EP1794468A1 - Roue libre a liaison de forme - Google Patents

Roue libre a liaison de forme

Info

Publication number
EP1794468A1
EP1794468A1 EP05737016A EP05737016A EP1794468A1 EP 1794468 A1 EP1794468 A1 EP 1794468A1 EP 05737016 A EP05737016 A EP 05737016A EP 05737016 A EP05737016 A EP 05737016A EP 1794468 A1 EP1794468 A1 EP 1794468A1
Authority
EP
European Patent Office
Prior art keywords
elements
coupling
fitting
freewheel according
coupling elements
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.)
Withdrawn
Application number
EP05737016A
Other languages
German (de)
English (en)
Inventor
Herwig Fischer
Thomas Müller
Jens Gebhardt
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.)
Satellite Gear Systems Ltd
Original Assignee
Satellite Gear Systems Ltd
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 Satellite Gear Systems Ltd filed Critical Satellite Gear Systems Ltd
Publication of EP1794468A1 publication Critical patent/EP1794468A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F16D43/16—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members with clutching members having interengaging parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/12—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F16D2043/145—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members the centrifugal masses being pivoting

Definitions

  • the invention relates to a positive freewheel with a connected to a first shaft hollow or gear, transmitted to the locking state under positive engagement coupling elements torque in one direction, and the coupling elements in the opposite direction in a freewheeling state, each coupling element formed as a circulating element and also is mounted pivotably about a rotation axis.
  • a freewheel Under a freewheel is understood to be a directional clutch in which the switching operation depends on the direction of relative rotational movement between a drive member and a driven member. This is prevented in one direction of the relative rotation (blocking state), not in the other direction (free-wheeling state).
  • Freewheels are built to different applications, so lock as:lauf ⁇ , z. B. in conveyor belts, fans and automotive transmissions, Matterholkupplun ⁇ conditions in starter drives, bicycle hubs.
  • torque transmission In one-way clutches, torque transmission is effected by pawls, clamping bodies or balls.
  • the Klemmkör ⁇ per- or clamping roller freewheels are among the so-called non-positive Frei ⁇ runs, which are characterized by a high switching accuracy, since they can lock in each Stel ⁇ ment.
  • DE 199 53 643 A1 proposes a form-locking free-running clutch of the type mentioned in the introduction.
  • a continuously variable transmission which has an annular disc with a peripheral groove and positive locking elements, which are preferably designed as an annular tooth profile.
  • coupling elements are guided which have positive-locking elements which are designed to be complementary to the form-locking elements of the annular disk.
  • the coupling elements pass through an applied torque transmitting load arc, which extends over a partial arc, and a blank sheet.
  • the clamping elements are engaged, ie between the interlocking elements of the annular disc and the corresponding currentlysenten ⁇ th interlocking elements of the clamping body is a Form gleicheingriff herge ⁇ by the coupling elements perform a pivoting about an endogenous axis, preferably parallel to the axes of rotation of the annular disc and the star wheel of the transmission is stationary.
  • This form-fitting engagement is maintained in the load arc.
  • KiemmSystem In the transition from the load arc in the blank sheet KiemmSystem be swung back, whereby the form-fitting engagement is released again.
  • Each coupling element has an axially projecting, in one of vor ⁇ seen radial guides of Stemscale movable transmission pin over which the voltage applied when passing through the load arc force is transmitted to the star wheel.
  • This freewheel is according to the invention characterized in that the coupling elements when a limit speed is exceeded, either by centrifugal force against a Anfederungskraft or due to a frictional force undergoes a arranged in each coupling element pin in a sliding movement along a ring track or a rolling bearing in a rolling motion on an annular surface, are released from the locked state.
  • the clutch elements are held in engagement via the spring suspension, so that torque transmission occurs in one direction at low speeds below the limit speed. As soon as a limiting speed is exceeded, the clutch elements are lifted out of the clutch engagement with centrifugal force, so that they can overtake noiselessly and wear-free without contact with the positive-locking contours of the hollow or gear wheel.
  • a Jacob ⁇ contour may be provided in the sense of a stop surface on which the Kupplungsele ⁇ elements abut in centrifugal force due to overtaking.
  • a contact pin may be arranged, which is slidably guided along a circular path and thereby experiences a frictional force, which is utilized for locking and unlocking.
  • This frictional force generates a circumferential force whose sign changes depending on the direction of rotation of the freewheel and which together with the force of the torque-transmitting pin forms a pair of forces with which the desired locking torque can be generated.
  • a switching of a coupling element from an unlocked to a locked position can also be generated by using cylindrical, spherical or tapered rolling elements of a rolling bearing, in which the coupling elements are subjected to an increased frictional force relative to the respective rolling elements, so that the rolling elements during a rotation, the relevant Kupplungsele ⁇ ment moved into the respective switching position.
  • Due to the relatively small Ahmed ⁇ diameter of the rolling elements to the diameter of the (rolling bearing) annular surface can be achieve high rolling body rotation speeds and thus fast locking or unlocking of the coupling elements in the ring gear.
  • the coupling element can be designed as one-toothed or multi-toothed.
  • the rolling bearing may have an inner and an outer bearing ring, between which the rolling elements are inserted.
  • the rolling elements are rotated in a direction in which the rotating co-moving coupling elements occupy the freewheeling position.
  • the rolling elements are offset at the ends in a cylindrical or conical manner and roll on the offset surfaces in the bores of a carrier ring.
  • the rolling elements also run on an annular surface of a Zahnrin ⁇ ges. If the rolling elements make a rotary movement, the clamping elements are pivoted about the same angle of rotation and engage with their toothing in a complementary toothing of the toothed ring, wherein the torque is transmitted via the clamping elements in the toothed ring.
  • the reliability of the freewheel depends on whether the rolling elements are carried by the relevant ring surface without slippage.
  • a Lagervorspan ⁇ tion is preferably set or provided a radial springing, in which the rolling elements are pressed with a spring element to the annular surface of the bearing.
  • This spring element can be, for example, a leaf spring in a bearing cage or in the carrier ring.
  • a higher friction of the rolling bearing can also by a provided with Koch ⁇ elastic covering of the rolling body, z. B. in the form of a rubber ges in a groove in the rolling body or by using a traction fluid can be generated.
  • An optimization of the switching operation between the rolling element and the Klemm ⁇ body can be achieved if by means of a resilient element of the rolling elements in a bore or a surface is held against the clamping body or if a non-positive locking element is used as a rolling element in the clamping element.
  • any forms of hydraulic brakes or silicone brakes are possible.
  • the slidably guided contact pins are spring-loaded in a recess or bore of the coupling elements, in particular in a zwe ⁇ arrangement.
  • the projecting free end or the protruding free ends of the contact pins slide along a surface of a disc, which is connected to the first shaft or the hollow or gear.
  • the pins pass through the coupling elements in their center of gravity.
  • the contact pins project through radial slots of an annular disc, which bears frictionally upon locking with a contact surface on a movably guided contact disc when locking, so that these contact disc rotational movements on the annular disc and thereby over the contact pins on the clamping elements transfers.
  • slip and surface pressure are significantly minimized, increases the Triboverschlauervolumina, and thus increases the wear resistance, since the contact discs can move on a smaller radius.
  • all clamping elements are simultaneously moved synchronously via a single contact disk.
  • the coupling elements are arranged in pocket-shaped Ausneh ⁇ regulations with a ramp surface and a stop surface and slide or lock directional in the manner of a sprag freewheel or Klemm ⁇ roller freewheel.
  • the geometry of the form-fitting contours of the coupling elements as well as the hollow or gear is formed so that the clutch engagement within predetermined limits even above the limit speed - with identical direction of the torque closing and the Kupp ⁇ ment direction - is maintained.
  • a positive locking geometry is selected in which an applied positive torque keeps the coupling elements against locking centrifugal forces in engagement.
  • the freewheel according to the invention thus always switches to freewheeling operation as soon as torque reversal takes place, it automatically remains out of contact as soon as a limit speed is exceeded, wherein the clutch elements have been disengaged by means of a single clutch interruption and only engaged again be after a lower limit speed has been exceeded.
  • the coupling elements are preferably arranged within a guide contour, by means of which the swivel angle is limited to a minimum, the swivel angle ensuring reliable detachment from the clutch engagement in overrunning mode, on the other hand a further additional pivoting of the coupling elements the guide contour or corresponding stop surfaces for the coupling elements is prevented.
  • additional contours or components are provided, through which, after exceeding a certain overtaking angle, the coupling elements are pressed over a dead center into the unlocked position, in which they continue to rest automatically by centrifugal force action.
  • additional additional components such as bistable springs, ball snaps or the like, can be provided, with which the coupling elements are held in the locked and / or unlocked position via a dead center, so that a rapid movement into the respective End position is achieved instead of a slow transition movement, a hysteresis between the input and Ausriegelfitiere is achieved and also a further control variable for tuning the freewheel parameters is created.
  • the coupling elements have according to a further embodiment at least two, preferably more than five teeth.
  • elastically formed coupling elements can serve according to the invention to cushion a shock or impact movement during engagement.
  • each coupling element has a control tooth, which by its arrangement on the coupling element when Ein ⁇ locking the other teeth of the coupling element leads and by its elastic cal education, by a springing or by an external Synchronsteue ⁇ tion alignment Internal toothing causes the hollow disc.
  • the control tooth made of an elastic material and / or is spring gela ⁇ siege.
  • the control tooth may be formed as a leaf spring. The control tooth ensures that any displacements of the tooth profile of the coupling element relative to the tooth profile of the hollow disc are balanced out from the ideal position relative to each other before the tooth profiles engage in a locking manner. This prevents tilting (and high differential speeds, which arise due to delayed unlocking operations) and associated increased tooth wear.
  • control tooth is arranged in the direction of rotation of the coupling element relative to the hollow disc in the non-locking state viewed in front of the pivot point of the coupling element.
  • the freewheel is arranged in a drive train between a starter and an internal combustion engine of a motor vehicle, the clutch elements being arranged on a driven pulley connected to the crankshaft.
  • the pivotable coupling elements When the engine is stopped, the pivotable coupling elements are brought by a spring in the locking clutch engagement. In a starter operation, the coupling elements transmit the torque to the crankshaft. Even if the lower limit speed is exceeded, the clutch elements remain engaged as long as the engine has not yet started, since the interlocking geometry, ie. H. the toothing presses the coupling elements against the centrifugal forces due to the torque direction into the tooth base.
  • the freewheel torsionally elastic components are integrated, which in a very short-term torque reversal, z. B.
  • a stutter start of the engine to prevent an unlocking of the coupling elements by the Drehmomentum ⁇ traffic is elastically cushioned. Only when two conditions are simultaneously fulfilled continuously, namely, that the engine is running and the lower limit speed is exceeded, are the clutch elements released due to centrifugal forces or frictional forces, so that a completely contactless and therefore noiseless overtake operation is possible.
  • motion-damping components can be provided which slow down the Ausriegelvorgang so far that short-term torque changes, as z. B.
  • the angle of rotation which the first and the further shaft sweep out of the coupling engagement when releasing is preferably chosen to be no greater than the angle which results from the pitch of the gearwheel or ring gear, wherein the shifting accuracy of the free-running only depends on the division of the gearing depends.
  • the freewheel can also be designed according to a further embodiment of the invention so that the coupling elements are so deformed in overload or destroyed in parts that they are stuck in the locked state and thus the failure to a permanent clutch and not to a permanent idle leads.
  • the clutch elements deform in the event of overloading or are destroyed in parts in such a way that they are stuck in the unlatched state and thus the failure does not lead to a permanent clutch but to a permanent idling.
  • FIG. 1 is a schematic view of a freewheel according to the invention
  • Fig. 3 is a sectional view taken along the line A - A in Fig. 2,
  • FIGS. 4 is a perspective view of the freewheel according to FIGS. 2 and 3
  • 5 is a perspective view of a coupling element
  • Fig. 6 is an exploded view of a freewheel with an annular disc with
  • FIG. 9 is a sectional view of the view of FIG. 8 and
  • Fig.10-13 schematic views of a clamp body with a control tooth.
  • a first embodiment of the invention freewheel is dar ⁇ provided, the drive pulley 10, the z. B. can be connected to a starter shaft of a car engine and a ring gear with form-locking elements 11 auf ⁇ has.
  • the tooth flank profile of the interlocking elements can be designed to be symmetrical or asymmetrical and corresponds to the tooth flank or positive locking profile of the coupling elements 12, which are each pivotally mounted on a pin 13.
  • the pins 13 protrude from a driven pulley 16, which is connected for example to the crankshaft of the internal combustion engine.
  • Contours 17 are also arranged on this output disk 16 and delimit the pivot angle of the coupling elements 12 via corresponding stop surfaces.
  • the springing 15 shown in Fig. 1 is designed as a compression spring with a cylindrical pin and holds the respective coupling element 12 in engagement.
  • the flanks of the form-locking elements 11 ensure that at a torque flow from Starter to the crankshaft, so in the selected representation of a running direction in the clockwise direction, the coupling elements 12 always remain engaged.
  • the coupling elements 12 are lifted by means of the flank geometry from the form-locking elements 11 and compress the springing 15 together.
  • the centrifugal forces on the balance edge 14 of the Kupplungs ⁇ elements 12 exceed the spring force, so that the coupling elements in the course of noise and wear can overtake without touching the teeth.
  • Fig. 2 to 5 an alternative embodiment is shown, in which the drive element is a ring gear 200 with internal teeth 201 and annular axial side walls 203 and the output element consists of a star profile 207 with radially projecting arms, at the outer free end of a Bore is vorgese ⁇ hen, which is correspondingly penetrated by a pin 206 as a rotation axis corresponding to the holes of a coupling element 202, that the coupling element 202 and each coupling element is pivotally mounted.
  • the drive element is a ring gear 200 with internal teeth 201 and annular axial side walls 203 and the output element consists of a star profile 207 with radially projecting arms, at the outer free end of a Bore is vorgese ⁇ hen, which is correspondingly penetrated by a pin 206 as a rotation axis corresponding to the holes of a coupling element 202, that the coupling element 202 and each coupling element is pivotally mounted.
  • a spring-loaded contact pin is loaded in a bore 204 which projects laterally from the coupling element 202 and slides on the inside of the side wall 203 or a contour provided there and depending on the relative rotation of the drive element to the output element, the coupling element 202nd directionally bound with its teeth in the locked state in or out of der ⁇ sem blocking state.
  • the drive pulley 20 of FIG. 6 has a toothing which is formed corresponding to the toothing of a coupling element 21 which is pivotally mounted about a rotation axis 22.
  • the coupling elements are pivotable via a pin 13, in Fig. 7 to 9, a roller bearing guide ver ⁇ used.
  • internal teeth are provided in a hollow disk 30 and external teeth 33 are provided in a further hollow disk 32.
  • coupling elements 34 which have a rolling body 35 as a rotation axis, which is positively or frictionally connected to the coupling element 34.
  • a Federele ⁇ element 36 ensures the frictional engagement of the rolling element 35 on the coupling element 34.
  • the rolling element runs between an inner roller bearing ring 37 and an outer roller bearing ring, which are connected to the hollow disk 30 and the hollow disk 32.
  • the rolling elements and hereby the coupling element 34 are carried.
  • the tooth profiles 39 of the coupling element engage in the internal toothing 31 or external toothing 33.
  • the embodiment according to FIG. 8 has coupling elements 40 which have a toothing on only one side which is complementary to the toothed ring 41 of the hollow disc 42 is formed.
  • the rolling element 35 rolls on the annular surface 43.
  • the rolling elements 35 are cylindrically offset at the ends and roll on annular surfaces 44 of a carrier ring 45 via a radial spring 46 and the already mentioned leaf spring 46. This allows a sufficient frictional connection of the rolling element to be generated to perform slip-free circuits.
  • the coupling element 50 in FIGS. 10 to 13 has, apart from a serration 51, which is designed correspondingly to the corresponding toothing 52 of a ring gear, a control tooth, which in the case of FIG its free end opposite the toothing 51 her ⁇ protrudes. If the coupling element is moved in the direction of the arrow 54, engage First, the free end of the leaf spring 53 in a tooth gap or tooth flank. Due to the elastic design of the control tooth, ie the leaf spring 53, the coupling element 50 is displaced into one another before the engagement of the toothings 51 and 52 in an ideal relative position of the two toothings without damage due to high impact velocities.
  • an existing of an elastomeric material control tooth 55 is used, which may be gege ⁇ additionally acted upon by a spring 56.
  • Fig. 12 shows an embodiment with a control tooth 57, which is pivotally movable between stops 58 and 59 and is held by the spring-loaded pressure pin 62 in the respective position.
  • FIG. 13 shows a further optimization, which serves in particular to minimize increased wear of the tooth tip of the toothings.
  • a control tooth 61 is provided, which is limitedly pivotable in a recess of the coupling element between abutment surfaces.
  • This control tooth 61 is located in front of the radial plane, which is determined by the pivot point 60 of the coupling element 50.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Abstract

Roue libre à liaison de forme qui comporte une roue dentée ou à denture intérieure couplée à un premier arbre, à laquelle des éléments de couplage (12, 202) pourvus d'au moins trois, et de préférence de plus de huit dents, transmettent, à l'état de verrouillage dû à un engrènement par liaison de forme, un couple de rotation dans un sens de roulement, lesdits éléments de couplage entrant dans le sens opposé dans un état de roue libre. Chaque élément de couplage, qui est conçu sous forme d'élément circulant, est en outre monté rotatif autour d'un axe de rotation. Selon la présente invention, en cas de dépassement d'une vitesse de rotation limite, les éléments de couplage (12, 202) peuvent être libérés de l'état de verrouillage soit contraints par la force centrifuge contre une force de ressort, soit contraints par une force de friction exercée sur une broche de contact (206) située dans chaque élément de couplage (202) en cas de mouvement de glissement le long d'une trajectoire annulaire, ou sur un corps de roulement (35) lors d'un mouvement de roulement sur une surface annulaire (43).
EP05737016A 2004-09-29 2005-04-21 Roue libre a liaison de forme Withdrawn EP1794468A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004047802A DE102004047802A1 (de) 2004-09-29 2004-09-29 Formschlüssiger Freilauf
PCT/EP2005/004286 WO2006034735A1 (fr) 2004-09-29 2005-04-21 Roue libre a liaison de forme

Publications (1)

Publication Number Publication Date
EP1794468A1 true EP1794468A1 (fr) 2007-06-13

Family

ID=34966048

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05737016A Withdrawn EP1794468A1 (fr) 2004-09-29 2005-04-21 Roue libre a liaison de forme

Country Status (3)

Country Link
EP (1) EP1794468A1 (fr)
DE (1) DE102004047802A1 (fr)
WO (1) WO2006034735A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7451862B2 (en) * 2004-07-27 2008-11-18 Ford Global Technologies, Llc Ratcheting one-way clutch having rockers retained in closed pockets
DE102005052954B4 (de) * 2005-11-03 2010-06-17 Mbm Technologie Gmbh Freilaufeinrichtung
WO2008046579A1 (fr) 2006-10-19 2008-04-24 Satellite Gear Systems Ltd. Transmission oscillante à mécanisme de commutation, de structure simple et de stabilité accrue
JP2016528455A (ja) * 2013-08-15 2016-09-15 シェフラー テクノロジーズ アー・ゲー ウント コー． カー・ゲーＳｃｈａｅｆｆｌｅｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ ＡＧ ＆ Ｃｏ． ＫＧ フリーホイール
DE102014216082B4 (de) 2013-09-18 2022-08-18 Schaeffler Technologies AG & Co. KG Schaltbarer Freilauf
CN108869571A (zh) * 2017-05-13 2018-11-23 潘国陶 一种离合器及使用该离合器的变速器
CN107289162A (zh) * 2017-08-27 2017-10-24 杭州富阳鸿祥技术服务有限公司 一种基于双向超越离合器控制的可调安全泄压阀
CN107327517B (zh) * 2017-08-29 2019-02-15 蒋祥初 一种双向超越离合器
CN109519487A (zh) * 2017-09-19 2019-03-26 周承岗 齿盘超越离合器

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FR871072A (fr) * 1940-03-26 1942-04-07 Konstruktion Und Verwertung Au Roue libre à cliquets
GB622595A (en) * 1947-03-31 1949-05-04 Freeborn Power Converters Ltd Improvements in relating to unidirectional pawl and rachet devices
DE3047891C2 (de) * 1980-12-19 1982-09-02 Jean Walterscheid Gmbh, 5204 Lohmar Freilaufkupplung
DE3922222A1 (de) * 1989-07-06 1991-01-24 Walterscheid Gmbh Jean Freilaufkupplung
DE19953643B4 (de) 1999-11-09 2005-02-03 Innowacja Consulting Stufenloses Getriebe
US6757975B1 (en) * 2001-01-25 2004-07-06 Brigham Young University Multi-layered compliant mechanisms and method of manufacture
DE10301348A1 (de) 2003-01-16 2004-07-29 Satellite Gear Systems Ltd. Stufenlos regelbares Getriebe

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Also Published As

Publication number Publication date
DE102004047802A1 (de) 2006-04-06
WO2006034735A1 (fr) 2006-04-06

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