EP3722888B1 - Mechanischer oszillator mit abstimmbarem isochronismusmangel - Google Patents

Mechanischer oszillator mit abstimmbarem isochronismusmangel Download PDF

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EP3722888B1
EP3722888B1 EP19168095.8A EP19168095A EP3722888B1 EP 3722888 B1 EP3722888 B1 EP 3722888B1 EP 19168095 A EP19168095 A EP 19168095A EP 3722888 B1 EP3722888 B1 EP 3722888B1
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Prior art keywords
inertial mass
slider
mechanical oscillator
compensation spring
oscillator
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French (fr)
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EP3722888A1 (de
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Mohammad Hussein Kahrobaiyan
Mohamed Zanaty
Simon Henein
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ETA SA Manufacture Horlogere Suisse
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Ecole Polytechnique Federale de Lausanne EPFL
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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
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/26—Compensation of mechanisms for stabilising frequency for the effect of variations of the impulses
    • 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

Definitions

  • the present invention relates to the technical field of mechanical oscillators. More particularly, it relates to one degree of freedom mechanical oscillators with tuneable isochronism.
  • the most common horological mechanical oscillators comprise an inertial mass, such as a balance, arranged to oscillate about a neutral position under the effect of a restoring force provided by an elastic element such as a hairspring.
  • the oscillations are typically maintained by means of a conventional escapement mechanism powered by a mainspring kinematically connected to an escapement wheel by means of a suitable gear train.
  • fusée The classical solution to isochronism defect is the so-called "fusée” mechanism (see e.g. EP2735919 ), in which variations of the torque of the mainspring are compensated by a chain mechanism arranged such that its output torque is maintained constant as the mainspring unwinds. Since the excitation forces to which the oscillator is subjected do not vary, the amplitude of oscillation remains substantially constant.
  • fusée mechanisms are bulky and complex, and have hence found limited application in wristwatches.
  • An aim of the present invention is hence to propose oscillators for which the isochronism can be tuned, and thereby to at least partially overcome the drawbacks of the prior art.
  • the invention relates to a mechanical oscillator for a timepiece (such as a wristwatch), as defined in claim 1.
  • This oscillator comprises an inertial mass arranged to oscillate about a neutral position under the effect of a restoring force provided by at least one elastic element, which may be e.g. a conventional hairspring, a flexure pivot system which also serves to support the inertial mass, or any other known configuration.
  • This oscillation can be rectilinear along an axis of translation, or rotational around an axis of rotation.
  • the oscillator further comprises a compensation spring pivotably linked to said inertial mass by means of a substantially rigid first connecting bar so as to apply a compensating force to said inertial mass in such a manner that said compensating force varies in function of displacement of said inertial mass from its neutral position.
  • the first connecting bar is hence directly or indirectly attached pivotably at one end to the compensation spring and at its other end to the inertial mass.
  • the restoring force can be provided by any convenient type of elastic element such as a spring, or a flexure pivot also designed to support and guide the inertial mass. All pivot points can either be conventional pivots or defined by suitable flexures.
  • said compensation spring is attached to a slider arranged to translate along a respective axis, said slider being pivotally linked to said substantially rigid bar.
  • This axis is ideally substantially parallel to the line of action of the first connecting bar when the inertial mass is in its neutral position.
  • At least a part of the force applied by the compensating spring acts on the second order term of spring stiffness (i.e. the x 2 or ⁇ 2 term, depending on whether the oscillator is translational or rotational) without influencing the first order term (i.e. the x or ⁇ term).
  • the linear stiffness of the elastic element can be left unchanged and hence the nominal frequency of oscillation remains unchanged, whereas the nonlinear regime can be modified so as to be able to compensate for nonideal changes in the stiffness of the spring as the inertial mass moves away from its neutral position.
  • the x 2 or ⁇ 2 term can be manipulated such that the effective stiffness of the overall restoring force applied to the inertial mass (i.e. that applied as the sum of forces acting thereupon as restoring forces, irrespective of whether they come from the elastic element or the compensation spring) is substantially linear over its full working range.
  • the isochronism of the oscillator can be tuned, and the isochronism defect which is usually caused by nonlinearity of the elastic restoring force of the elastic element can be reduced and even eliminated.
  • the first connecting bar is ideally arranged such that its line of action is substantially perpendicular to said axis of translation when said inertial mass is in its neutral position. Since the bar can take any shape between its pivot points without affecting its function, its line of action is referred to here, which is defined as an axis passing through its two pivot points.
  • the first connecting bar is arranged such that its line of action is aligned with the axis of rotation when the inertial mass is in its neutral position. This ensures that the action of the compensation spring is symmetrical about the neutral position of the inertial mass.
  • the compensating force applied by the compensation spring can be arranged to either decrease or increase respectively with increasing displacement of the inertial mass.
  • the overall compensating force is considered, i.e. the force parallel to the line of action of the first connecting bar. If the compensation spring is in tension when the inertial mass is in its neutral position, the force will increase with increasing displacement, compensating for an elastic element which softens, and if the compensation spring is in compression, the force will decrease with increasing displacement, compensating for an elastic element which hardens. As the inertial mass displaces, the component of the compensating force acting in the same direction as the restoring force hence changes in function of the geometry of the system and the arrangement of the compensation spring.
  • said compensation spring is arranged such that its pre-stress (i.e. its tension or compression when the inertial mass is in its neutral position) is adjustable, which eliminates any need to precisely determine the stiffness of the compensation spring at the point of manufacture since the effective zero-order (linear) stiffness of the oscillator (and hence the nominal frequency of oscillation) can be adjusted.
  • This can be achieved in a particularly simple way by attaching the compensation spring between the aforementioned slider and a further slider arranged such that it can be moved so as to stretch or compress the compensation spring, e.g. with a screw or cam system or similar.
  • the mechanical oscillator can comprise a further compensation spring pivotally linked to said slider by a substantially rigid second connecting bar pivotally attached to said slider such that its line of action is substantially perpendicular to that of said first connecting bar when the inertial mass is in its neutral position (and hence the oscillator is in its neutral state), said further compensation spring being arranged to apply a further compensating force to said slider which varies in function of the displacement of said slider from its neutral position.
  • a further compensation spring pivotally linked to said slider by a substantially rigid second connecting bar pivotally attached to said slider such that its line of action is substantially perpendicular to that of said first connecting bar when the inertial mass is in its neutral position (and hence the oscillator is in its neutral state)
  • said further compensation spring being arranged to apply a further compensating force to said slider which varies in function of the displacement of said slider from its neutral position.
  • the pre-stress of the compensation spring affects both the nominal frequency and the isochronism (i.e. the second-order stiffness), whereas the pre-stress of the further compensation spring affects only the second-order stiffness and hence the isochronism.
  • said elastic element may be constructed as a flexure pivot arranged to support and to guide said inertial mass in translation or in rotation, as the case may be.
  • the compensation spring and further compensation spring, if present
  • the entire oscillator can be constructed as a flexure pivot system.
  • any of the mechanical oscillators as defined above can be incorporated into a timepiece movement further comprising a crank arrangement or an escapement arranged to case the inertial mass to oscillate under the effect of energy supplied by a motor such as a mainspring.
  • the term "flexible” should be understood as meaning that an element is intended to undergo a deformation in use which has an impact on its function, this deformation being in at least one particular direction.
  • "Rigid” should be understood as meaning that an element does not undergo a deformation which affects its function.
  • Flexible elements may be flexible in one direction and “rigid” in another, as is the case with blade and col flexures. Of course, small undesired deformations of rigid elements (and of flexible elements in a direction in which they are rigid) cannot be excluded, but they are so small as to be trivial and can be ignored.
  • rigid elements are at least 100 times as stiff, preferably at least 1000 times as stiff, as “flexible” elements, considered in the direction in which they are flexible. The skilled person fully understands this principle, and it need not be described at length below.
  • oscillators with which the present invention is concerned are one degree-of-freedom (DOF) harmonic oscillators, and can be either linear oscillators as illustrated schematically in figure 1 , or rotational oscillators as illustrated in figure 2 . In each of these figures, the oscillator 1 is illustrated in its neutral state
  • the oscillator 1 comprises an inertial mass 3 which is arranged to oscillate about a neutral position under the effect of a restoring force provided by at least one elastic element 5 attached at one of its ends to a substantially rigid framework 7, and at its other end to the inertial mass 3.
  • Extra masses can be present out of the plane of the system as illustrated, and the inertial mass 3 defines at least 75%, preferably at least 90%, of the oscillating inertia of the oscillator 1.
  • the inertial mass is guided in translation by means of a suitable bearing arrangement 9 such as rollers, sliding friction bearings, or a flexure mechanism (see for instance The Art of Flexure Mechanism Design, Simon Henein, Lennart Rubbert, Florent Cosandier, Murielle Richard, EPFL Press, 2017 ).
  • a suitable bearing arrangement 9 such as rollers, sliding friction bearings, or a flexure mechanism (see for instance The Art of Flexure Mechanism Design, Simon Henein, Lennart Rubbert, Florent Cosandier, Murielle Richard, EPFL Press, 2017 ).
  • Such arrangements are generally considered to be equivalent, and have simply been represented schematically by rollers.
  • the bearings illustrated have only one degree of freedom, and in the context of figure 1 the inertial mass 1 is constrained to move only in the x direction.
  • the inertial mass 3 is a balance of any convenient form, mounted so as to be able to rotate about an axis of rotation O.
  • This latter may be defined by a physical axis (e.g. an arbor), or may be a virtual axis defined by a flexure mechanism, such as a Remote Centre Compliance (RCC) pivot or similar.
  • RRC Remote Centre Compliance
  • the flexures which support the mass 3 and define its axis of rotation O may also provide the restoring force for oscillations, and hence also constitute the at least one elastic element 5.
  • FR1044957 describes a very simple arrangement which can be applied easily to either a rotationally-oscillating or rectilinearly-oscillating inertial mass 3, as indeed is illustrated schematically on figure 10 (see below).
  • the isochronism of an oscillator is optimised when its frequency is independent of amplitude.
  • mechanical harmonic oscillators should obey Hooke's Law, meaning that their elastic element should have as linear a restoring force or torque (as appropriate) as possible with respect to the amplitude of oscillations.
  • the stiffness of the elastic element should be constant with respect to the amplitude of oscillations.
  • the effective inertia also should be constant with respect to the amplitude of oscillations in order to achieve a constant frequency.
  • k k 0 + k 2 ⁇ 2 + O ⁇ 4
  • k 0 the zero-order, i.e. linear, coefficient of stiffness
  • k 2 the second-order coefficient of stiffness which varies with amplitude ⁇ (whether expressed in linear or angular displacement, according to the type of oscillator)
  • O ( ) term is fourth order so considered negligible.
  • Figure 3 illustrates qualitatively the effect of variations of the value of k 2 , which is dependent on the changes of the geometry of the elastic element 5 as the inertial mass 3 oscillates.
  • the rotational case can be derived simply by substituting J for m , and expressing displacement ⁇ as an angle ⁇ rather than as linear displacement x.
  • K 1 2 ⁇ ⁇ 2 m 0 + m 2 ⁇ 2 + O ⁇ 4
  • V 1 2 ⁇ 2 k 0 + 1 2 k 2 ⁇ 2 + O ⁇ 4 .
  • the isochronism defect can be estimated by examining how the oscillator's frequency varies as its total energy (i.e. the sum of K + V at any given moment) varies, since this is a proxy for oscillator amplitude due to conservation of energy.
  • ⁇ 86400 ⁇ ⁇ ⁇ n ⁇ n , where ⁇ is the frequency of oscillations and ⁇ n is the nominal frequency of oscillations, i.e., the frequency of oscillations at a nominal amplitude ⁇ n .
  • E % 100 E ⁇ E n E n .
  • the principle of the present invention revolves around mechanisms which cause ⁇ to vary, thereby acting on the value k 2 of the term k 2 ⁇ 2 of equation (1). In doing so, the nonlinearity of the elastic element 5 can be compensated for without modifying the linear stiffness unless desired, and hence without modifying the nominal frequency of oscillation of the oscillator 1 unless desired.
  • a practical way of acting on the value of m 2 of the term m 2 ⁇ 2 of equation (2) has not been achieved, hence the problem of compensating for this source of isochronism defect remains open for the moment.
  • FIG 4 illustrates a first embodiment of an oscillator 1 according to the invention.
  • This oscillator 1 is translational, similar to that illustrated in figure 1 , and only the differences with this latter figure will be described in the following.
  • the inertial mass 3 is constrained by an appropriate guide arrangement 9 so as to move along a rectilinear axis, here deemed to be the x axis, under the effect of the elastic element 5, whose linear stiffness is referred to as k 5 (i.e. the zero-order stiffness) in the following text.
  • the oscillator 1 further comprises a compensation spring 11 with zero-order stiffness k 11 , attached at one end to a frame element 7, and at its other end to a slider 13 which is arranged to translate along an axis y , which is perpendicular to the axis x , guided by a suitable bearing 9, again illustrated schematically by rollers, representing a sliding bearing.
  • this bearing 9 can also be a flexure mechanism giving the slider 13 substantially one degree of freedom in translation parallel to the y direction.
  • Slider 13 is deemed to have negligible mass.
  • Axis y intersects the centre of mass of inertial mass 3 when this latter is in a neutral position, as illustrated, and the slider 13 is attached to the inertial mass 3 by means of a substantially rigid first connecting bar 15 with effective length L , pivoted on each of these elements by means of either a conventional pinned pivot (as illustrated) or by a flexure pivot such as a col, a blade spring or equivalent.
  • Effective length L is measured between the respective pivot points, and its line of action is along an axis joining its pivot points, irrespective of the actual shape of the bar.
  • the compensation spring 11 applies a compensating force to the inertial mass 3, whose component parallel to the x axis varies as a function of the length L and the stiffness of compensation spring 11, and the displacement x of inertial mass along the x axis.
  • the effective stiffness k comprises a component deriving from the stiffness of spring 5 and from the compensation spring 11, this latter only acting upon the x 2 term in such a situation, leaving the linear term (and hence the nominal frequency of oscillation) unchanged.
  • Figure 5 illustrates a second embodiment of an oscillator 1 according to the invention, which applies the same arrangement of slider 13 and compensation spring 11 as that of figure 4 , but in the context of a rotational hairspring-balance oscillator.
  • inertial mass 3 is arranged to oscillate about an axis of rotation O
  • the substantially rigid first coupling bar 15 is pivotally attached to said mass 3 at a location which is eccentric with respect to the axis of rotation O.
  • the oscillator 1 is in its neutral position (as illustrated)
  • the line of action of the substantially rigid bar 15 intersects the axis of rotation of the inertial mass 3; in other words, the axis of rotation O and the two pivot points of the bar 15 are aligned along the same axis.
  • Figure 6 illustrates an embodiment similar to that of figure 4 , in which the nominal stiffness is tuneable rather than simply being set by the fixed value of k 5 .
  • the nominal value of k 11 would have to be changed in order to tune the frequency of oscillation.
  • the nominal stiffness k to which the inertial mass 3 is subjected can be modified without changing the zero-order stiffness k 5 of the spring 5 itself, and hence the nominal frequency of the oscillator 1 can be modified.
  • Figure 7 shows the same principle applied to a rotational oscillator 1.
  • the length L 1 is the distance from the pivot point of the inertial mass 3 (which is highly schematically represented) with respect to the frame 7 to its pivot point with respect to connecting bar 15, and L 2 is the effective length of the connecting bar 15 between its two pivot points.
  • Figure 8 illustrates an oscillator 1 which combines the principles of both figure 4 and figure 6 .
  • the compensation spring 11 is arranged so as to supply not only a compensating force which varies by virtue of Hooke's Law, but also the constant force p mentioned above by means of pre-stressing compensation spring 11.
  • one extremity of compression spring is attached to the slider 13 as in figure 4 , and its other extremity is attached to a further slider 17 which is arranged to be displaceable by a distance d from a position in which the compensation spring 11 is not stretched or compressed when the bar 15 is parallel to the y axis, guided by a suitable bearing 9.
  • This pre-stress generates the constant force p, and the overall force applied is the sum of the pre-stress and the variations in stress due to Hooke's Law as the spring 11 changes length.
  • the force applied by compensation spring 11 hence varies as the slider 13 displaces.
  • the displacement d of further slider 17 can be arranged by means of an appropriate arrangement such as a screw, a cam or similar (not illustrated).
  • Figure 9 illustrates a further embodiment of an oscillator 1 according to the invention which is based upon that of figure 8 , and in which both the nominal frequency and the isochronism can be adjusted.
  • this oscillator 1 also comprises a substantially rigid second connecting bar 19 pivotally connected to slider 13 perpendicular to the first bar 15 when the system is in a neutral position.
  • This bar 19 is also pivotally connected to a further slider 21, and has an effective length L 2 between its pivot points. Again, slider 21 is guided by an appropriate bearing 9.
  • a further compensation spring 23 with linear spring constant k 23 links slider 21 with a yet further slider 25 in a manner analogous to the compensation spring 11. Again, slider 25 is guided by a suitable bearing 9. This spring 23 is preloaded by moving slider 25 by a distance d 1 from a position in which the spring 23 is not stressed when the system is in the neutral position illustrated. In this figure, d 0 corresponds to d in figure 8 . As a result, further compensation spring 23 acts in respect of compensation spring 11 in the same manner that this latter acts in respect of elastic element 5. In other words, the spring stiffness component of further compensating spring 23 acts to compensate the second-order stiffness term of compensation spring 11, and its pre-stress due to displacement d 1 acts to modify the effective zero-order stiffness to which the slider 13 is subjected.
  • adjusting d 0 acts upon both the nominal stiffness and the second-order stiffness
  • adjusting d 1 acts only upon the second-order stiffness and hence only upon the isochronism without affecting nominal frequency.
  • d 0 can be adjusted to set the nominal frequency
  • d 1 can be set to correct the isochronism without affecting the nominal frequency.
  • d 0 is simply zero in the above equation.
  • figure 10 illustrates an entirely flexure-based realisation of the oscillator 1 of figure 9 .
  • the simpler embodiments of the earlier figures can be constructed in a similar manner by eliminating the elements not present therein, such as the second connecting rod 19, sliders 21 and 25, and spring 23, and even slider 17 if the force of the compensation spring 11 is preset.
  • Spring 5 is integrated with the corresponding bearing 9 and is constructed as a parallelogram flexure pivot comprising a pair of functionally-parallel elongated bars 5a terminated by blade flexures or cols 5b (which are equivalent), attached at one end each to framework 7, and at the opposite end each to inertial mass 3. It should be noted that the exact shape of the bars 5a is unimportant, so long as the pivot functions as a parallelogram flexure pivot. For small displacements of the inertial mass 3 that substantially obey the small angle approximation (i.e.
  • the movement of the inertial mass 3 is substantially rectilinear along the x direction, for which its stiffness k 5 in the x direction can be defined as is generally known.
  • the bar-and-blade flexures can be replaced with simple blade flexures.
  • Substantially rigid bar 15 is also constructed as an elongated bar with a blade or col flexure at each end, its effective length L 1 being measured between the effective pivot points, which are generally considered as being at the midpoints of the flexures. Since many of the flexure pivots used correspond to the type used for bar 15, there is no need to re-describe them exhaustively each time.
  • Slider 13 is constrained to move substantially only parallel to the y axis by a flexure pivot bearing 9 comprising a single flexure pivot of the same bar-and-blade/col type as rigid bar 15.
  • this bearing 9 can be a single blade flexure or a parallelogram flexure pivot of the type 5, 9 constraining the inertial mass 3 or comprising a pair of simple blade flexures.
  • Such a parallelogram flexure pivot may be constructed of simple blade flexures or bar-and-blade/col type flexures.
  • Compensation spring 11 is formed as a single, simple blade flexure, and further slider 17 is guided by a pair of functionally-parallel blade flexures 9b forming its bearing 9, although only a single flexure is necessary.
  • These flexures can each be replaced by an equivalent flexure of the bar and blades/cols type (i.e. of the types used for guiding the inertial mass 3 and the slider 13 in the construction of figure 10 ).
  • Second connecting bar 19 is likewise formed as a substantially rigid bar terminating at each end in a blade flexure or col, and has an effective length L 2 again defined between the effective pivot points as for the connecting bar 15.
  • Slider 21 is again connected to slider 25 via a spring 23 comprising a pair of functionally-parallel blade flexures 23a, although again only one is required, and alternative forms are possible as described above, such as bar-and-blade/col flexures.
  • slider 25 is again joined to framework 7 by yet another pair of functionally-parallel blade flexures 25a forming a parallelogram flexure pivot. Again, the same comments apply.
  • the oscillator 1 of this embodiment functions in the same manner as that of figure 9 , displacements d 0 and d 1 applied to sliders 17 and 25 acting as before.
  • Figure 11 illustrates a variant of the oscillator 1 of figure 10 , incorporating a rotary inertial mass 3 similar to that of figures 2 , 5 and 7 instead of a translational mass 3. Only the differences with respect to figure 10 will be described in the following.
  • Inertial mass 3 is formed as a balance-type rotary mass, supported by a pair of blade flexures 5c arranged at right angles to one another in the plane of the oscillator 1.
  • These blades 5c constitute a Remote Centre Compliance (RCC) flexure pivot, and also provide a restoring force for the oscillations of inertial mass 3.
  • RRC Remote Centre Compliance
  • they constitute both the spring 5 and bearing 9 for the mass 3, and ensure that it can oscillate about its virtual centre of oscillation O.
  • Other forms of flexure pivots are of course possible.
  • Substantially rigid bar 15 is attached by one of its terminal flexures to the mass 3 at a convenient point, this flexure being oriented towards the axis of rotation O when the mass 3 is in a neutral position.
  • the bearing 9 joining the slider 13 to the frame 7 is illustrated as being a parallelogram flexure rather than a single flexure as in figure 10 , as was described as one of the non-illustrated variants for this latter.
  • a conventional escapement 29 has been schematically illustrated, powered by an escape wheel 29a itself driven by a source of energy such as a mainspring.
  • a crank system as illustrated in the context of figure 10 can equally be applied.
  • Figure 12 illustrates graphs plotting return force against displacement of the inertial mass for various values of p for an oscillator dimensioned as explained in [ Zanaty, Mohamed, Ilan Vardi, and Simon Henein. "Programmable multistable mechanisms: Synthesis and modelling.” Journal of Mechanical Design 140.4 (2016): 042301 .]

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Inductance-Capacitance Distribution Constants And Capacitance-Resistance Oscillators (AREA)

Claims (14)

  1. Mechanischer Oszillator (1) für eine Uhr, umfassend eine Trägheitsmasse (3), die derart angeordnet ist, um unter der Wirkung einer durch mindestens ein elastisches Element (5) bereitgestellten Rückstellkraft um eine Neutralstellung zu oszillieren,
    wobei der mechanische Oszillator (1) ferner eine Kompensierungsfeder (11) umfasst, die mit der Trägheitsmasse (3) mittels einer im Wesentlichen starren ersten Verbindungsstange (15) schwenkbar verbunden ist, wobei die Kompensierungsfeder (11) und die erste Verbindungsstange (15) derart angeordnet sind, dass eine Kompensierungskraft auf die Trägheitsmasse (3) aufgebracht wird, die in Abhängigkeit von einer Verschiebung der Trägheitsmasse (3) von ihrer Neutralstellung variiert,
    dadurch gekennzeichnet, dass die Kompensierungsfeder (11) an einem Schieber (13) angebracht ist, der derart angeordnet ist, um translatorisch entlang einer jeweiligen Achse zu bewegen, wobei der Schieber (13) mit der im Wesentlichen starren ersten Verbindungsstange (15) schwenkbar verbunden ist.
  2. Mechanischer Oszillator (1) nach dem vorhergehenden Anspruch, wobei die Trägheitsmasse (3) derart angeordnet ist, dass sie translatorisch entlang einer Translationsachse (x) oszilliert.
  3. Mechanischer Oszillator (1) nach dem vorhergehenden Anspruch, wobei die im Wesentlichen starre erste Verbindungsstange (15) derart angeordnet ist, dass ihre Wirkungslinie im Wesentlichen senkrecht zu der Translationsachse (x) ist, wenn sich die Trägheitsmasse (3) in ihrer Neutralstellung befindet.
  4. Mechanischer Oszillator (1) nach Anspruch 1, wobei die Trägheitsmasse (3) derart angeordnet ist, dass sie rotatorisch um eine Rotationsachse (O) oszilliert.
  5. Mechanischer Oszillator (1) nach dem vorhergehenden Anspruch, wobei die im Wesentlichen starre erste Verbindungsstange (15) derart angeordnet ist, dass ihre Wirkungslinie mit der Rotationsachse (O) ausgerichtet ist, wenn sich die Trägheitsmasse (3) in ihrer Neutralstellung befindet.
  6. Mechanischer Oszillator (1) nach einem der vorhergehenden Ansprüche, wobei die Kompensierungsfeder (11) derart angeordnet ist, dass ihre Vorspannung einstellbar ist.
  7. Mechanischer Oszillator (1) nach Anspruch 6, wobei die Kompensierungsfeder (11) zwischen dem Schieber (13) und einem weiteren Schieber (17) angebracht ist, der beweglich angeordnet ist.
  8. Mechanischer Oszillator (1) nach einem der vorhergehenden Ansprüche, ferner umfassend eine weitere Kompensierungsfeder (23), die mit dem Schieber (13) durch eine im Wesentlichen starre zweite Verbindungsstange (19) schwenkbar verbunden ist, die an dem Schieber (13) derart schwenkbar angebracht ist, dass die Wirkungslinie der zweiten Verbindungsstange (19) im Wesentlichen senkrecht zu der Wirkungslinie der ersten Verbindungsstange (15) ist, wenn sich die Trägheitsmasse (3) in ihrer Neutralstellung befindet, wobei die weitere Kompensierungsfeder (23) derart angeordnet ist, dass sie eine weitere Kompensierungskraft auf den Schieber (13) aufbringt, die in Abhängigkeit von der Verschiebung des Schiebers (13) aus seiner Neutralstellung variiert.
  9. Mechanischer Oszillator (1) nach Anspruch 8, wobei die weitere Kompensierungsfeder (23) derart angeordnet ist, dass ihre Vorspannung einstellbar ist.
  10. Mechanischer Oszillator (1) nach Anspruch 9, wobei die weitere Kompensierungsfeder (23) zwischen einem weiteren Schieber (21) und noch einem weiteren Schieber (25) angebracht ist, wobei der noch weitere Schieber (25) beweglich angeordnet ist.
  11. Mechanischer Oszillator (1) nach einem der vorhergehenden Ansprüche, wobei das elastische Element (5) ein Kreuzfedergelenk ist, das derart angeordnet ist, dass es die Trägheitsmasse (3) lagert und führt.
  12. Mechanischer Oszillator (1) nach einem der vorhergehenden Ansprüche, wobei die Kompensierungsfeder (11) als eine Kreuzfedergelenkanordnung ausgebildet ist.
  13. Mechanischer Oszillator (1) nach einem der Ansprüche 8-10 oder nach einem der Ansprüche 11-12, wenn abhängig von einem der Ansprüche 8-10, wobei die weitere Kompensierungsfeder (23) als Biegegelenkanordnung ausgebildet ist.
  14. Uhrwerk, umfassend einen mechanischen Oszillator (1) nach einem der vorhergehenden Ansprüche und eine Kurbelanordnung (27) oder Hemmung (29), die derart angeordnet ist, um die Trägheitsmasse (3) zum Oszillieren zu bringen.
EP19168095.8A 2019-04-09 2019-04-09 Mechanischer oszillator mit abstimmbarem isochronismusmangel Active EP3722888B1 (de)

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EP3992729A1 (de) * 2020-10-29 2022-05-04 The Swatch Group Research and Development Ltd Flexible führung mit verschiebetisch für einen rotierenden resonatormechanismus, insbesondere eines uhrwerks
EP4016193A1 (de) * 2020-12-18 2022-06-22 Omega SA Resonatormechanismus eines uhrwerks mit flexibler führung, die mit mitteln zur einstellung der steifigkeit ausgestattet ist
EP4273633A1 (de) 2022-05-02 2023-11-08 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Mechanischer oszillator mit isochronismuskorrektur

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FR1044957A (fr) 1951-11-09 1953-11-23 Mécanisme d'échappement silencieux pour mouvement d'horlogerie
CH296060A (fr) 1952-01-31 1954-01-31 Marti Fritz Mécanisme de transmission de force dit à force constante.
ATE389902T1 (de) 2005-06-23 2008-04-15 Suisse Electronique Microtech Uhr
EP2290476B1 (de) 2009-08-18 2014-04-23 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Isochronismuskorrektor für Uhrhemmungsmechanismus und mit einem solchen Korrektor ausgestatteter Hemmungsmechanismus
EP2735919B1 (de) 2012-11-27 2015-07-22 Montres Breguet SA Uhrwerk, das eine Schnecke umfasst
EP3032352A1 (de) 2014-12-09 2016-06-15 LVMH Swiss Manufactures SA Uhrregler, Uhrwerk und Uhr mit solch einem Regler
FR3048790B1 (fr) * 2016-03-14 2018-04-06 Lvmh Swiss Manufactures Sa Mecanisme pour piece d'horlogerie, mouvement horloger et piece d'horlogerie comprenant un tel mecanisme.
US11029649B2 (en) * 2016-03-14 2021-06-08 LVHM Swiss Manufactures SA Device for timepiece, clockwork movement and timepiece comprising such a device
FR3059792B1 (fr) 2016-12-01 2019-05-24 Lvmh Swiss Manufactures Sa Dispositif pour piece d'horlogerie, mouvement horloger et piece d'horlogerie comprenant un tel dispositif

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