WO2008049668A1 - Injecteur d'injection de carburant dans des chambres de combustion de moteurs à combustion interne - Google Patents

Injecteur d'injection de carburant dans des chambres de combustion de moteurs à combustion interne Download PDF

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Publication number
WO2008049668A1
WO2008049668A1 PCT/EP2007/058949 EP2007058949W WO2008049668A1 WO 2008049668 A1 WO2008049668 A1 WO 2008049668A1 EP 2007058949 W EP2007058949 W EP 2007058949W WO 2008049668 A1 WO2008049668 A1 WO 2008049668A1
Authority
WO
WIPO (PCT)
Prior art keywords
fuel
valve
injector
seat
pressure
Prior art date
Application number
PCT/EP2007/058949
Other languages
German (de)
English (en)
Inventor
Helmut Clauss
Francois Rossignol
Friedrich Howey
Olivier Charvet
Tony Dumont
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 WO2008049668A1 publication Critical patent/WO2008049668A1/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
    • 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
    • F02M63/0031—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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves

Definitions

  • Injector for injecting fuel into combustion chambers of internal combustion engines
  • the invention relates to an injector according to the preamble of claim 1.
  • EP 1 612 403 A1 describes a Come-Rail Injector with a pressure-balanced control valve in the axial direction for blocking and opening a fuel discharge path from a control chamber.
  • the control valve By means of the control valve, the fuel pressure can be influenced within the control chamber.
  • the control chamber is supplied via a pressure channel with fuel from a high-pressure fuel storage.
  • a nozzle needle By varying the fuel pressure within the control chamber, a nozzle needle is moved between an open position and a closed position, with the nozzle needle in its open position releasing the fuel flow into the combustion chamber of an internal combustion engine.
  • the control valve has an adjustable in the axial direction by means of a solenoid drive valve sleeve, which cooperates sealingly with a stationary conical valve seat surface.
  • valve seat surface of the control valve is formed on a component (throttle plate) defined within the injector body, through which the fuel discharge path for fuel is led out of the control chamber.
  • a disadvantage of the known injector that the guide clearance of the valve sleeve must be chosen to be relatively large, to compensate for any offset between the valve seat and valve sleeve and any misalignment of the conical valve seat surface and thus ensure the tightness of the control valve. Since the leadership of the valve sleeve has the task of sealing the fuel pressure from the fuel drainage path, an increased guide clearance also increased leakage losses. However, with increasing leakage losses, the required flow rate of compressed fuel increases, which requires a correspondingly larger, cost-intensive and energy-intensive high-pressure pump.
  • the invention is therefore based on the object to propose an injector in which the leakage losses of the control valve are low.
  • the invention is based on the idea to arrange the valve seat surface on a seat element which is displaceable relative to the valve sleeve.
  • a mobile seat element or a mobile valve seat surface is obtained, which preferably during assembly or during operation by the action of the valve sleeve au- automatically moves to the correct position relative to the valve sleeve, so that the valve sleeve in the closing position of the control valve sealingly on the valve seat surface of the element can rest. Since the guide clearance of the valve sleeve does not have to compensate for this offset, the guide can be designed accordingly narrow, whereby leakage losses are minimized.
  • a fuel passage channel is introduced, which is part of the fuel drain path from the control chamber.
  • Fuel can pass from the control chamber into the valve sleeve through the fuel passage channel and flow out in the radial direction when the valve sleeve is lifted off the valve seat surface.
  • the control valve used is preferably a pressure-compensated valve in the axial direction, which means that, when the control valve is closed, no or only minimal pressure forces are exerted on the valve sleeve by the fuel from the fuel discharge path in the axial direction only low contact forces are required in the closed state to ensure tightness.
  • An axially-pressure compensated control valve can be realized in a simple manner in that the sleeve bore has the same diameter as the valve seat. In other words, the valve sleeve preferably bears with its inner diameter sealingly against the valve seat surface.
  • the seat element is displaceable in a plane transverse to the adjustment of the valve sleeve.
  • the throttle plate as Cylinder disk with throttle bore to be executed.
  • the two parallel surfaces of the throttle plate can be easily produced by double-plan loops.
  • the valve seat surface describes a spherical surface. It is not necessary to form the entire seat element spherical or partial spherical. A partial spherical formation in the area of the valve seat surface is sufficient. Due to the spherical valve seat surface angle errors are compensated in a simple manner, whereby an even longer and thus more accurate, low-backlash axial guidance of the valve sleeve can be realized with low radial clearance, which leakage losses are also significantly reduced. As a result, advantageously small-sized high-pressure pumps can be used.
  • valve seat surface By combining the part-spherical design of the valve seat surface with a, in particular in a transverse plane to the adjustment axis displaceable seat member, a three-dimensional tolerance adjustment between the valve sleeve and the valve seat surface can take place.
  • the seat element In order to avoid that the seat element can slide out of the engagement region of the valve sleeve, it is advantageously provided that the seat element also projects into the valve sleeve in the axial direction even when the control valve is open. Thus, a movement of the seat member is limited transversely to the direction of movement of the valve sleeve.
  • the seat element slidably on a throttle plate.
  • the throttle plate can be characterized in that the valve seat surface is no longer must be incorporated into this, flat on both sides and thus cost, for example, as a cylinder plate produced.
  • the seat element When the control valve is closed, the seat element, in particular by a compression spring, preferably on the adjacent support member, in particular the throttle plate, pressed so that the tightness between the seat member and the adjacent support member is ensured.
  • a dynamic pressure acts on the annular surface of the seat element. This back pressure generated in the open valve state, a contact pressure on the mobile seat element, which prevents its lifting from the adjacent support member.
  • the diameter of the fuel passage channel within the seat member is greater than the diameter of the fuel drain path in the adjacent support member in an embodiment of the invention.
  • the mobile seat element In order to avoid that under high pressure fuel from the control chamber or the fuel drain path between the support member, in particular the throttle plate, and the mobile seat moves element and thus lifts the mobile seat element in the axial direction of the support member is in an embodiment of the invention with fuel under high pressure maximum surface of the seat element to be underdeveloped maximum dimensioned so large that just no Axialkraft- component in the opening direction, ie away from the support member, the seat element acts.
  • the maximum in the axial direction with fuel pressure from the control chamber or the fuel outlet paths is underwent derbare surface of the seat member is smaller than in the direction of the adjacent support member with fuel from a surrounding the seat element fuel chamber surface of the seat element.
  • the recess is preferably hydraulically connected to the fuel chamber surrounding the seat element, so as to ensure that even with complete pressure infiltration of the seat element from the inner diameter of the fuel passageway to the inner diameter of the (relief) recess a resultant axial force remains, which the seat element on the adjacent support member, in particular the throttle plate presses.
  • the valve sleeve is penetrated in the axial direction of a bolt, the lateral surface can also serve as a guide surface for the valve sleeve.
  • the bolt is supported on the injector body or formed integrally therewith, in the axial direction acting on him from the fuel flow path pressure forces can be given to the injector further.
  • the bolt is not fixedly connected to the injector, but slidably disposed within the valve sleeve. The bolt is raised only by the axial pressure acting on it from the seat element and in the direction of the interior. pressed down. The length of the bolt is dimensioned such that a sleeve chamber remains on its end facing the seat element.
  • FIG. 1 shows a first embodiment of an injector with a mobile seat element and lateral high-pressure supply
  • FIG. 2 shows a detail of FIG. 1, which serves a pressure channel within a throttle plate for supplying a control chamber with high-pressure fuel
  • FIG. 3 shows an enlarged partial view of FIG. 1, from which the arrangement of the mobile seat element can be seen on the throttle plate,
  • FIG. 4 shows a further exemplary embodiment of an injector in which the control chamber is formed within a sleeve which partly encloses the nozzle needle,
  • FIG. 5 shows another embodiment of an injector, which is only partially shown and Fig. 6: a perspective view of a possible embodiment of the mobile seat element.
  • an injector 1 is shown.
  • the injector 1 has an injector body 2, a nozzle body 3 and a cylindrical throttle plate 4 accommodated between the injector body 2 and the nozzle body 3.
  • a nozzle retaining nut 5 is screwed to the injector body 2 and thus clamps the nozzle body 3 and the throttle plate 4 against the injector body 2.
  • the nozzle retaining nut 5 coaxially surrounds the throttle plate 4 and partially the injector body 2 and the nozzle body 3.
  • the nozzle body 3 passes through a passage opening 6 of the nozzle retaining nut 5 in the axial direction.
  • a guide bore 7 is formed, in which an elongated nozzle needle 8 is guided axially movable.
  • the nozzle needle 8 has a closing surface 10 with which it can be brought into tight contact with a needle seat 11 formed inside the nozzle body 3.
  • the nozzle needle 8 is biased by a biasing spring 14 in the direction of its closed position.
  • the biasing spring 14 is disposed within a control chamber 15 and is supported at one end on an upper end face 16 of the nozzle needle 8 and the other end on the throttle plate 4 from.
  • control chamber 15 is supplied via a pressure channel 17 within the throttle plate 4 with fuel under high pressure from a fuel supply line 18 guided through the injector body 2.
  • the fuel supply line 18 is in hydraulic communication with a high-pressure fuel accumulator, not shown, and continues through the throttle plate 4 and the nozzle body 3 into a high-pressure annulus 19 within the nozzle body 3, from where fuel via the annulus 13 to the nozzle hole arrangement 12 can flow.
  • an inlet throttle 20 is arranged within the pressure channel 17, with which the control chamber 15 is supplied with fuel. Fuel can flow out of the control chamber 15 to a relief space via a drainage path 22 equipped with an outlet throttle 21 (drainage bore in the throttle plate 4). By means of an electromagnetic actuator 23, a pressure-balanced in the axial direction control valve 24 block the fuel flow to the discharge space.
  • the flow cross-sections of the inlet throttle 20 and the outlet throttle 21 are matched to one another such that the inflow through the pressure channel 17 is weaker than the outflow through the drainage path 22 and thus results in a net outflow of fuel when the control valve 24 is open.
  • the resulting pressure drop in the control chamber 15 causes the amount of the closing force falls below the amount of the opening force and the nozzle needle 8 lifts off the needle seat 11.
  • control valve 24 has an axially displaceable valve sleeve 26, which is firmly connected to an anchor plate 27 or formed integrally therewith.
  • the anchor plate 27 acts with an electromagnet 28 of the electromagnetic actuator 23 together, wherein the electromagnet 28 is received in a bore 29 of the injector body 2.
  • a piezoelectric actuator may also be used.
  • a spring 30, which is supported on an annular shoulder 31 within the injector body 2, presses the electromagnet 28 against an upper end annular surface of an armature stroke adjusting collar 32, which in turn is supported by the opposing end annular surface on a sliding surface 33 of the throttle plate 4.
  • the anchor plate 27 Coaxially within the Ankerhubein- collar 32, the anchor plate 27 is received and is thereby guided in the axial direction.
  • a helical spring 34 By means of a helical spring 34, the valve sleeve 26 in the closing direction, ie in the direction of a mobile seat member 35 with a part-spherical valve seat surface 36 spring-loaded.
  • the coil spring 34 is supported on the plane of the drawing in the upper ring edge of the valve sleeve 26 and on a shim 37 on an annular shoulder 38 of the injector 2 from.
  • the seat member 35 is movable (slidable) on the sliding surface 33 of the throttle plate 4.
  • the valve sleeve 26 is shown in Fig. 3 in the closed position and is sealingly with its inner peripheral edge 39 on the annular valve seat surface 36 at.
  • a fuel passage channel 40 is provided, which is aligned with the fuel drain path 22 within the throttle plate 4 and is itself part of this fuel drain path 22.
  • the inner diameter of the fuel passageway 40 is greater than the inner diameter of the fuel drainpath 22 within the Throttle plate 4, so that the seat member 35 can not lift off from the fuel flow in the drawing plane above. It can be seen that the seat element 35 projects in the axial direction into the valve sleeve 26.
  • a cylindrical pin 41 is accommodated, which is held in a short bore 42 of the injector body 2.
  • the lower end face 43 of the bolt 41 is arranged at an axial distance from the mouth of the fuel passage channel 40, so that a fuel-filled sleeve space 44 remains free within the valve sleeve 26.
  • a fuel-filled sleeve space 44 remains free within the valve sleeve 26.
  • the compressive forces in the axial direction are supported on the injector body 2 via the bolt 41, which seals the sleeve space 44 upwards in the plane of the drawing.
  • the anchor plate 27 fixedly connected to the valve sleeve 26, as mentioned, is guided over the Ankerhubeinstellring 32.
  • the bolt 41 is received in the bore 42, wherein the bolt 41 in turn constitutes a guide for the valve sleeve 26 enclosing it. Due to the relatively large distance of the guides, the angular error of the armature plate 27 to the electromagnet 28 is low.
  • the solenoid 28 is aligned over the Ankerhubeinstellring 32 parallel to the throttle plate 4.
  • valve sleeve 26 may be guided over its outer diameter in an inner bore 45 of the electromagnet 28, as is realized in the embodiment of FIG. 5.
  • the leadership is eliminated of the bolt 41 in the injector body 2 and the guide between the armature plate 27 and the Ankerplatteneinstellring 32nd
  • the bolt 41 is received longitudinally displaceably within the valve sleeve 26 and is pressed against the injector body 2 in the axial direction by the fuel pressure within the sleeve space 44.
  • the seat member 35 is in the embodiment of FIG. 5 also displaceable transversely to the adjustment of the valve sleeve 26 on the sliding surface 33 of the throttle plate 4, whereby an offset of the throttle plate 4 and the seat member 35 to the injector 2 and the valve sleeve 26, during the Assembly may occur offset by the mobile seat member 35.
  • the mobile seat member 35 will still be in the correct, i.e., correct, position during assembly and / or operation. in the axial direction with the valve sleeve 26 aligned position, moved.
  • control chamber 15 is formed in contrast to the embodiment shown in FIG. 1 within a sleeve 46 which surrounds the nozzle needle 8 coaxially.
  • the pressure channel 17 for supplying the control chamber 15 with high-pressure fuel is formed as an annular channel radially between the nozzle needle 8 and the sleeve 46.
  • Fig. 6 shows a possible embodiment of a seat member 35 is shown.
  • the seat member 35 is substantially circular cylindrical trained. While the control valve 24 is open, a dynamic pressure from a surrounding the seat member 35, shown in Fig. 3, the fuel chamber 47 acts on the in the drawing plane of FIG. 4 upper annular surface of the mobile seat member 35th This dynamic pressure generated in the open state of the control valve 35th a pressing force on the mobile seat member 35, which prevents lifting from the throttle plate 4.
  • the cross-sectional area of the central fuel passageway 40 within the seat member 35 is greater than the cross-sectional area of the drainage path 22 within the throttle plate 4, so that the flow does not lift the seat member 35 upwardly.
  • a relief groove 48 is introduced with an inner diameter D in the bottom 49 of the seat member 35.
  • the inner diameter D of the relief groove is smaller than the outer diameter of the seat member 35 at its, the underside 49 opposite top. This ensures that even with complete pressure infiltration of the seat element 35 from the inner diameter of the fuel passage channel 40 to the inner diameter of the relief groove 48, a resultant axial force remains, which presses the seat member 35 on the throttle plate 4.
  • the relief groove 48 is connected to a depression formed in FIG. 6 as a spiral groove 50 with the outer diameter of the seat element 35 and thus to the fuel chamber 47 shown in FIG. 3 so that the built-up fuel pressure can flow into the low-pressure region within the fuel chamber 47 ,

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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)

Abstract

L'invention concerne un injecteur d'injection de carburant dans les chambres de combustion de moteurs à combustion interne et en particulier un injecteur (1) d'un système dit à rampe commune ou à haute pression, qui présente un actionneur (23) disposé dans un corps d'injecteur (2) et agencé pour actionner dans la direction axiale la douille (26) d'une soupape-pilote (24) par rapport à la surface (36) du siège de soupape. Un parcours (22) de sortie du carburant hors d'une chambre-pilote (15), en communication hydraulique avec un canal sous pression (17) qui sert à amener le carburant, peut être bloqué ou libéré au moyen de la soupape-pilote (24), ce qui permet d'agir sur la pression qui règne dans la chambre-pilote (15). Un pointeau d'injecteur (8) peut être déplacé entre une position d'ouverture qui libère l'écoulement de carburant et une position de fermeture en fonction de la pression qui règne dans la chambre-pilote. Selon l'invention la surface (36) du siège de soupape est disposée sur un élément de siège (35) disposé de manière à pouvoir coulisser par rapport à la douille de soupape (26) et doté d'un canal (40) de passage de carburant.
PCT/EP2007/058949 2006-10-24 2007-08-29 Injecteur d'injection de carburant dans des chambres de combustion de moteurs à combustion interne WO2008049668A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006050042.3 2006-10-24
DE200610050042 DE102006050042A1 (de) 2006-10-24 2006-10-24 Injektor zur Einspritzung von Kraftstoff in Brennräume von Brennkraftmaschinen

Publications (1)

Publication Number Publication Date
WO2008049668A1 true WO2008049668A1 (fr) 2008-05-02

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ID=38824936

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/058949 WO2008049668A1 (fr) 2006-10-24 2007-08-29 Injecteur d'injection de carburant dans des chambres de combustion de moteurs à combustion interne

Country Status (2)

Country Link
DE (1) DE102006050042A1 (fr)
WO (1) WO2008049668A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007025961A1 (de) * 2007-06-04 2008-12-11 Robert Bosch Gmbh Injektor
DE102008001597A1 (de) * 2008-05-06 2009-11-12 Robert Bosch Gmbh Kraftstoff-Injektor
DE102008002717A1 (de) * 2008-06-27 2010-01-14 Robert Bosch Gmbh Kraftstoffinjektor mit zweiteiligem Magnetanker
DE102008040161A1 (de) * 2008-07-04 2010-01-07 Robert Bosch Gmbh Magnetventil für einen Kraftstoff-Injektor sowie Kraftstoff-Injektor

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19630124A1 (de) * 1995-07-26 1997-01-30 Nippon Denso Co Kraftstoffeinspritzvorrichtung mit Druckspeicher
EP0916843A1 (fr) * 1997-11-18 1999-05-19 ELASIS SISTEMA RICERCA FIAT NEL MEZZOGIORNO Società Consortile per Azioni Soupape de dosage réglable pour injecteur de combustible d'un moteur à combustion interne
GB2341893A (en) * 1998-09-23 2000-03-29 Lucas Industries Ltd Two-stage electromagnetically actuated fuel injector for i.c. engines
US20040217214A1 (en) * 2001-10-12 2004-11-04 Mario Ricco Internal combustion engine fuel injector
EP1612403A1 (fr) * 2004-06-30 2006-01-04 C.R.F. Societa' Consortile per Azioni Soupape servo pour controller l'injecteur d'un moteur à combustion interne

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19630124A1 (de) * 1995-07-26 1997-01-30 Nippon Denso Co Kraftstoffeinspritzvorrichtung mit Druckspeicher
EP0916843A1 (fr) * 1997-11-18 1999-05-19 ELASIS SISTEMA RICERCA FIAT NEL MEZZOGIORNO Società Consortile per Azioni Soupape de dosage réglable pour injecteur de combustible d'un moteur à combustion interne
GB2341893A (en) * 1998-09-23 2000-03-29 Lucas Industries Ltd Two-stage electromagnetically actuated fuel injector for i.c. engines
US20040217214A1 (en) * 2001-10-12 2004-11-04 Mario Ricco Internal combustion engine fuel injector
EP1612403A1 (fr) * 2004-06-30 2006-01-04 C.R.F. Societa' Consortile per Azioni Soupape servo pour controller l'injecteur d'un moteur à combustion interne

Also Published As

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