Tourbillon with two oscillators in a cage

Abstract

Watchmaker's tourbillon comprising: A) a cage (CC) mounted to rotate about 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) with two control systems, each comprising an oscillator (OSa,b), an anchor, and a movable escapement element (MEa,b) located in the respective half-cage (1a, 1b); the two control systems consist of identical elements but are arranged oppositely and installed in each half-cage (1a, b) in a position symmetrical to the median plane (RC) such that the directions of rotation of the two movable escapement elements (MEa,b) are identical in the median plane; each control system has a fixed balance wheel (RFa,b) connected to its movable escapement element (MEa,b); B) a differential (D) comprising two outputs (Sa,b), each equipped with a fixed compensating wheel (RFa,b) are connected and create a positional compensation, - an input (ED) connected to the clockwork MH, C) a drive connection (EC) connecting the clockwork (MH) to the cage (CC) for a rotary drive about its axis (ZC).

Description

AREA OF INVENTION

[0001] The present invention relates to a watchmaker's tourbillon with two oscillators in a cage. STATE OF THE ART

[0002] The tourbillon, invented by Abraham-Louis Breguet in 1810, is a mechanism in which the escapement and balance spring regulator rotate inside a cage. The primary purpose of this mechanism is to average out the pendulum positions, thus mitigating any static and dynamic fluctuations in balance, which is useful in the case of a pocket watch. In practice, the results for chronometry in a wristwatch are controversial and do not compensate for the additional difficulty involved in constructing such a horological device. Nevertheless, the tourbillon remains a testament to the expertise of watchmaking and is visually captivating.

[0003] The tourbillon's principle is based on the fact that the escapement is returned to the seconds wheel. A fixed wheel supports the escape wheel. While the seconds wheel rotates with each impulse, the escapement actually rotates the cage and all its internal components. The cage's inertia is a crucial factor: if the cage is too heavy, its acceleration is reduced, and the impact on the escape wheel upon stopping is greater.

[0004] With each impulse, the balance wheel absorbs a small amount of energy from the escapement, causing it to rotate sometimes clockwise, sometimes counterclockwise. In contrast, the cage, whose rotation is released with each impulse, only reaches its release angle in one direction (clockwise or counterclockwise).

[0005] The balance spring used as a regulator is attached to the cage with a ring screw, which secures its terminal curve to the cage.

[0006] Consequently, during every second impulse, the cage and balance wheel move in the same direction, and the balance wheel receives one impulse from the pallet fork and one impulse in the same direction from the cage via the terminal curve of its hairspring. During the other half of the impulses, the balance wheel receives one impulse from the pallet fork and one impulse in the opposite direction via the terminal curve of its hairspring, since the movement of the cage and balance wheel is opposite.

[0007] In a conventional tourbillon configuration, half of the impulses therefore produce a higher amplitude than average, and the other half produce a reduced amplitude. The oscillator's operation is thus asymmetrical with respect to the equilibrium point.

[0008] While the influence of the cage on the balance wheel, although problematic, can be compensated for by adjusting the various components of the balance wheel, the influence of the movement of the balance wheel on the dynamics of the cage cannot be remedied.

[0009] When the escapement gives an impulse in the direction of the movement of the balance wheel, the cage's reaction is a movement in the opposite direction, thus slowing down the rotational movement of the cage and minimizing the shock when stopping.

[0010] If the escapement gives an impulse in the opposite direction to the rotation of the balance wheel, the cage's reaction is a movement in the direction of the cage's rotation, thereby accelerating the cage's rotation and causing an excessive shock upon stopping.

[0011] From the point of view of the escapement, the asymmetry between the two changes described by the balance wheel can also pose a problem as soon as the balance wheel passes through its free angle.

[0012] Once the balance wheel has received its initial impulse, the terminal curve of the balance spring exerts a pressure force on the cage during a change in the direction of rotation. This pressure force is transmitted by the escapement to the fixed wheel via its pressure, which is unproblematic and further secures the balance wheel.

[0013] The pallet fork is a safety feature of the escapement. The angle of the pallet fork and its contact with the teeth of the escape wheel ensure that, in the event of a shock, the pallet fork is returned to its resting position on the balance wheel. This safety feature minimizes the duration of disruptive contact between the pallet fork and the pallet fork by pressing the pallet fork against its limiting pins.

[0014] During a change in the direction opposite to the cage's rotation, its terminal curve, after the balance wheel has received its impulse, exerts a pulling force on the cage. This pulling force opposes the pressure exerted on the cage by the gear train and tends to push the cage back. As a result, the pressure of the escapement gear's wings on the teeth of the fixed wheel decreases, which in turn reduces the pressure of the escape wheel's teeth on the pallet fork's wings. Consequently, the pulling force decreases.

[0015] Thus, in a conventional tourbillon cage, which incorporates a balance spring regulator and a lever escapement, disturbances occur from the cage to the balance wheel and vice versa due to the balance wheel's inertia. There is also a risk of significant disturbances every other change due to the drop in tension when the balance spring is nearing its maximum deformation.

[0016] Currently, the closest design to addressing these problems inherent in the tourbillon cage is the H2 resonance tourbillon by Beat Haldimann. PURPOSE OF THE INVENTION

[0017] The purpose of the invention is to develop a watchmaker's tourbillon device in the geometric configuration of the control system which makes it possible to minimize the disturbances of the tourbillon cage. PRESENTATION AND BENEFITS OF THE INVENTION

[0018] For this purpose, the present invention relates to a watchmaker's tourbillon comprising: A) a cage mounted in such a way that it rotates about an axis and is divided into two half-cages by a median plane perpendicular to the axis of rotation, - a double tourbillon, each consisting of a regulating system comprising an oscillator, its anchor and its movable escapement element, located in each half-cage, - the two control systems consist of identical elements, but are arranged in opposite directions and installed in each half-cage in a symmetrical position to the central plane, so that in the central plane the directions of rotation of the two movable inhibiting elements are identical, - Each control system has a fixed compensating wheel that is connected to its movable locking element, B) a differential comprising - two outputs, each connected to a fixed compensating wheel, generating position compensation - an entrance connected to the clockwork mechanism, C) A drive link connecting the clockwork to the cage for a rotating drive around its axis. Thus, the watchmaker's tourbillon consists of two balance wheels in a rotating cage in two parts.

[0019] According to another property, the axes of the oscillators coincide along a principal axis that corresponds to the axis of the cage. - the oscillators and their components are identical or identical except for planar symmetry - the inhibition of the two oscillators is identical or identical except for planar symmetry.

[0020] This configuration according to the invention has two distinct advantages: When both balance wheels are in operation, they oscillate in opposite directions. In this way, the sum of the rotational inertia of the two balance wheels about their axis is always zero. The resultant of the forces exerted by the balance wheels on the cage is therefore zero. When the two oscillators are coupled for synchronization, the disturbance generated by the cage is distributed between them. Each oscillator in the system with two oscillators experiences less disturbance than if it were alone in the cage.

[0021] According to another advantageous feature, the balance wheels and spirals are identical in order to ensure the closest inertia.

[0022] According to another advantageous feature, the two spirals are located between the balance wheels in order to minimize the distance between the spirals and increase the compactness of the system.

[0023] According to another advantageous feature, the two spirals are identical in the winding direction to enable the synchronized development of the spirals during their operation.

[0024] According to another advantageous feature, the two inhibition assemblies are identical except for planar symmetry, in order to facilitate balancing the double cage along its main axis.

[0025] According to another property, the two oscillators comprise a flat spiral or a Breguet spiral.

[0026] According to another property, the inhibitions can be of any type (Swiss anchor, relaxation, etc.) as long as they are identical for the two oscillators.

[0027] In other words, the two oscillators are mounted in opposite directions, with one oscillator above and the other below the middle plane. - The plane of one escapement lies above the plane of the associated balance wheel, and the plane of the other escapement lies below the plane of the associated balance wheel and - The two spirals are located in the space bounded by the wheel rim of the tumbling blocks.

[0028] As already stated, the movable inhibiting elements are arranged in axial symmetry around the main axis of the cage. - the pivot axes of the movable tethering elements run parallel to the main axis of the cage and are arranged diametrically opposite to this main axis, as are the axes of the anchors.

[0029] According to another property, the cage is formed by a cage wheel that forms the median plane, with the half-cages on both sides each consisting of plates and bridges, - the movable locking element leaves its respective half-cage to engage with the fixed compensating wheel, which is aligned with the cage axis, and - The cage wheel has a toothed ring to drive the cage directly from the clockwork mechanism.

[0030] According to another characteristic, the differential is a flat gear differential, comprising: - a frame of the axis of rotation - two output gears on the axle, connected by at least one pair of compensating bevel gears installed in opposite directions, wherein each compensating bevel gear has two gears which are supported by the same axis, - the two compensating bevel gears mesh with each other via two corresponding gears and The other gear engages the two compensating bevel gears with a movable output element.

[0031] According to another property, the axis of the double tourbillon and the axis of the differential are parallel.

[0032] The differential frame comprises a base that supports two aligned pivot pins, one of which is fitted with the input gear, the base supporting two plates fitted with bearings, between which the compensating bevel gears are installed.

[0033] According to another property, each balancing bevel gear consists of a long gear and a short gear, with the balancing bevel gears of each pair being combined in opposite positions and with parallel axes to form a pair. wherein the pairs of compensating bevel gears are arranged in an axial symmetry of 180° with respect to the axis of rotation of the differential, the long gear of one compensating bevel gear is dimensioned such that it engages with both the tubular gear of the moving output element and the short gear of the other compensating bevel gear of this pair of compensating bevel gears, The long gear of each pair of compensating bevel gears engages with the tubular gear of the movable output element over part of its length and with the short gear of the same pair over the other part of its length, so that the tubular output gear and the short gear are offset and do not mesh.

[0034] In other words, the planetary gear comprises the following: - a long gear dimensioned so that it can mesh with the gear of the movable output element and the second planetary gear, - a short gear that engages only with the second planetary gear and does so without engaging with the gear of the counter-rotating movable output element, - a free axle section through which the toothing of the cage wheel can pass and the size of the differential cage system of a tourbillon can be minimized.

[0035] The planetary gears operate in pairs, and a single pair would suffice to generate the differential effect. However, according to the invention, there are preferably two pairs of compensating bevel gears positioned diametrically opposite each other to maintain the vector of the sum of the gear pressures on the differential axis. This protects the pivot pins from premature wear and does not create a preferred direction of engagement.

[0036] According to another particularly advantageous feature, the base of the differential frame has notches at its equator to allow the toothing of the cage wheel to pass through and to reduce the size on the equatorial plane, with all compensating bevel gears of the differential being notched and their axes being free to minimize the distance between the tourbillon axis and the differential axis.

[0037] In other words, in order to allow the axis of the differential to approach the axis of the tourbillon cage, the differential has the shape of an hourglass or a diabolo, and at its equator the teeth of the differential's compensating bevel gears are released.

[0038] Thus, the watchmaker's tourbillon according to the invention represents a particularly compact embodiment, which enables a significant improvement in the control of the mechanism. List of characters

[0039] The present invention is described in more detail below with reference to embodiments illustrated in the accompanying drawings, wherein: [ Fig. 1] General scheme 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 compensating gears. [ Fig. 3] Isometric perspective view of the skeleton 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 control systems, showing the symmetrical distribution of the elements along the axis of the cage. [ Fig. 6] Isometric perspective view of the tourbillon from Fig. 2, which clearly highlights the elements of the cage's inhibitions. [ 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 spirals [ Fig. 9] Sectional view of the cage's functional elements [ Fig. 10] Isometric perspective view of the differential and the drive gear meshing with the input gear of the differential. [ Fig. 11] Isometric perspective view of the differential with its frame [ Fig. 12] Simplified schematic view of the differential without frame [ Fig. 13] Side view of the differential without frame DESCRIPTION OF THE EXECUTION FORMS

[0040] Fig. Figure 1 is a general scheme of the watchmaker's tourbillon according to the invention, which consists of a double tourbillon TD consists of the clockwork mechanism MH through a differential D is connected, whose entrance ED with the clockwork MH is connected and whose two outputs Sa , Sb with the two outputs of the double tourbillon TD are connected, whose cage CC through the clockwork MH is being filmed.

[0041] According to watchmaking tradition, the functioning of the mechanism is described in terms of the force flow from the drive to the control, so that the description of the connection by the differential D which corresponds to the opposite of certain terminologies for input and output terms.

[0042] The speed of the clockwork MH is determined by the control system consisting of the double tourbillon TD and its two combined oscillators. The two oscillators have different frequencies, although they are close together, which implies that this difference must be compensated for to prevent the mechanism from stopping. The double tourbillon TD The imposed velocity (ω) is the average of the velocities ω1 = ((ω) + δω) and ω2 = ((ω) - δω) of the two oscillators OSa,b, since the frame CH the differential is thus pressed in order to align itself with the average speed ω 1 + ω 2 2 = ω to turn.

[0043] The watchmaker's tourbillon according to the invention T consists of the double tourbillon TD , that from a cage CC consists of a mechanism that rotates around the ZG axis while being driven by the clockwork. MH is driven by a gear train connected to the input EC the CC cage is in operation.

[0044] The cage wheel RC forms the middle plane of the cage CC There is an oscillator on each side of this layer. OSa or OSb These oscillators are housed in a housing. Due to their design and adjustable frequency, they have frequencies that are as close as possible to each other and cannot be completely identical in practice.

[0045] This slight frequency shift around the average frequency is accounted for by the differential. We call (ω)1 = (ω) + δω the velocity of one of the oscillators and ω2 = (ω) - δω the velocity of the other.

[0046] This frequency difference manifests itself through a shift in the speed of the compensating gears and thus in the speed of the differential outputs.

[0047] The average speed of these two speeds necessarily corresponds to the speed ω that the control system assigns to the clockwork. MH imposed.

[0048] Each oscillator OSa , OSb is equipped with a movable inhibiting element at the output. MEa ,b connected to the cage CC is carried and engages with a wheel, which here acts as a fixed compensating wheel. Rfa , RFb is designated as the one that is connected to one of the two inputs of the differential. D by a drive of the fixed wheel ERFa or is connected to ERFb.

[0049] The interlocking of the movable locking element MEa , b and the fixed compensating wheel RFa , b , which itself is a movable element, is not detailed, as this structure is in Fig. 1 appears clearly.

[0050] To simplify the execution, the movable inhibiting elements pass through MEa , MEb the cage CC not along its axis of rotation ZC , but these movable elements are offset from the sides of the cage CC worn. The fixed compensating wheels RFa , RFb run coaxial to the axis ZC of the cage CC ; this offset does not modify the movement produced by the movable locking elements MEa , MEb on the respective fixed compensating wheel RFa , RFb is transferred.

[0051] The differential D consists of a frame CH , which revolves around its axis ZD is rotated and coaxial to the axis ZD the movable starting elements Sa , Sb carries, each axis of which has a respective output gear Pa , Pb carries the two output gears Pa , Pb are through two “compensating bevel gears” STa , STb connected, which are separated from the frame CH They are carried. The compensating bevel gears reverse the rotational motion of the two gears. Pa , Pb according to the traditional operation of a differential.

[0052] In the case of the scheme of Fig. 1 is the differential D a differential with flat and non-conical gears, such that the compensating bevel gear is replaced by a pair of compensating bevel gears STa , STb formed with flat gears that perform this reversal of motion.

[0053] Each compensating bevel gear STa , STb consists of two gears ( ST1a long, ST2a (briefly) and ( ST1b long, ST2b (short), each attached to a common axis ASa, ASb, which is from the frame CH is worn: - the gears ST1a , ST1b Each is connected to one of the gears Pa , Pb in intervention. - the gears ST2a , ST2b interlock.

[0054] Since the number of teeth on the gears ST1a ... ST2b If the combination of the two compensating bevel gears is the same, it reverses. STa and STb the motion transmitted from one compensating bevel gear to the other, so that the motion of the two gears Pa , Pb The opposite occurs when the frame rotates at speed (ω) and the gears rotate at speed difference ± δω, as is actually specified by the operation of a differential.

[0055] The exits Sa , Sb The movements ω1, ω2 of the two oscillators are taken by the gears Pa , Pb on; since the pair of compensating bevel gears with the frame CH the axis of rotation ZD When connected, the frame will rotate according to the average speed ω = ω 1 + ω 2 2 around the axis ZD rotated, with the differences -δω and +δω being due to the relative rotation of the gears Pa , Pb in the opposite direction.

[0056] The watchmaker's tourbillon T therefore gives the clockwork MH the rotational speed (ω) that is generated by the double tourbillon TD is regulated.

[0057] For the purposes of the scheme from Fig. 1 The axes ASa, ASb are shown inclined to account for the angular offset of the two compensating bevel gears. Sa , Sb around the axis ZD within that framework CH to represent. In reality, one of the compensating bevel gears is located STa in front of the level in Fig. 1 and the other compensating bevel gear STb is located behind this level.

[0058] For reasons of balance and symmetry in the transmission of forces to the gears Pa , Pb The pair of compensating bevel gears STa , STb by a pair of compensating bevel gears ST'a , ST'b completed, which are identical in positions to those of the first pair with respect to the axis ZD are symmetrical.

[0059] The Fig. 2 to Fig. Figure 13 shows an embodiment of the watchmaker's tourbillon. T , whose various components in the figures are detailed by reference signs and, for remembrance, by the general references of the scheme from Fig. 1 are identified.

[0060] To illustrate the watchmaker's tourbillon T To simplify matters, given the identity of the shapes and symmetries, the components bear the reference symbols supplemented with the suffix (a) and the suffix (b).

[0061] Fig. Figure 2 shows an isometric perspective view of the entirety of an embodiment of the watchmaker's tourbillon, which consists of a double tourbillon TD consists of a differential 5 connected to the clockwork mechanism not shown in this figure.

[0062] The various parts of the double tourbillon TD are based on the Fig. 3-13 are described separately.

[0063] Fig. Figure 3 shows the skeleton of a half-cage, which is separated from the cage wheel. 10 is worn, both half-cages 1a , 1b have in common and the middle level RC of the cage 1 perpendicular to the axis of rotation ZC defined by the cage. The wheel 10 has a toothed ring 101 for its drive. It carries an escapement plate 11a through supports. 161 The escapement plate 11a carries the escapement bridge 13a.

[0064] The anchor bridge 12a is supported by the escapement plate 11a and the pivot pin 14a of the cage is attached to the anchor bridge 12a.

[0065] The cage elements are rigidly mounted. The escapement plates 11a, b are supported by struts. 16 on the shared bike 10 The anchor and brake bridges (12a, b and 13a, b respectively) are fastened via supports. 16mounted on the escapement plate 11a, b. The pivot pins 14a,b are mounted on the anchor bridges 12a,b.

[0066] The framework shown in 3 is recorded symmetrically in the sense defined above in order to receive the components of the other oscillator OSb taking these symmetry conditions into account.

[0067] Fig. Figure 4 shows an oscillator 4a, which, in the orientation of its shown position, is the upper one, which is in the Fig. 3 is installed in the half-cage shown. This oscillator 4a, taken on its own, has the usual overall structure of an oscillator, consisting of a wheel rim 41a of the balance wheel mounted on an axle 40a, the conical part of the axle 40a having a double plate 43a which carries an ellipse 44a.

[0068] A ring 42a, carrying a spiral 45a, is attached to the cylindrical part of the axle 40a. The spiral 450a installed in the wheel rim 41a consists of a body of an Archimedean spiral with a constant pitch and a Breguet terminal curve 451a. The terminal curve is connected to an eyebolt 46a, which is mounted in a common eyebolt holder. 15 is held, which is connected to the structure of the cage wheel. 10 is connected ( Fig. 5 and Fig. 6).

[0069] The anchor 3a, which consists of a plate 30a as well as its input wings 31a and output wings 32a, ends with a fork 33a which acts on the ellipse 44a of the oscillator 4a.

[0070] Fig. Figure 5 is a top view of the combination of the two oscillators 4a, 4b (as oscillator 4a is shown in Figure 5). Fig. 4) on the same axis ZC ( Fig. 1) on each side of the plane of the cage wheel 10, together, not shown. The two oscillators 4a, 4b are diametrically opposed and rotate in the same direction, as can be easily seen from the identical alignment of the escape wheels 21a, 21b.

[0071] Geometrically and in this configuration, the escapements are necessarily mirror images of each other. The operating principle of the Swiss lever escapement mechanism is well known and will not be described in detail here.

[0072] Oscillators 4a and 4b are necessarily identical and mounted in opposite directions. Their components (especially the ring 44a,b and the spiral 45a,b) are also geometrically identical and assembled in the same configuration when considered individually. Mounted in opposite directions and along the axis of the cage in Fig. Viewed from point 5, they appear to be planarly symmetrical to each other. Their movements are synchronized and opposite to each other. This is ideally the case, but there are a number of transition orders in which the frequencies are balanced and in which the movements are therefore not completely synchronous.

[0073] To balance the cage as much as possible, the axes of the two movable inhibiting elements 2a and 2b are parallel to the axis. ZC of the cage and arranged diametrically opposite to it. The axes of the two anchors 3a and 3b are also arranged diametrically opposite to the axis. ZC The cage is arranged diametrically opposite each other. This arrangement is in Fig. 5 shown.

[0074] The movable locking elements 2a,b consist of the gears 20a,b and the locking gears 21a,b. Each gear 20a,b rolls on a fixed differential gear 50a,b. To ensure the system's function during periods of non-synchronization, these two fixed differential gears are connected via two transmissions through the differential.

[0075] Fig. Figure 6 is a perspective view of the elements of Fig. Figure 5 additionally shows the two fixed compensating gears 50a and 50b and their relationship to the movable escapement elements. The meshing of gear 50a with the escapement gear 20a can be discerned. Only the position of the fixed compensating gears 50a and 50b is shown; their engagement with the drive pins has been omitted.

[0076] Fig. Figure 7 shows the combination of the two oscillators 4a, 4b in the skeleton. Fig. 3, which are formed by the symmetrical skeleton under the cage wheel 10 is completed and thus the cage1 of the double tourbillon TD educates.

[0077] The illustration is limited to the support elements of the double cage. 1a ,b, on the escapement (movable escapement element 2a,b and anchor 3a,b), on the oscillators 4a,b and on the elements 5a,b to set the cage in motion.

[0078] The cage 1 is caused by the interlocking 101 of the cage wheel 10 set in motion.

[0079] The fixed elements of the cage 1 correspond to a cage wheel 10 , the space between the two half-cages 1a , 1b in each of them. The escapement bridge 13a,b carries the anchor 3a,b and the movable escapement element 2a,b. The anchor 3a,b is positioned by the anchor bridge 12a,b, which also positions the oscillator 4a,b. The escapement bridge 13a,b positions the movable escapement element 2a,b.

[0080] The cage 1is held axially by its pivot pins 14a,b ( Fig. 3).

[0081] The layered orientation of the cage 1 appears in the side view of Fig. 8 and the sectional view of Fig. 9, wherein the components are distributed symmetrically on both sides of the axis of rotation ZC and the two eye bolts 46a, 46b on the double eye bolt carrier 15 , together, is highlighted.

[0082] The in the Fig. 1 and Fig. 11 differentials shown 5 ( D ) has a frame 52 up, which is based on a 521 consists of two pivot pins 526 are sunk. Two plates 522 , which the camps 523 the compensating bevel gears 55 They are secured with two screws each. 524 at the base 521 fastened. The pivot pins 526 define the axis of rotation ZD of the differential and serve as support for the rotation of the two movable output elements 53a,b.

[0083] The base 521 has two notches on the side 525 which are open towards the outside to allow the differential to be closer to the tourbillon TD is brought and the cage wheel 10 This can happen so that the framework 52 and the cage 1 around their respective axis ZD , ZC They can rotate and be as close to each other as possible to reduce the size.

[0084] The notches 525 span the median plane of the differential perpendicular to its axis ZD In other words, the basis of the framework 52 and his records 522 a cross-sectional shape which is at the angle of the diametrically opposite arrangement of the position of the two pairs of compensating bevel gears 55a,b; STa , STb ; ST'a , ST'b in relation to the axis ZD crosses and in the middle plane of the frame CH The base indicates 521 a notch 525 on, which is open to both outer sides of the base and the gears of the compensating bevel gears STa,b / ST'a , b leave the median plane for the free passage of the gear ring 101 of the cage CC free, so that an approximation of the axis ZD of the differential D with the axis ZC of the double tourbillon TD is made possible.

[0085] The frame 52 carries the input gear 54 of the differential, which is connected to the drive wheel 56 is involved, which is connected to the clockwork. MH is connected.

[0086] The movable output elements 53a,b each consist of a tubular gear 531 and an output wheel 532 , which is recessed on the tubular gear.

[0087] The compensating bevel gears 55 are assembled in pairs in opposite positions and the pairs are in the frame 52 in relation to the axis ZD installed in a symmetrical angular position.

[0088] The four compensating bevel gears 55 are identical.

[0089] According to the references shown in 11, a compensating bevel gear exists 55 from a tubular gear 551 and a flat gear 552 , which pass through an axis 553 are connected. The two gears 551 , 552 The flat or straight gears, which are equivalent to standard gears, have different lengths so that they can be combined and perform the inverse function of the compensating bevel gears; they mesh with the tubular gears. 531 the movable starting elements 53 one, as in the Fig. 12 and Fig. 13 shown.

[0090] In fact, according to sections 12 and 13, the compensating bevel gears 55a, 55b of the pair are installed in opposite directions and: * the compensating bevel gear 55a engages: - through its long gear 551a into the tubular output gear 531a - through its long gear 551a into the short gear 552b - through its short gear 552a into the long gear 551b * the compensating bevel gear 55b engages: - through its long gear 551b into the tubular output gear 531b - through its long gear 551b into the short gear 552a - through its short gear 552b into the long gear 551a

[0091] The long gear 551a,b of a planet gear 55a,b engages simultaneously with the tubular gear 531a,b of the movable output element 5a,b and with the short gear 552b,a of the other compensating bevel gear 55b,a of this pair of compensating bevel gears.

[0092] Since the axes of the compensating bevel gears are on a geometric cylinder of the axle ZD Each gear must be arranged in order to engage with the tubular gears 531a and 531b via their long gears 551a,b. 551 into the tubular gear 531 intervene without the gear 552 with the latter. It must therefore be above / below this tubular gear. 531 pass through, as in the side view in Fig. 13 shown. This pairwise interlocking of the gears 531 , 551 , 552 is caused by the asymmetry of the gear sizes 551 and 552enabled with respect to the equatorial plane of the differential.

[0093] The axes 553a,b of the compensating bevel gears 55a,b are in relation to the axis ZD diametrically opposite each other on a circle centered on this axis, so that the axes free through these 553 The dimension formed determines the possible degree of approximation of the differential. D and the double tourbillon TD defined. The notches 525 the base 52 are designed in such a way that this dimension around the axis ZD is not exceeded in the middle level.

[0094] The diametrically opposed arrangement of the pairs of compensating bevel gears in radial orientation and the radial transverse orientation of the base 52 and the plates 53 They form an otherwise balanced cross-shaped alignment.

[0095] This cross-shaped orientation is used in the Fig. 1, Fig. 12, Fig. 13 clearly highlighted.

[0096] Fig. Figure 12 also shows the rotation of the elements of the differential. 5 to: The movable output elements 53a,b are each moved at the speeds ω1 = ω-δω and ω2 = ω+δω (according to this example) driven, which causes the rotation about the axis ZD at a higher speed or at a lower speed than the average speed ω = ω 1 + ω 2 2 represents the functional principle of a differential.

[0097] In conclusion and summary, it should be noted that the structure of the differential of the embodiment ( Fig. 2) and those of the scheme ( Fig. 1) distinguish, whereby the scheme of Fig. 1 of a representation in the single plane of Fig. 1 corresponds and it was therefore not possible to implement the compact axial alignment of the differential in practice. D to show: In this embodiment, the frame runs through 52 the movable output elements 53a,b along the axis ZD axial, to the input gear 54 to be received axially beyond one of the two movable output elements 53a.

[0098] Referring again to the full view of Fig. 2 and on the general scheme of Fig. 1 the differential consists 5 ( D ) out of the box 52 ( CH ), which revolves around the axis ZD rotates. From the frame 52 ( CH ) the two movable output elements 53a are carried, b ( Sa,b ), which extend along the axis ZD rotate. The two gears of the movable output elements 53a, b They have the same number of teeth, which must be straight. They engage with the movable intermediate element 51a,b ( ERFa,b ) a.

[0099] The differential is a flat gear differential (straight gears), comprising: - a frame CH / 52 the ZD axis of rotation - two output wheels Sa , Sb on the axis ZD , which are fitted with at least one pair of compensating bevel gears STa,b ; ST'a,b are connected, which are installed in opposite directions, with each compensating bevel gear having two gears ST1a , ST1b ; ST2a , ST2b features which are supported by the same axis, - the two compensating bevel gears STa,b ; ST'a,b interlock * by two corresponding gears ST2a,b ; ST'2a,b and * through the other gear ST1a , ST1b ; ST'1a , ST'1b both with a movable output element Sa, b .

[0100] The compensating bevel gears 55a, b ( STa,b ) serve as a reverse connection to the two movable output elements 53a, b ( Sa,b The reversing gears work in pairs to cancel out the resulting pressure moments during engagement. The four compensating bevel gears 55 ( STa , STb , ST'a , ST'b They have the same number of teeth. The axes of rotation of the compensating bevel gears 55 STa,b are parallel to the axis of rotation ZD of the frame 52 ( CH ) of the differential 5 ( D The axes of the pairs of compensating bevel gears 55 ( STa,b ) are in relation to the axis of rotation ZD of the differential 5 ( D ) arranged diametrically.

[0101] The compensating bevel gears 55a,b ( STa,b ) simultaneously engage with their movable output element 53a,b (Sa, b), so that, as a result of the number of teeth of the elements present in the frame's reference system, the two output gears 532a,b ( Sa,b ) exhibit equal and opposite relative velocities.

[0102] According to the same reasoning, in a reference system outside the differential, the rotational speed of the frame is 52 ( CH ) equal to the average rotational speeds of the output gears 532a,b ( Sa,b ).

[0103] This stepped differential 5 ( D ) using flat wheels 53a,b, 55a,b (Pa,b, STa,b Figures 5a and 5b) illustrate the behavior of a differential with bevel gearing. Although this arrangement is more complex in terms of the number of elements, it allows the use of flat gears of a known standard (e.g., NIHS 20-25) instead of bevel gears, which are not very practical to manufacture for watchmaking, and allows a very efficient structure by pivoting between two bearings (for example, as opposed to pivoting around a recessed contact).

[0104] The two output gears 531 of the differential 5 are equipped with output wheels 532 ( Sa,b ) connected, which themselves are connected to two wheels of the movable intermediate element 51a,b ( ERFa,b ) intervene, which the compensating gears 50 (RF) are supposed to power them.

[0105] In this comparison of the general scheme ( Fig. 1) and the isometric perspective view of an embodiment according to Fig. The double tourbillon appears in 2 TD through his cage 1 ( CC ), wherein its cage wheel 10 ( RC ) into two half-cages 1a , b is divided, each with an oscillator 4a, b and its anchor 3a, b (OSa,b) and the movable locking element 2a, b ( MEa, b ) record. The interlocking 101 of the cage wheel 10 forms the entrance EC , which is from the clockwork MH is powered.

[0106] In a conventional tourbillon configuration, the fixed wheel serves as a support for the movable escapement element, which converts the rotation of the cage into a satellite rotational movement around the fixed wheel.

[0107] In the configuration according to the invention, it was decided to place the cage 1 ( CC ) to slow down and the remaining rotation via the fixed wheel 50(RF) (which becomes a compensating gear). The latter is therefore always under pressure against the escapement gear. 20 (ME), whereby the differential 5 ( D ) can be introduced to compensate for the speed differences between the two compensating wheels 50a,b ( RFa,b ) to be taken into account.

[0108] The differential 5 will be beyond the scope 52 ( CH ) turned, which has an input wheel 54 ( ED ) carries, which is rotated by the rest of the movement (not shown). Reference symbol list T Watchmaker's Tourbillon TD Double Tourbillon CC Tourbillon cage ZC axis of the double tourbillon RC cage wheel that defines the midplane OSa, b oscillator MEa, b Movable inhibitory element EC cage entrance RFa, b Fixed compensating gear D Differential ED input of the differential ZD axis of the differential CH Differential frame Sa, b output of the differential Pa, b output gear STa, b, ST'a, b Compensating bevel gear ST1a, b Long gear ST2a, b Short gear ERFa, b carrier of the fixed wheel MH clockwork 1 cage 1a, 1b Half cage 10 cage wheel 101 Toothing in the form of a toothed ring 102 Cage bridge 11. Hearing board 12 Anchor bridge 13. Barrier bridge 14 pivot points of the cage 15 Double ring bolt carrier (common) 16 support 161 Support of the circuit board bridge 2 Movable inhibiting element 20 Locking gear 21 Brake wheel 3 anchors 30 Anchor plate 31 Entrance wings 32 Exit wings 33 Fork 4 Oscillator 40 Balance wheel axis 41 Wheel rim of the balance wheel 42 Ring 43 Double plate 44 Ellipse 45 spiral 450 Archimedean spiral 451 End Curve 46 Eye bolt 5 Differential 50 Fixed compensating wheel 51 Movable intermediate element 52 frames 521 Base 522 plate 523 warehouses 524 screw 525 notch 526 pivot pins 53 Movable output element of the differential 531 tubular output gear 532 Output wheel 54 Input gear of the differential 55 Compensating bevel gear 551 Long gear 552 Short gear 553 Free axis 56 Drive gear of the differential

[0109] To simplify the presentation of the claims, not all similar references are systematically repeated within the claims. This only occurs when necessary for understanding.

Claims

[1] Watchmaker's tourbillon including: A) a cage (CC) mounted so that it rotates about an axis (ZC) and is divided into two half-cages (1a,b) by a median plane (RC) perpendicular to the axis of rotation (ZC), - a double tourbillon (TD) consisting of a control system comprising an oscillator (OSa,b), its anchor and its movable escapement element (MEa,b) located in each half-cage (1a, 1b), - the two control systems consist of identical elements, but are arranged in opposite directions and installed in each half-cage (1a, b) in a symmetrical position to the central plane (RC), so that in the central plane the directions of rotation of the two movable inhibiting elements (MEa,b) are identical, - Each control system has a fixed compensating wheel (RFa,b) connected to its movable locking element (MEa,b), B) a differential (D) comprising - two outputs (Sa,b) each connected to a fixed compensating wheel (RFa,b) and generating a position compensation - an input (ED) connected to the clockwork MH, C) a drive link (EC) that connects the clockwork (MH) to the cage (CC) for a rotary drive about its axis (ZC). [2] Watchmaker's tourbillon according to claim 1, characterized by , that: - the axes of the oscillators (4a, b) coincide along a principal axis that corresponds to the axis (ZC) of the cage (CC). - the oscillators (4a,b) and their components are identical or identical except for planar symmetry - the inhibitions (2a,b and 3a,b) of the two oscillators (4a,b) are identical or identical except for planar symmetry. [3] Watchmaker's tourbillon according to claim 1, characterized by , that: - the oscillators (4a,b) comprise a flat spiral or a Breguet spiral [4] Watchmaker's tourbillon according to claim 1, characterized by , that: - the two oscillators (4a,b) are mounted in opposite directions, with one oscillator (4a) above and the other oscillator (4b) below the middle plane. - the plane of one escapement (2a, 3a) lies above the plane of the associated balance wheel (4a), and the plane of the other escapement (2b, 3b) lies below the plane of the associated balance wheel (4b) and - the two spirals (45a,b) are located in the space bounded by the wheel rim (41a,b) of the unrest. [5] Watchmaker's tourbillon according to claim 1, characterized by , that - the movable inhibiting elements (2a,b; 3a,b) are arranged in axial symmetry around the main axis (ZC) of the cage - the pivot axes of the movable locking elements (2a,b; 3a,b) run parallel to the main axis (ZC) of the cage and are arranged diametrically opposite to this main axis, as are the axes of the anchors (3a,b). [6] Watchmaker's tourbillon according to claim 1, characterized by , that - the cage (1) consists of a cage wheel (10) forming the middle plane (RC), wherein the half-cages (1a,b) on both sides each consist of plates and bridges (10, 102a,b, 11a,b, 12a,b, 13a,b), - each movable escapement element (MEa,b) leaves its respective half-cage (1a, b) to engage with the fixed compensating wheel (RFa,b) which is aligned with the cage axis (ZC), and - the cage wheel (10) has a toothed ring (101) for its drive from the clockwork (MH). [7] Watchmaker's tourbillon according to claim 1, characterized by , that the differential (D, 5) is a flat gear differential, comprising: - a frame (CH / 52) of the pivot axis ZD - two output gears (Sa, Sb) on the axle (ZD) connected by at least one pair of compensating bevel gears (STa,b; ST'a,b) installed in opposite directions, each compensating bevel gear having two gears (ST1a, ST1b; ST2a, ST2b) supported by the same axle, - the two compensating bevel gears (STa,b; ST'a,b) mesh with each other via two corresponding gears (ST2a,b; ST'2a,b) and * through the other gear (ST1a, ST1b; ST'1a, ST'1b) both with a movable output element (Sa, b). [8] Watchmaker's tourbillon according to claim 1, characterized by , that the axis (ZC) of the double tourbillon (TD) and the axis (ZD) of the differential (D, 5) are parallel. [9] Watchmaker's tourbillon according to claim 1, characterized by, that the frame (CH / 52) of the differential (D, 5) comprises a base (521) which supports two pivot pins (526) aligned on an axis (ZD), one of which is provided with the input gear (54), and wherein the base (521) supports two plates (522) which are provided with bearings (523) between which the compensating bevel gears (55) are installed. [10] Watchmaker's tourbillon according to claim 7, characterized by , that Each compensating bevel gear (55a;b) consists of a long gear (551a,b) and a short gear (552a,b), wherein the compensating bevel gears (55a,b) of each pair are combined in opposite positions and with parallel axes to form a pair, wherein the pairs of compensating bevel gears are arranged in an axial symmetry of 180° with respect to the axis of rotation of the differential, the long gear (551a,b) of one compensating bevel gear (55a) is dimensioned to engage simultaneously with the tubular gear (531a,b) of the movable output element (53a,b) and with the short gear (552b,a) of the other compensating bevel gear (555b,a) of this pair of compensating bevel gears. The long gear (551a,b) of each pair of compensating bevel gears engages over part of its length with the tubular gear (5312a,b) of the movable output element (53a,b) and over the other part of its length with the short gear (552b,a) of the same pair, so that the tubular output gear (531a,b) and the short gear (552b,a) are offset and do not mesh. [11] Watchmaker's tourbillon according to claims 7 to 9, characterized by , that the base (521) of the frame (52) of the differential (5) has notches (525) at its equator to allow the toothing (101) of the cage wheel (10) to pass through and to reduce the size on the equatorial plane, wherein all compensating bevel gears (55a,b) of the differential are notched and their axes are free (553a,b) to minimize the distance between the axis of the tourbillon (ZC) and that of the differential (ZD).

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