Timepiece movement for a timepiece movement and timepiece comprising such a movement

Abstract

The invention relates to a timepiece movement (10) comprising a zero-reset mechanism (40) for resetting a time counter (22) to zero, the zero-reset mechanism comprising a zero-reset member (225) and a zero-reset hammer (50) shaped to cooperate with the zero-reset member, the zero-reset member being a worm cam comprising a helically extending cam track; the zero-reset hammer being displaceable by a zero-reset control member between a rest position, in which the zero-reset hammer is not in contact with the cam track, and a zero-reset position, in which the zero-reset hammer is in contact with the cam track and holds the zero-reset member in a reference position, the zero-reset hammer generating a drive torque on the zero-reset member between the rest position and the zero-reset position; the zero-reset hammer cooperating with a guide member shaped to guide the outward movement of the zero-reset hammer along a first path from the rest position to the zero-reset position and the return movement of the zero-reset hammer along a second path from the rest position to the zero-reset position, the first path and the second path not coinciding.

Description

Technical Field

[0001] This invention relates to a timing mechanism for a watch movement.

[0002] More specifically, the present invention relates to a timing mechanism including a zeroing mechanism.

[0003] The present invention also relates to a clock including such a timing mechanism. Background Technology

[0004] The timing mechanism can measure time as required using multiple timing counters (such as minute counters and second counters).

[0005] Timing mechanisms typically include a zeroing mechanism for resetting the timing counters to zero, that is, for repositioning them to a reference position so that time can be measured again as required.

[0006] Typically, such a zeroing mechanism includes a zeroing control that can be operated by the user, for example via a button or actuating pin that can be accessed from the outside of the middle part where the watch movement is mounted.

[0007] The zeroing control unit works directly or indirectly with the zeroing hammer, which strikes the zeroing cam carried by each timing counter.

[0008] The timing counter and its associated pointer are reset to zero by pressing a zeroing hammer against the surface of a zeroing cam, thereby generating a driving torque that changes the position of the associated timing counter until it returns to a reference position determined by the geometry of the zeroing hammer and the zeroing cam.

[0009] As is well known, zeroing cams have an eccentric or "snail" shape formed by a single helix, resulting in resetting always occurring in the same direction. Figure 1 shows an example of such a zeroing cam in the prior art.

[0010] These worm cams lack precision and cannot guarantee that the counter will reset to zero at any angular position on the cam. In fact, when the worm cam is in an angular position very close to its reference position, such as at an angular position corresponding to a fraction of a second of pointer rotation, the gaps between the components may mean that the zeroing hammer slips on the worm cam, causing the pointer visible to the user to move backward instead of being driven in the direction in which the pointer is reset to zero.

[0011] To overcome these drawbacks, a heart-shaped zeroing cam was developed, which has two identical helices but in opposite directions, thus forming a heart shape, as shown in the reference manual of C.-A. Reymondin et al. (“Théorie d'horlogerie”, Fédération des Ecoles Techniques, 2015, p. 238).

[0012] This zeroing cam is shown in Figure 2.

[0013] The zeroing hammer used to reset this heart-shaped cam to zero includes a horseshoe-shaped arm (visible in Figure 2). At the end of the zeroing hammer's stroke (linear or circular), the arm rests on a double protrusion formed by the heart-shaped piece to ensure that it is held in a stable position corresponding to the zeroing position of the counter and the corresponding pointer.

[0014] This type of zeroing mechanism is well-known, but it has several drawbacks.

[0015] First, the hands, especially the second hand, are often positioned randomly and lack precision when returning to zero. This is particularly disadvantageous in the case of a jumping second hand, which should be at a precise angular position every second to face the scale on the dial.

[0016] Secondly, considering the geometry of the heart-shaped component and the zeroing hammer, the frictional force at their interface is not constant. As a result, these components experience uneven wear, which is detrimental to the long-term reliability of the mechanism.

[0017] Third, at certain angles of the heart-shaped component, the zeroing hammer rubs against the heart-shaped component with its sharp edge, as described in the aforementioned manual. Figure 11 As shown in -29, this increases stress concentration, wear, and mechanical fatigue in the component.

[0018] Fourth, the inertia gained by the heart-shaped component during rotation means that it will not be locked in the reference position immediately at the end of the zeroing hammer's stroke, but will remain active through damped oscillations before resting, which will impair the sense of accuracy expected by experienced users.

[0019] Therefore, there is a need to improve the timing mechanism, especially the mechanism used to reset the counter of such a timing mechanism to zero. Summary of the Invention

[0020] In this context, one of the objectives of the present invention is to provide a timing mechanism that solves at least one of the above-mentioned problems.

[0021] One of the objectives of this invention is to provide a zeroing mechanism that provides precise zeroing, particularly for the chronograph second hand, which is precisely positioned relative to a predetermined scale on the dial.

[0022] One of the objectives of this invention is to provide a reliable and safe zeroing mechanism that enables the timer to be reset to zero in its direction of travel, while avoiding the phenomenon of the pointer moving backward when the zeroing hammer strikes the zeroing cam.

[0023] In this context, the present invention relates to a timing mechanism for a watch movement, comprising:

[0024] - A timing counter having an axis and a pointer that rotates integrally with the axis;

[0025] - A zeroing mechanism for resetting the timing counter to zero, the zeroing mechanism including a zeroing member integral with the shaft and a zeroing hammer, the zeroing hammer being shaped to cooperate with the zeroing member and generating a driving torque under the action of the zeroing control member until the zeroing member is positioned at a reference position by rotating along the travel direction of the timing counter;

[0026] The zeroing component is characterized in that the zeroing component is a worm cam with a cam track extending helically from a proximal end to a distal end around the axis of the timing counter, the proximal end defining a minimum radius region with respect to the axis, and the distal end defining a maximum radius region with respect to the axis;

[0027] The zeroing hammer can be moved between a rest position and a zero position by the zeroing control member. In the rest position, the zeroing hammer is not in contact with the cam track. In the zero position, the zeroing hammer is in contact with the cam track and holds the zeroing member in the reference position. The zeroing hammer generates a driving torque on the zeroing member between the rest position and the zero position.

[0028] The zeroing hammer cooperates with the guide member, which is shaped to guide the zeroing hammer to move outward along a first path from the rest position to the zeroing position and to guide the zeroing hammer to move back along a second path from the zeroing position to the rest position. The first path and the second path of the zeroing hammer do not coincide.

[0029] Advantageously, the return path (i.e., the second path) is different from the outward path (i.e., the first path), such that the return path deviates at least substantially from the first path.

[0030] The difference between the outward and return paths of the zeroing hammer, particularly at the point of contact with the cam track, ensures sufficient support surface on the cam track when the timing counter is reset to zero, especially when the counter stops at the position corresponding to the start of the timing time. This ensures that the zeroing hammer-cam contact occurs on the surface of the helix, not on the nose of the cam. This ensures that the counter returns to its reference position on the correct side.

[0031] In addition to the features mentioned in the preceding paragraphs, the timing mechanism according to the invention may have one or more of the following features, either individually or in any technically feasible combination:

[0032] - The guide member is shaped to guide the zeroing hammer along a first straight unidirectional path from the rest position to the zeroing position and along a second multidirectional path from the zeroing position to the rest position having at least two different directions;

[0033] - The guide member is shaped to guide the zeroing hammer along a first curved path from the rest position to the zeroing position and along a second path from the zeroing position to the rest position that is different from the first curved path;

[0034] - The guide member includes a disengaged guide yoke, the guide yoke being configured to not function during the outward movement of the zeroing hammer and to function during the return movement of the zeroing hammer;

[0035] - The disengageable guide yoke includes a guide cam that engages with a guide pin, the guide pin being integral with the zeroing hammer. The guide cam includes a first portion and a second portion, the first portion being configured to disengage the guide yoke during outward movement of the zeroing hammer, and the second portion being configured to guide the zeroing hammer during its return movement.

[0036] -The detachable guide yoke engages with a guide yoke spring, which is biased to reposition the guide yoke in a balanced position against the yoke stop.

[0037] - The zeroing hammer includes an arm having an inclined surface at its free end, the inclined surface being configured to contact the cam track of the zeroing member under the action of the zeroing control member and generate a driving torque until the zeroing member is positioned at the reference position;

[0038] - The arm has a stop surface configured to form an angular positioning stop for the zeroing member during zeroing operation;

[0039] - The arm has a beak-shaped end, the beak-shaped end forming a protrusion extending from the inclined surface, the protrusion protruding from the stop surface;

[0040] - The zeroing component includes a connecting portion connecting the proximal end and the distal end, the connecting portion not belonging to the cam track, the connecting portion including a recess forming a space for receiving and accommodating the beak-shaped end when the zeroing hammer is in the zeroing position;

[0041] - The second portion of the guide cam is shaped to disengage the beak-shaped end from the recess during the return motion of the zeroing hammer, so that the beak-shaped end passes around the distal end of the zeroing member;

[0042] -The timing counter is a second counter;

[0043] - The timing mechanism includes a minute counter with a minute counter shaft, a minute hand that rotates integrally with the minute counter shaft, and a minute counter bearing a heart-shaped second zeroing component;

[0044] The zeroing hammer includes a second arm that cooperates with the second zeroing component. The second arm is configured to generate a driving torque under the action of the zeroing control element until the second zeroing component is positioned at a reference position.

[0045] Another aspect of the invention relates to a watch movement that includes such a timing mechanism according to the invention.

[0046] Another aspect of the invention relates to a watch including a watch movement according to the invention, the watch movement including a timing mechanism according to the invention.

[0047] The timepiece is preferably a wristwatch, which includes a case configured to receive and house a timepiece movement according to the invention. Attached Figure Description

[0048] The objects, advantages, and features of the invention will be better understood after reading the detailed description given below with reference to the accompanying drawings, in which:

[0049] - Figure 1, already described in the background art, is a schematic diagram of a first example of a zeroing cam in a prior art timing mechanism;

[0050] - Figure 2, already described in the background art, is a schematic diagram of a second example of a zeroing cam in a prior art timing mechanism;

[0051] - Figure 3 This is a schematic 2D illustration of the timing mechanism of a watch movement according to the present invention, the timing mechanism being in a resting position.

[0052] - Figure 4 yes Figure 3 A detailed view of a portion of the timing mechanism shown, particularly the first arm of the zeroing hammer;

[0053] - Figure 5 This is a schematic 2D illustration of the timing mechanism of a watch movement according to the present invention, the timing mechanism being in the actuated zero position;

[0054] - Figure 6 yes Figure 5 A detailed view of a portion of the timing mechanism shown, particularly the first arm of the zeroing hammer in contact with the zeroing component;

[0055] - Figure 7 This is a detailed view showing the end portion of a disengaged guide yoke of the timing mechanism according to the invention, the guide yoke including a guide cam for guiding the zeroing hammer;

[0056] - Figure 8 The zeroing hammer is shown from Figure 3 The intermediate rest position shown Figure 5 The timing mechanism according to the invention is in the first intermediate position during the outward movement of the actuated zero position;

[0057] - Figure 9 The zeroing hammer is shown from Figure 5 The actuated zero position shown Figure 3 The timing mechanism according to the invention is in the first intermediate position during the return motion of the intermediate rest position shown;

[0058] - Figure 10 The zeroing hammer is shown from Figure 5 The actuated zero position shown Figure 3 The timing mechanism according to the invention is in the second intermediate position during the return motion from the intermediate rest position shown;

[0059] - Figure 11 The return motion of the zeroing hammer at the second counter of the timing mechanism according to the invention is shown.

[0060] In all the accompanying drawings, unless otherwise stated, common elements have the same reference numerals. Detailed Implementation

[0061] Figure 3 A schematic plan view of a timing mechanism 10 integrated into a watch movement 1 according to the present invention is shown.

[0062] Figure 3 Specifically, the timing mechanism 10 is shown in the intermediate position (i.e., the non-actuated position). It should be noted that, by example, the timing counter is in its reference position.

[0063] Figure 5 The same timing mechanism 10 is shown in the actuated zero position, in which the counters are repositioned to their reference positions regardless of their initial positions.

[0064] The watch movement 1 according to the invention generally includes a plate 2, which serves as a support for the various components of the watch movement 1, particularly for a gear train (not shown) driven by an energy source (not shown) and dedicated to timekeeping.

[0065] Energy source 50 is, for example, a spring barrel, which is configured as an energy storage device that provides power to the gear train.

[0066] Typically, the gear train drives the hands of a time display, particularly the hour hand which corresponds to the hour markers, the minute hand which corresponds to the minute markers, and the second hand or second hand which corresponds to the second markers.

[0067] The speed of a gear train is usually regulated by a speed regulating component.

[0068] Speed ​​regulating components typically include an oscillator and an escapement mechanism. The oscillator can be an electrical oscillator or a mechanical oscillator.

[0069] For example, the oscillator is a mechanical balance wheel type oscillator. This type of balance wheel oscillator has an oscillation frequency, for example, between 2.5 Hz and 4 Hz.

[0070] For example, the oscillator is a high-frequency electrical oscillator or a mechanical oscillator, that is, oscillating at a frequency greater than 4 Hz.

[0071] For example, the oscillator is a high-frequency electrical oscillator or a mechanical oscillator, that is, oscillating at a frequency greater than or equal to 5 Hz.

[0072] The timing mechanism 10 includes a timing gear train 20, which can be kinematically connected to a running gear train via a coupling (not shown) as required, the coupling being controlled by a timing start / stop control member 30.

[0073] According to an alternative embodiment, the connector is a yoke connector that allows the connecting wheel to be pivoted.

[0074] According to an alternative embodiment, the connector is a vertical connector.

[0075] According to another alternative embodiment, the connector is a differential connector that engages with a connector yoke controlled by a timing start / stop control member to block one of the differential connector inputs.

[0076] Typically, the timing gear train 20 includes at least one timing counter.

[0077] refer to Figure 3 and Figure 5 The timing gear system 20 includes a first timing counter formed by a second counter 22 and a second timing counter formed by a minute counter 21.

[0078] The minute counter 21 includes a minute counter wheel 211, which is connected to a shaft 213 called the minute counter shaft and drives the minute hand 214 (in...). Figure 3 (shown as dashed lines in the middle).

[0079] The second counter 22 includes a second counter wheel 221, which is connected to a shaft 223 called the second counter shaft and drives the chronograph second hand 224. Figure 3 (shown as dashed lines in the middle).

[0080] Preferably, the minute counter wheel 211 is integral with the shaft 213 of the minute counter 21, and the second counter wheel 221 is frictionally mounted on the shaft 223 of the second counter 22. Of course, the opposite configuration is also possible without departing from the background of the invention.

[0081] According to an alternative embodiment, minute counter wheel 211 and second counter wheel 221 are frictionally mounted on their respective shafts 213, 223.

[0082] The timing gear train 20 may also include an additional fractional-second counter (not shown), also known as a femtosecond counter.

[0083] The chronograph train 20 may include intermediate chronograph gear pairs 23, 24, and 25 to achieve a desired ratio between the various counters 21 and 22 of the chronograph mechanism 10. The chronograph train 20 may include more intermediate gear pairs, depending on the requirements and architecture of the watch movement 1 and the layout of the minute counter 21, second counter 22, and optional femtosecond counter on the mainplate 2 of the watch movement 1.

[0084] The timing mechanism 10 also has a zeroing mechanism 40 for resetting the minute counter 21 and the second counter 22 to zero, and more specifically for resetting the pointers 214, 224 associated with these counters to zero.

[0085] The zeroing mechanism 40 includes zeroing components 215 and 225 integrated with the shafts 213 and 223 of the timing counters 21 and 22. The zeroing components 215 and 225 cooperate with the zeroing hammer 50 to position them in a reference position and reset the pointers 214 and 224 of the counters 21 and 22 to zero.

[0086] The zeroing components 215 and 225 of the minute counter 21 and the second counter 22 are, for example, worm-shaped, heart-shaped or similarly shaped zeroing cams, the shape of which allows the pointers 214 and 224 to be repositioned at the reference position at the end of the stroke of the zeroing hammer 50.

[0087] exist Figures 3 to 11 In the example shown, the zeroing component 215 of the minute counter 21 is, for example, a heart-shaped component with two identical spirals arranged in opposite directions. In the remainder of the specification, the zeroing component 215 of the minute counter 21 is simply referred to as a heart-shaped cam.

[0088] According to the present invention, the zeroing member 225 of the second counter 22 is a worm cam having a single helical shape. In the remainder of the specification, the zeroing member 225 of the second counter 22 is simply referred to as a worm cam.

[0089] refer to Figure 4 , in order to Figure 3 The same approach more precisely illustrates the second counter 22 and the zeroing hammer 50 in their intermediate rest position. A worm cam 225 defines a cam track 226 that extends radially from a proximal end 227 to a distal end 228 about the axis 223 of the second counter 222. The proximal end 227 defines the minimum radius region of the cam track 226 about the axis 223, and the distal end 228 defines the maximum radius region of the cam track 226 about the axis 223. The cam track 226 defines the outer track of the worm cam 225, against which the zeroing hammer 50 abuts to apply a driving torque on the axis 223.

[0090] The distal end 228 and proximal end 227 of the cam track 226 are connected by a connecting portion 230, which does not form part of the cam track 226. In the example shown, the connecting portion 230 has a generally S-shaped form that extends radially relative to the axis 223 of the second counter 22.

[0091] The connecting portion 230 has a recess 232 positioned near the proximal end 227. The recess 232 creates a space suitable for receiving a portion of the zeroing hammer 50 at the end of its stroke (zeroing position), particularly at the protruding end of the first arm 510.

[0092] The connecting portion 230 may also include an additional support surface 231 positioned near the distal end 228 to extend the area intended to abut against the zeroing hammer 50 when the worm cam 225 is reset to zero.

[0093] The zeroing mechanism 40 includes a zeroing control 60, which can be operated by a user, for example, via a button or actuating pin 61. The zeroing control 60 can rotate about a rotation axis 66 and cooperates directly or indirectly with a zeroing hammer 50, which in turn acts on cams 215 and 225 to reset the pointers 214 and 224 of the associated counters 21 and 22 to zero.

[0094] like Figure 3 and Figure 5 As shown, the zeroing control 60 cooperates with the flexible zeroing element 62, which is configured to reposition the zeroing control 60 to the intermediate rest position between each user operation. Figure 3 Under the elastic action of the elastic element, the repositioning zeroing control component 60 will reposition the zeroing hammer 50 to the middle position.

[0095] The zeroing mechanism 40 also includes a retaining member 64 to secure the zeroing mechanism 40 and ensure that the zeroing hammer 50 is fully actuated until it reaches its zero position. The retaining member 64 is configured to temporarily hold the actuation of the zeroing control member 60, thereby holding the actuation of the zeroing hammer 50 until a certain force is applied to the zeroing control member 60.

[0096] The retaining member 64 is a safety component that prevents the pointers 214 and 224 of the timing mechanism 10 from being unintentionally reset to the zero position. The retaining member 64 has dynamic behavior similar to that of a mechanical fuse.

[0097] like Figure 3 and Figure 5 As shown, the retaining member 64 includes a portion integral with the machine plate 2 and includes an elastic portion arranged to apply a retaining force against actuation of the zeroing control member 60. The elastic portion is configured to deform when a force greater than the retaining force is applied to the zeroing control member 60, thereby releasing all movement of the zeroing control member 60, allowing the zeroing hammer 50 to move until it reaches its zeroing position. Figure 5 For example, the zeroing control 60 includes a stud 65 designed to rest on a resilient portion of the retaining member 64.

[0098] More specifically, the stud 65 rests on a retaining recess formed at the free end of the elastic portion of the retaining member 64. The retaining recess has a retaining surface and an inclined point beyond which the retaining member 64 allows the zeroing control 60 to be actuated quickly and unimpeded, thus enabling the zeroing hammer 50 to be fully actuated until it contacts the zeroing cams 215 and 225 of the timing counters 21 and 22 and repositions these cams to their reference positions.

[0099] The zeroing hammer 50 includes a first arm 510, which has an inclined surface 512 at its free end. This inclined surface 512 forms a first support surface, which is configured to tilt against the cam track 226 of the worm cam 225 of the second counter 22. Figure 4 and Figure 6 It is shown in more detail in the middle.

[0100] Specifically, Figure 4 The first arm 510 of the zeroing hammer 50 is shown in its intermediate resting position, while Figure 6 The same arm 510 of the zeroing hammer 50 is shown at the end of its stroke, in its zeroing position.

[0101] The first arm 510 has a stop surface 513 forming a positioning stop, which serves as a reference for the angular positioning of the worm cam 225. When the support surface 231 and / or the distal end 228 of the cam track 226 contacts the stop surface 513, the stop surface 513 stops the rotation of the worm cam 225 and resets it to the zero position, thereby positioning the worm cam 225 in its reference position.

[0102] The inclined surface 512 of the first arm 510, together with the stop surface 513, forms a beak-shaped end 514. The beak-shaped end 514 forms a protrusion that extends from the inclined surface 512 and protrudes from the stop surface 513.

[0103] Therefore, the first arm 510 of the zeroing hammer 50 has a shape different from the horseshoe shape known in the prior art.

[0104] The beak-shaped end 514 ensures sufficient overlap between the inclined surface 512 of the arm 510 and the cam track 226 during zeroing operations, especially when the worm cam 225 is in a critical position, i.e., when it is already in its reference position or very close to it. In fact, in these specific positions, using a zeroing hammer with a conventional horseshoe shape, the arm 510 "slides" and pushes the worm cam, rather than causing it to rotate in the usual zeroing direction. This phenomenon can be perceived by the user as the counter pointer moving backward instead of rotating in the usual zeroing direction (clockwise in this case).

[0105] Therefore, by utilizing such a beak-shaped end 514, the contact surface of the inclined surface 512 is extended, which ensures that when the zeroing control 60 of the timing mechanism 10 is actuated and when the zeroing hammer 50 strikes the worm cam 225, the worm cam 225 begins to move regardless of its angular position.

[0106] When the worm cam 225 is in its reference position and when the zeroing hammer 50 is at the end of its stroke, the recess 232 of the connecting portion 230 of the worm cam 225 receives and accommodates the beak-shaped end 514 of the first arm 510, as... Figure 5 As shown.

[0107] When the beak-shaped end 514 is received in the recess 232, the support surface 231 of the worm cam 225 or at least the distal end 228 of the cam track 226 abuts against the stop surface 513 of the first arm 510 of the zeroing hammer 50.

[0108] The zeroing hammer 50 has a second arm 520, which is configured to engage with the heart-shaped cam 215 of the minute counter 21.

[0109] like Figure 3 and Figure 5 As shown, the second arm 520 has a support surface 521 with two inclined surfaces forming a V-shape, and the support surface 521 is configured to cooperate with the heart-shaped cam 215 of the minute counter 21.

[0110] Thus, each inclined surface of the support surface 521 can engage with one of the two heart-shaped spirals of the heart-shaped cam 215, depending on its relative position when the zeroing control 60 is actuated. The inclination of each inclined surface is configured to generate a driving torque on the shaft 213 integrated with the minute hand 214, and to reposition the heart-shaped cam 215 to its reference position in a clockwise or counterclockwise direction.

[0111] The heart-shaped cam 215 has a notch between the two helices to receive the tip formed by the two inclined surfaces of the support surface 521, so as to keep the heart-shaped cam 215 and thus the minute hand 214 in a stable position at its zero position, thereby avoiding the phenomenon of the hand 214 swaying.

[0112] The timing mechanism 10, and especially the pointers 214 and 224 of the counters 21 and 22, are reset to zero in the following manner.

[0113] When operated by the user and when a force greater than the holding force of the holding member 64 is applied to the zeroing control member 60, the zeroing control member is released, allowing the zeroing hammer 50 to move quickly and completely to its zeroing position, as... Figure 5 As shown.

[0114] Then, the zeroing hammer 50 from Figure 3 The intermediate rest position shown (in which the zeroing hammer is not in contact with the zeroing components 215 and 225 of the counters 21 and 22) is where the movement reaches... Figure 5The zeroing position is shown, thereby repositioning the zeroing components 215 and 225 of counters 21 and 22 to their reference positions and holding them in a stable position until the user releases the zeroing control 60.

[0115] The zeroing hammer 50 cooperates with the guide member 140, which is configured to guide the zeroing hammer 50 when the zeroing control member 60 is actuated and when the zeroing control member 60 is released by the user. When the zeroing control member 60 is released by the user, the zeroing control member 60 is repositioned to an intermediate rest position by the action of the elastic zeroing element 62. In this way, the guide member 140 defines and guides the outward movement of the zeroing hammer 50 along a first path and the return movement along a second path.

[0116] Specifically, the outward movement of the zeroing hammer 50 corresponds to the travel of the zeroing hammer 50 from its intermediate rest position to its zeroing position, and conversely, the return movement of the zeroing hammer 50 corresponds to the travel of the zeroing hammer 50 from its zeroing position to its intermediate rest position.

[0117] The path of the return motion of the zeroing hammer 50, under the elastic return of the elastic zeroing element 62, is different from the path of its outward motion. Specifically, this is necessary to release the beak-shaped end 514, which is accommodated in the recess 232 at the zeroing position, without changing the angular position of the worm cam 225 during the return motion of the zeroing hammer 50. In this way, the reset of the cam to the zero position is unaffected.

[0118] For example, the zeroing hammer 50 travels in a unidirectional path during its outward movement, but its path during its return movement is at least bidirectional.

[0119] For example, the zeroing hammer 50 travels in a straight line and in one direction during its outward movement, while during its return movement, it travels in a straight line and in at least two different directions.

[0120] For example, the path of the zeroing hammer 50 during outward movement is circular, while the path during return movement can be curved, so as to have a different path from the outward movement.

[0121] In order to change the stroke of the zeroing hammer 50 between outward and return motions, the guide member 140 includes a guide yoke 142, which can disengage according to the outward or return motion of the zeroing hammer 50, and cooperates with a guide pin 55, which is integral with the zeroing hammer 50.

[0122] In the illustrated example, the disengaged guide yoke 142 is configured to disengage during the outward movement of the zeroing hammer 50, i.e., to be inactive, and to alter the unidirectional path of the zeroing hammer 50 during the return movement, specifically by disengaging the beak-shaped end 514 from the recess 232 and moving it sufficiently away from the worm cam 225 to avoid any contact between the beak-shaped end 514 and the distal end 228 of the cam.

[0123] The disengaged guide yoke 142 can rotate about its axis of rotation 12 in a plane parallel to the plate 2. The guide yoke spring 143 is biased to reposition the guide yoke 142 in its intermediate equilibrium position, thereby abutting against the fixed yoke stop 144 and limiting its angular clearance in the first rotational direction of the guide yoke 142.

[0124] When the zeroing hammer 50 has no specific effect on the guide yoke 142, the guide yoke 142 is held in the intermediate position by the guide yoke spring 143, thereby abutting against the yoke stop 144.

[0125] The guide yoke 142 carries the guide cam 145, and the guide cam 145 cooperates with the guide pin 55 of the zeroing hammer 50.

[0126] The guide cam 145 has a first portion 146 configured to allow the guide yoke 142 to disengage by moving the guide yoke 142 away from the yoke stop 144 as the guide pin 55 advances when the zeroing control 60 is actuated.

[0127] The guide cam 145 has a second portion 147 configured to deflect the path of the zeroing hammer 50 when the zeroing control 60 is released.

[0128] refer to Figure 7 The diagram shows in more detail the guide cam 145 of the disengaged guide yoke 142, which has a generally rhomboid shape, for example, and its first portion 146 has a first inclined surface 146a for receiving the guide pin 55 during the outward stroke of the zeroing hammer 50. When the guide pin 55 contacts the first inclined surface 146a, its inclination allows the guide yoke 142 to disengage as the zeroing hammer 50 advances by rotating the guide yoke 142 about the axis of rotation 12. Disengagement is achieved by applying a force to the guide yoke spring 143.

[0129] The first part 146 also includes a first flat portion 146b of a predetermined length, which is configured to hold the guide yoke 142 in the disengaged position as long as the guide pin 55 does not cross the guide cam 145.

[0130] The second portion 147 has a second inclined surface 147a, which forms a gradually slightly inclined slope to receive and guide the guide pin during the return motion of the zeroing hammer 50. During the return motion of the zeroing hammer 50, when the guide pin 55 contacts the second inclined surface 147a, and is blocked by the guide yoke 142 abutting against the yoke stop 144, the second inclined surface 147a deflects the guide pin 55, and thus deflects the zeroing hammer 50, allowing the first arm 510 to pass over the worm cam 225. The second portion 147 also includes a second flat portion 147b of predetermined length, which is configured to keep the zeroing hammer 50 away from the worm cam 225 as long as the guide pin 55 does not cross the guide cam 145 during the return motion of the zeroing hammer 50.

[0131] The zeroing hammer 50 has an elongated oval first guide groove 51, which engages with a first guide pin 71, which is integral with the zeroing control member 60. The orientation of the first guide groove 51 is determined to convert the rotational motion of the zeroing control member 60 into approximately linear motion of the zeroing hammer 50, while allowing a certain angular displacement between the zeroing hammer 50 and the zeroing control member 60. The first guide groove 51 and the first guide pin 71 belong to the guide member 140. The first guide groove 51 is located at the first end of the zeroing hammer 50.

[0132] The zeroing hammer 50 has an elongated second guide groove 52, which is oriented substantially along the travel direction of the zeroing hammer 50. The second guide groove 52 is located at the end of the zeroing hammer 50 opposite to the zeroing control member 60.

[0133] The second guide groove 52 cooperates with the stationary second guide pin 72, which is, for example, integrated with the machine board 2.

[0134] The second guide groove 52 and the second guide pin 72 belong to the guide member 140 and form a pivot-sliding connection, thereby guiding and realizing the translational movement along the elongated shape of the second guide groove 52 and the rotational movement of the zeroing hammer 50 about the pivot formed by the second guide pin 72.

[0135] The zeroing hammer 50 also has a third guide groove 53, the outer contour of which defines the angular clearance of the zeroing hammer 50 during outward and return movements. The third guide groove 53 mates with a stationary third guide pin 73, which is integral with the machine plate 2, for example.

[0136] During the outward movement of the zeroing hammer 50, the zeroing control unit 60 initiates the linear displacement of the zeroing hammer 50. The zeroing hammer 50 is guided by a second guide pin 72 that mates with the second guide groove 52 and a third guide pin 73 that mates with the third guide groove 53. A zeroing hammer spring can be used to apply a biasing force to keep the zeroing hammer 50 against the third guide pin 73 during the outward stroke, such that the third guide pin 73 is aligned with the lower contour of the third guide groove 53 (e.g., ...). Figure 3 (As shown) Maintain contact.

[0137] Due to the slope of the first inclined surface 146a of the first portion 146 and the constraint imposed by the guide member 140, during the outward movement of the zeroing hammer 50, the linear displacement of the guide pin 55 in this case changes the angular position of the guide yoke 142 by deflecting the guide cam 145 during the linear advance of the guide pin 55. When the guide pin 55 passes the guide cam 55, the disengaged guide yoke 72 returns to its resting position under the action of the guide yoke spring 143.

[0138] During the outward movement of the zeroing hammer 50, the two arms 510 and 520 strike the zeroing components 215 and 225, thereby applying driving torque on the corresponding shafts 213 and 223 as described above. In this way, the zeroing components 215 and 225 are repositioned in their reference positions.

[0139] When the user releases the zeroing control 60, the zeroing hammer 50 initially moves along a straight path similar to outward travel under the action of the elastic zeroing element 62 until the guide pin 55 contacts the second part 147 of the guide cam 145 of the disengaged guide yoke 142.

[0140] Due to the slope of the second inclined surface 147a of the guide cam 145 and the yoke stop 144 that prevents the disengaged guide yoke 72 from rotating, the guide pin 55 and thus the zeroing hammer 50 are deflected by the guide cam 145, thereby applying a force against the zeroing hammer spring.

[0141] This angular offset of the zeroing hammer 50, imposed by the shape of the guide cam 145, is made possible in particular by the presence of the third guide groove 53, which gives the zeroing hammer 50 angular freedom about the pivot-sliding connection formed by the second guide groove 52 and the second guide pin 72.

[0142] Using diagrams Figure 3 The timing mechanism 10 according to the invention is shown, and specifically the zeroing hammer 50 is shown in its intermediate rest position when the zeroing control 60 has not been operated.

[0143] Figure 8The timing mechanism 10 according to the invention is shown, which is in an intermediate position between the intermediate rest position and the zeroing position of the zeroing hammer 50 during the outward movement of the zeroing hammer 50. Figure 8 As can be seen, the rotation of the zeroing control unit 60 has caused the zeroing hammer 50 to move linearly toward the counters 21 and 22. The guide pin 55 deflects the guide yoke 142 away from the yoke stop 144. The inclined surface 512 of the first arm 510 contacts the cam track 226 and has initiated the zeroing of the worm cam 225.

[0144] The further movement of the zeroing hammer 50 brings it to the aforementioned point. Figure 5 The location shown. In this... Figure 5 In the middle, arms 510 and 520 have struck the zeroing components 215 and 225, and the zeroing components 215 and 225 have been repositioned to their reference positions.

[0145] Figure 9 and Figure 10 The timing mechanism 10 according to the invention is shown to be in the state during the return motion of the zeroing hammer 50. Figure 5 The zero position and Figure 3 The two intermediate positions between the intermediate rest positions.

[0146] More specifically, Figure 9 The position of the zeroing hammer 50 is shown when it is deflected by the inclined surface 147a of the second inclined surface 147 of the second part 147 of the guide cam 145. The zeroing hammer then follows a path along the first direction t1.

[0147] Figure 10 The position of the zeroing hammer 50 is shown when the second flat portion 147b of the second portion 147 of the guide cam 145 is held apart. From this position, when the guide pin 55 is no longer deflected by the guide cam 145, the zeroing hammer 50 returns to abut against the third guide pin 73 under the action of the zeroing hammer spring (not shown), thus traveling in the second direction t2, and then returning to... Figure 3 The initial intermediate rest position is shown.

[0148] Figure 11 Specifically, the path of the first arm 510 around the worm cam 225 is shown during the return motion of the zeroing hammer 50.

[0149] The invention has been specifically described as a zeroing hammer moving along a straight path in one direction during outward movement and along a straight path in at least two directions during return movement. However, the invention is also applicable to zeroing hammers configured to cooperate with zeroing controls and guide members, thereby allowing the zeroing hammer to have circular, curved, or complex paths during outward and return movements, and paths in multiple directions during return movement, so as to generate offset in the return path of the first arm by using a disengaged guide cam.

[0150] As shown in the figures, the timing mechanism 10 includes a guide wheel 63 to control the various movements of various rods resting on or between two guide posts. Since the operation of the timing mechanism 10 with this guide wheel 63 is well-known, there is no need to further explain how this guide wheel operates.

[0151] Of course, the timing mechanism 10 can also be a timing mechanism with a cam instead of the guide wheel 63 without departing from the scope of the invention.

[0152] The present invention also relates to watches, such as wristwatches, that include such a watch movement.

Claims

1. A timing mechanism (10) for a watch movement (1), the timing mechanism (10) comprising: - A timing counter (22) having an axis (223) and a pointer (224) that rotates integrally with the axis (223). - A zeroing mechanism (40) for resetting the timing counter (22) to zero, the zeroing mechanism (40) including a zeroing member (225) integral with the shaft (223) and a zeroing hammer (50) formed to cooperate with the zeroing member (225) and generate a driving torque under the action of the zeroing control member (60) until the zeroing member (225) is positioned at a reference position by rotating along the travel direction of the timing counter (22); The zeroing component (225) is characterized in that it is a worm cam having a cam track (226) extending helically from a proximal end (227) to a distal end (228) about the axis (223) of the timing counter (22), the proximal end (227) defining a minimum radius region about the axis (223) and the distal end (228) defining a maximum radius region about the axis (223); The zeroing hammer (50) can be moved between a rest position and a zero position by the zeroing control member (60). In the rest position, the zeroing hammer (50) is not in contact with the cam track (226). In the zero position, the zeroing hammer (50) is in contact with the cam track (226) and holds the zeroing member (225) in the reference position. The zeroing hammer (50) generates a driving torque on the zeroing member (225) between the rest position and the zero position. The zeroing hammer (50) cooperates with the guide member (140), which is shaped to guide the zeroing hammer (50) to move outward along a first path from the rest position to the zeroing position and to guide the zeroing hammer to move back along a second path from the zeroing position to the rest position. The first path and the second path of the zeroing hammer (50) do not coincide.

2. The timing mechanism (10) for a watch movement (1) according to claim 1, characterized in that, The guide member (140) is shaped to guide the zeroing hammer (50) along a first straight unidirectional path from the rest position to the zeroing position and along a second multidirectional path from the zeroing position to the rest position having at least two different directions.

3. The timing mechanism (10) for a watch movement (1) according to claim 1, characterized in that, The guide member (140) is shaped to guide the zeroing hammer (50) along a first curved path from the rest position to the zeroing position and along a second path from the zeroing position to the rest position that is different from the first curved path.

4. The timing mechanism (10) for a watch movement (1) according to any one of the preceding claims, characterized in that, The guide member (140) includes a disengaged guide yoke (142) shaped to be inactive during the outward movement of the zeroing hammer (50) and to be active during the return movement of the zeroing hammer (50).

5. The timing mechanism (10) for a watch movement (1) according to claim 4, characterized in that, The guide yoke (142) includes a guide cam (145) that engages with a guide pin (55) integral with the zeroing hammer (50). The guide cam (145) includes a first portion (146) and a second portion (147). The first portion (146) is shaped to disengage the guide yoke (142) during the outward movement of the zeroing hammer (50), and the second portion (147) is shaped to guide the zeroing hammer (50) during the return movement of the zeroing hammer (50).

6. The timing mechanism (10) for a watch movement (1) according to claim 5, characterized in that, The guide yoke (142) engages with the guide yoke spring (143), which is biased to reposition the guide yoke (142) in a balanced position against the yoke stop (144).

7. The timing mechanism (10) for a watch movement (1) according to any one of claims 1 to 3, characterized in that, The zeroing hammer (50) includes an arm (510) having an inclined surface (512) at its free end, the inclined surface (512) being configured to contact the cam track (226) of the zeroing member (225) under the action of the zeroing control member (60) and generate a driving torque until the zeroing member (225) is positioned at the reference position.

8. The timing mechanism (10) for a watch movement (1) according to claim 7, characterized in that, The arm (510) has a stop surface (513) configured to form an angular positioning stop for the zeroing member (225) during zeroing operation.

9. The timing mechanism (10) for a watch movement (1) according to claim 8, characterized in that, The arm (510) has a beak-shaped end (514) that forms a protrusion extending from the inclined surface (512) and protruding from the stop surface (513).

10. The timing mechanism (10) for a watch movement (1) according to claim 9, characterized in that, The zeroing component (225) includes a connecting portion (230) connecting the proximal end (227) and the distal end (228), the connecting portion (230) not belonging to the cam track (226), the connecting portion (230) including a recess (232) forming a space for receiving and accommodating the beak-shaped end (514) when the zeroing hammer (50) is in the zeroing position.

11. The timing mechanism (10) for a watch movement (1) according to claim 10, characterized in that, The guide member (140) includes a disengaged guide yoke (142) shaped to be inactive during the outward movement of the zeroing hammer (50) and active during the return movement of the zeroing hammer (50). The guide yoke (142) includes a guide cam (145) cooperating with a guide pin (55) integral with the zeroing hammer (50). The guide cam (145) includes a first portion (146) and a second portion (147), the first portion (146) being shaped... To disengage the guide yoke (142) during the outward movement of the zeroing hammer (50), the second portion (147) is shaped to guide the zeroing hammer (50) during the return movement of the zeroing hammer (50), and the second portion (147) of the guide cam (145) is shaped to disengage the beak-shaped end (514) from the recess (232) during the return movement of the zeroing hammer (50) so that the beak-shaped end (514) passes around the distal end (228) of the zeroing member (225).

12. The timing mechanism (10) for a watch movement (1) according to any one of claims 1 to 3, characterized in that, The timing counter (22) is a second counter.

13. The timing mechanism (10) for a watch movement (1) according to claim 12, characterized in that, The timing mechanism (10) includes a minute counter (21) with a minute counter shaft (213), a minute hand (214) that rotates integrally with the minute counter shaft (213), and the minute counter shaft (213) carrying a heart-shaped second zeroing component (215).

14. The timing mechanism (10) for a watch movement (1) according to claim 13, characterized in that, The zeroing hammer (50) includes a second arm (520) that cooperates with the second zeroing component (215). The second arm (520) is configured to generate a driving torque under the action of the zeroing control member (60) until the second zeroing component (215) is positioned at a reference position.

15. A watch movement (1), characterized in that, The watch movement (1) includes a timing mechanism (10) for the watch movement (1) according to any one of claims 1 to 14.

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