EP0874139A2 - Commande de soupape d'un moteur à combustion interne - Google Patents

Commande de soupape d'un moteur à combustion interne Download PDF

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Publication number
EP0874139A2
EP0874139A2 EP98104376A EP98104376A EP0874139A2 EP 0874139 A2 EP0874139 A2 EP 0874139A2 EP 98104376 A EP98104376 A EP 98104376A EP 98104376 A EP98104376 A EP 98104376A EP 0874139 A2 EP0874139 A2 EP 0874139A2
Authority
EP
European Patent Office
Prior art keywords
cam
locking
valve train
valve
train 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
EP98104376A
Other languages
German (de)
English (en)
Other versions
EP0874139A3 (fr
EP0874139B1 (fr
Inventor
Dieter Kraxner
Joachim Grünberger
Dietmar Schwarzenthal
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.)
Dr Ing HCF Porsche AG
Original Assignee
Dr Ing HCF Porsche 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 Dr Ing HCF Porsche AG filed Critical Dr Ing HCF Porsche AG
Publication of EP0874139A2 publication Critical patent/EP0874139A2/fr
Publication of EP0874139A3 publication Critical patent/EP0874139A3/fr
Application granted granted Critical
Publication of EP0874139B1 publication Critical patent/EP0874139B1/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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction

Definitions

  • the invention relates to a valve train of an internal combustion engine according to the Genus of the main claim.
  • Such a valve train is described for example in EP 0 515 520 B1 and has a plunger made of two concentric cup elements, of which the inner abuts with its one end face on the valve stem of the gas exchange valve.
  • the tappet interacts with the cam of a camshaft, the three part cams with has different cam tracks.
  • the two outer cam tracks have the same stroke and act on the outer cup element.
  • the middle one Partial cam has a different stroke profile with a lower stroke height and acts on the inner cup element.
  • the two concentric cup elements can by hydraulic loading of a coupling element with each other coupled or independent in a second switching position of this coupling element be moved from each other.
  • the two are in the coupled switching position Cup elements connected to each other so that the stroke of the partial cam follow with a larger stroke. About the coupling element and the inner cup element this movement is transferred to the valve stem.
  • the two cup elements are independent of one another movable. In this switch position, the valve stem works with the middle part cam together with less stroke.
  • the outer plate element follows the lifting movement of the outer partial cams, but no connection to the inner cup element or to the valve stem. With these plungers, however, there is a possibility that Coupling element by hydraulic loading at any time from its current Switch position is adjustable.
  • the displacement of the coupling element is in generally only given if all the partial cams interact with the associated cup element are in their base circle phase, since only in this Switch position, the coupling element is freely movable.
  • the pressurization of the Coupling element takes place independently of it, so that under certain circumstances the time for a complete adjustment of the coupling element from a switching position in the others are not enough. Unwanted edge loads can then occur high wear occur. Under certain circumstances it can also happen that the Coupling element in the event of insufficient displacement due to the valve train acting forces is pushed back, so that the valve after a partial stroke beats back into the valve seat undamped, which is very annoying and causes additional wear.
  • a plunger for a switchable gas exchange valve which has a coupling element has, with which the associated gas exchange valve can be activated or deactivated.
  • This coupling element is longitudinally displaceable and has a bore in which in a Switch position of the valve stem can dip. In this switch position there is a Stroke movement of the tappet possible, but not transferred to the valve stem becomes. Moving the coupling element is only within defined Cam tracks possible.
  • the coupling element acts with a locking device together, which consists of a resilient locking tongue and an actuating pin. The resilient locking tongue engages in the coupling element in defined positions.
  • the stylus picks up a cam contour of the associated cam and transmits it on the locking element, wherein only in predetermined cam track areas Relief of the locking element and thus a displacement of the coupling element is possible.
  • the invention has for its object a valve train of an internal combustion engine to improve according to the genus of the main claim so that undefined Switching positions are avoided and it is ensured that the coupling element always be safely transferred from one of its end positions to the other end position can. This should at the same time cause undesirable component loads due to insufficient Wearing behavior can be avoided.
  • the cam track-dependent blocking or release of the coupling element can be advantageously be carried out so that a scanning element has a cam contour the camshaft scans and transmits to the locking element so that this locked in a first cam track area and in one releases second cam track area.
  • the locking element can for example an outer contour of the cam track or the cam area scan.
  • the locking of the coupling element can advantageously and without Additional components are made by the unlocking contour on the cam in the Sensing range of the locking element is arranged and the shape of an increase or recess.
  • the locking element can be particularly simple and inexpensive Be designed as a longitudinally movable locking pin that directly into the Locking contour engages on the coupling element.
  • the valve train shown in Fig. 1 a not shown Internal combustion engine has a cylindrical tappet 1 (cup tappet), which is coaxial is arranged to a switchable gas exchange valve 2 and by a cam 3rd a camshaft 4 is actuated.
  • the plunger 1 is in a bore 5 a Cylinder head 6 used and is supported on a compression spring 7 Valve spring plate 8 from.
  • the valve 2 gas exchange valve
  • the valve 2 includes one with a valve seat 9 of the cylinder head 6 cooperating valve plate 10 and a valve stem 11, on which the valve spring plate 8 is attached.
  • a valve spring 12 is arranged which the valve 2 in the holds closed position.
  • the plunger 1 has two concentric cup elements 13, 14, each with different cam areas (partial cams) 15 to 17 of cam 3 work together.
  • the two outer cam areas 15 and 17 are the same trained, i.e. they have the same lifting height and phase position.
  • This Cam regions 15 and 17 act with the outer of the two cup elements 13 together.
  • the central cam area 16 has compared to the two outer Cam areas 15 and 17 a lower lifting height and acts with the inner Cup element 14 together. This acts via one shown in more detail in FIG. 2 known hydraulic valve lash adjuster (HVA) 18 with the Valve stem 11 of the gas exchange valve 2 together.
  • HVA hydraulic valve lash adjuster
  • the outer cup element 13 has an approximately cup-shaped housing 19, the Bottom 20 facing the cam 3.
  • This floor 20 has a continuous Opening 21, which is on the inside of the bottom 20 by a peripheral edge 22nd is surrounded.
  • the bottom 20 is parallel to its outside 23 from a radial penetrated bore 24 which intersects the opening 21.
  • opening 21 is also cup-shaped housing 25 of the inner cup element 14 used. Its bottom 26 is the middle Cam area 16 facing. The bottom 26 is covered by a bore 27 penetrated, in the working position shown in Fig. 2 of the plunger 1 with the Bore 24 of the outer cup element 13 is aligned. From the area of bore 27 starting out is the outside of the housing 25 with two parallel flats 28, 29 provided, which extend to the end 30 of the housing facing away from the cam, so that only the area 31 above the bore is cylindrical over its entire circumference is trained. The flats 28, 29 are designed so that they are perpendicular to Axial position of the holes 24 and 27 run. Inside the housing 25 it is on known hydraulic valve lash adjuster 18 out. The floors 20 and 26 of the two cup elements are on their outer sides in the direction of the cam 3 barrel vaulted.
  • guide sleeves 32, 33 In the interior of the bore 27 are two opposite guide sleeves 32, 33 are used, the end faces 34 and 35 of which are flush with the flats 28, 29 to lock.
  • These guide sleeves 32 and 33 take a coupling element 36 in shape a cylindrical pin, the length of which is the distance between the two outside End faces 34, 35 of the guide sleeves corresponds.
  • the right guide sleeve 38 in FIG. 2 is approximately cup-shaped and dimensioned so that it protrudes into the opening 21 and its open end face 39 the end face 35 of the guide sleeve 33 abuts.
  • On the inside of the guide sleeve 38 one end of a compression spring 40 is supported, the opposite end of which a piston 41 guided inside the guide sleeve 38.
  • the face this piston 41 is located on the opposite end face of the coupling element 36 at.
  • the opposite guide sleeve 37 also projects into the opening 21 and borders with its end face 42 on the adjacent end face 34 of the guide sleeve 32.
  • the guide sleeve 37 is on its opposite end face by a cup-shaped insert 43 closed. Inside the guide sleeve 37, a piston 44 is guided in a longitudinally movable manner, the end face of which on the opposite end face of the coupling element 36. Through this Arrangement of the guide sleeves 37 and 38 and their interaction with the Flattenings 28, 29 is a rotation of the outer cup element 13 relative to inner cup element 14 prevented. At the same time, the guide sleeves 27 and 28 in conjunction with the area 31 of the housing 25 as a stop that the stroke of the outer cup element in the direction of cam 3 and relative to the inner one Cup element limited.
  • a bore opens into the guide sleeve 37, over the outside of the outer cup element 13 with a in the cylinder head 6th arranged controlled pressure line 45 is connected.
  • a pressure chamber 46 is formed inside guide sleeve 37, into which the pressure line 45 opens.
  • Pressure medium lubricating oil
  • the piston 44 are moved so that this the coupling element 36 and the piston 41 against the action of the compression spring 40 shifts.
  • a locking pin 48 is guided to move longitudinally, which is supported on the compression spring 7 via a disk 49.
  • the locking pin 48 is slidably guided but sealed in the bore 47. Its length is like this chosen to protrude above the top 23 of the outer cup element 13, provided the disc 49 under the action of the compression spring 7 on the inside of the Bottom 23 abuts. In the rotational position of the Camshaft 4 protrudes the locking pin 48 in a part of the Groove-shaped depression 50 extending around the circumference of the partial cam 15.
  • the locking pin 48 has two opposite in its central region Flattenings 51 and 52.
  • the piston 44 has the locking pin 48 in its facing end face an incision 53 which is arranged so that the piston 44th two opposite sections 54 and 55 with flat, parallel insides are trained. These sections 54 and 55 encompass the flats 51 and 52 with a small distance and thus prevent twisting of the locking pin 48.
  • the two sections 54 and 55 still have one on their underside from the free end face rounded section 56, which in a Parabolic incision 57 merges. In this parabolic Incisions 57 protrudes from a likewise parabolic elevation 58 lower end of the flats 51 and 52.
  • the movement of the piston 44 is dependent on the rotational position the camshaft 4 by the interaction of the piston 44, the Locking pin 48 and the recess 50 in the partial cam 15 prevented.
  • This Indentation 50 in the partial cam 15 extends in this exemplary embodiment from the transition of the base circle phase over the entire stroke phase of the partial cam.
  • the locking pin 48 can thus over the entire lifting phase and the respective Immerse the transition to the base circle phase in the recess 50.
  • the surface contour of the partial cam continuously changes, see above that the locking pin at the beginning of the base circle against the action of Compression spring 7 down and at the end of the base circle phase by the action of Compression spring 7 is pushed up.
  • the three partial cams are designed so that their base circles are the same Radius and at least over the major part of its circumference the same Have angular position.
  • the basic circle phase is the To understand the angle of rotation range of a cam in which its circumferential area with constant radius (base circle) so with the stroke transmission element (plunger) interacts that no valve lift is caused.
  • the stroke phase is still the To understand the angle of rotation range of a cam, in which its excessive range (Stroke range) cooperates with the stroke transmission element (plunger) in such a way that the gas exchange valve is actuated, i.e. that the valve disc lifts off the valve seat.
  • the piston 44 can only move as far to the right in the stroke phase of the camshaft are moved until the respective edges of the parabolic incisions 57 of the Piston 54 and the parabolic ridges 58 of the locking pin 48th blocking against each other.
  • the incisions 57 and the ridges 58 are like this dimensioned so that the piston 44 does not yet protrude into the bore 27, so that the inner and outer cup element continue to be free to each other in the axial direction are mobile.
  • the locking pin 48 is at the end of the recess 50 pressed against the action of the compression spring 7 so that the parabolic depressions 57 of the piston and the parabolic elevations 58 of the locking pin disengage.
  • the piston 44 is thereby released, i.e. it can move freely. If the pressure p in the pressure chamber 46 is high enough, the piston 44 is displaced to the right against the action of the compression spring 40, so that this protrudes into the bore 27 or the guide sleeve 32, while the Coupling element 36 projects into the guide sleeve 38. In this switching position the piston 44 and 41 and the coupling element 36 are the inner and the outer Cup element 13, 14 coupled together so that the inner cup element 14 the larger stroke of the outer cup element 13 follows and the gas exchange valve is operated with a larger stroke.
  • the second embodiment of the plunger shown in FIG. 4 differs from the above described essentially by the formation of the piston 44A and the locking element.
  • the lock piston 44A is in this Embodiment cylindrical and has a in its central region circumferential, annular recess 59 with a rounded cross section.
  • the Locking element is formed in two parts in this embodiment and consists of a locking pin 60 and a second locking part 61.
  • the Locking pin 60 is longitudinally movable in a bore 62 (shown in dashed lines) guided, which penetrates the bottom 20A of the outer cup member 13A.
  • the Bore 62 is offset from bore 24A so that it does not cuts.
  • the locking pin 60 lies - as in the previously described Embodiment - on the one hand on the partial cam 15 and on the other hand over the disc 49 on the compression spring 7.
  • the bottom 24A continues to be on the inside of it penetrated a bore 63 which extends into the interior of the guide sleeve 37A.
  • the second locking part 61 is guided. This is either as Locking ball or - as shown here - as a short cylindrical component with spherical end faces.
  • the second locking part 61 acts in Dependence on the switching position of the piston 44A - analogous to the previous one described embodiment - locking or releasing either with circumferential annular recess 59 or the end face 64 of the piston 44A together.
  • the piston 44A is in its right after the switching operation End position, the end face 64 acts with the second locking part 61 in this way together that pushing back into the first (left) switch position is only possible, provided the disc 49 against the action of the compression spring 7 from the locking pin 60th is pressed down and the second locking part 61 also down is moved. Otherwise, the end face 64 of the piston 44A presses against that in the Bore 63 and the guide sleeve 37A projecting end of the second locking part 61 so that shifting is prevented. A push back into the first Switch position is therefore also only possible in the base circle phase, provided that Locking pin 60 is pressed down by the partial cam 15 and not in the recess 50 of the partial cam protrudes.
  • This embodiment has the advantage that the pressure space on the piston 44A only is penetrated on one side by the bore 63, while the bore 62 den Pressure chamber does not cut. A leak from the pressure chamber towards This prevents the camshaft.
  • the one guided in the lower part of the bottom 20B and with the disc 49 and the compression spring 7 cooperating end 66 of the Locking pin 65 is formed with a larger diameter.
  • This end 66 larger diameter goes into a via a conical transition 67 Section 68 of smaller diameter across the outside of the bottom 20B penetrates and cooperates with the partial cam 15.
  • the piston 44B has in in its central area also an annular recess 69, the edges 70 and 71 are conical.
  • Piston 44B projects the free end of the locking pin 65 into that not shown Deepening of the partial cam 15, the conical transition 67 in the circumferential recess 69 protrudes.
  • the conical edge 70 on the conical transition 67 is in this switching position of the locking pin 65 prevents the piston 44B from moving. Only when when the Base circle phase of the locking pin 65 by the partial cam 15 against the Effect of the compression spring 7 is pressed down, the conical Recess 69 and the conical transition 67 out of engagement, so that a Moving the piston 44B is possible.
  • the piston 44C has a first, conical section 73 extending from the end face and adjoining it at a distance a circumferential annular recess 74 with conical edges 75 and 76 connects.
  • the locking pin 77 is again in this embodiment cylindrical and has on the circumferential side facing the piston 44C an incision 78 in which, depending on the switching position of the pistons 44C immersed.
  • the incision 78 has a hump-shaped extension on its lower side 79, in the switching position of the piston 44C shown in FIG. 6 in the rotating Grooves 74 engages. This hump 79 prevents - as in the previously described Embodiments - in cooperation with the annular recess 74 or the end face 73 of the piston 44C whose displacement during the stroke phase of the Partial cam 15.
  • the locking pin 82 in the exemplary embodiment according to FIG. 7 has a circumferential one Indentation 83, in which the piston 44D engages in the switching position shown.
  • the Locking due to the interaction between locking pin 82 and Piston 44D takes place in this exemplary embodiment and in that shown Switch position not by positive locking but by force locking.
  • FIGS. 8 and 9 differs from these in that they have a modified locking / unlocking contour on the partial cam 15 'and the cup elements 13', 14 '.
  • the bottoms of the two cup elements are not aligned on their side facing the respective partial cam.
  • the inner cup element 14 ' projects in the base circle phase of the cam in FIGS. 8 and 9 with respect to the outer cup element 13'. This position of the two cup elements is secured, for example, by the guide sleeves 37, 38 shown in FIG.
  • the base circle radius R G1 of the partial cam 15 ' is matched in a first section with respect to the direction of rotation to the protrusion of the inner cup element in such a way that the locking pin 90 is pressed downward and the movement of the piston (not shown in more detail) is released analogously to the previous embodiments.
  • the locking pin 90 replacement by any of the locking elements described above is also possible.
  • the base circle radius of the partial cam 15 ' is reduced (R G2 ), so that the locking pin can dip into the free space on the partial cam 15' and prevent the piston from being displaced.
  • a recess 91 is formed in the partial cam 15' in this transition area, into which the locking pin 91 can dip and lock the piston. After passing through this recess 91, the piston is locked by the position of the radial bores in the inner and outer cup element which is no longer in alignment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP98104376A 1997-04-25 1998-03-11 Commande de soupape d'un moteur à combustion interne Expired - Lifetime EP0874139B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19717537 1997-04-25
DE19717537A DE19717537C1 (de) 1997-04-25 1997-04-25 Ventiltrieb einer Brennkraftmaschine

Publications (3)

Publication Number Publication Date
EP0874139A2 true EP0874139A2 (fr) 1998-10-28
EP0874139A3 EP0874139A3 (fr) 1999-01-07
EP0874139B1 EP0874139B1 (fr) 2000-11-29

Family

ID=7827762

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98104376A Expired - Lifetime EP0874139B1 (fr) 1997-04-25 1998-03-11 Commande de soupape d'un moteur à combustion interne

Country Status (5)

Country Link
US (1) US5950583A (fr)
EP (1) EP0874139B1 (fr)
JP (1) JPH1113439A (fr)
KR (1) KR19980081752A (fr)
DE (2) DE19717537C1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8256394B2 (en) 2007-02-19 2012-09-04 Schaeffler Technologies AG & Co. KG Switchable cup tappet

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DE19642718A1 (de) * 1996-10-16 1998-04-23 Schaeffler Waelzlager Ohg Stößel für einen Ventiltrieb einer Brennkraftmaschine
DE19742777A1 (de) * 1997-09-27 1999-04-01 Schaeffler Waelzlager Ohg Stößel für einen Ventiltrieb einer Brennkraftmaschine
DE19837098A1 (de) * 1998-08-17 2000-02-24 Porsche Ag Verfahren zum Betrieb einer mehrzylindrigen Brennkraftmaschine und Ventiltrieb einer mehrzylindrigen Brennkraftmaschine
US6196176B1 (en) * 1998-12-15 2001-03-06 Ina Walzlager Schaeffler Ohg Switchable cam follower
DE19915532B4 (de) * 1999-04-07 2009-05-20 Schaeffler Kg Schaltbares Ventiltriebsglied
DE19957165A1 (de) * 1999-11-27 2001-06-07 Porsche Ag Ventilsteuerung für eine Brennkraftmaschine
US6457445B1 (en) * 2000-05-23 2002-10-01 Mitsubishi Denki Kabushiki Kaisha Valve lift control device
KR20030046963A (ko) * 2001-12-07 2003-06-18 현대자동차주식회사 실린더 휴지 엔진의 밸브태핏
EP1447547B1 (fr) * 2003-02-17 2006-04-19 Ford Global Technologies, LLC Moteur à combustion interne ayant un dispositif de variation de la course des soupapes
DE10360098B4 (de) * 2003-12-20 2015-03-12 Schaeffler Technologies AG & Co. KG Koppelmechanismus
EP1788202B1 (fr) * 2005-11-18 2009-03-25 Ford Global Technologies, LLC Moteur à combustion interne à système de levée de soupape variable et méthode de contrôle du changement d'une levée de soupape à l'autre
DE602005010718D1 (de) * 2005-11-18 2008-12-11 Ford Global Tech Llc Brennkraftmaschine mit variablem Ventilhub sowie Ventilsteuerung und Verfahren für eine solche Brennkraftmaschine
DE602005022322D1 (de) * 2005-11-18 2010-08-26 Ford Global Tech Llc Brennkraftmaschine mit einem Ventiltrieb mit variablem Ventilhub und Verfahren zur Steuerung des Ventilhubumschaltens
DE602006012952D1 (de) * 2006-06-28 2010-04-29 Ford Global Tech Llc Verbrennungsmotor mit variablem Ventilerhebungsprofilsystem und Verfahren zum Steuern der Ventilerhebungsprofilumstellung
TWI312830B (en) 2006-11-03 2009-08-01 Ind Tech Res Inst Variable valve actuation mechanism
KR100931041B1 (ko) * 2007-10-05 2009-12-10 현대자동차주식회사 태핏 장치
US8807101B2 (en) 2010-05-06 2014-08-19 Hyundai Motor Company Variable valve lift apparatus
KR101274237B1 (ko) * 2010-05-06 2013-06-11 현대자동차주식회사 가변 태핏 및 이를 포함한 가변 밸브 리프트 장치
KR101244845B1 (ko) * 2011-01-31 2013-03-19 (주)모토닉 엔진의 가변밸브 리프트 장치
WO2017079383A1 (fr) 2015-11-06 2017-05-11 Borgwarner Inc. Système d'actionnement de soupape offrant une levée de soupape variable et/ou un réglage de soupape variable
WO2019060131A1 (fr) * 2017-09-22 2019-03-28 Cummins Inc. Poussoir de commutation ou linguet à galet pour freinage à relâchement de compression
CN108506059B (zh) * 2018-03-05 2019-09-06 中国北方发动机研究所(天津) 一种机械式可变气门驱动装置
EP3814613A4 (fr) * 2018-06-29 2022-03-23 Jacobs Vehicle Systems, Inc. Systèmes d'actionnement de soupape de moteur avec composants de train de soupapes à mouvement perdu, comprenant des ponts de soupape de pliage dotés de broches de verrouillage

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Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0515520A1 (fr) 1990-02-16 1992-12-02 Lotus Group Plc Moyen de commande de soupape.
DE4405189A1 (de) 1994-02-18 1995-08-24 Porsche Ag Stößel für ein schaltbares Ventil einer Brennkraftmaschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8256394B2 (en) 2007-02-19 2012-09-04 Schaeffler Technologies AG & Co. KG Switchable cup tappet

Also Published As

Publication number Publication date
KR19980081752A (ko) 1998-11-25
US5950583A (en) 1999-09-14
DE59800352D1 (de) 2001-01-04
DE19717537C1 (de) 1998-12-24
EP0874139A3 (fr) 1999-01-07
JPH1113439A (ja) 1999-01-19
EP0874139B1 (fr) 2000-11-29

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