 2. Therefore, the two-part booster piston 10, 11 moves out of the compression space 9, in which fuel now flows in via the filling valve 16 from the cavity receiving the spring element 25 for refilling.
  • both the first sealing seat 38 and the second sealing seat 50 can be designed in a variety of ways.
  • the second servo valve piston 41 is designed, for example, with a contoured end face 44 which interacts with a flat seat on the servo valve housing 29.
  • the second sealing seat 50 can be closed after a small valve lift of the first servo valve piston 30, while the first sealing seat 38 opens independently of the closing of the second sealing seat 50.
  • the servo valve piston design proposed according to the invention means that the second sealing seat 50 is only opened by the piston-side stop 49 after the first sealing seat 38 to the second low-pressure side return 37 has already been partially closed is.
  • Pressure accumulator 30 first servo valve piston
  • Stop ring 38 first sealing seat
  • Locking piston 46 first piston shaft area

Landscapes

  • 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)

Abstract

L'invention concerne une servosoupape (3) conçue pour un injecteur de carburant (1) comprenant un dispositif multiplicateur de pression (2) dont la chambre de travail (7) est séparée d'une chambre de pression différentielle (8) par l'intermédiaire d'un piston multiplicateur (10, 11). Selon l'invention, une chambre de commande (33) de la servosoupape (3) peut être reliée avec une première conduite de retour (35) située côté basse pression, par l'intermédiaire d'un actionneur (4), tandis que la chambre de pression différentielle (8) du dispositif multiplicateur de pression (2) peut être reliée avec une deuxième conduite de retour (37) située côté basse pression ou avec un système de retour réunissant lesdits conduites de retour (35, 37). Une premier siège étanche (38) est ménagé sur un premier piston de servosoupape (30). Un deuxième piston de servosoupape (41) se présentant sous la forme d'un manchon étanche repose sur ledit premier piston de servosoupape (30) et forme un deuxième siège étanche (50) avec un logement de soupape (29). A la décompression de la chambre de commande (33), ce deuxième siège étanche se ferme plus tôt que le premier siège étanche (38) lors d'une course plus courte. Lorsque la chambre de commande (33) est soumise à une pression, le deuxième siège étanche (50) s'ouvre seulement lorsque le premier siège étanche (38) est fermé.
EP04738706A 2003-07-31 2004-06-17 Soupape de commande pour un injecteur de carburant comprenant un dispositif multiplicateur de pression Expired - Fee Related EP1651862B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10335059A DE10335059A1 (de) 2003-07-31 2003-07-31 Schaltventil für einen Kraftstoffinjektor mit Druckübersetzer
PCT/DE2004/001255 WO2005015002A1 (fr) 2003-07-31 2004-06-17 Soupape de commande conçue pour un injecteur de carburant comprenant un dispositif multiplicateur de pression

Publications (2)

Publication Number Publication Date
EP1651862A1 true EP1651862A1 (fr) 2006-05-03
EP1651862B1 EP1651862B1 (fr) 2008-10-01

Family

ID=34071999

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04738706A Expired - Fee Related EP1651862B1 (fr) 2003-07-31 2004-06-17 Soupape de commande pour un injecteur de carburant comprenant un dispositif multiplicateur de pression

Country Status (5)

Country Link
US (1) US7216815B2 (fr)
EP (1) EP1651862B1 (fr)
JP (1) JP2007500809A (fr)
DE (2) DE10335059A1 (fr)
WO (1) WO2005015002A1 (fr)

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JP4075894B2 (ja) * 2004-09-24 2008-04-16 トヨタ自動車株式会社 燃料噴射装置
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EP1836385B1 (fr) * 2004-12-03 2010-12-29 Ganser-Hydromag AG Soupape d'injection de combustible a multiplication de pression
DE102006026381A1 (de) * 2006-06-07 2007-12-13 Robert Bosch Gmbh Kraftstoffinjektor mit Druckübersetzer und niederdruckseitig angeordnetem Piezosteller
JP2009103080A (ja) * 2007-10-24 2009-05-14 Denso Corp 燃料噴射弁
US20090126689A1 (en) * 2007-11-16 2009-05-21 Caterpillar Inc. Fuel injector having valve with opposing sealing surfaces
DE102008014250A1 (de) * 2008-03-13 2009-09-17 Man Diesel Se Kraftstoffversorgungsanlage einer Brennkraftmaschine
DE102012212614A1 (de) * 2012-07-18 2014-01-23 Continental Automotive Gmbh Piezoinjektor mit hydraulisch gekoppelter Düsennadelbewegung
DE102012222509A1 (de) 2012-12-07 2014-06-12 Continental Automotive Gmbh Piezoinjektor
CN104847553A (zh) * 2015-04-09 2015-08-19 中国第一汽车股份有限公司无锡油泵油嘴研究所 可优化喷油速率且可增压式共轨喷油器
JP6583304B2 (ja) * 2017-02-17 2019-10-02 トヨタ自動車株式会社 内燃機関の制御装置
CN107725240B (zh) * 2017-11-21 2019-11-08 聊城科瑞汽车零部件有限公司 一种内部增压的喷油器
DE102018212090A1 (de) * 2018-07-19 2020-01-23 Robert Bosch Gmbh Düsenbaugruppe für ein Kraftstoffeinspritzventil zum Einspritzen eines gasförmigen und/oder flüssigen Kraftstoffs, Kraftstoffeinspritzventil
CN114458498B (zh) * 2022-02-24 2022-10-28 哈尔滨工程大学 一种基于节流阻容效应实现高稳定喷射的高压共轨喷油器

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DE502004008163D1 (de) 2008-11-13
WO2005015002A1 (fr) 2005-02-17
US20060202140A1 (en) 2006-09-14
US7216815B2 (en) 2007-05-15
EP1651862B1 (fr) 2008-10-01
JP2007500809A (ja) 2007-01-18
DE10335059A1 (de) 2005-02-17

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