• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention concerns a vortex. Watchmaking tourbillon comprising: a cage (CC) of axis (ZC), divided into two half-cages by a median plane (RC) perpendicular to the axis of rotation (ZC), with a regulation system comprising an oscillator (OSa , b), its anchor and its escape mobile (MEa, b) housed in each half-cage. The two regulation systems are composed of identical elements, organized in reverse order in each half-cage (1a, 1b) so that, in the median plane, the direction of rotation of the two exhaust wheels (MEa, b) are identical. A fixed compensated wheel (RFa, b) is connected to a respective escape wheel set (MEa, b). A differential (D) comprising two outputs (Sa, b) each connected to a fixed compensated wheel (RFa, b) creates position compensation. A drive link (EC) connects the clockwork mechanism (MH) to the cage (CC) for its drive in rotation about its axis (ZC).
    公开号:CH717176A2
    申请号:CH00170/21
    申请日:2021-02-22
    公开日:2021-08-31
    发明作者:Halter Vianney
    申请人:Halter Vianney；
    IPC主号:
    专利说明:

    FIELD OF THE INVENTION
    The present invention relates to a watchmaker's tourbillon with two oscillators in a cage.
    STATE OF THE ART
    [0002] Invented in 1810 by Abraham-Louis Breguet, the tourbillon is a mechanism in which the escapement and the sprung balance regulator are rotated inside a cage. Initially, the purpose of this mechanism is to mix up the hanged positions so as to average all the static and dynamic balancing faults, which makes sense in the case of a pocket watch. In practice, the results on chronometry for a wristwatch are questionable and do not compensate for the additional difficulty that the execution of such a horological device generates. Despite this, the watchmaking tourbillon remains a testament to watchmaking know-how, and is visually fascinating.
    The principle of the tourbillon is based on bringing the escapement inside the second wheel. A fixed wheel supports the escape wheel. The escapement, by letting the second wheel turn at each impulse, actually lets the cage and all the components it contains rotate. The inertia of the cage is an important factor: if the cage is too heavy, its acceleration will be less, and the shock given to the escape wheel when stopping will be stronger.
    [0004] At each impulse, the balance receives a little energy from the escapement, which propels it sometimes clockwise, sometimes counterclockwise. On the other hand, the cage, the rotation of which is released at each impulse, accomplishes its release angle only in one direction (clockwise or counterclockwise).
    [0005] The sprung balance used as a regulator is attached to the cage by a stud which secures its end curve to the cage.
    [0006] Consequently, during every other impulse, the cage and the balance have a movement in the same direction, and the balance receives an impulse from the anchor, and an impulse in the same direction of the part of the cage via the end curve of its balance spring. During the other half of the impulses, the balance receives an impulse from the anchor, and an impulse in the opposite direction via the end curve of its hairspring since the movement of the cage and the balance are opposed.
    [0007] Thus, with a conventional vortex configuration, half of the pulses will give a higher amplitude than the average, and the other half will give a reduced amplitude. The operation of the oscillator will therefore be asymmetric with respect to the equilibrium point.
    [0008] If the influence of the cage on the balance, although problematic, is compensable by the adjustment of the various components of the balance, the influence of the balance movement on the dynamics of the cage is irremediable.
    When the escapement gives an impulse in the direction of the movement of the balance, the reaction of the cage is a movement in the opposite direction, which slows down the rotational movement of the cage and minimizes the stopping shock.
    When the escapement gives an impulse in the direction opposite to the direction of rotation of the balance, the reaction of the cage is a movement in the direction of the rotation of the cage, which accelerates the rotational movement of the cage and causes excessive shock when stationary.
    From the point of view of the escapement, the asymmetry between the two alternations described by the balance can also pose a problem, as soon as the balance goes through its free angle.
    After the balance has undergone its impulse, during an alternation in the direction of rotation of the cage, the end curve of the balance spring exerts a pressure force on the cage. This pressure force is reflected on the exhaust via its pressure on the fixed wheel, which is not problematic and further secures the draft.
    The draft is a safety function of the escapement which, by the angle of the anchor vanes and their contact with the teeth of the escape wheel allows a return of the anchor fork away from the balance in shock. This safety feature minimizes the duration of disturbing contact between the small plate and the anchor stinger by forcing the anchor rod against its limiting pins.
    When alternating in the direction opposite to the direction of rotation of the cage, after the balance has undergone its impulse, its end curve exerts a tensile force on the cage. This tensile force opposes the pressure applied to the cage by the cog train, and tends to push the cage back. As a result, the pressure of the exhaust sprocket wings on the teeth of the fixed wheel decreases, which in turn decreases the pressure of the exhaust wheel teeth on the anchor vane. As a result, the pulling force decreases.
    Thus, in a conventional tourbillon cage carrying a sprung balance regulator and an anchor escapement, there are disturbances from the cage towards the balance and disturbances from the balance towards the cage, due to the inertia of the pendulum. There is also a risk of strong disturbances every second alternation due to the drop in the pulling force, while the hairspring is around its maximum deformation.
    At the present time, the closest execution making it possible to correct these problems inherent in the tourbillon cage is that of the H2 resonance tourbillon by Beat Haldimann.
    PURPOSE OF THE INVENTION
    The object of the invention is to develop a watch tourbillon device in the geometric configuration of the regulation system makes it possible to minimize the disturbances of the tourbillon cage.
    DISCLOSURE AND ADVANTAGES OF THE INVENTION
    To this end, the present invention relates to a watch tourbillon comprising: A) a cage mounted to rotate about an axis and divided into two half-cages by a median plane perpendicular to the axis of rotation, - a double tourbillon each formed by a regulation system comprising an oscillator, its anchor and its escapement mobile, housed in each half-cage, - the two regulation systems being composed of identical elements but organized in the opposite way and installed in each half-cage in a position symmetrical with respect to the median plane so that, in the median plane, the directions of rotation of the two exhaust wheels are identical - each regulation system having a fixed compensated wheel connected to its mobile exhaust B) a differential comprising - two outputs each connected to a fixed compensated wheel creating position compensation - an input connected to the clockwork mechanism C) a drive link connecting the mechanism clockwork mechanism with the cage for the drive in rotation around its axis. Thus the watch tourbillon is made up of two balances inside a rotating cage in two parts.
    According to another characteristic, the axes of the oscillators are merged along a main axis which is the axis of the cagethe oscillators, and their constituent elements are identical or identical except for planar symmetrythe escapements of the two oscillators are identical or identical except for planar symmetry.
    This configuration according to the invention has two distinct advantages: When the two balances are in operation, they both oscillate in rhythm, in the opposite direction. In this way, the sum of the rotational inertia of the two balances around their axis is zero at all times. The resultant of the forces applied by the balances on the cage is consequently zero.If the two balances are coupled for their synchronization, the disturbance generated by the cage on the balances is distributed. Each oscillator in the two-balancer system is less disturbed than if it were alone in the cage.
    According to another advantageous characteristic, the balances and springs are identical so as to guarantee the closest possible inertia.
    [0022] According to another advantageous characteristic, the two hairsprings are located between the balances, to minimize the space between said hairsprings and to increase the compactness of the system.
    According to another advantageous characteristic, the two balance springs are identical in the winding direction to allow the synchronized development of the balance springs during their operation.
    According to another advantageous characteristic, the two sets of exhausts are identical except for planar symmetry, so as to facilitate the balancing of the double cage along its main axis.
    [0025] According to another characteristic, the two oscillators comprise a flat hairspring or a Breguet hairspring.
    According to another characteristic, the escapements are of any type (Swiss anchor, trigger, etc.) as long as they are identical for the two oscillators.
    In other words the two oscillators are mounted head to tail, one oscillator being above and the other oscillator below the median plane.the plane of one escapement is above the plane of the associated balance, and the plane of the other escapement is below the plane of the associated balance andthe two balance-springs are contained in the space delimited by the serges of the balances.
    As already indicated, the mobile exhaust are arranged in axial symmetry around the main axis of the cagethe pivot axes of the exhaust wheels are parallel to the main axis of the cage and are arranged in diametrical opposition with respect to this main axis, as are the axes of the anchors.
    According to another characteristic the cage is formed of a cage wheel constituting the median plane with on either side the half-cages each composed of plates and bridges,the exhaust mobile each leaving its respective half-cage to mesh with the compensated fixed wheel aligned with the cage axis, andthe cage wheel has a crown gear for driving the cage directly from the clockwork mechanism.
    According to another characteristic, the differential is a flat gear differential comprising:a frame of rotation axistwo output wheels on the axle and connected by at least one pair of planet wheels installed head-to-tail, each planet gear having two pinions carried by the same axle,the two satellites meshing with each other by two corresponding pinions and by the other pinion, one and the other satellite meshes with an output mobile.
    According to another characteristic, the axis of the double tourbillon and the axis of the differential are parallel.
    The differential frame comprises a base carrying two aligned pivots, one of the pivots is provided with the input pinion, the base carrying two plates provided with bearings between which the satellites are installed.
    According to another characteristic, each satellite consists of a long pinion and a short pinion, the planet wheels of each pair being combined in the head to tail position and with parallel axes to form a pair,the pairs of satellites being arranged in axial symmetry of 180 ° with respect to the axis of rotation of the differential,the long pinion of a satellite is cut so as to mesh both with the tubular pinion of the output mobile and with the short pinion of the other planet of this pair of satellites,the long pinion of each pair of planet gears, meshing over part of its length with the tubular pinion of the output mobile and over the other part of its length with the short pinion of the same pair so that the tubular output pinion and the short pinion are offset and do not mesh.
    In other words, the satellite pinion comprisesa long pinion cut so as to be able to mesh with the pinion of the output mobile and the second planet pinion,a short pinion which meshes only with the second planet gear and without meshing with the pinion of the opposite output mobile,a free axle portion to allow the toothing of the cage wheel to pass through and minimize the size of the differential-tourbillon cage system The planet gears operate by torque and a single torque would be sufficient to create the differential effect but depending on the The invention preferably has two pairs of satellites, diametrically opposed, to maintain the vector of the sum of the gear pressures on the axis of the differential. This protects the pivots from premature wear and does not create a preferred direction of engagement.
    According to another particularly advantageous characteristic, the base of the differential frame has notches on its equator so as to allow the teeth of the cage wheel to pass through and reduce the size on the equatorial plane, all the satellites of the differential being notched. and their axes clear to minimize the distance between the axis of the tourbillon and that of the differential.
    In other words, to allow the approximation of the axis of the differential and the axis of the tourbillon cage, the differential has an hourglass or diabolo shape and at its equator, the teeth of the satellites of the differential are clear.
    Thus the watch tourbillon according to the invention constitutes a particularly compact embodiment which allows the regulation of the mechanism to be considerably improved.
    BRIEF DESCRIPTION OF THE DRAWINGS
    The present invention will be described below in more detail with the aid of embodiments shown in the accompanying drawings in which: [Fig. 1] general diagram of a watchmaker's tourbillon with two oscillators according to the invention [Fig. 2] isometric perspective view of an embodiment of a device with two oscillators in a tourbillon cage and a differential driving two compensation wheels. [Fig. 3] isometric perspective view of the framework of the upper part of the double tourbillon [Fig. 4] perspective view of a tourbillon oscillator and its escapement [Fig. 5] top view of the elements of the two regulation systems showing the symmetrical distribution of the elements along the axis of the cage. [Fig. 6] isometric perspective view of the tourbillon of FIG. 2, showing the elements of the escapements of the cage. [Fig. 7] perspective view of the double tourbillon according to the invention [Fig. 8] side view showing the structure of the cage, in particular the arrangement of the balance springs [Fig. 9] sectional view of the functional elements of the cage [Fig. 10] isometric perspective view of the differential and the drive wheel meshing with the input pinion of the differential [Fig. 11] isometric perspective view of the differential with its frame [Fig. 12] simplified schematic view of the differential without the chassis [Fig. 13] side view of the differential without the chassis
    DESCRIPTION OF EMBODIMENTS
    Figure 1 is a general diagram of the watch tourbillon according to the invention composed of a double tourbillon TD connected to the clockwork mechanism MH by a differential D whose input ED is connected to the clockwork mechanism MH and whose two outputs Sa, Sb are connected to the two outputs of the double tourbillon TD, the cage CC of which is rotated by the clockwork mechanism MH.
    According to watchmaking tradition the operation of the mechanism is described in the direction of the flow of power from the drive to the regulation so that the description of the connection by the differential D is the reverse of some terminologies for the concepts of entry and exit.
    The speed of the MH clockwork mechanism is imposed by the regulation system consisting of the double tourbillon TD and its two combined oscillators. The two oscillators have a different frequency although they are close, which implies that this difference must be compensated for to avoid stopping the mechanism. The speed ω imposed by the double tourbillon TD is the average of the speedω1 = (ω + δω) and ω2 = (ω - δω) of the two oscillators OSa, b since the chassis CH of the differential is thus pushed to rotate at the average speed
    The watch tourbillon T according to the invention consists of the double tourbillon TD composed of a CC cage rotating around the axis ZG while being driven from the watch mechanism MH by a cog meshing with the input EC of the CC cage.
    The RC cage wheel forms the median plane of the CC cage. On either side of this plane is housed an oscillator OSa, OSb respective. These oscillators have, by construction and by adjustment, a frequency that is as close as possible, which in practice cannot be completely identical. This slight frequency shift around the average frequency is taken into account by the differential. We will call ω1 = ω + δω the speed of one of the oscillators andω2 = ω - δω the speed of the other.This frequency difference results in a shift in the speed of the compensation wheels and therefore in the speeds of the outputs of the differential.
    The average speed of these two speeds is necessarily the speed ω imposed by the regulation system on the clock mechanism MH.
    Each oscillator OSa, OSb is connected at the output to an exhaust mobile MEa, b carried by the cage CC, and meshing with a wheel called here the compensated fixed wheel Rfa, RFb, itself connected to one of the two inputs of the differential D by a respective fixed wheel drive ERFa, ERFb.
    The meshing between the exhaust mobile MEa, b and the compensated fixed wheel RFa, b which is itself a mobile, is not detailed because this structure appears clearly in Figure 1.
    To simplify the embodiment, the mobile exhaust MEa, MEb do not pass through the cage CC along its axis of rotation ZC but these mobiles are carried in an offset manner by the sides of the cage CC. The compensated fixed wheels RFa, RFb being co-axial with the axis ZC of the cage CC; this offset does not modify the movement transmitted by the escape wheels MEa, MEb to the respective compensated fixed wheel RFa, RFb.
    The differential D consists of a chassis CH driven in rotation about its axis ZD and carrying coaxially to the axis ZD, the output mobile Sa, Sb, each axis of which carries a respective output pinion Pa, Pb. The two output pinions Pa, Pb are connected by two “satellites” STa, STb carried by the chassis CH. The satellites reverse the rotational movement of the two pinions Pa, Pb according to the traditional operation of a differential.
    In the case of the diagram of Figure 1le differential D is a differential with flat and non-conical cogs so that the satellite is formed by a pair of satellites STa, STb with flat cogs and which perform this reversal of movement.
    Each satellite STa, STb is formed of two pinions (ST1a long, ST2a short) and (ST1b long, ST2b short) each secured to a common axis ASa, ASb carried by the chassis CH:the pinions ST1a, ST1b mesh respectively with one of the pinions Pa, Pb.the pinions ST2a, ST2b mesh with each other.
    The number of teeth of the pinions ST1a ... ST2b being the same, the combination of the two satellites STa and STb reverses the movement transmitted from one satellite to the other so that the movement of the two pinions Pa, Pb is properly reversed as required by the operation of a differential when the chassis rotates at speed ω and the pinions at the speed difference ± δω.
    The outputs Sa, Sb receive the movements ω1, ω2des two oscillators by the pinions Pa, Pb; as the pair of satellites is integral with the chassis CH with the axis of rotation ZD, the chassis is driven in rotation around the axis ZD according to the average rotation speed, the differences -δω and + δω being compensated by the relative rotation, by opposite direction, of the gears Pa, Pb.
    The watch tourbillon T therefore imposes the speed of rotation ω on the watch mechanism MH, regulated by the double tourbillon TD.
    For the purposes of the diagram of FIG. 1, the axes ASa, ASb are shown inclined to show the angular offset of the two satellites Sa, Sb around the axis ZD in the chassis CH. In reality, one of the satellites STa is in front of the plane of FIG. 1 and the other satellite STb behind this plane.
    For reasons of balancing and symmetry of transmission of forces to the pinions Pa, Pb, the pair of satellites STa, STb is completed by a pair of satellites ST'a, ST'b identical in positions symmetrical to those of the first pair with respect to the ZD axis.
    Figures 2 to 13 show an embodiment of the watch tourbillon T whose various components, detailed, are identified in the figures by numerical references and, as a reminder, by the general references of the diagram of Figure 1.
    To simplify the presentation of the watch tourbillon T, given the identity of the shapes and the symmetries, the components will bear the numerical references completed with the suffix (a) and the suffix (b).
    [0058] FIG. 2 shows an overall isometric perspective view of an embodiment of the watch tourbillon composed of a double tourbillon TD connected by a differential 5 to the clock mechanism not shown in this figure.
    The different parts of the TD double tourbillon will be described separately with the aid of Figures 3-13.
    Figure 3 shows the framework of a half-cage carried by the cage wheel 10, common to the two half-cages 1a, 1b and defining the RC median plane of the cage 1, perpendicular to the axis of rotation ZC of the cage. The wheel 10 has a toothed ring 101 for its drive. It carries an exhaust plate 11a by pillars 161. The exhaust plate 11a carries the exhaust bridge 13a.
    The anchor bridge 12a is carried by the exhaust plate 11a and the cage pivot 14a is fixed to the anchor bridge 12a.
    The elements of the cage are mounted rigidly. The exhaust plates 11a, b are fixed on the common wheel 10 via pillars 16. The anchor and exhaust bridges (resp. 12a, b and 13a, b) are mounted on the exhaust plate 11a, b via pillars 16. The pivots 14a, b are mounted on the anchor bridges 12a, b.
    The framework shown in Figure 3 is taken symmetrically in the sense defined above to receive the components of the other oscillator OSb respecting these conditions of symmetry.
    Figure 4 shows an oscillator 4a which, in the orientation of its position shown, is the one above, installed in the half-cage shown in Figure 3. This oscillator 4a taken in isolation has generally the usual structure of a oscillator composed of a balance rim 41a, mounted on an axis 40a, the conical part of the axis 40a of which has a double plate 43a carrying an ellipse 44a.
    A ferrule 42a carrying a balance spring 45a is mounted on the cylindrical part of the axis 40a. The spiral 450a installed in the rim 41a consists of an Archimedean spiral body with constant pitch and a Breguet 451a end curve. The terminal curve is integral with a stud 46a maintained in a common stud holder 15solidaire with the structure of the cage wheel 10 (FIGS. 5 and 6).
    The anchor 3a consisting of a board 30a, its inlet 31a and outlet 32a pallets, ends with a fork 33a acting on the ellipse 44a of the oscillator 4a.
    FIG. 5 is a plan view of the combination of the two oscillators 4a, 4b (like the oscillator 4a of FIG. 4) on the same axis ZC (FIG. 1) on either side of the plane of the wheel cage 10, common, not shown. The two oscillators 4a, 4b are diametrically opposed and rotate in the same direction, as shown very simply by the identical orientation of the escape wheels 21a, 21b.
    Geometrically, and in this configuration, the exhausts are necessarily the mirror image of one another. The operation of the Swiss lever escapement mechanism is well known, and will not be described in more detail.
    The oscillators 4a, 4b are necessarily identical, and mounted head to tail. Their components (in particular the ferrule 44a, b and the balance spring 45a, b) are also geometrically identical and assembled in the same configuration if they are considered individually. Mounted head-to-tail and observed along the axis of the cage in FIG. 5, they appear to be planar symmetrical to each other. Their movements are synchronized and are opposite to each other. This is ideally the case, but there is a whole range of transient regimes during which the frequencies are being balanced, and therefore during which the movements are not completely synchronous.
    So as to balance the cage as well as possible, the axes of the two mobile exhaust 2a and 2b are parallel to the axis of the cage ZC, and arranged in diametrical opposition with respect to the latter. The axes of the two anchors 3a and 3b are also arranged in diametrical opposition with respect to the cage axis ZC. This arrangement is visible in figure 5.
    The mobile exhaust 2a, b consist of the pinions 20a, b and the escape wheels 21a, b. Each pinion 20a, b rolls on a fixed compensated wheel 50a, b. In order to guarantee the operation of the system during periods of non-synchronicity, these two compensated fixed wheels are connected by the differential, via two transmissions.
    FIG. 6 is a perspective view of the elements of FIG. 5 showing in addition the two compensated fixed wheels 50a, 50b and their relationship with the exhaust wheels. One can guess the meshing of the wheel 50a with the exhaust pinion 20a. Only the stage of the compensated fixed wheels 50a and 50b has been shown; the meshing with the driving mobiles has been omitted.
    FIG. 7 shows the combination of the two oscillators 4a, 4b in the framework of FIG. 3, completed by the symmetrical framework under the cage wheel 10 and thus constituting the cage 1 of the double tourbillon TD.
    The representation is limited to the supporting elements of the double cage 1a, b, to the escapement (escape mobile 2a, b and anchor 3a, b), to the oscillators 4a, b and to the elements for setting the movement of cage 5a, b.The cage 1 is set in motion by the teeth 101 of the cage wheel 10.
    The fixed elements of the cage 1 are a cage wheel 10, shared between the two half-cages 1a, 1b in each of them. The escape bridge 13a, b carries the anchor 3a, b and the escape mobile 2a, b. The anchor 3a, b is positioned by the anchor bridge 12a, b, which also positions the oscillator 4a, b. The exhaust bridge 13a, b positions the exhaust mobile 2a, b.
    The cage 1est held axially by its pivots 14a, b (Figure 3).
    The layered organization of the cage 1 appears in the side view of Figure 8 and the sectional view of Figure 9 showing the symmetrical distribution of the components on either side of the axis of rotation ZC and the two eyebolts 46a, 46b on the 15double, common eyebolt carrier.
    The differential 5 (D) shown in Figures 1 and 11a a frame 52composed of a base 521 in which are driven two pivots 526. Two plates 522 carrying the bearings 523 of the satellites 55 are secured to the base 521 by two screws 524 each. The pivots 526 define the axis of rotation ZD of the differential and serve as a support for the rotation of the two output wheels 53a, b.
    The base 521a laterally two notches 525ouvert towards the outer sides to allow the differential of the tourbillon TD to be brought closer and to allow the cage wheel 10 to pass so that the chassis 52 and the cage 1 can rotate around their respective axis ZD, ZC and be brought together as much as possible to reduce bulk.
    The notches 525 are straddling the median plane of the differential, perpendicular to its axis ZD. In other words the base of the frame 52 and its plates 522ont a transverse shape crossing at the square of the diametrically opposite arrangement of the location of the two pairs of satellites 55a, b; STa, STb; ST'a, ST'b with respect to the axis ZD and in the median plane of the chassis CH the base 521a a notch 525 respectively open towards the two outer sides of the base and the pinions of the satellites STa, b / ST'a, b leave the median plane clear for the free passage of the toothed ring 101 of the cage CC, allowing the ZD axis of the differential D to be brought closer to the ZC axis of the double tourbillon TD.
    The chassis 52porte the input pinion 54du differential which meshes with the drive wheel 56relied to the clock mechanism MH.
    The output wheels 53a, b each consist of a tubular pinion 531 and an output wheel 532 driven on the tubular pinion.
    The satellites 55 are assembled in pairs in a head-to-tail position and the pairs are installed in the frame 52 in an angular position symmetrical with respect to the axis ZD.
    The four satellites 55 are identical.
    According to the references given in Figure 11, a satellite 55 consists of a tubular pinion 551 and a flat pinion 552 connected by an axis 553. The two pinions 551, 552 assimilated to flat or straight pinions have a different length for be able to be combined and perform the function of satellite inverter; they mesh with the tubular pinions 531 of the mobile output 53 as shown in Figures 12 and 13.
    Indeed according to Figures 12 and 13 the satellites 55a, 55b of the pair are installed head to tail and: * the satellite 55a meshes: - by its long pinion 551a with the tubular output pinion 531a - by its long pinion 551a with the short pinion 552b - by its short pinion 552a with the long pinion 551b * the satellite 55b meshes: - by its long pinion 551b with the tubular output pinion 531b - by its long pinion 551b with the short pinion 552a - by its short pinion 552b with long sprocket 551a
    The long pinion 551a, b of a satellite pinion 55a, b meshes both with the tubular pinion 531a, b of the output mobile 5a, b and with the short pinion 552b, a of the other satellite 55b, a of this pair of satellites.
    As the axes of the satellites must be located on a geometric cylinder of axis ZD to mesh by their long pinions 551a, b respectively with the tubular pinions 531a, 531b, each pinion 551 must mesh with the tubular pinion 531 without the pinion 552 does not mesh with the latter. It must therefore pass above / below this tubular pinion 531 as shown in the side view of figure 13. This two-by-two meshing of the pinions 531, 551, 552 is made possible by the asymmetry of the sizes of the pinions 551 and 552 with respect to the equatorial plane of the differential.
    The axes 553a, b of the satellites 55a, b are diametrically opposed with respect to the axis ZD, on a circle centered on this axis so that the space formed by these released axes 553 defines the degree of possible approximation of the differential D and the TD double tourbillon. The notches 525de the base 52sont made so as not to exceed this space around the axis ZD in the median plane.
    The diametrically opposed arrangement of the pairs of satellites in a radial orientation and the radial transverse orientation of the base 52 and of the plates 53 form an otherwise balanced cross organization.
    This cross orientation is demonstrated in Figures 1, 12, 13.
    FIG. 12 also indicates the rotation of the elements of the differential 5the output mobiles 53a, b are driven respectively at speeds ω1 = ω-δω and ω2 = ω + δω (according to this example) which represents the rotation around the axis ZD at a higher speed and at a lower speed respectively than the average speed according to the operating principle of a differential.
    In conclusion and in summary, it should be noted that the structure of the differential of the embodiment (FIG. 2) is that of the diagram (FIG. 1) differ, the diagram of FIG. 1 being a representation in the single plane of FIG. 1, it was not possible to show the compact axial organization of the differential D produced in practice: In the embodiment, the frame 52 axially crosses the output wheels 53a, b along the axis ZD to receive the input pinion. 54 beyond axially one of the two mobile output 53a.
    Returning to the complete view of Figure 2 and the general diagram of Figure 1, the differential 5 (D) is composed of the frame 52 (CH) rotating around the axis ZD. Carried by the frame 52 (CH) are the two mobile output 53a, b (Sa, b), in rotation along the axis ZD. The two pinions of the output wheels 53a, b have the same number of teeth, which must be even. They mesh with the intermediate mobile 51a, b (ERFa, b).
    The differential is a differential with flat cogs (straight cogs) comprising:a CH / 52 chassis with a ZD rotation axistwo output wheels Sa, Sb on the axis ZD and connected by at least one pair of satellites STa, b; ST'a, b installed head to tail, each satellite having two pinions ST1a, ST1b; ST2a, ST2b carried by the same axis,the two satellites STa, b; ST'a, b meshing with each other* by two homologous pinions ST2a, b; ST'2a, b and* by the other pinion ST1a, ST1b; ST1a, ST'1b both with an output mobile Sa, b.
    The satellites 55a, b (STa, b) serve as a reversing link to the two output mobiles 53a, b (Sa, b). The reversers operate in pairs so as to cancel the resulting pressure torques during engagement. The four satellites 55 (STa, STb, ST'a, ST'b) have the same number of teeth. The axes of rotation of the satellites 55STa, b are parallel to the axis of rotation ZD of the chassis 52 (CH) of the differential 5 (D). The axes of the pairs of satellites 55 (STa, b) are arranged diametrically with respect to the axis of rotation ZD of the differential 5 (D).
    The satellites 55a, b (STa, b) mesh simultaneously with their output mobile 53a, b (Sa, b) so that, as a consequence of the number of teeth of the elements present, in the frame of reference of the frame, the two output pinions 532a, b (Sa, b) will have equal relative speeds and in opposite directions.
    According to the same reasoning, in a frame of reference outside the differential, the rotational speed of the frame 52 (CH) will be equal to the average of the rotational speeds of the output pinions 532a, b (Sa, b).
    This differential 5 (D), stepped, using flat gears 53a, b, 55a, b (Pa, b, STa, b, 5a, b) reproduces the behavior of a bevel gear differential. Although more complex in terms of the number of elements, this arrangement makes it possible to use flat gears of a known standard (NIHS 20-25 for example) instead of bevel gears which are not very practical to machine in watchmaking, and allows a very efficient structure using pivot points. between two bearings (unlike pivoting around a driven stud, for example).
    [0100] The two output gears 531du differential 5 are integral with output wheels 532 (Sa, b) themselves meshing on two wheels of the intermediate mobile 51a, b (ERFa, b) intended to drive the compensation wheels 50 (RF ).
    In this comparison of the general diagram (Figure 1) and the isometric perspective view of an embodiment according to Figure 2, the double tourbillon TD appears by its cage 1 (CC) with its cage wheel 10 (RC ) divided into two half-cages 1a, b each housing an oscillator 4a, b and its anchor 3a, b (OSa, b) as well as the escape mobile 2a, b (MEa, b). The toothing 101 of the cage wheel 10 constitutes the input EC driven by the clock mechanism MH.
    [0102] In a traditional tourbillon configuration, the fixed wheel acts as a support for the escapement mobile, which transforms the rotation of the cage into a satellite rotational movement around the fixed wheel.
    In the configuration according to the invention, it was chosen to slow down the cage 1 (CC) and to provide the remaining rotation via the fixed wheel 50 (RF) (which becomes a compensation wheel). This is consequently always in pressure against the exhaust pinion 20 (ME) which makes it possible to introduce the differential 5 (D) to take account of the speed differences of the two compensation wheels 50a, b (RFa, b ).
    The differential 5 is rotated via the frame 52 (CH) which carries an input wheel 54 (ED), rotated by the rest of the movement (not shown).
    NOMENCLATURE OF THE MAIN ELEMENTS
    [0105] T Watchmaking tourbillon TD Double tourbillon CC Tourbillon cage ZC Double tourbillon axis RC Cage wheel defining the median plane OSa, b Oscillator MEa, b Exhaust mobile EC Cage entry RFa, b Fixed compensated wheel D Differential ED Differential input ZD Differential axis CH Differential frame Sa, b Differential output Pa, b Output pinion STa, b, ST'a ,, b Satellite ST1a, b Long pinion ST2a, b Short pinion ERFa, b Wheel drive fixed MH Clockwork mechanism 1 Cage 1a, 1b Half-cage 10 Cage wheel 101 Teeth in the form of a toothed crown 102 Cage bridge 11 Exhaust plate 12 Anchor bridge 13 Exhaust bridge 14 Cage pivot 15 Door Double eyebolt (common) 16 Pillar 161 Platinum bridge pillar 2 Exhaust mobile 20 Exhaust pinion 21 Escape wheel 3 Anchor 30 Anchor board 31 Inlet paddle 32 Outlet paddle 33 Fork 4 Oscillator 40 Axis from Balance 41 Balance rod 42 Ferrule 43 Double plate 44 Ellipse 45 Spiral 450 Archimedean hairspring 451 End curve 46 Piton 5 Differential 50 Compensated fixed wheel 51 Intermediate mobile 52 chassis 521 Base 522 Plate 523 Bearing 524 Screw 525 Notch 526 Pivot 53 Output mobile differential 531 Tubular output pinion 532 Output wheel 54 Differential input pinion 55 Satellite 551 Long pinion 552 Short pinion 553 Free axle 56 Differential drive wheel
    [0106] To simplify the presentation of the claims, all similar references are not systematically repeated in the claims. They are only if it is necessary for understanding.
    权利要求:
    Claims (11)
    [1]
    1. Watchmaking tourbillon comprising:A) a cage (CC) mounted to rotate around an axis (ZC) and divided into two half-cages (1a, b) by a median plane (RC) perpendicular to the axis of rotation (ZC),- a double tourbillon (TD) each formed of a regulation system comprising an oscillator (OSa, b), its anchor and its escape wheel (MEa, b) housed in each half-cage (1a, 1b),- the two regulation systems being composed of identical elements but organized in reverse order and installed in each half-cage (1a, b) in a symmetrical position with respect to the median plane (RC) so that this, in the median plane , the directions of rotation of the two exhaust wheels (MEa, b) are identical- each regulation system having a fixed compensated wheel (RFa, b) connected to its exhaust mobile (MEa, b)B) a differential (D) comprising- two outputs (Sa, b) each connected to a fixed compensated wheel (RFa, b) creating position compensation- an input (ED) connected to the clockwork mechanism MH C) a drive link (EC) connecting the clockwork mechanism (MH) to the cage (CC) for driving in rotation around its axis (ZC ).
    [2]
    2. Watch tourbillon according to claim 1,characterized in that:- the axes of the oscillators (4a, b) are merged along a main axis which is the axis (ZC) of the cage (CC)- the oscillators (4a, b), and their constituent elements are identical or identical except for planar symmetry- the exhausts (2a, b and 3a, b) of the two oscillators (4a, b) are identical or identical except for planar symmetry.
    [3]
    3. Watch tourbillon according to claim 1,characterized in that:- the oscillators (4a, b) have a flat hairspring or a Breguet hairspring
    [4]
    4. Watchmaking tourbillon according to claim 1,characterized in that:- the two oscillators (4a, b) are mounted head to tail, one oscillator (4a) being above and the other oscillator 4b below the median plane.- the plane of one escapement (2a, 3a) is above the plane of the associated balance (4a), and the plane of the other escapement (2b, 3b) is below the plane of the associated balance (4b) and- the two balance-springs (45a, b) are contained in the space delimited by the serges of the balances (41a, b).
    [5]
    5. Watchmaking tourbillon according to claim 1,characterized in that- the mobile exhaust (2a, b; 3a, b) are arranged in axial symmetry around the main axis (ZC) of the cage- the pivot axes of the exhaust wheels (2a, b; 3a, b) are parallel to the main axis (ZC) of the cage and are arranged in diametrical opposition with respect to this main axis, as are the axes anchors (3a, b).
    [6]
    6. Watch tourbillon according to claim 1,characterized in that-the cage (1) is formed of a cage wheel (10) constituting the median plane (RC) with on either side the half-cages (1a, b) each composed of plates and bridges (10, 102a, b, 11a, b, 12a, b, 13a, b),- each exhaust mobile (MEa, b) each coming out of its respective half-cage (1a, b) to mesh with the compensated fixed wheel (RFa, b) aligned with the cage axis (ZC), and- the cage wheel (10) has a toothed crown (101) for its drive from the clockwork mechanism (MH).
    [7]
    7. Watch tourbillon according to claim 1,characterized in thatthe differential (D, 5) is a flat-wheel differential comprising- a frame (CH / 52) with an axis of rotation (ZD)- two output wheels (Sa, Sb) on the axis (ZD) and connected by at least one pair of satellites (STa, b; ST'a, b) installed head to tail,each satellite having two pinions (ST1a, ST1b; ST2a, ST2b) carried by the same axis,- the two planet wheels (STa, b; ST'a, b) meshing with two homologous pinions (ST2a, b; ST'2a, b) and- by the other pinion (ST1a, ST1b; ST'la, ST'1b) both with an output mobile (Sa, b).
    [8]
    8. Watch tourbillon according to claim 1,characterized in thatthe axis (ZC) of the double tourbillon (TD) and the axis (ZD) of the differential (D, 5) are parallel.
    [9]
    9. Watch tourbillon according to claim 1,characterized in thatthe chassis (CH / 52) of the differential (D, 5) comprises a base (521) carrying two pivots (526) aligned on its axis (ZD), one of which is provided with the input pinion (54), and the base (521) carries two plates (522) provided with bearings (523) between which the satellites (55) are installed.
    [10]
    10. Watch tourbillon according to claim 7,characterized in thateach planet gear (55a; b) consists of a long pinion (551a, b) and a short pinion (552a, b), the planet wheels (55a, b) of each pair being combined in head-to-tail position and with parallel axes to form a pair,the pairs of satellites being arranged in axial symmetry of 180 ° with respect to the axis of rotation of the differential,the long pinion (551a, b) of a satellite (55a) is cut so as to mesh both with the tubular pinion (531a, b) of the output mobile (53a, b) and with the short pinion (552b, a) the other satellite (555b, a) of this pair of satellites,the long pinion (551a, b) of each pair of planet wheels, meshing over part of its length with the tubular pinion (5312a, b) of the output mobile (53a, b) and over the other part of its length with the short sprocket (552b, a) of the same pair so that the tubular output sprocket (531a, b) and short sprocket (552b, a) are offset and not mesh.
    [11]
    11. Watch tourbillon according to claims 7 to 9,characterized in thatthe base (521) of the frame (52) of the differential (5) has notches (525) on its equator so as to allow the teeth (101) of the cage wheel (10) to pass through and reduce the bulk on the plane equatorial, all the satellites (55a, b) of the differential being indented and their axes clear (553a, b) to minimize the distance between the axis of the tourbillon (ZC) and that of the differential (ZD).
    类似技术:
    公开号 | 公开日 | 专利标题
    EP1706796B1|2007-06-13|Timepiece comprising two turbillons
    EP1738230B1|2009-04-08|Watch comprising at least two tourbillons
    EP2259157B1|2018-10-31|Clockwork for wristwatch
    EP2802942B1|2015-11-04|Timepiece having a plurality of balances
    EP1918790B1|2010-09-01|Tourbillon for watch movement and movement comprisingthe same
    EP1744229A1|2007-01-17|Timepiece
    EP2502118B1|2013-08-28|Timepiece movement
    CH717176A2|2021-08-31|Tourbillon with two oscillators in a cage.
    WO1999064936A1|1999-12-16|Method for transmitting bursts of mechanical energy from a power source to an oscillating regulator
    EP3120198B1|2020-05-27|Clockwork
    WO2018215284A1|2018-11-29|Adjustment device for timepiece with isotropic harmonic oscillator having rotating masses and a common return force
    CH695797A5|2006-08-31|Watch, has two tourbillons mounted on common rotating support, and connected by respective trains to differential gear that averages speed of carrier and output wheel in revolution speed of plate
    FR3070508B1|2019-09-06|WATCHMAKING MECHANISM AND WATCH
    CH716084A2|2020-10-15|Device for coupling two clock oscillators.
    CH705120B1|2012-12-31|Tourbillon mechanism for use in watch movement in timepiece field, has cage whose lower and upper bridges are provided with pivots to pivot cage, where lower bridge is wheel with external teeth kinematically connected to finishing train
    EP2189855B1|2012-11-14|Tourbillon mechanism
    WO2000004424A1|2000-01-27|Timepiece with mechanical regulation
    CH713829B1|2022-01-14|Regulation device for a timepiece with an isotropic harmonic oscillator having rotating masses and a common restoring force.
    EP0964319A1|1999-12-15|Method for the transmission of mechanical energy pulses from a driving source to an oscillating regulator
    WO2013104634A1|2013-07-18|Watch movement comprising a tourbillon for a chronograph
    CH708960A2|2015-06-15|Tourbillon or carousel mechanism.
    同族专利:
    公开号 | 公开日
    DE102021104441A1|2021-08-26|
    US20210263472A1|2021-08-26|
    FR3107603B1|2022-01-21|
    FR3107603A1|2021-08-27|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    CH702294B1|2009-11-16|2014-05-30|Complitime Sa|Movement timepiece.|
    CH711928A2|2015-12-18|2017-06-30|Montres Breguet Sa|Coupled clock oscillators.|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    FR2001889A|FR3107603B1|2020-02-26|2020-02-26|“Tourbillon with two oscillators in a cage”|
    [返回顶部]