EP3136187B1 - Mechanical clock comprising a tourbillon - Google Patents

Description

Technical area

The present invention relates to a mechanical movement with a tourbillon and a mechanical clock equipped therewith.

background

Tourbillons for mechanical watches and movements are well known. Here, the escape wheel, the anchor and the so-called balance of the movement are arranged on a bogie, which is coupled to the shaft of the second wheel, and thus the second drive, or firmly connected. The balance or balance axis typically coincides with an imaginary axle extension of the second drive. Finally, a gearwheel connected to the escape wheel meshes with a stationary gear wheel arranged coaxially with the balance axis, so that the tourbillon, and therefore its frame, undergoes a complete revolution per minute.

For the exact setting of a mechanical watch, it is necessary to stop the seconds display. In conventional movements this is usually realized by a so-called balance rest, which can be activated for example by pulling out a crown and deactivated by pushing the crown wheel back.

In watches with minute tourbillon, in which the seconds display is realized directly through the bogie of the tourbillon, the realization of such trouble-rest designed as extremely difficult and complicated.

A rest stop for a tourbillon, for example, is from the EP 2 793 087 A1 known. This has a with the balance engageable and axially to the balance axis movable brake element. To balance the clock with a time standard, it is thus possible to stop the balance and thus the tourbillon mechanism as desired.

Summary of the invention

In contrast, the present invention is an object of the invention to provide an improved rest stop for a tourbillon of a mechanical watch. In addition to stopping the tourbillon is also a zero position of the tourbillon for comfortable timing can be realized. This is to improve the operability and the time setting of the clock and also give the clock an increased range of functions.

This object is achieved with a movement with a tourbillon unit according to the independent claim 1 and with such a clockwork having clock according to claim 15. Advantageous embodiments are the subject of dependent claims.

In that regard, a clockwork of a mechanical watch with a tourbillon unit is provided. The movement has a board on which all movable components of the movement are arranged. The movement, in particular its tourbillon unit further has a frame connected to a second drive, rotatably mounted on the board frame and mounted on the frame balance. In addition to the balance, an escape wheel in operative connection with the balance is also mounted on the frame. The escape wheel is typically via an armature in operative connection with the balance. The balance, the anchor and the escape wheel form the inhibition of the mechanical movement. The second drive is typically coupled to an energy storage device, such as a barrel, which ultimately drives the movement.

The movement is further provided with a balance engageable with the balance rest device. By means of the balance stop device, the balance for stopping the movement relative to the board or relative to the frame at least temporarily fixed. Furthermore, the movement is provided with a zeroing device, which allows to adjust the angular orientation of the frame in a predetermined position, which preferably corresponds to the zero position of a mounted on the frame second hand. According to a preferred embodiment, the zeroing device is optionally rotatably engageable with the frame or with the board. The zeroing device is typically in the normal operation of the clock with the circuit board rotatably engaged.

That is, the zeroing device is fixed relative to or on the board, while the frame together with the entire tourbillon unit is subjected to a rotational movement relative to the board. When the movement is stopped, in particular for setting the time, the zeroing device is also detachable from the circuit board or rotatably decoupled, so that it can be rotated relative to the board. In this case, it is typically rotatably engaged with the frame. The zeroing device is thus always either with the frame rotatably engaged or rotatably engaged with the board or the zeroing device is even with both the frame and the circuit board rotatably engaged.

By selectively with the frame or with the board rotatably engageable zeroing device can be achieved to decouple the frame for adjusting the time at least temporarily from the energy storage device of the movement. By an alternate fixation or rotationally fixed connection of the zeroing device with the frame or with the board can be achieved that the zeroing device together with the frame to bring about a zero stop function also approximately under the action of the mechanical Energy storage of the movement, but decoupled from the minute or hourly drive of the movement in a defined zero position can be converted.

The optional engagement of the zeroing device with the frame or with the board can be done by successive and stepwise pulling out a crown, such as an elevator or Einstellkrone the clockwork. According to a preferred embodiment of the claimed movement, the crown may be in three different axial positions, ie a first so-called rest position in which, for example, a barrel can be wound through the crown as usual, a second position in which the balance is stopped, eg according to the solution of EP2793087 , and a third further drawn axial position in which the zeroing device is no longer engaged with the board, but now with the frame in engagement. In this third position of the crown then the zeroing device and the frame can be rotated as a whole on the second drive through the drive, and thus the zero position of the frame is done automatically, the minute hand position can be provided by turning the crown in this position. Preferably, there may also be a minute catch, including handgrinding in a minute wheel assembly similar to the patent EP2224294 shown; the tourbillon unit and the zeroing device according to the present invention are compatible with it thanks to the constant engagement between the minute wheel, small bottom wheel and second drive.

According to a development, it is provided that in a basic configuration, the zeroing device is fixed against rotation on the circuit board. In the basic configuration, the crown is in a basic position, in which the movement is driven by the mechanical energy storage in motion. Due to the fixation on the board, the zeroing device acts as a kind of basis for the tourbillon unit. It may be provided in particular that the tourbillon unit or part thereof with the Zero setting are in operative connection. In the basic configuration with a zero-setting device fixed on the board, this only acts as a carrier for other mechanical components of the movement, for example for the tourbillon unit or for individual components thereof.

According to a further embodiment, the zeroing device is non-rotatably coupled to the frame when the balance is stopped by means of the balance rest stop device. In the basic configuration, the frame is freely rotatably mounted relative to the board. That is, only under the influence of the inhibition, the frame rotates relative to the board under the action of the spring drive outgoing mechanical drive energy. Once the frame is stopped by means of the balance stop device and fixed relative to the board, the zeroing device can be coupled either directly or indirectly with the frame rotatably.

It is conceivable that the zeroing device and the balance stop device interact with one another in such a way that the zeroing device is rotationally fixedly coupled to the frame by activating the balance stop device. It is also conceivable that the zeroing device is already firmly connected to the balance stop device. A fixation of the frame relative to the board by means of the balance rest device thus inevitably leads to a rotationally fixed fixing of the frame relative to the zeroing device.

By a direct or indirect coupling of zeroing device and frame can be achieved that about the purpose of setting the clock, the zeroing device is rotatably connected to the frame. By means of the zeroing device can then be transferred from any position in which the frame was stopped, the frame fixed thereto in a defined zero position in which a second hand arranged on the frame pointer points to zero.

According to a further embodiment, the balance stop device has a bogie and frictionally engaged with the balance in Engage engageable axially to a balance axis movable brake element. By means of such a braking element, a balance rest can be realized, which exerts no radial asymmetric forces on the balance or on the bogie of the tourbillon. By means of such a brake element, the balance can also be braked directly via the brake element, in particular stopped. By slowing down and stopping the balance will inevitably stop the rotation of the tourbillon, that is, the rotational movement of the bogie.

Due to the axial mobility of the brake element, this can come about with an axially aligned end face of the balance or with a fixed connected to the balance section, such as with a non-rotatably connected to the balance double role decelerating engaged. The balance can thus be braked and stopped directly or indirectly, so that when the balance is activated, the balance must not be re-vibrated. The fact that the balance-rest device acts exclusively on the balance in the axial direction makes the balance-rest stop device particularly suitable for achieving a rest stop in the case of a flying tourbillon.

Due to the frictional interaction of brake element and balance can also be achieved to increase the braking element acting on the balance friction force upon activation of the braking element abruptly or steadily. The latter allows in particular a muted nachschwingfreies stopping the balance. A frictional braking of the balance also allows the balance to be stopped in any arbitrary orientation and position of the balance.

According to a further embodiment, it is further provided that the zeroing device via the brake element rotatably coupled to the frame. The zeroing device can, in particular, act directly or indirectly on the brake element arranged, for example, on the frame. The zeroing device, but at least individual components or parts thereof may or may be in particular in the power flow of the balance rest stop device.

According to a further embodiment, the zeroing device by means of a fixing member rotationally fixed to the board can be fixed. By means of the fixing element, the zeroing device can optionally be fixed in a rotationally fixed manner to the printed circuit board or else detached therefrom, so that the zeroing device is rotatable with respect to the printed circuit board.

In this case, it is further provided that the fixing element can be transferred only in a rotationally fixed coupling of frame and zeroing device in a release position, in which the zeroing device is rotatable together with the frame relative to the board. By virtue of the fact that the fixing element can be transferred into a release position only after a rotationally fixed coupling of the frame and the zeroing device, it is possible to prevent the drive force emanating from the mechanical energy storage device of the movement from being released in an uncontrolled manner.

If the frame is coupled to the zeroing device and the fixing element is transferred to the release position, typically an optionally damped rotational movement of the ensemble formed by frame and zeroing ensembles, wherein the bogie is operatively connected by the activated balance device with the energy storage device of the movement. The second drive of the tourbillon is in this configuration still with the energy storage device of the movement, such as the barrel, in mechanical operative connection.

According to a further embodiment, a pawl is further arranged to be movable on the board. This cooperates with a frame arranged on the locking cam to stop the frame in a neutral position. The pawl, for example, can be transferred radially inwardly into a locking position, in which they are so with the locking cam of the Gestells cooperates, which prevents rotation of the frame beyond the pawl or past the pawl.

The latching cam may, for example, protrude radially outward from the frame. The pawl is, for example, in a radially inwardly engaged detent position and the zeroing device together with the frame subject of a rotary motion at a located in the release position fixing element, the locking cam of the frame comes into engagement with the pawl. The pawl thus acts as an end stop for the locking cam and thus for the frame so that it comes to rest in the intended zero position for adjusting the movement.

According to a further embodiment, the pawl is coupled to the fixing element. The pawl is at least only in a detent position for stopping the frame when the fixing passes from the fixing position in the release position. The pawl and the fixing are so far rigidly coupled together. If the ensemble of frame and zeroing device is released for rotational movement, the pawl engages radially inward to stop the free rotation of the ensemble at a fixed predetermined position.

The mutual arrangement of detent cam and pawl thus determines the zero position of the frame and thus the arranged on the frame second hand of the tourbillon.

According to a further embodiment, the zeroing device has a carrier wheel with a rim-like circulation tire. The circulating tire is rotatably mounted on its outer circumference at least three arranged on the board bearing rollers. The zeroing device has in particular a ring-like basic geometry. In a final assembly configuration of the movement, the hub of the tourbillon unit typically extends through the remaining center of the nulling device. By means of a bearing over the outer circumference on the carrier wheel, the Zeroing device are also moved independently of the hub of the tourbillon unit rotatable on the board.

According to a further embodiment, the zeroing device on a ring-like epicyclic gear with an internal toothing, which meshes with a pinion of the escape wheel. The planetary gear of the zeroing device, which is also fixed relative to the board in the basic configuration or while the movement is running, meshes with the escape wheel. The escapement wheel moves in particular due to the teeth of its pinion with the internal toothing along that internal toothing, when the tourbillon unit is subject to a prevailing during operation of the movement rotational movement. In the basic configuration, the zeroing device acts in this respect as an extended board, on the internal toothing of which the escape wheel runs along with its pinion.

According to a further embodiment of the movement, the zeroing device has a, relative to its axis of rotation, axially movable stop ring. This has on a radially outer edge on a run-on slope, which corresponds to a run-on slope of a movable arranged on the board stop pawl. Typically, two diametrically opposed stop pawls are provided. These can experience a radially inwardly directed movement in the direction of the stop ring with a pulling out of the crown.

By the mutually corresponding and with respect to their slopes matched ramps of stop ring and stop pawl or stop pawls, the stop ring undergoes an axial movement when the stop pawl or the pawls are moved radially inward. By means of the mutually corresponding run-up slopes of stop ring and stop pawl or stop pawls, a radial movement can thus be converted into an axial movement.

According to a further embodiment, that axially on the zeroing device movably mounted stop ring at a radial inner edge of a further run-on slope, which cooperates with at least one cam at least one against a restoring force radially inwardly mounted on the zeroing device pawl. In this way can be pivoted radially by an axial displacement of the stop ring relative to the zeroing device, in particular with respect to the at least one axially adjacent thereto latch mounted pawl.

In particular, it is provided that the at least one pawl of the zeroing device can be deflected radially inwards by an axial movement of the stop ring induced by means of the at least one stop pawl. By the mutual engagement of the stop pawl, stop ring and pawl of the zeroing device can be achieved that a radially acting from the outside radially to the zeroing device pivoting movement is converted into a pivoting movement of a radially inside provided on the zeroing device pawl.

According to a further embodiment, the at least one pawl at its radially inner end on a run-on slope, which is engageable with a run-on slope of a brake ring. The brake ring is typically disposed axially adjacent the pawl and is also axially slidable relative to the zeroing device on a major axis of the tourbillon unit, for example, on the hub of the tourbillon unit. Since the at least one pawl and the brake ring engaging therewith have mutually corresponding run-on slopes, the typically radially inwardly directed pivoting or adjusting movement of the pawl can be transmitted into an axially directed displacement movement of the brake ring.

According to a further embodiment thereof, it is finally provided that a brake pin is axially movably guided in a hub of the tourbillon unit or in the frame and for the deflection of the brake element and for stopping the balance by means of the brake ring axially is displaceable. The brake pin is in particular against a restoring force, in particular against the action of a spring element axially displaceable to the brake ring. In particular, the brake pin deflects the brake element, which is movable axially relative to the balance spring, in such a way that it frictionally engages with the balance and finally stops the balance.

At the zeroing device is typically not only one, but there are several, approximately three circumferentially equidistantly arranged pawls provided, which perform a synchronous, radially inwardly directed movement due to an axial movement of the adjacent thereto arranged stop ring. Accordingly, a possible uniform and symmetrical displacement force can be exerted on the brake ring, which ultimately leads to the axial propulsion of the brake pin.

According to a further aspect, finally, a watch, in particular a mechanical wristwatch is provided, which is equipped with a previously described movement.

Brief description of the figures

Fig. 1

eine Draufsicht auf Teile des Uhrwerks,

Fig. 2

eine Seitenansicht des Uhrwerks gemäß Fig. 1,

Fig. 3

eine perspektivische Darstellung des Uhrwerks,

Fig. 4

eine Draufsicht auf die Nullstelleinrichtung in Grundkonfiguration von unten mit abgenommenem Stoppring,

Fig. 5

einen Querschnitt durch die Nullstelleinrichtung gemäß Fig. 4,

Fig. 6

eine Draufsicht auf die Nullstelleinrichtung von oben,

Fig. 7

eine Darstellung der Nullstelleinrichtung gemäß Fig. 4, jedoch mit radial nach innen ausgelenkten Klinken,

Fig. 8

einen Querschnitt durch die Nullstelleinrichtung gemäß Fig. 7,

Fig. 9

eine Draufsicht auf die Nullstelleinrichtung gemäß Fig. 7 von oben,

Fig. 10

eine Explosionsdarstellung der Nullstelleinrichtung,

Fig. 11

einen Querschnitt A-A gemäß Fig. 6 in einer Endmontagekonfiguration mit Tourbilloneinheit,

Fig. 12

einen Querschnitt B-B gemäß Fig. 9, ebenfalls mit Tourbilloneinheit,

Fig. 13

eine perspektivische und teils Explosionsdarstellung des Uhrwerks in Grundkonfiguration und

Fig. 14

eine der Fig. 13 entsprechende Darstellung des Uhrwerks, jedoch bei aktivierter Unruhstoppvorrichtung und mit einer in Lösestellung befindlichen Nullstelleinrichtung.

Other objects, features and advantageous embodiments will be explained in the following description of an embodiment with reference to the drawings. Hereby show:

Fig. 1

a top view of parts of the movement,

Fig. 2

a side view of the movement according to Fig. 1 .

Fig. 3

a perspective view of the movement,

Fig. 4

a top view of the zeroing device in basic configuration from below with the stop ring removed,

Fig. 5

a cross section through the zeroing device according to Fig. 4 .

Fig. 6

a top view of the zeroing device from above,

Fig. 7

a representation of the zeroing device according to Fig. 4 , but with radially inwardly deflected pawls,

Fig. 8

a cross section through the zeroing device according to Fig. 7 .

Fig. 9

a plan view of the zeroing device according to Fig. 7 from above,

Fig. 10

an exploded view of the zeroing device,

Fig. 11

a cross section AA according to Fig. 6 in a final assembly configuration with tourbillon unit,

Fig. 12

a cross section BB according to Fig. 9 , also with tourbillon unit,

Fig. 13

a perspective and partially exploded view of the movement in basic configuration and

Fig. 14

one of the Fig. 13 corresponding representation of the movement, but with activated balance stop device and with a release position located in the zeroing device.

Detailed description

In the Fig. 1 to 3 For example, a tourbillon unit 10 of a mechanical movement 1 not shown in its entirety is illustrated. The movement 1 has a board 2, on which the tourbillon unit 10 is rotatably mounted. The tourbillon unit 10 is, as from a synopsis of Fig. 2 and 11 emerges coupled via a second drive 5 with a Kleinbodenrad 7. The Kleinbodenrad 7 meshes with a minute wheel 8, which is in engagement with a barrel 9, which in the present case acts as a mechanical energy storage device.

The tourbillon unit 10 also has an in Fig. 11 shown in cross-section hub 6, which is rotatably mounted on the board 2 and fixedly connected to a frame 11 of the tourbillon unit 10.

The frame 11 comprises a lower frame 11a with various radially aligned spokes 11d, via which the frame 11 is connected to the hub 6. About the outer circumference of the lower frame 11 a three vertically or axially aligned pillar 11 c are arranged in the present case. At the lower frame 11a facing away from the end portion, an upper frame 11b is arranged. Between the upper and the lower frame 11a, 11a, the balance 15 of the movement 1 is mounted. The balance 15 is pivotally mounted with respect to a balance shaft 17, wherein the balance shaft 17 is in extension of the second drive 5.

The balance 15 is further coupled to a balance spring 16. On the frame 11, an escapement 14 is also provided. On the frame 11 so far an escape wheel 12 is rotatably mounted. The axis of rotation of the escape wheel 12 in this case extends parallel to the balance axis 17. The escapement 14 also has an anchor, which is not explicitly shown here, which alternately engages with the teeth of the escape wheel 14 in a known manner. The balance 16, the anchor not explicitly shown and the escape wheel 12 form the escapement 14.

As seen from the cross section of FIGS. 11 and 12 shows, the escape wheel 12 is provided with a pinion 19 which meshes with an internal toothing 49 of a zeroing device 40. The zeroing device 40 is fixed to the board 2 during normal operation of the movement 1. The stepwise rotational movement of the escape wheel 12 thus leads to a rotation of the entire frame 11 with respect to the board 2. On the frame 11, a second hand 18 is further arranged, which protrudes with a pointer tip radially outwardly from the frame 11, in this case from the upper frame 11b , The rotational position of the frame 11 thus reflects the seconds of a time display.

In addition to the zeroing device 40, the movement 1 on a balance stop device 50, by means of which the balance 15 can be stopped or stopped if necessary.

The multi-part construction of the zeroing device 40 is based on Fig. 4 to 10 clarified. The zeroing device 40 has a carrier wheel 41, which centrally has a passage opening 71. The carrier wheel 41 has an annular contour. The central passage opening 71 is delimited in particular by an inner edge 72, as shown in FIG Fig. 4 is indicated. From the inner edge 72 project over the circumference of the inner edge 72 distributed distributed pawls 45 radially inwardly. These are rotatably or pivotally mounted in the plane of the carrier wheel 41. They are like a comparison of Fig. 4 and 7 clarified, radially inwardly deflectable.

Each of the pawls 45 has at its free and inwardly projecting end on a Steueranlaufschräge 45 a. At the bottom of the pawls 45, a dome-shaped latch cam 47 is formed in each case. Further, each of the pawls 45 is coupled to a pawl spring 46, by means of which the individual pawls 45 are deflected radially inwardly against a spring force. The radially inwardly directed deflection takes place via an axial force acting on the pawl cams 47. With decreasing force effect, the individual pawl springs 46 cause a movement of the pawls 45 radially outwards, in the in Fig. 4 shown starting position.

At the radially outer edge of the carrier wheel 41 of the zeroing device 40 is, as in Fig. 5 shown, on the one hand a circulating tire 44 is formed. Axially offset thereto, the carrier wheel 41 has an external toothing 48. At the top of the carrier wheel 41, a peripheral wheel 42 is arranged. The planet wheel 42 also has an annular contour. On an inner side of the planetary gear 42 is a circumferential internal teeth 49 formed, which, as already mentioned, with the pinion 19 of the balance 15 meshes.

On the underside of the carrier wheel 41, a stop ring 43 is further attached. The stop ring 43 has an outer run-on slope 53 on its outer edge. In addition, the stop ring 43 is mounted axially displaceably on the carrier wheel 41. The stop ring 43 further has, as in Fig. 5 shown via a further run-on slope 54 at its inner edge.

Due to the rotationally fixed connection and axial displaceability of the stop ring 43 and the carrier wheel 41, the inner starting bevel 54 of the stop ring 43 can engage with the pawl cams 47. An upward axial movement of the stop ring 43 towards the carrier wheel 41 thus causes a radially inwardly directed deflection of the three pawls 45. This is based on a comparison of Fig. 5 and 8th or the Fig. 6 and 9 recognizable.

The entire zeroing device 40 is rotatably mounted on the circuit board 2 via the circulating tire 44 at a plurality of bearing rollers 31 distributed over the circumference of the zeroing device 40. In addition, the zeroing device 40 via a fixing element 30, which is configured here as a fixing lever, on the circuit board 2 releasably fixed. A free end of the fixing element 30 is frictionally engaged with an outer edge of the zeroing device 40, for example.

By a pivoting movement of the fixing element 30, the zeroing device 40 can be released so that it is rotatable relative to the board 2 with respect to a central axis of rotation 73. The axis of rotation 73 of the zeroing device 40 may coincide in particular with the balance axis 70 and with the axis of the secondary drive 5.

On a top side of the lower frame 11a, a brake element 60, in the present case in the form of a flat brake spring, is also arranged. The brake element 60, in particular its free and radially inwardly projecting end, is arranged axially movably on the frame 11. It is in particular by means of an axially displaceable in the hub 6 or on the frame 11 brake pin 58 from a starting position, as in Fig. 11 shown in a braking position, as in Fig. 12 shown, deflectable.

The brake pin 58 is located with a head in a recess of the lower frame 11 a. By an axially upward deflection of the brake pin 58 presses axially on the brake member 60, so that its free end rubbing and in the axial direction with a corresponding thereto configured friction surface of a double roller 62 engages, which is connected to the balance 15. In this way, the balance 15 can be stopped and fixed with respect to the frame 11.

The brake pin 58 is by means of an axially displaceably mounted brake ring 56 of the in Fig. 11 shown initial or basic position in the in Fig. 12 shown braking position can be transferred. Radially outward and at the lower end, the brake ring 56 on a run-on slope 56a, which is formed circumferentially and corresponding to the control starting slope 45a of the pawls 45 configured. A radially inwardly directed pivoting movement of the pawls 45 thus leads to an upward, in the direction of the frame 11 directed axial displacement of the brake ring 56, whereby the brake pin 58 and hereby also the brake member 60 axially displaced or axially deflected. By the radially inwardly directed pivoting movement of the pawls 45, the brake element 60 finally comes with the double roller 62 of the balance 15 into engagement.

The axial displacement of the brake ring 56 relative to the hub 6 or relative to the frame 11 takes place counter to the restoring force of a spreading spring 57, which is arranged axially between the hub 6 and the brake ring 56. For example, the pawls 45 under the action of their respective pawl springs 46 back into the in Fig. 4 swung back starting position shown, takes place under the action of the spreading spring 57 also equally a movement of the brake ring 56 in his in Fig. 11 shown starting position. As a result, the balance 15 is released again, causing the stopped movement 1 automatically starts again.

To stop the movement 1 and the tourbillon unit 10, two opposing first and second stop pawls 20, 22 are provided on the outer circumference of the zeroing device 40, as these in Fig. 13 are shown. The first stop pawl 20 and second stop pawl 22 are pivotally mounted on the board 2. At their free ends in each case a first run-on slope 21, and a second run-on slope 23 are provided. These are formed for example in the form of conical wheels. The respective first and second run-on slopes 21, 23 of the respective first and second stop pawls 20, 22 are located at the level of the outer run-on slope 53 provided on the outer edge of the stop ring 43.

A radially inwardly directed pivoting of the first and second stop pawls 20, 22 leads to a uniform lifting or axial displacement of the stop ring 43 from the in Fig. 11 shown starting position or basic configuration in the in Fig. 12 illustrated stop configuration. For the sake of simplicity, the position of the first and second chamfers 21, 23 in the FIGS. 11 and 12 not explicitly shown. The axial movement of the stop ring 43 leads, as already described, to the radially inwardly directed deflection of the pawls 45 and thus to an axial displacement of the brake pin 58 and ultimately to the balance 15 lasting deflection of the brake element 60th

That one stopping of the movement 1 causing synchronous pivotal movement of the two first and second pawls 20, 22 can be done by pulling a crown in a predetermined detent position. The movement 1 is thus stopped. Is the present not explicitly shown crown, starting from that stop configuration in a further, for example, pulled out in a second detent position, this causes a coupled pivoting of the fixing element 30 and a pawl 26th

It is initially provided that the in Fig. 13 shown pawl 26 is moved radially inwardly, so that at its free end radially inwardly projecting locking lug 27 comes to rest radially overlapping to a arranged on the outer periphery of the frame 11 locking cam 28. In that regard, the pawl 26 is out of its in Fig. 13 shown starting position in an in Fig. 14 indicated detent position can be transferred. In this prevents the pawl 26 that the frame 11 can be rotated with its locking cam 28 on the position of the locking lug 27.

In the course of a zeroing operation, the frame 11 is freely rotatably mounted on the board 2. Due to the mutual engagement of pawl 26 and locking cam 28, a defined end stop for the frame 11, thus created for the entire tourbillon unit 10, so that the second hand 18 typically comes to rest on the twelve. After the pawl 26 is engaged in its detent position, in the course of the pull-out movement of the crown, the fixing element 30 engaging with the zeroing device 40 is deflected radially outward. As a result, the zeroing device 40 is transferred into a release position, so that their rotational fixation is canceled relative to the board 2.

The coupled movement of pawl 26 and fixing member 30 is via an in Fig. 13 indicated control lever 24 initiated. The pivoting movements of the fixing element 30 and the pawl 26 are rigidly coupled together. It is in any case necessary to ensure that the fixing lever 30 can only be transferred to its release position when the pawl 26 is in its locked position.

For adjusting the clock as the control lever 24 by pulling a crown out of a basic position out in a first moved outward position, this causes a radially inwardly directed pivoting of the two first and second stop pawls 20, 22. As a result, the balance 15 is stopped. The balance 15 is thereby fixed to the frame 11 and to the hub 6. In that configuration, the rack and the nulling means 40 form an ensemble which is rotatable relative to the board 2 in common.

Next comes the pawl 26 due to a further extension movement of the crown in the in Fig. 14 indicated detent position. Finally, in a final step, the fixing element 30 is transferred to the release position, so that the ensemble of zeroing device 40 and frame 11 is rotatable about the bearing rollers 31 with respect to the board 2. The second drive 5 of the tourbillon unit 10 in this case remains in engagement with the barrel 9. The still existing power flow between the tourbillon unit 10 and the barrel 9 causes the frame 11 together with the zeroing device 40 rotates until the locking cam 28th with the pawl 26 engages.

In this axial position of the crown, the second hand 18 thus automatically moves into a well-defined zero position or zero position, without the crown having to be further manipulated. Here, the usual interaction of a zeroing lever with a common zero heart is no longer needed. Since the zero position of the secondary pointer 18 is effected by a combined rotational movement of the zeroing device 40 and the tourbillon unit 10 driven by the barrel via the second drive 5, this rotary movement can preferably be damped or braked by means of a separate braking mechanism. The braking mechanism not explicitly shown here, for example, can be permanently engaged with the external toothing 48 of the zeroing device 40, for example. That braking device can act, for example, as a rotary damper. It can for example comprise a so-called windscreen, which limits the free rotational movement of the zeroing device 40 to a predetermined maximum speed. According to a preferred embodiment, not shown, the rotary damper is realized as a hydraulic damper module which is in engagement with the external toothing 48 of the zeroing device 40 via an intermediate gear. Thus, both the gear ratios in this transmission chain, as well as the viscosity of the liquid of the hydraulic damper module can be adjusted for an adapted rotational speed.

The conical first and second chamfers 21, 23 are used in addition to the bearing rollers 31 of the radial and axial bearing of the zeroing device 40 on the board. 2

If the crown of the movement 1 is again engaged stepwise, the fixing element 30 first comes into frictional engagement with the zeroing device 40 again. Then the pawl 26 is transferred from its rest position back to a starting position. As a result, on the one hand, the zeroing device 40 is again fixed to the board 2, while the frame 11 is disengaged from the pawl 26.

To automatically restart the movement 1, it is only necessary to move the two first and second stop pawls 20, 22 radially outwards again by further engagement of the crown. As a result, the force on the stop ring diminishes. This is in particular by the pawl springs 46 and the mutual engagement between pawls 45 and stop ring 43 back in his in Fig. 5 converted starting position shown. At the same time there is an axial displacement of the brake ring 56 in its initial position under the action of the spreading spring 57. The brake pin 58 thus reaches its starting position and the brake element 60 releases the double roller 62 of the balance 15 again.

Due to the interaction of zeroing device and rest stop device 50, it is possible for the first time, an entire Tourbilloneinheit 10 independently controlled by the escapement 14 in the movement 1 to move. This independent movement makes it possible to move a tourbillon unit 10 in any conceivable position faster and automatically to a reference point. This option is particularly suitable for a so-called minute tourbillon, which also serves as a seconds display. In that regard, a second zero stop is provided for a setting operation of the movement 1.

In this case, it is particularly advantageous that no radial forces act on the tourbillon unit, neither when stopping the balance 15, nor during the zeroing process. The inhibitor 14 is namely stopped during the zeroing process and thus protected against external influences. Furthermore, the embodiment shown here of the zeroing device 40 with the balance stop device 50 allows little constructive interference with an existing flying tourbillon, as for example from the EP 2 793 087 A1 is known.

LIST OF REFERENCE NUMBERS

1

clockwork

2

circuit board

5

second pinion

6

hub

7

Third wheel

8th

minute wheel

9

barrel

10

Tourbilloneinheit

11

frame

11a

lower frame

11b

upper frame

11c

pier

11d

spoke

12

escape wheel

14

inhibition

15

balance

16

balance spring

17

balance axis

18

second hand

19

Pinion of the anchor wheel

20

First stop pawl

21

First run-up slope

22

Second stop pawl

23

Second run-up slope

24

control lever

26

pawl

27

locking lug

28

locking cam

30

fixing

31

bearing roller

40

Zero setting device

41

carrier wheel

42

bull wheel

43

stop ring

44

circulation Reif

45

pawl

45a

starting slope

46

pawl spring

47

latch cam

48

external teeth

49

internal gearing

50

Balance stop device

53

Outside run-up slope

54

Inner run-up slope

56

brake ring

56a

starting slope

57

splay

58

brake bolt

60

braking element

62

dual role

71

Through opening

72

inner edge

73

axis of rotation

Claims (15)

1. Clockwork movement with a tourbillon unit, comprising:

   - a base plate (2),

   - a cage (11) placed rotatably on the base plate (2), and being connected to a fourth pinion (5),

   - a balance (15) placed on the cage (11) and an escape wheel (12) that is placed on the cage (11) and that is in work connection with the balance (15),

   - a balance stop device (50) being capable to be brought into engagement with the balance (15), characterized in that it further comprises

   - a zero-setting device (40) for the angular orientation of the cage (11).
2. Clockwork movement according to claim 1 wherein said zero-setting device can be torque-proof engaged either with the cage (11) or with the base plate (2) and the zero-setting device (40) is torque-proof fixed to the base plate (2) in a base configuration.
3. Clockwork movement according to one of the previous claims, wherein the zero-setting device (40) is capable of being torque-proof coupled to the cage (11) by means of the balance (15) being stopped by the balance stop device (50).
4. Clockwork movement according to one of the previous claims, wherein the balance stop device (50) comprises a braking element (60) being arranged on the rotating cage (11), being capable of being brought into frictional engagement with the balance (15) and being movable axial to a balance axis (17).
5. Clockwork movement according to claim 4, wherein the zero-setting device (40) is capable of being torque-proof coupled to the cage (11) via the brake element (60).
6. Clockwork movement according to one of the previous claims, wherein the zero-setting device (40) is capable of being torque-proof fixed to the base plate (2) by a fixing element (30) and only by a torque-proof coupling between cage (11) and zero-setting device (40) the fixing element (30) is transferable into a released position in which the zero-setting device (40) together with the cage (11) is rotatable mounted relative to the base plate (2).
7. Clockwork movement according to one of the previous claims, further comprising a locking latch (26) movable arranged on the base plate (2), the said latch interacting with a catch cam (28) being arranged on the cage (11) for stopping the cage (11) at a zero position.
8. Clockwork movement according to one of the previous claims 6 and 7, wherein the locking latch (26) is coupled to the fixing element (30) and being transferred to a catch position for stopping the cage (11) when the fixing element (30) passes from the fixing position to the release position.
9. Clockwork movement according to one of the previous claims, wherein the zero-setting device (40) has a carrier wheel (41) with a rim-type circumference (44) which is supported at its outer circumference by at least three rotatable rollers (31) that are arranged on the base plate (2).
10. Clockwork movement according to one of the previous claims, wherein the zero-setting device (40) comprises a ring-type circular wheel (42) with inner teeth (49) meshing with a pinion (19) of the escape wheel (12).
11. Clockwork movement according to one of the previous claims, 9 or 10, wherein the zero-setting device (40) comprises axially movable relative to its axis of rotation a stop ring (43) having at a radial outer edge an outer start slope (53) that corresponds to a respective first or second start slope (21, 23) of a first or second stop latch (20, 22) being movable arranged on the base plate (2).
12. Clockwork movement according to claim 11, wherein the stop ring (43) comprises at a radial inner-lying edge at start slope (54) that interacts with at least one cam (47) of at least one latch (45) that is movably mounted on the zero-setting device (40) radially inwards against a restoring force.
13. Clockwork movement according to claim 12, wherein the at least one latch (45) comprises at its radial inner end a control start slope (45a) being capable to be brought into engagement with a start slope (56a) of a brake ring (56).
14. Clockwork movement according to claim 13, further comprising a brake bolt (58) which is axially movable guided in a hub (6) of the tourbillon unit (10) or in the cage (11) and being designed axial movable by means of the brake ring (56) for the displacement of the brake element (60) and for stopping the balance (15).
15. Timepiece with a clockwork movement (1) according to one of the previous claims.

Images