CH716385A1 - Clockwork driving and blocking mechanism for a jumping mobile. - Google Patents

Abstract

The invention relates to a clockwork mechanism (1) for driving and blocking a jumping mobile (40), said clockwork mechanism (1) comprising: - an actuating device (30); – the jumping mobile (40); - an ascender (10), comprising: - an end having a shape able to be engaged in a hollow (410) between two consecutive teeth (411) of the jumping mobile (40); - a rocker (20), comprising: - a trigger (220), arranged to come into contact with the blocker (10); - a pawl (210), arranged to come into contact with the jumping mobile (40); - a feeler (230), arranged to come into contact with the cam (30); the blocker (10) is arranged to pivot about an axis (100) under the action of the trigger (220) between: a blocking position, in which said actuator (30) rotates said feeler (230 ) in a first direction around an axis (200) of the rocker (20) and in which the end is engaged in the hollow (410) between two consecutive teeth (411) of the jumping mobile (40), thus blocking the position of the jumping mobile (40), and a drive position, in which said actuating device (30) rotates said feeler (230) in a second direction around the axis (200) of the rocker (20 ) and wherein the end is disengaged from said recess (410), thereby allowing the pawl (210) to rotate the jumper (40).

Description

Description

Technical area

The present invention relates to a watch mechanism for driving and blocking a jumping mobile.

State of the art

[0002] In this context, the expression "mobile" designates a mobile timepiece, that is to say which can be set in rotation. In this context, the expression "jumping mobile" designates a mobile which can be set in rotation by jump or step by step. In particular, a jumping mobile carries or is linked to jumping information.

[0003] A wheel of a counter for a chronograph watch, for example a wheel of a minute counter or timed seconds, is a non-limiting example of a jumping mobile. Such a wheel is generally linked to an indicator, for example a needle. As a general rule, a mobile is driven in rotation by a driving mobile. As a general rule, the driven mobile only Tests once or several times per turn of the driving mobile, which creates a reduction.

[0004] In the context of the present invention, the word "counter" indicates a means providing information relating to a counted duration. More precisely, a dial and an indicator form a counter. an indicator.

[0005] A disc, for example a disc which carries jumping information such as the date (that is to say the serial number of each day in the month), the month, the day of the week, the name of the day of the week, the year, the phases of the moon too, etc., is another non-limiting example of a jumping mobile.

[0006] In a clockwork mechanism for driving and blocking (and therefore positioning) a jumping mobile, it is important to minimize the force necessary to drive and/or biocate this jumping mobile, in order on the one hand to minimize any disturbance of the watch movement which causes it and on the other hand to minimize the reduction in the power reserve of this movement. This is all the more important when this timepiece mechanism is far from the driving member, for example a barrel: the torque available to the timepiece mechanism is lower and the consumption of the mechanism therefore becomes proportionally greater.

[0007] In addition, it is also important that the position of the jumping mobile be ensured with accuracy, that the jumping mobile be driven jump by jump at a well-determined instant, and that its position not be altered by shocks to the timepiece, for example a watch, in which this device can be mounted.

[0008] An example of a clockwork mechanism for driving and blocking a jumping mobile for a known perpetual calendar, displaying for example the days of the week, is illustrated in FIG. 1 (reference 1000'). This mechanism 1000' belongs to a timepiece such as a watch, illustrated schematically by its case 2000'.

[0009] Displays make it possible to display indications such as the chronometer time, the date, the month, the day of the week, the name of the day of the week, etc. In the following, we will refer for simplicity only to the days of the week.

[0010] The watch mechanism 1000' comprises a wheel, in the example an hour wheel 10', which meshes with another wheel, in the example a twenty-four hour wheel 20', which performs a complete rotation by day.

[0011] A 24-hour display mobile (not shown) is linked to a weekday wheel (or star) 40', with seven branches in the example shown, and which is driven at the rate of a times a day by a gear finger 50' coaxial with the twenty-four hour wheel 20'.

[0012] A pin 30', integral with the twenty-four-hour wheel 20', rotates the gear finger 50' which meshes with the weekday star 40', and causes it to perform a seventh of a turn each day. The angular freedom left to the gear finger 50' by the sector cooperating with the pin 30' allows the gear finger 50' to rotate independently of the twenty-four hour wheel 20' when it is pushed by the star weekdays 40', for example when this star 40' performs its jump or during a display correction action.

[0013] In the known mechanism 1000', the indexing of the weekday star 40' by exactly one seventh of a turn is guaranteed by the elastic indexing element (or jumper) 100' which is positioned between two teeth of the 40' weekday star, such that each indexing step corresponds exactly to one seventh of a turn.

The jumper 100' is a spring terminated by two inclined planes which press between the tips of two consecutive teeth of a wheel (the weekday star 40' in the example of Figure 1) to hold it in a certain position. When this wheel is actuated, the teeth raise jumper 100' which then falls between two other teeth.

[0015] In the example of FIG. 1, the torque transmitted to the weekday star 40' only tests on the angle making it possible to overcome the positioning force of the star 40', this torque depending on the ratio of the radii of application of the forces, and not of the resulting final reduction.

[0016] The presence of this jumper 100' involves certain disadvantages: firstly, the forces imposed by the jumper 100' on the weekday star 40' must be overcome to make the star 40' advance, which requires a high torque requirement, which also reduces the movement's power reserve.

[0017] In addition, this high torque is used for a very limited time, in particular during the time in which the jumping wheel is rotating, which disturbs the running of the watch movement in which the watch mechanism 1000' is integrated.

[0018] Secondly, still because of its elastic nature, it is difficult to place the jumper 100' when mounting the mechanism 1000'.

[0019] Finally, in the event of shocks to the watch, jumper 100' can easily be lifted, thus deprogramming the watch. A deprogramming can result in the example of FIG. 1 in an indication of the day of the week which does not correspond to that in progress.

The positioning function of the jumper 100 'of Figure 1 also generates resistance to angular shocks of the mechanism. It follows from the mechanism 1000' that the minimum torque generated by the jumper 100' for this shock resistance is also to be overcome during training for the jump.

In addition, the mechanism of Figure 1 does not include a mechanism for correcting the information displayed.

[0022] The above considerations also apply to horological mechanisms for driving and blocking a jumping mobile for a chronograph watch, in which the jumping mobile blocked by jumper 100' is a chronometer time counter. .

[0023] As a general rule, a jumping mobile, in particular a jumping mobile for a chronograph watch, often has a small mass. For this reason, it is generally subjected to friction, to limit its freedom when it turns, in order to reduce or eliminate small untimely movements, for example due to games or frolics. This does not concern the jumping mobile (the star 40') of FIG. 1, because the presence of the jumper 100' makes it possible to eliminate this problem.

[0024] Friction acts by friction and consequently the parts subjected to friction are susceptible to premature wear. In addition, it also consumes energy to limit the freedom of the mobile jumping when it turns, by disturbing the running of the watch movement and also by reducing the movement's power reserve.

[0025]There is therefore a need for a watchmaking mechanism for driving and blocking a jumping mobile free from these limitations of the prior art.

Brief summary of the invention

[0026] An object of the present invention is to provide a clockwork mechanism for driving and blocking a jumping mobile free from the known limitations.

[0027] Another object of the present invention is to propose a clockwork mechanism for driving and blocking a jumping mobile which allows precise positioning of the jumping mobile, while reducing the force necessary for its step-by-step training and/or or its positioning.

Another object of the present invention is to provide a watch mechanism for driving and blocking a jumping mobile which disturbs the operation of the watch movement as little as possible in which this mechanism can be integrated and/or which reduces the less possible the power reserve of the watch movement in which this mechanism can be integrated.

According to the invention, these objects are achieved in particular by means of a clockwork mechanism for driving and blocking a jumping mobile according to claim 1.

The clockwork mechanism for driving and blocking a jumping mobile according to the invention comprises:

- an actuating device;

- the jumping mobile, comprising at least one toothed portion;

- a blocker, comprising:

- an end having a shape capable of being engaged in a hollow between two consecutive teeth of the toothed portion of the jumping mobile;

- a rocker, comprising:

- a ratchet, arranged to come into contact with the jumping mobile;

- a feeler, arranged to come into contact with the cam.

According to the invention, the blocker is arranged to pivot, for example to pivot around an axis, under the action of the trigger between:

- a blocking position, in which the actuating device rotates the probe in a first direction around an axis of the rocker and in which the end of the blocker is engaged in the hollow between two consecutive teeth of the jumping mobile, in thereby blocking the position of the jumping mobile, and

- a drive position, in which the actuating device rotates the probe in a second direction opposed to the first direction around the axis of the rocker and in which the end of the blocker is disengaged from the hollow, thus allowing the pawl to spin the jumping mobile.

[0032] The arrangement of the watchmaking mechanism for driving and blocking a jumping mobile according to the invention makes it possible to separate the two functions of driving and blocking and to create a step-by-step display without having to overcome efforts. imposed by a jumper on the mobile jumping, as is typically the case in the state of the art.

[0033] The arrangement of the watchmaking mechanism for driving and blocking a jumping mobile according to the invention also makes it possible to overcome the presence of friction, because there is no longer the need to limit the freedom of the mobile jumping when it turns.

[0034] The blocker of the watch mechanism according to the invention is not a spring nor does it have an elastic nature like a jumper. It is not necessary to overcome the forces imposed by the ascender on the jumping mobile as is typically the case for the jumper of the state of the art, because the ascender is lifted under the action of the trigger of the seesaw. In addition, as the trigger and the pawl belong to the same part, namely the rocker, the actions of lifting the ascender in order to release the jumping mobile, advancing the jumping mobile and lowering the ascender in order to biocate the new position of the jumping mobile are synchronized.

[0035] In addition, as the blocker is not a spring nor does it have an elastic nature like a jumper, it is also possible to position it more easily in a movement of a timepiece.

[0036] The torque requirement of the clockwork drive and blocking mechanism of a jumping mobile according to the invention is thus reduced, which makes it possible to reduce disturbances in the running of the movement and also to increase the power reserve. movement.

[0037] The watchmaking mechanism for driving and blocking a jumping mobile according to the invention is therefore well suited for movements comprising mobiles which rotate quickly, and therefore which have a low torque, for example of the order of size of 10 3 N ■ mm, because its energy consumption for driving and/or blocking the jumping mobile is low, while guaranteeing strong hold when positioning the jumping mobile.

The clockwork mechanism for driving and blocking a jumping mobile according to the invention is also suitable for mobiles having larger torques, for example date discs.

[0039] Advantageously, the blocker of the mechanism according to the invention is lifted by releasing or unlocking the jumping mobile exactly when it is necessary to drive the jumping mobile. This self-synchronism is guaranteed by the fact that the rocker comprises both the trigger, which acts on the blocker, the pawl, which makes it possible to advance the counter wheel and the sensor, which makes it possible to transfer to the watch mechanism according to the invention via the actuating device the information when to drive the counter wheel.

[0040] In a presential variant, the rocker comprises:

- a pawl spring; And

- a trigger spring.

[0041] In a preferred variant, in the locking position, when the trigger spring is wound, the pawl spring is not being wound and vice versa.

This makes it possible to "smooth" the energy consumption of the mechanism according to the invention over the time of its use, while avoiding the peaks of the state of the art.

[0043] In a preferred variant, the mechanism according to the invention also comprises a return spring on the feeler island. In this context, the expression "a single-component spring" also indicates the case where the spring is not attached to the component. restore this energy in the training position.

[0044] In a variant, the arrangement of the clockwork mechanism for driving and blocking a jumping mobile according to the invention also makes it possible to better withstand shocks.

[0045] The rocker body may comprise at least one recess, also allowing the watch mechanism to better withstand shocks, by balancing the mechanism in addition to or as an alternative to at least one measure of the following two measures against shocks, namely :

- a counterweight zone which can carry the feeler and belonging to a second plane substantially parallel to the first plane of the rocker;

- A recess of the pawl having a shape which allows that in the event of shocks the pawl is in contact with the ascender in correspondence of at least two points of a recess of the ascender; at the same time, in the event of shocks, a head of a tooth of the jumping mobile comes into contact with the body of the pawl spring in correspondence of at least one other point of contact; the presence of three contact points means that in the event of shocks, the pawl spring does not undergo any torsion.

[0046] Advantageously, the clockwork mechanism for driving and blocking a jumping mobile according to the invention can be used with different types of jumping mobiles, provided that the gap between two consecutive teeth of these jumping mobiles is substantially the same. , so that the blocker can position them.

[0047] In a variant, the clockwork mechanism for driving and blocking a jumping mobile according to the invention also allows a reset-to-zero of the jumping mobile.

[0048] In another variant, the clockwork mechanism for driving and blocking a jumping mobile according to the invention also allows correction in steps of the information carried by the jumping mobile.

Other advantages and other embodiments of the invention are described in the following description and in the appended dependent claims.

[0050] Although some of the aforementioned advantages are associated more particularly with a mechanical timepiece, the invention is in no way limited to this type of timepiece. This timepiece could also be an electronic timepiece, in particular a quartz watch with a rotary display, in particular an analog display. Likewise in the case of a mechanical timepiece, this may or may not be self-winding.

Brief description of figures

Examples of implementation of the invention are indicated in the description illustrated by the appended figures in which:

FIG. 1 illustrates a schematic and simplified top view of a watch comprising a known timepiece mechanism.

Figure 2 a view from above of an embodiment of the timepiece mechanism according to the invention.

FIG. 3 illustrates a perspective view of one embodiment of the blocker of the timepiece mechanism according to the invention.

Figure 3A illustrates another perspective view of a portion of the blocker of Figure 3.

FIG. 4 illustrates a perspective view of an embodiment of the rocker of the timepiece mechanism according to the invention.

FIG. 5 illustrates a top view of an embodiment of the timepiece mechanism according to the invention, in starting position (phase 0).

Figure 6 illustrates a top view of the clock mechanism of Figure 5, when the pawl is raised (phase 1).

FIG. 7 illustrates a view from above of the timepiece mechanism of FIG. 5, during the transition between the winding of the pawl spring and the winding of the trigger spring (phase 2).

FIG. 8 illustrates a top view of the timepiece mechanism of FIG. 5, when the trigger has fallen behind the hook of the ascender (phase 3).

FIG. 9 illustrates a top view of the timepiece mechanism of FIG. 5, during the maximum operation of the actuation device (phase 4).

FIG. 10 illustrates a view from above of the timepiece mechanism of FIG. 5, during the start of the training of the jumping mobile (phase 5).

FIG. 11 illustrates a top view of the timepiece mechanism of FIG. 5, at the limit of the self-release of the trigger (phase 6).

FIG. 12 illustrates a view from above of the clockwork mechanism of FIG. 5, when the trigger releases the blocker and pushes it onto the teeth of the jumping mobile (phase 7).

Figure 13 illustrates a top view of the clockwork mechanism of Figure 5, when the actuating device and the rocker have returned to their positions of phase 0, but the blocker has not finished positioning the counter wheel ( stage 8).

FIG. 14 illustrates a top view of another embodiment of the clockwork mechanism according to the invention, in which the actuating device, the rocker and the blocker are in any position (phase 0 of the reset to zero) .

FIG. 15 illustrates a view from above of the clockwork mechanism of FIG. 14, when the hammer comes into contact with the rocker (phase 1 of the reset-to-zero).

FIG. 16 illustrates a view from above of the clockwork mechanism of FIG. 14, when the hammer has pushed the rocker until the pawl and the blocker are disengaged (phase 2 of the reset-to-zero).

FIG. 17 illustrates a view from above of the clockwork mechanism of FIG. 14, during the start of the reset-to-zero (phase 3 of the reset-to-zero).

FIG. 18 illustrates a view from above of the clockwork mechanism of FIG. 14, when the jumping mobile is reset to zero (phase 4 of the reset).

FIG. 19 illustrates a view from above of the clockwork mechanism of FIG. 14, during the start of the return of the hammer (phase 5 of the reset-to-zero).

FIG. 20 illustrates a view from above of another embodiment of the timepiece mechanism according to the invention.

FIG. 21 illustrates a top view of another embodiment of the timepiece mechanism according to the invention, in which the actuating device, the rocker and the blocker are in any position (phase 0 of the step correction) .

FIG. 22 illustrates a top view of the embodiment of FIG. 21, when the pawl presses against the blocker (phase 1 of the step correction).

Figure 23 illustrates a top view of the embodiment of figure 21, when the ascender begins to rise and the skate begins to press against the teeth of the jumping mobile (phase 2 of the step correction).

FIG. 24 illustrates a top view of the embodiment of FIG. 21, when the beak of the hammer comes into contact with a tooth of the jumping mobile (phase 3 of the step correction).

FIG. 25 illustrates a top view of the embodiment of FIG. 21, when the jumping mobile has rotated (phase 4 of the step correction).

Example(s) of embodiment of the invention

[0052] In the following exemplary description, reference will be made, for simplicity, to a counter wheel as an example of a jumping spindle. It should however be understood that the invention is not limited to such a jumping mobile, but also includes any other jumping mobile, such as for example a date disc.

The invention is not limited to the field of watch mechanisms for chronograph watches, but also includes watch mechanisms for watches which are not necessarily chronograph watches.

[0054] The timepiece mechanism according to the invention is intended to be integrated into a movement for a timepiece, for example into a movement for a watch. This movement of the timepiece will not be described in detail here, insofar as this description is not necessary for the understanding of the invention.

[0055] Figure 2 illustrates a view from above of an embodiment of the watch mechanism 1 according to the invention. The illustrious mechanism includes:

- an actuating device 30, which in the illustrated example is a cam; in the following, both the actuator and the cam will be designated with the reference numeral 30;

- a jumping mobile 40, which in the illustrated example is a counter wheel; in the following, both the jumping mobile and the counter wheel will be designated with the reference 40;

- a blocker 10, intended to cooperate with the counter wheel 40, blocking its position;

- a rocker 20, intended to cooperate with the counter wheel 40, with the cam 30, and with the blocker 10.

[0056] In a variant, the clockwork mechanism 1 according to the invention can also allow the resetting of the jumping mobile. This can be useful (but not necessary) for example when the watch mechanism is integrated into a movement for a chronograph watch. For this reason, the clockwork mechanism 1 can also comprise:

- a hammer 60, arranged to cooperate with the rocker 20 when resetting the jumping mobile 40;

- a support pin 70 for the hammer spring 610;

- a manual actuator such as for example a button 90 to actuate the reset of the jumping mobile 40.

In the following, the actuating device 30, the jumping mobile 40, the blocker 10, and the rocker 20 will be described in detail with reference to Figures 2 to 4 and 20. Next, an example of the operation of the clockwork mechanism 1 will be illustrated with reference to FIGS. 5 to 13. Next, an example of operation of the reset-to-zero of the clock mechanism 1 will be illustrated with reference to FIGS. watchmaker 1 will be illustrated with reference to Figures 21 to 25.

The actuator 30 in the illustrated examples is a cam. As a general rule, this actuating device 30 makes it possible to rotate a feeler 230 of the rocker 20 in a first direction around an axis 200 of the rocker in the locking position, and to rotate the feeler 230 of the rocker 20 in a second direction opposite to the first around fax 200 of the rocker 20 in the drive position. In other words, the actuator 30 is a device arranged to generate a back and forth movement of the probe 230.

In a preferred variant, the actuating device 30 comprises a portion 320 arranged to control the speed of the mobile jumping 40 in the drive position.

In a preferred variant, the actuation device 30 has a shape allowing distribution of the torques and rotations of the mechanism according to the invention.

In a preferred variant, the speed with which the feeler 230 of the rocker 20 rotates under the action of the actuating device 30 in a first direction in the blocking position is lower than the speed with which the feeler 230 of the rocker 20 rotates under the action of the actuating device in a second direction in the drive position.

[0062] In the following exemplary description, reference will be made, for simplicity, to a cam as an example of an actuator. It should however be understood that the invention is not limited to a cam, but also includes any other actuating device, such as for example a manual actuator, for example a push button, or a combination of actuating devices. For example, one can imagine that the mechanism according to the invention can trigger the driving of the jumping mobile 40 both by a cam and by a push button.

[0063] The cam 30 of FIG. 2 is linked to a second mobile (not illustrated), which is not necessarily a jumping mobile. In a variant, this second mobile is another counter wheel.

In a preferred embodiment, the cam 30 is driven on the same axis 300 of this second mobile not shown. The cam 30 makes it possible in particular to trigger the driving of the jumping mobile (the counter wheel 40 in the case of FIG. 2) when the second mobile, not shown, has rotated through a certain angle.

[0065] In one example, the second non-illustrated mobile can be a wheel that makes one revolution in a period of time X (for example and without limitation, X = 30 minutes) and the jumping mobile (the counter wheel 40 in figure 2) can be a wheel which makes one revolution in a period of time Y which is a multiple of X, for example Y = N*X, N being a whole number and positive (for example and in a non-limiting way, Y = 12 o'clock). In this case, it is therefore necessary that the counter wheel 40 can rotate with a speed which is N times smaller than the speed of rotation of the second wheel not shown.

However, it should be understood that the ratio between X and Y only depends on the number of teeth of the counter wheel 40, so this ratio is not necessarily the inverse of an integer N.

According to the invention, the cam 30 has a profile comprising a first portion 310 and a second portion 320; in the example shown, this first portion 310 has a shape allowing a distribution of torques and rotations and the second portion 320 is arranged to control the speed of the mobile jumping 40 in the training position. In the variant of FIG. 1, this first portion 310 is a portion of a spiral and the second portion 320 is substantially rectilinear.

[0068] The cam 30 is arranged to rotate around its axis 300 during the rotation of the second mobile not shown to which it is linked. In the examples of Figures 5 to 13, the non-illustrated counter wheel is permanently rotating in the direction indicated by the arrow F1, and therefore the cam 30 too.

[0069] In the example of Figure 2, counter wheel 40 is associated with a core (not shown). This heart is associated with an indicator, for example a hand, which it allows to control and orient in order to display the corresponding indications. For example, the axis of a needle can be mounted directly on the axis of the heart, or linked to this axis of the heart by means of a chain of gears as short as possible, for example a wheel and a pinion.

In the example shown, the counter wheel 40 is a wheel comprising thirty teeth 411. Obviously, any other number of teeth is possible. In a preferred variant and illustrated in FIG. 2, the counter wheel 40 comprises teeth 411 which are all equidistant. In another variant, at least a portion of the counter wheel 40 comprises teeth 411, in particular equidistant teeth 411. In another variation, at least a portion of counter wheel 40 includes (slightly) non-equidistant teeth 411 .

[0071] FIG. 3 illustrates a perspective view of an embodiment of the blocker 10 of the timepiece mechanism according to the invention.

[0072] The illustrious blocker 10 is arranged to pivot around rotation fax 100.

[0073] The blocker 10 comprises an arm 101 and substantially three protrusions 102, 103 and 104, the arm and the protrusions extending from its center of rotation 100.

[0074] In a preferred variant, the blocker 10 is a one-piece piece. In another variant, it is made by two or more parts linked together, in a removable or non-removable way.

In a preferred variant, the blocker 10 is made of nickel, a nickel alloy, silicon or a silicon alloy.

[0076] In a preferred variant, the blocker 10 does not have an elastic nature like a state-of-the-art jumper. It is therefore a substantially rigid part.

The arm 101 comprises a first end 110 having a shape arranged to be engaged in the hollow 410 between two consecutive teeth 411 of the counter wheel 40, visible for example in Figure 2.

[0078] According to the invention and as will be seen in detail later, the blocker 10 is arranged to pivot around Taxe

100 between:

- A blocking position, in which the end 110 of the blocker 10 is engaged in the hollow 410 between two consecutive dents411 of the counter wheel 40, thereby blocking the position of the counter wheel 40; And

- a drive position, in which the end 110 of the blocker 10 is disengaged from the hollow 410, thus allowing the pawl 210 to rotate the counter wheel 40.

[0079] In the variant of FIG. 3, the shape of this end 110 is defined by a set of different surfaces 1101, 1102, 1103 and 1104. These surfaces develop in planes which are substantially perpendicular to the main surface of the blocker. 10, which is substantially perpendicular to rotation axis 100.

In a preferred variant, all these surfaces 1101, 1102 and 1104 are substantially planar, and surface 1103 is substantially concave.

In a preferred variant, the end 110 of the blocker 10 comprises all these surfaces 1101, 1102, 1103 and 1104. In another variant, the end 110 of the blocker 10 comprises at least a subset of these surfaces 1101, 1102, 1103 and 1104.

The first surface 1101 of the first end 110 is that in correspondence of which the blocker 10 is based on the head 412 of the teeth 411 (visible for example in Figure 2), as will be seen later. In the variant illustrated, this surface 1101 is substantially planar: in this case, it allows the end 110 to "slide" over the head 412 of the teeth 411.

The second surface 1102 of the first end 110 is that which allows the pre-positioning of the blocker 10. It also allows, when passing between the blocking position and that of training, to bring the end 110 into the hollow 410 between two teeth 411. In this way, it allows the blocker 10 to return to the blocking position. It therefore allows the dynamic effect of the counter wheel 40 to be determined. In the variant illustrated, the end 110 comprises two second surfaces 1102, each being adjacent to the first surface 1101.

The third surface 1103 of the first end 110 is that which allows the blocker 10 to withstand shocks. In the variant illustrated, the end 110 comprises two third surfaces 1103, each being adjacent to the second surface 1102. In a preferred variant, these two surfaces 1103 are substantially concave.

[0085] The fourth surface 1104 of the first end 110 is that which allows the precision of the positioning of the blocker 10 in the hollow 410 between two teeth 411.

[0086] The angular position of the jumping mobile 40 is thus very precisely fixed thanks to the fourth surface 1104 of the first end 110 and moreover, if the watch mechanism 1 according to the invention is subjected to a shock, thanks to the third surface 1103 of the first end 110, the first end 110 remains engaged in the hollow 410. Consequently, the jumping mobile 40 is indexed very precisely and shocks alter very little or do not alter this indexing precision at all.

[0087] The extremity 110 is the first extremity (or distal extremity, because it is farthest from the axis of rotation 100) of an arm

101 of blocker 10, which extends from rotation rate 100.

[0088] The second end 120 (or proximal end, because it is closer to the axis of rotation 100) of the arm 101 comprises a portion defined by a set of different surfaces 1201, 1202 and 1203. These surfaces also develop in planes which are substantially perpendicular to the main surface of the blocker 10, which is substantially perpendicular to the axis of rotation 100.

The portion defined by the surfaces 1201, 1202 and 1203 is arranged to come into contact with the pawl 210 of the rocker 20, as will be seen later.

In a preferred variant, the end 120 of the blocker 10 includes all of these surfaces 1201, 1202 and 1203. In another variant, the end 120 of the blocker 10 includes at least a subset of these surfaces 1201, 1202 and 1203.

[0091] The first surface 1201 of the second end 120 is that which allows release of the pawl 210 in the "normal" function of the clockwork mechanism 1, namely when the clockwork mechanism 1 is not used to reset the wheel to zero. counter 40 n to absorb a shock. This first surface 1201 is curved towards the inside of the blocker 10, in other words it is a concave surface. It therefore defines a hollow which, during the maximum winding of the pawl spring , allows the pawl 210 not to lift the blocker 10.

The second surface 1202 of the second end 120 is present in particular when the clockwork mechanism 1 is used to reset the counter receipt 40. This second surface 1202 is curved towards the outside of the blocker 10, in other words eile is a convex surface. It therefore defines a rounded tip in correspondence of which the pawl 210 is positioned during a phase of the reset-to-zero.

The third surface 1203 of the second end 120 is also present in particular when the clock mechanism 1 is used to reset the counter wheel 40 to zero. This third surface 1203 is curved towards the inside of the blocker 10, at other words eile is a concave surface. It therefore defines a hollow in correspondence of which the pawl 210 is positioned during a reset-to-zero phase. This hollow also allows a fulcrum of the ratchet210 during an impact.

[0094] The first protuberance 102 is also defined by several surfaces. Among these surfaces, there is one (the surface 1021, which in the illustrated example is substantially flat) which makes it possible to limit the displacements of the pawl 210 of the rocker 20, mainly by maintaining the pawl 210 in the teeth 411 during shocks when the blocker 10 is lifted.

In the variant of figure 3, between the second end 120 of the arm 101 and the first protuberance 102, the blocker 10 defines a recess 140 which in a preferred variant cooperates with a portion of the pawl 210.

[0096] Figure 3A illustrates another perspective view of the portion of the blocker 10 of Figure 3 indicated in the dotted rectangle, with another point of view in order to better illustrate the surfaces which define the second protuberance 103 (or hook) and the third protuberance 104.

The second protuberance (or hook) 103 and the third protuberance 104 are intended to cooperate with the trigger of the rocker 20.

In the example of Figure 3A, the hook 103 is defined by several surfaces. Among these surfaces, there is one (surface 1031, which in the illustrated example is substantially flat) which allows the spring of the trigger to be cocked, while maintaining the position of the blocker 10.

In the example of Figure 3A, the third protuberance 104 is defined by several surfaces. Among these surfaces, the first surface 1041, which in the illustrated example is substantially planar, constitutes a support for the trigger. The second surface 1042, which in the illustrated example is substantially planar, allows the trigger to be moved back for self-release. The third surface 1043, which in the illustrated example is also substantially flat, is a support zone for the trigger after the winding of the trigger spring, after the passage of the beak 2202 beyond the hook 103.

[0100] In a preferred variant, the first surface 1041 and the third surface 1043 are slightly concave to ensure constant support for the ascender. The second surface 1042 can also be convex as well, which is useful for unhooking.

[0101] In other words, surfaces 1031, 1041, 1042 and 1043 all cooperate with the trigger of rocker 20.

[0102] Between the second protuberance 103 and the third protuberance 104 there are therefore two recesses 1044 and

1045, the first 1044 having a substantially pointed shape and being delimited by the hook 103 and a first asperity

1046, and the second 1045 having a polygonal shape defined in particular by the surfaces 1042 and 1043 and being delimited by the first asperity 1046 and by a second asperity 1047.

[0103] The trigger 220, better visible in FIG. 4, comprises a finger 2201 that is substantially straight and substantially perpendicular to at least a portion of the trigger spring 212, and a beak or nose 2202, having a substantially triangular shape. Finger 2201 and beak 2202 define a first recess 2203. Beak 2202 and trigger spring 212 define a second recess 2204.

[0104] In a variant, the shape of the first recess 2203 of the trigger matches that of the hook 103 of the ascender 10, as for example visible in FIG. 2. In other words, the first recess 2203 is a clearance allowing the finger 2201 can lean on the ascender without being prevented by the shape of the hook 103 (second protrusion) of the ascender 10.

[0105] The finger 2201 of the trigger 220 is arranged to contact and move on the first surface 1041 of the third protrusion 104 before the beak 2202 contacts and moves on the first surface 1031 of the hook 103. This displacement of the beak 2202 on the first surface 1031 of the hook 103 makes it possible to arm the trigger spring 212, when the blocker 10 maintains the position of the counter wheel 40.

[0106] Then, after moving away from the blocker 10, the finger 2201 of the trigger 220 comes into contact with and moves over the third surface 1043 and then with the second surface 1042 of the third protrusion 104.

[0107] Figure 4 illustrates a perspective view of an embodiment of the rocker 20 of the clockwork mechanism 1 according to the invention. According to the invention, the latch 20 comprises:

- a 220 trigger,

- a ratchet 210,

- a 230 feeler.

The rocker 20 is arranged to pivot around the axis of rotation 200. The axis of rotation 200, like any other axis of rotation mentioned in the description, can be a real or virtual axis.

[0109] The rocker 20 comprises a main body which belongs to a first plane and a counterweight zone 231, which can carry the feeler 230 intended to cooperate with the cam 30, which in the variant of FIG. 4 belongs to a second plane. substantially parallel to the foreground. In another variant, the feeler 230 could be on the main body. One or more spacers 240 can be placed between the body 201 and the counterweight zone 231. The counterweight zone 231 allows the watch mechanism 1 to better withstand shocks, by balancing it if necessary.

The body 201, the counterweight zone 231 and the spacers 240 can constitute a one-piece piece. In another variant, at least two of these parts are separate parts, linked together, in a removable or non-removable way.

[0111] In a preferred variant, the rocker 20 is also made of nickel, a nickel alloy, silicon or a silicon alloy or any other material or according to any process allowing the realization of spring functions with very low rigidity. .

[0112] The latch 20 of the variant of FIG. 4 comprises three springs, namely:

- a pawl spring 211;

- a trigger spring 212; And

- a return spring 213.

The three springs belong to the plane of the main body 201. They are advantageously leaf springs. The pawl spring 211 of Figure 4 is adjacent to the trigger spring 212. In a preferred variant, their width L (indicated in Figure 4 for the return spring 213 only) is substantially identical. In a variant, this width is within the range 40 μm - 80 μm. In a preferred variant, it is equal to 60 μm.

[0114] The trigger spring 212 is strong enough to press the blocker 10 during shocks. Pawl spring 211 provides friction during zeroing as will be seen later, but with the help of blocker 10. The stiffness of trigger spring 212 is therefore not directly related to the stiffness of the trigger spring. ratchet 211.

[0115] Advantageously, at least one and preferably each of these springs is a "weak" spring. In this context, a spring is weak if the torque required to move it is low, namely equal to or less than 0.04 N. .mm compared to 200 rotation tax.

[0116] If the trigger spring 212 is weak, the force to move the blocker 10 is also weak. If the pawl spring 211 is weak, the force to move the counter wheel 40 is also weak. In addition, this force translates into a constraint close to a simple traction on the pawl spring 211 and it is combined with the maintenance of the pawl 210 between the teeth by friction, which causes the pawl spring 211 to self -position. The pawl spring 211 is also disarmed in its functional position, which means that a very low force must be exerted to lift it during the winding phase. If the return spring 213 is weak, the frictional force of the feeler 230 on the cam 30 is also weak. Consequently, the disturbance due to the mechanism 1 according to the invention on the running of the movement driving the cam 30 is reduced to a much lower value compared to the known solutions.

[0117] Indeed, the force necessary for unlocking the jumping mobile 40 is low and that necessary for its training is also weak, because the jumping mobile 40 is free once unlocked.

[0118] These weak forces nevertheless allow the mechanism 1 according to the invention a strong hold of the jumping mobile 40, thanks to the shape of its end 110.

[0119] Thus, the disturbance due to the mechanism 1 according to the invention on the running of the movement driving the cam 30 is reduced to a much lower value than is the case in the known movements, in which the jumping mobile is indexes by a traditional jumper.

[0120] In a preferred variant, the pawl spring 211 comprises a first end 2110 which connects it to the body 201 and which has a width smaller than the width of the main body of the pawl spring 211, for example a width included in the range 20 pm - 40 pm: this allows a better displacement of the pawl spring 211. In correspondence of its second end is the pawl 210.

[0121] As a general rule, this minimum width is concentrated in a small zone at the base of the springs. This arrangement makes it possible to maintain great flexibility while eliminating the risk of the blades buckling. In addition, the tilting of the free head of the springs is better controlled.

[0122] In the variant illustrated in FIG. 4, between the first end 2110 and the pawl 210, the pawl spring 211 comprises a first substantially linear portion 2111, a second substantially linear portion 2112 which forms an angle a with respect to the first portion and a substantially linear third portion 2113 and substantially parallel to the first portion 2111. The second portion 2112 is placed between the first portion 2111 and the third portion 2113. In a variant, Lang le a is included in the range 190°- 220°. However, the value of this angle a may vary, provided that a connection between the portions of the pawl spring 211 is ensured.

[0123] In the alternative variant illustrated in FIG. 20, the pawl spring 211 comprises a single substantially linear portion 2111 and a pad 2114 (linear or curved). This slider 2114 is optional and it is used if the clockwork mechanism allows a reset to zero. In particular, it comes into contact with the head of at least one tooth of the spindle 40 during a reset-to-zero phase, thus creating friction by maintaining the pawl 210 and the blocker 10 in the disengaged position, as shown see further.

[0124] In the variant of figure 4, this slider is "integrated" into the body of the pawl spring 211, i.e. a portion of the pawl spring 211 of figure 4 comprises a friction zone (in particular the zone located between the portions 2112 and 2113) linear or in the shape of an arc having a radius equal to or close to that of the mobile jumping 40 to avoid wear, and substantially concentric with the mobile jumping 40 in the setting position to zero, which comes into contact with the head of at least one tooth of the jumping mobile 40 during a reset-to-zero phase, thus creating friction by maintaining the pawl 210 and the blocker 10 in the disengaged position.

The pawl 210 of Figure 4 comprises a first protuberance 2101, a second protuberance 2102, these two protuberances defining a substantially triangular zone. The pawl 201 also includes a tail 2103, the shape of which can vary (cf for example the shape of FIG. 20).

[0126] The first protuberance 2101, as well as the surface 2104 between the first protuberance 2101 and the second protuberance 2102 are intended to come into contact with the toothed portion of the jumping mobile 40. The second protuberance 2102 in "normal" function of the watch mechanism 1, namely when the clockwork mechanism 1 is not used to reset the counter wheel 40, cooperates with the first surface 1201 of the blocker 10 defining a hollow which, during the maximum winding of the pawl spring 211 allows that the pawl 210 does not lift the blocker 10.

[0127] In a preferred variant, the recess 2105 between the second protuberance 2102 and the tail 2103 has a shape which allows that in the event of shocks, the pawl 210 is in contact in correspondence of at least two points of the recess 140 of the blocker 10.

[0128] In a preferred variant, in the event of shocks, the mechanism according to the invention is arranged so that at the same time the head of a tooth of the jumping mobile 40 comes into contact with the body of the pawl spring 211 in correspondence of at least one other point of contact, which gives a total of three points of contact: this implies that in the event of shocks, the pawl spring 211 does not undergo any torsion.

[0129] The tail 2103 is arranged to cooperate with the surface 1021 of the first protuberance 102 of the blocker 10, in order to limit the pawl 210 of the rocker 20. In other words, during the training of the jumping mobile 40, this surface 1021 prevents the pawl 210 from disengaging.

[0130] In a preferred variant, the surface 2104 between the first protuberance 2101 and the second protrusion 2102 is not straight, but curved outwards: this concave surface makes it possible to optimize the energy consumption of the mechanism according to the 'invention.

[0131] The trigger spring 212 comprises a first end 2120 which connects it to the body 201 and which has (as for the pawl spring 211) a width smaller than the width of the main body of the trigger spring 212, for example a width included in the place 20 μm - 40 μm: this allows a better movement of the trigger spring 212. In correspondence of its second end is the trigger 220.

[0132] In the variant illustrated in FIG. 4, between the first end 2120 and the trigger 220, the trigger spring 212 comprises a first substantially linear portion 2121 and a second substantially linear portion 2122 which forms an angle β with respect to the first portion. In a variant, the angle β is comprised in the range 140°-170°. This makes it possible to leave room for the second protuberance 103 while maintaining the lifting force of the ascender 10 substantially in traction.

In an important variant of the invention and as will be seen later, when the trigger spring 212 is wound, the pawl spring 211 is not being wound and vice versa. This makes it possible to "smooth" the energy consumption of the mechanism according to the invention over the time of its use, while avoiding the peaks of the state of the art.

The body 201 of the latch 20 may also include at least one recess 250 (four in the example of Figure 4 and five in the example of Figure 20). These recesses 250, of variable shape, also allow the watch mechanism 1 to better withstand shocks, by balancing the mechanism 1 in addition to or as an alternative to the three contact points described above and to the counterweight zone 231.

[0135] The body 201 of the rocker 20 may comprise, when the mechanism 1 also allows a reset-to-zero of the jumping mobile 40, a protuberance 260 defined by surfaces which are substantially perpendicular in the example of FIG. 4: the surfaces 2601 and 2602 intended to cooperate with the hammer 60 during the resetting.

[0136] The feeler 230 is intended to come into contact with the cam 30. In a preferred variant, during the rotation of the cam 30 this contact is continuous, permanent. Unlike the finger 50 'of the state of the art illustrated in Figure 1, which comes into contact with the wheel 40' only when a displacement of the wheel 40 'is desired, in the mechanism 1 according to the invention this contact is permanent, like a real gear. This implies that the value of the ratio between the torque and the speed of the cam 30 is substantially the same as that of the jumping mobile 40.

This also implies the existence of a permanent friction between the cam 30 and the feeler 230. However, this friction is advantageously exploited to arm the return spring 213 and can be used to counter any floating of the previous mobiles.

The rotation of the cam 30 causes a translational movement of the point of contact between the cam 30 and the feeler 230: as will be seen later, this results in a rotational movement of the rocker 20 around its axis. rotation 200.

[0139] In the variant of Figure 4, the counterweight zone 231 comprises a support zone 232 aimed at the tax 200 to perform measurements, for example measurements of the torque consumed and/or supplied by the mechanism according to the invention, such as the measurement of the torque to lift the blocker, etc.

[0140] The return spring 213 allows the rocker 20 to rest on the cam 30. Advantageously, the shape of the cam is designed to arm the return spring 213 more or less according to the torques to be restored necessary during the Training position.

[0141] In the variant illustrated in Figure 4, the return spring 213 comprises a first substantially linear portion 2131, a second substantially curved portion 2132 and a third substantially linear portion 2133 aligned with the first portion 2131.

The second portion 2132 is arranged to cooperate with a support pin 50, visible in Figure 2. The shape of this second portion 2132 is also arranged to optimize the energy consumption of the mechanism 1.

[0143] In the variant of figure 20, the return spring 213 does not include a second substantially curved portion 2132 like that of figure 4.

We will now describe an example of the operation of the watch mechanism 1 which will be illustrated with reference to Figures 5 to 13.

[0145] Figure 5 illustrates a top view of an embodiment of the clockwork mechanism 1 according to the invention, in the starting position (phase 0).

In this phase 0, the feeler 230 rests on the first portion 310 of the cam 30. The cam rotates in the direction indicated by the arrow F1.

In phase 0, the end 110 of the blocker 10 is engaged in the hollow 410 between two consecutive teeth 411 of the counter wheel 40, thus blocking its position.

[0148] In phase 0, the pawl 210 comes into contact with another tooth of the counter wheel 40, in particular via its surface 2104 between the first protuberance 2101 and the second protuberance 2102. The pawl spring 211 is slightly pre- armed.

[0149] In phase 0, the spring of the trigger 212 is pre-cocked and the trigger 220 presses against the blocker 10. In particular, the free end of the finger 2201 of the trigger 220 comes into contact with the first surface 1041 of the third protuberance 104 of the blocker 10.

[0150] In phase 0, return spring 213 is also pre-armed and presses rocker 20 on cam 30.

[0151] Figure 6 illustrates a top view of the clock mechanism of Figure 5, when the pawl 210 is raised (phase 1).

In this phase 1, the feeler 230 moves along the first portion 310 of the cam 30. The cam always rotates in the direction indicated by the arrow F1.

In phase 1, the end 110 of the blocker 10 is still engaged in the hollow 410, thus blocking its position, as in phase 0 of Figure 5.

[0154] In phase 1, the pawl 210 rises on the tooth 411, via its surface 2104, thereby winding the pawl spring 211. Note that in this phase the trigger spring is not being wound, but he keeps his pre-armage pressing blocker 10.

[0155] In phase 1, the free end of the finger 2201 of the trigger 220 advances along the first surface 1041 of the third protuberance 104 of the blocker 10.

[0156] In phase 1, the return spring 213 is armed and presses the rocker 20 on the cam 30.

FIG. 7 illustrates a view from above of the watch mechanism 1 of FIG. 5, during the transition from the winding of the pawl spring to the winding of the trigger spring (phase 2).

In this phase 2, the feeler 230 continues to move along the first portion 310 of the cam 30. The cam still rotates in the direction indicated by the arrow F1.

[0159] In phase 2, the end 110 of the blocker 10 is still engaged in the recess 410, thus blocking its position, as in phases 0 and 1 of Figures 5 and 6.

In phase 2, pawl 210, and in particular its protrusion 2201, is mounted on tooth 411, which completes the phase during which pawl spring 211 is charged. This corresponds in the variant illustrated to the beginning of the winding of the trigger spring 212.

[0161] In particular, in phase 2, the free end of the finger 2201 of the trigger 220 reaches the end of the first surface 1041 of the third protuberance 104 of the blocker 10. At the same instant, the beak 2202 of the trigger 220 comes into contact with the surface 1031 of the hook 103 of the blocker, which makes it possible to arm the trigger spring 212. At the end of phase 2, the free end of the finger 2201 of the trigger can move away from the blocker 10 .

[0162] In phase 2, the return spring 213 is armed and still presses the rocker 20 on the cam 30.

[0163] FIG. 8 illustrates a top view of the timepiece mechanism of FIG. 5, when the trigger has fallen behind the hook 103 of the blocker 10 (phase 3).

In this phase 3, the sensor 230 continues to move along the first portion 310 of the cam 30. The cam still rotates in the direction indicated by the arrow F1.

[0165] In phase 3, the end 110 of the blocker 10 is still engaged in the hollow 410, thus blocking its position, as in phases 0 and 1 of Figures 5 and 6.

In phase 3, pawl 210, in particular its protrusion 2201, descends from head 412 of tooth 411.

[0167] In phase 3, the free end of the finger 2201 of the trigger 220 moves along the recess 1044 of the blocker 10. that the hook 103 is in correspondence of the second recess 2204 of the trigger.

[0168] In phase 3, the return spring 213 is still armed and presses the rocker 20 on the cam 30.

[0169] FIG. 9 illustrates a view from above of the timepiece mechanism of FIG. of the portion 310. The cam 30 always rotates in the direction indicated by the arrow F1.

[0170] In phase 4, the end 110 of the blocker 10 is still engaged in the hollow 410, thus blocking its position, as in phases 0 and 1 of Figures 5 and 6.

[0171] In phase 4, the pawl 210 is slightly lifted from the tooth 411 and its protuberance 2202 engages in the hollow defined by the first surface 1201 of the ascender 10.

[0172] In phase 4, the free end of the finger 2201 of the trigger 220 continues to move along the recess 1044 of the ascender 10. At the same instant, the nose 2202 of the trigger 220 lifts off the hook 103 10: this represents a fall safety of the trigger 220.

[0173] In phase 4, the return spring 213 is still armed and presses the rocker 20 on the cam 30.

[0174] FIG. 10 illustrates a view from above of the timepiece mechanism of FIG. 5, during the start of the driving of the jumping mobile 40 in the direction indicated by the arrow F3 (phase 5). In other words, in the phase of FIG. 10 the ascender 10 is in the driving position.

[0175] In this phase 5, the sensor 230 is in contact with the cam in correspondence of its second portion 320. The second portion 320, in particular its slope in the example illustrated, regulates the drive speed of the counter wheel. 40. Cam 30 always rotates in the direction indicated by arrow F1. In another variant, the change in direction of rotation of the sensor 230 and therefore the driving of the counter wheel 40, is instantaneous: in this case the second portion 320 of the cam 30 is arranged so as to avoid contact with the feeler 230.

[0176] In phase 5, the end 110 of the blocker 10 is raised relative to the hollow 410.

[0177] In phase 5, pawl 210, in particular its protrusion 2101, rests on tooth 411, in particular on one of its sides, thus causing counter wheel 40 to rotate in the direction indicated by arrow F3 .

In phase 5, the free end of the finger 2201 of the trigger 220 continues to move along the recess 1044 of the blocker 10. At the same instant, the beak 2202 of the trigger 220 presses against the hook : this allows the trigger 220 to lift the end 110 of the ascender 10.

[0179] In phase 5, the return spring 213 restores the energy of its winding. In this example, the point of contact between the feeler 230 and the cam moves along the portion 320, in particular according to a translational movement indicated by the arrow F2 in figure 10.

Advantageously, the blocker 10 of the mechanism according to the invention lifts exactly when it is necessary to drive the counter wheel 40. This self-synchronism is guaranteed by the fact that the rocker 20 comprises both the trigger 220, which acts on the blocker 10, the pawl, which makes it possible to advance the counter wheel 40 and the sensor 230, which makes it possible to transfer via the cam 30 to the mechanism the information of the moment when the counter wheel 40 must be driven.

FIG. 11 illustrates a top view of the clockwork mechanism of FIG. 5, at the limit of the self-unhooking of the trigger (phase 6).

In this phase 6, the sensor 230 advances in the direction indicated by the arrow F2 on the second portion 320 of the cam 30, which always rotates in the direction indicated by the arrow F1.

In phase 6, the end 110 of the blocker 10 is raised more relative to the hollow 410. In particular, its distance from the reue counter40 is the greatest that the mechanism 1 according to the invention can allow.

[0184] In phase 6, the pawl 210, in particular its tail 2103 approaches the surface 1021 of the first protuberance 102 of the blocker 10, which prevents the pawl 210 from coming out of the teeth in the event of an impact.

[0185] In phase 6, at the same instant the free end of the finger 2201 of the trigger 220 reaches the end of the recess 1044 of the blocker 10, bounded by the asperity 1046.

In phase 6, the return spring 213 continues to restore the energy of its winding. Its shape makes it possible to vary the direction of the reaction force of the pin 50 on the rocker 20 and therefore to vary the lever arm relative to the pivot point 200 and therefore to modulate the torque restored to the rocker 20.

FIG. 12 illustrates a view from above of the watch mechanism 1 of FIG. 5, when the trigger 220 releases the blocker 10 and pushes it onto the teeth of the jumping mobile 40 (phase 7).

In this phase 7, the feeler 230 continues to advance in the direction indicated by the arrow F2 on the second portion 320 of the cam 30, which still rotates in the direction indicated by the arrow F1.

In phase 7, the end 110 of the blocker 10 approaches the head 412 of one of the two teeth which defined the hollow 410 in which it was engaged in the blocking position. In particular, its first surface 1101 which is flat rests on the head 412, which in the illustrated example is concentric with Tax 400, by "sliding" on this head 412.

[0190] In phase 7, the pawl 210, in particular its protrusion 2101 is based on the tooth 411, in particular on one of its sides, as was the case in FIG. 10, thus causing the wheel to turn. counter 40 in the direction indicated by arrow F3.

[0191] In phase 7, the free end of the finger 2201 of the trigger 220 comes into contact with the first surface 1041 of the blocker 10, thereby pushing the blocker 10 towards the teeth of the counter wheel 40. At the same time , the spout 2202 moves away from the hook 103.

[0192] In phase 7, the return spring 213 continues to restore the energy of its winding.

[0193] Figure 13 illustrates a top view of the clockwork mechanism 1 of Figure 5, when the cam 30 and the rocker 20 have returned to their positions of phase 0 of Figure 5, but the blocker 10 has not finishes positioning the counter wheel 40 (phase 8).

[0194] In this phase 8, the feeler 230 reaches the end of its path on the second portion 320 of the cam 30, which still rotates in the direction indicated by the arrow F1.

[0195] In phase 8, the end 110 of the blocker 10 begins to enter the hollow 410' successive to that in which it was engaged in phase 0 of FIG. 110 rests on the head 412, in order to bring the end 110 back into the hollow 410'.

[0296] In phase 8, the pawl 210, in particular its protuberance 2101, continues to rest on the tooth 411, in particular on one of its sides, as was the case in FIGS. 11 and 12, making thus turn counter wheel 40 in the direction indicated by arrow F3.

[0197] In phase 8, the free end of the finger 2201 of the trigger 220 continues to move along the first surface 1041 of the blocker 10, and approaches the recess 1044.

[0198] In phase 8, the return spring 213 finishes restoring the energy of its winding.

[0199] Next, the blocker 10 positions the counter wheel 40 by engaging the recess 410', as was the case for phase 0 of FIG. 5. The fourth surface 1104 of the first end 110 of the blocker allows the precision of the positioning of the blocker 10 in this hollow.

[0200] An example of the operation of the reset-to-zero of the clockwork mechanism 1 will now be illustrated with reference to FIGS. 14 to 19.

[0201] FIG. 14 illustrates a top view of another embodiment of the timepiece mechanism 1 according to the invention, in which the cam 30, the rocker 20 and the blocker 10 are in any position (phase 0 of the reset-ä-zäro).

[0202] In the case of Figure 14, the clockwork mechanism 1 also includes:

- a hammer 60, arranged to cooperate with the rocker 20 when resetting the jumping mobile 40;

- a support pin 70 for the hammer spring 610;

- a manual actuator such as for example a button 90 to actuate the resetting of the jumping mobile 40.

[0203] The hammer 60 is arranged to pivot around an axis of rotation 600 and comprises in particular:

- a hammer spring 610, substantially parallel to the main body 601 of the hammer 60; in a variant, the hammer spring 610 defines with the hammer a groove 611; in another variant, the hammer spring 610 is not integral with the hammer 60;

- A first protrusion 690 (which in the example of Figure 14 has a substantially rectangular shape in the plane of the body 601) arranged to come (directly) into contact with the manual actuator 90;

- A second bent projection 620 (which in the example of Figure 14 has a substantially rectangular shape in the plane of the body 601) arranged to come into contact with the projection 260 of the rocker 20;

- a third protrusion 680 arranged to come into contact with the core 80 linked to the counter wheel 40; And

- a fourth protrusion or face 602 arranged to come into contact with a component such as the plate 2, partially illustrated in FIG. 14, a pin, a bridge, the manual actuator 90, etc.

[0204] In particular, in phase 0 of the reset-to-zero, the plate 2 limits the recoil of the hammer 60.

[0205] In phase 0 of the reset-to-zero, the hammer spring 610 maintains the hammer 60 in the retracted position.

[0206] In phase 0 of the reset-to-zero, hammer 60 is not in contact with rocker 20.

[0207] In phase 0 of the reset-to-zero, the hammer 60 is also not in contact with the actuator 90. In another variant (not illustrated), the hammer 60 could be in contact with the actuator 90.

[0208] In phase 0 of the reset-to-zero, the feeler 230 is in contact with the cam 30.

[0209] Figure 15 illustrates a top view of the clockwork mechanism of Figure 14, when the hammer 60 comes into contact with the rocker 20 (phase 1 of the reset-to-zero).

[0210] In phase 1 of the reset-to-zero, the actuator 90 actuates the hammer 60 via its protuberance 690.

[0211] Hammer 60 therefore comes into contact with rocker 20 via its bent protuberance 620.

[0212] In phase 1 of the reset-to-zero, the counter wheel 40 is still locked via the end 110 of the blocker 10.

[0213] In phase 1 of the reset-to-zero, the hammer 60 is not yet in contact with the heart 80.

[0214] In phase 1 of the reset-to-zero, the feeler 230 is still in contact with the cam 30.

[0215] Figure 16 illustrates a top view of the clockwork mechanism 1 of Figure 14, when the hammer 60 has pushed the rocker 20 until the pawl 210 and the blocker 10 are disengaged (phase 2 of the reset-to-zero ).

[0216] In phase 2 of the reset-to-zero, the feeler 230 is no longer in contact with the cam 30.

[0217] In phase 2 of the reset-to-zero, the hammer 60 pushes the rocker 20 via the bent protuberance 620 until the pawl 210 and the blocker 10 are engaged. In particular, the end 110 is disengaged from the hollow 410 , thereby releasing counter wheel 40. Further, the area between portions 2112 and 2113 of pawl spring 211 as discussed above is a "skate" area 2114; it is substantially concentric with jumping spindle 40 in the reset position This shoe 2114 lands on the head of at least one tooth 411 of the counter wheel 40, allowing both the pawl to be in the disengaged position and allowing the blocker to be lifted via the contact between the pawl 210 and the blocker 10.

[0218] In the variant of FIG. 16, this slider 2114 is integrated into the spring of the pawl 211, ie it belongs to its main body. In the variant of FIG. 20, this shoe 2114 is defined by a portion 2114 linked to the body of the pawl spring 211 but remote from this body.

[0219] In phase 2 of the reset-to-zero, the hammer 60, in particular its protrusion 680, is close to the heart 80. The coordination with the disengagement by the rocker is carried out by the hammer 60.

FIG. 17 illustrates a view from above of the watch mechanism 1 of FIG. 14, during the start of the reset-to-zero (phase 3 of the reset-to-zero).

[0221] In phase 3 of the reset-to-zero, the feeler 230 is no longer in contact with the cam 30.

[0222] In phase 3 of the reset-to-zero, the hammer 60 no longer pushes the rocker 20 but, still via its elbow protuberance 620, keeps it in the disengaged position.

[0223] In phase 3 of the reset-to-zero, the end 110 is always disengaged from the recess 410.

[0224] In phase 3 of the reset, the pad 2114 still creates friction which allows both the pawl 210 and the clutch 10 to be in the disengaged position.

[0225] In phase 3 of the reset-to-zero, the hammer 60, in particular its protuberance 680, comes into contact with the reader 80 and causes it to rotate.

[0226] FIG. 18 illustrates a view from above of the clockwork mechanism of FIG. 14, when the jumping mobile is reset to zero (phase 4 of the reset-to-zero).

[0227] In phase 4 of the resetting, the feeler 230 is no longer in contact with the cam 30 and the cam 30 has been reset with its counter wheel not shown.

[0228] In phase 4 of the reset-to-zero, the hammer 60 still maintains the rocker 20 in the disengaged position.

[0229] In phase 4 of the reset-to-zero, the end 110 is always disengaged from the recess 410.

[0230] In phase 4 of the reset-to-zero, the pad 2114 still creates friction which allows both the pawl 210 and the clutch 10 to be in the disengaged position.

[0231] In phase 4 of the reset-to-zero, the hammer 60, in particular its protrusion 680, ends its travel on the heart 80. The orientation of this heart 80 allows both to position the jumping mobile 40 at least a tooth and to add a small additional angle which corresponds to that which will be generated by the friction during the recoil of the hammer 60 and before the blocker 10 is put back into place.

[0232] FIG. 19 illustrates a view from above of the clockwork mechanism of FIG. 14, during the start of the return of the hammer (phase 5 of the reset-to-zero).

[0233] In phase 5 of the reset-to-zero, the feeler 230 approaches the cam 30.

In phase 5 of the reset-to-zero, the hammer 60 still maintains the rocker 20 in the disengaged position.

[0235] In phase 5 of the reset-to-zero, the shoe 2114 always creates friction which makes it possible to hold the counter wheel 40 in a determined position.

[0236] In phase 5 of the reset-to-zero, the hammer 60, in particular its protuberance 680, moves away from the heart 80.

[0237] Finally, the pawl 210 drives a tooth 411 of the counter wheel 40 to repair the counter wheel 40, which in the position of Figure 18 was at least one tooth away. We then return to the initial position, illustrated in figure 14.

An example of operation of correction by step of the clockwork mechanism 1 will now be illustrated with reference to FIGS. 21 to 25.

FIG. 21 illustrates a top view of another embodiment of the timepiece mechanism 1 according to the invention, which allows the displayed information to be corrected in steps. In the clockwork mechanism 1 of FIG. 21, the cam 30, the rocker 20 and the blocker 10 are in any position (phase 0 of the step correction).

[0240] In the case of Figure 21, the clockwork mechanism 1 also includes:

- a hammer 60, arranged to cooperate with the rocker 20 when resetting the jumping mobile 40;

- a support pin 70 for the hammer spring 610;

- a manual actuator such as for example a button 90 to actuate the reset of the jumping mobile 40.

[0241] The hammer 60 is arranged to pivot around an axis of rotation 600 and comprises in particular:

- a hammer spring 610, substantially parallel to the main body 601 of the hammer 60; in a variant, the hammer spring 610 defines with the hammer a groove 611; in another variant, the hammer spring 610 is not integral with the hammer 60;

- a first protrusion 690 (which in the example of Figure 21 has a substantially rectangular shape in the plane of the body 601) arranged to come (directly) into contact with the manual actuator 90;

- A second bent protuberance 620 (which in the example of FIG. 21 has a substantially rectangular shape in the plane of the body 601) arranged to come into contact with the protuberance 260 of the rocker 20; And

- a beak 640 arranged to come into contact with the teeth of the jumping mobile 40.

[0242] In phase 0 of the step correction, the hammer spring 610 maintains the hammer 60 in the retracted position.

In phase 0 of the step correction, the blocker 10, in particular its end 110, is engaged in a recess in the toothing of the jumping mobile 40, thus maintaining its position.

In phase 0 of the step correction, hammer 60 is not in contact with rocker 20.

In phase 0 of the step correction, the hammer 60 is not in contact with the actuator 90 either.

In phase 0 of the correction by steps, feeler 230 is in contact with cam 30.

[0247] In phase 0 of the step correction, the beak 2202 of the trigger 220 is in contact with the first surface

1031 of the hook 103. The figure 22 illustrates a top view of the embodiment of figure 21, when the pawl 210 is based on the blocker 10 (phase 1 of the step correction).

[0248] Figure 22 illustrates a top view of the embodiment of Figure 21, when the pawl rests on the blocker (phase 1 of the step correction).

[0249] In phase 1 of the step correction, hammer 60 is actuated by actuator 90, which causes hammer 60 to contact rocker 20 via its bent protrusion 620. Notably, bent protuberance 620 of the hammer 60 pushes the protuberance 260 of the rocker 20.

[0250] Consequently, the sensor 230 is no longer in contact with the cam 30. In addition, the beak 2202 of the trigger 220 goes beyond the hook 103 and the trigger 220 engages in the recess 1045 of the blocker 10.

[0251] In phase 1 of the correction by step, the pawl 210, in particular its second protuberance 2102, rests on the blocker 10, in particular on its surface 1201.

In phase 1 of the step correction, the blocker 10, in particular its end 110, remains engaged in a recess in the toothing of the jumping mobile 40, thus maintaining its position.

[0253] Figure 23 illustrates a top view of the embodiment of Figure 21, when the ascender 10 begins to rise and the shoe 2144 to press against the toothing 411 of the jumping mobile 40 (phase 2 of the correction per step).

[0254] In phase 2 of the step correction, the hammer 60 is still in contact with the rocker 20 via its bent protuberance 620, the feeler 230 is no longer in contact with the cam 30 and the trigger 220 is still engaged. in the recess 1045 of the blocker 10.

In phase 2 of the step correction, the pad 2144 bears against the toothing 411 of the jumping mobile 40, as indicated by the arrow F4.

[0256] In phase 2 of the step correction, the pawl 210, in particular its second protuberance 2102, disengages from the hollow defined by the concave surface 1201 and advances towards the convex surface 1202.

[0257] In phase 2 of the step correction, the blocker 10, in particular its end 110, begins to disengage from the hollow 410 of the toothing of the jumping mobile 40, thus beginning to unlock the jumping mobile 40.

In phase 2 of the correction by step, the beak 640 of the hammer 60 comes closer to the jumping mobile 40.

FIG. 24 illustrates a top view of the embodiment of FIG. 21, when the beak 640 of the hammer 60 comes into contact with a tooth 411 of the jumping mobile 40 (phase 3 of the step correction).

[0260] In phase 3 of the step correction, the bent protuberance 620 begins to pass the protuberance 260 of the rocker 20, while remaining in contact with the rocker 20. The trigger 220 continues its displacement on the blocker 10, passes the recess 1045 of the blocker 10 and comes into contact with the second asperity 1047 of the blocker 10.

[0261] In phase 3 of the correction by step, the pawl 210, in particular its second protuberance 2102, rises on the convex surface 1202 of the blocker 10.

In phase 3 of the step correction, the blocker 10, in particular its end 110, completely disengages from the hollow 410 of the toothing of the jumping mobile 40, and the jumping mobile 40 is completely unlocked.

[0263] In phase 3 of the correction by step, the beak 640 of the hammer 60 comes into contact with a tooth 411 of the jumping mobile 40, which will cause its displacement by step and therefore a correction of the information carried by the mobile. jumping 40.

FIG. 25 illustrates a top view of the embodiment of FIG. 21, when the jumping mobile 40 has rotated (phase 4 of the step correction).

[0265] In phase 4 of the correction by step, the bent protuberance 620 has exceeded the protrusion 260 of the rocker 20, while remaining in contact with the rocker 20. The trigger 220 is still in contact with the second asperity 1047 of the blocker 10.

[0266] In phase 4 of the step correction, the pawl 210, in particular its second protrusion 2102, is still on the concave surface 1202 of the blocker 10.

[0267] In phase 4 of the correction by step, the beak 640 of the hammer 60 engages in the hollow 410 consecutive to the tooth 411 with which it is in contact in FIG. the direction indicated in the arrow F5, which causes a stepwise correction of the information carried by the jumping mobile 40.

[0268] We then return to the initial position, illustrated in figure 21.

[0269] Although in the examples of Figures 21 to 25 the beak 640 is arranged to rotate the jumping mobile 40 in only one direction of rotation, it is possible to modify its shape so that it can rotate the jumping mobile 40 in the other direction of rotation (opposite to that indicated by the arrow F5 in figure 25). For example, beak 640 can be arranged to step two teeth in one direction (e.g., counterclockwise), at a time, since the System itself will step in the opposite direction (e.g., counterclockwise). time) at the end of the function.

[0270] It is also possible to modify its shape so that it can rotate the jumping mobile 40 both in the direction of rotation indicated by the arrow F5 and also in the opposite direction of rotation: in this variant, it is thus possible to increase and decrease the information carried by the jumping mobile 40. In a variant, the mechanism according to the invention comprises a single actuator 90 which makes it possible both to increase and to decrement the information carried by the mobile jumping 40, depending for example on the number of times that this actuator 90 is actuated by the user. In another variant, the mechanism according to the invention comprises two separate actuators, one for increasing and the other for decreasing the information carried by the jumping mobile 40.

Numbers

[0271]

1021

1031

1041

1042

1043

1044

1045

1046

1047 1101 1102

and reference signs used in the figures

Watch mechanism

Platinum

Blocker

Seesaw

Actuating device (cam)

Speedometer wheel

Support pin for return spring 213 of rocker 20

Hammer (zeroing or correction)

Support pin for hammer spring 601

heart

Manual actuator

Axis of rotation of the ascender 10

Blocker arm

First bulge

Second protrusion (hook)

Third

First end of blocker 10

Second end of ascender 10

First blocker recess 10

Second blocker recess 10

Axis of rotation of the rocker 20

Rocker body

Pawl

Pawl spring

Trigger spring

Spring

Trigger

Feeler

counterweight area

Support area for taking measurements

spacer

recess

Seesaw protuberance 20

Cam rotation axis 30

First portion of cam profile 30

Second portion of cam profile 30

40 meter wheel rotation axis

Hollow between two consecutive teeth

40 meter wheel tooth

Head of tooth 411

Hammer rotation axis 60

Hammer 60 main body

Fourth Hammer Protuberance 60

hammer spring

Hammer Throat

Second protuberance (cubit) of hammer 60

Hammer 60 beak

Third Hammer Protrusion 60

First Hammer Protrusion 60

First surface of the first protrusion 102

First surface of second protuberance 103

First surface of third protuberance 104

Second surface of third protrusion 104

Third surface of the third protuberance 104

First recess of the third protuberance 104

Second recess of the third protuberance 104

First asperity of the third protuberance 104

Second asperity of the third protuberance 104

First end surface 110

Second surface of end 110

Claims (26)

1103 Third surface of end 110 1104 Fourth end surface 110 1201 First end surface 120 2101 First ratchet protrusion 210 2102 Second pawl protrusion 210 2103 Ratchet tail 210 2104 Ratchet Surface 210 2105 Pawl Bulge 210 2110 First end of pawl spring 211 2111 First portion of pawl spring 211 2112 Second portion of pawl spring 211 2113 Third portion of pawl spring 211 2114 Skate 2120 First end of trigger spring 212 2121 First portion of trigger spring 212 2122 Second portion of trigger spring 212 2131 First portion of return spring 213 2132 Second portion of return spring 213 2133 Third portion of return spring 213 2201 Trigger finger 220 2202 Trigger nose 220 2203 First depression of the trigger 220 2204 Second trigger recess 220 2601 First surface of protuberance 260 2602 Second surface of protuberance 260 10' Known hour wheel 20' Known twenty-four hour wheel 30' Known Pin 40' Wheel (or star) of weekdays known 50' Gear finger known 100' Known necklace 1000' Known watch mechanism 2000' Box (x Angle of pawl spring 211 ß Trigger spring angle 212 F1 Arrow F2 Arrow F3 Arrow F4 Arrow F5 Arrow L Return spring width 231 Claims 1. Clockwork mechanism (1) for driving and blocking a jumping mobile (40), said clockwork mechanism (1) comprising: - an actuating device (30); - said jumping mobile (40), comprising at least one toothed portion (411); - a blocker (10), comprising: - an end (110) having a shape able to be engaged in a hollow (410) between two consecutive teeth (411) of the toothed portion of the jumping mobile (40); - a rocker (20), comprising: - a trigger (220), arranged to come into contact with said blocker (10); - a pawl (210), arranged to come into contact with said jumping mobile (40); - a sensor (230), arranged to come into contact with said cam (30); in which said blocker (10) is arranged to pivot around an axis (100) under the action of the trigger (220) between: - a blocking position, in which said actuating device (30) rotates said probe (230) in a first direction around an axis (200) of the rocker (20) and in which said end (110) is engaged in the hollow (410) between two consecutive teeth (411) of the jumping mobile (40), thereby blocking the position of the jumping mobile (40), and - a drive position, in which said actuating device (30) rotates said probe (230) in a second direction opposite to the first direction around the axis (200) of the rocker (20) and in which said end (110) is disengaged from said recess (410), thereby allowing said pawl (210) to rotate said jumper (40). 2. The clockwork mechanism (1) according to claim 1, in which the latch (20) comprises: - a pawl spring (211); And - a trigger spring (212). 3. The watch mechanism (1) according to claim 2, wherein in the locking position, the pawl (210) is arranged to monier on a tooth (411) of the jumping mobile (40), which makes it possible to advance the spring pawl (211) of a tooth of the jumping mobile (40). 4. The watch mechanism (1) according to one of claims 2 or 3, wherein in the locking position, a beak (2202) of the trigger (220) is arranged to come into contact with a surface (1031) of a hook (103) of the blocker (10), which makes it possible to arm the trigger spring (212). 5. The timepiece mechanism (1) according to one of claims 2 to 4, wherein in the locking position, when winding the trigger spring (212), the pawl spring (211) is not in arming phase and vice versa. 6. The clockwork mechanism (1) according to one of claims 1 to 5, also comprising a return spring (213) connected to the feeler (230) and in which the return spring (213) is arranged to arm itself in blocking position, and to restore this energy in the training position. 7. The watch mechanism (1) according to one of claims 2 to 6, in which the torque required to move the pawl spring (211), the trigger spring (212) and/or the return spring (213) relative to the axis (200) of the rocker (20) is less than or equal to 0.04 N.Mm. 8. The timepiece mechanism (1) according to one of claims 1 to 7, wherein the pawl (210) comprises a tail (2103), a first protuberance (2101) and a second protuberance (2102), these two protuberances defining a substantially triangular area. blocker (10) in the hollow (410) between two teeth (411) in the blocking position. 9. The watch mechanism (1) according to claim 8, in which the first protuberance (2101), as well as a surface (2104) between the first protuberance (2101) and the second protuberance (2102) are intended to come into contact with the toothed portion of the mobile jumping (40). 10. The watch mechanism (1) according to one of claims 8 to 9, wherein a recess (2105) between the second protuberance (2102) and the tail (2103) has a shape which allows that in the event of shocks, the pawl (210) is in contact in correspondence of at least two points of a recess (140) of the blocker (10), and at the same time a head (412) of a tooth (411) of the jumping mobile (40 ) comes into contact with the body of the pawl spring (211) in correspondence of at least one other point of contact, which allows that in the event of shocks, the pawl spring (211) does not undergo any torsion. 11. The watch mechanism (1) according to one of claims 8 to 10, in which the tail (2103) is arranged to cooperate with a surface (1021) of the first protrusion (102) of the blocker (10), in order to limit the pawl (210) of the rocker (20). 12. The clockwork mechanism (1) according to one of claims 1 to 11, wherein the rocker (20) comprises at least one recess (250) also allowing the clockwork mechanism (1) to balance the mechanism (1) by case of shocks. 13. The timepiece mechanism (1) according to one of claims 1 to 12, in which the end (110) of the blocker (10) comprises a first surface (1101) arranged to rest on a head (412) of a tooth (411) of the jumping mobile (40) in the drive position. 14. The watch mechanism (1) according to one of claims 1 to 13, wherein the end (110) of the blocker (10) comprises a fourth surface (1104) arranged to allow precision positioning of the blocker (10) in the hollow (410) between two teeth (411) in the locking position. 15. The timepiece mechanism (1) according to one of claims 1 to 14, in which the end (110) of the blocker (10) is a first end of an arm (101) of the blocker (10), which is extends from the axis of rotation (100) of the blocker (10), said arm (101) comprising a second end (120) arranged to come into contact with the pawl (210) of the rocker (20). 16. The watch mechanism (1) according to one of claims 1 to 15, in which the blocker (10) comprises a first protrusion (102) comprising a surface (1021) arranged to limit the pawl (210) of the rocker ( 20) in training position. 17. The clockwork mechanism (1) according to one of claims 1 to 16, in which the blocker (10) comprises a second protuberance or hook (103) and a third protuberance (104) intended to cooperate with the trigger (210). of the rocker (20). 18. The clockwork mechanism (1) according to claim 17, in which the third protuberance (104) is defined by: - a first surface (1041) arranged to form a support for the trigger (210); - a second surface (1042), arranged to allow the trigger (210) to be moved back for the self-release; - a third surface (1043) arranged to constitute a support for the trigger after the winding of the trigger spring (211), after the passage of the beak (2202) beyond the hook (103). 19. The timepiece mechanism (1) according to one of Claims 2 to 18, in which the trigger (220) comprises a finger (2201) substantially straight and substantially perpendicular to at least a portion of the trigger spring (212), said beak ( 2202), having a substantially triangular shape, and wherein the finger (2201) and the beak (2202) define a first recess (2203), the beak (2202) and the trigger spring (212) define a second recess (2204 ). 20. The horological mechanism (1) according to one of claims 1 to 19, in which the rocker (20) is arranged to pivot around the axis of rotation (200) and comprises a body (201) which belongs to a first plane and a counterweight zone (231), which can carry the sensor (230) and belonging to a second plane substantially parallel to the first plane and at least one spacer (240) between the body (201) and the counterweight zone (231). 21. The clockwork mechanism (1) according to one of claims 1 to 20, said actuating device comprising a portion (320) arranged to control the speed of the jumping mobile (40) in the drive position. 22. The clockwork mechanism (1) according to one of claims 1 to 21, comprising: - a hammer (60), arranged to cooperate with the rocker (20) during a reset of the jumping mobile (40); - a support pin (70) for a hammer spring (601); - a manual actuator (90) to actuate the resetting of the jumping mobile (40). 23. The timepiece mechanism (1) according to claim 22, in which the hammer (60) comprises: - said hammer spring (610); - a first protrusion (690) arranged to come into contact with the manual actuator (90); And - a second protrusion (620) arranged to come into contact with a protuberance (260) of the rocker (20). 24. The timepiece mechanism (1) according to claim 23, in which the hammer (60) comprises: - a third protrusion (680) arranged to come into contact with a core (80) linked to the counter wheel (40); And - a fourth protuberance or face (602) arranged to come into contact with a component such as a plate (2), a pin, a bridge, and/or the manual actuator (90). 25. The watch mechanism (1) according to one of claims 23 to 24, said pawl spring (210) comprising a substantially linear or curved part (2112, 2113; 2114) arranged to create friction when it comes into contact with a head (412) of at least one tooth (411) of the speedometer wheel (40), allowing both the pawl (210) to be in the disengaged position and allowing the blocker (10) to be lifted via the contact between the pawl (210) and the blocker (10). 26. The timepiece mechanism (1) according to claim 23, in which the hammer (60) comprises: - a beak (640) arranged to come into contact with the teeth of the jumping mobile (40), in order to perform a stepwise correction of Information carried by the jumping mobile (40).