EP1556607B1 - Injecteurs de carburant pour moteurs a combustion interne - Google Patents

Injecteurs de carburant pour moteurs a combustion interne Download PDF

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Publication number
EP1556607B1
EP1556607B1 EP03740029A EP03740029A EP1556607B1 EP 1556607 B1 EP1556607 B1 EP 1556607B1 EP 03740029 A EP03740029 A EP 03740029A EP 03740029 A EP03740029 A EP 03740029A EP 1556607 B1 EP1556607 B1 EP 1556607B1
Authority
EP
European Patent Office
Prior art keywords
valve
conical
partial surface
conical partial
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
EP03740029A
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German (de)
English (en)
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EP1556607A1 (fr
Inventor
Friedrich Boecking
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 EP1556607A1 publication Critical patent/EP1556607A1/fr
Application granted granted Critical
Publication of EP1556607B1 publication Critical patent/EP1556607B1/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
    • F02M61/1873—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
    • F02M61/1806—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

  • a fuel injection valve for internal combustion engines as corresponds to the preamble of claim 1.
  • a fuel injection valve for example in the published patent application DE 100 31 265 A1 described and has a valve body in which a bore is formed.
  • the bore is delimited at its combustion-chamber-side end by a valve seat, from which at least one injection opening discharges, which opens into the combustion chamber of the internal combustion engine in the installation position of the fuel injection valve.
  • a piston-shaped valve needle is arranged longitudinally displaceable, which has at its combustion chamber side, so the valve seat facing the end, a valve sealing surface with which the valve needle cooperates with the valve seat.
  • the longitudinal movement of the valve needle in the bore is effected by the ratio of two forces: on the one hand a hydraulic force, which is formed by the pressure in the pressure chamber, which is formed between the wall of the bore and the valve needle and filled with fuel, so that a hydraulic force on the Valve needle is exercised.
  • a closing force acts on the valve needle, which faces away from the combustion chamber End of the valve needle is exercised by means of a suitable device.
  • the hydraulic force on the valve needle depends on the effective area occupied by the fuel, which results in a longitudinal force component.
  • the opening pressure of the fuel injection valve so the fuel pressure in the pressure chamber, in which the hydraulic force on the valve needle just sufficient to move away against a given closing force in the longitudinal direction of the valve seat, thus depends inter alia on the support line of the valve needle on the valve seat, the so-called hydraulically effective seat diameter, because of which depends on the fuel pressure acted on the partial surface of the valve sealing surface. Due to wear between the valve sealing surface and the valve seat, in the course of the service life of the fuel injection valve there is a change in this area and thus a change in the hydraulically effective seat diameter. This also changes the opening pressure, which is reflected in a change in the opening dynamics of the valve needle. As a result, the injection timing and the injection quantity of the fuel also change, which can lead to problems in modern, high-speed internal combustion engines, in particular with regard to fuel consumption and pollutant emissions.
  • An injection valve which has a valve seat with three conical surfaces, wherein the conical surfaces are arranged one after the other in the direction of flow of the fuel.
  • the second conical surface viewed in the direction of flow, is raised in relation to the first conical surface.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that with unchanged geometry of the valve needle, a constant opening pressure over the entire life of the fuel injection valve can be maintained.
  • the valve seat has three conical partial surfaces, of which the second conical partial surface is arranged downstream of the first conical partial surface and the third conical partial surface downstream of the second conical partial surface.
  • the second conical surface is raised relative to the first conical surface, so that the valve needle in Closed position on the second conical surface comes to rest, defines the edge at the transition of the first conical surface to the second conical surface, the hydraulically effective seat diameter.
  • the fuel injection valve according to the invention has a third conical partial surface formed on the valve seat downstream of the second conical partial surface, which is set back relative to the second conical partial surface.
  • the valve seat surface on which the valve needle can rest is also delimited downstream by a shoulder. This results in precisely defined hydraulic conditions at the contact surface of valve needle and valve seat.
  • the second conical partial surface is preferably raised by 2 ⁇ m to 20 ⁇ m in relation to the first conical partial surface.
  • the fuel injection valve according to the invention has all of the conical partial area the same opening angle as the first conical partial area.
  • the three conical partial surfaces can be produced with the same tool, which saves a readjustment of the milling or grinding tool during production.
  • valve seat according to the invention are when the valve needle has a sealing edge, which is formed between two Konusdichtvid and which rests in the closed position of the valve needle on the second conical surface. This ensures the Constancy of the opening pressure even over very long operating periods.
  • FIG. 1 a fuel injection valve according to the invention is shown in longitudinal section.
  • a valve body 1 a bore 3 is formed, in which a piston-shaped valve needle 5 is arranged longitudinally displaceable.
  • the valve needle 5 is guided sealingly in this case with a guide chamber 15 facing away from the combustion chamber in a guide section 23 of the bore 3.
  • the valve needle 5 tapers to the combustion chamber to form a pressure shoulder 13 and merges at its combustion chamber end into a substantially conical valve sealing surface 7.
  • a pressure chamber 19 is formed which is radially expanded at the level of the pressure shoulder 13.
  • FIG. 2 is an enlargement of the section marked II FIG. 1 shown.
  • the valve sealing surface 7 of the valve needle 5 is subdivided into a first cone sealing surface 107 and a second cone sealing surface 207, at whose transition by different opening angles of the two cone sealing surfaces 107, 207 a sealing edge 17 is formed.
  • the valve seat 9 has a substantially conical shape and comprises three conical partial surfaces, wherein the first conical partial surface 109 adjoins the second conical partial surface 209 and this in turn adjoins the third conical partial surface 309.
  • the second conical partial surface 209 is raised relative to the first conical partial surface 109 and positioned relative to the valve needle 5, that in the closed position of the valve needle 5, when it rests against the valve seat 9, the sealing edge 17 abuts against the second conical partial surface 209.
  • FIG. 3 shows an enlargement of the designated III section of FIG. 2
  • a first annular shoulder 21 is formed, which limits the hydraulically effective seat diameter.
  • the longitudinal movement of the valve needle 5 in the bore 3 is determined by the ratio of two forces: On the one hand, a closing force on the combustion chamber facing away from the end of the valve needle by means not shown in the drawing, suitable Device is exercised. On the other hand acts on the valve needle 5, a hydraulic opening force, which is directed against the closing force and by the fuel pressure in the pressure chamber 19 is exerted on the valve needle 5.
  • valve needle 5 The surfaces of the valve needle 5, the pressure of which results in a force acting in the longitudinal direction resultant force component, especially the pressure shoulder 13 and parts of the valve sealing surface 7. If the closing force is constant, so this is the opening pressure, ie the fuel pressure in the force chamber 19 at the valve needle 5 begins its ⁇ Stammshubiolo.
  • the sealing edge 17 of the valve needle 5 would define the hydraulically effective seat diameter.
  • the entire surface of the valve sealing surface 7, which lies upstream of the sealing edge 17, in this embodiment, therefore, the first cone sealing surface 107, would be acted upon by the fuel pressure, thereby defining the hydraulic opening pressure.
  • the hydraulically effective seat diameter also changes in such a way that the pressurized area becomes smaller becomes, whereby the opening pressure rises.
  • FIG. 4 shows the same section as FIG. 2 another fuel injection valve, which has a slightly different seat geometry.
  • the third conical surface 309 is set back relative to the second conical surface 209, so that a second annular shoulder 22 is formed.
  • the third conical partial surface 309 merges into a blind hole 30, from which the injection openings 11 exit.
  • the valve needle 5 has a slightly modified valve sealing surface 7, on which a first cone sealing surface 107 and a second cone sealing surface 207 continue to be formed, however, an annular groove 27 is formed between these two cone sealing surfaces 107, 207.
  • the recessed third partial cone surface 309 achieves two things: on the one hand, a geometric limitation of the effective seating surface on the second conical partial surface 209, which precisely defines the hydraulic relationships in the gap between the valve seat 9 and the valve sealing surface 7, in particular at the very beginning of the opening stroke movement and makes it predictable.
  • the height d of the annular shoulder 21, as in FIG. 3 is shown, is preferably 2 microns to 20 microns, which ensures that on the one hand the hydraulically effective seat diameter is precisely determined and on the other hand, the stability ratios in the region of the valve seat 9 of the valve body 1 remain unchanged.
  • the width a of the second conical Part surface, as in FIG. 2 is shown, is preferably 0.2 mm to 0.5 mm.

Claims (4)

  1. Soupape d'injection de carburant pour moteurs à combustion interne comprenant un corps de soupape (1), dans lequel est réalisé un alésage (3), qui est limité à son extrémité du côté de la chambre de combustion par un siège de soupape (9), et au niveau de la région d'extrémité duquel, du côté de la chambre de combustion, est réalisée au moins une ouverture d'injection (11), et comprenant une aiguille de soupape (5) en forme de piston, qui est disposée de manière déplaçable longitudinalement dans l'alésage (3) et qui présente à son extrémité du côté de la chambre de combustion une surface d'étanchéité de soupape (7) essentiellement conique, avec laquelle l'aiguille de soupape (5) coopère avec le siège de soupape (9), de sorte que l'au moins une ouverture d'injection (11) soit fermée lors de l'appui de l'aiguille de soupape (5) sur le siège de soupape (9), et que lorsque l'aiguille de soupape (5) est soulevée du siège de soupape (9), du carburant afflue entre le siège de soupape (9) et la surface d'étanchéité de soupape (7) jusqu'aux ouvertures d'injection (11), le siège de soupape (9) comprenant une première surface partielle conique (109), une deuxième surface partielle conique (209), et une troisième surface partielle conique (309), la deuxième surface partielle conique (209) étant disposée en aval de la première surface partielle conique (109) et étant réalisée de manière rehaussée par rapport à celle-ci, la troisième surface partielle conique (309) étant réalisée en aval de la deuxième surface partielle conique (209), caractérisée en ce que la troisième surface partielle conique est en retrait par rapport à la deuxième surface partielle conique (209), toutes les surfaces partielles coniques (109 ; 209 ; 309) présentant un angle d'ouverture identique.
  2. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que l'aiguille de soupape (5) vient s'appuyer dans sa position de fermeture contre la deuxième surface partielle conique (209).
  3. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que la deuxième surface partielle conique (209) est rehaussée de 2 µm à 20 µm par rapport à la première surface partielle conique (109).
  4. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce qu'une arête d'étanchéité (17) est réalisée sur la surface d'étanchéité de soupape (7), laquelle s'applique dans la position de fermeture de l'aiguille de soupape (5) contre la deuxième surface partielle conique (209).
EP03740029A 2002-10-22 2003-05-23 Injecteurs de carburant pour moteurs a combustion interne Expired - Lifetime EP1556607B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10249144A DE10249144A1 (de) 2002-10-22 2002-10-22 Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10249144 2002-10-22
PCT/DE2003/001679 WO2004040124A1 (fr) 2002-10-22 2003-05-23 Injecteurs de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1556607A1 EP1556607A1 (fr) 2005-07-27
EP1556607B1 true EP1556607B1 (fr) 2010-07-14

Family

ID=32087093

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03740029A Expired - Lifetime EP1556607B1 (fr) 2002-10-22 2003-05-23 Injecteurs de carburant pour moteurs a combustion interne

Country Status (6)

Country Link
US (1) US7077340B2 (fr)
EP (1) EP1556607B1 (fr)
JP (1) JP2006504037A (fr)
CN (1) CN100379979C (fr)
DE (2) DE10249144A1 (fr)
WO (1) WO2004040124A1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006062008A1 (de) * 2006-12-29 2008-07-03 Robert Bosch Gmbh Vorrichtung für Hochdruckanwendungen
US20090057446A1 (en) * 2007-08-29 2009-03-05 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
US7669789B2 (en) * 2007-08-29 2010-03-02 Visteon Global Technologies, Inc. Low pressure fuel injector nozzle
US8006715B2 (en) * 2007-09-20 2011-08-30 Caterpillar Inc. Valve with thin-film coating
US20090090794A1 (en) * 2007-10-04 2009-04-09 Visteon Global Technologies, Inc. Low pressure fuel injector
JP2009138614A (ja) * 2007-12-05 2009-06-25 Mitsubishi Heavy Ind Ltd 蓄圧式燃料噴射装置の燃料噴射弁
US20090200403A1 (en) * 2008-02-08 2009-08-13 David Ling-Shun Hung Fuel injector
DE102008039920A1 (de) * 2008-08-27 2010-03-04 Continental Automotive Gmbh Düsenkörper, Düsenbaugruppe und Kraftstoffinjektor, sowie Verfahren zum Herstellen eines Düsenkörpers
JP5237054B2 (ja) * 2008-11-07 2013-07-17 三菱重工業株式会社 蓄圧式燃料噴射装置の制御弁構造
KR101154579B1 (ko) * 2010-11-23 2012-06-08 현대자동차주식회사 엔진의 인젝터홀 구조
JP5838701B2 (ja) * 2011-10-05 2016-01-06 株式会社デンソー 燃料噴射弁
EP2905457B1 (fr) 2014-01-15 2018-08-29 Continental Automotive GmbH Ensemble de soupape et injecteur de fluide pour moteur à combustion
JP6354519B2 (ja) * 2014-10-23 2018-07-11 株式会社デンソー 燃料噴射弁
US20230374961A1 (en) * 2022-05-20 2023-11-23 Caterpillar Inc. Fuel injector nozzle assembly including needle having flow guiding tip for directing fuel flow

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR445873A (fr) * 1912-04-03 1912-11-21 Robert Bosch Attache-fil pour l'assemblage d'un cable et d'un balai frotteur en charbon
US1952816A (en) * 1931-04-04 1934-03-27 Bendix Res Corp Fuel injector
GB726248A (en) * 1952-04-12 1955-03-16 Bosch Gmbh Robert Improvements in fuel injection valves for internal combustion engines
US2927737A (en) * 1952-04-12 1960-03-08 Bosch Gmbh Robert Fuel injection valves
DE3014958A1 (de) * 1980-04-18 1981-10-29 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese, insbesondere lochduese, fuer brennkraftmaschinen
AT389352B (de) * 1983-10-13 1989-11-27 Steyr Daimler Puch Ag Kraftstoff-einspritzduese fuer brennkraftmaschinen mit direkter kraftstoffeinspritzung
DE19609218B4 (de) * 1996-03-09 2007-08-23 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19755057A1 (de) * 1997-12-11 1999-06-17 Bosch Gmbh Robert Kraftstoffeinspritzdüse für selbstzündende Brennkraftmaschinen
DE19820513A1 (de) * 1998-05-08 1999-11-11 Mtu Friedrichshafen Gmbh Kraftstoffeinspritzdüse für eine Brennkraftmaschine
DE19931891A1 (de) * 1999-07-08 2001-01-18 Siemens Ag Kraftstoffeinspritzventil für eine Brennkraftmaschine
DE10031265A1 (de) * 2000-06-27 2002-01-10 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen

Also Published As

Publication number Publication date
US7077340B2 (en) 2006-07-18
WO2004040124A1 (fr) 2004-05-13
CN100379979C (zh) 2008-04-09
JP2006504037A (ja) 2006-02-02
DE50312891D1 (de) 2010-08-26
DE10249144A1 (de) 2004-05-06
EP1556607A1 (fr) 2005-07-27
US20060032947A1 (en) 2006-02-16
CN1688807A (zh) 2005-10-26

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