WO2003017009A2

WO2003017009A2 - Clockwork movement and part

Info

Publication number: WO2003017009A2
Application number: PCT/IB2002/003061
Authority: WO
Inventors: Robert Greubel; Stephen Forsey
Original assignee: Complitime S.A.
Priority date: 2001-08-20
Filing date: 2002-07-24
Publication date: 2003-02-27
Also published as: DE60207267T2; WO2003017009A3; EP1419419B1; ATE309559T1; EP1419419A2; CH1419419H1; DE60207267D1; AU2002313572A1

Abstract

The invention concerns a clockwork part movement comprising a frame (10, 12) and a finish clock train. Said movement includes two carriages, one (20) being mounted on the frame (10) and pivoting about an axis (A-A) perpendicular to the plane of the movement, the other (22) mounted in the first carriage (20), pivoting about an axis (B-B), which defines the envelope of a cone with its axis merging with the first axis (A-A).

Description

Movement and timepiece

The present invention relates to a device of the tourbillon type intended to equip a timepiece movement of the type comprising a frame and a gear train as well as to a movement or timepiece provided with such a tourbillon.

This device is a device intended to average walking in vertical positions. It comprises, for this purpose, a cage pivotally mounted on the frame, in general an assembly formed by a bridge and a plate and, pivotally mounted on this cage, a spiral balance and an exhaust comprising in particular an exhaust mobile fitted with a wheel and a pinion.

The cage comprises a cage gear, kinematically connected to the gear train of the timepiece, in general to the average wheel. A toothed wheel, mounted on the frame, meshes with the exhaust pinion. In this way, each time the balance wheel is in position to receive a driving impulse from the exhaust, the torque applied by the medium wheel to the cage gear causes the cage to turn slightly, the impulse to the balance wheel being given. by the exhaust, the mobile of which rotates by meshing its pinion with the toothed wheel. The wheels and pinions are, in general, arranged and numbers so that the vortex makes one revolution per minute. Thus, when the timepiece is arranged vertically, the dead center position of the balance therefore rotates one minute, which averages the deviations in the vertical positions. However, the gap between horizontal and vertical positions remains. To overcome this drawback, the German watchmaker Walter Prendel (Groitzsch,

Germany) produced a pocket watch in which the pendulum axis makes an angle of 30 ° with that of the tourbillon cage and those of the other watch mobiles. In this way, the position of the balance varies from 30 to 60 ° maximum when the watch is either in the vertical position or in the horizontal position. But if the walking tests of the watches are carried out by placing them in different horizontal and vertical positions, the orientations are, however, arbitrary during wearing. The problem posed above is therefore modified. Furthermore, in order to be able to maintain the movement of the balance wheel, the components of the escapement are also inclined relative to the axis of the cage, the angle of inclination of the axes of these moving parts increasing from the escape wheel to the balance. Such a solution is difficult to master from a technical point of view and the working conditions of the exhaust are not very favorable.

The review "Alte Uhre" 4/79 published an article presenting a pendulum provided with a tourbillon rotating simultaneously around two orthogonal axes, so that the axis of the pendulum sweeps practically all the space. Such a solution certainly makes it possible to obtain the expected effect, but is inapplicable in a watch, because this leads to a very large thickness of the movement, even with a small diameter pendulum. Such an improvement can therefore only affect the precision of the watch and / or generate an excess thickness without commensurate measurement with the desired improvement.

We also know from the review "Horlogical Journal" of April 1983, p.15 to 19, a triple vortex, that is to say a vortex causing rotation in three orthogonal planes. Also in such a construction, the bulk is exorbitant and this type of tourbillon can only be difficult to envisage for a pocket watch or a wristwatch.

The aim of the present invention is to propose a tourbillon for a timepiece making it possible to appreciably reduce the walking differences between the horizontal and vertical positions, without having to reduce the diameter of the balance wheel, while maintaining a thickness of movement. compatible with a pocket watch or a wristwatch.

It therefore relates to a tourbillon intended to equip a timepiece movement of the type comprising a frame and a gear train as well as a pivoting cage on said frame carrying the balance wheel and the escapement. This tourbillon is characterized by the characteristics set out in claims 1 to 17.

The invention also relates to a timepiece or a timepiece movement as claimed in claim 18. The device, object of the invention, is intended to equip a timepiece movement comprising a frame and a finishing cog. This tourbillon is distinguished by:

- an escapement cage mounted movable in rotation about an axis I B-B forming an angle relative to the axis of rotation of the moving parts of the gear train;

- This escapement cage comprising a cage gear coaxial with the axis B-B meshing with a mobile mounted on the frame;

- a balance spring and an escapement comprising a mobile provided with an exhaust pinion pivots in the escapement cage; and in which

- The exhaust pinion is engaged with a toothing mounted on the frame and located in a plane perpendicular to the axis B-B of rotation of the exhaust holder cage.

Said angle a, other than 90 °, can be between 20 ° and 70 ° and is preferably equal to 30 °.

I

The balance and the movable parts of the escapement can pivot along axes parallel to the axis B-B of rotation of the escapement cage.

The teeth mounted on the frame and which is engaged with the exhaust pinion is either integral with said frame, or carried by a large cage pivoted on this frame around an axis AA forming an angle different from 90 ° with the axis BB of rotation of the exhaust cage. Other characteristics of this tourbillon device will be described in detail in the description which follows.

This vortex-type device is arranged so that, under the effect of the torque applied by the gear train on the cage gear of the cage

I exhaust pipe, the large cage rotates around the first axis AA at a first angular speed, and the exhaust pipe cage rotates around the second axis BB at a second angular speed defined by the ratio of the numbers of teeth that the gear comprises cage of the large cage and the toothing of the mobile mounted on the frame, the second axis BB defining the envelope of a cone of axis coincident with the first axis AA, or axis of rotation of the large cage.

In order to prevent the vortex from occupying too much thickness, it is advantageous for the angle at the top of the cone generated by the second axis BB, or axis of rotation of the escapement cage, to be equal to or less than 90 ° . The most favorable conditions are obtained for an angle at the apex close to 60 °, generally between 20 and 70 °.

I

| By using pinions as cage gears, it is possible to produce a vortex having as low a mass and inertia as possible. Like the cage of most known tourbillons, the escapement cage of the tourbillon according to the invention can make a revolution in one minute. In this particular case, it is advantageous for the large cage to make a turn in a time of between 4 and 10 minutes for example.

In order to guarantee as good meshing conditions as possible, the teeth of the mobile mounted on the frame are conical at the same angle at the top as the cone defined by the second axis.

Advantageously and to allow the use of a balance having a moment of inertia as high as possible, the axes of the escapement cage and of the balance are parallel, or even coincident. Other advantages and characteristics of the invention will emerge from the description which follows, given with reference to the appended drawing, in which the mono- or bi-axial vortex according to the invention is shown diagrammatically in axial section. More specifically: - Figure 1 shows the general structure of the cages of the biaxial tourbillon according to the invention mounted on the frame;

- Figures 2 and 3 show the large cage of the biaxial vortex in orthogonal views.

- Figure 4 shows the escapement cage of the biaxial tourbillon equipped with the balance and the escapement.

! - Figure 5 illustrates the biaxial vortex in a variant where the cages are pivoted in overhang.

- Figure 6 illustrates an embodiment of the biaxial vortex in which the large cage constitutes a carousel. - Figure 7 illustrates a simplified embodiment of the tourbillon comprising only one inclined cage, pivoted in overhang, the escapement cage. In these figures, and in order to avoid overloading the drawing, the screws are suggested by an axis line. FIG. 1 represents a portion of watch movement, with:

a frame comprising, visible in the drawing, a plate 10 and a bridge 12, which are provided with stones each forming a bearing 14,

a biaxial vortex 16, mounted to pivot about an axis A-A on the bearings 14, and

- a wheel of average 18, of which only the board is visible in the drawing, part of a gear train thus partially represented, and mounted pivoting on the frame along an axis perpendicular to the plane of movement and parallel to the axis AA.

The tourbillon 16 has two cages 20 and 22. The large cage 20 is illustrated in detail in FIGS. 2 and 3. It is mounted on the bearings 14. The escapement cage 22, shown in FIG. 4, pivots in the large cage 20, around an axis BB forming an angle (a) with the axis AA different from 90 °.

The plate 10 is provided with a drop 24, surrounding the hole where the bearing 14 is housed, which carries an annular wheel plate 25, comprising a second conical toothing 25a, the function of which will be specified below. This plate 25 is fixed by means not shown in the drawing, for example by driving or screwing. The drop 24 is provided with a lateral opening 26 allowing the passage of the middle wheel 18. As can be seen very particularly in FIGS. 2 and 3, the large cage 20, comprises:

a frame formed by two parts, one lower 28, the other upper 30, assembled to each other by means of screws 32,

lower 34 and upper 36 shafts, respectively integral with the lower 28 and upper 30 parts and intended to be engaged in the bearings 14 to pivotally mount the large cage 20 on the frame, and

- Lower 40 and upper 42 supports, respectively fixed on the lower 28 and upper 30 parts by means of screws 44 and intended to receive the exhaust-holder cage 22, as will be explained below. The parts 28 and 30 each include a middle portion, in the form of a bar identified by the letter a, and two uprights identified by the letter b, the j ends of the uprights 28b and 30b being fixed in pairs, by means of the screws.

32, and advantageously positioned by means of feet, which have not been shown in the drawing, in order to avoid overloading it.

The bars 28a and 30a and the uprights 28b and 30b define a substantially rectangular opening 46, the width and height of which are chosen so that the exhaust cage 22 can be housed there and rotate there freely, as will be explained further. The two shafts 34 and 36 each comprise a pivot identified by the letter a and intended to be engaged in one of the bearings 14, and a plate identified by the letter b. The plates 34b and 36b are respectively attached and fixed, for example by driving or screwing, to the middle part of the bars 28a and 30a. The shaft 34 carries, in addition, a first cage pinion 45 fixed by driving out and intended to mesh with the medium wheel 18.

The lower support 40 has a truncated pyramidal shape, with an apex angle of approximately 120 °. One of the faces 40a of the pyramid is placed in abutment against the internal face of the bar 28a, the support 40 being fixed there by the screws 44. The base of the pyramid comprises a recess whose bottom is pierced with a cylindrical hole , of axis BB, which opens onto the truncated face and inside which is chased a bearing 47 intended to receive the escapement cage 22. The base of the pyramid carries a board 48, provided with a first toothing 48a at its periphery and coaxial with the bearing 47, the function of which will be specified below. As shown in the drawing, the board 48 is fixed to the support 40 by driving or screwing into the recess, this board is arranged in a plane perpendicular to the axis B-B.

The upper support 42 comprises a protuberance 42a provided with a cylindrical hole in which a bearing 50 is driven, coaxial with the bearing 47 and also intended to receive the exhaust-holder cage 22. The exhaust cage 22, shown in detail and equipped in FIG. 4, comprises a frame formed by two parts, one lower 52, the other upper 54 connected together by means of screws 56. Parts 52 and 54 each comprise a median portion in the form of a bar identified by the letter a and two uprights identified by the letter b, the ends of the uprights 52b and 54b being fixed two by two by the screws 56 (FIG. 1).

The exhaust cage also includes:

two exhaust bridges 58 and 59 mounted on the lower part 52,

a lower shaft 60, mounted on the external face of the middle portion 52a, fixed in its central part by means of a plate 60a, and which comprises a pivoting 60b and a toothing at the end forming a pinion of cage 60c exhaust pipe, and

an upper shaft 62 mounted on the outer face of the middle portion 54a, fixed in its central part by means of a plate 62a and provided with a pivot 62b.

The middle portions 52a and 54a are pierced with a hole identified by the letter ç, with an axis coincident with the axis B-B. j

The shafts 60 and 62 are fixed on the parts 52 and 54 by means of screws 64, diagrammatically shown. The pivot 60b and the pivot 62b are coaxial and oriented along the axis B-B. They are intended to be respectively engaged in the bearings 47 and 50 of the large cage 20, to ensure the rotation of the escapement cage 22 in the large cage 20.

The second cage pinion 60c is arranged so that it meshes with the second toothing 25a of the board 25, integral with the frame 10. The escapement cage 22 carries a balance 66 provided with a hairspring not shown in the drawing, an anchor 68 and an exhaust mobile 70 comprising a pinion 70a and a wheel 70b, the latter cooperating with the anchor 68 to maintain the pendulum movement 66. All these mobiles are pivoted on the escapement cage 22 along axes which are parallel to each other and relative to the axis BB of rotation of this cage 22.

More specifically, the pendulum 66 pivots about an axis concentric with the axis BB, in two bearings 72 and 73 mounted one 72 in the hole 52c of the middle portion 52a, the other 73 in the hole 54c of the middle portion 54a. The exhaust bridges 58 and 59 each comprise a bearing 74, in which the exhaust mobile 70 pivots. The pinion 70a is arranged, so that its teeth protrude from the lower surface of the middle portion 52a, to allow its meshing with the first toothing 48a of the board 48 of the large cage 20. The mounting of a tourbillon as described begins with the assembly of the constituent parts of the escapement cage 22, and more particularly the driving of the bearings 72 and 73 and the fixing of the shafts 60 and 62. The exhaust bridge 58 is put in place, then the exhaust mobile 70 and the anchor 68, and finally the exhaust bridge 59, so that the components of the exhaust can pivot in their bearings.

The pendulum 66 is then engaged by its lower pivot in the bearing 72, then positioned by the fixing of the upper part 54 on the lower part 52, the upper pivot of the balance being engaged in the bearing 73. The two parts 52 and 54 are assembled by means of the screws 56. The starting can then be carried out in a conventional manner, by subjecting the exhaust mobile 70 to an engine torque, on an appropriate fitting.

When the balance spring and the escapement are adjusted appropriately, the escapement cage 22 can then be placed in the lower part 28 of the large cage 20, the pivot 60b being engaged in the bearing 47. The part upper 30 is then fixed by means of screws 32 on the lower part 28, the pivot 62b being engaged in the bearing 50.

The vortex 16 is thus finished and can be placed on the frame, between the plate 10 and the bridge 12, the pivots 34a and 36a each being engaged in one of the bearings 14.

When the spring which comprises the movement is armed, the medium wheel 18 subjects the large cage 20 to a driving torque, by meshing with the first cage pinion 45. This torque can only generate a rotation of the large cage 20 if the second cage pinion 60c rolls on the second toothing 25a of the board 25, that is to say that the escapement cage 22 rotates about the axis BB. As the toothing of the exhaust pinion 70a is in prijse with the toothing of the first board 48, this movement is not possible

I only when the escapement gives a driving impulse to the balance wheel 66. This occurs at each alternation of the balance wheel. This therefore amounts to saying that each time the pendulum 66 receives an impulse, the escapement cage 22 rotates around the axis BB and the large cage 20 around the axis AA, the angles covered being a function of the numbers of teeth. of the gears involved. These gears can be chosen so that the exhaust cage 22 makes one revolution in one minute and the large cage 20 one revolution in a few minutes, typically from 4 to 10.

In this way, the axis BB scans the envelope of a cone of axis AA, whose angle at the apex is approximately equal to 60 °, that is to say twice the angle a that make the axes AA and BB together. . As a result, whatever the position of the movement of the watch, the pendulum axis has an average inclination of between 20 ° and 70 ° approximately, which considerably reduces the differences in running between the positions. (

The angle at the top of the cone can vary depending on the construction of the watch. The higher the angle, the more space the cage 22 occupies in thickness, unless the diameter of the pendulum 66 is reduced. The tests carried out seem to show that the optimum is in the range of 40 ° to 140 ° for the angle at the top, and more precisely in the vicinity of 60 °.

It will also be noted that, for the meshing conditions to be optimal, it is desirable that the second conical toothing 25a of the wheel 25 has an apex angle equal to that of the cone generated by the rotation of the axis BB around l 'axis AA.

The tourbillon, as described, can of course be the subject of numerous variants without departing from the scope of the invention. Thus, the cage pinions 45 and 60c could be replaced by wheels meshing respectively with a mobile of the gear train and with the board 25, which would then advantageously be provided with internal toothing. This makes it possible to obtain an opposite direction of rotation of the two cages.

In another variant which has not been shown, it is the pinion 60c which could include a conical toothing, the toothing 25a of the wheel 25 then being straight. It is also possible to distribute the taper between the two teeth.

It is also conceivable to arrange the balance so that it is not coaxial with the escapement cage 22, the axes being parallel. However, this solution has the disadvantage that the moment of inertia of the balance wheel is reduced for a given size of cage. | It is obvious that the escapement used in the tourbillon can be of any type with free oscillation, for example with anchor or detent.

In the example illustrated, the axes of the mobiles of the gear train are parallel to the axis A-A of rotation of the first cage, which could not be the case in other variants. The rotational speeds of the cages 20 and 22 can be equal or different. Likewise, the direction of rotation of the cages 20 and 22 can be the same or opposite.

In the variant illustrated in Figure 5, the large cage has only a lower portion 28 pivoted overhanging on the frame 10 by a bearing 14 following the axis AA parallel to the axes of the mobiles of the gear train. This lower part 28 of the large cage 20 carries, as in the first embodiment, a lower support 40 pierced with an axis hole BB inside which is driven a bearing 47 intended to receive the carrier cage exhaust 22. The exhaust holder cage 22 also has only its lower part 52 and is pivoted in overhang on the large cage 20 by its lower shaft 60 carrying at the end the second cage pinion 60c meshing with the second toothing 25a secured to the frame 10.

This variant makes it possible to achieve the same advantages of the tourbillon while having a reduced bulk.

In the embodiment illustrated in FIG. 6, the tourbillon type device also includes a large cage 20 and an escapement cage 22 as described in the first embodiment or its variant, and the exhaust pinion 70a is also in engagement with the first toothing 48a disposed in a plane perpendicular to the axis (BB) of the escapement cage.

In this embodiment, this toothing 48a is carried by a board 48 mounted on the pyramidal base 40 of the large cage 20 concentrically with the axis BB of the escapement cage 22. The first cage pinion 45 of the large cage is as previously engaged with the wheel 18 of the finishing mobile generally the average mobile.

In this embodiment, the large cage is designed as a carousel and the cage pinion 60c of the escapement cage is engaged with one of the wheels 80a of a mobile 80 pivoted on the frame 10, the second wheel 80b of which is it engaged with a second wheel 18a of the finishing mobile.

Thus, in this embodiment, the device comprises a vortex comprising in fact only one cage, the escapement cage pivoted in an inclination relative to the frame 10, and the large cage 20 forms a carousel which carries i

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the escapement cage in its rotation controlled by the driving train of the movement.

The embodiment illustrated in FIG. 7 is a simplified version of the tourbillon comprising only one escapement cage 22 pivoted in an inclined manner on the frame 10 by its shaft 60. The frame 10 secured to the inclined support 40 comprising the first peripheral toothing 48a situated in a plane perpendicular to the axis of rotation BB of the escapement cage 22. This axis BB forms an angle a with a direction parallel to the axis of the finishing mobile 18. The shaft 60 of this cage 22 is pivoted in bearings 47 and 47a of the frame 10 and the cage pinion 60c of the escapement cage 22 is engaged with the finishing wheel 18. The exhaust pinion 70a is engaged with the first toothing 48a carried by the support 40 of the frame 10.

This solution has the advantage of being simple and compact. As in the previous embodiments, the balance, the anchor and the exhaust mobile carried by the escapement cage 22 are pivoted on this cage along axes parallel to each other and to the axis of rotation of the cage exhaust 22.

It goes without saying that in variants of each embodiment described, the balance and the exhaust pivots in the escapement cage 22 could be of the Prendel type.

Claims

1. Whirlpool device (16), intended to equip a timepiece movement comprising a frame (10; 12) and a finishing train (18), characterized in that it comprises an escapement cage (22 ) j mounted movable in rotation about an axis BB forming an angle (a) different from 0 ° or 90 ° relative to the axis of rotation of the mobiles of the gear train (18); this escapement cage (22) comprising a cage gear (60c) coaxial with the axis B-B, meshing with a mobile (18; 25; 80) mounted on the frame (10; 12); by the fact that a spiral balance (66) and an exhaust (68,70) comprising a mobile (70) provided with an exhaust pinion (70a) are pivoted in the exhaust cage (22); and by the fact that the exhaust pinion (70a) is engaged with a toothing (48a) mounted on the frame (10; 12) and situated in a plane perpendicular to the axis (BB) of the exhaust cage-door (22).

2. Whirlpool device according to claim 1, characterized in that said angle (a) is between 20 ° and 70 °, preferably substantially equal to 30 °.

3. A tourbillon device according to claim 1 or claim 2, characterized in that the balance (66) and the moving parts of the escapement (68,70) pivot around axes parallel to the axis (B-B).

4. Whirlpool device according to one of the preceding claims, characterized in that the balance (66) pivots about an axis coincident with said axis (BB) of the exhaust cage (22). )

5. Whirlpool device according to one of the preceding claims, characterized in that the escapement carrier cage (22) is pivoted in overhang along the second axis (B-B) on the frame (10).

6. Whirlpool device according to one of the preceding claims, characterized in that the cage gear (60c) of the escapement cage (22) is engaged with a mobile (18) of the gear train; and by the fact that the toothing (48a) is integral with the frame

(10; 12).

7. Whirlpool device according to one of claims 1 to 4, characterized in that it also comprises a large cage (20) mounted movable in rotation on the frame (10; 12) around a first axis (AA) forming an angle other than 90 ° with the second axis (BB); by the fact that the escapement cage (22) is rotatably mounted on this large cage (20) around the second axis (B-B); by the fact that the large cage (20) carries a first cage gear (45) coaxial with the first axis (A-A) meshing with a mobile (18) of the gear train; by the fact that the cage gear (60c) of the exhaust cage (22) is engaged with a mobile (25, 80) mounted on the frame (10; 12) and coaxial with the axis (AA) the large cage (20); and by the fact that the exhaust pinion (70a) is engaged with the first toothing (48) which is integral with the large cage (20).

8. Whirlpool device according to claim 7, characterized in that the escapement carrier cage (22) is pivoted in overhang on the large cage (20).

9. A tourbillon device according to claim 7 or 8, characterized in that the large cage (20) is pivoted in overhang on the frame (10; 12).

10. Whirlpool device according to one of claims 7 or 8, characterized in that the large cage (20) is pivoted along its axis (AA) between two bearings (14) of the movement, one carried by the frame ( 10) and the other by a bridge (12).

11. Whirlpool device according to one of claims 7 to 10, characterized in that the cage gear (60c) of the escapement cage (22) is engaged with the teeth (25a) of a board ( 25) integral with the frame (10; 12) and coaxial with the axis (AA) of the large cage (20).

12. Whirlpool device according to one of claims 7 to 10, characterized in that the cage gear (60c) of the escapement cage (22) is engaged with one of the wheels (80a) of a mobile (80) pivoted on the frame (10; 12) coaxial with the axis (AA) of the large cage (20), ce | mobile comprising a second wheel (80b) meshing with a mobile

(18a) of the gear train.

13. Whirlpool device according to one of claims 7 to 12, characterized in that the angular speeds of the cages (20,22) are equal or different from each other.

14. Whirlpool device according to one of claims 7 to 13, characterized in that the directions of rotation of the cages (20,22) are the same or vice versa.

15. Device according to one of claims 7 to 14, characterized in that the axis A-A of the large cage (20) is parallel to the axes of the moving parts of the gear train (18).

16. Watch movement fitted with a tourbillon device according to one of claims 1 to 15.