EP3147725A1 - Oszillator mit rotierendem gesperr - Google Patents

Oszillator mit rotierendem gesperr Download PDF

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Publication number
EP3147725A1
EP3147725A1 EP15187214.0A EP15187214A EP3147725A1 EP 3147725 A1 EP3147725 A1 EP 3147725A1 EP 15187214 A EP15187214 A EP 15187214A EP 3147725 A1 EP3147725 A1 EP 3147725A1
Authority
EP
European Patent Office
Prior art keywords
resonator
oscillator
flexible
stop
pivoting shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP15187214.0A
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English (en)
French (fr)
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EP3147725B1 (de
Inventor
Pierre Cusin
Romain Le Moal
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nivarox Far SA
Original Assignee
Nivarox Far SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nivarox Far SA filed Critical Nivarox Far SA
Priority to EP15187214.0A priority Critical patent/EP3147725B1/de
Priority to US15/228,684 priority patent/US9921547B2/en
Priority to TW105125184A priority patent/TWI713564B/zh
Priority to JP2016181376A priority patent/JP6243496B2/ja
Priority to KR1020160120021A priority patent/KR101944586B1/ko
Priority to CN201610855878.2A priority patent/CN106557009B/zh
Publication of EP3147725A1 publication Critical patent/EP3147725A1/de
Application granted granted Critical
Publication of EP3147725B1 publication Critical patent/EP3147725B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape wheel
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/28—Compensation of mechanisms for stabilising frequency for the effect of imbalance of the weights, e.g. tourbillon
    • G04B17/285—Tourbillons or carrousels
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/06—Free escapements
    • G04B15/08—Lever escapements
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/02—Oscillators acting by gravity, e.g. pendulum swinging in a plane
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/06—Free escapements
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/045—Oscillators acting by spring tension with oscillating blade springs
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/26—Compensation of mechanisms for stabilising frequency for the effect of variations of the impulses

Definitions

  • the invention relates to a vortex type oscillator comprising a resonator of the inertia - elasticity type cooperating with a revolving escapement.
  • the detent escapement systems are known for bringing high accuracy to marine chronometers in the 18th century by offering a direct pulse and low sensitivity to friction. However, they have proved particularly difficult to adjust and sensitive to shocks.
  • Some marine chronometers have been mounted under vacuum, in sand or on cardan suspensions to avoid any transmission of shocks inducing gallop, that is to say the accidental passage of two teeth of the escape wheel instead of one, proper to disrupt the running of the timepiece.
  • shocks inducing gallop that is to say the accidental passage of two teeth of the escape wheel instead of one, proper to disrupt the running of the timepiece.
  • the aim of the present invention is to overcome all or part of the aforementioned drawbacks by proposing an oscillator comprising an inertia-elasticity resonator cooperating with an expansion escapement of a new type which is free from gallop and whose operation induces advantages usually belonging to the swirl type oscillators much more complex.
  • the invention relates to an oscillator comprising a pivoting shaft connected to a source of mechanical energy, a one-piece resonator of the inertia-elasticity type comprising a member forming said inertia provided with a release 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 detent integral with the pivoting shaft which comprises at least one flexible blade and a stop lever arranged to elastically lock the shaft pivoting relative to a concentric exhaust toothing, the release element being arranged to unlock elastically, by the movement of the member forming said inertia, the stop lift relative to the concentric escape toothing so that the pivoting shaft counts each oscillation of the resonator while transmitting the energy able to maintain it.
  • the oscillator has very few parts to mount because they are, for the most part, monoblocks which allows the parts to be more easily referenced to each other.
  • the resonator has a very low thickness and inherently induces the elimination of gallop.
  • 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 usual expansion escapement.
  • the pivoting shaft cancels by turning the oscillations of the oscillator in the vertical positions.
  • the invention relates to an oscillator for a timepiece, that is to say a resonator coupled with a distribution system and maintenance such as, for example, an exhaust system.
  • the oscillator 1 comprises a pivoting shaft 3 connected to a source of mechanical energy 2, for example, using a finishing train 5.
  • a power source 2 may comprise energy storage means by elastic deformation and / or by pneumatic storage.
  • the accumulation means may take the form of a metal blade mounted in a pivoting drum to form a barrel.
  • other types of mechanical energy sources can be envisaged.
  • the oscillator 1 comprises a resonator 7 monoblock type of inertia - elasticity.
  • This resonator 7 preferably comprises a member 9 forming said inertia and a flexible guide 11 forming said elasticity.
  • the flexible guide 11 is preferably monobloc with the member 9 and is mounted between the pivoting shaft 3 and the member 9.
  • the member 9 forming the inertia is also provided with a member 13 release.
  • 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 deflections nevertheless makes it impossible to run the resonator 7, which, by construction, solves the main problem that usually penalizes the exhaust systems.
  • the oscillator 1 further comprises an escapement 15 with a detent comprising a detent 17 integrally also integral with the pivoting shaft 3.
  • the trigger 17 comprises at least one flexible blade 16 and a lifting stop 18 arranged to resiliently lock the shaft 3 pivoting relative to a toothing 19 exhaust concentric with respect to the pivoting shaft 3.
  • the release element 13 is arranged to unlock elastically, by the movement of the inertia member 9, the lift 18 stop relative to the toothing 19 fixed concentric exhaust so that the pivoting shaft 3 counts each oscillation of the resonator 7 while transmitting the energy able to maintain it.
  • the oscillator 1 has very few parts to mount because they are, for the most part, monoblocks which allows the parts to be more easily referenced to each other.
  • the resonator 7 has a very small thickness and intrinsically induces the elimination of gallop.
  • the oscillator 1 according to the invention advantageously allows the resonator 7 to have a pulse by a direct torque rather than a force by contact as with a usual expansion escapement.
  • the pivoting shaft 3 cancels by turning the oscillations of the oscillator 1 in the vertical positions.
  • the oscillator 101 comprises a pivoting shaft 103 connected to a source of mechanical energy (not shown) and a monoblock resonator 107 of the inertia-elasticity type.
  • 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.
  • 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 pivot axis of the resonator 107 coincides with the center of rotation of the pivoting shaft 103.
  • the flexible means 123 comprise at least one base 120 connecting, by at least one flexible blade 122, 124, respectively the inertia member 109 and the at least one anchoring means 121.
  • the element 109 of inertia is preferably formed by two sectors 125 connected to each other by a ring 127 to obtain a member 109 of inertia monobloc.
  • 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 respectively using a beam 126 substantially T-shaped. It is noted that each beam 126 is thus integral with an anchoring means 121 and two sectors 125 forming said inertia.
  • the amplitude of the resonator 107 is therefore limited to the maximum deflections of the flexible guide 111 and in particular of the geometry of the beams 126, the bases 120 and the blades 122, 124.
  • This limitation of the deflections makes the resonator gallop intrinsically impossible. This solves, by construction, the main problem that usually penalizes the exhaust systems.
  • the inertia member 109 is also provided with a release member 113. More specifically, the inner surface of one of the sectors 125 comprises the element 113 of clearance.
  • the clearance element 113 comprises a flexible body 131 whose free end is provided with a clearance lift 132 whose displacement, controlled by the inertia member 109, is arranged to enter. in contact with the expansion 117 monoblock at each alternation of the resonator 107.
  • the first embodiment comprises a release element 113 allowing, in one direction of the oscillation, a mute alternation, that is to say that the clearance member 113 contacts the trigger 117 but does not move the trigger 117.
  • the clearance member 113 further comprises a release stop 133 arranged to force the flexible body 131. to move the one-piece trigger 117 in one direction oscillations of the resonator 107.
  • the oscillator 101 further comprises an escapement 115 with a detent comprising a detent 117 integrally integral with the pivoting shaft 103.
  • the trigger 117 comprises at least one flexible blade 116, 116 'and a stop lift 118 arranged to resiliently lock the shaft 103 pivoting relative to an exhaust gear 119 concentric with respect to the pivoting shaft 103.
  • the toothing 119 is fixed relative to the pivoting shaft 103.
  • the pivoting shaft 103 under the constraint of the mechanical energy source, will make a rotation, at each oscillation of the resonator 107, which will correspond to the angle between two teeth of the escape toothing 119, c that is to say, each time the lift 118 stop trigger 117 allow its movement from one tooth to another.
  • the one-piece trigger 117 comprises two crosspieces 135, 136 parallel and two parallel blades 116, 116 '.
  • a first cross member 135 is connected at a first end to the pivoting shaft 103 and at a second end perpendicularly to a first flexible blade 116.
  • the second cross member 136 is connected at a first end to the stop 118 and, at a second end perpendicularly, to a second flexible blade 116 '.
  • the first 116 and second 116 'flexible blades are respectively connected to the second 136 and first 135 sleepers.
  • the cross members 135, 136 visible in the rest position at Figures 3 and 4 , are able, with the aid of the elastic deflection of the flexible blades 116, 116 ', to move relatively relative to one another. More specifically, the element 113 of clearance is arranged to force the flexible blades 116, 116 'to bend in order to elastically unlock, by the movement of the body 109 of inertia, the lifting 118 stop relative to the concentric exhaust gear 119 so that the pivoting shaft 103 counts each oscillation of the resonator 107 while transmitting the energy capable of maintaining it.
  • the one-piece detent 117 has a thrust stop 137 integral with the second crossmember 136 which is arranged to come into contact with the release element 113 at each alternation of the resonator 107.
  • the stop 137 of relaxation forms a cam which, when it comes into contact with the lifting 132 of clearance, forces, by the action of the stop 133 of clearance, the cross 136 to deviate from the teeth 119 exhaust to release the shaft 103 pivoting.
  • the pivoting shaft 103 under the constraint of the mechanical energy source, will perform a rotation corresponding to the angle between two teeth of the escape toothing 119 and, at the same time, restart the resonator 107 by the transmission of its movement directly by the beams 126 via the anchoring means 121.
  • the thrust stop 137 forms a cam which, when it comes into contact with the release lift 132, forces, by the absence of action of the stop 133 of clearance in the opposite direction, the clearance 132 of disengagement to move away elastically and, once the abutment stop 137 escaped, to return elastically along the stop 133 of disengagement.
  • the oscillator 101 has very few parts to mount because they are, for the most part, one-piece which allows the parts to be more easily referenced, some by compared to others.
  • the monoblock resonator 107 and the one-piece expansion 117 could be formed in two single solid-state plates forming at least two functional levels of the pivoting axis 103. This could, for example, be obtained by secured and then etched silicon plates or by electroforming a multi-level metal part.
  • the resonator 107 has a very small thickness and intrinsically induces the elimination of gallop.
  • the oscillator 101 according to the invention advantageously allows the resonator 107 to have a pulse by a direct torque rather than a force by contact as with a usual expansion escapement.
  • the operation induces advantages usually belonging to the swirl type oscillators much more complex.
  • the whirlpool is a device imagined by Mr A.-L. Breguet in the early 19th century to cancel the rate errors in vertical positions. It comprises a movable cage which carries all the organs of the exhaust and, in its center the regulating organ.
  • the escape gear rotates around the seconds wheel which is fixed.
  • the cage which makes 1 turn per minute cancels by turning the deviations in the vertical positions.
  • the pivoting shaft 103 of the first embodiment cancels out the oscillations of the oscillator 101 in the vertical positions by turning the resonator 107 at the same time. time as relaxation 117.
  • the pivoting shaft 103 further comprises a pinion gear 141 arranged to mesh with a finishing train in order to be connected to the source of mechanical energy and to display the time.
  • the pinion 141 is mounted loosely on the pivoting shaft 103 via an elastic energy accumulator 143 in order to provide sufficient energy for the maintenance of the resonator 107 for the duration clearance.
  • the elastic energy accumulator 143 is a spiral spring.
  • the elastic energy accumulator 143 can not be limited to a spring in the form of a spiral.
  • pivoting shaft assembly 103 elastic energy accumulator 143 and pinion 141 could alternatively be one of the embodiments of energy transmission mobiles described in the document.
  • EP 2 455 821 incorporated by reference in the present description.
  • pivoting shaft assembly 103 elastic energy accumulator 143 and pinion 141 is not essential and could also be replaced by a pivoting shaft 103 provided with a peripheral toothing. geared to the finishing gear. Whatever the choice of transmission of energy, it is Immediately that the force of the finishing train and, optionally that of the elastic energy accumulator 143, must be dimensioned so as not to cause the actuation of the trigger 117 other than by the element 113 release.
  • FIG. 5 A second embodiment of an oscillator 201 according to the invention is presented to Figures 5 and 6 .
  • the oscillator 201 comprises a pivoting shaft 203 and a monoblock resonator 207 of the inertia-elasticity type similar to those 103, 107 of the first embodiment.
  • This resonator 207 thus 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.
  • the amplitude of the resonator 207 is therefore limited to the maximum deflections of the flexible guide 211 and in particular of the geometry of the beams 226, the bases 220 and the plates 222, 224. This limitation of the deflections nevertheless makes the resonator gallop intrinsically impossible. This solves, by construction, the main problem that usually penalizes the exhaust systems.
  • the inertia member 209 is also provided with a release element 213 similar to that 113 of the first embodiment.
  • the second embodiment comprises a release element 213 allowing, in one direction of the oscillation, a mute alternation, that is to say that the release member 213 comes into contact with the trigger 217 but does not move the trigger 217.
  • the clearance element 213 comprises a flexible body 231 and a stop 233 of clearance arranged to force to move the one-piece expansion 217 in one direction oscillations of the resonator 207.
  • the oscillator 201 further comprises an escapement 215 with a detent comprising a trigger 217 monobloc integral with the pivoting shaft 203.
  • the trigger 217 comprises a single flexible blade 216 and a lifting 218 stop arranged to resiliently lock the shaft 203 pivoting relative to a toothing 219 exhaust concentric with respect to the pivoting shaft 203.
  • the clearance element 213 of the second embodiment is arranged to force the flexible blade 216 to bend in order to elastically unlock, by the movement of the inertia member 209, the lift 218. stopping relative to the concentric exhaust toothing 219 so that the pivoting shaft 203 counts each oscillation of the resonator 207 while transmitting the energy capable of maintaining it.
  • the one-piece detent 217 comprises a stop 237 of expansion integral with the flexible blade 216 which is arranged to come into contact with the release element 213 at each alternation of the resonator 207.
  • the stop 237 of relaxation forms a cam which, when it comes into contact with the lifting 232 release, forces, by the action of the stop 233 release, the blade 216 flexible to deviate from the toothing 219 d exhaust to release the swivel shaft 203.
  • the pivoting shaft 203 under the constraint of the mechanical energy source, will perform a rotation corresponding to the angle between two teeth of the exhaust toothing 219 and, at the same time, restart the resonator 207 by the transmission of its movement directly by the beams 226 via the anchoring means 221.
  • the stop 237 for expansion forms a cam which, when it comes into contact with the release lift 232, forces, by the absence of action of the abutment stop 233 in the opposite direction, the release lift 232 to move away elastically and, once the abutment stop 237 escaped, to return elastically along the abutment 233 release.
  • the oscillator 201 has very few parts to mount because they are, for the most part, monoblocks which allows the parts to be more easily referenced, some by compared to others.
  • the one-piece resonator 207 and the one-piece expansion 217 could be formed in two single integral plates forming at least two functional levels of the pivoting axis 203. This could, for example, be obtained by secured and then etched silicon plates or by electroforming a multi-level metal part.
  • the resonator 207 has a very small thickness and intrinsically induces the elimination of gallop.
  • 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 escapement.
  • the operation induces advantages usually belonging to the more complex vortex oscillators as already explained in the first embodiment. Therefore, in the manner of a vortex but without its developmental complexity, the pivoting shaft 203 of the second embodiment cancels the oscillations of the oscillator 201 in the vertical positions by turning the resonator 207 at the same time. time as relaxation 217.
  • the pivoting shaft 203 may comprise, directly or via an elastic energy accumulator, a pinion arranged to mesh with a finishing gear train in order to be connected. to the source of mechanical energy and to display the time.
  • the strength of the finishing gear train and, possibly, that of the energy accumulator elastic must be dimensioned not to cause the actuation of the trigger 217 other than by the element 213 release.
  • FIG. 7 A third embodiment of an oscillator 301 according to the invention is presented to Figures 7 and 8 .
  • the oscillator 301 comprises a pivoting shaft 303 and an inertia-elastic monoblock resonator 307 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.
  • the amplitude of the resonator 307 is therefore limited to the maximum deflections of the flexible guide 311 and in particular of the geometry of the beams 326, the bases 320 and the blades 322, 324. This limitation of the deflections makes the resonator gallop intrinsically impossible. 307 which solves, by construction, the main problem that usually penalizes the exhaust exhaust systems.
  • the inertia member 309 is also provided with a clearance element 313 similar to that 113, 213 of the first and second embodiments.
  • the third embodiment comprises a release element 313 allowing, in one of the directions of the oscillation, a mute alternation, that is to say that the clearance member 313 comes into contact with the trigger 317 but does not move the trigger 317.
  • the clearance member 313 comprises a flexible body 331 and a stop 333 clearance arranged to force to move the one-piece expansion 317 in one direction oscillations of the resonator 307.
  • the oscillator 301 further comprises an exhaust 315 expansion comprising a detent 317 integrally integral with the shaft 303 pivoting.
  • the trigger 317 comprises at less a flexible blade 316, 316 'and a lifting 318 stop arranged to resiliently lock the shaft 303 pivoting relative to an exhaust gear 319 concentric with respect to the shaft 303 pivoting.
  • the clearance element 313 of the third embodiment is arranged to force said at least one flexible blade 316, 316 'to bend in order to elastically unlock, by the movement of the body 309 of inertia, the lifting 318 stop with respect to the concentric exhaust gear 319 so that the pivoting shaft 303 counts each oscillation of the resonator 307 while transmitting the energy able to maintain it.
  • the expansion 317 monobloc comprises two crosspieces 335, 336 parallel and two blades 316, 316 'parallel.
  • a first cross member 335 is connected at a first end to the pivoting shaft 303 and, at the same end perpendicularly, to a first flexible blade 316.
  • the second cross member 336 is connected, at a first end, to the lift 318 stop (better visible in the figure 7 ) and at a second end perpendicularly to a second flexible blade 316 '.
  • the first 316 and second 316 'flexible blades are respectively connected to the second 336 and first 335 sleepers.
  • the second cross member 336 preferably comprises three rectilinear sections.
  • the first section 336a connects the two flexible blades 316, 316 'and is attached, substantially perpendicularly in the trigonometrical direction, to the second section 336b which runs along the first flexible blade 316 which is itself attached, substantially perpendicularly in the retrograde direction, to the third section 336c which carries the lift 318 stop. It is therefore clear that the sections 336a and 336c are substantially parallel.
  • the cross members 335, 336 visible in the rest position at Figures 7 and 8 are capable, with the aid of the elastic deflection of the flexible blades 316, 316 ', to move relative to one another. More specifically, the clearance element 313 is arranged to force the flexible blades 316, 316 'to bend in order to elastically unlock, by the movement of the inertia member 309, the lift 318 with respect to the concentric exhaust gear 319 so that the pivoting shaft 303 counts each oscillation of the resonator 307 while transmitting to it the energy capable of maintaining it.
  • the detent 317 monobloc comprises a stop 337 of expansion secured to the second cross member 336, at the first section 336a, which is arranged to come into contact with the element 313 release at each alternation of the resonator 307.
  • the stop 337 of relaxation forms a cam which, when it comes into contact with the release lift 332, forces, by the action of the stop 333 clearance, the cross member 336, and in particular its third section 336c, s move away from the exhaust teeth 319 to release the pivoting shaft 303.
  • the pivoting shaft 303 under the constraint of the source of mechanical energy, will perform a rotation corresponding to the angle between two teeth of the escape toothing 319 and, at the same time, restart the resonator 307 by the transmission of its movement directly by the beams 326 via the anchoring means 321.
  • the stop 337 for expansion forms a cam which, when it comes into contact with the disengagement lift 332, forces, by the absence of action of the stop 333 clearance in the opposite direction, the lift 332 release to elastically deviate and, once the abutment 337 trigger escaped, to return elastically along the stop 333 release.
  • the oscillator 301 has very few parts to assemble because they are, for the most part, monoblocks which allows the parts to be more easily referenced, some by compared to others.
  • the monobloc resonator 307 and the detent One-piece 317 could be formed in two single integral plates forming at least two functional levels of the pivoting axis 303. This could, for example, be obtained by secured and then etched silicon plates or by electroforming a multi-level metal part.
  • the resonator 307 has a very small thickness and intrinsically induces the elimination of gallop.
  • 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 escapement.
  • the operation induces advantages usually belonging to the more complex vortex oscillators as already explained in the first embodiment. Consequently, in the manner of a vortex but without its developmental complexity, the pivoting shaft 303 of the third embodiment cancels the oscillations of the oscillator 301 in the vertical positions by turning the resonator 307 at the same time. time as relaxation 317.
  • the pivoting shaft 303 may comprise, directly or via an elastic energy accumulator, a pinion arranged to mesh with a finishing gear train in order to be connected to the mechanical power source and display the time.
  • the strength of the finishing gear train, and possibly that of the elastic energy accumulator must be dimensioned so as not to trigger the actuation of the trigger 317 other than by the element 313 release.
  • FIG. 9 A fourth embodiment of an oscillator 401 according to the invention is presented to Figures 9 and 10 .
  • the oscillator 401 comprises a pivoting shaft 403 and a resonator 407 monoblock of the inertia-elasticity type similar to those 103, 203, 303, 107, 207, 307 of the three first embodiments.
  • This resonator 407 thus comprises a member 409 forming said inertia and a flexible guide 411 forming said elasticity with the same advantages as those 109, 209, 309 and 111, 211, 311 of the first three embodiments.
  • the amplitude of the resonator 407 is therefore limited to the maximum deflections of the flexible guide 411 and in particular of the geometry of the beams 426, the bases 420 and the blades 422, 424. This limitation of the deflections nevertheless makes the resonator gallop intrinsically impossible. 407 which solves, by construction, the main problem that usually penalizes exhaust exhaust systems.
  • the inertia member 409 is also provided with a clearance element 413 similar to that 113, 213, 313 of the first three embodiments.
  • the fourth embodiment comprises a release member 413 allowing, in one of the directions of the oscillation, a mute alternation, that is to say that the clearance member 413 comes into contact with the trigger 417 but does not move the trigger 417.
  • the clearance member 413 comprises a flexible body 431 and a stop 433 of clearance arranged to force to move the one-piece expansion valve 417 in one direction oscillations of the resonator 407.
  • the oscillator 401 further comprises an escapement 415 trigger comprising a detent 417 integrally integral with the shaft 403 pivoting.
  • the detent 417 comprises at least one flexible blade 416a, 416b, 416c, 146d and a lifting lever 418 arranged to resiliently lock the pivoting shaft 403 with respect to an exhaust gear 419 concentric with respect to the pivoting shaft 403. .
  • the clearance element 413 of the fourth embodiment is arranged to force said at least one flexible blade 416a, 416b, 416c, 146d to bend in order to to unlock elastically, by the movement of the inertia member 409, the lifting 418 stop relative to the concentric exhaust teeth 419 so that the pivoting shaft 403 counts each oscillation of the resonator 407 while transmitting it energy able to maintain it.
  • the detent 417 monobloc comprises first and second flexible non-parallel blades 416a, 416b each connecting the shaft 403 pivoting to a fastener 435 substantially cylindrical.
  • the fastener 435 is further connected to a third flexible blade 416d whose free end includes the lifting 418 stop.
  • the fastener 435 also comprises a fourth flexible blade 416c having a stop 437 for detent which is arranged to come into contact with the element 413 of release at each alternation of the resonator 407.
  • the third and fourth blades 416d, 416c are substantially perpendicular.
  • the blades 416a, 416b, 416c, 146d flexible visible in the rest position to Figures 9 and 10 , are able, with the aid of their elastic deflection to move relatively relative to each other. More specifically, the element 413 clearance is arranged to force the blades 416a, 416b, 416c, 146d flexible to bend in order to unlock elastically, by the movement of the member 409 of inertia, the lift 418 stop by relative to the concentric exhaust toothing 419 so that the pivoting shaft 403 counts each oscillation of the resonator 407 while transmitting to it the energy capable of maintaining it.
  • the blades 416c and 416d are less flexible than the blades 416a and 416b to obtain the rotational movement around the fastener 435 in order to release the lift 418 of the toothing 419 exhaust.
  • the detent 417 monobloc comprises a stop 437 of expansion integral with the fourth flexible blade 416c which is arranged to come into contact with the element 413 of release at each alternation of the resonator 407.
  • the The stop 437 forms a cam which, when it comes into contact with the release lift 432, forces the third flexible blade 436d to move away from the teeth 419 by the action of the stop 433. exhaust to release the shaft 403 pivoting.
  • the pivoting shaft 403 under the constraint of the mechanical energy source, will perform a rotation corresponding to the angle between two teeth of the escape toothing 419 and, at the same time, restart the resonator 407 by the transmission of its movement directly by the beams 426 via the means 421 anchoring.
  • the stop 437 for expansion forms a cam which, when it comes into contact with the release lift 432, forces, by the absence of any action of the abutment stop 433 in the opposite direction, the lifting 432 release to elastically deviate and, once the abutment stop 437 escaped, to return elastically along the stop 433 release.
  • the oscillator 401 has very few parts to mount because they are, for the most part, monoblocks which allows the parts to be more easily referenced, some by compared to others.
  • the one-piece resonator 407 and the one-piece detent 417 could be formed in two single integral plates forming at least two functional levels of the pivoting axis 403. This could, for example, be obtained by secured and then etched silicon plates or by electroforming a multi-level metal part.
  • the resonator 407 has a very small thickness and intrinsically induces the elimination of gallop.
  • the oscillator 401 according to the invention advantageously allows the resonator 407 to have a pulse by a couple direct rather than a force by contact as with a usual detent escapement.
  • the operation induces advantages usually belonging to the more complex vortex oscillators as already explained in the first embodiment. Consequently, in the manner of a vortex but without its developmental complexity, the pivoting shaft 403 of the fourth embodiment cancels the oscillations of the oscillator 401 in the vertical positions by turning the resonator 407 at the same time. time as relaxation 417.
  • the pivoting shaft 403 may comprise, directly or via an elastic energy accumulator, a pinion arranged to mesh with a finishing gear to be connected to the mechanical power source and display the time.
  • FIG. 11 A fifth embodiment of an oscillator 501 according to the invention is presented to Figures 11 to 13 .
  • the oscillator 501 comprises a pivoting shaft 503 and an inertia-elastic type resonator 507 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, 411 of the first four embodiments.
  • the amplitude of the resonator 507 is therefore limited to the maximum deflections of the flexible guide 511 and in particular of the geometry of the beams 526, the bases 520 and the blades 522, 524. This limitation of the deflections nevertheless makes the resonator gallop intrinsically impossible. 507 which solves, by construction, the problem that usually penalizes exhaust systems.
  • the member 509 of inertia is also provided with a clearance element 513 similar to that 113, 213, 313, 413 of the first four embodiments.
  • the fifth embodiment comprises a release element 513 allowing, in one direction of the oscillation, a mute alternation, that is to say that the 513 clearance member contacts the trigger 517 but does not move the trigger 517.
  • the clearance member 513 comprises a flexible body 531 and a stop 533 clearance arranged to force to move the one-piece trigger 517 in one direction oscillations of the resonator 507.
  • the oscillator 501 further comprises an escapement 515 with a detent comprising a detent 517 integrally integral with the pivoting shaft 503.
  • the trigger 517 comprises at least one flexible blade 516, 516 'and a lifting 518 stop arranged to elastically lock the shaft 503 pivoting relative to a set of teeth 519 exhaust concentric with respect to the shaft 503 pivoting.
  • the toothing 519 is fixed relative to the pivoting shaft 503.
  • the pivoting shaft 503 under the constraint of the mechanical energy source, will make a rotation, at each oscillation of the resonator 507, which will correspond to the angle between two teeth of the escape toothing 519, c that is to say, each time the lifting 518 stop trigger 517 will allow its movement from one tooth to another.
  • the one-piece trigger 517 comprises two parallel crosspieces 535, 536 and two parallel blades 516, 516 '.
  • a first cross member 535 is connected at a first end to the pivoting shaft 503 and, at a second end perpendicularly, to a first flexible blade 516.
  • the second cross 536 is connected to a first end, the lifting 518 stop and, at a second end perpendicularly, a second blade 516 'flexible.
  • the first 516 and second 516 'flexible blades are respectively connected to the second 536 and first 535 sleepers.
  • the second cross 536 preferably comprises three sections.
  • the first rectilinear section 536a connects the two flexible blades 516, 516 ', carries the lifting 318 stop at one end and, at the opposite end, is attached, substantially perpendicularly in the retrograde direction, to the second curved section 536b shaped of a quarter circle which runs along the pivoting shaft 503 which is itself attached, substantially perpendicularly in the trigonometrical direction, to the third rectilinear section 336c which carries a stop stop 537. It is therefore understood that the sections 536a and 536c are substantially perpendicular.
  • the sleepers 535, 536 visible in the rest position at Figures 11 to 13 are able, by means of the elastic deflection of the flexible blades 516, 516 ', to move relative to one another. More specifically, the clearance element 513 is arranged to force the flexible blades 516, 516 'to flex in order to elastically unlock, by the movement of the inertia member 509, the lifting lever 518 with respect to the 519 exhaust gear concentric so that the pivoting shaft 503 counts each oscillation of the resonator 507 while transmitting energy capable of maintaining it.
  • the one-piece detent 517 comprises the abutment stop 537 integral with the second crossmember 536 which is arranged to come into contact with the release element 513 at each alternation of the resonator 507.
  • the detent stop 537 forms a cam which, when it comes into contact with the disengagement lift 532, forces the first rectilinear section 536a to move away from the tooth 519 by the action of the disengagement stop 533. exhaust to release the shaft 503 pivoting.
  • the pivoting shaft 503 under the constraint of the mechanical energy source, will perform a rotation which corresponds to the angle between two teeth of the teeth 519 exhaust and, at the same time, restart the resonator 507 by the transmission of its movement directly by the beams 526 via the anchoring means 521.
  • the stop 537 for expansion forms a cam which, when it comes into contact with the disengagement lift 532, forces, by the absence of action of the stop 533 clearance in the opposite direction, the lift 532 release to elastically deviate and, once the abutment stopper 537 escaped, to return elastically along the stop 533 release.
  • the oscillator 501 has very few parts to mount because they are, for the most part, monoblocks which allows the parts to be more easily referenced, some by compared to others.
  • the one-piece resonator 507 and the one-piece detent 517 could be formed in two single integral plates forming at least two functional levels of the pivoting axis 503. This could, for example, be obtained by secured and then etched silicon plates or by electroforming a multi-level metal part.
  • the resonator 507 has a very small thickness and intrinsically induces the elimination of gallop.
  • the oscillator 501 according to the invention advantageously allows the resonator 507 to have a pulse by a direct torque rather than a force by contact as with a usual expansion escapement.
  • the operation induces advantages usually belonging to the more complex vortex oscillators as already explained in the first embodiment. Consequently, in the manner of a vortex but without its developmental complexity, the pivoting shaft 503 of the fifth embodiment cancels out the oscillations of the oscillator 501 in the vertical positions by turning the resonator 507 at the same time. time as relaxation 517.
  • the pivoting shaft 503 may comprise, directly or via an elastic energy accumulator, a pinion arranged to mesh with a finishing gear train to be connected to the mechanical power source and display the time.
  • the strength of the finishing gear train, and possibly that of the elastic energy accumulator must be dimensioned so as not to trigger the actuation of the trigger 517 other than by the element 513 release.
  • the pivoting shaft 3, 103, 203, 303, 403, 503 counts each oscillation of the resonator 7, 107, 207, 307, 407, 507.
  • the gear ratios of the gear train it is possible to display directly or indirectly from one of the mobile of the work train, hourly information such as, for example, seconds, minutes, hours or a value calendar.
  • a manual release means acting on the lift 18, 118, 218, 318, 418, 518 stop may be necessary for the user to to start the oscillator 1, 101, 201, 301, 401, 501. Indeed, according to the configuration of the oscillator 1, 101, 201, 301, 401, 501, it is excluded that a movement induced by the user allowing the displacement of the member 9, 109, 209, 309, 409, 509 of inertia is not sufficient for the element 113, 213, 313, 413, 513 release actuates the trigger 17, 117, 217, 317, 417, 517.
  • such a manual unlocking means could take the form of a crown or a pusher on the middle part of the timepiece and control a lug arranged to pass a tooth of the teeth 19, 119, 219, 319, 419, 519 stop exhaust 18, 118, 218, 318, 418, 518 to provide the resonator 7, 107, 207, 307, 407, 507 the energy required to start the oscillator 1, 101, 201, 301, 401, 501.
  • the present invention is not limited to the illustrated example but is susceptible of various variations and modifications that will occur to those skilled in the art.
  • the resonator 7, 107, 207, 307, 407, 507 and / or the detent 17, 117, 217, 317, 417, 517 can be modified especially as to their geometry ( inertia, relaxation) or their flexible guides.
  • the embodiments described above are capable of being combined with each other without departing from the scope of the invention. It is also possible, alternatively with the use of the ring 127, to connect the stops 133, 233, 333, 433, 533 of clearance of the element 113, 213, 313, 413, 513 of release in order to couple the two sectors 125 of the member 109, 209, 309, 409, 509 of inertia such as, for example, bypassing laterally and / or vertically the shaft 3, 103, 203, 303, 403, 503 pivoting or crossing through an opening of the shaft 3, 103, 203, 303, 403, 503. It could also be envisaged to connect the two sectors 125 by means other than the ring 127.
  • anti-release means could be added such as a safety arm or counter-inertial means arranged to lock the trigger 17, 117, 217, 317, 417, 517 when the clearance is not desired. That is, when the trigger 17, 117, 217, 317, 417, 517 would be displaced other than by the lift 132, 232, 332, 432, 532, as, for example, following a shock undergone by the oscillator 1, 101, 201, 301, 401, 501.
  • damping means can cooperate with the oscillator 1, 101, 201, 301, 401, 501, as in particular with the shaft 3, 103, 203, 303, 403, 503, in order to make it less sensitive to shocks.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Micromachines (AREA)
  • Percussion Or Vibration Massage (AREA)
  • Braking Arrangements (AREA)
  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
  • Surgical Instruments (AREA)
  • Invalid Beds And Related Equipment (AREA)
EP15187214.0A 2015-09-28 2015-09-28 Oszillator mit rotierendem gesperr Active EP3147725B1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP15187214.0A EP3147725B1 (de) 2015-09-28 2015-09-28 Oszillator mit rotierendem gesperr
US15/228,684 US9921547B2 (en) 2015-09-28 2016-08-04 Oscillator with rotating detent
TW105125184A TWI713564B (zh) 2015-09-28 2016-08-08 具有轉動掣子的振盪器
JP2016181376A JP6243496B2 (ja) 2015-09-28 2016-09-16 回転するデテント部を有する振動器
KR1020160120021A KR101944586B1 (ko) 2015-09-28 2016-09-20 회전 멈춤쇠를 구비한 오실레이터
CN201610855878.2A CN106557009B (zh) 2015-09-28 2016-09-27 具有旋转制动器的振荡器

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EP15187214.0A EP3147725B1 (de) 2015-09-28 2015-09-28 Oszillator mit rotierendem gesperr

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EP3147725A1 true EP3147725A1 (de) 2017-03-29
EP3147725B1 EP3147725B1 (de) 2018-04-04

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EP3637196A1 (de) 2018-10-08 2020-04-15 Manufacture et fabrique de montres et chronomètres, Ulysse Nardin Le Locle S.A. Mechanischer oszillator
US11397408B2 (en) 2018-05-25 2022-07-26 Société Anonyme de la Manufacture d'Horlogerie Audemars Piguet & Cie Automatically starting and secured detent escapement for a timepiece

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EP3032351A1 (de) * 2014-12-09 2016-06-15 LVMH Swiss Manufactures SA Uhrmechanismus, Uhrwerk und Uhr mit solch einem Mechanismus
EP3299905B1 (de) * 2016-09-27 2020-01-08 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Mechanischer oszillator für ein uhrwerk
NL2020384B1 (en) * 2018-02-06 2019-08-14 Flexous Mech Ip B V Mechanical watch oscillator
FR3094803B1 (fr) * 2019-04-05 2021-04-23 Lvmh Swiss Mft Sa Oscillateur sphérique pour mécanisme horloger
EP3770693B1 (de) * 2019-07-23 2022-08-31 Omega SA Anschlagmechanismus für uhrenkäfig mit anschlagrad
EP3770694B1 (de) * 2019-07-23 2021-12-08 Omega SA Anschlagkäfig für uhr mit zwei elastischen anschlagelementen

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KR101944586B1 (ko) 2019-01-31
CN106557009B (zh) 2019-05-07
EP3147725B1 (de) 2018-04-04
TWI713564B (zh) 2020-12-21
JP2017067770A (ja) 2017-04-06
CN106557009A (zh) 2017-04-05
US9921547B2 (en) 2018-03-20
US20170090422A1 (en) 2017-03-30
KR20170037823A (ko) 2017-04-05
TW201723690A (zh) 2017-07-01
JP6243496B2 (ja) 2017-12-06

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