CH702313B1 - Energy distributing escapement for mechanical watch movement, has kinematic inversion units arranged to allow teeth alternately exert meshing action to permit transmission of optimal energy for completeness and consistency - Google Patents

Abstract

The escapement has an assortment comprising a main balance (30) connected to an auxiliary balance (50) by connecting units (48) to rotate around an axis. The auxiliary balance comprises a pulse lever (52) with a pulse face (33) receiving quantity of energy from peripheral teeth of an escapement wheel (10). Kinematic inversion units are arranged to allow the teeth alternately exert meshing action of same nature with each of the pulse levers so as to permit transmission of optimal energy for completeness and consistency.

Description

The present invention relates to an exhaust according to the preamble of independent claim 1.

[0002] The proposed escapement is likely to be implemented in any type of time instrument, even if, in this text, reference will only be made to mechanical watch movements.

[0003] We know that the energy-distributing organ that is the exhaust fulfills a dual function. On the one hand, it maintains the oscillations of the regulating organ, therefore of the sprung balance of the movement of a mechanical watch, by transmitting to it, by small successive impulses, alternately on one side and the other , the part of the energy of the mainspring reaching it via the counter gear train, or finishing gear, as long as the energy reserve is not exhausted. On the other hand, it ensures the smooth running of the gear train, so as to allow the displays to indicate the duration of the oscillations made by the regulator.

[0004] At the end of this process, the escape wheel (which will be, hereinafter, frequently designated by the sole term wheel), receives only about 60% of the driving force, a part of the order of 40% of this being dissipated upstream by various frictions and other resistances due in particular to the cog.

[0005] In turn, in the majority of cases, the balance collects only about 70% of the energy transmitted by the wheel, the difference being absorbed by the escapement.

[0006] Also the improvement of the efficiency of the transmission of energy from the anchor wheel, therefore of its two components which are the efficiency of the {escape wheel-anchor} sub-assembly, the main component as regards its effect, and the performance of the {anchor-regulator} sub-assembly, a more subsidiary component, continues to worry watch manufacturers. But they are equally, if not more, concerned with the constancy of pulse intensity, in other words, the uniformity of that output. And these concerns persist.

[0007] Thus, by first referring to the Swiss lever escapement, the most widely used at the present time, it is observed that the teeth of the wheel work on the input and output pallets under conditions very different working conditions, wheel and anchor rotating alternately in the same direction (inner gear) and in the opposite direction to each other (outer gear) respectively. This means that the mode of transmission of force from the wheel to the anchor, taking place under these conditions which do not correspond to those of the cogwheels, is quite other than ideal. In addition, the percussion at the origin of the action of a tooth on a pallet is followed by a sliding of the impulse plane of the tooth of the wheel on the impulse plane of the pallet of the anchor . The resulting resistance and friction cause two types of inconvenience: The first, of a functional nature, consists of an entirely different performance and a lack of uniformity thereof, the performance of the inlet pallet being higher than that of the outlet pallet. This efficiency imbalance causes anisochronism of the oscillator, therefore a loss of precision of the movement.

[0008] The second is of a manufacturing nature. In fact, in order to reduce the antagonistic forces of friction, it is absolutely necessary to lubricate the impulse planes of the anchor vanes. This operation increases the cost of assembly all the more as it is extremely delicate, especially in its dosage. In addition, to ensure satisfactory operation of the movement over time, the lubrication must be renewed periodically (on average every two to three years) by a specialist from the manufacturer's after-sales service network.

[0009] From a detailed study, in particular of the performance component of the {escape wheel-anchor} sub-assembly, established beforehand for the purpose of clearly defining the parameters on which it is necessary to act to improve this performance , CH-570 644 proposes a Swiss lever escapement, of general conventional shape with two arms, an input arm carrying an input pallet and an output arm carrying an output pallet, each of these pallets having a plane of impulse and a rest plane, but where the function of transmitting most of the energy is devolved to the input pallet, which, in comparison with the output pallet, is appreciably wider, further from the line connecting the centers of the wheel and the anchor, and embraces, from this line, at least one more tooth of said wheel, the anchor embracing a number of teeth of the wheel greater than the fifth of the number teeth than this one presents.

[0010] The objective of improving performance can be considered to be achieved. However, the torque is transmitted in the traditional way, that is to say according to the working conditions of the teeth of the wheel on the very different pallets, and by percussion followed by sliding of the impulse planes of the teeth of the wheel. the escape wheel on the impulse planes of the anchor vanes, the energy losses (in this case, those due in particular to friction are all the greater as the impulse surface on the pallet d entry is large) significantly limit this improvement. As an extension of this observation, the problem of the imbalance in yields between the inlet and outlet vanes, as well as that of lubrication, remain and are even amplified.

EP-A-1 367 462 discloses an escapement comprising, on the one hand, two identical toothed escapement wheels meshing with one another and to one of which is transmitted a driving force and, of on the other hand, an anchor in the form of a symmetrical rocker. At the periphery of this lever are arranged two planes receiving alternately from one and the other of said wheels impulses, two transmission teeth of these impulses to a plate integral with the balance as well as two stop faces making it possible to block alternately. said wheels after transmission of each pulse.

[0012] According to this device, the mobiles, the wheels and the rocker, turn in the opposite direction each time, like an external gear. While it is at first sight likely to provide better uniformity of performance, it nevertheless conceals several drawbacks which affect its practical and economic interest. Among them, we note, first of all, poor efficiency due to the increased moment of inertia resulting from the presence of two escapement wheels, which also create a dynamic load. Then, high manufacturing costs, due to the machining of teeth with a complex profile, while it hardly seems possible to do without this very specific profile, except to make the pulling function deficient. Finally, the surface area required for the installation of the device is practically doubled in comparison, for example, with a traditional Swiss lever escapement.

[0013] EP-A-0 018 796 proposes an exhaust whose arrangement of the elements is such that it does not require any lubrication of the vanes. It includes one or preferably two coaxial escapement wheels and four paddles. Three of these pallets are arranged on a rocker with three arms capable of pivoting about an axis. A median arm carries a first impulse vane and two arms extending on either side of said medial arm each carry a locking vane (or rest), one input, the other output, this rocker further comprising a rod that comes to rest alternately on limiting pins. A plate integral with the balance, fixed on the axis of the latter, carries a second impulse pallet. The two impulse vanes transmit in turn an impulse to the balance, during each passage of the latter approximately at the neutral point separating two vibrations, the surface of the corresponding pallet then being in the radial position of the escape wheel, therefore in a plane containing the axes of the escape wheels (or wheel) and of the balance. The goal of saving on vane lubrication can be expected to be achieved. On the other hand, serious drawbacks remain.

[0014] Thus, the increase in the moment of inertia caused by the addition of a second escape wheel, coaxial with the first, according to the preferred embodiment, or the necessary extra thickness of the single wheel of escapement, according to the second embodiment, significantly reduces the efficiency of the {wheel-anchor (rocker)} sub-assembly. In addition, this arrangement, as well as the multi-stage conformations of the lever and of a third plate on the balance, lead to a substantial extra thickness of the movement.

[0015] The pulses are transmitted, for each alternation, either directly to the additional plate carrying a pallet, or indirectly via the rocker; this mode of transmission causes an imbalance of yields, and therefore a lack of isochronism.

Finally, the production of the escapement, whatever the embodiment chosen, is extremely expensive, since it requires a whole series of indexing of the different elements relative to each other, the most delicate and difficult, in addition to specific machining, for example bar turning.

We can easily measure the extent of the difficulty posed by the design of a new escapement which, freed at best from the weight of the drawbacks defined above and those that are still noted on the devices of the prior art , satisfies with equal success the fundamental quality factors expected of it, namely, in particular, not only optimal but also uniform efficiency, that is to say a practically full and regular transmission of energy, the all at a minimal or at least flexible manufacturing cost.

[0018] This is the task undertaken by the inventor of the present invention.

Its object is achieved by means of the means defined in independent claim 1, the particular means according to the dependent claims allowing various advantageous embodiments of the exhaust.

Thanks to a significant improvement in the balancing of the efficiency of the escapement at each pulse, the regulator member receives pulses of practically constant intensity, so that a variation in the amplitude of the oscillations of this member , if it were to remain, will remain truly negligible, independently of the variations in the energy received upstream due to the gears of the train.

[0021] The simulations and tests undertaken with a mechanical movement provided with the new escapement according to various embodiments have made it possible to confirm, at the same time as a virtual eradication of the disadvantages set out above, a series of advantages.

Indeed, the transmission of energy is effected by combining the percussion no longer with a sliding, therefore a friction, but on the contrary a bearing, or at least a pseudo-bearing of the active faces (cumulatively performing the functions of impulse faces and rest faces) of the teeth of the escape wheel, successively and alternately on the impulse face of the impulse lever of the primary rocker, then on the impulse face of the control lever. impulse of the auxiliary rocker, like the meshing of two toothed wheels between them. Lubrication is unnecessary, the performance of the escapement is significantly improved and disparities are eliminated, which leads to optimum precision in the cadences of the oscillator body. In addition, the reduced exhaust losses allow for the placement of a weaker mainspring ensuring a more uniform amplitude of the balance and a reduction in Hertz pressures in the finishing gear train. The reduction in the torque required to wind the barrel, in turn, simultaneously increases the operating autonomy, the reduction of friction in the train, and the precision and longevity of the movement.

The invention will be easily understood and the advantages which it provides will readily appear on reading the description of two embodiments and of an alternative embodiment of the first of said forms - by way of non-limiting examples -, in support of the accompanying drawings in which: FIG. 1 <sep> is a schematic perspective representation of an escapement according to a first embodiment, seen from the dial side and integrated into a cog of a simple mechanical watch movement, Figs. 2-7 <sep> are enlarged plan views of the first embodiment of the escapement, Figs. 8 to 19 <sep> are plan views on a smaller scale showing the positions of the elements of the escapement according to the first embodiment, at different stages of operation, FIGS. 20 to 25 <sep> are views equivalent to fig. 8 to 13, but relate to an alternative embodiment of the first embodiment, FIG. 26 <sep> is a schematic perspective representation of an escapement according to a second embodiment, seen from the dial side and integrated into a cog of a simple mechanical watch movement, fig. 27 <sep> is a plan view of this second embodiment, and FIG. 28 <sep> is a section taken along line XXVIII – XXVIII of fig. 27.

We can see on the cog diagram in FIG. 1 a barrel 2, a driving member, a finishing gear or counter gear 3 and a general reference exhaust 1 according to a first embodiment. This diagram is completed by the partial representation of a sprung balance 5, a regulating member, that is to say of the only balance 25, without its balance spring, having the ability to oscillate around its axis 25A. The escapement 1 comprises a wheel 10 integral with a pinion 14 driven around an axis of rotation 10A by a second wheel 4, an anchor 30, 50 whose particular construction is noted and, finally, a double plate 20 integral balance 25.

[0025] The assortment therefore consists of three sets, wheel, anchor and double plate, but the original characteristics of which will emerge from the support of fig. 2 to 7. In all these figures, the arrangement of these assemblies relative to each other corresponds, functionally, to the same momentary phase of an alternation, in this case, approximately that of the end of release and of the beginning. pulse (see fig. 17).

The wheel 10, of axis 10A passing through its center ORE, actuated in rotation in the direction of the arrow FRE (see FIG. 2) comprises a set of teeth 11 (of twenty teeth according to the example), each tooth 12 of which has an active face 13 cumulating the functions of impulse face and of rest face and exhibiting an inclination of angle η with respect to the radius of the wheel. In other words, the impulse and rest faces are the same, unlike those of a Swiss lever escapement wheel, but like a detent escapement wheel. The profile of the flanks of a tooth 12, or at least of the active face 13 thereof, can be adapted according to technical and economic considerations. Thus, depending on the case, we will choose plane faces (see figures) or curved faces such as involute of a circle, epicycloid or a combination of these curves (which, of course, will involve higher costs, but which, on the other hand, will provide better rolling, due to a reduction in friction forces).

The anchor, element transforming the rotary movement of the wheel 10 into a reciprocating movement and successively receiving therefrom the amounts of energy to transmit them to the regulator member, is formed of a double rocker consisting of 'a primary rocker 30 and an auxiliary rocker 50, both interconnected, each being able to pivot about its respective axis 30A, 50A (FIG. 1) passing through the respective center OBP, OBA. The primary latch 30 comprises, on the one hand, three arms 31, 34, 37 placed opposite the teeth 11, one of which 31 carries an impulse lever 32 having an impulse face 33 and of which the other two 34, 37 extend parallel to each other to carry a rest lever 35 having a rest face 36, the arm 37 extending by a toothed sector 38 with three teeth. On the other hand, opposite these arms 31, 34, 37, conventionally emerges a rod 39 extended by a fork 40 which comprises an input horn 41 and an output horn 42, and which is provided with 'a 45 dart designed to avoid overturning. The angular movement of the rocker 30 is limited by input and output limiting pins 43, 44. The auxiliary rocker 50 comprises three arms placed opposite the teeth 11, one of which 51 carries an impulse lever 52 having an impulse face 53, a second arm 54 carries a rest lever 55 having a rest face 56 and, finally, a third arm 57 carries a toothed sector 58 with two teeth. According to the example presented, the impulse faces 33, 53 of the impulse levers 32, 52 are flat, but just like the faces 13 of the wheel 10, they could be curved, responding for example to the equation of an involute of a circle, of an epicycloid or of a combination of these curves. The teeth 38, 58 of the two arms 37, 57 mesh with one another, simultaneously constituting the mentioned connecting means 48 and the kinematic inversion means, so that the pivoting of one of the levers in one direction causes the other to pivot in the opposite direction. Instead of toothed elements, the means 48 could be in any other form, such as ball joints for example, allowing the levers to perform the aforementioned pivoting.

Conventionally, the double plate 20, which comprises a large plate 21 provided with a pin 23 and a small plate 22 having a notch 24 allowing the passage of the dart during the angle of lift, is integral with the balance 25 of the regulating member 5 (not shown in fig. 2, but see fig. 1), to allow the exercise of the reciprocal actions of the ankle 23 on the fork 40 during disengagement and of said fork on said ankle during of impulse.

The combined action of the faces 13 of the teeth 12 of the wheel 10, successively and alternately on the impulse faces 33, 53, and of the kinematic inversion means 48 connecting the two rockers 30, 50, allows meshing of the two moving parts, wheel and double rocker, of the same nature, like a gear, in this case external, therefore an almost integral transmission of energy, this with an optimal regularity, transmission which is not influenced more than by the only disturbing forces due to residual friction.

Indeed, during an impulse, the percussion of a tooth 12 against an impulse face is followed by a rolling, or at least a pseudo rolling of this tooth on this face, in the direction of rolling. The pitch circumferences 15, 16, 17 of the wheel 10, of the rocker 30 and of the rocker 50, respectively, shown by way of indication, are determined by the construction, in a manner known to those skilled in the art, with reference to the meshing law, so that the stresses on the teeth 12 and the levers 32, 52 are minimal.

In the example shown, where the active face 13 of the tooth 12 is flat, the base circumference 15 merges with the outer circumference of the teeth 10, or is very close to it. Referring to a pulse start phase on the lever 32 of the primary rocker 30, as shown in FIG. 2, the end edge 7 of the side of a tooth 12 strikes the impulse face 33 on a segment 6 of the side thereof (thickness of the tooth), then rolls over a section 18 of this side which s 'extends between segment 6 and end edge 8 of said face 33. Ideally, the start of a pulse occurs (percussion) while segments 6 and 7 are found coincident in a plane (not shown) formed by the axes 10A, 30A, therefore passing through the line of centers ORE – OBP (this observation being of course applicable mutatis mutandis for a start of a pulse of a tooth 12 on the lever 52 of the rocker 50). However, it can be seen that, according to the example, the contact at the start of the pulse occurs shortly after the wheel 10 has passed the line of centers ORE – OBP, rather than on the line of centers itself, in this case with a low angular offset ε, to show that such an offset can, by construction, be imposed, on the condition that the extreme edge 8 must imperatively be cleared outside the outer circle of the wheel (here confused with the pitch circle 15 ), when the horn 41 is resting against the limiting pin 43. Of course, care will be taken to ensure that the angle ε is minimum, so that the transmission of energy, proportional to the cosine of said angle ε, is not noticeably diminished. This mode of engagement takes place in a similar manner during the rolling or pseudo rolling of a tooth 12 on a section 19 of the impulse face 53 of the lever 52 of the auxiliary rocker 50.

To further ensure an identity of the working conditions of engagement, so that the latter are optimal, at least the impulse faces 33, 53 of each impulse lever 32, 52 of the latches 30, 50 are reciprocally transforms or images of one another in at least one geometric transformation T (i) (the index i serving to distinguish the transformation by a sequence number and a geometric symbol), of ratio 1 / 1. That is, at the end of these applications, the image of an impulse face 33; 53 of a rocker merges with the impulse face 53; 33 of the other scale, subject to possible corrections (see general comment below).

Of course, it will be advantageous to shape the rockers 30, 50 by applying these transformations T (i) to all other desired points, elements or parts of elements (in particular the articulation elements of the rockers, the arms 31, 51; 34, 54; the faces and rest levers 36, 56; 35, 55).

[0034] In general, the ratio of an object and its image in these geometric transformations is, as we have just said, theoretically 1/1 each time. But in practice, the completion and all other construction or mechanical considerations (for example due to the load in the link 48 between the scales 30, 50) may lead the manufacturer, during his work necessary to ensure optimal functioning of the escapement, to be corrected to said report.

[0035] This observed, the geometric features will be explained and easily understood in support of Figs. 3 to 7.

We will specify beforehand with the support of FIG. 3 that according to the angular arrangement of the primary and auxiliary rockers 30, 50 relative to the wheel 10 (already evident from reading Figs. 1 and 2), the axes 10A, 30A passing through the centers ORE, OBP, on the one hand, and the axes 10A; 50A passing through the centers ORE, OBA, on the other hand, constitute two planes (symbolized in fig. 3 by their traces P1 and P2 in phantom) forming an angle α. The centers OBA, OBP lie on arcs of circles with centers ORB and radii RBP; RBA respectively, with RBP = RBA = R1. As for the OBP center, it is located on the line of ORE – OREG centers.

For the reasons mentioned above, the identity RBP = RBA could be corrected, so that RBP = px RBA, where p is a proportionality factor approximately equal to 1. Similarly, the need for a correction , ie a slight angular shift of OBP on the line of centers ORE – OREG could prove to be indicated or advantageous.

For a general understanding of the aforementioned geometric transformations, we consider a line segment 47 (projected on the plane of the figure) delimited by the center OBA and the end edge 9 of the impulse face 53 of the lever 52 of the auxiliary rocker 50 and a straight segment 46 (projected on the plane of the figure) delimited by the center OBPet the end edge 8 of the impulse face 33 of the lever 32 of the primary rocker 30 (see FIG. 4). Let us recall at the outset that the respective positions of the rockers 30, 50, and more particularly of the levers 32, 52 correspond to a given operating phase; consequently, the support line of segment 47 forms with the line of centers ORE – OBAa defined angle δ and the support line of segment 46 forms with the line of centers ORE – OBPa defined angle ζ.

By applying a first transformation T (1, α +) in the form of a rotation of angle α around the center ORE in the direction indicated by the arrow (positive direction), the segment 47 a as transposed or image one segment 47 ́ delimited by the center OBP and point 9 ́. Then by applying a second transformation T (2, β +) in the form of an angle rotation β around OBP, in the direction indicated by the arrow (positive direction), with β = δ – ζ, the segment 47 ́ has as transform or image a segment 47 ́ ́ delimited by the center OBP and the point 9 ́ ́, which merges with the point 8. The segment 47 ́ ́, image of the segment 47 in the transformations T (1, α +) , T (2, β +), is thus superimposed on the corresponding segment 46.

This operation, resulting from the product of two rotations, is by definition reciprocal and commutative.

In particular, the segment 46 will image the segment 47 in a transformations T (1, α-), T (2, β-).

[0042] We will say more generally and by convention that the segments 46, 47 are reciprocal images of each other in a transformation T (i).

In particular, knowing that the levers 32, 52, perform identical functions which must be performed under identical conditions display at a given moment different given angular orientations defined above by the angles δ and ζ, we can see at the fig. 4that by applying the rotations α and β in the positive direction around the centers ORE and OBP, (transformations T (1, α +), T (2, β +), the rocker 50 has for image the transposed rocker 50 ́ (shown in dotted line), the impulse face 53 has for image the face 53 ́ which itself has for image the face 53 ́ ́ coming to merge with the impulse face 33 of the lever 32 of the rocker 30. Advantageously, the entire lever 52 has the image of the lever 52 ́ which itself has the image of the lever 52 ́ ́, which merges with the lever 32. Analogously to the impulse face, the rest face 56 and advantageously all the rest lever 55 have for images the face 56 ́ and the lever 55 ́, respectively, which themselves have for images the face 56 ́ ́ - which merges with the rest face 36 of the rocker 30 - and the lever 55 ́ ́ - which merges with the rest lever 35 of the rocker 30.

[0044] FIG. 5 illustrates the transformations in the opposite direction T (1, α–) and T (2, β–) around the centers ORE and OBA respectively). The impulse face 33 and the lever 32 of the rocker 30 have for images the faces 33 ́ ́ and the lever 32 ́ ́ (via the images 33 ́ and 32 ́), which merge with the impulse face 53 and the impulse lever 52 of the rocker 50. Likewise, the rest face 36 and the rest lever 35 of the rocker 30 are imaged as the faces 36 ́ ́ and the lever 35 ́ ́ (via the images 36 ́ and 35 ́), which merge with the rest face 56 and the rest lever 55 of the rocker 50.

[0045] Figs. 6 and 7 illustrate that instead of the rotations of angles α and β around the centers ORE and OBP or ORE and OBA, respectively, as described above, the transformations can consist of a linear vector translation, i.e. T, followed by 'a rotation of angle γ, either T (4, γ +) or a translation T followed by a rotation of angle γ, or T (4, γ–). We find in these figures the reciprocal images of the faces and impulse levers as well as the faces and rest levers of the rockers 30, 50, like what has been seen in support of Figs. 4 and 5, all these elements being assigned the same references (52 ́, 52 ́ ́; 53 ́, 53 ́ ́, etc.; 32 ́, 32 ́ ́; 33 ́, 33 ́ ́), these figures not requiring further comments.

The transformations could also consist, each time, in an orthogonal symmetry followed or preceded by a rotation, similar to those which will be seen in more detail during the description of the second embodiment, to which the reader can refer, to transcribe them here without difficulty.

It is interesting to note - besides the fact that the escapement according to the invention thus designed ensures optimum transmission and uniformity of energy to the regulator member - that the calculations have shown that the moment of inertia of the double articulated rocker just described is practically equal to half of that of a Swiss anchor (i.e. 2.5051 × 10 kgm <2> against 4.652 × 10 kgm <2>), which allows great flexibility of construction , in particular of the auxiliary rocker.

[0048] In support of fig. 8 to 19, we will now describe the operation of the escapement according to this first embodiment, by breaking it down into its successive phases or sequences during a complete oscillation, FIGS. 8 to 13 and 14 to 19 corresponding respectively to a first and to the second alternation thereof. In these figures, the movements of mobiles and the direction of these movements are indicated by unreferenced arrows, helping understanding, without it being necessary to return to them in the description of said phases.

In FIG. 8, the double plate 20, after having completed its additional ascending arc, performs its additional descending arc, during which the escapement wheel 10 and the primary and auxiliary rockers 30, 50 are stopped.

In FIG. 9, the pin 23 comes into contact with the exit horn 42 of the fork 40 of the primary latch 30.

In FIG. 10, the rest face 36 of the rest lever 35 of the rocker 30 leaves the active face 13 (performing the function of the rest face) of a tooth 12 of the wheel 10, disengagement which causes a geometric decline of the latter, with regard to the pulling angle and the inclination of the face 13, and a dynamic recoil due to the inertia of the wheel 10 set in motion. Depending on the choice of the profile of the face 13 of the teeth 12 (see above), these setbacks could be reduced to a minimum.

In FIG. 11, the clearance being completed and the corresponding angle of the wheel relative to the double scale 30, 50 being filled, the active face 13 (performing the function of the impulse face) of a tooth 12 of the wheel 10 between in contact with the impulse face 53 of the impulse lever 52 of the auxiliary latch 50. The latter initiates a pivoting under the action of the wheel 10 and transmits the movement to the primary latch 30, which will pivot in the direction reverse: this is the start of an impulse, an action transmitted to the ankle 23 by the input horn 41.

In FIG. 12, the active face 13 of the tooth 12 (cited in FIG. 11) leaves the impulse face 53 of the impulse lever 52 of the auxiliary rocker 50: this is the end of the impulse mentioned in fig. . 11.

[0054] In FIG. 13, the wheel 10 has finished its fall (safety phase) and the active face 13 (exercising its rest function) of a tooth 12 is pressed against the rest face 56 of the lever 55 of the auxiliary rocker 50. The rocker primary 30 is maintained against the output limiting pin 44 under the action of the pulling while the double plate 23 of the balance performs its additional ascending arcs (the completion of which closes the first alternation) then descending (whose initiation marks the start of the second alternation).

In FIG. 14, the double plate 20 completes its additional descending arc, the angle traversed during a period during which the wheel 10 and the double rocker 30, 50 are at a standstill.

[0056] In FIG. 15, the pin 23 comes into contact with the entrance horn 41 of the fork 40 of the primary rocker 30.

[0057] In FIG. 16, the rest face 56 of the rest lever 55 of the rocker 50 leaves the active face 13 (performing the function of the rest face) of a tooth 12 of the wheel 10, disengagement which causes a geometric recoil and a dynamic recoil (see the observations above (commentary on fig. 10)).

In FIG. 17, the clearance being completed and the corresponding angle of the wheel relative to the double scale 30, 50 being filled, the active face 13 (performing its function of impulse face) of a tooth 12 of the wheel 10 between in contact with the impulse face 33 of the impulse lever 32 of the primary latch 30. The latter initiates a pivoting under the action of the wheel 10 and transmits the movement to the auxiliary latch 50, which will pivot in the direction reverse: this is the start of an impulse, an action transmitted to the ankle 23 by the output horn 42.

In FIG. 18, the active face 13 of tooth 12 leaves the impulse face 33 of the impulse lever 32 of the primary latch 30: this is the end of the impulse mentioned in figure 17.

[0060] In FIG. 19, the wheel 10 has finished its fall (safety phase) and the active face 13 (exercising its rest function) of a tooth 12 is pressed against the rest face 36 of the lever 35 of the primary rocker 30. The latter is held against the entry limiting pin 43 under the action of the pulling while the double plate 23 of the balance performs its additional ascending arcs (the completion of which closes the second alternation) then descending (whose initiation marks the beginning of the first alternation of the following oscillation).

[0061] Figs. 20 to 25 correspond to figs. 8 to 13; they show the operating phases according to a first variant embodiment of the first embodiment described above. Similar to those which have just been explained, and being deduced from the obvious, we will limit ourselves to those of a first alternation.

According to this first variant - see fig. 20 - the escapement wheel 80, which has teeth 81 composed of teeth 82 each having an active face 83, is similar to that of a detent escapement wheel. The anchor is formed by a double rocker, that is to say a primary rocker 60 and an auxiliary rocker 70, both connected by connecting means 48 ensuring at the same time an inversion kinematics (unchanged reference, just like those of the others unmodified items). The primary rocker comprises three arms, namely an impulse arm 61 carrying an impulse lever 62 having an impulse face 63 and, on either side of the latter, two rest arms, one 64A carrying a rest lever 65A having a rest face 66A, the other 64B carrying a rest lever 65B having a rest face 66B.

According to a second variant, not shown, also conceivable and in a way symmetrical to the aforementioned first variant, the primary rocker carries only one lever, or a pulse, while the auxiliary rocker carries three levers, or an impulse lever and, on either side of it, a rest lever.

In all cases, the double articulated rocker anchor has a total of four separate levers, ie two thrust levers and two rest levers.

Returning to the operating phases according to the first variant, it is observed in FIG. 20that the double plate 20, after having completed its additional ascending arc, performs its additional descending arc, during which the escapement wheel 80 and the primary and auxiliary rockers 60, 70 are stopped.

In FIG. 21, the pin 23 comes into contact with the exit horn 42 of the fork 40 of the primary latch 60.

In FIG. 22, the rest face 66A of the rest lever 65A of the rocker 60 leaves the active face 83 (performing the function of the rest face) of a tooth 82 of the wheel 80, disengagement which causes a geometric recoil and a dynamic recoil .

In FIG. 23, the clearance being completed and the corresponding angle of the wheel relative to the double scale 60, 70 being filled, the active face 83 (performing the function of the impulse face) of a tooth 82 of the wheel 80 between in contact with the impulse face 73 of the impulse lever 72 of the auxiliary latch 70. The latter initiates a pivoting under the action of the wheel 80 and transmits the movement to the primary latch 60, which will pivot in the direction reverse: this is the start of an impulse, an action transmitted to the ankle 23 by the input horn 41.

In FIG. 24, the active face 83 of the tooth 82 which has just supplied the impulse leaves the impulse face 73 of the impulse lever 72 of the auxiliary rocker 70: this is the end of the impulse mentioned in FIG. 23.

In FIG. 25, the wheel 80 has completed its fall (safety phase) and the active face 83 (exercising its rest function) of a tooth 82 is pressed against the rest face 66B of the lever 65B of the primary rocker 60. The latter is held against the output limiting pin 44 under the action of the pulling while the double plate 23 of the balance performs its additional ascending arcs (the completion of which closes the first alternation) then descending (the initiation of which marks the beginning of the second alternation of the oscillation).

As indicated, it appears unnecessary to explain the operating phases of the second half of the oscillation, the person skilled in the art understanding them without further difficulty.

A second embodiment of the escapement according to the invention will be described, more succinctly, with reference to FIGS. 26, 27 and 28 (where references of elements identical to those presented in support of the first embodiment may be left unchanged).

The movement reversal means, necessary to allow the moving parts to work under identical conditions, like gears, moving which are formed here by two escape wheels and a double rocker, are arranged upstream of said lever to act on the exhaust wheel assembly.

[0074] The exhaust 100 shown in FIG. 26, disposed between a second wheel 104 from which it receives energy and a plate 20, of axis 25A, integral with a balance (not shown) receiving this energy, comprises a device 110 of escape wheels 10, 10B coaxial, of axis 110A, cooperating with the wheel 104 by means of an inversion mechanism formed of a return device 90 and of an inversion mobile 120, and an anchor formed of a double rocking. This double rocker comprises a primary rocker 30, pivoting about an axis 30A, and an auxiliary rocker 50, pivoting about an axis 50A, these two rockers, (identical to the rockers 30, 50 of the first embodiment) , being connected by kinematic and connecting means in the form of an intermediate latch 148 pivoting about an axis 148A.

[0075] The return device 90 (see section in FIG. 28) comprises a shaft 91 and a tube 95. The shaft 91 having lower and upper pivots (not referenced) comprises, at its lower part, an exhaust pinion 114 which it is integral with, this pinion meshing with the second wheel 104. On an upper support part 92 is driven out. the upper escape wheel 10. The tube 95 is mounted to rotate freely around the shaft 91 via two ruby bearings 96, 97, in upper and lower recesses (not referenced) from which these are driven. It has an escapement pinion 94 on its casing. The second escapement wheel 10B is driven onto a support part 98, resting against a bearing 99.

As can be seen clearly in FIG. 27, the coaxial escape wheels 10, 10B have teeth 11, 11B respectively and are identical to each other, with the difference that they are mounted so that the teeth of wheel 10 and those of wheel 10B are oriented opposite to each other.

The reversing mobile 120, axis 120A, comprises two identical wheels, a lower wheel 126 and an upper wheel 127 (Fig. 28) carried by a shaft 121 having upper and lower pivots (not referenced). These wheels are driven on support parts 122, 123, against bearings 124, 125 respectively of said shaft 121 and are indexed relative to each other.

The lower wheel 126 is arranged at the height of the second wheel 104 with which it meshes. Similarly, the upper wheel 127 is arranged at the height of the pinion 94 with which it meshes. The ratio of the pitch radius dimensions to the number of teeth of the second wheel 104 and the lower wheel 126 respectively is determined by construction. According to the example, this ratio is 1/1.

[0079] Based on FIGS. 26 and 27, it is observed that the lever 30 is arranged on the plane of the escape wheel 10, so that its impulse 32 and rest lever 35 can cooperate with the teeth 11 of said wheel 10. The lever 50 is arranged survival plane of the escape wheel 10B, so that its impulse 52 and rest lever 55 can cooperate with the teeth 11B of said wheel 10B, which is made possible thanks to a recess 149 provided in an arm 157 of the intermediate latch 148.

In the operating phase, the second wheel 104 rotates in the negative trigonometric direction (view from the dial side according to FIG. 27) and prints to the escape wheel 10 as well as to the wheel 126 of the reversing wheel set 120 a movement in the positive direction. The wheel 127 of the reversing wheel set, set in motion at the same time as the wheel 126, therefore in the positive direction, drives the lower escape wheel 10B in rotation in the negative direction, via the pinion 94 of the tube 95.

The reversal of movement being created at this stage, the escape wheels being driven by the same rotational movement, but in the opposite direction to each other, it is necessary to arrange the rockers 30 , 50 so that they pivot about their respective axes 30A, 50A in the same direction. This form of pivoting is provided by the intermediate lever 148 with two arms 137, 157, the ends of which have teeth 138, 158 respectively. The teeth 138 mesh with the teeth 38 of the arm 37 of the lever 30, and the teeth 158 mesh with the teeth 158 of the arm 57 of the lever 50.

Like the first embodiment, the primary and auxiliary rockers 30, 50 are arranged angularly with respect to the assembly 110 of the coaxial wheels 10 and 10B. The axes 110A, 30A passing through the centers ORE, OBF, on the one hand, and the axes 110A, 50A passing through the centers ORS, OBA, on the other hand, constitute two planes (symbolized in fig. 27 by their traces P3 and P4 in axis line) forming an angle ϕ. The centers OBA, OBP lie on arcs of circles of RBP radii; RBA, respectively, of center ORE, with RBA = p × RBP, where p is a coefficient at least approximately equal to 1 (according to the example presented, RBP = RBA = R2), a correction which may result from the completion or others construction considerations. The OBP center is located on the line of ORE – OREG centers, a possible angular shift can also be considered for the same reasons. According to the example shown, the center OBI of the intermediate latch 148 is also located on this arc of a circle of radius R2. A trace plane P5 formed by the axes 110A and 148A form a plane whose trace P5 is the bisector of the angle ϕ.

According to this second embodiment, the levers 30, 50 cooperate with the coaxial wheels 10, 10B, respectively, under conditions of the same nature also, that is to say like an external gear , and work identically, the same considerations as those set out above with regard to the first embodiment being applicable.

In particular, the identity of the working conditions is optimally assured, since, viewed in plan, at least the impulse faces 33, 53 of each impulse lever 32, 52 of the latches 30, 50 are conversely images of one another in at least one geometric transformation T (i) of ratio 1/1 or at least approximately 1/1. In other words, in this application, the image of one impulse face of one latch merges at least approximately with the impulse face of the other latch.

Considering an instant t, where the levers 32, 35; 52, 55 of the primary and secondary flip-flops 30; 50 show given positions such as those reproduced in FIG. 27 for example, the impulse face 53 and the lever 52 have as images the impulse face 33 and the lever 32 respectively, in a geometric transformation T (i) of ratio 1/1 consisting of an orthogonal vector symmetry, either T (5, +), of axis P5 (by which the elements 53, 52 have for images the elements 53 ́, 52 ́, and of a rotation of angle θ, or T (6, θ +), around the OBP center, by which the images 53 ́, 52 ́ themselves have as images the elements 53 ́ ́, 52 ́ ́ which merge with the impulse face 33 and the lever 32 respectively. reciprocal transformations T (5, -), T (6, θ–), the impulse face 33 and the lever 32 have as images the impulse face 53 and the lever 52. Here too, the theoretical ratio 1 / 1 may be subject to corrections as a function of technical considerations (see the remarks made in this connection in the context of the description of the first embodiment).

The operating phases of the exhaust according to this second embodiment are identical to those of the exhaust according to the first embodiment, explained in support of FIGS. 8 to 19, to which the reader can refer.

Finally, note that the escapement according to this second embodiment can be matched with a double lever corresponding to the manufacturing variants mentioned in the context of the description of the first embodiment, one of these variants having been explained in support of fig. 20 to 25.

List of references

[0088] exhaust according to 1 <è> <re> 001: <sep> embodiment (general designation) 002: <sep> motor unit 003: <sep> counter / finishing gear train 004: <sep> second wheel 005: <sep> regulator 006: <sep> segment on the flank of the impulse face (rocker 30) against which a tooth 12 strikes (via segment 7 of the flank of this tooth) 007: <sep> segment on the flank of the tooth 12 impacting against an impulse face) 008: <sep> extreme edge of the impulse face 33 009: <sep> extreme edge of the impulse face 53 010: <sep> escape wheel 010A: <sep> axis wheel 10 011: <sep> toothing of the wheel 10 012: <sep> any tooth of the wheel 10 013: <sep> active face of any tooth 12 (pulse and rest) 014: <sep> exhaust pinion 015 : <sep> pitch circle wheel 10 016: <sep> pitch circle rocker 30 (impulse lever) 017: <sep> pitch circle rocker 50 (impulse lever) 018: <sep> section on flank of face d 'pulse 33 on which a tooth 12 rolls (by its edge 7) 019: <sep> section on flank of the impulse face 53 on which a tooth 12 rolls (by its edge 7) 020: <sep> double chainring (general reference) 021: <sep> large chainring 022: <sep> small chainring 023: <sep> ankle plate weight 024: <sep> notch 025: <sep> balance 025A: <sep> balance axle 25 026-029: <sep> Ø 030: <sep> primary rocker (general reference) 030A: <sep> primary rocker axis 031 : <sep> impulse lever support arm 032: <sep> impulse lever 033: <sep> impulse face of lever 32 034: <sep> support arm of rest lever 035: <sep> control lever rest 036: <sep> rest face of the lever 35 037: <sep> supporting arm of the connecting means and kinematics 038: <sep> teeth of the arm 37 039: <sep> rod 040: <sep> fork 041: <sep > input horn 042: <sep> output horn 043: <sep> input limiting pin 044: <sep> output limiting pin 045: <sep> dart 046: <sep> segment OBP - edge 8 (lever 32 ) 047: <sep> segment OBA - edge 98 (lever 32) 048: <sep> connecting means and kinematics 049: <sep> Ø 050: <sep> auxiliary rocker 050A: <sep> auxiliary rocking axis 051: <sep> support arm of the impulse lever 052: <sep> impulse lever 053: <sep> impulse face of the lever 52 054: <sep> support arm of the lever rest 055: <sep> rest lever 056: <sep> rest face of the lever 55 057: <sep> supporting arm for the connection and kinematics 058: <sep> toothing of the arm 57 059: <sep> Ø 060 : <sep> Primary rocker (depending on version) 061: <sep> support arm of the impulse lever 062: <sep> impulse lever 063: <sep> impulse face of the lever 62 064A: <sep > support arm of rest lever 064B: <sep> support arm of rest lever 065A: <sep> rest lever 065B: <sep> rest lever 066A: <sep> rest face of lever 65A 066B: <sep> rest face of lever 65B 067-069: <sep> Ø 070: <sep> auxiliary rocker (execution variant) 071: <sep> support arm of the impulse lever 072: <sep> impulse lever 073: <sep> side of the impulse lever 72 074–079: <sep> Ø 080: <sep> escape wheel (depending on the version) 081: <sep> toothing of the wheel 80 082: <sep> any tooth of the wheel 80 083: <sep> active face of any tooth 82 (pulse and rest) 084–089: <sep> Ø 090: <sep> reversing device 091: <sep > shaft 092: <sep> upper support part of shaft 91 (wheel 10) 093: <sep> Ø 094: <sep> exhaust pinion (for wheel 10) 095: <sep> tube 096: <sep > bearing 097: <sep> bearing 098: <sep> support part for impeller 10B 099: <sep> bearing surface 982 <è> <me> 100: <sep> embodiment (general designation) 101–109: <sep> Ø 110: <sep> set of coaxial escape wheels 110A: <sep> axle of assembly 110 010: <sep> upper escape wheel 010C: <sep> lower escape wheel 111–113 : <sep> Ø 114: <sep> exhaust pinion (from wheel 10C) 115–119: <sep> Ø 120: <sep> reversing mobile 120A: <sep> reversing mobile shaft 121: < sep> shaft 122–136: <sep> Ø 137: <sep> arm of the means 148 cooperating with the rocker 30 138: <sep> toothing of the arm 137 139–147: <sep> Ømeans of connection and kinematics between the rockers 30 and 50 according to the 2 <rd> 148: <sep > embodiment 148A: <sep> axis of the means 148 149: <sep> setback 150–156: <sep> Ø 157: <sep> arm of the means 148 cooperating with the lever 50 158: <sep> teeth of the arm 157

Claims (18)

1. - Exhaust distributing energy to a regulating organ in successive pulses and whose assortment comprises At least one escape wheel having a peripheral toothing, free to rotate about an axis and subjected to a driving force, and A rocker adapted to pivot about an axis and comprising, on the one hand, at least one lever having a pulse face successively receiving from said toothing a quantity of energy and, on the other hand, a member cooperating with the regulating member for transmitting each time to the latter said quantity of energy, characterized in that Said flip-flop constitutes a primary flip-flop which is connected by connecting means to an auxiliary flip-flop capable of pivoting about an axis, these flip-flops being arranged relative to one another so that their axes constitute with the axis of the escape wheel two planes forming an angle α, The auxiliary rocker comprises at least one lever having a pulse face successively receiving from said toothing a quantity of energy, And in that kinematic inversion means are arranged to allow the toothing of the escape wheel to alternately exert a meshing action of the same type with each of the pulse levers, so as to allow a transmission optimal energy for its completeness and regularity. 2. Exhaust according to claim 1, characterized in that, in plan view, at least the pulse faces are reciprocally images of each other in a geometric transformation T (i). 3. - Exhaust according to claim 2, characterized in that the ratio of all elements selected to be mutually images of each other in the transformation T (i) is at least approximately 1/1. 4. - Exhaust according to claim 2 or 3, characterized in that the geometric transformation T (i) can proceed from the application, at any time, - An angle rotation defined around the ORS center of the escape wheel followed or preceded by a defined angle rotation around the center OBP; OBA of the primary or auxiliary rocker respectively, Or a defined vector translation followed or preceded by a rotation of angle defined around the center OBP i OBAde the primary or auxiliary rocker respectively, Or of a definite orthogonal symmetry followed or preceded by a rotation of angle defined around the center OBP; OBA of the primary or auxiliary rocker respectively. 5. - Exhaust according to one of claims 1 to 4, characterized in that it comprises a single escape wheel and said kinematic inversion means proceed from said means for connecting the latches together and act on the latter, a pivoting of one of the latches in one direction causing a pivoting of the other in the opposite direction. 6. - Exhaust according to claim 5, characterized in that each of the primary and auxiliary latches comprises a device cooperating with each other, preferably a toothed sector meshing with one another, to form said connecting means and kinematics of inversion. 7. - Exhaust according to one of claims 1 to 4, characterized in that it comprises two coaxial escapement wheels, said kinematic inversion means proceed from means acting on said wheels to ensure an inversion of their directions of rotation, that a defined escape wheel meshes with each pulse lever of the primary rocker while the other escape wheel meshes with each pulse lever of the auxiliary rocker, and in that said linkage means primary and auxiliary latches act on the latter, so that a pivoting of one in one direction causes a pivoting of the other in the same direction. 8. - Exhaust according to claim 7, characterized in that the reversing means comprise a return device and an inverting mobile cooperating with each other. 9. - Exhaust according to claim 7 or 8, characterized in that the connecting means and kinematics connecting the primary and auxiliary flip-flops are formed of an intermediate flip-flop. 10. - Exhaust according to one of claims 1 to 9, characterized in that the primary and the auxiliary rocker each comprise, on the one hand, a lever having a pulse face to form a pulse lever and, on the other hand, a lever having a rest face to form a rest lever. 11. - Exhaust according to one of claims 1 to 9, characterized in that the primary and the auxiliary rocker each comprise a lever having a pulse face to form a pulse lever and the primary rocker, Either has two levers each having a rest face to form two idle levers, while the auxiliary latch has none, - Or has no rest lever, while the auxiliary rocker has two. 12. - Exhaust according to one of claims 1 to 11, characterized in that the primary and auxiliary latches are arranged such that at the start of a pulse provided by a tooth of an escape wheel alternately lever pulse of one then the other of these latches, the contact segment between the tooth and the impulse face is located at least near a plane formed by the axis of the wheel and the axis of the corresponding rocker. 13. - Exhaust according to one of claims 1 to 12, characterized in that the teeth forming the peripheral toothing of an escape wheel each have a single active face cumulatively filling the functions of pulse face and face of rest. 14. - Exhaust according to claim 13, characterized in that the profile of the active faces of the teeth is flat. 15. - Exhaust according to claim 13, characterized in that at least the profile of the active faces of the teeth is curved, preferably responding to the equations of involute circle, epicycloid or a combination of these curves. 16. - Exhaust according to one of claims 1 to 15, characterized in that the profile of the pulse faces of the pulse levers is flat. 17. - Exhaust according to one of claims 1 to 15, characterized in that the profile of the pulse faces of the pulse levers is curved, preferably responding to the equations of involute of circle, epicycloid or a combination of these curves. Hourly instrument comprising an exhaust according to one of claims 1 to 17.