EP1519037B1 - Soupape d'injection de carburant - Google Patents

Soupape d'injection de carburant Download PDF

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Publication number
EP1519037B1
EP1519037B1 EP20040104647 EP04104647A EP1519037B1 EP 1519037 B1 EP1519037 B1 EP 1519037B1 EP 20040104647 EP20040104647 EP 20040104647 EP 04104647 A EP04104647 A EP 04104647A EP 1519037 B1 EP1519037 B1 EP 1519037B1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
injection valve
coupler
valve according
equalizing element
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 - Fee Related
Application number
EP20040104647
Other languages
German (de)
English (en)
Other versions
EP1519037A1 (fr
Inventor
Hubert Stier
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 EP1519037A1 publication Critical patent/EP1519037A1/fr
Application granted granted Critical
Publication of EP1519037B1 publication Critical patent/EP1519037B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/707—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for avoiding fuel contact with actuators, e.g. isolating actuators by using bellows or diaphragms

Definitions

  • the invention relates to a fuel injection valve according to the preamble of the main claim.
  • a fuel injection valve with a piezoelectric or magnetostrictive actuator which is in operative connection with a valve needle.
  • the valve needle has at its discharge end a valve closing body which cooperates with a valve seat surface to a sealing seat.
  • a coupler which serves to compensate for changes in length of components of the fuel injection valve, in particular of temperature-induced changes in length of the actuator, is arranged on the inflow side of the actuator module.
  • the coupler has two mutually axially movable portions which engage with each other and thereby form an annular gap and a hydraulic volume.
  • the annular gap connects the hydraulic volume with a balanced under a form equalization space.
  • the hydraulic medium is exchanged between the hydraulic volume and the compensation chamber, wherein the annular gap serves as a throttle point.
  • a disadvantage of the fuel injection valve known from the above publication is in particular that the temperature-induced expansion of the hydraulic medium are only insufficiently compensated. If a change in volume of the hydraulic medium is compensated for by exchanging hydraulic medium between the hydraulic volume and the compensation chamber, the pressure in the compensation chamber changes, resulting in a pressure increase in the expansion chamber when filling the compensation chamber, which counteracts further filling. The force with which the valve closing body acts in the sealing seat is undesirably changed in this way via different temperature states of the fuel injection valve. This leads in particular to the fact that the design of other components of the fuel injection valve is possible only with considerably more effort and also lower tolerances must be maintained.
  • the fuel injection valve according to the invention with the features of the main claim has the advantage that in particular the sealing force of the sealing seat in all temperature ranges can be kept constant by simple and inexpensive measures. This simplifies the design and construction of other components and the fuel injector as a whole.
  • the coupler is also more independent of temperature fluctuations in its behavior.
  • the compensation element has a solid state of aggregation at the operating temperatures of the fuel injection valve. This can be the Permanently separate the compensating element from the hydraulic medium.
  • first coupler section forms a hollow cylindrical shape closed on one side into which the cylindrically shaped second coupler section at least partially engages and thereby forms the gap.
  • the coupler can be constructed in a particularly simple manner.
  • the second coupler section consists at least partially of the compensation element.
  • the fuel injection valve can be very easily constructed and assembled.
  • a recess is made in one of the coupler sections, in which the compensation element is arranged.
  • the coupler can be made more compact and easier.
  • the compensating element has a lower coefficient of thermal expansion than the hydraulic medium, the compensation can take place in a particularly simple manner.
  • the coupler can be very easy to assemble and assemble.
  • the coupler can thereby be better integrated into the actuation strand of the fuel injection valve, since, for example, the flexible section can easily be arranged on the coupler so that the flexible section does not lie in the actuation axis of the actuation strand.
  • the flexible section can be very easily manufactured and assembled.
  • the movements of the actuator module can be transferred directly to the coupler sections and the dynamic characteristics of the fuel injection valve are only minimally negatively affected.
  • the hydraulic medium ideally consists of an oil or a gel.
  • An inventive fuel injection valve 1 shown in an axial sectional view in FIG. 1 is used in particular for the direct injection of fuel into a combustion chamber of a mixture-compressing, spark-ignited internal combustion engine.
  • an interlocking housing upper part 4 and a coaxially arranged housing lower part 5, a valve needle 8, an actuator 2, a nozzle body 6 and a hydraulic coupler 3 are arranged coaxially to each other.
  • the nozzle body 6 penetrates from the inside with its downstream end, the downstream end of the Housing lower part 5.
  • actuator 2 communicates with the valve needle 8 via an actuator head 10 and an intermediate piece 9, which passes through the upper housing part 4 in the region of the discharge end of the upper housing part 4 in operative connection.
  • the first spring element 21 is clamped between a shoulder 40 formed in the nozzle body 6 and a flange 26 arranged on the inflow side thereof and fixed to the valve needle 8.
  • the spring force of the first spring element 21 pulls the valve closing body 7 into the sealing seat in the case of the fuel injection valve 1 that opens outward in this exemplary embodiment.
  • the hydraulic coupler 3 in this embodiment essentially has a first coupler section 23 and a cylindrical second coupler section 24.
  • the first coupler portion 23 forms a closed on one side, introduced in the upper housing part 4, hollow cylindrical shape 17, in which the second coupler section 24 engages downstream.
  • a located between the bottom of the mold 17 and the mold 17 facing the end face of the second portion 24 befindliches hydraulic volume 36 is variable by the axial displacement of the second coupler portion 24 relative to the first coupler section 23.
  • the second coupler section 24 is guided in the first coupler section 23, or in the form 17, with a clearance 32 which, for example, is between 2 and 10 micrometers and is generated by a gap 25.
  • the ratio of the minimum engagement depth of the second portion 24 to its diameter is selected so that the second portion 24 in the mold 17 can not tilt.
  • a second spring element 20 designed as a spiral spring in this exemplary embodiment revolves around the second coupler section 24 in the area of its downstream end. The second spring element 20 presses the actuator base 11 with a bias on the actuator 2, wherein the second spring element 20 is supported on the inflow side of a first stage 42 rotating around the mold 17 and on the second stage 43 downstream.
  • a corrugated tube-shaped, made of steel and elastic flexible portion 27 is disposed within the second spring element 20 in this embodiment.
  • the upstream end of the flexible portion 20 is in the first stage 42 hermetically sealed, for example by welding, joined.
  • the downstream end of the flexible portion 20 is in the vicinity of the actuator base 11 laterally hermetically sealed to the second coupler portion 24, for example by welding.
  • the flexible section 27 closes off the gap 25 and, together with the region of the discharge-side end of the second coupler section 24, defines a compensation chamber 14.
  • the compensation chamber 14 is connected to the hydraulic volume 36 through the gap 25.
  • a recess 16 Arranged in the second coupler section 24 is a recess 16 which is open towards the hydraulic volume 36 and which is assigned to the hydraulic volume 36 and, in this embodiment, has a hollow-cylindrical shape.
  • a of the shape of the recess 16 similar compensating element 15 is arranged, wherein the compensating element 15 is inserted only in the recess 16 and thus all its outer surfaces are surrounded by hydraulic medium.
  • the compensation element 15 may be fixed or joined in the recess 16, for example, by a weld at the bottom of the recess 16 or a positive connection.
  • the in Invar 16 inserted from Invar steel compensating element 15 has a lower coefficient of thermal expansion than the hydraulic medium and / or the materials of which the first coupler section 24 in the hydraulic volume 36 is. Since the commonly used hydraulic media expand more than the coupler sections 23, 24, but the compensating element 15 expands less strongly, the compensating element 15 at least partially compensates for the different expansions of the coupler sections 23, 24 and the hydraulic medium.
  • the first coupler portion 23 in particular in the region of the hollow cylindrical shape 17 and the hydraulic volume 36, consist of the compensating element 15.
  • the part of the first coupler portion 23 made of, for example, bronze, brass, aluminum or a thermoplastic resin material has an expansion coefficient greater than or equal to that of the hydraulic medium.
  • the compensation chamber 14, the gap 25 and the hydraulic volume 36 with the recess 16 are completely filled with an oily, gas-free and incompressible hydraulic medium.
  • the flexible section 27 is characterized by the selection of materials and / or by a coating diffusion-tight and acts on the hydraulic medium by its elasticity with a pressure.
  • the actuator 2 If the actuator 2 is energized via an electrical line, not shown, it expands quickly. Since the hydraulic medium can not drain off fast enough from the hydraulic volume 36 in the compensation chamber 14, the coupler 3 behaves very hard, whereby the length of the actuator 2 acts almost completely on the valve needle 8. The valve needle 8 is moved axially against the biasing force of the first spring element 21 in the discharge direction. As a result, the sealing seat opens and the fuel, which is supplied with pressure via the fuel channel 22, which is shown only in part, is sprayed via the injection opening 12 into the combustion chamber (not shown). Slow changes in length of the actuator 2 are compensated by the exchange of hydraulic fluid between the hydraulic volume 36 and the compensation chamber 14.
  • the invention is not limited to the illustrated embodiments and may, for. B. also be used for inward-opening fuel injectors.

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

Claims (14)

  1. Injecteur de carburant (1), en particulier, destiné à injecter directement du carburant dans une chambre de combustion d'un moteur à combustion interne, comportant un actionneur piézoélectrique, électrostrictif ou magnétostrictif (2), un obturateur de soupape (7) en liaison active avec l'actionneur (2) et qui coopère avec une surface de siège de soupape (13) pour former un siège d'étanchéité, et un coupleur (3) qui présente un premier segment de coupleur (23) et un second segment de coupleur (24), les deux segments de coupleur (23, 24) mobiles l'un contre l'autre étant en liaison active l'un avec l'autre par un milieu hydraulique situé dans un volume hydraulique (36), lequel volume hydraulique (36) est en liaison avec au moins une chambre de compensation (14) pour échanger le moyen hydraulique, alors qu'au moins l'un des segments de coupleur (23, 24) est guidé avec un jeu (32) formé par une fente (25),
    caractérisé en ce qu'
    au moins un élément de compensation (15) compense les modifications de volume du milieu hydraulique dues aux températures, et l'élément de compensation (15) au moins en partie limite le volume hydraulique (36) et/ou est installé dans le volume hydraulique (36).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    l'élément de compensation (15) présente un état solide avec des températures de service de l'injecteur de carburant (1), en particulier entre 20°C et 100°C.
  3. Injecteur de carburant selon la revendication 1 ou 2,
    caractérisé en ce que
    le premier segment de coupleur (23) est une forme cylindrique creuse fermée sur un côté (17), et le second segment de coupleur (24) cylindrique s'engage au moins en partie pour former la fente (25).
  4. Injecteur de carburant selon la revendication 3,
    caractérisé en ce que
    le second segment de coupleur (24) se compose au moins en partie de l'élément de compensation (15).
  5. Injecteur de carburant selon la revendication 3 ou 4,
    caractérisé en ce qu'
    au moins un évidement (16) ouvert directement vers le volume hydraulique (36) est pratiqué dans au moins l'un des segments de coupleur (23, 24), avec au moins un élément de compensation (15) installé dans l'évidement (16).
  6. Injecteur de carburant selon la revendication 5,
    caractérisé en ce que
    la surface extérieure totale de l'élément de compensation (15) est en contact avec le milieu hydraulique.
  7. Injecteur de carburant selon l'une quelconque des revendications 3 à 6,
    caractérisé en ce que
    l'élément de compensation (15) présente un coefficient de dilation de température plus faible que le milieu hydraulique et/ou que les matériaux dont se compose le premier segment de coupleur (24) dans la zone du volume hydraulique (36).
  8. Injecteur de carburant selon l'une quelconque des revendications 3 à 7,
    caractérisé en ce que
    l'élément de compensation (15) se compose d'acier Invar.
  9. Injecteur de carburant selon la revendication 3,
    caractérisé en ce qu'
    au moins une partie du premier segment de coupleur (23), en particulier dans la zone de la forme cylindrique creuse (17), se compose de l'élément de compensation (15).
  10. Injecteur de carburant selon la revendication 9,
    caractérisé en ce que
    le coefficient de dilation de température de l'élément de compensation (15) est supérieur ou égal à celui du milieu hydraulique.
  11. Injecteur de carburant selon la revendication 9 ou 10,
    caractérisé en ce que
    l'élément de compensation (15) se compose au moins en partie d'un alliage cuivre-étain, d'un alliage cuivre-zinc, d'aluminium ou d'un matériau thermoplastique.
  12. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'
    une partie flexible (27) limite au moins en partie la chambre de compensation (14).
  13. Injecteur de carburant selon la revendication 12,
    caractérisé en ce que
    la partie flexible (27) a la forme d'un disque à trous ou d'un tube ondulé.
  14. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le milieu hydraulique est une huile ou un gel.
EP20040104647 2003-09-29 2004-09-24 Soupape d'injection de carburant Expired - Fee Related EP1519037B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10345203 2003-09-29
DE2003145203 DE10345203A1 (de) 2003-09-29 2003-09-29 Brennstoffeinspritzventil

Publications (2)

Publication Number Publication Date
EP1519037A1 EP1519037A1 (fr) 2005-03-30
EP1519037B1 true EP1519037B1 (fr) 2006-07-05

Family

ID=34178010

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20040104647 Expired - Fee Related EP1519037B1 (fr) 2003-09-29 2004-09-24 Soupape d'injection de carburant

Country Status (2)

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EP (1) EP1519037B1 (fr)
DE (2) DE10345203A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE602005005242T2 (de) * 2004-04-26 2009-04-02 Isuzu Motors Ltd. Längen-Ausgleichselement und dieses enthaltendes Kraftstoff-Einspritzventil
DE102005009147A1 (de) * 2005-03-01 2006-09-07 Robert Bosch Gmbh Kraftstoffinjektor für Verbrennungskraftmaschinen
EP1813805A1 (fr) * 2006-01-27 2007-08-01 Siemens VDO Automotive S.p.A. Ensemble de compensation pour un injecteur
DE102008035087B4 (de) * 2008-07-28 2015-02-12 Continental Automotive Gmbh Einspritzventil
DE102010027278B4 (de) * 2010-07-15 2020-07-02 Metismotion Gmbh Thermisch volumenneutraler Hubübertrager sowie Dosierventil mit einem solchen Hubübertrager und Verwendung des Dosierventils
GB201512350D0 (en) * 2015-07-15 2015-08-19 Delphi Int Operations Lux Srl Servo actuator for fuel injector
EP3139028A1 (fr) 2015-09-03 2017-03-08 Delphi International Operations Luxembourg S.à r.l. Coupleur à double extrémité pour servocommande

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3533085A1 (de) * 1985-09-17 1987-03-26 Bosch Gmbh Robert Zumessventil zur dosierung von fluessigkeiten oder gasen
DE59811027D1 (de) * 1997-04-04 2004-04-29 Siemens Ag Einspritzventil mit Mitteln zur Kompensation der thermischen Längenänderung eines Piezoaktors
DE19727992C2 (de) * 1997-07-01 1999-05-20 Siemens Ag Ausgleichselement zur Kompensation temperaturbedingter Längenänderungen von elektromechanischen Stellsystemen
DE19940055C1 (de) * 1999-08-24 2001-04-05 Siemens Ag Dosierventil
DE19940054C2 (de) * 1999-08-24 2003-11-27 Siemens Ag Dosierventil für ein unter Druck stehendes Fluid
DE19946841A1 (de) * 1999-09-30 2001-05-03 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE19947779A1 (de) * 1999-10-02 2001-04-12 Bosch Gmbh Robert Brennstoffeinspritzventil
DE19950760A1 (de) * 1999-10-21 2001-04-26 Bosch Gmbh Robert Brennstoffeinspritzventil
WO2002031349A1 (fr) * 2000-10-11 2002-04-18 Siemens Vdo Automotive Corporation Ensemble compensateur muni d'une soupape sensible a la pression destine a etre accouple a un actionneur a solide situe dans un injecteur de carburant

Also Published As

Publication number Publication date
DE10345203A1 (de) 2005-05-04
DE502004000909D1 (de) 2006-08-17
EP1519037A1 (fr) 2005-03-30

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