EP2141555A1 - Coupled resonators for timepiece - Google Patents

Abstract

The resonator (1) has a low frequency resonator (2) coupled with a high frequency resonator (3). The low and high frequency resonators have inertia masses associated with balance springs (5, 7), respectively. Another balance spring (8) is arranged between the inertia masses to couple the low frequency and high frequency resonators. The inertia masses are respectively formed by balances (4, 6). The resonators are placed coaxially inside a timepiece.

Description

The present invention relates to a timepiece resonator resulting from the coupling of a first low frequency resonator with a second resonator at a higher frequency.

A resonator as defined above has been described in the document EP 1 843 227 A1 . In this presentation, the first low-frequency resonator is a balance-spring and the second high-frequency resonator is a tuning fork. A branch of the tuning fork is directly connected to the outer turn of the hairspring to form the coupling between the two resonators. The purpose of this arrangement is to stabilize the frequency of operation of the timepiece and make this frequency more independent of external stresses to ultimately improve the running accuracy of the same room. In the arrangement described the natural frequency of the first resonator is a few hertz, that of the second resonator being of the order of kHz. The idea is to enslave a first resonator very sensitive to external disturbances to a second resonator which, because of its high operating frequency, is much less sensitive to said disturbances. This enslavement will result in an improvement in the performance of the first resonator as for its impact resistance for example, this first resonator cooperating with a conventional exhaust system.

The embodiment that has just been described, however, uses two resonators very different from each other which we can think that the coupling and adjustment will present difficulties, certainly not insurmountable, but still large enough in view of the low inertia of the high frequency resonator and therefore its ability to influence the operation of the first low frequency resonator.

As a result of what has just been described, it is possible to regulate the operation of a first low-frequency resonator using a balance spring by means of a second resonator with a higher frequency also using a balance-spring. it will be possible to stabilize up to a certain point the operating frequency of the timepiece and this by implementing resonators that have no secret to the skilled person.

The hourly alternation numbers of 18000, 21600 and 28800, corresponding to oscillation frequencies of 2.5, 3 and 4 Hz, are commonly used in watchmaking for the sprung balance resonator. However, watches are known with oscillating balance springs oscillating at higher frequencies, the purpose being to allow the watch to achieve better chronometric performance to wear.

As the book shows "Exhaust and Stepper Engines" by Charles Huguenin et al (FET, Neuchatel 1974, pages 137 to 148 ) multiplying the frequency by two decreases the effect of a lack of equilibrium on the diurnal walk of four times. Thus an increase in the oscillation frequency of the balance has the double advantage of increasing the regulating power of the resonator and making the operation of the watch less sensitive to changes in positions.

These advantages must however be paid for by an increase in the number of teeth of the escape wheel. Indeed, the conventional escape wheel generally has 15 teeth for frequencies of the balance-spring resonator of 2.5 to 3 Hz. This number has been widely accepted as such, because it takes into account the manufacturing problems of the escape wheel and a judicious distribution of the ratios and the number of teeth of the wheels and gears of the finishing gear of the watch. With higher frequencies of the resonator between 4 and 10Hz, gear ratios become too great, but this disadvantage disappears if the number of teeth of the escape wheel is increased. The number of 21 teeth is cited for a frequency oscillation of 5Hz, this change however bringing a reduction in safety such as rest and falls that require special care during reassembly. On the other hand and generally, it is well known that the efficiency of a Swiss lever escapement drops sharply above 4 or 5 Hz.

Thus, to benefit from the advantages of a high-frequency resonator, it will be coupled with a low-frequency resonator, the latter being controlled by a conventional escapement without increasing the number of teeth of the escape wheel and with the well-known safety devices that accompany this type of exhaust.

This arrangement is represented in the block diagram of the figure 1 . In this figure, the first low frequency resonator 2,41 is constituted by a sprung balance driven by an escapement and a finishing train 70, this wheel being actuated by a cylinder 71. Derived from the gear train 70, there is the display 72 hour materialized by needles for example. The second higher frequency resonator is represented by block 3,42. The coupling between the two resonators is represented by the double-headed block 8.46.

The present invention presents two embodiments, the second mode being a special case of the first mode.

The first embodiment, in addition to satisfying what is said in the first paragraph of this description, is remarkable in that the first resonator comprises a first mass of inertia associated with a first spring, in that the second resonator comprises a second mass of inertia associated with a second spring and a third spring is disposed between the first and second masses of inertia to couple said first and second resonators.

The second embodiment, in addition to satisfying what is said in the first paragraph of this description, is remarkable in that the first resonator comprises a first mass of inertia associated with a first spring, in that the second resonator comprises a second inertial mass associated with a second spiral spring and in that said second spring connects said first and second inertial masses to couple said first and second resonators.

• la figure 1 est un schéma bloc illustrant le résonateur de l'invention et son implication dans une pièce d'horlogerie,
• la figure 2 est un schéma équivalent montrant comment sont arrangés et couplés les deux résonateurs selon le premier mode de réalisation de l'invention,
• la figure 3 est une vue en plan du premier mode de réalisation d'un résonateur résultant du couplage de résonateurs composés chacun d'un balancier-spiral,
• la figure 4 est une coupe selon la ligne IV-IV de la figure 3,
• les figures 5 et 6 sont des vues en perspective du résonateur montré en plan et en coupe sur les figures 3 et 4.
• la figure 7 est un graphique montrant la fréquence d'oscillation propre de chacun des résonateurs lorsqu'on fait varier le couple du ressort spiral reliant les deux résonateurs,
• la figure 8 est un graphique montrant l'effet stabilisant résultant du couplage des premier et second résonateurs sur des perturbations affectant soit le couple du ressort spiral du premier résonateur, soit la masse d'inertie du balancier dudit premier résonateur lorsqu'on fait varier le couple du ressort spiral reliant les deux résonateurs,
• la figure 9 est un schéma équivalent montrant comment sont arrangés et couplés les deux résonateurs selon le second mode de réalisation de l'invention,
• la figure 10 est une vue en plan du second mode de réalisation d'un résonateur résultant du couplage de résonateurs composés chacun d'un balancier-spiral,
• la figure 11 est une coupe selon la ligne XI-XI de la figure 10,
• les figures 12 et 13 sont des vues en perspective du résonateur montré en plan et en coupe sur les figures 10 et 11,
• la figure 14 est un graphique montrant la fréquence d'oscillation propre de chacun des résonateurs lorsqu'on fait varier le couple du ressort spiral du premier résonateur, et
• la figure 15 est un graphique montrant l'effet stabilisant résultant du couplage des premier et second résonateurs sur des perturbations affectant soit le ressort spiral du premier résonateur, soit la masse d'inertie du balancier dudit premier résonateur lorsqu'on fait varier le couple du ressort spiral de ce même premier résonateur.

The invention will now be explained in detail below by means of drawings illustrating the two embodiments mentioned above, these modes being given by way of non-limiting example, drawings in which:

• the figure 1 is a block diagram illustrating the resonator of the invention and its implication in a timepiece,
• the figure 2 is an equivalent diagram showing how the two resonators are arranged and coupled according to the first embodiment of the invention,
• the figure 3 is a plan view of the first embodiment of a resonator resulting from the coupling of resonators each composed of a balance-spring,
• the figure 4 is a section along line IV-IV of the figure 3 ,
• the Figures 5 and 6 are perspective views of the resonator shown in plan and in section on the Figures 3 and 4 .
• the figure 7 is a graph showing the own oscillation frequency of each of the resonators when the torque of the spiral spring connecting the two resonators is varied,
• the figure 8 is a graph showing the stabilizing effect resulting from the coupling of the first and second resonators on disturbances affecting either the pair of the spiral spring of the first resonator or the mass of inertia of the balance of said first resonator when the spring torque is varied. spiral connecting the two resonators,
• the figure 9 is an equivalent diagram showing how are arranged and coupled the two resonators according to the second embodiment of the invention,
• the figure 10 is a plan view of the second embodiment of a resonator resulting from the coupling of resonators each composed of a balance-spring,
• the figure 11 is a section along line XI-XI of the figure 10 ,
• the Figures 12 and 13 are perspective views of the resonator shown in plan and in section on the Figures 10 and 11 ,
• the figure 14 is a graph showing the own oscillation frequency of each of the resonators when the spring coil torque of the first resonator is varied, and
• the figure 15 is a graph showing the stabilizing effect resulting from the coupling of the first and second resonators on disturbances affecting either the spiral spring of the first resonator or the mass of inertia of the balance of said first resonator when the torque of the spiral spring of this same first resonator.

First embodiment of the invention

The resonator 1 executed according to the first embodiment of the invention can be assimilated to the equivalent diagram of the figure 2 . This resonator 1 results from the coupling of a first resonator 2 with a second resonator 3. The first resonator 2 comprises a first mass of inertia 4 (here illustrated by a square mass) associated with a first spring 5 (illustrated here by a spring helical, one end of which is attached to the square mass and whose other end is attached to a fixed part 73 of the timepiece, for example to the plate). The second resonator 3 comprises a second mass of inertia 6 (here illustrated by a square mass) associated with a second spring 7 (illustrated here by a spring helical whose one end is attached to the square weight and the other end is attached to a fixed portion 74 of the timepiece, for example to a bridge). A third spring 8 (here represented by a helical spring) is disposed between the first (4) and second (6) masses of inertia for coupling said first (2) and second (3) resonators.

The Figures 3 to 6 illustrate a practical construction of the first embodiment of the invention. Here the first and second masses of inertia are respectively constituted by first and second balances 4 and 6, and the first, second and third springs are respectively first, second and third spiral springs 5, 7 and 8.

It can also be seen that, according to a preferred embodiment of the invention, the first and second resonators 2 and 3 are arranged coaxially inside the timepiece between a plate 11 and a bridge 17. The invention However, it is not limited to this arrangement, the two resonators being able to be arranged, for example, side by side in the timepiece.

More particularly and as it appears on the figure 4 , the first resonator 2 essentially comprises a first rocker 4 with which is associated a first spiral spring 5. This first resonator 2 is mounted on a first shaft 9 which pivots at its first end in a bearing 10 fixed in a plate 11 and its second end in a bearing 12 fixed in an intermediate bridge 13. The outer and inner turns of the first spiral spring 5 are respectively fixed on a peak 23 carried by the plate 11 and on an inner attachment point 28 fixed on the first shaft 9.

The second resonator 3 essentially comprises a second rocker 6 with which is associated a second spiral spring 7. This second resonator 3 is mounted on a second shaft 14 which pivots at its first end in a bearing 15 fixed in the intermediate bridge 13 and its second end in a bearing 16 fixed in a bridge 17. The turns outer and inner of the second spiral spring 7 are respectively fixed on a stud 25 carried by the bridge 17 and on an inner attachment point 26 fixed on the second shaft 14.

The examination of Figures 3 to 6 shows again that the first resonator 2 comprises a balance 4 having a larger diameter than the balance 6 of the resonator 3, which indicates that the frequency of the first resonator is lower than the frequency of the second resonator, provided of course that the torque developed by each of the spiral springs is substantially the same. Under these conditions, it will be understood that the escape mechanism will be linked to the first resonator, the one that is enslaved to the second to improve its resistance to disturbances. The figure 4 shows that the first shaft 9 which is attached to the first resonator 2 carries a plate 18 and a plate pin 19, the latter cooperating for example with an anchor which in turn cooperates with an escape wheel.

It remains to describe the coupling existing between the resonators 2 and 3. This coupling is achieved by means of a third spiral spring 8. figures 4 and 5 show that this spiral spring 8 comprises two windings 20 and 21 arranged in series and mounted on either side of the intermediate bridge 13. In this way, the inner turn of the first winding 20 is fixed to an internal point of attachment. 27 fixed on the second shaft 14 while the inner coil of the second winding 21 is fixed to an inner attachment point 22 fixed on the first shaft 9, the outer turns of said windings being connected to each other by a ribbon 75.

The invention is not limited to what has just been said. Indeed the third spiral spring may have only one winding. In this case, and without it being necessary to show it by a drawing, the inner turn of this single winding is fixed to an attachment point 27 fixed on the second shaft 14 while the outer turn is fixed to a peak carried by the first pendulum 4.

We will now briefly show the advantage of coupling two resonators oscillating one low frequency and the other higher frequency in order to make more stable oscillating resonator low frequency.

A mechanical resonator composed of a mass and a spring is characterized by the weight of its mass m and the constant of its spring k which are expressed, in the case of the equivalent diagram of the figure 2 and in orders of magnitude relating to watchmaking, in milligram (mg) and micronewton per meter (μN / m), respectively. In the present case the mass m is a balance characterized by its mass of inertia expressed in milligram square centimeter (mg · cm ² ), and the constant k is relative to a spiral spring which is characterized by its unit torque expressed in micronewtonmeter by radian (μN · m / rad). That being so, the frequency of a resonator is written: $$f=\frac{1}{2\pi }\sqrt{\frac{k}{m}}$$

To take an example taken from a current clock gauge on the market, we have ak = 1 · 10 ^-6 Nm / rad and m = 16 · 10 ^-10 kg · m ² , which results in the frequency f = 4 Hz.

relation dans laquelle ω₁ est la pulsation normale du premier résonateur seul, ω_1p la pulsation perturbée du premier résonateur seul, Ω₁ la pulsation normale du système couplé et Ω_1p la pulsation perturbée du système couplé. On comprendra que si le facteur de stabilisation S est égal à deux, la pièce d'horlogerie est deux fois plus précise avec un système de résonateurs couplés qu'avec le premier résonateur seulement. Par exemple, une pièce d'horlogerie ayant une avance de dix secondes par jour n'en n'aura plus que cinq pour la même période.The central question is whether the presence of the second higher frequency resonator stabilizes the frequency of the first low frequency resonator. This effect is taken into account by the stabilization factor S defined by: $$S=\frac{{\mathrm{<figure-callout\; id="1"\; label="\omega "\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_{1p}-{\mathrm{<figure-callout\; id="1"\; label="\omega "\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_1}{{\mathrm{<figure-callout\; id="1"\; label="\omega "\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">\omega </figure-callout>}}_1}\frac{{\mathrm{<figure-callout\; id="1"\; label="\Omega "\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">\Omega </figure-callout>}}_1}{{\mathrm{<figure-callout\; id="1"\; label="\Omega "\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">\Omega </figure-callout>}}_{1p}-{\mathrm{<figure-callout\; id="1"\; label="\Omega "\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">\Omega </figure-callout>}}_1}$$

in which ω ₁ is the normal pulsation of the first resonator alone, ω _1p the disturbed pulsation of the first resonator alone, Ω ₁ the normal pulsation of the coupled system and Ω _1p the disturbed pulsation of the coupled system. It will be understood that if the stabilization factor S is equal to two, the timepiece is twice as accurate with a system of coupled resonators as with the first resonator only. For example, a timepiece with a lead of ten seconds a day will have only five for the same period.

• Résonateur 1 : m₁=21 mg·cm², k₁=1µN·m/rad d'où f₁=3,47Hz
• Résonateur 2 : m₂=21 mg·cm², k₂=5µN·m/rad d'où f₂=7,75Hz

ces résonateurs étant couplés par un ressort spiral de constante k_c.We will now take a practical example using first and second resonators having the following characteristics:

• Resonator 1: m ₁ = 21 mg · cm ² , k ₁ = 1μN · m / rad hence f ₁ = 3.47 Hz
• Resonator 2: m ₂ = 21 mg · cm ² , k ₂ = 5 μN · m / rad hence f ₂ = 7.75 Hz

these resonators being coupled by a spiral spring constant k _c .

If we refer to Figures 2 and 4 , The low frequency resonator 1 bears the reference 2, m ₁ being the rocker arm 4, k ₁ being the constant of the spiral spring 5. The resonator 2 higher frequency carries the reference 3, m ₂ being the balance wheel 6, k ₂ being the constant of the spiral spring 7. It will be noted however that in this practical example the rockers are of the same dimensions, which is not the case of the rockers of the figure 4 the second resonator having a higher natural frequency due to its higher spring constant.

Analytical calculations made it possible to establish the graphs of Figures 7 and 8 on the basis of the practical data set out above.

The figure 7 is a graph showing the evolution of the natural frequencies f ₁ and f ₂ of the coupled resonator system as a function of the constant k _c of the spiral spring which couples the two resonators.

The figure 8 is a graph showing the evolution of the stabilization factor S as a function of the constant k _c of the spiral spring 8 which couples the two resonators.

The curve S _m shows the stabilizing effect resulting from the coupling of the first and second resonators on disturbances affecting the mass of inertia of the balance of the first low frequency resonator when the constant k _c is varied. This effect is not very pronounced, which is relatively unimportant, the mass of inertia of the balance being little influenced by external disturbances.

The curve S _k shows the stabilizing effect that results from the coupling of the first and second resonators on disturbances affecting the torque of the spiral spring of the first resonator, ie that caused by the exhaust system. We see that for a value of k _c of 1 pNm / rad, the stabilization factor is not far from reaching 2, which is positive, because it is especially on the spiral spring that the disturbances inter alia spring position, shock and temperature variations.

Second embodiment of the invention

The resonator 40 executed according to the second embodiment of the invention can be likened to the equivalent diagram of the figure 9 . The resonator 40 results from the coupling of a first resonator 41 with a second resonator 42. The first resonator 41 comprises a first mass of inertia 43 (here illustrated by a square mass) associated with a first spring 44 (illustrated here by a spring helical, one end of which is attached to the square mass and whose other end is attached to a fixed part 73 of the timepiece, for example to the plate). The second resonator 42 comprises a second mass of inertia 45 (here illustrated by a square mass) associated with a second spring 46 (here illustrated by a helical spring whose one end is attached to the square mass 43 and whose other end is attached to the square mass 45). This second spiral spring 46 thus connects the first (43) and second (45) masses of inertia to couple said first (41) and second (42) resonators. In fact the spring 46 plays a dual role here: that of forming the second resonator 42 and that of coupling the first and second resonators 41 and 42.

This second embodiment can be considered as a special case of the first embodiment. Indeed, if in this first mode represented by the figure 2 , we remove the third spring 7 and its attachment to a fixed point 74, we find the equivalent diagram of the figure 9 which illustrates the second mode of execution and which will be explained now in detail with the help of Figures 10 to 13 .

The Figures 10 to 13 illustrate a practical construction of the second embodiment of the invention. Here, as has been said with respect to the first embodiment of the invention, the first and second masses of inertia are constituted respectively by first and second balances 43 and 45, and the first and second springs are respectively first and second spiral springs 44 and 46.

We also see that the first balance 43 has a circular cage inside which is confined the second resonator 42 at higher frequency, said circular cage 43 forming with the first spiral spring 44 the first resonator 41 low frequency.

As the cup of the figure 11 , the circular cage 43 forming the first balance is equipped with a first cheek 47 carrying a first pivoting pin 48 in a bearing 49 fixed in a plate 50. This first pin 48 carries a plate 51 and a plateau pin 52, the latter cooperating for example with an anchor which cooperates in turn with an escape wheel. The circular cage 43 is also equipped with a second cheek 53 carrying a second pin 54 pivoting in a bearing 55 fixed in a bridge 56. The bridge 56 is equipped with a pin 57 to which is fixed the outer turn of the first spiral spring 44 , the inner turn of said first spiral spring 44 being fixed to an internal attachment point 58 fixed on the second pin 54. The circular cage or balance 43 and the spiral spring 44 form the first resonator 41 at low frequency, the one of which it s is to improve performance.

The figure 11 shows again that the second balance 45 and spiral spring 46 constituting the second resonator 42 - and which is confined in the cage 43 - are supported by a shaft 59 pivoting at its first end in a bearing 60 fixed in the first cheek 47 of the cage 43 and at its second end in a bearing 61 fixed in the second cheek 53 of the cage. In addition, the outer and inner turns of the second spiral spring 46 are respectively fixed to a peg 62 carried by the second cheek 53 of the cage 43 and to an inner attachment point 63 fixed on the shaft 59.

The examination of Figures 10 to 12 shows that the first resonator 41 comprises a rocker or cage 43 having a larger diameter than the rocker 45 of the second resonator 42, which indicates that the frequency of the first resonator is lower than the frequency of the second resonator, the torque developed by each spiral springs being equal elsewhere. It will therefore be understood that the escape mechanism will be linked to the first resonator, the one that is to enslave the second to improve its resistance to disturbances.

• résonateur 1 : m₁ = 20mg·cm², k₁=variable
• résonateur 2 : m₂ = 6,4 mg·cm², k_c=0,4µN·m/rad, k₂=0

The advantage of coupling two oscillating resonators, one at low frequency and the other at higher frequency, in order to improve the performance of the oscillator resonator at low frequency. We will not return here to the developed theory that also applies to the second embodiment just described.
However, we will take a practical example:

• resonator 1: m ₁ = 20mg · cm ² , k ₁ = variable
• resonator 2: m ₂ = 6.4 mg · cm ² , k _c = 0.4μN · m / rad, k ₂ = 0

If we refer to Figures 9 and 11 , The low frequency resonator 1 is referenced 41, m ₁ being the balance, or the cage 43, k ₁ being the constant of the spiral spring 44 and the resonator 2 at a higher frequency has the reference 42, m ₂ being the balance 45 , k _c being the constant of the spiral spring 46, k _c being also the spiral spring which couples the two resonators.

On the basis of the practical data set out above, analytical calculations have made it possible to Figures 14 and 15 . The chosen variable is no longer k _c as in the first execution mode but k ₁ which seemed to be the most decisive parameter.

The figure 14 is a graph showing the evolution of the natural frequencies f ₁ and f ₂ of the coupled resonator system as a function of the constant k ₁ of the spiral spring 44 constituting the first resonator 41.

The figure 15 is a graph showing the evolution of the stabilization factor - which has been defined above with respect to the first embodiment - as a function of the constant k ₁ of the spiral spring 44 affecting the first resonator 41.

The curve S _m shows the stabilizing effect resulting from the coupling of the first and second resonators 41 and 42 on disturbances affecting the mass of inertia of the balance of the first low frequency resonator 41 when the constant k ₁ of the spiral spring is varied. 44. This effect is much more pronounced than that observed with regard to the first embodiment.

The curve S _k shows the stabilizing effect which results from the coupling of the first and second resonators 41 and 42 on disturbances affecting the torque of the spiral spring 44 of the first resonator 41. It can be seen that for a value of k ₁ of 2 μN · m / rad, the stabilization factor S is of the order of 2.5.

conclusions

The two embodiments presented have shown that the performances of a first low-frequency spiral balance resonator, the latter being of the order of 2 to 6 Hz, can be improved if it is coupled to a second pendulum resonator. -Spiral higher frequency, the latter being of the order of 10Hz. The first low frequency resonator is more sensitive to certain disturbances due for example to wearing, or to shocks than the second resonator to more high frequency. One can imagine to compensate the thermal variation and / or the isochronism defect of the first resonator by those of the second. Moreover, the first resonator cooperates easily with a usual exhaust system whereas this is not the case of the second resonator. It is therefore logical to couple the two resonators in question to benefit from both the good adaptation of the first to the exhaust system and the good insensitivity of the second to the disturbances mentioned above.

Claims (10)

Resonator (1) for a timepiece resulting from the coupling of a first resonator (2) at a low frequency with a second resonator (3) at a higher frequency, characterized in that the first resonator (2) comprises a first mass of inertia (4) associated with a first spring (5), in that the second resonator (3) comprises a second mass of inertia (6) associated with a second spring (7) and in that a third spring ( 8) is disposed between the first (4) and second (6) masses of inertia for coupling said first (2) and second (3) resonators. Resonator according to claim 1, characterized in that the first and second masses of inertia are respectively constituted by first (4) and second (6) rockers and in that the first, second and third springs are respectively first (5) and ), second (7) and third (8) spiral springs. Resonator according to claim 2, characterized in that the first (2) and second (3) resonators are arranged coaxially inside the timepiece. Resonator according to claim 3, characterized in that the first resonator (2) is mounted on a first shaft (9) pivoting at its first end in a bearing (10) fixed in a plate (11) and at its second end in a bearing (12) fixed in an intermediate bridge (13), the outer and inner turns of the first spiral spring (5) of said first resonator (2) being respectively fixed on a pin (23) carried by the plate (11) and on a inner attachment point (28) fixed on said first shaft (9) and in that the second resonator (3) is mounted on a second shaft (14) pivoting at its first end in a bearing (15) fixed in said bridge intermediate (13) and at its second end in a bearing (16) fixed in a bridge (17), the outer and inner turns of the second spiral spring (7) of said second resonator (3) being respectively fixed on a stud (25) carried by the bridge (17) and on an inner attachment point (26) fixed on said second shaft (14). Resonator according to claim 4, characterized in that the first shaft (9) carries a plate (8) and a pin (19) plate, the latter cooperating with an exhaust mechanism. Resonator according to claim 4, characterized in that the third spiral spring (8) has two windings (20, 21) arranged in series and mounted on either side of the intermediate bridge (13), the inner coil of the first winding ( 20) being attached to an inner attachment point (27) attached to the second shaft (14) and the inner coil of the second winding (21) being attached to an inner attachment point (22) fixed to the first shaft ( 9). Timepiece resonator (40) resulting from the coupling of a first low-frequency resonator (41) with a second resonator (42) at a higher frequency , characterized in that the first resonator (41) comprises a first resonator (41) inertia (43) associated with a first spring (44), in that the second resonator (42) comprises a second mass of inertia (45) associated with a second spring (46) and in that said second spring connects said first and second masses of inertia for coupling said first (41) and second (42) resonators. Resonator according to claim 7, characterized in that the first and second masses of inertia are respectively constituted by first (43) and second (45) rockers and in that the first and second springs are respectively first (44) and second (46) spiral springs. Resonator according to claim 8, characterized in that the first rocker (43) has a circular cage (43) inside which is confined the second resonator (42) at higher frequency, said circular cage (43) forming with the first spiral spring (44) the first low frequency resonator (41). Resonator according to claim 9, characterized in that the circular cage (43) is equipped with a first cheek (47) carrying a first pin (48) pivoting in a bearing (49) fixed in a plate (50), this first trunnion (48) carrying a plate (51) and a plate pin (52) to cooperate with an escape mechanism, and in that said circular cage (43) is equipped with a second cheek (53) carrying a second trunnion (54) pivoting in a bearing (55) fixed in a bridge (56), the latter being equipped with a peg (57) to which is fixed the outer turn of the first spiral spring (44), the inner coil of said first spring spiral being attached to an inner attachment point (58) attached to the second journal (54), and in that the second balance (45) and spiral spring (46) constituting the second resonator (42) are supported by a shaft (59) pivoting at its first end in a bearing (60) fixed in the first cheek (47) of the age (43) and at its second end in a bearing (61) fixed in the second flange (53) of the cage (43), the outer and inner turns of the second spiral spring (46) being respectively fixed to a pin (62). ) carried by the second cheek (53) of the cage (43) and an inner attachment point (63) fixed on the shaft (59).

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