EP3602206B1 - Mechanische uhr, die ein uhrwerk mit verbesserter ganggenauigkeit durch eine korrekturvorrichtung umfasst - Google Patents

Mechanische uhr, die ein uhrwerk mit verbesserter ganggenauigkeit durch eine korrekturvorrichtung umfasst Download PDF

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Publication number
EP3602206B1
EP3602206B1 EP18710877.4A EP18710877A EP3602206B1 EP 3602206 B1 EP3602206 B1 EP 3602206B1 EP 18710877 A EP18710877 A EP 18710877A EP 3602206 B1 EP3602206 B1 EP 3602206B1
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EP
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Prior art keywords
mechanical
braking
oscillator
resonator
pulses
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EP18710877.4A
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English (en)
French (fr)
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EP3602206A1 (de
Inventor
Lionel TOMBEZ
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Swatch Group Research and Development SA
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Swatch Group Research and Development SA
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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
    • 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
    • G04B15/00—Escapements
    • G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape wheel

Definitions

  • the present invention relates to a mechanical timepiece comprising a movement the rate of which is improved by a device for correcting a possible time drift in the operation of the mechanical oscillator which rates the rate of the movement.
  • a time drift occurs in particular when the average natural oscillation period of said mechanical oscillator is not equal to a set period.
  • This reference period is determined by an auxiliary oscillator which is incorporated in the correction device.
  • Timepieces as defined in the field of the invention have been proposed in some prior documents.
  • the patent CH 597 636 published in 1977 , offers such a timepiece with reference to its figure 3 .
  • the movement is equipped with a resonator formed by a sprung balance and a conventional maintenance device comprising an anchor and an escape wheel in kinematic connection with a barrel provided with a spring.
  • This watch movement further comprises an electronic device for regulating the frequency of its mechanical oscillator.
  • This regulation device comprises an electronic circuit and a magnetic assembly formed of a flat coil, arranged on a support under the rim of the balance, and two magnets mounted on the balance and arranged close to each other so as to both pass over the coil when the oscillator is on.
  • the electronic circuit comprises a time base comprising a quartz resonator and serving to generate a reference frequency signal FR, this reference frequency being compared with the frequency FG of the mechanical oscillator.
  • the detection of the FG frequency of the oscillator is carried out via the electrical signals generated in the coil by the pair of magnets.
  • the regulation circuit is designed to be able to momentarily generate a braking torque via a magnet-coil magnetic coupling and a switchable load connected to the coil.
  • the aim is to synchronize the frequency of the mechanical oscillator with that of a quartz oscillator by an interaction between the finger and the stop when the mechanical oscillator exhibits a time drift relative to a frequency of instruction, the finger being provided to be able to either momentarily block the balance which is then stopped in its movement for a certain time interval (the stop resting against the finger moved in its direction during a return of the balance in the direction of its neutral position), or limit the amplitude of oscillation when the finger arrives against the stop while the balance turns in the direction of one of its two extreme angular positions (defining its amplitude), the finger then stopping the oscillation and the balance starting directly in the opposite direction.
  • the movement of the finger is provided to make it possible to stop the balance by contact with the stopper, but the finger is arranged so as not to come into contact with the rim of the balance.
  • the instant of an interaction between the finger and the stopper also depends on the amplitude of the oscillation of the sprung balance.
  • the desired synchronization appears improbable. This is because, in particular for a sprung balance whose frequency is greater than the setpoint frequency timing the back and forth movements of the finger and with a first interaction between the finger and the stopper which momentarily retains the balance returning from one of its two extreme angular positions (correction reducing the error), the second interaction, after numerous oscillations without the stop touching the finger during its reciprocating movement, will certainly stop the balance by the finger with immediate reversal of its direction of motion. oscillation, by the fact that the stop abuts against the finger while the balance rotates in the direction of said extreme angular position (correction increasing the error).
  • An aim of the present invention is to find a solution to the technical problems and drawbacks of the prior art mentioned in the technological background.
  • a general aim of the invention is to find a device for preventing a potential temporal drift of a mechanical movement, namely a device for regulating its rate in order to increase its precision, without however giving up the need for it. can operate autonomously with the best precision that it is possible for it to have thanks to its own characteristics, that is to say in the absence of the regulation device or when the latter is inactive.
  • Another object of the present invention is to achieve the aforementioned objects without having to incorporate electrical and / or electronic devices in the timepiece according to the invention, that is to say by using organs and systems specific to so-called mechanical watches, the latter being able to integrate, according to various developments in the field of mechanical watchmaking, magnetic elements such as magnets and ferromagnetic elements, but no devices requiring an electrical power supply and therefore a source of electrical energy.
  • the present invention relates to a timepiece as defined in independent claim 1 attached.
  • the mentioned mechanical system is configured so that said range of positions of the mechanical resonator of the slave oscillator, in which the periodic braking pulses can start, also extends from the second to both sides of the neutral position. of said mechanical resonator over at least a second range of amplitudes that the slave oscillator is likely to have of this second side, along the general axis of oscillation, for the useful operating range of this mechanical oscillator.
  • each of the two parts of the range of positions of the mechanical resonator identified above, respectively incorporating the first and second ranges of the amplitudes that the slave oscillator is capable of having respectively on both sides of the neutral position of its mechanical resonator has a certain extent over which it is continuous or almost continuous.
  • the mechanical braking device is arranged so that the periodic braking pulses each essentially have a duration of less than a quarter of the setpoint period corresponding to the inverse of the setpoint frequency.
  • the periodic braking pulses have a duration of less than 1/10 of the reference period.
  • the duration of the periodic braking pulses is essentially planned to be less than 1/40 of the reference period.
  • the mechanical regulation device constitutes a device for synchronizing the slave mechanical oscillator on the master mechanical oscillator, and this without closed-loop control and without a sensor for measuring the movement of the mechanical oscillator.
  • the mechanical regulation device therefore operates in an open loop and it makes it possible to correct both an advance and a delay in the natural course of the mechanical movement, as will be explained subsequently. This result is quite remarkable.
  • the operation of regulation device is such that the braking frequency derived from the reference frequency of the master oscillator is imposed on the slave oscillator which rates the operation of the indicator mechanism of a temporal datum.
  • the braking frequency of the mechanical braking pulses determines the average frequency of the slave oscillator.
  • timing the operation of a mechanism' is understood the fact of timing the movement of the movable elements of this mechanism when it is operating, in particular of determining the speeds of rotation of its wheels and thus of at least one indicator of a temporal data.
  • the mechanical system formed by the mechanical resonator and the mechanical braking device is configured so as to allow the mechanical braking device to start, in the useful operating range of the slave mechanical oscillator, a pulse of mechanical braking substantially at any time during the period of natural oscillation of this slave mechanical oscillator.
  • one of the periodic braking pulses can start at substantially any position of the mechanical resonator of the slave mechanical oscillator along the general axis of oscillation of this mechanical resonator.
  • the braking pulses have a dissipative character because part of the energy of the oscillator is dissipated by these braking pulses.
  • the mechanical braking torque is applied substantially by friction, in particular by means of a mechanical braking member exerting a certain pressure on a braking surface of the mechanical resonator which has a certain extent (not point). along the axis of oscillation.
  • the braking pulses exert a braking torque on the slave resonator, the value of which is intended not to temporarily block this slave resonator during periodic braking pulses.
  • the mechanical system mentioned above is arranged to allow the mechanical braking torque generated by each of the braking pulses to be applied to the slave resonator during a continuous or quasi-continuous time interval (non-zero or one-off). , but having a certain significant duration).
  • a mechanical timepiece 2 comprises a mechanical watch movement 4 which comprises a mechanism 12 indicating time data.
  • the mechanical movement also includes a mechanical resonator 6, formed by a balance 8 and a hairspring 10, and a main device for maintaining this mechanical resonator which is formed by a main escapement.
  • This main escapement 14 and the mechanical resonator 6 form a mechanical oscillator 18 which rates the operation of the indicator mechanism.
  • the main escapement 14 is formed for example by an anchor and an escapement wheel which is kinematically connected to a main source of mechanical energy 16.
  • the mechanical resonator is capable of oscillating around a neutral position (position of rest / zero angular position) corresponding to its state of minimum potential energy, along a circular axis whose radius corresponds for example to the outer radius of the rim 9 of the balance.
  • a neutral position position of rest / zero angular position
  • the radius of the circular axis is here irrelevant. It defines a general axis of oscillation which indicates the nature of the movement of the mechanical resonator, which may for example be linear in another particular embodiment.
  • the timepiece 2 further comprises a mechanical device 20 for correcting a possible temporal drift in the operation of the mechanical oscillator 18, this mechanical correction device comprising for this purpose a mechanical braking device 24 and a mechanical oscillator master 22 (hereinafter also called 'master oscillator').
  • the master oscillator is associated / coupled to the mechanical braking device to provide it with a reference frequency which gives rhythm to its operation and determines the braking frequency of the mechanical braking pulses supplied by the mechanical braking device.
  • the master oscillator 22 is an auxiliary mechanical oscillator insofar as the main mechanical oscillator, which directly rates the rate of the watch movement, is the mechanical oscillator 18, the latter thus being a slave oscillator.
  • the auxiliary mechanical oscillator is by nature or by construction more precise than the main mechanical oscillator.
  • the master oscillator 22 is associated with a mechanism for equalizing the force exerted on it to maintain its oscillation.
  • the master oscillator 22 comprises an auxiliary mechanical resonator 28, conventionally formed here by a balance 30 and a hairspring, and an auxiliary maintenance device formed by an auxiliary escapement 32, which comprises for example an anchor 33 and an escape wheel 34 which rotates in steps, one step being taken at each alternation of the master oscillator.
  • the braking device 24 comprises a control mechanism 48 and a braking pulse generator mechanism 50 (also called ' pulse generator 'hereinafter) arranged to generate mechanical braking pulses at a braking frequency determined by the control mechanism.
  • This control mechanism comprises a control wheel 37, which is integral with a mobile 36 or forming the latter.
  • the braking pulse generator mechanism comprises a braking member, formed by a pivoting member 40, and a spring 44 associated with the pivoting member.
  • the mobile 36 is kinematically connected to an auxiliary source of mechanical energy 26.
  • This mobile 36 is a mobile for transmitting mechanical energy from the auxiliary source 26, on the one hand, to the master oscillator 22 and, on the other hand, on the other hand, to the braking pulse generator 50.
  • This is an advantageous variant insofar as the mechanical correction device requires a single source of mechanical energy.
  • the escapement 32 maintains the resonator 28 via the mobile 36 which meshes with a pinion of the escape wheel 34, the latter communicates to the mobile 36 a rhythm and therefore determines its average angular speed (because it advances step by step) , which is a function of the reference frequency of the master oscillator.
  • the pivoting member 40 is mounted on an axis of rotation 43 and thus forms a rocker with two arms.
  • the first end 41 of the rocker cooperates with the control wheel 37, which carries pins 38 arranged so as to come successively into contact with said first end to actuate the rocker so as to first arm the generator. pulses by pressing laterally against this first end so as to cause the lever to pivot by compressing the spring 44.
  • the pulse generator is therefore armed during the step-by-step advance of the control wheel up to one step for triggering a braking pulse when the pin in contact with the first end passes beyond this first end which is then released.
  • the braking device will be adjusted so that this release takes place clearly during a determined pitch of the control wheel.
  • the rocker 40 here forms a kind of hammer.
  • the lever 40 has at its second end a relatively rigid leaf spring 42 which forms a brake shoe.
  • the lever is driven in rotation, thanks to the pressure exerted by the spring 44 then compressed, in the direction of the rim 9 of the balance and the leaf spring undergoes a relatively radial movement. to the axis of rotation of the balance when it approaches the rim.
  • the pulse generator is configured so that the braking pad comes into contact with the lateral surface 46 of the rim 9 during the first swing of the lever following its release and so that it thus exerts on the balance a certain torque of force to brake it momentarily.
  • the braking pulse generator is preferably configured so that the movement of the rocker is sufficiently damped so as to avoid rebounds which would generate a series of braking pulses instead of having a single braking pulse at the frequency of. braking. However, this damping is adjusted so that the braking pad comes into contact with the balance during the first swing of the lever following its release.
  • the brake pulse generator is arranged so that the periodic brake pulses can have a certain duration, mainly by dynamic dry friction.
  • the stiffness and mass of the leaf spring 42 can be suitably selected.
  • the leaf spring 42 makes it possible to absorb the shock during the impact of the latter on the balance while prolonging the contact time and by causing friction braking between this leaf spring and the braking surface provided on the balance.
  • other parameters of the pulse generator will be advantageously adjusted, in particular the length of each of its two arms and the position of the anchoring of the spring on one of its two arms.
  • the balance of the master resonator is mounted on flexible blades.
  • the anchor of the escapement can be formed of flexible blades defining a bistable system and not include a pivoted shaft.
  • the coupling between the anchor and the escape wheel is magnetic. In this case, we have a magnetic escapement with stopper. Any high precision mechanical oscillator can therefore be incorporated into a timepiece according to the invention.
  • the master oscillator 22 oscillates at a natural frequency of 10 Hz and has an intrinsic precision greater than the slave oscillator 18 whose setpoint frequency is equal to 3 Hz.
  • the escape wheel 34 has twenty. teeth and so it performs a half turn per second (1/2 turn / s).
  • the control wheel carries five pins 38 regularly spaced on its rim.
  • the reduction ratio between the pinion of the escape wheel and the drive wheel being set here at 7.5 (6-tooth pinion and wheel with 45 teeth), the control wheel 37 performs 1/15 of a revolution per second (1 / 15 revolutions / s) and the pulse generator is therefore armed and released every third of a second, thus generating braking pulses at a frequency of 1/3 Hz (called 'braking frequency').
  • the mechanical correction device 20 generates a mechanical braking pulse every nine setpoint periods, which corresponds substantially to one pulse per nine periods of the main oscillator, the natural frequency of which is best adjusted to the reference frequency.
  • the synchronization obtained by the mechanical correction device according to the invention will be described in detail below.
  • the control wheel In a variant, provision is made for the control wheel to carry only one pin so as to generate a single braking pulse per revolution.
  • the braking frequency is equal to 1/15 Hz and a braking pulse occurs every forty-five reference periods.
  • the control wheel has two diametrically opposed pins. In this case, the braking frequency is equal to 2/15 Hz and a braking pulse occurs every twenty-two and a half periods, that is to say only every forty-five vibrations (odd number) of the main slave oscillator 18.
  • the mechanical braking device 24 is designed to be able to periodically apply to the mechanical resonator 6 braking pulses at a braking frequency selected only as a function of the setpoint frequency for the main slave oscillator and determined by the oscillator.
  • auxiliary master 22 The mechanical braking device comprises a braking member capable of momentarily coming into contact with a braking surface of the slave mechanical resonator 6.
  • the braking member is movable and exhibits a back-and-forth movement. - comes which is controlled by a mechanical control device which periodically actuates it at a braking frequency, so that the braking member periodically comes into contact with the braking surface of the slave mechanical resonator to apply braking pulses to it .
  • the mechanical system formed of the slave mechanical resonator 6 and the mechanical braking device 24, is configured so to allow the mechanical braking device to be able to start the periodic braking pulses at any position of the slave mechanical resonator at least within a certain continuous or quasi-continuous range of positions through which this slave mechanical resonator is likely to pass along its general axis of oscillation.
  • the variant shown in Figure 1 corresponds to a preferred variant in which the mechanical system is configured so as to allow the mechanical braking device to apply a mechanical braking pulse to the slave mechanical resonator at any instant of an oscillation period in the useful operating range of the slave oscillator.
  • the outer lateral surface 46 of the rim 30 defines a continuous and circular braking surface, so that the shoe 42 of the braking member 40 can exert a mechanical braking torque at any angular position of the sprung balance.
  • a braking pulse can start at any angular position of the slave mechanical resonator between the two extreme angular positions (the two amplitudes of the slave oscillator respectively on both sides of the neutral position of its mechanical resonator) that it is likely to reach when the slave oscillator is functional.
  • the braking surface may be other than the outer lateral surface of the balance rim.
  • it is the central shaft of the balance which defines a circular braking surface.
  • a shoe of the braking member is arranged so as to exert pressure against this surface of the central shaft during the application of the mechanical braking pulses.
  • the mechanical braking device 24 is arranged so that the periodic braking pulses each have essentially a duration of less than a quarter of the set period for the oscillation of the slave mechanical oscillator 18.
  • the range of values for the average braking torque is between 0.2 ⁇ Nm and 10 ⁇ Nm
  • the range of values for the duration of the braking pulses is between 5 ms and 20 ms
  • the range of values relating to the braking period for applying periodic braking pulses is between 0.5 s and 3 s.
  • the range of values for the average braking torque is between 0.1 ⁇ Nm and 5 ⁇ Nm
  • the range of values for the duration of the periodic braking pulses is between 1 ms and 10 ms
  • the range of values for the braking period is between 3 s and 60 s, ie at least once per minute.
  • the main slave oscillator is not limited to a version comprising a sprung balance and an escapement with a stopper, in particular of the Swiss lever type.
  • Other mechanical oscillators can be provided, in particular with a flexible blade balance.
  • the escapement may include a stopper or be of the continuous rotation type.
  • the auxiliary mechanical oscillator forming the master oscillator.
  • the master oscillator is the one which ultimately gives the high precision required for the operation of the mechanical movement, we will therefore seek to select for it an oscillator of the mechanical type which is as precise as possible, knowing that this oscillator does not have to drive the mechanism (s) of the watch movement, in particular a time indicator mechanism. This is illustrated by the second embodiment of the invention described below.
  • FIG. 2A To the Figure 2A is shown a second embodiment of a timepiece according to the invention.
  • the correction device is formed by a master mechanical oscillator 54 and by a mechanical braking device 56 which comprises a braking pulse generator mechanism 50 similar to that presented in the context of the first embodiment.
  • the resonator 6, similar to that of the Figure 1 , and the pulse generator 50 will not be described again here in detail.
  • the master oscillator 54 is of the magnetic escapement type. It comprises a resonator 60 formed by a balance 62 and a hairspring 66 (shown schematically). In a variant, the balance is mounted on flexible blades. This balance comprises two arms which are located on two sides of its pivot axis and which carry at their respective ends two magnets 63 and 64. These two magnets serve to couple the resonator 60 to an escape wheel 68. This wheel of escapement and the magnets 63 and 64 form the magnetic escapement of the master oscillator 54.
  • the escape wheel comprises a magnetic structure formed of two annular tracks 70 and 72.
  • Each of the two annular tracks has an alternation of annular sectors 74 and 76, a sector 74 and an adjacent sector 76 together defining an angular period of the magnetic structure.
  • the two tracks are angularly out of phase by half a period.
  • a sector 74 has at least one physical characteristic or defines at least one physical parameter, relative to the magnets carried by the balance, which is different from a similar physical characteristic of a sector 76 or from a similar physical parameter. defined by a sector 76.
  • the magnetic potential for any of the two magnets passing over a sector 74 is different from the magnetic potential it has when passing over a sector 76.
  • the escape wheel turns, it generates a rocking of the resonator 60 at its own oscillation frequency (natural frequency) which then imposes a continuous speed of rotation on the escape wheel as a function of the value of this frequency of oscillation, here called 'reference frequency'.
  • the escape wheel advances by one angular period of the magnetic structure per period of oscillation of the balance 62. It will be noted that if it is the resonator which is directly excited and that it oscillates at its resonant frequency (natural frequency ), then the escape wheel is rotated at the aforementioned continuous rotational speed. By continuous speed of rotation, it is understood here that the wheel turns without stopping; but there may be a periodic variation in speed.
  • the sectors 74 are formed of a ferromagnetic material while the sectors 76 are formed of a non-magnetic material.
  • the sectors 74 are formed from a magnetic material while the sectors 76 are formed from a non-magnetic material.
  • the sectors 74 are formed from a material magnetized in a first direction while the sectors 76 are formed from a material magnetized in a second direction opposite to the first direction (opposite polarities). In the latter case, each of the two magnets 63 and 64 undergoes a force of magnetic repulsion above one of the two sectors and a force of magnetic attraction above the other sector.
  • Other improved variants are described in the patent application EP 2,891,930 . One can refer to this document to understand more in depth the operation of the master oscillator 54.
  • the escape wheel carries at its periphery a finger 58 arranged to be able to actuate the pulse generator 50 on each revolution made by the escape wheel.
  • This finger belongs to the braking device 56 and its role is similar to a pin 38 of the first embodiment. So, the escape wheel and the actuating finger 58 together form a control mechanism for the pulse generator 50.
  • a sequence of the operation of the correction device of the second embodiment is given to Figures 2A to 2D .
  • the pulse generator 50 is at rest and the actuating finger 58 gradually rotates in its direction.
  • the actuating finger has come into contact with the end 41 of the rocker 40 and the latter has started to rotate in a clockwise direction.
  • the pulse generator is thus armed.
  • the finger slides along the end 41 until it loses contact with this end, which releases the latch and then triggers the generation of a braking pulse, an event which is represented at the Figure 2C .
  • the spring 44 compressed beforehand drives, during a first swing, the rocker in a counterclockwise direction and the leaf spring 42, defining a brake shoe, comes to press against the braking surface 46 of the balance rim for a certain time interval.
  • the reference frequency of the master oscillator 54 is equal to 12 Hz and the magnetic structure of the escape wheel has magnetic periods of 30 °, ie 12 periods in total.
  • the braking pulse generator mechanism is therefore actuated at a braking frequency of 1 Hz because the escape wheel performs one revolution per second.
  • the number of magnetic periods is equal to 24 so that the braking frequency is then equal to 2 Hz.
  • the Figure 3 shows a third embodiment of a timepiece according to the invention.
  • Timepiece 80 (shown in part) differs from that of the Figure 1 by only a few characteristics of the main slave resonator 6A and of the braking pulse generator mechanism 50A.
  • the resonator 6A comprises a rim 9A having cavities 84 (in the general plane of the balance) in which are housed screws 82 for balancing the balance.
  • the external lateral surface 46A of the balance no longer defines a continuous circular surface, but a discontinuous circular surface with four continuous angular sectors.
  • the leaf spring 42 has a contact surface with an extent such that braking pulses remain possible for any angular position of the balance 8A, even when a cavity appears opposite the leaf spring, as shown.
  • the rocker 40A of the pulse generator 50A is held in a central part by two elastic blades 86A and 86B which extend respectively on both sides of the rocker, which can thus pivot around a fictitious axis defined by the two elastic blades.
  • the two elastic blades are fixed to two studs each having a slot in which one end of the blade is rigidly inserted.
  • a damper 88 is associated with the latch 40A so as to sufficiently dampen the oscillation of this latch, after the generation of a first braking pulse, to prevent other significant braking pulses from being applied to the resonator 6A in a braking period following this first braking pulse.
  • FIG. 4 and 5 schematically represented two alternative configurations for the general arrangement of a timepiece according to the invention.
  • the Figure 4 relates to a preferred arrangement which has been implemented in the embodiments described above.
  • a main source of mechanical energy formed by a main barrel, transmits its energy, via a main transmission, to a slave oscillator 92 and to a control mechanism. indication of the hour whose rate is clocked by this slave oscillator.
  • a braking device is arranged to brake the slave resonator, the intensity of this braking varying periodically at a braking frequency, as already explained.
  • This braking device is part of a mechanical correction device independent of the elements of the main part of the mechanical movement.
  • the mechanical correction device comprises an auxiliary source of mechanical energy formed by an auxiliary barrel which is separate from the main barrel.
  • This auxiliary barrel supplies its energy, via an auxiliary transmission, on the one hand to the master oscillator 94 and on the other hand to the braking device.
  • the energy is supplied to the braking device through the auxiliary transmission (version V1), a mobile of this auxiliary transmission forming a control mechanism of the pulse generator which not only determines the instants of triggering of the braking pulses but in addition transmits the energy necessary to arm this pulse generator.
  • it is the escape wheel which performs these two functions directly with the actuating finger (version V2).
  • This arrangement has the advantage of entirely separating the mobiles linked to the slave oscillator from the mobiles linked to the master oscillator. This makes it possible to avoid a possible coupling between the two oscillators which could possibly influence the operation and the precision of the master oscillator.
  • the only interaction expected between the slave oscillator and the master oscillator is the braking pulses.
  • the Figure 5 shows an alternative general arrangement which can be considered. It is characterized by the fact that the main part of the watch movement and the correction device have in common a single source of energy, namely a barrel supplying its energy, via a possible common transmission, to a differential mechanism which distributes this energy on the one hand to the slave oscillator 92 and to the time indication mechanism and, on the other hand, to the master oscillator 94 and to the braking device. Note that this alternative does not prevent having several barrels in series or in parallel supplying energy to the differential mechanism.
  • the first graph indicates the instant t P1 at which a braking pulse P1, respectively P2, is applied to the mechanical resonator considered in order to correct the rate of the mechanism which is clocked by the mechanical oscillator formed by this resonator.
  • the last two graphs show respectively the angular speed (values in radians per second: [rad / s]) and the angular position (values in radians: [rad]) of the oscillating member (hereinafter also 'the balance') of the mechanical resonator over time.
  • the curves 90 and 92 correspond respectively to the angular speed and to the angular position of the freely oscillating balance (oscillation at its natural frequency) before the intervention of a braking pulse.
  • the speed curves 90a and 90b are shown corresponding to the behavior of the resonator respectively in the case disturbed by the braking pulse and in the undisturbed case.
  • the position curves 92a and 92b correspond to the behavior of the resonator respectively in the case disturbed by the braking pulse and the undisturbed case.
  • the times t P1 and t P2 at which the braking pulses P1 and P2 intervene correspond to the temporal positions of the middle of these pulses.
  • the start of the braking pulse and its duration are considered as the two parameters which temporally define a braking pulse.
  • the pulses P1 and P2 are represented at figures 6 and 7 by binary signals.
  • the control pulse can occur at least in part before the application of a mechanical braking pulse.
  • the braking pulses P1, P2 correspond to the mechanical braking pulses applied to the resonator and not to previous control pulses.
  • the braking pulses can be applied with a constant force torque or a non-constant force torque (for example substantially in a Gaussian or sinusoidal curve).
  • a torque of force to the mechanical resonator which brakes its oscillating member (balance), that is to say which opposes the oscillation movement of this oscillating member.
  • the duration of the pulse is generally defined as the part of this pulse which has a significant torque force to brake the mechanical resonator. It will be noted that a braking pulse can exhibit a strong variation. It can even be chopped and form a succession of shorter pulses.
  • each braking pulse can either brake the mechanical resonator without however stopping it, as in Figures 6 and 7 , either stop it during the braking pulse and stop it momentarily during the remainder of this braking pulse.
  • Each period of free oscillation T0 of the mechanical oscillator defines a first half-wave A0 1 followed by a second half-wave A0 2 each occurring between two extreme positions defining the amplitude of oscillation of this mechanical oscillator, each half-wave having an identical duration T0 / 2 and having a passage of the mechanical resonator through its zero position at a median instant.
  • the two successive alternations of an oscillation define two half-periods during which the balance respectively undergoes an oscillating movement in one direction and then an oscillating movement in the other direction.
  • an alternation corresponds here to a swing of the balance in one direction or the other direction between its two extreme positions defining the amplitude of oscillation.
  • the braking pulse is triggered after a time interval T A1 following the instant t D1 marking the start of the alternation A1.
  • the duration T A1 is less than one half-wave T0 / 4 reduced by the duration of the braking pulse P1. In the example given, the duration of this braking pulse is much less than one half-wave TO / 4.
  • the braking pulse is therefore generated between the start of an alternation and the passage of the resonator through its neutral position in this alternation.
  • the angular speed in absolute value decreases at the moment of the braking pulse P1.
  • Such a braking pulse induces a negative time phase shift T C1 in the oscillation of the resonator, as shown in Figure 6 the two curves 90a and 90b of the angular speed and also the two curves 92a and 92b of the angular position, that is to say a delay relative to the theoretical undisturbed signal (shown in broken lines).
  • the duration of the alternation A1 is increased by a time interval T C1 .
  • the oscillation period T1 comprising the alternation A1 is therefore extended relative to the value T0. This generates a punctual reduction in the frequency of the mechanical oscillator and a momentary slowing down of the associated mechanism, the operation of which is clocked by this mechanical oscillator.
  • the braking pulse P2 at the instant t P2 which is located in the half-wave A2 after the median instant t N2 at which the resonator passes through its neutral position.
  • this alternation A2 ends at the final instant t F2 at which the resonator again occupies an extreme position (maximum positive angular position in the period T2) and therefore also before the corresponding final instant t F0 of the undisturbed oscillation.
  • the braking pulse is triggered after a time interval T A2 following the initial instant t D2 of the alternation A2.
  • the duration T A2 is greater than one half-wave T0 / 4 and less than one half-wave T0 / 2 reduced by the duration of the braking pulse P2. In the example given, the duration of this braking pulse is much less than half a wave.
  • the braking pulse is therefore generated, in an alternation, between the median instant at which the resonator passes through its neutral position (zero position) and the final instant at which this alternation ends.
  • the angular speed in absolute value decreases at the moment of the braking pulse P2.
  • the braking pulse here induces a positive time phase shift T C2 in the oscillation of the resonator, as shown in Figure 4 the two curves 90b and 90c of the angular speed and also the curves 92b and 92c of the angular position, ie an advance relative to the theoretical undisturbed signal (shown in broken lines).
  • T C2 the duration of the alternation A2 is reduced by the time interval T C2 .
  • the oscillation period T2 including the alternation A2 is therefore shorter than the value T0. This consequently generates a punctual increase in the frequency of the mechanical oscillator and a momentary acceleration of the associated mechanism, the operation of which is clocked by this mechanical oscillator. This phenomenon is surprising and not intuitive, which is why those skilled in the art have ignored it in the past. Indeed, to obtain an acceleration of the mechanism by a braking pulse is a priori surprising, but such is the case when this rate is clocked by a mechanical oscillator and the braking pulse is applied to its resonator.
  • the aforementioned physical phenomenon for mechanical oscillators is involved in the synchronization method implemented in a timepiece according to the invention. Contrary to the general teaching in the watchmaking field, it is not only possible to reduce the frequency of a mechanical oscillator by braking pulses, but it is also possible to increase the frequency of such a mechanical oscillator also by means of braking pulses. braking pulses. Those skilled in the art expects to be able to practically only reduce the frequency of a mechanical oscillator by braking pulses and, as a corollary, only to be able to increase the frequency of such a mechanical oscillator by the application of driving pulses. when energy is supplied to this oscillator.
  • the application of a braking torque during an alternation of the oscillation of a sprung balance causes a negative or positive phase shift in the oscillation of this sprung balance depending on whether this braking torque is applied respectively before or after the sprung balance has passed through its neutral position.
  • the error generated at the Figure 8B can correspond in fact to a correction for the case where the mechanical oscillator has a natural frequency which does not correspond to a reference frequency.
  • the oscillator has a too low natural frequency
  • braking pulses occurring in the second or fourth quarter of the oscillation period can allow a correction of the delay taken by the free oscillation (not disturbed), this correction being more or less strong depending on the instant of the braking pulses within the oscillation period.
  • braking pulses occurring in the first or third quarter of the oscillation period can allow a correction of the advance taken by the free oscillation, this correction being more or less strong depending on the instant of the braking pulses in the oscillation period.
  • the braking frequency is thus proportional to the setpoint frequency for the master oscillator and depends only on this reference frequency as soon as the positive integer number N is given.
  • the braking frequency is therefore proportional to the reference frequency and determined by this reference frequency, which is supplied by the auxiliary mechanical oscillator which is by nature or by construction more precise than the main mechanical oscillator.
  • the angular position of the slave mechanical resonator, in particular of the sprung balance of a watch resonator, oscillating freely (curve 100) and oscillating with braking (curve 102) is represented on the top graph.
  • the first mechanical braking pulses 104 (hereinafter also referred to as 'pulses') occur here once per oscillation period in a half-wave. between the passage through an extreme position and the passage through zero. This choice is arbitrary because the system provided does not detect the angular position of the mechanical resonator; it is therefore just one possible hypothesis among others that will be analyzed subsequently.
  • the braking torque for the first braking pulse is provided here greater than a minimum braking torque in order to compensate for the advance which the free oscillator takes over a period of oscillation. This has the consequence that the second braking pulse takes place a little before the first within the quarter of a period in which these pulses occur.
  • Curve 106 which gives the instantaneous frequency of the mechanical oscillator, in fact indicates that the instantaneous frequency decreases below the setpoint frequency from the first pulse.
  • the second braking pulse is closer to the preceding extreme position, so that the effect of braking increases and so on with the following pulses.
  • the instantaneous frequency of the oscillator therefore gradually decreases and the pulses gradually approach an extreme position of the oscillation.
  • the braking pulses include the passage through the extreme position where the speed of the mechanical resonator changes direction and the instantaneous frequency then begins to increase.
  • Braking is unique in that it opposes the movement of the resonator whatever the direction of its movement.
  • the braking torque automatically changes sign at the instant of this reversal.
  • braking pulses 104a which have, for the braking torque, a first part with a first sign and a second part with a second sign opposite to the first sign.
  • the correction then decreases to stabilize finally and relatively quickly at a value for which the instantaneous frequency of the oscillator is equal to the reference frequency (corresponding here to the braking frequency).
  • the transient phase is followed by a stable phase, also called synchronous phase, where the oscillation frequency is substantially equal to the setpoint frequency and where the first and second parts of the braking pulses have a substantially constant and defined ratio.
  • the graphs of the Figure 10 are analogous to those of Figure 9 .
  • the first pulses 104 occur in the same half-wave as at the Figure 9 .
  • the oscillation with braking 108 therefore momentarily takes even more delay in the transient phase, this until the pulses 104b begin to encompass the passage of the resonator. by an extreme position. From this moment, the instantaneous frequency begins to increase until it reaches the setpoint frequency, because the first part of the pulses occurring before the extreme position increases the instantaneous frequency. This phenomenon is automatic.
  • the graphs of the Figure 11 are analogous to those of Figure 10 .
  • the major difference comes from the fact that the first braking pulses 114 occur in a different half-wave than at the Figure 10 , namely in a half-cycle between the passage through zero and the passage through an extreme position.
  • an increase in the instantaneous frequency given by the curve 112 is observed here in a transient phase.
  • the braking torque for the first braking pulse is here provided greater than a minimum braking torque to compensate for the braking torque. delay that the free mechanical oscillator takes over a period of oscillation. The consequence of this is that the second braking pulse takes place a little after the first within the quarter period in which these pulses occur.
  • Curve 112 in fact indicates that the instantaneous frequency of the oscillator increases above the reference frequency from the first pulse.
  • the second braking pulse is closer to the following extreme position, so that the effect of braking increases and so on with the following pulses.
  • the instantaneous frequency of the oscillation with braking 114 therefore increases and the braking pulses gradually approach an extreme position of the oscillation.
  • the braking pulses include passing through the extreme position where the speed of the mechanical resonator changes direction. From that moment, we have a phenomenon similar to that explained above.
  • the braking pulses 114a then have two parts and the second part decreases the instantaneous frequency.
  • the Figure 12 represents a period of oscillation with the curve S1 of the positions of a mechanical resonator.
  • the natural oscillation frequency F0 of the free mechanical oscillator (without braking pulses) is greater than the reference frequency F0c (F0> F0c).
  • the oscillation period conventionally comprises a first alternation A1 followed by a second alternation A2, each between two extreme positions (t m-1 , A m-1 ; t m , A m ; t m + 1 , A m + 1 ) corresponding to the oscillation amplitude. Then, there is shown, in the first half wave, a braking pulse 'Imp1' whose middle time position occurs at an instant t 1 and, in the second half wave, another braking pulse 'Imp2' whose middle time position occurs at a time t 2 .
  • the pulses Imp1 and Imp2 have a phase shift of T0 / 2, and they are specific because they correspond, for a given profile of the braking torque, to corrections generating two unstable balances of the system. As these pulses intervene respectively in the first and the third quarter of the oscillation period, they therefore brake the mechanical oscillator to an extent which makes it possible to correct exactly the too high natural frequency of the free mechanical oscillator (with the frequency of brake selected for applying the brake pulses). Note that the pulses Imp1 and Imp2 are both first pulses, each being considered for itself in the absence of the other. It will be noted that the effects of the pulses Imp1 and Imp2 are identical.
  • the Figure 13 shows the synchronous phase corresponding to a final stable situation occurring after the transient phase described above.
  • this extreme position will lock onto the braking pulses as long as these braking pulses are configured (the force torque and the duration) to be able to sufficiently correct the time drift of the free mechanical oscillator at least by a braking pulse occurring entirely, as the case may be, just before or just after an extreme position.
  • a first pulse occurs in the first half wave A1
  • either the extreme position A m-1 of the oscillation is set on the pulses Imp1a, or the extreme position A m of the oscillation is set on the Imp1b pulses.
  • the pulses Imp1a and Imp1b each have a first part whose duration is shorter than that of their second part, so as to correct exactly the difference between the too high natural frequency of the oscillator main slave and the setpoint frequency imposed by the master auxiliary oscillator.
  • the pulses Imp1a and Imp1b each have a first part whose duration is shorter than that of their second part, so as to correct exactly the difference between the too high natural frequency of the oscillator main slave and the setpoint frequency imposed by the master auxiliary oscillator.
  • the pulses Imp1a, respectively Imp1b, Imp2a and Imp2b occupy stable relative temporal positions. Indeed, a slight deviation to the left or to the right of one of these pulses, due to an external disturbance, will have the effect of bringing a following pulse back to the initial relative time position. Then, if the time drift of the mechanical oscillator varies during the synchronous phase, the oscillation will automatically undergo a slight phase shift so that the ratio between the first part and the second part of the pulses Imp1a, respectively Imp1b, Imp2a and Imp2b varies to an extent which adapts the correction generated by the braking pulses to the new frequency difference. Such behavior of the timepiece according to the present invention is truly remarkable.
  • the Figures 14 and 15 are similar to Figures 12 and 13 , but for a situation where the natural frequency of the oscillator is lower than the reference frequency. Consequently, the impulses Imp3 and Imp4, corresponding to an unstable equilibrium situation in the correction made by the braking pulses, are respectively located in the second and the fourth quarter of a period (instants t 3 and t 4 ) where the pulses generate an increase in the oscillation frequency.
  • the explanations in detail will not be given here again because the behavior of the system follows from the preceding considerations.
  • the impulses Imp3a and Imp3b each have a first part whose duration is longer than that of their second part, so as to correct exactly the difference between the too low natural frequency of the oscillator main slave and the setpoint frequency imposed by the master auxiliary oscillator.
  • the correction device The invention is efficient and rapidly synchronizes the frequency of the mechanical oscillator, timing the operation of the mechanical movement, on the reference frequency which is determined by the reference frequency of the master auxiliary oscillator, which controls the braking frequency at which the Braking pulses are applied to the resonator of the mechanical oscillator. This remains true if the natural frequency of the mechanical oscillator varies and even if it is, in certain periods of time, higher than the reference frequency, while in other periods of time it is lower than this reference frequency.
  • the teaching given above and the synchronization obtained by virtue of the characteristics of the timepiece according to the invention also apply in the case where the braking frequency for the application of the braking pulses is not equal to the setpoint frequency.
  • the pulses taking place at unstable positions correspond to corrections for compensate for the time drift during a single period of oscillation.
  • the planned braking pulses have a sufficient effect to correct a time drift during several periods of oscillation, it is then possible to apply a single pulse per time interval equal to these several periods of oscillation.
  • the Figures 16 and 17 show the synchronous phase for a variant with a braking frequency F FR equal to a quarter of the reference frequency, a braking pulse therefore occurring every four oscillation periods.
  • the Figures 18 and 19 are partial enlargements respectively of Figures 16 and 17 .
  • the braking pulses generate a phase shift only in the corresponding periods.
  • the instantaneous periods are measured from a zero crossing on a rising edge of the oscillation signal to such a next crossing.
  • the synchronous pulses which occur at the extreme positions are entirely included in periods of oscillation.
  • the Figure 20 shows the specific case where the natural frequency is equal to the reference frequency.
  • the oscillation periods T0 * all remain equal, the braking pulses Imp5 occurring exactly at the extreme positions of the free oscillation with the first and second parts of these pulses which have identical durations (case of a constant braking torque), so that the effect of the first part is canceled by the opposite effect of the second part.
  • This error is very important, but the braking device is configured to allow correcting such an error.
  • the effect of the braking having to be relatively large here, there is a large variation in the instantaneous period but the average period is substantially equal to the set period after the engagement of the correction device in the timepiece according to the invention. and a short transitional phase.
  • the total time error increases linearly as a function of time, whereas this error stabilizes rapidly after switching on the correction device.
  • the total error also called 'cumulative error'
  • the timepiece indicates by the following one hour with an accuracy corresponding to that of the oscillator master incorporated in this timepiece and associated with the braking device.
  • the Figure 22 shows the evolution of the amplitude of the slave mechanical oscillator after the engagement of the correction device according to the invention.
  • the transient phase a relatively marked decrease in amplitude is observed in a case where the first pulse takes place close to the zero position (neutral position).
  • the various braking pulses occurring in particular in a first part of this transient phase generate relatively large energy losses, this resulting from the graph of the Figure 8C .
  • the energy losses decrease quickly enough to finally become minimal for a given correction in the synchronous phase.
  • the part according to the invention has the additional benefit of stabilizing in a synchronous phase for which the energy dissipated by the oscillator, due to the braking pulses provided, is minimal. Indeed, the oscillator has after stabilization of its amplitude the smallest possible decrease in amplitude for the braking pulses provided.
  • the device for correcting the rate of a mechanical movement which generates synchronization according to the invention therefore has a minimized influence on the power reserve.
  • the braking pulses each have a duration less than 1/10 of the reference period.
  • the braking pulses each have a duration of between 1/250 and 1/40 of said set period. In the latter case, for a reference frequency equal to 4 Hz, the duration of the pulses is between 1 ms and 5 ms.
  • timepieces with mechanical resonators having a circular braking surface allowing the braking device to apply a mechanical braking pulse to the slave mechanical resonator substantially at any time of an oscillation period in the range useful operating time of the slave oscillator.
  • watch movements generally have balances having a circular rim with an advantageously continuous outer surface
  • the preferred variant indicated above can be easily implemented in such movements without requiring modifications to their mechanical oscillator. It will be understood that this preferred variant makes it possible to minimize the duration of the transition phase and to ensure the desired synchronization as quickly as possible.
  • the stable synchronization can already be obtained, after a certain period of time, with a mechanical system, formed of the slave mechanical resonator and the mechanical braking device, which is configured in such a way as to allow the mechanical braking device to be able to start the brakes.
  • periodic braking pulses at any position of the slave mechanical resonator only within a continuous or quasi-continuous range of positions of this defined resonator, from a first to both sides of the neutral position of the slave mechanical resonator, by the amplitude range of the slave oscillator for its useful operating range.
  • this range of positions is increased, on the side of the minimum amplitude, at least by an angular distance corresponding to the duration of a braking pulse, so as to allow for a minimum amplitude a braking pulse by a dynamic dry friction. So that the mechanical system can act in all the alternations and not only in all the periods of oscillation, it is then necessary that this mechanical system be configured in such a way as to allow the mechanical braking device to be able to also start the periodic braking pulses. at any position of the second mechanical resonator on both sides of said neutral position, within the range of amplitudes of the slave mechanical oscillator for its useful operating range.
  • the range of positions is also increased, on the side of the minimum amplitude, at least by an angular distance corresponding substantially to the duration of a braking pulse.
  • the aforementioned continuous or quasi-continuous range of positions of the slave mechanical resonator extends, from a first to both sides of its neutral position, at least over the range of amplitudes that the slave oscillator is capable of having on this first side for a useful operating range of this slave oscillator and advantageously in addition, on the side of a minimum amplitude of the range of amplitudes, at least over an angular distance corresponding substantially to the duration of the pulses of braking.
  • the aforementioned mechanical system is configured so as to allow the mechanical braking device also to be able to start the periodic braking pulses at any position of the slave mechanical resonator, on the second on both sides of its neutral position, at least in a second continuous or quasi-continuous range of positions of this slave mechanical resonator extending over the range of amplitudes that the slave oscillator is likely to have on this second side for said useful operating range and advantageously in addition, on the side of a minimum amplitude of the latter range of amplitudes, at least over said first angular distance.
  • two categories of periodic braking pulses can be distinguished in relation to the intensity of the mechanical force torque applied to the slave mechanical resonator and the duration of the periodic braking pulses.
  • the braking torque and the duration of the braking pulses are provided, for the useful operating range of the slave oscillator, so as not to temporarily block the slave mechanical resonator during the periodic braking pulses at less in most of the eventual transitional phase that was previously described.
  • the system is arranged so that the mechanical braking torque can be applied to the slave mechanical resonator, at least in said major part of the possible transient phase, during each braking pulse.
  • the oscillating member and the braking member are arranged so that the periodic braking pulses can be applied, at least in said major part of the possible transitional phase, mainly by dynamic dry friction between the braking member and a braking surface of the oscillating member.
  • the mechanical braking torque and the duration of the periodic braking pulses are provided so as to block the mechanical resonator during periodic braking pulses at least in their terminal part.
  • FIG. 23A to 23C is shown a sequence of the operation of a correction device in a fourth embodiment of a timepiece according to the invention. Only the main slave resonator 6 and the mechanical correction device 52A have been shown.
  • the correction device is formed by a master auxiliary oscillator 96 and by a braking device 56A, similar to that presented in the context of the first embodiment, which comprises a braking pulse generator mechanism 50A.
  • the master oscillator 96 is related to the oscillator 54 of the second embodiment. Its operation is similar and will not be described here again. It is distinguished by its resonator 98 formed by a tuning fork which carries at the free ends of its two vibrating branches respectively two magnets 99 and 100 which have an axial magnetization.
  • the tuning fork serves to couple the resonator 98 to an escape wheel 68.
  • the escape wheel and the two magnets form the magnetic escape of the master oscillator 96.
  • the tuning fork exhibits a fundamental resonance mode with its two branches oscillating in phase opposition and that the two magnets 99 and 100 that it carries are arranged at rest in a diametrically opposed manner relative to the axis of rotation of the escape wheel, the number of magnetic periods of the magnetic structure of the escape wheel is provided pair.
  • the tuning fork may have a relatively high natural frequency, so that it is envisaged in a variant to arrange the actuating finger 58 on a mobile of an auxiliary transmission gear for the mechanical energy necessary for the operation of the control device. correction 52A, this mobile rotating at a slower speed than the escape wheel 68.
  • the operation of the correction device differs from that of the previous embodiments in that the control mechanism formed by the escape wheel 68 and the actuating finger 58 acts at the reverse on the braking pulse generator mechanism 50A.
  • the control mechanism formed by the escape wheel 68 and the actuating finger 58 acts at the reverse on the braking pulse generator mechanism 50A.
  • the force of the spring 44A can here be very low, but preferably sufficient damping is provided to prevent oscillation of the lever, following its release, generating a second parasitic braking pulse during the braking period following the first pulse.
  • the duration of the braking pulses is determined by the angular distance over which the actuating finger remains in contact with the end of the lever following the instant when the leaf spring touches the braking surface. This angular distance can be adjusted to a given value by an adjustment in particular of the length of the actuating finger. It will be noted that the braking torque increases here during the braking pulse and then decreases almost instantly as soon as the latch is released. This torque can be adjusted to a given value in particular as a function of the rigidity of the leaf spring and the length ratio between the two arms of the lever.
  • FIG. 24A to 24C a sequence of the operation of a correction device in a fifth embodiment of a timepiece according to the invention. Only the main slave resonator 6 and part of the mechanical correction device have been shown.
  • the correction device is formed by a master auxiliary oscillator 22A, of which only the escape wheel 34A has been shown (its resonator and the anchor being similar to those shown in Figure 1 ), and by a braking device 56A.
  • the escape wheel rotates step by step with an angular speed determined by the reference frequency of the master resonator.
  • the braking device comprises a braking pulse generator mechanism 50A similar to that presented above in the context of the fourth embodiment. This pulse generator operates in the same way as that of the fourth embodiment.
  • the control mechanism 48A of the braking device is formed here by the escape wheel and by two pins 38 fixed to this wheel in a diametrically opposed manner.
  • the control mechanism advances in steps.
  • the generation of a braking pulse is provided during a step of the escape wheel ( Figure 24B ).
  • This wheel has for example 15 teeth and the master oscillator 22A operates at a reference frequency of 7.5 Hz.
  • the escape wheel performs 1/2 revolution per second so that the braking pulses are performed at a frequency of braking of 1 Hz.
  • the wheel 34A takes two steps and advances an angular distance equal to 24 °, so that at least one of the two steps corresponds to a rotation of at least 12 °.
  • the end 41 of the rocker 40 is configured and positioned relative to the circle described by the rotating pins 38 so as to allow the braking pulse to be fully effected during a given pitch of the control wheel. It will be noted that it is advantageous that the lever is already moved in rotation during a step of the control wheel preceding that which occurs to generate a braking pulse. In this case, care will be taken to arrange the braking device so that the leaf spring 42 rotates in the direction of the braking surface 46 of the balance during of said previous step without touching this braking surface, but stopping a short distance from it ( Figure 24A ).
  • the Figures 24A to 24C show three configurations of the braking device occurring over a reference period during which the escape wheel performs two successive steps.
  • the figure 24A represents a first state of the braking device at the end of a determined pitch of the wheel 34A.
  • the Figure 24B represents a second state of the braking device during a first step directly following said determined step (application of a braking pulse to the balance 8).
  • the Figure 24C corresponds to a third state where the wheel 34A has completed the first step shown in Figure 24B , before a second step takes place directly following said first step. Since during a step, the wheel 34A turns very quickly (free rotation), the duration of the braking pulses can thus be relatively short.

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Claims (23)

  1. Uhr (2, 80), die ein mechanisches Werk (4) umfasst, das Folgendes umfasst:
    - einen Mechanismus (12) zur Anzeige mindestens eines Zeitdatums,
    - einen mechanischen Resonator (6, 6A), der in der Lage ist, entlang einer allgemeinen Oszillationsachse um eine neutrale Position (0) herum zu oszillieren, die seinem potenziellen Mindestenergiezustand entspricht,
    - eine Vorrichtung (14) zur Instandhaltung des mechanischen Resonators, die mit diesem mechanischen Resonator einen mechanischen Oszillator (18) bildet, der angeordnet ist, um den Gang des Mechanismus zur Anzeige zu rhythmisieren;
    wobei die Uhr weiter eine Vorrichtung zum Regeln der mittleren Frequenz des mechanischen Oszillators umfasst;
    dadurch gekennzeichnet, dass die Vorrichtung zum Regeln (20, 52, 52A) vom Typ mechanisch ist, wobei diese mechanische Vorrichtung zum Regeln durch einen mechanischen Hilfsoszillator (22, 22A, 54, 96) gebildet wird, welcher einen Meister-Oszillator definiert, und durch eine mechanische Bremsvorrichtung (24, 56, 56A) des mechanischen Resonators; und dadurch, dass die mechanische Bremsvorrichtung angeordnet ist, um während periodischer Bremsimpulse, die mit einer Bremsfrequenz generiert werden, die nur in Abhängigkeit von einer Vorgabefrequenz für den mechanischen Oszillator ausgewählt wird, welcher einen Slave-Oszillator definiert, und durch den Meister-Oszillator bestimmt wird, ein dissipatives mechanisches Bremsmoment an den mechanischen Resonator (6, 6A) anzulegen, wobei das aus dem mechanischen Resonator und die mechanische Bremsvorrichtung gebildete mechanische System derart konfiguriert ist, um es der mechanischen Bremsvorrichtung (24, 56, 56A) zu ermöglichen, die periodischen Bremsimpulse in irgendeiner Position des mechanischen Resonators in einem Bereich von Positionen entlang der allgemeinen Oszillationsachse beginnen zu können, die sich mindestens von einer ersten der beiden Seiten der neutralen Position des mechanischen Resonators erstreckt über mindestens einen Bereich von Amplituden erstreckt, den der Slave-Oszillator von dieser ersten Seite für einen Nutzbetriebsbereich dieses Slave-Oszillators in der Lage ist, aufzuweisen.
  2. Uhr nach Anspruch 1, dadurch gekennzeichnet, dass ein erster Teil des Bereichs von Positionen des mechanischen Resonators, der den Bereich von Amplituden einbezieht, den der mechanische Oszillator von der ersten Seite der neutralen Position des mechanischen Resonators in der Lage ist, aufzuweisen, eine bestimmte Ausdehnung aufweist, auf der er kontinuierlich oder quasi kontinuierlich ist, wobei sich dieser erste Teil auf Seiten einer Mindestamplitude des Bereichs von Amplituden, mindestens über einen Winkelabstand erstreckt, der im Wesentlichen der Dauer eines der periodischen Bremsimpulse für diese Mindestamplitude entspricht.
  3. Uhr nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das mechanische System derart konfiguriert ist, dass sich der Bereich von Positionen des mechanischen Resonators, in dem die periodischen Bremsimpulse beginnen können, auch von der zweiten der beiden Seiten der neutralen Position des mechanischen Resonators auf mindestens einem Bereich von Amplituden erstreckt, den der mechanische Oszillator von dieser zweiten Seite für den Nutzbetriebsbereich dieses mechanischen Oszillators in der Lage ist, aufzuweisen.
  4. Uhr nach Anspruch 3, dadurch gekennzeichnet, dass ein zweiter Teil des Bereichs von Positionen des mechanischen Resonators, der den Bereich der Amplituden einbezieht, den der mechanische Oszillator von der zweiten Seite der neutralen Position des mechanischen Resonators in der Lage ist aufzuweisen, eine bestimmte Ausdehnung aufweist, auf der er kontinuierlich oder quasi kontinuierlich ist, wobei sich dieser zweite Teil auf Seiten einer Mindestamplitude des Bereichs von Amplituden erstreckt, den der mechanische Oszillator von der zweiten Seite der neutralen Position mindestens auf einem Winkelabstand in der Lage ist, aufzuweisen, der im Wesentlichen der Dauer eines der periodischen Bremsimpulse für diese Mindestamplitude entspricht.
  5. Uhr nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die Bremsfrequenz gleich oder doppelt so groß wie die Vorgabefrequenz geteilt durch eine positive ganze Zahl N, also FFR = 2-F0c/N vorgesehen ist, wobei FFR die Bremsfrequenz ist und F0C die Vorgabefrequenz ist.
  6. Uhr nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die mechanische Bremsvorrichtung (24, 56, 56A) angeordnet ist, um an den mechanischen Resonator das dissipative mechanische Bremsmoment im Wesentlichen durch Reibung und derart anzulegen, dass die periodischen Bremsimpulse jeweils im Wesentlichen eine Dauer von weniger als dem Viertel des Vorgabezeitraums aufweisen, der der umgekehrten Vorgabefrequenz entspricht.
  7. Uhr nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die mechanische Bremsvorrichtung (24, 56, 56A) angeordnet ist, um an dem mechanischen Resonator das dissipative mechanische Bremsmoment im Wesentlichen durch Reibung und derart anzulegen, dass die periodischen Bremsimpulse jeweils im Wesentlichen eine Dauer aufweisen, die kleiner als 1/10 des Vorgabezeitraums ist, der der umgekehrten Vorgabefrequenz entspricht.
  8. Uhr nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die mechanische Bremsvorrichtung (24, 56, 56A) angeordnet ist, um an dem mechanischen Resonator das dissipative mechanische Bremsmoment im Wesentlichen durch Reibung und derart anzulegen, dass die periodischen Bremsimpulse jeweils im Wesentlichen eine Dauer aufweisen, die kleiner als 1/40 des Vorgabezeitraums ist, der der umgekehrten Vorgabefrequenz entspricht.
  9. Uhr nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass das mechanische System derart konfiguriert ist, um es der mechanischen Bremsvorrichtung (24, 56, 56A) zu ermöglichen, in dem Nutzbetriebsbereich des Slave-Oszillators einen der periodischen Bremsimpulse in irgendeiner Position des mechanischen Resonators entlang der allgemeinen Oszillationsachse zu beginnen.
  10. Uhr nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Meister-Oszillator (22, 22A) einen Meister-Resonator (28) umfasst, der aus einer Spiral-Unruh oder einer Unruh gebildet ist, die auf flexiblen Lamellen montiert ist.
  11. Uhr nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Meister-Oszillator (22, 22A) eine Hemmung umfasst, die mit einem Gesperr (33) versehen ist, und somit in einem schrittweisen Modus funktioniert.
  12. Uhr nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass der Meister-Oszillator (96) einen Meister-Resonator umfasst, der aus einer Stimmgabel (98) gebildet wird.
  13. Uhr nach einem der Ansprüche 1 bis 10 und 12, dadurch gekennzeichnet, dass der Meister-Oszillator (54, 96) eine Hemmung mit kontinuierlicher Rotation vom Typ magnetisch, mit einer magnetischen Steuerung zwischen einem Meister-Resonator (60, 98), der diesen Meister-Oszillator bildet, und einem Hemmungsrad (68), das die Hemmung mit kontinuierlicher Rotation bildet, umfasst.
  14. Uhr nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Meister-Oszillator einem Ausgleichsmechanismus für die Kraft, die auf seinen Meister-Resonator ausgeübt wird, zugeordnet ist, um dessen Oszillation zu erhalten.
  15. Uhr nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die mechanische Bremsvorrichtung (24, 56, 56A) einen Steuermechanismus (48, 48A, 58 & 68) und einen Bremsimpulserzeugungsmechanismus (50, 50A) umfasst, der angeordnet ist, um durch den Steuermechanismus mit der Bremsfrequenz betätigt zu werden, um auf ein oszillierendes Organ (8, 8A) des mechanischen Resonators (6, 6A) des Slave-Oszillators während der periodischen Bremsimpulse das dissipative mechanische Bremsmoment anzulegen.
  16. Uhr nach Anspruch 15, dadurch gekennzeichnet, dass der Bremsimpulserzeugungsmechanismus eine Wippe (40, 40A) umfasst, die einer Feder (44, 44A) oder einem flexiblen Element zugeordnet ist, und mit einem Bremsorgan (42) versehen ist, das angeordnet ist, um bei den periodischen Bremsimpulsen in Kontakt mit einer Bremsfläche (46) des oszillierenden Organs zu kommen.
  17. Uhr nach Anspruch 16, dadurch gekennzeichnet, dass der Steuermechanismus einen Betätigungsfinger (58) oder einen Betätigungssperrstift (38) umfasst, der derart auf einem Steuerrad (68, 37, 34A) angeordnet ist, um bei jeder Umdrehung dieses Steuerrades die Wippe betätigen zu können, um einen der periodischen Bremsimpulse zu verursachen; und dadurch, dass das Steuerrad mit einer mittleren Geschwindigkeit in Drehung angetrieben wird, die durch den Meister-Oszillator bestimmt wird.
  18. Uhr nach Anspruch 17, dadurch gekennzeichnet, dass das Steuerrad fest mit einem Hemmungsrad (34A) des Meister-Oszillators verbunden ist.
  19. Uhr nach Anspruch 17, dadurch gekennzeichnet, dass das Steuerrad fest mit einem Drehteil (36) zum Übertragen der Energie eines mechanischen Federhauses (26) zum Meister-Oszillator verbunden ist, wobei dieses Übertragungsrad kinematisch mit einem Hemmungsrad des Meister-Oszillators verbunden ist.
  20. Uhr nach einem der Ansprüche 17 bis 19, dadurch gekennzeichnet, dass die mechanische Bremsvorrichtung (24, 56) derart angeordnet ist, dass der Betätigungsfinger (58) oder der Betätigungssperrstift (38) bei jeder Umdrehung des Steuerrades vorübergehend in Kontakt mit der Wippe (40) kommt, um sie erstens in Drehung anzutreiben, und so den Bremsimpulserzeugungsmechanismus zu spannen, und danach einen der periodischen Bremsimpulse auszulösen, während der Kontakt zwischen dem Betätigungsfinger oder dem Betätigungssperrstift und dem Erzeugungsmechanismus unterbrochen wird.
  21. Uhr nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass sie ein Hilfsfederhaus umfasst, das vorgesehen ist, um dem Meister-Oszillator und nicht dem Slave-Oszillator Energie bereitzustellen, wobei Letzterem durch das Hauptfederhaus Energie bereitgestellt wird.
  22. Uhr nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die periodischen Bremsimpulse ein Kraftmoment und eine Dauer aufweisen, die für den Nutzbetriebsbereich des Slave-Oszillators vorgesehen sind, um den mechanischen Resonator im Laufe der periodischen Bremsimpulse mindestens im Hauptteil einer eventuellen Übergangsphase des Betriebs der Uhr nicht vorübergehend zu blockieren, wobei diese Übergangsphase insbesondere nach einem Einrücken der Vorrichtung zum mechanischen Regeln vor einer synchronen Phase eintreten kann, in der der Slave-Oszillator mit den periodischen Bremsimpulsen synchronisiert wird; und dadurch, dass das mechanische System derart angeordnet ist, dass das dissipative mechanische Bremsmoment mindestens in dem Hauptteil der eventuellen Übergangsphase während der Dauer jedes der periodischen Bremsimpulse an den mechanischen Resonator angelegt werden kann.
  23. Uhr nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass für den Nutzbetriebsbereich des Slave-Oszillators und in einer synchronen Phase des Betriebs der Uhr, in der dieser Slave-Oszillator mit den periodischen Bremsimpulsen synchronisiert wird, diese periodischen Bremsimpulse ein Kraftmoment und eine Dauer aufweisen, die derart vorgesehen sind, um den mechanischen Resonator im Laufe der periodischen Bremsimpulse mindestens in ihrem abschließenden Teil vorübergehend zu blockieren.
EP18710877.4A 2017-03-28 2018-03-16 Mechanische uhr, die ein uhrwerk mit verbesserter ganggenauigkeit durch eine korrekturvorrichtung umfasst Active EP3602206B1 (de)

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US20200026240A1 (en) 2020-01-23
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