EP4160323A1 - Mechanische einstellvorrichtung für uhr mit selbstanlaufendem, halb freistehendem hemmungsmechanismus mit geringem anstellwinkel - Google Patents

Mechanische einstellvorrichtung für uhr mit selbstanlaufendem, halb freistehendem hemmungsmechanismus mit geringem anstellwinkel Download PDF

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Publication number
EP4160323A1
EP4160323A1 EP21200709.0A EP21200709A EP4160323A1 EP 4160323 A1 EP4160323 A1 EP 4160323A1 EP 21200709 A EP21200709 A EP 21200709A EP 4160323 A1 EP4160323 A1 EP 4160323A1
Authority
EP
European Patent Office
Prior art keywords
escapement
fork
phase
rest
regulator
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.)
Pending
Application number
EP21200709.0A
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English (en)
French (fr)
Inventor
Olivier LEASSER
Gregory Musy
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CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement
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CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement
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Priority to EP21200709.0A priority Critical patent/EP4160323A1/de
Priority to US17/937,808 priority patent/US12429820B2/en
Publication of EP4160323A1 publication Critical patent/EP4160323A1/de
Pending legal-status Critical Current

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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
    • 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
    • G04B17/04—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
    • G04B18/00—Mechanisms for setting frequency
    • G04B18/02—Regulator or adjustment devices; Indexing devices, e.g. raquettes

Definitions

  • the present invention relates to the field of watchmaking, more specifically, the present invention relates to a mechanical watch regulator comprising an escapement and an oscillator.
  • a clock regulator mechanism typically includes an escapement as illustrated in figure 1 .
  • Such an escapement 10 typically comprises an escape wheel 11 provided with teeth 112 configured to cooperate with pallets 121 of an anchor 12.
  • the anchor 12 comprises a fork 122 cooperating with a pin 130 of a plate 131.
  • the plate 131 is rigidly linked to an oscillator (or regulator member) not shown.
  • the purpose of the escapement is to maintain and count the oscillations of the oscillator.
  • a mechanical oscillator comprises an inertial element, a guide and an elastic return element.
  • the mechanical oscillator can comprise a hairspring balance in which the balance wheel constitutes the inertial element, the guide corresponds to the balance shaft and to the stones of the plate and bridge, and the hairspring constitutes the elastic return element.
  • FIG 2a shows a diagram showing different oscillation angles of the balance wheel of a spiral balance oscillator, cooperating with an escapement as described above.
  • the balance wheel having an amplitude Ao of the order of 300°, can be characterized by a portion of free oscillation ⁇ LI and a portion of oscillation corresponding to the angle of lift ⁇ LE , of the order of 50°, where the release of the escape wheel and the impulse from the escapement to the inertial element occur.
  • the amplitude Ao is the maximum angular position, with respect to the line of centers, that takes the inertial element during an oscillation (or alternation).
  • the line of centers ⁇ 0 is defined as the angular position of the inertial element at equilibrium without the escapement (when the elastic return element is completely relaxed).
  • a horological oscillator on flexible guidance, or with a flexible pivot is an oscillator whose inertial element (which may include a balance wheel) is guided in rotation by an arrangement of elastic parts and not by a physical axis of rotation rotating in conventional bearings (eg: ruby bearing), as in the case of a balance spring.
  • the flexible pivot exerts an elastic return torque on the balance like the hairspring of a hairspring balance oscillator.
  • FIG. 2b shows a diagram plotting different oscillation angles of an oscillator on flexible guidance (for example, such as that shown in figure 19 ) cooperating with an escapement as described above.
  • the inertial element having an amplitude Ao typically comprised between 10° and 50°, is characterized by a portion of free oscillation ⁇ LI typically of the order of 10° to 20°, and by an angle of lifting ⁇ LE , of the order of 6° maximum.
  • ⁇ LI free oscillation
  • ⁇ LE angle of lifting
  • an oscillator on flexible guidance is distinguished by greater rigidity of the elastic return element and by lower amplitudes of oscillations Ao.
  • the lift half-angle ⁇ LE /2 of an oscillator corresponds to the angle between the line of the centers of the inertial element ⁇ 0 and its angular position at the end of the pulse ⁇ IM .
  • minimizing the lift angle ⁇ LE amounts to bringing the end-of-pulse angular position ⁇ IM closer to the line of centers ⁇ 0 and therefore to reducing the elastic restoring torque of the oscillator at the end of the pulse, this which facilitates self-starting.
  • Self-starting is the property of an escapement that starts only thanks to the torque supplied by the escape wheel following winding of the barrel in its working area. Self-starting guarantees start-up of the oscillator without outside help during the barrel winding phase, for example after the watch has been stored for a long time. Self-starting is an advantageous property of any wristwatch escapement because it is regularly subject to shocks, which causes the balance wheel to brake against its shock absorbers. This braking can lead to momentary stops of the balance. If the escapement is not self-starting, the balance wheel will remain blocked until the intervention of the user or a watchmaker. Thus an escapement which is not self-starting poses reliability problems in the context of the wristwatch.
  • a system is self-starting when the torque at the escape wheel is sufficient to, among other things, complete the pulse phase.
  • the elastic return torque of the oscillator (this elastic return torque is directly proportional to the stiffness of the return spring and to the end-of-pulse angular position ⁇ FI ) is then counterbalanced by the torque at the escape wheel .
  • Increasing the torque at the escape wheel to ensure the self-starting of an oscillator on flexible guidance amounts to increasing its energy consumption, which is not a satisfactory solution given that the energy available in a watch bracelet is limited.
  • the document CH715589A1 describes a rubbing rest escapement which is adapted to an oscillator on a flexible guide.
  • the advantage of a rubbing rest escapement is that it can be sized to be compatible with a lift angle ⁇ LE on the balance arm of less than 6°, which is advantageous for self-starting.
  • the disadvantage is that the balance wheel is linked to the lever (elastically in this specific case) which implies a permanent rotation of the lever during the oscillation of the balance wheel and therefore a permanent rubbing contact between the escape wheel and the 'anchor.
  • the loss of energy resulting from this rubbing contact is substantial, which de facto limits the operating amplitudes of the oscillator to low values, of the order of 6 to 8°.
  • the Swiss lever escapement is a free escapement because it only comes into contact with the oscillator during the lift angle to perform the release and impulse phases.
  • the present invention relates to a watchmaking mechanical regulator comprising an escapement cooperating with a watchmaking mechanical oscillator provided with an inertial element oscillating in an oscillation plane thanks to an elastic return element.
  • the exhaust comprises a pin rigidly linked to the inertial element, an anchor and an escape wheel.
  • the anchor comprises a fork configured to cooperate with the peg, an input pallet and an output pallet, each of the pallets being configured to cooperate with the teeth of the escape wheel.
  • the escapement is configured so that, during a release phase, the peg pushes the fork in order to release the escape wheel from one of the pallets and, during an impulse phase, the fork pushes the peg in order to transmitting to the inertial element the torque of the escape wheel which is in contact with one of the pallets.
  • the regulator is configured so that the release phase is preceded by a first frictional rest phase, itself preceded by a first free oscillation phase, and the pulse phase is followed by a second frictional rest phase. , itself followed by a second phase of free oscillation.
  • the inertial element oscillates freely without contact between the pin and the fork; and during the first and second frictional rest phase, the pin is in contact with the fork so as to push it, a tooth of the escape wheel being in frictional contact with one of the pallets.
  • the escapement is at rest rubbing during a given portion of oscillation, but is free outside this portion of oscillation.
  • the oscillation portions in frictional rest make it possible to guarantee the self-starting of the oscillator because, thanks to them, it is possible to build a fork-peg mechanism with a very low angle of lift as well as reasonable games and safeties.
  • the lift angle can be at least twice as small as what is attainable with the escapements proposed in the state of the art, ie typically between 2° and 6°.
  • the escapement thus makes it possible to recover the self-starting property of the oscillator, even in the case where the operating amplitude of the oscillator is low and its rigidity high.
  • the regulator according to the invention also allows a portion of oscillation of the inertial element to be largely free and there is therefore no frictional contact between the escape wheel and the lever during a large part of the oscillation of the inertial element. This makes it possible to minimize the energy loss of the regulator and therefore to obtain a higher amplitude of the inertial element. This makes it possible to guarantee the isochronism of a flexible-guided oscillator (for most flexible-guided oscillators and escapements, isochronism faults are generally critical below 10° of amplitude) and makes the element inertial less disturbed by shocks against stops.
  • the regulator described here can be applied to any type of escapement whose wheel and lever form a double impulse escapement.
  • the principle can easily be applied in the case of a free lever escapement.
  • the regulator proposed here greatly simplifies the design of the oscillator compared to the solution proposed in the document CH714361 .
  • the anchor of the present invention does not need a dart to cooperate with such an oscillator.
  • the anchor and the wheel can therefore be parts produced on one level.
  • the regulator described here is simple in its implementation and makes it possible to ensure low energy consumption and the self-starting of an oscillator on flexible guidance.
  • the escapement 10 comprises an escapement wheel 11 provided with teeth 112 configured to cooperate with an entry pallet 121 and an exit pallet 127 of an anchor 12.
  • the anchor 12 pivotally mounted on an axis, comprises a fork 122 cooperating with an impulse cam 130 (here a pin) of a plate 131.
  • the escapement 10 cooperates with an oscillator (not shown) comprising an inertial element 21 (for example a pendulum or other) capable of oscillating around of an oscillator axis 23 thanks to an elastic return element.
  • the plate 131 is intended to cooperate with the oscillator.
  • the plate 131 can be arranged concentric with the oscillator so as to pivot with an inertial element, as in a conventional clockwork regulator mechanism.
  • FIG 4a shows a detail of the input palette 121
  • the figure 4b shows a detail of the output pallet 127
  • the figure 4c shows a detail of a tooth 112 comprising a tooth nose 112a and a tooth heel 112b.
  • Each of the input pallet 121 and the output pallet 127 is provided with a pallet rubbing rest plane P RF , a pallet release plane P DE , and a pallet impulse plane P IM .
  • the pallet release plane P DE corresponds to a rest plane, that is to say, the plane on which a tooth 112 of the escape wheel presses at the time of its release.
  • the P IM vane impulse plane has three sections with variable curvature, continuous and tangent.
  • the vane impulse plane P IM can also be formed from a single or multiple curved or planar sections.
  • the vane rubbing rest plane P RF and the vane clearance plane P DE are also shown as two continuous sections of different curvatures but these two planes could also be realized as a single flat surface.
  • the pallet rubbing rest plane P RF is pull-type and the pallet release plane P DE may or may not be pull-type.
  • the pallets 121, 127 of the anchor 12 of the escapement 10 therefore comprise an additional resting plane, the pallet rubbing resting plane P RF , configured to block the escapement wheel 11 during the rubbing rests of the escapement .
  • THE figures 5a and 5b show a diagram reporting different angles of oscillation of an inertial element of an oscillator on flexible guide cooperating with the escapement 10, when the oscillator oscillates counterclockwise ( figure 5a ) and schedule ( figure 5b ).
  • the exhaust 10 has two different operating regimes.
  • the escapement 10 functions as an escapement at rest rubbing, that is to say that the amplitude of oscillation of the inertial element is greater than the half-angle of lift ⁇ LE /2 and less than half -friction angle of repose ⁇ RF /2.
  • the angle of lift ⁇ LE corresponds to the portion of oscillation of the inertial element from the start angular position of release ⁇ DE to the end angular position of the pulse ⁇ IM .
  • the angle of frictional rest ⁇ RF corresponds to the portion of oscillation from the angular position of the inertial element from the start of the first frictional rest ⁇ RF1 to the end angular position of the second frictional rest ⁇ RF2 .
  • the oscillator At greater amplitude of oscillation of the inertial element, greater than the half-angle of rest rubbing at ⁇ RF /2, the oscillator also has a portion of free oscillation (angle of free oscillation ⁇ LI ).
  • THE figures 6 to 15 show the escapement 10 during the different phases of its operation.
  • the diagram of the figure 5 is also reproduced: the angle of oscillator 2 corresponding to the phase illustrated is indicated there by an arrow.
  • a drop or fork clearance compensation
  • a drop occurs as a transition between two escapement operating phases and is not considered as an escapement phase.
  • the fall is added in the construction of the escapement in order to avoid the blocking of the mechanism which would be caused by a double contact between two escapement parts (safeties of the escapement).
  • the chute is dimensioned according to the assembly and manufacturing tolerances of the system. It must be minimized because it causes a loss of energy that does not contribute to the accuracy of the system's time base.
  • FIG. 6 shows the escapement 10 at the start of a first phase of rubbing rest, when the oscillator oscillates in the anti-clockwise direction.
  • the first phase of frictional rest occurs following a first phase of free oscillation during which the inertial element 21 oscillates freely without contact between the pin 130 and the fork 122 .
  • the first phase of rubbing rest occurs before a release phase of the escapement 10.
  • the escapement wheel 11 is blocked by the anchor 12 and cannot move forward.
  • the pin 130 (for example arranged coaxial with an axis of the inertial element) rotates counter-clockwise and meets a fork first plane 122a of the fork 122.
  • the anchor 12 then pivots clockwise (around its pivot axis 126). Under the action of pin 130 on fork 122, pallet 121 will cause escape wheel 11 to move back slightly. A tooth 112 of the escape wheel is in frictional contact on the frictional rest plane of the pallet P RF of the input palette 121.
  • lever 12 rotates while escape wheel 11 is almost stationary. There is therefore a frictional contact between a tooth 112 and the input pallet 121 (on the pallet frictional rest plane P RF ) of the anchor 12.
  • the inertial element oscillates from the angular position of the start of the first rubbing rest ⁇ RF1 to the angular position of the start of disengagement ⁇ DE .
  • FIG. 7 shows the escapement 10 at the start of a release phase, corresponding to the end of the first rubbing rest.
  • the balance pin 130 continues to rotate counter-clockwise and to push on the first fork plane 122a of the fork 122.
  • the escapement wheel 11 is stationary, or recoils slightly, and the anchor 12 continues to turn clockwise.
  • a tooth 112 of the escape wheel 11 leaves the pallet rubbing rest plane P RF to join the pallet release plane P DE of the input pallet 121.
  • the angular position of the inertial element is that of start of release ⁇ DE .
  • FIG 8 shows the escapement 10 at the start of the backlash adjustment of the fork 122 occurring at the end of the release phase.
  • the beginning of the backlash of the fork 122 is identical to that of a classic lever escapement.
  • Pin 130 continues to rotate counter-clockwise.
  • a tooth 112 of the escape wheel 11 leaves the pallet clearance plane P DE to join the pallet impulse plane P IM of the entry pallet 121.
  • the escape wheel 11 will then actuate the anchor 12 which will allow the second plane of the fork 122b to catch up with the pin 130 and strike it at the end of the backlash of the fork 122.
  • the elastic return torque of the oscillator must at least be sized to be able to bring back, without momentum, the escapement 10 in the position of the figure 8 . Otherwise the escapement 10 is not self-starting.
  • FIG. 9 shows the escapement 10 at the start of a pulse phase occurring at the end of the first fork drop and corresponds to the start of the input pallet pulse 121.
  • This first pulse phase is identical to that of a classic lever escapement.
  • Pin 130 continues to rotate counter-clockwise.
  • the second fork plane 122b of fork 122 has joined pin 130 and is beginning to push pin 130 counterclockwise.
  • the escapement wheel 11 continues to rotate clockwise and actuates the pin 130 via the lever 12.
  • the tooth nose 112a of the tooth 112 of the escapement wheel 11 pushes on the plane of pallet pulse P IM from the input pallet 121.
  • FIG 10 shows the escapement 10 during the pulse phase, at the transition between the pulse of the tooth nose 112a on the pallet plane and the tooth plane pulse on the pallet nose.
  • Pin 130 continues to rotate counterclockwise and second fork plane 122b continues to push pin 130 counterclockwise.
  • the escape wheel 11 also continues to rotate clockwise and actuates the peg 130 through the anchor 12.
  • FIG. 11 shows escapement 10 during a first drop of escape wheel 11 and a second drop of fork 122 occurring at the end of the impulse phase.
  • This transition is identical to that of a conventional lever escapement for the drop of the escapement wheel 11.
  • pin 130 continues to rotate counterclockwise.
  • the peg 130 leaves the second fork plane 122b because the lever 12 is no longer actuated by the escapement wheel 11.
  • a tooth 112 of the escapement wheel 11 separates from the end of the impulse plane of pallet P IM of the input pallet 121.
  • the escapement wheel 11 drops, that is to say rotates in a vacuum, and will join the rubbing rest plane of the pallet P RF of the output pallet 127.
  • the angular position of the inertial element corresponds approximately to the end of pulse angular position ⁇ IM with respect to the reference position of the line of centers ⁇ 0 (this corresponds to the half-angle of lift ⁇ LE /2).
  • the exhaust 10 is characterized by a lift angle ⁇ LE typically of at most 6°.
  • FIG 12 shows the escapement 10 at the start of a second rubbing rest phase occurring after the impulse phase, at the end of the fall of the escape wheel 11 and of the second fall of the fork 122.
  • This second phase of rubbing rest does not exist in a conventional lever escapement.
  • Pin 130 continues to rotate counter-clockwise, joins first fork plane 122a and pushes fork 122 out.
  • the escape wheel 11 is blocked by the anchor 12 but pivots very slightly clockwise due to the pull.
  • the anchor 12 still pivots clockwise under the action of the pin 130.
  • the tooth beak 112a of the tooth 112 of the escapement wheel 11 will therefore rub against the rubbing rest plane of the pallet P RF of the exit pallet 127. There is therefore a frictional contact between the escapement wheel 11 and the pallet 12 and between the pallet 12 and the peg 130.
  • the expression “frictional contact” means that at the point of contact between the tooth 112 and the frictional resting plane of the paddle P RF and between the pin 130 and the first fork plane 122a, there is a regular relative displacement between these exhaust parts during the first and the second rubbing rest phase.
  • the angular position of the inertial element goes from the angular position of the end of the pulse ⁇ IM to the angular position of the end of the second frictional rest ⁇ RF2 .
  • FIG 13 shows the escapement 10 at the end of the second rubbing rest phase.
  • the peg 130 has finished pushing the first fork plane 122a and is freed from it.
  • the anchor 12 has not yet joined the exit stop 125b, the draw is therefore not finished.
  • a tooth 112 of the escapement wheel 11 rests on the rubbing resting plane of the pallet P RF of the output pallet 127.
  • the escapement wheel 11 transmits a torque to the anchor 12 which allows it to always pivot clockwise to reach the exit stop 125b and its rest position.
  • the angular position of the inertial element is slightly greater than the angular position at the end of the second rubbing rest ⁇ RF2 . Similar to falls, we do not consider, in this document, the draw as a phase of the escapement strictly speaking.
  • FIG 14 shows the escapement 10 during a second phase of free oscillation occurring after the second phase of rubbing rest.
  • the ankle 130 is free and will remain so until the next rubbing rest phase.
  • Fork 122 of anchor 12 has joined exit stop 125b.
  • the escape wheel 11 is blocked by the anchor 12 and both are stationary.
  • Contact between pin 130 and fork 122 occurs during the second phase of frictional rest.
  • the angular position of the inertial element is greater than the angular position at the end of the second frictional rest ⁇ RF2 .
  • FIG. 15 shows the escapement 10 at the start of the first rubbing rest phase, when the oscillator oscillates clockwise.
  • This phase does not exist in a classic lever escapement.
  • Pin 130 which rotates clockwise, meets second fork plane 122b of anchor 12, which is about to rotate counter-clockwise. In this position, if the system were stopped, it is the elastic torque of the oscillator which would cause the escapement 10 to rotate.
  • the escapement wheel 11 is blocked by the lever 12 and cannot move forward.
  • the lever 12 rotates, under the action of the pin 130 on the second fork plane 122b of the fork 122, the escapement wheel 11 will move back slightly, pushed back by the rubbing rest plane of the pallet P RF of the output pallet 127.
  • the inertial element pivots from the angular position of the start of the first frictional rest ⁇ RF1 to the angular position of the start of disengagement ⁇ DE .
  • Pin 130 is therefore configured to push fork 122 during the first frictional rest phase and the second frictional rest phase. During these phases, a tooth 112 of the escapement wheel 11 is in frictional contact against the frictional rest plane of the pallet P RF of the input pallet 121 or of the output pallet 127. The pin 130 is not in contact with the fork 122 on the free oscillation portions of the inertial element, preceding the first frictional rest phase and following the second frictional rest phase.
  • the self-starting of the escapement 10 does not depend on the angle of rest rubbing ⁇ RF but only on the angle of lift ⁇ LE .
  • the proposed escapement considerably facilitates the self-starting of the oscillator.
  • the presence of the first phase of rubbing rest and of the first phase of free oscillation makes it possible to characterize the escapement 10 as a semi-free escapement.
  • the escapement 10 is also self-starting.
  • the escapement 10 can be configured so that the frictional rest angle ⁇ RF , corresponding to the portion of oscillation from the angular position of the inertial element from the start of the first frictional rest ⁇ RF1 to the end angular position of the second rubbing rest ⁇ RF2 , ie at most 12°.
  • the escapement must be configured so that the pin 130 is in contact with the fork 122 so as to push it when the angular position of the inertial element with respect to the line of centers ⁇ 0 is smaller than the half-angle of rest rubbing ⁇ RF /2 and greater than the half-angle of lift ⁇ LE /2. More particularly, the first fork plane 122a and the second fork plane 122b must be dimensioned so that they can be engaged with the pin 130 in this angular range.
  • the escapement 10 When oscillator 2 starts up or in operation at amplitudes less than or equal to the half-angle of friction rest ⁇ RF /2, the escapement 10 functions as a friction rest escapement. In this mode, the anti-rollover devices are useless since the pin does not leave the fork. If the escapement 10 can push the inertial element 21 to the limit of the half-angle of lift ⁇ LE /2 (corresponding to the angular position of end of pulse ⁇ IM ), then the system is self-starting.
  • the kinematics of the escapement 10 at the start of the oscillator or in operation at amplitudes less than or equal to a half-angle of rest rubbing at ⁇ RF /2 is illustrated in figures 16a-16c when the oscillator swings clockwise and at figures 16d to 16f when the oscillator swings counterclockwise.
  • a tooth 112 bears against the anchor output rest plane 127a of the output pallet 127.
  • the second fork plane 122b of the fork 122 is in contact with the pin 130 and follows the inertial element 21 in its swing. If the oscillation is large enough, then the escapement wheel 11 outlines a slight movement due to the pulling of the anchor exit rest plane 127a.
  • the inertial element 21 has entered the lift angle ⁇ LE and has completed the disengagement.
  • the fork has caught up and is pushing peg 130 with the fork foreground.
  • Tooth 112 provides its impulse to output pallet 127, via anchor output impulse plane 127b.
  • the inertial element 21 reaches the limit of the lift angle ⁇ LE .
  • another tooth 112' drops onto the anchor entry rest 121a of the entry pallet 121.
  • the pin 130 still engaged in the fork 122, carrying the latter with it.
  • THE figures 16d-16f illustrate the same phases as the figures 16a-16c , respectively.
  • a tooth 112 comes into contact with the anchor entry rest plane 121a of the entry pallet 121 ( figures 16a and 16b ).
  • the inertial element 21 and the anchor 12 rotate in the opposite direction to the direction illustrated in figures 16a-16c .
  • the balance 21 reaches the limit of the angle of lift ⁇ LE ( figure 16f )
  • another tooth 112' falls on the anchor exit rest plane 127a of the exit pallet 127.
  • the fork-pin mechanism of the escapement 10 must be equipped with sufficient securities and safeties to prevent the escapement from being brought into a blocking position.
  • the securities and sureties in question are distances between the pin 130 and the fork 122 in particular positions of the exhaust 10 and must be dimensioned according to the inaccuracies of manufacture and assembly of the exhaust parts.
  • FIG 17a illustrates the play E and the penetration P of the peg 130 into the fork 122 in a position of start of impulse (corresponds to the position of the escapement at the figure 9 ).
  • the play E serves to prevent the ankle from getting stuck in the fork and the penetration P to ensure that the second plane of the fork 122b pushes the ankle during the impulse.
  • FIG 17b illustrates the free movement D of the ankle 130 in the fork 122 in a position at the end of the second rubbing rest (corresponds to the position of the figure 13 , to the nearest draw).
  • the release action D serves to guarantee that the peg 130 can come out of the fork 122. It is these three distances (E, P and D) which become too small when constructing a traditional free lever escapement (without rest rubbing) for lift angles less than approximately 10°.
  • the pin 130 comes out of the fork 122.
  • the anchor 12 is then at rest, resting against the entry stop 125a ( picture 18a ) or the exit stop 125b ( figure 18b ), and escape wheel 11 remains stationary.
  • the escapement 10 must then include a device preventing overturning, that is to say preventing the rocking of the lever 12 which would cause the plate pin 130 to meet the lug 123.
  • a device preventing the overturning may comprise a stinger 124 and/or a pair of horns 123.
  • THE figures 19a-19f illustrate different positions of the fork 122 and of a tooth 112 with respect to the pallets 121, 127, for amplitudes of oscillation of the inertial element 21 beyond the half-angle of rest rubbing ⁇ RF /2.
  • the inertial element 21 freely traverses its additional arc. Thanks to the pulling of the tooth 112 on the pallet rubbing rest plane P RF of the output pallet 127, the fork 122 is wedged against the output stop 125b or against any other limiting device.
  • the rest position is such that on the return of the inertial element 21, the pin 130 enters freely into the fork 122.
  • the dart 124 has entered the notch 132a of the small plate 132.
  • the dart 124 is inactive and unable to retain the anchor 12. It is then the horn 123, blocked by the pin 130, which prevents overturning in the event of an impact.
  • the tooth beak 112a of the tooth 112 is still engaged on the rubbing rest plane of the pallet P RF of the output pallet 127. Once the shock has passed, the anchor 12 returns to its equilibrium position thanks to the pull.
  • the escapement 10 according to the invention can be made of silicon using the usual etching techniques.
  • This material has many advantages: it does not undergo fatigue failure, is non-magnetic and has no plastic domain.
  • silicon makes it possible to manufacture parts in series with high machining precision, while offering great design freedom.
  • the exhaust 10 can be made of a material selected from the group of materials comprising a ceramic, a glass, an alloy or a metallic glass.
  • the material selected may include silicon nitride, silicon carbide, steel, gold or one of its alloys, nickel, nickel-phosphorus, brass, steel, an amorphous alloy , a copper alloy, copper-beryllium, or nickel silver.
  • the escapement 10 can be configured so that the angle of rest rubbing ⁇ RF is at most 12°, and the lugs 123 can prevent any overturning of the anchor up to an amplitude of 36°, thus the anchor 12 may not include dart 124. It is then possible to manufacture anchor 12 on a single level, that is to say that anchor 12 may be included in a single plane, without dart 124 fixed at a level above (or below) the level of the anchor 12 and the fork 122.
  • the regulator 1 described here is particularly suitable for an oscillator 2 on flexible guidance.
  • An example of integration of the escapement 10 with a CR3 type oscillator as described in the patent EP3299905B1 by the present applicant is illustrated in figure 20 .
  • There figure 21 shows a detail of the escapement 10.
  • the pin 130 which interacts with the anchor 12, as well as the stops 125a, 125b, are directly integrated into the inertial element 21 of the oscillator 2.
  • the oscillator 2 comprises an elastic return element comprising a flexible pivot comprising flexible blades 22.
  • the flexible pivot 22 performs both the role of elastic return and of guiding in rotation of the inertial element 21.
  • the flexible pivot 22 is of one side fixed to a plate (not shown) and the other linked to the inertial element 21.
  • Oscillator 2 typically has 20° amplitude.
  • the horns 123 can prevent any overturning of the anchor 12 up to an amplitude of 36°, so a dart is unnecessary in this example.
  • the frictional angle of repose ⁇ RF is about 10° and the lift angle ⁇ LE is about 5°.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Vibration Dampers (AREA)
  • Micromachines (AREA)
  • Piezo-Electric Or Mechanical Vibrators, Or Delay Or Filter Circuits (AREA)
EP21200709.0A 2021-10-04 2021-10-04 Mechanische einstellvorrichtung für uhr mit selbstanlaufendem, halb freistehendem hemmungsmechanismus mit geringem anstellwinkel Pending EP4160323A1 (de)

Priority Applications (2)

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EP21200709.0A EP4160323A1 (de) 2021-10-04 2021-10-04 Mechanische einstellvorrichtung für uhr mit selbstanlaufendem, halb freistehendem hemmungsmechanismus mit geringem anstellwinkel
US17/937,808 US12429820B2 (en) 2021-10-04 2022-10-04 Mechanical regulator for horology comprising a semi-detached self-starting escapement with low lift angle

Applications Claiming Priority (1)

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EP21200709.0A EP4160323A1 (de) 2021-10-04 2021-10-04 Mechanische einstellvorrichtung für uhr mit selbstanlaufendem, halb freistehendem hemmungsmechanismus mit geringem anstellwinkel

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Publication number Priority date Publication date Assignee Title
EP4383012B1 (de) * 2022-12-08 2026-07-08 ETA SA Manufacture Horlogère Suisse Selbstaufrichtendes profil für uhrhemmung

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EP3035126A1 (de) 2014-12-18 2016-06-22 The Swatch Group Research and Development Ltd. Resonator einer Uhr mit sich kreuzenden Blättern
CH714361A2 (fr) 2017-11-22 2019-05-31 Eta Sa Mft Horlogere Suisse Résonateur rotatif à guidage flexible entretenu par un échappement libre à ancre.
EP3545365A1 (de) 2016-11-23 2019-10-02 ETA SA Manufacture Horlogère Suisse Rotierender resonator mit flexiblem führungssystem auf basis einer abgelösten ankerhemmung
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
CH715589A1 (fr) 2018-11-27 2020-05-29 Lvmh Swiss Mft Sa Echappement à repos frottant.

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CH702930A2 (fr) * 2010-04-01 2011-10-14 Patek Philippe Sa Geneve Echappement d'horlogerie à protection contre les chocs.
JP5485859B2 (ja) * 2010-11-17 2014-05-07 セイコーインスツル株式会社 アンクル脱進機及びこれを備えた機械式時計
CH706532B1 (fr) * 2012-11-26 2013-11-29 Detra Sa Zi Echappement à ancre pour pièce d'horlogerie.
CH713144A1 (fr) * 2016-11-17 2018-05-31 Richemont Int Sa Échappement pour pièce d'horlogerie.
US11409245B2 (en) * 2018-11-08 2022-08-09 Eta Sa Manufacture Horlogere Suisse Anti shock protection for a resonator mechanism with a rotary flexure bearing

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EP3035126A1 (de) 2014-12-18 2016-06-22 The Swatch Group Research and Development Ltd. Resonator einer Uhr mit sich kreuzenden Blättern
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
EP3545365A1 (de) 2016-11-23 2019-10-02 ETA SA Manufacture Horlogère Suisse Rotierender resonator mit flexiblem führungssystem auf basis einer abgelösten ankerhemmung
CH714361A2 (fr) 2017-11-22 2019-05-31 Eta Sa Mft Horlogere Suisse Résonateur rotatif à guidage flexible entretenu par un échappement libre à ancre.
CH715589A1 (fr) 2018-11-27 2020-05-29 Lvmh Swiss Mft Sa Echappement à repos frottant.

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US20230106693A1 (en) 2023-04-06

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