EP2689298B1 - Momentaner antriebsmechanismus für ein uhrwerk - Google Patents

Momentaner antriebsmechanismus für ein uhrwerk Download PDF

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Publication number
EP2689298B1
EP2689298B1 EP12717214.6A EP12717214A EP2689298B1 EP 2689298 B1 EP2689298 B1 EP 2689298B1 EP 12717214 A EP12717214 A EP 12717214A EP 2689298 B1 EP2689298 B1 EP 2689298B1
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EP
European Patent Office
Prior art keywords
lever
mobile
cam
counter
radius
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Active
Application number
EP12717214.6A
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English (en)
French (fr)
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EP2689298A1 (de
Inventor
Huy Van Tran
Ludovic Perez
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Pequignet SA
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Pequignet SA
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Publication of EP2689298A1 publication Critical patent/EP2689298A1/de
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    • 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
    • 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
    • G04B19/00—Indicating the time by visual means
    • G04B19/24—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars
    • G04B19/243—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator
    • G04B19/247—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator disc-shaped
    • G04B19/25—Devices for setting the date indicators manually
    • 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
    • G04B27/00—Mechanical devices for setting the time indicating means
    • G04B27/005—Mechanical devices for setting the time indicating means stepwise or on determined values

Definitions

  • the present invention relates to an instantaneous drive mechanism for a watch movement
  • a mobile and a lever intended to be pivotally mounted on at least one frame element of the watch movement.
  • the lever is arranged to cooperate, on the one hand, with the mobile to be moved and, on the other hand, with a counter of the watch movement, with the aim of incrementing it by means of instantaneous pulses.
  • the mobile comprises a first wheel, intended to be driven from a drive member of the watch movement and arranged to drive in rotation a first cam of the mobile, coaxial with the first wheel and, having a periphery of variable radius.
  • the latter is arranged to cooperate with a spout carried by a first arm of the lever and away from the center of the mobile when the latter rotates in a first direction of rotation, before letting it fall, under the effect of the action elastic means, when the spout moves from a point of the periphery corresponding to the largest radius to a point of the periphery corresponding to the smallest radius.
  • EP 1406131 A1 which describes a clock mechanism arranged to drive, by successive instantaneous jumps, disks display current hours and minutes.
  • this mechanism comprises, for each of these two units of time to display, a mobile comprising a drive wheel and a cam coaxial with this wheel and having a periphery of variable radius, more precisely sawtooth.
  • the cam is integral in rotation with the drive wheel, the latter being driven from a finishing train.
  • a pivoting lever is arranged to cooperate on the one hand with the cam, via a spout, and, on the other hand, with a counter of the corresponding unit of time, via a rocker carrying a ratchet and with which it meshes.
  • Elastic means are provided for applying the spout permanently against the periphery of the cam, so that the lever pivots while the spout follows the rising profile of a saw tooth of the cam, before falling when the spout is facing of the radial face of this same tooth.
  • the falling of the nose, and therefore the return of the lever in its position closest to the cam, causes an instantaneous incrementation of the counter of the corresponding unit of time.
  • this document provides a device for correcting the current time arranged so as to prevent any rotation of the cam in the wrong direction of rotation. More precisely, this correction device makes it possible to modify the current time without involving the levers.
  • the patent EP 1918792 B1 discloses a correcting mechanism associated with a similar drive mechanism and for correcting the value of a time indication both forward and backward.
  • this correction mechanism comprises a return lever, arranged near the lever cooperating with the cam to control the display of the time indication, in the same plane, to lift the lever by through a return and place its spout out of range of the periphery of the cam, when a correction back is operated.
  • a main object of the present invention is to propose an alternative to known watch movements having a control mechanism of an instantaneous jumping display, by proposing such a mechanism in which both the cam with which the lever cooperates can be driven into the two directions of rotation, to prevent any damage during manual corrections, and having a limited footprint in the plane of the corresponding watch movement.
  • the present invention more particularly relates to an instant drive mechanism of the type mentioned above, characterized in that the mobile comprises a safety member coaxial with the drive wheel and arranged to cooperate with the lever. to move the first arm away from the center of the mobile when the latter rotates in the second direction of rotation and allow the nose to move from the point corresponding to the smallest radius to the point corresponding to the largest radius.
  • the drive mechanism according to the invention makes it possible to make rapid corrections of the information to be displayed or of other information related to it, in particular by allowing rotation in both directions of the cam. controlling the pulses transmitted by the lever to the first counter.
  • the safety member has a kinematic connection with the first cam as they are angularly movable relative to each other between first and second relative angular positions.
  • a first of these relative angular positions is associated with the first direction of rotation while the spout cooperates with the cam to define the position of the lever.
  • At least one other position is associated with the second direction of rotation while the safety member cooperates with the lever to define the position of the latter.
  • the safety member may comprise a board, coaxial with the first cam and having a slope at its periphery, inclined relative to the radial direction and extending between points respectively corresponding to the smallest radius and the largest radius of the board.
  • the board and the first cam are advantageously made integral with each other in rotation by means of an elastic member arranged to allow their relative angular mobility between the first and second positions.
  • the mobile has a pin integral with one of the first cam and the safety member, and a portion of which is arranged in a slot, of predefined length, formed in the other elements to define the two relative angular positions.
  • the mobile may further comprise an elastic member having a base integral in rotation with that of the elements comprising the slot and a finger arranged to cooperate with the pin to tend to position the first cam and the safety member in the direction of the first position relative angular.
  • the cam and the safety member are controlled relative to each other, depending on the direction of rotation of the mobile, so that the one of these two elements able to move the lever acts on the latter if necessary.
  • the lever comprises a first retractable finger arranged to act at least indirectly on the first counter and transmit the pulses, the lever further comprising a retraction device controlled by the mobile and arranged to act on the first retractable finger and, on the one hand, move it so that it is located out of range of the first counter during the phase in which the first arm of the lever is remote from the center of the mobile and secondly , release it before the fall of the lever so that it can transmit a pulse to the first counter.
  • the retraction device may comprise a feeler pivotally mounted on the lever and arranged to cooperate, on the one hand, with the periphery of the board of the safety member, the latter having a radius increasing from the point of weakest radius to the point of greatest radius, and, secondly, at least indirectly with the retractable finger.
  • the finger actuating the counter does not come into contact with the latter during the phase during which it is positioned upstream relative thereto, thus preserving the proper operation of the corresponding clock movement.
  • the retractable finger can be integral with a guide member arranged to cooperate with a fixed pin, in particular housed in a frame member of the corresponding clock movement.
  • the cooperation of the guiding member with the pin has a predefined path as a function of the movements of the lever.
  • the latter further comprises an elastic member arranged to define a position at rest of the guide member with reference to the lever and exerting on it a force contributing to define the predefined path.
  • the mechanism according to the invention can advantageously be implemented to increment, instantaneously, a second counter of the watch movement.
  • the lever comprises a second arm arranged to cooperate with the second counter of the watch movement, for the purpose of incrementing by means of instantaneous pulses substantially simultaneous with those acting on the first counter.
  • the lever may comprise a second retractable finger arranged to act at least indirectly on the second counter and transmit the pulses thereto, the retraction device being arranged to act also on the second finger and, on the one hand, to move it such that it is located out of range of the second counter during the phase during which the first arm of the lever is remote from the center of the mobile and, secondly, to release it before the fall of the lever in such a way that it can transmit a pulse to the second counter.
  • the retraction device may also comprise a rocker pivotally mounted on the lever and having first and second ends arranged to cooperate respectively with the first and second second retractable fingers.
  • a rocker pivotally mounted on the lever and having first and second ends arranged to cooperate respectively with the first and second second retractable fingers.
  • the figure 1 represents a simplified front view of an instantaneous drive mechanism for watch movement according to a first preferred embodiment of the present invention. More precisely, the mechanism represented is intended to control the display of the date, in the form of a big date, as well as the day of the week.
  • the mechanism comprises a finishing gear, connecting a time base to a conventional motor unit (not shown) and, driving a wheel hours 1 in rotation, at a rate of one complete turn every 12 hours, to non-limiting indicative title.
  • the hour wheel 1 is kinematically connected to a mobile 2 of the drive mechanism according to the invention by means of a set of references 3, arranged in engagement with a first toothed wheel 4 of the mobile 2, in such a way that the latter performs a complete turn on itself in 24 hours.
  • the mobile 2 cooperates with a lever 6, in a manner to be described in detail later, to increment, instantaneously and substantially simultaneously, the date and weekday meters every 24 hours.
  • the lever 6 comprises a first arm 7 for incrementing a first counter of the days of the week 8 by transmitting pulses to a pinion 9, seven teeth, integral with a display disc 10 days of the week.
  • the lever 6 furthermore comprises a second arm 12 for incrementing a second date counter 13 by transmitting pulses to a two-stage control wheel 14 intended to control the movements of two pinions 15 and 16, respectively integral with discs. units and dozens of date, to achieve a conventional large date type display.
  • Jumper springs 18, 19, 20 and 21 are provided, in known manner, to ensure good angular positioning of the discs and the control wheel.
  • a spring 22 is formed integrally with the lever 6 to ensure its good cooperation with the mobile 2.
  • This spring 22 is disposed in abutment against a cam 24, held on a frame member of the watch movement by means of a screw 25.
  • the periphery of the cam 24 has a succession of segments more or less distant from the center of the cam. The prestressing of the spring 22 can thus be adjusted according to the segment against which it is placed in support.
  • the figure 2 represents an exploded perspective view of the mobile 2 according to a first preferred embodiment of the present invention.
  • the first toothed wheel 4 is integral with a barrel 27 on which are engaged a cam 28, an elastic member 29 and a retaining board 30.
  • the hollow central axis of the barrel is intended to be engaged on a tenon carried by an element frame of the watch movement to mount the mobile pivot.
  • the barrel 27 has a flat 32 with which cooperate openings 33, 34 of complementary shape formed in the elastic member 29 and the retaining board 30. By this cooperation, the barrel 27, the elastic member 29 and the retaining board 30 are integral in rotation.
  • the barrel 27 has a shoulder 36 defining a radial guide surface for the cam 28, mounted on the barrel being free to rotate relative thereto.
  • the barrel 27 also carries a safety member 38 whose operation will be explained later.
  • the safety member is secured to the barrel, and therefore the toothed wheel 4, in rotation.
  • the safety member comprises a board whose periphery has a variable radius, more precisely here, whose radius increases substantially continuously between a weakest radius and a largest radius.
  • An inclined slope 39 relative to the radial direction defines the junction between the points of the smallest radius and the largest.
  • the safety member further comprises a slot 40 extending substantially in a circular path.
  • the cam 28 is positioned on the barrel 27 being adjacent to the safety member 38. It also has a periphery of variable radius, more precisely here, having its radius which increases substantially continuously between a weakest radius and a largest radius.
  • the junction 42 between the points of largest radius and the smallest radius has a curvature located between the region of the periphery corresponding to the largest radii and the center of the cam, so as to define a sudden interruption of the periphery after the point of greatest radius towards the point of the weakest radius.
  • cam 28 carries a pin 44 intended to cooperate with the slot 40 of the safety member, as will be explained later in detail.
  • the elastic member 29 comprises a base 45 to ensure its holding on the barrel 27 and from which extend a peripheral ring 46 and an elastic arm 47, of generally circular shape.
  • the latter has two fingers in the form of claws 48, 49 oriented facing each other, at its free end intended to cooperate with the pin 44 carried by the cam 28, to tend to move in one direction or in the other inside the slot 40.
  • the pin 44 is free to position between the two claws 48 and 49.
  • the retaining board 30 has the general shape of a ring and comprises two windows 51, 52 whose presence is purely illustrative, their function being to allow the visualization of a detail of the mechanism according to the invention during operation.
  • the main function of the retaining board is to ensure that the elastic arm 47 does not deform outside its worktop.
  • FIGS 3a and 3b represent perspective views of the first and second faces of the lever 6 intended to cooperate with the mobile 2 which has just been described.
  • the lever 6 comprises a bore 60 intended to allow its pivotal attachment to a frame member of the watch movement.
  • the first arm 7 comprises, near its free end, a first spout 61 intended to cooperate with the periphery of the cam 28, followed by a second spout 62 defining a first abutment surface for a first retractable finger 63, pivotally mounted on the first arm 7 and arranged to transmit pulses to the pinion 9 of the weekday counter 8.
  • a second abutment surface 64 is provided to define a range of movement of the first retractable finger.
  • a spring 65 here formed in one piece with the lever 6 is provided for applying a force on the first retractable finger, via an extension 66, tending to hold it against the second abutment surface 64.
  • the first arm 7 also carries a probe 68 intended to cooperate with the periphery of the safety member 38 and pivotally mounted on the first arm.
  • the lever 6 carries a latch 70, rotatably mounted on the lever, with an axis of rotation coaxial with the bore 60 and having first and second arms 71, 72 respectively superimposed on the first and second arms of the lever 7, 12.
  • the free end of the first arm 71 of the rocker is arranged near the probe 68 and has a folded portion 69 arranged in abutment against the back of the probe 68, so that the latter causes a pivoting of the rocker, simultaneously with a pivoting of the first retractable finger 63 when it pivots.
  • the folded portion is arranged in such a way that it can exert on the extension 66 a force that is antagonistic to that of the spring 65, to separate the first retractable finger from the second abutment surface 64.
  • the free end of the second arm 72 of the rocker cooperates with a second retractable finger 74 to pivot substantially simultaneously to the first retractable finger 63.
  • First and second abutment surfaces 75, 76 are formed in the second arm 12 to limit the stroke of the second retractable finger 74 in both directions of rotation.
  • an additional abutment surface 77 is provided on the first arm 7 of the lever to limit the stroke of the probe 68.
  • the Figures 4a to 4d represent the operating kinematics of the instantaneous driving mechanism according to the first embodiment of the present invention, in a first direction of rotation, in the same simplified front view, similar to that of the figure 1 .
  • the first direction of rotation is here the normal operating direction of the mechanism, that is to say, especially when it is driven by the gear train.
  • the hour wheel 1 rotates in the clockwise direction on the Figures 4a to 4d , which corresponds to a rotation of the mobile 2 in the anti-clockwise direction of rotation.
  • the spout 61 follows, for nearly 24 hours, the periphery of the cam 28 to the position illustrated on the figure 4a , which corresponds to one hour just after midnight, the next day. Indeed, the wheel 4 being driven in the direction of rotation anti-clockwise, it drives the cam 28 in the same direction by cooperation of its slot 40 with the pin 44 carried by the cam 28.
  • the feeler 68 follows the periphery of the safety member 38, the radius of which, starting from its substantially lowest value, progressively increases to its largest value, as illustrated in FIG. figure 4a .
  • the relative forces of the springs 22 and 65 are advantageously chosen in such a way that the action of the spring 22 predominates over that of the spring 65.
  • the pivoting of the probe 68 has resulted in a retraction of the first and second retractable fingers 63 and 74.
  • the growth slope of the radius of the safety member is chosen such that the two retractable fingers are sufficiently retracted to be out of reach counters 8 and 13 as they pass in front of the respective teeth to which they will transmit the next pulse.
  • the probe 68 exceeds the point of greatest radius of the security member and reaches the slope 39 thereof. At this moment, the probe 68 is no longer constrained except that of the spring 65 which pivots it against its abutment surface 77.
  • the two retractable fingers 63 and 74 leave their retracted position by turning clockwise on the figure 4b , to prepare to transmit each a pulse to the corresponding counter.
  • the figure 4d illustrates the configuration of the instant drive mechanism according to the present invention immediately after midnight, immediately after the fall of the lever 6 at the junction 42 of the periphery of the cam 28. At this time, each of the date meters and the days of the week has been incremented.
  • the time setting operation can potentially give rise to damage, if no safety measures are taken, when the hour wheel 1 is driven in the anti-clockwise direction, because of the shapes. respective of the spout 61 and the cam 28.
  • FIGS. 5a to 5e illustrate the operation of the safety member 38 in relation to the lever 6 to prevent damage to the instant drive mechanism in such a case.
  • the toothed wheel 4 can continue its travel by moving the pin 44 inside the slot 40 formed in the safety member 38, which is visible on the figure 5a , the cam 28 remaining stationary.
  • the probe 68 comes into contact with the slope 39 of the safety member, in a locked position against its abutment surface 77.
  • the rotation of the safety member 38 thus causes the probe 68 to slide along the slope 39, causing an uplift of the first arm 7 of the lever 6 relative to the mobile 2.
  • the tip of the spout 61 crosses the edge defined between the junction 42 and the point of greatest radius of the periphery of the cam 28 to arrive at the configuration illustrated in FIG. figure 5b .
  • the probe 68 continues its course along the slope 39, it further moves the first arm 7 from the center of the cam 28 thus allowing the spout 61 to cross the aforementioned edge to present the configuration illustrated on the figure 5c .
  • the cam has slightly rotated clockwise, under the effect of the action of the elastic arm 47 on the pin 44.
  • the spout 61 is out of reach of the cam 28, particularly in order to provide a margin of safety, as is apparent from the configuration illustrated on the figure 5d .
  • the current time display changed from a position indicating a time shortly after midnight to a time of a few hours before midnight.
  • the user can start turning the hour wheel in the normal direction, i.e. the clockwise direction, to return the display of the current time to a time after midnight.
  • the first gearwheel 4 is rotated in the anticlockwise rotation direction.
  • the cam 28 remains substantially stationary, until the slot 40 comes to reposition itself in abutment against the pin 44.
  • the feeler 68 returns to position itself facing the slope 39 and pivots to again in the anti-clockwise rotation direction on the figure 5e , so as to place the retractable fingers 63 and 74 within reach of the associated teeth (in a configuration close to that of the figure 4b , apart from the relative positioning of the slot 40 and the pin 44).
  • the position of the lever 6 relative to the cam 28 is defined by the interaction between the spout 61 and the periphery of the cam.
  • the drive mechanism behaves similarly when the hour wheel 1 is driven manually in the clockwise direction.
  • the cam and the nose may be in abutment with each other leading to the jamming of the cam and, in this case, the interaction between the probe 68 and the slope 39 of the safety member 38 allows the spout 61 to overcome the junction 42, to move from the smallest radius point of the periphery of the cam 28 to its largest radius point , without causing damage to the mechanism.
  • the operation of the mechanism according to the present invention makes it easier to place the needles for a watchmaker responsible for assembling a corresponding timepiece.
  • the setting of the current hour and minute hands is generally performed when the hour wheel and the roadway are arranged in their corresponding position at midnight, this position being detectable by the jump of the date counter.
  • the watchmaker can roughly search the midnight position by identifying the leap of the lever 6 and set up the needles without completely chasing them, at first. He can then go back by manually correcting the current time and then changing direction to train the mechanism in the normal direction, more slowly, to more accurately detect the midnight position and completely chase the needles.
  • FIGS. 6 and 7 represent, in similar and simplified front views, the operation of a fast correction mechanism of the date and the day of the week which can advantageously be implemented in addition to the drive mechanism which has just been described.
  • This fast correction mechanism comprises a correction flip-flop 80 pivotally mounted on a frame element of the watch movement, between at least one first neutral position (that illustrated in particular on the figure 4a ), a second correction position of the date ( figure 6 ) and a third correction position of the day of the week ( figure 7 ).
  • the fast correction mechanism also comprises a control wheel 81 arranged to define the position of the rocker at a given moment in relation to the action of a spring 82 acting on the rocker 80.
  • the control wheel 81 comprises first and second toothed wheels, integral in rotation and only one of which is visible in the figures, namely the first drive wheel 84.
  • the second control wheel has a toothing similar to that of the first wheel with the difference that its pitch is three times that of the first wheel, that is to say it has only one tooth in three.
  • the two wheels can be formed in one piece, that is to say in the form of a single wheel whose two teeth in three are truncated in the direction of the thickness of the wheel.
  • the first wheel 84 is arranged to be rotated from rotational movements applied to a time setting rod in a conventional manner.
  • the kinematic connection between the time-setting rod and the drive wheel 84 is conventional, of the type comprising in particular a sliding pinion, and will not be described in more detail to the extent that the person skilled in the art will not encounter of particular difficulty to implement it according to its needs.
  • the control wheel is arranged to cooperate with a first nozzle 86 of the latch 80 in order to control the pivoting.
  • the latter also comprises second and third nozzles 88, 89 arranged to transmit pulses, respectively, to the date counters and days of the week.
  • the tooth that allowed the pivoting of the rocker passes beyond the first mouth of the latter and releases it. Because the two following teeth of the control wheel are truncated, the first nose then has sufficient space to allow an immediate return of the latch in its rest position, under the effect of the action of the spring 82 .
  • the date counter is further incremented incrementally every three steps of rotation of the control wheel.
  • the tooth that allowed the pivoting of the rocker passes beyond the first mouth of the latter and releases it. Because the two following teeth of the control wheel are truncated, the first nose then has sufficient space to allow an immediate return of the latch in its rest position, under the effect of the action of the spring 82 .
  • the weekday counter is incremented successive increments every three steps in rotation of the control wheel.
  • the drive mechanism according to the present invention offers the possibility of adjusting the date at any time without risk of causing damage to the drive mechanism according to the invention, unlike many parts of Known watchmaking in which a date adjustment between 21h and 3h in the morning should be avoided because it can create damage to the watch movement.
  • the figure 8 represents an exploded perspective view of a mobile 102, equivalent to the mobile 2 illustrated on the figure 2 according to a second embodiment of the present invention.
  • the mobile 102 comprises a first gear 104 integral with a gun 127 on which are engaged a cam 128 and a resilient member 129 similar to those of first embodiment.
  • the hollow central axis of the barrel is intended to be engaged on a tenon carried by a frame member due to watch movement to mount the pivotal mobile.
  • the barrel 127 has a flat portion 132 with which cooperates an opening 133, of complementary shape, formed in the base 145 of the elastic member 129, and a shoulder 136 defining a radial guide surface for the cam 128, mounted on the barrel being free to turn relative to the latter.
  • the barrel 127 also carries a safety member 138 whose operation is similar to that of the safety member 38 described in connection with the first embodiment.
  • the security member 138 comprises a board whose periphery has a variable radius. More specifically here, the security member 138 comprises a first portion 201 having a first constant radius and extending over a little more than half a turn, and a second portion 202 having a second constant radius and s' extending over a little less than a quarter turn. While the first portion 201 is intended to be positioned opposite a portion of the cam 128 of small radius, its first ray is in all points inferior (or equal) to that of the cam. The second portion 202 is intended to be positioned facing the portion of the cam 128 having the largest radius and its second radius is substantially greater than that of the cam in this region. An inclined slope 139 relative to the radial direction defines the junction between the points of the smallest radius and the largest.
  • the safety member further comprises a slot 140 extending substantially in a circular path and intended to receive a pin 144 of the cam 128.
  • the elastic member 129 comprises an elastic arm 147 carrying two fingers in the form of claws 148, 149 facing each other at its free end intended to cooperate with the pin 144.
  • the pin 144 is free to position between the two claws 148 and 149.
  • FIGS. 9a and 9b are perspective views of the first and second faces of a lever 106 for cooperating with the mobile 102 which has just been described.
  • the lever 106 has a bore 160 for pivotally attaching it to a frame member of the watch movement and from which first and second arms 107 and 112 extend, and a spring 122.
  • the first arm 107 comprises, near its free end, a spout 161, assembled to the arm so as to have a slight play in pivoting, and a first retractable finger 163 pivotally mounted on the first arm 107 and arranged to transmit pulses at pinion 9 of the weekday counter 8.
  • the first arm 107 also has a feeler 168 intended to cooperate with the periphery of the safety member 138.
  • the lever 106 carries a lever 170, rotatably mounted on the lever, with an axis of rotation coaxial with the bore 160 and having first and second arms 171, 172 respectively superimposed on the first and second arms of the lever 107 , 112.
  • the free end of the first arm 171 of the rocker shaped substantially in the shape of a ball joint cooperates with the first retractable finger 163.
  • the free end of the second arm 172 of the rocker also substantially shaped in the form of a ball joint, cooperates with a second retractable finger 174, located on the free end of the second arm 172, to rotate substantially simultaneously to the first finger retractable 163.
  • rocker 170 and the spout 161 have antagonist surfaces of substantially complementary shapes, such that the first spout guiding the rocker and limiting the amplitude of its displacements.
  • a spring 165 here formed in one piece with the lever 106, is provided to apply a force on the second retractable finger 174 to define a rest position. At the same time, the spring 165 defines the rest position of the first finger 163 via the second finger 174 and the rocker 170. It will be noted that, advantageously, a tab 204 is provided on the rocker 170 to define a guide of the spring 165.
  • the second finger 174 is provided with an extension 206 having a first bent portion 208 followed by a third finger 210 defining a guide member, as will be explained later in connection with the following figures.
  • the first portion 208 has a reduced thickness with reference to the second finger 174, while the third finger 210 has a greater thickness than the second finger.
  • the Figures 10a to 10i represent the operating kinematics of the instantaneous driving mechanism according to the second embodiment of the present invention, in a first direction of rotation, in the same simplified front view, similar to that of the Figures 4a to 4d .
  • the first direction of rotation is here the normal operating direction of the mechanism, that is to say, especially when it is driven by the gear train.
  • the hour wheel 1 rotates in the clockwise direction on the Figures 10a to 10i , which corresponds to a rotation of the mobile 102 in the direction of rotation anti-clockwise.
  • the spout 161 follows, for nearly 24 hours, the periphery of the cam 128 to the position illustrated on the figure 10d , which corresponds to a time close to midnight of the following day.
  • the wheel 104 being driven in the direction of rotation anti-clockwise, it drives the cam 128 in the same direction by cooperation of its slot 140 with the pin 144 carried by the cam 128.
  • the third finger 210 rests on the pin 212 by a first curved surface 214.
  • This rotational movement of the second finger 174 causes rotation of the latch 170 in the clockwise direction with reference to the lever 106, thereby causing a pivoting of the first finger 163 in the anti-clockwise direction of rotation.
  • the lever rotates and the first and second fingers 163 and 174 are retracted and can pass next to the teeth with which they are intended to cooperate without being within their reach.
  • first and second fingers 163 and 174 then pivot in the opposite direction to approach the teeth with which they are intended to cooperate.
  • the cam 128 continues its rotation and still drives the lever 106, so the third finger 210 is again in abutment against the pin 212, this time by a second face 216 opposite the first face 214.
  • the board carrying the extension 206 and the second finger 174 then pivots in the direction of clockwise rotation, driving the first finger 163 in the same direction, via the rocker 170.
  • the thickness of the first portion 208 is chosen such that the pin 212 can pass through the extension 206 while passing at its level, as shown in FIG. figure 10h , while the lever 106 continues its fall.
  • each of the fingers 163 and 174 transmits a pulse to the wheel which it controls, under the effect of the action of the fall of the lever 106, as represented on the figure 10i .
  • the mechanism then returns to the position illustrated on the figure 10a .
  • the mechanism according to the present embodiment reacts in a manner similar to that described with respect to the first embodiment.
  • the safety member 138 acts on the lever 106, via the probe 168, to rotate it in the clockwise direction of rotation.
  • the third finger 210 reproduces the predefined path by its cooperation with the pin 212, as just described in connection with the Figures 10a to 10d .
  • the third finger 210 behaves as described above in relation to the figures 10e to 10i and each of the first and second fingers 163, 174 transmits a pulse to the corresponding wheel.
  • the figure 11 represents a front view of a construction detail according to an alternative embodiment of the present invention, more specifically a lever 306, similar to the lever 106 of the figure 9a but, whose end of the first arm 307, which interacts with the pinion 9 with seven teeth, has an extension 308 additional to increase the level of security of the device, in connection with the risk of double jumps of the body of display days of the week.
  • the extension 308 has substantially the shape of a spout arranged within the range of the toothing of the pinion 9, so that a wall 310 of the spout defines a stop for this toothing in the clockwise direction of rotation.
  • the extension 308 is positioned between two teeth of the pinion 9 to eliminate any risk of double jump.
  • an instantaneous drive mechanism comprising a mobile arranged to rotate in a predefined direction, in normal operating mode, and for controlling the movements of a lever for the purpose of transmitting instantaneous pulses to at least one counter of a watch movement, the mechanism further comprising a security member coaxial with the mobile and arranged to allow a rotation of the mobile in the contrary direction without risk of damage, without departing from the scope of the present invention.
  • the invention is not limited to the setting implement a single set third finger - pin. Indeed, it is possible to provide a similar set to control the pulses transmitted to the counter days of the week, for example or any other information displayed in the context of other applications.
  • the flip-flop 170 is no longer necessary in this case. It is then possible to adjust independently of one another the penetrations of the first and second fingers 163, 174 in the teeth associated with them.
  • the periphery of the cam has a curve studied as a function of the force of the spring 22, 122 as it rotates at substantially constant torque.

Claims (11)

  1. Momentaner Antriebsmechanismus für Uhrwerke, der ein Drehteil (2, 102) und einen Hebel (6, 106) aufweist, die dazu bestimmt sind, drehbar auf mindestens einem Gestellelement des Uhrwerks gelagert zu sein, wobei der Hebel eingerichtet ist, um einerseits mit dem Drehteil, um bewegt zu werden, und andererseits mit einem Zähler (8, 13) des Uhrwerks mit dem Ziel zusammenzuwirken, ihn mittels momentaner Antriebe zu inkrementieren, wobei das Drehteil (2, 102) ein erstes Rad (4, 104) aufweist, das dazu bestimmt ist, ausgehend von einem Antriebsorgan (1) des Uhrwerks angetrieben zu werden, und eingerichtet ist, um eine erste Kurvenscheibe (28, 128) des Drehteils drehbar anzutreiben, das koaxial zum ersten Rad ist (4, 104) und einen veränderlichen Radiusumfang aufweist, der eingerichtet ist, um mit einem Schnabel (61, 161) zusammenzuwirken, der durch einen ersten Arm (7, 107) des Hebels getragen wird, und ihn schrittweise von dem Mittelpunkt des Drehteils (2, 102) zu entfernen, wenn dieses letztere sich in eine erste Drehrichtung dreht, bevor er ihn unter der Einwirkung von elastischen Mitteln (22, 122) fallen lässt, wenn der Schnabel (61, 161) sich ausgehend von einem Punkt des Umfangs, der dem größten Radius entspricht, auf einen Punkt des Umfangs bewegt, der dem kleinsten Radius entspricht,
    dadurch gekennzeichnet, dass das Drehteil (2, 102) ein Sicherheitsorgan (38, 138) aufweist, das koaxial zu dem ersten Rad (4, 104) ist und eingerichtet ist, um mit dem Hebel (6, 106) zusammenzuwirken, um den ersten Arm (7, 107) von dem Mittelpunkt des Drehteils zu entfernen, wenn dieses letztere sich in die zweite Drehrichtung dreht, und es dem Schnabel (61, 161) zu ermöglichen, von dem Punkt, der dem kleinsten Radius entspricht, in Richtung des Punkts überzugehen, der dem größten Radius entspricht.
  2. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass das Sicherheitsorgan (38, 138) eine kinematische Verbindung (40, 44, 47, 140, 144, 147) mit der ersten Kurvenscheibe (28, 128) aufweist, derart, dass sie winklig in Bezug zueinander zwischen entsprechenden ersten und zweiten Winkelstellungen, einer ersten, die der ersten Drehrichtung zugehörig ist und in der der Schnabel (61, 161) mit der Kurvenscheibe (28, 128) zusammenwirkt, um die Stellung des Hebels (6, 106) zu definieren, und mindestens einer zweiten beweglich sind, die der zweiten Drehrichtung zugehörig ist und in der das Sicherheitsorgan (38, 138) mit dem Hebel (6, 106) zusammenwirkt, um seine Position zu definieren.
  3. Mechanismus nach Anspruch 2, dadurch gekennzeichnet, dass das Sicherheitsorgan (38, 138) eine Platte aufweist, die koaxial zur ersten Kurvenscheibe (28, 128) ist und an ihrem Umfang eine Steigung (39, 139) aufweist, die in Bezug zur radialen Richtung geneigt ist und sich zwischen Punkten erstreckt, die dem kleinsten Radius beziehungsweise dem größten Radius der Platte entsprechen, wobei diese letztere und die erste Kurvenscheibe (28, 128) über ein elastisches Organ (47, 147) drehfest aneinander befestigt werden, das derart eingerichtet ist, dass ihre relative winklige Beweglichkeit zwischen der ersten und der zweiten Position ermöglicht wird.
  4. Mechanismus nach Anspruch 3, dadurch gekennzeichnet, dass das Drehteil (2, 102) einen Sperrstift (44, 144) aufweist, der fest mit einem der Elemente von der ersten Kurvenscheibe (28, 128) und dem Sicherheitsorgan (38, 138) verbunden ist, und von dem ein Abschnitt in einem Spalt (40, 140) mit vordefinierter Länge angeordnet ist, der im anderen der Elemente eingerichtet ist, um die zwei relativen Winkelstellungen zu definieren.
  5. Mechanismus nach Anspruch 4, dadurch gekennzeichnet, dass das elastische Organ (47, 147) eine Auflage (45, 145), die drehfest mit demjenigen der Elemente verbunden ist, das den Spalt (40, 140) aufweist, und einen Finger (48, 49, 148, 149) aufweist, der eingerichtet ist, um mit dem Sperrstift (44, 144) zusammenzuwirken, um dazu zu neigen, die erste Kurvenscheibe (28, 128) und das Sicherheitsorgan (38, 138) in Richtung der ersten relativen Winkelstellung zu positionieren.
  6. Mechanismus nach einem der vorhergehenden Ansprüche, wobei außerdem der Hebel (6) einen ersten zurückziehbaren Finger (63) aufweist, der eingerichtet ist, um mindestens indirekt auf den ersten Zähler (8) einzuwirken und die Antriebe auf ihn zu übertragen, wobei der Hebel (6) ferner eine Zurückziehvorrichtung (65, 68, 70) aufweist, die durch das Drehteil (2) gesteuert wird und eingerichtet ist, um auf den ersten zurückziehbaren Finger (63) einzuwirken und ihn einerseits derart zu verschieben, dass er sich während der Phase, während der der erste Arm (7) von dem Mittelpunkt des Drehteils entfernt ist, außerhalb der Auflagefläche des Zählers (8) befindet, und ihn andererseits vor dem Fall des Hebels (6) freizugeben, derart, dass er einen Antrieb auf den ersten Zähler übertragen kann.
  7. Mechanismus nach Anspruch 3 und 6, dadurch gekennzeichnet, dass die Zurückziehvorrichtung (65, 68, 70) einen Taster (68) aufweist, der drehbar auf dem Hebel (6) gelagert ist und eingerichtet ist, um einerseits mit dem Umfang der Platte des Sicherheitsorgans (38), wobei diese einen Umfang aufweist, der ausgehend von dem Punkt mit dem kleinsten Radius bis zu dem Punkt mit dem größten Radius zunimmt, und andererseits mindestens indirekt mit dem ersten zurückziehbaren Finger (63) zusammenzuwirken.
  8. Mechanismus nach einem der Ansprüche 1 bis 5, wobei außerdem der Hebel (106) einen zurückziehbaren Finger (174) aufweist, der eingerichtet ist, um mindestens indirekt auf einen Zähler (13) einzuwirken und die Antriebe auf ihn zu übertragen, wobei der Mechanismus ferner eine Zurückziehvorrichtung (170, 206, 210, 212) aufweist, die eingerichtet ist, um auf den zurückziehbaren Finger (174) einzuwirken und ihn einerseits derart zu verschieben, dass er sich während der Phase, während der der erste Arm (107) von dem Mittelpunkt des Drehteils (102) entfernt ist, außerhalb der Auflagefläche des Zählers (13) befindet, und ihn andererseits vor dem Fall des Hebels (106) freizugeben, derart, dass er einen Antrieb auf den Zähler übertragen kann.
  9. Mechanismus nach Anspruch 8, dadurch gekennzeichnet, dass die Zurückziehvorrichtung (170, 206, 210, 212) ein Führungsorgan (210) aufweist, das fest mit dem zurückziehbaren Finger (174) verbunden ist und eingerichtet ist, um als Reaktion auf die Verschiebung des Hebels (106) mit einem festen Sperrstift (212) entlang eines vordefinierten Wegs zusammenzuwirken.
  10. Mechanismus nach einem der Ansprüche 6 bis 9, dadurch gekennzeichnet, dass der Hebel (6, 106) einen zweiten Arm (12, 112) aufweist, der einen zusätzlichen zurückziehbaren Finger (74, 163) trägt, der eingerichtet ist, um mit einem zweiten Zähler (8, 13) des Uhrwerks mit dem Ziel zusammenzuwirken, ihn mittels momentaner Antriebe zu erhöhen, die im Wesentlichen gleichzeitig mit denjenigen erfolgen, die auf den ersten Zähler (8, 13) einwirken, wobei die Zurückziehvorrichtung (65, 68, 70, 170, 206, 210, 212) eingerichtet ist, um auch auf den zweiten zurückziehbaren Finger (74, 163) einzuwirken und ihn einerseits derart zu verschieben, dass er sich während der Phase, während der der erste Arm (7, 107) vom Mittelpunkt des Drehteils (2, 102) entfernt ist, außerhalb der Auflagefläche des zweiten Zählers (8, 13) befindet, und er andererseits beim Fall des Hebels (6, 106) freigegeben wird, derart, dass er einen Antrieb auf den zweiten Zähler (8, 13) übertragen kann.
  11. Mechanismus nach Anspruch 10, dadurch gekennzeichnet, dass die Zurückziehvorrichtung (65, 68, 70, 170, 206, 210, 212) eine Wippe (70, 170) aufweist, die drehbar auf dem Hebel (6, 106) gelagert ist und ein erstes und ein zweites Ende (71, 72, 171, 172) aufweist, die eingerichtet sind, um mit dem zurückziehbaren Finger (63, 174) beziehungsweise mit dem zusätzlichen zurückziehbaren Finger (74, 163) zusammenzuwirken, derart, dass eine Drehung des einen eine Drehung des anderen über die Wippe antreibt.
EP12717214.6A 2011-03-23 2012-03-23 Momentaner antriebsmechanismus für ein uhrwerk Active EP2689298B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1152402A FR2973123B1 (fr) 2011-03-23 2011-03-23 Mecanisme d'entrainement instantane pour mouvement horloger
PCT/EP2012/055268 WO2012127054A1 (fr) 2011-03-23 2012-03-23 Mecanisme d'entrainement instantane pour mouvement horloger

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EP2689298A1 EP2689298A1 (de) 2014-01-29
EP2689298B1 true EP2689298B1 (de) 2015-06-03

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US8995238B2 (en) * 2013-03-28 2015-03-31 Rolex S.A. Device for displaying time information
EP3173876B1 (de) * 2015-11-26 2020-09-02 Rolex Sa Kalendersystem für uhr
CH713659A1 (de) * 2017-03-30 2018-10-15 Richemont Int Sa Uhr mit digitaler Zeitanzeige.
CH714365B1 (fr) * 2017-11-24 2023-03-31 Blancpain Sa Mobile d'horlogerie à roue unidirectionnelle.
CH715723B1 (fr) * 2019-01-10 2022-08-15 Richemont Int Sa Mécanisme de saut instantané d'un mobile d'affichage.
EP3904964B1 (de) * 2020-05-01 2023-03-08 Rolex Sa Anzeigevorrichtung einer uhrzeitanzeige oder eines abgeleiteten uhrzeitwerts und indexierungsvorrichtung
EP4246247A1 (de) * 2022-03-14 2023-09-20 Patek Philippe SA Genève Betätigungsmechanismus für uhr
CH719977A1 (fr) * 2022-08-22 2024-02-29 Patek Philippe Sa Geneve Mécanisme horloger à affichage sautant

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DE1242512B (de) * 1964-08-25 1967-06-15 United States Time Corp Anzeigevorrichtung an einer Uhr zum Anzeigen einer Vielzahl von Kalenderinformationen
GB1169329A (en) * 1968-03-29 1969-11-05 Suwa Seikosha Kk Calendar Timepiece
DE2060056A1 (de) * 1970-12-07 1972-06-15 Pforzheimer Uhren Rohwerke Datumschaltung fuer Uhren
CH483974A4 (de) * 1974-04-05 1976-03-15
SG102647A1 (en) * 2000-12-22 2004-03-26 Ebauchesfabrik Eta Ag Timepiece provided with a date having a large aperture
EP1336907A2 (de) * 2002-02-14 2003-08-20 Richemont International S.A. Steuerungsmechanismus für Einstellvorrichtungen einer Uhr sowie diesen Mechanismus integrierende Uhren
EP1406131A1 (de) 2002-10-01 2004-04-07 Manufacture Roger Dubuis S.A. Mechanische Vorrichtung zur Anzeige von Stunden und Minuten
ATE431580T1 (de) 2005-12-22 2009-05-15 Montres Breguet Sa Mit arretierungsmitteln versehene kalenderuhr
EP1857890B1 (de) * 2006-03-30 2012-05-30 Richemont International S.A. Vorrichtung zur Auslösung eines Impulses
EP1918792B1 (de) 2006-11-06 2010-04-21 Compagnie des Montres Longines, Francillon SA Uhr, die einen Korrekturmechanismus für eine Vorrichtung zur Anzeige einer Zeitgröße umfasst

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US8750080B2 (en) 2014-06-10
US20140022874A1 (en) 2014-01-23
FR2973123A1 (fr) 2012-09-28
EP2689298A1 (de) 2014-01-29
WO2012127054A1 (fr) 2012-09-27
FR2973123B1 (fr) 2014-01-03

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