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EP1519034B1 - Soupape d'injection de carburant - Google Patents

Soupape d'injection de carburant Download PDF

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Publication number
EP1519034B1
EP1519034B1 EP20040104460 EP04104460A EP1519034B1 EP 1519034 B1 EP1519034 B1 EP 1519034B1 EP 20040104460 EP20040104460 EP 20040104460 EP 04104460 A EP04104460 A EP 04104460A EP 1519034 B1 EP1519034 B1 EP 1519034B1
Authority
EP
European Patent Office
Prior art keywords
coupler
fuel injection
injection valve
sections
housing
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
EP20040104460
Other languages
German (de)
English (en)
Other versions
EP1519034A1 (fr
Inventor
Fevzi Yildirim
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 EP1519034A1 publication Critical patent/EP1519034A1/fr
Application granted granted Critical
Publication of EP1519034B1 publication Critical patent/EP1519034B1/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
    • F02M61/04—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
    • 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
    • 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

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.
  • a coupler in the form of an adaptive, mechanical tolerance compensation with stroke ratio for the stroke of a piezoelectric actuator is known, for example, from EP 0 447 400 A1.
  • the coupler described here has two mutually axially movable sections which form an annular gap and a hydraulic volume.
  • the annular gap connects the hydraulic volume with a compensation chamber.
  • the hydraulic medium between the hydraulic volume and the Exchanged compensation space the annular gap serves as a throttle point. Due to the different sized surfaces of the sections in the hydraulic volume is given a stroke ratio.
  • a disadvantage of the above-mentioned prior art is, in particular, that as a result of prolonged injection phases or Aktorerregonne, which are necessary, for example, at a start of the associated internal combustion engine from hot and cold state, come to oversized loss of hydraulic fluid from the hydraulic volume can. The consequence of this is that the valve closing body prematurely closes the sealing seat and the required amount of fuel can not be discharged into the combustion chamber.
  • WO 03/081020 A describes a fuel injection valve which comprises a piezoelectric or magnetostrictive actuator which actuates a valve closing body formed on a valve needle via a hydraulic coupler and which cooperates with a valve seat surface to form a sealing seat.
  • the hydraulic coupler has a Geberkoben and a slave piston.
  • a coupler gap formed between the master piston and the slave piston is dimensioned so that it opens in the cold state of the fuel injection valve by a temperature-induced change in length of the actuator.
  • WO 03/064848 A describes a fuel injection valve for direct injection of fuel into the combustion chamber of an internal combustion engine with a piezoelectric or magnetotrictive actuator, which operates via a hydraulic coupler arranged on a valve needle valve closing body, which cooperates with a valve seat surface to a sealing seat.
  • the coupler has a guide cylinder, in which a master piston and a slave piston are guided, wherein between the master piston and the slave piston, a coupler gap is formed.
  • a first spring exerts a biasing force on the slave piston.
  • EP 1 079 158 A describes a metering device for a valve with a variable length in the axial direction electro-mechanical actuator which is mounted within a tikbehellbaren working chamber of the housing, and which is connected at one end with an axially displaceable hydraulic piston and with a hydraulic chamber through a first fit between the hydraulic piston and the housing is throttled hydraulically connected to the working chamber.
  • the first fit is designed so that is fixed relative to the housing at a rapid change in length of the actuator, the hydraulic piston.
  • the fuel injector according to the invention with the features of the main claim has the advantage that even with significantly extended injection phases or Aktorerregened the valve closing body can follow the actuator movements in the stroke direction exactly, the flow rate in each operating state of the fuel injector is precisely controlled.
  • the fuel is used as hydraulic medium.
  • the fuel injector This makes it easier to set up and the hydraulic volume can be applied directly to the fuel pressure without the need for complex and pressure-reducing seals.
  • first coupler area of the first coupler section is larger than the second coupler area of the second section.
  • the two coupler sections are piston-shaped and engage from opposite sides in each case at least partially into a coupler housing.
  • the coupler sections are guided in the coupler housing with a first annular gap and a second annular gap, wherein these each form throttle points for the hydraulic medium.
  • the opposing faces of the coupler sections in the coupler housing form the two coupler surfaces over which the hydraulic medium acts axially on the coupler sections.
  • the fuel injection valve can be particularly easy to build.
  • the coupler can be constructed in a particularly simple manner.
  • coupler sections in part, in particular in axial sections, made of a material, in particular aluminum, that under hydraulic pressure deformed more than the material from which the housing and / or the coupler housing consists.
  • the gap is also advantageous to set the gap to 0 to 3 micrometers with a fuel pressure of 0.3 to 0.7 MPa acting axially on the coupler sections or coupler surfaces, with the coupler surfaces at a gap of 0 micrometers only touch almost without pressure.
  • the housing on compensation elements the temperature-related changes in the size of the gap compensate.
  • the size of the gap is thereby independent of temperature fluctuations of the fuel injection valve.
  • the gap is advantageous to dimension the gap at a fuel pressure of 10 MPa or higher to at least 100 micrometers, more preferably at a fuel pressure of 60 Mpa or higher to at least 25 micrometers.
  • the function of the coupler is ensured in this way at higher fuel pressures.
  • 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.
  • a valve needle 8 In a hollow cylindrical housing 5, which tapers stepwise downwards in the direction of discharge, a valve needle 8, an actuator 2 and a hydraulic coupler 3 are arranged coaxially to one another.
  • the housing 5 On the inflow side, the housing 5 is hermetically sealed by a housing cover 4.
  • On the housing cover 4 On the housing cover 4 is supported on the inside of the actuator 2 with its inflow end.
  • the actuator 2 On the outflow side, the actuator 2 has a disk-shaped actuator head 10.
  • the actuator head 10 is axially movably guided in a hollow cylindrical actuator housing 9.
  • the actuator housing 9 has at the downstream end an inwardly facing third flange 16 and is hermetically attached to the housing cover 4 on the inflow side.
  • a third spring element 22 is clamped between the actuator head 10 and the third flange 22 with a bias and holds the actuator head 10 in constant contact with the actuator. 2
  • the hydraulic coupler 3 is disposed between the actuator 2 and the valve needle 8, wherein in a coupler housing 25, a first coupler section 23 on the inflow side and a second coupler section 24 downstream partially engage.
  • the first coupler section 23 has on the inflow side a rod-shaped, consisting of aluminum intermediate piece 34 and downstream a cup-shaped end piece 35.
  • the intermediate piece 34 engages the outflow side to the bottom of the cup-shaped end piece, where it is firmly bonded, for example, and engages on the inflow side partially into the actuator housing 9, where it is firmly connected to the actuator head 10.
  • the flexible portion 26 is hermetically sealed with one end in the region of the downstream end of the actuator housing 9 and the other end on the intermediate piece 34.
  • the second coupler section 24 is piston-shaped.
  • the first coupler section 23 has a first coupler face 28 and the second coupler section 24 has a second coupler face 29, the coupler faces 28, 29 being disposed on the opposite end faces of the coupler sections 23, 24 are.
  • the first is also Coupler face 28 larger than the second coupler face 29.
  • the two coupler sections 23, 24 are spaced by a gap 27.
  • the size of the gap 27 is variable by the axial displaceability of the coupler sections between 0 and for example 50 microns.
  • a hydraulic volume 17 is arranged, which is bounded by the coupler housing 25 and the two coupler sections 23, 24, wherein in this embodiment, the hydraulic volume 17 via a through a first annular gap 32nd produced first throttle body 30 and is connected via a generated by a second annular gap 33 second throttle body 31 with the fuel-filled interior of the housing 5 in connection.
  • a second flange 15 is arranged in the region of the downstream end of the second coupler section 24 in the region of the downstream end of the second coupler section 24 .
  • a second spring element 21 is clamped between the second flange 15 and the edge of the coupler housing 25 which is thickened downstream and biases the second coupler section 24 slightly in the direction of discharge. Downstream of the second coupler section 24, the valve needle 8 is arranged.
  • the valve needle 8 On the discharge side, the valve needle 8 has a valve closing body 7 and engages through a valve seat body 6 arranged at the discharge end of the housing 5.
  • the valve seat body 6 has a centrally disposed injection opening 12 and a valve seat surface 13 which cooperates with the valve closing body 7 to form a sealing seat.
  • the valve needle 8 On the inflow side, the valve needle 8 has a first flange 14. Between the first flange 14 and the valve seat body 6, a first spring element 20 is clamped, which pulls the valve closing body 7 in the sealing seat and as the second spring element 21 and the third spring element 22 is formed spirally.
  • the fuel injection valve 1 opens to the outside.
  • compensation elements 36 which consist for example of Invar steel, compensate for the temperature-induced changes in length, which could affect the size of the gap, so that the size of the gap 27 is just before a start of the engine from hot and cold state at 0 microns.
  • the fuel pressure is usually 0.5 MPa, since a mechanical drive of a pump by the internal combustion engine is not possible. Instead, the fuel pressure is usually generated by an electrically driven pump, which, without having to operate much effort, only about 0.3 to 0.7 MPa applies.
  • both hot and cold internal combustion engine usually a multiple of the full load fuel quantity is injected. This is achieved by extended valve opening times or longer Aktorerregonne.
  • Aktorerregonne In conventional fuel injection valves, especially in hot start phases, escapes from the hydraulic coupler in these starting phases so much hydraulic medium that the valve closing body 7 can not be sufficiently actuated by the actuator 2. The seal seat closes too early and the required amount of fuel can not be injected.
  • the valve needle 8 and the valve closing body 7 is operated directly in start phases, without interposition of a hydraulic cushion.
  • the size of the gap 27 is ideally between 25 and 100 microns.
  • the increased fuel pressure which acts axially in opposite directions on the two coupler sections 23, 24 via the two coupler surfaces 28, 29, causes a compression in the axial direction of the example made of aluminum intermediate piece 34, whereby during operation of the coupler. 3 the functions, Hubüber GmbH and / or compensation of temperature-induced changes in length of the actuator 2, can take over.
  • the actuator 2 If the actuator 2 is energized after the starting phase via an electrical line, not shown, it expands quickly. Since the hydraulic medium can not flow off quickly enough through the throttle points 30, 31 from the hydraulic volume 17, the coupler 3 behaves very stiff, 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 20 in the discharge direction. As a result, the sealing seat opens and the pressure-fed fuel 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 17 and the fuel-filled interior of the housing 5.
  • 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 (10)

  1. Injecteur de carburant (1), en particulier pour l'injection directe de carburant dans une chambre de combustion d'un moteur à combustion interne, comprenant un boîtier (5), un actionneur (2) piézoélectrique, électrostrictif ou magnétostrictif, un obturateur de fermeture de soupape (7) en liaison active avec l'actionneur (2) et coopérant 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) avec une première surface de coupleur (28) et un deuxième segment de coupleur (24) avec une deuxième surface de coupleur (29), les deux segments de coupleur (23, 24) étant mobiles l'un par rapport à l'autre et coopérant l'un avec l'autre dans un volume hydraulique (17), le volume hydraulique (17) étant rempli par un fluide hydraulique introduit ou extrait par au moins un point d'étranglement (30, 31) et sollicité par la pression du carburant, alors qu'on intervalle (27) entre les segments de coupleur (23, 24) permet au fluide hydraulique d'agir axialement respectivement sur les surfaces de coupleur (28, 29) ou les segments de coupleur (23, 24), la pression du carburant agissant sur au moins l'un des segments de coupleur (23, 24) pour le raccourcir axialement, l'intervalle (27) s'agrandissant avec la pression croissante du carburant,
    caractérisé en ce qu'
    au moins l'un des segments de coupleur (23, 24) est au moins partiellement en un matériau qui sous la pression hydraulique se déforme plus fortement que le matériau du boîtier (5) et/ou du boîtier de coupleur (25).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    le fluide hydraulique est le carburant.
  3. Injecteur de carburant selon la revendication 1 ou 2,
    caractérisé en ce
    que la première surface de coupleur (28) est plus grande que la deuxième surface de coupleur (29).
  4. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    les deux segments de coupleur (23, 24), dans la zone de leurs extrémités engagées au moins partiellement par des côtés opposés dans un boîtier de coupleur (25), présentent chacun la forme d'un piston et sont engagés dans le boîtier de coupleur (25), de sorte que le premier segment de coupleur (23) est guidé dans une première fente annulaire (32), qui forme un point d'étranglement (30), et le deuxième segment de coupleur (24) dans une fente annulaire (33), qui forme un deuxième point d'étranglement (31).
  5. Injecteur de carburant selon la revendication 4,
    caractérisé en ce que
    les deux surfaces de coupleur (28, 29) des segments de coupleur (23, 24) sont formées par les surfaces frontales des segments de coupleur (23, 24) tournées l'une vers l'autre dans le boîtier de coupleur (25).
  6. Injecteur de carburant selon la revendication 4 ou 5,
    caractérisé en ce que
    le volume hydraulique (17) est délimité par le boîtier de coupleur (25) et les deux segments de coupleur (23, 24).
  7. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'
    au moins l'un des segments de coupleur (23, 24) est au moins partiellement en aluminium.
  8. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    une pression de carburant de 0,3 à 0,7 MPa agissant sur les segments de coupleur (23, 24) ou les surfaces de coupleur (28, 29) forme un intervalle (27) de 0 à 3 micromètres, alors qu'en présence d'un intervalle (25) de 0 micromètre les surfaces de coupleur (28, 29) se touchent pratiquement sans pression.
  9. Injecteur de carburant selon la revendication 8,
    caractérisé en ce que
    le boîtier (5) présente des éléments de compensation (36) qui compensent des variations dues à la température de la grandeur de la fente (27).
  10. Injecteur de carburant selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'
    une pression de carburant de 10 MPa ou plus agissant axialement sur les segments de coupleur (23, 24) ou les surfaces de coupleur (28, 29) forme un intervalle (27) d'environ 25 micromètres.
EP20040104460 2003-09-17 2004-09-15 Soupape d'injection de carburant Expired - Lifetime EP1519034B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10343086 2003-09-17
DE2003143086 DE10343086A1 (de) 2003-09-17 2003-09-17 Brenntoffeinspritzventil

Publications (2)

Publication Number Publication Date
EP1519034A1 EP1519034A1 (fr) 2005-03-30
EP1519034B1 true EP1519034B1 (fr) 2006-12-27

Family

ID=34177802

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20040104460 Expired - Lifetime EP1519034B1 (fr) 2003-09-17 2004-09-15 Soupape d'injection de carburant

Country Status (2)

Country Link
EP (1) EP1519034B1 (fr)
DE (2) DE10343086A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004002309A1 (de) * 2004-01-16 2005-08-04 Robert Bosch Gmbh Kraftstoffinjektor mit direkter Nadelstreuerung
DE102007002402B4 (de) * 2006-12-13 2014-12-31 Siemens Aktiengesellschaft Gaseinblasvorrichtung für einen Verbrennungsmotor
US10006429B2 (en) 2016-03-31 2018-06-26 GM Global Technology Operations LLC Variable-area poppet nozzle actuator

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0477400B1 (fr) * 1990-09-25 2000-04-26 Siemens Aktiengesellschaft Dispositif compensateur de tolérance dans la direction de mouvement du transformateur de déplacement d'un dispositif d'actionnement piézoélectrique
DE19839125C1 (de) * 1998-08-27 2000-04-20 Siemens Ag Vorrichtung und Verfahren zur Dosierung von Fluid
DE19940056A1 (de) * 1999-08-24 2001-03-22 Siemens Ag Dosiervorrichtung und Verfahren zur Dosierung
DE10203659A1 (de) * 2002-01-30 2003-07-31 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10203655A1 (de) * 2002-01-30 2004-01-22 Robert Bosch Gmbh Brennstoffeinspritzventil
DE10213858A1 (de) * 2002-03-27 2003-10-30 Bosch Gmbh Robert Brennstoffeinspritzventil

Also Published As

Publication number Publication date
DE10343086A1 (de) 2005-05-19
DE502004002424D1 (de) 2007-02-08
EP1519034A1 (fr) 2005-03-30

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