EP1382840B1 - Soupape d'injection de carburant pour un moteur a combustion interne - Google Patents

Soupape d'injection de carburant pour un moteur a combustion interne Download PDF

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Publication number
EP1382840B1
EP1382840B1 EP03009122A EP03009122A EP1382840B1 EP 1382840 B1 EP1382840 B1 EP 1382840B1 EP 03009122 A EP03009122 A EP 03009122A EP 03009122 A EP03009122 A EP 03009122A EP 1382840 B1 EP1382840 B1 EP 1382840B1
Authority
EP
European Patent Office
Prior art keywords
valve
injection
fuel
valve needle
fuel injection
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.)
Expired - Lifetime
Application number
EP03009122A
Other languages
German (de)
English (en)
Other versions
EP1382840A1 (fr
Inventor
Oliver Heinold
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 EP1382840A1 publication Critical patent/EP1382840A1/fr
Application granted granted Critical
Publication of EP1382840B1 publication Critical patent/EP1382840B1/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
    • 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
    • F02M61/1893—Details of valve member ends not covered by groups F02M61/1866 - F02M61/188
    • 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
    • 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
    • F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging orifices
    • 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
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size

Definitions

  • the invention is based on a fuel injection valve for Internal combustion engine, as it is the type of claim 1 corresponds.
  • a fuel injection valve for Internal combustion engine as it is the type of claim 1 corresponds.
  • Such fuel injection valves are known from the prior art.
  • the DE 196 shows 09 218 A1 a fuel injector, which is a valve body having a bore.
  • the hole will be at her combustion chamber end bounded by a conical valve seat, from which depart several injection channels in the Combustion chamber of the internal combustion engine open.
  • a valve needle arranged longitudinally displaceable, which with a also conical valve sealing surface cooperates with the valve seat and so the fuel flow to the injection channels controls.
  • injection channels are in this case preferably evenly over the circumference of the fuel injection valve distributed and it prevails within the injection channels a uniform flow of fuel. This achieves a high penetration depth of the fuel jet in the combustion chamber, resulting in large combustion chambers and thus large displacement to a rapid distribution of the Fuel leads and thus to a good combustion.
  • JP 59-136563 is a fuel injection valve known to be a single injection port with circular Cross-section, wherein the fuel flow through a Valve needle is controlled, which cooperates with a valve seat.
  • a pin is formed in the Injection opening protrudes, wherein the pin is an oval or having elliptical cross-section. This creates between the Tenon and the wall of the injection opening a gap, the narrow and has wide areas.
  • the fuel flows, depending from the azimuth angle with respect to the longitudinal axis of the bore, at different speeds into the injection channels, so that is at the inlet opening of the injection channels forms a velocity gradient in the circumferential direction.
  • the fuel flow in the injection channel in a Whirling motion that gives rise to the above-mentioned strong Atomization of the escaping fuel in the combustion chamber leads.
  • valve needle at the level of the inlet openings of the injection channels designed with a cross section of a triangle with convex corresponding to curved side surfaces. This allows in simple way of adding an inflow characteristic to the Injection channels leading to the desired vortex in the injection channel leads.
  • Design of a valve needle, at the level of the inlet openings has a cross section of a hexagon corresponds, with the interior angles of the adjacent Pages are alternately larger and smaller than 120 °.
  • the Inlet openings are in this case preferably in a radial plane arranged to the longitudinal axis of the bore, so that in all injection channels the same vortices are generated.
  • the inlet openings opposite surface of the valve needle is flattened, wherein the imaginary extension of the injection channels this area the valve needle cuts at an oblique angle.
  • the inflow conditions for each injection channel modify separately. Plus, that's how it works the desired inflow conditions for any number reach of injection channels.
  • FIG. 1 shows a longitudinal section through an inventive device Fuel injection valve, with only the combustion chamber side End of the otherwise well-known from the prior art Fuel injection valve is shown.
  • a bore 3 is formed, which is a Has longitudinal axis 4.
  • the bore 3 is at its combustion chamber side End of a substantially conical valve seat 5 limited, in which the inlet openings 107 of several Injection channels 7 are arranged in the installed position of the Fuel injection valve in the internal combustion engine in the Combustion open the same.
  • a piston-shaped Valve needle 10 arranged longitudinally displaceable, whose combustion chamber side end cooperates with the valve seat 5.
  • the valve needle 10 has a cylindrical portion 13, followed by a conical section 11, which in turn has a second cylindrical section 16 borders.
  • a pressure chamber 8 is formed, which is fuel with high Pressure can be filled.
  • the closed position of the valve needle 10 that is, when the valve sealing surface 12 at the valve seat 5 is applied, the injection ports 7 through the valve needle 10 separated from the pressure chamber 8.
  • opening position of Valve needle 10 so if the valve sealing surface 12 by a Longitudinal movement of the valve needle 10 lifted off the valve seat 5 is fuel flows from the pressure chamber 8 between the Valve sealing surface 12 and the valve seat 5 through to the Inlets 107 of the injection channels 7 and is of there injected into the combustion chamber of the internal combustion engine.
  • FIG 2 shows a cross section along the line AA of Figure 1 of a fuel injection valve, as is known in the prior art.
  • the valve needle 10 has here at the level of the inlet openings 107 of the injection channels 7, of which six are arranged distributed over the circumference of the valve body 1 here, a circular shape. This results in the open position of the valve needle 10, a circular annular gap 17 between the valve needle 10 and the valve seat 5, through which the fuel flows to the injection channels 7. Due to the rotationally symmetrical configuration of the annular gap 17, which has a constant width D over the entire circumference of the valve body 1, the same flow velocity of the fuel results everywhere.
  • FIG. 2A shows a part of the valve body 1 in a sectional view in the region of the valve seat 5.
  • an injection channel 7 which is shown with an enlarged diameter for clarity, is used here.
  • the tangential inlet velocities V L and V R of the fuel are the same, so that there is a uniform flow of the fuel in the injection channel 7 and thus the known high penetration depth into the combustion chamber of the internal combustion engine.
  • FIG. 3 like FIG. 2, shows a cross section along the line A-A of Figure 1 of a first embodiment of the Inventive fuel injection valve.
  • the valve needle 10 has the height of the inlet openings 107 of the injection channels 7 has a shape that corresponds to a hexagon, whereby six side surfaces 20 are formed on the valve needle 10 become.
  • the interior angles of the adjoining side surfaces 20 is alternately smaller and larger than 120 °, so that the extension of the injection channels 7 a crooked Angle with the respective opposite side surface 20th forms.
  • the annular gap 17 thus varies in width over the circumference of the valve body 1.
  • the previously known form the valve needle 10 is indicated by a dotted line, whereby not the same width D of the annular gap everywhere 17 is clarified.
  • the gap between the side surface 20 of the valve needle 10 and the left edge of the inlet opening 107 of the injection channel 7 is smaller than the gap between the right edge of the inlet opening 107 and the side surface 20.
  • the lower flow resistance results in a correspondingly higher tangential velocity v L. Due to these different entry speeds of the fuel on both sides of the injection channel 7, a vortex results, which leads to a strong atomization when the fuel exits into the combustion chamber of the internal combustion engine and thus to a lower penetration depth.
  • the speed ratios so that the vortex in these injection channels 7 has an opposite direction of rotation.
  • the tangential velocities v L and v R in all injection channels 7 are indicated by arrows.
  • FIG. 3A shows, in the same representation as FIG. 2A, the inflow conditions at an injection channel 7 of the injection valve illustrated in FIG.
  • the tangential velocity components v L and v R lead in the injection channel 7 to a vortex, which here seen from the inlet opening 107 from rotating counterclockwise.
  • FIG. 4 shows another embodiment of a fuel injection valve according to the invention, again as a cross section along the line AA of Figure 1.
  • the valve needle 10 has here at the level of the inlet openings 107 of the injection channels 7 a triangular shape with convex, ie outwardly curved side surfaces.
  • Injection channels 7 have different orientation.
  • the smallest width of the annular gap 17 is denoted by D 1 in FIG. 3, the largest by D 2 .
  • This shape of the valve needle 10 is tuned to six injection channels 7, which are arranged distributed uniformly over the circumference of the valve body 1.
  • the usual circular shape of the valve needle 10 is indicated by a dotted line.
  • valve needle 10 has a cross section which corresponds to a triangle with concave, ie inwardly curved side surfaces. Again, there are inflow conditions that lead to a vortex in the injection channels 7 in the manner outlined above.
  • FIG 5 shows a further embodiment in the same Representation as Figure 4.
  • the valve needle 10 has here Height of the inlet openings 107 has a cross-sectional shape, which resembles a circular saw shape.
  • the injection channels 7th opposite side surfaces 20 of the valve needle 10 are with respect to the imaginary extension of the injection channels 7 arranged obliquely, as in the embodiment Figure 3 is the case.
  • the inflow conditions are here However, identical at each injection port 7, so that the forming vortex in all injection channels 7 the same Has direction of rotation.
  • FIG. 6 shows a further exemplary embodiment, wherein here only four injection channels 7 over the circumference of the valve body 1 are arranged distributed. This requires a different form the valve needle 10, at the level of the inlet openings 107th an oval shape with sharpened ends. Here too results from the changing in the circumferential direction Annular gap 17 inflow conditions in the injection channels 7, which create a vortex there.
  • FIG. 7 shows a further embodiment of the invention Fuel injector.
  • the valve needle 10th is here in the region of the inlet openings 107 circular designed as known from the prior art. Instead, the valve seat surface 5 is modified so that similar inflow conditions in the injection channels 7 result as in a correspondingly shaped valve needle 10.
  • the valve seat 5 has a shape in cross-section, which corresponds to a triangle with concavely curved side surfaces, that is about the shape, in Figure 4, the valve needle 10 owns.
  • This embodiment has the advantage that the Valve needle 10 can remain unchanged and from the known Fuel injection valves can be adopted.
  • the other embodiments of the valve needle 10, in the Figures 3, 5 and 6 are shown, in an analogous manner be transferred to the shape of the valve seat 5 at a at the same time circular shaped valve needle 10 in Area of the inlet openings 107th
  • a vortex is not included all injection channels 7 is desired.
  • all injection channels 7 is desired.
  • a vortex is not included all injection channels 7 is desired.
  • For better Distribution of the fuel with larger combustion chambers can be advantageous, for example, only every second injection channel 7 to create a vortex.
  • This has the advantage that a part of the injection channels 7 the fuel far into the combustion chamber, while the injection channels with Vortex atomize the fuel more strongly, so that the injected fuel through these injection channels only achieved a low penetration depth.
  • the valve needle 10th or the valve sealing surface 12 designed so that the distance the inlet opening 107 of the valve sealing surface 12 at least two digits is different, which is different Influx speeds caused and thus a vortex formation.
  • the valve sealing surface 12 is in the range the remaining inlet openings 107 designed so that the Inflow conditions over the entire inlet opening 107th are the same, as already shown in Figure 2.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (6)

  1. Injecteur de carburant pour des moteurs à combustion interne, comprenant un corps de soupape (1) traversé par un alésage (3) d'axe longitudinal (4) et limité à son extrémité située du côté de la chambre de combustion par un siège de soupape (5) dans lequel se trouvent les orifices d'entrée (107) de plusieurs canaux d'injection (7) débouchant dans la chambre de combustion du moteur, une aiguille de soupape (10) montée coulissante dans l'alésage (3) et dont une portée d'étanchéité (12) coopère avec le siège de soupape (5) pour commander ainsi l'amenée de carburant aux canaux d'injection (7), de sorte que le soulèvement de la tige de soupape (11) au-dessus du siège de soupape (5) commande la formation d'une fente annulaire (17) à travers laquelle le carburant arrive aux canaux d'injection (7) répartis à la périphérie du corps de soupape (1), les ouvertures d'entrée (107) étant disposées dans un plan radial par rapport à l'axe longitudinal (4) de l'alésage (3),
    caractérisé en ce que
    dans au moins un canal d'injection (7), la distance entre l'orifice d'entrée (107) et la portée d'étanchéité de soupape (12), est différente pour au moins deux emplacements d'orifices d'entrée, et ainsi la largeur de la fente annulaire (17) est différente sur l'espace compris entre le bord gauche et le bord droit de l'orifice d'entrée (107).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce qu'
    à hauteur de l'orifice d'entrée (107) d'au moins un canal d'injection (7), l'aiguille de soupape (10) présente, une section dont la forme est celle d'un triangle dont les côtés sont bombés vers l'extérieur.
  3. Injecteur de carburant selon la revendication 1,
    caractérisé en ce qu'
    à hauteur de l'orifice d'entrée (107) d'au moins un canal d'injection (7), l'aiguille de soupape (10) présente, une section ovale.
  4. Injecteur de carburant selon la revendication 1,
    caractérisé en ce qu'
    il existe plusieurs canaux d'injection (7) dont les orifices d'entrée (107) se trouvent en face d'une surface latérale aplatie (20) de l'aiguille de soupape (10), le prolongement virtuel des canaux d'injection (7) coupant, selon un angle oblique, la surface latérale aplatie (20).
  5. Injecteur de carburant selon la revendication 1,
    caractérisé en ce qu'
    à hauteur de l'orifice d'entrée (107) d'au moins un canal d'injection (7), l'aiguille de soupape (10) présente une section correspondant à un hexagone, mais dont les angles entre côtés contigus sont alternativement inférieurs et supérieurs à 120°.
  6. Injecteur de carburant selon la revendication 1,
    caractérisé en ce qu'
    à hauteur d'au moins un orifice d'entrée (107), l'aiguille de soupape (10) présente, une section circulaire.
EP03009122A 2002-07-16 2003-04-22 Soupape d'injection de carburant pour un moteur a combustion interne Expired - Lifetime EP1382840B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10232049A DE10232049A1 (de) 2002-07-16 2002-07-16 Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10232049 2002-07-16

Publications (2)

Publication Number Publication Date
EP1382840A1 EP1382840A1 (fr) 2004-01-21
EP1382840B1 true EP1382840B1 (fr) 2005-07-27

Family

ID=29761980

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03009122A Expired - Lifetime EP1382840B1 (fr) 2002-07-16 2003-04-22 Soupape d'injection de carburant pour un moteur a combustion interne

Country Status (4)

Country Link
EP (1) EP1382840B1 (fr)
JP (1) JP2004052766A (fr)
KR (1) KR20040010178A (fr)
DE (2) DE10232049A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2891318A3 (fr) * 2005-09-26 2007-03-30 Renault Sas Injecteur de gazole pour moteur a combustion interne
DE102015205423A1 (de) 2015-03-25 2016-09-29 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen und Verwendung des Kraftstoffeinspritzventils

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59136563A (ja) * 1983-01-24 1984-08-06 Daihatsu Motor Co Ltd 燃料噴射ノズル
DE3502642A1 (de) * 1985-01-26 1986-07-31 Daimler-Benz Ag, 7000 Stuttgart Kraftstoffeinspritzventil fuer eine luftverdichtende einspritzbrennkraftmaschine
DE19609218B4 (de) * 1996-03-09 2007-08-23 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10050053B4 (de) * 2000-10-10 2005-04-28 Bosch Gmbh Robert Brennstoffeinspritzventil

Also Published As

Publication number Publication date
DE10232049A1 (de) 2004-02-05
DE50300845D1 (de) 2005-09-01
KR20040010178A (ko) 2004-01-31
JP2004052766A (ja) 2004-02-19
EP1382840A1 (fr) 2004-01-21

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