EP1771651B1 - Kraftstoffinjektor mit direkter mehrstufiger einspritzventilgliedansteuerung - Google Patents

Kraftstoffinjektor mit direkter mehrstufiger einspritzventilgliedansteuerung Download PDF

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Publication number
EP1771651B1
EP1771651B1 EP05749972A EP05749972A EP1771651B1 EP 1771651 B1 EP1771651 B1 EP 1771651B1 EP 05749972 A EP05749972 A EP 05749972A EP 05749972 A EP05749972 A EP 05749972A EP 1771651 B1 EP1771651 B1 EP 1771651B1
Authority
EP
European Patent Office
Prior art keywords
valve member
fuel injector
injection valve
booster piston
control chamber
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.)
Not-in-force
Application number
EP05749972A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1771651A1 (de
Inventor
Friedrich Boecking
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1771651A1 publication Critical patent/EP1771651A1/de
Application granted granted Critical
Publication of EP1771651B1 publication Critical patent/EP1771651B1/de
Not-in-force 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
    • 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
    • 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
    • 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
    • F02M2200/708—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with hydraulic chambers formed by a movable sleeve

Definitions

  • high-pressure accumulator injection systems Today, in addition to pump nozzle fuel injection systems, high-pressure accumulator injection systems (common rail) are used on modern self-igniting internal combustion engines.
  • the individual fuel injectors assigned to the cylinders of the internal combustion engine are supplied with fuel from a high-pressure accumulator (common rail).
  • the fuel injectors can be actuated either via solenoid valves or else via piezo actuators. If the fuel injectors are actuated via piezoactuators, an injection valve member which can be actuated directly via the piezoactuator can be realized.
  • the injection valve comprises a valve needle, which is tensioned by a spring located within a spring chamber against a seat surface.
  • the spring is sandwiched between a spring abutment which communicates with the valve needle and a movable stop.
  • the injector further includes a valve including a movable abutment surface, which valve may be actuated during operation of the injector such that fuel may exit the spring chamber at a second, higher rate.
  • the valve is formed by a seating surface formed around an opening communicating with the spring chamber, the movable fence being engageable with the seating so that fuel flow through the opening can be controlled.
  • the movable stop can be designed to be movable under the action of the fuel pressure within a pump chamber.
  • the actuator To be able to open the injection valve member in fuel injectors with direct controllability of the injection valve member via an actuator, the actuator must overcome a high opening force.
  • the high required opening force applied by the actuator is, finds its cause in that the nozzle needle formed injector member with system pressure (pressure level in the high-pressure reservoir common rail) is applied, is pressed into its seat.
  • the force required to open the injection valve member from its seat is on the order of several hundred N, such as about 400 N.
  • Said variables ie the force of several 100 N required to open the injection valve member and the maximum representable stroke of the injection valve member from its fully closed to its fully open position are essentially the determining parameters for the size of a piezoelectric actuator to be integrated into a fuel injector.
  • the length / diameter ratio of the piezoelectric actuator can be varied by integration of a hydraulic ratio, as in the example of FIG DE19500706 A1
  • the size of the actuator also referred to as Aktorvolumen, is substantially proportional to the applied opening force and the maximum stroke to be represented of the needle-shaped injection valve member.
  • the driver engages in a recess of a the piston, which is so dimensioned that the driver takes only from a certain sub-stroke an outer, slidably mounted on an inner booster piston booster piston
  • the gear ratio in the lower Operahub Scheme is by the diameter ratio d 1 to d 2 , ie the diameter ratio between the diameter of the Given the head portion of the injection valve member and the diameter of an internally arranged booster piston, while the effective in the upper Generalhub Scheme the injection valve member gear ratio by the diameter ratio d 1 to d 3 , ie the diameter of the head portion of the injection valve member and the outer diameter of a second booster piston is given over the already mentioned driver is coupled to the first booster piston
  • the single FIGURE shows a section through a fuel injector with a multi-stage controllable directly operated nozzle needle-shaped injection valve member.
  • the figure shows a fuel injector 1, which comprises an injector body 2, an intermediate disk 3 and a nozzle body 4.
  • the injector 2 and the nozzle body 4 are screwed together by means of a nozzle lock nut 5; Before screwing the injector body 2 and the nozzle body 4, the washer 3 is applied to the nozzle body 4, which has at least two flow channels 26 and 40, which will be described in more detail below.
  • the fuel injector 1 comprises a needle-shaped injection valve member 6 which can be configured in one or more parts and with which injection openings (not illustrated in the drawing) formed on the combustion chamber end of the fuel injector 1 can be closed or released.
  • the intermediate disk 3 between the injector body 2 and the nozzle body 4 comprises an upper end face 7 which assigns a lower end face of the injector body 2 and a lower end face 8 which assigns the upper end face of the nozzle body 4.
  • a cavity 9 is formed in the injector body 2 of the fuel injector 1, in which an actuator 39 is formed, for example, as one of a piezocrystal stack constructed piezoelectric actuator can be formed.
  • a fuel inlet 10 opens from a high-pressure accumulator (common rail), not shown in the drawing, in which fuel held at system pressure fuel is stored. Via the fuel inlet 10, this fuel, which is under system pressure (rail pressure), enters the cavity 9 and flows from it along a multistage pressure booster 12 accommodated in the fuel injector 1 to the channel 40 of the intermediate plate and from there into the nozzle body 4.
  • the multistage pressure booster 12 comprises a first booster piston 13 and a second booster piston 14 surrounding and guided on the first booster piston 13.
  • the first booster piston 13, formed in diameter d 2 comprises a groove 30 for a ring-shaped driver 20, which is inserted into a recess 19 of the first booster piston 13 enclosing the second booster piston 14 engages.
  • the recess 19 in the second booster piston 14 is bounded by a first stop side 21 and a second stop side 22.
  • the outer, second booster piston 14 has an end face 16 which is acted upon by a spring element 15 which can be embodied as a spiral spring, which is supported on a support disk 11 formed below the piezoactuator 39, which undergoes a vertical movement when the actuator 39 is energized.
  • the support disk 11 is supported by a tubular spring 17, which is supported with its opposite end of the support disk 11 on the upper plane surface 7 of the washer 3. By means of the tubular spring 17, the support disk 11 is set in its rest position when the energization of the piezocrystal stack of the actuator 39 is canceled.
  • the tubular spring 17 between the support plate 11 and the upper end surface 7 of the washer 3 surrounds a stop sleeve 18.
  • the stop sleeve 18 extends below a shoulder of the second booster piston 14 and surrounds a spring 28, a control chamber 25 defining a first control chamber sleeve 27 to the upper Plane 7 of the washer 3 of the fuel injector 1 hires.
  • the spring 28 is permanently tensioned due to the pressure prevailing in the cavity 9 fuel pressure, so that it is ensured that the first control chamber sleeve 27 is always employed with its formed on the underside biting edge 29 against the upper end surface 7 of the washer 3, so that the control chamber 25 is sealed is.
  • control chamber 25 is acted on the one hand by the upper end face 7 of the intermediate disc 3 and on the other hand both from the end face 23 of the first booster piston 13 and from the end face 24 of the second booster piston 14.
  • the needle-shaped injection valve member 6 arranged below the intermediate disk 3 has a head 31 which is formed in a diameter d 1 .
  • the second booster piston 14 has an outer diameter d 3 , which exceeds both the diameter d 2 of the first booster piston 13 and the head diameter d 1 of the needle-shaped injection valve member 6.
  • the hydraulic space between the lower face 8 of the washer 3 and the upper end of the needle-shaped injection valve member 6 is limited by a second control sleeve 32
  • the second control chamber sleeve 32 is in turn acted upon by a spring 33, which is supported on a support ring 34, for example the designedsff kaue a needle-shaped injection valve member 6 may be shrunk, that is connected by means of a press fit with the lateral surface of the needle-shaped injection valve member 6.
  • the free surfaces 36 can be oriented by 120 °, in the case of the formation of three flow relief surfaces 36 or at an angle of 90 °, in the case of the formation of four flow relief surfaces 36 on the needle-shaped injection valve member 6.
  • the piezocrystal stack of the actuator 39 and pulls together Elongation in the vertical direction decreases. Due to the pre-tensioned tube spring 17, the support plate 11 moves in the vertical direction according to the Reduction of the elongation of the piezocrystal stack of the actuator 39 upwards, so that the first booster piston 13 extends with its the control chamber 25 facing end face 23 from the control chamber 25, whereby there the pressure decreases. Due to the pressure drop in the control chamber 25 and its hydraulic connection to the hydraulic space above the head 31 of the needle-shaped injection valve member 6 also moves the needle-shaped injection valve member 6 upwards and the injection ports are released.
  • the multi-stage pressure intensifier 12 works with a transmission ratio of 1: 1-1.5.
  • the transmission ratio within the sketched sectionhub Symposiumes is defined by the diameter d 1 / d 2 , wherein d 1 denotes the diameter of the head 31 of the needle-shaped injection valve member 6 and d 2 denotes the outer diameter of the first booster piston 13 of the multistage pressure booster 12. Due to the effective in this Sectionhub Scheme gear ratio of 1: 1-1.5 can be done quickly, precisely and stably opening the injection ports formed at the combustion chamber end of the fuel injector 1.
  • the multistage pressure intensifier now operates with a second transmission ratio of 1: 4 -7, which is defined by the diameter ratio of d 1 / d 3 .
  • d 1 is - as already mentioned above - the head diameter of the head 31 of the needle-shaped injection valve member 6 denotes, while d 3 denotes the outer diameter of the first booster piston 13 displaceably movable second booster piston 14. Due to the exceeding of the stroke h 1 together from the control chamber 25 extending end faces 23 and 24, the pressure in the control chamber 25 decreases faster compared to the state in which only the end face 23 of the first booster piston 13 extends out of the control chamber 25. Due to this, a complete actuator needle opening can achieve complete opening of the needle-shaped injection valve member 6 by moving a larger hydraulic surface (23 +24), which is important in the full load range of the internal combustion engine.
  • the crystal stack of the piezoelectric actuator 39 is energized again, then an elongation of this crystal stack corresponding to the energization level of the piezocrystal stack sets in, whereby the support disk 11 is compressed against the action of the tubular spring 17, which is supported on the upper planar surface 7 of the intermediate disk 3.
  • the tube spring 17 surrounds the stop sleeve 18, which in turn engages with its upper edge a paragraph on the outer circumference of the second booster piston 14 and define its basic position.
  • the inner, first booster piston 13 is moved with its end face 23 into the control chamber 25 and, as soon as the underside of the driver 20 on the second stop side 22 of FIG Recess 19 abuts - and the second booster piston 14 moves to its normal position, which is defined by the stop sleeve 18, which is also supported on the upper end face 7 of the washer 3
  • the fuel flows via the channel 40 into the nozzle body 4 and enters via the provided at the periphery of the needle-shaped injection valve member 6 free surface 36 in an annular gap 37 which is defined between the outer periphery of the needle-shaped injection valve member 6 and the inside of the nozzle body
  • Fuel volume flowing in the flow direction 38 flows to the injection openings formed at the combustion chamber end of the fuel injector 1 and, via this, when the injection valve member 6 is open or only partially opened, enters the combustion chamber of the self-igniting internal combustion engine.
  • the proposed solution according to the invention is characterized in particular by the fact that in the first Generalhub Scheme of the needle-shaped injection valve member 6 opening the needle-shaped injection valve member with a high rigidity, effected by the small ratio of 1: 1-1.5, realized between Aktorhub and Einspritzvenhlglied can be. Accordingly, the following in the first Generalhub Scheme the injection valve member opening of the combustion chamber side arranged injection openings is controlled, ie occurring due to rapid opening of the needle-shaped injection valve member 6 occurring Volume jumps with regard to the amount of fuel introduced into the combustion chamber are avoided, so that the production of soot during combustion drops to a considerable extent.

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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)
  • Mechanically-Actuated Valves (AREA)
  • Float Valves (AREA)
EP05749972A 2004-07-21 2005-05-13 Kraftstoffinjektor mit direkter mehrstufiger einspritzventilgliedansteuerung Not-in-force EP1771651B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004035280A DE102004035280A1 (de) 2004-07-21 2004-07-21 Kraftstoffinjektor mit direkter mehrstufiger Einspritzventilgliedansteuerung
PCT/EP2005/052201 WO2006008200A1 (de) 2004-07-21 2005-05-13 Kraftstoffinjektor mit direkter mehrstufiger einspritzventilgliedansteuerung

Publications (2)

Publication Number Publication Date
EP1771651A1 EP1771651A1 (de) 2007-04-11
EP1771651B1 true EP1771651B1 (de) 2009-10-07

Family

ID=34969382

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05749972A Not-in-force EP1771651B1 (de) 2004-07-21 2005-05-13 Kraftstoffinjektor mit direkter mehrstufiger einspritzventilgliedansteuerung

Country Status (6)

Country Link
US (1) US20080093483A1 (ja)
EP (1) EP1771651B1 (ja)
JP (1) JP2008506888A (ja)
AT (1) ATE445096T1 (ja)
DE (2) DE102004035280A1 (ja)
WO (1) WO2006008200A1 (ja)

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005029976A1 (de) * 2005-06-28 2007-01-11 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102005040912A1 (de) * 2005-08-30 2007-03-08 Robert Bosch Gmbh Einspritzdüse
DE102007002758A1 (de) * 2006-04-04 2007-10-11 Robert Bosch Gmbh Kraftstoffinjektor
DE102006036781A1 (de) * 2006-08-07 2008-02-14 Robert Bosch Gmbh Injektor und zugehöriges Betriebsverfahren
DE102007002278A1 (de) * 2007-01-16 2008-07-17 Robert Bosch Gmbh Injektor zum Einspritzen von Kraftstoff
DE102007002282A1 (de) * 2007-01-16 2008-07-17 Robert Bosch Gmbh Kraftstoffinjektor mit Koppler
DE102007016866A1 (de) 2007-04-10 2008-10-16 Robert Bosch Gmbh Hochdichter Kraftstoffinjektor
JP4633766B2 (ja) * 2007-06-08 2011-02-16 株式会社日本自動車部品総合研究所 燃料噴射弁
FR2919022B1 (fr) * 2007-07-19 2012-10-26 Vianney Rabhi Centrale hydraulique pour moteur a taux de compression variable.
JP4831131B2 (ja) * 2008-06-06 2011-12-07 株式会社デンソー 燃料噴射弁
JP4911435B2 (ja) * 2008-10-03 2012-04-04 株式会社デンソー 燃料噴射弁
DE102009047560A1 (de) * 2009-12-07 2011-06-09 Robert Bosch Gmbh Kraftstoffinjektor
DE102010002845A1 (de) * 2010-03-15 2011-09-15 Robert Bosch Gmbh Kraftstoff-Injektor
DE102010044205A1 (de) * 2010-11-22 2012-05-24 Robert Bosch Gmbh Kraftstoffinjektor
US9012489B2 (en) 2011-08-03 2015-04-21 Boehringer Ingelheim International Gmbh Phenyl-3-aza-bicyclo[3.1.0]hex-3-yl-methanones and the use thereof as medicament
DE102012212266B4 (de) 2012-07-13 2015-01-22 Continental Automotive Gmbh Fluidinjektor
DE102012212264B4 (de) 2012-07-13 2014-02-13 Continental Automotive Gmbh Verfahren zum Herstellen eines Festkörperaktuators
DE102012021643B4 (de) 2012-11-03 2014-12-24 Peter Lischka Preiswerter Druckübersetzer für hohe Drücke
JP6443109B2 (ja) * 2015-02-17 2018-12-26 株式会社Ｓｏｋｅｎ 燃料噴射弁
CN116753096B (zh) * 2023-08-11 2023-10-13 山西焦煤集团正仁煤业有限公司 一种煤矿卡车用供油部结构

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3224769A1 (de) * 1981-11-19 1983-05-26 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen, insbesondere pumpeduese fuer dieselbrennkraftmaschinen
DE19500706C2 (de) * 1995-01-12 2003-09-25 Bosch Gmbh Robert Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen
DE19720145A1 (de) 1997-05-14 1998-11-19 Beiersdorf Ag Doppelseitiges Klebeband und seine Verwendung
DE69911670T2 (de) * 1998-02-19 2004-08-12 Delphi Technologies, Inc., Troy Kraftstoffeinspritzventil
DE19817320C1 (de) * 1998-04-18 1999-11-11 Daimler Chrysler Ag Einspritzventil für Kraftstoffeinspritzsysteme
DE10034444A1 (de) * 2000-07-15 2002-01-24 Bosch Gmbh Robert Brennstoffeinspritzventil

Also Published As

Publication number Publication date
DE102004035280A1 (de) 2006-03-16
US20080093483A1 (en) 2008-04-24
EP1771651A1 (de) 2007-04-11
ATE445096T1 (de) 2009-10-15
WO2006008200A1 (de) 2006-01-26
JP2008506888A (ja) 2008-03-06
DE502005008285D1 (de) 2009-11-19

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