CH711571A2 - Oscillator with revolving trigger. - Google Patents

Abstract

The invention relates to an oscillator (1), of the swirl type, comprising a pivoting shaft (3) connected to a source (2) of mechanical energy, a monobloc resonator (7) of the inertia-elasticity type which is mounted on The pivoting shaft (3), a detent escapement (15) comprising a one-piece detent (17) integral with the pivot shaft (3) which comprises at least one flexible blade (16) Arranged to elastically lock the pivot shaft (3) relative to a concentric exhaust teeth (19), a release element being arranged to resiliently release the stop lift (18) by the movement of the resonator (7) ) With respect to the concentric exhaust teeth (19) so that the pivot shaft (3) counts each oscillation of the resonator (7) while transmitting the energy capable of maintaining it.The invention relates to the field of horology.

Description

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The invention relates to an oscillator of the tourbillon type comprising a resonator of the inertia-elasticity type cooperating with a rotary-expansion escapement.

Arrière-plan de l’invention [0002] Les systèmes d’échappement à détente sont connus pour avoir apporté une grande précision aux chronomètres de marine au 18e siècle en offrant une impulsion directe et une faible sensibilité aux frottements. Toutefois, ils se sont révélés particulièrement difficiles à régler et sensibles aux chocs. Certains chronomètres de marine ont ainsi été montés sous vide, dans du sable ou encore sur des suspensions à cardan pour éviter toute transmission de chocs induisant du galop, c’est-à-dire le passage accidentel de deux dents de la roue d’échappement au lieu d’une, propre à dérégler la marche de la pièce d’horlogerie. Ainsi, entre la sensibilité aux chocs et l’encombrement de tels montages, il est actuellement inenvisageable de mettre en oeuvre un système fiable d’échappement à détente dans une montre-bracelet. Résumé de l’invention [0003] Le but de la présente invention est de pallier tout ou partie les inconvénients cités précédemment en proposant un oscillateur comportant un résonateur du type inertie - élasticité coopérant avec un échappement à détente d’un nouveau type qui soit exempt de galop et dont le fonctionnement induit des avantages appartenant habituellement aux oscillateurs du type tourbillon beaucoup plus complexe.

To this end, the invention relates to an oscillator comprising a pivoting shaft connected to a source of mechanical energy, a monoblock resonator of the inertia-elasticity type comprising a member forming said inertia provided with a disengagement element and A flexible guide forming said elasticity which is mounted between the pivoting shaft and the member forming said inertia, a detent escapement comprising a one-piece trigger integral with the pivoting shaft which comprises at least one flexible blade and a stop lift arranged For elastically locking the pivot shaft relative to a concentric exhaust teeth, the disengagement element being arranged to resiliently release, by the movement of the member forming said inertia,The stop lift with respect to the concentric exhaust teeth so that the pivoting shaft counts each oscillation of the resonator while transmitting to it the energy capable of maintaining it.

Advantageously according to the invention, it will thus be understood that the oscillator has very few parts to be mounted since they are, for the most part, monoblocs, which allows the parts to be more easily referenced with respect to one another. Moreover, thanks to the use of flexible guides, the resonator has a very low thickness and intrinsically induces the elimination of the gallop. Moreover, the oscillator according to the invention advantageously allows the resonator to have a pulse by a direct torque rather than a contact force as with a conventional expansion exhaust. Finally, the pivoting shaft cancels out by turning the oscillator offsets in the vertical positions.

According to other advantageous variants of the invention: the flexible guide comprises at least one anchoring means integral with the pivoting shaft and flexible means arranged to form a virtual pivoting axis of the resonator merged with the Center of rotation of the pivoting shaft; The flexible means comprise at least one base connecting, by at least one flexible blade, respectively the member forming said inertia and said at least one anchoring means; The member forming said inertia is formed by two sectors, the internal surface of one of the sectors comprising the disengagement element; The disengagement element comprises a flexible body, the free end of which is provided with a release lift, the movement of which, controlled by the member forming said inertia, Is arranged to contact the one-piece trigger at each alternation of the resonator; The release element further comprises a release stop arranged to force the flexible body to displace the one-piece trigger in only one direction of oscillations of the resonator; In a first variant, the single-piece trigger comprises a single flexible blade, an expansion stop being integral with said single flexible blade and being arranged to come into contact with the disengagement element at each half-wave of the resonator; In a second variant, the one-piece detent comprises two parallel crosspieces, a first cross-member being connected at one end to the pivot shaft and at a second end perpendicular to a first flexible strip, At a first end, At the stop lift and at a second end perpendicular to a second flexible blade, the first and second flexible blades being parallel and respectively connected to the second and first cross bars; In a third variant, the one-piece detent comprises two parallel crosspieces, a first cross-member being connected at one end to the pivoting shaft and perpendicularly to a first flexible strip, a second cross-member being connected at a first end , At the stop lift and at a second end perpendicular to a second flexible blade, the first and second flexible blades being parallel and respectively connected to the second and first cross bars; - according to the second and third variants, The one-piece detent comprises an expansion stop integral with the second cross-member which is arranged to come into contact with the disengagement element at each alternation of the resonator; According to a fourth variant, the single-piece trigger comprises first and second non-parallel flexible blades each connecting the pivoting shaft to a fastener, the fastener being furthermore connected to a third flexible blade whose free end comprises the lifting of a non- And a fourth flexible blade including a detent stop which is arranged to contact the disengaging element at each alternation of the resonator; The pivoting shaft comprises a pinion arranged to mesh with a finishing train to be connected to the mechanical energy source and to display the time; The pinion is mounted idly on the pivoting shaft via an elastic energy accumulator in order to provide sufficient energy for the maintenance of the resonator during the pulse time; The one-piece resonator and the single-piece trigger are formed in two integral single plates forming two functional levels of the pivoting axis.

BRIEF DESCRIPTION OF THE DRAWINGS Other features and advantages will become clear from the following description thereof, by way of non-limiting indication, with reference to the accompanying drawings, in which: FIG. 1 is a diagrammatic sectional representation of an oscillator according to the invention; FIG. 2 is a perspective view of a first embodiment of an oscillator according to the invention; FIG. 3 is an inverted representation of FIG. 1; FIG. 4 is an enlarged representation of FIG. 3; FIG. 5 is a perspective view of a second embodiment of an oscillator according to the invention; FIG. 6 is an enlarged representation of FIG. 5; FIG. 7 is a perspective view of a third embodiment of an oscillator according to the invention; FIG. 8 is an enlarged representation of FIG. 7; FIG. 9 is a perspective view of a fourth embodiment of an oscillator according to the invention; FIG. 10 is an enlarged representation of FIG. 9; FIG. 11 is a perspective view of a fifth embodiment of an oscillator according to the invention; FIG. 12 is a first enlarged representation of FIG. 11; FIG. 13 is a second enlarged representation of FIG. 11. 12 is a first enlarged representation of FIG. 11; FIG. 13 is a second enlarged representation of FIG. 11. 12 is a first enlarged representation of FIG. 11; FIG. 13 is a second enlarged representation of FIG. 11.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The invention relates to an oscillator for a timepiece, that is to say a resonator coupled with a distribution and maintenance system such as, for example, a Exhaust system.

[0009] As illustrated schematically in FIG. 1, the oscillator 1 according to the invention comprises a pivoting shaft 3 connected to a source of mechanical energy 2, for example, by means of a finishing train 5. Such an energy source 2 may Comprise means for accumulating energy by elastic deformation and / or by pneumatic storage. By way of example, the accumulation means may take the form of a metal blade mounted in a pivoting drum to form a barrel. However, other types of mechanical energy source may be considered.

The oscillator 1 according to the invention comprises a single-piece resonator 7 of the inertia-elasticity type. This resonator 7 preferably comprises a member 9 forming said inertia and a flexible guide 11 forming said elasticity. As illustrated schematically in FIG. 1, the flexible guide 11 is preferably one-piece with the member 9 and is mounted between the pivoting shaft 3 and the member 9. Finally, the member 9 forming the inertia is also provided with a disengagement element 13.

[0011] The amplitude of the resonator 7 is limited to the maximum deflections of the flexible guide 11 as will be better explained in the embodiments below. This limitation of the travels nevertheless renders the gallop of the resonator 7 inherently impossible, which solves, by construction, the main problem which usually penalizes the expansion-exhaust systems.

[0012] As illustrated schematically in FIG. 1, the oscillator 1 also comprises a detent escapement 15 comprising a one-piece trigger 17 also integral with the pivoting shaft 3. The trigger 17 comprises at least one flexible blade 16 and a stop lever 18 arranged to resiliently lock the pivoting shaft 3 relative to an exhaust spur 19 concentric to the pivoting shaft 3.

[0013] As will be better explained in the embodiments below, the release element 13 is arranged to resiliently release, by the movement of the inertia member 9, the stop lift 18 with respect to the toothing 19 so that the pivoting shaft 3 counts each oscillation of the resonator 7 while transmitting to it the energy capable of maintaining it.

Advantageously according to the invention, it will therefore be understood that oscillator 1 has very few parts to be mounted since they are, for the most part, monoblocs, which allows the parts to be more easily referenced with respect to one another . Moreover, thanks to the use of the flexible guide, the resonator 7 has a very small thickness and intrinsically induces the elimination of the gallop. In addition, the oscillator 1 according to the invention advantageously allows the resonator 7 to have a pulse by a direct torque rather than a contact force as with a conventional expansion exhaust. Finally, the pivoting shaft 3 cancels out by turning the oscillator 1 in the vertical positions.

All these advantages will be better understood in the light of a first embodiment of an oscillator 101 according to the invention in relation to FIGS. 2 to 4. Thus, the oscillator 101 comprises a pivoting shaft 103 connected to a source of mechanical energy (not shown) and an integral resonator 107 of the inertia-elasticity type.

[0016] This resonator 107 comprises a member 109 forming said inertia and a flexible guide 111 forming said elasticity. The flexible guide 111 is integral with the member 109 and is mounted between the pivoting shaft 103 and the member 109. As illustrated in FIG. 3, the flexible guide 111 comprises at least one anchoring means 121 integral with the pivoting shaft 103 and flexible means 123 arranged to form a virtual pivotal axis of the resonator 107 coinciding with the center of rotation of the pivoting shaft 103 .

More precisely, the flexible means 123 comprise at least one base 120 connecting the inertia member 109 and the at least one anchoring means 121 via at least one flexible blade 122, 124. As illustrated in FIG. 3, the inertia member 109 is preferably formed by two sectors 125 connected to each other by a ring 127 in order to obtain a monobloc inertia member 109.

[0018] Moreover, as can be seen in FIG. 3, each of the sectors 125 is integral with flexible means 123. More precisely, each sector 125 forming said inertia is connected by two flexible blades 122 to the partially annular base 120, which is integral with two other flexible blades 124 with two anchoring means 121 using respectively a beam 126 In the form of a T. It will be noted that each beam 126 is thus integral with an anchoring means 121 and with the two sectors 125 forming said inertia.

It will be understood that the amplitude of the resonator 107 is therefore limited to the maximum deflections of the flexible guide 111 and in particular to the geometry of the beams 126, the bases 120 and the blades 122, 124. This limitation of the travels nevertheless makes the Galop of the resonator 107, which solves, by construction, the main problem which usually penalizes the triggered exhaust systems.

[0020] As can be seen in FIGS. 3 and 4, the inertia member 109 is also provided with a release member 113. More precisely, the internal surface of one of the sectors 125 comprises the disengagement element 113. In the first embodiment, the disengagement element 113 comprises a flexible body 131 whose free end is provided with a release lift 132 whose displacement, controlled by the inertia member 109, is arranged to enter In contact with the trigger 117 one-piece at each alternation of the resonator 107.

More precisely, in the manner of a conventional expansion exhaust, the first embodiment comprises a disengagement element 113 allowing, in one direction of the oscillation, a dumb alternation, that is to say That the release member 113 comes into contact with the trigger 117 but does not displace the trigger 117. Thus, preferably in the first embodiment, the release member 113 further includes a release abutment 133 arranged to force the release member Body 131 flexible to move the single-piece trigger 117 in a single direction of the oscillations of the resonator 107.

[0022] As best illustrated in FIG. 4, the oscillator 101 further comprises a detent escapement 115 comprising a one-piece trigger 117 integral with the pivoting shaft 103. The trigger 117 comprises at least one flexible blade 116, 116 'and a stop lever 118 arranged to elastically lock the pivoting shaft 103 relative to an exhaust teeth 119 concentric with the pivoting shaft 103.

It will therefore be understood that the toothing 119 is fixed with respect to the pivoting shaft 103. In fact, the shaft 103 pivoting, under the constraint of the mechanical energy source, will rotate at each oscillation of the resonator 107, which will correspond to the angle between two teeth of the exhaust teeth 119, c That is to say each time the stop 118 of the trigger 117 permits its movement from one tooth to the other.

[0024] In the first embodiment illustrated in FIGS. 2 to 4, the one-piece trigger 117 comprises two parallel crossmembers 135, 136 and two parallel blades 116, 116 '. As best seen in FIG. 4, a first crossbar 135 is connected at one end to the pivoting shaft 103 and at a second end perpendicularly to a first flexible blade 116. In addition, the second cross-member 136 is connected at one end to the stop 118 and at a second end perpendicularly to a second flexible blade 116 '. Finally, the first 116 and second 116 'flexible blades are respectively connected to the second 136 and first 135 crosspieces.

[0025] It will therefore be understood that the crosspieces 135, 136, visible in the rest position in FIGS. 3 and 4 are able to move relative to one another by means of the resilient deflection of the flexible blades 116, 116 '. More specifically, the release member 113 is arranged to cause the flexible blades 116, 116 'to bend to resiliently release, by movement of the inertia member 109, The concentric escapement 119 so that the pivoting shaft 103 counts each oscillation of the resonator 107 while transmitting to it the energy capable of maintaining it.

This is made possible because the one-piece trigger 117 comprises a detent stop 137 integral with the second cross-member 136 which is arranged to come into contact with the disengagement element 113 at each half-wave of the resonator 107. As can be seen in FIG. . 4, the detent stop 137 forms a cam which, when engaged with the release lift 132, causes the cross member 136 to move away from the toothing 119 d by the action of the release abutment 133 To release the pivoting shaft 103. The shaft 103 pivots, under the constraint of the mechanical energy source, to perform a rotation which corresponds to the angle between two teeth of the exhaust teeth 119 and, at the same time, restarts the resonator 107 by the Transmission of its movement directly by the beams 126 via the anchoring means 121.

On the other hand, in the inverse alternation of the resonator 107, it can be seen that the detent stop 137 forms a cam which, when it comes into contact with the release lift 132, obliges, by the absence of The release latch 132 in the reverse direction, the release latch 132 elastically move away and then, once the release stub 137 has escaped, to return elastically along the release abutment 133.

Advantageously according to the first embodiment of the invention, it will therefore be understood that the oscillator 101 has very few parts to be mounted since they are, for the most part, monoblocs, which enables the parts to be more easily referenced In relation to each other. Indeed, by way of example, the one-piece resonator 107 and the one-piece trigger 117 could be formed in two integral single plates forming at least two functional levels of the pivoting pin 103. This could, for example, be obtained by solidarized and then etched silicon plates or by the electroforming of a metallic component at several levels.

Moreover, by using the flexible guide 111, the resonator 107 has a very low thickness and intrinsically induces the elimination of the gallop. Furthermore, the oscillator 101 according to the invention advantageously allows the resonator 107 to have a pulse by a direct torque rather than a contact force as with a usual expansion exhaust.

[0030] Additionally, the operation induces advantages usually belonging to the much more complex vortex type oscillators. Indeed, the tourbillon is a device designed by Mr. A.-L. Breguet in the early 19th century to cancel walking distances in vertical positions. It comprises a movable cage which carries all the components of the exhaust and, at its center, the regulating member. The exhaust sprocket rotates about the seconds wheel which is fixed. The cage which makes 1 revolution per minute cancels by turning the gaps in the vertical positions.

Consequently, in the manner of a vortex but without its complexity of focusing, the pivoting shaft 103 of the first embodiment cancels out the deviations of the oscillator 101 in the vertical positions by rotating the resonator 107 at the same time as the detente 117.

Finally, as illustrated in FIG. 2, the pivoting shaft 103 further comprises a pinion 141 arranged to mesh with a finishing train to be connected to the mechanical energy source and to display the time. Preferably, according to the first embodiment, the pinion 141 is mounted loosely on the pivoting shaft 103 via an accumulator 143 of elastic energy in order to provide sufficient energy for the maintenance of the resonator 107 for the duration Of the clearance. In the example of FIG. 2, it can be seen that the elastic energy accumulator 143 is a spiral spring. However, the accumulator 143 of elastic energy can not be limited to a spring in the form of a spiral. Thus, by way of non-limiting example, the pivoting shaft assembly 103,

On reading the first embodiment, it can thus be understood that the pivoting shaft assembly 103, the elastic energy accumulator 143 and the pinion 141 is not essential and could also be replaced by a pivoting shaft 103, A peripheral toothing meshed with the finishing train. Whatever the energy transmission choice, it is immediate that the force of the finishing train and, if necessary, that of the accumulator 143 of elastic energy, must be dimensioned so as not to cause the actuation of the trigger 117 Other than by the release member 113.

[0034] A second embodiment of an oscillator 201 according to the invention is shown in FIGS. 5 and 6. Thus, the oscillator 201 comprises a pivoting shaft 203 and an integral resonator 207 of the inertial-elasticity type similar to those 103, 107 of the first embodiment. This resonator 207 therefore comprises a member 209 forming said inertia and a flexible guide 211 forming said elasticity with the same advantages as those 109 and 111 of the first embodiment.

It will be understood that the amplitude of the resonator 207 is therefore limited to the maximum deflections of the flexible guide 211 and in particular to the geometry of the beams 226, the bases 220 and the blades 222, 224. This limitation of the travels nevertheless makes the intrinsic Gallop of the resonator 207, which solves, by construction, the main problem that usually penalizes the expansion exhaust systems.

As can be seen in FIGS. 5 and 6, the inertia member 209 is also provided with a release member 213 similar to that 113 of the first embodiment. More precisely, in the manner of a conventional expansion exhaust, the second embodiment comprises a disengagement element 213 allowing, in one direction of the oscillation, a dumb alternation, that is to say, The release member 213 comes into contact with the trigger 217 but does not displace the trigger 217. Thus, preferably in the second embodiment, the release member 213 includes a flexible body 231 and a release abutment 233 arranged to force Move the single-ended trigger 217 in only one direction of the oscillations of the resonator 207.

[0037] As best illustrated in FIG. 6, the oscillator 201 also comprises a detent escapement 215 comprising a one-piece detent 217 integral with the pivoting shaft 203. The trigger 217 includes a single flexible blade 216 and a stop lift 218 arranged to resiliently lock the pivot shaft 203 relative to a concentric exhaust teeth 219 relative to the pivot shaft 203.

As in the first embodiment, the disengagement element 213 of the second embodiment is arranged to cause the flexible leaf 216 to flex so as to elastically release, by the movement of the inertia member 209, The stop lift 218 with respect to the concentric exhaust teeth 219 so that the pivoting shaft 203 counts each oscillation of the resonator 207 while transmitting the energy capable of maintaining it.

This is made possible because the one-piece detent 217 comprises an expansion stop 237 integral with the flexible blade 216 which is arranged to come into contact with the release element 213 at each half-wave of the resonator 207. As can be seen in FIG. . 6, the detent stop 237 forms a cam which, when engaged with the release lift 232, causes the flexible blade 216 to move away from the toothing 219 by the action of the abutment 233 To release the pivot shaft 203. The shaft 203 pivoting, under the constraint of the mechanical energy source, will rotate which corresponds to the angle between two teeth of the exhaust teeth 219 and, at the same time, restarts the resonator 207 by the Transmission of its movement directly by the beams 226 via the anchoring means 221.

On the other hand, in the inverse rotation of the resonator 207, it can be seen that the detent stop 237 forms a cam which, when it comes into contact with the release lift 232, obliges, by the absence of The release latch 233 in the reverse direction, the release latch 232 to elastically move apart and then, once the release stub 237 has escaped, to return elastically along the release abutment 233.

Advantageously according to the second embodiment of the invention, it will therefore be understood that the oscillator 201 has very few parts to be mounted since they are, for the most part, monoblocs, which allows the parts to be more easily referenced In relation to each other. Indeed, by way of example, the single-piece resonator 207 and the one-piece expansion device 217 could be formed in two integral single plates forming at least two functional levels of the pivoting pin 203. This could, for example, be obtained by solidarized and then etched silicon plates or by the electroforming of a metallic component at several levels.

In addition, by using the flexible guide 211, the resonator 207 has a very low thickness and intrinsically induces the elimination of the gallop. Furthermore, the oscillator 201 according to the invention advantageously allows the resonator 207 to have a pulse by a direct torque rather than a force by contact as with a usual expansion exhaust.

[0043] Additionally, the operation induces advantages usually belonging to the much more complex vortex type oscillators as already explained in the first embodiment. Consequently, in the manner of a vortex but without its complexity of focusing, the pivoting shaft 203 of the second embodiment cancels out the deviations of the oscillator 201 in the vertical positions by turning the resonator 207 at the same time 217.

Finally, as for the first embodiment, the pivoting shaft 203 may comprise, directly or via an elastic energy accumulator, a pinion arranged to mesh with a finishing train in order to d Be connected to the mechanical power source and display the time. Thus, regardless of the choice of transmission of the energy chosen in the second embodiment, it is immediate that the force of the finishing train and possibly that of the elastic energy accumulator must be dimensioned so as not to Causing the trigger 217 to act otherwise than by the release member 213.

A third embodiment of an oscillator 301 according to the invention is shown in FIGS. 7 and 8. Thus, the oscillator 301 comprises a pivoting shaft 303 and an integral resonator 307 of the inertia-elasticity type similar to those 103, 203, 107, 207 of the first and second embodiments. This resonator 307 thus comprises a member 309 forming said inertia and a flexible guide 311 forming said elasticity with the same advantages as those 109, 209 and 111, 211 of the first and second embodiments.

It will be understood that the amplitude of the resonator 307 is therefore limited to the maximum deflections of the flexible guide 311 and in particular to the geometry of the beams 326, the bases 320 and the blades 322, 324. This limitation of the travels nevertheless intrinsically makes it impossible to Gallop of the resonator 307, which solves, by construction, the main problem which usually penalizes the expansion exhaust systems.

As can be seen in FIGS. 7 and 8, the inertia member 309 is also provided with a release member 313 similar to that 113, 213 of the first and second embodiments. More precisely, in the manner of a conventional expansion exhaust, the third embodiment comprises a disengagement element 313 allowing, in one direction of the oscillation, a dumb alternation, that is to say, The release member 313 comes into contact with the trigger 317 but does not displace the trigger 317. Thus, preferably in accordance with the third embodiment, the release member 313 includes a flexible body 331 and a release abutment 333 arranged to force Move the single-piece trigger 317 in only one direction of the oscillations of the resonator 307.

As best illustrated in FIG. 8, the oscillator 301 also comprises a detent escapement 315 comprising a one-piece trigger 317 integral with the pivoting shaft 303. The detent 317 comprises at least one flexible blade 316, 316 'and a stop lift 318 arranged to elastically lock the pivot shaft 303 relative to an exhaust teeth 319 concentric with respect to the pivoting shaft 303.

As for the first and second embodiments, the release element 313 of the third embodiment is arranged to cause said at least one blade 316, 316 'to bend in order to elastically unblock by the movement of The inertia member 309, the stop lift 318 with respect to the concentric exhaust teeth 319 so that the pivoting shaft 303 counts each oscillation of the resonator 307 while transmitting the energy capable of maintaining it.

[0050] In the third embodiment illustrated in FIGS. 7 and 8, the one-piece trigger 317 comprises two parallel cross-members 335, 336 and two parallel blades 316, 316 '. As best seen in FIG. 8, a first cross-member 335 is connected at a first end to the pivot shaft 303 and at the same end perpendicularly to a first flexible blade 316. In addition, the second cross-member 336 is connected at one end to the stop lift 318 (better visible in FIG. 7) and at a second end perpendicularly to a second flexible blade 316 '. Finally, the first 316 and second 316 'flexible blades are respectively connected to the second 336 and first 335 cross members.

[0051] As can be seen in FIGS. 7 and 8, the second cross-member 336 preferably comprises three straight sections. The first section 336a connects the two flexible blades 316, 316 'and is attached, substantially perpendicularly in the trigonometric direction, to the second section 336b which runs along the first flexible strip 316 which is itself attached substantially perpendicularly in the retrograde direction to the second section 336a. Third section 336c which carries the stop lift 318. It will thus be understood that the sections 336a and 336c are substantially parallel.

Thus, the crosspieces 335, 336, visible in the rest position in FIGS. 7 and 8 are capable of moving relative to one another by means of the resilient deflection of the flexible blades 316, 316 '.

More precisely, the release element 313 is arranged to cause the flexible blades 316, 316 'to bend in order to elastically unlock, by the movement of the inertia member 309, the stop lift 318 by Relative to the concentric exhaust teeth 319 so that the pivoting shaft 303 counts each oscillation of the resonator 307 while transmitting to it the energy capable of maintaining it.

This is made possible because the one-piece trigger 317 comprises a detent stop 337 integral with the second cross-member 336, at the level of the first section 336a, which is arranged to come into contact with the release element 313 at each half-wave of the Resonator 307. As can be seen in FIG. 8, the detent stop 337 forms a cam which, when it comes into contact with the release lift 332, causes the cross-member 336, and in particular its third section 336c, to be engaged by the action of the stop 333. To move away from the exhaust teeth 319 to release the pivoting shaft 303. The shaft 303 pivoting under the constraint of the mechanical energy source will rotate which corresponds to the angle between two teeth of the exhaust teeth 319 and, at the same time,

On the other hand, in the inverse rotation of the resonator 307, it can be seen that the detent stop 337 forms a cam which, when it comes into contact with the release lift 332, obliges, by the absence of The action of the release stop 333 in the reverse direction, the release lift 332 to elastically move apart and then, once the expansion stop 337 has escaped, to return elastically along the release stop 333.

Advantageously according to the third embodiment of the invention, it will therefore be understood that the oscillator 301 has very few parts to be mounted since they are for the most part monoblocks, which allows the parts to be more easily referenced In relation to each other. Indeed, by way of example, the one-piece resonator 307 and the one-piece trigger 317 could be formed in two integral single plates forming at least two functional levels of the pivoting pin 303. This could, for example, be obtained by solidarized and then etched silicon plates or by the electroforming of a metallic component at several levels.

Moreover, by using the flexible guide 311, the resonator 307 has a very low thickness and intrinsically induces the elimination of the gallop. Furthermore, the oscillator 301 according to the invention advantageously allows the resonator 307 to have a pulse by a direct torque rather than a contact force as with a usual expansion exhaust.

In addition, the operation induces advantages usually belonging to the much more complex vortex type oscillators as already explained in the first embodiment. Consequently, in the manner of a vortex but without its complexity of focusing, the pivoting shaft 303 of the third embodiment cancels out the oscillator 301 in the vertical positions by turning the resonator 307 at the same time 317.

[0059] Enfin, comme pour les premier et deuxième modes de réalisation, l’arbre 303 pivotant peut comporter, directement ou par l’intermédiaire d’un accumulateur d’énergie élastique, un pignon agencé pour s’engrener avec un rouage de finissage afin d’être relié à la source d’énergie mécanique et d’afficher l’heure. Ainsi, quel que soit le choix de transmission de l’énergie choisi dans le troisième mode de réalisation, il est immédiat que la force du rouage de finissage et, éventuellement celle de l’accumulateur d’énergie élastique, doivent être dimensionnées pour ne pas entraîner l’actionnement de la détente 317 autrement que par l’élément 313 de dégagement.

[0060] Un quatrième mode de réalisation d’un oscillateur 401 selon l’invention est présenté aux fig. 9 et 10. Ainsi, l’oscillateur 401 comporte un arbre 403 pivotant et un résonateur 407 monobloc du type inertie -élasticité semblables à ceux 103, 203, 303, 107, 207, 307 des trois premiers modes de réalisation. Ce résonateur 407 comprend donc un organe 409 formant ladite inertie et un guidage 411 flexible formant ladite élasticité avec les mêmes avantages que ceux 109, 209, 309 et 111,211,311 des trois premiers modes de réalisation.

It will be understood that the amplitude of the resonator 407 is therefore limited to the maximum deflections of the flexible guide 411 and in particular to the geometry of the beams 426, the bases 420 and the blades 422, 424. This limitation of the displacements nevertheless makes the intrinsic Gallop of the resonator 407, which solves, by construction, the main problem that usually penalizes the expansion exhaust systems.

[0062] As can be seen in FIGS. 9 and 10, the inertia member 409 is also provided with a release member 413 similar to that 113, 213, 313 of the first three embodiments. More precisely, in the manner of a conventional expansion exhaust, the fourth embodiment comprises a disengagement element 413 enabling, in one direction of the oscillation, a dumb alternation, that is to say, Element 413 comes into contact with the trigger 417 but does not displace the trigger 417. Thus, preferably in the fourth embodiment, the release member 413 comprises a flexible body 431 and a release abutment 433 arranged to force Move the single-ended trigger 417 in only one direction of the oscillations of the resonator 407.

As best illustrated in FIG. 10, the oscillator 401 also comprises a detent escapement 415 comprising a one-piece trigger 417 integral with the pivoting shaft 403. The trigger 417 comprises at least one flexible blade 416a, 416b, 416c, 146d and a stop lift 418 arranged to elastically lock the pivoting shaft 403 relative to a concentric exhaust teeth 419 with respect to the pivoting shaft 403 .

As for the first three embodiments, the disengagement element 413 of the fourth embodiment is arranged to cause said at least one blade 416a, 416b, 416c, 146d to bend in order to elastically unblock by the The inertia member 409, the stopping lift 418 relative to the concentric exhaust teeth 419 so that the pivoting shaft 403 counts each oscillation of the resonator 407 while transmitting the energy capable of maintaining it.

[0065] In the fourth embodiment illustrated in FIGS. 9 and 10, the single-piece trigger 417 comprises first and second non-parallel flexible blades 416a, 416b each connecting the pivoting shaft 403 to a substantially cylindrical fastener 435. The fastener 435 is further connected to a third flexible blade 416d whose free end comprises the stop lift 418. Finally, the fastener 435 also comprises a fourth flexible blade 416c comprising an expansion abutment 437 which is arranged to come into contact with the disengagement element 413 at each half-wave of the resonator 407. As can be seen in FIG. 10, preferably the third and fourth blades 416d, 416c are substantially perpendicular.

Thus, the flexible blades 416a, 416b, 416c, 146d which are visible in the rest position in FIGS. 9 and 10 are capable, by means of their elastic bending, of moving relative to each other. More specifically, the disengagement element 413 is arranged to cause the flexible blades 416a, 416b, 416c, 146d to flex so as to resiliently unblock the inertia member 409 from the stop 418a To the concentric escapement 419 so that the pivoting shaft 403 counts each oscillation of the resonator 407 while transmitting to it the energy capable of maintaining it. Preferably according to the invention,

This is made possible because the one-piece trigger 417 comprises an expansion stop 437 integral with the fourth flexible blade 416c which is arranged to come into contact with the disengagement element 413 at each half-wave of the resonator 407. As can be seen in FIG. fig. 10, the detent stop 437 forms a cam which, when engaged with the release lift 432, causes the third flexible blade 436d to move away from the toothing by the action of the release abutment 433 419 for releasing the pivoting shaft 403. The shaft 403 pivoting under the constraint of the mechanical energy source will perform a rotation which corresponds to the angle between two teeth of the exhaust teeth 419 and, at the same time,

On the other hand, in the inverse rotation of the resonator 407, it can be seen that the expansion stop 437 forms a cam which, when it comes into contact with the release lever 432, obliges, by the absence of The action of the release abutment 433 in the reverse direction, the release lift 432 to elastically move apart and then, once the expansion stop 437 has escaped, to return elastically along the release abutment 433.

Advantageously according to the fourth embodiment of the invention, it will therefore be understood that the oscillator 401 comprises very few parts to be mounted since they are for the most part monoblocks, which allows the parts to be more easily referenced In relation to each other. Indeed, by way of example, the single-piece resonator 407 and the single-piece trigger 417 could be formed in two integral single plates forming at least two functional levels of the pivoting pin 403. This could, for example, be obtained by solidarized and then etched silicon plates or by the electroforming of a metallic component at several levels.

Moreover, thanks to the use of the flexible guide 411, the resonator 407 has a very low thickness and intrinsically induces the elimination of the gallop. Furthermore, the oscillator 401 according to the invention advantageously allows the resonator 407 to have a pulse by a direct torque rather than a contact force as with a usual expansion exhaust.

[0071] Additionally, the operation induces advantages usually belonging to the much more complex vortex type oscillators as already explained in the first embodiment. Consequently, in the manner of a tourbillon but without its complexity of focusing, the pivoting shaft 403 of the fourth embodiment cancels out the oscillator 401 in the vertical positions by turning the resonator 407 at the same time 417.

Finally, as for the first three embodiments, the pivoting shaft 403 can comprise, directly or via an elastic energy accumulator, a pinion arranged to mesh with a finishing train in order to To be connected to the mechanical power source and to display the time. Thus, regardless of the choice of transmission of the energy chosen in the fourth embodiment, it is immediate that the force of the finishing train and, possibly that of the elastic energy accumulator, must be dimensioned so as not to Cause actuating the trigger 417 other than by the release member 413.

A fifth embodiment of an oscillator 501 according to the invention is shown in FIGS. 11-13. Thus, oscillator 501 includes a pivoting shaft 503 and an integral resonator 507 of the inertia-elasticity type similar to those 103, 203, 303, 403, 107, 207, 307, 407 of the first four embodiments. This resonator 507 thus comprises a member 509 forming said inertia and a flexible guide 511 forming said elasticity with the same advantages as those 109, 209, 309, 409 and 111, 211, 311, 401 of the first four embodiments.

It is understood that the amplitude of the resonator 507 is therefore limited to the maximum deflections of the flexible guide 511 and in particular to the geometry of the beams 526, the bases 520 and the blades 522, 524. This limitation of the travels nevertheless makes the intrinsic Gallop of the resonator 507 which solves, by construction, the main problem which usually penalizes the trigger exhaust systems.

As can be seen in FIGS. 11 and 13, the inertia member 509 is also provided with a release member 513 similar to that 113, 213, 313, 413 of the first four embodiments. More precisely, in the manner of a conventional expansion exhaust, the fifth embodiment comprises a disengagement element 513 allowing, in one direction of the oscillation, a dumb alternation, that is to say, The relief member 513 comes into contact with the trigger 517 but does not displace the trigger 517. Thus, preferably in accordance with the fifth embodiment, the release member 513 includes a flexible body 531 and a release abutment 533 arranged to force Move the single-piece trigger 517 in only one direction of the oscillations of the resonator 507.

[0076] As best illustrated in FIGS. 12 and 13, the oscillator 501 further comprises an expansion exhaust 515 comprising a trigger 517 integral with the pivoting shaft 503. The trigger 517 comprises at least one flexible blade 516, 516 'and a stop lift 518 arranged to elastically lock the pivoting shaft 503 relative to a concentric exhaust teeth 519 with respect to the pivoting shaft 503.

It will therefore be understood that the toothing 519 is fixed with respect to the pivoting shaft 503. In fact, the shaft 503 pivoting, under the constraint of the mechanical energy source, will rotate, at each oscillation of the resonator 507, which corresponds to the angle between two teeth of the exhaust teeth 519, c That is to say whenever the lifting 518 for stopping the trigger 517 will allow its movement from one tooth to the other.

[0078] In the fifth embodiment illustrated in FIGS. 11 to 13, the single-piece trigger 517 comprises two parallel crossbars 535, 536 and two parallel blades 516, 516 '. As best seen in FIG. 12, a first cross-member 535 is connected at one end to the pivot shaft 503 and at a second end perpendicular to a first flexible blade 516. In addition, the second cross-member 536 is connected at one end to the stop lift 518 and at a second end perpendicular to a second flexible blade 516 '. Finally, the first 516 and second 516 flexible blades are respectively connected to the second 536 and first 535 cross-members.

As can be seen in FIGS. 11 to 13, the second cross-member 536 preferably comprises three sections. The first rectilinear section 536a connects the two flexible blades 516, 516 ', carries the stop lift 318 at one end and, at the opposite end, is attached substantially perpendicularly in the retrograde direction to the second curved section 536b Of a quarter circle which runs along the pivoting shaft 503 which is itself attached substantially perpendicularly in the trigonometric direction to the third rectilinear section 336c which carries an abutment 537 for expansion. It will therefore be understood that the sections 536a and 536c are substantially perpendicular.

It will therefore be understood that the crosspieces 535, 536, visible in the rest position in FIGS. 11 to 13 are able to move relative to one another by means of the resilient deflection of the flexible blades 516, 516 '. More precisely, the disengagement element 513 is arranged to cause the flexible blades 516, 516 'to bend in order to elastically unlock, by the movement of the inertia member 509, the stopping lift 518 relative to the Concentric escapement 519 so that the pivoting shaft 503 counts each oscillation of the resonator 507 while transmitting the energy capable of maintaining it.

This is made possible because the one-piece trigger 517 comprises the expansion stop 537 integral with the second cross-member 536 which is arranged to come into contact with the disengagement element 513 at each half-wave of the resonator 507. As can be seen in FIG. . 13, the detent stop 537 forms a cam which, when it comes into contact with the release lift 532, causes the first rectilinear section 536a to move away from the toothing by the action of the abutment stop 533 519 for releasing the pivoting shaft 503. The shaft 503 pivoting under the constraint of the mechanical energy source will perform a rotation which corresponds to the angle between two teeth of the exhaust teeth 519 and, at the same time,

On the other hand, in the inverse rotation of the resonator 507, it can be seen that the detent stop 537 forms a cam which, when it comes into contact with the release lift 532, obliges, by the absence of The action of the release stop 533 in the reverse direction, the release lift 532 to elastically move apart and then, once the release stop 537 has escaped, to return elastically along the release abutment 533.

Advantageously according to the fifth embodiment of the invention, it will therefore be understood that the oscillator 501 comprises very few parts to be mounted since they are, for the most part, monoblocks, which allows the parts to be more easily referenced In relation to each other. Indeed, by way of example, the single-piece resonator 507 and the one-piece trigger 517 could be formed in two integral single plates forming at least two functional levels of the pivoting pin 503. This could, for example, be obtained by solidarized and then etched silicon plates or by the electroforming of a multi-level metal part.

Moreover, thanks to the use of the flexible guide 511, the resonator 507 has a very low thickness and intrinsically induces the elimination of the gallop. Furthermore, the oscillator 501 according to the invention advantageously allows the resonator 507 to have a pulse by a direct torque rather than a contact force as with a usual expansion exhaust.

In addition, the operation induces advantages usually belonging to the much more complex tourbillon oscillators as already explained in the first embodiment.

Consequently, in the manner of a vortex but without its complexity of focusing, the pivoting shaft 503 of the fifth embodiment cancels out the deviations of the oscillator 501 in the vertical positions by rotating the resonator 507 at the same time as the trigger 517.

[0087] Enfin, comme pour les quatre premiers modes de réalisation, l’arbre 503 pivotant peut comporter, directement ou par l’intermédiaire d’un accumulateur d’énergie élastique, un pignon agencé pour s’engrener avec un rouage de finissage afin d’être relié à la source d’énergie mécanique et d’afficher l’heure. Ainsi, quel que soit le choix de transmission de l’énergie choisi dans le cinquième mode de réalisation, il est immédiat que la force du rouage de finissage et, éventuellement celle de l’accumulateur d’énergie élastique, doivent être dimensionnées pour ne pas entraîner l’actionnement de la détente 517 autrement que par l’élément 513 de dégagement.

Whatever the embodiment, it is indicated that the pivoting shaft 3, 103, 203, 303, 403, 503 counts each oscillation of the resonator 7, 107, 207, 307, 407, 507. This means The construction of the resonator 7, 107, 207, 307, 407, 507 that each oscillation is associated with a predetermined regulated time. It will therefore be understood that each movement of the pivoting shaft 3, 103, 203, 303, 403, 503 is associated with a predetermined time period suitable for displaying the time passing as for any timepiece. Thus, depending on the gearing of the finishing train, it is possible to display, directly or indirectly, from one of the wheels of the finishing train, time information such as seconds, minutes, hours or a value Of the calendar.

Whatever the embodiment, the mechanical power source being sufficiently charged, a manual release means acting on the stop lever 18, 118, 218, 318, 418, 518 can be made necessary for The user in order to start the oscillator 1, 101, 201, 301, 401, 501. Indeed, depending on the configuration of oscillator 1, 101, 201, 301, 401, 501, it is excluded that a movement induced by the user allowing the movement of the member 9, 109, 209, 309,

Claims (14)

409, 509 d’inertie ne soit pas suffisant pour que l’élément 113, 213, 313, 413, 513 de dégagement actionne la détente 17, 117, 217, 317, 417, 517. [0090] Ainsi, à titre d’exemple nullement limitatif, un tel moyen de déblocage manuel pourrait prendre la forme d’une couronne ou d’un poussoir sur la carrure de la pièce d’horlogerie et commander un ergot agencé pour faire passer une dent de la denture 19,119, 219, 319, 419, 519 d’échappement à la levée 18,118, 218, 318, 418, 518 d’arrêt afin de fournir au résonateur 7, 107, 207, 307, 407, 507 l’énergie nécessaire pour démarrer l’oscillateur 1, 101,201,301,401,501. [0091] Bien entendu, la présente invention ne se limite pas à l’exemple illustré mais est susceptible de diverses variantes et modifications qui apparaîtront à l’homme de l’art. En particulier, suivant l’application souhaitée, le résonateur 7, 107, 207, 307, 407, 507 et/ou la détente 17, 117, 217, 317, 417, 517 peuvent être modifiés notamment quant à leur géométrie (organe d’inertie, détente) ou leurs guidages flexibles. [0092] De plus, les modes de réalisation décrits ci-dessus sont susceptibles d’être combinés entre eux sans sortir du cadre de l’invention. Il est également possible, alternativement à l’utilisation de l’anneau 127, de relier les butées 133, 233, 333, 433, 533 de dégagement de l’élément 113, 213, 313, 413, 513 de dégagement afin de coupler les deux secteurs 125 de l’organe 109, 209, 309, 409, 509 d’inertie comme, par exemple, en contournant latéralement et/ou verticalement l’arbre 3,103, 203, 303, 403, 503 pivotant ou en traversant par un ajourage de l’arbre 3,103, 203, 303, 403, 503. Il pourrait également être envisagé de relier les deux secteurs 125 par un autre moyen que l’anneau 127. [0093] De manière additionnelle, des moyens anti-dégagements pourraient être ajoutés comme un bras de sécurité ou des moyens contre-inertiels agencés pour bloquer la détente 17,117, 217, 317, 417, 517 lorsque le dégagement n’est pas souhaité, c’est-à-dire lorsque la détente 17, 117, 217, 317, 417, 517 serait déplacée autrement que par la levée 132, 232, 332, 432, 532 de dégagement, comme, par exemple, suite à un choc subit par l’oscillateur 1, 101,201,301, 401, 501. [0094] Enfin, des moyens d’amortissement peuvent coopérer avec l’oscillateur 1, 101, 201, 301, 401, 501, comme notamment avec l’arbre 3, 103, 203, 303, 403, 503, afin de le rendre moins sensible aux chocs. Revendications

1. An oscillator (1, 101, 201, 301, 401, 501) comprising a pivoting shaft (3, 103, 203, 303, 403, 503) connected to a source (2) of mechanical energy, a resonator (7,107,207,307,407,507) Inertial-type elastic element comprising a member (9,109,209,309,409,509) forming said inertia provided with a release member (13,113,213,313,413,513) and a guide (11,111,211,311,411,511 ) Which forms the elasticity which is mounted between the pivoting shaft (3, 103, 203, 303, 403) and the member (9, 109, 209, 309, 409, 509) forming said inertia, an escapement (15, 215, 315, 415, 515) comprising a single-piece trigger (17, 117, 217, 317, 417, 517) integral with the pivoting shaft (3, 103, 203, 303, 403, 503) (16, 116, 116 ", 216, 316, 316", 416a, 416b, 416c, 416d, 516, 516 ') And a stop lever (18, 118, 218, 318, 418, 518) arranged to elastically lock the pivotable shaft (3, 103, 203, 303, 403, 503) 119, 219, 319, 419, 519), the release member (13, 113, 213, 313, 413, 513) being arranged to resiliently release by movement of the member , 209, 309, 409, 509) forming said inertia, the stop lever (18, 118, 218, 318, 418, 518) with respect to the toothing (19,119,219,319,419,519) (3, 103, 203, 303, 403, 503) counts each oscillation of the resonator (7, 107, 207, 307, 407, 507) while transmitting to it the energy adapted to 'maintain.503) pivotable relative to a concentric escapement toothing (19, 119, 219, 319, 419, 519), the release member (13, 113, 213, 313, 413, 513) being arranged to resiliently release, (18, 118, 218, 318, 418, 518) of the stop (19, 109, 209, 309, 409, 509) forming said inertia with respect to the toothing (19, 119, 219, 319, 419, 519) so that the pivoting shaft (3,103,203,303,403,503) counts each oscillation of the resonator (7,107,207,307,407,507 ) While transmitting to it the energy capable of maintaining it.503) pivotable relative to a concentric escapement toothing (19, 119, 219, 319, 419, 519), the release member (13, 113, 213, 313, 413, 513) being arranged to resiliently release, (18, 118, 218, 318, 418, 518) of the stop (19, 109, 209, 309, 409, 509) forming said inertia with respect to the toothing (19, 119, 219, 319, 419, 519) so that the pivoting shaft (3,103,203,303,403,503) counts each oscillation of the resonator (7,107,207,307,407,507 ) While transmitting to it the energy capable of maintaining it.418, 518) with respect to the concentric exhaust teeth (19, 119, 219, 319, 419, 519) so that the pivoting shaft (3, 103, 203, 303, 403, 503) counts each Oscillating the resonator (7, 107, 207, 307, 407, 507) while transmitting the energy capable of maintaining it.418, 518) with respect to the concentric exhaust teeth (19, 119, 219, 319, 419, 519) so that the pivoting shaft (3, 103, 203, 303, 403, 503) counts each Oscillating the resonator (7, 107, 207, 307, 407, 507) while transmitting the energy capable of maintaining it.

2. An oscillator according to claim 1, wherein the flexible guide comprises at least one anchoring means, (3, 103, 203, 303, 403, 503) and means (120, 122, 123, 124, 126, 220, 222, 224, 226, 320, 322, 324, 326, 420 (7,107,207,307,407,507) coinciding with the center of rotation of the shaft (3,103,203,303, 422,424,426,520,522,524,526) arranged to form a virtual pivot axis of the resonator (7,107,207,307,407,507) 403, 503).

3. Oscillateur (1,101,201,301,401,501) selon la revendication précédente, caractérisé en ce que les moyens (120,122, 123, 124, 126, 220, 222, 224, 226, 320, 322, 324, 326, 420, 422, 424, 426, 520, 522, 524, 526) flexibles comportent au moins une base (120, 220, 320, 420, 520) reliant, par au moins une lame (122, 124, 222, 224, 322, 324, 422, 424, 522, 524) flexible, respectivement l’organe (9, 109, 209, 309, 409, 509) formant ladite inertie et ledit au moins un moyen (121,221,321,421,521) d’ancrage.

4. Oscillateur (1,101,201,301,401,501) selon l’une des revendications précédentes, caractérisé en ce que l’organe (9, 109, 209, 309, 409, 509) formant ladite inertie est formé par deux secteurs (125), la surface interne d’un des secteurs (125) comportant l’élément (13, 113, 213, 313, 413, 513) de dégagement.

5. The oscillator according to claim 1, wherein the displacement element comprises a body, , 531), the free end of which is provided with a release lift (132, 232, 332, 432, 532) whose displacement, controlled by the member (9,109,209,309,409,509) (17, 117, 217, 317, 417, 517) is arranged to come into contact with the one-piece expansion (17, 117, 217, 317, 417, 517) at each alternation of the resonator (7,107,207,307,407,507).

6. An oscillator according to claim 1, characterized in that the disengagement element (13, 113, 213, 313, 413, 513) further comprises an abutment (133, 233, 333, To cause the flexible body (131, 231, 331, 431, 531) to displace the one-piece expansion (17, 117, 217, 317, 417, 517) in one direction only of oscillations of the resonator (7,107,207,307 , 407, 507).

7. An oscillator according to claim 1, wherein the single-piece expansion device comprises a single flexible blade, a detent stroke being integral with the first detent, Of said single flexible blade and being arranged to contact the release element (13, 113, 213, 313, 413, 513) at each alternation of the resonator (7,107,207,307,407,507).

8. An oscillator according to claim 1, wherein the one-piece trigger comprises two parallel cross-members, a first cross-member (1, 2, 3, 4, 135, 535) being connected at one end to the pivoting shaft (3, 103, 203, 303, 403, 503) and at one end perpendicular to a first flexible blade (116, 516) (136, 536) being connected at one end to the stop lift (118, 518) and at a second end perpendicular to a second flexible blade (116 ', 516'), wherein the first and second cross members Second flexible strips (116, 116 ', 516, 516') being parallel and respectively connected to the second and first crosspieces (136, 135, 536, 535).

9. An oscillator according to claim 1, wherein the single-piece expansion device comprises two parallel cross-members, a first cross-member being connected to a first cross-member and a second cross-beam (335, 336, (3, 103, 203, 303, 403) pivotally and perpendicularly to a first flexible blade (316), a second crosspiece (336) being connected at a first end (336c) to a first end To the stop latch (318) and at a second end (336a) perpendicularly to a second flexible leaf (316 '), the first and second flexible leafs (316, 316') being parallel and respectively connected to the second and First cross members (336, 335).

10. The oscillator as claimed in claim 8, wherein the single-piece expansion device comprises an expansion lug (137, 337, 537) integral with the second cross-member (10, 117, 217, (136, 336, 536) which is arranged to come into contact with the release element (13, 113, 213, 313, 413, 513) at each alternation of the resonator (7,107,207,307,407,507).

11. The oscillator as claimed in claim 1, wherein the single-piece expansion device comprises first and second oscillators, Second non-parallel flexible blades (416a, 416b) each connecting the pivoting shaft (3,103,203,303,403,503) to a fastener (435), the fastener (435) being further connected to a third blade (416d), the free end of which comprises the stop latch (418) and a fourth flexible leaf (416c) having a trigger stop (437) which is arranged to contact the element (13, 113, 213 , 313, 413, 513) at each alternation of the resonator (7, 107, 207, 307, 407, 507).

12. The oscillator as claimed in claim 1, wherein the pivoting shaft comprises a pinion (141, 201, 201, 301, 401, 501) ) Arranged to mesh with a finishing train (5) so as to be connected to the source (2) of mechanical energy and to display the time.

13. An oscillator according to claim 1, wherein the pinion is mounted on the shaft pivoting by means of a pivot pin (13, 113, 213, 313, 413, 513) Accumulator (143) for providing sufficient energy to maintain the resonator (7, 107, 207, 307, 407, 507) during the pulse time.

14. The oscillator as claimed in claim 1, wherein the monoblock resonator and the trigger are connected to the resonator, 317, 417, 517) are formed in two integral single plates forming two functional levels of the pivoting axis (3, 103, 203, 303, 403, 503).