EP2235354B1 - Injecteur de carburant dont l'élément soupape de commande présente une zone d'appui - Google Patents

Injecteur de carburant dont l'élément soupape de commande présente une zone d'appui Download PDF

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Publication number
EP2235354B1
EP2235354B1 EP08871236.9A EP08871236A EP2235354B1 EP 2235354 B1 EP2235354 B1 EP 2235354B1 EP 08871236 A EP08871236 A EP 08871236A EP 2235354 B1 EP2235354 B1 EP 2235354B1
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EP
European Patent Office
Prior art keywords
control valve
pressure
valve element
approximately
valve seat
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Active
Application number
EP08871236.9A
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German (de)
English (en)
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EP2235354A1 (fr
Inventor
Nadja Eisenmenger
Hans-Christoph Magel
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2235354A1 publication Critical patent/EP2235354A1/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
    • F02M63/007—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
    • F02M63/0073—Pressure balanced 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0077—Valve seat details
    • 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
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to an injector, in particular a common rail injector, for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • the control valve comprises a sleeve-shaped control valve element which can be adjusted in the axial direction by means of an electromagnetic actuator and which is guided on a guide pin formed integrally with a valve piece.
  • the sleeve-shaped control valve element delimits with its inner circumference a valve chamber of the control valve formed on a reduced-diameter section of the guide pin only radially outward so that no opening or closing forces from the high pressure fuel within the valve chamber act on the control valve.
  • a sealing line is arranged, which cooperates sealingly with a control valve seat arranged on the valve piece.
  • the diameter of the sealing line corresponds to the guide diameter of the control valve element, wherein the guide diameter corresponds to the outer diameter of the guide pin plus a minimum clearance. Due to its pressure balance, the control valve is suitable for switching very high pressures.
  • a disadvantage of the known injector is the high load on the line-shaped sealing edge when closing the control valve, which can lead to a significant wear on the sealing line.
  • the invention has for its object to provide an injector with a pressure balanced at least approximately in the axial direction control valve, wherein the sealing line wear of the control valve element is reduced.
  • the invention is based on the idea that stability, i. to increase the wear insensitivity of the control valve element in that the approximately line-shaped sealing edge (sealing line) of the control valve element, which rests in the closed position of the control valve sealingly against a control valve seat to assign a support region, viewed in the radial direction across the sealing line away, in the high pressure area of the injector, which is connected with the control valve open to the low pressure region of the injector, thus causing a rapid pressure drop in the control chamber of the injector, which in turn results in an opening movement of the injection valve element.
  • stability i. to increase the wear insensitivity of the control valve element in that the approximately line-shaped sealing edge (sealing line) of the control valve element, which rests in the closed position of the control valve sealingly against a control valve seat to assign a support region, viewed in the radial direction across the sealing line away, in the high pressure area of the injector, which is connected with the control valve open to the low pressure region of the injector, thus
  • the control valve element is not limited in the radial direction from the sealing edge to the pressure chamber, but rather by a support region adjoining the sealing line.
  • the impact pulse with which the control valve element strikes the control valve seat assigned to it is distributed more uniformly in the control valve, in particular in the control valve element, and consequently leads to lower component tensions. This in turn has an increased stability of the control valve element result, with the positive consequence that wear of the sealing line over the life of the injector are minimized.
  • the support region is designed and / or arranged in such a way that it provides the pressure balance of the control valve element in its closed position not or at least not significantly negatively affected.
  • This can be realized, for example, in that the support region is designed and / or arranged such that the pressure forces acting on it in opposite directions cancel each other, at least approximately completely, preferably completely.
  • This is achieved with a support region in which the effective or projection surfaces for generating pressure forces pointing in opposite directions are equal.
  • the inner or the outer diameter (depending on the design) of the control valve element in the region of the sealing line corresponds to the diameter of the control valve element above the support region.
  • the injector in which the diameter of the sealing line, which widened by unavoidable wear over the life of the injector something, and the guide diameter (inner diameter or outer diameter of the control valve element - depending on the design of the control valve element) corresponds.
  • a fully pressure compensated control valve is obtained when the inner diameter of the sealing line exactly corresponds to the inner guide diameter or the outer diameter of the sealing line exactly the outer guide diameter of the control valve element.
  • the high pressure relief angle greater than the low pressure release angle of the control valve.
  • the high-pressure freewheeling angle is the angle in the high-pressure region between the boundary line of the support region or of the control valve element adjoining the sealing line and the control valve seat surface.
  • the low-pressure release angle is the angle between the (lower) boundary line of the control valve element and the control valve seat surface arranged in the low-pressure region of the injector.
  • the low-pressure release angle is from an angle range between 0.5 ° to 5 °, preferably 0.5 ° to 2 °.
  • the high pressure release angle is selected from an angle range between about 5 ° and about 60 °, preferably from an angle range between about 10 ° and about 50 °, more preferably from an angle range between about 20 ° and about 40 °.
  • the difference between the high-pressure freewheeling angle and the low-pressure freewheeling angle is selected from an angle range up to approximately 10 °.
  • the angular difference is between about 1 ° and about 5 °, more preferably between about 1.5 ° and about 3 °.
  • the control valve element angle which is spanned by both extending in the radial direction, adjacent to the sealing line boundary lines of the control valve element, and the control valve seat angle are not the same size.
  • the angular difference is more than 10 °, particularly preferably more than 20 °.
  • Particularly good results with regard to the production accuracy of the sealing line are to be expected with an angular difference between a range between approximately 30 ° and approximately 60 °.
  • the control valve seat angle is greater than the control valve element angle.
  • an at least approximately trapezoidal design of the support region is preferred, wherein the oblique flanks of the trapezoid are connected to one another with a line running parallel to the longitudinal central axis of the control valve element.
  • the pressure compensated control valve is realized with a sleeve-shaped control valve element (valve sleeve).
  • a pressure pin is received within the control valve element.
  • the pressure pin is preferably designed as a separate component from the valve member having the control valve seat, which component has a radially inside the control valve element trained valve chamber seals in the axial direction.
  • the sleeve-shaped control valve element is guided with its inner circumference on the outer circumference of the pressure pin, which is preferably supported on an injector component in the axial direction, preferably on an injector cover or an electromagnet arrangement.
  • an outer guide for the sleeve-shaped control valve element can be provided.
  • the diameter of the sealing line preferably corresponds at least approximately to the outer diameter of the pressure pin, possibly plus a minimum clearance.
  • the support region preferably protrudes into the valve chamber formed inside the sleeve-shaped control valve element, preferably directly connected to the control chamber, and is located between the sealing line and the pressure pin in the axial direction.
  • control valve seat is particularly advantageous to design the control valve seat as a flat seat or a conical seat.
  • Fig. 1 is designed as a common rail injector injector 1 for injecting fuel into a combustion chamber, not shown, of an internal combustion engine of a motor vehicle.
  • a high pressure pump 2 delivers fuel from a reservoir 3 in a high-pressure fuel storage 4 (Rail). In this fuel, especially diesel or gasoline, under high pressure, of about 2000 bar in this embodiment, stored.
  • the injector 1 is connected via other, not shown, injectors via a supply line 5.
  • the supply line 5 opens into a pressure chamber 6.
  • a return line 8 a low-pressure region 9 of the injector 1 is connected to the reservoir 3. Via the return line 8, a later to be explained control amount of fuel from the injector 1 to the reservoir 3 to flow.
  • an injection valve element 11 is arranged within a nozzle body 13.
  • the injection valve element 11 is on the one hand guided longitudinally displaceable in a lower, sleeve-shaped portion of a valve member 12 and at an axial distance to it in a bore of a nozzle body 13.
  • 13 axial channels 14 (Ausschliffe) are formed on the outer circumference of the injection valve element 11 in the region of its leadership within the nozzle body, via which the pressure chamber 6 is connected to the nozzle chamber 7.
  • the nozzle body 13 is screwed to the injector body 10 via a union nut, not shown.
  • the injection valve element 11 has at its tip 15 a closing surface 16 with which the injection valve element 11 can be brought into close contact with an injection valve element seat 17 formed inside the nozzle body 13.
  • an injection valve element seat 17 formed inside the nozzle body 13.
  • the injection valve element 11 abuts against its injection valve element seat 17, ie is in a closed position, the fuel outlet from a nozzle hole arrangement 18 is blocked. If, on the other hand, it is lifted off its injection valve element seat 17, fuel can flow out of the pressure chamber 6 via the axial channels 14 into the nozzle chamber 7 past the injection valve element 11 to the nozzle hole arrangement 18 within the nozzle body 13 and there substantially under high pressure (rail pressure) into the combustion chamber (FIG. not shown).
  • a control chamber 20 is limited, via a radially in the sleeve-shaped portion of the valve member 12th running inlet throttle 21 is supplied with high-pressure fuel from the pressure chamber 6.
  • the control chamber 20 is connected via a, arranged in the upper, plate-shaped portion of the valve member 12 drain passage 22 with outlet throttle 23 with a valve chamber 24 which is bounded radially outwardly by a sleeve-shaped control valve element 25 of a control valve 26 (servo valve).
  • valve chamber 24 fuel can flow from the valve chamber 24 (high-pressure region) into the low-pressure region 9 of the injector 1 when the control valve element 25 which can be actuated by an electromagnetic actuator 27 lifts off from its control valve seat 28 which is designed as a flat seat and is arranged on the plate-shaped section of the valve piece 12, ie the control valve 26 is open.
  • the control valve seat angle is 180 ° in the flat seat shown.
  • the flow cross sections of the inlet throttle 21 and the outlet throttle 23 are matched to one another such that when the control valve 26 is open, a net outflow of fuel (control quantity) from the control chamber 20 via the valve chamber 24 into the low-pressure region 9 of the injector 1 and from there via the return line 8 into the reservoir 3 results ,
  • the control valve 26 is designed as a valve pressure-balanced in the axial direction in the closed state.
  • the control valve element 25 is formed integrally with its in the drawing plane upper portion with an anchor plate 29 which cooperates with an electromagnet assembly 30 of the electromagnetic actuator.
  • a pressure pin 31 is arranged, which is designed as a separate component from the valve member 12, and which seals the valve chamber 24 in the axial direction upwards. The pressure forces acting on it are supported by the pressure pin 31 on an injector cover 32 screwed to the injector body 10.
  • the pressure pin 31 passes through a central passage opening 33 within the solenoid assembly 30.
  • An annular, line-shaped sealing line 34 of the control valve element 25, which cooperates sealingly in the closed state of the control valve 26 with the control valve seat 28, located on an inner guide diameter D iF , with the Control valve element 25 is guided on the pressure pin 31.
  • the control valve member 25 is guided at its outer periphery by means of a guide plate 35 which is penetrated by the control valve member 25 and which is located axially between the anchor plate 29 and the valve member 12 with its control valve seat 28.
  • control closing spring 36 which is supported in the axial direction on the one hand on the injector cover 32 and on the other from the unit consisting of control valve element 25 and anchor plate 29.
  • the sleeve-shaped control valve element 25 lifts off from its control valve seat 28 designed as a flat seat, whereby the valve chamber 24, ie the high-pressure region 37 of the injector 1, is connected to the low-pressure region 9, whereby the pressure within the hydraulic via the outlet throttle 23 connected to the valve chamber 24 control chamber 20 drops rapidly and the injection valve element 11 moves in the axial direction of the drawing plane up into the control chamber, whereby fuel in the sequence can flow from the nozzle chamber 7 into the combustion chamber.
  • the energization of the solenoid assembly 30 of the electromagnetic actuator 27 is interrupted.
  • the control closing spring 36 subsequently moves the sleeve-shaped control valve element 25 back onto its control valve seat 28 on the upper side of the valve piece 12 in the drawing plane.
  • the fuel flowing in through the inlet throttle 21 rapidly increases the pressure in the control chamber 20, as a result of which the injection valve element 11, supported by the spring force of a closing spring 38, which is supported on a peripheral collar 39 of the injection valve element 11 and on the sleeve-shaped, lower portion of the valve piece 12, is moved in the direction of the injection valve element seat 17, which in turn the flow of fuel from the nozzle hole arrangement 18 into the combustion chamber is interrupted.
  • the at least approximately line-shaped sealing edge is located on the inner guide diameter D iF .
  • the (inner) diameter D D of the sealing line 34 corresponds to the inner guide diameter D iF of the control valve element 25.
  • the sealing line 34 is surmounted by an annular, trapezoidal support region 40 extending from the sealing line 34, which is completely within the high-pressure region 37 , More specifically, is disposed within the valve chamber 24.
  • Fig. 2 the sleeve-shaped control valve element 25 is shown, into which the pressure pin 31 protrudes.
  • the control valve element 25 (additionally) is guided on its outer circumference, an embodiment of the injector 1 can be realized, is dispensed with in an external guide for the sleeve-shaped control valve element.
  • the sleeve-shaped control valve element 25 is delimited at its lower end face in the plane of the drawing by a delimiting line 41 which, in the exemplary embodiment shown, extends exactly in the radial direction outwards from the sealing line 34. Radially inside adjacent to the sealing line 34 at a lower boundary line 42 of the support portion 40 at.
  • the two boundary lines 41, 42 include a control valve element angle ⁇ . This is about 140 ° in the embodiment shown.
  • the control valve seat angle ⁇ ie the angle between two diametrically opposite surface portions of the control valve seat 28 is in the illustrated embodiment about 160 °. The difference between the angles ⁇ and ⁇ is thus 20 °.
  • a high pressure release angle ⁇ between the (lower) boundary line 42 of the support portion 40 and the conical control valve seat surface 43 in the high pressure region 37 is about 3 ° greater than the low pressure release angle ⁇ between the lower boundary line 41 of the control valve element 25 in the low-pressure region 9 and the control valve seat surface 43.
  • the in connection with Fig. 2 Angular ratios described also apply to the embodiment according to Fig. 1 ., Wherein only the control valve seat 28 is not formed as a conical seat, but as a flat seat, whereby in the sequence compared to the embodiment according to Fig. 1 the boundary line 41 can not extend exactly perpendicular to the longitudinal central axis of the control valve element 25.

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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 (8)

  1. Injecteur, en particulier injecteur à rampe commune, pour injecter du carburant dans une chambre de combustion d'un moteur à combustion interne, comprenant un élément de soupape d'injection (11) déplaçable entre une position de fermeture et une position d'ouverture, lequel peut être commandé au moyen d'une soupape de commande (26), laquelle comprend un élément de soupape de commande (25) pourvu d'une ligne d'étanchéité (34), déplaçable au moyen d'un actionneur (27) entre une position de fermeture et une position d'ouverture, et au moins approximativement équilibré en pression dans la position de fermeture, laquelle ligne d'étanchéité coopère de manière étanche avec un siège de soupape de commande (28) dans la position de fermeture de l'élément de soupape de commande (25), et laquelle est soulevée du siège de soupape de commande (28) dans la position d'ouverture et libère ainsi le flux de carburant hors d'une zone haute pression (37) dans une zone basse pression (9) de l'injecteur (1), l'élément de soupape de commande (25) comprenant une zone d'appui (40) dépassant au-delà de la ligne d'étanchéité (34) dans la direction radiale vers la zone haute pression (37) et étant réalisé sous forme de douille, un angle de libération de haute pression (γ) entre une ligne de délimitation (42) de la zone d'appui (40), laquelle ligne de délimitation est tournée vers le siège de soupape de commande (28) et adjacente à la ligne d'étanchéité (34) dans la zone haute pression (37), et la surface de siège de soupape de commande (43) étant supérieur à un angle de libération de basse pression (γ) entre une ligne de délimitation (41) de l'élément de soupape de commande (25), laquelle ligne de délimitation est adjacente à la ligne d'étanchéité (34) dans la zone basse pression (9) et tournée vers le siège de soupape de commande (28), et la surface de siège de soupape de commande (43), caractérisé en ce que l'angle de libération de basse pression (δ) est sélectionné dans une plage angulaire entre 0,5° et 5°, de préférence entre 0,5° et 2°.
  2. Injecteur selon la revendication 1, caractérisé en ce que la zone d'appui (40) est réalisée et/ou disposée de telle sorte qu'aucune force de pression axiale résultante n'agisse sur celle-ci lorsque la soupape de commande (26) est fermée.
  3. Injecteur selon l'une quelconque des revendications 1 ou 2, caractérisé en ce que le diamètre (Dd) de la ligne d'étanchéité (34) correspond au moins approximativement, de préférence exactement, à un diamètre de guidage (DiF, DaF) de l'élément de soupape de commande (25).
  4. Injecteur selon la revendication 1, caractérisé en ce que l'angle de libération de haute pression (γ) est sélectionné dans une plage de valeurs entre approximativement 5° et approximativement 60°, de préférence entre approximativement 10° et approximativement 50°, de manière particulièrement préférée entre approximativement 20° et approximativement 40°.
  5. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une différence entre l'angle d'élément de soupape de commande (α) défini par les lignes de délimitation (41, 42) adjacentes à la ligne d'étanchéité (34) et l'angle de siège de soupape de commande (β) est supérieure à 10°, de préférence supérieure à 20°, de manière particulièrement préférée supérieure à 30°.
  6. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce que la zone d'appui (40) est réalisée au moins approximativement sous forme trapézoïdale en section transversale.
  7. Injecteur selon la revendication 1, caractérisé en ce qu'une goupille de pression (31) en une ou plusieurs parties, séparée de la pièce de soupape (12) comprenant le siège de soupape de commande (28), est reçue dans la douille, et en ce que la zone d'appui (40) est disposée axialement entre la goupille de pression (31) et le siège de soupape de commande (28) sur la périphérie intérieure de la douille.
  8. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce que le siège de soupape de commande (28) est réalisé sous forme de siège plat ou sous forme de siège conique.
EP08871236.9A 2008-01-22 2008-12-30 Injecteur de carburant dont l'élément soupape de commande présente une zone d'appui Active EP2235354B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008005532A DE102008005532A1 (de) 2008-01-22 2008-01-22 Kraftstoffinjektor, dessen Steuerventilelement einen Stützbereich aufweist
PCT/EP2008/068341 WO2009092507A1 (fr) 2008-01-22 2008-12-30 Injecteur de carburant dont l'élément soupape de commande présente une zone d'appui

Publications (2)

Publication Number Publication Date
EP2235354A1 EP2235354A1 (fr) 2010-10-06
EP2235354B1 true EP2235354B1 (fr) 2015-07-08

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP08871236.9A Active EP2235354B1 (fr) 2008-01-22 2008-12-30 Injecteur de carburant dont l'élément soupape de commande présente une zone d'appui

Country Status (7)

Country Link
US (1) US8671912B2 (fr)
EP (1) EP2235354B1 (fr)
JP (1) JP5264934B2 (fr)
CN (1) CN101925733B (fr)
DE (1) DE102008005532A1 (fr)
RU (1) RU2505701C9 (fr)
WO (1) WO2009092507A1 (fr)

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DE102008040956A1 (de) 2008-08-04 2010-02-11 Robert Bosch Gmbh Kraftstoff-Injektor
DE602008005349D1 (de) 2008-12-29 2011-04-14 Fiat Ricerche Brennstoffeinspritzsystem mit hoher Betriebswiederholbarkeit und -stabilität für einen Verbrennungsmotor
DE102009029355A1 (de) 2009-09-10 2011-03-24 Robert Bosch Gmbh Injektor
DE102009046563A1 (de) * 2009-11-10 2011-05-12 Robert Bosch Gmbh Kraftstoffinjektor
EP2383454A1 (fr) 2010-04-27 2011-11-02 C.R.F. Società Consortile per Azioni Formage du débit d'injection de carburant dans un moteur à combustion interne
EP2405121B1 (fr) 2010-07-07 2013-10-09 C.R.F. Società Consortile per Azioni Système d'injection de carburant pour moteur à combustion interne
DE102010031670A1 (de) 2010-07-22 2012-01-26 Robert Bosch Gmbh Steuerventil
DE102011078564A1 (de) * 2011-07-04 2013-01-10 Robert Bosch Gmbh Steuerventil für einen Kraftstoffinjektor und Kraftstoffinjektor
CN102877994B (zh) * 2012-10-12 2014-12-24 福建省莆田市中涵机动力有限公司 共轨喷油器压力平衡式内密封平面控制阀
US9212639B2 (en) 2012-11-02 2015-12-15 Caterpillar Inc. Debris robust fuel injector with co-axial control valve members and fuel system using same
US20150316010A1 (en) * 2012-11-05 2015-11-05 Delphi International Operations Luxembourg S.A.R.L 3-Way Valve Assembly
DE102013212140A1 (de) * 2013-06-25 2015-01-08 Robert Bosch Gmbh Steuerventil
CN103644056B (zh) * 2013-12-05 2015-09-02 中国第一汽车股份有限公司无锡油泵油嘴研究所 一种共轨系统喷油器
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JP5264934B2 (ja) 2013-08-14
US20100294241A1 (en) 2010-11-25
RU2505701C9 (ru) 2014-05-27
CN101925733A (zh) 2010-12-22
US8671912B2 (en) 2014-03-18
RU2505701C2 (ru) 2014-01-27
WO2009092507A1 (fr) 2009-07-30
JP2011510221A (ja) 2011-03-31
EP2235354A1 (fr) 2010-10-06
DE102008005532A1 (de) 2009-07-23
RU2010134798A (ru) 2012-02-27
CN101925733B (zh) 2014-07-02

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