Trigger mechanism for triggering a clockwork mechanism and a watch equipped with such a trigger mechanism

Abstract

The present invention relates to a trigger mechanism 56 for triggering a clockwork mechanism configured to perform a function. The invention also relates to a timepiece equipped with such a trigger mechanism.

Description

[Technical Field]

[0001] The present invention relates to a trigger mechanism for triggering a clockwork mechanism configured to perform a function.

[0002] The invention also relates to a timepiece equipped with such a trigger mechanism. [Background technology]

[0003] Publication CH717672 describes a mechanism for triggering an animation disc, for example, depicting a shooting star. The control member is the ratchet wheel of the barrel of the watch movement, which is rotated at least via an oscillating weight and possibly via an operating member that can be activated by the user. The trigger mechanism is essentially governed by the ratchet wheel of the barrel, which provides a substantially constant torque, so that the trigger mechanism is systematically triggered to start the animation.

[0004] Document CH717672 does not provide any information about the effects on the triggering of the animation or on the mechanism if a user tries to trigger the animation at will by actuating the movement member by applying insufficient or excessively large force.

[0005] Also known is the document EP2068210, which describes a trigger mechanism according to the preamble of attached claim 1. This trigger mechanism makes it possible to convert a continuous movement, e.g. a continuous rotation of the wheel of an input wheel and pinion, into a periodic, instantaneous triggering movement of the output wheel and pinion. No information is provided as to whether an insufficient or excessively large force has been applied to this trigger mechanism.

[0006] Furthermore, clockwork trigger mechanisms based on other configurations are known that are configured to manage the application of insufficient force to the control member by having what is called an "all-or-nothing" functionality. This means that the action associated with the trigger mechanism is triggered only if the user applies sufficient force to the control or operating member. Such "all-or-nothing" mechanisms are described, for example, in documents EP 1959317 and CH 3873. "All-or-nothing" mechanisms are typically based on a ratchet system, the operation of which is not always optimal. In addition, they do not allow the application of excessively large forces to the control member to be managed.

[0007] Clockwork trigger mechanisms are also known which are configured to be able to manage very large forces exerted on the control member by the user by having a device which ensures a constant output torque of the trigger mechanism. Such mechanisms are described, for example, in documents EP 1960844 and CH 717359. However, these mechanisms do not make it possible to manage excessively small forces exerted on the control member. [Prior art documents] [Patent documents]

[0008] [Patent Document 1] CH717672 [Patent Document 2] EP2068210 [Patent Document 3] EP1959317 [Patent Document 4] CH3873 [Patent Document 5] EP1960844 [Patent Document 6] CH717359 [Patent Document 7] CH2021 / 0070690 Summary of the Invention [Problem to be solved by the invention]

[0009] The present invention aims to remedy these drawbacks by proposing a trigger mechanism for triggering clockwork mechanisms that makes it possible to adequately manage the application of insufficient and excessively high forces on the control member alike. [Means for solving the problem]

[0010] To this end, the present invention relates to a trigger mechanism for triggering a clockwork mechanism configured to perform a function, said trigger mechanism comprising: a control device including a control member; - a rotationally movably mounted trigger wheel and pinion, comprising a trigger member intended to be rotated by a control member, a trigger operating wheel kinematically connected to the trigger member and integral in rotation with a first end of a resilient member, and a trigger output wheel kinematically connected to an element of a clockwork mechanism and integral in rotation with a second end of the resilient member, wherein said trigger member is a rotating trigger cam; - an actuation device kinematically coupled to the trigger actuation wheel and configured to lock or release the trigger output wheel in response to rotation of said trigger actuation wheel; Equipped with The control member is configured to exert a first rotational driving force on said trigger cam.

[0011] According to the present invention, the trigger mechanism includes a trigger lever configured to follow a trigger cam, and the trigger lever rotates when following the trigger cam rotated by a control member. - storing energy to counteract the first rotational driving force by exerting a second rotational driving force on said trigger cam as long as the first rotational driving force is below a predetermined threshold; and - returning said energy beyond said predetermined threshold such that said second rotational driving force exerted on the trigger cam causes rotation of the trigger operating wheel, causing the actuating device that previously locked the trigger output wheel to release said trigger output wheel and perform said function. The aforementioned trigger cam and trigger lever are configured so that:

[0012] The trigger mechanism according to the present invention is therefore of the "all or nothing" type by allowing the trigger output wheel to rotate, which allows the clockwork mechanism to perform its function only if the force applied to the control member is sufficient to cause rotation of the trigger cam and therefore rotation of the trigger operating wheel required to operate the operating device to release the trigger output wheel and perform its function.

[0013] In addition, the trigger mechanism according to the invention advantageously constitutes an intermediate device that makes it possible to manage the force applied to the control member by standardizing the torque that must be transmitted to the associated clockwork mechanism in order to perform its function: the clockwork mechanism therefore receives a constant torque from the trigger output wheel connected to the elastic member, this torque being independent of the force applied to the control member, which may in particular be a very large force.

[0014] The trigger lever is advantageously provided with a return spring configured to store and return said energy as the trigger lever follows the rotating trigger cam, enabling said trigger lever to exert a second rotational driving force on the trigger cam.

[0015] The trigger cam preferably has n branches defining n peaks and n valleys, each branch having a rising flank and a falling flank.

[0016] The return spring of the trigger lever is advantageously configured to store said energy when the trigger lever follows the ascending flank of the rotating trigger cam and to return said energy when the trigger lever follows the descending flank of the rotating trigger cam, enabling the trigger lever to exert a second rotational driving force on the trigger cam.

[0017] In order to exert a first rotational driving force on the trigger cam, the control member is advantageously a control lever having a hook preferably configured to grip the tip of one of the branches of the trigger cam and thereby rotate said trigger cam.

[0018] The trigger cam is advantageously coaxial with the trigger operating wheel and rotates together with it, which makes it possible to reduce the volume of the mechanism.

[0019] The trigger lever preferably includes a runner configured to follow the trigger cam, such a runner allowing for reduced friction and easier follow-up of the trigger cam.

[0020] The elastic member is preferably a spiral coil spring.

[0021] The actuation device advantageously comprises an actuation pinion which rotates freely and is kinematically connected to the trigger actuation wheel, an actuation cam which is integral with said actuation pinion, an actuation fork which is mounted in a rotationally movable manner and which is configured to cooperate with the actuation cam, and an actuation anchor which rotates integrally with the actuation fork, said actuation anchor comprising two arms which are configured to alternately lock a locking pawl which rotates integrally with a locking pinion which is configured to be kinematically connected to the trigger output wheel.

[0022] In a preferred embodiment, the clockwork mechanism is the corrector of at least one display element, for example the corrector of a display element associated with GMT time.

[0023] The invention also relates to a timepiece comprising a clockwork mechanism adapted to perform a function and a trigger mechanism for triggering said clockwork mechanism as defined above.

[0024] Other characteristics and advantages of the present invention will become apparent from the following detailed description of embodiments of the invention, given as non-limiting examples, with reference to the accompanying drawings, in which: [Brief explanation of the drawings]

[0025] [Figure 1] 1 is an isometric view of a trigger mechanism according to the invention used in a timepiece for correcting a display element associated with GMT time. FIG. [Figure 2] FIG. 1 is an isometric view of a differential gear. [Figure 3] FIG. 3 is a cross-sectional view of the differential gear of FIG. 2. [Figure 4] An isometric view of a phase-shifting wheel and pinion. [Figure 5] FIG. 5 is an isometric view of the lower phase-shifting wheel of the phase-shifting wheel and pinion of FIG. [Figure 6] FIG. 2 is a diagram of a display device configured to display the difference between local time HT and GMT time used in the present invention. [Figure 7] Isometric view of the trigger wheel and pinion. [Figure 8] FIG. 7 is an isometric view of the trigger operating wheel of the trigger wheel and pinion. [Figure 9] FIG. 1 is an isometric view of an actuation device. [Figure 10] 10 is an isometric view of an actuation pinion, an actuation cam, and an actuation fork of the actuation device of FIG. 9. FIG. [Figure 11] 1A-1C are top views of a trigger mechanism according to the present invention in various stages of operation; [Figure 12] 1A-1C are top views of a trigger mechanism according to the present invention in various stages of operation; [Figure 13]1A-1C are top views of a trigger mechanism according to the present invention in various stages of operation; [Figure 14] 1A-1C are top views of a trigger mechanism according to the present invention in various stages of operation; DETAILED DESCRIPTION OF THE INVENTION

[0026] The present invention relates to a trigger mechanism for triggering a clockwork mechanism. In the exemplary embodiment described, said clockwork mechanism is a correction mechanism for a display element associated with GMT time provided in a timepiece, elements useful for understanding the invention are shown in Figure 1.

[0027] The aforementioned timepiece comprises, in a known manner, an cannon pinion 1 which integrally carries a minute display element (hand, etc., not shown) and which is kinematically coupled to a drive organ (not shown) of the timepiece, such as a barrel. During normal operation of the timepiece, in a conventional manner, the cannon pinion 1 is driven via the drive organ and drives an hour wheel (not shown) via a drive wheel and pinion 2, which corresponds to the minute wheel and pinion, and which is arranged to drive a first local time HT display element (hand, etc., not shown) in cooperation with the minute display element.

[0028] The watch also comprises a second display member, such as a hand, symbolically represented by reference numeral 4, configured to be able to display GMT time in a time zone different from the time zone of local time HT.

[0029] Obviously, any other suitable components for displaying local HT and GMT times can be used.

[0030] The timepiece also comprises a correcting mechanism 6 for the second display member 4, which is configured to be able to correct the GMT time independently of the local time HT.

[0031] The aforementioned correction mechanism 6 is explained in more detail below.

[0032] The timepiece also comprises a drive mechanism 8 for the second display member 4, which drive mechanism 8 comprises a differential gear 10 and a phase-shifting wheel and pinion 12.

[0033] More specifically, and with reference to Figures 2 and 3, the aforementioned differential gear 10 comprises at least one upper differential wheel and pinion 14 configured to be kinematically coupled to the second display member 4, a lower differential wheel and pinion 16 configured to be kinematically coupled to the drive wheel and pinion 2 of the first display member (minute wheel and pinion) by means of a phase-shifting wheel and pinion 12 as will be explained below, and an input part 18 configured to be kinematically coupled to the correction mechanism 6 of the second display member 4.

[0034] More specifically, the differential gear 10 preferably comprises a differential block 20 pivotally mounted on a component frame and mounted so as to rotate freely on two half-axes 22a, 22b integral with the upper and lower differential wheel and pinions 14, 16. The differential block 20 carries at least one first intermediate wheel 24a configured to mesh with a pinion 26a integral with the half-axle 22a of the upper differential wheel and pinion 14 and a second intermediate wheel 24b configured to mesh with a pinion 26b integral with the half-axle 22b of the lower differential wheel and pinion 16, the intermediate wheels 24a, 24b being mounted so as to rotate freely on the differential block 20.

[0035] The differential block 20 is also integral with the wheel that forms the input 18 of the differential gear 10 and is configured to be kinematically coupled to a trigger mechanism as will be explained below.

[0036] 4 and 5, the phase-shift wheel and pinion 12 comprises a lower phase-shift wheel 28 configured to be kinematically coupled to the drive wheel and pinion 2 of the first display member, more specifically to the minute wheel 2a. As shown in Fig. 1, the lower phase-shift wheel 28 is also configured to be kinematically coupled to the lower differential wheel and pinion 16 of the differential gear 10, for example by means of two integral stepped intermediate wheels 30a, 30b, the pinion 30a being configured to cooperate with the lower phase-shift wheel 28 and the pinion 30b being configured to cooperate with the lower differential wheel and pinion 16.

[0037] The phase-shifting wheel and pinion 12 also comprises an upper phase-shifting wheel 32 that is coaxial with the lower phase-shifting wheel 28 and configured to drive the second display member 4 and to be kinematically coupled to the upper differential wheel and pinion 14 of the differential gear 10.

[0038] The upper phase-shift wheel 32 is also kinematically coupled to the lower phase-shift wheel 28 in a detachable manner, so that the aforementioned upper phase-shift wheel 32 is separated from the lower phase-shift wheel 28 during correction of GMT time independent of local time HT by the correction mechanism 6, while enabling repositioning of the second display member 4 synchronized with the positioning of the first display member after the correction.

[0039] The upper phase-shifting wheel 32 is kinematically connected to the lower phase-shifting wheel 28 in an detachable manner by a phasing cam 34 integral with the lower phase-shifting wheel 28 and coaxial with the lower phase-shifting wheel 28, and a hammer 36 on which a phase-shifting spring 38 carried by the upper phase-shifting wheel 32 is mounted, the hammer 36 being configured to cooperate with the phase-adjusting cam 34.

[0040] More specifically, the hammer 36 is pivotally attached to the upper phase shift wheel 32 by a pivot shaft that is integrally attached to the upper phase shift wheel 32 described above.

[0041] The hammer 36 has a first end 36a provided with a runner 40 that cooperates with the phase adjustment cam 34 to promote tracking of the phase adjustment cam 34, and a second end 36b that cooperates with a first end 38a of the phase shift spring 38. The second end 38b of the phase shift spring 38 is pivotally attached to the upper phase shift wheel 32 by a pivot shaft that is integrally attached to the upper phase shift wheel 32 described above.

[0042] The watch may also be equipped with a display device 42, shown in FIG. 6, configured to display the difference between local time HT and GMT time.

[0043] The display device 42 includes a fixed dial 44, a display 46 fixedly mounted on the dial 44 and configured to define local time HT as a reference, and a third display member 48 rotatably mounted relative to the dial 44 to allow it to be moved, and the position of the third display member 48 on the dial 44 relative to the display 46 indicates the difference between local time HT and GMT time. In the operational mode, the third display member 48 is fixed. The dial 44 includes a scale to indicate the time zone difference between local time HT and GMT time using the third display member 48. For example, the fixed dial 44 can be graduated from 0 to -12 on one side of the zero indicated by the fixed display 46 and graduated from 0 to +12 on the other side of the zero, allowing the third display member 48 to directly indicate to the user the time zone difference from 0 hours to 12 hours in one or the other direction. In the example of FIG. 6, the third display member 48 shows a difference of −11 hours on the dial 44 to inform the user that local time HT is 11 hours ahead of GMT time.

[0044] The aforementioned display device 42 may also comprise a day / night disc 50 having two angular sectors 52 and 54 extending over 180° on either side of the axis of symmetry of the disc. The disc 50 is driven clockwise by the watch movement of the timepiece by one revolution every 24 hours. The position of the indicator 46 and the third display member 48 on the day / night disc 50 makes it possible to indicate whether it is day or night in local HT and GMT time, respectively, at a given time.

[0045] Such a display device 42 is described in the applicant's application CH2021 / 0070690.

[0046] In order to enable the difference between the displayed local time HT and the GMT time to be corrected independently of the local time HT during the correction of the second GMT time display member 4, i.e. during the correction of the third display member 48, the display device 42, more particularly the aforementioned third display member 48, is kinematically coupled to a trigger mechanism, as will be described in detail below, so that it can be corrected by the correction mechanism 6 of the second display member 4.

[0047] The correction mechanism 6 of the second indicating member 4 includes a trigger mechanism 56 .

[0048] With reference to Figures 1 and 7 to 10, the aforementioned trigger mechanism 56 comprises a control device including a control member 58 intended to be accessible to a user, for example via a push button, for performing the function of the associated clockwork mechanism, which here is the function of correcting the second GMT time display member 4 and, if present, also the third display member 48, which indicates the time zone difference between local time HT and GMT time, independently of local time HT.

[0049] The control member 58 is advantageously a control lever pivotally mounted on the frame and having its return spring 60 mounted thereon. The control lever is actuated by the user, for example via a push button (not shown).

[0050] The trigger mechanism 56 also comprises a trigger wheel and pinion 62, which can be seen in particular in Figure 7, configured to be rotatably mounted on the frame of the part. The trigger wheel and pinion 62 comprises a trigger member 64 intended to be rotated directly or indirectly by the control member 58, a trigger operating wheel 66 kinematically connected to the trigger member 64 and rotating integrally with a first end of a resilient member 68, and a trigger output wheel 70 kinematically connected to an element of the clockwork mechanism to be triggered and rotating integrally with a second end of the resilient member 68. The resilient member is advantageously a spiral coil spring.

[0051] In the example described, the trigger output wheel 70 is kinematically coupled to the wheel constituting the input part 18 of the differential gear 10, making it possible to correct the second GMT time display member 4 independently of the local time HT. The trigger output wheel 70 is also kinematically coupled to the third display member 48, if present, making it possible to correct said third display member 48 at the same time that the second display member 4 is corrected.

[0052] The trigger mechanism 56 also includes an actuation device 72, shown in Figures 9 and 10, kinematically coupled to the trigger actuation wheel 66 and configured to lock or release the trigger output wheel 70 in response to rotation of the trigger actuation wheel 66.

[0053] The actuation device 72 advantageously comprises an actuation pinion 74 mounted so as to be freely rotatable on the frame and configured to be kinematically coupled to the trigger actuation wheel 66 .

[0054] The actuation device 72 also comprises an actuation cam 76 which is integral with the aforementioned actuation pinion 74 and constitutes an eccentric member relative to the actuation pinion 74, more particularly relative to the axis of rotation of the actuation pinion 74. The actuation device 72 further comprises an actuation fork 78 which is mounted on a frame in a rotationally movable manner about an axis 80 and which is configured to cooperate with the aforementioned actuation cam 76 so as to be alternately pivoted in one direction or the other.

[0055] The actuation device 72 also includes an actuation anchor 82 rotatably mounted on a shaft 80 and configured to rotate integrally with the actuation fork 78, for example, via a post 84 integral with the actuation anchor 82 and the actuation fork 78. The actuation anchor 82 includes two arms 82a, 82b configured to alternately lock a locking pawl 86 that rotates integrally with the locking pinion 88. The locking pinion 88 is mounted for free rotation on the frame and kinematically coupled to the trigger output wheel 70. When the locking pawl 86 is locked by one of the arms 82a, 82b, the locking pinion 88 is locked, preventing rotation of the trigger output wheel 70. When the actuation anchor 82 pivots to release the locking pawl 86, the locking pinion 88 rotates freely, releasing the trigger output wheel 70 and allowing it to rotate under the action of the energy released by the elastic member 68.

[0056] The actuation pinion 74, the locking pawl 86, and the locking pinion 88 are advantageously aligned along the same axis.

[0057] The trigger member 64 is advantageously a rotary trigger cam. Said trigger cam 64 preferably has n branches 64a defining n peaks and n valleys. To this end, each of the branches 64a has an ascending flank and a descending flank. In the example shown, the trigger cam has four branches 64a.

[0058] The trigger cam 64 is advantageously coaxial with the trigger operating wheel 66 and rotates integrally therewith. The trigger cam 64 can be made integral with the trigger operating wheel 66, for example by means of a cylindrical counterform 90 which is integral with the trigger operating wheel 66 and coaxial with the trigger cam 64 and the trigger operating wheel 66. The counterform 90 is provided with four catches 90a as shown in Figure 8 and is configured to fit into corresponding openings 64b provided in the center of the trigger cam 64, the catches 90a resting against the inner walls of the openings 64b.

[0059] The trigger output wheel 70 is mounted between the trigger cam 64 and the trigger operating wheel 66 so as to be able to rotate freely on a counterform 90 coaxially with the trigger cam 64 and the trigger operating wheel 66. The spiral coil spring 68 is positioned between the trigger output wheel 70 and the trigger operating wheel 66, with one of its ends being integral with the trigger output wheel 70 and the other end being integral with the trigger operating wheel 66.

[0060] The control member 58, here a control lever, is advantageously configured to exert a first rotational driving force directly or indirectly on said trigger cam 64, making it possible to initiate the rotation of said trigger cam 64. For this purpose, the control lever advantageously has, at the side of its end cooperating with the trigger cam 64, an arm 92, which can be seen in particular in FIGS. 1 and 11, pivotally attached to said control lever 58 and whose free end is terminated by a hook 92a (see FIG. 11). Said hook 92a is configured to rotate said trigger cam 64, for example by gripping the tip of one of the branches 64a of said trigger cam 64. As will be seen below, the hook 92a more particularly makes it possible to exert a first driving force on said trigger cam 64, making it possible to initiate the rotation of said trigger cam 64.

[0061] The trigger mechanism 56 also advantageously comprises a trigger lever 94 pivotally mounted on the frame and adapted to follow the trigger cam 64 by means of a follower member. When the trigger lever 94 follows the aforementioned trigger cam 64, the rotation of which is initiated by the control member 58, here the control lever, the trigger lever 94 - storing energy to act counteract the first rotational driving force by exerting a second rotational driving force on said trigger cam 64 as long as the first rotational driving force is below a predetermined threshold; and - returning said energy beyond said predetermined threshold so that said second rotational driving force exerted on the trigger cam 64 causes the trigger actuation wheel 66 to rotate, thereby terminating the rotation of the trigger cam 64, thereby enabling the actuation device 72, which had previously locked the trigger output wheel 70, to release said trigger output wheel 70 and perform the function described above. The trigger cam 64 and the trigger lever 94 are configured to allow the trigger cam 64 to rotate in the second direction. To this end, the trigger lever is advantageously provided with a return spring 96 configured to store and return the aforementioned energy when the trigger lever 94 follows the rotating trigger cam 64, allowing the trigger lever 94 to exert the aforementioned second rotational driving force on the trigger cam 64.

[0062] More specifically, the return spring 96 is configured to store the aforementioned energy when the trigger lever 94 follows the ascending flank of the rotating trigger cam branch 64a' and to return this energy when the trigger lever 94 follows the descending flank of the rotating trigger cam branch 64a', enabling the trigger lever 94 to exert a second rotational driving force on the aforementioned trigger cam 64.

[0063] For this purpose, the trigger lever 94 advantageously has, on the side of its end which cooperates with the trigger cam 64, an arm 98, which can be seen in particular in Figures 1 and 11, and which arm 98 has at its free end a runner 100 (see Figure 11) which constitutes a reading member adapted to follow the trigger cam 64 by following the ascending and descending flanks of each branch 64a.

[0064] The various elements of the trigger mechanism 56 are dimensioned and configured so that the function associated with the clockwork mechanism is performed only when said control lever 58 exerts a first necessary and sufficient rotational driving force on the trigger cam 64, particularly in response to the force of the return spring 96, the first rotational force being at least equal to a predetermined threshold determined by the structure of the elements of the trigger mechanism 56. The rotation of said trigger cam 64 is such that the return spring 96 of the trigger lever 94 winds and stores energy when the trigger lever 94 follows the ascending flank of one of the branches 64a of the rotating trigger cam 64. This energy is then returned when the trigger lever 94 follows the descending flank of said branch 64a of the rotating trigger cam 64, thus enabling the trigger lever 94 to exert a second rotational driving force on the trigger cam 64 and drive the trigger cam 64 together with the trigger operating wheel 66 associated with the trigger cam 64 in a complementary rotational phase. In this way, the actuating device 72 that had locked the trigger output wheel 70 is actuated to release said trigger output wheel 70, allowing the trigger output wheel 70 to be driven to rotate by the energy released by the elastic member 68, thereby performing its function.

[0065] With more particular reference to the correction mechanism 6 of the second GMT time display member 4 and the correction mechanism 6 independent of the local time HT of the third display member 48 which indicates the time zone difference, if any, between the above-mentioned local time HT and GMT time, the operation of the correction mechanism 6 and its trigger mechanism 56 will be explained below with reference to Figures 11 to 14.

[0066] During normal operation of the timepiece, the trigger mechanism 56 is in a rest state as shown in Figure 11. In this initial rest state, the trigger mechanism 56 is in a stable rest position with the runner 100 of the trigger lever 98 positioned in a valley at the bottom of the rising flank toward the tip of one of the branches 64a' of the trigger cam 64. The hook 92a of the control lever is preferably positioned at the tip of one of the branches 64a of the trigger cam 64. The locking pawl 86 is locked by the arm 82a of the actuation anchor 82 of the actuation device 72 so that the trigger output wheel 70 is locked against rotation and held by the locking pinion 88.

[0067] The drive mechanism of the timepiece drives the cannon pinion 1, which in turn drives the minute display element and the hour wheel via the minute wheel and pinion 2. The hour wheel drives the first local time HT display element in a standard manner. The minute wheel 2a also drives the lower phase shifter wheel 28 of the phase shifter wheel and pinion 8 and the upper phase shifter wheel 32, which is connected to the lower phase shifter wheel 28 by a phase adjustment cam 34 / hammer 36 assembly. The second GMT time display element 4 is then driven in a synchronized manner with the first local time HT display element. In this state, the lower phase shifter wheel 28 continuously drives the lower differential wheel and pinion 16 of the differential gear 10 via two stepped intermediate wheels 30a, 30b, and the upper phase shifter wheel 32 continuously drives the upper differential wheel and pinion 14 of the differential gear 10. The input wheel 18 of the differential gear 10 is locked by the trigger mechanism 56, so the differential block 20 does not rotate. The intermediate wheels 24a and 24b are also continuously driven by the pinions 26a, 26b integral with their respective half shafts 22a, 22b. The trigger output wheel 70 is locked, so the third indicator member 48 remains fixed.

[0068] During the adjustment of the second display member 4 and, if present, the third display member 48, independent of the local time HT, the user actuates the control member 58, here a control lever, for example via a push button on the control device, according to a force F indicated in FIG. 12 by an arrow. When the control lever pivots, the hook 92a of the control lever grips the tip of the branch 64a of the trigger cam 64, thereby starting and rotating said trigger cam 64. During this rotation of the trigger cam 64, the runner 100 of the trigger lever 94 follows said trigger cam 64 by following the ascending flank of the other branch 64a' of the trigger cam 64, which has the effect of winding the return spring 96 of the trigger lever 94. At the same time, the rotation of the trigger cam 64 rotates the trigger operating wheel 66 integral with the trigger cam 64, which has the effect of winding the potentially pre-wound trigger spring 68, while the trigger output wheel 70 is still locked by the actuation device 72. In fact, as shown in FIG. 12, the elements of the trigger mechanism 56 are dimensioned so that during this winding phase, rotation of the trigger operating wheel 66 results in rotation of the operating pinion 74 and its operating cam 76, and thus of the operating fork 78 and operating anchor 82, but not enough to cause the arm 82a to release the locking pawl 86.

[0069] 13, the runner 100 of the trigger lever 94 continues to follow its rotating trigger cam 64, passing the tip of the branch 64a' and following the downward flank of the aforementioned branch 64a' of the trigger cam 64, such that the return spring 96 of the trigger lever 94 redistributes stored energy to the trigger lever 94 which then motors the trigger cam 64. As the rotation of the trigger cam 64 continues, the trigger spring 68 continues to wind.

[0070] The elements of the trigger mechanism 56 are sized so that, as the runner 100 moves down the flank of the trigger cam 64, rotation of the aforementioned trigger cam 64 and trigger operating wheel 66 causes sufficient rotation of the operating pinion 74, its operating cam 76, operating fork 78, and operating anchor 82, as shown in FIG. 13, so that the arm 82a pivots sufficiently to disengage from and release the locking pawl 86.

[0071] Since the locking pawl 86 is released, the locking pinion 88 is free to pivot, so that the locking pinion 88 no longer locks the trigger output wheel 70, which is then released. The trigger output wheel 70 is then rotated under the action of the energy stored by the trigger spring 68.

[0072] If there is a third display member 48 that indicates the time zone difference between local time HT and GMT time, rotation of the released trigger output wheel 70 directly drives the third display member 48, which is kinematically coupled to the trigger output wheel 70, to correct the third display member 48, moving the third display member 48 step by step until the desired time zone difference is displayed on the dial 44.

[0073] At the same time, the rotation of the released trigger output wheel 70 rotates the input wheel 18 of the differential gear 10 to correct the second display member 4 .

[0074] For this purpose, the rotation of the input wheel 18 of the differential gear 10 rotates the differential block 20 so that the intermediate wheel 24a or 24b rotates the half shaft 22a or 22b via the pinion 26a or 26b, and thus rotates the upper differential wheel and pinion 14 and the lower differential wheel and pinion 16, respectively. The lower differential wheel and pinion 16 then constitutes the first output of the differential gear 10, which is kinematically connected to the lower phase-shifting wheel 28 and the minute wheel and pinion 2 of the phase-shifting wheel and pinion 12. The rotation of the lower differential wheel and pinion 16 then reduces the gear play of the differential gear 10 until the cannon pinion 1 is locked. This locking causes the upper differential wheel and pinion 14 to drive the upper phase-shifting wheel 32, thereby constituting the second output of the differential gear 10, which is kinematically connected to the upper phase-shifting wheel 32 of the phase-shifting wheel and pinion 12. Rotation of the upper differential wheel and pinion disengages the upper phase shifter wheel 32 from the lower phase shifter wheel 28 by means of the phase adjustment cam 34 / hammer 36 assembly, and rotation of the upper phase shifter wheel 32 rotates and corrects the second indicator member 4.

[0075] The differential block 20 rotates step by step through an angle determined by the gear ratio between the trigger cam 64 and the trigger output wheel 70 of the trigger cam 64. These steps determine the offset of the third display member 48, which here indicates the time zone difference between local time HT and GMT time, and the phase shift angle of the phase-shifting wheel and pinion 12, in order to correct the second GMT time display member 4. In the phase-shifting wheel and pinion 12, the correction angle of the upper phase-shifting wheel 32 corresponds to one step of the phase adjustment cam 34.

[0076] The correction mechanism 6 therefore enables the step-by-step correction of the second GMT hour display member 4 and, if present, the simultaneous correction of the third display member 48, independently of the local time HT, i.e. independently of the first local time HT display member and the minute display member.

[0077] The phase adjusting cam 34 / hammer 36 assembly of the phase-shifting wheel and pinion 12 enables the second GMT hour display member 4 to be precisely repositioned relative to the position of the first display member following each correction of said second display member 4. In fact, the runner 40 of the hammer 36 attached to the upper phase-shifting wheel 32 of the phase-shifting wheel and pinion 12 leaves one valley of the phase adjusting cam 34 to precisely reposition itself within the next valley, thereby positioning said second GMT hour display member 4 so that its position remains perfectly synchronized with that of the first local time HT display member relative to the position of the minute display member.

[0078] The phase-shift wheel and pinion 12 also advantageously makes it possible to reduce the play of the differential gear 10 in order to avoid excessive play between the minute wheel and pinion 2 and the display operated by the upper phase-shift wheel 32, here the second GMT hour display member 4. In addition, since the display is operated by the upper phase-shift wheel 32 of the phase-shift wheel and pinion 12, the upper phase-shift wheel 32 also makes it possible to avoid permanently transmitting torque to the differential gear 10 in order to drive said display.

[0079] Following the unlocking of the locking pawl 86, the trigger lever 94 continues its repositioning in the valley of the trigger cam 64. During this triggering phase, it may be possible to provide a rigid link (e.g., including an eyelet and pin) between the trigger operating wheel 66 and the trigger output wheel 70 to increase the energy supplied to unlock the phase shift of the phase-shifting wheel and pinion 12.

[0080] Concurrently with this triggering phase, the control lever (still under the influence of the user) completes its movement and contacts a stop (not shown) so as to no longer supply energy to the trigger cam 64 .

[0081] 14, the locking pawl 86, which has been pivoted together with the locking pinion 88 during the correction phase, abuts the other arm 82b of the actuation anchor 82 once the phase shift has been achieved. The trigger output wheel 70 is again locked. The locking of the locking pawl 86 by the actuation anchor 82 is alternately effected by the arms 82a and 82b each time the control member 58 is sufficiently actuated to perform the associated function.

[0082] When the user releases the push button of the control member 58, here a control lever, the hook 92a of the control lever repositions itself in the valley behind the branch 64a of the trigger cam 64 (i.e., downstream of the branch 64a) so that it is ready to grip the tip of the following branch 64a', as shown in Figure 14. The runner 100 of the trigger lever 94 returns to its stable rest position in the valley behind the branch 64a'.

[0083] It is easy to understand that if the user does not apply sufficient force to the control member 58, the correction mechanism will not be triggered and therefore no correction will be made. In fact, as mentioned above, the various elements of the trigger mechanism 56 are dimensioned and configured so that a first rotational driving force of the control lever 58 exerted on the trigger cam 64, which is equal to or exceeds a predetermined threshold, gives rise to a second rotational driving force exerted by the trigger lever 94. This second driving force makes it possible to obtain the necessary and sufficient rotation of said trigger cam 64 (and therefore of the associated trigger operating wheel 66, operating pinion 74, its operating cam 76, operating fork 78 and operating anchor 82) to release the locking pawl 86 and thus the trigger output wheel 70 so as to perform its function of correcting, here step by step, the second GMT time display member 4 and, if present, the third display member 48, independently of the local time HT.

[0084] If the force applied by the user is too weak, the first rotational driving force exerted by the control lever will be below a predetermined threshold of driving force that urges the aforementioned trigger cam 64 to rotate sufficiently to release the locking pawl 86, and as a result, the rotation of the actuation anchor 82 will not be sufficient to release the locking pawl 86. Thus, the trigger output wheel 70 will remain locked and will be unable to perform its function.

[0085] When the force applied by the user is sufficient so that the first rotational drive force exerted by the control lever is equal to or exceeds a predetermined threshold of necessary and sufficient rotational drive force, the rotation of the trigger cam 64 will be sufficient to cause the actuation anchor 82 to pivot sufficiently to release the locking pawl 86 and therefore the trigger output wheel 70 to perform its function.

[0086] The trigger mechanism of the present invention is therefore of the "all or nothing" type, allowing rotation of the trigger output wheel 70, which allows the clockwork mechanism to perform its function, only if the force applied to the control member 58 is sufficient to cause the rotation of the trigger cam 64, and therefore the trigger operating wheel 66, required to operate the operating device 72 to release the trigger output wheel 70.

[0087] In addition, the trigger mechanism 56 according to the invention advantageously constitutes an intermediate device that makes it possible to manage the force applied to the control member 58 by standardizing the torque that must be transmitted to the clockwork mechanism in order to perform its function. The clockwork mechanism therefore receives a constant torque from the trigger output wheel 70, linked to the properties of the elastic member 68, independent of the force applied by the user to the control member 58. In particular, even if the user applies a very large force to the push button, it is not possible to provide momentum to said clockwork mechanism.

[0088] The trigger mechanism according to the present invention therefore makes it possible to equally appropriately manage the application of insufficient force to the control member 58 by being of the "all or nothing" type, and the application of excessive force to the control member 58 by allowing it to perform its function at "constant force".

[0089] The advantage of the trigger mechanism according to the invention is that the user provides the impulse required to trigger the mechanism, and then said mechanism performs the function itself, so that the user cannot provide momentum to the correction mechanism, even if he presses the push button too hard.

[0090] In addition, the use of the rotation locking pawl 86 between the two stops formed by the arms 82a, 82b of the operating anchor 82 and the locking pinion 88 integral with the locking pawl 86 makes it possible to precisely control the angle of rotation of the correction gear train when correcting the second GMT time display member 4 and, if present, the third display member 48 independently of the local time HT, which makes it possible to enhance the accuracy of the repositioning of the second GMT time display member 4 and, if present, the third display member 48 after their correction.

[0091] The above example relates to a correction mechanism for a display element linked to GMT time. It is clear that the trigger mechanism according to the invention can be used in clockwork mechanisms configured to perform other functions, such as a mechanical animation configured to be triggered on demand by a user and operated by the upper phase-shift wheel 32 of the phase-shift wheel and pinion 12.

Claims

1. A trigger mechanism (56) for triggering a clockwork mechanism configured to perform a function, comprising: a control device comprising a control member (58); a rotationally movable mounted trigger wheel and pinion (62) comprising a trigger member intended to be rotated by said control member (58), a trigger operating wheel (66) kinematically connected to said trigger member and rotating integrally with a first end of a resilient member (68), and a trigger output wheel (70) rotating integrally with a second end of said resilient member (68) and kinematically connected to an element of said clockwork mechanism, said trigger member being a rotating trigger cam (64); an actuation device (72) kinematically coupled to the trigger actuation wheel (66) and configured to lock or release the trigger output wheel (70) in response to the rotation of the trigger actuation wheel (66); Equipped with A trigger mechanism (56) wherein the control member is configured to exert a first rotational driving force on the trigger cam (64), The trigger mechanism (56) includes a trigger lever (94) configured to follow the trigger cam (64), and when the trigger lever (94) follows the trigger cam (64) rotated by the control member, the trigger lever (94) - storing energy to counteract the first rotational driving force by exerting a second rotational driving force on said trigger cam (64) as long as said first rotational driving force is below a predetermined threshold; and - returning said energy beyond said predetermined threshold such that said second rotational driving force exerted on said trigger cam (64) causes said trigger actuation wheel (66) to rotate, so that said actuation device (72), which had previously locked said trigger output wheel (70), releases said trigger output wheel (70) to perform said function. The trigger cam (64) and the trigger lever (94) are configured so that A trigger mechanism (56) characterized by:

2. 2. The trigger mechanism (56) of claim 1, wherein the trigger lever (94) is provided with a return spring (96) configured to store and return the energy as the trigger lever (94) follows the rotating trigger cam (64) to enable the trigger lever (94) to exert the second rotational driving force on the trigger cam (64).

3. 3. The trigger mechanism (56) of claim 1 or 2, wherein the trigger cam (64) has n branches (64a, 64a') defining n peaks and n valleys, each branch (64a, 64a') having an ascending flank and a descending flank.

4. 4. The trigger mechanism of claim 2, wherein the return spring of the trigger lever is configured to store energy when the trigger lever follows an ascending flank of the rotating trigger cam and to return energy when the trigger lever follows a descending flank of the rotating trigger cam, thereby enabling the trigger lever to exert the second rotational driving force on the trigger cam.

5. 5. A trigger mechanism (56) according to claim 3 or 4, characterized in that the control member is a control lever (58) having a hook (92a) preferably configured to grip a tip of one of the branches (64a) of the trigger cam (64) and thereby rotate the trigger cam (64), in order to exert the first rotational driving force on the trigger cam (64).

6. 6. A trigger mechanism (56) according to any one of claims 1 to 5, characterized in that the trigger cam (64) is coaxial with the trigger operating wheel (66) and rotates integrally therewith.

7. 7. The trigger mechanism (56) of any one of claims 1 to 6, characterized in that the trigger lever (94) comprises a runner (100) configured to follow the trigger cam (64).

8. 8. A trigger mechanism (56) according to any one of claims 1 to 7, characterized in that the resilient member (68) is a spiral coil spring.

9. 9. The trigger mechanism according to claim 1, wherein the actuation device comprises: an actuation pinion that rotates freely and is kinematically connected to the trigger actuation wheel; an actuation cam that is integral with the actuation pinion; an actuation fork that is mounted in a rotationally movable manner and configured to cooperate with the actuation cam; and an actuation anchor that rotates integrally with the actuation fork, wherein the actuation anchor has two arms that are configured to alternately lock a lock pawl that rotates integrally with a lock pinion that is configured to be kinematically connected to the trigger output wheel.

10. Trigger mechanism (56) according to any one of claims 1 to 9, characterized in that the clockwork mechanism is a correcting mechanism (6) of at least one display element (4).

11. A timepiece comprising a clockwork mechanism configured to perform a function and a trigger mechanism (56) for triggering the clockwork mechanism according to any one of claims 1 to 10.

12. 12. The timepiece according to claim 11, comprising at least one first display member configured to display local time HT, a drive wheel and pinion (2) of the first display member, a second display member (4) configured to be able to display GMT time of a time zone different from the time zone of the local time HT, a drive mechanism (8) of the second display member (4), and a correction mechanism (6) of the second display member (4) configured to be able to correct the GMT time independently of the local time HT, wherein the correction mechanism (6) comprises the trigger mechanism (56).

13. 13. The timepiece according to claim 12, characterized in that the drive mechanism (8) of the second display member (4) comprises a differential gear (10) including at least one upper differential wheel and pinion (14) configured to be kinematically coupled to the second display member (4), a lower differential wheel and pinion (16) configured to be kinematically coupled to the drive wheel and pinion (2) of the first display member, and an input part (18) configured to be kinematically coupled to the correction mechanism (6) of the second display member (4).

14. The differential gear (10) comprises a differential block (20) mounted so as to be freely rotatable on two half shafts (22a, 22b) integral with the upper differential wheel and pinion (14) and the lower differential wheel and pinion (16), respectively, and the differential block (20) is configured to mesh with at least one pinion (26a) integral with the half shaft (22a) of the upper differential wheel and pinion (14).

14. Timepiece according to claim 13, characterized in that the differential block (20) is also integral with a wheel constituting the input (18) of the differential gear (10) configured to be kinematically coupled to the trigger output wheel (70) of the trigger mechanism (56), carrying a first intermediate wheel (24a) and a second intermediate wheel (24b) configured to mesh with a pinion (26b) integral with the half shaft (22b) of the lower differential wheel and pinion (16).

15. The drive mechanism (8) of the second display member (4) comprises a phase-shifting wheel and pinion (12), the phase-shifting wheel and pinion (12) comprising a lower phase-shifting wheel (28) configured to be kinematically connected to the drive wheel and pinion (2) of the first display member and kinematically connected to the lower differential wheel and pinion (16), and a phase-shifting wheel (28) configured to drive the second display member (4) and to be kinematically connected to the upper differential wheel and pinion (14). and an upper phase-shift wheel (32) configured as follows: said upper phase-shift wheel (32) is disengaged from said lower phase-shift wheel (28) when the GMT time is corrected by said correction mechanism (6) independently of said local time HT, while said upper phase-shift wheel (32) is kinematically connected to said lower phase-shift wheel (28) in an engagable manner so as to enable repositioning of said second display member (4) synchronized with the positioning of said first display member after correction.

16. 16. Timepiece according to claim 15, characterized in that the phase-shifting wheel and pinion (12) comprises a phase-adjusting cam (34) integral with the lower phase-shifting wheel (28) and a hammer (36) on which a phase-shifting spring (38) carried by the upper phase-shifting wheel (32) is mounted, the hammer (36) being adapted to cooperate with the phase-adjusting cam (34).

17. 17. A timepiece according to any one of claims 12 to 16, comprising a display device (42) configured to display the difference between the local time HT and the GMT time, the display device (42) being kinematically coupled to the trigger output wheel (70) of the trigger mechanism (56) so that it can be corrected by the correction mechanism (6) of the second display member (4) while correcting the second GMT time display member (4) independently of the local time HT.

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