EP0952333A2 - Injecteur à combustible pour systèmes d'injection de combustible - Google Patents

Injecteur à combustible pour systèmes d'injection de combustible Download PDF

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Publication number
EP0952333A2
EP0952333A2 EP99106924A EP99106924A EP0952333A2 EP 0952333 A2 EP0952333 A2 EP 0952333A2 EP 99106924 A EP99106924 A EP 99106924A EP 99106924 A EP99106924 A EP 99106924A EP 0952333 A2 EP0952333 A2 EP 0952333A2
Authority
EP
European Patent Office
Prior art keywords
piston
nozzle needle
piezo stack
injection valve
pressure
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.)
Granted
Application number
EP99106924A
Other languages
German (de)
English (en)
Other versions
EP0952333A3 (fr
EP0952333B1 (fr
Inventor
Karl-Heinz Hoffmann
Heinz Öing
Gregor Dr. Renner
Reinhard Fischer
Günter Vogt
Jens-Peter Wobbe
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.)
Erphi-Electronic GmbH
P & S Prototypen und Sondermaschinen Entwicklu
Mercedes Benz Group AG
Original Assignee
P & S Prototypen und Sondermaschinen Entwicklungsgesellschaft Mbh
ERPHI ELECTRONIC GmbH
Erphi-Electronic GmbH
P & S
DaimlerChrysler AG
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 P & S Prototypen und Sondermaschinen Entwicklungsgesellschaft Mbh, ERPHI ELECTRONIC GmbH, Erphi-Electronic GmbH, P & S, DaimlerChrysler AG filed Critical P & S Prototypen und Sondermaschinen Entwicklungsgesellschaft Mbh
Publication of EP0952333A2 publication Critical patent/EP0952333A2/fr
Publication of EP0952333A3 publication Critical patent/EP0952333A3/fr
Application granted granted Critical
Publication of EP0952333B1 publication Critical patent/EP0952333B1/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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/002—Arrangement of leakage or drain conduits in or from injectors
    • 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
    • F02M61/04—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
    • 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

Definitions

  • the invention relates to an injection valve for fuel injection systems according to the kind defined in the preamble of claim 1.
  • a generic injection valve is known from DE 195 19 191 C2.
  • the disadvantage here is that the actuating force for the nozzle needle decreases when the path is translated.
  • DE 195 00 706 A1 discloses a fuel injection valve for internal combustion engines, which has a hydraulic displacement amplifier for converting an actuating path of a piezoelectric actuator. With this valve there are fluid supply and discharge Channels separated from one another, wherein the fluid is guided into an annular space through a channel arranged in the valve housing.
  • a disadvantage of this injection valve is that although the path is increased, the actuating force is simultaneously reduced via the lever law.
  • a further disadvantage is that the channel subjects the fuel injection valve to a bending stress during the supply of fuel into the annular space.
  • EP 0 218 895 B1 a metering valve for metering liquids or gases with a piezoelectric actuator is known.
  • the pressure that acts on the valve acts directly on the piezoelectric actuator.
  • an exact function of the valve is no longer guaranteed due to loss of travel of the valve needle.
  • Another disadvantage is that after the valve needle has been lifted out of the valve seat, the fuel injects into the combustion chamber in an uncontrollable manner through the gap that is created.
  • the present invention has for its object to provide an injection valve of the type mentioned, with which a fuel injection with high accuracy and precisely and without loss of power is possible by a translation.
  • a hydraulic booster in the form of a working piston, it is possible to decouple the system in terms of force.
  • the path of the piezo stack is transferred to a displacement piston.
  • a control piston downstream of the displacer piston, which increases the adjustment path generated by the piezo stack, moves in the direction of the nozzle needle with a predetermined transmission ratio.
  • the nozzle needle is then actuated via the working piston, which increases the actuating force.
  • the path amplification according to the invention is decoupled from the force because the application of force for opening the nozzle needle is only via the system pressure, e.g. a rail pressure. Since there is no loss of power in the translation, the piezo stack position also has no negative influence on the opening of the nozzle needle.
  • a pressure compensation chamber is arranged between the displacement piston and the control piston for hydraulic length compensation of the piezo stack, which pressure chamber is connected on the one hand to a leakage line of the control piston and on the other hand to a leakage line of the displacement piston.
  • the pressure compensation chamber according to the invention with its hydraulic compensation volume serves to compensate for temperature and elongation effects of the piezo stack.
  • a pressure piece is arranged for a hydraulic length compensation for the nozzle needle between the nozzle needle and the working piston, with a length compensation space with a compensating spring being located between the pressure piece and the working piston.
  • This configuration according to the invention achieves hydraulic length compensation for the nozzle needle due to thermal and hydraulic length changes.
  • the injection valve according to the invention is suitable with the same principle of action for nozzle needles that open both outwards and inwards.
  • the injection valve 1 shown in FIG. 1 has an injector housing 2, a piezo guide 3, in which a piezo stack 4 is arranged, and a valve housing 6 connected to the injector housing 2 by means of a union nut 5.
  • a valve closing device 7 is arranged displaceably in the valve housing 6.
  • the valve closing device 7 has a tappet 8 as a nozzle needle with a valve stem 9, in which the tappet 8 is fitted.
  • a sealing member in the form of a shoulder 10 is provided at the end of the valve stem 9 facing the combustion chamber.
  • the annular gap 12 becomes a precisely metered quantity of fuel into a combustion chamber , which is not shown in the drawing, injected.
  • a flow limiter 13 is used for this purpose, which is pressed with a spring device 14 against a cross-sectional area of the shoulder 10 of the valve stem 9.
  • the spring device 14 is supported on a cylindrical stop 15.
  • annular space 16 is formed, into which a line 17 which supplies the valve 1 with fuel opens. From here, the fuel flows into the annular gap 12 via bores 18.
  • the piezo stack 4 lies completely in the low-pressure region of fuel-discharging channels and is therefore not impaired in its mode of operation by the fuel supplied at very high pressure.
  • the backflow of fuel takes place in this pressure region in a longitudinal groove 19, where it emerges from the valve 1 at the end of the piezo stack 4 facing away from the combustion chamber.
  • the piezo stack 4 is subjected to a control voltage, this causes the piezo stack 4 to be elongated in a known manner, which opens the valve closing device 7, since a corresponding gap is formed between the shoulder 10 of the valve stem 9 and a valve seat 6 or the flow limiter 13.
  • the control voltage is switched off, which shortens the piezo stack 4 again to its original length.
  • the resetting of the nozzle needle 8 causes a nozzle needle spring 51, which is supported on an annular collar 55 of the nozzle needle 8.
  • the piezo stack 4 is surrounded by a protective tube 20 provided with an end sealing cap.
  • the sealing cap of the protective tube 20 is arranged in the axial direction between the piezo stack 4 and a displacement piston 21 and thus actuates the latter when the piezo stack 4 is elongated.
  • a control piston 22 In the axial direction in front of the displacement piston 21 - in relation to the combustion chamber - there is a control piston 22.
  • the control piston 22 has a smaller effective pressure area than the displacement piston 21.
  • the hydraulic Gear ratios result from the different geometries or diameter ratios of the displacer piston 21 and control piston 22.
  • the pressure compensation chamber 24 is filled with test oil or with fuel.
  • the filling or pressure equalization takes place via targeted leakages between the control piston 22, the displacement piston 21 and the surrounding cylinder housing 25.
  • annular space 29 is subjected to system pressure (rail pressure) from the annular space 16 via an annular groove 27 and an oblique bore 28 which are arranged in the control piston 22.
  • system pressure rail pressure
  • the annular space 29 is formed between the control piston 22 and a sliding sleeve 30.
  • the piezo stack 4 receives a control voltage; the protective tube 20, the displacement piston 21 and the control piston 22 are shifted in the direction of arrow B, a pilot control edge 31 opening between the control piston 22 and the sliding sleeve 30, thus creating a high-pressure connection via the annular space 29 to a bore 32 in the sliding sleeve 30 and thus to an associated working cylinder or working pressure space 33, which is located radially between the sliding sleeve 30 is arranged with a return control edge 36 and the cylinder housing 25 and axially between an end wall of the cylinder housing 25 and a working piston 34.
  • the working piston 34 is displaced away from the control piston 22 in the direction of arrow B.
  • the sliding sleeve 30 follows the working piston 34 and seals the pressure chamber 33 with the return control edge 36.
  • the sliding sleeve 30 follows the working piston 34 until it meets the pilot control edge 31 between the control piston 22 and the sliding sleeve 30 again or blocks this control edge.
  • the working pressure chamber 33 is hydraulically sealed and the working piston remains in this position.
  • the displacer piston 21 specifies the path for the secondary amplifier consisting of the displacer piston 21, the control piston 22, the sliding sleeve 30 and the working piston 34, which is then converted onto the nozzle needle 8.
  • a hydraulic length compensation space 39 for the nozzle needle 8, due to thermal and hydraulic length changes, is formed in this way by the cylinder housing 25, the working piston 34, the compensation spring 40, the compensation bore 41 and the pressure piece 42. Changes in length and thereby changes in volume are compensated for by the bore 41. In this way, even if e.g. the nozzle needle 8 is compressed, the working piston 34 always defines the return control edge 36.
  • the protective tube 20 has the task of ensuring that the piezo stack 4 does not come into contact with fuel.
  • Hydraulic length compensation of the piezo stack 4 is achieved via the targeted leakage of the control piston 22 and a capillary incorporated in the outer diameter of the displacement piston 21, via which leakage reaches the return line or the longitudinal groove 19.
  • the mechanical performance of the piezo stack 4 is used exclusively for valve positioning. In other words, this means that the force amplification has nothing directly to do with the piezo stack 4. It is not the piezo force that is used to actuate the nozzle needle 8, but only the pressure that is applied in the pressure chamber of the working cylinder 33, and this pressure corresponds proportionally to the actuating force.
  • the exemplary embodiment described above referred to a nozzle needle 8 which opens outwards, the direction of travel of the piezo stack 4 corresponding to the direction of travel of the nozzle opening. It is advantageous to keep the leakage oil drain via the longitudinal groove 19 at 3 to 5 bar back pressure (cavitation, cavitation).
  • FIGS. 3 and 4 show an injection valve in which the nozzle needle 8 'opens inwards for injecting fuel. This means that the actuation direction of the piezo stack 4 'is reversed to the actuation direction of the nozzle needle 8'.
  • the parts that have the same function as those in the embodiment are according to Figures 1 and 2, the same reference numerals - provided with a corresponding index - used.
  • no ring line 16 is provided for supplying rail pressure, but instead a branch line 43.
  • a leakage line 44 is provided for the return flow of fuel.
  • the piezo bias can again be set in the pressure compensation chamber 24 'by means of plates or spiral springs 23'. With this injection valve system, the path must be reversed when the piezo stack 4 'is actuated. In this case, the space in which a spring 56 is located is only a ventilation space.
  • the pressure compensation chamber 24 ' is compressed at a control voltage 4'. In addition, a diameter difference acts in the pressure compensation chamber 24 '.
  • the fuel supply for the pressure compensation chamber 24 ' takes place via a connecting channel 54 in the control piston 22' to the inlet 26 via a collar in the control piston 22 '.
  • the sliding sleeve 30 ' is pressed against the working piston 34' by a plate spring 35 '.
  • the control piston 22 ' is reset by a plate spring 52', which is supported on the displacement piston 34 '.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP99106924A 1998-04-18 1999-04-08 Injecteur à combustible pour systèmes d'injection de combustible Expired - Lifetime EP0952333B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19817320A DE19817320C1 (de) 1998-04-18 1998-04-18 Einspritzventil für Kraftstoffeinspritzsysteme
DE19817320 1998-04-18

Publications (3)

Publication Number Publication Date
EP0952333A2 true EP0952333A2 (fr) 1999-10-27
EP0952333A3 EP0952333A3 (fr) 2002-02-13
EP0952333B1 EP0952333B1 (fr) 2004-06-23

Family

ID=7865016

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99106924A Expired - Lifetime EP0952333B1 (fr) 1998-04-18 1999-04-08 Injecteur à combustible pour systèmes d'injection de combustible

Country Status (3)

Country Link
US (1) US6302333B1 (fr)
EP (1) EP0952333B1 (fr)
DE (2) DE19817320C1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10006319A1 (de) * 2000-02-12 2001-08-16 Daimler Chrysler Ag Einspritzventil
EP1174615A2 (fr) * 2000-07-18 2002-01-23 Delphi Technologies, Inc. Injecteur de combustible
WO2006008200A1 (fr) * 2004-07-21 2006-01-26 Robert Bosch Gmbh Injecteur de carburant a commande polyetagee directe de l'element de soupape d'injection
EP1703119A1 (fr) * 2005-02-28 2006-09-20 Robert Bosch Gmbh Buse d'injection de carburant

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19953562A1 (de) * 1999-11-08 2001-05-23 Bosch Gmbh Robert Kraftstoff-Einspritzdüse
DE10000575A1 (de) * 2000-01-10 2001-07-19 Bosch Gmbh Robert Einspritzdüse
DE10112147A1 (de) * 2001-03-14 2002-09-19 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
ITBO20010279A1 (it) * 2001-05-08 2002-11-08 Magneti Marelli Spa Iniettore di carburante con attuatore piezoelettrico alloggiato in una camera isolata
DE10133265A1 (de) * 2001-07-09 2003-01-23 Bosch Gmbh Robert Brennstoffeinspritzventil
US6766965B2 (en) * 2001-08-31 2004-07-27 Siemens Automotive Corporation Twin tube hydraulic compensator for a fuel injector
US6792921B2 (en) * 2001-12-17 2004-09-21 Caterpillar Inc Electronically-controlled fuel injector
US6983894B2 (en) 2002-02-13 2006-01-10 Siemens Vdo Automotive Inc. Piezo-electrically actuated canister purge valve with a hydraulic amplifier
EP1391607A1 (fr) * 2002-08-20 2004-02-25 Siemens VDO Automotive S.p.A. Doseur
US6811093B2 (en) * 2002-10-17 2004-11-02 Tecumseh Products Company Piezoelectric actuated fuel injectors
DE10310790A1 (de) * 2003-03-12 2004-09-23 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102004027824A1 (de) 2004-06-08 2006-01-05 Robert Bosch Gmbh Kraftstoffinjektor mit variabler Aktorübersetzung
US7307371B2 (en) * 2005-11-18 2007-12-11 Delphi Technologies, Inc. Actuator with amplified stroke length
US7628139B2 (en) * 2006-07-11 2009-12-08 Detroit Diesel Corporation Fuel injector with dual piezo-electric actuator
US7658179B2 (en) * 2008-05-28 2010-02-09 Caterpillar Inc. Fluid leak limiter
US7661410B1 (en) 2008-08-18 2010-02-16 Caterpillar Inc. Fluid leak limiter
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
DE102014009025B4 (de) 2014-06-24 2016-02-18 Airbus Ds Gmbh Biegerahmen zur Velängerung des Stellwegs eines Aktors für ein mechanisch betätigtes Bauteil

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19519191C2 (de) 1995-05-24 1997-04-10 Siemens Ag Einspritzventil
DE19500706C2 (de) 1995-01-12 2003-09-25 Bosch Gmbh Robert Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3501099A (en) * 1967-09-27 1970-03-17 Physics Int Co Electromechanical actuator having an active element of electroexpansive material
DE3533085A1 (de) * 1985-09-17 1987-03-26 Bosch Gmbh Robert Zumessventil zur dosierung von fluessigkeiten oder gasen
DE4311627B4 (de) * 1993-04-08 2005-08-25 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
US5779149A (en) * 1996-07-02 1998-07-14 Siemens Automotive Corporation Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke
DE19701288C2 (de) * 1997-01-16 1999-10-14 Daimler Benz Ag Ventil zur dosierten Abgabe von Fluiden

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19500706C2 (de) 1995-01-12 2003-09-25 Bosch Gmbh Robert Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen
DE19519191C2 (de) 1995-05-24 1997-04-10 Siemens Ag Einspritzventil

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10006319A1 (de) * 2000-02-12 2001-08-16 Daimler Chrysler Ag Einspritzventil
EP1174615A2 (fr) * 2000-07-18 2002-01-23 Delphi Technologies, Inc. Injecteur de combustible
EP1174615A3 (fr) * 2000-07-18 2002-08-28 Delphi Technologies, Inc. Injecteur de combustible
US6776354B2 (en) 2000-07-18 2004-08-17 Delphi Technologies, Inc. Fuel injector
US7451938B2 (en) 2000-07-18 2008-11-18 Delphi Technologies, Inc. Fuel injector
WO2006008200A1 (fr) * 2004-07-21 2006-01-26 Robert Bosch Gmbh Injecteur de carburant a commande polyetagee directe de l'element de soupape d'injection
EP1703119A1 (fr) * 2005-02-28 2006-09-20 Robert Bosch Gmbh Buse d'injection de carburant

Also Published As

Publication number Publication date
EP0952333A3 (fr) 2002-02-13
EP0952333B1 (fr) 2004-06-23
DE59909783D1 (de) 2004-07-29
DE19817320C1 (de) 1999-11-11
US6302333B1 (en) 2001-10-16

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