EP2689295B1 - Regulating member for a mechanical wristwatch - Google Patents

Description

Technical area

The present invention relates to a regulating organ for a mechanical wristwatch. The present invention relates in particular to a regulating organ for a chronograph.

State of the art

Mechanical watches generally comprise a regulating member consisting of a flywheel called pendulum on the axis of which is fixed a spiral spring called spiral.

In the prior art there are different types of rockers of various shapes; the most common balancers used in wristwatches consist of an annular mass, the serge, held by two or three arms. Other types of pendulum exist, for example balancers devoid of serge and having only arms, as in FR330210A , or arms cooperating with flyweights made of high density metal to improve the weight / inertia ratio of the balance, as described for example in CH698125 .

Given the energy available, rockers usually have a high moment of inertia for a low mass; that is to say that their diameter is as large as the volume available, and that the mass is concentrated at the periphery, for example in the serge or in other elements, for example weights. This moment of inertia can also be modified to adjust the watch, either manually with screws, or automatically in the case of bimetallic rockers that deform with the temperature. Involuntary deformations of the balance, for example due to expansion, however, have the effect of disrupting the progress of the watch.

In spite of the multitude of forms that the pendulums can take in the state of the art, the term balance can be defined by its function, unique or in any case principal, which is to increase the inertia of the regulating member to determine, together with the spiral spring, the oscillation frequency of the regulating member. Indeed, in the state of the art, the sprung balance oscillates around its equilibrium position at a frequency that depends mainly on the rigidity of the balance spring and the moment of inertia of the balance.

According to this definition, a rocker therefore constitutes a piece mounted on the balance shaft, pivotable with this axis and whose mass is distributed around the axis so as to give the regulating member a greater inertia in rotation. In other words, the word "pendulum" in this context indicates a piece whose main function, or even unique, is to accumulate at each oscillation a potential and kinetic energy which is higher, generally much higher, than that accumulated by the axis of the balance around which the oscillation takes place. For example, the potential and kinetic energy accumulated by a balance according to this definition is greater than or equal to at least 10 times that accumulated by the balance shaft, typically at least 1000 times greater.

The balance therefore has a moment of inertia which is greater than or equal to at least 10 times the moment of inertia of the axis, preferably at least 1000 times greater.

The moment of inertia of a regulating member is determined by the set of rotating parts, including the balance shaft, the balance, the hub, the plate, the spiral, etc. In conventional regulating devices, this moment of inertia is, however, largely determined by the pendulum alone, which contributes at least 80% to the moment of total inertia of the rotating assembly. Preferably the moment of inertia of the balance represents at least 95% of the moment of inertia of the rotating assembly.

The rocker must therefore be distinguished from other elements such as the hub or the dowel plate, whose main function is not to increase the mass or the moment of inertia of the regulating member, whose moment of inertia is generally of the same order as the moment of the balance shaft, and which contribute only a small percentage to the moment of inertia of the rotating assembly

In other words the balance serves as flywheel and fills the lack of energy stored in the hairspring during deformation. However the pendulum is source of many disturbances, due to inaccuracies of its inertia during its manufacture, dilations, etc.

A given pendulum coupled to a given spiral oscillates at a given frequency. The number of alternations per unit of time determines the temporal resolution of the regulator. For example, a mechanical watch displaying the seconds of the current time must comprise a regulating member performing at least 3,600 vibrations per hour. In practice, the usual regulating bodies perform 28,800 or sometimes 36,000 vibrations per hour, which makes it possible to measure the time with a resolution of 0.125 or 0.1 seconds, respectively.

By increasing the oscillation frequency, the temporal resolution is improved, allowing shorter time intervals to be counted. An improved temporal resolution is especially useful for chronographs, for which a time resolution of the hundredth of a second is sometimes desired. A high oscillation frequency, however, generates significant energy losses, especially at the exhaust, which reduces the power reserve of the watch. For this reason, the oscillation frequency chosen is usually a compromise between the resolution requirements of the chronograph and the desire to maintain as high a power reserve as possible for the display of the current time.

The usual chronograph watches take the energy necessary for the operation of the chronograph on the kinematic chain linking the barrel to the regulating organ and to the indicators of the watch. As a result, the watch is disturbed when the chronograph is started.

The patent application WO03 / 065130 in the name of TAG Heuer SA suggests a construction in which a basic movement intended for the display of the current time is provided with a first barrel and a first regulating organ performing 28,800 oscillations per hour, while an auxiliary chronograph module is provided with a second barrel and a second regulator member performing 360'000 oscillations per hour. This construction makes it possible to produce a chronograph watch capable of measuring the time with a resolution of one hundredth of a second, without affecting the power reserve of the basic movement used for the display of the current time. Moreover, since the two kinematic chains are independent, the start of the chronograph does not affect the precision of the basic movement and the running of the watch. This solution was implemented in TAG Heuer's "Caliber 360" which demonstrated the technical feasibility of the solution.

Brief summary of the invention

An object of the present invention is to provide a regulating organ for a mechanical wristwatch, in particular a regulating organ for a mechanical chronograph, capable of measuring the time with an improved resolution compared to the prior art.

Another object of the invention is to propose a regulating organ for a mechanical wristwatch which makes it possible to measure the time with a resolution of one hundredth or even one thousandth of a second.

According to the invention, these objects are achieved in particular by means of a regulating organ comprising the characteristics of the independent claim 1 and a mechanical chronograph comprising such a regulating member.

This solution has the advantage over the prior art of overcoming problems related to the balance, including accuracy problems due to deformations and manufacturing tolerances of the pendulum.

The claimed regulating member is therefore devoid of any pendulum according to the definition given above, that is to say of any rotary member whose sole or principal function is to increase the moment of inertia of the assembly. rotation, and whose moment of inertia would contribute at least 80% to the moment of inertia of the rotating assembly.

This solution also has the advantage of considerably reducing the moment of inertia of the rotating elements on the axis of the spiral, and therefore to increase the frequency of oscillation.

Tests and calculations have shown that it is possible to achieve with this solution purely mechanical regulators capable of oscillating at 50 Hz, or even 500 Hz or more.

Brief description of the figures

• La figure 1 illustre une vue en perspective d'un organe régulateur selon l'invention.
• La figure 2 illustre une vue de dessus d'un organe régulateur selon l'invention.
• La figure 3 illustre une vue en perspective de l'axe, du moyeu et du plateau d'un organe régulateur selon l'invention.
• La figure 4 illustre un lanceur.
• La figure 5 illustre une vue de dessus de l'ancre.
• La figure 6 illustre une vue de dessous de l'ancre.
• La figure 7 illustre une vue tridimensionnelle de l'organe régulateur selon l'invention, du ressort, de l'ancre et de la roue d'ancre.

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

• The figure 1 illustrates a perspective view of a regulating member according to the invention.
• The figure 2 illustrates a top view of a regulating member according to the invention.
• The figure 3 illustrates a perspective view of the axis, the hub and the plate of a regulating member according to the invention.
• The figure 4 illustrates a launcher.
• The figure 5 illustrates a top view of the anchor.
• The figure 6 illustrates a bottom view of the anchor.
• The figure 7 illustrates a three-dimensional view of the regulating member according to the invention, the spring, the anchor and the anchor wheel.

Example (s) of embodiment of the invention

An embodiment of a regulating member according to one embodiment of the invention is illustrated on the Figures 1 and 2 . This regulating organ is in particular intended to serve as a regulator for the chronograph function of a mechanical chronograph; the same movement may comprise two regulating members on the same plate, or on two separate plates, one of the regulating organs serving to regulate the operation of the watch while the other regulating organ, similar or similar to that described in this application , serves to adjust the operation of the chronograph function. A separate barrel provides the energy required by each regulator member, which avoids disruptions in the operation of the watch when the chronograph is engaged.

The power reserve of the second cylinder, which indicates the duration that can still be timed before having to recharge the second cylinder, is preferably indicated on the dial by means of a chronograph power reserve indicator. The power reserve of the first barrel charging the first regulator member used for the display of the current time is advantageously indicated separately on the dial by means of a power reserve indicator of the watch. The two barrels can preferably be loaded simultaneously by means of a common winding rod engaging on the two barrels and / or by means of a common oscillating mass. In another variant the first barrel is automatically reassembled and the second manually. In a variant, the two barrels can be raised separately by means of two separate winding rods and / or oscillating masses. In another variant, one of the barrels (for example the chronograph cylinder) is loaded by the other cylinder manually or automatically remounted; the energy available is distributed between the two barrels.

The illustrated regulator comprises a hairspring 1 mounted with a ferrule 5 on a hairspring axis 2. The regulating member is devoid of balance. According to the example, the regulating organ of the chronograph is sized to oscillate at frequencies never reached before, preferably at a frequency of 3'600'000 vibrations per hour, or 500 Hz.

In order to reach these high frequencies, the regulating member comprises in particular an axis 2, which is intended to rotate between two non-represented bearings when the hairspring 1 is stretched and relaxed. A plate 4 mounted on this axis carries the plate pin 40 which collaborates with the horns 60, 65 and with the stinger 61 of an anchor 6 shown in FIGS. Figures 5 and 6 , similar to the more conventional Swiss anchor escapements.

In this context, the word "plate" therefore designates a part intended to be mounted on the axis of the regulating organ and which comprises an ankle, called a plateau pin, arranged to collaborate with the horns and with the stinger of an anchor .

The plate 4 is advantageously made of silicon or ceramic or other material with a lower density than that of the axis 2, in order to reduce its moment of inertia. It is advantageously formed of two disks: the large plate 42 and the small plate 43, interconnected by a gun 45. The small plate may comprise a notch 430 for the dart. A simple tray, with a single disc, can also be used.

Axle 2 also carries a hub 3 driven or glued which serves to provide a bearing surface for whip 72 of the launcher, described below in connection with the figure 4 . The axis of the regulating member is thus accelerated almost instantaneously when the pushbutton 75 is engaged so as to communicate a pulse to the hub 3 through the blade 73, the column wheel 74 and the launcher 7. At the stop of the chronograph, the pressure of the whip 72 on the hub makes it possible to block the hub while maintaining the regulating organ of the chronograph and thus to preserve the position of the chronograph hands.

In this context the term "hub" indicates any part intended to be mounted on the balance shaft, pivoting with this axis and cooperating with a spiral spring, which accumulates a potential energy and kinetics weak or comparable to that accumulated by the balance shaft. For example, the potential and kinetic energy accumulated by the hub is comparable to that accumulated by the balance shaft, or less than 10 times greater than the potential and kinetic energy of the axis, or smaller than that of the axis. 'axis. In the calculation of regulating members for conventional mechanical watches, the moment of inertia of the hub is generally neglected because it is significantly lower than the moment of inertia of the balance.

For example, the moment of inertia of the hub is of the order of magnitude of 0.001 mg · cm ² , that of the axis 0.010 mg · cm ² and that of the balance 10 mg · cm ² .

The only function of the hub according to the invention is to provide a bearing surface for the launcher whip 7.

In a preferred embodiment the hub 3 is a separate part of the plate 4. In another variant, as will be seen below, the hub 3 and the plate 4 are integrated into a single element.

In another variant, it is the axis 2 which provides a bearing surface of the launcher whip: in this case the presence of the hub 3 is not necessary.

Unlike a beam, the hub 3 is devoid of rays; its mass is thus concentrated near the center, so as to reduce its moment of inertia. The hub 3 is advantageously made of silicon or of another material with a lower density than that of the axis 2, in order to reduce its moment of inertia. In a variant, the hub is made of titanium and / or aluminum and / or an alloy containing at least one of these materials.

Blind openings 30 in a plane perpendicular to the axis 2 further lighten the hub 3. Blind or through openings in other direction, including holes through the hub parallel to the axis or according to any which direction, can also be used to lighten the hub 3. It is also possible to lighten the hub 3 by making it with a lighter core covered with a stronger coating on which the whip 72 of the launcher can give a pulse without deforming the hub 3.

In the same way, it is also possible to lighten the plate 4 by leaving through openings or blind, it is given a non-circular shape, in order to reduce its moment of inertia.

The openings in the hub and / or in the plate have the sole function of reducing their mass and therefore their moment of inertia. They do not serve as fixing means, and do not allow to receive adjustment screws or to avoid breaks in the hub or plate and are not used either to fix the hub or the plate to the axis.

The regulating organ is devoid of a pendulum; its adjustment is done only with the raquetterie spiral 1, preferably by adjusting the length of the oscillating portion of the spiral by means of a screw perpendicular to the plate and to adjust the fixing point of the outer end of the spiral on platinum or on a bridge. This system allows a very precise adjustment of the length of the hairspring, but other known types of adjustment are applicable to the hairspring.

In a variant, the expression "regulating member without pendulum" indicates that the regulating member comprises a spring arranged to oscillate at high frequencies, for example at 50 Hz, or even at 500 Hz or more, and a solid balance shaft , that is to say an axis which determines, with a hub and / or plateau, the moment of inertia of the regulating member, no additional piece being added on this axis in order to increase the moment of inertia.

The diameter of the hub 3 is as small as possible, always in order to reduce its moment of inertia. In a preferred embodiment, the diameter of the hub 3 is between 1.5 and 10 times the maximum diameter of the axis 2, for example between 5 and 6 times the diameter of the axis 2. In the example shown, the The outer diameter of the hub 3 is identical to the outside diameter of the plate 4. If a bearing surface for the larger launcher 7 is required, it will be possible to use a hub 3 which is slightly larger than the plate 4, although its diameter preferably does not exceed not double the maximum diameter of the large plate 42.

Unlike a regulator comprising a balance, which provides a potential energy and kinematic substantially greater than that of the axis 2, the potential and kinetic energy accumulated by the hub 3 is less than that which is accumulated by the axis 2 at each oscillation, preferably negligible compared to that of the axis 2.

The hub 3 can also be an integral part of the axis 2. In a variant, the hub 3 and the plate 4 are integrated in a single element, for example made by bar turning, which carries the plate pin 40 is on which s' supports the launcher 7. In another variant the ferrule is also integrated in this element. This element may advantageously be made of titanium and / or aluminum and / or an alloy containing at least one of these materials.

The ferrule 5 maintains the inner end of the spring 1 on the axis 2. It is advantageously made in the form of a circular disc whose two or more segments are truncated to lighten it and reduce its momentum. inertia. A notch 50 in the side of the shell 5 is used to fix the spiral. The maximum diameter of the ferrule is preferably of the same order of magnitude as the maximum diameter of the plate and the hub. For example, the diameter of the hub 3 may be between 1 and 3 times the maximum diameter of the ferrule 5.

• C = constante de rigidité du spiral
• M = couple de rappel du spiral,
• ϕ = angle de torsion.

The hairspring 1 can be made of metal, preferably invar, silicon, diamond, corundum or any other suitable material. Advantageously, the hairspring is much stiffer than a conventional hairspring, and therefore exerts a restoring torque to the rest position significantly greater than a conventional hairspring. The stiffness (or rigidity) of the hairspring is given by the formula: $$\mathrm{VS}=\mathrm{M}/\mathrm{\phi }$$

• C = stiffness constant of the spiral
• M = return torque of the spiral,
• φ = torsion angle.

• Le nombre de spires est moins élevé que dans les spiraux traditionnels, de manière à réduire la longueur de la partie vibrante. Avantageusement, le spiral comporte moins de 5 spires, par exemple 4,5, de préférence 3 spires ou moins.
• Le spiral est plus épais que les spiraux conventionnels : par exemple son épaisseur est supérieur à 40 µm, de préférence supérieur à 50 µm, par exemple 55 µm.
• Il est plus haut que les spiraux conventionnels : par exemple son hauteur est supérieure à 200 µm, de préférence supérieure à 215 µm, par exemple 230 µm.
• Il peut être réalisé dans un matériau plus rigide, de préférence pas sensible aux variations de température.
• Des nervures ou une section rectangulaire peuvent être utilisés pour le rigidifier.
• Un revêtement de surface peut être utilisé pour le rigidifier.
• La section du spiral peut être non constante le long du spiral pour le rigidifier.

High rigidity required for oscillation at 500 Hz can be achieved by combining at least two of the following:

• The number of turns is lower than in traditional spirals, so as to reduce the length of the vibrating part. Advantageously, the spiral comprises less than 5 turns, for example 4.5, preferably 3 turns or less.
• The hairspring is thicker than conventional hairsprings: for example its thickness is greater than 40 μm, preferably greater than 50 μm, for example 55 μm.
• It is higher than conventional spirals: for example its height is greater than 200 microns, preferably greater than 215 microns, for example 230 microns.
• It can be made of a more rigid material, preferably not sensitive to temperature variations.
• Ribs or a rectangular section may be used to stiffen it.
• A surface coating can be used to stiffen it.
• The section of the hairspring may be non-constant along the hairspring to stiffen it.

The ratio ( e ³ · h ) / l, e being the thickness of the hairspring, its height and its length, is about 30 times greater than the same ratio of a conventional hairspring.

The spiral is advantageously constituted by a perfect Archimedean spiral, which is favorable to isochronism. Because of its stiffness and short length, it hardly deforms under the effect of gravity so that Philips end curves may not be necessary or even advantageous. Its rigidity also makes it less sensitive to disturbances due to magnetostriction. In addition, a rigid spring has the effect of increasing the frequency of oscillations and reducing their amplitude, which makes it possible to operate in a reduced oscillation range favorable to isochronism. Oscillations of reduced amplitude bring in other words a great precision to the watch. Since the oscillations of the hairspring are practically isochronous, the use of a coating, for example of silicon oxide, is no longer necessary.

The stiffness of the hairspring gives it an effective geometric stability: the hairspring therefore does not deform almost in different planes of space. Advantageously therefore this stiff spring has a greater static and dynamic stability compared to conventional spirals at 3-5 Hz. The stiffness of the hairspring also makes it non-self-starting, unlike conventional spring-balance regulators.

The oscillation frequency of conventional spiral-balance assemblies used in horology can be determined using the known formula $$f=\frac{1}{2\mathrm{\Pi }}\sqrt{\frac{M}{I}}$$

This frequency is thus inversely proportional to the square root of the moment of inertia / balance.

In the state of the art, the moment of inertia I of the rotating parts of the regulating member is determined almost exclusively by the serge, which approximates a portion of hollow cylinder. $$I=\frac{1}{2}m\left({\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">R</figure-callout>}}^2+{\mathrm{<figure-callout\; id="2"\; label="r"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">r</figure-callout>}}^2\right)$$

• f Fréquence d'oscillation [Hz]
• M Couple élastique du spiral [Nm]
• I Moment d'inertie du balancier [kg·m²]
• R Diamètre externe du balancier [m]
• r Diamètre interne du balancier [m]
• h Epaisseur du balancier [m]
• ρ Masse spécifique du balancier [kg/m³]

From which we deduce: $$f=\frac{1}{2\mathrm{<figure-callout\; id="1"\; label="\Pi \; M"\; filenames="imgf0001.png,imgf0003.png"\; state="\{\{state\}\}">\Pi \; </figure-callout>}}\sqrt{\frac{M}{}}\sqrt{\frac{}{\frac{1}{2}\mathrm{\Pi }\mathit{h\rho }\left(R^4-{\mathrm{<figure-callout\; id="4"\; label="r"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">r</figure-callout>}}^4\right)}}$$

• f Oscillation frequency [Hz]
• M Elastic torque of the spiral [Nm]
• I moment of inertia of the pendulum [kg · m ² ]
• R External diameter of the balance [m]
• r Internal diameter of the balance [m]
• h Thickness of the pendulum [m]
• ρ Specific mass of the pendulum [kg / m ³ ]

Equations 2) and 3) can not, however, be applied to the regulator of the invention, since this body is devoid of a pendulum. According to the invention, the regulating member is therefore dimensioned by integrating in the equation 1) above a moment of inertia I calculated taking into account elements that are traditionally neglected in the prior art, notably by integrating into the calculation of the moment of inertia I the moments of inertia of the axis 2, the plate 4, the hub 3 and the spiral 1 itself, which gives us an approximation for the frequency of oscillation.

The moment of inertia of the hairspring 1 however varies during each cycle when the hairspring is deformed, so that the application of the formula above gives only an approximation. In practice, an organ oscillating regulator at the desired frequency is obtained using the formula 1) above, I being approximated by adding the mass of inertia of all rotating parts. An adjustment is then obtained by successive approximations by modifying by means of the cock, a racket with a screw on the top, or another adjustment element not shown the length of the portion of the spiral 1 which can vibrate.

Prototypes were made with regulating devices capable of performing 500 oscillations per second, which makes it possible to measure timed durations with a resolution of one thousandth of a second. It is thus possible to achieve a mechanical chronograph at 500 Hz or thousandths of a second.

The Figures 5 and 6 illustrate an embodiment of an escapement anchor 6 that can be used with such a regulating member. Compared to a conventional regulating member, the regulating member of the invention is characterized by substantially higher axis rotation speeds, for example 125 times greater. The impulse provided by the tooth of the anchor wheel (not shown) to the anchor 6 is therefore much shorter, the energy transmitted being on the other hand more important. This results in a much faster acceleration of the anchor 6: each time the anchor wheel transmits an impulse, the anchor switches almost instantly (in less than a thousandth of a second) between a position and the position opposite. The rotational speed of the teeth of the anchor wheel is such that the vanes can be removed and these teeth rest directly on the anchor inlet and outlet arms by projecting the entry and exit arms. the anchor at a distance as soon as they hit them; the arms do not have time to slip on the teeth of the anchor wheel. In other words the impulse response of the anchor is faster than those known and is of the annular type.

Therefore, according to an independent feature of the invention, and as illustrated in the Figures 5 and 6 , the pallets are removed and an annular contact, that is to say a point contact on a stop or distributed according to a set of coplanar points and whose contact norms compete, is done directly between the teeth of the anchor wheel and the arms 62, 63 of the anchor. The length of the contact between the anchor and the anchor wheel is advantageously less than one tenth of a millimeter, instead of one millimeter of the state of the art. Advantageously, the end of these arms has a rounded shape, for example involute or spiral or involute, this shape can be adjusted finely depending on the frequency of the spiral. In a variant, the teeth of the anchor wheel advantageously have a shape in complementary development, which makes it possible to better adapt to high frequencies and to ensure a perfectly punctual contact. These forms of anchor arms are advantageous for ensuring a fast and punctual contact between the anchor and the anchor wheel, without rebound and almost without slipping, even if, for example following an impact, the anchor or the wheel anchor are not exactly at the expected position during the impulse.

In order to be able to move quickly, the anchor 6 is preferably made of a material lighter than steel, for example silicon. Through holes 64 can lighten it even more. The stinger 61 is constituted by a bridge joining the two horns 60 and 65 but less thick than these horns and the rest of the anchor. The end of the stinger 61 opposite the center of the anchor is pointed to cooperate with the plateau pin 40.

The regulating member illustrated in the figures is advantageously used as an independent regulating member for a chronograph, in order to adjust the running of a chronograph hand in the center of the movement. For example, this regulator member may cause a hand in the center of the dial displaying thousandths of a second of a timed duration, and which travels 100 graduations on the periphery of the dial in a tenth of a second. In order to avoid any play and any loss of energy, the regulating member is preferably arranged in an unusual manner very close to the center of the watch movement, which makes it possible to drive the needle directly to the center, or in any case through a gear chain as short as possible, for example a chain gear having a single wheel to reverse the direction of rotation given by the anchor wheel. Preferably, the axis 2 of the hairspring is in an imaginary circle coaxial with the movement and of diameter less than 50% of the maximum external diameter of the movement, preferably less than 30% of the maximum external diameter of the movement, therefore very close to the center of the movement.

The accelerated chronograph hand can be deformed in the manner of a fishing rod during acceleration, which affects the reading accuracy during movement. In order to limit the extent of these deformations, the needle is advantageously ribbed and / or profiled to make it more rigid. The needle can also be replaced by a disc.

The figure 4 illustrates the launcher mechanism that allows to start the chronograph regulator member when the user presses the push button 75, then to block the regulator organ off. In the case of a regulating member according to the invention, the launcher comprises a flexible whip 72 which bears directly on the hub 3. In a variant comprising a rocker, this launcher mechanism may comprise a whip 72 coming to rest on the pendulum. The whip can include one or more parts and is more flexible than the rest of the launcher, precisely to whip the hub and start it instantly. The pressure of the pushbutton 75 is transmitted by the blade 73 to the column wheel 74, which suddenly releases the launcher 7 which is actuated by the launcher spring 71. The energy of this spring 71 is transmitted to the whip 72, which imparts a force at the hub 3 having a large tangential component, so as to accelerate suddenly the hub or the balance and the axis of the spiral which allows to launch almost instantaneously the oscillator. At rest, when the user has pressed the push button 75, or an additional push button STOP not shown, the whip 72 presses on the hub 3 exerting a large radial force, in the position illustrated on the figure 4 , which blocks the axis of the hub or balance momentarily and energetically.

The push button 75 in a preferred embodiment allows the user to perform both START and STOP functions. Another push button, not shown, allows reset.

When the user actuates the STOP function, he allows the launcher to mount on one of the columns of the column wheel 74. When he actuates the STOP function, the spring of the launcher 71 allows the launcher 7 to fall in the space between two columns of the column wheel 74 and at the same time to give a speed whip 72 which accelerates the hub or the balance.

Advantageously, the blade 73 comprises a hook 730 which is intended to cooperate with the column wheel 74. In a variant, the blade and the hook constitute a single piece which is quite difficult to machine but which allows a reduction in the number of parts. In another variant the hook 730 is a separate part of the blade 73 and connected to it for example through a screw, which allows a better ease of machining.

The figure 7 illustrates a three-dimensional view of the regulating member according to the invention, the spring 1, the anchor 6 and the anchor wheel 8. The racket 9 cooperates with the screw 90 of fine adjustment of the length of the spring 1, with a tuning fork 10 as well as with a bridge 12 which is connected to the plate of the movement through the screw 14.

The regulating member of the invention is also distinguished from the regulating members of the prior art by the noise produced, which is different from the noise of the watch; because of the high oscillation frequencies, the usual ticking is replaced by a high-frequency hum, with a main harmonic at 500 Hz and secondary harmonics at multiples of 500 Hz. This very characteristic and very noticeable buzz allows the user to detect by ear that the chronograph is running, and thus avoid an unwanted discharge of the chronograph cylinder if the chronograph is started inadvertently or if one forgets to stop it. The distinct and characteristic sound of the organ The chronograph regulator is therefore used as a signal indicating that the chronograph works. The watch case may advantageously comprise elements, for example vents or a resonance cage, in order to amplify this useful noise.

Reference numbers used in the figures

1

hairspring

10

Tuning fork

12

Bridge

14

Fixing screw from deck to deck

2

Axis of the spiral

3

Hub

30

Obviously in the hub

4

Tray

40

Plateau dowel

42

Large plateau

43

Small tray

430

Notch of the small plateau

45

gun

5

Ferrule

50

Notch of the ferrule

6

Anchor

60

Horn of entry

61

sting

62

1 ^st anchor arm

63

^2nd arm of the anchor

64

Holes crossing through the anchor

65

Horn output

7

Launcher

71

Launcher spring

72

Whip

73

Blade

730

Hook of the blade

74

Column wheel

75

Pushbutton

8

Anchor wheel

9

Racket

90

Fine adjustment screw of the spiral length

Claims (22)

1. Regulating organ for mechanical watch movement, comprising:

   an axis (2);

   a hairspring (1) mounted on said axis (2), and arranged to oscillate about an equilibrium position;

   wherein said hairspring (1) is arranged to oscillate around said equilibrium position at a frequency of 50 Hz or more;
   characterized in that
   said axis (2) is massive, thereby determining most of the moment of inertia of the regulating member.
2. The regulating organ of claim 1, comprising only parts mounted on said axis (2) whose moment of inertia is less than 10 times the moment of inertia of the axis.
3. The regulating organ of claim 1, comprising a plate (4) mounted on said axis (2), and a plate pin (40) mounted on said plate (4).
4. The regulating organ according to claim 3, said axis (2) being made of metal and said plate (4) being made of silicon or ceramic.
5. The regulating organ according to one of claims 2 to 4, said parts having a hub (3) mounted on said axis (2) and intended to collaborate with a launcher (7) to accelerate or decelerate said regulator organ.
6. The regulator organ according to claim 5, said hub (3) consisting of a disk mounted on said axis (2).
7. The regulating organ according to one of claims 5 or 6, said hub (3) being provided with several blind openings (30) in a plane perpendicular to said axis (2), in order to reduce moment of inertia of said hub (3) and/or blind or through openings in other direction.
8. The regulator organ according to one of claims 5 to 7, said hub (3) being made of a material having a density lower than that of said axis (2).
9. The regulator organ according to one of claims 5 to 8, the diameter of said hub (3) being between 1.5 and 10 times the maximum diameter of the axis (2).
10. The regulating organ according to one of claims 2 to 9, said parts comprising a pin plate (4) mounted on said axis (2).
11. The regulating organ according to claim 10, the diameter of said hub (3) being less than twice the diameter of said plate (4).
12. The regulating organ according to claim 11, the diameter of said hub (3) being equal to that of the plate (4).
13. The regulating organ according to one of claims 6 to 12, said hub (3) and said plate (4) being integrated in a single element carrying said plate pin (40).
14. The regulator organ according to one of claims 10 to 13, said hub (3) and/or said plate (4) and/or said element being made of titanium and/or aluminum and/or an alloy containing at least one of these materials.
15. The regulating organ according to one of claims 1 to 14, further comprising a collet (5) for mounting said hairspring (1) on said axis (2).
16. The regulating organ according to claim 15, said collet (5) being constituted by a ring mounted on said axis (2) and having a notch (50) for fixing the inner end of said spiral (1).
17. The regulator organ according to one of claims 15 or 16, said collet (5) being constituted by a ring mounted on said axis (2) and whose section is non-circular in order to reduce the moment of inertia of said collet (5).
18. The regulating organ according to claim 17, the diameter of said hub (3) being between 1 and 3 times the maximum diameter of said collet (5).
19. The regulator organ according to one of claims 1 to 18, said spiral (1) having three winds or less.
20. The regulator organ according to one of claims 1 to 19, said spiral (1) being devoid of terminal curve.
21. The regulator organ according to one of claims 1 to 20, said spiral being arranged to oscillate at a frequency of 500 Hz or more.
22. Mechanical chronograph comprising a first regulating organ according to one of claims 1 to 21 for measuring durations, and a second regulating organ oscillating more slowly for displaying the current time.

Images