Mechanical watch with isochronic position insensitive rotary resonator

Patent metadata

Field	Value
Publication number	US-10126711-B2
Application number	US-201715727837-A
Country	US
Kind code	B2
Filing date	Oct 9, 2017
Priority date	Oct 25, 2016
Publication date	Nov 13, 2018
Grant date	Nov 13, 2018

Abstract

A timepiece resonator mechanism having a central wheel train fixed in rotation around an axis of an input wheel train subjected to a driving torque, arranged to turn continuously, and having a plurality of N inertial elements, each movable in relation to the central wheel train, and restored to the axis by elastic restoring device. The mechanism having device between all the inertial elements that are arranged to maintain all centers of mass of these inertial elements at the same distance from the axis at any time, and the elastic restoring device cause an elastic potential such as: Vtot=(dα0/dt)2·Σj (Mj·Rj2), where: Vtot is the elastic potential, Σj is the sum over the js of the quantity between parentheses, (dα0/dt) is the speed of rotation to be imposed, Rj is the position of the center of mass G of the inertial element j of mass Mj.

First claim

What is claimed is:

1. A resonator mechanism for a timepiece movement having an input wheel train mounted to pivot around an axis of rotation and subjected to a driving torque, and having a central wheel train fixed in rotation to said input wheel train around said axis of rotation and arranged to turn continuously, wherein said resonator mechanism has a plurality of N inertial elements, each being movable in relation to said central wheel train, and restored to said axis of rotation by elastic restoring means belonging to said resonator mechanism, which are arranged to cause a restoring effort on the centre of mass of said inertial element, wherein said resonator mechanism has a rotational symmetry of order N, wherein said resonator mechanism has kinematic linkage means between all said inertial elements that are arranged to maintain at any time the centres of mass of said inertial elements at the same distance from said axis of rotation, and also wherein said elastic restoring means, which are rotational and borne by said resonator mechanism, cause an elastic potential wherein by the following equation:
V= ½·( dα 0 /dt ) 2 ·Σ( MjRj 2 )

where:
V is the elastic potential
Σj is the sum of the quantity between parentheses
(dα 0 /dt) is the speed of rotation to be imposed
Rj is the distance of the axis of rotation from the centre of mass G of said inertial element
Mj is the mass of said inertial element.

2. The resonator mechanism according to claim 1 , wherein said resonator mechanism has a pantograph structure articulated around said axis of rotation having at least all said inertial elements either directly articulated or indirectly articulated with arms, wherein the variants are given the references, around said central wheel train and a secondary central wheel train, which is arranged to pivot around said axis of rotation and wherein together with the central wheel train constitutes a crossed structure.

3. The resonator mechanism according to claim 2 , wherein said crossed structure formed by said central wheel train and said secondary central wheel train has its centre of mass on said axis of rotation.

4. The resonator mechanism according to claim 2 , wherein each member of said pantograph comprises four segments articulated to one another and in relation to a pivot axis formed by a main joint or said axis of rotation, wherein said central wheel train is formed from two first segments in the extension of one another in relation to said main joint, and said secondary central wheel train is formed from two second segments in the extension of one another in relation to said main joint, and wherein said elastic restoring means generate a potential energy V, which is dependent on the angle of deformation β 1 of said pantograph member in accordance with equation:
∂ V (β 1 )/∂β=½·( dα 0 /dt ) 2 ·Σj ( Mj·Rj (β 1 )· R′j (β 1 )),

where:
V(β 1 ) is the potential as a function of angle β 1 ,
β 1 is the opening angle of the pantograph, i.e. the angle between, on the one hand, the straight line that joins the point of the pantograph opposite the pivot axis to the pivot axis and, on the other hand, the segment in question,
dα 0 /dt is the speed of rotation of said rotary resonator mechanism,
Σj is the sum over the js of the quantity between parentheses,
Mj is the mass of the inertial element of row j
Rj(β 1 ) is the distance of the axis of rotation to the centre of mass Gj of the inertial element,
R′j(β 1 ) is the derivative of the distance between the pivot axis and the centre of mass of the inertial element in relation to β 1 .

5. The resonator mechanism according to claim 2 , wherein said pantograph structure has a symmetry around said axis of rotation or having a symmetry of rotation of order around said axis of rotation.

6. The resonator mechanism according to claim 2 , wherein all said inertial elements are articulated directly to said central wheel train and said secondary central wheel train.

7. The resonator mechanism according to claim 2 , wherein the centre of mass of each of said arms, which is contained between two articulations, is located on a straight line joining the two articulations on either side of said arm in question.

8. The resonator mechanism according to claim 7 , wherein each member of said pantograph comprises four segments of equal length and together form a regular rhombus, and wherein the potential energy V tot of said elastic restoring means is linked to their angle of deformation by the equation:
V tot (β1)= L ( M 3 ·R 3 +M 4 ·R 4 )·( dα 0 /dt ) 2 ·cos 2β 1

where:
β 1 is the opening angle of the pantograph, which is the angle between the straight line that joins the point of the pantograph opposite the pivot axis to the pivot axis, on the one hand, and the segment in question, on the other hand,
L is the length of each segment between the articulations,
M 3 is the mass of a third segment forming one of the two inertial elements opposite the pivot axis formed by a main joint or by said axis of rotation and contained between a first lateral joint and an apex joint opposite an axis joint forming said main joint,
M 4 is the mass of a fourth segment forming the other of the two inertial elements opposite said pivot axis and contained between a second lateral joint and said apex joint,
R 3 is the distance of the first lateral joint from the centre of mass G 3 of said third segment,
R 4 is the distance of the second lateral joint from the centre of mass G 4 of said fourth segment,
dα 0 /dt is the speed of rotation of the rotary resonator.

9. The resonator mechanism according to claim 2 , wherein each member of said pantograph comprises four segments of equal length and together form a regular rhombus.

10. The resonator mechanism according to claim 2 , wherein said central wheel train and said secondary central wheel train are each fixed to said input wheel train by an elastic connection.

11. The resonator mechanism according to claim 10 , wherein said elastic connection is a flexible rotary guide arrangement having two elastic blades.

12. The resonator mechanism according to claim 2 , wherein each said inertial element is guided directly or indirectly with arms or secondary articulated systems in relation to the pantograph structure by at least one guide means, and wherein at least one of the guide elements and at least one of said elastic restoring means are joined together by a flexible guide means.

13. The resonator mechanism according to claim 12 , wherein except for guide arrangements at the level of said axis of rotation, all the guide arrangements in rotation and elastic restoring means belonging to said resonator mechanism are formed by flexible guide means.

14. The resonator mechanism according to claim 12 , wherein at least one said flexible guide means has at least two elastic blades contained in planes that together define the virtual axis of rotation of a flexible rotary guide arrangement.

15. The resonator mechanism according to claim 14 , wherein at least one said flexible rotary guide arrangement between two components is a guide arrangement with crossed blades projecting on a projection plane, the opening angle θ of which, read on the projection plane between the intersection axis C of the projections of said blades on said plane and the anchorage points of the blades on one of the components, has a value of 40°+/−4°, and the blades cross at a proportion of length of 0.15+/−0.015.

16. The resonator mechanism according to claim 12 , wherein said flexible guide means are made from oxidi

Assignees

• Eta Sa Mft Horlogere Suisse
• Eta Sa Mft Horlogere Suisse

Inventors

• Winkler Pascal
• Helfer Jean-Luc
• Di Domenico Gianni

Classifications

• G04B17/30

  Rotating governors, e.g. centrifugal governors, fan governors (for striking mechanism G04B21/06 {; electrically driven G04C3/0335}) · CPC title

• G04B17/28 Primary

  for the effect of imbalance of the weights, e.g. tourbillon · CPC title

• G04B21/06

  Details of striking mechanisms, e.g. hammer, fan governor {(escapements in general G04B15/00; mechanisms for stabilising frequency G04B17/00; resistance regulators G05D13/00; mechanical toys A63H)} · CPC title

• G04B17/32

  Component parts or constructional details, e.g. collet, stud {, virole or piton} · CPC title

• G04B17/04 Primary

  Oscillators acting by spring tension · CPC title