EP4273634A1 - Regulierorgan für uhrwerk - Google Patents

Regulierorgan für uhrwerk Download PDF

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Publication number
EP4273634A1
EP4273634A1 EP22171307.6A EP22171307A EP4273634A1 EP 4273634 A1 EP4273634 A1 EP 4273634A1 EP 22171307 A EP22171307 A EP 22171307A EP 4273634 A1 EP4273634 A1 EP 4273634A1
Authority
EP
European Patent Office
Prior art keywords
mobile
balances
regulating member
oscillator
balance
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP22171307.6A
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English (en)
French (fr)
Inventor
Jean-François Mojon
Xavier Clement
Sébastien Dordor
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Chronode Sa
Original Assignee
Chronode Sa
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Chronode Sa filed Critical Chronode Sa
Priority to EP22171307.6A priority Critical patent/EP4273634A1/de
Priority to PCT/IB2023/054547 priority patent/WO2023214300A1/fr
Publication of EP4273634A1 publication Critical patent/EP4273634A1/de
Pending legal-status Critical Current

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    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/26—Compensation of mechanisms for stabilising frequency for the effect of variations of the impulses

Definitions

  • the present invention relates to a regulating member for a watch movement.
  • the invention also relates to a watch movement comprising the regulating member and a timepiece comprising such a movement.
  • mechanical watches include a watch movement whose oscillation frequency of the regulating organ varies between 3Hz and 5Hz. This oscillation frequency can, however, go beyond 5Hz in order to increase the precision of the watch. That being said, a low-frequency regulating organ can bring several advantages, in particular an increase in the power reserve and a simplification of the watch movement.
  • CH75063 discloses an escapement having a reversing wheel arranged to impart the impulse to the balance via a gear in order to reduce the number of oscillations of the balance so that the latter oscillates at a frequency of 0.5 Hz.
  • the inertia of the balance In order to maintain an acceptable quality factor for a low frequency regulating organ, the inertia of the balance must be increased compared to a mechanical movement equipped with a higher frequency oscillator. frequency. This increase in inertia has the main disadvantage of increasing sensitivity to angular accelerations.
  • An aim of the present invention is therefore to propose a regulating member canceling or, at least, reducing the sensitivity to angular accelerations.
  • Another aim of the present invention is to propose a simplified watch movement comprising a low frequency regulating member.
  • An additional aim of the present invention is to propose a method of adjusting the frequency of the oscillator of the regulating member.
  • the regulating member comprises an oscillator comprising at least a first and a second balance wheel. Each balance wheel includes a flywheel and a balance axis.
  • the oscillator comprises at least one elastic member intended to maintain its oscillations.
  • This oscillator further comprises a gear train comprising at least two mobiles.
  • the flywheel of each balance wheel is integral in rotation with a mobile part of the gear train.
  • the gear train is arranged to connect the flywheels of the first and second balance wheels together by a desmodromic connection so that the respective oscillations of the first and second balance wheels are in phase opposition.
  • the regulating member further comprises an escapement comprising at least one escapement wheel and at least one anchor intended to regulate said at least one escapement wheel and to maintain the oscillations of the oscillator.
  • the regulating member comprises at least three balance wheels each comprising a flywheel.
  • the respective oscillations of two pendulums following each other in the kinematic chain of the at least three pendulums are in phase opposition.
  • the gear train includes more than two mobiles.
  • the balance axes of the first and second balance wheels are coaxial.
  • the balance axes of the first and second balance wheels are parallel while their respective flywheels are arranged to oscillate in two parallel planes.
  • the flywheels of the first and second balances are substantially included in the same plane.
  • the balance axes of the first and second balances are contained in intersecting planes.
  • the flywheel of each of the first and second balances comprises a plurality of disjoint serge segments, for example two, three, or even four serge segments, together forming the serge of each flywheel the along respective circles. These circles respectively define a first and a second disk intersecting or intersecting in order to form an overlapping zone or an intersection zone.
  • the overlapping zone has the shape of a lens.
  • This lens is preferably a symmetrical lens.
  • the intersection zone is a straight line segment.
  • At least one of the first and second balances does not include said at least one elastic member.
  • At least one elastic member is mounted on an intermediate mobile of the gear train.
  • the inertia of the intermediate mobile is at least five times, preferably at least ten times, or even at least twenty times lower than the inertia of any of the balances of the oscillator.
  • At least one of the first and second balances and/or an intermediate mobile of the gear train comprises an even number, preferably two, of elastic members wound in opposite directions.
  • the escapement only comprises one anchor arranged to cooperate with one of the first and second balances and the escapement mobile.
  • the escapement comprises two anchors arranged to cooperate, on the one hand, with respectively the first and second balances and, on the other hand, with a single escapement mobile, or with respectively a first and a second escape mobile.
  • the escapement comprises a first and a second half-anchor arranged to cooperate with the first and second balance wheels respectively.
  • the first and second half-anchors respectively comprise a first pallet and a second pallet arranged to cooperate with a single exhaust wheel or with a first and a second exhaust wheel respectively.
  • the escapement comprises an anchor arranged to cooperate with one of the first and second balances.
  • the anchor comprises a first pallet arranged to cooperate with a first escape wheel and a second pallet arranged to cooperate with a second escape wheel.
  • the escapement comprises an anchor arranged to cooperate with an intermediate mobile of the gear train and an exhaust mobile.
  • Another aspect of the invention relates to a method of adjusting the frequency of the oscillator of the regulating member.
  • the method consists of determining, firstly, the inertia of all the balances and the restoring torque of said at least one elastic member of the oscillator.
  • This method also consists, in a second step, of replacing at least one of the mobiles of the gear train, preferably an intermediate mobile, with a mobile of different inertia so as to obtain a ratio between the inertia of the gear train. set of balances and the return torque of said at least one elastic member defined by the desired frequency of the oscillator.
  • Another aspect of the invention relates to a method of adjusting the frequency of the oscillator of the regulating member according to an alternative solution.
  • the method consists of determining, initially, the inertia of all the balances and the restoring torque of said at least one elastic member.
  • This method also consists, in a second step, of replacing at least the mobiles of the train of gears, preferably an intermediate mobile with a mobile of different pitch diameter from the replaced mobile so as to obtain a ratio between the inertia of all the balances and the return torque of said at least one elastic member defined by the frequency desired oscillator.
  • Another aspect of the invention relates to a method of adjusting a watch movement comprising a driving source, in particular a barrel, and the regulating member.
  • the method consists of determining, firstly, the torque supplied by the driving source to the escapement wheel, the inertia of all the balances of the oscillator and the return torque of said at least one hairspring.
  • This method also consists of replacing, in a second step, at least one mobile of the gear train, preferably an intermediate mobile, by a mobile of different inertia and/or of different pitch diameter so as to obtain a defined ratio between the inertia of all the balances of the oscillator and the restoring torque of said at least one elastic member as well as a defined ratio between the sustaining power of the oscillations of the oscillator and the power available to the wheel exhaust.
  • the term “oscillator” means a resonator comprising, on the one hand, several balances and, on the other hand, a cog arranged to engage with the balances so as to make these balances dependent on each other.
  • the term “regulating member” means an assembly comprising the oscillator and a counting member, in particular an escapement.
  • the watch movement 10 has a simplified construction thanks to a low-frequency regulating member with a double-spiral balance 22a, 22b, which will be described later, configured to oscillate at a frequency lower than 1.5 Hz.
  • the power reserve can be considerably increased, particularly if achieving high chronometric performance is not a priority.
  • the simplified watch movement comprises a plate 12 on which a barrel 14 is mounted, an escapement 15 comprising an escape wheel and a kinematic connection 19 connecting the barrel 14 to the pinion of the escape wheel.
  • the kinematic link 19 has fewer than three mobiles.
  • this kinematic connection only comprises a mobile 19 engaged on the one hand with the ratchet of the barrel 14 and, on the other hand, with the pinion of the escape wheel.
  • the mobile 19 therefore replaces the center wheel, the middle wheel and the second wheel of a traditional movement.
  • the kinematic connection comprises no less and no more than two meshing mobiles together.
  • One of the two mobiles is engaged with the barrel ratchet while the other of the two mobiles is engaged with the pinion of the escape wheel.
  • the simplified watch movement has the advantage of providing a new architecture with possibilities for identifying the unique product due to the fact that the geometric constraints, for example the center distances, are very different from traditional movements. Furthermore, the simplification of the movement makes it possible to increase the overall efficiency by reducing the number of gears.
  • a seconds indicator member 50 can be mounted on the axis of the escape wheel.
  • the mobile 19 can directly display the minutes.
  • the gear ratio between the barrel and the mobile 19 is therefore chosen so that the latter can perform one complete rotation per hour.
  • a minute indicator member 52 can for example be mounted on the axis of the mobile 19.
  • barrel 14 can display the time.
  • an hour indicator member 54 can be mounted on the shaft of the barrel 14.
  • the production of a simplified watch movement is only possible by the implementation of a low frequency regulating organ.
  • the inertia of the balance must be increased compared to a mechanical movement equipped with a higher frequency oscillator.
  • This increase in inertia has the main disadvantage of increasing sensitivity to angular accelerations.
  • the oscillator of the regulating member comprises at least two balances coupled in phase opposition according to different embodiments, that is to say that a hairspring is associated with each of the two balancers so that one of the hairsprings is in a contraction phase while the other of the hairsprings is in an expansion phase.
  • the phase opposition can be achieved by mounting on one of the balances of the oscillator two hairsprings wound in the opposite direction so that one of the two hairsprings is in a contraction phase when the other of the two spirals is in a phase of expansion.
  • the oscillator 22 comprises a first and a second sprung balance 22a, 22b arranged in the same plane.
  • Each balance spring 22a, 22b comprises a flywheel 24a, 24b, a balance spring 32a, 32b and a balance shaft 34a, 34b.
  • the flywheel includes serge segments 28a, 28b and balance arms 26a, 26b connecting the serge segments to the balance shaft.
  • each hairspring 32a, 32b is connected to the respective balance axis by means of, for example, a ferrule 36a, 36b ( figure 5 ) driven on the axis while the other end is connected for example to a eyebolt mounted on a eyebolt holder itself secured to a bridge or fixed cock (not illustrated) in relation to the plate 12 of the watch movement 10 .
  • the oscillator may include an elastic member other than a conventional flat spiral spring, for example a cylindrical balance spring, a hemispherical or spherical balance spring or even a conical balance spring.
  • the hairspring can also have several turns according to a variant.
  • the oscillator can also include an elastic member not resembling a hairspring to fulfill the function of returning the balance.
  • the first and second sprung balances 22a, 22b of the oscillator 22 are connected by a gear train 40 in order to drive these sprung balances by a desmodromic connection so that the flywheel 24a of one of the two sprung balances 22a, 22b can oscillate in phase opposition to the flywheel 24b of the other of the two sprung balances.
  • the balance spring 32a of one of the two balance springs 22a, 22b is in an expansion phase while the balance spring 32b of the other of the two balance springs 22a, 22b is in a phase of expansion. contraction, which has the consequence of driving the respective flywheels 24a, 24b in an opposite direction.
  • This particular arrangement of the two hairsprings 32a, 32b makes it possible to cancel or, at least, reduce the sensitivity of the oscillator 22 to angular accelerations.
  • the gear train 40 ensuring the desmodromic connection between the two sprung balances 22a, 22b, comprises a first mobile 42 secured to the balance axis 34a of the balance of one of the two sprung balances 22a, 22b, a second mobile 44 secured to the balance axis 34b of the balance of the other of the two sprung balances 22a, 22b and two intermediate mobiles 46, 48 engaged with respectively the first and second mobiles 42, 44.
  • the reports and the number of gears have been determined so that the first and second flywheels 24a, 24b of the respective sprung balances 22a, 22b can oscillate in opposition to phase.
  • the flywheel 24a, 24b of each sprung balance 22a, 22b comprises four arms 26a, 26b separated by an angle of 90° from each other.
  • Each arm 26a, 26b extends from the respective balance axis 34a, 34b, in a radial direction, to a distal part 28a, 28b.
  • the thickness of each arm 26a, 26b increases from the balance axis to the corresponding distal part.
  • the distal parts of the first and second flywheels 24a, 24b each form four disjoint serge segments 28a, 28b along respectively a first and a second circle 25a, 25b as shown in Fig. Figure 4 .
  • Each of the four disjoint serge segments 28a, 28b of each balance 24a, 24b extends along an arc of a circle comprised for example between 20° and 50° and preferably along an arc of a circle comprised between 30 ° and 40°.
  • the flywheel of each sprung balance may have only two or three arms.
  • the serge segment associated with each arm will be larger so that the inertia of each balance remains constant.
  • each discontinuous serge segment of the flywheel can extend along an arc of a circle greater than 45° in the case where each balance wheel has three arms, or even greater than 60° in the case where each balance wheel has only two arms.
  • a weight 30a, 30b in the form of screws are screwed into each serge segment 28a, 28b, for example in a radial direction, in order to be able to modify the inertia of the flywheel 24a, 24b of each sprung balance to adjust their oscillation frequency.
  • the center distance between the two balance axes 34a, 34b respectively of the first and second sprung balances 22a, 22b is reduced so as to limit the differences in the influence of acceleration between the first and second flywheels 24a, 24b.
  • This configuration also has the advantage of reducing the bulk of the balances (surface).
  • the dimensions of the two flywheels are substantially identical. These two flywheels define two discs with an overlapping zone 29a resembling a symmetrical lens as illustrated in Figure 28 .
  • the diameter D1 of one of the flywheels 24a, 24b is less than the diameter D2 of the other flywheel.
  • the first diameter D1 represents for example less than 80% of the second diameter D2.
  • the overlapping zone 29b resembles an asymmetrical lens.
  • the oscillations of the flywheels 24a, 24b of the sprung balances 22a, 22b are synchronized in phase opposition so that the serge segments 28a of the flywheel 24a of one of the two sprung balances 22a, 22b never comes into contact with the serge segments 28b of the flywheel 24b of the other of the two sprung balances 22a, 22b.
  • the oscillator 22 comprises a first and a second spiral balance 22a, 22b mounted coaxially.
  • the first and second sprung balances 22a, 22b are interconnected by a gear train 40 so that the flywheel 24a of one of the two sprung balances 22a, 22b can oscillate in phase opposition to the flywheel. of inertia 24b of the other of the two sprung balances to cancel or, at least, reduce the sensitivity of the oscillator 22 to angular accelerations.
  • the first and second sprung balance are arranged so that their respective flywheel oscillates in two parallel planes with their respective axis parallel to each other.
  • the gear train 40 comprises a first mobile 42 secured to the balance axis 34a of the first sprung balance 22a, a second mobile 44 secured to the balance axis 34b of the second sprung balance 22b as well as a gear train intermediate.
  • the intermediate cog comprises a third mobile 45 engaged with the first mobile 42, a fourth mobile 46 engaged with the second mobile 44, a fifth mobile 47 engaged with the fourth mobile 45 as well as a lower mobile 48 and an upper mobile 49 mounted coaxially so that the lower and upper mobiles 48, 49 engage respectively with the fifth mobile 47 and the third mobile 45.
  • the flywheel 24a, 24b of each sprung balance 22a, 22b comprises four arms 26a, 26b separated by an angle of 90° relative to each other and having the same characteristics of the arms of the two sprung balances of the regulating organ illustrated in particular in figure 2 .
  • the number of arms can be different from four.
  • Each flywheel 24a, 24b can for example comprise only two or three arms as mentioned above.
  • the oscillator 22 comprises a first and a second sprung balance 22a, 22b mounted so that their respective balance axes are concurrent.
  • the first and second axes form an angle between them substantially equal to 45° according to the Figure 10 although this angle can vary significantly depending on execution variants, for example between 30° and 60°.
  • the oscillator comprises three balances each comprising a flywheel 24a, 24b, 24c, each defining a disk.
  • the balance wheels are arranged so that a first and a second disk a third disk according to a first and a second intersection zone 29a which are rectilinear.
  • the advantage of this embodiment lies in particular on the simplified gear train so that the flywheels 24a, 24b respectively of the first and second sprung balances 22a, 22b can oscillate in phase opposition since this gear train only includes two mobiles 42, 44 with appropriate teeth, conical for example, in direct engagement.
  • the flywheel 24a, 24b of each sprung balance comprises four arms 26a, 26b separated by an angle of 90° from each other and having the same characteristics of the arms of the two sprung balances of the regulating organ illustrated in particular in figure 2 .
  • Each balance 24a, 24b can only have two or three arms according to a variant of execution as already specified previously.
  • the oscillations of the flywheel 24a of one of the two sprung balances 22a, 22b are synchronized in phase opposition with respect to the oscillations of the flywheel flywheels 24b of the other of the two sprung balances 22a, 22b so that the serge segments 28a, 28b of the respective flywheels 24a, 24b never come into contact.
  • the regulating member 20 according to the invention can be implemented according to different configurations of the oscillator and the exhaust according to schematic figures 11 to 24 in order to transmit the oscillation frequency of the regulating member 20 to the connection kinematic 19 connecting the barrel 14 to the pinion of the escape wheel 16, preferably via a single mobile 19 according to the schematic representation of the figure 1 .
  • the escapement may include one or more anchors, for example of the Swiss anchor type.
  • the escapement may comprise any other device acting between the oscillator and an escape wheel, for example a detent or coaxial escapement.
  • anchor is therefore to be taken in the present application in the broad sense, designating any organ intended to cooperate between the regulating organ and the exhaust mobile(s).
  • the regulating member 20 comprises an oscillator 22 comprising two sprung balances 22a, 22b, for example the oscillator 22 illustrated in figure 2 .
  • the first and second flywheels 24a, 24b are arranged to oscillate in opposition to phase.
  • the escapement includes a single escapement anchor 17, for example a Swiss anchor.
  • the anchor 17 comprises an entry vane 170 and an exit vane 172 arranged to cooperate with the escape wheel 16 in a conventional manner in order to transmit the oscillations of the flywheel 24a of a single sprung balance 22a of the regulating member 20 to the escape wheel 16 so that the rotation of the escape wheel 16 takes place according to the oscillations of the flywheel 24a.
  • the anchor 17 comprises a fork 179 arranged to cooperate with a plate pin of the balance axis.
  • the flywheel 24a of one of the sprung balances is connected to the flywheel 24b of the other of the sprung balances by a gear train with an even number of references 42, 44, 46, 48 of so as to reverse the direction of rotation of the balancers.
  • Each hairspring 22a, 22b comprises a hairspring 32a, 32b wound in the same direction so that during the course of the movement, the hairspring of one of the hairspring balances is in a contraction phase for that the hairspring of the other balance spring is in an expansion phase, that is to say in phase opposition.
  • the regulating member 20 has an architecture comparable to that of the Figure 11 , with the difference that the first and second sprung balances 22a, 22b cooperate respectively with a first and a second anchor 17a, 17b, which cooperate with the same escape wheel 16.
  • the first anchor 17a comprises an entry pallet 170a, and an outlet pallet 172a arranged to cooperate with the teeth of the escape wheel 16 while the second escape anchor 17b comprises an entry pallet 170b and a output pallet 172b arranged to cooperate with the teeth of the escape wheel 16 alternating with the first escape anchor 17a.
  • the first and second escape anchor 17a, 17b are arranged so that the entry and exit pallets of each anchor can cooperate with different teeth.
  • the exit pallet 172a of the first anchor 17a is arranged opposite the entry pallet 170b of the second anchor 17b while the entry pallet 170a of the first anchor and the exit pallet 172b of the second anchor 17b are spaced apart from each other in order to cooperate with teeth of the escape wheel 16 which are separated by an angle less than 180° passing through the center of the wheel 16.
  • the escape wheel exhaust 16 has for this purpose at least 20 teeth while one fork 179a, 179b of each anchor is arranged to cooperate with the plate pin 35a of the plate 35 of the axis of the corresponding sprung balance 22a, 22b.
  • the escape wheel with less than 20 teeth, for example 15 teeth, can also be used under certain conditions.
  • the anchors 17a, 17b work symmetrically.
  • There figure 25a has a tooth of the escape wheel 16 on the rest plane 176 of the entry pallet 170a of the first anchor 17a and another tooth of the escape wheel 16 on the rest plane 176 of the outlet pallet 172b of the second anchor 17b.
  • the angle ⁇ defined by the points of contact between the respective rest planes 176 of the entry pallet 170a and the exit pallet 172b respectively of the first and second anchor 17a, 17b with respectively a first and a second tooth of the escape wheel 16 and through the center of the escape wheel 16 is less than 180° and is preferably located between 130° and 160°.
  • the operating principle of the exhaust 15 of the figure 25a requires that the adjustments be made so that the operating phases of the anchors are carried out simultaneously.
  • the impulse plane of the output paddle 172a of the first anchor 17a and the impulse plane of the output paddle 172b of the second anchor 17b are removed so that the distal part of the output paddles 172a, 172b of the first and second anchor 17a, 17b forms an angle of approximately 90° with the resting plane 176 of the pallet.
  • This specific shape of the distal part of the aforementioned pallets has the advantage of avoiding the constraint imposed by the operating phases of the first and second anchors which must be carried out in a manner simultaneous according to the embodiment illustrated in figure 25a .
  • the pallets are however sized so that the pulling function is fulfilled.
  • the dimensions of the pallets are such that the teeth of the escape wheel rest well on the rest planes of the truncated pallets so as to ensure locking of the anchor in a conventional manner and that the release phase on this pallet is not longer than on the non-truncated pallet of the other anchor in order to avoid a loss of energy during the impulse.
  • This embodiment has the advantage of facilitating the self-starting of the exhaust 15.
  • the exhaust uses the operating principle described in EP2923242A1, the content of which is incorporated by reference in the present application, so as to avoid hyperstatism of the exhaust 15 according to the figure 25a and the residual sensitivity of the exhaust adjustment according to the figure 25b .
  • the tooth resting on the inlet or outlet pallets must be positioned very precisely in relation to the end of the resting plane of the pallets so that the exhaust release and impulse phases take place correctly.
  • a conventional lever escapement typically requires final adjustment of the inlet and outlet vane positions. This adjustment is generally long and delicate because it can strongly influence the performance of the exhaust.
  • Exhaust 15 according to figure 25c is similar to the exhaust of the figure 25a by the arrangement of a first and a second anchor 17a, 17b arranged to cooperate with an escape wheel 16.
  • the escape wheel nevertheless differs in the profile of its teeth.
  • each tooth of the escape wheel 16 includes a driving plane 182 ( figure 25d ) oriented so that the contact between the input pallet 170a, 170b and the output pallet 172a, 172b of each anchor 17a, 17b and the escape wheel via the driving plane 182 creates a torque which tends to reduce the angle between the anchor and the reference axis V 1 , V 2 connecting the axes of the anchor and the balance for each of the first and second anchor 17a, 17b.
  • the present implementation provides a driving plan which means that the anchor will naturally arrive in an equilibrium position, because the driving plan is arranged to create a torque creating a movement towards the position of balance.
  • the driving plan can be located on one of the pallets of the first and second anchor while the escape wheel has conventional teeth.
  • the regulating member 20 has an architecture comparable to that of the Figure 12 , with the difference that one of the balances does not have a hairspring.
  • This balance includes a flywheel 24 secured to the first mobile 42. This engages with a gear train comprising two intermediate mobiles 46, 48 and the second mobile 44 secured to the sprung balance 22b.
  • the flywheel 24a is thus driven by a desmodromic connection to oscillate according to the oscillations of the sprung balance 22b but in the opposite direction.
  • the sprung balance 22b may have only one spiral or according to a variant not shown but similar to the Figure 14 , a pair of spirals wound in opposite directions to obtain phase opposition.
  • the flywheel 24a is thus driven by a desmodromic connection to oscillate according to the oscillations of the sprung balance 22b but in the opposite direction.
  • the sprung balance 22b comprises, for its part, a single hairspring or preferably two hairsprings 32a, 32b mounted coaxially and wound in opposite directions to obtain phase opposition.
  • the oscillator 22 of the regulating member 20 comprises three balances, namely two balance springs 22a, 22b as well as a balance without a balance spring.
  • This comprises a flywheel 24c secured to a mobile 43 of the gear train and is arranged to cooperate with the escape wheel 16 via an anchor 17.
  • the two sprung balances 22a, 22b are arranged at the end of the CC kinematic chain of the desmodromic connection of the oscillator 22 on either side of the balance without a hairspring.
  • the flywheels 24a, 24b rotate in the same direction thanks to the odd number of mobiles 43, 46, 47, 48, 49 of the gear train connecting the two sprung balances 24a, 24b.
  • the hairspring 32a of the hairspring balance 22a is therefore wound in the opposite direction relative to the hairspring 32b of the hairspring balance 22b to obtain phase opposition.
  • the respective oscillations of two rockers following each other in the CC kinematic chain of a regulating member comprising at least three rockers are in phase opposition.
  • the oscillator 22 comprises of the regulating member 20 also three balances, namely a central sprung balance 22c arranged to cooperate with the escape wheel 16 and two balances without a balance spring and which are arranged on either side of the central sprung balance.
  • This comprises two spirals 32a, 34 mounted coaxially and wound in opposite directions to obtain phase opposition.
  • the central sprung balance may have only one spiral. The oscillations of the flywheels 24a, 24b located on either side of the central sprung balance 22c occur according to the oscillations of the latter by the gear train.
  • the first and second sprung balances 22a, 22a of the regulating member 20 cooperate respectively with a first and a second escapement half-anchor 18a, 18b which cooperate with the same escape wheel 16.
  • the first half-anchor 18a comprises an entry pallet 180a while the second half-anchor 18b comprises an exit pallet 180b.
  • the operation of the escapement 15 is thus decoupled by producing two half-anchors each working with the plate pin of a balance shaft. In this case, the pulses are distributed between the first and second hairspring balances 22a, 22b of the oscillator 22.
  • the hairsprings 32a, 32b of the respective hairspring balances 22a, 22a are wound in the same direction in order to obtain opposition phase. According to a variant not shown, one of the balances does not have a hairspring while the other balance has a pair of hairsprings mounted in opposite phase.
  • the regulating member 20 has an architecture comparable to that of the Figure 17 with the difference that the first and second sprung balances 22a, 22b cooperate respectively with a first and a second escape wheel 16a, 16b via a first and a second anchor 17a, 17b according to the regulating member 20 of the Figure 18 or via a first and a second half-anchor 18a, 18b depending on the organ of the Figure 19 .
  • the hairsprings 32a, 32b of the respective hairspring balances 22a, 22a are also wound in the same direction in order to obtain phase opposition. According to a variant not shown, one of the balances does not have a hairspring while the other balance has a pair of hairsprings mounted in opposite phase.
  • the oscillator 22 of the regulating member 20 comprises a balance spring 22a and a balance wheel without a balance spring.
  • the regulating member comprises an escapement comprising, on the one hand, a first and a second escapement wheel 16a, 16b arranged to be driven in an opposite direction between them, and on the other hand, an anchor 17 arranged to cooperate with one of the balance wheels, for example the one without a hairspring, and with the two escape wheels.
  • the sprung balance 22a preferably comprises two balance springs mounted in opposition to phase. In a variant not shown, each balance wheel has a hairspring.
  • the first and second balance wheels of oscillator 22 are mounted in phase opposition and do not have a hairspring. These balances therefore only include a flywheel 24a, 24b.
  • the hairspring 32 is mounted on a mobile 48 of the gear train of the oscillator 22. Centering the hairspring in the gear train has the advantage of reducing the return effects compared to a hairspring at one of the ends of the gear train. the oscillator chain.
  • the flywheels 24a, 24b are then preferably free of spirals.
  • the inertia of the mobile 48 is at least five times, preferably at least ten times, or even at least twenty times lower than the inertia of any of the balances.
  • the gear train is arranged to give a back and forth movement to the mobile 48, which cooperates with the anchor 17 by means, for example, of a pin (not shown) secured to the mobile 48.
  • the mobile 48 can be larger or smaller than the mobiles 42, 44 secured respectively to the first and second balances 24a, 24b, so as to increase the sizing range of the balance-spring couplings and the amplitudes (the amplitude of the mobile- balance spring can be adapted to the ideal functioning of the escapement while the amplitude of the balance wheels can be adapted to their inertia).
  • the pitch diameter of the mobile 48 is greater than the pitch diameter of the respective mobiles 42, 44 of the first and second rockers 24a, 24b.
  • FIG. 23 Another example of a regulating organ is schematically illustrated by the Figure 23 .
  • This regulating organ is similar to the regulating organ of the Figure 22 with the difference that the spring 32 is mounted on a mobile 48 of the gear train whose pitch diameter is less than the pitch diameter of the respective wheels 42, 44 of the first and second balances 24a, 24b.
  • the regulating member comprises two sprung balances 22a, 22b mounted in phase opposition while the mobile 48 of the gear train is arranged to cooperate with the anchor 17 by means for example of a pin (not shown) secured to the mobile 48. This is driven back and forth during movement of the regulating member in order to regulate the rotation of the escape wheel 16 and maintain the oscillations of the first and second balance springs.
  • the escape wheel 16 can be replaced by two coaxial escape wheels which can be integral or movable with each other, in particular to take up play and/or to optimize contact with the pallets.
  • the oscillator of the regulating member comprises four flywheels 24a, 24b, 24c, 24d.
  • Each flywheel 24a, 24b, 24c, 24d is similar to the flywheels of the regulating member according to the embodiment illustrated in particular in figures 2 to 4 .
  • the distal parts of each flywheel together form several disjoint serge segments, for example three or four segments, along respectively a first, a second, a third and a fourth circle. The center distance between the four balance axes is reduced so that each circle intersects another circle among the four circles.
  • the four flywheels 24a, 24b 24c, 24d are connected together by a gear train (not shown) adapted so that two flywheels 24a, 24c oscillate in the same phase and in phase opposition to each other. to the two other oscillators 24b, 24d.
  • the four flywheels 24a, 24b, 24c, 24d are preferably arranged to oscillate in the same plane.
  • the adjustment according to these methods can be complementary to various other conventional adjustments, in particular adjustment by screw or by eccentrics mounted on balances or adjustment by the racket.
  • the inertia of the gear wheels is very much lower than that of the balance wheels (the wheels do not have sufficient inertia to allow them to maintain oscillations, that is to say they cannot be assimilated to balances), a variation thereof can however modulate in small proportions the relationship between the inertia of the balance-spring and the return torque of the balance-spring and modify the period of the oscillations, and therefore the operation of the watch movement equipped of such a regulatory body.
  • the modification of the inertia of a mobile part of the gear train can be carried out in different ways, in particular by 1) a change of material to target different densities and therefore different inertias with equal dimensions, by 2) a change of thickness, therefore different inertias at equal pitch diameter (or contour profile), or by 3) a change in effective mass at equal external dimensions, using perforated mobiles.
  • the energy available to the escape wheel may vary upstream (in particular due to the moment developed by the barrel spring which may vary in production, but also in more specific cases such as additional openings on mobiles - skeletons, or again in the case of driving additional modules with different consumptions), it is also possible to modify these pairings to adapt the characteristics of the regulating member to the quantity of energy available to the escape wheel.
  • the guide means can in particular be mounted on intermediate supports allowing this adjustment, but other means are also possible beyond the scope of the invention.

Landscapes

  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Gears, Cams (AREA)
EP22171307.6A 2022-05-03 2022-05-03 Regulierorgan für uhrwerk Pending EP4273634A1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP22171307.6A EP4273634A1 (de) 2022-05-03 2022-05-03 Regulierorgan für uhrwerk
PCT/IB2023/054547 WO2023214300A1 (fr) 2022-05-03 2023-05-02 Organe réglant pour mouvement horloger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP22171307.6A EP4273634A1 (de) 2022-05-03 2022-05-03 Regulierorgan für uhrwerk

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EP4273634A1 true EP4273634A1 (de) 2023-11-08

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH75063A (fr) 1916-12-09 1917-06-01 Theodore Jequier Echappement à nombre réduit d'oscillations
US1232285A (en) * 1916-10-19 1917-07-03 John H Greeley Escapement for clocks and watches.
CH131854A (fr) 1928-04-03 1929-03-15 Tavannes Watch Co Sa Echappement à cylindre.
EP2923242A1 (de) 2012-11-26 2015-09-30 Detra SA Ankerhemmung für ein uhrwerk
EP3120198A2 (de) * 2014-03-21 2017-01-25 Gfpi S.A. Uhrwerk
EP3208662A1 (de) * 2016-02-08 2017-08-23 Hepta Swiss SA Uhrwerk, das eine reguliervorrichtung umfasst

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1232285A (en) * 1916-10-19 1917-07-03 John H Greeley Escapement for clocks and watches.
CH75063A (fr) 1916-12-09 1917-06-01 Theodore Jequier Echappement à nombre réduit d'oscillations
CH131854A (fr) 1928-04-03 1929-03-15 Tavannes Watch Co Sa Echappement à cylindre.
EP2923242A1 (de) 2012-11-26 2015-09-30 Detra SA Ankerhemmung für ein uhrwerk
EP3120198A2 (de) * 2014-03-21 2017-01-25 Gfpi S.A. Uhrwerk
EP3208662A1 (de) * 2016-02-08 2017-08-23 Hepta Swiss SA Uhrwerk, das eine reguliervorrichtung umfasst

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