• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
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    • 专利摘要:
    The invention relates to a mechanism (100) for a clock movement, comprising: a power source (1), a first drive train connecting the power source (1) to a first regulating member (O1), a second drive train connecting the power source (1) to a second regulating member (O2), the second regulating member (O2) having a different operation from the first regulating member (O1), an output moving wheel serving to drive the second time display, adapted to be kinematically connected to both the first drive train and the second drive train, the mechanism (100) being arranged such that the step of the first regulating member (O1) or the operation of the second regulating member (O2) enables the driving of the time display with the same speed of rotation. The first and the second regulating members (O1, O2) belong to the group comprising mechanical oscillators, comprising, for example, a balance and a spiral spring, piezoelectric oscillators, quartz electric oscillators, tuning fork oscillators and switches. electric.
    公开号:CH712597A1
    申请号:CH00784/16
    申请日:2016-06-20
    公开日:2017-12-29
    发明作者:Cornibé Sylvain；Bouquin Jean-Marie
    申请人:Richemont Int Sa；
    IPC主号:
    专利说明:

    TECHNICAL FIELD [0001] The present invention relates to a mechanism for a watch movement comprising two regulating members, such as oscillators, which allows the adaptation of the motive power.
    State of the art [0002] The watch movements with several regulating members have been known for a long time (patent CH 156 801 of 1931) and are used for various reasons. Regulator means a regulating system comprising a time base, such as a balance-balance oscillator, and a counting device such as an escapement. For example, the use of two permanently coupled oscillators, driven by a single barrel, is mainly intended to improve the running of a watch by averaging the deviations of each oscillator or conferring on each oscillator compensating qualities with regard to disturbances outside (temperature, positions, ..).
    Some movements have two regulators, driven by a single source of energy, intended to operate alternately. This is the case of the movement presented in EP1 864 190, which allows operation alternately day and night. Indeed, the document EP 1 864 190 describes a solution in which a single energy source in the form of a barrel alternately drives one then the other among two identical regulators (carousels or vortices), and this with an automatic rocker every twelve hours carried out by means of a suitable return system.
    Other movements have two separate wheels, each with its motive power, its cog and its oscillator. The first wheel can be dedicated to displaying the time and the second wheel can be sized for a specific application. This dissociation makes it possible not to disturb the first wheel and therefore the accuracy of the display of the time.
    The above mechanisms do not allow, or little, to modulate the driving energy of a single source of energy to drive two different, different oscillators.
    BRIEF SUMMARY OF THE INVENTION [0006] An object of the present invention is to propose a movement for a timepiece free from the limitations of known movements.
    Another object of the invention is to propose a movement for a timepiece with two regulating members, such as oscillators, which are different and which are intended to be able to operate in a decoupled manner: when a regulating member is active, the other is at rest.
    According to the invention, these objects are achieved in particular by means of a mechanism for a watch movement, comprising a power source, a first drive train connecting the power source to a first regulating member, a second drive train connecting the power source to a second regulating member, the second regulating member having a different operation of the first regulating member, an output mobile serving to cause the time display, adapted to be kinematically connected both at the first drive train and the second drive train, the mechanism being arranged so that the operation of the first regulating member or the operation of the second regulating member allows the training of the time display with the same speed of rotation.
    This solution has the particular advantage of proposing an adaptation of the available motive energy in the energy source to drive one or the other of the two regulatory bodies, without any particular constraint binding these two regulating members.
    Thus, the movement according to the invention allows two modes of operation, these two modes of operation respectively controlled by the first regulating member, and the second regulating member, to adapt the movement to the desired use and, for example, according to the "complications" proposed by such a movement.
    According to one embodiment, the first regulator member has a first frequency and the second regulator member has a second frequency different from the first frequency.
    According to another embodiment, the energy source cooperates directly with the first drive train and with the second drive train.
    Still according to another embodiment, the mechanism comprises a first differential, the first drive train and the second drive train being kinematically connected to the output mobile via the first differential.
    Still according to another embodiment, the mechanism comprises a second differential, the energy source cooperating with the first drive train and with the second drive train via the second differential.
    According to another embodiment, said energy source comprises a barrel provided with a drum and a barrel shaft between which is mounted a motor spring, the drum having a first toothing.
    The use of a barrel as a power source allows to integrate the movement according to the invention in a timepiece with well known operating energy parameters.
    According to another embodiment, the movement further comprises a locking device for simultaneously stopping the march of one of the first and second regulating member and to release the step of the other of the first and second regulating member. In this way, the movement is permanently driven either by the first regulating member 01 or by the second regulating member 02, without dead time.
    Still according to another embodiment, the mobile output of said mechanism is in kinematic connection with a wheel hours or a minute wheel or a wheel of seconds. In this way, a unique display of the time is preserved, irrespective of the regulating member that carries out the movement training.
    Brief description of the figures [0019] FIG. 1 is a perspective view of an embodiment of the movement according to the invention, from above the movement; fig. 2 is a perspective view of the movement of FIG. 1, from below the movement, FIG. 3 schematically shows a configuration of the mechanism according to a variant; fig. 4 schematically shows a configuration of the mechanism according to another variant; fig. 5 schematically shows a configuration of the mechanism according to yet another variant; fig. 6 shows a sectional and perspective view of an alternative embodiment of the mechanism according to the configuration of FIG. 5; fig. 7 is a sectional and perspective view of another alternative embodiment of the mechanism according to the configuration of FIG. 5; fig. 8 schematically shows a configuration of the mechanism according to yet another variant; and FIG. 9 is a sectional and perspective view of another alternative embodiment of the mechanism according to the configuration of FIG. 8.
    Example (s) of embodiment of the invention [0020] Referring to FIGS. 1 and 2 illustrating a first embodiment of a mechanism according to the invention. The mechanism 100 comprises (see Figs 1 and 2) a barrel drum 1 rotatable about the axis 111 and equipped with a first toothing 1a cylinder. A barrel shaft 1d pivoting about the barrel axis 111 is secured to a winding toothing 1c. At least one motor spring (not visible in the figures) is disposed in the barrel and has a first end fixed to the barrel shaft 1d and a second end fixed on or cooperating with the barrel drum 1a. The barrel 1 also comprises a second cylinder gear 1b connected to the barrel shaft 1d by a unidirectional clutch (for example a unidirectional clutch release system) so that the winding of the mainspring of the barrel 1 can be reassembled. using the winding teeth 1c.
    The energy supplied by the barrel 1 can be transmitted to a first regulator member 01 via a first gear train formed of a first drive train 4 and a first gear train RF1. According to the embodiment illustrated in FIGS. 1 and 2, the first drive train comprises a first mobile 4 pivotally mounted about an axis 40 and comprising a first wheel 4a and a first pinion 4b meshing with the first set of teeth 1a.
    The energy supplied by the barrel 1 can also be transmitted to a second regulator member 02 via a second gear train formed of a second drive train 2, 3 and a second RF2 finishing train. According to the embodiment illustrated in FIGS. 1 and 2, the second drive train comprises a second mobile 2 pivotally mounted about an axis 20 and comprising a second wheel 2a and a second pinion 2b meshing with the second set of teeth 1b. The second drive train comprises a third mobile 3 pivotally mounted about an axis 30 and formed of a third pinion 3a meshing with the second wheel 2a, and a third wheel 3b.
    The mechanism 100 further comprises a first differential D1, 9, 10, 11, 12 cooperating with the first and the second gear 4, RF1 and 2, 3, RF2.
    Still according to the example of Figs. 1 and 2, the first differential D1 comprises a satellite gate 9 pivotable about an axis 90. The satellite gate 9 forms a cage on which one or more planet gears 11 (two satellites in the example illustrated in FIGS. 2) are pivotally mounted about an axis 50 (or axes 50), substantially perpendicular to the axis 90. A first sun gear 10 also pivotally mounted about the axis 90 comprises a first sun gear 10b of a sun gear coming into position. taken with the planet or satellites 11, as well as a first sun gear 10a engaging the first wheel 4a of the first wheel set 4. The first differential D1 further comprises a second sun gear 12 pivotally mounted about the axis 90 and comprising a second sun gear toothed cone 12a meshing with the at least one planet 11 and a second sun gear 12b meshing with the third wheel 3b of the wheel 3.
    The first differential D1 further comprises an output mobile, here an output shaft 15 which is integral with the satellite door 9 for driving a minute hand (not shown). In variants, the output may comprise a mobile driving, directly or indirectly, a mobile integral with the minute hand. The first differential D1 is therefore rotated at least by one or the other of the first drive train 4 and the first finishing work train RF1 (via the first wheel 4a) and the second work train. drive 2, 3 and the second work train RF2 (via the third wheel 3b). The first differential D1 must therefore be configured to rotate the output shaft 15 with an angular speed of one revolution in one hour, regardless of the rotational speed of the third wheel 3b and the first wheel 4a.
    According to a first mode of operation, the second regulator member 02 is at a standstill. The second transmission chain formed by the second drive train 2, 3 and the second finishing train RF2 is immobilized under the effect of the torque delivered by the mainspring of the barrel on the barrel shaft 1d and transmitted to the second gear 2b. The barrel shaft 1d and the second barrel teeth 1b, as well as the second sun gear 12 are immobilized. In this case, for example, an escape wheel is supported on an anchor, itself bearing on limiting pins.
    Under the effect of the engine torque exerted by the mainspring of the barrel, the barrel drum will drive the first pinion 4b of the first mobile 4 in rotation via the first toothing 1a. The rotation of the first pinion 4b drives the first wheel 4a in rotation. In turn, the first wheel 4a rotates the first gear 10a of the first sun gear 10 with which it meshes. The first toothed bevel gear 10b of the first sun gear 10 rotates the planet or satellites 11 which themselves engage with the second toothed bevel gear 12a of the second sun gear 12 which is stationary. In this way, the rotation of the first sun gear 10 forces the planet or satellites 11 to roll on the second toothed conical wheel 12a, immobile, driving the planet carrier 9, and thus the output shaft 15, in rotation in the same direction of rotation. rotation that the first sun gear 10. The transmission ratio of the first drive train 4, the first finishing train RF1 and the first differential D1 is such that the output shaft 15 pivots with a rotational speed of one turn per hour.
    In one embodiment, the first regulating member 01 oscillates with a first frequency f 1 and is adapted for the operation of a movement of a watch in normal use, when worn. The transmission ratio of the first drive train 4 and the first finishing train RF1 is then adapted to the first frequency of the first regulating member 01 (power reserve given).
    In a second mode of operation, the first regulating member 01 is stopped. A first transmission chain formed by the first drive train 4 and the first finishing train RF1 is immobilized under the effect of the torque delivered by the mainspring of the cylinder on the barrel drum 1 and transmitted to the first pinion 4b. The barrel drum 1 and the first set of teeth 1a of the barrel, as well as the first sun gear 10 are immobilized.
    Under the effect of the engine torque exerted by the mainspring of the barrel, the barrel shaft will drive the second pinion 2b of the second mobile 2 in rotation via the second toothing 1b barrel. The rotation of the second pinion 2b drives the second wheel 2a in rotation which itself drives the third pinion 3a and the third wheel 3b in rotation. In turn, the third wheel 3b rotates the second gear 12b of the second sun gear 12 with which it meshes. The second toothed conical wheel 12a of the second sun gear 12 rotates the planet or satellites 11 which themselves are engaged with the first toothed bevel gear 10b of the first sun gear 10 which is stationary. In this way, the rotation of the second sun gear 12 forces the planet or satellites 11 to roll on the first toothed conical wheel 10a, immobile, driving the planet carrier 9, and thus the output shaft 15, in rotation in the same direction of rotation. as the second sun gear 12. The transmission ratio of the second drive train 3, the second work train RF2 and the first differential D1 is such that the output shaft 15 is rotated with a rotational speed of one revolution per revolution. hour.
    The speed of rotation of the satellite door 9 is always one turn per hour, whether driven by the first drive train 4 and the first finishing train RF1 or by the second drive train 3 and the second wheel of finishing RF2.
    The second mode of operation maintains the activity of a second regulator member 02. It is obtained by sizing the second gear train 2, 3, RF2, and the second regulator member 02 according to the desired objective. It is therefore possible with this arrangement to adapt the torque of the barrel 1 for various applications. For example, the second regulator member 02 may have a second frequency f2 different from the first frequency f 1 of the first regulator member 01. The second frequency f2 may be lower or higher than the first frequency f 1 so as to deliver a torque given at the output shaft 15 for the training of a specific mechanism (timing mechanism, complications). For example, the second frequency f2 may be lower than the first frequency f 1 so as to obtain a greater power reserve than that obtained in the first mode of operation. It is then possible to operate the first regulator member 01 with a first frequency f 1 high for the operation of a watch when worn and operate the second regulator member 02 with a second frequency f2 lower when the watch is not range, without the rotational speed of the output shaft 15 is changed.
    According to a variant, the second frequency is at least two times lower than the first frequency. By way of example, the first oscillation frequency f 1 may be between 2 and 7 Hz, preferably between 3 and 5 Hz and the second oscillation frequency f 2 may be between 0.5 and 1.5 Hz, preferably In this case, it is understood that the transition to the second mode of operation extends the power reserve. The first mode of operation is for example used when the watch with the mechanism 100 is worn (especially the day) and the second mode of operation when the watch is not worn (at night and on periods of non-use or rest of the watch).
    In another example, the first regulator member 01 may comprise a Swiss lever escapement and the second regulator member 02 may comprise a detent escapement, the latter having a better performance but being more sensitive to shocks within range.
    More generally, the first and second regulator member 01.02 may comprise a mechanical oscillator such as a balance spring-type system or a tuning fork-type oscillator. It may also include an electromechanical oscillator such as a piezoelectric quartz oscillator or any other suitable form of oscillator.
    The transition from the first mode of operation to the second mode of operation and vice versa is achieved by stopping one of the two regulating members 01, 02. The shutdown of the first and second regulator member 01.02 will be adapted to the type of regulator used. For example, in the case of a sprung balance type regulator member, a stop-second mechanism (or balance stop, not shown) can be used.
    The transition from the first mode of operation to the second mode of operation and vice versa can be performed on manual control of the user. For this purpose, a manual control is used to control a stop device for the passage of the step from one to the other among the first and second regulating members 01, 02.
    On the other hand, this arrangement is compatible with the use of several barrels in series according to the energy needs and volumes available within a movement.
    It is therefore possible, with this arrangement, to modulate and adapt the torque delivered by the mainspring barrel for each regulating member 01 and 02, by modifying only the gear ratios of the first and second gear wheels. training 4 and 2, 3, without any other change in motion. For example, only the first drive train 4, only the second drive train 2,3, or the two drive trains 4, 2, 3 can be modified at a time, depending on the desired applications for each drive mode. operation.
    According to one embodiment, the first regulator member 01 and the second regulator member 02 operate simultaneously (third mode of operation). In this case, in general, the mechanism 100 is configured to allow further simultaneous operation of the first gear set 4, RF1 and the second gear set 2, 3, RF2. The first differential D1 is then moved both by the wheel 3b (driven by the second regulator member 02) at its toothing 12b and both by the wheel 4a (driven by the first regulator member 01) at its level. toothing 10a. In this case, there are accumulated rotational speeds (driving speeds generated by the simultaneous rotation of the wheels 4a and 3b) within the differential gear train, so that the output shaft 15 rotates twice as much. faster than in the first mode of operation or the second mode of operation. In this way, the mechanism 100 is permanently driven by the first regulating member 01 and / or by the second regulating member 02, without dead time.
    If one wants to be able to use this third mode of operation and keep a rotational speed of the output shaft 15 identical to that of the first and second modes of operation, the mechanism 100 is also equipped, optionally, a speed reduction module which is engaged on the output shaft 15 during this third mode of operation, and which is disengaged from the output shaft 15 for the first and second modes of operation. It is therefore a question of implementing a reduction gear actuated manually (or automatically) and mounted on the output shaft 15 in order to make it possible to reduce the speed of rotation of the output shaft 15 and in particular to divide this speed by two.
    Note that if the first differential D1 has been shown so far in the form of a mechanical differential, and in particular with a bevel gear train, other configurations are possible. In particular, according to a configuration not shown, the first differential D1 may be a flat differential gear.
    It goes without saying that the present invention is not limited to the embodiment which has just been described and that various modifications and simple variants can be envisaged by the skilled person without departing from the scope of the present invention. .
    Lafig. 3 shows schematically and more generally, a possible configuration of the mechanism 100 according to the invention. The first transmission chain comprises the first drive train (represented by the symbol RV1) and the first finishing work train RF1, between the barrel drum (represented by the symbol T) and the first regulating member 01. The first finishing gear RF1 kinematically connects the first drive train RV1 to the first regulator member 01. The cylinder itself is represented by the symbol B. The second transmission chain comprises the second drive train (represented by the symbol RV2) and the second RF2 finishing train, between the barrel shaft (represented by the symbol A) and the second regulating member 02. The second finishing train RF2 kinematically links the second drive train RV2 to the second regulating member 02. The first gear wheel drive RV1 and the second drive train RV2 engage the first differential D1. In particular, the first drive train RV1 engages the first differential D1 through a first input (which includes the first gear 10a in the example of Figs 1 and 2).
    The output shaft (represented by the symbol S) of the first differential D1 is intended to drive a minute hand. An hour setting device MH acting on the output shaft S and a winding device R of the barrel B are also shown in FIG. 3.
    In the first mode of operation, the barrel B drives the first gear train RV1, RF1 and the first regulator member 01 having a first frequency f1, and the second gear train RV2, RF2 and the second regulator member 02 are motionless. In the second mode of operation, the barrel B drives the second gear train RV2, RF2 and the second regulator member 02 having a second frequency f2, and the first gear train RV1, RF1 and the first regulator member 01 are immobile. . The transition from one mode to another is obtained instantaneously or almost instantaneously.
    As discussed above, the first mode of operation may correspond to a transmission of energy for the operation of a time display in a watch movement. The barrel B and the gear ratios of the first drive train RV1 and the first finishing train RF1 are then sized according to the characteristics of the oscillator and the exhaust of the first regulator member 01 for a given power reserve.
    The second mode of operation can be configured to deliver a given torque at the output shaft S for driving a specific mechanism by adapting accordingly the second regulator member 02. It is thus possible to obtain a power reserve different from that of the first mode for the same output shaft S which can also be used to cause calendar complications whatever the operating mode chosen.
    The proposed solution is compatible with the use of several barrels in series according to the energy needs and volumes available within the movement.
    FIG. 4 shows another possible configuration of the mechanism 100 according to the invention. In this alternative configuration, the first drive train RV1 and the first work train RF1 are not connected in series as in the example of FIG. 3 but in parallel with the barrel B. For example, each of the first drive train RV1 and the first finishing train RF1 engages with the barrel drum T. Similarly, the second drive train RV2 and the second work train RF2 are connected in parallel with the barrel B, more particularly, each of the second work train RV2 and the second work train RF2 comes into contact with the A barrel shaft. The mechanism 100 may also include any combination of the configurations shown in FIGS. 3 and 4.
    FIG. 5 schematically shows another possible configuration of the mechanism 100 according to the invention. The first transmission chain comprises the following kinematic sequence: the first drive train RV1, the first differential D1, the first finishing train RF1 and the first regulating member 01. The second transmission chain comprises the following kinematic sequence: the second drive train RV2 the first differential D1, the second finishing train RF2 and the second regulating member 02. The barrel B engages with the first transmission chain or the second transmission chain via a second differential D2. Similarly to the configurations of FIGS. 3 and 4, the first drive train RV1 and the second drive train RV2 engage with the first differential D1. The first differential D1 engages the output shaft S. The time setting device MH acting on the output shaft S and the winding device R of the cylinder B are also shown in FIG. 5.
    FIG. 6 illustrates an embodiment of the mechanism according to the configuration of FIG. 5. In particular, the second differential D2 comprises a first satellite gate 190 rotatable about an axis 191, on which is mounted a satellite wheel 192 of one or more satellites 193, each being guided in rotation on the satellite gate 190 around a satellite axis 194. An upper wheel 196 meshes with the planet or satellites 193 via an upper conical wheel 195 pivotally mounted about the axis 191. A lower wheel 197 meshes with the one or more satellites 193 via a lower conical wheel 198 pivoting on the axis 191.
    The mechanism also comprises a first differential D1 comprising a second satellite gate 200 pivotally mounted about a satellite gate axis 201, on which is also pivotally mounted one or more satellites 203 guided in rotation about a satellite axis 204, substantially perpendicular to the axis 201. An upper wheel 206 meshes with the satellite or satellites 203 via a second conical gear 205 pivotally mounted about the axis 201. A lower wheel 208 is secured to an intermediate wheel 207 and a first conical gear 209 pivotably mounted on the axis 201, the first conical gear 209 meshing with the planet or satellites 203.
    In the lafig configuration. 6, the first drive train RV1 comprises the upper wheel 196 and the upper wheel 206. The first finishing train RF1 driving the first regulating member 01 engages with the upper wheel 206. The second drive train RV2 comprises the lower wheel 197 and the intermediate wheel 207. The second finishing train RF2 driving the second regulating member 02 engages with the lower wheel 208. The first set of teeth 1 a (not shown in Fig. 6) engages with the teeth of the satellite wheel 192.
    The operation of the mechanism according to the embodiment of FIG. 6 is described here. When the second regulator member 02 is blocked (first mode of operation), the torque delivered by the barrel 1 immobilizes the second finishing train RF2 (in the case of a balance-sprung member, the escape wheel bears on anchor). The lower wheel 197 and the intermediate wheel 207 are then immobile. The torque of the barrel 1 will rotate the first satellite carrier 190 which drives the planet or satellites 193 rolling on the lower conical wheel 198 and rotates the upper conical wheel 195. The upper conical wheel 195 transmits the movement to the second conical toothed wheel 205 of the first differential D1 via the upper wheel 196. On the one hand, the second conical gear 205 transmits energy to the first regulating member 01 via the first finishing train RF1. On the other hand, the second conical gear 205 drives the planet or satellites 203 rolling on the first stationary conical gear 209, thus causing the second planet carrier 200 to rotate in the same direction of rotation as the second conical gear 205. The speed ratio between the speed of the second satellite gate 200 and the speed of the first satellite gate 190 is 1 (with the sign). The rotational speed of the second satellite gate 200 is one turn per hour, imposed by the first regulator member 01 and the first finishing train RF1.
    When the first regulator member 01 is blocked (second mode of operation), the torque delivered by the barrel 1 immobilizes the first finishing gear RF1 as well as the upper wheel 196 and the upper wheel 206. The torque of the barrel results in rotating the first satellite gate 190 which drives the planet or satellites 193 rolling on the upper conical wheel 195 stationary, the planet or satellites 193 driving the lower conical wheel 198 in rotation. The rotation of the lower conical wheel 198 drives the lower wheel 197 which drives the first differential D1 in rotation through the first conical gear 209. The second conical gear 205 will, on the one hand, transmit the energy to the first regulator member 01 via the first finishing train RF1 and, secondly, force the satellite or satellites 203 to roll on the first conical gear 209, immobile, thus causing the second satellite carrier 200 to rotate in the same direction of rotation as the second conical gear 205. The overall speed ratio between the speed of the second satellite carrier 200 and the speed of the first satellite carrier 190 is equal to the speed ratio of the second drive train RV2 (at the sign near). The rotational speed of the second satellite carrier 200 is one revolution per hour, imposed by the second regulating member 02 and the second finishing train RF2.
    The mechanism according to the embodiment of FIG. 6 thus makes it possible to modulate the torque delivered by the barrel 1 for the second mode of operation, by modifying only the gear ratio of the second gear train RV2, without any other modification of the mechanism. This amounts to changing the gear consisting of the lower wheel 197 and the first conical gear 209 to obtain a gear ratio or multiplier, depending on the desired application for this second mode of operation.
    FIG. 7 illustrates an embodiment of the mechanism according to the configuration of FIG. 5. In particular, the second differential D2 comprises a first satellite gate 300 rotatable about an axis 301. The first toothing of cylinder 1a engages a toothing of the satellite gate 300. One or more satellites 303, each guided by rotation on the satellite gate 300 about a satellite axis 304. A pinion 302, integral and coaxial with a wheel 305, is pivotally mounted on the axis 301 and meshes with the planet or satellites 303. An upper crown 306 is pivotally mounted on the axis 301. The upper ring 306 has an internal toothing 306 'meshing with the satellite or satellites 303. The upper ring 306 also has an external toothing 306 ".
    The first differential D1 comprises a second satellite gate 400 rotatable about a satellite gate axis 401, on which pivots one or more satellites 403 mounted around a satellite axis 404 (substantially parallel to the axis 401). ). A pinion 402 is pivotally mounted on the axis 401 and meshes with the planet or satellites 403. An upper pinion 405 and an upper wheel 406 are mounted on the pinion 402. A ring 407, pivotally mounted about the axis 401, has an internal toothing 407 'and an external toothing 407 ", the internal toothing 407' meshes with the planet or satellites 403. The first drive train RV1 comprises the upper crown 306, the upper pinion 405 and the upper wheel 406 with which the The first work train RV2 comprises the wheel 305, the second satellite carrier 400 and the crown 407, the second work train RF1 engaging with the external toothing 407 "of the crown 407. .
    In the first mode of operation, the second regulator member 02 is blocked. The second finishing train RF2 and the crown 407 are stationary. The torque of the cylinder 1 rotates the first satellite carrier 300. At the second differential D2, no element is blocked and the power of the cylinder can be transmitted to the first differential D1 via the wheel 305 and the external toothing 306 "of the upper ring 306 of the second differential D2 to the second satellite gate 400 and to the upper gear 405.
    The rotational speed of the second satellite gate 400 is one turn per hour, imposed by the first regulator member 01 and the first finishing gear RF1.
    In the second mode of operation, the first regulating member 01 is blocked and the first finishing gear RF1 as well as the upper gear 405, the upper wheel 406, the pinion 402 and the upper ring 306 are stationary. The torque of the barrel 1 drives in rotation the first satellite gate 300 which forces the planet or satellites 303 to roll on the internal toothing 306 ", thus driving the pinion 302 in rotation.The movement is transmitted to the second satellite gate 400 of the first differential D1 by the wheel 305. In its movement, the second satellite gate 400 will force the satellite or satellites 403 to roll on the pinion 402, immobile, thus driving the ring 407 in rotation in the same direction of rotation as the second satellite gate 400. The ring 407, via its external toothing 407 ", will transmit the energy to the second regulating member 02 via the second finishing train RF2.
    The rotational speed of the second satellite gate 400 is one turn per hour, imposed by the second regulating member 02 and the second finishing gear RF2.
    The speed ratio between the speed of the crown 407 and the speed of the first satellite door 300 is equal to the overall speed ratio of the second differential D2 in the second operating mode, times the speed of the second drive train RV2 , times the overall speed ratio of the first differential D1 in the second mode of operation. The speed of the second finishing train RF2 can therefore be sized according to the speed of the second drive train RV2 and the overall speed ratio of the first differential D1 in the second operating mode.
    The arrangement of the mechanism according to the embodiment of FIG. 7 makes it possible to modulate the torque delivered by the barrel 1, for the second mode of operation, by modifying the speed ratio of the second differential D2, and / or the speed ratio of the drive train RV2. This amounts to changing the satellite or satellites 303, the pinion 302, possibly the internal toothing 306 'of the upper ring 306, and / or the wheels 305 and 400 to obtain a speed ratio according to the desired application for this second mode of operation. The arrangement of the mechanism according to the embodiment of FIG. 7 offers the advantage of having no play at the level of the display of the minutes which is achieved by a shaft 408, on the axis 401 and secured to the second satellite door 400.
    In general, several types of gear trains can be used to make the second differential D2 and / or the first differential D1 and satisfy this arrangement, be it bevel gears or planes, of basic reason equal to 1 or -1 (usual cases of the differentials), or other values by suitably adapting the ratios as well as the inputs / outputs of these differentials. It is also conceivable to have, for a constructive solution, a second differential D2 different from the first differential D1, and therefore any combination of differentials D1 and D2 to achieve this adaptation of the motive power.
    FIG. 8 schematically shows another possible configuration of the mechanism 100 according to the invention. This configuration is the same as that of FIG. Except that it does not include the second differential D2 and that the cylinder B engages directly with the first transmission chain RV1-D1-RF1-01 or with the second transmission chain RV2-D1-RF2- 02.
    FIG. 9 illustrates an embodiment of the mechanism according to the configuration of FIG. 8. The mechanism comprises a first differential D1 comprising a satellite gate 500 rotatable about an axis 501, on which can rotate one or more satellites 503 guided in rotation about a satellite axis 505. The satellite gate 500 supports the minute hand (not shown) and thus performs one revolution in one hour. A first sun gear 502 that can rotate about the axis 501 meshes, on the one hand, with the satellite or satellites 503 through a lower toothing 502 "and, on the other hand, with the drum drum 1 by the bias of the first toothing of cylinder 1a and an upper toothing 502 ". A second sun gear 504 rotatable about the axis 501 engages, on the one hand, with the planet or satellites 503 via an upper toothed wheel 504 'and, on the other hand, with a wheel 606. a sun gear 600 through a lower toothing 504 "In this configuration, the first sun gear 502 forms the first drive train RV1.
    The second drive train RV2 comprises a satellite gate 604 pivotally mounted about an axis 601 and on which can rotate one or more satellites 603 guided in rotation about a satellite axis 604 '. The satellite carrier 604 has a toothed wheel 604 "meshing with a wheel 605. A sun gear 600 rotatable about the axis 601 meshes, on the one hand, with the satellite or satellites 603 via an upper toothed wheel 602. and, secondly, with the second sun gear 504 of the first differential D1 through a lower gear 606. A sun gear 607 is pivotally mounted about the axis 601 and meshes with the planet or satellites 603 by the intermediate of internal teeth 608 which is integral with the barrel shaft 609.
    In the first mode of operation, the second regulator member 02 is blocked. Under the effect of the torque delivered by the barrel spring on barrel 609, transmitted to the lower gear 606 via the train formed by the internal toothing 608, the planet or satellites 603 and the upper toothed wheel 602, then to the upper gear 504 ', the second finishing gear RF2 will stop. The barrel shaft 609 is then stationary. Under the effect of the engine torque exerted by the mainspring, the drum 1 will drive in rotation the first sun gear 502. The first sun gear 502, on the one hand, transmits the energy to the first regulating member 01 via the first work train RF1 and, secondly, force the planet or satellites 503 to roll on the upper gear 504 ", immobile, thus causing the satellite gate 500 to rotate in the same direction of rotation as the first sun gear 502. The speed of rotation of the satellite gate 500 is one turn per hour, imposed by the first regulating member 01 and the first finishing train RF 1. The speed ratio of the first drive train RV1 is none other than the ratio of the gearing between the first toothing of cylinder 1a and the upper toothing 502 ".
    In the second mode of operation, the first regulating member 01 is blocked and the first finishing wheel RF1 and the first sun gear 502 and the barrel drum 1 are stationary. The engine torque is then delivered by the barrel shaft 609, rotating in the opposite direction of the drum 1. The gear train formed by the internal toothing 608, the satellite or satellites 603 and the upper gear 602 corresponds to a train ordinary since the satellite gate 604 is blocked. This gear train carries a first gear ratio RV2a. The torque is then transmitted to the second sun gear 504 by the lower gear 606 by producing a second gear ratio RV2b. The overall speed ratio of the second drive train RV2 is therefore: RV2 = RV2a x RV2b (Equation 1).
    The direction of rotation of the planet or satellites 603, the upper toothed wheel 602 of the cylinder shaft 609 and the first and second sun wheels 502, 504 is indicated by the arrows in solid lines.
    In the variant of FIG. 9, the reassembly is achieved by acting on the satellite gate 604 via the wheel 605. The gear train formed by the internal toothing 608, the satellite or satellites 603 and the upper gear 602 is in this case used as a differential power distributor train.
    In the case where the first and the second regulating members 01 and 02 are stopped. The drum 1 and the sun gear 600 are therefore also immobile. By rotating the satellite gate 604 anti-clockwise, the satellite or satellites 603 will roll on the upper gear 602 clockwise and thus drive the barrel shaft 609 clockwise corresponding to the winding direction. The directions of rotation of the wheel 605, the toothed wheel 604 "and the barrel shaft 609 are indicated by the broken arrows The first and second sun wheels 502, 504 rotate in the same direction as in the second mode of rotation. operation.
    The gear of the first mode of operation is always under the action of a torque exerted by the drum and there is no play in the chain B - RV1 - D1 - RF1. It is the same in the gear of the second mode of operation due to the gearing forces at the planet or satellites 603 and the upper gear 602.
    The blocking of the satellite gate 604 can be realized in different ways, for example by a unidirectional gear (for example the wheel 605 and the toothed wheel 604 "), by ratchet (not shown), or by other means. appropriate.
    The mechanism according to the configuration of FIG. 9 makes it possible to modulate the torque delivered by the barrel 1, for the second mode of operation, by modifying only the speed ratio of the second drive train RV2, without any other modification of the mechanism. This amounts to changing either the gear ratio of the train formed of the lower gear 606 and the lower gear of the second sun gear 504 "(RV2b), that of the train formed by the internal toothing 608, or the satellites 603 , and the upper gear 602 (RV2a), or both trains to obtain a gear ratio according to the desired application for this second mode of operation.
    There is always a driving torque exerted on the lower gear 606 regardless of the operating mode envisaged, that is to say the first or the second mode of operation or during reassembly.
    Compared to the configuration of FIGS. 6 or 7, the transmission of energy to the first and second regulating members 01, 02 is more "direct". Indeed, in the first and second mode of operation, the gear trains are ordinary (fixed axes of rotation). The first differential D1 is only used to reconstruct the minute and the train placed under the barrel 1 is used in differential mode only during reassembly.
    In the configuration of FIG. 9 the differential D1 may be a flat differential gear. This configuration can also be adapted to put the RV2 train next to the barrel to reduce its thickness.
    Reference numbers used in fig.
    [0080] 01 first regulator member 02 second regulator member f1 first frequency f2 second frequency D1 first differential D2 differential MH time setting device R reassembly RV1 first drive train RF1 first work train RV2 second drive train RF2 second gear wheel T barrel drum 1, B barrel 1a first barrel toothing 1b second barrel toothing 1c toothing reassembly 1 d, A barrel shaft 2 second moving 2a second wheel 2b second gear 3 third moving 3a third gear 3b third wheel 4 first movable 4a first wheel 4b first gear 9 9 planetary first planet door 10a first planetary gear 10b first planetary geared bevel gear 11 satellite 12 second planetary gear 12a second planetary geared bevel gear 12b second planetary gear 15, S shaft output 20 axis of rotation of the mobile 2 30 axis of rotation of the mobile 3 40 a xe rotation of the mobile 4 50 axis of rotation of the satellite 90 axis of the satellite door 111 axis of rotation of the cylinder 190 first satellite door 191 axis 192 satellite wheel 193 satellite 194 satellite axis 195 conical upper wheel 196 upper wheel 197 lower wheel 198 lower conical wheel 200 second satellite door 201 satellite door axis 203 satellite 204 satellite axis 205 second conical gear wheel 206 upper wheel 207 intermediate wheel 208 lower wheel 209 first conical gear 300 first satellite carrier 301 axis 302 gear 303 satellite 304 satellite 305 wheel 306 upper crown 306 'internal toothing 306' external toothing 400 second satellite door 401 satellite door pin 402 pinion 403 satellite 404 satellite pin 405 upper pinion 406 upper wheel 407 crown
    权利要求:
    Claims (18)
    [1]
    407 'internal toothing 407' external toothing 408 shaft 500 satellite door 501 axis 502 first sun gear 502 'upper toothing of first sun gear 502' lower toothing of first sun gear 503 satellite 504 second sun gear 504 'upper gear to second sun gear 504' lower gear second sun gear 505 600 planet spindle 602 upper gear 603 satellite 604 satellite carrier 604 'satellite axis 604' gear wheel 605 wheel 606 lower gear 607 sun gear 608 internal toothing 609 barrel shaft
    A mechanism (100) for a watch movement, comprising: a power source (1), a first drive train (RV1) connecting the power source (1) to a first regulator member (01), a driving train (RV2) connecting the energy source (1) to a second regulating member (02), the second regulating member (02) having a different operation from the first regulating member (01), an output moving member (S) ) serving to cause the display of the time, able to be kinematically connected to both the first drive train (RV1) and the second drive train (RV2), the mechanism (100) being arranged so that the operation of the first regulating member (01) or the operation of the second regulating member (02) enables the driving of the time display with the same speed of rotation.
    [2]
    2. The mechanism (100) according to claim 1, wherein the first regulating member (01) has a first frequency (f 1) and the second regulating member (02) has a second frequency (f2) different from the first frequency ( f 1).
    [3]
    3. The mechanism (100) according to one of the preceding claims, wherein the energy source (1) cooperates directly with the first drive train (RV1) and with the second drive train (RV2).
    [4]
    4. The mechanism (100) according to one of the preceding claims, comprising a first differential (D1), the first drive train (RV1) and the second drive train (RV2) being kinematically connected to the output mobile ( S) via the first differential (D1).
    [5]
    5. The mechanism (100) according to claim 4, comprising a second differential (D2), the energy source (1) cooperating with the first drive train (RV1) and with the second drive train (RV2) through the second differential (D2).
    [6]
    6. The mechanism (100) according to one of the preceding claims, wherein said energy source comprises a barrel provided with a drum (1) and a barrel shaft (1 d) between which is mounted a spring motor, the drum (1) having a first toothing (1a).
    [7]
    7. The mechanism (100) according to one of the preceding claims, wherein the first drive train (RV1) cooperates with the drum (1) via the first toothing (1a) and the second gear train. drive (RV2) cooperates with the barrel shaft (1 d).
    [8]
    8. The mechanism (100) according to claim 7, wherein the barrel shaft (1d) is secured to, or made integral with, a second toothing (1b), and wherein the second drive train (RV2). cooperates with the second toothing (1b).
    [9]
    9. The mechanism (100) according to one of the preceding claims, comprising a first finishing train (RF1) kinematically connecting the first drive train (RV1) to the first regulating member (01) and a second finishing train (RF2). ) kinematically connecting the second drive train (RV2) to the second regulating member (02).
    [10]
    10. The mechanism (100) according to one of the preceding claims, further comprising a locking device for simultaneously stop the operation of one of the first and second regulating member (01, 02) and release the march the other of the first and second regulating members (01, 02).
    [11]
    The mechanism (100) of claim 10, wherein the first differential (D1) is configured to allow one of the first and the second drive train (RV1, RV2) to travel while the other among the first and second drive train (RV1, RV2) is stopped.
    [12]
    12. The mechanism (100) according to one of claims 1 to 9, wherein the first regulating member (01) and the second regulating member (02) operate simultaneously, and wherein said mechanism is configured to allow the simultaneous operation of the first drive train (RV1) and the second drive train (RV2).
    [13]
    13. The mechanism (100) according to one of claims 4 to 12, wherein the first differential (D1) comprises one or more planet gears (11, 203) and a sun gear (10, 200) having a first conical gear (10b, 205) cooperating with the first drive train (RV1) and a second conical gear (12b, 209) cooperating with the second drive train (RV2).
    [14]
    The mechanism (100) according to claim 13, wherein said one or more planet gears (11,203) is pivotally mounted about a satellite axis (50,204) and the first and second conical gears (10b, 12b). ) are pivotally mounted about a satellite gate axis (90, 201) substantially perpendicular to the satellite axis (50, 204).
    [15]
    15. The mechanism (100) according to one of claims 4 to 12, wherein the first differential (D1) comprises one or more satellites (403) pivotally mounted about a satellite axis (404) and a ring gear (407). pivotally mounted around a satellite gate axis (401) substantially parallel to the satellite axis (404); the first differential (D1) further comprising an upper wheel (406) pivotally mounted on the satellite gate axis (401).
    [16]
    16. The mechanism (100) according to claims 9 and 15, wherein the first finishing train (RF1) cooperates with the upper wheel (406) and the second finishing train (RF2) cooperates with the ring (407).
    [17]
    17. The mechanism according to one of claims 1 to 16, wherein the first and the second regulating organ (01,02) belong to the group comprising mechanical oscillators, piezoelectric oscillators, quartz electronic oscillators, oscillators tuning fork and electrical switches (switch).
    [18]
    18. The mechanism according to claim 17, wherein the first regulating member (01) and the second regulating member (02) are mechanical oscillators comprising a balance and a spiral spring.
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    同族专利:
    公开号 | 公开日
    CH712597B1|2020-08-14|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    CH698622B1|2004-12-21|2009-09-15|Gfpi S A|Movement for mechanical timepiece, has differential gear assuring kinematic connection between finishing gear-train and escapements i.e. tourbillons, of time base, where upper and lower wheels respectively interlock escapements|
    EP1708048A1|2005-03-30|2006-10-04|Montres Breguet S.A.|Watch comprising at least two regulation systems|
    CH704063A1|2010-11-09|2012-05-15|Complitime Sa|Timepiece.|
    EP2570870A1|2011-09-15|2013-03-20|The Swatch Group Research and Development Ltd.|Timepiece with permanently coupled oscillators|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    CH00784/16A|CH712597B1|2016-06-20|2016-06-20|Mechanism for a watch movement comprising two regulating organs.|CH00784/16A| CH712597B1|2016-06-20|2016-06-20|Mechanism for a watch movement comprising two regulating organs.|
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