Horology movement fitted with a bidirectional drive mechanism for a jumping indicator

Abstract

The side-view movement is equipped with an indicator (4) and includes a mechanism (6) for driving the indicator by jumping in a first direction, the mechanism includes a wheel plate (8) defining a rotation axis, a rigid portion (10) arranged on the wheel plate and forming a driving finger (12), and a spring (16), the spring having one end rotatably attached to the wheel plate and the other end rotatably attached to the rigid portion, the rigid portion being rotatably movable relative to the wheel plate and connected through an opening (26) that allows the driving finger to retract toward the rotation axis. The mechanism is arranged to contract as the spring is loaded so as to drive the indicator in both directions and to cause the indicator to jump in the first direction. The mechanism subsequently includes a first stop rotatably attached to the wheel plate and a second stop rotatably attached to the rigid part whenever at least the indicator is driven in the second direction, and the first stop and the second stop restrict or prevent the spring from expanding.

Description

Technology Field

[0001] The present invention relates to a timekeeping movement comprising a jumping indicator and a bidirectional drive mechanism for the jumping indicator, as well as a watch comprising the timekeeping movement equipped with such a bidirectional drive mechanism. In particular, the indicator is a date indicator. "Jumping" is considered to mean an indicator that displays discrete values ​​when driven by a timekeeping movement in a given direction of the expected movement for the indicator in jumps in the normal functional direction of the indicator. Meanwhile, in other directions of the movement, the drive may be non-jumping or "dragging" as is known in the timekeeping industry. Thus, in the case of a date indicator, the movement is driven in semi-instantaneous or instantaneous jumps to indicate a sequence of dates while the watch is in operation. However, when the date is corrected by rotation in the opposite direction, the drive may generate gain in the indicator at each period but not necessarily at each jump, which is referred to as "dragging." Background Technology

[0002] EP 3828644 describes a mechanism for driving a jumping indicator that solves the previous technical problem in that it includes a rigid finger drum that is rotationally and translationally guided by an arbor extending through a rectangular hole of the drum, and a spring that is arranged on the finger drum and rotatably attached to a wheel plate that provides a driving couple for the jumping indicator.

[0003] The aforementioned drive mechanism has several disadvantages. First, the spring is designed to expand when the date disc is driven and the spring coil is designed to be supported against the inner wall of the drum when the spring is mounted, which limits the expansion of the spring and prevents it from reaching the plastic range of the spring. This results in a drastic reduction in the active length of the spring. Given manufacturing tolerances for various elements, the loading time of the drive mechanism can vary because the moment the spring contacts the inner wall of the drum can change from one loading to the next, and the angular position of the contact zone can also change. Consequently, the time at which the disc transitions to the next date is inaccurate. Furthermore, another problem arises from the fact that the driving force is transmitted to the finger through the spring coil; therefore, for this purpose, it must be sufficiently rigid / stiff over its entire length, more specifically over the part between the contact zone on the wall of the drum and the mechanism for coupling to this drum arranged at the second end of the spring, and this part must ultimately withstand the entire additional coupling generated from the moment of contact until the moment the indicator jumps.

[0004] An additional problem with the mechanism is that when the indicator is driven, the spring coil tends to apply a radial force to the drum in the area opposite the finger and thus oriented outward in the longitudinal direction of the rectangular hole, thereby moving the finger away from the toothing on the disc. Then, especially in the event of a slight impact in this situation, the finger is more likely to move past the toothing without driving the indicator. Furthermore, it should be noted that this situation reduces the angular path through which the finger can drive the toothing while maintaining contact, so the finger may move past the toothing before accommodating the drive couple over a sufficient angular distance to ensure a date jump, and the date disc remains stationary in an intermediate position or returns to its previous stable position once the finger moves past the toothing. Additionally, lowering the lever arm to apply drive force to the toothing requires an increase in the required drive force for a given drive couple, which also requires an increase in the force provided by the spring and, therefore, its tension.

[0005] Furthermore, the geometry of the coupling mechanism relative to the bed machined from the drum wall allows for sufficient clearance and a certain amount of mobility of the coupling mechanism within the bed, which creates another problem. In fact, when the spring is loaded, this distorts the spring coil and causes the coupling mechanism to rotate on its own due to the sufficient angular clearance provided. This rotation causes the coupling mechanism to slide against the forward axial wall of the bed, which will cause the point of force application from the spring on the finger drum to decrease radially as the spring is loaded. When the spring is loaded to a given level, the driving coupling provided by the spring on the finger decreases in proportion to the descent of the lever arm applying force from the spring to the finger drum. This raises a problem because the driving force from the finger to the indicator tooth decreases at the same rate for a given point of contact. However, as a given drive couple is required to jump the indicator, the spring must generate greater force as the lever arm descends while the spring is loaded; this negatively affects the performance of the side movement, which requires providing more couples after the spring is loaded into the drive mechanism. This also necessitates a spring with dimensions that are more robust than required.

[0006] Finally, the aforementioned driving mechanism allows the indicator to be driven in only one direction. To drive the indicator in the opposite direction, particularly to calibrate the display of such an indicator, an additional mechanism is required, which makes the device for driving the indicator in both directions relatively complex and cumbersome. The problem to be solved

[0007] The present invention aims to provide a mechanism for driving a jumping indicator that does not have the disadvantages of the aforementioned prior art. The present invention also aims to provide a mechanism for driving a jumping indicator that is efficient, accurate in each observation movement including such a mechanism, and whose function is minimally or not interfered with at all by external stresses such as shock. means of solving the problem

[0008] To this end, the present invention relates to a side-view movement equipped with an indicator, comprising a mechanism for driving the indicator in a first direction of the expected movement of the indicator, wherein the driving part jumps in a first direction corresponding to the direction of the movement of the indicator when the side-view movement is functioning normally. The mechanism comprises a wheel plate defining a rotation axis, a rigid part forming a driving finger arranged on the wheel plate and configured to drive the indicator, and a spring having a coil and a first end and a second end, wherein the first end is rotatably attached to the wheel plate and the second end is rotatably attached to the rigid part when the spring is loaded before the indicator jumps in at least the first direction and when the indicator is driven by the driving finger to form this jump. The rigid portion is rotatable with respect to the wheel plate and is rotatably guided about the axis of rotation by an arbor that is aligned with the axis of rotation and extends through an opening of the rigid portion, which allows the driving finger to retract toward the axis of rotation under the action of a radial component of a force that can be applied to the driving finger. According to the present invention, the mechanism is arranged so that when the wheel plate rotates in a first rotational direction and a second rotational direction, respectively, the indicator is driven by the driving finger in a first direction of the indicator's movement and in a second direction opposite to the first direction. Furthermore, the mechanism is arranged so that whenever the spring is loaded, it contracts so that the indicator jumps in the first direction.Additionally, the mechanism includes a first stop rotatably attached to at least a wheel plate and a second stop rotatably attached to a rigid part whenever the indicator is driven in the second direction by the driving finger, and the mechanism is arranged so that the first stop rotates the second stop whenever the indicator is driven in the second direction by the driving finger, the first stop, and the second stop, so that the first stop and the second stop limit or prevent the expansion of the spring. More specifically, when the driving finger is not in contact with the indicator, the initial angular distance between the first stop and the second stop is less than half the normal angular movement of the second stop relative to the first stop when the spring contracts as the spring is loaded to drive the indicator in the first direction.

[0009] In a preferred variant, the initial angular distance between the first stop and the second stop is less than 1 / 4 of the angular path. In an advantageous variant, when the driving finger is not in contact with the indicator, the spring is in a substantially equilibrium position (no pre-tension by design).

[0010] Due to the aforementioned features of the present invention, the driving mechanism can drive the indicator in both directions, which allows the user to rapidly drive the indicator forward and backward, particularly through a control mechanism accessible from the outside of the watch case, thereby making it advantageous to perform corrections on the display associated with the indicator, i.e., variable data displayed by the indicator. A notable feature is that, in order to drive the indicator in the jumps in the first direction (normal function direction), the spring coil contracts along its entire length during the duration of spring loading, and subsequently causes the indicator to jump, thereby incrementing the indicator. In practice, the spring coil is left free to expand or contract throughout the entire loading process. First, this contraction is much less important than expansion, as in the prior art where only a portion of the coil is active at the end stage of spring loading, with respect to the dimensions of the spring and the characteristics of the material forming it. Next, the duration of spring loading up to a given force couple that causes the indicator to jump depends solely on the spring itself, particularly its stiffness. As long as the spring is maintained in its initial state, particularly in constant stiffness, the angular displacement between the two ends of the spring is maintained substantially invariant from one loading to the next, so that the loading time is maintained substantially invariant whenever the spring is loaded, and thus the moment of each jump occurs at a given moment that is maintained precisely. In a preferred variant, the angular displacement is very precisely limited by a stop attached to the first end of the spring, to which a stiffness part attached to the second end of the spring contacts. Additionally, the compression of the spring ensures a constant radius for the application of a driving force from the finger to the indicator tooth supported by the finger, thereby optimizing the driving couple provided for this driving force and consequently for the indicator to jump.Finally, due to the contraction of the spring, there is no need to provide a wall around the spring to limit the expansion of the spring coil and also to significantly increase the force couple applied to the finger to release the indicator jump. Thus, the present invention does not require a finger drum, but a finger drum is provided as one specific variant.

[0011] As described above, the mechanism according to the present invention is arranged such that whenever the spring is loaded, the spring contracts so that the indicator can be driven by jumps in a first direction of the expected movement of the indicator, and this first direction corresponds to the normal direction of the movement of the indicator when the side movement functions without external intervention (normal function). However, according to the present invention, the driving mechanism is also provided to be used to drive the indicator in the second direction opposite to the first direction of the movement of the indicator. In the second direction in which the indicator is driven by the mechanism, without special measures, the spring will expand while a force couple of the same order of magnitude as when driven in the first direction is applied to the spring. In fact, the force couple required to drive the indicator is determined in principle by the jumper spring, and since the jumper spring maintains the indicator in a stable position between consecutive jumps and generally has a similar strength curve in both directions of indicator driving, the jump driving part will be similar to the driving part in the second direction. Therefore, the problem solved by the present invention for driving in the direction occurring during normal functioning will exist in a second direction in which the indicator is driven by the mechanism without the specific measures proposed by the present invention. Additionally, the spring must be dimensioned so that it can function accurately over the full range of contraction and expansion distortion without the risk of deterioration over time. This makes manufacturing the spring more complex, allowing it to absorb such loading in both directions without fatigue and also prevent failure.To improve this problematic situation and eliminate the resulting disadvantages, the mechanism according to the present invention comprises a first stop member rotatably attached to at least a wheel plate and a second stop member rotatably attached to a rigid part whenever the indicator is driven in the second direction by a driving finger, and the mechanism is arranged such that the first stop member rotates the second stop member whenever the indicator is driven in the second direction by the driving finger, the first stop member, and the second stop member, so that the first stop member and the second stop member limit or prevent the expansion of the spring. More specifically, the mechanism is arranged such that when the driving finger is not in contact with the indicator, the initial angular distance between the first stop member and the second stop member is less than half of the normal angular movement of the second stop member relative to the first stop member when the spring is loaded and driving the indicator in the first direction (the normal functional direction of the indicator in which the indicator is jumping).

[0012] According to a main embodiment, the mechanism comprises a coupling body extending the coil on the side of the second end of the spring such that the second end of the spring is defined by one end of the coil and is at least partially introduced into a bed within a rigid portion, and the coupling body rotatably attaches the second end of the spring to the rigid portion when the spring is loaded and when at least an indicator is driven in the first direction by a driving finger.

[0013] According to a first specific embodiment, when the indicator is driven in the second direction by a driving finger, the arbor is rotatably attached to a wheel plate, and the coupling mechanism is rotatably attached to a rigid portion. Then, the first stop is integrally connected to or coupled thereto with the arbor or a central portion rotatably attached to the arbor, and the second stop is integrally connected to or coupled thereto with a spring or coupling mechanism on the side of the second end of the spring.

[0014] According to a second specific embodiment, the arbor is rotatably attached to a wheel plate, the first stop is integrally formed with or connected thereto to the arbor or a central portion rotatably attached to the arbor, and the second stop is formed by a rigid portion. According to an advantageous variation, the first stop is formed by the outer profile of a flange forming one end of the central portion forming the arbor rotatably attached to the wheel plate, and the second stop is formed by the profile of a recess within the plate forming the rigid portion, and the flange is located within the recess over at least a portion of its thickness.

[0015] According to the first general feature, the opening of the rigid portion is a rectangular hole machined in the plate forming the rigid portion. According to the second general feature, the driving finger is substantially radial and designed to engage with a tooth profile included on the indicator, and has two lateral flanks capable of driving the indicator in the first direction and the second direction, respectively. Brief explanation of the drawing

[0016] The objects, advantages, and features of the present invention will be described in more detail below with reference to the accompanying drawings, which are given as non-limiting examples. FIG. 1 is a plan view of a side-viewing mechanism designed to drive an indicator in one direction and drag in the other direction during a jump, particularly a semi-instantaneous jump, according to a first embodiment of the present invention. Figure 2 is an exploded perspective view of the observation mechanism of Figure 1. FIG. 3 is a perspective view showing the rigid part forming the driving finger and the spring in the reverse position in the side view mechanism of FIG. 1. FIG. 4 is a drawing of a part of a viewing mechanism according to a first variation of a first embodiment of the present invention similar to that of FIG. 3. FIG. 5 is a drawing of a part of a viewing mechanism according to a second variation of a first embodiment of the present invention similar to that of FIG. 3. FIGS. 6a to 6d partially illustrate a viewing movement incorporating the viewing mechanisms of FIGS. 1 to 3 in each of four consecutive states occurring during a semi-instantaneous jump drive in a first direction corresponding to the normal functional direction of the date disk by the viewing mechanism. FIGS. 7A and FIGS. 7B partially illustrate a viewing movement comprising the viewing mechanism of FIGS. 1 to 3 in each of two consecutive states that occur when the date disk is dragged in a second direction opposite to the first direction. FIGS. 8A and FIGS. 8B partially illustrate a viewing movement comprising the viewing mechanism of FIGS. 1 to FIGS. 3 in two consecutive states that occur when the date disk is incorrectly positioned when the driving finger is rotated in a first direction. FIGS. 9A and FIGS. 9B partially illustrate a viewing movement comprising the viewing mechanism of FIGS. 1 to 3 in each of two consecutive states that occur when the date disk is incorrectly positioned when the driving finger is rotated in a second direction. FIG. 10 is a plan view of a sighting mechanism according to a second embodiment of the present invention, designed to drive an indicator in one direction and drag in the other direction in jumps, particularly semi-instantaneous jumps. Fig. 11 is an exploded perspective view of the observation mechanism of Fig. 10. FIG. 12 is a perspective view showing the rigid part and spring forming the driving finger in the side view mechanism of FIG. 10 in an inverted position. FIG. 13 is a drawing of part of a viewing mechanism according to a specific variation of a second embodiment of the present invention similar to that of FIG. 12. FIGS. 14a to 14d partially illustrate a viewing movement incorporating the viewing mechanisms of FIGS. 10 to 12 in each of four consecutive states occurring during a semi-instantaneous jump drive in a first direction corresponding to the normal functional direction of the date disk by the viewing mechanism. FIGS. 15a and FIGS. 15b partially illustrate a viewing movement comprising the viewing mechanism of FIGS. 10 to FIGS. 12 in each of two consecutive states that occur when the date disk is dragged in a second direction opposite to the first direction. FIGS. 16a and FIGS. 16b partially illustrate a viewing movement comprising the viewing mechanism of FIGS. 10 to FIGS. 12 in each of two consecutive states that occur when the date disk is incorrectly positioned when the driving finger is rotated in a first direction. FIGS. 17a and FIGS. 17b partially illustrate a viewing movement comprising the viewing mechanism of FIGS. 10 to FIGS. 12 in each of two consecutive states that occur when the date disk is incorrectly positioned when the driving finger is rotated in a second direction. Specific details for implementing the invention

[0017] With reference to FIGS. 1 to 9b, a general embodiment of the present invention, followed by a first embodiment of a mechanism for driving an indicator according to the present invention and its function in both directions for driving the indicator, will be described below. It should be noted that the features of the present embodiment exist by definition in the first and second embodiments as described below.

[0018] According to a general embodiment of the present invention described below with reference to various elements and parts of the first embodiment, which will be described more specifically thereafter, a viewing movement (2) is equipped with an indicator (4) and includes a mechanism (6) for driving the indicator in a first direction (30) of the expected movement for the indicator and a second direction opposite to the first direction, wherein the driving unit jumps in a first direction corresponding to the direction of movement of the indicator when the viewing movement (2) is functioning normally. It should be noted that the indicator may move in various ways, particularly linearly or rotaryly. This mechanism comprises a wheel plate (8) defining a rotation axis (22), a rigid portion (10) forming a driving finger (12) arranged on the wheel plate and configured to drive an indicator, and a spring (16), the spring comprising a coil (18) and having a first end (17) and a second end (19), and when the spring is loaded before a jump of the indicator (4) in at least a first direction (30) and then the indicator (4) is driven by the driving finger (12) to form this jump, the first end is rotatably attached to the wheel plate (8) and the second end is rotatably attached to the rigid portion (10). The rigid portion (10) is rotatable with respect to the wheel plate (8) and is rotatably guided around the rotation axis (22) by an arbor (36) that is aligned with the rotation axis and extends through the opening (26) of the rigid portion, which allows the drive finger (12) to retract toward the rotation axis (22) under the action of a radial component of a force that can be applied to the drive finger. The mechanism (6) is configured to drive the indicator with the drive finger (12) in the first direction (30) and the second direction of the indicator's movement when the wheel plate rotates in the first rotation direction (50) and the second rotation direction, respectively. Subsequently, the mechanism (6) is arranged to retract whenever the spring (16) is loaded, so that the indicator then jumps in the first direction.Furthermore, the mechanism includes a first stop (74) rotatably attached to the wheel plate and a second stop (76) rotatably attached to the rigid part whenever the indicator (4) is driven in the second direction by the driving finger (12). The mechanism (6) is arranged so that the first stop (74) rotates the second stop (76) whenever the indicator is driven in the second direction, and thus the first stop and the second stop limit or prevent the expansion of the spring (16), and when the driving finger is not in contact with the indicator, the initial angular distance (θ) between the first stop (74) and the second stop (76) is less than half of the normal angular movement (α) of the second stop relative to the first stop when the spring contracts as the spring is loaded to subsequently drive the indicator in the first direction (30) of its movement.

[0019] According to the first advantageous variant, when the driving finger (12) is not in contact with the indicator (4), the spring (16) is in a substantially equilibrium position (no pre-tension by design; only residual stress due to friction between the spring and its support can potentially generate low initial tension). In particular, the initial angular distance (θ) between the first stop and the second stop is intended to be non-zero, as in the variants illustrated in the drawings for the specific embodiments.

[0020] According to a first major variant, the driving finger (12) has two flanks (14, 15) configured to engage with a tooth (5) on the indicator (4) so ​​that the indicator (4) can be driven in a first direction (30) and a second direction, respectively. According to a second general variant, the opening is a rectangular hole (26) machined into a plate (38) forming a rigid portion (10). As non-limiting examples, the indicator is a jump-type minute, hour, date, day, or month indicator.

[0021] In a first embodiment of a side-view movement comprising a mechanism (6) for driving an indicator according to the present invention, the rigid portion (10) is formed by a plate (38) that extends over a spring and has a rectangular hole (26) machined therein, and an axial wall (40) that is arranged at the edge of the plate and slopes away toward a wheel plate (8) that can be placed in a main variant. A portion of the axial wall (40) and a portion of the plate (38) superimposed thereon together form a driving finger (12) having a height (H) that extends from at least the lower side of the spring (16) to the upper surface (39) of the plate. The rigid portion (10) forms a finger drum in which the spring defines an internal space (11) between the wheel plate (8) and the plate (38) on the rigid portion.

[0022] Near the drive finger (12), the axial wall (40) has a bed (42) having a lateral opening on the side of the internal space (11). The second end (19) of the spring (16) is extended by a coupling mechanism (20) for coupling to the rigid portion (10), and the coupling mechanism (20) is configured to penetrate at least partially into the bed (42), thereby enabling the spring to apply a driving force coupled to the rigid portion (10) in a first rotational direction so that the drive finger (12) can drive the data disk (4) in a first direction (normal direction). Accordingly, the mechanism (6) includes a coupling body (20) that extends the spring (16) on the side of the second end (19) and is introduced at least partially into the bed (42) within the rigid part (10) to couple the spring to the rigid part, and the coupling body rotatably attaches the second end of the spring to the rigid part when the spring is loaded and when at least the indicator (4) is driven by the driving finger to jump in the first rotational direction. Advantageously, the coupling body (20) is rigid.

[0023] In a general variation, when the indicator (4) is driven in the second direction by the driving finger (12), the arbor (36) is rotatably attached to the wheel plate (8), and the coupling mechanism (20) is rotatably attached to the rigid part (10). Then, the first stop is manufactured integrally with or connected to the arbor or the central part rotatably attached to the arbor, and the second stop is manufactured integrally with or connected to the spring (16) on the side of the second end (19), or manufactured integrally with or connected to the coupling mechanism. In the main variant shown in the drawings, the first stop (74) is manufactured integrally with the center portion (24) which is rotatably attached to the wheel plate (8) via the arbor (36), and the second stop (76) is manufactured integrally with the coupling mechanism (20) which is rigid and rotatably attached to the rigid portion (10) when the indicator (4) is rotated in the second direction by the driving finger. Also in the advantageous variant shown in the drawings, the center portion (24) and the coupling mechanism (20) are manufactured integrally with the spring (16) and together form a single portion. Then, the spring (16) is formed by a single coil (18) extending in a plane orthogonal to the axis of rotation (22), and the two ends of the single coil thus form the first end (18) and the second end (19) of the spring. It should be noted that the coil is referred to as a “coil” in this description and claims because of its general shape, which does not form a full turn in the illustrated advantageous example, but may have a circular shape at rest or an expansion that does not exhibit a gradual radial increase with angle in certain cases.

[0024] The mechanism (6) includes a central part (34) that is connected through a rectangular hole (26) within the rigid part (10) and includes an arbor (36) that rotates and translates this rigid part relative to the wheel plate. In a specific variant, the wheel plate (8) and the central part (24) are driven on the arbor (36), and the central part (34) also includes an annular flange (35) that forms an axial stop for the rigid part (10) on the opposite side of the wheel plate (8). The driving finger (12) has two flanks (14, 15) that are substantially radial, and the flank (14) is designed to drive the indicator (4) through the tooth (5) in the first direction of rotational movement that the indicator may undergo (normal direction allowing continuous and progressive display of month date), while the flank (15) is designed to drive the indicator (4) through the tooth (5) in the second direction of rotational movement.

[0025] In the first variant illustrated in FIG. 3, the coupling body (20) on the mechanism (6) is configured to penetrate at least partially into the bed (42) through a lateral opening, which means that the coupling body can be introduced at least partially into the bed (42) from the internal space (11). Furthermore, the bed (42) has a lateral surface (46) oriented obliquely in the rotational direction (50) (first rotational direction) of a wheel plate (8) designed to drive the indicator (4) in the first direction with respect to the radial direction, in a configuration in which the spring contracts when the spring is loaded and extends through the center of the lateral surface, advantageously, and the coupling body (20) has a lateral flank (48) facing the lateral surface and also inclined obliquely in the same direction as the lateral surface and supporting at least partially against the lateral surface whenever the spring (16) contracts when the spring is loaded to drive the jumping indicator in the first direction by the mechanism (6). These specific features make it possible to ensure that the coupling mechanism is maintained in a given driving position inside the bed as soon as the spring is compressed as the spring is loaded before the date disk (4) jumps to the next date at midnight. Thus, the contact point or contact zone of the bed (42) where the force of the spring is applied through the coupling mechanism (20) does not change significantly as the spring is compressed as the spring is loaded. Only slight fluctuations may occur during the initial stage of spring loading. Furthermore, these features limit the possibility of the coupling mechanism (20) rotating on its own, in order to allow or facilitate the lateral introduction of the coupling mechanism (20) into the bed (42), particularly by rotating the rigid part (10) with respect to the spring (16), even if a relatively large angular gap is provided for the coupling mechanism within the bed (42).

[0026] Advantageously, the coupling mechanism and the bed are configured such that when the spring is loaded, the coupling mechanism (20) undergoes a specific rotation of itself at least in an initial stage, and then drives the indicator (4) by jumps in the first direction. It will be known that the coupling mechanism rotates itself in a direction corresponding to the first rotational direction of the wheel plate (8), which means the rotational direction of the wheel plate when the spring is compressed as the spring is loaded. However, when the spring is compressed as the spring (16) is loaded, it is essential that the coupling mechanism (20) remain within the bed (42). Preferably, only a slight rotation occurs in the initial stage when the spring is compressed as the spring is loaded. In addition to the specific features described above, the coupling mechanism (20) and the bed (42) are configured to lock the coupling mechanism against rotation of itself in a direction corresponding to the rotational direction (50) of the wheel plate (the expected rotational direction for normal indicator driving) once it is positioned within the bed and after a slight expected rotation. To this end, the coupling mechanism (20) has an outer portion spaced apart at an angle from the lateral flank (48), which includes a heel (52) that is relatively close to the rear of the bed (42) and / or radially supported against the wall (41) that contacts the bed (42) on the opposite side of the lateral surface (46) when the spring (16) begins to contract as it is loaded.

[0027] In an advantageous variant of the present invention, the angular movement of the first end (17) of the spring and, accordingly, the second end (19) of the spring (16) and, accordingly, the driving finger (12) with respect to the wheel plate (8) is limited by a third stop (28) rotatably attached to the wheel plate when the spring is compressed. Then, the indicator (4) and the mechanism (6) are arranged such that, when functioning normally, the indicator jumps after the angular movement is stopped by the third stop, thereby defining the end of the compression of the spring while being loaded before this jump, and thus corresponding to a limited angular displacement (α), which means that it does not change over time by continuous loading so that the indicator can be advanced in the first direction in continuous jumps. In this advantageous variant, when the spring is compressed as the spring is loaded, the normal angular displacement between the first end and the second end of the spring corresponds to the defined angular displacement (α).

[0028] In the illustrated variant, the coupling mechanism (20) has a contact surface (54) that is supported by a third stop (28) that extends from the heel (52) in the direction of the axis of rotation (22) and stops the rotation of the coupling mechanism around the axis of rotation after the spring has completed contraction as the spring is loaded, so that the indicator jumps in the first direction. Preferably, the third stop (28) is located between the first end (17) of the spring and the rigid disk (24) at the angled extension of the coil (18) of the spring, and is defined by one identical part forming the rigid disk and the spring. In other words, the stop (28) is formed by the rigid part in the middle between the rigid disk (24) and the coil (18) of the spring (16). It should be noted that it is advantageous for the third stop (28) to be formed integrally with the coupling mechanism (20) and the spring (16) defining the contact surface (54).

[0029] Once the coupling mechanism (20) is assembled to the finger drum (10) without external stress and, in particular, without impact, this coupling mechanism is always kept coupled to the finger drum regardless of the state of the mechanism (6), which means when the spring is in an angular equilibrium position during the period when there is no interaction between the tooth profile (5) on the indicator (4) and the driving finger (12), when the spring is compressed as the spring is loaded before the indicator jumps, then when the indicator jumps, and also when the spring is slightly expanded, in particular to correct the data displayed by the indicator, in particular when the wheel plate (8) is rotated in a second rotational direction opposite to the first rotational direction provided to drive the indicator (4) normally. In conclusion, when the side-view movement is functioning normally, the coupling mechanism (20) is kept coupled to the finger drum, which means in its proper position within the bed (42), thereby being attached to the finger drum.

[0030] Surprisingly, in a preferred variant corresponding to the illustrated variant, the mechanism (6) is arranged such that when the coupling body (20) exits the bed (42) during an impact, the coupling body cannot move over the bed in the first rotational direction (50) of the wheel plate (8), regardless of the state the mechanism was in prior to such impact. In the case of an impact on the coupling body that potentially generates a force capable of causing the coupling body to exit its bed, this is highly unlikely, and the spring is in a state where the coupling body can be returned to the bed, that is, upstream of the bed in the driving direction (50). The rigid part and coupling mechanism are arranged such that when the coupling mechanism (20) is upstream of the bed (42) with respect to the driving direction of the wheel plate, the driving finger (12) stops against the toothed part (5a) on the indicator (4), and then the driving of the spring (16) by the wheel plate (8) returns the coupling mechanism to the bed to form the next scheduled jump, and before the next jump of the indicator occurs, the indicator does not skip any jump, and thus the indicator continues to display accurate information.

[0031] In a favorable variation, the side of the bed (42) with the opening has a minimum dimension slightly smaller than the maximum dimension of the coupling body, which is radially perpendicular to the axis of rotation (22) of the spring in an angularly balanced state (coordinates with the central axis of the rigid disk (24)). More generally, the coupling body and the bed are arranged so that the coupling body cannot exit the bed by at least one translation relative to the rigid part, which means that it does not undergo rotation itself (rotation around its geometric center or center of mass along an axis parallel to the axis of rotation (22)). Thus, to fit into the bed through the lateral opening, the coupling body must rotate slightly itself, which is provided first by the profile of the axial wall (40) of the rigid part (10) and second by the profile of the coupling body. These specific features ensure that once the coupling mechanism is properly inserted into the bed (42) and thus in place, there is very little risk of the coupling mechanism coming out of the bed in the event of a specific impact, although this is not impossible in exceptional cases.

[0032] A first embodiment of the observation movement, more specifically the function of the mechanism (6) for driving the date disc (4), and other specific features of the first embodiment will be described in more detail below with reference to FIGS. 6a through 9b. It should be noted that in FIGS. 6a through 9b, the plate (38) on the finger drum (10) is not shown in order to better illustrate the elements within the internal space (11) of the finger drum.

[0033] FIGS. 6a through 6d illustrate four consecutive states of a mechanism (6) for driving a date disk (4) during a jump, particularly a semi-instantaneous jump, in the first direction (30) of the expected rotational movement. FIGS. 6a through 6d respectively illustrate the mechanism (6) and the date disk (4) when the disk is driven to switch to the next date at midnight:

[0034] - When the driving finger (12) comes into contact with the tooth portion (5a) on the date disk (4) and the spring (16) is substantially in angle equilibrium (meaning not angle-tensioned);

[0035] - When the spring (16) is loaded and the contact surface (54) of the coupling body (20) is supported against the third stop (28) after undergoing an angular displacement (α) with respect to the wheel plate (8), this angular displacement is defined by the angular position of the coupling body and the third stop when the spring is in an equilibrium position;

[0036] - When mechanical energy stored in the compressed spring is applied to the finger drum (10), the date disc jumps;

[0037] - When the jump ends, if the date disk reaches the next stable position, which is accurately moved by the jumper spring for positioning the date disk.

[0038] It should be noted that, in order to prevent the tooth portion (5a) on the indicator (4) from moving up or down the driving finger (12) when the indicator is driven, the height between the wheel plate (8) containing the gap and the bottom surface of the teeth (5) is provided to be positioned at a constant height between the lower height and the upper height of the driving finger relative to the wheel plate containing the gap. To this end, in a favorable variation, the distance between the wheel plate (8) and the bottom surface of the driving finger (12) is smaller than the thickness of the tooth portion on the tooth (5). Preferably, in a watch including a side-watch movement (2), the distance between the upper surface of the driving finger and the component or dial covering the indicator is also designed to be smaller than the thickness of the tooth portion on the tooth (5). Advantageously, a significant height of the finger (12) that can rise above the plate (38) forming the upper surface of the mechanism (6) from at least the bottom of the spring (16) facilitates avoiding passing the tooth portion (5a) below or above the driving finger (12).

[0039] The mechanism (6) is arranged so that the spring (16) retracts when loaded, so as to create a jump of the date disk (4) in the first direction (30) of the rotatable movement, particularly a semi-instantaneous jump. Additionally, any angular movement of the driving finger (12) and the second end (19) of the spring, and accordingly the first end (17) of the spring, is limited by a third stop (28) rotatably attached to the wheel plate (8) when the coil (18) retracts after the spring is loaded. Preferably, the indicator and mechanism are arranged so that, when functioning normally, the indicator (4) jumps after the angular movement is stopped by the third stop (28) when the spring is fully loaded before this jump, and then corresponds to an invariant angular displacement (α). In a less advantageous alternative variant, it should be noted that when functioning normally, the indicator jumps before the angle movement is stopped by the third stop (28). In this case, the third stop serves to protect the spring upon impact. It should be noted that the energy stored in the spring (16) will be slightly greater than in the variant where the jump is released by the third stop, because it is necessary to overcome the hold of the jumper spring and propel the indicator solely by the couple of the springs.

[0040] FIGS. 7A and 7B illustrate two consecutive states of the mechanism (6) that occur when the date disk (4) is driven in the second direction of the expected rotatable movement. FIG. 7A illustrates the mechanism (6) at the moment when the driving finger (12) contacts the tooth (5a) on the date disk (4), while the wheel plate (8) is rotating in the second rotational direction, the coupling mechanism (20) is supported against the rear lateral surface (43) of the bed (42), and the spring (16) is still in angular equilibrium. In this state, the spring is not angularly tensioned, and the first stop (74) and the second stop (76) have an angular lag equal to the initial angular distance (θ). This initial angular distance is relatively small to achieve one objective of the present invention, which is to significantly limit the expansion of the spring (16) in the mechanism according to the present invention, and the mechanism is arranged so that the indicator can be rotated in both directions by the driving finger and to enable jump driving in the first direction. In the preferred variant shown in the drawing, the initial angular distance (θ) between the first stop (74) and the second stop (76) is smaller than one-quarter of the defined angular displacement (α) between these two stops when loading before the indicator jump in the first direction, particularly fixed and determined by the third stop (28) in the advantageous variant shown in the drawing and described above.

[0041] FIG. 7b illustrates a drive that essentially drags the indicator (4) in the second direction while the first stop (74) rotates the second stop (76) to rotate the rigid part (10), particularly the drive finger (12). It should be noted that during this dragging drive, after a short initial phase ends when the first stop comes into contact with the second stop (76), the spring (16) is no longer deflected to drive the indicator. As soon as the first stop (74) comes into contact with the second stop (76) attached to the coupling mechanism (20), the slight expansion of the spring (16) ends and the drive finger (12) begins to drive the indicator in the second direction.

[0042] According to an advantageous variation of the first embodiment illustrated in the drawing, the second stop (76) is manufactured integrally with or connected to the coupling mechanism (20), the coupling mechanism is rigid, and has a center of mass (21) that is radially further from the axis of rotation (22) than the first stop (74). When the indicator (4) is driven in the second direction by the driving finger, the first stop is pressed tangentially against the second stop, and the coupling mechanism is pressed tangentially against the rear wall (43) of the bed (42), which is radially further from the axis of rotation (22) than the first stop (74). This generates a first force coupling on the coupling mechanism (20), which causes the coupling mechanism to rotate on itself in a direction corresponding to the first rotational direction (50) of the wheel plate (8), and consequently causes it to rotate on the end portion of the coil (18) at the second end (19) of the spring (16). The first force couple is significantly high and can cause premature fatigue of the end portion or even deterioration of the spring.

[0043] Advantageously, the driving mechanism according to the present invention tends to relieve the lever arm of the force that can cause the coupling body to twist against the end portion (19) of the spring (16) by positioning the force acting on the coupling body as close as possible to this end portion, thereby relieving the lever arm of this force coupling. This is made possible, in particular, by separating the driving finger and the spring (16), and the spring acts to store mechanical energy so that the indicator jumps at a given moment.

[0044] In a general variation, to prevent the first force couple from being the only force couple applied to the coupling body (20) when the indicator (4) is driven in the second direction, the coupling body and the rigid part (10), particularly the bed (42), are configured to limit the braking system that provides a second force couple on the coupling body that itself opposes any rotation of the coupling body in a direction corresponding to the first rotational direction of the wheel plate (8) when the indicator is driven in the second direction by the driving finger (12), thereby limiting tension at the end portion (19) of the spring.

[0045] In a favorable variant, the coupling body and the rigid part, particularly the bed, are configured such that the brake system itself limits the rotation of the coupling body. In a preferred variant, the coupling body and the rigid part are arranged such that, at least substantially, as soon as the first stop rotates the second stop in the second rotational direction, the brake system itself locks the coupling body against rotation. In particular, as illustrated in the drawing, the brake system is formed at least partially by a heel (52) on the side of the coupling body facing the second end (19) of the spring (16) and beyond the center of mass (21) of the coupling body, the heel is outside the bed (42), and is supported against the axial surface (41) of the rigid part in contact with the bed (42) on the side facing the side facing the end portion of the spring (16) when the indicator is driven in the second direction by the driving finger.

[0046] FIGS. 8a through 9b illustrate two situations that may occur for the mechanism (6) when the date disk is not in one of its expected separation and stable positions, particularly as a result of impact or strong acceleration experienced by the date disk (4). FIGS. 8a and 8b illustrate two consecutive states of the mechanism (6) when the wheel plate (8) rotates in a first rotational direction (50) and the driving finger (12) is stopped with respect to the tangential lateral surface of the tooth portion (5a) of the tooth profile (5). The rigid portion (10) is movable in a rotational direction relative to the wheel plate (8) and is guided in a rotational direction around the axis of rotation (22) by an arbor (36) formed by a central portion (34) extending through the opening of the rigid portion, and the rigid portion (10) is also translationally movable due to the fact that the opening is a rectangular hole (26), and the rectangular hole is configured and particularly oriented so that the driving finger (12) can be retracted toward the axis of rotation (22) under the action of a radial force applied, for example, by a tooth portion (5a) on the outer lateral surface of the finger which is circular relative to the axis of rotation (22) in the absence of such radial force. This retraction is useful for enabling the driving finger (12) to retract momentarily when the finger stops on the tangential lateral surface of the tooth portion (5a) on the tooth portion of the indicator (4) until the driving finger moves past the tooth portion (5a) in the first rotational direction (50). FIGS. 9a and 9b illustrate two consecutive states of the mechanism (6) similar to those of FIGS. 8a and 8b, but in which the wheel plate (8) rotates in the second rotational direction opposite to the first direction and the driving finger (12) stops on the tangential lateral surface of the tooth portion (5a).

[0047] FIG. 4 illustrates a first variation of the first embodiment. The mechanism (6A) is essentially different from the mechanism (6) described above in the configuration of the bed (42A) and the configuration of the coupling mechanism (20A) rotated on this bed on the rigid portion (10A). References already described are not described again here. The bed (42A) has a substantially square shape, and the coupling mechanism (20A) has an outer portion that is inserted into the bed (42A) and is also substantially square in shape. The coupling mechanism (20A) is substantially arranged within the bed without an angular gap, and has a profile defining at least one zone for locking the coupling mechanism against rotation in a direction corresponding to the first rotational direction (50) of the wheel plate (8). In the illustrated example, the bed defines two zones (70, 72) for locking the member (20A) against rotation itself in a direction corresponding to the first rotational direction, and these two locking zones are substantially aligned diagonally with respect to the square outer portion of the coupling mechanism located in the bed. Thus, as soon as the first stop (74) rotates the second stop (76) in the second rotational direction, the two locking zones (70, 72) form a braking system that locks the coupling mechanism (20A) against rotation itself. It is understood that the bed (42A) and the coupling mechanism (20A) are less complex and therefore less advantageous than the bed (42) and the coupling mechanism (20). Even if this is not directly evident, it is easier to laterally fit the engine (20) into the bed (42) than to fit the engine (20A) into the bed (42A) when the spring is rotated relative to the rigid part (10A). The engine (20A) can then exit the bed (42A) if the mechanism (6A) undergoes strong radial acceleration through the bed (42A), especially in the case of an impact.Afterward, in the case of retraction loading, the mechanism (20A) may undergo some radial displacement toward the axis of rotation (22), but this is limited by the force coupling applied to this coupling mechanism with respect to the center of mass when the spring (16) retracts as it is loaded when the wheel plate rotates in the first rotational direction (50), and also when the indicator (4) is dragged in the second direction when the wheel plate (8) rotates in the second rotational direction.

[0048] FIG. 5 illustrates a second variation of the first embodiment. The mechanism (6B) differs essentially from the aforementioned mechanism (6) in that the rigid portion (60) no longer forms a finger drum. This rigid portion (60) is formed by a plate (62) having an elongated shape along the longitudinal axis of the rectangular hole (26) and an axial wall (64) rising from one end of the plate and machined into the bed (42B). The coupling mechanism (20B) does not have a heel on the opposite side of the second end (19) of the spring (16), but is arranged within the bed (42B) substantially without an angular gap. The lateral surface (46) of the bed (42B) and the axial surface (71) at the rear of the bed lock the mechanism (20B) against rotation. Accordingly, at least substantially, as soon as the first stop (74) rotates the second stop (76) in the second rotational direction, the lateral surface (46) and the axial surface (71) form a brake system that locks the coupling mechanism (20B) against rotation itself in a direction corresponding to the first rotational direction (50) of the wheel plate (8). The mechanism (20B) may potentially undergo rotation itself in a direction corresponding to the second rotational direction of the wheel plate (8), but this does not pose any specific functional problem, as the risk of it coming out of the bed in the event of an impact is relatively low and this can facilitate the lateral insertion of the coupling mechanism into the bed (42B).

[0049] Now, with reference to FIGS. 10 to 17b, a second embodiment of a viewing movement (3) according to the present invention will be described, and such a viewing movement includes a mechanism (7) for driving an indicator (4). References already described will not be described in detail again, and only the differences from the first embodiment will be emphasized. The second embodiment is essentially different from the first embodiment in the arrangement of the first stop (84) and the second stop (86) provided to drive the indicator in the second direction of the movement, that is, in a direction opposite to the first direction corresponding to the normal functional direction of the mechanism (7) in particular for displaying the date.

[0050] In a second embodiment, the arbor (36) is rotatably attached to the wheel plate (8). Then, generally, the first stop is integrally with or connected to the arbor, or integrally with / connected to a central portion rotatably attached to the arbor, and the second stop is formed by a rigid portion including a drive finger (12) as described above. In the illustrated advantageous variant, the first stop (84) is defined by the outer profile of a flange (35C) arranged at one end of the central portion (34C) forming the arbor (36), and the second stop (86) is defined by the profile / contour of a recess (82) within the plate (38C) forming the rigid portion (80). More specifically, the first stop (84) is formed by a portion of the flange having an outer axial surface that partially defines the lateral surface of the flange (35C) that is substantially radially oriented. The flange (35C) is located within the recess (82) over at least a portion of its thickness. The rectangular hole (26) is located within the recess (82). Thus, the central portion (24C) to which the first end (17) of the spring (16) is attached has an external profile having a single stop (28) (third stop). Similarly, because the second stop (86) is formed by the rigid portion (80), the coupling mechanism (20C) has a profile different from the profile of the coupling mechanism (20) described above.

[0051] The coupling mechanism (20C) includes a stop portion (52) at the rear, which is useful for maintaining the coupling mechanism on the bed (42C) in the event of an impact, and also useful for restricting any rotation of the mechanism (20C) in the direction corresponding to the first direction when the spring (16) is loaded and the spring contracts before the indicator (4) jumps to the first direction (30).

[0052] FIG. 13 illustrates a variation of the second embodiment. This variation is not about the arrangement of the first and second stop parts (84, 86) which remain the same, but at least the arrangement of the coupling mechanism (20D) and the bed (42D) into which the coupling mechanism is inserted when the indicator jumps and is driven in the first direction (30) of the movement. The mechanism (7A) is essentially different from the variation shown in FIG. 12 in that the coupling mechanism (20D) has a different shape and the profile of the bed (42D) designed to accommodate it is also different. The bed (42D) arranged on the axial wall (40D) of the finger drum (80A) is generally triangular in shape and opens progressively toward the internal space (11) of the finger drum where the spring (16) is arranged. The shape of the part of the coupling mechanism (20D) inserted into the bed (42D) through the lateral opening substantially corresponds to the shape of this bed. This configuration allows the coupling mechanism to be easily inserted into the bed, and although the bed is designed to be relatively deep, no other means are provided to prevent this, and it will a priori allow the mechanism to potentially escape in the event of an impact. In particular, in the event of an impact, the means provided in this case to keep the coupling mechanism as secure as possible within the bed are the shape of the inner part of the coupling mechanism (20D) and the shape of the central part (24C), as well as the relative arrangement of this inner part and this central part. In most potential situations, the inner part of the coupling mechanism will stop relative to the central part (24C) before the coupling mechanism (20D) completely escapes the bed (42D). Additionally, the coupling mechanism is substantially aligned with the longitudinal axis of the rectangular hole (26), so that when the coupling mechanism undergoes substantially radial acceleration in the direction of the axis of rotation (22), particularly along the longitudinal axis of the bed (42D), the larger finger drum (80A) undergoes the same radial movement in the same direction, which tends to keep the coupling mechanism within the bed.

[0053] Preferably, once inserted into the bed (42D), the coupling mechanism (20D) is maintained in place within the bed by applying a radial force from the spring against the axial wall (40D) of the finger drum (80A). It should be noted that this radial force increases as the driving finger is retracted toward the axis of rotation (22) through the radial displacement of the finger drum. The bed (42D) has a lateral surface (46D) oriented obliquely in the rotational direction (50) of the wheel plate (8), which is advantageously designed to drive the indicator (4) by jumping in the first direction (30) (normal function direction) with respect to the radial direction in a spring-loaded configuration, and the coupling mechanism (20D) has a lateral flank (48D) facing the lateral surface, which is also a lateral surface, which is obliquely inclined in the same direction with respect to the rotational axis (22), and is at least partially supported on this lateral surface when the spring is compressed as the spring is loaded, and then when the indicator (4) is driven by jumping in the first direction (30) by the mechanism (7A). Furthermore, the lateral surface and the lateral flank are advantageously very long. These specific features ensure that the coupling mechanism is properly maintained within the bed as soon as the spring (16) is compressed to drive the indicator by jumping in the first direction. In particular, the contact point or contact zone of the bed where the force of the spring is applied through the coupling mechanism does not change while the spring is compressed as the spring is loaded.

[0054] Furthermore, as the spring is loaded and the spring contracts, the coupling mechanism (20D) itself cannot rotate, particularly in a direction corresponding to the first rotational direction of the wheel plate. Finally, when the transmission of the force coupling to the rigid part (80A) by the wheel plate (8) occurs through the first stop (84) which directly rotates the second stop (86) in the second rotational direction while the plate rotates in a second rotational direction opposite to the first rotational direction, the spring (16) does not expand slightly or only expands slightly as described above. Therefore, the configuration of the bed (42D) and the coupling mechanism (20D) is not problematic, as driving the indicator (4) in the second direction does not cause the spring (16) or the coupling mechanism to be deflected. If the initial angular distance (θ) is not zero, this initial angular distance is selected so that the force coupling applied to the spring when the indicator (4) is driven in the second direction by the driving finger (12) is kept relatively small so that the coupling mechanism (20D) does not move backward out of the bed (42D), but at most moves slightly and is maintained over most of the bed. In either case, generally speaking, if the coupling mechanism (20D) receives a backward movement to exit the bed, the coupling mechanism will easily re-enter the bed (42D), and then the indicator (4) will be rotated in the first direction without skipping a jump in the first direction.

[0055] FIGS. 14a through 14d illustrate four consecutive states of a mechanism (7) for driving the date disk (4) during a jump, particularly a semi-instantaneous jump, in the first direction (30) of the expected rotational movement, as in FIGS. 6a through 6d. These figures will not be described in further detail here as they are clear from what is mentioned above. It should be noted that in FIG. 14a, the driving finger (12) is only in contact with the tooth portion (5a) on the tooth profile (5), and the spring (16) is not yet tensioned (i.e., in a stationary state). In this state, the first stationary portion (84) and the second stationary portion (86) have a non-zero initial angular distance (θ) between them. FIG. 14b illustrates a state in which the spring (16) is fully loaded, and the contact surface (54) of the coupling mechanism (20C) is stopped relative to the third stop (28) defined by the central portion (24C). FIG. 14b illustrates the normal angular movement (α) of the second stop relative to the first stop as the spring retracts as the spring is loaded to drive the indicator in the first direction. The recess (82) is machined so that the angle (α) of the flange (35C) can be rotated from the angular resting position of the spring (16) shown in FIG. 14a.

[0056] FIGS. 15a and FIGS. 15b respectively illustrate two states of the mechanism (7) when the date is corrected, particularly in the case of the date indicator (4), during the drive of the indicator in the second direction by the drive finger (12). The mechanism (7) is arranged so that whenever the indicator is driven in the second direction by the mechanism, the first stop (84) rotates the second stop (86), and thus the first stop (84) and the second stop (86) limit or prevent the expansion of the spring (16), and when the drive finger (12) does not contact the indicator (4), the initial angular distance (θ) between the first stop and the second stop is less than half of the normal angular displacement (α) of the second stop relative to the first stop when the spring is compressed as the spring is loaded to drive the indicator by jumping in the first direction.

[0057] In a first variant not illustrated, the first stop is defined by the outer profile of a flange attached to a central portion forming an arbor (36), as in the illustrated variant, and the second stop is formed by a protrusion rising from a plate forming a rigid portion. In a second variant not illustrated, the first stop and the second stop are arranged in the internal space (11) of the rigid portion, the first stop is fastened to or formed by the rigid portion, and the second stop is fastened to or formed integrally with the wheel plate and protrudes therefrom. In particular, the first stop is defined by the internal profile of the axial wall of the rigid portion (this axial wall has an internal profile modified with respect to the axial wall (40), having a substantially radial surface defining the first stop), and the second stop is formed by a protrusion rising from the wheel plate (8) into the internal space (11), for example, a pin.

[0058] FIGS. 16a and 16b illustrate two states of a mechanism (7) similar to that of FIGS. 8a and 8b in the case of an indexing problem of a date disk (4) (meaning the disk is not in a separate stable position defined by the tooth (5) and the positioning jumper spring) when the driving finger (12) reaches the tangential lateral surfaces of the tooth portions on the tooth, each tooth portion (5a) having two radial lateral surfaces connected by tangential lateral surfaces. Similarly, FIGS. 17a and 17b illustrate a mechanism (7) in two states similar to that of FIGS. 9a and 9b.

Claims

Claim 1 A horology movement (2; 3) equipped with an indicator (4), comprising a mechanism (6, 6A, 6B; 7, 7A) for driving the indicator in a first direction (30) of the movement provided for the indicator, wherein the driving part jumps in the first direction corresponding to the direction of the movement of the indicator when the horology movement is functioning normally, and the mechanism comprises a wheel plate (8) defining a rotation axis (22), a rigid part (10, 10A, 60; 80, 80A) forming a driving finger (12) arranged on the wheel plate and configured to drive the indicator, and a spring (16), wherein the spring comprises a first end (17) rotatably attached to the wheel plate (8) at least when the spring is loaded before the jump of the indicator in the first direction and thereafter when the indicator is driven by the driving finger to execute the jump and includes a coil (18) having a second end (19) rotatably attached to the rigid portion, wherein the rigid portion is rotatably movable relative to the wheel plate and is rotatably guided around the axis of rotation by an arbor (36) aligned with the axis of rotation and connected through an opening (26) of the rigid portion, which allows the driving finger (12) to retract toward the axis of rotation under the action of a radial component of a force that can be applied to the driving finger; the mechanism is arranged so as to drive the indicator by the driving finger in the first direction (30) of the movement of the indicator and in the second direction opposite to the first direction when the wheel plate (8) rotates in the first direction of rotation (50) and the second direction of rotation opposite to the first direction, respectively; the mechanism is arranged so as to contract whenever the spring (16) is loaded so that the indicator then jumps in the first direction;The above mechanism comprises a first stop (74; 84) rotatably attached to the wheel plate (8) and a second stop (76; 86) rotatably attached to the rigid part whenever the indicator (4) is driven in the second direction by the driving finger, and the mechanism is arranged such that the first stop rotates the second stop whenever the indicator is driven in the second direction by the driving finger (12), so that the first stop and the second stop limit or prevent expansion of the spring (16), and the mechanism has an initial angular distance (θ) when the driving finger is not in contact with the indicator, wherein the initial angular distance is less than half of the normal angular displacement (α) of the second stop relative to the first stop when the spring is compressed as it is loaded to drive the indicator in the first direction (30). Claim 2 A directional movement according to claim 1, characterized in that the initial angular distance (θ) between the first stop part (74; 84) and the second stop part (76; 86) is less than 1 / 4 of the normal angular displacement (α). Claim 3 A side-view movement according to claim 1, characterized in that when the driving finger (12) does not contact the indicator (4), the spring (16) is in a substantially balanced position. Claim 4 A side-viewing movement according to any one of claims 1 to 3, wherein the driving finger has two flanks configured to engage with a toothing (5) on the indicator so as to enable the indicator to be driven in the first direction (30) and the second direction, respectively. Claim 5 A directional movement according to any one of claims 1 to 3, wherein the angular movement of the first end (17) of the spring and, accordingly, the second end (19) of the spring (16) and, accordingly, the driving finger (12) with respect to the wheel plate (8) is limited by a third stop (28) rotatably attached to the wheel plate when the spring is contracted; and the indicator and the mechanism (6, 6A, 6B; 7, 7A) are arranged such that, when functioning normally, the indicator jumps after the angular movement is stopped by the third stop, thereby defining the end of spring loading before this jump, and then corresponds to a limited angular displacement (α) corresponding to the normal angular displacement. Claim 6 A side-view movement according to any one of claims 1 to 3, wherein the mechanism (6, 6A, 6B; 7, 7A) comprises a coupling body (20, 20A, 20B, 20C, 20D) that extends the spring (16) on the side of the second end (19) and is at least partially inserted into a bed (42, 42A, 42B, 42, 42D) within the rigid portion (10, 10A, 60; 80, 80A) so that the spring is coupled to the rigid portion, and the coupling body is characterized by rotatably attaching the rigid portion and the second end of the spring when the spring is loaded and when at least the indicator is driven in the first direction (30) by the driving finger. Claim 7 In claim 6, the coupling mechanism (20, 20C) and the bed (42) are configured such that when the spring (16) is loaded to drive the indicator (4) in the first direction, the coupling mechanism can rotate itself to a predetermined degree, at least in the initial stage, a side-view movement. Claim 8 In claim 6, when the indicator is driven in the second direction by the driving finger (12), the arbor (36) is rotatably attached to the wheel plate (8) and the coupling mechanism (20, 20A, 20B) is rotatably attached to the rigid part (10, 10A, 60); the first stop part (74) is manufactured integrally with or connected thereto with the arbor or the central part (24) rotatably attached to the arbor, and the second stop part (76) is manufactured integrally with or connected thereto with the spring (16) on the side of the second end, or manufactured integrally with or connected thereto with the coupling mechanism, characterized by a side-view movement. Claim 9 In claim 8, the second stop is integrally formed with or connected to the coupling mechanism; the coupling mechanism has a center of mass (21) that is radially further from the axis of rotation (22) than the first stop; when the indicator is driven in the second direction by the driving finger, the first stop (74) presses tangentially against the second stop (76) and the coupling mechanism (20, 20A, 20B) presses tangentially against the rear wall (43) of the bed (42, 42A, 42B), the rear wall being radially further from the axis of rotation (22) than the first stop; and when the indicator (4) is driven in the second direction by the driving finger (12), the coupling mechanism and the rigid part (10, 10A, 60), or the bed, when the indicator (4) is driven in the second direction by the driving finger (12), these are the first of the wheel plate (8). A side-view movement characterized by being configured to limit a brake system that provides a force coupling on the coupling mechanism in a direction corresponding to the direction of rotation, which itself opposes any rotation of the coupling mechanism. Claim 10 A side movement according to claim 9, wherein the coupling mechanism and the rigid part, or the bed, are configured such that the brake system itself limits the rotation of the coupling mechanism. Claim 11 A side movement according to claim 9, wherein the coupling mechanism and the rigid part are arranged such that, at least substantially, as soon as the first stop part rotates the second stop part in the second direction, the brake system itself locks the coupling mechanism against rotation. Claim 12 In claim 9, the brake system is characterized in that the coupling mechanism (20) is formed at least partially by a heel (52) which is opposite to the second end (19) of the spring (16) and beyond the center of mass (21) of the coupling mechanism, the heel is outside the bed (42) and is supported against an axial surface (41) on the rigid portion that contacts the bed when the indicator (4) is driven in the second direction (30) by the driving finger (12), thus forming a lateral movement. Claim 13 A lateral movement according to claim 10, wherein the coupling mechanism (20A, 20B) is arranged within the bed (42A, 42B) substantially without an angular gap and has a profile defining at least one zone for rotatably locking the coupling mechanism within the bed in a direction corresponding to the first rotational direction (50) of the wheel plate (8). Claim 14 A side-view movement according to any one of claims 1 to 3, wherein the arbor (36) is rotatably attached to the wheel plate (8); the first stop (84) is manufactured integrally with or connected to the arbor or the center part (24C) rotatably attached to the arbor, and the second stop (86) is formed by the rigid part (80, 80A). Claim 15 In claim 14, the first stop (84) is defined by the outer profile of a flange (35C) arranged at one end of the central portion (34C) forming the arbor, and the second stop (86) is defined by the profile of a recess (82) within a plate (38C) forming the rigid portion (80, 80A), wherein the flange is located within the recess over at least a portion of its thickness, characterized in that it is a side-view movement. Claim 16 A lateral movement according to claim 14, wherein the first stop portion is defined by the outer profile of a flange attached to the central portion forming the arbor, and the second stop portion is formed by a protruding portion rising from the plate forming the rigid portion. Claim 17 A side-view movement according to claim 14, wherein the first stop and the second stop are arranged in the internal space (11) of the rigid portion, the first stop is fastened to or formed by the rigid portion, and the second stop is fastened to or manufactured integrally with the wheel plate and protrudes therefrom. Claim 18 A side-view movement according to any one of claims 1 to 3, wherein the opening is a rectangular hole (26) machined in the plate (38, 38C) forming the rigid portion. Claim 19 A side-view movement characterized in that, in item 15, the opening is a rectangular hole (26) machined in the plate. Claim 20 A side-viewing movement according to claim 16, characterized in that the opening is a rectangular hole machined in the plate. Claim 21 A side-view movement characterized in that, in claim 17, the opening is a rectangular hole (26) machined in the plate. Claim 22 A time-measuring movement characterized in that, in any one of claims 1 to 3, the indicator (4) is a minute, hour, date, day, or month indicator.

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