EP1421271B1 - Brennstoffeinspritzventil - Google Patents

Brennstoffeinspritzventil Download PDF

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Publication number
EP1421271B1
EP1421271B1 EP02740381A EP02740381A EP1421271B1 EP 1421271 B1 EP1421271 B1 EP 1421271B1 EP 02740381 A EP02740381 A EP 02740381A EP 02740381 A EP02740381 A EP 02740381A EP 1421271 B1 EP1421271 B1 EP 1421271B1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
injection valve
actuator
piston
valve according
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
EP02740381A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1421271A1 (de
Inventor
Andreas Eichendorf
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 EP1421271A1 publication Critical patent/EP1421271A1/de
Application granted granted Critical
Publication of EP1421271B1 publication Critical patent/EP1421271B1/de
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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements

Definitions

  • the invention relates to a fuel injection valve according to the preamble of the main claim.
  • a hydraulic coupler for a piezoelectric actuator in which the actuator transmits a lifting force to a master piston.
  • the master piston is positively connected to a guide cylinder for a slave piston.
  • the slave piston, the guide cylinder and the master cylinder finalizing the master cylinder form a hydraulic chamber.
  • a spring is arranged, which presses apart the master piston and the slave piston.
  • a rubber sleeve Arranged around an end section of the guide cylinder and the slave piston is a rubber sleeve, through which a reservoir for a viscous hydraulic fluid is sealed against a fuel chamber. The viscosity of the hydraulic fluid is adapted to the annular gap between slave piston and guide cylinder.
  • the slave piston mechanically transfers a lifting movement to, for example, a valve needle.
  • the actuator transmits a stroke movement to the master piston and the guide cylinder
  • this stroke movement is transmitted to the slave piston by the pressure of the hydraulic fluid in the hydraulic chamber, since the hydraulic fluid in the hydraulic chamber is not can compress and only a small proportion of the hydraulic fluid can escape through the annular gap during the short period of a stroke in the reservoir formed by the rubber sleeve.
  • the slave piston In the resting phase, when the actuator exerts no pressure force on the master piston, the slave piston is pushed out of the guide cylinder by the spring and by the resulting negative pressure penetrates through the annular gap, the hydraulic fluid in the hydraulic chamber and fills it again.
  • the coupler automatically adjusts to length expansions and pressure-related expansions of a fuel injection valve.
  • a disadvantage of the known prior art is that the seal is permanently incomplete by a rubber sleeve, which is usually pressed by two clamping rings against the end portion of the guide cylinder and the slave piston.
  • the high viscosity hydraulic fluid and the fuel may mix and failure of the coupler may occur. If fuel, such as gasoline, enters the interior of the coupler, it may lead to malfunction, since due to the low viscosity of gasoline, this liquid can pass through the annular gap too quickly and can build up in the pressure chamber pressure during the time of the stroke.
  • the known prior art also offers no solution to how the piezoelectric actuator can be protected from contact with fuel, in particular gasoline.
  • a fuel injection valve with a piezoelectric actuator which is connected to a large-scale pressure piston.
  • This pressure piston is biased against the piezoelectric actuator with a plate spring, which is supported against a fuel injection valve body.
  • the pressure piston is guided in a bore of the valve body and has a central bore in which a slave piston is guided, which is connected to a valve needle.
  • a spring In the bore of the plunger, between the bottom of the bore and the slave piston, there is a spring, which biases the slave piston toward a valve seat and pushes out of the bore.
  • the fuel injection valve has a valve needle which opens inwards. Between the fuel injection valve body and the pressure piston and the opposite side of the slave piston is a pressure chamber.
  • the pressure chamber communicates with the actuator chamber via the annular gap between slave piston and pressure piston, the bore in the pressure piston and a connecting bore.
  • the actuator chamber serves as a reservoir for a hydraulic fluid.
  • a disadvantage of this known prior art is that no solution for an outwardly opening fuel injection valve is made possible. Furthermore, it is disadvantageous that no devices for fast refilling of the pressure chamber are provided after returning to the rest position. Finally, the structure is multi-part and complicated, since a pressure piston, which is guided in the fuel injection valve in an exact bore, again must have a bore to be produced exactly for the slave piston.
  • the fuel injection valve according to the invention with the characterizing features of the main claim has the opposite advantage that can be achieved by the movable diaphragm secure sealing of the actuator chamber relative to the fuel chamber. Furthermore, it is advantageous that a fast refilling of the pressure chamber after return of the piezoelectric actuator in its initial position and after return of the slave piston in its initial position and thus resulting volume increase of the pressure chamber is carried out by the check valve. The resulting negative pressure becomes the check valve opened and the hydraulic fluid flows quickly and quickly into the pressure chamber.
  • the movable diaphragm can be permanently sealed, for example when it is a thin metal diaphragm which can be secured by welds both to the slave piston and to a fuel injector body.
  • the sealing lines themselves are therefore no movable sealing lines and permanently sealed for life.
  • the required mobility occurs solely from the elasticity of the membrane. It is particularly advantageous that the membrane does not interfere with the mobility of the slave piston, as in the actuator chamber and in the fuel chamber, the same pressure prevails and the membrane moves by their deformability in such a position that they themselves do not have to absorb forces from occurring pressure differences ,
  • the piezoelectric actuator is thus safely protected from contact with the fuel and can be cooled by the high-viscosity hydraulic fluid at the same time, as well as being protected against wear by contact friction with the housing of the fuel injection valve.
  • the slave piston as well as the master piston can be formed as a deep-drawn part of sheet metal.
  • At least one partial section of the annular gap is between master piston or slave piston and a guide cylinder in the installed position of the fuel injection valve in the rising direction of any gas bubbles, arranged at the highest point of the pressure chamber.
  • the slave piston is sealingly and non-positively connected to the guide cylinder.
  • the guide cylinder consists of a deep-drawn sheet metal part or a pipe section, which is sealingly connected to the slave piston by welding, creating a simple component.
  • the master piston is guided in this cup-like component.
  • a path ratio can be effected and the low stroke of a piezoelectric actuator can be translated in a larger travel.
  • the check valve is a ball check valve whose valve seat is formed on the master piston.
  • a ball check valve is inexpensive to manufacture and can be well placed in the pressure chamber with a small size.
  • a silicone oil is used as the hydraulic fluid.
  • An actuator spring may be formed as a spiral spring and enclose the hydraulic coupler.
  • the necessary biasing force on the actuator can thus be effected in a space-saving arrangement.
  • the membrane has a wavy contour in a radial section.
  • Fig. 1 shows schematically a section of a fuel injection valve 1, wherein the region of a piezoelectric or magnetostrictive actuator 2 and an actuator chamber 3, which communicates via a connecting bore 4 with a lower actuator chamber 5, are shown.
  • the actuator 2 is arranged in an actuator chamber housing 6, which is bounded by a closure plate 7.
  • electrical connections 9 are passed and sealed by an O-ring 10.
  • the actuator 1 is driven by an electrical voltage.
  • An actuator spring 11 is supported on an intermediate disc 12 and presses an actuator head 13 against the actuator 2 so that it comes into contact with the closure plate 7.
  • On the actuator head 13 is located on a master piston 14 which is guided in a guide cylinder 15.
  • the guide cylinder 15 is sealingly and non-positively connected to a slave piston 16 by a weld 17.
  • a coupler spring 18 exerts on the master piston 14 a biasing force which seeks to drive the master piston 14 out of the guide cylinder 15.
  • the master piston 14, the guide cylinder 15, the slave piston 16 and the coupler spring 18 form the coupler 19.
  • a check ball 20 is arranged, which is pressed by a check spring 21 and a guide sleeve 22 against a valve seat 23 into the master piston 14 ,
  • the check ball 20, the return spring 21 and the sealing seat 23 form a check valve 24.
  • the hydraulic fluid can pass from the upper actuator chamber 3 to the valve sealing seat 23 of the check valve 24.
  • the coupler 19 is guided with its guide cylinder 15 in a bore 26 of the washer 12.
  • a diaphragm 29 is sealingly connected to the washer 12 and via an inner weld 28, the same membrane 29 is sealingly connected to the slave piston 16.
  • the membrane 29 separates a fuel chamber 30 from the lower actuator chamber 5. Since the lower actuator chamber 5 is connected via the connecting bore 4 with the upper actuator chamber 3, prevails in the upper actuator chamber 3, the lower actuator chamber 5 and the fuel chamber 30, the same pressure the membrane 29 deformed so far until pressure equalization is established.
  • the diaphragm 29 also follows the movement of the slave piston 16, and further radially outwardly disposed parts of the diaphragm 29 perform an opposite movement, so that also the pressure balance between the lower actuator chamber 5 and the fuel chamber 30 is maintained during a lifting movement of the slave piston 16.
  • the lifting movement of the slave piston 16 is not or only slightly prevented or influenced by the diaphragm 29.
  • the slave piston 16 transmits a possible lifting movement to a valve needle 31st
  • the actuator 2 When a voltage is applied to the actuator 2 via the electrical supply line 9, the actuator 2 exerts on the actuator head 13 a lifting movement, which continues to be transmitted to the master piston 14 of the coupler 19.
  • the master piston 14 is pressed into the interior of the guide cylinder 15 which is formed with the slave piston 16 as a one-piece deep-drawn part.
  • the hydraulic fluid inside a pressure chamber 32 formed by the slave piston 16, the guide cylinder 15 and the master piston 14 is a highly viscous liquid, such as a silicone oil, almost non-compressible.
  • the properties of the silicone oil for the coupler and the use in the actuator chamber 3 can be optimized.
  • it can be achieved by setting a suitable viscosity that the components of the master piston 14, the guide cylinder 15 and the slave piston 16 can be designed as inexpensive to be produced deep-drawing plates, which require relatively large gap dimensions.
  • the described embodiment of a fuel injection valve 1 according to the invention further enables a secure sealing of the actuator 2 relative to the fuel chamber 30, since the sealing membrane 29 does not have to absorb pressure forces.
  • the silicone oil exerts a damping effect both on the actuator 2 as well as all other moving parts. Due to the high actuation rate of fuel injection valves 1, which is necessary in modern internal combustion engines, vibrations can occur, which are effectively damped.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP02740381A 2001-08-20 2002-05-25 Brennstoffeinspritzventil Expired - Lifetime EP1421271B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10140799A DE10140799A1 (de) 2001-08-20 2001-08-20 Brennstoffeinspritzventil
DE10140799 2001-08-20
PCT/DE2002/001926 WO2003018992A1 (de) 2001-08-20 2002-05-25 Brennstoffeinspritzventil

Publications (2)

Publication Number Publication Date
EP1421271A1 EP1421271A1 (de) 2004-05-26
EP1421271B1 true EP1421271B1 (de) 2006-01-18

Family

ID=7696038

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02740381A Expired - Lifetime EP1421271B1 (de) 2001-08-20 2002-05-25 Brennstoffeinspritzventil

Country Status (6)

Country Link
US (1) US6948667B2 (ko)
EP (1) EP1421271B1 (ko)
JP (1) JP4116548B2 (ko)
KR (1) KR100881583B1 (ko)
DE (2) DE10140799A1 (ko)
WO (1) WO2003018992A1 (ko)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1511932B1 (de) * 2002-04-04 2006-11-29 Siemens Aktiengesellschaft Einspritzventil
JP4288182B2 (ja) * 2002-04-22 2009-07-01 シーメンス アクチエンゲゼルシヤフト 流体のための調量装置、特に自動車用噴射弁
DE10245109A1 (de) 2002-09-27 2004-04-08 Siemens Ag Injektor, insbesondere Kraftstoff-Einspritzventil, mit einem piezoelektrischen Aktor
DE10307816A1 (de) * 2003-02-24 2004-09-02 Robert Bosch Gmbh Brennstoffeinspritzventil
DE10344061A1 (de) * 2003-09-23 2005-04-28 Siemens Ag Einspritzventil mit einem hydraulischen Ausgleichselement
US7100577B2 (en) * 2004-06-14 2006-09-05 Westport Research Inc. Common rail directly actuated fuel injection valve with a pressurized hydraulic transmission device and a method of operating same
DE102005025953A1 (de) * 2005-06-06 2006-12-07 Siemens Ag Einspritzventil und Ausgleichselement für ein Einspritzventil
US7472844B2 (en) * 2005-12-21 2009-01-06 Caterpillar Inc. Fuel injector nozzle with tip alignment apparatus
DE602006021529D1 (de) * 2006-02-03 2011-06-09 Continental Automotive Gmbh Aktoreinheit für ein Einspritzventil und Einspritzventil
DE102006019308A1 (de) * 2006-04-26 2007-10-31 Robert Bosch Gmbh Injektor
US7353806B2 (en) * 2006-09-06 2008-04-08 Cummins Inc. Fuel injector with pressure balancing valve
DE102007043532A1 (de) * 2007-09-12 2009-03-19 Robert Bosch Gmbh Ventilanordnung zur Dosierung einer wässrigen Harnstofflösung
US7665445B2 (en) * 2008-04-18 2010-02-23 Caterpillar Inc. Motion coupler for a piezoelectric actuator
US8201543B2 (en) * 2009-05-14 2012-06-19 Cummins Intellectual Properties, Inc. Piezoelectric direct acting fuel injector with hydraulic link
DE112010002435B4 (de) * 2009-06-10 2019-08-01 Cummins Intellectual Properties, Inc. Piezoelektrisch direkt wirkende Kraftstoff-Einspritzdüse mit Hydraulikverbindung
DE102013012444A1 (de) * 2013-07-29 2015-01-29 Astrium Gmbh Ventilanordnung zum Schalten und/oder Regeln eines Medienstroms eines Raumfahrttriebwerks und Raumfahrttriebwerk
DE102013219225A1 (de) * 2013-09-25 2015-03-26 Continental Automotive Gmbh Piezo-Injektor zur Kraftstoff-Direkteinspritzung

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3121572A1 (de) * 1981-05-30 1982-12-16 Robert Bosch Gmbh, 7000 Stuttgart "einspritzventil"
ATE192263T1 (de) * 1990-09-25 2000-05-15 Siemens Ag Anordnung für einen in hubrichtung wirkenden adaptiven, mechanischen toleranzausgleich für den wegtransformator eines piezoelektrischen aktors
DE4306072C2 (de) * 1993-02-26 1994-12-08 Siemens Ag Vorrichtung zum Öffnen und Verschließen einer in einem Gehäuse vorhandenen Durchtrittsöffnung
DE4306073C1 (de) * 1993-02-26 1994-06-01 Siemens Ag Zumeßvorrichtung für Fluide
DE19500706C2 (de) * 1995-01-12 2003-09-25 Bosch Gmbh Robert Zumeßventil zur Dosierung von Flüssigkeiten oder Gasen
DE19727992C2 (de) * 1997-07-01 1999-05-20 Siemens Ag Ausgleichselement zur Kompensation temperaturbedingter Längenänderungen von elektromechanischen Stellsystemen
DE19744235A1 (de) * 1997-10-07 1999-04-08 Fev Motorentech Gmbh & Co Kg Einspritzdüse mit piezoelektrischem Aktuator
US5875764A (en) * 1998-05-13 1999-03-02 Siemens Aktiengesellschaft Apparatus and method for valve control
DE19912666A1 (de) * 1999-03-20 2000-09-21 Bosch Gmbh Robert Brennstoffeinspritzentil
DE19940054C2 (de) * 1999-08-24 2003-11-27 Siemens Ag Dosierventil für ein unter Druck stehendes Fluid
DE19946833C2 (de) * 1999-09-30 2002-02-21 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10006319A1 (de) * 2000-02-12 2001-08-16 Daimler Chrysler Ag Einspritzventil
DE10015268A1 (de) * 2000-03-28 2001-10-04 Siemens Ag Einspritzventil mit Bypaßdrossel
DE60125207T2 (de) * 2000-10-11 2007-10-25 Siemens Vdo Automotive Corp., Auburn Hills Ausgleichsvorrichtung mit einem druckventil für einen festkörperaktor eines kraftstoffeinspritzventils

Also Published As

Publication number Publication date
KR100881583B1 (ko) 2009-02-03
KR20040027899A (ko) 2004-04-01
US20040031862A1 (en) 2004-02-19
EP1421271A1 (de) 2004-05-26
JP4116548B2 (ja) 2008-07-09
US6948667B2 (en) 2005-09-27
JP2005500469A (ja) 2005-01-06
DE50205654D1 (de) 2006-04-06
DE10140799A1 (de) 2003-03-06
WO2003018992A1 (de) 2003-03-06

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