EP4273634A1 - Regulating device for a timepiece movement - Google Patents
Regulating device for a timepiece movement Download PDFInfo
- 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
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- European Patent Office
- Prior art keywords
- mobile
- balances
- regulating member
- oscillator
- balance
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- 230000001105 regulatory effect Effects 0.000 title claims abstract description 104
- 230000010355 oscillation Effects 0.000 claims abstract description 34
- 238000000034 method Methods 0.000 claims abstract description 19
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- 238000009826 distribution Methods 0.000 description 3
- 230000000284 resting effect Effects 0.000 description 3
- 238000004513 sizing Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 229940082150 encore Drugs 0.000 description 2
- BASFCYQUMIYNBI-UHFFFAOYSA-N platinum Chemical compound [Pt] BASFCYQUMIYNBI-UHFFFAOYSA-N 0.000 description 2
- 230000008569 process Effects 0.000 description 2
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- 240000008042 Zea mays Species 0.000 description 1
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- 239000000463 material Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 229910052697 platinum Inorganic materials 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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Classifications
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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.
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Abstract
L'invention concerne un organe réglant (20) pour mouvement horloger (10). L'organe réglant (20) comprend un oscillateur (22) comportant au moins un premier et un deuxième balancier. Chaque balancier comporte un volant d'inertie (24a, 24b) et un axe de balancier (34a, 34b). L'oscillateur (22) comporte au moins un organe élastique (32, 32a, 32b) destiné à entretenir les oscillations de l'oscillateur. Ce dernier comporte en outre un train d'engrenages (40) comprenant au moins deux mobiles (42, 44, 45, 46, 47, 48, 49). Le volant d'inertie (24a,24b) de chaque balancier est solidaire en rotation d'un mobile du train d'engrenages (40). Le train d'engrenages (40) est agencé pour connecter entre eux les volants d'inertie (24a, 24b) des premier et deuxième balanciers par une liaison desmodromique de sorte à ce que les oscillations respectives des premier et deuxième balanciers soient en opposition de phase. L'organe réglant (20) comporte en outre un échappement (15) comportant au moins un mobile d'échappement (16, 16a, 16b) et au moins une ancre (17, 17a, 17b) destinée à réguler ledit au moins un mobile d'échappement (16, 16a, 16b) et à entretenir les oscillations de l'oscillateur oscillateur (22). L'invention concerne également une méthode de réglage de la fréquence de l'oscillateur (22) de l'organe réglant (20)The invention relates to a regulating member (20) for a watch movement (10). The regulating member (20) comprises an oscillator (22) comprising at least a first and a second balance wheel. Each balance wheel includes a flywheel (24a, 24b) and a balance shaft (34a, 34b). The oscillator (22) comprises at least one elastic member (32, 32a, 32b) intended to maintain the oscillations of the oscillator. The latter further comprises a gear train (40) comprising at least two mobiles (42, 44, 45, 46, 47, 48, 49). The flywheel (24a, 24b) of each balance wheel is integral in rotation with a mobile part of the gear train (40). The gear train (40) is arranged to connect the flywheels (24a, 24b) 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 opposition to each other. phase. The regulating member (20) further comprises an escapement (15) comprising at least one escapement mobile (16, 16a, 16b) and at least one anchor (17, 17a, 17b) intended to regulate said at least one mobile exhaust (16, 16a, 16b) and to maintain the oscillations of the oscillator oscillator (22). The invention also relates to a method for adjusting the frequency of the oscillator (22) of the regulating member (20).
Description
La présente invention concerne un organe réglant pour mouvement horloger. L'invention concerne également un mouvement horloger comportant l'organe réglant et une pièce d'horlogerie comportant un tel mouvement.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.
En règle générale, les montres mécaniques comportent un mouvement horloger dont la fréquence d'oscillation de l'organe réglant varie entre 3Hz et 5Hz. Cette fréquence d'oscillation peut toutefois aller au-delà de 5Hz afin d'augmenter la précision de la montre. Cela étant, un organe réglant basse fréquence peut apporter plusieurs avantages, notamment une augmentation de la réserve de marche et une simplification du mouvement horloger.As a general rule, 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.
Les organes réglant basse fréquence sont déjà connus de l'état de la technique.Low frequency regulating bodies are already known from the state of the art.
A titre d'exemple,
Afin de maintenir un facteur de qualité acceptable pour un organe réglant basse fréquence, l'inertie du balancier doit être augmentée par rapport à un mouvement mécanique équipé d'un oscillateur à plus haute fréquence. Cette augmentation d'inertie comporte le désavantage principal d'augmenter la sensibilité aux accélérations angulaires.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.
Un but de la présente invention est par conséquent de proposer un organe réglant annulant ou, tout du moins, diminuant la sensibilité aux accélérations angulaires.An aim of the present invention is therefore to propose a regulating member canceling or, at least, reducing the sensitivity to angular accelerations.
Un autre but de la présente invention est de proposer un mouvement horloger simplifié comprenant un organe réglant basse fréquence.Another aim of the present invention is to propose a simplified watch movement comprising a low frequency regulating member.
Un but additionnel de la présente invention est de proposer une méthode de réglage de la fréquence de l'oscillateur de l'organe réglant.An additional aim of the present invention is to propose a method of adjusting the frequency of the oscillator of the regulating member.
Ces buts sont atteints notamment par un organe réglant pour mouvement horloger. L'organe réglant comprend un oscillateur comportant au moins un premier et un deuxième balancier. Chaque balancier comporte un volant d'inertie et un axe de balancier. L'oscillateur comporte au moins un organe élastique destiné à entretenir ses oscillations. Cet oscillateur comporte en outre un train d'engrenages comprenant au moins deux mobiles. Le volant d'inertie de chaque balancier est solidaire en rotation d'un mobile du train d'engrenages. Le train d'engrenages est agencé pour connecter entre eux les volants d'inertie des premier et deuxième balanciers par une liaison desmodromique de sorte à ce que les oscillations respectives des premier et deuxième balanciers soient en opposition de phase. L'organe réglant comporte en outre un échappement comportant au moins un mobile d'échappement et au moins une ancre destinée à réguler ledit au moins un mobile d'échappement et à entretenir les oscillations de l'oscillateur.These goals are achieved in particular by a regulating body for a watch movement. 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.
Selon une forme de réalisation, l'organe réglant comporte au moins trois balanciers comportant chacun un volant d'inertie. Les oscillations respectives de deux balanciers se suivant dans la chaine cinématique des au moins trois balanciers sont en opposition de phase.According to one embodiment, 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.
Selon une forme de réalisation, le train d'engrenages comporte plus de deux mobiles.According to one embodiment, the gear train includes more than two mobiles.
Selon une forme de réalisation, les axes de balancier des premier et deuxième balanciers sont coaxiaux.According to one embodiment, the balance axes of the first and second balance wheels are coaxial.
Selon une forme de réalisation, les axes de balancier des premier et deuxième balanciers sont parallèles alors que leur volant d'inertie respectif sont agencés pour osciller dans deux plans parallèles.According to one embodiment, the balance axes of the first and second balance wheels are parallel while their respective flywheels are arranged to oscillate in two parallel planes.
Selon une forme de réalisation, les volants d'inertie des premier et deuxième balanciers sont sensiblement compris dans le même plan.According to one embodiment, the flywheels of the first and second balances are substantially included in the same plane.
Selon une forme de réalisation, les axes de balancier des premier et deuxième balanciers sont contenus dans des plans qui s'intersectent.According to one embodiment, the balance axes of the first and second balances are contained in intersecting planes.
Selon une forme de réalisation, le volant d'inertie de chacun des premier et deuxième balanciers comporte une pluralité de segments de serge disjoints, par exemple deux, trois, voire quatre segments de serge, formant ensemble la serge de chaque volant d'inertie le long de cercles respectifs. Ces cercles définissent respectivement un premier et un deuxième disque se recoupant ou s'intersectant afin de former une zone de recoupement ou une zone d'intersection.According to one embodiment, 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.
Selon une forme de réalisation, la zone de recoupement à la forme d'une lentille. Cette lentille est de préférence une lentille symétrique.According to one embodiment, the overlapping zone has the shape of a lens. This lens is preferably a symmetrical lens.
Selon une forme de réalisation, la zone d'intersection est un segment de droite.According to one embodiment, the intersection zone is a straight line segment.
Selon une forme de réalisation, au moins un des premier et deuxième balanciers ne comporte pas ledit au moins un organe élastique.According to one embodiment, at least one of the first and second balances does not include said at least one elastic member.
Selon une forme de réalisation, au moins un organe élastique est monté sur un mobile intermédiaire du train d'engrenages. L'inertie du mobile intermédiaire est au moins cinq fois, de préférence au moins dix fois, voire au moins vingt fois inférieure à l'inertie de l'un quelconque des balanciers de l'oscillateur.According to one embodiment, 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.
Selon une forme de réalisation, au moins un des premier et deuxième balanciers et/ou un mobile intermédiaire du train d'engrenages comporte un nombre pair, de préférence deux, d'organes élastiques enroulés en sens inverse.According to one embodiment, 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.
Selon une forme de réalisation, l'échappement ne comporte qu'une ancre agencée pour coopérer avec un des premier et deuxième balanciers et le mobile d'échappement.According to one embodiment, the escapement only comprises one anchor arranged to cooperate with one of the first and second balances and the escapement mobile.
Selon une forme de réalisation, l'échappement comporte deux ancres agencées pour coopérer, d'une part, avec respectivement les premier et deuxième balanciers et, d'autre part, avec un mobile d'échappement unique, ou avec respectivement un premier et un deuxième mobile d'échappement.According to one embodiment, 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.
Selon une forme de réalisation, l'échappement comporte une première et une seconde demi-ancre agencées pour coopérer avec respectivement les premier et deuxième balanciers. Les première et seconde demi-ancres comportent respectivement une première palette et une seconde palette agencées pour coopérer avec un mobile d'échappement unique ou avec respectivement un premier et un second mobile d'échappement.According to one embodiment, 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.
Selon une forme de réalisation, l'échappement comporte une ancre agencée pour coopérer avec l'un des premier et deuxième balanciers. L'ancre comporte une première palette agencée pour coopérer avec un premier mobile d'échappement et une seconde palette agencée pour coopérer avec un second mobile d'échappement.According to one embodiment, 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.
Selon une forme de réalisation, l'échappement comporte une ancre agencée pour coopérer avec un mobile intermédiaire du train d'engrenage et un mobile d'échappement.According to one embodiment, the escapement comprises an anchor arranged to cooperate with an intermediate mobile of the gear train and an exhaust mobile.
Un autre aspect de l'invention porte sur une méthode de réglage de la fréquence de l'oscillateur de l'organe réglant. La méthode consiste à déterminer, dans un premier temps, l'inertie de l'ensemble des balanciers et le couple de rappel dudit au moins un organe élastique de l'oscillateur. Cette méthode consiste par ailleurs, dans un second temps, à remplacer au moins un des mobiles du train d'engrenages, de préférence un mobile intermédiaire, par un mobile d'inertie différente de sorte à obtenir un rapport entre l'inertie de l'ensemble des balanciers et le couple de rappel dudit au moins un organe élastique défini par la fréquence souhaitée de l'oscillateur.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.
Un autre aspect de l'invention porte sur une méthode de réglage de la fréquence de l'oscillateur de l'organe réglant selon une solution alternative. Selon cette alternative, la méthode consiste à déterminer, dans un premier temps, l'inertie de l'ensemble des balanciers et le couple de rappel dudit au moins un organe élastique. Cette méthode consiste par ailleurs, dans un second temps, de remplacer au moins des mobiles du train d'engrenages, de préférence un mobile intermédiaire par un mobile de diamètre primitif différent du mobile remplacé de sorte à obtenir un rapport entre l'inertie de l'ensemble des balanciers et le couple de rappel dudit au moins un organe élastique défini par la fréquence souhaitée de l'oscillateur.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. According to this alternative, 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.
Un autre aspect de l'invention porte sur une méthode de réglage d'un mouvement horloger comprenant une source motrice, notamment un barillet, et l'organe réglant. La méthode consiste à déterminer, dans un premier temps, le couple fourni par la source motrice au mobile d'échappement, l'inertie de l'ensemble des balanciers de l'oscillateur et le couple de rappel dudit au moins un spiral. Cette méthode consiste par ailleurs à remplacer, dans un second temps, au moins un mobile du train d'engrenages, de préférence un mobile intermédiaire, par un mobile d'inertie différente et/ou de diamètre primitif différent de sorte à obtenir un rapport défini entre l'inertie de l'ensemble des balanciers de l'oscillateur et le couple de rappel dudit au moins un organe élastique ainsi qu'un rapport défini entre la puissance d'entretien des oscillations de l'oscillateur et la puissance disponible à la roue d'échappement.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.
Des exemples de mise en oeuvre de l'invention sont décrits dans la description illustrée par les figures annexées dans lesquelles :
- la
figure 1 est une vue schématique de dessus d'un mouvement horloger simplifié selon une forme de réalisation de l'invention ; - la
figure 2 illustre une vue en perspective d'un oscillateur comportant deux balanciers-spiraux entrainés ensemble par un rouage desmodromique selon une forme de réalisation de l'invention ; - la
figure 3 illustre une vue de dessus de lafigure 2 ; - la
figure 4 illustre une vue similaire à lafigure 3 sans la représentation des spiraux; - la
figure 5 illustre une vue de côté de lafigure 2 , - la
figure 6 illustre une vue en perspective d'un oscillateur selon une autre forme de réalisation de l'invention ; - la
figure 7 illustre une vue de dessus de lafigure 6 ; - la
figure 8 illustre une vue de côté de lafigure 6 ; - la
figure 9 illustre une vue en perspective de l'organe réglant comportant deux balanciers-spiraux entrainés ensemble par un rouage desmodromique selon une autre forme de réalisation de l'invention, - la
figure 10 illustre une vue de côté de lafigure 9 , - la
figure 11 est une vue schématique de dessus d'un organe réglant selon une forme de réalisation, - la
figure 12 est une vue schématique de dessus d'un organe réglant selon une autre forme de réalisation, - la
figure 13 est une vue schématique de dessus d'un organe réglant selon une autre forme de réalisation, - la
figure 14 est une vue schématique de dessus d'un organe réglant selon une autre forme de réalisation, - la
figure 15 est une vue schématique de dessus d'un organe réglant selon une autre forme de réalisation, - la
figure 16 est une vue schématique de dessus d'un organe réglant selon une autre forme de réalisation, - la
figure 17 est une vue schématique de dessus d'un organe réglant selon une autre forme de réalisation, - la
figure 18 est une vue schématique de dessus d'un organe réglant selon une autre forme de réalisation, - la
figure 19 est une vue schématique de dessus d'un organe réglant selon une autre forme de réalisation, - la
figure 20 est une vue schématique de dessus d'un organe réglant selon une autre forme de réalisation, - la
figure 21 est une vue schématique de dessus d'un organe réglant selon une autre forme de réalisation, - la
figure 22 est une vue schématique de dessus d'un organe réglant selon une autre forme de réalisation, - la
figure 23 est une vue schématique de dessus d'un organe réglant selon une autre forme de réalisation, - la
figure 24 est une vue schématique de dessus d'un organe réglant selon une autre forme de réalisation, - la
figure 25a illustre une vue de dessus d'un échappement de l'organe réglant de lafigure 12 , - la
figure 25b illustre une vue du dessus d'un échappement, selon une autre forme de réalisation, de l'organe réglant de lafigure 12 , - la
figure 25c illustre une vue du dessus d'un échappement, selon une autre forme de réalisation, de l'organe réglant de lafigure 12 , - la
figure 25d illustre une vue au niveau du point de contact entre une palette d'une des ancres de lafigure 25c et un dent de la roue d'échappement, - la
figure 26 illustre une vue du dessus d'un échappement de l'organe réglant de lafigure 17 , - la
figure 27 est une vue schématique de dessus de l'oscillateur selon une autre forme de réalisation, - la
figure 28 est une vue schématique de dessus de l'oscillateur illustrant une zone de recoupement entre deux balanciers selon une autre forme de réalisation, - la
figure 29 est une vue schématique de dessus de l'oscillateur illustrant une zone de recoupement entre deux balanciers selon une autre forme de réalisation, et - la
figure 30 est une vue schématique de l'oscillateur illustrant deux zones d'intersections entre trois balanciers selon une autre forme de réalisation.
- there
figure 1 is a schematic top view of a simplified watch movement according to one embodiment of the invention; - there
figure 2 illustrates a perspective view of an oscillator comprising two sprung balances driven together by a desmodromic gear train according to one embodiment of the invention; - there
Figure 3 illustrates a top view of thefigure 2 ; - there
Figure 4 illustrates a view similar toFigure 3 without the representation of the hairsprings; - there
Figure 5 illustrates a side view of thefigure 2 , - there
Figure 6 illustrates a perspective view of an oscillator according to another embodiment of the invention; - there
Figure 7 illustrates a top view of theFigure 6 ; - there
figure 8 illustrates a side view of theFigure 6 ; - there
Figure 9 illustrates a perspective view of the regulating member comprising two sprung balances driven together by a desmodromic gear train according to another embodiment of the invention, - there
Figure 10 illustrates a side view of theFigure 9 , - there
Figure 11 is a schematic top view of a regulating member according to one embodiment, - there
Figure 12 is a schematic top view of a regulating member according to another embodiment, - there
Figure 13 is a schematic top view of a regulating member according to another embodiment, - there
Figure 14 is a schematic top view of a regulating member according to another embodiment, - there
Figure 15 is a schematic top view of a regulating member according to another embodiment, - there
Figure 16 is a schematic top view of a regulating member according to another embodiment, - there
Figure 17 is a schematic top view of a regulating member according to another embodiment, - there
Figure 18 is a schematic top view of a regulating member according to another embodiment, - there
Figure 19 is a schematic top view of a regulating member according to another embodiment, - there
Figure 20 is a schematic top view of a regulating member according to another embodiment, - there
Figure 21 is a schematic top view of a regulating member according to another embodiment, - there
Figure 22 is a schematic top view of a regulating member according to another embodiment, - there
Figure 23 is a schematic top view of a regulating member according to another embodiment, - there
Figure 24 is a schematic top view of a regulating member according to another embodiment, - there
figure 25a illustrates a top view of an exhaust from the regulating organ of theFigure 12 , - there
figure 25b illustrates a top view of an exhaust, according to another embodiment, of the regulating member of theFigure 12 , - there
figure 25c illustrates a top view of an exhaust, according to another embodiment, of the regulating member of theFigure 12 , - there
figure 25d illustrates a view at the point of contact between a pallet of one of the anchors of thefigure 25c and a tooth of the escape wheel, - there
Figure 26 illustrates a top view of an exhaust from the regulating organ of theFigure 17 , - there
Figure 27 is a schematic top view of the oscillator according to another embodiment, - there
Figure 28 is a schematic top view of the oscillator illustrating an overlapping zone between two pendulums according to another embodiment, - there
Figure 29 is a schematic top view of the oscillator illustrating an overlapping zone between two pendulums according to another embodiment, and - there
figure 30 is a schematic view of the oscillator illustrating two zones of intersection between three pendulums according to another embodiment.
Dans la présente demande, on entend par «oscillateur» un résonateur comportant, d'une part, plusieurs balanciers et, d'autre part, un rouage agencé pour être en prise avec les balanciers de sorte à rendre ces deniers dépendants entre eux. Par ailleurs, dans la présente demande on entend par «organe réglant» un ensemble comprenant l'oscillateur et un organe de comptage, notamment un échappement.In the present application, 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. Furthermore, in the present application the term “regulating member” means an assembly comprising the oscillator and a counting member, in particular an escapement.
En référence à la
Le mouvement horloger simplifié comporte une platine 12 sur laquelle sont montés un barillet 14, un échappement 15 comportant une roue d'échappement et une liaison cinématique 19 reliant le barillet 14 au pignon de la roue d'échappement. La liaison cinématique 19 comporte moins de trois mobiles.The simplified watch movement comprises a
Selon une forme avantageuse de réalisation, cette liaison cinématique comporte uniquement un mobile 19 en prise d'une part avec le rochet du barillet 14 et, d'autre part, avec le pignon de la roue d'échappement. Le mobile 19 remplace par conséquent la roue du centre, la roue de moyenne et la roue de seconde d'un mouvement traditionnel.According to an advantageous embodiment, this kinematic connection only comprises a mobile 19 engaged on the one hand with the ratchet of the
Selon une variante d'exécution non-illustrée, la liaison cinématique ne comporte pas moins et pas plus que deux mobiles engrenant ensemble. L'un des deux mobiles est en prise avec le rochet du barillet alors que l'autre des deux mobiles est en prise avec le pignon de la roue d'échappement.According to a variant of execution not illustrated, 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.
Le mouvement horloger simplifié à l'avantage d'apporter une architecture nouvelle avec des possibilités d'identification du produit unique due au fait que les contraintes géométriques, par exemple les entraxes, sont très différentes des mouvements traditionnels. Par ailleurs, la simplification du mouvement permet d'augmenter le rendement global par la réduction du nombre d'engrenages.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.
Sous certaines conditions liées aux rapports d'engrenage et à l'échappement, il est possible d'afficher la seconde directement sur la roue d'échappement. Dans ce cas, les rapports d'engrenage entre le barillet 14, le mobile 19 et le pignon de la roue d'échappement 16 sont choisis de sorte à ce que cette dernière puisse effectuer une rotation complète par minute. Un organe indicateur des secondes 50 peut être monté sur l'axe la roue d'échappement.Under certain conditions related to gear ratios and escapement, it is possible to display the second directly on the escapement wheel. In this case, the gear ratios between the
De même, sous certaines conditions liées aux rapports d'engrenage, le mobile 19 peut directement afficher les minutes. Le rapport d'engrenage entre le barillet et le mobile 19 est par conséquent choisi de sorte à ce que ce dernier puisse effectuer une rotation complète par heure. Un organe indicateur des minutes 52 peut par exemple être monté sur l'axe du mobile 19.Likewise, under certain conditions linked to gear ratios, 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
Enfin, sous certaines conditions liées aux rapports d'engrenage, le barillet 14 peut afficher l'heure. Par exemple, un organe indicateur des heures 54 peut être monté sur l'arbre du barillet 14.Finally, under certain conditions linked to gear ratios,
Comme évoqué précédemment, la réalisation d'un mouvement horloger simplifié est uniquement possible par la mise en oeuvre d'un organe réglant à basse fréquence. Afin de maintenir un facteur de qualité acceptable, l'inertie du balancier doit être augmenté par rapport à un mouvement mécanique équipé d'un oscillateur à plus haute fréquence. Cette augmentation d'inertie comporte le désavantage principal d'augmenter la sensibilité aux accélérations angulaires. De manière à contrer cette sensibilité aux accélérations, l'oscillateur de l'organe réglant comporte au moins deux balanciers couplés en opposition de phase selon différentes formes de réalisation, c'est-à-dire qu'un spiral est associé à chacun des deux balanciers de sorte à ce que l'un des spiraux est dans une phase de contraction alors l'autre des spiraux est dans une phase d'expansion. Selon une variante, l'opposition de phase peut être réalisé en montant sur l'un des balanciers de l'oscillateur deux spiraux enroulés un sens inverse pour que l'un des deux spiraux soit dans une phase de contraction lorsque l'autre des deux spiraux est dans une phase d'expansion.As mentioned previously, the production of a simplified watch movement is only possible by the implementation of a low frequency regulating organ. In order to maintain an acceptable quality factor, 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. In order to counter this sensitivity to 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. According to a variant, 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.
Selon une forme de réalisation avantageuse, illustrée par les
L'oscillateur peut comporter un organe élastique autre qu'un ressort spiral plat conventionnel, par exemple un spiral cylindrique, un spiral hémisphérique ou sphérique ou encore un spiral conique. Le spiral peut également comporter plusieurs spires selon une variante. L'oscillateur peut également comporter un organe élastique ne s'apparentant pas à un spiral pour remplir la fonction de rappel du balancier.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.
Les premier et deuxième balanciers-spiraux 22a, 22b de l'oscillateur 22 sont reliés par un train d'engrenages 40 afin d'entraîner ces balanciers-spiraux par une liaison desmodromique pour que le volant d'inertie 24a de l'un des deux balanciers-spiraux 22a, 22b puisse osciller en opposition de phase par rapport au volant d'inertie 24b de l'autre des deux balanciers-spiraux. En d'autres termes, le spiral 32a de l'un des deux balanciers-spiraux 22a, 22b est dans une phase d'expansion alors que le spiral 32b de l'autre des deux balanciers-spiraux 22a, 22b est dans une phase de contraction, ce qui a pour conséquence d'entrainer les volants d'inerties respectifs 24a, 24b dans un sens opposé. Cet agencement particulier des deux spiraux 32a, 32b permet d'annuler ou, tout du moins, diminuer la sensibilité de l'oscillateur 22 aux accélérations angulaires.The first and second sprung
Comme on peut le voir en particulier à la
En référence notamment à la
Les parties distales des premier et deuxième volants d'inertie 24a, 24b forment chacun quatre segments de serge disjoints 28a, 28b le long respectivement d'un premier et d'un deuxième cercle 25a, 25b comme représenté à la
Selon d'autres variantes d'exécution, le volant d'inertie de chaque balancier-spiral peut ne comporter que deux ou trois bras. Dans ce cas, le segment de serge associé à chaque bras sera de dimension plus importante afin que l'inertie de chaque balancier reste constante. Par exemple, chaque segment de serge discontinu du volant d'inertie peut s'étendre le long d'un arc de cercle supérieur à 45° dans le cas où chaque balancier comporte trois bras, voire supérieur à 60° dans le cas où chaque balancier comporte uniquement deux bras.According to other execution variants, the flywheel of each sprung balance may have only two or three arms. In this case, the serge segment associated with each arm will be larger so that the inertia of each balance remains constant. For example, 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.
Une masselotte 30a, 30b sous la forme de vis sont vissée dans chaque segment de serge 28a, 28b, par exemple selon une direction radiale, afin de pouvoir modifier l'inertie du volant d'inertie 24a, 24b de chaque balancier-spiral pour ajuster leur fréquence d'oscillation.A
L'entraxe entre les deux axes de balancier 34a, 34b respectivement des premier et deuxième balanciers-spiraux 22a, 22b est réduit de manière à limiter les écarts d'influence de l'accélération entre les premier et deuxième volant d'inertie 24a, 24b. Selon cette configuration, les premiers et deuxième cercles 25a, 25b, le long desquels sont disposés les segments de serge disjoints 28a, 28b respectivement du premier et deuxième balancier 24a, 24b, se recoupe. Cette configuration a également l'avantage de réduire l'encombrement des balanciers (surface). Selon une forme de réalisation, les dimensions des deux volants d'inertie sont sensiblement identiques. Ces deux volants d'inertie définissent deux disques avec une zone de recoupement 29a s'apparentant à une lentille symétrique comme illustré à la
Lorsque l'organe réglant 20 est en marche, les oscillations des volants d'inertie 24a, 24b des balanciers-spiraux 22a, 22b sont synchronisées en opposition de phase de sorte à ce que les segments de serge 28a du volant d'inertie 24a de l'un des deux balanciers-spiraux 22a, 22b ne rentre jamais en contact avec les segments de serge 28b du volant d'inertie 24b de l'autre des deux balanciers-spiraux 22a, 22b.When the regulating
Selon une autre forme de réalisation illustrée par les
Selon la
Tout comme la première forme de réalisation, le volant d'inertie 24a, 24b de chaque balancier-spiral 22a, 22b comporte quatre bras 26a, 26b séparés d'un angle du 90° les uns par rapport aux autres et comportant les mêmes caractéristiques des bras des deux balanciers-spiraux de l'organe réglant illustré notamment à la
Selon une autre forme de réalisation illustrée par les
L'avantage de cette forme de réalisation réside notamment sur le train d'engrenage simplifié afin que les volants d'inertie 24a, 24b respectivement des premier et deuxième balanciers-spiraux 22a, 22b puissent osciller en opposition de phase puisque ce train d'engrenage ne comprend que deux mobiles 42, 44 à dentures appropriées, coniques par exemple, en prise direct.The advantage of this embodiment lies in particular on the simplified gear train so that the
Tout comme les première et deuxième formes de réalisation, le volant d'inertie 24a, 24b de chaque balancier-spiral comporte quatre bras 26a, 26b séparés d'un angle du 90° les uns par rapport aux autres et possédant les mêmes caractéristiques des bras des deux balanciers-spiraux de l'organe réglant illustré notamment à la
Tout comme pour la première forme de réalisation, lorsque l'oscillateur 22 est en marche, les oscillations du volant d'inertie 24a de l'un des deux balanciers-spiraux 22a, 22b sont synchronisées en opposition de phase par rapport aux oscillations du volant d'inertie 24b de l'autre des deux balanciers-spiraux22a, 22b de sorte à ce que les segments de serge 28a, 28b des volants d'inertie respectifs 24a, 24b ne rentrent jamais en contact.Just as for the first embodiment, when the
L'organe réglant 20 selon l'invention peut être mis en oeuvre selon différentes configurations de l'oscillateur et de l'échappement selon les figures schématiques 11 à 24 afin de transmettre la fréquence d'oscillation de l'organe réglant 20 à la liaison cinématique 19 reliant le barillet 14 au pignon de la roue d'échappement 16, de préférence par l'intermédiaire d'un mobile unique 19 selon la représentation schématique de la
Selon la forme de réalisation de la
L'ancre 17 comprend une palette d'entrée 170 et une palette de sortie 172 agencées pour coopérer avec la roue d'échappement 16 de manière conventionnelle afin de transmettre les oscillations du volant d'inertie 24a d'un seul balancier-spiral 22a de l'organe réglant 20 à la roue d'échappement 16 afin que la rotation de la roue d'échappement 16 se fasse au gré des oscillations du volant d'inertie 24a. A cet effet, l'ancre 17 comporte une fourchette 179 agencée pour coopérer avec une cheville de plateau de l'axe de balancier.The
Le volant d'inertie 24a de l'un des balanciers-spiraux est relié au volant d'inertie 24b de l'autre des balanciers-spiraux par un train d'engrenage avec un nombre pair de renvois 42, 44, 46, 48 de manière à inverser le sens de rotation des balanciers.The
Chaque balancier-spiral 22a, 22b comporte un spiral 32a, 32b enroulé dans le même sens de manière à ce qu'au cours de la marche du mouvement, le spiral de l'un des balanciers-spiraux se trouve dans une phase de contraction pendant que le spiral de l'autre des balanciers-spiraux se trouve dans une phase d'expansion, c'est-à-dire en opposition de phase.Each
Selon la
En particulier, en référence notamment à la
Selon cette disposition, la palette de sortie 172a de la première ancre 17a est agencée en regard de la palette d'entrée 170b de la seconde ancre 17b alors que la palette d'entrée 170a de la première ancre et la palette de sortie 172b de la seconde ancre 17b sont éloignées l'une de l'autre afin de coopérer avec des dents de la roue d'échappement 16 qui sont séparées d'un angle inférieur à 180° en passant par le centre de la roue 16. La roue d'échappement 16 comporte à cet effet au moins 20 dents alors qu'une fourchette 179a, 179b de chaque ancre est agencée pour coopérer avec la cheville de plateau 35a du plateau 35 de l'axe du balancier-spiral 22a, 22b correspondant. La roue d'échappement de moins de 20 dents, par exemple 15 dents, peut également être utilisée sous certaines conditions.According to this arrangement, the
De par les sens de rotation inverse des volants d'inertie 24a, 24b (
Selon la forme de réalisation illustrée à la
Cette forme spécifique de la partie distale des palettes susvisées a l'avantage d'éviter la contrainte imposée par les phases de fonctionnement des première et seconde ancres qui doivent s'effectuer de manière simultanée selon la forme de réalisation illustrée à la
Les dimensions des palettes sont telles que les dents de la roue d'échappement reposent bien sur les plans de repos des palettes tronquées de manière à assurer un verrouillage de l'ancre de manière classique et que la phase de dégagement sur cette palette ne soit pas plus longue que sur la palette non tronquée de l'autre ancre afin d'éviter une perte d'énergie lors de l'impulsion. Cette forme de réalisation à l'avantage de faciliter l'auto-démarrage de l'échappement 15.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
Selon la forme de réalisation illustrée à la
Compte tenu des tolérances de fabrication, un échappement à ancre classique nécessite généralement un ajustement final des positions des palettes d'entrée et de sortie. Cet ajustement est en général long et délicat car il peut influencer fortement le rendement de l'échappement.Given manufacturing tolerances, 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.
L'échappement 15 selon la
En l'espèce, chaque dent de la roue d'échappement 16 comporte un plan de conduite 182 (
Selon une variante d'exécution non-illustrée, le plan de conduite peut se trouver sur l'une des palettes de la première et seconde ancre alors que la roue d'échappement comporte une denture classique.According to a variant of execution not shown, the driving plan can be located on one of the pallets of the first and second anchor while the escape wheel has conventional teeth.
L'organe réglant 20 selon la forme de réalisation de la
Selon la forme de réalisation de la
Selon la forme de réalisation de la
Selon la forme de réalisation de la
Selon la forme de réalisation de la
Selon les formes de réalisation des
Selon la forme de réalisation de la
Deux autres formes de réalisation de l'organe réglant sont illustrées par les
En référence à la
Le mobile 48 peut être plus grand ou plus petit que les mobiles 42, 44 solidaires respectivement des premier et deuxième balanciers 24a, 24b, de sorte à augmenter la plage de dimensionnement des couplages balancier-spiral et des amplitudes (l'amplitude du mobile-spiral peut être adaptée au fonctionnement idéal de l'échappement alors que l'amplitude des balanciers peut être adaptée à leur inertie). Selon l'organe réglant de la
Un autre exemple d'un organe réglant est schématiquement illustré par la
Selon une autre forme de réalisation schématiquement illustrée par la
Selon les formes de réalisation illustrées par les
Selon une autre forme de réalisation schématiquement illustrée à la
L'organe réglant selon l'invention permet de faire intervenir entre le balancier, le spiral et la roue d'échappement, qui sont directement liés entre eux dans un organe réglant conventionnel, plusieurs mobiles d'un train d'engrenage. Le dimensionnement de chaque mobile conditionne leurs couplages respectifs. Ce dimensionnement permet la mise en œuvre de nouvelles méthodes de réglage entre :
- le couple de rappel du au moins un ressort spiral et l'inertie des balanciers tout en maintenant inchangée la puissance nécessaire à l'entretien des oscillations de l'oscillateur,
- la puissance nécessaire à l'entretien de l'oscillateur et la puissance délivrée par le au moins un mobile d'échappement.
- the return torque of at least one spiral spring and the inertia of the balance wheels while maintaining unchanged the power necessary for maintaining the oscillations of the oscillator,
- the power necessary for maintaining the oscillator and the power delivered by the at least one exhaust mobile.
Ces méthodes de réglage peuvent notamment avoir l'avantage de permettre de palier à :
- des variations dans la production de composants en série (distribution des couples de spiraux ou des inerties de balancier dans des lots de production),
- des variations de couple fourni par l'organe moteur d'un mouvement équipé d'un tel organe réglant,
- des variations engendrées par la consommation de fonctions additionnelles de mécanismes dans un mouvement équipé d'un tel organe réglant (le même mouvement de base pouvant alimenter plusieurs calibres dont les fonctions additionnelles varient, mais pour lesquelles le même organe réglant serait utilisé, sa puissance étant adaptée selon la consommation de ces fonctions additionnelles).
- variations in the production of serial components (distribution of hairspring couples or balance inertias in production batches),
- variations in torque provided by the driving member of a movement equipped with such a regulating member,
- variations generated by the consumption of additional functions of mechanisms in a movement equipped with such a regulating organ (the same basic movement being able to power several calibers whose additional functions vary, but for which the same regulating organ would be used, its power being adapted according to the consumption of these additional functions).
Le réglage selon ces méthodes peut être complémentaires à différant autres réglages conventionnels, notamment un réglage par vis ou par des excentriques montés sur des balanciers ou un réglage par la raquetterie.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.
Il est possible, en modifiant les propriétés géométriques (diamètre primitif et/ou inertie) de mobiles du train d'engrenage, notamment d'au moins un des mobile 42, 43, 44, 45, 46, 47, 48, 49 du train d'engrenages 40, de modifier l'appairage entre le couple de rappel du au moins un ressort spiral et l'inertie des balanciers tout en maintenant inchangée la puissance nécessaire à l'entretien des oscillations de l'oscillateur.It is possible, by modifying the geometric properties (pitch diameter and/or inertia) of mobiles of the gear train, in particular of at least one of the
Le procédé comprend donc les étapes suivantes:
- déterminer l'inertie de l'ensemble des balanciers de l'oscillateur,
- déterminer le couple de rappel de l'organe élastique de l'oscillateur,
- comparer ces valeurs aux valeurs théoriques donnant les performances visées et déterminer la modification à apporter pour y parvenir, qu'il s'agisse d'un mobile d'inertie plus grande/faible ou un mobile de diamètre nominal plus grand/petit,
- remplacer le ou les mobiles initiaux par des mobiles déterminés à l'étape précédente
- optionnellement, mesurer les performances chronométriques de l'organe réglant, et
- optionnellement recommencer si l'appairage doit encore être amélioré/affiné.
- determine the inertia of all the pendulums of the oscillator,
- determine the restoring torque of the elastic member of the oscillator,
- compare these values to the theoretical values giving the targeted performances and determine the modification to be made to achieve this, whether it is a mobile with greater/lower inertia or a mobile with a larger/smaller nominal diameter,
- replace the initial mobile(s) with mobiles determined in the previous step
- optionally, measure the chronometric performance of the regulating organ, and
- optionally start again if the pairing still needs to be improved/refined.
Bien que l'inertie des mobiles du rouage est très largement inférieure à celle des balanciers (les mobiles n'ayant pas une inertie suffisante pour leur permettre d'entretenir des oscillations, c'est-à-dire qu'ils ne peuvent être assimilés à des balanciers), une variation de celle-ci peut toutefois moduler dans des petites proportions la relation entre l'inertie du balancier-spiral et le couple de rappel du spiral et modifier la période des oscillations, et donc la marche du mouvement horloger équipé d'un tel organe réglant.Although 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.
La modification de l'inertie d'un mobile du train d'engrenage peut être effectuée de différentes manières, notamment par 1) un changement de matière pour viser des masses volumiques différentes et donc des inerties différentes à dimensions égales, par 2) un changement d'épaisseur, donc inerties différentes à diamètre primitif (ou profil de contour) égal, ou par 3) un changement de masse effective à dimensions extérieures égales, en utilisant des mobiles ajourés.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.
En modifiant le diamètre primitif d'un des mobiles, notamment un mobile portant un spiral, on modifie le rapport entre l'inertie et le couple de rappel du spiral. La modification du diamètre primitif en engrenage suppose généralement, à module égal, un changement du nombre de dents. Il existe cependant d'autres moyens de modulation fine comme les déports, qui consistent à modifier à nombre de dents égal le diamètre primitif et ainsi la relation entre des mobiles engrenant ensemble.By modifying the pitch diameter of one of the mobiles, in particular a mobile carrying a hairspring, we modify the ratio between the inertia and the return torque of the hairspring. Changing the pitch diameter in gearing generally assumes, for the same module, a change in the number of teeth. However, there are other means of fine modulation such as offsets, which consist of modifying the original diameter for an equal number of teeth and thus the relationship between mobiles meshing together.
L'énergie disponible à la roue d'échappement pouvant varier en amont (notamment en raison du moment développé par le ressort de barillet qui peut varier en production, mais aussi dans des cas plus spécifiques comme des ajourages supplémentaires sur des mobiles - squelettes, ou encore dans le cas d'entraînement de modules additionnels aux consommations différentes), il est aussi possible de modifier ces appairages pour adapter les caractéristiques de l'organe réglant à la quantité d'énergie disponible à la roue d'échappement.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.
Cela implique les étapes suivantes :
- déterminer le couple fourni par la source motrice à un ou plusieurs mobiles d'échappement,
- déterminer l'inertie effective des balanciers équipant l'organe réglant,
- déterminer le couple de rappel de l'organe élastique équipant l'organe réglant,
- comparer ces valeurs aux valeurs théoriques donnant les performances visées et déterminer la modification à apporter pour y parvenir, une modification d'inertie d'un mobile pouvant s'accompagner d'une modification de diamètre nominal du même mobile ou d'un autre mobile du train d'engrenage, ceci afin de conserver l'équilibre balancier-spiral,
- remplacer le ou les mobiles initiaux par des mobiles déterminés à l'étape précédente
- optionnellement mesurer les performances chronométriques de l'organe réglant, et
- optionnellement recommencer si l'appairage doit encore être amélioré / affiné.
- determine the torque supplied by the driving source to one or more exhaust mobiles,
- determine the effective inertia of the balances equipping the regulating organ,
- determine the return torque of the elastic member fitted to the regulating member,
- compare these values to the theoretical values giving the targeted performances and determine the modification to be made to achieve this, a modification of the inertia of a mobile being able to be accompanied by a modification of the nominal diameter of the same mobile or of another mobile of the gear train, this in order to maintain the balance-spring balance,
- replace the initial mobile(s) with mobiles determined in the previous step
- optionally measure the chronometric performance of the regulating organ, and
- optionally start again if the pairing still needs to be improved/refined.
Afin d'optimiser le procédé de réglage précédemment décrit, il peut être utile de procéder à des déterminations statistiques (s'il s'agit uniquement de palier à des distributions en série) ou des déterminations de besoins (s'il s'agit de palier à des variations de consommation de fonctions additionnelles) afin de répartir les mobiles d'appairage par classes, et de dimensionner ces classes (écarts) en fonction des besoins précités.In order to optimize the adjustment process previously described, it may be useful to carry out statistical determinations (if it is only a matter of adjusting to series distributions) or determinations of needs (if it is a matter of to compensate for variations in consumption of additional functions) in order to distribute the pairing mobiles by classes, and to size these classes (gaps) according to the aforementioned needs.
Enfin, s'il s'agit de faire intervenir des mobiles de diamètres primitifs différents, il est évident que les positionnements des mobiles dans leur support (porte-échappement, platine-coq ou autre), des moyens de guidage (palier, roulements à billes, etc.) devront être configurés pour que leur espacement relatif puisse être adapté aux variations d'entraxe résultant de l'appairage. Ces moyens pour ajuster les entraxes sont bien connus de l'état de la technique, comme divulgué par exemple dans
Les moyens de guidage peuvent notamment être montés sur des supports intermédiaires permettant ce réglage, mais d'autres moyens sont aussi envisageables dans sortir du cadre de l'invention.
Claims (21)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP22171307.6A EP4273634A1 (en) | 2022-05-03 | 2022-05-03 | Regulating device for a timepiece movement |
PCT/IB2023/054547 WO2023214300A1 (en) | 2022-05-03 | 2023-05-02 | Regulating member for a timepiece movement |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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EP22171307.6A EP4273634A1 (en) | 2022-05-03 | 2022-05-03 | Regulating device for a timepiece movement |
Publications (1)
Publication Number | Publication Date |
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EP4273634A1 true EP4273634A1 (en) | 2023-11-08 |
Family
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP22171307.6A Pending EP4273634A1 (en) | 2022-05-03 | 2022-05-03 | Regulating device for a timepiece movement |
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EP (1) | EP4273634A1 (en) |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH75063A (en) | 1916-12-09 | 1917-06-01 | Theodore Jequier | Exhaust with reduced number of oscillations |
US1232285A (en) * | 1916-10-19 | 1917-07-03 | John H Greeley | Escapement for clocks and watches. |
CH131854A (en) | 1928-04-03 | 1929-03-15 | Tavannes Watch Co Sa | Cylinder exhaust. |
EP2923242A1 (en) | 2012-11-26 | 2015-09-30 | Detra SA | Lever escapement for a timepiece |
EP3120198A2 (en) * | 2014-03-21 | 2017-01-25 | Gfpi S.A. | Clockwork |
EP3208662A1 (en) * | 2016-02-08 | 2017-08-23 | Hepta Swiss SA | Clock movement comprising a regulating device |
-
2022
- 2022-05-03 EP EP22171307.6A patent/EP4273634A1/en active Pending
Patent Citations (6)
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 (en) | 1916-12-09 | 1917-06-01 | Theodore Jequier | Exhaust with reduced number of oscillations |
CH131854A (en) | 1928-04-03 | 1929-03-15 | Tavannes Watch Co Sa | Cylinder exhaust. |
EP2923242A1 (en) | 2012-11-26 | 2015-09-30 | Detra SA | Lever escapement for a timepiece |
EP3120198A2 (en) * | 2014-03-21 | 2017-01-25 | Gfpi S.A. | Clockwork |
EP3208662A1 (en) * | 2016-02-08 | 2017-08-23 | Hepta Swiss SA | Clock movement comprising a regulating device |
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