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EP1364114B1 - Dispositif de dosage de liquide comprenant une zone d'etranglement - Google Patents

Dispositif de dosage de liquide comprenant une zone d'etranglement Download PDF

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Publication number
EP1364114B1
EP1364114B1 EP01992833A EP01992833A EP1364114B1 EP 1364114 B1 EP1364114 B1 EP 1364114B1 EP 01992833 A EP01992833 A EP 01992833A EP 01992833 A EP01992833 A EP 01992833A EP 1364114 B1 EP1364114 B1 EP 1364114B1
Authority
EP
European Patent Office
Prior art keywords
chamber
valve needle
dosing device
fluid dosing
metal bellows
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
EP01992833A
Other languages
German (de)
English (en)
Other versions
EP1364114A2 (fr
Inventor
Andreas Kappel
Bernhard Fischer
Randolf Mock
Bernhard Gottlieb
Enrico Ulivieri
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.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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
Priority claimed from DE2000154182 external-priority patent/DE10054182A1/de
Priority claimed from DE2000160939 external-priority patent/DE10060939A1/de
Application filed by Siemens AG, Siemens Corp filed Critical Siemens AG
Publication of EP1364114A2 publication Critical patent/EP1364114A2/fr
Application granted granted Critical
Publication of EP1364114B1 publication Critical patent/EP1364114B1/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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • 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
    • F02M61/08—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 the valves opening in direction of fuel flow
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for

Definitions

  • the present invention relates to a Fluiddosiervoriques for a pressurized fluid having a chamber located in a housing, which is supplied through a fluid supply line, the pressurized fluid, and with a valve needle guided through the chamber, the first end portion is acted upon outside the chamber with a stroke and whose second end portion forms a valve seat connected to the chamber with a valve seat provided on the housing.
  • valve needle can continue to take place similar to diesel injectors by a clearance of the needle in a cylindrical housing bore.
  • the disadvantage here is the unavoidable leakage along the needle feedthrough. By the larger hydraulic losses also reduce the overall efficiency of the engine.
  • a fluid device according to the preamble of claim 1 is known from EP1046809 A2.
  • Object of the present invention is to provide in a generic Fluiddosiervorraum particular dense implementation of the valve needle, which achieves a required creep rupture strength.
  • a Fluiddosiervorraum according to the preamble of claim 1, characterized in that circumferentially provided between the valve needle and the chamber inner wall at least one throttle point in the chamber section between the lead-through element and the mouth of the fluid supply line into the chamber.
  • the metal bellows fail when used in a high-pressure injection valve at a static pressure load of 200 bar already after about 10 min. This is due to the fact that when opening and closing the injector or injector pressure waves in the fuel chamber of the injector are triggered, in response to the opening and closing time of the injector with an amplitude of up to ⁇ 50% of the set fuel pressure and a frequency from about 500 Hz - 10 kHz, typically in the range of about 500 - 800 Hz, to swing the set basic pressure. The occurrence of such pressure oscillations leads to failure of the metal bellows seal when pressure waves are triggered.
  • the throttle points provided according to the invention protect the metal bellows against the destructive effect of these pressure oscillations.
  • the invention thus a sufficient tightness of the fuel chamber is realized by the metal bellows, the bellows seal is protected from the pressure waves occurring during operation and thereby a motor vehicle technically typical creep rupture strength of at least 10 9 load cycles (about 2000 operating hours) is reached.
  • the metal bellows has a wall thickness of 25 to 500 ⁇ m. These low wall thicknesses have proven to be completely sufficient at high pressures of for example 300 bar. Experiments have shown that a formation of the metal bellows in the form of - visible in longitudinal section - juxtaposed semicircular segments provides particular advantages. These semicircular segments can each be supplemented by intervening straight sections.
  • the elastic feedthrough element is fastened to a mounting sleeve, in particular by a welded connection.
  • a metal bellows can be attached directly to the valve needle only with comparatively great effort.
  • the mounting sleeve is also an element ready, can be realized by a simple way a precisely dimensioned throttle in the fuel chamber.
  • an upper guide sleeve is an alternative or in addition to the suitably dimensioned mounting sleeve designed such that a tight and long as possible clearance fit is realized by this valve needle guide. Since the upper valve needle guide is provided anyway at the fuel injector, additional components can be omitted.
  • the free cross section between the valve needle and the chamber inner wall is changed abruptly in the region of the throttle point. This results in the desired reflection of the pressure waves at the chamber inner wall section extending transversely to the propagation direction of the pressure waves.
  • the gap width of the throttle point is selected as a function of the position of the throttle point in the fuel chamber and the length of the throttle gap, taking into account the static and dynamic pressure conditions. There have been some microns as a typical value for the gap width of the throttle point in the fuel chamber of a high pressure fuel injector.
  • the fuel injection valve 1 has a housing 3 with a central bore in which a valve body 5 is mounted.
  • a valve needle 9 is guided axially displaceable.
  • a lower and front and an upper or rear guide sleeve 11, 13 are attached, forming the corresponding valve needle guides.
  • the constrictions realized thereby are designed so that they do not hinder or restrict a liquid flow when opening and closing the valve 1.
  • valve needle 9 is provided both at the level of the lower and the upper guide sleeve 11, 13 and the two valve needle guides with a circumferentially protruding, rounded square section according to Fig. 1a, b (section AA and section BB).
  • the free gap between the four side surfaces of the square of the valve needle 9 and the cylindrical inner wall of the guide sleeves 11, 13 is designed to be significantly larger in order to avoid any throttling effect.
  • valve plate 15 formed on the front end portion of the valve needle 15 closes a valve seat 16 in the valve body.
  • the valve body has a valve body fuel supply line 17 which, viewed in the axial extent, lies between the lower and upper guide sleeves 11, 13 with a junction 19 the valve body bore 7 opens. Accordingly, a housing fuel supply line 21 is provided in the valve housing 3.
  • a spring plate 23 is attached to this. In this presses a nozzle spring 25, which is supported on the housing side and thereby biases the valve needle 9 in the closing direction.
  • an outer mounting sleeve 27 is fixed in the central bore of the valve housing 3.
  • the outer mounting sleeve 27 has at the lower end a sleeve collar 44 which rests on an annular bearing surface 45 on the housing 3.
  • the sleeve collar has an outer surface 46, which is arranged an inner wall 47 of the housing 3. Between the outer surface 46 and the inner wall 47, a sealing element 48 is inserted in the form of a sealing ring.
  • the sleeve collar 44 is sealed with an annular circumferential weld 49 tightly welded to the inner wall 47. This forms through an opening in a sleeve bottom 29 a needle feedthrough, which is sealed as described below.
  • the outer mounting sleeve 27 whose inner wall forms a bottleneck described in more detail below with the outer wall of an inner mounting sleeve 31, which in turn is attached to the valve needle 9.
  • 31 is welded to the outer and inner mounting sleeve 27, 31 is welded a cylindrical metal bellows 33, through which the valve needle 9 is guided to the outside.
  • the metal bellows 33 serves to hermetically seal the fuel chamber 35 with respect to a pressureless, air-filled gap 36.
  • the metal bellows 33 in the region of the opening on Sleeve bottom 29 and mounted on a surface of the inner mounting sleeve 31, which faces the sleeve bottom 29.
  • the use of the metal bellows 33 in the needle feedthrough allows a complete, permanent and reliable sealing of the high-pressure region in the chamber 35 of the injection valve 1 with respect to the gap 36 with the drive region, not shown.
  • the metal bellows 33 despite a small wall thickness of, for example, 50 to 500 ⁇ m, withstand very high pressures due to its high radial rigidity, without being irreversibly deformed.
  • the metal bellows 33 may be further configured to provide high mechanical compliance, i. a small spring constant in the direction of movement of the valve needle or axial direction is achieved. This ensures that the deflection of the valve needle 9 is not affected, and that caused by temperature-induced changes in length of the needle feedthrough into the valve needle forces are kept as small as possible. Furthermore, the fuel leakage can be prevented by the use of the metal bellows 33 in the needle feedthrough with high reliability.
  • the metal bellows-sealed needle feedthrough in the outer mounting sleeve 27 can also be designed so that the forces acting on the valve needle 9 pressure-related forces compensate each other. As a result, the valve needle 9 is kept completely free of pressure.
  • the hydraulically effective diameter of the metal bellows is selected so that it corresponds exactly to the diameter of the valve seat 16 (not shown).
  • the metal bellows 33 Due to its metallic material, the metal bellows 33 furthermore have a wide operating temperature range with constant functionality. Thermal changes in length of the metal bellows 33 themselves lead due to the small axial spring constant of the metal bellows only negligible force changes to the valve needle 9 in the axial direction. The metal bellows can also partially or completely replace the nozzle spring 25 due to its mechanical spring action in the axial direction.
  • the outer mounting sleeve 27 is shown in FIG. 1a now designed so that it forms a close and long as possible clearance together with the inner mounting sleeve 31.
  • the game is only a few microns. Due to the throttling effect of this long cylindrical fit, rapid pressure changes in the fuel chamber 35 are kept away from the metal bellows 33, while static pressures can act unimpeded on the bellows wall.
  • the pressure waves in the region of the jump in cross section of the first throttle body 37 are reflected at the chamber wall section or the sleeve end face extending transversely to the axial direction so that only a pressure wave with a greatly reduced pressure amplitude continues into the annular gap formed by the first throttle restriction 37.
  • a fuel injection valve 1 according to the second embodiment in contrast to the valve 1 according to the first embodiment, only a modification in the first throttle body 37 made in that the free inner diameter of the sleeve collar 44 of the outer mounting sleeve 27 at the same throttle gap dimensions in favor of Outer diameter of the inner mounting sleeve 31 is reduced.
  • the throttle gap between inner and outer Mounting sleeve 27, 31 chosen so small and long that a sufficient throttling effect is realized.
  • the triggered during the opening and closing of the valve 1 in the fuel chamber 35 pressure waves can not or only slightly act on the metal bellows 33 due to the small distance between the inner and outer mounting sleeve 27, 31.
  • a fuel injection valve 1 according to the third embodiment shown in Fig. 3a, b instead of the first throttle point according to the first two embodiments, alternatively, a second throttle point 39 in the region of the upper valve needle guide and the upper guide sleeve 13. Since the fuel supply line 17 opens below the upper valve needle guide 13 into the space between the valve needle 9 and the valve body 5 or the fuel chamber 35, the fuel to be injected therein does not have to pass the upper valve needle guide 13. Therefore, the upper valve needle guide itself can be formed as a tight, long cylindrical clearance of the valve needle 9 in the upper guide sleeve 13, as shown in section BB in Fig. 3b.
  • valve needle 9 in contrast to the lower valve needle guide (section AA) is not formed as a square, but cylindrical (section BB).
  • the pressure waves triggered during opening and closing operations are reflected and a dynamic volume exchange in the direction of the metal bellows 33 is strongly throttled.
  • the throttling action of the upper valve needle guide 13 separates the fuel chamber 35 into two sub-volumes, namely first and second chamber sub-volumes 41, 43.
  • the throttling points 37, 39 shown in FIGS. 1, 2 and 3 are realized together in one valve.
  • the first throttle body 37 is formed by the inner and outer mounting sleeves 27, 31 and the second throttle body 39 is formed by the upper guide sleeve 13 and the upper valve needle guide, respectively.
  • a bellows in the form of a metal bellows has been described as an elastic feedthrough element.
  • the invention is not limited to this type of elastic feedthrough element but can also be applied to other types of elastic feedthrough elements such as e.g. a membrane or a resilient plastic or rubber sleeve are used.
  • the membrane is preferably made of metal.
  • the membrane and the sleeve are glued or welded according to the described metal bellows with the inner and outer mounting sleeve 27, 31.
  • the pressure in the second chamber sub-volume 43 can be adjusted by the choice of the diameter of the clearance fit of the valve needle 9 compared to the hydraulically effective diameter of the metal bellows 33.
  • the diameter of the clearance larger (or smaller) than the hydraulically effective diameter of the metal bellows 33 is achieved that the pressure in the second chamber sub-volume 43 when opening the injector decreases (or increases). It is particularly advantageous if the diameter of the clearance fits the hydraulically effective diameter of the metal bellows 33, because in this way the pressure in the second chamber sub-volume 43 remains substantially constant when the injection valve is opened; the metal bellows 33 is then exposed in all operating conditions only a constant pressure load.

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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)
  • Containers And Packaging Bodies Having A Special Means To Remove Contents (AREA)

Claims (9)

  1. Doseur de fluide pour un fluide sous pression, ledit doseur comportant une chambre (35) située dans un boîtier (3) et alimentée en fluide sous pression par un conduit d'amenée de fluide (17, 21), et une aiguille de soupape (9) passant à travers ladite chambre (35) et dont la première extrémité peut être soumise, à l'extérieur de la chambre, à une course, et dont la deuxième extrémité forme, avec un siège de soupape (16) prévu dans le boîtier (3), une soupape reliée à la chambre (35), un élément de passage élastique (33) étant prévu pour permettre le passage de la première extrémité de l'aiguille de soupape (9) depuis la chambre (35) vers l'extérieur, lequel ferme de manière étanche la chambre au niveau de cette zone,
       caractérisé en ce qu'
       il est prévu sur la circonférence, entre l'aiguille de soupape (9) et la paroi intérieure de la chambre, au moins un point d'étranglement (37, 39) dans la partie de la chambre située entre l'élément de passage (33) et l'embouchure (19) du conduit d'amenée de fluide (17) donnant dans la chambre (35), une fente constituant le point d'étranglement (37, 39) ayant une largeur ne dépassant pas quelques µm.
  2. Doseur de fluide selon la revendication 1,
       caractérisé en ce que
       l'élément de passage prévu est un soufflet, notamment un soufflet métallique (33).
  3. Doseur de fluide selon la revendication 2,
       caractérisé en ce que
       le soufflet métallique (33) présente une épaisseur de paroi comprise entre 25 et 500 µm.
  4. Doseur de fluide selon les revendications 1 à 3,
       caractérisé en ce que
       l'élément de passage (33) est fixé à une douille de montage (31), notamment par une soudure.
  5. Doseur de fluide selon la revendication 4,
       caractérisé en ce que
       le point d'étranglement (37) dans la chambre (35) est formé par la douille de montage (31).
  6. Doseur de fluide selon l'une des revendications précédentes,
       caractérisé en ce qu'
       il est prévu un guide supérieur d'aiguille de soupape (13) et en ce que le point d'étranglement (39) dans la chambre (35) est formé par le guide supérieur d'aiguille de soupape.
  7. Doseur de fluide selon l'une des revendications précédentes,
       caractérisé en ce que,
       dans la zone du point d'étranglement (37, 39), la section libre entre l'aiguille de soupape (9) et la paroi intérieure de la chambre est modifiée de manière brusque.
  8. Doseur de fluide selon l'une des revendications précédentes,
       caractérisé en ce que
       le fluide utilisé est du carburant, et en ce que la pression du carburant est comprise entre 1 et 500 bars.
  9. Doseur de fluide selon l'une des revendications précédentes,
       caractérisé en ce que
    le diamètre d'un ajustement avec jeu de l'aiguille de soupape (9) correspond au diamètre efficace, sur le plan hydraulique, du soufflet métallique (33).
EP01992833A 2000-11-02 2001-10-29 Dispositif de dosage de liquide comprenant une zone d'etranglement Expired - Lifetime EP1364114B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10054182 2000-11-02
DE2000154182 DE10054182A1 (de) 2000-11-02 2000-11-02 Fluiddosiervorrichtung mit Drosselstelle
DE10060939 2000-12-07
DE2000160939 DE10060939A1 (de) 2000-12-07 2000-12-07 Fluiddosiervorrichtung mit Drosselstelle
PCT/DE2001/004089 WO2002036959A2 (fr) 2000-11-02 2001-10-29 Dispositif de dosage de liquide comprenant une zone d'etranglement

Publications (2)

Publication Number Publication Date
EP1364114A2 EP1364114A2 (fr) 2003-11-26
EP1364114B1 true EP1364114B1 (fr) 2005-09-21

Family

ID=26007546

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01992833A Expired - Lifetime EP1364114B1 (fr) 2000-11-02 2001-10-29 Dispositif de dosage de liquide comprenant une zone d'etranglement

Country Status (6)

Country Link
US (1) US7044407B2 (fr)
EP (1) EP1364114B1 (fr)
JP (1) JP3914875B2 (fr)
KR (1) KR100588766B1 (fr)
DE (1) DE50107526D1 (fr)
WO (1) WO2002036959A2 (fr)

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DE202007012345U1 (de) * 2007-09-04 2009-01-08 Witzenmann Gmbh Metallbalg

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JP4079144B2 (ja) * 2004-12-20 2008-04-23 株式会社豊田中央研究所 燃料噴射弁
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DE102006057425A1 (de) * 2006-05-23 2007-11-29 Robert Bosch Gmbh Vorrichtung zur Regeneration, zur Temperaturbeaufschlagung und/oder zum Thermomanagement, zugehöriges Einspritzventil und Verfahren
US20100001094A1 (en) * 2008-07-03 2010-01-07 Caterpillar Inc. Apparatus and method for cooling a fuel injector including a piezoelectric element
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DE102009000186A1 (de) * 2009-01-13 2010-07-15 Robert Bosch Gmbh Vorrichtung zur Einspritzung von Kraftstoff
EP2366888A1 (fr) 2010-03-17 2011-09-21 Continental Automotive GmbH Ensemble de soupape pour soupape d'injection, soupape d'injection et procédé pour assembler un ensemble de soupape d'une soupape d'injection
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DE102011003163A1 (de) * 2011-01-26 2012-07-26 Robert Bosch Gmbh Einspritzventil mit Durchflussbegrenzer
EP2500550A1 (fr) * 2011-03-16 2012-09-19 Siemens Aktiengesellschaft Transmetteur de course pour turbine à gaz
EP2568155B1 (fr) * 2011-09-09 2018-11-14 Continental Automotive GmbH Ensemble de soupape et soupape d'injection
DE102012203607A1 (de) * 2012-03-07 2013-09-12 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids
DE102012203700A1 (de) * 2012-03-08 2013-09-12 Man Diesel & Turbo Se Vorrichtung zum Freigeben eines Strömungsquerschnitts einer Gasleitung
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DE102013012444A1 (de) * 2013-07-29 2015-01-29 Astrium Gmbh Ventilanordnung zum Schalten und/oder Regeln eines Medienstroms eines Raumfahrttriebwerks und Raumfahrttriebwerk
EP2863048B1 (fr) * 2013-10-21 2017-12-06 C.R.F. Società Consortile Per Azioni Électro-injecteur à combustible pour système d'injection de carburant d'un moteur à combustion interne
DE102014200756A1 (de) * 2014-01-17 2015-07-23 Robert Bosch Gmbh Gasinjektor zum Direkteinblasen von gasförmigem Kraftstoff in einen Brennraum
DE102021203738A1 (de) * 2021-04-15 2022-10-20 Robert Bosch Gesellschaft mit beschränkter Haftung Gasinjektor mit kurzer axialer Bauweise
CN114653540B (zh) * 2022-04-19 2023-12-22 深圳市启扬智能装备有限公司 关节式喷射阀
CN114791051B (zh) * 2022-04-26 2023-12-26 浙江三花智能控制股份有限公司 一种节流阀装置

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Publication number Priority date Publication date Assignee Title
DE202007012345U1 (de) * 2007-09-04 2009-01-08 Witzenmann Gmbh Metallbalg

Also Published As

Publication number Publication date
US20040004139A1 (en) 2004-01-08
JP3914875B2 (ja) 2007-05-16
KR20030051777A (ko) 2003-06-25
JP2004513286A (ja) 2004-04-30
EP1364114A2 (fr) 2003-11-26
WO2002036959A2 (fr) 2002-05-10
DE50107526D1 (de) 2005-10-27
KR100588766B1 (ko) 2006-06-14
US7044407B2 (en) 2006-05-16
WO2002036959A3 (fr) 2003-09-12

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