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
  • G04B17/00—Mechanisms for stabilising frequency
  • G04B17/20—Compensation of mechanisms for stabilising frequency
  • G04B17/28—Compensation of mechanisms for stabilising frequency for the effect of imbalance of the weights, e.g. tourbillon
  • G04B17/285—Tourbillons or carrousels
• • 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
  • G04B17/00—Mechanisms for stabilising frequency
  • G04B17/20—Compensation of mechanisms for stabilising frequency
  • G04B17/28—Compensation of mechanisms for stabilising frequency for the effect of imbalance of the weights, e.g. tourbillon
• • 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
  • G04B1/00—Driving mechanisms
  • G04B1/10—Driving mechanisms with mainspring
  • G04B1/22—Compensation of changes in the motive power of the mainspring
• • 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

Definitions

• the present invention relates to the field of watchmaking. More particularly, it relates to a clockwork movement provided with a regulating member mounted in a pivoting mobile support.
• the document EP2729849 proposed a vortex in which the regulating member is mounted in a cage in a conventional manner, the cage being pivoted inside a first ring, itself rotated inside. of a second ring, in order to form indeed a triaxial vortex with limited angular displacement for the second and third axes.
• the cage which performs complete rotations, is thus forced to move in a compound motion that resembles the precession of a gyroscope. Since the angular displacements around the second and third axes are not complete, the necessary height for the system can be significantly reduced, and the complexity can also be reduced.
• a main object of the present invention is to overcome the disadvantages of the prior art, by proposing a watch movement that allows to present chronometric benefits, without requiring a significant thickness in the movement, and without using the cog as a power take-off for certain movements of the regulating member.
• the present invention more particularly relates to a watch movement comprising at least one motor member, consisting for example of one or more motor springs housed in one or more barrels, of one or more electric motors. , and a regulating member such as a sprung balance member associated with an escapement, a tourbil lon, a carousel, a flywheel or the like, kinematically connected to said at least one a motor unit via a finishing train to maintain it in a known manner.
• the at least one drive member is in kinematic connection with a first power take-off which drives the finishing gear train (the latter thereby starting with this power take-off).
• the movement comprises a mobile support, such as a cradle, a ring, a cage, a board or the like, pivoted on a frame member and carrying said regulating member and adapted to pivot between two angles. pivoting limits, which can not be exceeded.
• the movable support is arranged to be pivoted along at least one axis between said limit pivot angles in a predetermined sequence by means of a pivot control device arranged to pivot said movable support in a gated movement. comes.
• a control train connects said pivot control device to a second power take-off (where the control gear train begins), distinct from the first, and which is in kinematic connection with said at least one motor unit.
• the pivot control train is therefore distinct from said work train, at least at the level of the torque transmission between the work train and the work train.
• the pivoting of the mobile support is not driven by a torque emanating from the work train, and thus do not represent additional torque load on the latter, which minimizes, or eliminates, the disturbances on the wheel due to these pivoting.
• the movement of the mobile support does not represent any load on the latter, and therefore can not influence the progress of the regulating member.
• the fact that the mobile support performs a back and forth pivoting requires less height in the movement than a vortex whose / a cage pivots about an axis perpendicular (or almost) to the axis. rotation of the balance.
• a larger regulating organ can therefore be used in the case of such a vortex, which improves the isochronism, while keeping the "whirlwind" or even "double vortex” effect, according to the construction of the vortex.
• regulating member namely a conventional balance-spring, respectively a conventional vortex. Indeed, it is not obligatory to carry out complete rotations to present a positive effect on the isochronism provided by changes of angular positions as in a "classic" vortex.
• said at least one motor member comprises a first motor unit arranged to drive it end gear issage through said first power take-off and a second motor member arranged to drive said control gear of pivoting through the second PTO.
• the two wheels mentioned can thus be totally isolated from one another at the torque transmission, each having its own source of energy.
• the slewing control train therefore does not contribute to the disarming of the motor unit used by the gear train.
• the pivoting of said movable support is engaged by a member driven by said work train, such as a cam, a lever or the like. Movements of the movable support can therefore be synchronized with the running of the regulating member, without requiring transfer of torque between the work train and the slewing control train.
• the pivot control train can be autonomous, or can be triggered and / or blocked manually.
• said control device comprises a speed controller, such as a flywheel, a finned flywheel, a sprung balance or the like.
• This speed controller is provided with at least one brake, such as a rocker stop, a friction brake or the like.
• This brake can thus be used to block and trigger the operation of the pivot control wheel in a simple manner.
• This brake may, for example, be arranged to be released via said element driven by said work train.
• This element may be a cam arranged to actuate a release member such as a lever, this release member being arranged to release said brake.
• said brake is arranged to be activated, that is to say to stop the speed controller, via an element of said pivot control device.
• the pivoting of the mobile support is thus stopped by the control device, which prevents these pivoting can be out of sync, particularly in the case where they are triggered by a member driven by the work train.
• the pivoting will remain synchronized with the running of the gear train.
• the movement may comprise a brake arranged to be actuated manually, said brake being also arranged to allow and selectively prevent the operation of said speed controller.
• This brake may be the same as mentioned above, or an additional brake. In any case, this allows the user to stop the mobile support in a desired position, for example to observe it.
• said work train includes a differential gear having a first input arranged to be driven by said drive member, a second input arranged to be driven directly or indirectly depending on the angular position of said movable support, for example by via a toothed member integral in rotation with the movable support or displaced by the latter, and an output arranged to drive said regulating member.
• This differential is used to isolate the gear train from the pivoting of the mobile support, in order to avoid torque variations due to these.
• the pivoting speed of the movable support can also be chosen optimally because the counter-force generated by the movements of the regulating member is canceled and therefore has no influence on the work train.
• said finishing gear train may comprise a torque compensator comprising a shaft integral in rotation with an input arranged to be driven directly or indirectly by said first power take-off, a second input arranged to be driven according to the angular position of said movable support, said second input comprising a wheel mounted idle on said shaft and connected thereto via an elastic member, and an output arranged to drive directly or indirectly said regulating organ.
• Said output comprises another wheel also mounted idle on said shaft and connected thereto via its own elastic element.
• said control device comprises at least one control cam integral in rotation with the movable support, said control cam comprising at least one actuating surface arranged to cooperate with an actuation cam driven by said control train. to drive said movable support pivotally.
• This system makes it possible to drive the mobile support pivotally. Therefore, the system does not require any jumper to ensure the positioning of the mobile support when it is stopped. The energy consumption is thus reduced.
• a system with partial teeth can also be used.
• said pivoting control device comprises a safety lever secured to rotate said movable support, said safety lever comprising a plurality of limiting pins (ideally three, but two, four or even more are still possible) which take place in tracks that comprises a track disc arranged to be rotated by said pivot control train, said tracks being shaped to prevent inadvertent pivoting of said movable support.
• said safety lever secured to rotate said movable support
• said safety lever comprising a plurality of limiting pins (ideally three, but two, four or even more are still possible) which take place in tracks that comprises a track disc arranged to be rotated by said pivot control train, said tracks being shaped to prevent inadvertent pivoting of said movable support.
• the exact shape of the tracks, the rotational angular velocity of the track disk and the arrangement of the pins on the safety lever can be defined according to the geometry of the system as well as the sequence of pivoting of the movable support in order to block and release the media at the desired moments.
• said pivot control device comprises a locking eccentric arranged to be driven by said pivot control wheel, said locking eccentric being arranged to cooperate with a stop lever arranged to stop said speed controller.
• the pivoting of the mobile support is thus stopped under the control of the slewing control gear, which prevents the pivoting of the movable support can desynchronize.
• said pivot control device is arranged in such a way that said movable support has periods of displacement. when said movable support is moving, and stopping periods when said movable support is stopped.
• said periods of displacement are of longer duration than said stopping periods, which implies a limited or even moderate speed of pivoting. This limited speed reduces the shocks to various components at the time of shutdown.
• said locking eccentric is arranged to cooperate with a stop lever arranged to stop directly or indirectly said speed controller.
• the invention also relates to a timepiece comprising such a movement.
• FIG. 1 represents a schematic diagram of a watch movement according to the invention
• FIG. 2 represents a schematic diagram of a variant of a watch movement according to the invention
• FIG. 3 represents a simplified perspective partial view of a concrete embodiment of a variant of a clockwork according to the invention, particularly illustrating the pivoting control gear as well as the pivot control device;
• Figure 4 shows a plan view of the variant of Figure 3
• Figures 5 and 6 show partial perspective views of the pivot control device of the variant of Figure 3;
• FIGS 7 to 9 show partial perspective views of the gear train and the differential gearing of the variant of Figure 3
• Figures 10a to 10c show views of a security system that includes the embodiment of Figures 3 to 9;
• FIG. 11 represents a schematic diagram of an alternative solution for compensating the displacements of the mobile support.
• FIG. 1 schematically illustrates the principle of the invention in its simplest form, in the context of a watch movement 1.
• This movement 1 comprises one or more motor members 3, such as one or more motor springs housed in one or more barrels.
• This or these motor member (s) 3 is associated with a first PTO 3c and a second PTO 3d.
• these power take-offs 3c, 3d can simply be mobile meshing with a toothing that includes the barrel (for example a toothing extending from a drum), or outputs of a gear to differential whose input is in kinematic connection with the barrel.
• This regulating member may be a pendulum-balance assembly, a vortex, a carousel, or any other suitable regulating organ, conventional or inclined.
• the work train passes through a first input 9a and an output 9c of a differential gear 9 or an alternative system, the operation will be better understood later.
• the regulating member 7 is carried by a movable support 1 1 pivotally mounted at least one axis relative to a frame 1 2, the movable support 1 1 pivoting back and forth between angles of pivoting limits under the control of a pivot control device 13 through a control wheel 15a.
• This latter connects the second power take-off 3d of the drive member 3 to the pivot control device 1 3, which controls the pivoting of the movable support 1 1.
• the work train 5 and the drive train 15a are independent at the torque transmission downstream of the power take-offs 3c, 3d.
• the pivoting of the movable support 1 1 can be made in a single axis, or alternately along several axes, cutting the movable support 1 1 or not, for example in order to perform a cardan movement or patella.
• a second input 9b of the differential gear is kinematically linked to the mobile support, so that the second entry rotates according to the angular displacements of the movable support 1 1.
• the torque provided by the part of the finishing gear 5b downstream of the differential gear 9 remains independent of the pivoting of the movable support.
• the differential gear 9 has the effect of isolating the torque transmission along the work train 5 displacements of the movable support 1 1. In the absence of the differential gearing 9, the movements of the movable support January 1 would cause a counter-force due to the fact that the regulating member 7 is carried by the movable support 1 1 and is also moving relative to the frame .
• FIG. 1 An alternative solution to the differential gear 9 is a torque compensator 9z as schematically illustrated in Figure 1 1.
• the same reference signs have been used in this figure to make as clear as possible the equivalence between the operation of the differential gear 9 and that of the torque compensator 9z.
• the arrangement illustrated in this figure comprises a shaft 9k, integral in rotation with an inlet 9a comprising a wheel 9d driven by the first part 5a of the finishing train 5.
• a second inlet 9b comprises a wheel 91 mounted idle on the shaft 9k. This wheel 91 is rotated according to the movements of the pivoting support 1 1, and is linked to the shaft 9k by means of an elastic element 9m such as a spiral spring or other. The latter is fixed on the shaft via a ferrule 9n.
• the output 9c also consists of a wheel 9o in kinematic connection with the regulating member 7 and linked to the shaft 9k via a second elastic element 9m and a ferrule 9n.
• the ferrules 9n can be omitted if the elastic elements are otherwise secured to the shaft 9k, for example by means of a weld.
• the elastic elements 9m When installing the torque compensator 9z, the elastic elements 9m must be prestressed. During operation of the system, when the mobile support 1 1 remains stationary, the torque arriving on the wheel 9d is transmitted to the wheel 9o through its elastic member 9m. The wheel 91 remaining stationary, its elastic element is stretched or relaxed in its winding direction.
• any friction may be incorporated between the wheel 91 and the movable support January 1.
• the pivot control device 13 may be autonomous, and / or may control the operation following actions of a user, for example by means of a pushbutton 14 or the like, and / or controlled The last two possibilities are shown in FIG. 1 by dashed arrows.
• FIG. 2 illustrates a variant in which each gear train 5, 15a is provided with its own motor member 3a respectively 3b each having its own power take-off 3c, 3d respectively, and are therefore completely independent with respect to the transmission. of couple.
• the pivot control device 13 is associated with a speed controller 17, which may take the form of a balance-balance assembly, a flywheel, a finned flywheel , or the like, in kinematic connection with the pivot control device 13 via a second gear 15b.
• the speed controller 17 is locked and / or released under the control of the work train 5, for example by means of a brake controlled by a cam, a wheel, or one or more levers.
• the speed controller 17 can also be released by the finishing train 5 and locked under the control of the pivot control train 15a, as is the case in the specific embodiment which will be described later.
• FIGs 3 to 9 illustrate a concrete embodiment of a clockwork according to the invention, corresponding to the diagram of Figure 2. Given the complexity of the mechanism, some elements have not been represented in some figures to avoid overloading them.
• Figures 3 and 4 particularly illustrate the drive train 15a, the pivot control device 13, the movable support 1 1, and the speed controller 1 7.
• the latter is formed of a regulating member spiral balance 17a associated with a classic exhaust 17b.
• This exhaust 17b has no influence on the movement and acts exclusively in connection with the pivot control device 13.
• the alternative control forms mentioned above can of course be used in place of the exhaust 17b and sprung balance
• the pivot control device 13 is kinematically connected to the movable support 11, which is pivoted to the movement frame (not shown).
• the movable support 1 1 supports the regulating member 7, which is a simple tourbillon in the illustrated variant, but can also be a simple balance-spring associated with an exhaust, or any other type of regulating member known to man of career.
• the pivot control device 13 will now be described in detail in connection with FIGS. 3 to 6.
• the pivot control device 13 drives the movable support 1 1 pivotally so that it performs the predetermined sequence of pivoting -35 ° - 0 ° - + 35 ° - 0 ° - -35 ° etc. around its axis of rotation 1 1 a relative to the plane of the movement.
• the angles of -35 ° and + 35 ° represent extreme and extreme angles of rotation in this case, and that of 0 ° represents an intermediate pivoting stop angle, which is the same as the position angles imitated .
• These are absolute and can never be exceeded by the movable support 1 1, the ndisqued awake you angels of stopping intermediate pivoting are exceeded at the next pivoting of the movable support 1 1.
• the mobile support is stopped for five seconds at each corner of the sequence, and pivoted for fifteen seconds. Changes to the movement to control the mobile support 1 1 according to other sequences of pivoting are within the reach of the skilled person. More generically, the periods of displacement of the movable support 1 1 are advantageously longer than the stopping periods, which reduces the impact experienced by the various components of the pivot mechanism. Nevertheless, this system is also suitable for periods of displacement equal or shorter than those stop, and it is also possible to provide different periods of immobilization in each stop position, according to the provisions of the cams.
• Solidarity in rotation of the movable support 1 1 is a first control cam 1 1b and a second control cam 1 1 c.
• the first control cam 1 1b comprises three safety surfaces
• a wheel 21 When the control train is running, a wheel 21 is in kinematic connection with another wheel 23, which is integral in rotation with an actuation cam 25.
• the wheels 21, 23 have been omitted from the figure 6 to better visualize the locking eccentric 19 (here in the form of a cam, but which can alternatively be a finger or a pin mounted eccentrically on a mobile) and the actuation cam 25, which turns in the direction counterclockwise to drive the first control cam 1 1b clockwise.
• the actuation cam 25 comprises two fingers 25a, angularly spaced 90 °, and which drive the movable support 1 1 in its two clockwise rotation steps (according to the orientation of Figures 5 and 6) .
• the second control cam 11c resumes a shape similar to that of the first control cam 11b, but inverted and angularly offset by an ad hoc angle defined in FIG. function of the construction.
• the second control cam 11c has a shape inverted with respect to the other control cam 11b and is rotated by its own actuating cam 27 (see Figure 6). The latter is coaxial and integral with the wheel 21 and thus rotates in the same direction, and serves to drive the mobile support 1 1 counterclockwise
• a security system 42 is provided. This security system 42 is illustrated in more detail in the form of exploded diagrams in FIGS. 10a to 10c.
• the security system 42 comprises a track disc 43, integral in rotation with the wheel 21.
• a safety lever 45 is integral in rotation with the movable support 1 1 as well as the control cams 1 1 b, 1 1 c, and therefore follows the reciprocating movement of the support January 1.
• This safety lever 45 also comprises three limiting pins 45a arranged at the end of the lever 45, which take place in tracks 43a which is provided with the track disc.
• the position of the pins 45a and the shape of the tracks 43a can be chosen ad hoc according to the sequence of movements of the components, so that the safety lever 45 is blocked when the mobile support 1 1 is stopped (the tracks walls 43a serving as stops for the pins 45a), and can pivot when the fingers 25a, 27a drive the control cams 1 1b, 1 1c (the pins are at this time in recessed areas 43b of the tracks that do not prevent tilting of the safety lever 45).
• abutment surfaces 25b, 27b are provided on the actuating cams 25, 27, adjacent to the fingers 25a, 27b respectively. These abutment surfaces 25b, 27b are positioned facing the safety surfaces 1 1 d when the mobile support 1 1 is at rest so that, during a shock that could overcome the effect of the security system 42, the safety surface 1 1d next to an abutment surface 25b, 27b, abuts against the latter.
• This arrangement avoids the use of a jumper to maintain the movable support in each angular position of stop, which is advantageous since the use of a jumper is greedy energy during pivoting.
• the pivot control device 13 may use toothed segments with interrupted teeth instead of the control cams 1 1b, 1 1c, as well as interrupted wheels instead of the actuation cams 25, 27.
• the control device 13 can drive the mobile support 1 1 in a single pivoting direction, then release it to return to its starting position by means of an elastic return member.
• An example of such a sequence would be -30 ° - 0 ° - +30 - -30 ° ...
• downtime could be different in each of the stop positions, depending on the shape and arrangement of the various cams.
• the speed controller 17 comprises a sprung-balance assembly 17a and an exhaust.
• the escape wheel forms the last mobile of the second gear 15b, branch of the control train 15a.
• the movement 1 is provided with a brake, in particular a rocker stopper 17c, integral with one end of a rocker stop rocker 29b which is subjected to a restoring force via a return member (not shown) which serves to bring the balance stop 17c in contact with the periphery of the balance.
• This rocker is pivoted on a frame member (not shown), and interacts with an intermediate lever 29a which is the link between the stop lever 29 and rocker stop rocker 29b.
• the locking eccentric 19 actuates the stop lever 29, and causes the stop balance 17c in contact with the periphery of the balance under the effect of its return spring (not shown) , and prevents it from oscillating until it is released by the balance stop 17c.
• the gear train connects firstly (through part 5a) the first barrel 3a to a first input 9a d ' a differential gear 9 via the first power take-off 3c, and on the other hand (through the part 5b of the work train 5 which is mounted on the movable support 1 1), an output 9c of the differential gear 9 to the regulating member 7 carried by the movable support 1 1.
• the first input 9a consists of a carrier chassis carrying at least one satellite gear (invisible) in a known manner. The chassis is secured in rotation with a pinion 9d driven by the first barrel 3a.
• Said output 9c consists of a barrel comprising a 9h edge toothing meshing with the planet gears, and a second edge toothing 9i which meshes with a toothed wheel 39 pivoted on the movable support 1 1 and which is in kinematic connection. with the regulating organ 7.
• the toothed wheel 39 and the others movable downstream of the latter form the second part 5b of the work train 5 and drive the regulating member 7.
• the second input 9b remains stationary, and the satellites act as references kinematically connecting the pinion 9d and the output of the barrel 9c.
• the latter is in kinematic connection with said second input 9b of the differential gearing 9.
• the second input 9b is formed of a mobile comprising a first ring gear 9f constituting another solar mobile differential gear 9, and a second set of teeth 9g engene with a 41a reference, itself driven via a toothed segment 41b integral in rotation of the mobile support 1 1.
• the pivoting of the mobile support 1 1 is transmitted to the second input 9b and are "subtracted" from those of the work train 5 so as not to influence the torque supplied to the regulating member 7 and not to disturb it. Pivoting of the movable support rotates the second input 9b, and thus the satellites, which results in the chassis of the carrier 9a does not pivot according to the pivoting of the movable support 1 1.
• the chassis of the carrier is also provided with a peripheral gear 9j, which serves to drive a gear 31, which in turn drives a pinion 33a integral in rotation with an actuating cam 33b.
• This cam 33b therefore rotates continuously and performs one revolution in one minute, regardless of the position of the movable support.
• a release member 35 in the form of a rocker in this case.
• the latter is provided at one end with a roller 35a to minimize friction with the cam 33b.
• the other end 35b of the release member 35 rests against a block 29c integral with the rocker stop rocker 29b.
• the sprung balance 17a is thus released and the drive train 15a is turned on.
• the control cams 1 1b, 1 1c and the actuation cams 25, 27 begin to pivot as described above, which causes the movable support 11 to pivot to its next position in the predetermined sequence.
• the locking eccentric 19 has pivoted by a small angle, it moves the stop lever 29, which pivots counterclockwise in FIG. 3.
• the intermediate lever 29a thus pivots clockwise in FIGS. 4 under the effect of a return spring (not shown) which is strong enough to overcome the effect of the return spring of the balance stop rocker 29b.
• the end 29d of the intermediate flip-flop approaches the pivot of the rocker stop rocker 29b, and slides along its flank 29e, which prevents the pendulum rocker from falling back on the balance.
• control gear 15a is triggered by means of the actuating cam 33b, there is no torque transmission between the work train 5 and the work train 15a, and they are therefore independent from one another to the kinematic one.
• the movement of the movement 1 is thus independent of the operation of the drive train 15a. If, for example, the second drive member 3b is disarmed so that the drive train 15a no longer operates, the movable support 1 1 remains stationary and the work train 5 continues to operate.
• the pivoting of the movable support can be stopped at a time.
• the control member can act on the only brake 17c already described. The user can thus stop the balance in a desired position, for example to observe the regulating member 7 in a precise position. If the user stops the mobile support 1 1 in an intermediate position, once the second brake no longer stops the balance, the next passage of a top of the actuating cam 33b, the balance will be released and the support The mobile will pivot to the next stopping angle in the predetermined sequence before the pendulum is stopped again via the set of levers 29, 29a, 29b.
• a needle 37 is kinematically connected with the second gear 15b.
• the gear ratios are chosen such that it performs one revolution per minute when the drive train 15a is operating. Indeed, this needle travels 120 ° in fifteen seconds when the mobile support is rotating, then pauses for five seconds when the mobile support is at rest, and then repeats this sequence as long as the mobile support continues its sequence of pivoting. In doing so, the needle 27 acts as unconventional second hand, which brings additional interest to the movement 1 for the user.
• the regulating member can traverse a series of different angular positions.
• this system has a tourbillon effect on an additional axis that the regulating member 7 presents itself, without the mobile support 1 1 performs complete rotations.
• a larger diameter rocker can thus be used in the same thickness of the movement, and / or the thickness of the movement can be significantly reduced for a rocker of the same size.
• a larger scale may, for example, contribute to an improvement of the isochronism of the movement.
• the movement of the invention provides the effect of a bi-axial vortex, without requiring as much height in the movement as a vortex bi-axial "classic" having a balance having the same dimensions.
• the movement provides a uniaxial vortex effect, whose axis of rotation is perpendicular to that of the balance.

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• Physics & Mathematics (AREA)
• General Physics & Mathematics (AREA)
• Transmission Devices (AREA)

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• 2016
  • 2016-06-23 CH CH00799/16A patent/CH712601A1/fr not_active Application Discontinuation
• 2017
  • 2017-05-08 CN CN201780034919.4A patent/CN109313411A/zh active Pending
  • 2017-05-08 WO PCT/EP2017/060952 patent/WO2017220246A1/fr unknown
  • 2017-05-08 EP EP17721727.0A patent/EP3475764B1/de active Active

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