WO2009135708A1 - Injecteur de carburant comprenant une vanne de commande dotée d'un étage de pression - Google Patents

Injecteur de carburant comprenant une vanne de commande dotée d'un étage de pression Download PDF

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Publication number
WO2009135708A1
WO2009135708A1 PCT/EP2009/052672 EP2009052672W WO2009135708A1 WO 2009135708 A1 WO2009135708 A1 WO 2009135708A1 EP 2009052672 W EP2009052672 W EP 2009052672W WO 2009135708 A1 WO2009135708 A1 WO 2009135708A1
Authority
WO
WIPO (PCT)
Prior art keywords
control valve
valve element
pressure
fuel
gap
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.)
Ceased
Application number
PCT/EP2009/052672
Other languages
German (de)
English (en)
Inventor
Matthias Burger
Gerhard Suenderhauf
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 WO2009135708A1 publication Critical patent/WO2009135708A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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

Definitions

  • the invention relates to a fuel 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.
  • a common rail injector with a pressure-balanced control valve in the axial direction is known.
  • the control valve which has a sleeve-shaped control valve element, the fuel pressure can be influenced within a control chamber bounded on the end side by an injection valve element.
  • the injection valve element is adjusted between an open position and a closed position, the injection valve element releasing the fuel flow into the combustion chamber of an internal combustion engine in its open position.
  • Newer fuel injectors for very high injection pressures are carried out without leakage by dispensing with a low-pressure stage assigned to the injection valve element. Due to the lack of this low-pressure stage only low closing forces are available, which in turn leads to steep maps and thus to a deteriorated Kleinstmengenrich. This disadvantage can be compensated with very fast switching fuel injectors. the. However, with very fast switching fuel injectors Preller often occur when closing the control valve, which lead to map ripples. The bumpers of the control valve element have a direct effect on the injection valve element and lead to large Hub- scattering.
  • a bounce on the lower stroke stop of the control valve element is amplified by a hydraulic effect, which is due to the fact that when opening the control valve an opening hydraulic, acting on the control valve element, force arises.
  • This opening force is in turn due to the fact that the control valve element is pressure-infiltrated in its closed position.
  • This opening hydraulic force is especially great for small strokes of the control valve element. Only when the strokes of the control valve element become larger, the opening force decreases again, which is mainly due to the fact that the outlet throttle kavitiert and attacks as a result, only a comparatively low hydraulic pressure on the control valve seat. In certain operating conditions, this opening hydraulic force can lead to a so-called buzzing of the control valve, since the control valve immediately opens again after a closing operation.
  • the invention is therefore based on the object to propose a fuel injector in which the risk of bouncing of the control valve element is minimized.
  • the invention is based on the idea of at least partially, preferably completely, compensating the hydraulic force arising in the opening direction of the control valve element by a closing hydraulic force when the control valve is structurally designed as pressure-compensated in its closed position.
  • a fuel injector designed according to the concept of the invention in that a pressure stage projecting into the high-pressure region of the fuel injector is provided on the control valve element, which is arranged and designed such that it is open, preferably open, Control valve element is generated in the closing direction acting on the control valve member hydraulic closing force.
  • the pressure stage In the closed state of the control valve element, the pressure stage is pressure-balanced in the axial direction and causes neither an opening nor a closing hydraulic force.
  • This hydraulic, acting in the closing direction force compensates, at least in part - depending on the design of the pressure stage - acting in the opening direction, attributable to a pressure inflow hydraulic opening force, whereby the risk of bouncing of the control valve element is minimized when closing.
  • This in turn leads to lower map ripples of the fuel Inj ector and consequently to minimized Hub / Hub scattering.
  • the axial pressure balance of the control valve element can be realized in a simple manner in that the diameter with which the control valve element rests on its control valve seat corresponds to the inner guide diameter of the control valve element, with which the control valve element is guided on a guide pin in its axial adjustment movement.
  • the pressure stage is dimensioned such that the hydraulic force resulting from the opening of the control valve element and attributable to the provision of the pressure stage at least near the hydraulic opening force acting in the opposite direction. Approximately, preferably fully compensated, in order to minimize the risk of Steuerventilelementprelriv.
  • the pressure stage of the control valve element is associated with a high-pressure side gap which is formed axially between the control valve element and another injector component, preferably the control valve seat auf josden, in particular designed as a plate member injector.
  • the gap extends, starting from the, preferably at least approximately linear, sealing edge of the control valve element, which flakes (somewhat) due to signs of wear during operation, preferably at least approximately in the radial direction. Since this gap increases with increasing stroke of the control valve element, the closing force acting on the control valve element in the closing direction decreases in the same way as the hydraulic force acting on the control valve element in the opening direction.
  • the pressure stage on the side facing away from the gap side has a pressure application surface, wherein the pressure application surface is dimensioned such that the pressure stage is pressure-balanced in the axial direction with the control valve element closed.
  • the effective pressure application surface of the pressure stage must be the same size as the gap formed in the opposite axial pressure effective pressure surface of the pressure stage.
  • the force compensation of the hydraulic force acting through pressure infiltration in the opening direction by the hydraulic closing force produced by the pressure stage when opening the control valve element, acting in the closing direction can be advantageously influenced by the gap formed between the pressure stage and an injector component comprising an annular groove which preferably is introduced frontally into the control valve element.
  • this annular groove directly adjoins the sealing line of the control valve element.
  • the annular groove has the additional effect that flattening effects of the sealing line are minimized by wear occurring during operation.
  • a structurally particularly favorable variant of the fuel injector consciously dispenses with the provision of an annular groove in the high pressure side gap.
  • the equilibrium between opening and closing hydraulic force is then adjusted exclusively via the size ratio of the high-pressure side gap and a low-pressure side gap.
  • Such a fuel injector variant is easier to produce, but usually requires a little more space.
  • the gap height, ie the thickness of the gap, in particular radial, longitudinal extension is at least approximately, preferably completely constant - of course without the consideration of an optionally be provided before described annular groove.
  • control valve seat there are different possibilities.
  • the control valve seat it has been found to be advantageous to design the control valve seat as a flat seat or as a conical seat, in particular as an inner taper seat or as an outer taper seat.
  • the side of the high-pressure-side pressure stage of the control valve element which delimits the high-pressure-side gap preferably runs parallel to the seat surface.
  • the injector in which the injection valve element is formed without a low-pressure stage - the injector is thus quasi leak-free. It is further particularly preferred to guide the control valve element to a guide pin, wherein the guide pin is designed as a separate component from the injector component having the control valve seat.
  • the inner diameter with which the control valve element bears against the guide pin corresponds to the diameter of the sealing line with which the control valve element cooperates sealingly with the control valve seat in its closed position.
  • Fig. 1 is a schematic, fragmentary view of a fuel injector with a control valve that has a the high-pressure side pressure stage to ⁇ ,
  • FIG. 2 is an enlarged view of a possible embodiment of the high pressure side pressure stage in conjunction with a fancy flat seat ⁇ th control valve seat, wherein a formed between the pressure stage and the control valve seat high-pressure side gap comprises an annular groove,
  • FIG 3 is an enlarged view of an alternative embodiment of the pressure stage in the assembly ⁇ play with a trained as mecanickegelsitz control valve seat, wherein the gap formed between the pressure stage and the control valve seat has an annular groove,
  • Fig. 4 is an enlarged view of an alternative embodiment of the pressure stage, wherein the control valve seat is designed as a flat seat and the high-pressure side gap has no annular groove ⁇ and Fig. 5 is an illustration as an alternative embodiment of the high-pressure side pressure stage in conjunction with a trained as mecanickegelsitz control valve seat, wherein the high-pressure side gap between the pressure stage and the control valve seat has no annular groove and tapers in the direction of the sealing line of the control valve element.
  • Fig. 1 designed as a common rail injector fuel Inj ector 1 for injecting fuel into a combustion chamber, not shown, also shown 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, fuel injectors via a supply line 5.
  • the supply line 5 or provided in the fuel injector 1 supply channel 6 opens into a pressure chamber 7 (high pressure area) of the fuel injector 1. From there, fuel flows in an injection process in the drawing plane axially downwards into the combustion chamber of the internal combustion engine.
  • the fuel injector 1 is connected via an injector return port 8 via a return line. tion 9 connected to the reservoir 3. Via the return line 9, a control amount of fuel, which will be explained later, can flow from the fuel injector 1 to the storage container 3 and be fed back from there to the high-pressure circuit.
  • an injector body 10 Within an injector body 10 is a one-piece injection valve element 11, which may be designed in several parts if necessary, adjustable in the axial direction.
  • the injection valve element 11 is designed without a low-pressure stage.
  • the injection valve element 11 is guided within a nozzle body, not shown, on its outer periphery. This, not shown, nozzle body is clamped by means of a likewise not shown union nut with the injector 10 body.
  • a control chamber 15 is delimited, which via a radially extending into the sleeve-shaped portion 13 of the plate member 14 inlet throttle 16 with high-pressure fuel from the Pressure chamber 7 is supplied.
  • the plate element 14 is braced against an inner annular shoulder 39 of the injector body 10 by means of an externally threaded ring 38, which is screwed to an internal thread of the injector body 10.
  • control chamber 15 is radially outwardly surrounded by fuel under high pressure, so that an annular guide gap 17 radially between the sleeve-shaped portion 13 and the Einspritzventilele- element 11 is comparatively fuel-tight.
  • the control chamber 15 is above, in the plate member
  • valve 14 arranged drain channel 18 with outlet throttle 19 connected to a valve chamber 20, which is radially outwardly of a, adjustable in the axial direction, sleeve-shaped control valve element 21 of a pressure-balanced in the closed state in the axial direction control valve 22 (servo valve) is limited.
  • fuel can flow into a low-pressure region 23 of the fuel injector 1 and from there to the injector return port 8, when the sleeve-shaped control valve element 21, which is integrally formed with an anchor plate 24, lifted from its formed on the plate element 14 control valve seat 25, ie the control valve 22 is open.
  • an electromagnetic actuator 26 with an electromagnet 27 (coil) is provided, which cooperates with the armature plate 24 and subsequently with the integrally formed with this sleeve-shaped control valve element 21.
  • the actuator 26 more precisely of the electromagnet 27, lifts the control valve element 21 from its, designed in this embodiment as a flat seat control valve seat 25 from.
  • the energization of the electromagnetic actuator 26 is interrupted, whereby the sleeve-shaped control valve element 21 by means of a control closing spring 28 which is axially supported on the armature plate 24 in the drawing plane down to its control valve seat 25 is adjusted.
  • the fuel flowing in through the inlet throttle 16 into the control chamber 15 provides for a rapid pressure increase in the control chamber 15 and thus for a closing force acting on the injection valve element 11.
  • the resulting closing movement of the injection valve element 11 is supported by a closing spring 29, which is supported at one end on a circumferential collar of the injection valve element 11, not shown, and at the other end on the lower, annular end face 30 of the sleeve-shaped portion 13 of the plate element 14 in the drawing plane.
  • the valve chamber 20 is sealed in the axial direction upward by a guide pin 31, more precisely by a thickened, in the drawing plane lower, section 32.
  • the inner guide diameter D F of the sleeve-shaped control valve element 21 corresponds to the outer diameter D A of the lower, thickened portion 32 of the guide pin 31.
  • the guide pin 31 is formed as a separate member of the plate member 14, the the control closing spring 28 is spring-loaded in the axial direction in the drawing plane upwards against an injector cover 33.
  • the control closing spring 28 is supported on an annular shoulder 34 of the control valve element 21.
  • the sleeve-shaped control valve element 21 is guided on its outer circumference.
  • a sleeve-shaped guide portion 35 of the plate member 14 is provided, which extends in the plane of the drawing upwards in a direction away from the pressure chamber 7.
  • a radial bore 36 is introduced into the guide section 35 in an axially lower region, which opens into an anchor plate space 37.
  • the sleeve-shaped control valve element 21 has a pressure stage 40 protruding radially inward into the high-pressure region, more precisely into the valve chamber 20, the mode of operation of which will be explained in more detail below with reference to different exemplary embodiments according to FIGS becomes.
  • the pressure stage 40 is shown in an enlarged view. It can be seen that the pressure stage 40, starting from the guide diameter D F, extends inward in the radial direction into the valve chamber 20.
  • the pressure stage 40 has an upper in the drawing plane pressure application surface 41, to the axially spaced a lower pressure application surface 42 is arranged.
  • the axial projection surfaces of the pressure application surfaces 41, 42 are the same size, so that the pressure stage 40, when the control valve element 21 is closed, is pressure-balanced in the axial direction.
  • the diameter D D of the sealing edge 43 corresponds to the guide diameter D F.
  • the sleeve-shaped control valve element 21 bears against a front-side sealing edge 43, which will flatten somewhat during operation due to signs of wear, on a control valve seat 25 in the form of a flat seat.
  • a gap 44 which is formed between the lower pressure-engaging surface 42 of the pressure stage 40 of the control valve element 21 and the control valve seat 25.
  • annular groove 45 is provided, which is introduced as part of the gap 44 directly into the pressure stage 40 (inner ring extension). In an area radially inward of the annular groove 45, the thickness extension of the gap 44 is constant.
  • Radially outside the sealing edge 43 includes a radially inwardly tapered low pressure gap 46 which is received in the low pressure region 23.
  • the low-pressure gap 46 is bounded in the axial direction by an outer conical surface 47 of the control valve element 21 and the control valve seat 25 designed as a flat seat in the embodiment shown.
  • In the low-pressure gap 46 migrates with closed, in the axial direction pressure balanced constructed control valve element 21 under high pressure. Pressure fuel from the valve chamber 20 into it, so that in the opening direction acting on the control valve member 21 opening force is generated. This opening force is compensated by the provision of the high-pressure-side pressure stage 40. In the closed state shown, the pressure stage 40, as described above, pressure balanced in the axial direction.
  • control valve seat 25 is no longer designed as a flat seat, but as an inner conical seat.
  • the lower pressure-engaging surface 42 of the pressure stage 40 extends radially within a region the annular groove 45 parallel to the control valve seat 25, more precisely to the control valve seat surface.
  • the low-pressure gap 46 is bounded by an end-face conical surface 47 of the control valve element 21 and the control valve seat 25.
  • FIG. 4 substantially corresponds to the exemplary embodiment according to FIG. 2 with the essential difference that an annular groove 45 in the gap 44 has been dispensed with.
  • the gap 44 has in the embodiment shown no uniform height extent, but the height extent increases in the radial direction inwardly towards the center of the valve chamber 20 to.
  • the low-pressure gap 46 is delimited by the control valve seat 25 formed as a flat seat and a radially inner conical surface 48 of the control valve element 21 which has a larger cone angle than a radially outer conical surface 47 adjoining the radially inner conical surface 48.
  • the embodiment shown in Fig. 5 corresponds substantially to the embodiment of FIG. 3, wherein also here an annular groove in the gap 44 has been omitted.
  • the control valve seat 25 is embodied as an internal cone-shaped seat and, together with a conical lower pressure engagement surface 42, delimits a radially outwardly tapering gap 44.
  • the low pressure gap 46 is in turn bounded by a conical surface 48 adjoining the sealing edge 43 and located radially outward a conical surface 47 passes.

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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 (1) de carburant, en particulier un injecteur à rampe commune, pour l'injection de carburant dans la chambre de combustion d'un moteur à combustion interne, comprenant un élément de soupape d'injection (11) commandé par une vanne de commande (22), la vanne de commande (22) comprenant un élément de vanne de commande (21) en forme de manchon qui, en position de fermeture, est équilibrée en pression dans la direction axiale, et vient se placer contre un siège de vanne de commande (25) pour l'obturer hermétiquement. Selon l'invention, un étage de pression (40) est prévu sur la vanne de commande (21), du côté haute pression, ledit étage produisant, uniquement lorsque l'élément de vanne de commande (21) est levé de son siège (25), une force de fermeture hydraulique agissant sur l'élément de vanne de commande (21) dans la direction de fermeture.
PCT/EP2009/052672 2008-05-06 2009-03-06 Injecteur de carburant comprenant une vanne de commande dotée d'un étage de pression Ceased WO2009135708A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810001600 DE102008001600A1 (de) 2008-05-06 2008-05-06 Kraftstoff-Injektor mit einem eine Druckstufe aufweisenden Steuerventil
DE102008001600.4 2008-05-06

Publications (1)

Publication Number Publication Date
WO2009135708A1 true WO2009135708A1 (fr) 2009-11-12

Family

ID=40775377

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/052672 Ceased WO2009135708A1 (fr) 2008-05-06 2009-03-06 Injecteur de carburant comprenant une vanne de commande dotée d'un étage de pression

Country Status (2)

Country Link
DE (1) DE102008001600A1 (fr)
WO (1) WO2009135708A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114165371B (zh) * 2021-12-17 2023-05-05 中国船舶集团有限公司第七一一研究所 流体喷射器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
EP1867868A1 (fr) * 2006-06-14 2007-12-19 Robert Bosch Gmbh Vanne d'injection de carburant dotée d'une soupape de commande de sécurité
DE102006050032A1 (de) * 2006-10-24 2008-04-30 Robert Bosch Gmbh Injektor mit einem eine konische Hubanschlagfläche aufweisenden Steuerventil
WO2008068093A1 (fr) * 2006-12-04 2008-06-12 Robert Bosch Gmbh Injecteur de carburant avec électrovanne à siège sphérique

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
EP1867868A1 (fr) * 2006-06-14 2007-12-19 Robert Bosch Gmbh Vanne d'injection de carburant dotée d'une soupape de commande de sécurité
DE102006050032A1 (de) * 2006-10-24 2008-04-30 Robert Bosch Gmbh Injektor mit einem eine konische Hubanschlagfläche aufweisenden Steuerventil
WO2008068093A1 (fr) * 2006-12-04 2008-06-12 Robert Bosch Gmbh Injecteur de carburant avec électrovanne à siège sphérique

Also Published As

Publication number Publication date
DE102008001600A1 (de) 2009-11-12

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