EP1041252B1 - Soupape à commande électromagnétique - Google Patents

Soupape à commande électromagnétique Download PDF

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Publication number
EP1041252B1
EP1041252B1 EP00105716A EP00105716A EP1041252B1 EP 1041252 B1 EP1041252 B1 EP 1041252B1 EP 00105716 A EP00105716 A EP 00105716A EP 00105716 A EP00105716 A EP 00105716A EP 1041252 B1 EP1041252 B1 EP 1041252B1
Authority
EP
European Patent Office
Prior art keywords
valve
mass
spring
anchor
armature
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
EP00105716A
Other languages
German (de)
English (en)
Other versions
EP1041252A3 (fr
EP1041252A2 (fr
Inventor
Martin Dr.-Ing. Pischinger
Hans Dipl.-Ing. Kemper
Günter Rudolf Dipl.-Ing. Feyerl
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.)
FEV Europe GmbH
Original Assignee
FEV Motorentechnik GmbH and Co KG
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
Priority claimed from DE19938297A external-priority patent/DE19938297A1/de
Application filed by FEV Motorentechnik GmbH and Co KG filed Critical FEV Motorentechnik GmbH and Co KG
Priority to DE20023636U priority Critical patent/DE20023636U1/de
Publication of EP1041252A2 publication Critical patent/EP1041252A2/fr
Publication of EP1041252A3 publication Critical patent/EP1041252A3/fr
Application granted granted Critical
Publication of EP1041252B1 publication Critical patent/EP1041252B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/40—Methods of operation thereof; Control of valve actuation, e.g. duration or lift
    • F01L2009/4098—Methods of operation thereof; Control of valve actuation, e.g. duration or lift relating to gap between armature shaft and valve stem end

Definitions

  • An electromagnetically actuated gas exchange valve arrangement for a reciprocating internal combustion engine consists essentially of a valve body connected to a closing spring and a electromagnetic actuator, two electromagnets has, the pole faces aligned with each other and with Spaced apart, and the one between the pole faces movable back and forth guided anchor with guide pin having, at one end with the valve body and at the other end with a ⁇ ffnerfeder in connection, being between the guide pins and the valve body a valve clearance is present.
  • Such a gas exchange valve arrangement forms a vibratory Spring mass system, whose total mass is substantially through the anchor with its guide pins and is formed by the valve body and its "spring” through the NC and the closing spring is formed.
  • the order is usually made so that the two return springs are designed the same.
  • this gas exchange valve arrangement for reducing the necessary for the operation of electrical Energy the self-sustaining ability of this spring-mass system is exploited, so that in principle the respective catching and for the opening and closing time holding solenoid only must be energized so strong that the armature respectively when overshooting its central position from the magnetic field of the catching magnet is attracted, but otherwise the kinetic Energy of the total mass for a substantial part the movement is exploited.
  • valve clearance compensation systems are technically complicated to manufacture on the possibilities of fully variable electromagnetic Valve gear, it would be desirable to allow a valve clearance, about appropriate measures in the control of the current supply to avoid problems occurring during valve movement.
  • detection of the armature movement and / or the anchor speed in the first movement phase of importance, wherein the derivative of a signal directly via the detection of the respective anchor position and the anchor speed is advantageous.
  • the anchor mass is defined by the mass of the anchor plate even with the associated leadership Anchor bolt and the reduced mass of the opening spring and the mass of the opener spring associated spring pin.
  • the mass of the valve body is defined by the Mass of the valve body itself including valve spring plate as well as the reduced mass of the closing spring.
  • Another advantage of the embodiment of the invention consists in that on a so-called valve clearance compensation can be omitted, as by shortening the bounce and natural vibrations of armature and valve body during the opening movement and a reduction of the amplitudes the natural vibrations of the armature and the valve body the noise is also reduced.
  • the anchor mass also for a gas exchange valve assembly an electromagnetic actuator of the aforementioned Art provided that the two return springs different Have spring characteristics.
  • an electromagnetic Actuator 5 is provided, which consists essentially of a Opener magnet 7 and a closing magnet 6, whose Pole faces 8 against each other and spaced from each other are arranged.
  • an armature 9 guided back and forth, the one end is firmly connected to an anchor bolt 10 and the other end via a spring pin 11 on a ⁇ ffnerfeder 12 is supported.
  • Fig. 1 the overall arrangement is shown in the closed position, d. H. the armature 9 is located on the pole face of the closing magnet 6, so that the ⁇ ffnerfeder 12 compressed by a corresponding amount is.
  • the valve body 1 is through the Closing spring 3 held in the closed position.
  • a so-called valve clearance present, the in practice in the range of about 0.15 mm.
  • the valve clearance VS may be due to thermal influences, in particular Length change of the valve stem 2 at temperature increase and / or correspondingly rectified change in length of the electromagnetic actuator 5 bearing cylinder head change within certain limits during operation.
  • the energization of the closing magnet 6 is turned off, so that the armature 9 through the ⁇ ffnerfeder 12 in the direction of the gas exchange valve 1 is accelerated, here after overcoming the valve clearance VS impinges on the end of the valve stem 2 and the Advances valve body 1 in the opening direction.
  • the opening magnet 7, depending on the control in the course of the armature movement energized so that the armature overshoots over its central position in the influence of the developing magnetic field device and then against the force of the closing spring 3 comes to rest on the pole face 8 of the opening magnet 7.
  • the opening magnet 7 After expiration of the predetermined by the engine control holding time the opening magnet 7 is de-energized, so that the armature 9 can move back into the closed position, captured by the closing magnet and until the next opening process is held.
  • the closing spring 3 and the opening spring 12 form for the armature 5, the so-called return springs.
  • valve clearance compensation by the valve clearance VS by a corresponding hydraulic Coupling is bridged, there is practically a same direction movement of the armature 9 and the valve body. 1 each time the current is switched off at the holding magnet. However, if a valve clearance is present, then moves Opening operation of the anchor 9 with his from anchor bolt 10 and Spring bolt 11 formed guide bolt initially independently under the influence of the accelerating force of the opening spring 12, until the anchor bolt 10 on the free end of the valve stem 2 hits and then the anchor mass and mass the total mass of the valve body is further moved.
  • the mechanical system shown in Fig. 1 is now to be resolved as a vibration system in springs and masses. This resolution is shown in FIG.
  • the anchor mass m A * to be considered here is formed by the mass of the armature 9 with its anchor bolt 10 and by the mass of the spring bolt 11 and the so-called reduced mass of the opening spring 12.
  • the mass m A * is given by a corresponding mass point shown, while the opening spring 12 is symbolized by its spring constant C12 and the anchor bolt 10 is shown only as a massless component.
  • the oscillating valve mass m V * is shown as a mass point, whereby the mass of the valve body 1 and the reduced mass of the closing spring 3 including the valve plate 4 are also taken into account here.
  • the closing spring 3 is here indicated only schematically by its spring constant C3, while the valve stem 2 is reproduced here as a massless component.
  • the exciter force P acts on the anchor mass m A * .
  • the subsystem C3-m V * also performs its own movement, ie after the first acceleration (FIG. Position I), the mass m V * swings back by a small amount, but then again on renewed impingement of the armature mass m A * in the opening direction further driven (position II), as shown in the illustration. Fig. 3 can be seen.
  • Fig. 3 reveals that the overlapping intermittent oscillations of the two partial masses m A * and m V * continue far beyond the vertex. It should not be disregarded that the longitudinal elasticities of the anchor bolt 10 on the one hand and the valve stem 2 on the other hand play a role, so that in the selection of largely inelastic materials, at least for the valve stem, such as ceramic materials, which possibly also for the anchor bolt can be used, these bounce operations can be reduced.
  • the ratio m A * / m V * may only be changed so far with a view to increasing the armature mass, that for a given sensitivity Sensor technology and the impact time from the armature movement can still be detected, ie the mass ratio must be selectively changed so that even a detectable first rebound of the armature mass m A * takes place.
  • the modified electromagnetic actuator for actuation a gas exchange valve 2 is shown in FIG. 1 substantially again from a closing magnet 6 and a ⁇ ffnermagneten 7, which are arranged at a distance from each other and between which an armature 9 against the force of return springs, namely an opening spring 12 and a closing spring. 3 is guided back and forth movable.
  • the closing spring 3 acts directly via a connected to the shaft of the gas exchange valve 2 Spring plate 4 a.
  • the anchor bolt 10 of the electromagnetic Actuator is separated from the valve stem, in the Rule is here in the closed position a gap in the form of so-called valve clearance VS available.
  • the opening spring 12th in turn is supported on a spring plate 11.1 on the spring bolt 11, so that in the opening movement under the opposing Effect of NC spring 12 and closing spring 3 of the spring pin 11 on the shaft of the gas exchange valve supported.
  • the actuator is associated with a sensor 15, the detection allows the actuator functions.
  • the sensor 15 is here shown schematically. Depending on the design of the sensor For example, the path of the armature 5 can be detected, so that the respective armature position of the engine control 14th and / or the current controller 14.1 can be transmitted. In the Motor controller 14 or the current controller 14.1 can then over appropriate arithmetic operations possibly also the anchor speed be determined so that, depending on the anchor position and / or depending on the anchor speed the energization of the two electromagnets 6, 7 controlled can be.
  • the closing spring 3 “harder” designed, d. H. it has a higher spring characteristic than the opening spring 12.
  • the spring-mass system "detuned", so that due to the impact of the anchor mass after overcoming the valve clearance VS forming, the Opening movement overlapping vibrations during the Opening movement virtually completely degraded, as the system the possibility of oscillation in the natural frequency because of the different spring design is taken.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Electromagnets (AREA)
  • Magnetically Actuated Valves (AREA)

Claims (4)

  1. Dispositif de soupape alternative à gaz dans un moteur à combustion interne à pistons, avec un corps de soupape (1) relié à un ressort de fermeture (3) et avec un actionneur électromagnétique (5), qui comporte deux électroaimants (6, 7) dont les faces polaires (8) sont orientées l'une vers l'autre et sont disposées à distance l'une de l'autre et qui présente une armature (9) guidée de façon mobile en mouvement alternatif entre les faces polaires (8), avec des tiges de guidage (10, 11) qui sont reliées par une extrémité au corps de soupape (1) et par l'autre extrémité à un ressort d'ouverture (12), dans lequel on prévoit un jeu de soupape (VS) entre la tige de guidage (10) et le corps de soupape (1), et dans lequel la masse oscillante (mA*) de l'armature (5) vaut au moins le double de la masse oscillante (mV*) du corps de soupape (1).
  2. Dispositif de soupape alternative à gaz selon la revendication 1, caractérisé en ce que le ressort d'ouverture (12) et le ressort de fermeture (3) présentent les mêmes constantes de ressort et les mêmes masses.
  3. Dispositif de soupape alternative à gaz selon la revendication 1 ou 2, caractérisé en ce que la masse oscillante (mA*) de l'armature (5) n'est plus grande que la masse oscillante (mV*) du corps de soupape (1) que dans la mesure où, à l'ouverture de la soupape, le premier impact de la tige de guidage (10) sur le corps de soupape (1) ne peut encore être détecté que comme une chute de la vitesse.
  4. Dispositif de soupape alternative à gaz dans un moteur à combustion interne à pistons selon la revendication 1, caractérisé en ce que celui-ci comporte une soupape alternative à gaz (2) et deux électroaimants (6, 7) disposés à distance l'un de l'autre, entre lesquels une armature (9) est guidée de façon mobile en mouvement alternatif contre la force de deux ressorts de rappel (3, 12), dans lequel on prévoit un jeu de soupape (VS) entre la tige de guidage (10) et le corps de soupape (1), et dans lequel les deux ressorts de rappel (3, 12) présentent des constantes de ressort différentes.
EP00105716A 1999-03-31 2000-03-17 Soupape à commande électromagnétique Expired - Lifetime EP1041252B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE20023636U DE20023636U1 (de) 1999-03-31 2000-03-17 Gaswechselventilanordnung mit elektromagentischem Aktuator

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19914692 1999-03-31
DE19914692 1999-03-31
DE19938297 1999-08-12
DE19938297A DE19938297A1 (de) 1999-03-31 1999-08-12 Gaswechselventilanordnung mit elektromagnetischem Aktuator

Publications (3)

Publication Number Publication Date
EP1041252A2 EP1041252A2 (fr) 2000-10-04
EP1041252A3 EP1041252A3 (fr) 2002-08-14
EP1041252B1 true EP1041252B1 (fr) 2005-06-01

Family

ID=26052696

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00105716A Expired - Lifetime EP1041252B1 (fr) 1999-03-31 2000-03-17 Soupape à commande électromagnétique

Country Status (4)

Country Link
US (1) US6247432B1 (fr)
EP (1) EP1041252B1 (fr)
JP (1) JP2000310105A (fr)
AT (1) ATE296944T1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19951315A1 (de) * 1999-10-25 2001-04-26 Fev Motorentech Gmbh Verfahren zum Betrieb einer Kolbenbrennkraftmaschine bei zeitweiligem Funktionsausfall eines elektromagnetischen Ventiltriebs
IT1311131B1 (it) * 1999-11-05 2002-03-04 Magneti Marelli Spa Metodo per il controllo di attuatori elettromagnetici perl'azionamento di valvole di aspirazione e scarico in motori a
JP2002130518A (ja) * 2000-10-30 2002-05-09 Mikuni Corp 電磁アクチュエータによる開閉弁駆動装置
JP2002231530A (ja) * 2001-02-07 2002-08-16 Honda Motor Co Ltd 電磁アクチュエータ制御装置
DE10112999A1 (de) * 2001-03-17 2002-09-19 Bayerische Motoren Werke Ag Verfahren beim Abstellen einer Brennkraftmaschine mit elektromagnetisch betätigten Gaswechselventilen
DE10207658B4 (de) * 2002-02-22 2008-09-04 Meta Motoren- Und Energie-Technik Gmbh Verfahren zum Verkürzen der Öffnungs- und Schließflanke eines Ventils, sowie Ventil
US6820598B2 (en) * 2002-03-22 2004-11-23 Chrysalis Technologies Incorporated Capillary fuel injector with metering valve for an internal combustion engine
FR2842862B1 (fr) * 2002-07-25 2006-03-03 Procede de determination d'un jeu de distribution a partir d'un couple position/caracteristique electrique
US7165529B2 (en) * 2004-12-02 2007-01-23 Ford Global Technologies, Llc Method to control electromechanical valves in a DISI engine
DE102007037333A1 (de) * 2007-08-08 2009-02-26 Daimler Ag Betätigungsvorrichtung
FR2922941B1 (fr) * 2007-10-31 2014-05-02 Valeo Sys Controle Moteur Sas Procede de determination d'un jeu de distribution au moyen de l'acceleration
FI20145100L (fi) * 2014-01-30 2015-07-31 Ixtur Oy Magneetti
DK179123B1 (en) * 2016-09-16 2017-11-13 Danfoss As Valve attachment, valve and method for controlling a valve
SE542805C2 (sv) * 2018-07-31 2020-07-14 Hedman Ericsson Patent Ab Elektriskt aktiverad ventilaktuator för en internförbränningsmotor

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3513107A1 (de) * 1985-04-12 1986-10-16 Fleck, Andreas, 2000 Hamburg Elektromagnetisch arbeitende stelleinrichtung
DE3826978A1 (de) * 1988-08-09 1990-02-15 Meyer Hans Wilhelm Elektromagnetisch betaetigbare stellvorrichtung
DE19518056B4 (de) 1995-05-17 2005-04-07 Fev Motorentechnik Gmbh Einrichtung zur Steuerung der Ankerbewegung einer elektromagnetischen Schaltanordnung und Verfahren zur Ansteuerung
DE19529155B4 (de) * 1995-08-08 2007-05-24 Fev Motorentechnik Gmbh Verfahren zur Messung des Ventilspiels an einem durch einen elektromagnetischen Aktuator betätigten Gaswechselventil
DE19531437A1 (de) * 1995-08-26 1997-02-27 Fev Motorentech Gmbh & Co Kg Verfahren zur Erfassung des Ventilspiels an einem durch einen elektromagnetischen Aktuator betätigten Gaswechselventil
KR100248332B1 (ko) * 1995-12-23 2000-04-01 정몽규 차량의 흡/배기밸브용 개폐장치
DE29604946U1 (de) * 1996-03-16 1997-07-17 FEV Motorentechnik GmbH & Co. KG, 52078 Aachen Elektromagnetischer Aktuator für ein Gaswechselventil mit Ventilspielausgleich
DE19628860B4 (de) * 1996-07-17 2008-07-31 Bayerische Motoren Werke Aktiengesellschaft Elektromagnetische Betätigungsvorrichtung für ein Brennkraftmaschinen-Hubventil
DE29615396U1 (de) * 1996-09-04 1998-01-08 FEV Motorentechnik GmbH & Co. KG, 52078 Aachen Elektromagnetischer Aktuator mit Aufschlagdämpfung
JPH10205314A (ja) * 1996-12-13 1998-08-04 Fev Motorentechnik Gmbh & Co Kg ガス交換弁の電磁弁駆動部を制御する方法
JPH11148328A (ja) * 1997-11-12 1999-06-02 Fuji Heavy Ind Ltd 電磁駆動バルブの開閉時期検出装置
DE19801396C1 (de) * 1998-01-16 1999-03-04 Daimler Benz Ag Betätigungsvorrichtung für ein Gaswechselventil in einer Brennkraftmaschine

Also Published As

Publication number Publication date
EP1041252A3 (fr) 2002-08-14
EP1041252A2 (fr) 2000-10-04
US6247432B1 (en) 2001-06-19
JP2000310105A (ja) 2000-11-07
ATE296944T1 (de) 2005-06-15

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