EP1367231B1 - Système de contrôle de levée de soupape pour moteurs à combustion interne de véhicules - Google Patents

Système de contrôle de levée de soupape pour moteurs à combustion interne de véhicules Download PDF

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Publication number
EP1367231B1
EP1367231B1 EP03009499A EP03009499A EP1367231B1 EP 1367231 B1 EP1367231 B1 EP 1367231B1 EP 03009499 A EP03009499 A EP 03009499A EP 03009499 A EP03009499 A EP 03009499A EP 1367231 B1 EP1367231 B1 EP 1367231B1
Authority
EP
European Patent Office
Prior art keywords
control
valve
valve lift
hydraulic medium
hollow piston
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
EP03009499A
Other languages
German (de)
English (en)
Other versions
EP1367231A1 (fr
Inventor
Dieter Maisch
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.)
Hilite Germany GmbH
Original Assignee
Hydraulik Ring 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 Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
Publication of EP1367231A1 publication Critical patent/EP1367231A1/fr
Application granted granted Critical
Publication of EP1367231B1 publication Critical patent/EP1367231B1/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
    • F01L13/0005—Deactivating valves
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/143—Tappets; Push rods for use with overhead camshafts
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • 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
    • F01L13/0031—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 by modification of tappet or pushrod length
    • 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
    • F01L13/0047—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 the movement of the valves resulting from the sum of the simultaneous actions of at least two cams, the cams being independently variable in phase in respect of each other

Definitions

  • the invention relates to a valve lift control for internal combustion engines of Motor vehicles according to the preamble of claim 1.
  • valve lift controls are valves of an internal combustion engine of Cars only so far open that for the respective power requirement of the engine, the corresponding amount of fuel in the combustion chamber is injected.
  • the control shaft acts on an actuating element in the form of a Levers acting on the valve stem. This mechanical control is susceptible to interference and does not allow precise adjustment of the valve lift.
  • EP-A-0 814 240 there is the Control device of two intermeshing reciprocating pistons, which together to limit a cavity to be connected to a hydraulic medium source.
  • the one hollow piston is axially immovable in the motor housing, however rotatably mounted about its axis.
  • staggered openings which can be closed by the inner hollow piston. He is with one arm of a two-armed rocker arm connected to the other Arm the shaft of an intake valve attacks.
  • the rocker arm is centered provided with a roller on which a cam of a camshaft is supported.
  • FR-A-2 724 975 It is also known (FR-A-2 724 975) for stroke control of an intake valve to steer a control unit at one end of a two-armed rocker arm.
  • the control unit can be vertical by a cam of a control shaft be moved to the pivot axis of the tilt bracket.
  • In a raised Position can be a standing under the pressure of a hydraulic medium Piston arranged in the control unit locking bolt partially against spring force in a housing-fixed locking opening move.
  • the control unit is thereby locked in an upper position in the housing, so that the camshaft on the tilt bracket of the intake valve over a larger Stroke can be adjusted.
  • the invention is based on the object, the generic Ventilhub tenuung form so that the valve in a structurally simple Can be set accurately and reliably.
  • the control device hydraulically operated.
  • the control device can easily with the necessary Hydraulic medium to be supplied.
  • the hub the valve can be adjusted easily and accurately.
  • FIG. 1 shows a cylinder head 1 of an internal combustion engine, in which, depending on the type of engine a different Number of combustion chambers and associated valves 2 is provided is.
  • a valve plate 3 has, closed with the one inlet opening 4 in the combustion chamber can be.
  • the valve plate 3 is seated at the end of a valve stem 5, against the force of at least one compression spring 6 in a Open position can be moved.
  • the valve stem 5 indicates his the valve plate 3 opposite end of a spring plate 7, on which one end of the compression spring 6 is supported. you the other end is supported on the cylinder head side.
  • valve plate 3 This will be the Valve plate 3 by the compression spring 6 in his in Fig. 1 shown Closed position pulled.
  • the projecting beyond the spring plate 7 end 8 the valve stem 5 is formed dome-shaped and lies in one pan-like receptacle 9 at the free end of an arm 10 of a He is being transposed to his two-armed rocker arm Swivel axis in a fork 12 position secured, the cylinder head 1 is provided.
  • the other arm 13 of the rocker arm 11 is located on a Adjusting cylinder 14, which in a bore 15 in the cylinder head. 1 is slidably mounted.
  • the actuating cylinder 14 takes a hollow piston 16, which bears against a cam 17 of a control shaft 18.
  • the hollow piston 16 receives at least one compression spring 19, which is with one end to a bottom 20 of the hollow piston 16 and with her other end on a bottom 21 of the adjusting cylinder 14 is supported.
  • the hollow piston 16 is always loaded by the compression spring 19 so that he with his bottom 20 on a cam 22 of the cam 17 of the Control shaft 18 is present.
  • the hollow piston 16 is sealed in the actuating cylinder 14 slidably guided. Since the hollow piston 16, the compression spring 19 receives, results in a very compact design.
  • the part 16 also be solid. Then, because of the compression spring 19, the between the end face of the part 16 and the bottom 21 of the adjusting cylinder 14 is given a greater length of the control device.
  • the actuating cylinder 14 is over part of its length by an annulus Surrounded 23, which is provided in the cylinder head 1 and in the a bore 24 opens.
  • the annular space 23 is replaced by a in Diameter extended portion of the bore 15 formed.
  • the actuating cylinder 14 has a small distance from its bottom 21 arranged in its cylinder wall 25 distributed over the circumference Passageways 26, preferably bores, over which the annulus 23 is connected to the interior 27 of the adjusting cylinder 14.
  • the two ends of the lever arms 10, 13 are in the direction of the Valve stem 5 and the actuating cylinder 14 angled.
  • On the other Side of the rocker arm 11 is provided with an increase 28, which is extends over most of the length of the rocker arm 11 and at a camshaft 29 abuts. With her, the rocker arm 11 in pivoted yet to be described manner to open the valve 2.
  • the rocker arm 11 is not fixed, but lies with the ends his arms 10, 13 on the valve stem 5 and the adjusting cylinder 14 at.
  • Fig. 1 shows the initial position of the valve lift control, in a Cam 30 of the camshaft 29 is not engaged with the rocker arm 11 is.
  • the control shaft 18 is rotated to a position in which a touch area 31 between the cam 22 and the bottom 20 of the Hollow piston 16 the largest distance to the axis 32 of the control shaft 18 has.
  • the valve 2 is closed.
  • the hollow piston 16 is spaced from the bottom 21 of the actuating cylinder 14, whose Holes 26, the annular space 23 with the interior 27 of the actuating cylinder 14 and with the interior 33 of the hollow piston 16 connect.
  • Fig. 4 shows the maximum valve lift. He is reached when the Camshaft 29 is rotated so far that the cam 30 in the direction of the rocker arm 11 protrudes furthest. In this position (FIG. 4) the rocker arm 11 is pivoted furthest counterclockwise, so that the valve stem 5 is moved furthest. The valve 2 has thus executed the largest stroke. The valve plate 3 is farthest from his valve seat.
  • the force of the compression spring 19 in the actuating cylinder 14 is significantly smaller than the force of the compression spring 6, with which the valve 2 is loaded.
  • the Force of the compression spring 19 is in any case so large that a safe Applying the adjusting cylinder 14 and the hollow piston 16 am Rocker arm 11 and the control cam 22 of the control shaft 18 ensures is.
  • the running clearance between the hollow piston 16 and the actuating cylinder 14th is so low that a sealing function is present.
  • the hydraulic medium therefore does not escape to the outside, so that leakage losses avoided or only negligibly small.
  • a lever 11 with the corresponding valve lift control provided on the control shaft
  • 18 can have several or just one tax path 22 lie.
  • valve lift can be changed. Of the Valve lift can be adjusted so that in the respective combustion chamber only as much fuel is injected as for the current one Power of the internal combustion engine is needed.
  • FIGS. 5 and 6 show the case that the hollow piston 16 from the axis 32 of the control shaft 18 the has the smallest distance.
  • the control shaft 18 is for this purpose from the position As shown in FIGS. 1 to 4 has been rotated clockwise until the Control shaft 5 has reached the position shown in FIGS. 5 and 6.
  • the Hollow piston 16 is located with its bottom 20 under the force of the compression spring 19 on the control cam 22 of the cam 17 of the control shaft 18 at.
  • the hollow piston 16 is pushed out so far from the adjusting cylinder 14, that the end face 35 of the hollow piston 16 in the area below the holes 26 in the cylinder wall 25 of the adjusting cylinder 14th lies.
  • the inner spaces 27, 33 of the adjusting cylinder 14 and the hollow piston 16 are thus connected to the annular space 23 and the bore 24.
  • the actuating cylinder 14 and the hollow piston 16 act in the described manner as a fixed bearing for the rocker arm 11. Due the large displacement of the actuating cylinder 14 is the rocker arm 11 in the clockwise direction very far. As a consequence, that by turning the camshaft 29, the valve 2 is not opened becomes. As shown in FIG. 6, the cam 30 of the camshaft 29 takes its maximum stroke position, without the rocker arm 11 is pivoted so is that the valve 2 is opened. By means of the control shaft 18 can Thus, a zero stroke of the valve 2 can be achieved.
  • Fig. 7 shows that the position of the camshaft 29 and control shaft 18th can be reversed.
  • the hollow piston 16 is located on the increase 28 of the rocker arm 11 under the force of the compression spring 19. With the bent end of his arm 13 of the rocker arm 11 is located on the camshaft 29 at.
  • the actuating cylinder 14 is located on the control cam 22 of the cam 17 of the Control shaft 18 on. It is rotated so that the actuating cylinder 14 the smallest distance from the axis 32 of the control shaft 18 has.
  • the End face 35 of the hollow piston 16 is spaced from the holes 26 in the cylinder wall 25 of the adjusting cylinder 14.
  • the holes 26, which closely adjacent to the previous embodiment are provided to the bottom of the adjusting cylinder 14, thus not closed by the hollow piston 16.
  • the hydraulic medium can from the bore 24 into the annular space 23 and from there via the holes 26 in the interiors 27 and 33 of the adjusting cylinder 14th and the hollow piston 16 arrive.
  • This position of the hollow piston 16 is corresponding to the previous Embodiment already achieved when the cam 30 of the Camshaft 29 is not yet in its maximum Verstellage, in which the cam 30, based on the position shown in FIG. 7, is located on the diametrically opposite side of the camshaft 29.
  • the rocker arm 11 during further rotation of the camshaft 29 tilted counterclockwise, causing the valve stem 5 displaced against the force of the compression spring 6 and thus the valve 2 is opened.
  • valve 2 closes again, by the valve stem 5 via the spring plate 7 of the compression spring 6 is pushed back.
  • the rocker arm 11 is in this case in a clockwise direction tilted.
  • the Cam 30 of the camshaft 29 again in such a position that the Compression spring 19 the hollow piston 16 pushes back while the rocker arm 11 leads back to the starting position according to FIG. 7.
  • the holes 26 releases in the actuating cylinder 14, the Hydraulic medium sucked from the bore 24.
  • the control shaft 18 turned. Depending on the rotational position of the control shaft 18 and its cam 17, the stroke of the valve 2 is variably changed. This will achieve that the fuel only in such an amount in the combustion chamber of the internal combustion engine is sprayed, as for the respective Power of the internal combustion engine is necessary.
  • the hydraulic medium used for the operation of the control device 14, 16 is necessary, can also be in a preloaded memory are located. Are the hollow piston 16, the holes 26 in the actuating cylinder 14 free, the hydraulic medium from the preloaded memory. sucked. Conversely, the hydraulic medium can shrink when zooming of the interior 27, 33 of the control device 14, 16 in the memory be displaced.
  • the circuit of the hydraulic medium with the preloaded memory can be self-contained. But it is also possible, the preloaded memory via a check valve with the engine oil circuit to connect and feed about him. This will in particular achieved a leakage compensation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (11)

  1. Commande de soupape pour des moteurs à combustion interne de véhicule automobile, comprenant au moins un moyen de commande (14, 16) prévu pour le réglage de la course de soupape (2) et avec lequel coopèrent au moins un arbre à cames (29) et au moins une partie de commande (18), ledit moyen de commande (14, 16) pouvant être actionné par un fluide hydraulique et comprenant deux éléments de commande (14 et 16) déplaçables l'un par rapport à l'autre à l'encontre de la force d'au moins un élément à ressort (19), parmi lesquels un élément de commande (14) est réalisé en forme de douille qui reçoit l'autre élément de commande (16) qui est réalisé sous forme de piston creux, et les deux éléments de commande (14 et 16) délimitent une cavité commune (27, 33) susceptible d'être reliée à une source de fluide hydraulique et dans laquelle se trouve du fluide hydraulique, et dans laquelle un premier des éléments de commande (14) comprend au moins une liaison (26) via laquelle le fluide hydraulique peut parvenir dans la cavité (27, 33) et en sortir, et qui peut être obturée par l'autre élément de commande (16), ledit premier élément de commande (14) étant soutenu sur un levier basculant (11), de préférence à deux bras, qui agit sur une tige (5) de la soupape (2), et l'autre élément de commande (16) coopérant avec la partie de commande (18),
    caractérisée en ce que la partie de commande (18) est un arbre de commande avec une came (17), tel que l'autre élément de commande (16) s'applique en permanence par son fond contre la courbe de commande (22) de ladite came sous la force de l'élément à ressort (17).
  2. Commande de soupape, en particulier selon la revendication 1,
    caractérisée en ce que le levier basculant (11) est monté en flottement.
  3. Commande de soupape selon l'une ou l'autre des revendications 1 et 2, caractérisée en ce que ledit premier élément de commande (14) attaque l'un des bras de levier (13), et la tige de soupape (5) attaque l'autre bras de levier (10) du levier basculant (11).
  4. Commande de soupape selon la revendication 3, caractérisée en ce que la tige de soupape (5) s'engage, par une extrémité (8) en forme de calotte, dans un logement (9) en forme de coupelle d'articulation du levier basculant (11).
  5. Commande de soupape selon l'une des revendications 1 à 4,
    caractérisée en ce que l'arbre à cames (29) attaque le levier basculant (11) approximativement à la moitié de sa longueur.
  6. Commande de soupape selon l'une des revendications 1, 2 est 4,
    caractérisée en ce que l'arbre à cames (29) attaque l'un des bras de levier (13) du levier basculant (11) et l'autre élément de commande (16) approximativement à la moitié de sa longueur.
  7. Commande de soupape selon l'une des revendications 1 à 6,
    caractérisée en ce que le moyen de commande (14, 16) forme un palier fixe pour le levier basculant (11) lorsque de la liaison (26) du premier élément de commande (14) est obturée.
  8. Commande de soupape selon l'une des revendications 1 à 7,
    caractérisée en ce que les deux éléments de commande (14, 16) sont déplaçables l'un par rapport à l'autre par l'arbre à cames (29).
  9. Commande de soupape selon l'une des revendications 1 à 8,
    caractérisée en ce que la force du ressort (19) des deux éléments de commande (14, 16) est inférieure à la force d'un ressort (6) qui charge la soupape (2) dans la direction de fermeture.
  10. Commande de soupape selon l'une des revendications 1 à 9,
    caractérisée en ce que le fluide hydraulique peut être prélevé du circuit d'huile du moteur.
  11. Commande de soupape selon l'une des revendications 11 10,
    caractérisée en ce que le fluide hydraulique peut être prélevé d'un accumulateur, qui se trouve avantageusement dans un propre circuit hydraulique et est de préférence raccordé au circuit d'huile du moteur par une soupape antiretour, et qui est alimenté par le circuit d'huile du moteur.
EP03009499A 2002-05-10 2003-04-28 Système de contrôle de levée de soupape pour moteurs à combustion interne de véhicules Expired - Lifetime EP1367231B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10220692 2002-05-10
DE10220692A DE10220692A1 (de) 2002-05-10 2002-05-10 Ventilhubsteuerung für Verbrennungsmotoren von Kraftfahrzeugen

Publications (2)

Publication Number Publication Date
EP1367231A1 EP1367231A1 (fr) 2003-12-03
EP1367231B1 true EP1367231B1 (fr) 2005-04-20

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EP03009499A Expired - Lifetime EP1367231B1 (fr) 2002-05-10 2003-04-28 Système de contrôle de levée de soupape pour moteurs à combustion interne de véhicules

Country Status (4)

Country Link
US (1) US6779497B2 (fr)
EP (1) EP1367231B1 (fr)
DE (2) DE10220692A1 (fr)
ES (1) ES2242120T3 (fr)

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US7012315B1 (en) * 2000-11-01 2006-03-14 Micron Technology, Inc. Frame scale package using contact lines through the elements
US7401584B2 (en) * 2004-07-01 2008-07-22 Schaeffler Kg Adjustable engine
DE102004060433A1 (de) * 2004-12-14 2006-07-06 Daimlerchrysler Ag Nockenfolger zur Betätigung eines Gaswechselventiles einer Brennkraftmaschine
DE102006007121A1 (de) * 2006-02-16 2007-08-23 Daimlerchrysler Ag Gaswechselventilbetätigungsvorrichtung
CN101225759B (zh) * 2008-01-25 2010-06-09 许小法 可变气门升程装置
CN102979589B (zh) * 2011-09-06 2015-05-20 北汽福田汽车股份有限公司 发动机配气机构、发动机及汽车
DE102011114588A1 (de) * 2011-09-30 2013-04-04 Thyssenkrupp Presta Teccenter Ag Ventiltrieb für Brennkraftmaschinen mit verstellbarer Nockenwelle
JP6036757B2 (ja) * 2014-07-16 2016-11-30 トヨタ自動車株式会社 内燃機関の可変動弁機構
EP3000996B1 (fr) * 2014-09-23 2017-05-10 FPT Motorenforschung AG Ensemble de commande auxiliaire destinée à commander l'ouverture/la fermeture des soupapes principales d'un moteur à combustion interne, en particulier pour une opération de freinage d'un moteur de décompression
CN110374707A (zh) * 2019-06-19 2019-10-25 浙江吉利控股集团有限公司 一种连续可变升程装置、发动机及汽车

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DE2825316A1 (de) * 1978-06-09 1979-12-20 Maschf Augsburg Nuernberg Ag Regelbare hydraulische ventilsteuerung fuer hubkolbenkraft- oder arbeitsmaschinen
JPS59201911A (ja) * 1983-04-28 1984-11-15 Mazda Motor Corp エンジンの弁不作動装置
JPS60116809A (ja) * 1983-11-25 1985-06-24 Mazda Motor Corp エンジンの弁不作動装置
JP2750800B2 (ja) * 1992-12-24 1998-05-13 株式会社ユニシアジェックス 内燃機関の吸気弁制御装置
FR2724975B1 (fr) * 1994-09-27 1996-12-20 Peugeot Dispositif pour l'actionnement d'au moins une soupape de moteur a combustion interne
US5570665A (en) * 1995-04-04 1996-11-05 Chrysler Corporation Valve train for internal combustion engine
US5829397A (en) * 1995-08-08 1998-11-03 Diesel Engine Retarders, Inc. System and method for controlling the amount of lost motion between an engine valve and a valve actuation means
GB9612178D0 (en) * 1996-06-11 1996-08-14 Ricardo Consulating Engineers Hydraulic tappets
US6293237B1 (en) * 1997-12-11 2001-09-25 Diesel Engine Retarders, Inc. Variable lost motion valve actuator and method

Also Published As

Publication number Publication date
EP1367231A1 (fr) 2003-12-03
ES2242120T3 (es) 2005-11-01
DE50300451D1 (de) 2005-05-25
DE10220692A1 (de) 2003-11-20
US20030209215A1 (en) 2003-11-13
US6779497B2 (en) 2004-08-24

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