EP2171255B1 - Étranglement au niveau du pointeau d'une soupape d'injection de carburant pour moteurs à combustion interne - Google Patents

Étranglement au niveau du pointeau d'une soupape d'injection de carburant pour moteurs à combustion interne Download PDF

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Publication number
EP2171255B1
EP2171255B1 EP08760983.0A EP08760983A EP2171255B1 EP 2171255 B1 EP2171255 B1 EP 2171255B1 EP 08760983 A EP08760983 A EP 08760983A EP 2171255 B1 EP2171255 B1 EP 2171255B1
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EP
European Patent Office
Prior art keywords
valve
pressure chamber
valve needle
collar
fuel
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
EP08760983.0A
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German (de)
English (en)
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EP2171255A1 (fr
Inventor
Matthias Burger
Hans-Christoph Magel
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP2171255A1 publication Critical patent/EP2171255A1/fr
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Publication of EP2171255B1 publication Critical patent/EP2171255B1/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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to a fuel injection valve for internal combustion engines, as it is preferably used for the injection of fuel under high pressure directly into a combustion chamber of an internal combustion engine.
  • a fuel injection valve for internal combustion engines as it is preferably used for the injection of fuel under high pressure directly into a combustion chamber of an internal combustion engine.
  • use in the fuel injection of self-igniting internal combustion engines is advantageous.
  • the valve needle is servo-operated.
  • the corresponding control valves are controlled by piezo or magnetic actuators, which switch very quickly and thus enable a quick opening of the valve pins.
  • a permanent low-pressure stage on the nozzle needle which constantly exerts a closing force and thus accelerates the closing movement of the valve needle.
  • a low-pressure stage has the disadvantage that it brings with it a high leakage and thus a higher pump performance, resulting in lower system efficiency and higher fuel consumption. This fact can be problematic especially when introducing even higher pressures.
  • Valve needles as for example from the published patent DE 100 24 703 A1 are known, are guided in a central guide portion in the pressure chamber of the injection valve, wherein the fuel is passed by two, three or four polishes on the valve needle.
  • the resulting throttling point results in a pressure drop in this area, so that the pressure in the pressure space upstream of the guide portion is higher than downstream of the guide portion, which causes a permanent closing force on the valve needles and partially compensates for the above-mentioned disadvantages.
  • the throttling action depends on the viscosity of the fuel, which in turn is a function of the pressure and the temperature.
  • Fuel injection valves according to the preamble of claim 1 are for example from the DE 101 49 961 known.
  • a defined throttle point is created, which causes a pressure drop independent of the Reynolds number of the fuel, so that the throttle effect is independent of the temperature of the fuel.
  • a sharp-edged gap throttle is formed between the valve needle and the wall of the pressure chamber, which causes a pressure drop regardless of the Reynolds number of the fuel with suitable dimensioning.
  • the Reynolds number depends, among other things, on the density and the dynamic viscosity, which in turn are essentially determined by the temperature of the fuel. Due to the independence of the Reynolds number, the damping effect of the gap choke is independent of the temperature and thus constant, which causes a constant closing force on the valve needle.
  • the gap throttle is thereby formed by a collar which has a sharp edge at its outer edge, so that between the edge of the collar and the wall of the pressure chamber, the sharp-edged gap choke is formed.
  • the collar can be formed both upstream and downstream of the guide section.
  • one or more poles are formed on the collar, which also have a sharp edge. Due to the size of the polished sections, the flow and thus the throttle effect of the gap throttle and the closing force can be determined.
  • a substantially triangular cross-section of the collar is advantageous, which is achieved by three bevels.
  • the federal government can be integrally formed with the valve needle or even after completion of the valve needle glued to this, welded or shrunk.
  • the fuel injector includes a fuel injection valve 1 and an injector body 100 including a control valve 30 for controlling the injection.
  • the injector body 100 is connected to the fuel injection valve 1, which comprises a valve body 2 and are provided in the injection ports 8, through which the fuel is ejected.
  • a valve needle 3 is arranged, which is connected to a piston rod 32, wherein the piston rod 32 defines with its end face a control chamber 36 which is formed in a sleeve 38.
  • the control chamber 36 is connected via an outlet throttle 42, which can be opened or closed by the control valve 30, with a non-pressurized leakage oil space connectable.
  • an armature 31 of the control valve is attracted by an electromagnet 33, so that the outlet throttle 42 is opened and fuel can flow from the control chamber 36 into the leakage oil space.
  • the energization of the electromagnet 33 is turned off, and the armature 31 slides spring-loaded back into its initial position and closes the outlet throttle 42.
  • the inlet throttle 44 the drained fuel in the pressure chamber 36 is replaced.
  • the compressed fuel is made available in a high-pressure accumulator 34, the so-called rail, and fed via a high-pressure line 35 to the fuel injection valve.
  • Fig. 2 is the fuel injection valve the Fig. 1 shown enlarged in longitudinal section, wherein only the part of the injection valve is shown, which faces in the installation position of the combustion chamber.
  • the fuel injection valve 1 comprises a pressure chamber 5 which can be filled with fuel under high pressure and which is limited to the combustion chamber from the valve seat 7, which is substantially conical and from which several injection openings 8 emanate.
  • the valve needle 3 is arranged longitudinally displaceable, which is formed in a piston-shaped with an axis 9.
  • the valve needle 3 is guided in a guide section 10 in the pressure chamber 5, so that it is always oriented with respect to the conical valve seat 7 exactly in the middle.
  • the fuel which flows into the injection openings 8, flows through the annular gap remaining between the valve needle 3 and the wall of the pressure chamber 5 and is guided in the region of the guide section 10 by a plurality of bevels 12, which provide a sufficiently large flow cross-section.
  • a sealing surface 11 is formed, with which the valve needle 3 cooperates with the valve seat 7.
  • a collar 17 is formed on the valve needle 3, which extends annularly over the entire circumference of the valve needle 3.
  • the collar 17 is formed sharp-edged on its outer side, wherein the thus formed edge 20 has a length L. This results in a sharp-edged gap throttle 15 between the wall of the pressure chamber 5 and the edge 20th
  • the operation of the Kraftstoffeinspritventils is as follows: At the beginning of the injection cycle, the valve needle 3 is in its closed position, that is in contact with the valve seat 7.
  • the valve needle 3 is by a closing force, which is hydraulically the pressure in the control chamber 36 is generated, pressed against the valve seat 7.
  • fuel is at high pressure, but due to the closing force no resulting force in the longitudinal direction on the valve needle 3 exerts. If an injection takes place, then the closing force is reduced, and the valve needle 3 lifts off from the valve seat 7 and releases a flow of fuel from the pressure chamber 5 to the injection openings 8.
  • the closing force is increased again, so that the valve needle 3 experiences a resultant force on the valve seat 7 and slides back into its closed position.
  • the amount of this closing force depends crucially on the size of the pressure drop across the gap throttle 15.
  • the height of the pressure drop is in turn dependent on the cross section of the gap throttle 15 and the viscosity of the fuel, which is a function of the temperature and the pressure in the pressure chamber 5.
  • the sharp-edged design of the edge 20 ensures that the pressure drop and thus the damping at the gap throttle 15 is independent of the Reynolds number and thus independent of the viscosity and temperature of the fuel. This results in an always constant closing force on the valve needle 3 and a reproducible closing behavior regardless of the operating point and regardless of the temperature of the fuel.
  • Fig. 3a shows a plan view of the collar 17 and the gap choke 15 of a non-inventive embodiment.
  • the gap throttle 15 is formed by a sharp edge 20.
  • the gap throttle 15 is an annular gap with an outer diameter D a and an inner diameter D i , wherein the outer diameter D a the inner diameter of the pressure chamber 5 and the inner diameter D i corresponds to the diameter of the collar 17.
  • Fig. 3b shows an inventive embodiment of the collar 17, in which lateral poles 25 are provided, which give the collar 17 in cross section a substantially triangular shape.
  • the polished sections 25 are exaggerated here for the sake of clarity and the length K of these polished sections 25 of course depends on the length L of the collar 17.
  • a larger number of bevels 25 may be provided, for example, 4, 5 or 6 poles 25th
  • Fig. 3c shows a further non-inventive embodiment of the collar 17, in which case the gap throttle 15 is realized by a plurality of grooves 27 in the collar 17 and the maximum length L of the collar 17 in this case depends on the dimensions of the grooves 27.
  • the remaining gap between the valve needle 3 and the wall of the pressure chamber 6 is dimensioned between the grooves 27 so that there is practically a seal and the fuel thus flows exclusively through the grooves 27.
  • the boundary of the grooves 27 is sharp-edged, so that the independence of Reynolds number is maintained.
  • the gap choke 15 can be arranged inside or outside the guide section 10.
  • a gap choke On one side of the gap reactor 15 forming components may have a sharp edge and on the other side a smooth wall, as in the above example, the wall of the pressure chamber 5. It can also be provided that the gap choke 15 by a sharp edge on both sides is formed, for example by the sharp-edged collar 17 in the above embodiment Fig. 3a an equally sharp-edged ridge facing the inner wall of the pressure chamber 5. In a not too large opening stroke of the valve needle 3, the effect is maintained throughout the opening process.
  • collar and ridge are aligned with each other so that the maximum damping effect acts only in the open state of the nozzle needle 3, so the collar and ridge are exactly opposite, while at the beginning of the opening stroke only a small damping acts on the gap choke, which favors the pressure build-up at the injection openings 8.

Claims (2)

  1. Soupape d'injection de carburant pour moteurs à combustion interne, comprenant un corps de soupape (1), dans lequel est réalisée une chambre de pression (5) dans laquelle est disposé de manière mobile longitudinalement un pointeau de soupape (3), lequel coopère, par une surface d'étanchéité (11) réalisée sur le pointeau de soupape (3), avec un siège de soupape (7) qui délimite la chambre de pression (5), un flux de carburant jusqu'à au moins un orifice d'injection (8) étant rendu possible ou interrompu par la coopération du pointeau de soupape (3) avec le siège de soupape (7), le flux de carburant s'écoulant entre le pointeau de soupape (3) et la paroi de la chambre de pression (5) jusqu'aux orifices d'injection (8), une fente d'étranglement (15) à arêtes vives étant réalisée entre le pointeau de soupape (3) et la paroi de la chambre de pression (5), et comprenant un épaulement (17) réalisé sur le pointeau de soupape (3), lequel épaulement présente sur son bord extérieur une arête vive (20), de telle sorte que la fente d'étranglement (15) à arêtes vives soit réalisée entre l'épaulement (17) et la paroi de la chambre de pression (5), caractérisée en ce que l'épaulement (17) présente sur son côté extérieur un biseau (25) ou plusieurs biseaux (25), et en ce que l' arête (20) de l'épaulement (17) dans la région des biseaux (25) est réalisée sous forme d'arête vive, la région entre les biseaux (25) réalisant dans une large mesure l'étanchéité avec la paroi de la chambre de pression (5), de telle sorte que le carburant ne franchisse l'épaulement (17) que pratiquement dans la région des biseaux (25), la fente d'étranglement (15) à arêtes vives satisfaisant à la condition L/DHyd < 5, dans laquelle L est la longueur de la fente d'étranglement (15) et DHyd est le diamètre hydraulique (DHyd).
  2. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que le pointeau de soupape (3) est guidé à travers la paroi de la chambre de pression (5) par une portion de guidage (10) de la chambre de pression (5), la fente d'étranglement (15) étant disposée à proximité de la portion de guidage (10) en amont ou en aval de celle-ci.
EP08760983.0A 2007-07-13 2008-06-13 Étranglement au niveau du pointeau d'une soupape d'injection de carburant pour moteurs à combustion interne Active EP2171255B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007032741A DE102007032741A1 (de) 2007-07-13 2007-07-13 Kraftstoffeinspritzventil für Brennkraftmaschinen
PCT/EP2008/057451 WO2009010348A1 (fr) 2007-07-13 2008-06-13 Étranglement au niveau du pointeau d'une soupape d'injection de carburant pour moteurs à combustion interne

Publications (2)

Publication Number Publication Date
EP2171255A1 EP2171255A1 (fr) 2010-04-07
EP2171255B1 true EP2171255B1 (fr) 2014-12-17

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP08760983.0A Active EP2171255B1 (fr) 2007-07-13 2008-06-13 Étranglement au niveau du pointeau d'une soupape d'injection de carburant pour moteurs à combustion interne

Country Status (7)

Country Link
US (1) US20100193611A1 (fr)
EP (1) EP2171255B1 (fr)
JP (2) JP2010533263A (fr)
CN (1) CN101743394B (fr)
DE (1) DE102007032741A1 (fr)
RU (1) RU2468242C2 (fr)
WO (1) WO2009010348A1 (fr)

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EP2216542A1 (fr) * 2009-02-06 2010-08-11 Continental Automotive GmbH Ensemble de soupape pour soupape d'injection et soupape d'injection
DE102009029562A1 (de) 2009-07-30 2011-02-03 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE102009046452A1 (de) 2009-11-06 2011-05-12 Robert Bosch Gmbh Einspritzdüse für einen lecklosen Kraftstoffinjektor
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DE102009055135A1 (de) 2009-12-22 2011-06-30 Robert Bosch GmbH, 70469 Leckagefreier Kraftstoffinjektor
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WO2014066696A1 (fr) 2012-10-25 2014-05-01 Picospray, Llc Système d'injection de carburant
JP5716788B2 (ja) * 2013-04-25 2015-05-13 株式会社デンソー 燃料噴射弁
DE102013209251A1 (de) 2013-05-17 2014-11-20 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
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DE102015219376A1 (de) * 2015-10-07 2017-04-13 Robert Bosch Gmbh Düsenbaugruppe für einen Kraftstoffinjektor und Kraftstoffinjektor
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US10859073B2 (en) 2016-07-27 2020-12-08 Briggs & Stratton, Llc Reciprocating pump injector
DE102016215710A1 (de) 2016-08-22 2018-02-22 Robert Bosch Gmbh Düsenbaugruppe für einen Kraftstoffinjektor, Kraftstoffinjektor
DE102016215798A1 (de) 2016-08-23 2018-03-01 Robert Bosch Gmbh Düsenbaugruppe für einen Kraftstoffinjektor, Kraftstoffinjektor
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CN109681360A (zh) * 2019-02-28 2019-04-26 一汽解放汽车有限公司 一种用于燃料喷射阀的长针阀

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DE10024703A1 (de) 2000-05-18 2001-11-22 Bosch Gmbh Robert Einspritzanordnung für ein Kraftstoff-Speichereinspritzsystem einer Verbrennungsmaschine
DE10055651A1 (de) * 2000-11-10 2002-05-23 Bosch Gmbh Robert Druckgesteuerter Injektor mit optimierten Einspritzverlauf über den Hubweg
DE10149961A1 (de) * 2001-10-10 2003-04-30 Bosch Gmbh Robert Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine, insbesondere Common-Rail-Injektor, sowie Kraftstoffsystem und Brennkraftmaschine
JP3855101B2 (ja) * 2002-03-27 2006-12-06 株式会社ケーヒン 燃料噴射弁の取付け構造
DE102005009147A1 (de) * 2005-03-01 2006-09-07 Robert Bosch Gmbh Kraftstoffinjektor für Verbrennungskraftmaschinen

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CN101743394B (zh) 2015-06-24
JP2012193748A (ja) 2012-10-11
JP5542879B2 (ja) 2014-07-09
RU2010104947A (ru) 2011-08-20
DE102007032741A1 (de) 2009-01-15
EP2171255A1 (fr) 2010-04-07
CN101743394A (zh) 2010-06-16
US20100193611A1 (en) 2010-08-05
JP2010533263A (ja) 2010-10-21
WO2009010348A1 (fr) 2009-01-22
RU2468242C2 (ru) 2012-11-27

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