EP2480783B1 - Soupape d'injection de carburant pour un moteur à combustion interne - Google Patents

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

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Publication number
EP2480783B1
EP2480783B1 EP10754337.3A EP10754337A EP2480783B1 EP 2480783 B1 EP2480783 B1 EP 2480783B1 EP 10754337 A EP10754337 A EP 10754337A EP 2480783 B1 EP2480783 B1 EP 2480783B1
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EP
European Patent Office
Prior art keywords
injector
needle
hole
nozzle
valve seat
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.)
Active
Application number
EP10754337.3A
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German (de)
English (en)
Other versions
EP2480783A1 (fr
Inventor
Wolfgang Gerber
Thomas Hofmann
Uwe Leuteritz
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.)
Continental Automotive GmbH
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Continental Automotive GmbH
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Publication date
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Publication of EP2480783A1 publication Critical patent/EP2480783A1/fr
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Publication of EP2480783B1 publication Critical patent/EP2480783B1/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
    • 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
    • F02M61/1866—Valve seats or member ends having multiple cones
    • 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
    • F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
    • 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
    • F02M61/1886—Details of valve seats 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/06—Fuel-injection apparatus having means for preventing coking, e.g. of fuel injector discharge orifices or valve needles

Definitions

  • the invention relates to a fuel injection valve for an internal combustion engine.
  • a fuel injection valve for an internal combustion engine.
  • Such a fuel injection valve is used for temporally and quantitatively targeted, direct injection of fuel, gasoline or diesel, in the combustion chamber of a cylinder of an internal combustion engine during operation.
  • injectors are widely manufactured and used for internal combustion engines, especially for the automotive industry.
  • Such a fuel injection valve consists of the injector body having a nozzle shaft with nozzle annulus, nozzle needle, closing spring, valve seat and spray holes, and an actuator with actuator assembly and transmission mechanism or control hydraulics with control valve for actuating the nozzle needle.
  • actuator come here electromagnetic actuators or piezo actuators in question.
  • the nozzle needle is through sennadel pressed by the closing spring in the valve seat and seals the fuel-filled, high-pressure nozzle annulus opposite the spray holes from.
  • the nozzle needle For injecting fuel into the combustion chamber of the internal combustion engine, the nozzle needle is lifted out of the valve seat by actuation of the actuator and by means of the transfer mechanism or the control hydraulics, thus releasing the injection holes.
  • the high-pressure fuel is injected through the spray holes directly into the associated combustion chamber.
  • a fuel injection valve is for example from the DE 33 03 470 A1 known.
  • the GB 21 98785 A shows a nozzle arrangement of a fuel injection valve with a nozzle blind hole and a nozzle needle, the needle tip has a contoured and expanded needle pin.
  • the DE 33 03 470 A1 discloses an injection nozzle for internal combustion engines with a pressure chamber in a valve body and a nozzle needle.
  • the nozzle needle has a sealing cone on which rests in a conical seat of the valve body and the injection ports seals against the pressure chamber.
  • the conical seat of the valve body merges into a blind hole-shaped recess called a well, from which the injection holes originate.
  • an injection nozzle is known.
  • the needle tip on a nozzle blind hole in contour and expansion adapted needle pin which projects into the nozzle blind hole and thus reduces a trained between valve seat and spray hole Schadvolumen.
  • the cross-sectional area of the between the nozzle blind hole and needle pin formed annular gap is widened by an annular groove on the Nadelzapfenenberg.
  • Performance and emission behavior of the internal combustion engine depend very much on the accuracy of the individual injections and on the geometric conditions in the nozzle shaft.
  • the accuracy of the injection quantities depends very much on the available pressure and its constancy in the nozzle annulus and the precision of the control and tolerances of the mechanics and in particular of the injection holes. It is a known effect that increases with increasing power density and increasing exhaust gas recirculation rate increasingly deposits formed by coking in the spray holes which negatively affects the required accuracy of the injection and thus performance and emission behavior.
  • the design-related dead volume also referred to below as the void volume which forms between the valve seat and the spray hole exit through the structural conditions and which is filled with fuel
  • the void volume which forms between the valve seat and the spray hole exit through the structural conditions and which is filled with fuel
  • HC emissions hydrocarbon emissions
  • the present invention is therefore based on the object to provide a fuel injection valve, which ensures a permanently improved and consistent performance and emission behavior of the internal combustion engine.
  • the fuel injection valve according to the invention for an internal combustion engine consists of an injector body having a nozzle shaft and a receiving bore for a nozzle needle, wherein the receiving bore is formed as a blind hole.
  • the receiving bore forms a needle guide in the upper region and a nozzle annulus in the region of the nozzle stem and forms at its base a conical valve seat and in the region of the conical tip of the valve seat a blind hole-shaped recess, also referred to below as nozzle blind hole. From this recess at least one spray hole goes out, the Nozzle ring space below the valve seat with the outer region, ie the respective combustion chamber of the internal combustion engine, connects.
  • the nozzle needle arranged so as to be movable in the longitudinal direction in the receiving bore has an at least partially conical needle tip and in the closed state of the fuel injection valve contacts the needle tip in the valve seat in such a way that it seals the nozzle blind hole and thus the at least one spray hole with respect to the nozzle ring space.
  • the needle tip of the nozzle needle has a shape adapted to the nozzle blind hole in contour and expansion, hereinafter also referred to as needle pin formation, which protrudes into the nozzle blind hole and thus reduces a formed between the valve seat and the injection hole Schadvolumen.
  • the advantages of the subject invention lie in the fact that the HC emissions can also be reduced by the reduced harmful volume.
  • the flow cross section in front of the at least one spray hole is reduced so that it increasingly leads to a cavitating fuel flow in the spray holes, which counteracts the deposits in the spray holes. In this way, a consistently high level of performance of the internal combustion engine is achieved.
  • the nozzle blind hole is at least partially conical and has a smaller cone angle than the valve seat itself. This allows a simplified production and dimensional adjustment of the inner contour of the nozzle blind hole and the outer contour of the needle pin of the needle tip of the nozzle needle. Furthermore, this configuration allows that between the inner contour of the nozzle blind hole and the outer contour of the needle pin through the annular gap formed flow cross section increases with increasing needle lift of the nozzle needle and thus provides an additional way of influencing the fuel metering by varying the flow rate.
  • the cross-sectional area of the annular gap formed between the nozzle blind hole of the valve seat and the needle pin of the needle point is at least locally widened by at least one partial depression in the needle pin wall, in the nozzle pocket hole wall or both. This causes an additional turbulence of the fuel flow in the annular gap between the needle pin and the nozzle blind hole and enhances the self-cleaning effect of the fuel flow in the annular gap and the spray holes.
  • the partial depressions in the nozzle sack hole wall and the needle journal wall are designed as punctiform, crater-shaped, dellen-shaped or spherical-segment-shaped recesses.
  • Other possibilities of shaping the depressions are also included here, provided that they fall under the claimed subject matter.
  • the above-mentioned partial depressions are arranged at the level of the at least one injection hole or, viewed from the nozzle tip, above it. With respect to the needle pin this is true when the valve is closed. As a result, there is the local extension of the annular gap between the nozzle blind hole and the needle pin in the flow direction of the fuel between the valve seat and the spray holes, which increases the cavitation of the fuel flow before and in the spray holes and thus the self-cleaning effect.
  • the cross-sectional area of the annular gap formed between the inner contour of the nozzle blind hole of the valve seat and the outer contour of the needle pin of the needle tip, in the open state of the fuel injection valve smaller than the outlet cross-sectional area of the at least one spray hole or possibly the sum of the outlet cross-sectional areas all spray holes emanating from the nozzle blind hole of the valve seat.
  • FIG. 1 shows the nozzle stem portion of a fuel injection valve. Shown are the injector body 1 and the nozzle needle 6. The other components of a fuel injection valve, such as the actuator with actuator assembly and transmission mechanism or control hydraulic control valve for actuating the nozzle needle are not shown here, since they are irrelevant to the invention.
  • the injector body 1 has a blind hole-shaped receiving bore 3 for the nozzle needle 6. At the lower end, ie at the bottom of the blind-hole-shaped receiving bore 3 of the injector body 1, a conical valve seat 4 is formed
  • the nozzle needle 6 has a multi-stepped diameter.
  • the outer diameter of the nozzle needle corresponds approximately to the inner diameter of the receiving bore 3 of the injector body 1 such that a sliding guidance of the nozzle needle 6 in the receiving bore 3 is ensured.
  • the tightest possible seat of the nozzle needle 6 is ensured in the receiving bore 3.
  • the nozzle needle 6 has a reduced outer diameter relative to the inner diameter of the receiving bore 3, so that a nozzle annular space 3 a is formed in the region of the nozzle shaft 2 between the nozzle needle 6 and the injector body 1.
  • the nozzle annulus 3a has in its upper region an annular groove-shaped extension and is connected via a fuel inlet bore 3b with a high-pressure fuel accumulator, not shown, of the injection system.
  • a fuel inlet bore 3b of the nozzle annulus 3a is filled with fuel and acted upon by the operating pressure of the high-pressure fuel accumulator.
  • the nozzle needle 6 has a further gradation and a conical needle tip 7.
  • FIG. 1 X marked area of the needle tip 7 and the valve seat 4 is in FIG. 2 shown enlarged as a section. It can be seen that here the cone angle of the needle tip 7 is slightly larger than the cone angle of the valve seat 4. This results in only a linear contact between the needle tip 7 and valve seat 4 and thus to increased surface pressure and tight sealing of the nozzle annulus 3a in this area.
  • the cone-shaped valve seat 4 in the nozzle shaft 2 of the injector body 1 is widened in its tip with a blind hole-shaped recess, which is also referred to here as the nozzle blind hole 8.
  • a blind hole-shaped recess which is also referred to here as the nozzle blind hole 8.
  • dome-shaped Around this nozzle blind hole 8 around the nozzle shaft 2 is formed dome-shaped. This formation is referred to hereinafter as nozzle tip 2a.
  • the injection holes 5, the connection between the nozzle blind hole 8 and the outer space of Nozzle shaft 2 so in the installed state produce a combustion chamber of the internal combustion engine. If the valve is opened, that is, the nozzle needle 6 is lifted off the valve seat 4, the high pressure applied in the nozzle annulus causes fuel to be injected through the injection holes 5 into a combustion chamber of the internal combustion engine.
  • the nozzle needle 6 has at its needle point 7 on a peg-shaped formation, which is hereinafter referred to as needle pin 9.
  • the needle pin 9 is formed in its outer contour and its extent so that it protrudes in the closed state of the fuel injection valve in the nozzle blind hole 8 on the inside of the nozzle tip 2a. In this way, the harmful volume between the needle tip 7 and nozzle blind hole 8 is significantly reduced.
  • the dimensional coordination between the needle pin 9 and nozzle blind hole 8 is chosen so that a sufficiently large annular gap between the needle pin 9 and nozzle blind hole 8 is ensured for the required fuel flow during fuel injection, ie in the open state of the fuel injection valve.
  • the cross-sectional area of the annular gap is dimensioned such that, in the opened state of the fuel injection valve, it is smaller than the sum of the outlet cross-sectional areas of all the injection holes 5 emanating from the nozzle blind hole 8 of the valve seat 4. This causes, that forms a cavitating fuel flow, which is suitable to prevent deposits in the annular gap and the spray holes or even remove existing deposits.
  • FIG. 2 shows a pairing of the needle pin 9 and nozzle blind hole 8 with a substantially cylindrical contour and crown-shaped conclusion. This causes that at small opening strokes of the nozzle needle 6, the cross-sectional area of the annular gap does not change and thus always the same flow conditions in the nozzle blind hole 8 and spray holes 5 are present. Only at much larger nozzle needle strokes, as soon as the needle pin 9 is almost completely withdrawn from the nozzle blind hole 8, the flow cross-sectional area increases in front of the spray holes 5 and the flow rate and thus the injection rate increase.
  • FIG. 3 an alternative embodiment of needle pin 9 and nozzle blind hole 8 is shown.
  • FIG. 3 shows first coming from the valve seat 4 ago, in the direction of needle end, a frusto-conical or conical contour of the nozzle blind hole 8 and the needle pin 9.
  • Needle pin 9 and nozzle blind hole 8 are again dimensionally coordinated so that between them, even in the illustrated closed state of the fuel injection valve remains an annular gap.
  • the annular gap increases with increasing needle stroke when opening the valve.
  • FIG. 4 shows how FIG. 3 a needle pin 9 and a nozzle blind hole 8 with truncated cone contour.
  • two pin-pin grooves 11 and 12 were added to the truncated cone contour of the needle pin on the circumference.
  • the lower needle-pin groove 12 in the figure is located on the truncated cone of the needle pin 9 approximately at a height such that it is arranged directly opposite the inlet opening of the two marked injection holes 5 when the fuel injection valve is closed.
  • the second, upper needle-pin groove 11 is located at a small distance above the first needle-pin groove 12.
  • annular grooves of the fuel flow in the annular gap between the needle pin 9 and nozzle hole 8 is additionally swirled, whereby the tendency of the fuel flow to cavitate and thus the cleaning effect is increased in the annular gap and the spray holes 5.
  • a needle pin 9 with two annular grooves 11, 12 is shown, however, configurations with only one annular groove or with more than two annular grooves are also possible.
  • a nozzle blind hole annular groove 15 is arranged on the circumference of the nozzle blind hole wall, which extends between the spray holes 5 and the valve seat 4 over the circumference of the nozzle blind hole 8.
  • FIG. 5 shows how FIG. 3 a needle pin 9 and a nozzle blind hole 8 with truncated cone contour.
  • a plurality of punctiform depressions 14, 15 were arranged both on the truncated cone contour of the needle pin and on the inner wall of the nozzle bag hole on the circumference.
  • the needle-pin recesses 14 are embodied here as ball-shaped recesses
  • the nozzle-blind hole recesses 15 are shown as crater-shaped recesses.
  • These two Embodiments of the recesses are shown here 5 representatively for further possible forms of the recesses, which may possibly result from different manufacturing processes.

Claims (3)

  1. Soupape d'injection de carburant pour un moteur à combustion,
    - avec un corps d'injecteur (1), qui comprend une tige de buse (2) et un alésage de logement (3) pour une aiguille de buse (6), l'alésage de logement (3) étant conçu comme un trou borgne, qui forme un espace annulaire de buse (3a) dans l'axe de buse (2) et qui comprend, au niveau de sa base, un siège de soupape (4) conique ainsi qu'un trou borgne de buse (8) au niveau de la pointe de cône du siège de soupape,
    - avec au moins un trou d'injection (5), qui part de ce trou borgne de buse (8) et relie l'espace annulaire de buse (3a) en dessous du siège de soupape (4) avec l'extérieur, et
    - avec une aiguille de buse (6), qui comprend une pointe d'aiguille (7) au moins partiellement conique, l'aiguille de buse (6)étant disposée de manière mobile dans la direction longitudinale dans l'alésage de logement (3) et s'appuie, lorsque la soupape d'injection de carburant est fermée, avec la pointe d'aiguille (7) dans le siège de soupape (4), de façon à ce que le trou borgne de la buse (8) et étanchéifie ainsi l'au moins un trou d'injection (5) vis-à-vis de l'espace annulaire de buse (3a),
    la pointe d'aiguille (7) comprend un tenon d'aiguille (9) adapté au trou borgne de buse (8), en terme de contour et de dilatation, qui pénètre à l'intérieur du trou borgne de buse (8) du siège de soupape (4) et réduit ainsi un volume mort (10) se trouvant entre le siège de soupape (4) et le trou d'injection (5), le trou borgne de buse (8), que présente le siège de soupape (4), présentant une forme au moins partiellement conique et présente un angle de cône inférieur au siège de soupape (4), caractérisé en ce que la surface de la section de l'interstice annulaire formé entre le trou borgne de buse (8) du siège de soupape et le tenon d'aiguille (9) de la pointe d'aiguille (7) est élargi à certains endroits par au moins une dépression partielle sur la circonférence du tenon d'aiguille et/ou sur la circonférence du tour borgne de buse, la dépression étant conçue comme une dépression pontuelle.
  2. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que l'au moins une dépression (11) est disposée, lorsque la soupape d'injection de carburant est fermée, à hauteur de l'au moins un trou d'injection (5) ou, vu de la calotte de la buse (2a), au-dessus de celui-ci.
  3. Soupape d'injection de carburant selon l'une des revendications 1 ou 2, caractérisée en ce que la surface de la section de l'interstice annulaire formé entre le trou borgne de buse (8) et le tenon d'aiguille (9) est, lorsque la soupape d'injection de carburant est ouverte, inférieure à la surface de section de sortie de l'au moins un trou d'injection (5) ou à la somme des surfaces de sections de sortie de tous les trous d'injection (5) qui partent du trou borgne de buse (8) du siège de soupape (4).
EP10754337.3A 2009-09-21 2010-09-16 Soupape d'injection de carburant pour un moteur à combustion interne Active EP2480783B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009042155A DE102009042155A1 (de) 2009-09-21 2009-09-21 Kraftstoff-Einspritzventil für eine Brennkraftmaschine
PCT/EP2010/063640 WO2011033036A1 (fr) 2009-09-21 2010-09-16 Soupape d'injection de carburant pour un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2480783A1 EP2480783A1 (fr) 2012-08-01
EP2480783B1 true EP2480783B1 (fr) 2015-06-24

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ID=42936917

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10754337.3A Active EP2480783B1 (fr) 2009-09-21 2010-09-16 Soupape d'injection de carburant pour un moteur à combustion interne

Country Status (4)

Country Link
US (1) US9297344B2 (fr)
EP (1) EP2480783B1 (fr)
DE (1) DE102009042155A1 (fr)
WO (1) WO2011033036A1 (fr)

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DE102011007887A1 (de) * 2011-04-21 2012-10-25 Continental Automotive Gmbh Düsenbaugruppe für ein Einspritzventil und Einspritzventil
WO2012085901A2 (fr) * 2011-05-09 2012-06-28 Lietuvietis Vilis I Canal d'égalisation de pression à trous recouverts par aiguille
DE102011077272A1 (de) * 2011-06-09 2012-12-13 Robert Bosch Gmbh Einspritzventil für Brennkraftmaschinen
US9903329B2 (en) * 2012-04-16 2018-02-27 Cummins Intellectual Property, Inc. Fuel injector
DE102013217371A1 (de) * 2013-08-30 2015-03-05 Robert Bosch Gmbh Kraftstoffinjektor
WO2016018375A1 (fr) * 2014-07-31 2016-02-04 Cummins Inc. Procédé de réduction de carbone/coke dans les injecteurs de carburant dans des applications à deux carburants
DE102014218056A1 (de) * 2014-09-10 2016-03-10 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102014220104B3 (de) * 2014-10-02 2016-01-28 Continental Automotive Gmbh Kraftstoffeinspritzventil
JP6354519B2 (ja) * 2014-10-23 2018-07-11 株式会社デンソー 燃料噴射弁
US10865754B2 (en) * 2017-04-05 2020-12-15 Progress Rail Services Corporation Fuel injector having needle tip and nozzle body surfaces structured for reduced sac volume and fracture resistance
DE102018106822A1 (de) 2018-03-22 2019-09-26 Volkswagen Ag Regenerationsverfahren zur Reduzierung des Verkokungsgrades eines einen Injektor umgebenden Ringspaltes
DE102019103512A1 (de) * 2019-02-12 2020-08-13 Liebherr-Components Deggendorf Gmbh Düse für einen Kraftstoffinjektor

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Publication number Publication date
DE102009042155A1 (de) 2011-04-07
US9297344B2 (en) 2016-03-29
WO2011033036A1 (fr) 2011-03-24
EP2480783A1 (fr) 2012-08-01
US20120180757A1 (en) 2012-07-19

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