EP0704620A2 - Dispositif d'injection de combustible - Google Patents

Dispositif d'injection de combustible Download PDF

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Publication number
EP0704620A2
EP0704620A2 EP95114025A EP95114025A EP0704620A2 EP 0704620 A2 EP0704620 A2 EP 0704620A2 EP 95114025 A EP95114025 A EP 95114025A EP 95114025 A EP95114025 A EP 95114025A EP 0704620 A2 EP0704620 A2 EP 0704620A2
Authority
EP
European Patent Office
Prior art keywords
atomizing
fuel
valve
atomizer
grid
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
EP95114025A
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German (de)
English (en)
Other versions
EP0704620A3 (fr
EP0704620B1 (fr
Inventor
Bernd Taubitz
Michael Dipl.-Ing. Mettner
Thanh-Hung Dipl.-Ing. Nguyen-Schaefer
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 EP0704620A2 publication Critical patent/EP0704620A2/fr
Publication of EP0704620A3 publication Critical patent/EP0704620A3/fr
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Publication of EP0704620B1 publication Critical patent/EP0704620B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/08—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by the fuel being carried by compressed air into main stream of combustion-air
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1853—Orifice plates

Definitions

  • the invention relates to a fuel injection device according to the preamble of the main claim.
  • a fuel injector is already known from EP-OS 0 302 660, at the downstream end of which an adapter is provided, into which fuel coming from an outlet opening passes, which in turn at the downstream end of the adapter onto a flat, meshed metal disc for breaking open the Fuel hits.
  • the metal disc is arranged so that an air flow through holes in the adapter ensures that fuel drops stuck to the metal disc are torn away.
  • a better atomization quality is only achieved when the fuel is surrounded by an air stream near the metal disc, but through which an accurate spray geometry cannot be achieved.
  • the square meshes of the metal disc are of equal size due to the even braid and form a checkered pattern that is symmetrical in all directions.
  • the braid of the metal disc is thus grid-shaped, the braid having no cross-sectional changes in the axial direction having. There are therefore no special atomizer edges.
  • a fuel breaker in the form of a flat thin disk on a fuel injection valve downstream of a metering opening, which has a plurality of curved narrow slots.
  • the arcuate slots which are made by etching in the disk, ensure with their geometry, that is to say with their radial width and their arc length, that a fuel veil is formed which breaks up into small droplets.
  • the etching process for producing the slots is cost-intensive.
  • the individual slot groups have to be introduced very precisely in relation to one another in order to achieve the breaking up of the fuel in the desired manner.
  • the arcuate slots each have a constant opening width over the entire axial extent of the break-open member. The atomization is said to be improved by the horizontal, radially formed geometry of the slots in the plane of the rupture member.
  • the fuel injector according to the invention with the characterizing features of the main claim has the advantage that an atomizing grille can be provided on a fuel injector at low cost, which contributes to a significant improvement in the atomization quality without any auxiliary energy, since the fuel striking the atomizing grille is particularly fine in the smallest droplets is atomized, which have a reduced so-called Sauter Mean Diameter (SMD), i.e. a reduced mean drop diameter of the sprayed fuel.
  • SMD Sauter Mean Diameter
  • the exhaust emissions of an internal combustion engine are further reduced and a reduction in fuel consumption can also be achieved.
  • the atomizing grid for the injection of fuels has completely new atomizing structures, which is particularly characterized by a simple and very variably producible, but in terms of geometry, complicated arrangement of atomizing bars with atomizing edges.
  • the atomizer webs or the entire atomizer structure not only have new geometries running horizontally, that is to say radially, but also have axial changes, that is, across the thickness of the atomizer grid, of cross-sectional changes, one enable optimal atomization of the fuel.
  • the fuel hits the sharp-edged atomizer structures with their atomizer edges facing the valve closing body, becomes unstable as a result and disintegrates into finer droplets.
  • the atomizing grille can be attached to the injection valve very easily either downstream of an orifice plate or directly downstream of a valve seat surface, for example by means of gluing, soldering, welding or latching. If an orifice plate is connected upstream of the atomizing grid, a so-called secondary atomization takes place on the atomizing grid.
  • the gas is advantageously supplied via an injection grille with a large number of openings.
  • the injection grille can also be produced very well using the LIGA process.
  • the mixture of fuel and gas bubbles is braked immediately after the gas injection by increasing the cross section for the fuel flow again. As the pressure increases, the gas bubbles in the mixture are compressed. Up to a certain gas concentration in the mixture, there is still a bubbly flow in the injection valve. Immediately downstream of a sealing edge of the injection valve, the gas bubbles suddenly relax during injection and thus ensure a fine atomization of the fuel.
  • the sharp-edged atomizer structure then immediately provides further atomization improvement in accordance with the processes already mentioned.
  • FIG. 1 shows a partially illustrated injection valve with atomizing grids according to the invention
  • FIG. 2 shows a simplified atomizing area with an atomizing grid
  • FIG. 3 shows an enlargement of the atomizing structure from FIG. 2
  • FIGS. 4 to 9 show examples of atomizing structures with triangular, diamond-shaped or kite-quadrangular and at least partially cross sections having curved boundaries
  • FIG. 10 shows an atomizing grille with a square basic structure
  • FIG. 11 shows an atomizing grid with a circular basic structure
  • FIG. 12 shows an atomizing grid with hexagonal base structure
  • FIG. 13 an atomizing grille with a triangular base structure
  • FIG. 14 a schematic illustration of the fuel injection device with a gas injection device
  • FIG. 15 an exemplary embodiment of a gas injection device
  • FIG. 16 an injection grill for a gas injection device.
  • the injection valve has a tubular valve seat support 1, in which a longitudinal opening 3 is formed concentrically with a valve longitudinal axis 2.
  • a longitudinal opening 3 is formed concentrically with a valve longitudinal axis 2.
  • the injection valve is actuated in a known manner, for example electromagnetically.
  • An indicated electromagnetic circuit with a magnet coil 10, an armature 11 and a core 12 serves for the axial movement of the valve needle 5 and thus for opening against the spring force of a return spring (not shown) or closing the injection valve.
  • the armature 11 is facing away from the valve closing body 7 End of the valve needle 5 by z.
  • a guide opening 15 of a valve seat body 16 serves to guide the valve closing body 7 during the axial movement.
  • the valve seat carrier 1 facing away from the core 12 is shown in FIG Concentric to the longitudinal axis 3 of the valve longitudinal axis 2 of the cylindrical valve seat body 16 tightly mounted by welding.
  • the valve seat body 16 On its lower end face 17 facing away from the valve closing body 7, the valve seat body 16 is concentrically and firmly connected to a, for example, cup-shaped injection orifice disk 21, which thus lies directly against the valve seat body 16.
  • valve seat body 16 and the spray orifice plate 21 takes place, for example, by means of a circumferential and tight first weld seam 22 which is formed by a laser.
  • first weld seam 22 which is formed by a laser.
  • This type of assembly increases the risk of undesired deformation of the spray orifice plate 21 in its central region 24, For example, four injection holes 25 formed by stamping or eroding are avoided.
  • the spray plate 21 is further connected to the wall of the longitudinal opening 3 in the valve seat support 1, for example by a circumferential and tight second weld 30.
  • the insertion depth of the valve seat part consisting of valve seat body 16 and cup-shaped spray orifice disk 21 into the longitudinal opening 3 determines the size of the stroke of the valve needle 5, since the one end position of the valve needle 5 when the solenoid coil 10 is not energized due to the valve closing body 7 resting on a valve seat surface 29 of the valve seat body 16 is set.
  • the other end position of the valve needle 5 is determined when the solenoid 10 is excited, for example by the armature 11 resting on the core 12. The path between these two end positions of the valve needle 5 thus represents the stroke.
  • the spherical valve closing body 7 interacts with the valve seat surface 29 of the valve seat body 16 that tapers in the shape of a truncated cone is formed in the axial direction between the guide opening 15 and the lower end face 17 of the valve seat body 16.
  • An atomizing grille 32 according to the invention is arranged downstream of the spray hole disk 21 in the longitudinal opening 3 of the valve seat carrier 1.
  • the atomizing grid 32 is a thin disk which is firmly connected to the valve seat support 1, for example by means of gluing.
  • the area of the attachment of the atomizing grid 32 is only shown schematically and by way of example in FIG. 1, since a wide variety of connection techniques 33 can be used to fix the atomizing grid 32, such as, for example, B. welding, soldering or snapping.
  • a second atomizing grid 32 is shown in FIG. 1, which is delimited in the circumferential direction by a circumferential clamping ring 34.
  • the atomizing grid 32 is clamped, clamped or cast in the clamping ring 34.
  • the clamping ring 34 enables a very simple assembly of the atomizing grille 32, since the atomizing grid 32 can be clamped with the clamping ring 34 in one process step between the downstream end of the valve seat support 1 and a protective cap 35 forming the downstream end of the injection valve.
  • the assembly can take place, for example, in such a way that the atomizing grille 32 is already inserted into the protective cap 35 and then fastened together with the protective cap 35 to the valve seat carrier 1 by the protective cap 35 and the valve seat carrier 1 making a latching connection.
  • connection techniques 33 such as welding or soldering, which are not described here, but are quite common, are also conceivable for fastening the atomizing grid 32.
  • the connection techniques 33 only play a subordinate role, since atomizer structures 36 in middle regions 37 of the invention Atomization grids 32 are crucial for a desired excellent atomization quality of the fuel.
  • the four spray holes 25 of the spray plate 21, for example, are located e.g. B. symmetrically around the longitudinal valve axis 2 in the form of corner points of a square and thus each have the same distance from each other and to the longitudinal valve axis 2.
  • the fuel jets emerging from the spray holes 25 collide downstream of the spray plate 21 with the atomizing structures 36 of the atomizing grille 32.
  • the colliding or Impingement and flow around the fuel at the atomizer structures 36 according to the invention represents a particularly effective type of treatment in which atomization takes place in particularly small droplets and which is explained in more detail below. So-called secondary atomization takes place on the atomization grid 32, by means of which the fuel droplets are further reduced in size.
  • the arrangement of the spray perforated disk 21 is by no means a condition for the optimal operation of the atomizing grid 32; rather, the atomizer arrangement without a spray plate 21 downstream of the valve seat surface 29 in the injection valve proves to be particularly effective.
  • FIG. 2 shows in simplified form the injection region of the injection valve, in particular the regions around the valve seat surface 29 and the atomizing grille 32.
  • a spray orifice plate 21 is not provided.
  • the atomization grille 32 according to the invention is intended in particular to improve the atomization quality of the fuel without additional auxiliary energy, the new geometries of the atomizer structure 36 in particular contributing to this. So far, it has been customary in the case of injection valves to atomize the fuel, inter alia, by means of spray perforated disks 21.
  • the pressure drop at the orifice plate 21 is approximately 90% of the pressure difference between the injection valve and an intake manifold, not shown, of the internal combustion engine. Due to viscous friction and turbulent dissipation, the pressure energy is converted into thermal energy and also into kinetic energy.
  • the speed of the fuel increases significantly due to the narrowing of the cross section, which is a factor for the atomization quality of the fuel. Due to the contact with the sharp edges of the spray holes 25, the fuel jets downstream of the spray plate 21 become unstable and turbulent due to the disturbance of the surface of the fluid, here the fuel, and the development of local cavitation.
  • Turbulence of the fluid jet which is expressed in a large Reynolds number, is required for good atomization of the fuel.
  • z. B. the atomizer structure 36 according to the invention with its special geometry.
  • the atomizer structure 36 and the fluid movements are shown schematically in FIG. Due to the relatively large cross-sectional areas of flow areas 38 between the atomizer structures 36, which cross-section to the longitudinal axis 2 of the valve, the pressure drop at the atomizing grille 32 is significantly lower than the pressure drop at the spray nozzle disk 21.
  • FIG. 3 a partial area of the atomizing grid 32 is shown enlarged again, the triangular grid profile being particularly clear in cross section.
  • the atomizing grid 32 has e.g. B. such a triangular atomizer structure 36 that a flat surface 41 with an inner and outer atomizer edge 42 shows the valve closing body 7, while a triangular tip 43 is formed facing away from the valve closing body 7.
  • the atomization process of the fuel can be seen from FIG. 3.
  • the fluid jet 40 with a high flow velocity, which is indicated by an arrow 45, is initially unstable due to the flow against the sharp-edged atomizer structure 36, especially at the atomizer edges 42, and then breaks down into fine droplets.
  • Streamlines 47 extending from the atomizer edges 42 illustrate the instability of the fuel.
  • the aim of this type of treatment is to spray particularly finely atomized fuel in the form of tiny droplets from the injection valve in order, for example, to achieve very low exhaust gas emissions from the internal combustion engine and to reduce fuel consumption.
  • This requirement can be met in a particularly advantageous manner with the atomizing grid 32.
  • the fine droplet mist just described is created downstream of the atomizing grid 32.
  • These particularly small fuel droplets forming the droplet mist now have a substantially larger surface area than the fuel jets before they hit the atomizing grid 32, which in turn is an indication of good atomization. It can also be said that a fuel spray is formed downstream of the atomizing grille 32.
  • This mode of operation just described also characterizes all of the exemplary embodiments of the atomizer structures 36 listed below.
  • FIGS. 4 to 9 some advantageous and easily manufactured atomizer structures 36 are shown in cross-section, which can be used in atomizing grids 32 for injection valves.
  • the angles of the fuel sprays can be varied by the different geometries of the atomizer structures 36.
  • FIGS. 4 and 5 show triangular atomizer structures 36 which differ from one another in terms of their angles.
  • FIGS. 6 and 7 the atomizer structures 36 here having a diamond or have a kite-shaped cross-section.
  • the fuel does not hit a flat surface 41 running perpendicular to the longitudinal axis 2 of the valve, but rather two surfaces 44 running obliquely to the longitudinal axis 2 of the valve, which in addition to the two atomizing edges 42 also have a further tear-open edge 50 directed towards the valve closing body 7, which are precise lies between the two inclined surfaces 44.
  • the exemplary embodiments in FIGS. 8 and 9 each have a flat surface 41 and a curved surface 46, it being possible for the curved surface 46 facing away from the valve closing body 7 to be designed with both a constant and a variable radius.
  • the transitions from the flat surface 41 to the curved surface 46 each represent the two atomizer edges 42.
  • FIGS. 10 to 13 show some exemplary embodiments of atomizing grids 32 in their top view and thus illustrate the arrangement of the atomizing structures 36 even in a radial extent.
  • the circular atomization grids 32 each have an outer annular edge zone 52, which thus completely surrounds the central region 37 with the atomizer structure 36 and the flow regions 38 resulting therebetween in the circumferential direction.
  • the atomizer structures 36 can be produced in a very variable manner and can be matched to desired shapes of fuel mists. In their basic tendency, the atomizer structures 36 have, for example, square (FIG. 10), circular (FIG. 11), hexagonal (FIG. 12) or triangular (FIG. 13) geometries.
  • atomizer webs 55 which usually run through a center 54 of the atomization grid 32 and extend from the edge zone 52, are provided in the atomizer structures 36. These atomizer webs 55 cross the base structure 53 of the atomizer structure 36 under them different angles.
  • the atomizer webs 55 in the circular basic structure 53 (FIG. 11) run, for example, at right angles to one another from the edge zone 52 to the center 54, while the atomizer webs 55 in the hexagonal basic structure 53 (FIG. 12) each enclose an angle of 60 °.
  • the atomizer webs 55 are e.g. B. introduced at an angle of 120 ° and run completely within the triangular base structure 53, since this is also formed starting from the edge zone 52.
  • the circular, the square or the hexagonal basic structure 53 are formed at a radial distance from the edge zone 52 in the interior of the atomizing grid 32. Since the atomizer webs 55 run from the edge zone 52 to the center point 54 and thereby cross the base structure 53, flow areas 38 result between the edge zone 52 and the base structure 53 and also between the base structure 53 and the center 54.
  • the basic structure 53 is consequently formed by the atomizer webs 55, six outer and six inner flow areas 38.
  • the atomizer structure 36 with the square base structure 53 is e.g. B.
  • the so-called LIGA example (Li thographie, G alvanoformung, A bformung) - or MIGA (Mi kro Mathleiter, G alvanoformung, A bformung) method applied, which is three-dimensional particularly useful for preparing Microstructures are suitable.
  • the LIGA process is described in more detail, for example, in Heuberger: “Micromechanics", Springer-Verlag 1989, page 236 ff. And in Reichl: “Micro System Technologies 90", Springer-Verlag 1990, page 521 ff resist structuring was carried out by means of optical lithography.
  • Atomizer structures 36 or atomizer webs 55 which have a greatest width between ⁇ 50 ⁇ m and 200 ⁇ m and an axial extension, that is to say a profile height of approximately 200 ⁇ m, can be produced with the aforementioned methods without any problems.
  • the atomizer structures 36 can also be produced, for example, by means of plastic injection molding. Some fuel-resistant plastics are suitable for this, in particular polyether ether ketone (PEEK), polyphenylene sulfide (PPS), epoxy resin (EP) and phenolic resin (PH). Injection molding can also be used to achieve very precise structures which have sharp atomizer edges 42. Because of a desired inherent stability, the individual atomizer webs 55 should have a minimum width at their widest point of 100 ⁇ m and a minimum profile height of 100 ⁇ m. In addition, the atomizer structures 36 can be done using known silicon technology such. B. are produced by etching.
  • FIG. 14 shows a schematic illustration of a fuel injection device in which a gas injection device 57 is connected upstream of an injection valve with the atomizer structure 36 according to the invention.
  • the gas injection device 57 is arranged, for example, between a mass flow sensor (not shown) and the injection valve.
  • the gas supply 58 into the gas injection device 57 takes place, for example, perpendicular to the direction of fuel flow.
  • FIG. 15 shows an exemplary embodiment of a gas injection device 57, enlarged compared to FIG. 14, again schematically as a single component.
  • the gas injection device 57 is designed such that a clear cross-sectional constriction 60 for the fuel is provided in a central gas injection region 59. There is therefore a narrow gap in the gas injection region 59 for the fuel to flow through.
  • the speed of the fuel increases noticeably as a result of the cross-sectional constriction 60, the inflows with a system pressure
  • Fuel stored pressure energy is converted into kinetic energy.
  • the gas is then blown into the fuel with a low excess pressure of, for example, 0.5 bar.
  • An inlet connection 61 is provided on the gas injection device 57 in order to supply the gas, which is used for improved preparation and atomization of the fuel.
  • a gas z. B the by a bypass in front of a throttle valve in an intake manifold of the internal combustion engine, air supplied by an additional fan, but also recirculated exhaust gas from the internal combustion engine or a mixture of air and exhaust gas can be used.
  • the use of recirculated exhaust gas enables a reduction in the pollutant emissions of the internal combustion engine.
  • the supply of the gas to the gas injection device 57 is not shown in detail.
  • the gas From the inlet connection 61, the gas enters a chamber 63 which is delimited by a disk-shaped inlet grille 64 towards the cross-sectional constriction 60.
  • the gas injection device 57 can also be designed in such a way that gas can be injected into the fuel via two chambers 63 and two injection grids 64, wherein the chambers 63 can be connected to one another or can be supplied with gas separately from one another via different inlet connections 61.
  • the injection grid 64 several perforated tubes can also be used in the gas injection device 57.
  • the gas reaches the fuel directly through openings 66 formed in the injection grid 64.
  • the mixture of fuel and gas bubbles 67 is braked immediately after the gas injection by the cross section for the Fuel flow is increased again, for example, to the size of the cross section when entering the gas injection device 57.
  • the gas bubbles 67 are compressed in the mixture. Due to the surface tension between gas and fuel, the pressure in the gas bubbles 67 is correspondingly higher than the mixture pressure, depending on the bubble size. Up to a certain gas concentration in the mixture, there is still a bubbly flow in the injection valve. Immediately downstream of the sealing edge 39, the gas bubbles 67 suddenly relax during the injection. The process is called a bubble explosion, which ensures a very fine atomization according to the "shear-type" decay mechanisms of the fuel.
  • the sharp-edged atomizer structure 36 then immediately provides a further improvement in the atomization quality in accordance with the processes already described.
  • the spray orifice plate 21 should be dispensed with between the sealing edge 39 and the atomizer structure 36, in order to avoid bubble blockage in the spraying holes 25.
  • the injection grille 64 represents a rectangular base body, the edge lengths of which are e.g. be between 1 mm and 5 mm and in which a plurality of openings 66 are arranged in a sieve-like manner, so that one can speak of a perforated film.
  • the LIGA method already described can also be used very well to produce the injection grille 64.
  • the blow-in grilles 64 can be produced in very large numbers with high dimensional accuracy.
  • the inlet grille 64 shown in FIG. 16 other sieve-shaped or lattice-shaped inlet means are also conceivable. Since the LIGA process enables the smallest structures to be manufactured precisely, it is possible at any time to use the injection grille 64 with openings 66 which have a diameter of, for. B. between 10 microns and 50 microns to provide.

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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)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
EP95114025A 1994-10-01 1995-09-07 Dispositif d'injection de combustible Expired - Lifetime EP0704620B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4435270 1994-10-01
DE4435270A DE4435270A1 (de) 1994-10-01 1994-10-01 Brennstoffeinspritzvorrichtung

Publications (3)

Publication Number Publication Date
EP0704620A2 true EP0704620A2 (fr) 1996-04-03
EP0704620A3 EP0704620A3 (fr) 1996-07-24
EP0704620B1 EP0704620B1 (fr) 1999-02-10

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EP95114025A Expired - Lifetime EP0704620B1 (fr) 1994-10-01 1995-09-07 Dispositif d'injection de combustible

Country Status (4)

Country Link
US (1) US5662277A (fr)
EP (1) EP0704620B1 (fr)
JP (1) JPH08100745A (fr)
DE (2) DE4435270A1 (fr)

Cited By (6)

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WO1997020659A1 (fr) * 1995-12-05 1997-06-12 Robert Bosch Gmbh Obturateur de soupape et procede et dispositif pour l'obtention de surfaces d'etancheite sur de tels obturateurs
WO2003001053A1 (fr) * 2001-06-22 2003-01-03 Robert Bosch Gmbh Soupape d'injection de carburant
WO2008068104A1 (fr) * 2006-12-05 2008-06-12 Robert Bosch Gmbh Soupape d'injection de carburant et procédé de fabrication d'un siège de soupape pour une soupape d'injection de carburant
WO2009118623A1 (fr) * 2008-03-27 2009-10-01 Toyota Jidosha Kabushiki Kaisha Soupape d’injection de carburant pour moteur à combustion interne
EP3296554A1 (fr) 2016-09-14 2018-03-21 Global Design Technology - GDTech SA Injecteur ouvrant vers l'intérieur permettant l'injection directe d'un combustible gazeux
EP3710682B1 (fr) * 2017-11-15 2023-04-19 Delphi Automotive Systems Luxembourg SA Injecteur

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JP3156554B2 (ja) * 1995-07-24 2001-04-16 トヨタ自動車株式会社 燃料噴射弁
KR100373257B1 (ko) * 1996-07-04 2003-05-12 기아자동차주식회사 차량용 엔진의 연료분사 인젝터
US5765750A (en) * 1996-07-26 1998-06-16 Siemens Automotive Corporation Method and apparatus for controlled atomization in a fuel injector for an internal combustion engine
DE19631066A1 (de) * 1996-08-01 1998-02-05 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19736548A1 (de) * 1997-08-22 1999-02-25 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19936942A1 (de) * 1999-08-05 2001-02-08 Bosch Gmbh Robert Brennstoffeinspritzventil
US6357677B1 (en) * 1999-10-13 2002-03-19 Siemens Automotive Corporation Fuel injection valve with multiple nozzle plates
US6390067B1 (en) * 2000-08-10 2002-05-21 Delphi Technologies, Inc. Valve seat retainer for a fuel injector
US6783087B2 (en) * 2001-04-09 2004-08-31 Nippon Soken, Inc. Fuel injector
US6848635B2 (en) * 2002-01-31 2005-02-01 Visteon Global Technologies, Inc. Fuel injector nozzle assembly with induced turbulence
WO2005045232A2 (fr) * 2003-10-27 2005-05-19 Siemens Vdo Automotive Corporation Injecteur de combustible ayant un jet de pulverisation de combustible d'un diametre moyen sauter reduit par un disque d'orifice de dosage et procedes correspondants
US7137577B2 (en) * 2004-11-05 2006-11-21 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
US7124963B2 (en) * 2004-11-05 2006-10-24 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
US7051957B1 (en) * 2004-11-05 2006-05-30 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
US7438241B2 (en) * 2004-11-05 2008-10-21 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
US7104475B2 (en) * 2004-11-05 2006-09-12 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
US7185831B2 (en) * 2004-11-05 2007-03-06 Ford Motor Company Low pressure fuel injector nozzle
US7168637B2 (en) * 2004-11-05 2007-01-30 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
US7198207B2 (en) * 2004-11-05 2007-04-03 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
JP4079144B2 (ja) * 2004-12-20 2008-04-23 株式会社豊田中央研究所 燃料噴射弁
US7472845B2 (en) * 2005-03-11 2009-01-06 Continental Automotive Systems Us, Inc. Orifice disc for fuel injector
JP5035369B2 (ja) * 2010-03-11 2012-09-26 トヨタ自動車株式会社 燃料噴射ノズル
US9151416B2 (en) * 2010-12-22 2015-10-06 Ticona Llc Fiber reinforced shaped articles and process for making same
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WO1997020659A1 (fr) * 1995-12-05 1997-06-12 Robert Bosch Gmbh Obturateur de soupape et procede et dispositif pour l'obtention de surfaces d'etancheite sur de tels obturateurs
WO2003001053A1 (fr) * 2001-06-22 2003-01-03 Robert Bosch Gmbh Soupape d'injection de carburant
US7014129B2 (en) 2001-06-22 2006-03-21 Robert Bosch Gmbh Fuel-injection valve
KR100853642B1 (ko) * 2001-06-22 2008-08-25 로베르트 보쉬 게엠베하 연료 분사 밸브
WO2008068104A1 (fr) * 2006-12-05 2008-06-12 Robert Bosch Gmbh Soupape d'injection de carburant et procédé de fabrication d'un siège de soupape pour une soupape d'injection de carburant
WO2009118623A1 (fr) * 2008-03-27 2009-10-01 Toyota Jidosha Kabushiki Kaisha Soupape d’injection de carburant pour moteur à combustion interne
EP3296554A1 (fr) 2016-09-14 2018-03-21 Global Design Technology - GDTech SA Injecteur ouvrant vers l'intérieur permettant l'injection directe d'un combustible gazeux
WO2018050731A1 (fr) 2016-09-14 2018-03-22 Global Design Technology - Gdtech Sa Injecteur vers l'intérieur pour injection directe de combustible gazeux
EP3710682B1 (fr) * 2017-11-15 2023-04-19 Delphi Automotive Systems Luxembourg SA Injecteur

Also Published As

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EP0704620A3 (fr) 1996-07-24
DE59505075D1 (de) 1999-03-25
DE4435270A1 (de) 1996-04-04
JPH08100745A (ja) 1996-04-16
US5662277A (en) 1997-09-02
EP0704620B1 (fr) 1999-02-10

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