EP1925995B1 - Schlagwerk - Google Patents

Schlagwerk Download PDF

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Publication number
EP1925995B1
EP1925995B1 EP06124443.0A EP06124443A EP1925995B1 EP 1925995 B1 EP1925995 B1 EP 1925995B1 EP 06124443 A EP06124443 A EP 06124443A EP 1925995 B1 EP1925995 B1 EP 1925995B1
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EP
European Patent Office
Prior art keywords
wheel
rotation
mechanism according
input
gear
Prior art date
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Active
Application number
EP06124443.0A
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English (en)
French (fr)
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EP1925995A1 (de
Inventor
Alain Schiesser
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.)
CHRISTOPHE CLARET ENGINEERING SA
Original Assignee
Christophe Claret Engineering SA
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 Christophe Claret Engineering SA filed Critical Christophe Claret Engineering SA
Priority to EP06124443.0A priority Critical patent/EP1925995B1/de
Priority to JP2009537592A priority patent/JP2010510506A/ja
Priority to PCT/EP2007/061989 priority patent/WO2008061884A1/fr
Priority to CN200780043261XA priority patent/CN101542401B/zh
Priority to US12/514,518 priority patent/US7965585B2/en
Publication of EP1925995A1 publication Critical patent/EP1925995A1/de
Application granted granted Critical
Publication of EP1925995B1 publication Critical patent/EP1925995B1/de
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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B21/00—Indicating the time by acoustic means
    • G04B21/02—Regular striking mechanisms giving the full hour, half hour or quarter hour
    • G04B21/12—Reiterating watches or clocks
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B13/00—Gearwork
    • G04B13/007—Gearwork with differential work
    • G04B13/008—Differentials

Definitions

  • the present invention relates to the field of mechanical watchmaking. More particularly, it relates to a striking mechanism comprising a power source for driving rakes and a gear train connecting the power source to a regulating member.
  • the big ringtones are therefore equipped with a complete gear train for driving the ringing parts.
  • This wheel thus connects a barrel of ringing with its own winding system to a regulating organ.
  • the barrel provides energy to the ringing parts through a control and distribution member disposed in the train, possibly coaxially with the barrel.
  • the control and distribution member comprises a stack of several wheels, free or fixed in rotation relative to each other.
  • CH 689337 discloses a striking mechanism having a rocket axis driven by a ringer barrel.
  • the object of the present invention is to propose an advantageous alternative to the devices of the state of the art.
  • the ringing parts are kinematically connected to the energy source via a differential disposed in the gear train.
  • this differential comprises a first input wheel kinematically connected to the wheel and a second input wheel connected to a control member and an output wheel connected to the ringing parts.
  • control member is a camshaft comprising a first cam for blocking or free rotation of the first input wheel, a second cam for locking or free rotation of the second input wheel and at least a driving wheel for pivoting the shaft.
  • the mechanism may comprise a silencer device provided with a latch capable of changing between a first and a second position, in which it co-operates with the driving wheel to block the control organ.
  • This lock can be moved by manual control means, actuated by the carrier, or by automatic control means, for example to prevent a ringing at the passage to be triggered below a certain power reserve.
  • the figure 1 shows a barrel 10 whose winding system has not been shown, which drives a reduction gear train 12, which ends with a regulating member, for example a flywheel 14 provided with a flyweight brake as the knows the skilled person.
  • a regulating member for example a flywheel 14 provided with a flyweight brake as the knows the skilled person.
  • a differential 20 kinematically connects the gear 12 to the rakes so that they are driven during the ring by the barrel 10.
  • a differential 20 particularly adapted to the invention is represented on the figure 2 .
  • the differential 20 On a shaft AA axis, it comprises a first sun gear 22 constituting a first differential input and kinematically connected with a wheel of the train 12.
  • the differential 20 is coaxial and integral with the wheel of the gear 12.
  • This sun gear 22 meshes with at least one, typically three, lower satellites 24 rotatably mounted on a first level of a planet carrier wheel 26 provided with a peripheral toothing.
  • the latter constitutes a second differential input. It is free in rotation and coaxial with the sun gear 22.
  • the three lower satellites 24 are each mounted coaxial and integral in rotation with at least one, typically three, upper satellites 28 rotatably mounted on a second level of the planet carrier wheel. 26.
  • the upper satellites 28 meshes with an upper solar wheel 30, coaxial and rotationally integral with a reference 32.
  • This upper sun gear 30 is the output of the differential.
  • this return 32 is engaged with a toothed sector 34 of an hours probe, intended to cooperate with the snail hour.
  • a ratchet of 36 hours intended to actuate a lift to ring the hours, is also integral in rotation of the reference 32.
  • the hour ratchet 36 is therefore directly kinematically connected to the feeler hours.
  • the rakes 18 kinematically connected to the hour sensor can move independently of the gear train 12 and the cylinder 10.
  • This configuration is the one that is used, when the bell is triggered, for allow the feelers of the different rakes, to fall on their respective snail to take information relative to the current time.
  • the second configuration makes it possible to kinematically connect the barrel 10 to the rakes 18. This is the one that is used during the course of the ringing so that the rakes move relative to their lifting to operate the hammers.
  • the third configuration corresponds to the situation in which the rakes 18 are stopped and kept at rest.
  • the blocking of the lower sun gear 22 is, according to the preferred embodiment shown in the drawings, by blocking the unwinding of the ringer barrel 10.
  • this lock is obtained by a stop element 38 arranged to move between a first and a second extreme position, the stop element 38 crossing, in one of these extreme positions, the stroke of a pin 40 projecting on the This is where the torque is the least important and the locking can be done with optimum safety.
  • the locking planet wheel 26 is made directly via a latch 42, having the shape of a hook 42a disposed on a latch 42b and capable of changing between a first and a second extreme positions, the hook 42a cooperating with the toothing of the planet carrier wheel 26 when it is in one of these extreme positions.
  • a camshaft 50 is pivotally mounted in the frame and has a first cam 52 for controlling the locking of the lower sun gear 22 and a second cam 54 controlling the locking of the planet wheel 26.
  • Cams and stars are represented individually at figure 4 .
  • the camshaft 50 is positioned by a first star 56 having a first level 56a ( figure 4a ) provided with twelve teeth cooperating with a jumper 58 and a second level 56b ( figure 4b ) having only four teeth, regularly distributed on a cut of twelve teeth and superimposed with the teeth of the first level.
  • This star 56 also performs the function of training drive of the shaft 50, as will be described in detail later.
  • the positioning star 56 is numbered in a multiple of three, twelve having an angular pitch between two consecutive advantageous positions with respect to the size of these parts and the available space.
  • the first cam 52 shown in FIG. figure 4c has a succession of projecting parts and hollow parts. As mentioned above and illustrated by the figure 6 , the locking of the lower sun wheel 22 is at the level of the regulating member 14.
  • the stop element 38 can be disposed at the end of a double rocker 58, comprising two rocker bars 58a and 58b hinged one with the other by a pin 58c secured to one of them 58a and cooperating with a housing 58d formed in the other 58b.
  • a spring 60 is arranged to support the end of the rocker 58a against the first cam 52.
  • the pivot points of the double rocker 58 are arranged, in the example, so that when the rocker 58a supports against a protruding part of the cam 52, the stop element 38 cooperates with the regulating member 14, which blocks the lower sun gear 22. Conversely, when the cam 52 has a hollow portion at the rocker 58a, the lower sun wheel 22 is free.
  • the cam 52 is provided with a succession of a protruding part, a hollow part and a protruding part, this series being repeated four times according to the example of a shaft. cams 50 to twelve positions.
  • the second cam 54 ( figure 4d ) also has a succession of projecting parts and hollow parts.
  • a spring 62 is arranged to support the end of the latch 42 not carrying the hook 42a against the cam 54.
  • the pivot point of the latch 42 is arranged so that when the Cam 54 has a protruding portion at the latch 42, the hook 42a is outside the toothing of the planet carrier wheel 26 which is free to rotate. Conversely, when the rocker 42 presses against a hollow of the cam, the planet wheel 26 is blocked.
  • the cam 54 is provided with a succession of a protruding part and two hollow parts, this series being repeated four times according to the example of a twelve-position camshaft.
  • FIG 3 shows a flexible finger 70 intended to cooperate with the second level 56b of the star 56 and rotated by the basic movement of the timepiece.
  • the finger 70 moves back and forth under the action of a sleeve 72 whose periphery defines a kind of spiral and has an inclined plane 72a.
  • the finger 70 is held against the cam by a spring 74 at a lug 70a which it is provided.
  • the bushing is driven counter-clockwise from the figure 3 , by the minute wheel of the basic movement, at a rate of one revolution per hour, which rotates the finger 70 counterclockwise and loads the spring 74. Every hour, at the passage of time, the lug passes the inclined plane and the finger 70, under the effect of the spring 74, rotates clockwise and drives the star 56 one step, thus passing the differential to the configuration 1.
  • the sleeve 72 could also include a plurality of inclined planes so as to actuate the finger every quarter of an hour, to ring quarters, an isolator can then be provided if it is desired that the hours are not ringed during the quarter ringing.
  • FIG. 5 For manual triggering, reference is made to figure 5 . It is proposed that the user operates a bolt 76 integral with a rack 78, like a conventional minute repeater.
  • the rack 78 meshes with an external toothing of a ring 80, coaxial with the striking barrel 10.
  • This ring 80 is connected to the shaft of the barrel 10 by a radial spring 82 having a hub 82a mounted square on the shaft and typically two blades resilient 82b, exerting a radial pressure towards the outside of the wheel and ending in a toothed portion cooperating with an internal toothing that includes the ring 80.
  • the spring 82 and the internal toothing of the ring 80 are arranged in such a way as to forming a snap between the shaft of the barrel 10 and the rack 78.
  • the pivoting of the ring 80 in one direction drives the barrel shaft in rotation, but neither the pivoting of the barrel shaft in the other sense, for example during disassembly of the movement, nor the drive of the shaft during the manual winding of the barrel of ringing causes displacement of the bolt 76.
  • the outer toothing of the ring 80 transmits the movement of the bolt to a wheel 84 with which it meshes.
  • This wheel 84 is provided with a return system 86, for example a spiral spring, allowing the return of the bolt 76 to its rest position since the latching system mentioned above does not allow this return to be ensured by the energy provided by the barrel 10, as is the case in conventional repetitions.
  • the wheel 84 also carries an arm 88 mounted on its axis and ending with a bearing zone 88a intended to cooperate with a second star 90 ( figure 4e ), also acting as drive element of the shaft 50, to advance the camshaft 50 by one step and pass the differential to the configuration 1.
  • This star 90 is cut to the number twelve but has only four teeth, that is one per ringing cycle. It is also clearly visible on the figure 7 .
  • a simple rocker driven by a pusher disposed in the middle part of the watch drives the star 90 by one step, without rearming the barrel.
  • the teeth of the star 90 are likely to cross the path of a transmission wheel 92, rotated permanently by the main wheel of the movement. Typically, this wheel is driven by the wheel of small average at the rate of one turn in thirty seconds approximately.
  • the skilled person will determine the shape of the teeth of the star 90 and the transmission wheel 92 to ensure good torque transmission.
  • the teeth of the star 90 are disposed on the camshaft so as to cross the path of the transmission wheel 92 when the differential is in its first configuration.
  • the camshaft 50 is thus driven slowly by one step and passes the differential 20 to the configuration 2.
  • the rakes 18 are kinematically connected to the barrel 10 so as to allow the ringing to proceed as such.
  • the shaft 50 must therefore move one step further than the end of the ring.
  • one of the rakes 18, preferably the minute rake 18a allows the displacement of a transmission element to the end of the ring.
  • this element may be a finger 94 arranged to cooperate with the first star 56 to advance the camshaft 50 by one step.
  • the rake minutes 18a carries a pin 96 for driving the finger 94.
  • the finger 94 is located at the end of an elastic portion of a flip-flop 98, which improves the safety of the device.
  • a spring 99 holds the rocker 98 against the pin 96.
  • the differential 20 when the ring is at rest, the differential 20 is in its configuration 3, the barrel 10 being locked, and the rakes 18 thus being held in position.
  • the camshaft 50 When triggering the ring, either manually or in passing, the camshaft 50 is driven one step, which allows to bring the differential 20 in its configuration 1.
  • the rakes are then disengaged from the ring gear 12 and then they can freely fall, under the effect of their respective spring, on their snail to take a information relating to the current time. This step is very fast and is done while the transmission wheel 92 drives the second star 90 and passes the differential 20 in its configuration 2.
  • the rakes are then kinematically connected to the barrel 10 which is released.
  • the finger 70 cooperates with the second level 56b of the star 56, if a trip trigger occurs during the course of a ring that has just been triggered manually, then the finger 70 does not will find on its way that a space devoid of teeth and will not abut against the camshaft. This security is particularly advantageous because trying to trigger a ringing in passing while a ringing is already in progress would cause serious damage to the mechanism.
  • the mechanism according to the invention may further comprise a silencer device 100 represented on the figure 7 and allowing the user to prevent the triggering of the ringing.
  • a pusher or corrector not shown is arranged in the middle part of the watch and makes a slide 102 evolve between a first rest position and a second position.
  • This slide 102 is movably mounted in translation on the plate of the striking mechanism and comprises, for this purpose, two oblongs 102a in which pass screws in range.
  • the slide 102 cooperates with a pin 104 disposed on a rocker 106.
  • a latch 108 is pivotally mounted, coaxial with the rocker 106.
  • the latch 108 is arranged to be able to move between a first rest position and a second position in which it cooperates with the second star 90, to prevent the rotation of the shaft 50.
  • the lock 108 has a notch which substantially matches the circumference of the camshaft.
  • the notch defines a finger 108a capable of interacting with the teeth of the star 90. These teeth are shaped so as to bear substantially orthogonally on the finger 108a, to obtain an effective locking.
  • the lock 108 is provided with a rod 110 capable of cooperating with a bearing surface 106a that the rocker 106 presents.
  • a first spring 112 keeps the rod 110 in abutment against the surface 106a. The force exerted by this spring 112 on the lock tends to move it away from the camshaft 50 and bring it back to its first position.
  • a second spring 114 is arranged to press the rocker 106 against the slide 102.
  • the finger 108a blocks the rotation of the shaft 50 when the slide 102 is pulled, i.e. when in its furthest position relative to the shaft 50.
  • the extreme positions of the slide 102 may be marked by a notch system, advantageously obtained at the level of the corrector or the pusher.
  • the rocker 106 pivots and, the spring 112 being less strong than the spring 114, the lock 108 is brought into its second position and blocks the pivoting of the Conversely, when the slide 102 is pushed, the lock 108 returns to its first position under the effect of the spring 112, releasing the camshaft 50.
  • a second flip-flop 116 is also mounted coaxial with respect to the first.
  • This second flip-flop 116 is provided with a probe 116a held by a third spring 118 in abutment against a cam 120 making a turn, substantially in a duration equal to the power reserve of the striking barrel 10.
  • the cam 120 has a recess arranged so as to be at the level of the toggles when the power reserve of the cylinder is below a predetermined threshold.
  • the flip-flop 116 pivots and, the spring 112 being less strong than the spring 118, the latch 108 is brought into its second position and blocks the pivoting of the shaft. 50. Conversely, when the power reserve reverts above the predetermined threshold, the latch returns to its first position under the effect of the spring 112, releasing the camshaft 50.
  • the manual triggering system for ringing can reset the barrel 10
  • the arm 88 actuating the star 90 is arranged to intersect, in its race, the latch 108 if it is in its second position, so as to bring it into its first position. position the time necessary to advance the shaft 50. This clearance must be done before the arm 88 exerts a thrust on the star 90. Then, once the shaft has rotated, since the lock is in Looking at the toothless portions of the star 90, it no longer locks until, at the end of the ring, it cooperates with a next tooth.
  • a cam driven by the base gear wheel at a rate of one revolution per twenty-four hours may define parts of the day during which the ringing pass is engaged and others, for example during the night, during which time she is stuck.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
  • Measurement Of Unknown Time Intervals (AREA)

Claims (13)

  1. Schlagwerk, das Rechen (18), eine Energiequelle (10), um die Rechen (18) anzutreiben, und ein Räderwerk (12), das die Energiequelle (10) mit einem Regulierungsorgan (14) verbindet, aufweist, dadurch gekennzeichnet, dass die Rechen (18) mit der Energiequelle (10) über ein Differenzialgetriebe (20) kinematisch verbunden sind, das im Räderwerk (12) angeordnet ist.
  2. Werk nach Anspruch 1, dadurch gekennzeichnet, dass das Differenzialgetriebe (20) ein erstes Eingangsrad (22), das kinematisch mit dem Räderwerk (12) verbunden ist, und ein zweites Eingangsrad (24), das mit einem Steuerorgan (50) verbunden ist, und ein Ausgangsrad (30), das mit den Rechen (18) verbunden ist, umfasst.
  3. Werk nach Anspruch 2, dadurch gekennzeichnet, dass das Steuerorgan (50) derart ausgebildet ist, dass das Differenzialgetriebe (20) einnehmen kann:
    - eine erste Konfiguration, in der das erste Eingangsrad (22) in Rotation blockiert ist und das zweite Eingangsrad (24) in Rotation frei ist, wobei das Ausgangsrad (30) in Rotation frei ist,
    - eine zweite Konfiguration, in der das erste Eingangsrad (22) in Rotation frei ist, das zweite Eingangsrad (24) in Rotation blockiert ist, wobei das Ausgangsrad (30) dann frei ist, über das erste Eingangsrad (22) angetrieben zu sein, und
    - eine dritte Konfiguration, in der der das erste (22) und das zweite (24) Eingangsrad in Rotation blockiert sind, wobei auch das Ausgangsrad (30) in Rotation blockiert ist.
  4. Werk nach Anspruch 3, dadurch gekennzeichnet, dass das Differenzialgetriebe (20) auf einer Welle umfasst:
    - ein erstes Sonnenrad (22), das den ersten Eingang des Differenzialgetriebes bildet und mit einem Rad des Räderwerks (12) kinematisch verbunden ist,
    - mindestens ein unteres Planetenrad (24), das in das erste Sonnenrad (22) eingreift,
    - ein Planetenräderhalter-Rad (26), das auf der Welle in Rotation frei und mit dem ersten Sonnenrad (22) koaxial ist, das den zweiten Eingang des Differenzialgetriebes bildet, wobei das untere Planetenrad (24) rotierend auf einer ersten Ebene des Planetenräderhalter-Rads (26) montiert ist,
    - mindestens ein oberes Planetenrad (28), das rotierend auf einer zweiten Ebene des Planetenräderhalter-Rads (26) montiert ist, das koaxial und in Rotation verbunden mit dem unteren Planetenrad montiert ist,
    - ein oberes Sonnenrad (30), das in das obere Planetenrad eingreift und den Ausgang des Differenzialgetriebes bildet.
  5. Werk nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, dass das Steuerorgan eine Nockenwelle (50) ist, die eine erste Kurvenscheibe (52), um das erste Eingangsrad (22) zu blockieren oder frei drehen zu lassen, eine zweite Kurvenscheibe (54), um das zweite Eingangsrad (26) zu blockieren oder frei drehen zu lassen und mindestens ein Antriebsdrehteil (56, 90) für das Drehen der Welle umfasst.
  6. Werk nach Anspruch 5, das einen Auslösemechanismus des Schlagwerks aufweist, dadurch gekennzeichnet, dass der Auslösemechanismus einen Finger (70, 88a) aufweist, um das Antriebsdrehteil (56, 90) anzutreiben.
  7. Werk nach Anspruch 5, dadurch gekennzeichnet, dass es ein erstes Übertragungselement (92) aufweist, um die Welle (50) über das Antriebsdrehteils (90) anzutreiben, nachdem die Rechen auf ihre Staffel gefallen sind.
  8. Werk nach Anspruch 5, dadurch gekennzeichnet, dass es ein zweites Übertragungselement (94) aufweist, um die Welle (50) über das Antriebsdrehteil (56) anzutreiben, nachdem sich das Schlagwerk entrollt hat.
  9. Werk nach Anspruch 3, dadurch gekennzeichnet, dass das erste Eingangsrad (22) über das Räderwerk (12) mit dem Steuerorgan (50) verbunden ist, wobei das erste Eingangsrad durch die Blockierungdes Räderwerks, vorzugsweise durch die Bloockierungdes Regulierungsorgans (14), in Rotation blockiert ist.
  10. Werk nach Anspruch 2, wobei das zweite Eingangsrad (26) mit einer Umfangszahnung ausgestattet ist, dadurch gekennzeichnet, dass das zweite Eingangsrad von einer Wippe (42), die mit dem Steuerorgan (50) zusammenarbeitet, in Rotation blockiert ist.
  11. Werk nach einem der Ansprüche 2 bis 10, dadurch gekennzeichnet, dass es eine Geräuschlosvorrichtung (100) umfasst, die mit einem Riegel (108) ausgestattet ist, der zwischen einer ersten Position und einer zweiten Position bewegbar ist, in der er mit dem Antriebsdrehteil (90) zusammenarbeitet, um das Steuerorgan (50) zu blockieren.
  12. Werk nach Anspruch 11, dadurch gekennzeichnet, dass ein manuelles Steuermittel (102) ausgebildet ist, um den Riegel (108) der Geräuschlosvorrichtung in seine zweite Position zu stellen.
  13. Werk nach Anspruch 11, dadurch gekennzeichnet, dass ein automatisches Steuermittel (116, 118, 120) ausgebildet ist, um den Riegel der Geräuschlosvorrichtung in seine zweite Position zu stellen.
EP06124443.0A 2006-11-21 2006-11-21 Schlagwerk Active EP1925995B1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP06124443.0A EP1925995B1 (de) 2006-11-21 2006-11-21 Schlagwerk
JP2009537592A JP2010510506A (ja) 2006-11-21 2007-11-07 報時機構
PCT/EP2007/061989 WO2008061884A1 (fr) 2006-11-21 2007-11-07 Mecanisme de sonnerie
CN200780043261XA CN101542401B (zh) 2006-11-21 2007-11-07 振铃机构
US12/514,518 US7965585B2 (en) 2006-11-21 2007-11-07 Ringing mechanism

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06124443.0A EP1925995B1 (de) 2006-11-21 2006-11-21 Schlagwerk

Publications (2)

Publication Number Publication Date
EP1925995A1 EP1925995A1 (de) 2008-05-28
EP1925995B1 true EP1925995B1 (de) 2014-06-18

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ID=38324119

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06124443.0A Active EP1925995B1 (de) 2006-11-21 2006-11-21 Schlagwerk

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Country Link
US (1) US7965585B2 (de)
EP (1) EP1925995B1 (de)
JP (1) JP2010510506A (de)
CN (1) CN101542401B (de)
WO (1) WO2008061884A1 (de)

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EP3435169B1 (de) * 2017-07-25 2023-03-01 Blancpain SA Arretiermechanismus für schlagwerkmechanismus einer uhr
EP3435174B1 (de) * 2017-07-25 2021-06-16 Blancpain SA Moduswahlschalter für schlagwerk für armbanduhr oder andere uhr
CN109960135B (zh) * 2019-04-28 2023-11-24 烟台持久钟表有限公司 一种用于机械大钟报刻的装置
US11164552B1 (en) * 2021-05-12 2021-11-02 Malmark Inc. Bell and hammer rotational device

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Also Published As

Publication number Publication date
CN101542401B (zh) 2011-08-10
US7965585B2 (en) 2011-06-21
EP1925995A1 (de) 2008-05-28
US20100054091A1 (en) 2010-03-04
JP2010510506A (ja) 2010-04-02
CN101542401A (zh) 2009-09-23
WO2008061884A1 (fr) 2008-05-29

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