EP2894521A1 - Isotroper harmonischer Oszillator und zugehörige Zeitbasis ohne Hemmung oder vereinfachte Hemmung - Google Patents

Isotroper harmonischer Oszillator und zugehörige Zeitbasis ohne Hemmung oder vereinfachte Hemmung Download PDF

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Publication number
EP2894521A1
EP2894521A1 EP14173947.4A EP14173947A EP2894521A1 EP 2894521 A1 EP2894521 A1 EP 2894521A1 EP 14173947 A EP14173947 A EP 14173947A EP 2894521 A1 EP2894521 A1 EP 2894521A1
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EP
European Patent Office
Prior art keywords
oscillator
spring
isotropic
mass
escapement
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Withdrawn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
EP14173947.4A
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English (en)
French (fr)
Inventor
Simon Henein
Ilan Vardi
Lennart Rubbert
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
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Ecole Polytechnique Federale de Lausanne EPFL
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Publication date
Application filed by Ecole Polytechnique Federale de Lausanne EPFL filed Critical Ecole Polytechnique Federale de Lausanne EPFL
Priority to EP14173947.4A priority Critical patent/EP2894521A1/de
Priority to CN201580013815.6A priority patent/CN107250925B/zh
Priority to CN201580013818.XA priority patent/CN106462105B/zh
Priority to PCT/IB2015/050243 priority patent/WO2015104693A2/en
Priority to RU2016130167A priority patent/RU2686869C2/ru
Priority to EP15706927.9A priority patent/EP3095010A2/de
Priority to US15/109,829 priority patent/US10585398B2/en
Priority to RU2016130168A priority patent/RU2686446C2/ru
Priority to US15/109,821 priority patent/US10365609B2/en
Priority to JP2016563280A priority patent/JP6661543B2/ja
Priority to PCT/IB2015/050242 priority patent/WO2015104692A2/en
Priority to EP15706928.7A priority patent/EP3095011B1/de
Priority to JP2016563279A priority patent/JP6559703B2/ja
Publication of EP2894521A1 publication Critical patent/EP2894521A1/de
Priority to HK17105186.4A priority patent/HK1231572A1/zh
Priority to HK17105184.6A priority patent/HK1231571A1/zh
Withdrawn legal-status Critical Current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
    • G04B17/04—Oscillators acting by spring tension
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/045—Oscillators acting by spring tension with oscillating blade springs
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape wheel
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B21/00—Indicating the time by acoustic means
    • G04B21/02—Regular striking mechanisms giving the full hour, half hour or quarter hour
    • G04B21/08—Sounding bodies; Whistles; Musical apparatus
    • 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
    • G04B23/00—Arrangements producing acoustic signals at preselected times
    • G04B23/005—Arrangements producing acoustic signals at preselected times by starting up musical boxes or other musical recordings

Definitions

  • Escapements have an Inherent inefficiency since they are based on intermittent motion in which the whole movement must be stopped and restarted, leading to wasteful acceleration from rest and noise due to impacts. Escapements are well known to be the most complicated and delicate part of the watch, and there has never been a completely satisfying escapement for a wristwatch, as opposed to the detent escapement for the marine chronometer.
  • the present invention solves the problem of the escapement by eliminating it completely or, alternatively, by a family of new simplified escapements which do not have the drawbacks of current watch escapements.
  • the invention concerns a mechanical isotropic harmonic oscillator comprising at least a two degrees of freedom linkage supporting an orbiting mass with respect to a fixed base with springs having isotropic and linear restoring force properties.
  • the oscillator may be based on an x-y planar spring stage forming a two degree-of-freedom linkage resulting in purely translational motion of the orbiting mass such that the mass travels along its orbit while keeping a fixed orientation.
  • each spring stage may comprise at least two parallel springs.
  • each stage may be made of a compound parallel spring stage with two parallel spring stages mounted in series.
  • the invention concerns as oscillator system comprising at least two oscillators as defined herein.
  • each stage is rotated by an angle with respect to the stage next to it.
  • the angle is 90° or a value close to this one.
  • the oscillator system comprises four oscillators.
  • the oscillator or oscillator system may comprise a mechanism for continuous mechanical energy supply to the oscillator or oscillator system.
  • the mechanism for energy supply applies a torque or an intermittent force to the oscillator or to the oscillator system.
  • the mechanism may comprise a variable radius crank which rotates about a fixed frame through a pivot and a prismatic joint which allows the crank extremity to rotate with a variable radius.
  • the mechanism may comprise a fixed frame holding a crankshaft on which a maintaining torque M is applied, a crank which is attached to a crankshaft and equipped with a prismatic slot, wherein a rigid pin is fixed to the orbiting mass of the oscillator or oscillator system, wherein said pin engages in said slot.
  • the mechanism may comprise a detent escapement a for intermittent mechanical energy supply to the oscillator.
  • the detent escapement comprises two parallel catches which are fixed to the orbiting mass, whereby one catch displaces a detent which pivots on a spring to releases an escape wheel, and whereby said escape wheel impulses on the other catch thereby restoring lost energy to the oscillator or oscillator system.
  • the invention concerns a timekeeper such as a clock comprising an oscillator or an oscillator system as defined in the present application.
  • the timekeeper is a wristwatch.
  • the oscillator or oscillator system defined in the present application is used as a time base for a chronograph measuring fractions of seconds requiring only an extended speed multiplicative gear train, for example to obtain 100Hz frequency so as to measure 1/100 th of a second.
  • the oscillator or oscillator system defined in the present application is used as speed regulator for striking or musical clocks and watches, as well as music boxes, thus eliminating unwanted noise and decreasing energy consumption, and also improving musical or striking rhythm stability.
  • This oscillator is also known as a harmonic isotropic oscillator where the term isotropic means "same in all directions.”
  • Leopold Defossez states its application to measuring very small intervals of time, much smaller than its period, see reference [8, p. 534].
  • isochronism requires a true oscillator which must preserve all speed variations.
  • the wave equation ⁇ 2 ⁇ X ⁇ 1 c 2 ⁇ ⁇ 2 ⁇ X ⁇ ⁇ t 2 preserves all initial conditions by propagating them.
  • a true oscillator must keep a record of all its speed perturbation. For this reason, the invention described here allows maximum amplitude variation to the oscillator.
  • Figure 4 illustrates the principle of the conical pendulum and figure 5 a typical conical pendulum mechanism.
  • Figure 6 illustrates a Villarceau governor made by Antoine Breguet in the 1870s and figure 7 illustrates the propagation of a singularity for a plucked string.
  • Planar isotropy may be realized in two ways.
  • a rotating turntable 1 on which is fixed a spring 2 of rigidity k with the spring's neutral point at the center of rotation of the turntable is illustrated in Figure 8 .
  • a massless turntable 1 and spring 2 Assuming a massless turntable 1 and spring 2, a linear central restoring force is realized by this mechanism.
  • this realization has the disadvantages of having significant spurious mass and moment of inertia.
  • a rotating cantilever spring 3 supported in a cage 4 turning axially is illustrated in Figure 9 .
  • a physical model has been constructed, see Figure 10 where vertical motion of the mass 503 has been minimized by attaching the mass to a double leaf spring 504, 505 producing approximately linear displacement instead of the approximately circular displacement of the single spring of Figure 9 .
  • the rotating frame 501 is linked to the fixed base 506 by a rotational bearing 502.
  • FIG. 16 A simple example is given in Figure 16 illustrating a simple planar isotropic spring with an orbiting mass 10, an y-coordinate spring 11, an x- coordinate spring 12, an y-spring fixation to ground 13, an x-spring fixation to ground 14, a horizontal ground 15, the y-axis being vertical so parallel to force of gravity.
  • the two springs Sx 12 and Sy 11 of rigidity k are placed such that spring Sx 12 acts in the horizontal x-axis and spring Sy 11 acts in the vertical y -axis.
  • the geometry is chosen such that at the point (0, 0) both springs are in their neutral positions.
  • An embodiment illustrated in Figure 11 is composed of two serial compliant four-bar 5 is also called parallel arms linkage, which allows, for small displacements, translations in the X and Y directions.
  • Another embodiment, illustrated in figure 12 is composed of four parallel arms 6 linked with eight spherical joints 7 and a central bellow 8 connecting the mobile platform 9 to the ground.
  • the spring does not rotate around its own axis, minimizing spurious moments of inertia, and the central force is directly realized by the spring itself.
  • isotropic springs because their restoring force is the same in all directions.
  • FIG 18A A basic example of an embodiment of the oscillator made of planar isotropic springs according to the present invention is illustrated in figure 18A .
  • Said figure illustrates a mechanical isotropic harmonic oscillator comprising at least a two degrees of freedom linkage L1/L2 made by appropriate guiding means (for example sliding means, or linkages, springs etc.), supporting an orbiting mass P with respect to a fixed base B with springs S having isotropic and linear restoring force K properties.
  • appropriate guiding means for example sliding means, or linkages, springs etc.
  • the first method to address the force of gravity is to make a planar isotropic spring which when in horizontal position with respect to gravity does not feel its effect.
  • Figure 19 illustrates an example of such a spring arrangement as a 2 degree of freedom planar isotropic spring construction.
  • gravity has negligible effect on the planar motion of the orbiting mass when the plane of mechanism is placed horizontally. This provides single direction minimization of gravitational effect. It comprises a fixed base 20, Intermediate block 21, a frame holding the orbiting mass 22, an orbiting mass 23, an y-axis parallel spring stage 24 and an x-axis parallel spring stage 25.
  • figure 20 shows a gravity compensation in all directions for planar isotropic spring.
  • Rigid frame 31 holds time base comprising two linked non-independent planar isotropic oscillators 32 (symbolically represented here).
  • Lever 33 is attached to the frame 31 by a ball joint 34 (or x-y universal joint).
  • the two arms of the lever are telescopic thanks to two prismatic joints 35.
  • the opposing ends of the lever 33 are attached to the orbiting masses 36 by ball joints.
  • the mechanism is symmetric with respect to the point 0 at center of joint 34.
  • Linear shocks are a form of linear acceleration, so include gravity as a special case.
  • the mechanism of Figure 20 also compensates for linear shocks.
  • figure 21 illustrates a gravity compensation in all directions for planar isotropic spring with added resistance to angular acceleration. This is achieved by minimizing the distance "I" between the center of gravity of the two orbiting masses.
  • Rigid frame 41 holds a time base comprising of two linked non- independent planar isotropic oscillators 42 (symbolically represented here),
  • Lever 43 is attached to the frame 41 by a ball joint 47 (or x-y universal joint).
  • the two arms of the lever 43 are telescopic thanks to two prismatic joints 48.
  • the opposing ends of the lever 43 are attached the orbiting masses 46 by ball joints 49.
  • the mechanism is symmetric with respect to the point O at center of joint 47.
  • Figure 22 illustrates another embodiment of a Realization of gravity compensation in all directions for a planar isotropic spring using flexures.
  • a rigid frame 51 holds a time base comprising two linked non-independent planar isotropic oscillators 53 (symbolically represented here).
  • Lever 54 is attached to a frame 52 by x-y a universal joint made of leaf spring 56 and flexible rod 57.
  • the two arms of the lever 54 are telescopic thanks to two leaf springs 55.
  • the opposing ends of the lever 54 are attached the orbiting masses 52 by the two leaf springs 55 which form two x-y universal joints.
  • Figure 23 illustrates an alternate realization of gravity compensation in all directions for a planar isotropic spring using flexures.
  • both ends of lever 64 are connected to the orbiting masse 62 connected to springs 63 in the oscillator by two perpendicular flexible rods 61.
  • Figure 24 illustrates another realization of gravity compensation in all directions for an isotropic spring using flexures.
  • fixed plate 71 holds time base composed of two linked symmetrically placed non-independent orbiting masses 72.
  • Each orbiting mass 72 is attached to the fixed base by three parallel bars 73, these bars are either flexible rods or rigid bars with a ball joint 74 at each extremity.
  • Lever 75 is attached to the fixed base by a membrane flexure joint (not numbered) and vertical flexible rod 78 thereby forming a universal joint.
  • the extremities of the lever 75 are attached to the orbiting masses 72 via two flexible membranes 77.
  • Part 79 is attached rigidly to part 71.
  • Part 76 and 80 are attached rigidly to the lever 75.
  • Oscillators lose energy due to friction, so there needs a method to maintain oscillator energy. There must also be a method for counting oscillations in order to display the time kept by the oscillator. In mechanical clocks and watches, this has been achieved by the escapement which is the interface between the oscillator and the rest of the timekeeper. The principle of an escapement is illustrated in figure 15 and such devices are well known in the watch industry.
  • a torque or a force are applied, see Figure 13 for the general principle of a torque T applied continuously to maintain the oscillator energy, and figure 14 illustrates another principle where a force F T is applied intermittently to maintain the oscillator energy.
  • a mechanism is also required to transfer the suitable torque to the oscillator to maintain the energy, and in Figures 25 to 29 various crank embodiments according to the present invention for this purpose are illustrated.
  • Figures 37 and 38 illustrate escapement systems for the same purpose.
  • All these restoring energy mechanisms may be used in combination with the various embodiments of oscillators and oscillators systems (stages etc.) described herein, for example in figures 19 to 24 , 30 to 35 (as the mechanism 138 illustrated in figure 30 ), and 40 to 48 .
  • the torque/force may by applied by the spring of the watch which is used in combination with an escapement as is known in the field of watches.
  • the known escapement may therefore be replaced by the oscillator of the present invention.
  • FIG 25 illustrates the principle of a variable radius crank for maintaining oscillator energy.
  • Crank 83 rotates about fixed frame 81 through pivot 82.
  • Prismatic joint 84 allows crank extremity to rotate with variable radius.
  • Orbiting mass of time base (not shown) is attached to the crank extremity 84 by pivot 85.
  • the orientation of orbiting mass is left unchanged by crank mechanism and the oscillation energy is maintained by crank 83.
  • Figure 26 illustrates a realization of variable radius crank for maintaining oscillator energy attached to the oscillator.
  • a fixed frame 91 holds a crankshaft 92 on which maintaining torque M is applied.
  • Crank 93 is attached to crankshaft 92 and equipped with a prismatic slot 93'.
  • Rigid pin 94 is fixed to the orbiting mass 95 and engages in the slot 93'.
  • the planar isotropic springs are represented by 96. Top view and perspective exploded views are shown in this figure 26 .
  • Figure 27 illustrates a flexure based realization of a variable radius crank for maintaining oscillator energy.
  • Crank 102 rotates about fixed frame (not shown) through shaft 105.
  • Two parallel flexible rods 103 link crank 102 to crank extremity 101.
  • Pivot 104 attaches the mechanism shown in figure 27 to an orbiting mass. The mechanism is shown in neutral singular position in this figure 27 ,
  • Figure 28 illustrates another embodiment of a flexure based realization of variable radius crank for maintaining oscillator energy.
  • Crank 112 rotates about fixed frame (not shown) through shaft 115.
  • Two parallel flexible rods 113 link crank 112 to crank extremity 111.
  • Pivot 114 attaches mechanism shown to orbiting mass. Mechanism is shown in flexed position in this figure 28 .
  • Figure 29 illustrates an alternate flexure based realization of variable radius crank for maintaining oscillator energy.
  • Crank 122 rotates about fixed frame 121 through shaft.
  • Two parallel flexible rods 123 link crank 122 to crank extremity 124.
  • Pivot 126 attaches mechanism to orbiting mass 125. In this arrangement the flexible rods 123 are minimally flexed for average orbit radius.
  • Figure 30 illustrates an example of a completely assembled isotropic oscillator 131-137 and its energy maintaining mechanism. More specifically, a fixed frame 131 is attached to the ground or to a fixed reference (for example the object on or in which the oscillator is mounted) by three rigid feet 140 and top frame 140a. First compound parallel spring stage 131 holds second parallel spring stage 132 moving orthogonally to said spring stage 131. Compound parallel spring 132 is attached rigidly to stage 131. Fourth compound parallel spring stage 134 holds third parallel spring stage 133 moving orthogonally to spring stage 134. Outer frames of stages 133 and 134 are connected kinematically in the x and y directions by L-shaped brackets 135 and 136 as well as by notched leaf springs 137.
  • stages 133 and 134 constitute the orbiting mass of the oscillator while stages 132-133 are attached together and fixed to feet 140 and the orbiting mass moves therefore relatively to stages 132-133.
  • the moving mass may be formed by stages 132-133 and in that case the stages 131 and 134 are fixed to the feet 140.
  • Bracket 139 mounted on the orbiting mass holds the rigid pin 138 (illustrated in figures 30 and 31 ) on which the maintaining force is applied for example a torque or a force, by means identical or equivalent to the ones described above with reference to figures 25-29 .
  • Each stage 131-134 may be for example made as illustrated in figure 19 or in figures 42 to 47 discussed later herein in more details. Accordingly, the description of these figures applies to the stages 131-134 illustrated in these figures 30-35 .
  • the stages 131 and 132 are identical but placed with a relative rotation (in particular of 90°) to form the X-Y planar isotropic springs discussed herein.
  • Figure 31 shows the same embodiment of figure 30 , and shows the rigid pin 138 mounted rigidly on the orbiting masses (stages 134 and 131, for example as mentioned hereabove) and engages into slot 142 which acts as the driving crank and maintains the oscillation.
  • the other parts are numbered as in figure 30 and the description of this figure applies correspondingly.
  • the crank system used may be the one illustrated in figures 25-29 and described hereabove.
  • Figure 32 illustrates the stages 131-134 of the embodiment of Figures 30 and 31 without crank system 142-143 and using the reference numbers of Figure 30 .
  • Figure 33 illustrates the stages 131-133 of the embodiment of Figure 32 without stage 134 and using the reference numbers of Figure 30 .
  • Figure 34 illustrates the stages 131-132 of the embodiment of Figure 33 without stage 3 using the reference numbers of Figure 30 .
  • Figure 35 illustrates the stage 131 of Figure 34 without stage 132 using the reference numbers of Figure 30 .
  • each stage 131-134 may be made in accordance with the embodiments described later in the present specification in reference to figures 41-48 .
  • stage 131 of figure 35 comprises parallel springs 131a to 131 d which hold a mass 131e and the springs and masses of said figures 41-48 may correspond to the ones of figures 30-35 .
  • stages 131 and 132 are placed with a relative rotation of 90° between them, and their mass 131e-132e are attached together (see figure 34 ).
  • This provides a construction equivalent to the one of figure 43 described later with two parallel springs in each direction X-Y.
  • Stages 133 and 134 are attached as stages 131-132 and placed in a mirror configuration over stages 131-132, stage 133 comprising as stages 131 and 132 springs 133a-133d and a mass 133e.
  • stage 133 rotated by 90° with respect to stage 132 as one can see in figure 33 .
  • the frames of stages 132 and 133 are attached together such that they will not move relatively one to another.
  • Stage 134 also comprise springs 134a-134d and mass 134e.
  • Mass 134e is attached to mass 133e and the two stages 134 and 131 a linked together via brackets 135,136 to form the orbiting mass while stages 132 and 133 which are attached together are fixed to the frame 140, 140a.
  • the mechanism for applying a maintaining force or torque is placed on top of the stages 131-134 and comprises the pin 138 and the crank system 142, 143 which for example the system described in figure 26 , the pin 92 of figure 26 corresponding to pin 138 of figure 31 , the crank 93 corresponding to crank 142 and slot 93' to slot 143.
  • stages 131-134 of figures 30-34 may be replaced by other equivalent stages having the X-Y planar isotropy in accordance with the principle of the invention, for example, one may use the configurations and exemplary embodiments of figures 40 to 48 to realize the oscillator of the present invention.
  • the advantage of using an escapement is that the oscillator will not be continuously in contact with the energy source (via the gear train) which can be a source of chronometric error.
  • the escapements will therefore be free escapements in which the oscillator is left to vibrate without disturbance from the escapement for a significant portion of its oscillation.
  • the escapements are simplified compared to balance wheel escapements since the oscillator is turning in a single direction. Since a balance wheel has a back and forth motion, watch escapements generally require a lever in order to impulse in one of the two directions.
  • the first watch escapement which directly applies to our oscillator is the chronometer or detent escapement [6, 224-233].
  • This escapement can be applied in either spring detent or pivoted detent form without any modification other than eliminating passing spring whose function occurs during the opposite rotation of the ordinary watch balance wheel, see [6, Figure 471c].
  • Figure 4 illustrating the classical detent escapement the entire mechanism is retained except for Gold Spring i whose function is no longer required.
  • Embodiments of possible detent escapements for the rotational harmonic oscillator are shown in Figures 36 to 38 .
  • Figure 36 illustrates a simplified classical detent watch escapement for rotational harmonic oscillator.
  • the usual horn detent for reverse motion has been suppressed due to the unidirectional rotation of the oscillator.
  • Figure 37 illustrates an embodiment of a detent escapement for translational orbiting mass.
  • Two parallel catches 151 and 152 are fixed to the orbiting mass (not shown but illustrated schematically by the arrows forming a circle, reference 156) so have trajectories that are synchronous translations of each other.
  • Catch 152 displaces detent 154 pivoted at spring 155 which releases escape wheel 153. Escape wheel impulses on catch 151, restoring lost energy to the oscillator.
  • Figure 38 illustrates an embodiment of a new detent escapement for translational orbiting mass.
  • Two parallel catches 161 and 162 are fixed to the orbiting mass (not shown) so have trajectories that are synchronous translations of each other.
  • Catch 162 displaces detent 164 pivoted at spring 165 which releases escape wheel 163. Escape wheel impulses on catch 161, restoring lost energy to the oscillator.
  • Mechanism allows for variation of orbit radius. Side and top views shown in this figure 38 .
  • Figure 39 illustrates examples of compliant XY-stages shown in the prior art references cited herein,
  • the conical pendulum is a pendulum rotating around a vertical axis, that is, perpendicular to the force of gravity, see Figure 4 .
  • the theory of the conical pendulum was first described by Christiaan Huygens see references [16] and [7] who showed that, as with the ordinary pendulum, the conical pendulum is not isochronous but that, in theory, by using a flexible string and paraboloid structure, can be made isochronous.
  • Huygens' modification is based on a flexible pendulum and in practice does not improve timekeeping.
  • the conical pendulum has never been used as a timebase for a precision clock.
  • the conical pendulum has been consistently described as a method for obtaining uniform motion in order to measure small time intervals accurately, for example, by Defossez in his description of the conical pendulum see reference [8, p. 534].
  • the conical pendulum has been used in precision clocks, but never as a time base.
  • William Bond constructed a precision clock having a conical pendulum, but this was part of the escapement, the timebase being a circular pendulum see references [10] and [25, p.139-143].
  • our invention is therefore a superior to the conical pendulum as choice of time base because our oscillator has inherent isochronism. Moreover, our invention can be used in a watch or other portable timekeeper, as it is based on a spring, whereas this is impossible for the conical pendulum which depends on the timekeeper having constant orientation with respect to gravity.
  • governors are mechanisms which maintain a constant speed, the simplest example being the Watt governor for the steam engine.
  • these governors were used in applications where smooth operation, that is, without the stop and go intermittent motion of a clock mechanism based on an oscillator with escapement, was more important than high precision.
  • such mechanisms were required for telescopes in order to follow the motion of the celestial sphere and track the motion of stars over relatively short intervals of time. High chronometric precision was not required in these cases due to the short time interval of use.
  • Our invention uses a rotational oscillator as time base and does not require electricity or electronics in order to operate correctly.
  • the continuous motion of the movement is regulated by the rotational oscillator itself and not by an integrated circuit.
  • the present invention was conceived as a realization of the rotational harmonic oscillator for use as a time base. Indeed, in order to realize the rotational harmonic oscillator as a time base, there requires a physical construction of the central restoring force.
  • the theory of a mass moving with respect to a central restoring force is such that the resulting motion lies in a plane. It follows that for practical reasons, that the physical construction should realize planar isotropy. Therefore, the constructions described here will mostly be of planar isotropy, but not limited to this, and there will also be an example of 3-dimensional isotropy. Planar isotropy can be realized in two ways: rotational isotropic springs and translational isotropic springs.
  • Rotational isotropic springs have one degree of freedom and rotate with the support holding both the spring and the mass. This architecture leads naturally to isotropy. While the mass follows the orbit, it rotates about itself at the same angular velocity as the support. This leads to a spurious moment of inertia so that the mass no longer acts as a point mass and the departure from the ideal model described in Section 1.1 and therefore to a theoretical isochronism defect.
  • Translational isotropic springs have two translational degrees of freedom in which the mass does not rotate but translates along an elliptical orbit around the neutral point. This does away with spurious moment of inertia and removes the theoretical obstacle to isochronism.
  • a rotating cantilever spring 3 supported in a cage 4 turning axially is illustrated in Figure 9 , discussed above. This again realizes the central linear restoring force but reduces spurious moment of inertia by having a cylindrical mass and an axial spring. Numerical simulation shows that divergence from isochronism is still significant.
  • a physical model has been constructed, see Figure 10 , where vertical motion of the mass has been minimized by attaching the mass to a double leaf spring producing approximately linear displacement instead of the approximately circular displacement of the single spring of Figure 9 . The data from this physical model is consistent with the analytic model.
  • Compliant XY-stages are mechanism with two degrees of freedom both of which are translations. As these mechanisms are composed of compliant joints, see reference [28], they exhibit planar restoring forces so can be considered as planar springs.
  • the first one illustrated in Figure 11 comprises two serial compliant four-bar 5 mechanisms, also called parallel arms linkage, which allows, for small displacements translations in the X and Y directions.
  • the second one illustrated in Figure 12 comprises four parallel arms 6 linked with eight spherical joints 7 and a bellow 8 connecting the mobile platform 9 to the ground.
  • the same result can be obtained with three parallel arms linked and with eight spherical joints and a bellow connecting the mobile platform to the ground.
  • Isotropic springs are one object of the present invention and they appear most suitable to preserve the theoretical characteristics of the harmonic oscillator are the ones in which the central force is realized by an isotropic spring, where the term isotropic is again used to mean "same in all directions.”
  • the basic concept used in all the embodiment of the invention is to combine two orthogonal springs in a plane which ideally should be independent of each other. This will produce a planar isotropic spring, as is shown in this section.
  • Figure 16 the simplest version is given in Figure 16 .
  • two springs 11, 12 S x and S y of rigidity k are placed that spring 12 S x acts in the horizontal x -axis and spring 11 S y acts in the vertical y -axis.
  • Figure 18A is basic Illustration of the principle of the present invention (see above for its detailed description).
  • This model has two degrees of freedom as opposed to the model of Section 11.2 which has six degrees of freedom. Therefore, this model is truly planar, as is required for the theoretical model of Section 2. Finally, this model is insensitive to gravity when its plane is orthogonal to gravity.
  • a first plate 181 is mounted on top of a second plate 182.
  • Blocks 183 and 184 of first plate 181 are fixed onto blocks 185 and 186 respectively of second plate 182.
  • the grey shaded blocks 184, 187 of first plate and 186 of second plate 182 have a y-displacement corresponding to the y-component displacement of the orbiting mass 189, while the black shaded blocks 183 of the first plate 181 and 185, 188 of the second plate 182 remain immobile.
  • the grey shaded blocks 184, 187 of first 181 and 186 of second plate 182 have an x-displacement corresponding to the x-component displacement of the orbiting mass 189 while the black shaded blocks 183, 185, 188 of the first 181 and second 182 plates remain immobile. Since the first and second plates 181, 182 are identical, the sum of the masses of 184, 187 and 186 is equal to the sum of the masses of 184, 188 and 186. Therefore, the total mobile mass (grey blocks 184, 186, 187) is the same for displacements in x and in y directions, as well as in any direction of the plane.
  • the goal of this mechanism is to provide an isotropic spring stiffness Isotropy defect, that is, the variation from perfect spring stiffness isotropy, will be the factor minimized in our invention.
  • Our inventions will be presented in order of increasing complexity corresponding to compensation of factors leading to isotropy defects
  • FIGS 43 and 44 illustrate an embodiment of an in plane orthogonal compensated parallel spring stages according to the invention
  • Fixed base 191 holds first pair of parallel leaf springs 192 connected to intermediate block 193.
  • Second pair of leaf springs 194 (parallel to 192) connect to second intermediate block 195.
  • Intermediate block 195 holds third pair of parallel leaf springs 196 (orthogonal to springs 192 and 194) connected to third intermediate block 197.
  • Intermediate block 197 holds parallel leaf springs 198 (parallel to springs 196) which are connected to orbiting mass 199 or alternatively to a frame holding the orbiting mass 199
  • the in-plane orthogonal non-compensated parallel spring stages mechanism has a worst case isotropy defect of 6.301%.
  • worst case isotropy is 0.027%. The compensated mechanism therefore reduces the worst case isotropy stiffness defect by a factor of 200.
  • figure 46 discloses an embodiment minimizing the reduced mass isotropy defect.
  • a first plate 201 is mounted on top of a second plate 202 and the numbering has the same significance as in Figure 43 .
  • Blocks 191 and 199 of first plate 201 are fixed onto blocks 191 and 199 respectively of second plate 202.
  • the grey shaded blocks 197, 199 of first plate 201 and 193, 195, 197, 199 of second plate 202 have an x-displacement corresponding to the x-component displacement of the orbiting mass while the black shaded blocks 191, 193, 195 of the first plate 201 and 191 of the second plate 202 remain immobile.
  • the grey shaded blocks 193, 195, 197, 199 of first plate 201 and 199 of second plate 202 have a y-displacement corresponding to the y-component displacement of the orbiting mass while the black shaded block 191 of the first plate 201 and 191, 193, 195 of the second plate 202 remain immobile.
  • the reduced mass in the x and y directions are identical and therefore identical in every direction, thus in theory minimizing reduced mass isotropy defect.
  • a fixed base 301 holds first pair of parallel leaf springs 302 connected to intermediate block 303.
  • Second pair of leaf springs 304 (parallel to 302) connect to second intermediate block 305.
  • Intermediate block 305 holds third pair of parallel leaf springs 306 (orthogonal to springs 302 and 304) connected to third intermediate block 307.
  • Intermediate block 307 holds parallel leaf springs 308 (parallel to 306) which are connected to orbiting mass 309 (or alternatively frame holding the orbiting mass 309).
  • the first method to address the force of gravity is to make a planar isotropic spring which when in horizontal position with respect to gravity does not feel its effect as described above.
  • Linear shocks are a form of linear acceleration, so include gravity as a special case
  • the mechanism of Figure 20 also compensates for linear shocks, see description above
  • the three dimensional translational isotropic spring invention is illustrated in Figure 48
  • Three perpendicular bellows 403 connect to translational orbiting mass 402 to fixed base 401 Using the argument of section 10 2, see Figure 17 above, this mechanism exhibits three dimensional isotropy up to first order Unlike the two-dimensional constructions illustrated in Figures 16-18 , the bellows 403 provide a 3 degree-of-freedom translational suspension making this a realistic working mechanism insensitive to external torque
  • the invention can constitute an entirely mechanical two degree-of-freedom accelerometer, for example, suitable for measuring lateral g forces in a passenger automobile
  • the oscillators and systems described in the present application may be used as a time base for a chronograph measuring fractions of seconds requiring only an extended speed multiplicative gear train, for example to obtain 100Hz frequency so as to measure 1/100 th of a second.
  • a chronograph measuring fractions of seconds requiring only an extended speed multiplicative gear train, for example to obtain 100Hz frequency so as to measure 1/100 th of a second.
  • the gear train final ratio may be adapted in consequence.
  • the oscillator described herein may be used as a speed governor where only constant average speed over small intervals is required, for example, to regulate striking or musical clocks and watches, as well as music boxes.
  • the use of a harmonic oscillator, as opposed to a frictional governor, means that friction is minimized and quality factor optimized thus minimizing unwanted noise, decreasing energy consumption and therefore energy storage, and in a striking or musical watch application, thereby improving musical or striking rhythm stability.

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EP14173947.4A 2014-01-13 2014-06-25 Isotroper harmonischer Oszillator und zugehörige Zeitbasis ohne Hemmung oder vereinfachte Hemmung Withdrawn EP2894521A1 (de)

Priority Applications (15)

Application Number Priority Date Filing Date Title
EP14173947.4A EP2894521A1 (de) 2014-01-13 2014-06-25 Isotroper harmonischer Oszillator und zugehörige Zeitbasis ohne Hemmung oder vereinfachte Hemmung
RU2016130168A RU2686446C2 (ru) 2014-01-13 2015-01-13 Изотропный гармонический осциллятор с по меньшей мере двумя степенями свободы и соответствующий регулятор с отсутствующим спусковым механизмом или с упрощенным спусковым механизмом
US15/109,821 US10365609B2 (en) 2014-01-13 2015-01-13 Isotropic harmonic oscillator and associated time base without escapement or with simplified escapement
PCT/IB2015/050243 WO2015104693A2 (en) 2014-01-13 2015-01-13 General 2 degree of freedom isotropic harmonic oscillator and associated time base without escapement or with simplified escapement
RU2016130167A RU2686869C2 (ru) 2014-01-13 2015-01-13 Изотропный гармонический осциллятор и соответствующий регулятор с отсутствующим спусковым механизмом или с упрощенным спусковым механизмом
EP15706927.9A EP3095010A2 (de) 2014-01-13 2015-01-13 Isotroper harmonischer oszillator und zugehörige zeitbasis ohne hemmung oder mit vereinfachter hemmung
US15/109,829 US10585398B2 (en) 2014-01-13 2015-01-13 General two degree of freedom isotropic harmonic oscillator and associated time base
CN201580013815.6A CN107250925B (zh) 2014-01-13 2015-01-13 机械的各向同性谐波振荡器和振荡器系统
CN201580013818.XA CN106462105B (zh) 2014-01-13 2015-01-13 机械的各向同性谐波振荡器、包括其的系统及计时装置
JP2016563280A JP6661543B2 (ja) 2014-01-13 2015-01-13 脱進機のない、または簡易脱進機を有する一般２自由度等方性調和振動子および関連するタイムベース
PCT/IB2015/050242 WO2015104692A2 (en) 2014-01-13 2015-01-13 Xy isotropic harmonic oscillator and associated time base without escapement or with simplified escapement
EP15706928.7A EP3095011B1 (de) 2014-01-13 2015-01-13 Massenumlaufsystem
JP2016563279A JP6559703B2 (ja) 2014-01-13 2015-01-13 脱進機のない、または簡易脱進機を有する等方性調和振動子および関連するタイムベース
HK17105186.4A HK1231572A1 (zh) 2014-01-13 2017-05-22 沒有擒縱機構或具有簡化擒縱機構的般二自由度各向同性諧波振盪器及相關時基
HK17105184.6A HK1231571A1 (zh) 2014-01-13 2017-05-22 沒有擒縱機構或具有簡化擒縱機構的各向同性諧波振盪器及相關時基

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EP14173947.4A EP2894521A1 (de) 2014-01-13 2014-06-25 Isotroper harmonischer Oszillator und zugehörige Zeitbasis ohne Hemmung oder vereinfachte Hemmung
EP14183385 2014-09-03
EP14183624 2014-09-04
EP14195719 2014-12-01

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EP3339969A1 (de) 2016-12-20 2018-06-27 Ecole Polytechnique Fédérale de Lausanne (EPFL) Mechanischer oszillator
EP3361325A1 (de) 2017-02-14 2018-08-15 Ecole Polytechnique Fédérale de Lausanne (EPFL) EPFL-TTO Mechanischer oszillator, der zwei freiheitsgrade besitzt
WO2019141789A1 (en) 2018-01-18 2019-07-25 Ecole polytechnique fédérale de Lausanne (EPFL) Horological oscillator
CN110389519A (zh) * 2018-04-23 2019-10-29 Eta瑞士钟表制造股份有限公司 具有旋转柔性轴承的谐振器机构的抗震保护
EP3719584A1 (de) 2019-04-02 2020-10-07 Ecole Polytechnique Fédérale de Lausanne (EPFL) Oszillatorsystem mit zwei freiheitsgraden
CN115060355A (zh) * 2022-04-12 2022-09-16 东南大学 一种基于线性调频脉冲的谐振子品质因数测量方法

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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3339969A1 (de) 2016-12-20 2018-06-27 Ecole Polytechnique Fédérale de Lausanne (EPFL) Mechanischer oszillator
WO2018115101A1 (en) 2016-12-20 2018-06-28 Ecole polytechnique fédérale de Lausanne (EPFL) Mechanical oscillator
EP3361325A1 (de) 2017-02-14 2018-08-15 Ecole Polytechnique Fédérale de Lausanne (EPFL) EPFL-TTO Mechanischer oszillator, der zwei freiheitsgrade besitzt
WO2019141789A1 (en) 2018-01-18 2019-07-25 Ecole polytechnique fédérale de Lausanne (EPFL) Horological oscillator
CN110389519A (zh) * 2018-04-23 2019-10-29 Eta瑞士钟表制造股份有限公司 具有旋转柔性轴承的谐振器机构的抗震保护
CN110389519B (zh) * 2018-04-23 2021-09-03 Eta瑞士钟表制造股份有限公司 钟表谐振器机构、钟表振荡器机构、钟表机芯和手表
US11175630B2 (en) 2018-04-23 2021-11-16 Eta Sa Manufacture Horlogere Suisse Anti shock protection for a resonator mechanism with rotary flexure bearing
EP3719584A1 (de) 2019-04-02 2020-10-07 Ecole Polytechnique Fédérale de Lausanne (EPFL) Oszillatorsystem mit zwei freiheitsgraden
CN115060355A (zh) * 2022-04-12 2022-09-16 东南大学 一种基于线性调频脉冲的谐振子品质因数测量方法
CN115060355B (zh) * 2022-04-12 2024-03-26 东南大学 一种基于线性调频脉冲的谐振子品质因数测量方法

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