EP0795081A1 - Commande electro-hydraulique - Google Patents

Commande electro-hydraulique

Info

Publication number
EP0795081A1
EP0795081A1 EP95940120A EP95940120A EP0795081A1 EP 0795081 A1 EP0795081 A1 EP 0795081A1 EP 95940120 A EP95940120 A EP 95940120A EP 95940120 A EP95940120 A EP 95940120A EP 0795081 A1 EP0795081 A1 EP 0795081A1
Authority
EP
European Patent Office
Prior art keywords
actuator
piston
electro
hydraulic drive
drive 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.)
Granted
Application number
EP95940120A
Other languages
German (de)
English (en)
Other versions
EP0795081B1 (fr
Inventor
Andreas Kappel
Randolf Mock
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.)
Siemens AG
Original Assignee
Siemens 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 Siemens AG filed Critical Siemens AG
Publication of EP0795081A1 publication Critical patent/EP0795081A1/fr
Application granted granted Critical
Publication of EP0795081B1 publication Critical patent/EP0795081B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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

Definitions

  • the injection valve known from /! / Contains a compact drive, which has very good dynamic properties and still works reliably even at high actuation frequencies (f> 1 kHz). Since the drive enables valve opening and closing times in the range of ⁇ ⁇ 0.1 ms, even the smallest amounts of fuel can be injected precisely and reproducibly into the combustion chamber of an engine.
  • the main components of the drive are a piezo actuator generating the primary travel range and a hydraulic stroke transformer, which essentially consists of a pressure piston driven by the piezo actuator and a stroke piston which is axially displaceably mounted in a pressure piston bore and is connected to the valve needle.
  • the piezo actuator arranged in one of the hydraulic chambers is supported on the housing side on a ball cap bearing. This measure ensures that the actuator always rests on the pressure piston over the entire surface even when the end faces are non-parallel, and that there are no stroke losses.
  • the structure of the known valve places high demands on the axial symmetry and dimensional accuracy of the individual components.
  • the multiply guided reciprocating piston has to be manufactured to an accuracy of a few ⁇ m in order to prevent tilting or jamming. This complicates mass production and considerably increases the cost of manufacturing the valve.
  • the aim of the invention is to provide a reliable electrohydraulic drive which has a compact structure. sits, works within a wide temperature range and has good dynamic properties.
  • An electro-hydraulic drive with the features specified in claim 1 has these properties.
  • the advantage that can be achieved with the invention is, in particular, that even a comparatively large decentration of one of the multiply guided parts does not impair the functionality of the drive.
  • the drive can therefore be manufactured with much less effort and manufactured more cost-effectively.
  • Figure 1 shows an electro-hydraulic drive for a fuel injection valve in section
  • Figure 2 is a two-part reciprocating piston of the force-translation of the drive in section
  • FIG. 1 essentially shows only the components of a fast fuel injection valve relating to the drive according to the invention, as is known, for example, from / l / or described in more detail in the older German application / 2 /.
  • the injection valve contains an electromechanical actuator P which acts on a hydraulic stroke transformer DK / HK and which is supplied with the required operating voltages via a pressure-tight housing bushing LD.
  • the actuator P In order to initiate the injection of the fuel into the combustion chamber of the engine, the actuator P is activated and thereby elongated in the axial direction.
  • the change in length .DELTA.l of the actuator P results in a corresponding displacement of the pressure piston DK mounted in a cylindrical bore of the housing VG so that there is an overpressure p 1 # in the hydraulic oil-filled chamber KAI in the hydraulic oil-filled chamber and through a pressure piston bore Bl fluidly connected chambers KA2 and KA3 a vacuum P2 / 3 ⁇ Pi on aut.
  • the fuel injection is ended by the electrical discharge of the piezo actuator P.
  • the pressure piston DK moves back down to its starting position under the force of the restoring force exerted by a strong plate spring TF.
  • the spiral spring SF Supported by the spiral spring SF and the pressure difference existing between the chambers KAI and KA2 / KA3, the reciprocating piston HK executes an opposite movement upwards, so that the valve needle VN guided out of the housing VG is lowered onto the sealing seat and closes the injection opening.
  • the transient mode of operation of the drive makes it necessary to mechanically pretension the piezo actuator P.
  • the force required for this is generated by the plate spring TF arranged in the chamber KAI, which also supports the return of the pressure piston DK to its rest position.
  • Flow channels SK in the chamber ceiling ensure an unimpeded inflow and outflow of the hydraulic oil into the volume enclosed by the plate spring TF and the valve housing VG.
  • the compensation element AE which is in the form of a spherical layer, is preferably made of stainless steel or a chromium-nickel steel. Due to its polished surfaces, the compensating element AE can slide freely on the piezoceramic during assembly of the hydraulics and thus compensate for a non-concentric alignment of actuator P and pressure piston DK.
  • the free rotatability of the compensating element AE within the conical abutment WL also ensures that the upper part of the piezo actuator P, which is secured against rotation on the housing base, is always in contact with the pressure piston DK over the entire surface.
  • the disc spring TF which mechanically pre-stresses the piezo actuator P, ensures the frictional contact between the parts.
  • the force / displacement ratio driven by the actuator P consists of two coupled hydraulic transformers, the transmission ratio t
  • AD1 area of the piston top
  • AH1 area of the piston top
  • AD2 Actuator-side pressure piston surface
  • AH2 Actuator-side reciprocating piston surface
  • Equation (2) only applies on the condition that the actuator P arranged in the hydraulic chamber KA3 has the same volume in the elongated and unloaded state. Like the piezo stack P used, electrostrictive and magnetostrictive actuators also show such behavior in good proximity.
  • the pressure piston DK of the force / displacement ratio shown in FIG. 1 is designed in stages (AD1 ⁇ AD2) in order to take into account the inequality of the pressure-effective piston surfaces AH1 ⁇ AH2 caused by the valve needle.
  • the hydraulic coupling of the two stroke transformers has the result that with each change in length of the actuator P complementary pressures build up in the chambers KAI and KA2 / KA3, whereby a displacement of the pressure piston DK by ⁇ l increases in an opposite manner corresponding to the hydraulic transmission ratio ⁇ »1 Displacement of the HK piston in the pressure piston bore ZY.
  • the hydraulic chambers KAI, KA2, KA3 are connected both to one another and to the compensating volume AV, which is under pressure, between the pistons DK, HK and the corresponding cylinder bores KS. Temperature-related changes in volume of the hydraulic oil can therefore neither lead to the formation of static pressure differences between the chambers KAI and KA2 / KA3 (this would result in undefined positions of the HK reciprocating piston), nor to the formation of undefined pressure states in the entire system.
  • the connection between the ring chamber RV and the equalizing volume AV has been established via the housing bore Gl furthermore the advantage that there is no cavitation in the hydraulic oil which reduces the maximum actuation frequency.
  • the valve shuts off in the relevant working temperature range with the frequency and the desired duration specified by the control signal.
  • it is advisable, for example, to provide the bore G1 in the area of the pressure piston sealing surface. In principle, however, it can also open into the annular chamber RV (see FIG. 1) or be fitted in any other area of the valve housing VG, provided that flow resistances in the form of orifices, gaps, restrictors, constrictions etc. ensure that between the different volumes or chambers only comparatively slow compensation processes take place.
  • the chambers have to be sealed against one another to such an extent that the required shut-off times are achieved and the temperature independence of the drive is still guaranteed.
  • Temperature-dependent control of the gap flows is possible if the valve housing VG and the internals (pressure piston DK, reciprocating piston HK) are made from materials with different thermal volume / length expansion coefficients. It can thus be achieved that the gap widths decrease with increasing temperature, which increases the flow resistance accordingly.
  • Temperature-controlled flow resistances can of course also be manufactured as discrete components and installed in the corresponding holes G3 or supply lines.
  • the drive according to the invention has a number of advantages.
  • the drive thus allows symmetrical, cavitation-free switching with very short switching times, extremely short idle times and high actuation frequencies.
  • the drive is characterized by a high level of operational reliability.
  • the fact that the actuator P is hermetically encapsulated in one of the hydraulic chambers KA3 also contributes to this. A good dissipation of the generated heat and optimal protection against environmental influences are therefore guaranteed.
  • the drive is also largely closed, since the electrical connections L of the actuator P are led outside through a pressure-tight, electrically insulating element LD.
  • the reciprocating piston of the force / displacement transmission shown in FIG. 2 consists of two parts HK1, HK2, the cup-shaped outer part HKl, which is open on the valve needle side and rests on the spring SF, is guided with close tolerance in the pressure piston bore ZY.
  • This is the basis for the cup-shaped inner piston part HK2, which is open on the actuator side.
  • a screw S connects the inner part HK2, which can be moved transversely to the stroke direction, with the valve needle VN. Both parts can also be soldered or welded.

Landscapes

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

Abstract

Dans les soupapes d'injection rapides, on utilise depuis peu des transformateurs hydrauliques de levée, qui comprennent par exemple un piston de pression (DK) actionné par un piézo-actuateur (P) et un piston alternatif (HK) relié au pointeau de soupape (VN) et disposé dans un alésage du piston de pression (ZY) de manière à se déplacer dans le sens axial. Cette configuration soumet les constituants individuels à de fortes exigences en termes de symétrie axiale et de respect des cotes, ce qui complique la production en masse de la soupape et en rend la fabrication plus coûteuse. L'invention concerne une commande comprenant un piézo-actuateur (O) et une démultiplication hydraulique de force/course, de structure compacte et comparativement plus économique à produire. Afin de garantir la symétrie axiale de la commande en dépit des tolérances inhérentes à la fabrication, il est prévu un élément de compensation (AE) qui prend appui dans une cavité (WL) tronconique du piston de pression (DK) et se trouve entre le piézo-actuateur (P) et le transformateur de levée. L'élément (AE) est en acier et se présente sous forme de couche sphérique, ce qui lui permet de glisser librement sur la piézocéramique pendant la formation de l'énergie hydraulique et de pouvoir compenser un alignement non concentrique de l'actuateur (P) et du piston de pression (DK). La possibilité de rotation libre à l'intérieur de la butée (WL) garantit en outre le fait que toute la surface de la partie supérieure de l'actuateur (P) repose en permanence sur le piston de pression (DK). Cette commande s'utilise dans des soupapes d'injection, des pompes, etc.
EP95940120A 1994-11-30 1995-11-30 Commande electro-hydraulique Expired - Lifetime EP0795081B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4442649 1994-11-30
DE4442649A DE4442649C2 (de) 1994-11-30 1994-11-30 Elektrohydraulischer Antrieb
PCT/DE1995/001702 WO1996017165A1 (fr) 1994-11-30 1995-11-30 Commande electro-hydraulique

Publications (2)

Publication Number Publication Date
EP0795081A1 true EP0795081A1 (fr) 1997-09-17
EP0795081B1 EP0795081B1 (fr) 1998-05-27

Family

ID=6534560

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95940120A Expired - Lifetime EP0795081B1 (fr) 1994-11-30 1995-11-30 Commande electro-hydraulique

Country Status (5)

Country Link
US (1) US5875632A (fr)
EP (1) EP0795081B1 (fr)
JP (1) JPH10509790A (fr)
DE (2) DE4442649C2 (fr)
WO (1) WO1996017165A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6345771B1 (en) 2000-06-30 2002-02-12 Siemens Automotive Corporation Multiple stack piezoelectric actuator for a fuel injector
US6400066B1 (en) 2000-06-30 2002-06-04 Siemens Automotive Corporation Electronic compensator for a piezoelectric actuator
US6499471B2 (en) 2001-06-01 2002-12-31 Siemens Automotive Corporation Hydraulic compensator for a piezoelectrical fuel injector

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19743669A1 (de) * 1997-10-02 1999-04-08 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE19818475C2 (de) * 1998-04-24 2001-05-31 Siemens Ag Fluiddichtungsanordnung und Verfahren zur Abdichtung
DE19821768C2 (de) * 1998-05-14 2000-09-07 Siemens Ag Dosiervorrichtung und Dosierverfahren
US6291928B1 (en) * 1998-12-16 2001-09-18 Active Control Experts, Inc. High bandwidth, large stroke actuator
DE19939487A1 (de) * 1999-08-20 2000-10-19 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE19950760A1 (de) † 1999-10-21 2001-04-26 Bosch Gmbh Robert Brennstoffeinspritzventil
DE10141135A1 (de) * 2001-02-22 2002-09-05 Continental Teves Ag & Co Ohg Ventil, insbesondere für hydraulische Kraftfahrzeug-Bremsanlagen
DE50206891D1 (de) 2001-02-22 2006-06-29 Continental Teves Ag & Co Ohg Ventil, insbesondere für hydraulische kraftfahrzeug-bremsanlagen
US6766965B2 (en) 2001-08-31 2004-07-27 Siemens Automotive Corporation Twin tube hydraulic compensator for a fuel injector
DE10148874C2 (de) * 2001-10-04 2003-12-24 Siemens Ag Düseneinrichtung, insbesondere zur Kraftstoffeinspritzung
DE10149286C2 (de) * 2001-10-05 2003-12-11 Siemens Ag Düseneinrichtung, insbesondere zur Kraftstoffeinspritzung
DE10248433B4 (de) * 2002-10-17 2015-01-15 Cummins Ltd. Vorrichtung zum Fördern von Medien, insbesondere Einspritzvorrichtung für Brennkraftmaschinen von Kraftfahrzeugen
JP4270294B2 (ja) * 2007-03-05 2009-05-27 株式会社デンソー 燃料噴射弁
US8683982B2 (en) 2010-08-10 2014-04-01 Great Plains Diesel Technologies, L.C. Programmable diesel fuel injector
DE102012213827A1 (de) 2012-08-03 2014-02-06 Röchling Automotive AG & Co. KG Entlüftungsbox für Aktuatoren
US9385300B2 (en) 2013-02-06 2016-07-05 Great Plains Diesel Technologies, L.C. Magnetostrictive actuator

Family Cites Families (6)

* 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
DE2711393A1 (de) * 1977-03-16 1978-09-21 Bosch Gmbh Robert Kraftstoffeinspritzduese
DE4005774A1 (de) * 1990-02-23 1991-08-29 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen
JPH04175533A (ja) * 1990-11-05 1992-06-23 Nissan Motor Co Ltd 圧電アクチュエータの変位拡大機構
DE4306073C1 (de) * 1993-02-26 1994-06-01 Siemens Ag Zumeßvorrichtung für Fluide
DE4406522C1 (de) * 1994-02-28 1995-07-13 Siemens Ag Elektrohydraulisches Antriebselement

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9617165A1 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6345771B1 (en) 2000-06-30 2002-02-12 Siemens Automotive Corporation Multiple stack piezoelectric actuator for a fuel injector
US6400066B1 (en) 2000-06-30 2002-06-04 Siemens Automotive Corporation Electronic compensator for a piezoelectric actuator
US6650032B2 (en) 2000-06-30 2003-11-18 Siemens Automotive Corporation Electronic compensator for a piezoelectric actuator
US6499471B2 (en) 2001-06-01 2002-12-31 Siemens Automotive Corporation Hydraulic compensator for a piezoelectrical fuel injector

Also Published As

Publication number Publication date
WO1996017165A1 (fr) 1996-06-06
US5875632A (en) 1999-03-02
DE59502365D1 (de) 1998-07-02
EP0795081B1 (fr) 1998-05-27
DE4442649C2 (de) 1996-10-24
JPH10509790A (ja) 1998-09-22
DE4442649A1 (de) 1996-07-18

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