Timepiece comprising a mechanical movement whose running is improved by a correction device.

专利摘要:
The timepiece (34) according to the invention is provided with a mechanical movement (4) which comprises a mechanism indicating at least one temporal data, a mechanical resonator (6) forming a mechanical oscillator which speeds the running of the indicating mechanism, and a correction device (36) for preventing any temporal drift in the operation of the indicating mechanism. The correction device is formed by a master oscillator (42) and a device (38, 40) for mechanical braking of the mechanical resonator, this mechanical braking device being arranged to be able to periodically apply to the mechanical resonator braking pulses at a frequency of braking determined by the master oscillator. Then, the system, formed of the mechanical resonator and the mechanical braking device, is configured to allow the mechanical braking device to start the braking pulses preferably at any position of the mechanical resonator. Preferably, the braking pulses have a duration less than a quarter of a set period.
公开号:CH713637A2
申请号:CH00341/18
申请日:2018-03-16
公开日:2018-09-28
发明作者:Tombez Lionel
申请人:Swatch Group Res & Dev Ltd；
IPC主号:

专利说明:

Description
TECHNICAL FIELD [0001] The present invention relates to a timepiece comprising a mechanical movement whose progress is improved by a device for correcting a possible time drift in the operation of the mechanical oscillator which speeds the progress of the mechanical movement.
In particular, the timepiece is formed, on the one hand, by a mechanical movement comprising: a mechanism indicating at least one temporal data, a mechanical resonator capable of oscillating along a general axis of oscillation around a neutral position corresponding to its state of minimum potential energy, - a maintenance device of the mechanical resonator forming with it a mechanical oscillator which is arranged to clock the operation of the indicator mechanism, each oscillation of this mechanical oscillator defining an oscillation period, and, secondly, by a device for correcting a possible time drift in the operation of the mechanical oscillator. Such a time drift occurs especially when the average natural oscillation period of the mechanical oscillator is not equal to a set period. This set period is determined by an auxiliary oscillator which is associated with the correction device.
BACKGROUND [0003] Timepieces as defined in the field of the invention have been proposed in a few previous documents. Patent CH 597 636, published in 1977, proposes such a timepiece with reference to FIG. 3. The movement is equipped with a sprung balance resonator and a conventional maintenance device comprising an anchor and an escape wheel in kinematic connection with a spring-loaded barrel. This clock movement further comprises a device for regulating the frequency of its mechanical oscillator. This control device comprises an electronic circuit and a magnetic assembly formed of a flat coil, arranged on a support under the beam shank, 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 for generating a reference frequency signal FR, this reference frequency being compared with the frequency FG of the mechanical oscillator. The detection of the frequency FG of the oscillator is performed via the electrical signals generated in the coil by the pair of magnets. The control circuit is arranged to be able momentarily to generate a braking torque via a magnet-coil magnetic coupling and a switchable load connected to the coil.
The use of an electromagnetic magnet-coil type system for coupling the sprung balance with the electronic control circuit generates various problems. First, the arrangement of permanent magnets on the balance means that a magnetic flux is constantly present in the watch movement and that this magnetic flux spatially varies periodically. Such a magnetic flux can have a detrimental effect on various members or elements of the watch movement, in particular on magnetic material elements such as parts made of ferromagnetic material. This can have repercussions on the proper functioning of the watch movement and also increase the wear of pivotal elements. One can certainly think to shield to a certain extent the magnetic system in question, but a shielding requires particular elements that are carried by the pendulum. Such shielding tends to increase the bulk of the mechanical resonator and its weight. In addition, it limits the possibilities of aesthetic configurations for the sprung balance.
The skilled person also knows mechanical watch movements which are associated with a device for regulating the frequency of their sprung balance which is of the electromechanical type. More precisely, the regulation intervenes via a mechanical interaction between the sprung balance and the regulating device, the latter being arranged to act on the oscillating balance by a system consisting of an abutment arranged on the balance and an actuator provided with a movable finger which is actuated at a braking frequency in the direction of the stop, without however touching the beam of the balance. Such a timepiece is described in the document FR 2 162 404. According to the concept proposed in this document, it is intended 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 has a time drift relative to a set frequency, the finger being provided to be able to momentarily block the rocker which is then stopped in its movement during a certain time interval (the abutment bearing against the finger moved in its direction during a return of the beam towards its neutral position), or limit the amplitude of oscillation when the finger comes against the stop while the rocker rotates towards one of its two angular positions extremes (defining its amplitude), the finger then stopping the oscillation and the pendulum starting directly in the opposite direction.
Such a control system has many disadvantages and can seriously doubt that it can form a functional system. The periodic actuation of the finger relative to the oscillating movement of the abutment and also a potentially large initial phase shift, for the oscillation of the abutment with respect to the periodic movement of the finger in the direction of this abutment, pose several problems. It will be noted that the interaction between the finger and the stop is limited to a single angular position of the balance, this angular position being defined by the angular position of the actuator relative to the axis of the sprung balance and the angular position of the stop on the pendulum at rest (defining its neutral position). Indeed, the movement of the finger is provided to stop the balance by contact with the stop, but the finger is arranged not to come into contact with the balance beam. In addition, it will be noted that the instant of an interaction between the finger and the stop also depends on the amplitude of the oscillation of the sprung balance.
It will be noted that the desired synchronization seems unlikely. Indeed, in particular for a sprung balance whose frequency is greater than the reference frequency setting the back and forth of the finger and with a first interaction between the finger and the abutment which temporarily holds the pendulum returning from one of its two extreme angular positions (correction reducing the error), the second interaction, after many oscillations without the stop touching the finger during its reciprocating movement, will certainly be a stop of the pendulum by the finger with immediate inversion of its sense of oscillation, in that the stop abuts against the finger while the rocker rotates towards said extreme angular position (correction increasing the error). Thus, not only is there an uncorrected time drift during a time interval that may be long, for example several hundred oscillation periods, but certain interactions between the finger and the stopper increase the time drift instead of the reduce! It will also be noted that the phase shift of the oscillation of the abutment, and therefore of the sprung balance, during the above-mentioned second interaction can be significant according to the relative angular position between the finger and the abutment (balance in its neutral position).
It can thus be doubted that the desired synchronization is obtained. Moreover, particularly if the natural frequency of the sprung balance is close but not equal to the reference frequency, situations where the finger is blocked in its movement in the direction of the balance by the stop which is located at this time in front of the finger are predictable. Such parasitic interactions can damage the mechanical oscillator and / or the actuator. In addition, this virtually limits the tangential extent of the finger. Finally, the duration of maintaining the finger in the interaction position with the stop must be relatively short, thus limiting a correction generating a delay. In conclusion, the operation of the timepiece proposed in document FR 2 162 404 appears to the highly improbable person skilled in the art, and he turns away from such teaching. SUMMARY OF THE INVENTION [0010] An object of the present invention is to find a solution to the technical problems and disadvantages of the prior art mentioned in the technological background.
In the context of the present invention, it is generally sought to improve the accuracy of the running of a mechanical watch movement, that is to say, to reduce the daily time drift of this mechanical movement. In particular, the present invention seeks to achieve such a goal for a mechanical watch movement whose gait is initially set at best. Indeed, a general object of the invention is to find a device for correcting a time drift of a mechanical movement, namely a device for correcting its progress to increase its accuracy, without giving up what it is. it can operate autonomously with the best accuracy that it is possible to have through its own characteristics, that is to say, in the absence of the correction device or when the latter is inactive.
For this purpose, the present invention relates to a timepiece as defined above in the technical field, wherein the correction device is formed by a mechanical braking device of the mechanical resonator. The mechanical braking device is arranged to be able to apply to the mechanical resonator a mechanical braking torque during periodic braking pulses which are generated at a selected braking frequency only as a function of a reference frequency for the mechanical oscillator of the watch movement. and determined by an auxiliary oscillator associated with the correction device. The mechanical resonator and mechanical braking device system is configured to allow the mechanical braking device to be able to initiate periodic braking pulses at any position of the mechanical resonator within a range of positions along the mechanical resonator. a general axis of oscillation of this mechanical resonator, which extends at least a first of two sides of the neutral position of the mechanical resonator over at least a first range of the amplitudes that the mechanical oscillator is likely to have this first side for a useful operating range of this mechanical oscillator.
In a general variant, the system formed of the mechanical resonator and the mechanical braking device is configured in such a way that the position range of the mechanical resonator, into which the periodic braking pulses can begin, also extends from the second of the two sides of the neutral position of the mechanical resonator over at least a second range of amplitudes that the mechanical oscillator is likely to have from this second side, along the general axis of oscillation, for the useful operating range of this mechanical oscillator.
In a preferred embodiment, each of the two parts of the range of mechanical resonator positions identified above, respectively incorporating the first and second ranges of the amplitudes that the mechanical oscillator is likely to have respectively two sides of the neutral position of its mechanical resonator, have a certain extent on which it is continuous or almost continuous.
In a general variant, the mechanical braking device is arranged so that the periodic braking pulses each have essentially a duration less than one quarter of the corresponding reference period to the inverse of the target frequency. In a particular variant, the periodic braking pulses essentially have a duration of between 1/400 and 1/10 of the reference period. In a preferred variant, the periodic braking pulses have a duration of between 1/400 and 1/50 of the reference period.
In a preferred embodiment, the auxiliary oscillator is incorporated in the correction device that includes the timepiece.
Thanks to the characteristics of the invention, surprisingly, the mechanical oscillator of the watch movement is synchronized to the auxiliary oscillator in an efficient and fast manner, as will become clear later in the detailed description of the invention. 'invention. The correction device constitutes a synchronization device of the mechanical oscillator (slave mechanical oscillator) on the auxiliary oscillator (master oscillator), and this without closed-loop servocontrol and without measuring sensor of the movement of the mechanical oscillator. The correction device thus operates with an open loop and it makes it possible to correct both an advance and a delay in the natural progression of the mechanical movement, as will be explained later. This result is quite remarkable. By 'synchronization on a master oscillator', here is understood a servo (open loop, without feedback) of the mechanical oscillator slave to the master oscillator. The operation of the correction device is such that the braking frequency, derived from the reference frequency of the master oscillator, is imposed on the slave mechanical oscillator which cycles the operation of the indicating mechanism of a time data. We are not here in the situation of coupled oscillators, nor even in the standard case of a forced oscillator. In the present invention, the braking frequency of the mechanical braking pulses determines the average frequency of the slave mechanical oscillator.
It is understood by 'clocking the march of a mechanism' the rhythm of the movement of the movable elements of this mechanism when it operates, in particular to determine the rotational speeds of its wheels and so at least one indicator of a given time. By "braking frequency" is meant a given frequency at which the braking pulses are periodically applied to the slave mechanical resonator.
In a preferred embodiment, the system formed of the mechanical resonator and the mechanical braking device is configured to allow the mechanical braking device to start, within the useful operating range of the slave mechanical oscillator, a mechanical braking pulse substantially at any time of the natural oscillation period of this slave mechanical oscillator. In other words, one of the periodic braking pulses can begin substantially at any position of the mechanical resonator along the general axis of oscillation.
In general, the braking pulses have a dissipative nature because a portion of the energy of the oscillator is dissipated by these braking pulses. In a main embodiment, 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 (non-point) along the axis of oscillation.
In a particular embodiment, the braking pulses exert a mechanical braking torque on the mechanical resonator whose value is provided to not momentarily block the mechanical resonator during periodic braking pulses. In this case, preferably, the aforementioned system is arranged to allow the mechanical braking torque generated by each of the braking pulses to be applied to the mechanical resonator during a certain continuous or quasi-continuous time interval (non-zero or one-time, but having a certain significant duration).
The invention also relates to a synchronization module of a mechanical oscillator that includes a timepiece and which gait the march of a watch mechanism of this timepiece, the synchronization module being intended to be incorporated in the timepiece to synchronize the mechanical oscillator on an auxiliary oscillator incorporated in the synchronization module. This synchronization module comprises a mechanical braking device of a mechanical resonator forming the mechanical oscillator which is arranged to be able to apply to the mechanical resonator a mechanical braking torque during periodic braking pulses which are generated at a selected braking frequency only according to a reference frequency for the mechanical oscillator and determined by the auxiliary oscillator. The mechanical braking device is configured to be able to initiate periodic braking pulses at any position of the mechanical resonator in a range of positions along a general axis of oscillation which extends on both sides the neutral position of the mechanical resonator on respectively at least two ranges of the amplitudes that the mechanical oscillator is likely to have respectively of these two sides for a useful operating range of this mechanical oscillator.
In a particular embodiment of the synchronization module, the mechanical braking device comprises a braking member which is arranged to be actuated at the braking frequency so as to be able momentarily to come into contact with an oscillating member of the mechanical resonator. to exert said mechanical braking torque on said oscillating member during said periodic braking pulses.
In an advantageous variant, the braking member is arranged in such a way that the periodic braking pulses can be applied to the oscillating member, at least in a major part of a possible transitional phase that may occur in particular after activation. synchronization module, mainly by a dynamic dry friction between the braking member and a braking surface of the oscillating member.
BRIEF DESCRIPTION OF THE FIGURES The invention will be described hereinafter in detail with the aid of the accompanying drawings, given by way of non-limiting examples, in which:
Fig. 1 schematically shows a general embodiment of a timepiece according to the invention, FIG. 2 shows a first particular embodiment of a timepiece according to the invention, FIG. 3 shows the circuit diagram of the actuator control circuit of the correction device incorporated in the first particular embodiment, FIG. 4 shows a second particular embodiment of a timepiece according to the invention, FIG. 5 shows a third particular embodiment of a timepiece according to the invention, FIG. 6 shows the application of a first braking pulse to a mechanical resonator in a certain alternation of its oscillation before it passes through its neutral position, as well as the angular velocity of the balance of this mechanical resonator and its angular position in a time interval during which the first braking pulse occurs, FIG. 7 is a figure similar to FIG. 6 but for the application of a second braking pulse in a certain alternation of the oscillation of a mechanical oscillator after it has passed through its neutral position, FIGS. 8A, 8B and 8C respectively show the angular position of a balance-spring during a period of oscillation, the variation of the movement of the watch movement obtained for a fixed-duration braking pulse, for three values of one constant braking torque, depending on the angular position of the balance spring, and the corresponding braking power, FIGS. 9, 10 and 11 respectively show three different situations that can occur in an initial phase following the engagement of the correction device in a timepiece according to the invention, FIG. 12 is an explanatory graph of the physical process involved following the engagement of the correction device in the timepiece according to the invention and leading to the desired synchronization for the case where the natural frequency of the slave mechanical oscillator is greater than at the reference frequency, FIG. 13 represents, in the case of FIG. 12, an oscillation of the slave mechanical oscillator and the braking pulses in a stable synchronous phase for a variant where a braking pulse occurs in each half cycle, FIG. 14 is an explanatory graph of the physical process involved following the engagement of the correction device in the timepiece according to the invention and leading to the desired synchronization for the case where the natural frequency of the slave mechanical oscillator is lower than at the reference frequency, FIG. 15 represents, in the case of FIG. 14, an oscillation of the slave mechanical oscillator and the braking pulses in a stable synchronous phase for a variant where a braking pulse occurs in each alternation, FIGS. 16 and 17 give respectively for the two cases of fig. 12 and 14, the graph of the angular position of a mechanical oscillator and the corresponding oscillation periods for an operating mode of the correction device in which a braking pulse occurs every four periods of oscillation, FIGS. 18 and 19 are respectively partial enlargements of FIGS. 16 and 17, FIG. 20 shows, in a similar manner to the two previous figures, a specific situation in which the frequency of a mechanical oscillator is equal to the braking frequency, FIG. 21 shows, for a variant of a timepiece according to the invention, the evolution of the oscillation period of the slave mechanical oscillator as well as the evolution of the total time error, FIG. 22 shows, for another variant of a timepiece according to the invention, the graph of the oscillation of the mechanical oscillator slave in an initial phase following the engagement of the correction device of a possible time drift.
Detailed Description of the Invention [0026] In FIG. 1 is shown, in part schematically, a general embodiment of a timepiece 2 according to the present invention. It comprises a mechanical clock movement 4 which comprises at least one mechanism 12 indicating a given time, this mechanism comprising a gear train 16 driven by a barrel 14 (the mechanism is shown partially in FIG 1). The mechanical movement further comprises a mechanical resonator 6, formed by a rocker 8 and a hairspring 10, and a maintenance device for this mechanical resonator which is formed by an escapement 18, this maintenance device forming with the mechanical resonator an oscillator mechanical clocking the march of the indicator mechanism. The escapement 18 conventionally comprises an anchor and an escape wheel, the latter being kinematically connected to the cylinder via the gear train 16. The mechanical resonator is capable of oscillating about a neutral position (rest position / 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 balance beam. As the position of the balance is given by its angular position, it is understood that the radius of the circular axis here is unimportant. It defines a general axis of oscillation which indicates the nature of the movement of the mechanical resonator, which can be for example linear in a specific embodiment. Each oscillation of the mechanical resonator defines a period of oscillation.
The timepiece 2 further comprises a device for correcting a possible time drift in the operation of the mechanical oscillator of the mechanical movement 4, this correction device 20 comprising for this purpose a mechanical braking device 24 and an auxiliary oscillator 22, hereinafter also called master oscillator, which is associated with the control device 26 of the mechanical braking device to provide it with a reference frequency. The master oscillator 22 is an auxiliary oscillator insofar as the main oscillator, which directly rates the march of the watch movement, is the aforementioned mechanical oscillator, the latter thus being a slave oscillator. It should be noted that various types of auxiliary oscillators may be provided, in particular of the electronic type, such as an oscillator with a quartz resonator, or even an oscillator integrated entirely in an electronic circuit with the control circuit. Generally, the auxiliary oscillator is by nature or by construction more accurate than the main mechanical oscillator as arranged in the watch movement.
In general, the mechanical braking device 24 is arranged to be able to periodically apply to the mechanical resonator 6 mechanical braking pulses at a selected braking frequency as a function of a frequency / set period and determined by the oscillator. 22. This function is shown schematically in FIG. 1 by a braking member 28 comprising a pad capable of coming into contact with the outer lateral surface 32 of the strut 30 of the balance. This braking member is movable (here in translation), so as to temporarily exercise a braking torque on the mechanical resonator 6, and its reciprocating movement is controlled by the control device 26 which actuates periodically at the braking frequency so that the braking member periodically comes into contact with the balance to apply mechanical braking pulses.
Then, the system, formed of the mechanical resonator 6 and the mechanical braking device 24, is configured to allow the mechanical braking device to be able to start the mechanical braking pulses at any position of the mechanical resonator. less in a certain continuous or quasi-continuous range of positions by which this mechanical resonator is likely to pass along its general axis of oscillation. The case shown in FIG. 1 corresponds to a preferred variant in which the system formed of the mechanical resonator and the mechanical braking device is configured to allow the mechanical braking device to apply a mechanical braking pulse to the mechanical resonator substantially at any moment of a period. oscillation in the useful operating range of the slave mechanical oscillator. Indeed, the outer lateral surface 32 of the serge 30 is here continuous and circular, so that the pad of the braking member 28, which moves radially, can exert a braking torque at any angular position of the balance. Thus, in particular, a braking pulse can begin at any angular position of the mechanical resonator between the two extreme angular positions (the two amplitudes of the slave mechanical oscillator respectively on both sides of the neutral point of its mechanical resonator). it is likely to reach when the slave mechanical oscillator is functional.
Finally, the periodic mechanical braking pulses each have essentially a duration less than a quarter of the target period provided for the oscillation of the slave mechanical oscillator formed by the mechanical resonator 6 and the maintenance device 12.
In an advantageous embodiment, the various elements of the correction device 20 form a module independent of the mechanical movement 4. Thus, this synchronization module can be assembled or associated with the mechanical movement that when mounted in a box of shows in a terminal assembly step intervening before the casing. In particular, such a module can be attached to a casing ring that surrounds the watch movement. It is understood that the synchronization module can be advantageously associated with the watch movement once the latter fully assembled and adjusted, the assembly and disassembly of this module can occur without having to intervene on the mechanical movement itself.
Before describing in detail the remarkable operation of such a timepiece and how the synchronization of the main mechanical oscillator on the master auxiliary oscillator is obtained, it will be described using FIGS. 2 to 5 particular embodiments with an auxiliary oscillator of the electric / electronic type and a mechanical braking device of the electromechanical type.
According to a first particular embodiment shown in FIG. 2, the timepiece 34 comprises a mechanical clock movement (only the resonator 6 being shown) and a device 36 for correcting a possible time drift for a display mechanism of at least one time data whose running is clocked by the mechanical oscillator formed by the resonator 6. The correction device 36 comprises an electromechanical actuator 38, an electronic circuit formed of the electronic control circuit 40 and the clock circuit 50, a quartz resonator 42, a solar cell 44 and an accumulator 46 storing the electrical energy supplied by the solar cell. The actuator 38 is formed by a supply circuit 39 and a movable braking member 41, which is actuated in response to a control signal supplied by the electronic control circuit 40 so as to exert on the oscillating member of the resonator mechanical 6 a certain mechanical force during the mechanical braking pulses provided. For this purpose, the actuator 38 comprises a piezoelectric element which is powered by the circuit 39, an electric voltage being applied to this piezoelectric element as a function of the control signal. When the piezoelectric element is momentarily energized, the braking member comes into contact with a braking surface of the beam to slow it down.
In the example shown in FIG. 2, the blade 41 forming the braking member curves when the electric voltage is applied and its end portion presses against the circular lateral surface 32 of the seam 30 of the balance 8. Thus, this serge defines a braking surface circular. The braking member comprises a movable part, here the end portion of the blade 41, which defines a braking pad arranged to exert a pressure against the circular braking surface when applying the braking pulses. mechanical. A circular braking surface, for an oscillating member which is pivoted (balance) and at least one radially movable braking pad constitutes in the context of the invention a mechanical braking system which has decisive advantages. Indeed, in a preferred variant, provision is made for the oscillating member and the braking member to be arranged in such a way that the mechanical braking pulses are applied by a dynamic dry friction between the braking member and the braking surface. of the oscillating organ.
It will be noted that the braking surface may be other than the outer lateral surface of the beam seam. In a variant not shown, it is the central shaft of the balance which defines a circular braking surface. In this case, a pad of the braking member is arranged to exert a pressure against this surface of the central shaft during the application of the mechanical braking pulses.
By way of nonlimiting examples, for a clock resonator formed by a sprung balance, whose spiral constant k = 5.75 E-7 Nm / rad and the inertia I = 9.1 E-10 kg m2, and a set frequency FOc equal to 4 Hz, we can consider a first variant for a watch movement whose unsynchronized running is not very accurate, with a daily error of about five minutes, and a second variant for another watch movement whose Unsynchronized operation is more accurate with a daily error of about thirty seconds. In the first variant, the range of values for the braking torque is between 0.2 pNm and 10 pNm, the range of values for the duration of the braking pulses is between 5 ms and 20 ms and the range of values relative to the braking pulse is braking period for the application of the periodic braking pulses is between 0.5 s and 3 s. In the second variant, the range of values for the braking torque is between 0.1 pNm and 5 pNm, the range of values for the duration of the periodic braking pulses is between 1 ms and 10 ms and the range of values for the braking period is between 3s and 60s, ie at least once a minute.
FIG. 3 is a diagram which shows an alternative embodiment of the control circuit 40 of the timepiece 34. This control circuit is connected on the one hand to the clock circuit 50 and, on the other hand, to the actuator The clock circuit 50 maintains the crystal resonator 42 and generates back a clock signal Sq at a reference frequency, in particular equal to 215 Hz. The quartz resonator and the clock circuit together form a master oscillator. The clock signal SQ is supplied successively to two divisors DIV1 and DIV2 (these two dividers can form two stages of the same divider). The divider DIV2 supplies a periodic signal SD to a counter 52. The frequency of the signal SD is for example equal to 1 Hz, 2 Hz or 4 Hz. The counter 52 is an N counter, that is to say that it counts in loop a number N of successive pulses of the signal Sd and delivers a pulse each time it reaches this number N via the signal
Sr that it provides to a timer 54 ("Timer"). At each pulse received, the timer immediately opens the switch 56 to energize and thus feed the electromechanical actuator 38 for a duration T | mp defining the duration of each braking pulse. Since this duration is provided essentially less than T0c / 4 (where TOc is the reference period of the mechanical oscillator) and preferably much lower than this value, in particular between 1 ms and 10 ms, the timer receives a divider timing signal. DIV1.
In an example where the reference frequency FOc of the mechanical oscillator is equal to 4 Hz (FOc = 4 Hz), the pulse frequency of the SD signal equal to 8 Hz and the number N equal to 16, the frequency braking Ffr of the SR signal is then 0.5 Hz, which means that a braking pulse is provided by eight periods TOc, about every eight periods of the mechanical oscillator in that its natural frequency FO is close the reference frequency FOc. In a variant, the counter 52 is omitted and it is the divider DIV2 which delivers pulses directly to the timer to switch it periodically. In this case, preferably, the frequency of the pulses of the signal Sd is equal to or less than twice the reference frequency FO. Thus, for FO = 4 Hz, the frequency of the signal SD is equal to or less than 8 Hz, since a maximum of one alternating braking pulse of the mechanical oscillator is preferably provided.
[0039] Referring to FIG. 4, there will be described hereinafter a second particular embodiment of a timepiece 62, which differs the former first by the arrangement of its braking device 64. The actuator of this braking device comprises two modules braking systems 66 and 68 each formed by a blade 41 A, respectively 41B actuated by a magnetic magnet-coil system 70A, respectively 70B. The coils of the two magnetic systems are respectively controlled by two power supply circuits 72A and 72B which are electrically connected to the electronic circuit 40,50. The blades 41A and 41B respectively form a first braking member and a second braking member which define two pads that can bear against the outer lateral surface 32A of the serge 30A of the balance 8A. These two braking pads are arranged in such a way that, during the application of the periodic braking pulses, they come to exert on the sill of the balance respectively two radial forces diametrically opposite relative to the axis of rotation of the balance and in opposite directions. Of course, the force torque exerted by each of the two pads during a braking pulse is provided substantially equal to the other. Thus, the resultant forces in the general plane of the balance is substantially zero so that no radial force is exerted on the balance shaft during the braking pulses. This avoids mechanical stresses on the pivots of the balance and more generally at the bearings associated with these pivots. Such an arrangement may advantageously be incorporated in a variant where braking is performed on the balance shaft or on a disc carried by this shaft.
Then, the resonator 6A differs from that of the previous mode in that the balance 8A includes a serge 30A having cavities 74 (in the general plane of the balance) in which are housed screws 76 balance balancer . Thus, the outer lateral surface 32A no longer defines a continuous circular surface, but a discontinuous circular surface with four continuous angular sectors. Note however that the blades 41A and 41B have contact surfaces with an extent such that braking pulses remain possible for any angular position of the balance, even when two cavities are respectively opposite the ends of two blades, as shown in fig. 4.
In an alternative embodiment, the braking force exerted on the balance is provided axially. In such a variant, it is advantageous to provide a mechanical braking device of the type of the second embodiment, that is to say with two braking pads arranged axially vis-à-vis and between which passes in particular the serge of the pendulum. Thus, the actuator is arranged so that, during the application of the periodic braking pulses, the two pads come to exert on the balance two axial forces substantially aligned and in opposite directions. The force torque exerted by each of the two pads during a braking pulse is provided here also substantially equal to the other.
A timepiece 80 according to a third particular embodiment is shown in FIG. 5. It is distinguished from the first embodiment essentially by the choice of the actuator which comprises a watchmaker type motor 86 and a braking member 90 which is mounted on a rotor 88 (permanent magnet) of this motor so as to to exert a certain force on the beam of the balance 8 of the resonator 6 when the rotor performs a certain rotation, which is generated by a supply 82 of a motor coil during the braking pulses in response to a control signal provided by the control circuit 40.
According to various variants, the electromechanical actuator comprises a piezoelectric element or a magnetostrictive element or, to actuate said braking member, an electromagnetic system.
We will describe below, with reference to FIGS. 6 and 7, a remarkable physical phenomenon highlighted in the context of developments that led to the present invention and involved in the synchronization method implemented in the timepiece according to the invention. The understanding of this phenomenon will better understand the timing obtained by the correction device regulating the gait of the mechanical movement, a result which will be described later in detail.
In figs. 6 and 7, the first graph indicates the instant tP1 at which a braking pulse P1, respectively P2 is applied to the mechanical resonator considered to perform a correction of the operation of the mechanism which is clocked by the mechanical oscillator formed by this resonator. The last two graphs respectively show the angular velocity (values in radians per second: [rad / s]) and the angular position (values in radian: [rad]) of the oscillating organ (later also 'the pendulum') of the mechanical resonator over time. The curves 90 and 92 respectively correspond to the angular speed and to the angular position of the freely oscillating rocker (oscillation at its natural frequency) before the intervention of a braking pulse. After the braking pulse are represented the speed curves 90a and 90b corresponding to the behavior of the resonator respectively in the case disturbed by the braking pulse and the undisturbed case. Similarly, 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. In the figures, the instants tp-1 and tp2 in which the braking pulses P1 and P2 are involved correspond to the time positions of the medium of these pulses. However, the beginning of the braking pulse and its duration are considered as the two parameters which define a braking pulse temporally.
It will be noted that the pulses P1 and P2 are shown in FIGS. 6 and 7 by binary signals. However, in the following explanations, mechanical braking pulses applied to the mechanical resonator and not control pulses are considered. Thus, it will be noted that, in certain embodiments, in particular with mechanical correction devices having a mechanical control device, the control pulse can intervene at least in part before the application of a mechanical braking pulse. In such a case, in the following explanations, the braking pulses P1, P2 correspond to the mechanical braking pulses applied to the resonator and not to previous control pulses.
It will also be noted that the braking pulses may be applied with a constant force torque or a non-constant force torque (for example substantially Gaussian or sinusoidal curve). By braking pulse, it is understood the momentary application of a force torque to the mechanical resonator which brakes its oscillating member (balance), that is to say, which opposes the oscillating movement of this oscillating member. In the case of a non-zero torque that is variable, the duration of the pulse is generally defined as the portion of this pulse that has a significant torque force to brake the mechanical resonator. It will be noted that a braking pulse can have a large variation. It can even be chopped and form a succession of shorter pulses. In the case of a constant torque, the duration of each pulse is expected to be less than half a set period and preferably less than one quarter of a set period. It should be noted that each braking pulse can either brake the mechanical resonator without stopping it, as in FIGS. 6 and 7, either stop it during the braking pulse and stop it momentarily during the rest of this braking pulse.
Each free oscillation period TO of the mechanical oscillator defines a first alternation AO1 followed by a second alternation AO2 intervening each between two extreme positions defining the amplitude of oscillation of this mechanical oscillator, each alternation having a duration identical TO / 2 and having a passage of the mechanical resonator by its zero position at a median time. The two successive alternations of an oscillation define two half-periods during which the rocker is respectively subjected to an oscillation movement in one direction and then an oscillation movement in the other direction. In other words, an alternation here corresponds to a rocking of the balance in one direction or the other direction between its two extreme positions defining the amplitude of oscillation. In general, there is a variation of the oscillation period during which a braking pulse occurs and thus a point variation of the frequency of the mechanical oscillator. In fact, the temporal variation relates to the only alternation during which the braking pulse intervenes. By 'median moment', we understand a moment intervening substantially in the middle of the alternations. This is precisely the case when the mechanical oscillator oscillates freely. On the other hand, for the alternations in which regulation pulses occur, this median instant no longer corresponds exactly to the middle of the duration of each of these alternations due to the disturbance of the mechanical oscillator generated by the regulating device.
We will first describe the behavior of the mechanical oscillator in a first case of correction of its oscillation frequency, which corresponds to that shown in FIG. 6. After a first period TO then begins a new period T1, respectively a new alternation A1 during which a braking pulse P1 occurs. At the initial time tD1 starts the alternation A1, the resonator 14 occupying a maximum positive angular position corresponding to an extreme position. Then comes the braking pulse P1 at time tP1 which is located before the median time tNi at which the resonator passes through its neutral position and therefore also before the corresponding median time tNo of the undisturbed oscillation. Finally the alternation A1 ends at the final time tFi. The braking pulse is triggered after a time interval TAi following the instant you mark the beginning of the alternation A1. The duration TA1 is less than half-alternation TO / 4 less the duration of the braking pulse P1. In the example given, the duration of this braking pulse is much less than a half-alternation TO / 4.
In this first case, the braking pulse is generated between the beginning of an alternation and the passage of the resonator by 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 TCi in the oscillation of the resonator, as shown in FIG. 6 the two curves 90a and 90b of the angular velocity and also the two curves 92a and 92b of the angular position, that is to say a delay relative to the undisturbed theoretical signal (shown in broken lines). Thus, the duration of the alternation A1 is increased by a time interval TC1. The oscillation period T1, comprising the alternation A1, is therefore extended relative to the value TO. This causes a specific decrease in the frequency of the mechanical oscillator and a momentary slowing of the associated mechanism whose operation is clocked by this mechanical oscillator.
Referring to FIG. 7, will be described below the behavior of the mechanical oscillator in a second case of correction of its oscillation frequency. After a first period TO then begins a new oscillation period 12, respectively an alternation A2 during which a braking pulse P2 occurs. At the initial moment tD2 begins the alternation A2, the mechanical resonator then being in an extreme position (maximum negative angular position). After a quarter period TO / 4 corresponding to a half-wave, the resonator reaches its neutral position at the median time tN2. Then comes the braking pulse P2 at time tp2 which is located in alternating A2 after the median time tN2 at which the resonator passes through its neutral position. Finally, after the braking pulse P2, this alternation A2 ends at the final time tF2 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 tF0 of undisturbed oscillation. The braking pulse is triggered after a time interval TA2 following the initial time tD2 of the alternation A2. The duration TA2 is greater than a half-alternation TO / 4 and less than an alternation TO / 2 less the duration of the braking pulse P2. In the example given, the duration of this braking pulse is much less than half a half cycle.
In the second case considered, the braking pulse is generated, alternately, 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. Remarkably, the braking pulse here induces a positive phase shift TC2 in the oscillation of the resonator, as shown in FIG. 4 the two curves 90b and 90c of the angular velocity and also the curves 92b and 92c of the angular position, that is an advance relative to the undisturbed theoretical signal (shown in broken lines). Thus, the duration of the alternation A2 is reduced by the time interval TC2. The oscillation period T2 comprising the alternation A2 is therefore shorter than the value TO. This consequently generates a point increase in the frequency of the mechanical oscillator and a momentary acceleration of the associated mechanism whose operation is clocked by this mechanical oscillator. This phenomenon is surprising and unintuitive, which is why the skilled person ignored it in the past. Indeed, getting an acceleration of the mechanism by a braking pulse is a priori surprising, but such is the case when this step 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. Unlike general education in the horological field, it is possible not only 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 braking pulses. The person 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, to be able only to increase the frequency of such a mechanical oscillator by the application of driving pulses. during a supply of energy to this oscillator. Such intuition, which has imposed itself in the field of watchmaking and therefore comes first on board in the mind of a person skilled in the art, proves false for a mechanical oscillator. Thus, as will be explained later in detail, it is possible to synchronize, via an auxiliary oscillator defining a master oscillator, a mechanical oscillator which is otherwise very precise, that it momentarily has a frequency that is slightly too high or too low. It is therefore possible to correct a frequency that is too high or a frequency that is too low only by means of braking pulses. In summary, 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 synchronization method resulting from the correction device incorporated in a timepiece according to the invention is described below. In fig. 8A is shown the angular position (in degrees) of a clockwise mechanical resonator oscillating with an amplitude of 300 ° during an oscillation period of 250 ms. In fig. 8B is shown the daily error generated by braking pulses of one millisecond (1 ms) applied in successive oscillation periods of the mechanical resonator according to the instant of their application within these periods and therefore depending on the angular position of the mechanical resonator. Here, we start from the fact that the mechanical oscillator operates freely at a natural frequency of 4 Hz (undisturbed case). Three curves are given respectively for three pairs of forces (100 nNm, 300 nNm and 500 nNm) applied by each braking pulse. The result confirms the physical phenomenon explained above, namely that a braking pulse occurring in the first quarter period or the third quarter period generates a delay resulting from a decrease in the frequency of the mechanical oscillator, while a braking pulse occurring in the second quarter period or the fourth quarter period generates an advance from an increase in the frequency of the mechanical oscillator. Then, it is observed that, for a given torque force, the daily error is equal to zero for a braking pulse occurring at the neutral position of the resonator, this daily error increasing (in absolute value) as one s' approach to an extreme position of the oscillation. At this extreme position where the speed of the resonator passes through zero and the direction of motion changes, there is a sudden inversion of the sign of the daily error. Finally, in fig. 8C is given the braking power consumed for the three aforementioned force torque values as a function of the moment of application of the braking pulse during a period of oscillation. As the speed decreases when approaching the extreme positions of the resonator, the braking power decreases. Thus, while the generated daily error increases when approaching the extreme positions, the necessary braking power (and therefore the energy lost by the oscillator) decreases significantly.
The error generated in FIG. 8B may correspond to a correction in the case where the mechanical oscillator has a natural frequency that does not correspond to a set frequency. Thus, if the oscillator has a low internal frequency, braking pulses occurring in the second or fourth quarter of the oscillation period can allow correction of the delay taken by the free oscillation (undisturbed), this correction being more or less strong depending on the moment of the braking pulses within the oscillation period. On the other hand, if the oscillator has a high natural frequency, 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 moment of the braking pulses in the oscillation period.
The teaching given above allows to understand the remarkable phenomenon of the synchronization of a main mechanical oscillator (slave oscillator) on an auxiliary oscillator, forming a master oscillator, by the only periodic application of braking pulses on the resonator mechanical slave at a braking frequency Ffr advantageously corresponding to twice the reference frequency FOc divided by a positive integer N, ie Ffr = 2 F0c / N. The braking frequency is thus proportional to the reference frequency for the oscillator master and depends only on this set frequency as soon as the positive integer N is given. As the reference frequency is provided equal to a fractional number multiplied by the reference frequency, the braking frequency is therefore proportional to the reference frequency and determined by this reference frequency, which is provided by the auxiliary mechanical oscillator which is by nature or by construction more accurate than the main mechanical oscillator.
The aforementioned synchronization obtained by the correction device incorporated in the timepiece of the invention will now be described in more detail with the aid of FIGS. 9 to 22.
In FIG. 9 is represented on the top graph the angular position of the slave mechanical resonator, including the spring balance of a clock resonator, freely oscillating (curve 100) and oscillating with braking (curve 102). The frequency of the free oscillation is greater than the reference frequency FOc = 4 Hz. The first mechanical braking pulses 104 (hereinafter also called pulses') occur here once per oscillation period in a half-cycle between the passage through an extreme position and the passage through zero. This choice is arbitrary because the planned system does not detect the angular position of the mechanical resonator; it is therefore just one possible hypothesis among others that will be analyzed later. We are here in the case of a slowing down of the mechanical oscillator. The braking torque for the first braking pulse is provided here greater than a minimum braking torque to compensate for the advance that takes the free oscillator over a period of oscillation. This has the consequence that the second braking pulse takes place a little before the first inside the quarter period where these pulses occur. Curve 106, which gives the instantaneous frequency of the mechanical oscillator, in fact indicates that the instantaneous frequency decreases below the reference frequency at the first pulse. Thus, the second braking pulse is closer to the foregoing extreme position, so that the effect of braking increases and so on with subsequent pulses. In a transient phase, the instantaneous frequency of the oscillator thus gradually decreases and the pulses are gradually approaching an extreme position of the oscillation. After a certain time, 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.
The braking has this particular that it opposes the movement of the resonator regardless of the direction of its movement. Thus, when the resonator goes through an inversion of the direction of its oscillation during a braking pulse, the braking torque automatically changes sign at the moment of this inversion. There are then 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. In this situation, there is therefore the first part of the signal which intervenes before the extreme position and which opposes the effect of the second part which intervenes after this extreme position. If the second part decreases the instantaneous frequency of the mechanical oscillator, the first part increases it. The correction then decreases to stabilize finally and relatively quickly to a value for which the instantaneous frequency of the oscillator is equal to the reference frequency (corresponding here to the braking frequency). Thus, in the transient phase follows a stable phase, also called synchronous phase, where the oscillation frequency is substantially equal to the target frequency and where the first and second portions of the braking pulses has a substantially constant and defined ratio.
The graphs of FIG. 10 are similar to those of FIG. 9. The major difference is the value of the natural frequency of the free mechanical oscillator which is lower than the reference frequency FOc = 4 Hz. The first pulses 104 occur in the same half-wave as in FIG. 9. It is observed as expected a decrease in the instantaneous frequency given by the curve 110. The oscillation with braking 108 therefore takes momentarily more delay in the transient phase, until the pulses 104b begins to encompass the passage of the resonator by an extreme position. From this moment, the instantaneous frequency begins to increase until reaching the target frequency, because the first part of the pulses occurring before the extreme position increases the instantaneous frequency. This phenomenon is automatic. Indeed, as long as the duration of the oscillation periods is greater than the duration of the setpoint period TOc, the first part of the pulse increases while the second part decreases and consequently the instantaneous frequency continues to increase until a stable situation where the set period is substantially equal to the oscillation period. So we have the desired synchronization.
The graphs of FIG. 11 are analogous to those in fig. 10. The major difference comes from the fact that the first braking pulses 114 occur in another half-wave alternation in FIG. 10, namely in a half-wave between the zero crossing and the passage through an extreme position. According to what has been explained above, 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 delay that takes the free mechanical oscillator on a period of oscillation. This has the consequence that the second braking pulse takes place a little after the first inside the quarter period where these pulses occur. The curve 112 indicates that the instantaneous frequency of the oscillator increases above the setpoint frequency at the first pulse. Thus, the second braking pulse is closer to the end position that follows, so that the effect of braking increases and so on with subsequent pulses. In the transient phase, the instantaneous frequency of the oscillation with braking 114 thus increases and the braking pulses are gradually approaching an extreme position of the oscillation. After a certain time, the braking pulses include the passage 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. This decrease in the instantaneous frequency continues until it has a value equal to the reference value for the same reasons as given with reference to FIGS. 9 and 10. The frequency decrease stops automatically when the instantaneous frequency is substantially equal to the set frequency. This results in a stabilization of the frequency of the mechanical oscillator at the reference frequency in a synchronous phase.
With the help of FIGS. 12 to 15, the behavior of the mechanical oscillator in the transition phase will be explained for any moment in which a first braking pulse occurs during a period of oscillation, as well as the final situation corresponding to the phase synchronous where the oscillation frequency is stabilized on the set frequency. Fig. 12 represents a period of oscillation with the curve S1 of the positions of a mechanical resonator. In the case considered here, the natural oscillation frequency FO of the free mechanical oscillator (without braking pulses) is greater than the reference frequency FOc (FO> FOc). The oscillation period conventionally comprises a first alternation A1 followed by a second alternation A2, each between two extreme positions (Ui, Am_i; tm, Am; tm + 1, Am + 1) corresponding to the amplitude of oscillation. Then, there is shown, in the first half cycle, a braking pulse "Imp1" whose middle time position intervenes at a time h and, in the second half cycle, another braking pulse "Imp2 '" whose middle time position intervenes at a moment t2. The pulses Imp1 and Imp2 have a phase shift of TO / 2, and they are particular because they correspond, for a given profile of the braking torque, to corrections generating two unstable equilibriums of the system. Since these pulses occur respectively in the first and third quarter of the oscillation period, they therefore slow down the mechanical oscillator to an extent that makes it possible to correct the natural frequency that is too high for the free mechanical oscillator (with the frequency of braking selected for application of braking pulses). It will be noted 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 pulses Imp1 and Imp2 are identical.
If a first pulse occurs at time t-ι or t2, then we will theoretically have a repetition of this situation during the next oscillation periods and an oscillation frequency equal to the reference frequency. Two things are to be noted for such a case. First, the probability that a first pulse will occur exactly at time L or t2 is relatively small, although possible. Secondly, in the event that such a particular situation arises, it can not last long. Indeed, the instantaneous frequency of a sprung balance in a timepiece varies a little over time for various reasons (amplitude of oscillation, temperature, change of spatial orientation, etc.). Although these reasons are disruptions that we usually seek to minimize in luxury watchmaking, the fact remains that in practice such an unstable equilibrium will not last very long. Note that the higher the braking torque, the longer the time! and t2 are close to the two times of passage of the mechanical resonator by its neutral position which follow respectively. It will also be noted that the smaller the difference between the natural oscillation frequency FO and the reference frequency FOc, the more the times t 1 and t 2 are also close to the two passage times of the mechanical resonator by its neutral position which respectively follow them.
Now consider what happens as soon as one deviates a little time positions L or t2 during the application of the pulses. According to the teaching given with reference to FIG. 8B, if a pulse occurs on the left (previous time position) of the pulse Imp1 in the zone Z1a, the correction increases so that during the following periods, the last extreme position Am_i will progressively approach the pulse of braking. On the other hand, if a pulse intervenes on the right (posterior temporal position) of the pulse Imp1, to the left of the zero position, the correction decreases so that during the following periods the pulses drift towards this zero position where the correction becomes nothing. Then, the effect of the pulse changes and an increase in the instantaneous frequency occurs. As the natural frequency is already too high, the pulse will quickly drift to the extreme position Am. Thus, if a pulse occurs to the right of the pulse Imp1 in the zone Z1b, the following pulses will progressively approach the Next extreme position Am. The same behavior is observed in the second alternation A2.
If a pulse occurs to the left of pulse Imp2 in zone Z2a, the following pulses will progressively approach the previous extreme position Am. On the other hand, if a pulse occurs to the right of pulse Imp2 in zone Z2b , the following pulses will progressively approach the next extreme position Am + 1. It will be noted that this formulation is relative because in reality the frequency of application of the braking pulses is imposed by the master oscillator (braking frequency given), so that it is the periods of oscillation which vary and in fact is the end position in question which is close to the moment of application of a braking pulse. In conclusion, if a pulse occurs in the first alternation A1 at a time other than t-ι, the instantaneous oscillation frequency evolves in a transient phase during the following oscillation periods so that one of the two extreme positions of this first alternation (positions of reversal of the direction of movement of the mechanical resonator) progressively approaches the braking pulses. The same goes for the second alternation A2.
FIG. 13 shows the synchronous phase corresponding to a final stable situation occurring after the transitional phase described above. As already stated, as soon as the passage through an extreme position occurs during a braking pulse, this extreme position will be stalled on the braking pulses provided that these braking pulses are configured (the 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. Thus, in the synchronous phase, if a first pulse occurs in the first alternation A1, the extreme position Am_i of the oscillation is locked on the impulses Impla, or the extreme position Am of the oscillation is locked on the pulses Imp1 b . In the case of a substantially constant torque, the impulse pulses Imp1 and Impib each have a first portion whose duration is shorter than that of their second part, so as to correct exactly the difference between the natural frequency too high of the main oscillator slave and the set frequency imposed by the master auxiliary oscillator. Similarly, in the synchronous phase, if a first pulse occurs in the second alternation A2, the extreme position Am of the oscillation is locked on the pulse Imp2a, or the extreme position Am + i of the oscillation is set on the Imp2b pulses.
It will be noted that the impulses Impla, respectively Impib, Imp2a and Imp2b occupy stable relative temporal positions. Indeed, a slight deviation to the left or right of one of these pulses, due to an external disturbance, will have the effect of reducing a next pulse 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 Impla pulses, respectively Impib, Imp2a and Imp2b varies. in a measure that 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.
Figs. 14 and 15 are similar to FIGS. 12 and 13, but for a situation where the natural frequency of the oscillator is lower than the set frequency. Consequently, the pulses Imp3 and Imp4, corresponding to an unstable equilibrium situation in the correction provided by the braking pulses, are located respectively in the second and fourth quarter of periods (times t3 and t4) where the pulses generate a increase of oscillation frequency. The explanations in detail will not be repeated here because the behavior of the system follows from the preceding considerations. In the transient phase (Fig. 14), if a pulse occurs in alternation A3 to the left of Imp3 pulse in zone Z3a, the previous extreme position (tm_i, Am_i) will progressively approach the next pulses. On the other hand, if a pulse occurs to the right of pulse Imp3 in zone Z3b, the next extreme position (tm, Am) will progressively approach the next pulses. Similarly, if a pulse occurs in the alternation A4 to the left of the pulse Imp4 in the zone Z4a, the previous extreme position (tm, Am) will progressively approach the next pulses. Finally, if a pulse occurs to the right of the pulse Imp4 in the zone Z4b, the next extreme position (tm + 1, Am + 1) will progressively approach the next pulses during the transition phase.
In the synchronous phase (FIG 15), if a first pulse occurs in the first alternation A3, the extreme position Am-1 of the oscillation is keyed on the pulses Imp3a or the extreme position Am of the oscillation is calibrated on imp3b pulses. In the case of a substantially constant torque, the pulses Itnp3a and Imp3b each have a first portion whose duration is longer than that of their second part, so as to correct exactly the difference between the natural frequency too low of the oscillator main slave and the set frequency imposed by the master auxiliary oscillator. Similarly, in the synchronous phase, if a first pulse occurs in the second alternation A4, the extreme position Am of the oscillation is keyed to the pulses Imp4a, or the extreme position Απ + Ί of the oscillation is set on the Imp4b pulses. The other considerations made in the context of the case described above with reference to FIGS. 12 and 13 apply by analogy to the case of fig. 14 and 15. In conclusion, that the natural frequency of the free mechanical oscillator is too high or too low and whatever the moment of the application of a first braking pulse within a period of oscillation, the correction device of the invention is effective and quickly synchronizes the frequency of the mechanical oscillator, timing the movement 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, greater 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 thanks to the characteristics of the timepiece according to the invention also apply to the case where the braking frequency for the application of the braking pulses is not equal to the set frequency. In the case of the application of a pulse per oscillation period, the pulses occurring at the unstable positions (t-ι, Imp1, t2, Imp2, t3, Imp3, t4, Imp4) correspond to corrections to compensate the temporal drift during a single oscillation period. On the other hand, if the predicted braking pulses have a sufficient effect to correct a time drift during several oscillation periods, it is then possible to apply a single pulse per time interval equal to these several oscillation periods. We will then observe the same behavior as for the case where a pulse is generated by oscillation period. Considering the oscillation periods in which the pulses occur, we have the same transient phases and the same synchronous phases as in the case described above. In addition, these considerations are also correct if there is an integer number of alternations between each braking pulse. In the case of an odd number of alternations, alternate alternately, alternatively A1 or A3 alternately A2 or A4 alternately in FIGS. As the effect of two shifted pulses of an alternation is identical, it is understood that the synchronization is performed as for an even number of alternations between two successive braking pulses. In conclusion, as already indicated, the behavior of the system described with reference to FIGS. 12 to 15 is observed as soon as the braking frequency FFr is equal to 2F0c / N, FOc being the reference frequency for the oscillation frequency and N a positive integer.
Although not very interesting, it will be noted that the synchronization is also obtained for a braking frequency Ffr greater than twice the reference frequency (2F0), namely for a value equal to N times F0 with N> 2. In a variant with Ffr = 4F0, there is just a loss of energy in the system without effect in the synchronous phase, because a pulse on two occurs at the neutral point of the mechanical resonator. For a higher braking frequency Ffr, the pulses in the synchronous phase that do not intervene at the extreme positions cancel their effects two by two. We therefore understand that these are theoretical cases without much practical meaning.
Figs. 16 and 17 show the synchronous phase for a variant with a braking frequency Ffr equal to one quarter of the target frequency, a braking pulse therefore occurring every four periods of oscillation. Figs. 18 and 19 are partial enlargements respectively of FIGS. 16 and 17. FIG. 16 relates to a case where the natural frequency of the main oscillator is greater than the reference frequency FOc - 4 Hz, while FIG. 17 relates to a case where the natural frequency of the main oscillator is greater than this reference frequency. It can be seen that only the oscillation periods T1 * and T2 *, in which impulse pulses Imp1b or Imp2a, respectively Imp3b or Imp4a, occur have a variation relative to the natural period TO *. The braking pulses generate a phase shift only in the corresponding periods. Thus, the instantaneous periods oscillate here around an average value which is equal to that of the set period. It will be noted that in FIGS. 16 to 19, the instantaneous periods are measured from a zero crossing on a rising edge of the oscillation signal to such a next pass. Thus, the synchronous pulses that occur at the extreme positions are fully encompassed in periods of oscillation. To be complete, fig. 20 shows the specific case where the natural frequency is equal to the target frequency. In this case, the oscillation periods TO * remain all equal, the impulse pulses Imp5 occurring exactly at extreme positions of the free oscillation with 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.
FIG. 21 shows the variation of the oscillation periods for a set frequency FOc = 3 Hz and an appropriate braking pulse occurring every three periods of oscillation of the mechanical oscillator which clock the operation of a time-indicating mechanism with a daily error of 550 seconds a day, or about 9 minutes a day. This error is very important, but the mechanical braking device is configured to correct such an error. The effect of the braking must be relatively large here, there is a large variation of 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. When the correction device is inactive, it is observed, as expected, that the total temporal error increases linearly as a function of time, whereas this error stabilizes rapidly after the activation of the correction device. Thus, if a time setting is performed after such engagement of the correction device and the transient phase, the total error (also called 'cumulative error') remains low, so that the timepiece indicates by the following an hour with a precision corresponding to that of the master oscillator incorporated in this timepiece and associated with the braking device.
FIG. 22 shows the evolution of the amplitude of the slave mechanical oscillator after the activation of the correction device according to the invention. In the transient phase, there is a relatively marked decrease in amplitude in a case where the first pulse is near the zero position (neutral position). The various braking pulses occurring in particular in a first part of this transient phase generate relatively high energy losses, which follows from the graph of FIG. 8C. Subsequently, the energy losses decrease rather quickly and finally become minimal for a given correction in the synchronous phase. Therefore, it is observed that the amplitude increases again as soon as the pulses include the passage through an extreme position of the mechanical resonator and continues to increase at the beginning of the synchronous phase although the dissipated braking energy then stabilizes at its minimum, given a relatively large time constant for the amplitude variation of the mechanical oscillator. Thus, the part according to the invention also has the 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 amplitude decrease for the braking pulses provided. This is an advantage because when the mainspring servicing the main oscillator relaxes, the minimum oscillation amplitude to ensure the operation of the mechanical movement is reached as late as possible while ensuring accurate walking. The device for correcting the gait of a mechanical movement that generates the synchronization according to the invention therefore has a minimized influence for the power reserve.
In order to minimize the disturbances generated by the braking pulses and in particular the energy losses for the watch movement, short pulse durations or even very short pulse durations will preferably be selected. Thus, in a general variant, the braking pulses each have a duration of between 1/400 and 1/1 O of the reference period. In a preferred variant, the braking pulses each have a duration of between 1/400 and 1/50 of said reference period. In the latter case, for a reference frequency equal to 5 Hz, the duration of the pulses is between 0.5 ms and 4 ms.
[0075] Referring to FIGS. 1-5, there are described timepieces with mechanical resonators having a circular braking surface enabling the braking device to apply a mechanical braking pulse to the mechanical resonator substantially at any time during a period of oscillation in the useful operating range of the mechanical oscillator formed by the mechanical resonator. This is a preferred embodiment variant. Since the watch movements generally have pendulums having a circular serge with an advantageously continuous external surface, the preferred variant indicated above can easily be implemented in such movements without requiring modifications of 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 in the best time.
However, the stable synchronization can already be obtained, after a certain period of time, with a system, formed of the mechanical resonator and the mechanical braking device, which is configured to allow the mechanical braking device to be able to start the periodic braking pulses at any position of the mechanical resonator only in a continuous or quasi-continuous range of positions of this defined resonator, of a first of two sides of the neutral position of the mechanical resonator, by the range of the amplitudes of the mechanical oscillator for its useful operating range. Advantageously, this range of positions is increased, on the minimum amplitude side, at least by an angular distance substantially corresponding to the duration of a braking pulse, so as to allow for a minimum amplitude a braking pulse by a friction dry dynamic. In order for the system to be able to act in all alternations and not only once per oscillation period, it is then necessary for this system to be configured in such a way as to allow the mechanical braking device to also be able to start the periodic braking pulses at the same time. any position of the mechanical resonator of the second of both sides of said neutral position, in the amplitude range of the mechanical oscillator for its useful operating range. Advantageously, the range of positions is also increased, on the minimum amplitude side, at least by an angular distance substantially corresponding to the duration of a braking pulse.
Thus, in a first general variant, the aforementioned continuous or quasi-continuous range of positions of the mechanical resonator extends, from a first of the two sides of its neutral position, at least over the amplitude range that the oscillator mechanical slave is likely to have this first side for a useful operating range of this mechanical oscillator and advantageously moreover, on the side of a minimum amplitude of the amplitude range, at least over an angular distance substantially corresponding to the duration braking pulses. In a second general variant, in addition to the continuous or quasi-continuous range defined above in the first general variant, which is a first continuous or quasi-continuous range, the aforementioned system is configured to allow the braking device to be able to also start the periodic braking pulses at any position of the mechanical resonator, the second of the two sides of its neutral position, at least in a second continuous or quasi-continuous range of positions of this mechanical resonator extending over the range of amplitudes that the slave mechanical oscillator is likely to have 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 on said first angular distance. In an improved variant, the correction device is arranged so that the braking frequency can take several values, preferably a first value in an initial phase of the operation of the correction device and a second value, less than the first value. value, in a normal operating phase following the initial phase. In particular, we will select the duration of the initial phase so that the normal operating phase occurs while the synchronous phase has probably already begun. More generally, the initial phase includes at least the first braking pulses, following the engagement of the correction device, and preferably most of the transient phase. By increasing the frequency of the braking pulses, the duration of the transient phase is reduced. In addition, this variant makes it possible, on the one hand, to optimize braking efficiency during the initial phase to ensure the physical process leading to synchronization and, on the other hand, to minimize the braking energy and therefore the energy losses for the main oscillator during the synchronous phase that continues until the correction device is deactivated and the mechanical movement operates. The first braking pulses may occur near the neutral position of the resonator where the effect of the braking is less on the phase shift generated for oscillation of the main oscillator. On the other hand, once the synchronization is established, the braking pulses take place near the extreme positions of this oscillation where the effect of braking is the most important.
In the synchronous phase, the situation is robust and the maintenance of synchronization is already obtained with a relatively low braking frequency. It is therefore possible to reduce the braking frequency in the synchronous phase while maintaining synchronization with good robustness, especially in the event of disturbances or shocks that the timepiece may experience. It will be noted that the selected braking frequency can also vary as a function of various parameters outside the mechanical slave oscillator that can be measured by appropriate sensors, in particular the value of an ambient magnetic field, the temperature in the timepiece or the detection of shocks by an accelerometer.
Finally, in the context of the present invention, two categories of periodic braking pulses can be distinguished in relation to the intensity of the mechanical force torque applied to the mechanical resonator and the duration of the periodic braking pulses. Concerning the first category, the braking torque and the duration of the braking pulses are provided, for the useful operating range of the mechanical oscillator, so as not to momentarily block the mechanical resonator during the periodic braking pulses at least in most of the transitional phase that has been described previously. In this case, the system is arranged so that the mechanical braking torque is applied to the mechanical resonator, at least in most of the possible transient phase, during each braking pulse.
In an advantageous variant, the oscillating member and the braking member are arranged so that the periodic braking pulses can be applied, at least in most of the possible transient phase, mainly by dynamic dry friction. between the braking member and a braking surface of the oscillating member. Concerning the second category, for the useful operating range of the mechanical oscillator and in the synchronous phase which has been described above, the mechanical braking torque and the duration of the periodic braking pulses are provided so as to block the mechanical resonator at the same time. periodic braking pulses at least in their terminal part.
In a particular variant, a momentary blocking of the mechanical resonator by the periodic braking pulses is provided in the synchronous phase whereas, at least in an initial part of the eventual transient phase, where the periodic braking pulses occur outside the extreme positions of the mechanical resonator, the latter is not blocked by these periodic braking pulses.

权利要求:
Claims (20)
[1]
1. Timepiece (2, 34, 62, 80) comprising a mechanical movement (4) which comprises: - a mechanism (12) indicating at least one temporal data, - a mechanical resonator (6, 6A) capable of oscillating along a general axis of oscillation around a neutral position corresponding to its state of minimum potential energy, - a maintenance device (18) of the mechanical resonator forming with this mechanical resonator a mechanical oscillator which is arranged to clock the march of the indicator mechanism; the timepiece further comprising a correction device (20, 36) of a possible time drift in the operation of the mechanical oscillator, this correction device comprising a mechanical braking device of the mechanical resonator; characterized in that the mechanical braking device (24, 38, 40, 64) is arranged to be able to apply to said mechanical resonator a mechanical braking torque during periodic braking pulses which are generated at a braking frequency selected only as a function of the braking frequency. a set frequency for said mechanical oscillator and determined by an auxiliary oscillator (22, 42) associated with the correction device, the system formed of the mechanical resonator and the mechanical braking device being configured to allow the mechanical braking device to ability to initiate said periodic braking pulses at any position of the mechanical resonator in a range of positions along said general axis of oscillation, which extends at least a first of two sides of the neutral position of the resonator mechanical over at least a range of amplitudes as the mechanical oscillator is likely to have this first side for a useful operating range of this mechanical oscillator.
[2]
2. Timepiece according to claim 1, characterized in that a first part of said range of positions of the mechanical resonator, incorporating said range of amplitudes that the mechanical oscillator is likely to have said first side of the position neutral of the mechanical resonator, has a certain extent on which it is continuous or almost continuous.
[3]
3. Timepiece according to claim 1 or 2, characterized in that said system is configured such that said range of positions of the mechanical resonator, in which said periodic braking pulses can begin, also extends from the second of the two. sides of the neutral position of the mechanical resonator over at least a range of amplitudes that the mechanical oscillator is likely to have this second side for said useful operating range of this mechanical oscillator.
[4]
4. Timepiece according to claim 3, characterized in that a second portion of said range of positions of the mechanical resonator, incorporating said amplitude range that the mechanical oscillator is likely to have said second side of the neutral position of the mechanical resonator, has a certain extent on which it is continuous or almost continuous.
[5]
5. Timepiece according to any one of the preceding claims, characterized in that said braking frequency is provided equal to twice said reference frequency divided by a positive integer N, ie Ffr = 2 FOc / N where Ffr is the braking frequency and FOc is the set frequency.
[6]
6. Timepiece according to any one of the preceding claims, characterized in that said auxiliary oscillator is incorporated in this timepiece.
[7]
7. Timepiece according to any one of the preceding claims, characterized in that the mechanical braking device is arranged such that said periodic braking pulses each have substantially less than one quarter of the corresponding period of time corresponding to the opposite of the set frequency.
[8]
8. Timepiece according to any one of claims 1 to 6, characterized in that the mechanical braking device is arranged in such a way that the periodic braking pulses each have essentially a duration of between 1/400 and 1/10 of the setpoint period corresponding to the inverse of the setpoint frequency.
[9]
9. Timepiece according to any one of claims 1 to 6, characterized in that said mechanical braking device is arranged so that the periodic braking pulses each have a duration substantially between 1/400 and 1/50 of the setpoint period corresponding to the inverse of the setpoint frequency.
[10]
10. Timepiece according to any one of the preceding claims, characterized in that said system is configured to allow the mechanical braking device (24, 38, 40, 64) to start, in said useful operating range of said oscillator mechanical, one of said periodic braking pulses at any position of the mechanical resonator along said general axis of oscillation.
[11]
Timepiece according to claim 10, characterized in that the mechanical braking device comprises a braking member (41, 41A, 41B, 90) which is arranged to be actuated at said braking frequency by the device correction, so as to exert on an oscillating member (8, 8A) of said mechanical resonator (6, 6A) said mechanical braking torque during said periodic braking pulses.
[12]
12. Timepiece according to claim 11, characterized in that said auxiliary oscillator (42) is of the electric type; and in that the mechanical braking device is formed by an electromechanical actuator (38, 66, 68, 86) which actuates said braking member, said electromechanical actuator comprising a piezoelectric element or a magnetostrictive element or, for actuating said braking member , an electromagnetic system.
[13]
13. Timepiece according to claim 11 or 12, characterized in that said mechanical braking torque and the duration of the periodic braking pulses are provided in the operating range of said mechanical oscillator, so as not to momentarily block said mechanical resonator during the periodic braking pulses at least in most of a possible transient phase of the operation of the timepiece, this transient phase can occur, in particular following an engagement of the correction device, before a phase synchronously wherein said mechanical oscillator is synchronized with the periodic braking pulses.
[14]
Timepiece according to claim 13, characterized in that the oscillating member and the braking member are arranged in such a way that the periodic braking pulses can be applied, at least in the major part of said eventual transitional phase. , mainly by a dynamic dry friction between the braking member (41.41 A, 41 B, 90) and a braking surface (32, 32A) of the oscillating member.
[15]
Timepiece according to claim 13 or 14, characterized in that, in the useful operating range of the mechanical oscillator and in the synchronous phase of the timepiece's operation, said mechanical braking torque and the Periods of periodic braking pulses are provided to momentarily block the mechanical resonator during periodic braking pulses.
[16]
16. Timepiece according to any one of claims 11 to 15, characterized in that said mechanical braking torque applied to said oscillating member is substantially constant during the periodic braking pulses.
[17]
17. Timepiece according to any one of the preceding claims, characterized in that said correction device is arranged such that said braking frequency can successively take several values, a first value in an initial phase of the operation of the correction device and a second value, lower than the first value, in a normal operating phase succeeding the initial phase.
[18]
18. A synchronization module of a mechanical oscillator that includes a timepiece and which speeds the operation of a watch mechanism of this timepiece, this synchronization module being intended to be incorporated into the timepiece for synchronizing the mechanical oscillator with an auxiliary oscillator (22, 42) incorporated in the synchronization module; characterized in that it comprises a device (24, 38, 40, 64) for mechanical braking of a mechanical resonator forming said mechanical oscillator, this mechanical braking device being arranged to be able to apply to the mechanical resonator a mechanical braking torque during periodic braking pulses which are generated at a selected braking frequency only as a function of a target frequency for said mechanical oscillator and determined by the auxiliary oscillator, the mechanical braking device being configured so as to be able to start the pulses of periodic braking at any position of the mechanical resonator in a range of positions, along a general axis of oscillation, which extends at least on both sides of the neutral position of the mechanical resonator respectively on at least two ranges of amplitudes that the mechanical oscillator is likely to have respectively of these two sides for a useful operating range of this mechanical oscillator.
[19]
19. Synchronization module according to claim 18, characterized in that the mechanical braking device comprises a braking member (41, 41A, 41B, 90) which is arranged to be actuated at said braking frequency so as to be able to momentarily contacting an oscillating member (8, 8A) of said mechanical resonator (6, 6A) to exert said mechanical braking torque on said oscillating member during said periodic braking pulses.
[20]
20. Synchronization module according to claim 19, characterized in that the braking member is arranged so that the periodic braking pulses can be applied to said oscillating member, at least in a major part of a possible transitional phase that may occur. especially after an activation of the synchronization module, mainly by a dynamic dry friction between the braking member and a braking surface (32, 32A) of the oscillating member.

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同族专利:

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公开号 | 公开日

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引用文献:

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公开号 | 申请日 | 公开日 | 申请人 | 专利标题

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US5868112A|1996-12-19|1999-02-09|Cummins Engine Company, Inc.|Deep angle injection nozzle and piston having complementary combustion bowl|

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WO2021121711A1|2019-12-17|2021-06-24|The Swatch Group Research And Development Ltd|Timepiece component provided with a mechanical movement and a device for correcting a displayed time|

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法律状态:
2021-03-15| AZW| Rejection (application)|

优先权:

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申请号 | 申请日 | 专利标题

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CH4082017|2017-03-28|

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CH6722017|2017-05-23|

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