EP1382838B1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP1382838B1
EP1382838B1 EP03012488.7A EP03012488A EP1382838B1 EP 1382838 B1 EP1382838 B1 EP 1382838B1 EP 03012488 A EP03012488 A EP 03012488A EP 1382838 B1 EP1382838 B1 EP 1382838B1
Authority
EP
European Patent Office
Prior art keywords
actuator
piston
fuel injection
injection valve
actuator piston
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
EP03012488.7A
Other languages
German (de)
English (en)
Other versions
EP1382838A2 (fr
EP1382838A3 (fr
Inventor
Walter Maeurer
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 EP1382838A2 publication Critical patent/EP1382838A2/fr
Publication of EP1382838A3 publication Critical patent/EP1382838A3/fr
Application granted granted Critical
Publication of EP1382838B1 publication Critical patent/EP1382838B1/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.
  • This device has a piezoelectric, magnetostrictive or electostrictive actuator and a pressure piston operatively connected to this actuator which acts on a reciprocating piston via a hydraulic fluid.
  • the reciprocating piston actuates the valve closing body located in its extension. Due to the size ratio of the surfaces of the reciprocating piston and the pressure piston, which face a first chamber, which is filled with hydraulic fluid, a stroke ratio is given.
  • the hydraulic fluid directly in contact with the pressure piston is sealed against the actuator by means of an O-ring seal.
  • a defined guide gap with which the reciprocating piston is guided in a guide, allows the exchange of hydraulic fluid between the first chamber and a lying in a second chamber by a membrane space between the ejection and Reciprocating piston is located, wherein the membrane can be acted upon by a pressure in the second chamber.
  • An embodiment will be described in which the exchange between the first and second chamber takes place.
  • the gap and a pressure located in the second chamber is dimensioned so that slow, due to thermal influence length changes of the actuator can be compensated by exchange of hydraulic fluid through the guide gap.
  • a disadvantage of the fuel injection valve known from the above publication is in particular that special measures or components for the suppression of undesirable vibrations of parts of the fuel injection valve, which are caused in particular by the behavior of the actuator, completely missing and insufficiently suppressed by the existing components or be compensated.
  • a stable behavior of the fuel injection valve by the use or the utilization of frictional forces between the components of the fuel injection valve and by forces of spring elements is achieved insufficiently. Since said forces are relatively constant over a wide range, this means that in a suppression of unwanted vibrations, the valve dynamics suffers to the same extent.
  • the use of spring forces or sliding friction forces are unsuitable for the suppression of high-frequency vibrations.
  • the fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that mechanical vibrations in the fuel injector, in particular unwanted mechanical vibrations of the actuator and caused by him unwanted vibrations in moving parts of the fuel injection valve according to the invention, are effectively attenuated in a simple and cost-effective manner without significantly affecting the valve dynamics or significantly stressing components.
  • the edge times of the Aktorerregung and the plateau times can be shortened without the vibrations generated in particular by the actuator have a negative effect on the operation of the fuel injection valve or the valve dynamics is significantly adversely affected.
  • the throttle point is formed by a gap which is formed in cooperation with a first guide body either of a thickened or tapered part of the stage of the actuator piston.
  • a first guide body either of a thickened or tapered part of the stage of the actuator piston.
  • the fuel injection valve according to the invention can be configured so that by at least one of the guide gaps of actuator piston and reciprocating pressure medium to the working space zufle relatively slowly or can escape from it.
  • a stroke ratio realized by the size ratio of the surfaces of the two pistons, which face the working space, a stroke ratio.
  • the normally relatively small stroke which is possible by means of piezoelectric, magnetostrictive or electrostrictive actuators can be increased without making the actuator costly long and thin.
  • Thick, short actuators are more resilient to mechanical influences than thin, long actuators.
  • the Realization of the Hubüber GmbH by two pressure piston with different sized force-transmitting surfaces that transmit forces via a hydraulic medium, but otherwise, has the advantage over solutions in which membrane and channels are interposed, that the compressibility of the medium has less effect.
  • the thus realized, hubüber mecanicde power transmission is less prone to vibrations. There is less time between actuator and valve actuation. The system behaves stiffer.
  • the fuel injection valve according to the invention can also be characterized in that the force of a spring element is at least as large that actuator piston, connecting element and actuator are kept in constant contact.
  • the respective components are prevented from losing contact with each other and colliding with each other. It can be dispensed with costly and wear-prone joints.
  • FIG. 1 illustrated first embodiment of a fuel injection valve 1 according to the invention is carried out in the form of a fuel injection valve 1 for fuel injection systems of mixture-compression, spark-ignition internal combustion engines.
  • the fuel injection valve 1 is suitable in particular for the direct injection of fuel into a combustion chamber, not shown, of an internal combustion engine.
  • the fuel injection valve 1 has a housing cover 2 which sits hermetically sealed on the spray-off end of a valve housing 5. Via a fuel terminal 3 on the housing cover 2, a fuel channel 6 can be acted upon with fuel.
  • the fuel channel 6 extends only within the housing cover 2 and then within the valve housing 5, wherein in the spray-off, upper part of the fuel injection valve 1, an actuator housing 7, a seal 12, a neck ring 10 of an actuator piston 9, the spray-off part of the actuator piston 9 and a first Spring element 11 in the fuel passage 6 are surrounded by fuel.
  • the actuator housing 7 is hermetically connected to the housing cover 2 with its end remote from the sprayer.
  • An actuator 4 located in the actuator housing 7 is associated with its spray-off remote side of the housing cover 2 and is based on this.
  • a connecting element 8 is associated with its plate-shaped abspritzfernen end of the discharge side of the actuator 4 and engages with its discharge side tapered diameter profile through an opening 18 of the actuator housing 7.
  • a seal 12 which is corrugated pipe-shaped in this embodiment of the fuel injection valve 1 according to the invention, represents by their hermetic attachment of their two ends on the one hand on injection side as an attachment ring 13 formed part of the connecting element 8 and the other on the discharge end of the actuator housing 7, sure that the fuel under pressure can not penetrate into the actuator housing 7 and the connecting element The movements of the actuator 4 and the movements of the actuator piston 9 can follow unhindered.
  • the actuator piston 9 has a step 31, which is formed by its spray-off tapered diameter profile.
  • the thicker, spray-side profile of the actuator piston 9 is guided in a first guide body 14 with a first guide gap 28.
  • the abspritzferne, tapered diameter profile of the actuator piston 9 forms with the first guide body 14 has a gap which forms the throttle body 30, wherein the guide body 14 follows the tapered diameter profile of the actuator piston 9 at this point, that has a reduced inner diameter.
  • the thus formed damping chamber 27 serves to dampen unwanted vibrations of parts of the fuel injection valve, in particular for damping Aktorschwingieux in both directions of movement of the actuator 4 during operation of the fuel injection valve 1.
  • the damping properties are in particular by the geometric dimensions of the throttle body 30 forming gap and the damping chamber 27 determined.
  • the perpendicular in Abspritzraum distance between the tapered diameter profile of the actuator piston 9 and the reduced inner diameter of the guide body 14 at this point is usually greater than the corresponding distance, which is formed by the first guide gap 28.
  • the actuator piston 9 is formed by the first spring element 11, which is formed in this embodiment as a spiral spring and at a distance to the spray-off tapered diameter profile of the actuator piston. 9 attached first approach ring 10 engages, biased against the Abspritznahe side of the connecting element 8 and against the actuator 4, wherein the first spring element 11 abspritz food against the first guide body 14 is supported.
  • a second guide body 16 is hermetically connected to the discharge side of the first guide body 14, wherein a reciprocating piston 15 is guided with a second guide gap 29 in the second guide body 16.
  • a working space 26 which is bounded by the first guide body 14 and the second guide body 16, wherein the two guide gaps 28, 29 each open into the working space 26 with one end.
  • the second end of the first guide gap 28 opens into the damping chamber 27, the second end of the second guide gap opens at the discharge end of the second guide body 16 in the fuel channel.
  • the fuel channel 6 extends in the lower discharge-side part of the fuel injection valve 1 first between the housing 5 and the two guide bodies 14, 16. Then, the fuel in the fuel passage 6 passes and flows around the part of the lifting piston 15 protruding from the guide body 16, one in the course of the lifting piston 15 formed third approach ring 19, a between the third approach ring and the discharge end of the second guide body 16 bordered second spring element 17, an associated with the reciprocating piston 15 in operative connection valve needle 20 with a fourth neck ring 25, a between the fourth neck ring 25 and a shoulder 32 bordered third spring element 24.
  • the fuel enters when the fuel injection valve 1 is open from a spray orifice 23 between a valve seat body 21 and a valve closing body 22 arranged at the discharge end of the valve needle 20.
  • the second spring element 17 biases the reciprocating piston 15 against the discharge side associated Valve needle 20 before.
  • the third spring element 24 is supported on the shoulder 32 and biases the valve needle 20 via the frictionally connected with her fourth approach ring 25 against the sprayer remote associated reciprocating piston 15, wherein the third spring element is supported on the shoulder 32.
  • the force of the third spring element 24 keeps the sealing seat formed by valve closing body 22 and valve seat body 21 closed against the fuel pressure.
  • the gap represented by the throttle body 30 may also be used for guiding tasks.
  • Fig. 2 shows in much of the in Fig. 1 illustrated first embodiment similar second embodiment.
  • the actuator piston 9 is cup-shaped and has in its diameter profile, the step 31, whereby the diameter profile is increased counter to the direction of discharge.
  • the connecting element 8 extends through to the bottom of the cup-shaped actuator piston 9, wherein the actuator piston 9 and the bottom of the actuator piston 9 are biased by the spring element 11 against the connecting element 8.
  • the spring element 11 is designed in this embodiment as a tubular spring and secured to the inner side of the housing cover 2 and the spray-away end of the cup-shaped actuator piston 9 frictionally.
  • FIG. 3 showing a schematically illustrated partial section of the first embodiment in the region of the stage 31 and the damping chamber 27, and the following relationships and derivatives of the proportional relationship between damping force and Aktorkolbenising is shown.
  • C is a constant which depends on the geometric dimensions of the annular gap and ⁇ p represents the pressure difference.
  • the invention is not limited to the illustrated embodiments and may, for. B. also be used for inward-opening fuel injectors.

Landscapes

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

Claims (7)

  1. Soupape d'injection de carburant (1), en particulier pour l'injection directe de carburant dans une chambre de combustion d'un moteur à combustion interne, comprenant
    un actionneur (4) piézoélectrique, électrostrictif ou magnétostrictif,
    un piston d'actionneur (9) en liaison fonctionnelle avec l'actionneur (4), qui est guidé par une première fente de guidage (28),
    un piston alternatif (15) en liaison fonctionnelle avec le piston d'actionneur (9) par le biais d'un fluide sous pression, lequel est guidé par une deuxième fente de guidage (29),
    un pointeau de soupape (20) en liaison fonctionnelle avec le piston alternatif (15) qui présente au niveau de son extrémité du côté de l'injection un corps de fermeture de soupape (22) qui forme avec un corps de siège de soupape (21) un siège d'étanchéité,
    le transfert de force entre le piston d'actionneur (9) et le piston alternatif (15) s'effectuant par un espace de travail (26) rempli de fluide sous pression, délimité par le piston d'actionneur (9) et le piston alternatif (15),
    le piston d'actionneur (9) présentant au moins un étage (31) qui est adjacent à une chambre d'amortissement (27), la chambre d'amortissement (27) étant séparée physiquement de l'espace de travail (26) et étant configurée ou disposée de telle sorte que le fluide sous pression puisse affluer ou s'échapper par le biais d'une zone d'étranglement (30),
    caractérisée en ce que
    la zone d'étranglement (30) est formée par une fente qui est formée par une partie rétrécie ou une partie épaissie de l'étage (31) du piston d'actionneur (9) et par un corps de guidage (14) et le corps de guidage (14) suit l'allure de diamètre rétrécie du piston d'actionneur (9) de telle sorte qu'il se produise une force d'amortissement opposée au mouvement du piston d'actionneur (9) F = A2 / C * v proportionnelle à la vitesse (v) du piston d'actionneur (9) dans les deux sens de déplacement de l'actionneur (4), A étant la surface annulaire du piston d'actionneur (9) au niveau de la chambre d'amortissement (27) et C désignant une constante dépendant des dimensions géométriques.
  2. Soupape d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    le corps de guidage (14) se compose de plusieurs parties.
  3. Soupape d'injection de carburant selon la revendication 1 ou 2,
    caractérisée en ce que
    la zone d'étranglement (30) est formée par une ouverture, en particulier un alésage ou un alésage au laser qui présente un effet d'étranglement de l'écoulement.
  4. Soupape d'injection de carburant selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    le carburant sert de fluide sous pression.
  5. Soupape d'injection de carburant selon la revendication 4,
    caractérisée en ce que
    du carburant est échangé directement par le biais de la zone d'étranglement (30) avec un canal de carburant (6).
  6. Soupape d'injection de carburant selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    pour compenser les variations de longueur de l'actionneur (4) dues à la température, un fluide sous pression s'écoule hors de l'espace de travail (26) ou afflue dans l'espace de travail (26) par au moins l'une des fentes de guidage (28, 29).
  7. Soupape d'injection de carburant selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un rapport de démultiplication est donné par le rapport des surfaces du piston d'actionneur (9) et du piston alternatif (15) qui sont tournées vers l'espace de travail (26).
EP03012488.7A 2002-07-16 2003-06-02 Injecteur de carburant Expired - Lifetime EP1382838B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2002132193 DE10232193A1 (de) 2002-07-16 2002-07-16 Brennstoffeinspritzventil
DE10232193 2002-07-16

Publications (3)

Publication Number Publication Date
EP1382838A2 EP1382838A2 (fr) 2004-01-21
EP1382838A3 EP1382838A3 (fr) 2004-04-21
EP1382838B1 true EP1382838B1 (fr) 2017-08-16

Family

ID=29761999

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03012488.7A Expired - Lifetime EP1382838B1 (fr) 2002-07-16 2003-06-02 Injecteur de carburant

Country Status (3)

Country Link
EP (1) EP1382838B1 (fr)
JP (1) JP2004052767A (fr)
DE (1) DE10232193A1 (fr)

Families Citing this family (12)

* 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
DE102004002299A1 (de) * 2004-01-16 2005-08-04 Robert Bosch Gmbh Kraftstoffinjektor mit direkt angesteuertem Einspritzventilglied
DE102004024119B4 (de) 2004-05-14 2006-04-20 Siemens Ag Düsenbaugruppe und Einspritzventil
DE102004031790A1 (de) 2004-07-01 2006-01-26 Robert Bosch Gmbh Common-Rail-Injektor
DE102005009148A1 (de) * 2005-03-01 2006-09-07 Robert Bosch Gmbh Kraftstoffinjektor mit direktgesteuertem Einspritzventilglied mit Doppelsitz
FR2889257B1 (fr) * 2005-08-01 2007-11-02 Renault Sas Dispositif d'injection de carburant et procede de commande d'un tel dispositif
DE102006019308A1 (de) * 2006-04-26 2007-10-31 Robert Bosch Gmbh Injektor
ATE552420T1 (de) 2009-07-29 2012-04-15 Delphi Tech Holding Sarl Kraftstoffeinspritzdüse
US9897058B2 (en) 2009-07-29 2018-02-20 Delphi International Operations S.A.R.L. Fuel injector
CN102213165B (zh) * 2010-04-08 2013-02-13 北京亚新科天纬油泵油嘴股份有限公司 高压共轨电控喷油器
JP5462143B2 (ja) * 2010-12-09 2014-04-02 株式会社日本自動車部品総合研究所 燃料噴射弁
JP5839228B2 (ja) * 2011-11-21 2016-01-06 株式会社デンソー 燃料噴射弁

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3332808A1 (de) * 1983-09-12 1985-03-28 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE4306072C2 (de) 1993-02-26 1994-12-08 Siemens Ag Vorrichtung zum Öffnen und Verschließen einer in einem Gehäuse vorhandenen Durchtrittsöffnung
JP3736578B2 (ja) * 1996-01-19 2006-01-18 株式会社デンソー 燃料噴射ノズル
DE19642441A1 (de) * 1996-10-15 1998-04-16 Bosch Gmbh Robert Verfahren zum Betätigen eines Kraftstoffeinspritzventils für Brennkraftmaschinen
GB2339451A (en) * 1998-07-10 2000-01-26 Lucas Ind Plc A fuel injector with control chamber and a damped needle valve
DE19946828C1 (de) * 1999-09-30 2001-07-12 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
GB9925803D0 (en) * 1999-11-02 1999-12-29 Lucas Industries Ltd Damping device
DE19962177A1 (de) * 1999-12-22 2001-07-12 Siemens Ag Hydraulische Vorrichtung zum Übertragen einer Aktorbewegung
DE10121891A1 (de) * 2001-05-05 2002-11-07 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10155229B4 (de) * 2001-11-09 2004-07-15 Robert Bosch Gmbh Ventil zum Steuern von Flüssigkeiten

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP1382838A2 (fr) 2004-01-21
DE10232193A1 (de) 2004-02-05
JP2004052767A (ja) 2004-02-19
EP1382838A3 (fr) 2004-04-21

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