EP2613205A2 - Regulating mechanism for watch or chronograph - Google Patents

Abstract

The device has a vibratory oscillator (100) connected mechanically to an anchor (80) having impulse surfaces receiving alternately a mechanical impulse of teeth of an escapement wheel (60), so as to maintain isochronous oscillations of the oscillator and to advance a tooth of the escapement wheel at each alternation of the oscillations. A barrel (32) drives the escapement wheel through a gear train (35), where the teeth of the wheel and the anchor are arranged to allow an operation mode in which the escapement wheel has only one resting phase for each two, three, or more alternations. An independent claim is also included for a method for operating a timepiece movement or chronograph.

Description

Technical area

The present invention relates to an escapement for a watch movement, and in particular a mechanical regulating member with an escapement capable of maintaining and counting isochronous oscillations of a vibrating oscillator.

In one embodiment, the present invention relates to very high frequency mechanical chronographs for measuring time periods with a resolution better than 1/1000 ^th of a second, and having a vibrating oscillator with equal or greater frequency at a few tens of Hz, for example a frequency equal to or greater than 1 kHz. However, the regulating member of the invention can also operate at lower frequencies, from a few tens of Hz.

State of the art

Precise measurement of time over a given period amounts to adding the first N whole fractions of time counted over the period. A distinction must be made between measuring and counting time: to count an interval of time, for example a second, it is necessary to know how to divide it into equal fractions, for example in tenths or hundredths. Thus, it is not possible to count less than one unit of measure without cutting it more finely. To measure directly, it is necessary to note the position of a needle whose displacement is the result of a count.

There are certainly chronographs to interpolate whole fractions of counted time, to improve the displayed resolution. For example, there are chronographs equipped with a 5Hz oscillator which display by interpolation durations less than one-tenth of a second; one could also imagine other chronographs equipped with a 50Hz oscillator, for example, and able to display durations with a resolution of one thousandth of a second. The interpolation can for example be performed by determining the angular position of a needle, a gear, the balance, or the axis of the balance, for example by means of a cam rotating at each alternation with the balance and whose angular position determines the fraction of alternation in which one is at each moment. Such interpolation is by no means capable of counting or displaying the precise interval.

The precise mechanical measurement of time periods therefore requires an oscillator having a natural frequency corresponding to the resolution that one wishes to obtain, as well as an escapement capable of sustaining these oscillations without disturbing the isochronism, and of counting it. By increasing the oscillation frequency, the temporal resolution is improved, which makes it possible to distinguish very similar time intervals. An improved temporal resolution is especially useful for chronographs, for which a temporal resolution of the order of a hundredth of a second is sometimes desired. A high oscillation frequency, however, generates energy consumption, particularly at the level of the exhaust, which reduces the power reserve of the watch.

On the other hand, the incident energy that feeds the regulator into a traditional mechanical watch is done by means of a discontinuous system, the anchor wheel and the anchor. Traditionally, an exhaust stops then accelerates with each alternation to communicate the energy to the regulator. It is therefore necessary each time "raise" the escape wheel, and all the gear train which also stops and restarts with each alternation. The overall inertia of this system induces a limit in the acceleration that can receive the anchor wheel and therefore the energy transmitted. A conventional balance spring system, associated with a given mechanical transmission chain, therefore has a frequency limit and corolairement a limit in operating time.

For this reason, the oscillation frequency chosen is usually a compromise between the chronograph resolution requirements and the desire to maintain a high power reserve for the display of the current time.

The most common regulating devices comprise a balance-type oscillator and an escapement anchor. These devices, widely described in the technical literature, most often have oscillation frequencies of 4 or 5 Hz, ie 28,800 or 36,000 vibrations / hour.

There are known mechanical chronographs higher frequency, e.g. pulsing 360'000 / hour, and capable of measuring the 100 ^th of a second. The patent application US20110164477 describes a wristwatch with a first low-frequency regulating organ for counting time, and a second regulating organ at 360,000 vibrations per hour for the chronograph at 1 / ^100th of a second. The Applicant's 360 caliber and then the Carrera Mikrograph watch presented by the applicant exploit this construction. The 'Mikrotimer 1000' developed by the applicant, manages to mechanically measure the ^1000th of a second thanks to an oscillator comprising a spiral with very high rigidity and a regulating member without a balance, at a low moment of inertia, giving rise to 3'600 000 vibrations per hour.

We do not know, however, faster oscillators and mechanical exhausts, allowing even higher resolution. There is therefore a need to measure timed durations with a resolution equal to or greater than the known resolutions.

It has been found in the context of the invention that the conventional spiral regulator is no longer suitable for constituting useful standards for measuring the precise time or when we exceed frequencies of the order of 500 to 800 Hz, because it loses in precision and is too energy-consuming. Moreover, its overall inertia and dynamic behavior are not suitable for high frequency oscillation.

One of the difficulties encountered in the realization of organs regulating faster and faster is related to the increase in the energy required for their operation. In the conventional exhaust type, indeed, the escape wheel and all the gear that drives it are subject to alternating phases of acceleration and rest phases, which causes a large loss of energy, and greatly reduces the power reserve of the watch. When the barrel is insufficiently loaded, the power available at the escape wheel does not allow it to accelerate quickly enough to move from one pallet from the anchor to the next.

There is therefore a need for a regulating organ for watches capable of sustaining isochronous oscillations faster than known devices, with better energy efficiency.

Brief summary of the invention

An object of the present invention is to provide an exhaust for maintaining and counting very high frequency oscillations and a clockwork mechanism using such an exhaust. According to the invention, these objects are achieved in particular by means of the object of the appended claims.

In particular, these objects are achieved by means of a regulating member for a clockwork movement comprising a vibrating oscillator mechanically connected to an anchor having impulse surfaces alternately receiving a mechanical impulse of the teeth of a wheel. exhaust, so as to maintain isochronous oscillations of said vibrating oscillator, and to advance said escape wheel of a tooth at each alternation of said oscillations, a barrel driving said escape wheel through a gear train in which said teeth the escape wheel and said anchor are arranged to allow an operating regime in which the escape wheel has only a rest phase each two, three, or more alternations. This regulating member has the particular advantage of not necessarily braking the escape wheel at each alternation. In particular, this regulating member allows an operating regime in which the escape wheel is only braked each second alternation, or each third alternation, etc., so as to better use the available energy and to allow the wheel of Escape from accelerating during a prolonged acceleration time.

In particular, this operating speed can be used automatically when the power available to the escape wheel, and therefore its speed of rotation, is low so that the tooth of the escape wheel is released before it is released. reached the rest of the anchor. The escape wheel thus continues to accelerate. On the contrary, when the escape wheel rotates at high speed, it will abut each alternation against the stopper of the anchor, and thus be stopped or in any case slowed by one of the notches at each alternation.

For this purpose, the anchor advantageously comprises at the ends of the impulse surfaces resting notches against which the teeth of the escape wheel abut. These rest notches are sufficiently prominent to allow said operating speed in which the teeth of the escape wheel abut against said notches only every two, three or more alternations when the power available to the escape wheel is low.

This solution therefore allows the escape wheel to continue its acceleration for one, two, three or more alternations, depending on the operating regime. It is particularly suitable for high frequency regulating devices, in which the duration of each alternation is very short, and in which the escape wheel must rotate at high speed.

In an advantageous embodiment, the escape wheel is elastically coupled to the rest of the gear train. This reduces the inertia of the system which must be accelerated each time the escape wheel is released. This also allows the gear to continue its rotation without losing all its kinematic energy when the escape wheel is blocked.

Brief description of the figures

• La Fig. 1 illustre un mouvement d'horlogerie comprenant un organe réglant selon un aspect de l'invention.
• La Fig. 2 montre l'organe réglant de l'invention dans le mouvement de la figure 1, et
• La Fig. 3 représente le même organe réglant en vue explosée
• Les Fig. 4a-4e montrent des phases de l'action de l'échappement de l'organe réglant de l'invention.
• La fig. 5 illustre schématiquement une chaîne de transmission comprenant un barillet, un rouage multiplicateur, et un organe réglant selon un aspect de l'invention.
• La fig. 6 montre la position du point de début de l'impulsion sur la surface d'impulsion de l'ancre de l'organe réglant de l'invention.
• La figure 7 montre la distance angulaire θ parcourue par la roue d'échappement en fonction du temps

Examples of implementation of the invention are indicated in the description illustrated by the appended figures in which:

• The Fig. 1 illustrates a clockwork movement comprising a regulating member according to one aspect of the invention.
• The Fig. 2 shows the regulating organ of the invention in the movement of the figure 1 , and
• The Fig. 3 represents the same regulating organ in exploded view
• The Fig. 4a-4e show phases of the action of the escapement of the regulating member of the invention.
• The Fig. 5 schematically illustrates a transmission chain comprising a barrel, a multiplier gear, and a regulating member according to one aspect of the invention.
• The Fig. 6 shows the position of the start point of the pulse on the impulse surface of the anchor of the regulating member of the invention.
• The figure 7 shows the angular distance θ traveled by the escape wheel as a function of time

Example (s) of embodiment of the invention

One embodiment of the regulating member of the invention is illustrated, in a simplified manner, on the Fig. 1 and 2 . In this example, the movement comprises a dual chain with a first regulating member, a first gear and a first barrel (not shown) for measuring the current time, and a second regulating member, a second gear and a second barrel. 32 for the chronography. The oscillation frequency of the second regulating member is greater than the oscillation frequency of the first regulating member, in order to guarantee a necessary and sufficient power reserve for the channel devoted to displaying the time, and a very fine resolution. for the measurement of durations by the chronograph.

The regulating organ of the chronograph comprises an escape wheel 60 with a predetermined number of protruding teeth having a precise geometry 63, preferably more than 25 teeth, for example 40 teeth. The high number of teeth reduces the pitch between the teeth and thus makes it possible to reduce the angular distance traveled by the escape wheel 60 at each alternation, thereby reducing the amount of energy required for each alternation, and to increase the frequency oscillation.

This geometry and this number of teeth make it possible to accelerate the anchor wheel quickly and therefore to communicate the energy as often as possible to the regulating member. Instead of completely stopping the anchor wheel at each cycle, this geometry slows it down at the end of the impulse. The cycle requires a very short pulse angle and as such allows a large number of teeth. The duration of a cycle is very low and it is during this period that one must accelerate the wheel to create sufficient kinetic energy. This exhaust is characterized by very large accelerations. The beam oscillator thus produced consumes substantially less energy than a conventional scroll oscillator, typically at least two times less than a conventional oscillator.

The anchor 80 of the chronograph comprises a fork, comprising two arms intended to engage with the teeth of the escape wheel 60, integral with a flexible beam, also called rod, 90. The length of the flexible beam 90, as well as its section and the chosen material, gives it a voluntary flexibility; advantageously, the beam is longer than in a conventional Swiss anchor escapement anchor. The anchor is itself an oscillating element. The voluntary oscillations of the flexible beam (or rod) determine the resonance frequency of the coupled oscillator system consisting of the anchor and the vibrating blade 100.

The anchor pivots and deforms voluntarily at each alternation about the axis 91, which may be provided with a bearing of a ball bearing or stone.

The anchor is preferably devoid of pallets, in view of the speed of rotation of the escape wheel and the amount of energy transmitted to each pulse; the production of sapphire or ceramic pallets would be complex and would weigh considerably on the anchor. Instead, each of the two levers 84a, 84b (or arm) of the anchor has a notch (or projection) 83a-83b not prominent, with precise geometry, allowing the anchor to disengage the teeth of the wheel exhaust with a very low amplitude rotation. In a variant, however, the resting surfaces 83a-83b could be made by stone or ceramic pallets. According to a characteristic of the invention, the escapement thus comprises an anchor 80 which oscillates around the articulation point 93 with a very low oscillation angle, of the order of 4-5 ° for example. The cycle thus generated is different from the cycle of a conventional Swiss anchor escapement.

The anchor 80 does not include in this example either dart or ankle. The hinge 93 at the end of the anchor 80 connects the anchor in an articulated manner to an arm 95. The other end of the arm 95 is connected to the free end of a vibrating blade 100. In this example not In a limiting manner, the arm 95 is mounted almost perpendicular to the vibrating blade 100, so that the transverse vibrations of the vibrating blade 100 are transmitted to the arm 95 and to the flexible beam 90 of the anchor. The axis of rotation 91 of the anchor being fixed, the arm 95 and flexible beam 90 fold or unfold around joint 93 at each alternation.

Non-perpendicular fixtures may also be considered. Furthermore, it is also possible to produce systems in which the vibrating blade 100, the arm 95 and / or the anchor extend in different planes from each other.

The first end 103 of the vibrating blade is fixed relative to the plate. In this example, the first fixed end of the vibrating blade 100 is screwed on the plate by means of the screw 101, other fixing means may be provided. A device 102 makes it possible to tune the assembly by generating a prestressing: in the illustrated embodiment, this device comprises eccentric 102 also screwed onto the plate and which can be turned to apply a prestressing force on the vibrating plate 100; by turning this eccentric, one modifies the force of stress applied on the vibrating blade, and one modifies the resonance frequency of the vibrating blade and / or its coupling with the arm 95.

The vibrations of the free end of the vibrating blade 100 are transmitted to the anchor 90 through the arm 95. In one embodiment, the connection between the vibrating blade 100 and the arm 95 constitutes a single pivot and a slide simple, allowing possible rotation and sliding between the two elements; the vibrating blade 100 enters the arm. Any link allowing the desired relative movement between the vibrating blade and the arm or coupler can be used, so as to avoid an arching of the arm 95 or the vibrating blade 100 due to stresses exerted on this link.

The beam 90 of the anchor thus acts as an exciter, the arm 95 constitutes a connecting beam, or connector, to transmit this excitation to the blade 100 (or oscillator) and make it vibrate or oscillate around its point of rest. Other types of exciters, including a magnetic exciter exerting a variable magnetic field in time, can be used to vibrate the vibrating blade 100.

The escape wheel 60 is driven by a source of mechanical energy, for example one or more barrels 32 schematically represented on the Fig. 6 by means of a multiplier gear wheel 35. The surfaces 81a and 81b of the anchor 80 alternately receive a mechanical pulse of the teeth 63 of the escape wheel 60, thus determining isochronous oscillations of the blade vibrator 100 connected to the anchor 80. The escape wheel 60 advances a tooth at each alternation of said oscillations.

The mechanical power available to the escape wheel 60 is not constant but, in known manner, decreases with the running of the watch. From a maximum value, corresponding to the drum completely raised, the power is gradually reduced during the relaxation of the barrel. Therefore, the amount of energy transmitted to the anchor 80 at each pulse given by the anchor wheel decreases with the load of the barrel.

In order to maintain a constant amplitude of oscillations of the vibrating plate 100, and therefore an isochronous operation, the movement comprises means to ensure that the moment transmitted to the anchor at each pulse is substantially constant, whatever the load of the cylinder, at least during a barrel operating range sufficient to measure the times for which the chronograph is designed.

In a first embodiment, the barrel is modified so as to deliver a constant torque. For example, the barrel may include means for limiting the range of use in an area in which the torque supplied is substantially constant, artificially reducing the running time of the chronograph. A barrel that can theoretically perform 7 to 10 turns to ensure a significant power reserve It can be limited and prevented from relaxing beyond one revolution, or less than one turn, to ensure that in this range the torque supplied is as constant as possible.

In a second embodiment, which may also be combined with the first embodiment above, the barrel may be associated with a rocket or other equivalent element to regulate the torque transmitted to the gear train 35.

In a third embodiment, the escape wheel 60 and / or the fork of the anchor 80 are modified in their geometry so as to transmit to the anchor a moment of pulse which is substantially independent of the engine torque transmitted to the the escape wheel by gearing 35. The geometry of the receiving tooth of the anchor is calculated so that a variation of torque at the anchor wheel will cause a variation of speed and therefore a linear contact zone included between a contact point at maximum speed and a point of contact at a minimum speed. Whatever the point of contact, the moment will be constant by geometric variation of the lever arm. This third embodiment can be combined with the first and / or second embodiment above.

The Fig. 4a-4e show phases of the action of the escapement of the regulating member according to this third embodiment of the invention. The Fig. 4a corresponds to the end of the fall, and at the beginning of the impulse on the exit surface 81b of the anchor 80. The rotation of the escape wheel 60 continues until the tip of the tooth 63 in contact with the anchor does not stop against the rest stop 83b, as shown on the figure 4b . In this position of rest on the output, the rotation of the escape wheel 60 is interrupted by the notch 83b on the fork of the anchor 80.

The oscillation of the anchor 80 under the effect of the vibrations of the vibrating blade 100 leads to the release of the tooth 63 and the release of the escape wheel 60. A fall phase follows, until at the moment, visible on the Fig. 4c , where another tooth 63 of the wheel 60 comes into contact with the other impeller surface 81a of the lever or inlet arm of the anchor 80.

The rotation of the wheel 60 continues during the pulse phase on the input pulse surface 81a, until the tooth 63 reaches the rest stop 83a, as shown in FIG. Fig. 4d . This rest phase lasts until the moment of release, visible on the Fig. 4th , which gives rise to a new fall phase and the beginning of another cycle.

Thus, in the escapement according to the invention, the pulse phases precede rest phases, whereas in most of the escapements used in wristwatches, the rest phases are followed by pulse phases, and the phases impulse precede falls.

According to a preferred embodiment of the invention, the point of first contact between a tooth 26 and a pulse surface 81a-b of the anchor 80 is not fixed, but varies according to the rotation speed of the escape wheel 60, and therefore the power transmitted by the wheel. This aspect is illustrated on the Fig. 6 . When the barrel 32 is fully armed, the contact between the tooth 63 and the impulse surface occurs at point 86a. With reduced power, the acceleration of the escape wheel 60 is limited, the fall time increases, and the contact takes place at 81b, lower. The displacement of this point of contact has the effect of modifying both the moment of impulse transmitted to the anchor 80, and / or the duration during which a moment is transmitted. Advantageously, the moment of impulse transmitted to the anchor is thus substantially independent of the speed of rotation of the escape wheel. A rapidly rotating escape wheel exerts a large force on the anchor 80 at the moment of the impulse, but at a point 86a close to the center of rotation of the anchor. An exhaust wheel driven by a lower tensioned cylinder reaches the anchor with less energy, but exerts the momentum force at a point farther from the center of rotation of the anchor. This results in a pulse moment transmitted to the anchor substantially constant.

The shape of the impulse surfaces 81a and 81b is optimized to ensure this constant pulse moment. In one embodiment, these pulse surfaces are curved, for example cycloidal, preferably and for example brachistochronous. In another less optimal but simpler embodiment, the pulse surfaces are constituted by straight line segments.

According to an important aspect of the invention, if the power available to the exhaust is insufficient, for example when the cylinder is insufficiently reinforced, the release of the tooth 63 can take place before it reaches the notch. In this case, the impulse phase is followed by a falling phase without stopping the escape wheel 60. During the following alternation, the escape wheel does not start from a rest condition, but already has a non-zero rotation speed, and may reach the rest stop (on the other lever of the anchor) despite the reduced available power, or at least closer to it. It is also possible that the very slow escape wheel stops against the notch after a greater number of alternations, for example after three, four or more alternations. This characteristic, obtained in particular thanks to the slightly protruding notches 83a-83b and the geometer of the teeth 63, avoids completely stopping an escape wheel which has too little energy, and allows it to continue its acceleration during several successive alternations. .

The regulating member of the invention thus comprises, in addition to the normal operating mode, with a rest phase for each alternation, a reduced power operating mode, in which one has a rest phase each two, three or N alternations. In the reduced power regime, the gait of the regulating organ remains regular.

The figure 7 shows the angular distance θ traveled by the escape wheel 60 as a function of time. The line 200 shows the "ideal"walk; the escape wheel rotates at a constant speed. Curve 201 shows a curve corresponding to a conventional escapement, and the escapement of the invention in its normal operating mode, in which the escape wheel is stopped at each alternation by the anchor, then accelerates again until at the next point of rest during the next alternation. Curve 202 shows the angular distance traveled by the escape wheel of the invention in a reduced power operating regime; during certain cycles, the anchor releases the escape wheel before stopping it, which allows the wheel to continue its acceleration during one or more successive alternations.

It has been found that the excitation of the oscillations of the vibrating blade 100 is better when the beam 90 of the anchor is itself flexible, and has a mass concentrated at its end. The flexibility of the beam 90 is advantageous in that it makes it possible to transmit the vibratory energy to the blade 100 without stopping the oscillation. In the example shown on the figure 1 the mass is constituted by the hinge joint 93 itself. The connection between the flexible beam 90 of the anchor and the vibrating blade 100 is provided by an arm (or connector) 95. This arrangement thus constitutes a system of oscillators coupled between the vibrating blade 100 and the flexible beam 90 of the anchor. It is also possible to provide an arm 95 (or connector) provided with a certain flexibility to enable it to oscillate. In this case, the arrangement therefore constitutes a system with three oscillators 100, 95, 90 coupled. The small mass can also be an additional tuning device. This device can for example be peelable or automatically ablated by means of a laser (automatic tuning ...).

It is well understood that the inertia of the anchor 80 and the arm 95, and the coupling between the vibrations of the blade 100 and those of the flexible beam 90 modify the dynamics of the composite system. The oscillation eigenfrequencies are generally not calculable with analytical methods, but can be obtained by simulation methods known numerals and also depend on the prestressing applied to the blade 100. It is possible to obtain oscillation frequencies of 1 kHz or higher.

In a variant, the anchor 80, the flexible beam 90 of the anchor, the arm 95 and the blade 100 are made in one piece. In this variant, the system can be completely flexible and without joints.

The anchor 80, the flexible beam 90 of the anchor and the arm 95 and / or the blade 100 may be made by micromachining processes, for example from a silicon wafer by an ion etching process. reactive (DRIE) or any other suitable method. Silicon can be coated with a layer of silicon oxide to compensate for the influence of temperature.

In a variant, the anchor 80, the flexible beam 90 of the anchor and the arm 95 and / or the blade 100 may be made of metal, preferably a metal whose elastic and dimensional qualities do not depend on the temperature, such as than the elinvar.

The present invention also relates to a method of adjusting the oscillation frequency of a regulating member as described above. Several adjustment methods can be implemented independently of one another, or combined with one another.

As mentioned above, by turning the eccentric 102 near the fixed end 103 of the vibrating blade 100, the force of stress applied to this blade is modified, which makes it possible to modify the frequency of the system.

The oscillation frequency can also be adjusted by varying the length of the vibrating portion of the flexible blade 100, for example by varying the embedment depth of the flexible blade. A micrometer screw can be provided for this purpose.

The oscillation frequency can also be modified by modifying the mass of the oscillating blade, or preferably a mass along or at the end of the anchor, for example the mass 93 forming the articulation with the arm 95. The mass variation may for example be obtained by laser micromachining of the mass 93 to correct the resonance frequency of the oscillating member.

External elements, for example removable or displaceable masses, may be added to or moved along the vibrating mass 100, the arm 95 and / or the anchor 80 to modify the frequency. External magnets can also be moved to exert a controlled influence on the vibrating blade 100.

According to another aspect of the invention, the escape wheel 60 is elastically coupled to the barrel or to the energy source 32. In the embodiment illustrated in FIG. figure 1 , a spiral spring 65 is interposed between the escape wheel 60 and the pinion 37 forming part of the train and coaxial with the escape wheel. This spiral spring stores the energy transmitted by the barrel through the gear even when the escape wheel is blocked by the anchor and it can not rotate; as soon as the escape wheel is released following an oscillation of the anchor, the energy stored by the hairspring 65 is almost instantly released and transmitted to the escape wheel 60 which thus accelerates immediately. In addition, this acceleration is not slowed down by the inertia of the gear train. This device eliminates the inertia of the gear train, major obstacle to large accelerations of the escape wheel. The acceleration of the wheel 60 is limited mainly by its own inertia.

The escape wheel 60 will preferably be made to reduce its moment of inertia. It is preferably made of steel or a lightweight material, for example silicon, a Ni-P alloy, or titanium, or an alloy containing titanium.

The hairspring 65 then stretches during each rest phase of the anchor 80, then relaxes suddenly during the release. It oscillates with each alternation, like a spiral in a classic regulating organ. However, unlike a conventional regulating organ, this hairspring does not directly determine the cycles of the exhaust which are here determined by the vibrating blade. This spring is calculated specifically according to the mechanical power available to the anchor wheel, the inertia involved and the required speeds on the anchor wheel.

The hairspring 65 also makes it possible to damp the shocks associated with the alternation between the impulse phases and the rest phases. In this way, even if the rotation of the escape wheel is jerky, the gear train 35 and the barrel 32 rotate with a nearly constant speed, and the energy efficiency is improved.

Elastic coupling between the escape wheel and the wheel can also be obtained by means of an elastic element other than a spiral spring, for example another type of spring. Furthermore, an elastic coupling could also be provided at another location in the train between the barrel and the escape wheel, for example upstream of the pinion 37 on the exhaust axis.

The illustrated adjustment member oscillates at a high frequency (preferably greater than 50 Hz, typically greater than 500 Hz, for example 1000 Hz) requires a corresponding power which causes, as on any chronograph, a limited power reserve. Since the primary objective is to produce a precise instrument, care will be taken to guarantee a power reserve adapted to the duration of the time interval during which one is able to chronologically guarantee the target decimal place. This regulating organ is therefore primarily intended to regulate a chronograph used for limited periods, for example durations of less than a few minutes. hours, typically lasting a few minutes or corresponding for example to the typical duration of a sporting event. Tests and simulations have demonstrated that the use of a vibrating blade at 1000 Hz associated with the escapement of the invention makes it possible to reach or exceed the power reserve of a chronograph at 500 Hz based on a hairspring. which shows that at constant available energy, the efficiency, in terms of energy spent alternately, is at least twice as high. The high frequency regulating organ is thus stopped most of the time, except when the chronograph is used. In order to ensure an instantaneous start of the regulating member, an unillustrated launcher is advantageously provided for vibrating the vibrating blade when the user presses the START button of the chronograph. In one embodiment, this launcher acts by applying a pulse directly to the vibrating blade. In another embodiment, the launcher acts by applying a brief pulse on the mass 93 to the articulation between the arm 95 and the anchor 80, so as to constrain this articulation and thus exert a traction or a push on the free end of the vibrating blade which begins to oscillate. The same launcher can be used when the user presses the STOP key to lock the regulating member, for example by pressing the joint 93 thus preventing the anchor 80 from oscillating.

The movement advantageously comprises openings making it possible to see the vibrating blade 100, the arm 95 and / or the anchor 90. Advantageously, the movement also makes it possible to see the hairspring 65. The movement can be integrated in a watch which makes it possible to see through the dial one or more of the elements 90, 95, 100 and / or 65. Such an opening through the movement and the dial also makes it possible to hear the very characteristic noise of the oscillations of the regulating organ, for example the noise created by oscillations between 500 and 2000 Hz.

Reference numbers used in the figures

32

barrel

35

cog

37

Pinion on the axle of the escape wheel

60

escape wheel

63

tooth of the escape wheel

65

elastic coupling, spiral

80

anchor

81a, b

impulse surfaces

83a, b

notches

84a, b

levers (arms) of the anchor

86a, b

start point of the impulse

90

beam (rod) of flexible anchor

91

anchor axis

93

anchor joint

95

arms

100

vibrating blade

101

point of attachment of the vibrating blade

102

eccentric

103

fixed end of the vibrating blade

Claims (20)

Clock-setting member comprising a vibrating oscillator (100) mechanically connected to an anchor (80) having pulse surfaces (81a, 81b) alternately receiving a mechanical pulse of the teeth (63) of a wheel exhaust (60), so as to maintain isochronous oscillations of said vibrating oscillator, and to advance said escape wheel (60) of a tooth at each alternation of said oscillations, a barrel (32) driving said wheel of exhaust through a gear train (35), characterized in that said teeth (63) of the escape wheel and said anchor are arranged to allow an operating regime in which the escape wheel has only one phase rest every two, three, or more alternations. A regulating member according to claim 1, wherein said vibrating oscillator comprises a balance sprung assembly. A regulating member according to claim 1, wherein said vibrating oscillator comprises a tuning fork or a vibrating blade (100). A regulating member according to claim 3, wherein said vibrating blade is resilient and recessed at one end. A regulating member according to claim 4, said resilient blade being connected to a flexible rod (90) of said anchor by a mechanical connector (95). A regulating member according to claim 5, wherein said connecting means (95) comprises an arm (95) connected to the flexible rod (90) by a hinge. A regulating member according to claim 5, wherein said anchor (80), said flexible strip (90), said connector (95) and said elastic strip (100) are made in one piece. A regulating member according to one of claims 5 to 7, wherein said anchor (80), said flexible strip (90) and said connector (95) are made from a single silicon plate. Regulating member according to one of claims 4 to 8, wherein said elastic vibrating blade (100) is made elinvar. Regulating member according to one of claims 1 to 9, wherein the anchor (80) has, at the ends of the impulse surfaces (81 a, 81 b), rest notches (83a, 83b) against which the teeth (63) of the escape wheel,
said rest notches being sufficiently protruding (83a, 83b) to allow said operating speed in which the teeth (63) of the escape wheel abut against said notches only every two, three, or more alternations when the power available at the escape wheel is weak. Adjusting member according to one of claims 1 to 10, wherein the anchor and the escape wheel are arranged to allow the escape wheel to continue its acceleration for several successive alternations. Regulating member according to one of claims 1 to 11, wherein said escape wheel comprises more than 25 teeth. Regulating member according to one of claims 1 to 12, wherein said isochronous oscillations have a frequency of not less than 1 kHz. Adjusting member according to one of claims 1 to 13, arranged so that the torque applied to said anchor by said pulse is substantially constant regardless of the voltage of said barrel. A regulating member according to claim 14, arranged in such a way that the point of first contact between the teeth (63) and the impulse surfaces (81a, 81b) moves along the impulse surface as a function of the tension of the barrel (32), so as to regulate the torque applied to said anchor by said pulse. Chronograph or clockwork comprising a regulating member according to one of claims 1 to 15. Chronograph or clockwork according to the preceding claim, wherein said escape wheel (60) is elastically coupled to said energy source (32). Method of operating a clockwork movement comprising a barrel and regulated by means of a regulating member comprising an anchor and an escape wheel, characterized in that the escape wheel has an alternating rest phase when the torque provided by the barrel is maximum, and less than a rest phase alternately when the torque provided by the barrel is reduced. The method of claim 18, wherein the escape wheel continues to accelerate for several successive alternations when the torque provided by the barrel is reduced. Method according to one of claims 18 to 19, wherein the impulse phases of the exhaust precede the rest phases.

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