EP3739394A1 - Agencement à manivelle destiné à entraîner un oscillateur mécanique - Google Patents

Agencement à manivelle destiné à entraîner un oscillateur mécanique Download PDF

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Publication number
EP3739394A1
EP3739394A1 EP19174824.3A EP19174824A EP3739394A1 EP 3739394 A1 EP3739394 A1 EP 3739394A1 EP 19174824 A EP19174824 A EP 19174824A EP 3739394 A1 EP3739394 A1 EP 3739394A1
Authority
EP
European Patent Office
Prior art keywords
crank
pin
driving
slot
drive
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.)
Withdrawn
Application number
EP19174824.3A
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German (de)
English (en)
Inventor
Romain Gillet
Simon Henein
Billy NUSSBAUMER
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.)
Ecole Polytechnique Federale de Lausanne EPFL
Original Assignee
Ecole Polytechnique Federale de Lausanne EPFL
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 Ecole Polytechnique Federale de Lausanne EPFL filed Critical Ecole Polytechnique Federale de Lausanne EPFL
Priority to EP19174824.3A priority Critical patent/EP3739394A1/fr
Publication of EP3739394A1 publication Critical patent/EP3739394A1/fr
Withdrawn legal-status Critical Current

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    • 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
    • G04B17/30—Rotating governors, e.g. centrifugal governors, fan governors
    • 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
    • G04B15/02—Escapements permanently in contact with the regulating mechanism
    • 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

Definitions

  • the present invention relates to the technical field of mechanical oscillators. More particularly, it relates to a crank arrangement for continuously driving mechanical oscillators such as horological oscillators.
  • crank-driven oscillators have previously been explored in the prior art.
  • US1222757 describes a conical pendulum driven by an eccentric crank arm arranged proximate to the pendulum's point of suspension, the rotational movement of the pendulum governing the angular velocity of the driving crank arm.
  • FR359117 describes a similar but inverted arrangement in which the edge of an arm driven rotationally by the movement exerts a force on the tip of the pendulum bob to drive it in a substantially circular path.
  • CH5564 describes a similar arrangement, in which the lever comprises a slit in which the tip of the pendulum bob is situated. In each of these cases, the lever or arm drives the pendulum, and its movement governs the speed at which the driving lever can rotate about its axis of rotation.
  • crank-driven oscillator is described in US1595169 .
  • an inertial mass supported by three flexible blades is driven in a (quasi-) circular path by means of a simple eccentric pin and connecting rod crank, itself driven by a spring motor.
  • FR1044957 describes a simple crank-driven balance wheel, in which a rod is connected by eccentrically-arranged pins to both a disk driven by a spring motor and to the balance wheel such that rotation of the disk causes a back-and-forth oscillation of the balance wheel about its axis of rotation.
  • This oscillation of the balance wheel serves as a governor to limit the angular velocity of the disk and thereby to regulate the speed of the movement.
  • US9465363 describes an oscillator system comprising four coupled oscillators, each comprising an inertial mass supported by a flexure pivot which also provides the restoring force for each oscillator.
  • the four oscillators are arranged in a rotationally-symmetrical configuration with their respective axes of rotation parallel to each other, and they are each connected to a central driving ring by means of a respective rigid lever and a long, flexible blade.
  • driving the ring by means of a crank in a circular or oval pathway situated in a plane perpendicular to the axes of rotation, the individual oscillators are caused to oscillate back and forth. As before, this oscillation regulates the angular velocity at which the crank can turn.
  • WO 2015/104692 and WO 2015/104693 describe a number of variants of two-degree-of-freedom oscillators, both acting in a single plane or in rotation.
  • the oscillator comprises a driving pin which penetrates into a radial slot formed in a crank arm (see for instance figure 26 of WO 2015/104692 or figure 13 of WO 2015/104693 ).
  • the pin In order to be self-starting without requiring the oscillator to be deliberately perturbed e.g. by acting directly thereupon or by shaking the timepiece, and indeed to prevent the crank from rotating uncontrollably, the pin must be prevented from being in a position in which it is substantially coaxial with the axis of rotation of the crank when the oscillator is at rest.
  • the obvious solution to this problem would be to provide an elastic stop at or near the proximal extremity of the slot, for instance as shown in the arrangement illustrated in figures 7a and 7b .
  • the former of these figures is an isometric view of such a crank arrangement 101, and the latter is an isometric cutaway view illustrating also the pin 103 in contact with the elastic stop 110.
  • the slot 108 is formed between two plates 112 screwed to a spacer 114 which holds the plates 112 parallel and a predetermined distance apart.
  • the spacer 114 is integral with an interface element 116 arranged to be mounted on an arbor (not illustrated) such that the crank arrangement 101 can rotate about an axis of rotation 118, the slot 108 extending radially with respect to the axis 118.
  • the elastic stop 110 is formed here as a cantilevered blade spring extending along the axis of rotation 118 when in its neutral position, although different positions are possible, particularly one biased towards the distal end of the working-side of the slot 108, and different blade orientations are possible.
  • the elastic stop 110 can be formed by e.g. an elastomeric or rubber insert or similar.
  • the cantilevered blade spring can be arranged such that the pin can momentarily pass through a position in which it is coaxial with the axis of rotation of the crank.
  • the spring is arranged to restore the pin to a position which is eccentric with respect to the axis of rotation of the crank, on the correct working side thereof such that, when the oscillator is re-started, the pin can travel along the slot 108 and the crank cannot "free-wheel", i.e. rotate freely without being influenced by the oscillator when staying at the kinematic singularity (i.e. with the pin coaxial with crank rotation axis).
  • the pin can momentarily be coaxial with the axis of rotation of the crank, it cannot remain in such a position due to the action of the spring.
  • the spring absorbs shocks and prevents the pin from stopping in the singular central position.
  • the spring locates the resting position of the pin at a position which is very close to the rotation axis of the crank, which makes the self-starting energy of the system very low, hence increasing the chances self-starting of the system when driving torque is restored after the system has been stopped.
  • self-starting happens when the driving torque is greater than friction torque of the pin-crank interface, the friction torque being at a minimum when the pin is the closest to the rotation axis of the crank.
  • An object of the present invention is hence to at least partially overcome the above-mentioned drawbacks of the prior art.
  • the invention relates to a crank arrangement for driving a pin-driven mechanical oscillator having two degrees of freedom in either rotation or in translation, as defined in claim 1.
  • Such an oscillator typically comprises an inertial mass displaceable against a restoring force supplied by elastic elements such as springs, arranged such that it the inertial mass can oscillate with two degrees of freedom in translation or in rotation.
  • This crank arrangement comprises a crank element arranged to be rotationally driven about an axis of rotation by means of a mechanical source of energy such as a spring motor housed in a barrel, the crank element comprising a crank slot adapted to receive a driving pin arranged to cause the inertial mass of said oscillator to oscillate in response to rotation of said crank element under the torque provided by the mechanical source of energy.
  • the pin can for instance be fixed directly or indirectly on said inertial mass, or on an element connected thereto.
  • the crank slot comprises a driving section at least partially delimited by a drive surface and by a guide surface situated opposite at least part of the drive surface. Both of these surfaces can be straight or curved (concave or convex), and said drive surface is arranged to drive said pin in response to rotation of said crank element. In the case in which the drive surface is straight, it can extend parallel to a radial direction of said crank element considered with respect to the axis of rotation.
  • crank slot further comprises a return section adjoining said driving section, said return section being delimited by:
  • This crank slot is furthermore shaped such that said axis of rotation is situated in said return section at a distance of less than one radius of said drive pin from said braking surface, that is to say considered at the closest point of the braking surface to the axis of rotation.
  • the pin rides up the angled braking surface and is decelerated gently rather than impacting the end of the slot as in a conventional linear crank slot construction.
  • the axis of the pin is prevented from ever being coincident with the axis of rotation of the crank arrangement, and hence freewheeling of the crank arrangement cannot occur, and the oscillator can self-start from a stopped condition.
  • the angle of the braking surface with respect to the drive surface ensures that the pin, at rest, is situated towards the drive section, making self-starting more likely.
  • the angle of the return surface with respect to the braking surface contributes to returning the pin to the drive surface in case of a shock causing it to enter into the return section.
  • said obtuse interior angle between the drive and braking surfaces is between 120° and 180°, preferably between 150° and 170°
  • said nonzero acute angle interior angle between the abutment and return surfaces is between 0° (i.e. the surfaces are parallel) and 10°, preferably between 2° and 5°
  • said braking surface comprises a curved portion adjoining said drive surface.
  • This curved portion may be a radius which is tangential to the drive surface and to the rest of the braking surface, or any other convenient curved form. This minimises the impact of the pin on the braking surface when it enters into contact therewith in case of shock or sudden stopping of the movement.
  • said curved portion has a radius of curvature greater than the driving pin radius Rp.
  • a circular fillet with radius at least 10% greater than the driving pin radius can be used, ideally around 10% to 20% greater.
  • said return surface meets said guiding surface at a point directly opposite said drive surface, i.e. at a point which intersects a normal to the drive surface.
  • the guiding surface is shorter than the drive surface.
  • said slot is configured such that, under normal operation, said pin remains out of contact with an end surface joining said drive surface to said guiding surface. This prevents the pin being forced to the end of the driving section of the slot at its maximum kinetic energy, which would cause it to be over-driven such that it would rotate at a frequency greater than the natural frequency of the oscillator.
  • crank slot is configured such that, under the greatest anticipated shock in use, said pin remains out of contact with an end surface joining said braking surface to said return surface. The pin is hence prevented from causing impact damage to said end surface.
  • said guiding surface is substantially parallel to said drive surface so as to best guide the pin bilaterally during normal operation.
  • This crank arrangement can of course be incorporated in a timepiece movement so as to drive a two degree of freedom oscillator by means of a driving pin connected directly or indirectly with said oscillator.
  • This movement can be incorporated in a timepiece such as a wristwatch, pocket watch, clock or similar.
  • FIGS 1a and 1b illustrate a nonlimiting embodiment of a crank arrangement 1 according to the invention, together with a driving pin 3 illustrated in isolation.
  • Figure 2 illustrates a timepiece movement 23 in which this crank arrangement 1 is integrated, the movement 23 also comprising a source of mechanical energy M such as a spring motor kinematically linked to the crank arrangement 1 by a gear train 17 (represented schematically by a dotted arrow), which also drives indicator means 25 as is generally known.
  • a source of mechanical energy M such as a spring motor kinematically linked to the crank arrangement 1 by a gear train 17 (represented schematically by a dotted arrow), which also drives indicator means 25 as is generally known.
  • the driving pin 3 is arranged to be driven by the crank arrangement 1, and to this end is fixed directly or indirectly to a part of an oscillator 5 in order to drive the latter in oscillation according to two degrees of freedom in translation and/or rotation.
  • Oscillator 5 has been illustrated analogously to that of figure 26 of WO 2015/104692 or figure 13 of WO 2015/104693 , and hence comprises an inertial mass 5a which carries the pin 3 and which is attached to a frame 6 by means of springs.
  • These springs may for instance be formed as a flexure pivot arrangement (or any other convenient spring arrangement) which provides a restoring force and guides the inertial mass 5a such that it can translate along two perpendicular axes of displacement.
  • the other embodiments of oscillators disclosed in these documents, or equally in EP3339969 can also be applied here, irrespective of whether they relate to translational or rotational inertial masses with two degrees of freedom in rotation or translation.
  • the inertial mass constitutes at least 75%, preferably 90%, further preferably 95% of the inertia of the oscillator.
  • the oscillator 5 may be of the type described in US9465363 , the pin being fixed into the central driving ring by any appropriate means.
  • the crank arrangement 1 of the present invention can be used with any known two degree of freedom crank-driven oscillator, and is not limited to those mentioned above.
  • the crank arrangement 1 comprises a slotted crank element 7 and an interface element 9.
  • the crank element 7 is provided with a crank slot 8 arranged to receive the drive pin 3 such that this latter can slide therein, and the interface element 9 is arranged to support the crank element 7 and to interface with the remainder of the movement 23.
  • the interface element 9 comprises an axial opening 11 arranged to be fixed to an arbor 13 e.g. by force fitting, bonding, welding, pinning, riveting or similar, this arbor 13 defining an axis of rotation 19 and having a gear wheel 15 fixed thereupon by similar means, as is generally known.
  • the interface element 9 furthermore comprises three arms 9a designed to support the crank element 7, this latter being clipped into the interface element 9 between the three arms 9a, and held in place by a lug 7a elastically connected to the remainder of the crank element 7 by a pair of blade springs 7b integrally-formed therewith. These blade springs 7b urge the lug 7a to press against the arms 9a, and thereby causing a significant friction force fixing the crank element 7 into the interface element 9.
  • crank element 7 is made of a brittle material (i.e. one which does not undergo plastic deformation before breaking) such as silicon, silicon oxide, silicon nitride, silicon carbide, alumina (ruby, sapphire, corundum etc.), diamond-like carbon, glasses, ceramics, glass-ceramics, brittle steel alloys, certain metallic glasses or similar.
  • a brittle material i.e. one which does not undergo plastic deformation before breaking
  • These materials may be monocrystalline, polycrystalline, nanocrystalline, microcrystalline or amorphous as appropriate for the material(s) in question, and can be micromachined by means of processes such as LIGA, sintering in a mould, masking and etching from a wafer or plate of material by wet (chemical) or dry (DRIE, plasma, laser, reactive ion, etc.) etching techniques as appropriate for the given material.
  • the interface element can be formed by e.g. multilayer micromachining techniques, 3D printing (e.g. selective laser melting, selective laser sintering or similar), conventional machining from solid metal or similar.
  • crank element 7 can simply be force fitted, welded, soldered, glued, pinned, riveted or similar to the interface element, without use of a detente arrangement.
  • crank arrangement 1 can be monobloc, being formed by conventional machining from solid or by multi-layer micromachining techniques.
  • crank element 7 can be chosen at will, and can be e.g. circular, polygonal, or any desired shape.
  • crank arrangement 1 can be supported by any convenient known bearing arrangement 21 (illustrated schematically) such that it can rotate about its axis of rotation 11.
  • crank slot 8 The core of the present invention lies in the particular form of the crank slot 8, and it should be noted that although the crank slot 8 traverses the entire thickness of the crank element 7, this is not obligatory, particularly (but not exclusively) in the case in which the entire crank arrangement 1 is formed as a single piece.
  • Figure 3 illustrates in detail the shape of the crank slot 8, the driving pin 3 being shown at 3 different positions indicated as positions A, B and C which will be described below.
  • the crank element 7 is arranged to be driven in the counter-clockwise direction, as indicated by the arrow D.
  • crank slot 8 Since the crank slot 8 is delimited by its sidewalls, these will be described in sequence, with reference to the axis of rotation 19 as datum point.
  • crank slot 8 comprises a drive surface 8a which extends parallel to a radius R, at a distance r therefrom which substantially corresponds to the radius R p of the driving pin 3.
  • the drive surface 8a can in principle be arranged at a distance greater than or less than R p from the radius R, at which point the axis of the pin 3 will travel along a direction parallel to radius R when it is in contact with the drive surface 8a.
  • the drive surface 8a can be curved in a convex or concave manner.
  • the sidewall After the distal extremity of the drive surface 8a, the sidewall curves around to form an end surface 8b of the slot 8 on the driving side thereof, and hence defines a stop.
  • the maximum distance from the centre of rotation that the axis of the pin 3 can have is indicated on figure 3 as L 1 .
  • the length L 1 should be chosen such that when the maximum elastic potential energy of the oscillator 5 during normal operation is attained (maximum distance of the pin 3 from the centre), the pin 3 does not contact the end surface 8b.
  • the sidewall surface 8c which is situated opposite the drive surface 8a and parallel thereto is a guiding surface and defines, together with the portion of the drive surface 8a immediately opposite thereto, a parallel section of the slot 8.
  • This surface 8c is situated a distance r + L 6 from the radius R, where L 6 is the working play enabling the pin 3 to slide in the parallel section of the slot 8.
  • the pin 3 would not come into contact with surface 8c.
  • the motion is jittery and minor shocks often occur.
  • the pin 3 constantly rebounds between the sidewalls of the parallel section. While the pin 3 is between positions B and C, therefore, it is bilaterally guided by the slot 8.
  • the distance L 5 is that between the centre of rotation 19 and the axis of the pin 3 when it is in contact with the drive surface 8a at the very start of the parallel section (position B), i.e. where the axis of the pin 3 is directly opposite the vertex q which delimits the start of guiding surface 8c.
  • this surface be substantially parallel to drive surface 8a, this is not obligatory, and it could alternatively be situated at an angle thereto and/or be curved in a convex or concave manner.
  • the pin 3 would have more play in the slot 8 towards the axis of rotation 19 than towards the braking surface 8b, and hence the bilateral guidance of the pin would be worse at lower oscillator energies.
  • the term "parallel section" would naturally be inappropriate, and can be generalised as a "bilaterally guided section".
  • drive surface 8a stops short of the point at which the axis of the pin 3 would otherwise be coincident with the axis of rotation 19, in order to prevent the crank arrangement 1 from being able to turn without also acting on the pin 3. This also permits the system to self-start once a driving couple is reapplied to the crank arrangement 1.
  • the point p on an braking surface 8d which is closest to the axis of rotation 19 i.e. the point on the surface 8d at which the normal to said surface intersects the axis of rotation 19
  • the point p on an braking surface 8d which is closest to the axis of rotation 19 is situated at a distance of less than the radius R p of the pin 3 therefrom.
  • braking surface 8d extends from the proximal extremity of the drive surface 8a with its straight portion at an acute angle ⁇ to the extension thereof, such that the interior angle between the surfaces 8a and 8d is obtuse when viewed from inside the slot 8.
  • the junction between these two surfaces 8a, 8d is ideally formed as a radius which is tangential to both surface 8a and to the remainder of surface 8d, in order to provide a smooth transition between the two and to minimise shocks, but this is not obligatory, and other forms of transition are possible.
  • the majority of the length of the braking surface 8d, aside from the radiused portion immediately adjacent to the drive surface 8a is planar, it can also be curved, in which case angle ⁇ is considered at every tangent to the braking surface 8d. Furthermore, in the case in which the drive surface 8a is curved, ⁇ is considered with respect to a tangent to the drive surface 8a where it meets the radius defining the start of the braking surface 8d.
  • the pin 3 As the pin 3 rides along braking surface 8d, the acute angle ⁇ of this latter with respect to the plane of the drive surface 8a will cause the pin to 3 to decelerate angularly with respect to the crank arrangement 1 until such time that it has slowed sufficiently that the rotation of the crank arrangement 1 starts to "overtake” the pin. At this point, the pin 3 then leaves the braking surface 8d and crosses to the return surface 8e, which is situated opposite the braking surface 8d and which adjoins the guiding surface 8c at a reflex interior angle thereto (considered with respect to the interior of the slot 8 and clearly visible on the figures at point q), once the return surface 8e has "caught up” with the pin 3. This vertex can be radiused or otherwise curved if desired.
  • the return surface 8e is straight and is at a zero or nonzero acute angle ⁇ to the braking surface 8d, this angle being preferably situated between 0° and 10°, further preferably between 2° and 5°.
  • the portion 8f of the sidewall of the slot 8 which joins braking surface 8d and return surface 8e forms the end surface of the return portion of the slot 8.
  • the end surface 8f of the return portion also forms an abutment.
  • its axis (indicated with a "+" symbol) is at a distance L 4 from the centre of rotation 19.
  • L 1 and L 4 can be the same or different.
  • the pin 3 In the case of the movement suddenly being stopped, the pin 3 will travel down the parallel section of the slot 8, impact the braking surface 8d, and ride along this surface, attaining a distance which is a function of the kinetic energy of the oscillator 5. The pin 3 will then oscillate within the slot 8 either side of the centre of rotation 19 at least partly in contact with the braking surface 8d and the drive surface 8a, until such time as all of the kinetic energy of the oscillator has been expended. When this has occurred, the pin 3 ends up at rest at position A, which represents the state of minimum stored elastic energy of the oscillator 5. In this position, the axis of the pin 3 is situated at a distance L 0 from the axis of rotation 19.
  • the slot 8 is hence divided into a driving section and a return section, delimited on figure 4 by means of the line A-A which intersects on the one hand the vertex between surfaces 8c and 8e, and on the other hand the end of the drive surface 8a.
  • the driving section is hence delimited by line A-A and surfaces 8a, 8b and 8c, the pin 3 being situated in this section during normal operation.
  • This section incorporates not only the parallel section which bilaterally guides the pin 3, but also the triangular section between the parallel section and the line A-A in which the pin 3 is unilaterally guided, and when the axis of the pin 3 is in this section, it can be driven by the crank arrangement 1.
  • the return section is contiguous with the driving section and is delimited by line A-A and surfaces 8d, 8e and 8f. This section serves to return the pin 3 to the driving section in case of stopping and restarting the movement, or in case of a shock in a direction which causes the pin 3 to enter into the return section.
  • Figures 5 and 6 illustrate concrete examples which have been experimentally tested.
  • the pin 3 has a diameter of 398 ⁇ m (i.e. R p is 199 ⁇ m), and a maximum amplitude of 1.23mm.
  • the values of L 0 to L 6 , ⁇ , ⁇ and the working play of the pin 3 in the parallel section of the slot 8 are indicated in the table below:
  • Dimension Figure 5 Figure 6 L 0 24 ⁇ m 50 ⁇ m L 1 1.23 mm 1.23 mm L 2 80 ⁇ m 160 ⁇ m L 3 8 ⁇ m 17 ⁇ m L 4 1.23 mm 1.23 mm L 5 430 ⁇ m 528 ⁇ m L 6 15 ⁇ m 15 ⁇ m ⁇ 19.5° 19.5° ⁇ 3.5° 3.5°
  • crank arrangement functions not only with translational oscillators, in which the axis of the driving pin 3 remains parallel to the axis of rotation 19 of the crank arrangement, but also to rotational oscillators such as those disclosed in EP3339969 .
  • the axis of the pin inclines slightly with respect to the axis of rotation 19, this inclination being compensated for by means of appropriate tolerancing of the slot 8, particularly insofar as it concerns the dimension L 6 , which is the working play in the parallel section.

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  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
EP19174824.3A 2019-05-16 2019-05-16 Agencement à manivelle destiné à entraîner un oscillateur mécanique Withdrawn EP3739394A1 (fr)

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EP19174824.3A EP3739394A1 (fr) 2019-05-16 2019-05-16 Agencement à manivelle destiné à entraîner un oscillateur mécanique

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Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR359117A (fr) 1905-11-04 1906-03-16 Thomas Haller A. G. Commande pour balanciers coniques d'horloges ou tous autres genres de mouvements
US1222757A (en) 1915-11-08 1917-04-17 Ferdinand Gundorph Pendulum-escapement.
US1595169A (en) 1924-04-28 1926-08-10 Schieferstein Georg Heinrich Means for producing curve-shaped oscillations
FR1044957A (fr) 1951-11-09 1953-11-23 Mécanisme d'échappement silencieux pour mouvement d'horlogerie
WO2015104693A2 (fr) 2014-01-13 2015-07-16 Ecole Polytechnique Federale De Lausanne (Epfl) Oscillateur harmonique isotrope en général à deux degrés de liberté et base de temps associée sans échappement ou avec un échappement simplifié
WO2015104692A2 (fr) 2014-01-13 2015-07-16 Ecole Polytechnique Federale De Lausanne (Epfl) Oscillateur harmonique isotrope a direction x et y et base de temps associe sans echappement ou a echappement simplifie
WO2016037726A1 (fr) * 2014-09-09 2016-03-17 The Swatch Group Research And Development Ltd Résonateur combiné à isochronisme amélioré
US9465363B2 (en) 2015-02-03 2016-10-11 Eta Sa Manufacture Horlogere Suisse Timepiece oscillator mechanism
CH713056A2 (fr) * 2016-10-18 2018-04-30 Eta Sa Mft Horlogere Suisse Mouvement mécanique d'horlogerie avec résonateur à deux degrés de liberté avec mécanisme d'entretien par galet roulant sur une piste.
EP3339969A1 (fr) 2016-12-20 2018-06-27 Ecole Polytechnique Fédérale de Lausanne (EPFL) Oscillateur mécanique

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR359117A (fr) 1905-11-04 1906-03-16 Thomas Haller A. G. Commande pour balanciers coniques d'horloges ou tous autres genres de mouvements
US1222757A (en) 1915-11-08 1917-04-17 Ferdinand Gundorph Pendulum-escapement.
US1595169A (en) 1924-04-28 1926-08-10 Schieferstein Georg Heinrich Means for producing curve-shaped oscillations
FR1044957A (fr) 1951-11-09 1953-11-23 Mécanisme d'échappement silencieux pour mouvement d'horlogerie
WO2015104693A2 (fr) 2014-01-13 2015-07-16 Ecole Polytechnique Federale De Lausanne (Epfl) Oscillateur harmonique isotrope en général à deux degrés de liberté et base de temps associée sans échappement ou avec un échappement simplifié
WO2015104692A2 (fr) 2014-01-13 2015-07-16 Ecole Polytechnique Federale De Lausanne (Epfl) Oscillateur harmonique isotrope a direction x et y et base de temps associe sans echappement ou a echappement simplifie
WO2016037726A1 (fr) * 2014-09-09 2016-03-17 The Swatch Group Research And Development Ltd Résonateur combiné à isochronisme amélioré
US9465363B2 (en) 2015-02-03 2016-10-11 Eta Sa Manufacture Horlogere Suisse Timepiece oscillator mechanism
CH713056A2 (fr) * 2016-10-18 2018-04-30 Eta Sa Mft Horlogere Suisse Mouvement mécanique d'horlogerie avec résonateur à deux degrés de liberté avec mécanisme d'entretien par galet roulant sur une piste.
EP3339969A1 (fr) 2016-12-20 2018-06-27 Ecole Polytechnique Fédérale de Lausanne (EPFL) Oscillateur mécanique

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