EP4160323A1 - Mechanical timepiece regulator comprising a self-starting semi-free escapement with low angle of lift - Google Patents

Abstract

The present invention relates to a mechanical watch regulator (1) comprising an escapement (10) cooperating with an oscillator provided with an inertial element (21) oscillating in an oscillation plane thanks to a return element (22). The escapement comprises a pin (130) rigidly linked to the inertial element (21), an anchor (12) comprising a fork (122) cooperating with the pin (130), and two pallets (121, 127) cooperating with teeth (112) of an escape wheel (11). The regulator is configured such that, during a first frictional rest phase occurring before a release phase, and during a second frictional rest phase occurring after an impulse phase, the pin (130) is in contact with the fork (122) so as to push it, and a tooth (112) of the escape wheel (11) is in frictional contact with one of the pallets (121, 127).

Description

Technical area

The present invention relates to the field of watchmaking, more specifically, the present invention relates to a mechanical watch regulator comprising an escapement and an oscillator.

State of the art

A clock regulator mechanism typically includes an escapement as illustrated in figure 1 . Such an escapement 10 typically comprises an escape wheel 11 provided with teeth 112 configured to cooperate with pallets 121 of an anchor 12. The anchor 12 comprises a fork 122 cooperating with a pin 130 of a plate 131. The plate 131 is rigidly linked to an oscillator (or regulator member) not shown. The purpose of the escapement is to maintain and count the oscillations of the oscillator. A mechanical oscillator comprises an inertial element, a guide and an elastic return element. For example, the mechanical oscillator can comprise a hairspring balance in which the balance wheel constitutes the inertial element, the guide corresponds to the balance shaft and to the stones of the plate and bridge, and the hairspring constitutes the elastic return element.

There figure 2a shows a diagram showing different oscillation angles of the balance wheel of a spiral balance oscillator, cooperating with an escapement as described above. The balance wheel, having an amplitude Ao of the order of 300°, can be characterized by a portion of free oscillation Θ _LI and a portion of oscillation corresponding to the angle of lift Θ _LE , of the order of 50°, where the release of the escape wheel and the impulse from the escapement to the inertial element occur. The amplitude Ao is the maximum angular position, with respect to the line of centers, that takes the inertial element during an oscillation (or alternation). The line of centers θ ₀ is defined as the angular position of the inertial element at equilibrium without the escapement (when the elastic return element is completely relaxed).

A horological oscillator on flexible guidance, or with a flexible pivot, is an oscillator whose inertial element (which may include a balance wheel) is guided in rotation by an arrangement of elastic parts and not by a physical axis of rotation rotating in conventional bearings (eg: ruby bearing), as in the case of a balance spring. In addition to its function of guiding in rotation, the flexible pivot exerts an elastic return torque on the balance like the hairspring of a hairspring balance oscillator. There figure 2b shows a diagram plotting different oscillation angles of an oscillator on flexible guidance (for example, such as that shown in figure 19 ) cooperating with an escapement as described above. In this configuration, the inertial element, having an amplitude Ao typically comprised between 10° and 50°, is characterized by a portion of free oscillation Θ _LI typically of the order of 10° to 20°, and by an angle of lifting Θ _LE , of the order of 6° maximum. Compared to an oscillator of the spiral balance type, an oscillator on flexible guidance is distinguished by greater rigidity of the elastic return element and by lower amplitudes of oscillations Ao.

The lift half-angle Θ _LE /2 of an oscillator corresponds to the angle between the line of the centers of the inertial element θ ₀ and its angular position at the end of the pulse θ _IM . Thus, minimizing the lift angle Θ _LE amounts to bringing the end-of-pulse angular position θ _IM closer to the line of centers θ ₀ and therefore to reducing the elastic restoring torque of the oscillator at the end of the pulse, this which facilitates self-starting.

In the case of a traditional Swiss lever escapement 10 cooperating with an oscillator on a flexible guide, it is not possible to resize the fork to make the latter compatible with a lift angle Θ _LE on the balance wheel of 6° or less. Indeed, in this case, the Games and safeties between the fork and the chainring peg would be impracticable in practice. Furthermore, due to the higher rigidity of the elastic return element of an oscillator on flexible guide compared to a spiral balance, it is then difficult to ensure the self-starting of an oscillator on flexible guide. .

Self-starting is the property of an escapement that starts only thanks to the torque supplied by the escape wheel following winding of the barrel in its working area. Self-starting guarantees start-up of the oscillator without outside help during the barrel winding phase, for example after the watch has been stored for a long time. Self-starting is an advantageous property of any wristwatch escapement because it is regularly subject to shocks, which causes the balance wheel to brake against its shock absorbers. This braking can lead to momentary stops of the balance. If the escapement is not self-starting, the balance wheel will remain blocked until the intervention of the user or a watchmaker. Thus an escapement which is not self-starting poses reliability problems in the context of the wristwatch.

A system is self-starting when the torque at the escape wheel is sufficient to, among other things, complete the pulse phase. The elastic return torque of the oscillator (this elastic return torque is directly proportional to the stiffness of the return spring and to the end-of-pulse angular position θ _FI ) is then counterbalanced by the torque at the escape wheel . Increasing the torque at the escape wheel to ensure the self-starting of an oscillator on flexible guidance amounts to increasing its energy consumption, which is not a satisfactory solution given that the energy available in a watch bracelet is limited.

The document CH715589A1 describes a rubbing rest escapement which is adapted to an oscillator on a flexible guide. The advantage of a rubbing rest escapement is that it can be sized to be compatible with a lift angle Θ _LE on the balance arm of less than 6°, which is advantageous for self-starting. The disadvantage is that the balance wheel is linked to the lever (elastically in this specific case) which implies a permanent rotation of the lever during the oscillation of the balance wheel and therefore a permanent rubbing contact between the escape wheel and the 'anchor. The loss of energy resulting from this rubbing contact is substantial, which de facto limits the operating amplitudes of the oscillator to low values, of the order of 6 to 8°. In contrast, the Swiss lever escapement is a free escapement because it only comes into contact with the oscillator during the lift angle to perform the release and impulse phases.

An example of free exhaust which has been adapted for an oscillator on flexible guidance is presented in the document CH714361 . This document describes a regulator with a resonator with a flexible pivot fitted with a free lever escapement with an enlarged fork compared to that of a conventional Swiss lever. The escapement is particularly suitable for the flexible pivot presented in the document EP3035126 and goes hand in hand with the resonator mechanism on flexible guide disclosed in the document EP3545365 . This latter document describes a free anchor escapement with a lift angle Θ _LE of 10°, with inertial elements with specific properties. This escapement has a traditional kinematics with a free oscillation phase, then a release followed by an impulse phase. Due to its excessively large lift angle (10°), the escapement in question cannot be both self-starting and have a torque at the escape wheel that is small enough to have reasonable energy consumption.

Brief summary of the invention

The present invention relates to a watchmaking mechanical regulator comprising an escapement cooperating with a watchmaking mechanical oscillator provided with an inertial element oscillating in an oscillation plane thanks to an elastic return element. The exhaust comprises a pin rigidly linked to the inertial element, an anchor and an escape wheel. The anchor comprises a fork configured to cooperate with the peg, an input pallet and an output pallet, each of the pallets being configured to cooperate with the teeth of the escape wheel. The escapement is configured so that, during a release phase, the peg pushes the fork in order to release the escape wheel from one of the pallets and, during an impulse phase, the fork pushes the peg in order to transmitting to the inertial element the torque of the escape wheel which is in contact with one of the pallets. The regulator is configured so that the release phase is preceded by a first frictional rest phase, itself preceded by a first free oscillation phase, and the pulse phase is followed by a second frictional rest phase. , itself followed by a second phase of free oscillation. During each of the free oscillation phases, the inertial element oscillates freely without contact between the pin and the fork; and during the first and second frictional rest phase, the pin is in contact with the fork so as to push it, a tooth of the escape wheel being in frictional contact with one of the pallets.

The escapement is at rest rubbing during a given portion of oscillation, but is free outside this portion of oscillation. The oscillation portions in frictional rest make it possible to guarantee the self-starting of the oscillator because, thanks to them, it is possible to build a fork-peg mechanism with a very low angle of lift as well as reasonable games and safeties. . For example, the lift angle can be at least twice as small as what is attainable with the escapements proposed in the state of the art, ie typically between 2° and 6°. The escapement thus makes it possible to recover the self-starting property of the oscillator, even in the case where the operating amplitude of the oscillator is low and its rigidity high.

The regulator according to the invention also allows a portion of oscillation of the inertial element to be largely free and there is therefore no frictional contact between the escape wheel and the lever during a large part of the oscillation of the inertial element. This makes it possible to minimize the energy loss of the regulator and therefore to obtain a higher amplitude of the inertial element. This makes it possible to guarantee the isochronism of a flexible-guided oscillator (for most flexible-guided oscillators and escapements, isochronism faults are generally critical below 10° of amplitude) and makes the element inertial less disturbed by shocks against stops.

The regulator described here can be applied to any type of escapement whose wheel and lever form a double impulse escapement. For example, the principle can easily be applied in the case of a free lever escapement. The regulator proposed here greatly simplifies the design of the oscillator compared to the solution proposed in the document CH714361 . For example, given the low amplitudes characterizing oscillators on flexible guides, the anchor of the present invention does not need a dart to cooperate with such an oscillator. The anchor and the wheel can therefore be parts produced on one level.

The regulator described here is simple in its implementation and makes it possible to ensure low energy consumption and the self-starting of an oscillator on flexible guidance.

Brief description of figures

• la figure 1 illustre un régulateur classique d'horlogerie;
• les figures 2a et 2b montrent l'amplitude d'oscillation et l'angle de levée pour un oscillateur de type balancier spiral (figure 2a) et pour un oscillateur sur guidage flexible (figure 2b) ;
• la figure 3 montre un régulateur dont l'échappement comprend une cheville, une fourchette et une roue d'échappement, selon un mode de réalisation;
• les figures 4a-4c montrent un détail de la palette d'entrée (figure 4a), de la palette de sortie (figure 4b) de la fourchette et d'une dent de la roue d'échappement (figure 4c);
• Les figures 5a et 5b montrent un diagramme reportant différents angles d'oscillation d'un élément inertiel d'un oscillateur sur guidage flexible coopérant avec l'échappement 10, lorsque l'oscillateur oscille dans le sens anti-horaire (figure 5a) et horaire (figures 5b);
• la figure 6 montre l'échappement au début d'une première phase de repos frottant lorsque l'oscillateur oscille dans le sens anti-horaire;
• la figure 7 montre l'échappement au début d'une phase de dégagement;
• la figure 8 montre l'échappement pendant un premier rattrapage de jeu de fourchette;
• la figure 9 montre l'échappement au début d'une phase d'impulsion;
• la figure 10 montre l'échappement pendant la phase d'impulsion;
• la figure 11 montre l'échappement au début d'une première chute de la roue d'échappement;
• la figure 12 montre l'échappement au début d'une seconde phase de repos frottant après un deuxième rattrapage de jeu de fourchette;
• la figure 13 montre l'échappement à la fin d'une seconde phase de repos frottant;
• la figure 14 montre l'échappement pendant une phase d'oscillation libre;
• la figure 15 montre l'échappement pendant la première phase de repos frottant, lorsque l'oscillateur oscille dans le sens horaire;
• les figures 16a-16f montrent des phases de l'échappement aux faibles amplitudes de l'oscillateur;
• Les figures 17a-17b illustrent l'ébat et la pénétration (figure 17a) de la cheville dans la fourchette dans une position de début d'impulsion et l'ébat de dégagement (figure 17b) de la cheville dans la fourchette dans une position de fin de second repos frottant;
• les figures 18a-18b montrent des phases de l'échappement pour des amplitudes d'oscillation au-delà du demi-angle de repos frottant;
• les figures 19a-19f illustrent différentes positions de la fourchette et d'une dent par rapport aux palettes, pour des amplitudes d'oscillation de l'élément inertiel au-delà du demi-angle de repos frottant;
• la figure 20 montre l'échappement coopérant avec oscillateur sur guidage flexible, selon un premier exemple; et
• la figure 21 montre un détail de l'échappement de la figure 20.

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

• there figure 1 illustrates a classic clock regulator;
• THE figures 2a and 2b show the oscillation amplitude and lift angle for a spiral balance type oscillator ( figure 2a ) and for an oscillator on a flexible guide ( figure 2b );
• there picture 3 shows a regulator whose escapement comprises a pin, a fork and an escape wheel, according to one embodiment;
• THE Figures 4a-4c show a detail of the input palette ( figure 4a ), the output palette ( figure 4b ) of the fork and one tooth of the escape wheel ( figure 4c );
• THE figures 5a and 5b show a diagram reporting different angles of oscillation of an inertial element of an oscillator on flexible guide cooperating with the escapement 10, when the oscillator oscillates in the anti-clockwise direction ( figure 5a ) and schedule ( figure 5b );
• there figure 6 shows the escapement at the start of a first rubbing rest phase as the oscillator swings counter-clockwise;
• there figure 7 shows the escapement at the start of a release phase;
• there figure 8 shows the escapement during a first fork play recovery;
• there figure 9 shows the escapement at the start of a pulse phase;
• there figure 10 shows the escapement during the pulse phase;
• there figure 11 shows the escapement at the start of a first fall of the escape wheel;
• there figure 12 shows the escapement at the start of a second resting phase rubbing after a second fork play recovery;
• there figure 13 shows the escapement at the end of a second phase of rubbing rest;
• there figure 14 shows the escapement during a phase of free oscillation;
• there figure 15 shows the escapement during the first phase of rubbing rest, when the oscillator oscillates clockwise;
• THE Figures 16a-16f show phases of the escapement at low oscillator amplitudes;
• THE figures 17a-17b illustrate frolic and penetration ( Figure 17a ) of the ankle in the fork in a start-of-impulse position and the release frenzy ( figure 17b ) of the ankle in the fork in a position at the end of the second rubbing rest ;
• THE figures 18a-18b show phases of the escapement for oscillation amplitudes beyond the frictional half-angle of repose;
• THE figures 19a-19f illustrate different positions of the fork and of a tooth with respect to the pallets, for oscillation amplitudes of the inertial element beyond the half-angle of friction rest;
• there figure 20 shows the escapement cooperating with an oscillator on a flexible guide, according to a first example; And
• there figure 21 shows a detail of the exhaust of the figure 20 .

Example(s) of embodiment of the invention

There picture 3 shows a regulator 1 comprising an exhaust 10, according to one embodiment. The escapement 10 comprises an escapement wheel 11 provided with teeth 112 configured to cooperate with an entry pallet 121 and an exit pallet 127 of an anchor 12. The anchor 12, pivotally mounted on an axis, comprises a fork 122 cooperating with an impulse cam 130 (here a pin) of a plate 131. The escapement 10 cooperates with an oscillator (not shown) comprising an inertial element 21 (for example a pendulum or other) capable of oscillating around of an oscillator axis 23 thanks to an elastic return element. The plate 131 is intended to cooperate with the oscillator. For example, the plate 131 can be arranged concentric with the oscillator so as to pivot with an inertial element, as in a conventional clockwork regulator mechanism.

There figure 4a shows a detail of the input palette 121, the figure 4b shows a detail of the output pallet 127 and the figure 4c shows a detail of a tooth 112 comprising a tooth nose 112a and a tooth heel 112b. Each of the input pallet 121 and the output pallet 127 is provided with a pallet rubbing rest plane P _RF , a pallet release plane P _DE , and a pallet impulse plane P _IM . Here, the pallet release plane P _DE corresponds to a rest plane, that is to say, the plane on which a tooth 112 of the escape wheel presses at the time of its release.

In the example of Figures 4a-4b , the P _IM vane impulse plane has three sections with variable curvature, continuous and tangent. However, the vane impulse plane P _IM can also be formed from a single or multiple curved or planar sections. The vane rubbing rest plane P _RF and the vane clearance plane P _DE are also shown as two continuous sections of different curvatures but these two planes could also be realized as a single flat surface. Preferably, the pallet rubbing rest plane P _RF is pull-type and the pallet release plane P _DE may or may not be pull-type. The draw means that these two pallet planes can be oriented so that the force exerted by the tooth nose 112a of the tooth 112 against one of these pallet planes generates a torque at the anchor 12 causing the rotation of the latter against one of its stops 125a, 125b. Pulling makes it possible to ensure that the anchor stops in a well-determined position, defined by its stops 125, during the free oscillation of the inertial element 21. During the first phase of free oscillation there is no There is no contact between peg 130 and fork 122. Contact between peg 130 and fork 122 occurs during the first phase of rubbing rest.

The pallets 121, 127 of the anchor 12 of the escapement 10 therefore comprise an additional resting plane, the pallet rubbing resting plane P _RF , configured to block the escapement wheel 11 during the rubbing rests of the escapement .

THE figures 5a and 5b show a diagram reporting different angles of oscillation of an inertial element of an oscillator on flexible guide cooperating with the escapement 10, when the oscillator oscillates counterclockwise ( figure 5a ) and schedule ( figure 5b ). The exhaust 10 has two different operating regimes. On start-up, the escapement 10 functions as an escapement at rest rubbing, that is to say that the amplitude of oscillation of the inertial element is greater than the half-angle of lift Θ _LE /2 and less than half -friction angle of repose Θ _RF /2. The angle of lift Θ _LE corresponds to the portion of oscillation of the inertial element from the start angular position of release θ _DE to the end angular position of the pulse θ _IM . The angle of frictional rest Θ _RF corresponds to the portion of oscillation from the angular position of the inertial element from the start of the first frictional rest _θRF1 to the end angular position of the second frictional rest _θRF2 .

At greater amplitude of oscillation of the inertial element, greater than the half-angle of rest rubbing at Θ _RF /2, the oscillator also has a portion of free oscillation (angle of free oscillation Θ _LI ).

THE figures 6 to 15 show the escapement 10 during the different phases of its operation. The diagram of the figure 5 is also reproduced: the angle of oscillator 2 corresponding to the phase illustrated is indicated there by an arrow. It should be noted that a drop (or fork clearance compensation) occurs as a transition between two escapement operating phases and is not considered as an escapement phase. Note that, to facilitate the analysis and understanding of an escapement, it is customary to make the approximation that the inertial element does not pivot during a fall. The fall is added in the construction of the escapement in order to avoid the blocking of the mechanism which would be caused by a double contact between two escapement parts (safeties of the escapement). The chute is dimensioned according to the assembly and manufacturing tolerances of the system. It must be minimized because it causes a loss of energy that does not contribute to the accuracy of the system's time base.

Normal operation (at large amplitude)

There figure 6 shows the escapement 10 at the start of a first phase of rubbing rest, when the oscillator oscillates in the anti-clockwise direction. The first phase of frictional rest occurs following a first phase of free oscillation during which the inertial element 21 oscillates freely without contact between the pin 130 and the fork 122 . The first phase of rubbing rest occurs before a release phase of the escapement 10. In the first phase of rubbing rest, which does not exist in a conventional lever escapement, the escapement wheel 11 is blocked by the anchor 12 and cannot move forward. The pin 130 (for example arranged coaxial with an axis of the inertial element) rotates counter-clockwise and meets a fork first plane 122a of the fork 122. The anchor 12 then pivots clockwise (around its pivot axis 126). Under the action of pin 130 on fork 122, pallet 121 will cause escape wheel 11 to move back slightly. A tooth 112 of the escape wheel is in frictional contact on the frictional rest plane of the pallet P _RF of the input palette 121.

During the first entry rubbing rest phase, lever 12 rotates while escape wheel 11 is almost stationary. There is therefore a frictional contact between a tooth 112 and the input pallet 121 (on the pallet frictional rest plane P _RF ) of the anchor 12. During the first phase of frictional rest, the inertial element oscillates from the angular position of the start of the first rubbing rest θ _RF1 to the angular position of the start of disengagement θ _DE .

There figure 7 shows the escapement 10 at the start of a release phase, corresponding to the end of the first rubbing rest. During the release phase, the balance pin 130 continues to rotate counter-clockwise and to push on the first fork plane 122a of the fork 122. The escapement wheel 11 is stationary, or recoils slightly, and the anchor 12 continues to turn clockwise. A tooth 112 of the escape wheel 11 leaves the pallet rubbing rest plane P _RF to join the pallet release plane P _DE of the input pallet 121. At the start of the release phase, the angular position of the inertial element is that of start of release θ _DE .

There figure 8 shows the escapement 10 at the start of the backlash adjustment of the fork 122 occurring at the end of the release phase. The beginning of the backlash of the fork 122 is identical to that of a classic lever escapement. Pin 130 continues to rotate counter-clockwise. A tooth 112 of the escape wheel 11 leaves the pallet clearance plane P _DE to join the pallet impulse plane P _IM of the entry pallet 121. The escape wheel 11 will then actuate the anchor 12 which will allow the second plane of the fork 122b to catch up with the pin 130 and strike it at the end of the backlash of the fork 122. The elastic return torque of the oscillator must at least be sized to be able to bring back, without momentum, the escapement 10 in the position of the figure 8 . Otherwise the escapement 10 is not self-starting.

There figure 9 shows the escapement 10 at the start of a pulse phase occurring at the end of the first fork drop and corresponds to the start of the input pallet pulse 121. This first pulse phase is identical to that of a classic lever escapement. Pin 130 continues to rotate counter-clockwise. The second fork plane 122b of fork 122 has joined pin 130 and is beginning to push pin 130 counterclockwise. The escapement wheel 11 continues to rotate clockwise and actuates the pin 130 via the lever 12. The tooth nose 112a of the tooth 112 of the escapement wheel 11 pushes on the plane of pallet pulse P _IM from the input pallet 121.

There figure 10 shows the escapement 10 during the pulse phase, at the transition between the pulse of the tooth nose 112a on the pallet plane and the tooth plane pulse on the pallet nose. There Pin 130 continues to rotate counterclockwise and second fork plane 122b continues to push pin 130 counterclockwise. The escape wheel 11 also continues to rotate clockwise and actuates the peg 130 through the anchor 12. The second part of the impulse phase, and with it the first impulse, ends when the beak pallet 128 joins the heel of the tooth 112b of the escapement wheel 11 (see also the figure 4a ).

There figure 11 shows escapement 10 during a first drop of escape wheel 11 and a second drop of fork 122 occurring at the end of the impulse phase. This transition is identical to that of a conventional lever escapement for the drop of the escapement wheel 11. However, in a conventional escapement, there is no second drop of fork 122 because the peg 130 leaves the fork 122 at the end of the pulse without joining the first fork plane 122a. In the present transition pin 130 continues to rotate counterclockwise. The peg 130 leaves the second fork plane 122b because the lever 12 is no longer actuated by the escapement wheel 11. A tooth 112 of the escapement wheel 11 separates from the end of the impulse plane of pallet P _IM of the input pallet 121. The escapement wheel 11 drops, that is to say rotates in a vacuum, and will join the rubbing rest plane of the pallet P _RF of the output pallet 127.

During this transition corresponding to the drop of the escape wheel and the second drop of the fork, the angular position of the inertial element corresponds approximately to the end of pulse angular position θ _IM with respect to the reference position of the line of centers θ ₀ (this corresponds to the half-angle of lift Θ _LE /2). Unlike a conventional exhaust, the exhaust 10 is characterized by a lift angle Θ _LE typically of at most 6°.

There figure 12 shows the escapement 10 at the start of a second rubbing rest phase occurring after the impulse phase, at the end of the fall of the escape wheel 11 and of the second fall of the fork 122. This second phase of rubbing rest does not exist in a conventional lever escapement. Pin 130 continues to rotate counter-clockwise, joins first fork plane 122a and pushes fork 122 out. The escape wheel 11 is blocked by the anchor 12 but pivots very slightly clockwise due to the pull. The anchor 12 still pivots clockwise under the action of the pin 130. The tooth beak 112a of the tooth 112 of the escapement wheel 11 will therefore rub against the rubbing rest plane of the pallet P _RF of the exit pallet 127. There is therefore a frictional contact between the escapement wheel 11 and the pallet 12 and between the pallet 12 and the peg 130.

Here, the expression "frictional contact" means that at the point of contact between the tooth 112 and the frictional resting plane of the paddle P _RF and between the pin 130 and the first fork plane 122a, there is a regular relative displacement between these exhaust parts during the first and the second rubbing rest phase.

During the second phase of frictional rest, the angular position of the inertial element goes from the angular position of the end of the pulse θ _IM to the angular position of the end of the second frictional rest θ _RF2 .

There figure 13 shows the escapement 10 at the end of the second rubbing rest phase. The peg 130 has finished pushing the first fork plane 122a and is freed from it. The anchor 12 has not yet joined the exit stop 125b, the draw is therefore not finished. A tooth 112 of the escapement wheel 11 rests on the rubbing resting plane of the pallet P _RF of the output pallet 127. The escapement wheel 11 transmits a torque to the anchor 12 which allows it to always pivot clockwise to reach the exit stop 125b and its rest position.

During the pull, the angular position of the inertial element is slightly greater than the angular position at the end of the second rubbing rest θ _RF2 . Similar to falls, we do not consider, in this document, the draw as a phase of the escapement strictly speaking.

There figure 14 shows the escapement 10 during a second phase of free oscillation occurring after the second phase of rubbing rest. The ankle 130 is free and will remain so until the next rubbing rest phase. Fork 122 of anchor 12 has joined exit stop 125b. The escape wheel 11 is blocked by the anchor 12 and both are stationary. During the second phase of free oscillation there is no contact between pin 130 and fork 122. Contact between pin 130 and fork 122 occurs during the second phase of frictional rest.

During the second phase of free oscillation, the angular position of the inertial element is greater than the angular position at the end of the second frictional rest θ _RF2 .

There figure 15 shows the escapement 10 at the start of the first rubbing rest phase, when the oscillator oscillates clockwise. This phase does not exist in a classic lever escapement. Pin 130, which rotates clockwise, meets second fork plane 122b of anchor 12, which is about to rotate counter-clockwise. In this position, if the system were stopped, it is the elastic torque of the oscillator which would cause the escapement 10 to rotate. The escapement wheel 11 is blocked by the lever 12 and cannot move forward. When the lever 12 rotates, under the action of the pin 130 on the second fork plane 122b of the fork 122, the escapement wheel 11 will move back slightly, pushed back by the rubbing rest plane of the pallet P _RF of the output pallet 127.

During the first phase of frictional rest, the inertial element pivots from the angular position of the start of the first frictional rest θ _RF1 to the angular position of the start of disengagement θ _DE .

Pin 130 is therefore configured to push fork 122 during the first frictional rest phase and the second frictional rest phase. During these phases, a tooth 112 of the escapement wheel 11 is in frictional contact against the frictional rest plane of the pallet P _RF of the input pallet 121 or of the output pallet 127. The pin 130 is not in contact with the fork 122 on the free oscillation portions of the inertial element, preceding the first frictional rest phase and following the second frictional rest phase.

It should be noted that the self-starting of the escapement 10 does not depend on the angle of rest rubbing Θ _RF but only on the angle of lift Θ _LE . Thus, as the addition of these rubbing rest phases makes it possible to reduce the lift angle Θ _LE , the proposed escapement considerably facilitates the self-starting of the oscillator. The presence of the first phase of rubbing rest and of the first phase of free oscillation makes it possible to characterize the escapement 10 as a semi-free escapement. The escapement 10 is also self-starting.

The escapement 10 can be configured so that the frictional rest angle Θ _RF , corresponding to the portion of oscillation from the angular position of the inertial element from the start of the first frictional rest θ _RF1 to the end angular position of the second rubbing rest θ _RF2 , ie at most 12°.

The same phases as described above recur when the oscillator swings clockwise.

It will be noted that for the first and the second frictional rest phase to be able to occur, the escapement must be configured so that the pin 130 is in contact with the fork 122 so as to push it when the angular position of the inertial element with respect to the line of centers θ ₀ is smaller than the half-angle of rest rubbing Θ _RF /2 and greater than the half-angle of lift Θ _LE /2. More particularly, the first fork plane 122a and the second fork plane 122b must be dimensioned so that they can be engaged with the pin 130 in this angular range.

Starting and low amplitudes

When oscillator 2 starts up or in operation at amplitudes less than or equal to the half-angle of friction rest Θ _RF /2, the escapement 10 functions as a friction rest escapement. In this mode, the anti-rollover devices are useless since the pin does not leave the fork. If the escapement 10 can push the inertial element 21 to the limit of the half-angle of lift Θ _LE /2 (corresponding to the angular position of end of pulse θ _IM ), then the system is self-starting. The kinematics of the escapement 10 at the start of the oscillator or in operation at amplitudes less than or equal to a half-angle of rest rubbing at Θ _RF /2 is illustrated in figures 16a-16c when the oscillator swings clockwise and at figures 16d to 16f when the oscillator swings counterclockwise.

To the Figure 16a , a tooth 112 bears against the anchor output rest plane 127a of the output pallet 127. The second fork plane 122b of the fork 122 is in contact with the pin 130 and follows the inertial element 21 in its swing. If the oscillation is large enough, then the escapement wheel 11 outlines a slight movement due to the pulling of the anchor exit rest plane 127a.

To the figure 16b , the inertial element 21 has entered the lift angle Θ _LE and has completed the disengagement. The fork has caught up and is pushing peg 130 with the fork foreground. Tooth 112 provides its impulse to output pallet 127, via anchor output impulse plane 127b.

To the figure 16c , the inertial element 21 reaches the limit of the lift angle Θ _LE . At the end of the impulse on the anchor output impulse plane 127b of the output paddle 127, another tooth 112' drops onto the anchor entry rest 121a of the entry pallet 121. The pin 130, still engaged in the fork 122, carrying the latter with it.

THE figures 16d-16f illustrate the same phases as the figures 16a-16c , respectively. A tooth 112 comes into contact with the anchor entry rest plane 121a of the entry pallet 121 ( figures 16a and 16b ). The inertial element 21 and the anchor 12 rotate in the opposite direction to the direction illustrated in figures 16a-16c . When the balance 21 reaches the limit of the angle of lift Θ _LE ( figure 16f ), another tooth 112' falls on the anchor exit rest plane 127a of the exit pallet 127.

Safety and securities

The fork-pin mechanism of the escapement 10 must be equipped with sufficient securities and safeties to prevent the escapement from being brought into a blocking position. Concretely, the securities and sureties in question are distances between the pin 130 and the fork 122 in particular positions of the exhaust 10 and must be dimensioned according to the inaccuracies of manufacture and assembly of the exhaust parts. There Figure 17a illustrates the play E and the penetration P of the peg 130 into the fork 122 in a position of start of impulse (corresponds to the position of the escapement at the figure 9 ). The play E serves to prevent the ankle from getting stuck in the fork and the penetration P to ensure that the second plane of the fork 122b pushes the ankle during the impulse. There figure 17b illustrates the free movement D of the ankle 130 in the fork 122 in a position at the end of the second rubbing rest (corresponds to the position of the figure 13 , to the nearest draw). The release action D serves to guarantee that the peg 130 can come out of the fork 122. It is these three distances (E, P and D) which become too small when constructing a traditional free lever escapement (without rest rubbing) for lift angles less than approximately 10°.

As shown at figures 18a and 18b , for amplitudes of oscillation of the inertial element 21 beyond the half-angle of rest rubbing Θ _RF /2, the pin 130 comes out of the fork 122. The anchor 12 is then at rest, resting against the entry stop 125a ( picture 18a ) or the exit stop 125b ( figure 18b ), and escape wheel 11 remains stationary. The escapement 10 must then include a device preventing overturning, that is to say preventing the rocking of the lever 12 which would cause the plate pin 130 to meet the lug 123. A device preventing the overturning may comprise a stinger 124 and/or a pair of horns 123. In the case of an oscillator 2 intended for the escapement 1 described here, its oscillations have typically low amplitudes: The stinger 124 can then turn out to be useless and the pair of horns 123, or any equivalent system, may suffice. If the fork (or peg) is wide enough there is also no need for a stinger.

THE figures 19a-19f illustrate different positions of the fork 122 and of a tooth 112 with respect to the pallets 121, 127, for amplitudes of oscillation of the inertial element 21 beyond the half-angle of rest rubbing Θ _RF /2. By referring to figures 19a and 19d , the inertial element 21 freely traverses its additional arc. Thanks to the pulling of the tooth 112 on the pallet rubbing rest plane P _RF of the output pallet 127, the fork 122 is wedged against the output stop 125b or against any other limiting device. The rest position is such that on the return of the inertial element 21, the pin 130 enters freely into the fork 122.

By referring to figures 19b and 19e , following a shock, the fork 122 leaves its rest position. The pin 124 and the small plate 132 fulfill their role as anti-rollover devices. The point of the dart 124 comes into contact with the small plate 132, preventing the anchor 12 from passing on the wrong side. The tooth beak 112a is still in engagement with the rubbing rest plane of the pallet P _RF of the output pallet 127. Once the shock has passed, the anchor 12 is returned to the rest position thanks to the pull. Pin 130 passes freely in front of horn 123.

By referring to figures 19c and 19f , the dart 124 has entered the notch 132a of the small plate 132. In this configuration, the dart 124 is inactive and unable to retain the anchor 12. It is then the horn 123, blocked by the pin 130, which prevents overturning in the event of an impact. The tooth beak 112a of the tooth 112 is still engaged on the rubbing rest plane of the pallet P _RF of the output pallet 127. Once the shock has passed, the anchor 12 returns to its equilibrium position thanks to the pull.

Other aspects

The escapement 10 according to the invention, that is to say the lever 12, the peg 130, and/or the escapement wheel 11, can be made of silicon using the usual etching techniques. This material has many advantages: it does not undergo fatigue failure, is non-magnetic and has no plastic domain. In addition, silicon makes it possible to manufacture parts in series with high machining precision, while offering great design freedom. Alternatively, the exhaust 10 can be made of a material selected from the group of materials comprising a ceramic, a glass, an alloy or a metallic glass. For example, the material selected may include silicon nitride, silicon carbide, steel, gold or one of its alloys, nickel, nickel-phosphorus, brass, steel, an amorphous alloy , a copper alloy, copper-beryllium, or nickel silver.

As the escapement 10 can be configured so that the angle of rest rubbing Θ _RF is at most 12°, and the lugs 123 can prevent any overturning of the anchor up to an amplitude of 36°, thus the anchor 12 may not include dart 124. It is then possible to manufacture anchor 12 on a single level, that is to say that anchor 12 may be included in a single plane, without dart 124 fixed at a level above (or below) the level of the anchor 12 and the fork 122.

Implementation Examples

The regulator 1 described here is particularly suitable for an oscillator 2 on flexible guidance. An example of integration of the escapement 10 with a CR3 type oscillator as described in the patent EP3299905B1 by the present applicant is illustrated in figure 20 . There figure 21 shows a detail of the escapement 10.

In this example, the pin 130 which interacts with the anchor 12, as well as the stops 125a, 125b, are directly integrated into the inertial element 21 of the oscillator 2. In addition to the pin 130 interacting with the anchor 12, the oscillator 2 comprises an elastic return element comprising a flexible pivot comprising flexible blades 22. The flexible pivot 22 performs both the role of elastic return and of guiding in rotation of the inertial element 21. The flexible pivot 22 is of one side fixed to a plate (not shown) and the other linked to the inertial element 21.

Oscillator 2 typically has 20° amplitude. The horns 123 can prevent any overturning of the anchor 12 up to an amplitude of 36°, so a dart is unnecessary in this example. The frictional angle of repose Θ _RF is about 10° and the lift angle Θ _LE is about 5°.

It is possible to substitute the CR3 type oscillator by a Wittrick type oscillator as described in the patent EP3299905B1 by the present plaintiff.

Of course, these two examples are not limiting and, by its design, the present escapement is not limited to a specific family of oscillators on flexible guides.

Reference numbers used in the figures

1

mechanical watch regulator

10

exhaust

11

escape wheel

112, 112'

tooth

112a

tooth beak

112b

tooth stub

12

anchor

121

input pallet

122

fork

122a

fork foreground

122b

second fork plane

123

horn

124

stinger

125

stopper

125a

entry stop

125b

exit stop

126

anchor pivot axis

127

output pallet

128

paddle impulse spout

130

pulse cam, peg

131

plateau

132

small tray

132a

small tray notch

2

oscillator

21

inertial element, pendulum

22

elastic return element, flexible blade

23

oscillator axis

θDE

start of release angular position

θIM

pulse end angular position

θRF1

angular position of the start of the first frictional rest

θRF2

angular position at the end of the second rubbing rest

ISLAND

lift angle

ΘLI

free swing angle

ΘRF

rubbing angle of repose

ao

amplitude of oscillation

M

couple

PDE

pallet clearance plan

IMP

pallet impulse plane

FRP

pallet rubbing resting surface

E

frolic between fork and ankle

P

fork ankle penetration

D

ankle release romp

Claims (10)

Mechanical watch regulator (1) comprising an escapement (10) cooperating with an oscillator provided with an inertial element (21) oscillating in an oscillation plane thanks to an elastic return element (22); the escapement (10) comprising a peg (130) rigidly connected to the inertial element (21), an anchor (12) and an escape wheel (11); the anchor (12) comprising a fork (122) configured to cooperate with the peg (130), an input paddle (121) and an output paddle (127), each of the paddles (121, 127) being configured to cooperating with teeth (112) of the escape wheel (11); the escapement being configured so that, during a release phase, the pin (130) pushes the fork (122) in order to release the escapement wheel (11) from one of the pallets (121, 127) and, during an impulse phase, the fork (122) pushes the pin (130) in order to transmit to the inertial element (21) the torque of the escape wheel (11) which is in contact with one of the pallets (121, 127);
characterized in that the regulator is configured so that the release phase is preceded by a first frictional rest phase, itself preceded by a first free oscillation phase, and the pulse phase is followed by a second frictional rest phase , itself followed by a second phase of free oscillation; during each of the free oscillation phases, the inertial element (21) oscillates freely without contact between the pin (130) and the fork (122); and during the first and second frictional rest phase, the pin (130) is in contact with the fork (122) so as to push it, a tooth (112) of the escape wheel (11) being in frictional contact with one of the paddles (121, 127). The regulator (1) according to claim 1,
wherein the fork (122) has a fork plane (122a, 122b) that is sized to be engaged with the peg (130) during the first and second rubbing rest phases. The regulator (1) according to claim 1 or 2,
configured in such a way that the peg is not in contact with the fork during the free swing phases. The regulator (1) according to one of claims 1 to 3, wherein each pallet (121, 127) is provided with a clearance plane (P _DE ) coming into contact with a tooth (112) during the clearance phase, and an impulse plane (P _IM ) coming into contact with a tooth (112) during the impulse phase; And wherein each of the paddles (121, 127) is further provided with a friction rest plane (P _RF ) configured to come into friction contact with a tooth (112) during the first and second friction rest phase. The regulator (1) according to claim 4,
wherein the pallet rubbing rest plane (P _RF ) is configured to block the escape wheel (11) when the pin (130) is in contact with the fork (122). The regulator (1) according to claim 4 or 5,
in which the pallet rubbing rest plane (P _RF ) is drawn. The regulator (1) according to one of claims 1 to 6,
in which a lift angle (Θ _LE ), corresponding to the portion of oscillation of the inertial element (21) where the release of the escape wheel and the impulse from the escapement to the inertial element occur , is at most 6°. The regulator (1) according to one of claims 1 to 7,
wherein an angle of frictional rest (Θ _RF ) corresponding to the portion of oscillation of the inertial element (21) from the beginning of the first frictional rest until the end of the second frictional rest, is at most 12°. The regulator (1) according to one of claims 1 to 8,
wherein at least one of the pallet (12), peg (130), and escape wheel (11) is made of silicon. The regulator according to one of claims 1 to 9,
wherein the oscillator (2) comprises an oscillator on flexible guidance.

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