Escapement device for a clock and method of operation of such a device

Description

[0001] The invention relates to a method for operating a watch escapement device. The invention also relates to a watch escapement device. The invention also relates to a watch movement comprising such a device. The invention finally relates to a timepiece comprising such a device or such a watch movement. The invention also relates to a transmission device and a timepiece comprising such a transmission device.

[0002] Known escapement devices such as the Swiss lever escapement or the Robin type escapement, described for example in patent EP1122617B1, conventionally comprise an escape wheel and a blocker. The escape wheel and pinion consists of a first escape pinion meshing with or participating in the finishing gear train of a watch movement and an escape wheel designed to cooperate by contact with the blocker which is itself designed to cooperate by contact with an oscillator, in particular a sprung balance, in particular a roller pin of a sprung balance. In the disengagement phase, the roller pin directly actuates the blocker, by means of a blocker fork, which itself acts directly against the escape wheel. Such escapement devices have relatively low efficiencies, of the order of 30% to 40%.Documents WO2011064682A1, WO2013182243A1 and EP1041459A1 are also known, which disclose watch escapement devices, which comprise the intermediate moving parts between the blocker and the escape wheel. The aim of the invention is to provide a watch escapement device making it possible to overcome the drawbacks mentioned above and to improve the watch escapement devices known from the prior art. In particular, the invention provides an escapement device whose mechanical efficiency is improved.

[0003] A method of operation relating to the invention is defined by claim 1.

[0004] Different embodiments of the operating method are defined by dependent claims 2 to 4.

[0005] An exhaust device relating to the invention is defined by claim 5.

[0006] Various embodiments of the exhaust device are defined by dependent claims 6 to 15.

[0007] A watch movement relating to the invention is defined by claim 16.

[0008] A timepiece relating to the invention is defined by claim 17.

[0009] The attached figures represent, by way of examples, two embodiments of a timepiece according to the invention. There figure 1 is a schematic view of a first embodiment of a timepiece according to the invention comprising a first variant of a first embodiment of an escapement in a first rest position. The figure 2 is a view of the first variant of the first embodiment of the escapement in a second position. The figure 3 is a view of the first variant of the first embodiment of the escapement in a third rest position. The figure 4 is a view of the first variant of the first embodiment of the escapement in a fourth position. The figure 5 is a view of the first variant of the first embodiment of the escapement in a fifth impulse position. The figure 6 is a detailed view of a first variant of the blocker of the first embodiment of the escapement. The figure 7 is a detail view of a second variant of the blocker of the first embodiment of the escapement. The figure 8 is a detail view of a third variant of the blocker of the first embodiment of the escapement. The figure 9 is a schematic view of a first variant of a second embodiment of a timepiece according to the invention comprising a first variant of a second embodiment of an escapement in a first rest position. figure 10 is a view identical to the figure 9 on which the contact efforts were represented. The figure 11 is a view of the first variant of the second embodiment of the escapement in a second impulse position. The figure 12 is a schematic view of a second variant of the second embodiment of a timepiece according to the invention comprising a second variant of the second embodiment of an escapement in a first rest position. The figure 13 is a view of the second variant of the second embodiment of the escapement in a second impulse position. The figure 14 is a schematic view of a third variant of the second embodiment of a timepiece according to the invention comprising a third variant of the second embodiment of an escapement in a first rest position. figure 15 is a view of the third variant of the second embodiment of the escapement in a second impulse position.

[0010] A first embodiment of a timepiece 600 is described below with reference to figures 1 à 8 The timepiece is for example a watch, in particular a wristwatch. The timepiece comprises a first embodiment of a watch movement 500, in particular a mechanical movement. The movement comprises a first variant of a first embodiment of an escapement device 400 arranged between a gear train and an oscillator 4, 5.

[0011] The gear train is designed to connect a driving component, such as a barrel, to the escapement. The gear train thus allows energy to be transmitted from the driving component to the escapement. The escapement provides energy to the oscillator to maintain its oscillations.

[0012] The oscillator is for example a 4-spring 5 type oscillator. The balance is pivoted on an axis A4.

[0013] The escapement device 400 mainly comprises a first escape wheel 1 pivoted about an axis A1, a second escape wheel 2 pivoted about an axis A2 and a blocker 3 pivoted about an axis A3. The first escape wheel, the second escape wheel and the blocker are shaped and arranged so that, in a release phase of the escapement device, a force from the blocker controlled by the oscillator 4, 5 is transmitted to the first escape wheel via the second escape wheel. A release phase notably comprises a phase of release of the blocking means of the blocker from the teeth of the second wheel 2 under the control of the oscillator 4, 5, that is to say that the positions of the blocker are determined by the positions of the oscillator.

[0014] The first escapement wheel 1 comprises a first escape wheel 1a capable of acting, directly or indirectly, on the clockwork oscillator. A first pinion 1b of the finishing gear train is rotationally integral with the first escape wheel 1a, in particular is fixed to the first escape wheel 1a, in particular is fixed coaxially to the first escape wheel 1a.

[0015] In the first embodiment of the escapement device, the second escapement wheel comprises a single second escapement pinion 2b.

[0016] In a preferred variant of the first embodiment, the escapement device is a direct impulse escapement device, the operating principle of which is similar to that of a Robin type escapement device. This can, for example, be designed to cooperate with a 4-spiral 5 balance type oscillator.

[0017] The first escape wheel 1a is designed to directly actuate the balance 4 - balance spring 5 via one of its teeth which, during each impulse phase of the escapement device, acts against an impulse pallet 40b of a plate 40 of the balance 4. Thus, the balance receives, in the impulse phase, energy directly from the first escape wheel 1a. This avoids friction losses induced by the blockers of the indirect impulse escapement devices. To do this, the first escape wheel 1a is kinematically linked to the driving member of the clockwork movement via the first pinion 1b.

[0018] To minimize as much as possible the release energy to be provided by the balance, the first escape wheel 1a is capable of being blocked by the blocker 3 via the second escape wheel 2b which is interposed between the first wheel 1 and the blocker 3. To do this, the arrangement of the blocker, the first escape wheel and the second escape wheel is such that the force between the second escape wheel and the blocker 3 is significantly lower than the force between the first escape wheel and the second escape wheel, during the release phases. More particularly, the arrangement of the blocker, the first escape wheel and the second escape wheel is such that the force between the second escape pinion 2b and the blocker 3 is lower than the force between the first escape wheel 1a and the second escape pinion 2b.

[0019] There figure 1 illustrates a first rest position of the escapement device. In this figure, the balance wheel 40 rotates counterclockwise, and the pallet or pin 40a for releasing the balance wheel 40 moves away from a fork 3a of the blocker 3. A tooth 10a of the wheel 1a, under the effect of the torque produced by the driving member, exerts a force F2 on a rest surface 200b of a tooth 20b of the pinion 2b. The force F2, which passes substantially close to the axis A2, creates a torque which tends to pivot the second pinion 2b in the counterclockwise direction, which generates a force F3 of support of a tooth 21b of the pinion 2b on a rest surface 30b of blocking means 3b, in particular a pallet 3b, of the blocker 3. The rest surface 30b is arranged so that the direction of the force F3 passes substantially through the axis A3. These forces are the same during the disengagement phase which will follow, apart from the friction angles.

[0020] It can be seen that the angle α formed between the force vector F2 and the half-line originating from the point of contact between the wheel 1a and the pinion 2b and passing through the axis A2 (or formed between the force vector F2 and a radial vector D relative to the axis A2 and originating from the point of contact between the wheel 1a and the pinion 2b) is significantly less than 50°, in particular less than 30°, or even less than 20°.

[0021] At rest, neglecting friction: F 3 = F 2 × DO 2 / DO 3 with : F2 and F3: the values ​​of the intensities of the respective support forces against the surfaces 200b and 30b; DO2: the value of the lever arm of the force F2 with respect to the axis A2; DO3: the value of the lever arm of the force F3 with respect to the axis A2.

[0022] Since DO2< <DO3, on constate ainsi que l'intensité de la force F3 est sensiblement plus faible que l'intensité de la force F2.

[0023] There figure 2 illustrates the escapement device just after the release phase which follows the first rest position illustrated on the figure 1 . On the figure 2 , the plate 40 of balance wheel 4 rotates clockwise. During the release phase, the release pallet 40a of the plate 40 of balance wheel 4 came into contact with the fork 3a of the blocker 3 and caused the latter to pivot counterclockwise. This contact and this action are maintained on the figure 2 This action released tooth 21b of pinion 2b from rest surface 30b. The energy supplied by the balance wheel during this release to overcome friction and to set the wheels and the blocker in motion is significantly lower than that supplied in a conventional Robin-type escapement device.

[0024] This low energy expenditure is explained by the fact that the intensity of the force F3 is significantly lower than that of the support force F2. This intensity of the force F3 is minimized as much as possible if the inertias of the mobiles 1, 2 and of the blocker 3 are minimized as much as possible. Preferably, the total diameter D2b of the pinion 2b is reduced as much as possible so as to reduce as much as possible the inertia of the pinion 2b, as well as the dimensions of the blocker 3. Thus, preferably, the total diameter D2b of the pinion 2b is significantly less than the total diameter D1a of the first wheel 1a. For example, the total diameter D2b of the pinion 2b is less than 30% of the total diameter D1a of the first wheel 1a, or even less than 20% of the total diameter D1a of the first wheel 1a.

[0025] After the release phase, the pinion 2b rotates counterclockwise. The tooth 22b of this pinion approaches the resting surface 30c of second locking means 3c of the blocker 3 and rests on this surface in a second resting position.

[0026] There figure 3 illustrates this second rest position. In this figure, the pallet 40a of the plate 40 of the balance wheel 4 moves away from the fork 3a of the blocker 3. The tooth 10a of the wheel 1a, under the effect of the torque of the driving member, exerts a force F2* on the rest surface 200b of the tooth 20b of the pinion 2b. The force F2*, which passes substantially close to the axis A2, creates a torque which tends to pivot the pinion 2b in the counterclockwise direction, which causes a bearing force F3* of the tooth 22b on the rest surface 30c of the pallet 3c of the blocker 3. The rest surface 30c is arranged so that the direction of the force F3* passes substantially through the axis A3. These forces are the same during the disengagement phase which will follow, apart from the friction angles.

[0027] At rest, neglecting friction: F 3 * = F 2 * × DO 2 * / DO 3 * with : F2* and F3*: the values ​​of the intensities of the respective support forces against the surfaces 200b and 30c; DO2*: the value of the lever arm of the force F2* with respect to the axis A2; DO3*: the value of the lever arm of the force F3* with respect to the axis A2.

[0028] Since DO2*< <DO3*, on constate ainsi que l'intensité de la force F3* est sensiblement plus faible que l'intensité de la force F2*.

[0029] There figure 4 illustrates the escapement device just after the release phase which follows the second rest position illustrated on the figure 3 . On the figure 4 , the balance wheel rotates counterclockwise. During the release phase, the release pallet 40a of the balance wheel is in contact with the fork 3a of the blocker 3 and causes the latter to rotate clockwise. This contact and this action are maintained on the figure 4 . This action released tooth 22b of pinion 2b from rest surface 30c. For reasons similar to those described above, the energy supplied by the balance wheel during this release to overcome friction and to set the wheels and the blocker in motion is significantly lower than that supplied in a conventional Robin-type escapement device.

[0030] After this release, the first escape wheel 1a accelerates and pushes, in particular pushes tangentially, the second pinion 2b in the counterclockwise direction. Simultaneously, the tooth 11a of the escape wheel approaches the impulse pallet 40b of the balance wheel plate to transmit the energy to the balance wheel by the action of the tooth 11a on the pallet 40b during an impulse phase. Preferably, the force transmitted from the tooth 11a to the pallet 40b is substantially tangential relative to the axes A1 and A4.

[0031] There figure 5 illustrates the position of the escapement at the end of the impulse phase. On the figure 5 , the tooth 11a and the pallet 40b are in contact by their respective ends and the tooth 20b of the pinion 2b approaches the rest surface 30b of the pallet 3b of the blocker 3. As soon as the tooth 20b comes into contact with the blocker 3 and the tooth 10a comes into contact with the second escape wheel 2, we find ourselves in the configuration illustrated by the figure 1 .

[0032] The escapement device according to this variant of the first embodiment has a very high efficiency, because it allows, on the one hand, to significantly reduce the energy supplied by the balance during disengagement, and on the other hand allows to increase the efficiency of the energy transmission thanks to a direct impulse from the escape wheel 1a to the balance, in particular by means of a force transmitted from the first escape wheel directly to the balance and which is substantially tangential. Another advantage of such an escapement device is the preservation, and therefore the optimization, of the isochronism of the sprung balance due to the low energy to be transmitted by the balance during disengagement.

[0033] Preferably, the rest surfaces 30b, 30c of the locking means 3b, 3c of the blocker 3 are of concave shapes in order to guarantee the positioning precision of the teeth 20b of the pinion 2b on these surfaces. For example, these concave surfaces can each be formed by two inclined planes making an angle preferably between 120° and 170°, as illustrated in the figure 6 .

[0034] In a second variant of the escapement device, the blocker 3 may also be provided with mechanical transmission means 3d, 3e, for example protrusions 3d, 3e, capable of rotating the pinion 2b in the opposite direction to that of the first escape wheel 1a, in addition to the forces F2, F2*. Thus, these transmission means may exert an action complementary to those of the forces F2 and F2* to rotate the second escape wheel counterclockwise. The actions are for example exerted by the blocker via the transmission means at the rest surfaces of the second escape wheel. An example of an escapement device blocker according to the second variant is for example illustrated in the figure 7 .

[0035] In a third variant of the escapement device, the blocker 3 can also be provided with a 3f pin intended to cooperate with a complementary balance wheel plate 41 as shown in the figure 8 , and this in order to prevent untimely movements of the blocker in the event of an impact. This third variant can be combined with either of the first and second variants.

[0036] In the different variants of the first embodiment, the geometries of the elements of the exhaust can be as described below.

[0037] The first escapement wheel 1 comprises teeth 10a, in particular 20 teeth. The teeth are in the form of points. The teeth are oriented downstream (relative to their movement) in a direction making an angle of between 20 and 45° with the radial direction relative to the axis of the first wheel. The free end of each tooth may be in the form of a bevel.

[0038] The second escape wheel 2 comprises teeth 20b, in particular 4 teeth. The teeth extend substantially along an angular sector of approximately 45°. Each tooth comprises a rest surface 200b oriented to form an angle β of between 15° and 50°, or even between 20° and 45°, with the orthoradial direction relative to the axis A2 of the second wheel. The angle β is an acute angle measured between the tangent to the rest surface and an orthoradial vector O2 relative to the axis A2 and originating from the point of contact between the wheel 1a and the pinion 2b. This orientation makes it possible to create a slight torque tending to rotate the second wheel against the blocker in the rest and release phases. Each tooth is also limited by at least one lateral surface 202b oriented substantially radially relative to the axis A2.

[0039] The angles α and β are therefore equal to the friction angle. (friction angle at the point of contact between wheel 1a and pinion 2b)

[0040] The blocker 3 comprises resting surfaces 30b, 30c. The resting surfaces of the blocker are oriented at least substantially orthoradially relative to the axis A3.

[0041] In the rest phase, one end of a tooth 10a bears against a rest surface 200b of a tooth 20b of the second escape wheel and a lateral surface 202b of another tooth 21b of the second wheel bears against one or other of the rest surfaces 30b, 30c of the blocker.

[0042] Advantageously, in the rest phase and in the release phase (as long as the second escape wheel is resting against the blocker), a half-line having as its origin the axis A2 of the second escape wheel and passing through the first point of contact where the first force F2 of the first escape wheel is applied to the second escape wheel and a half-line having as its origin the axis A2 of the second escape wheel and passing through the axis A1 of the second escape wheel form an angle greater than 10°, or even greater than 20°, or even greater than 30°.

[0043] Advantageously, and in a complementary or alternative manner, in the rest phase and in the release phase (as long as the second escape wheel is resting against the blocker), a half-line having as its origin the axis A1 of the first escape wheel and passing through the axis A2 of the second escape wheel; and a half-line having as its origin the axis A1 of the first escape wheel and passing through the first point of contact where the first force F2 of the first escape wheel is applied to the second escape wheel form an angle greater than 5°, or even greater than 10°, or even greater than 20°.

[0044] A second embodiment of a timepiece 600', 600", 600* is described below with reference to figures 9 à 15 . The timepiece is for example a watch, in particular a wristwatch. The timepiece comprises a second embodiment of a watch movement 500', 500", 500*, in particular a mechanical movement. The movement comprises a second embodiment of an escapement device 400', 400", 400* arranged between a gear train and an oscillator 4, 5.

[0045] The gear train is designed to connect a driving component, such as a barrel, to the escapement. The gear train thus allows energy to be transmitted from the driving component to the escapement. The escapement provides energy to the oscillator to maintain its oscillations.

[0046] The oscillator is for example an oscillator of the type balance 4 - hairspring 5. The balance is pivoted on an axis A4', A4", A4*.

[0047] The escapement device 400', 400", 400* mainly comprises a first escape wheel 1', 1", 1* pivoted about an axis A1', A1", A1*, a second escape wheel 2', 2", 2* pivoted about an axis A2', A2", A2* and a blocker 3', 3", 3* pivoted about an axis A3', A3", A3*. The first escape wheel, the second escape wheel and the blocker are shaped and arranged so that, in a release phase of the escapement device, a force from the blocker controlled by the oscillator 4, 5 is transmitted to the first escape wheel via the second escape wheel.

[0048] The first escapement wheel comprises a first escape wheel 1a', 1a", 1a* capable of acting indirectly on the clockwork oscillator. A first pinion 1b', 1b", 1b* of the finishing gear train is rotationally fixed to the first escape wheel 1a', 1a", 1a*, in particular is fixed to the first escape wheel 1a, 1a", 1a*, in particular is fixed coaxially to the first escape wheel 1a', 1a", 1a*. In the first variant, the escapement device is a direct impulse escapement device, the operating principle of which is similar to that of a Robin type escapement device. This can, for example, be designed to cooperate with a 4-spiral 5 balance wheel type oscillator.

[0049] In the second embodiment of the escapement device, the second escapement wheel comprises a second escape pinion 2b', 2b", 2b* and a second wheel 2a', 2a", 2a*. The second wheel 2a', 2a", 2a* is secured to the second escape pinion 2b', 2b", 2b*, in particular the second wheel 2a', 2a", 2a* is fixed to the second escape pinion 2b', 2b", 2b* or vice versa. The blocker cooperates with the second escape pinion 2b', 2b", 2b* via the second escape wheel 2a', 2a", 2a*, and vice versa. Like the escapement device according to the first embodiment, the second pinion 2b', 2b", 2b* is designed to cooperate directly with a first escape wheel 1a', 1a", 1a* which is rotationally fixed to the first pinion 1b', 1b", 1b* of the finishing gear of the clockwork movement.

[0050] In the first variant of the second embodiment, the escapement device is of the direct impulse type. Its operating principle is similar to that of a Robin type escapement device. This can, for example, be designed to cooperate with a balance-spring type oscillator.

[0051] In the first variant of the second embodiment, the escapement device differs from that of the first embodiment in that the impulse to the sprung balance is produced by a tooth 20a' of the second escape wheel 2a'.

[0052] During the release phase, the exhaust device has an operation equivalent to that of the first embodiment.

[0053] In this first embodiment, the second wheel 2a' has the same number of teeth as the second pinion 2b', namely six teeth.

[0054] There figure 9 illustrates a rest position of such an escapement device, similar to that of the device according to the first embodiment illustrated by the figure 3 , which precedes a release phase.

[0055] The tooth 10a' of the wheel 1a', under the effect of the torque of the driving member, exerts a force F20 on a rest surface 200b' of the tooth 20b' of the pinion 2b'. The force F20, which passes substantially close to the axis A2', creates a torque which tends to pivot the pinion 2b' in the counterclockwise direction, which causes a bearing force F30 of a tooth 20a' on a rest surface 30c' of the locking means 3c' of the blocker 3'. The rest surface 30c' is arranged so that the direction of the force F30 passes substantially through the axis A3'. These forces are the same during the disengagement phase which will follow, apart from the friction angles.

[0056] At rest, neglecting friction: F 30 = F 20 × DO 20 / DO 30 with : F20 and F30: the values ​​of the intensities of the respective support forces against the surfaces 200b' and 30c'; DO20: the value of the lever arm of the force F20 with respect to the axis A2'; DO30: the value of the lever arm of the force F30 with respect to the axis A2'.

[0057] Since DO20< <DO30, on constate ainsi que l'intensité de la force F30 est sensiblement plus faible que l'intensité de la force F20.

[0058] The energy supplied by the balance wheel during the release phase to overcome friction and to set the wheels and the blocker in motion is significantly lower than that supplied in a conventional Robin-type escapement device.

[0059] This low energy expenditure is explained by the fact that the intensity of the F30 force is significantly lower than that of the F20 support force.

[0060] It is also noted here that the angle α' formed between the force vector F20 and the half-line originating from the point of contact between the wheel 1a' and the pinion 2b' and passing through the axis A2' (or formed between the force vector F20 and a vector D' radial relative to the axis A2' and originating from the point of contact between the wheel 1a' and the pinion 2b') is significantly less than 50°, or even less than 30°, or even less than 20°.

[0061] This intensity of the force F30 is minimized as much as possible if the inertias of the mobiles 1', 2' and of the blocker 3' are minimized as much as possible. Preferably, the total diameter D2b' of the pinion 2b' is reduced as much as possible so as to reduce as much as possible the inertia of the pinion 2b', as well as the dimensions of the blocker 3'. Thus, preferably, the total diameter D2b' of the pinion 2b' is substantially less than the total diameter D1a' of the first wheel 1a', in particular less than 50%, or even less than 40% of the total diameter D1a' of the first wheel 1a'.

[0062] The tooth profile of the elements 1a' and 2b' can also be shaped so that the torque transmitted by the first wheel 1a' to the second pinion 2b' during the impulse phase is significantly greater than that transmitted during disengagement.

[0063] When engaging in the release phase which follows the rest phase illustrated on the figure 9 , the torque C2d at the pinion 2b' can be expressed in the following way with respect to the torque C1d at the wheel 1a', and neglecting friction: C 2 d = C 1 d × DO 20 / DO 10 with : DO10: the value of the lever arm of force F20 relative to axis A1'; DO20: the value of the lever arm of force F20 relative to axis A2';

[0064] When engaging the impulse phase such as that illustrated by the figure 11 , an impulse surface 201b" of the second pinion 2b' is oriented so that the transmitted force F20' is substantially tangential to the trajectory of the point of contact between the wheel 1a' and the pinion 2b'. In other words, when the impulse phase is engaged, the force F20' is substantially normal to the half-line originating from the axis A1' and passing through the axis A2'.

[0065] When engaging this impulse phase, the torque C2i at the pinion 2b' can be expressed in the following manner with respect to the torque C1i at the wheel 1a', and neglecting friction: C 2 i = C 1 i × DO 20 ′ / DO 10 ′ with : DO10': the value of the lever arm of force F20' relative to axis A1'; DO20': the value of the lever arm of force F20' relative to axis A2'.

[0066] Given that: DO 20 / DO 10 ≪ DO 20 ′ / DO 10 ′ et que C 1 d = C 1 i

[0067] The torque C2i transmitted to the pinion 2b' during the impulse phase is substantially greater than the torque C2d transmitted to the pinion 2b' during the release phase. Thus, the energy to be supplied by the balance during the release phase is minimized and the energy transmitted by the driving member during the impulse phase to the escapement device is maximized. Such an escapement device thus has the advantage of having a maximized efficiency compared to the escapement devices known from the prior art, of the order of 120 to 160% compared to average reference efficiencies of the order of 30 to 40%. Such a device also has the advantage of minimizing the disturbances of the oscillator, and thus makes it possible to implement an oscillator with optimized isochronism compared to the oscillators cooperating with escapement devices known from the prior art.

[0068] In the first variant of the second embodiment, the geometries of the exhaust elements may be as described below.

[0069] The first escapement wheel 1' comprises teeth 10a', in particular 20 teeth. The teeth are oriented downstream (relative to their movement) in a direction making for example an angle of between 20° and 45° with the radial direction relative to the axis A1' of the first wheel. The free end of each tooth may be bevel-shaped.

[0070] The second escape pinion 2b' comprises teeth 20b', in particular 6 teeth. The teeth extend substantially along an angular sector of approximately 30°. Each tooth comprises a rest surface 200b' oriented to form an angle β' of between 15° and 50°, or even between 20° and 45°, with the orthoradial direction O2' relative to the axis A2' of the second wheel set. The angle β' is an acute angle measured between the tangent to the rest surface and an orthoradial vector O2' relative to the axis A2' and originating at the point of contact between the wheel 1a' and the pinion 2b'. This orientation makes it possible to create a slight torque tending to rotate the second wheel set against the blocker in the rest and release phases. Each tooth is also limited by at least one lateral surface oriented substantially radially relative to the axis A2'. This at least one lateral surface is an impulse surface 201b'.

[0071] The angles α' and β' are therefore equal to the friction angle. (friction angle at the point of contact between wheel 1a' and pinion 2b')

[0072] The blocker 3 comprises resting surfaces 30b', 30c'. The resting surfaces are oriented at least substantially orthoradially relative to the axis A3' of the blocker.

[0073] In the rest phase, one end of a tooth 10a' bears against a rest surface 200b' of a tooth 20b' of the second escape wheel and one end of a tooth 20a' of the second wheel bears against a rest surface 30b', 30c' of the blocker.

[0074] Advantageously, in the rest phase and in the release phase (as long as the second escape wheel is resting against the blocker), a half-line having as its origin the axis A2' of the second escape wheel and passing through the first point of contact where the first force F20 of the first escape wheel is applied to the second escape wheel and a half-line having as its origin the axis A2' of the second escape wheel and passing through the axis A1' of the second escape wheel form an angle greater than 10°, or even greater than 20°, or even greater than 30°.

[0075] Advantageously, and in a complementary or alternative manner, in the rest phase and in the release phase (as long as the second escape wheel is resting against the blocker), a half-line having as its origin the axis A1' of the first escape wheel and passing through the axis A2' of the second escape wheel; and a half-line having as its origin the axis A1' of the first escape wheel and passing through the first point of contact where the first force F20 of the first escape wheel is applied to the second escape wheel form an angle greater than 5°, or even greater than 10°, or even greater than 20°.

[0076] In a second variant of the second embodiment shown in the figures 12 And 13, the escapement device is of the indirect impulse type. Its general operating principle is similar to that of a Swiss lever escapement device. The escapement device according to the second variant of the second embodiment may, for example, be designed to cooperate with an oscillator of the sprung balance type.

[0077] Such an escapement device is distinguished from that of the first variant of the second embodiment by the fact that the impulse to the sprung balance is achieved by means of a 3" blocker whose fork 3a" is designed to cooperate exclusively with a 4" balance, in particular a 40" balance wheel plate, in particular a 40a" balance wheel pin.

[0078] There figure 12 illustrates a rest position of such an escapement device which precedes a release phase.

[0079] A tooth 10a" of the wheel 1a", under the effect of the torque of the driving member, exerts a force F21 on a rest surface 200b" of a tooth 20b" of the pinion 2b". The force F21, which passes substantially close to the axis A2", creates a torque which tends to pivot the pinion 2b" in the counterclockwise direction, which causes a bearing force F31 of a tooth 20a" on a rest surface 30c" of the blocking means 3c" of the blocker 3". The rest surface 30c" is arranged so that the direction of the force F31 passes substantially through the axis A3". These forces are the same during the disengagement phase which will follow, apart from the friction angles.

[0080] At rest, neglecting friction: F 31 = F 21 × DO 21 / DO 31 with : F21: the value of the intensity of the support force against the surface 200b"; F31: the value of the intensity of the support force against the surface 30c"; DO21: the value of the lever arm of the force F21 with respect to the axis A2"; DO31: the value of the lever arm of the force F31 with respect to the axis A2".

[0081] Since DO21< <DO31, on constate que l'intensité de la force F31 est sensiblement plus faible que l'intensité de la force F21.

[0082] The energy supplied by the balance wheel during release to overcome friction and to set the wheels and the blocker in motion is therefore significantly lower than that supplied in a conventional Swiss lever type escapement device.

[0083] This low energy expenditure is explained by the fact that the intensity of force F31 is significantly lower than that of the support force F21.

[0084] It is also noted here that the angle α" formed between the force vector F21 and the half-line originating from the point of contact between the wheel 1a" and the pinion 2b" and passing through the axis A2" (or formed between the force vector F21 and a vector D" radial relative to the axis A2" and originating from the point of contact between the wheel 1a" and the pinion 2b") is significantly less than 50°, or even less than 30°, or even less than 20°.

[0085] This intensity of the force F31 is minimized as much as possible if the inertias of the mobiles 1", 2" and of the blocker 3" are minimized as much as possible. Preferably, the total diameter D2b" of the pinion 2b" is reduced as much as possible so as to reduce as much as possible the inertia of the pinion 2b", as well as the dimensions of the blocker 3". Thus, preferably, the total diameter D2b" of the pinion 2b" is substantially less than the total diameter D1a" of the first wheel 1a", in particular less than 60% of the total diameter D1a" of the first escape wheel 1a", or even less than 50% of the total diameter D1a" of the first escape wheel 1a".

[0086] The tooth profile of the elements 1a" and 2b" can also be shaped so that the torque transmitted by the first wheel 1a" to the second pinion 2b" during the impulse phase is significantly greater than that transmitted during disengagement.

[0087] When engaging in the release phase which follows the rest phase illustrated in figure 12 , the torque C2d' at the pinion 2b" can be expressed in the following way with respect to the torque C1d' at the wheel 1a", and neglecting friction: C 2 d ′ = C 1 d ′ × DO 21 / DO 11 with : DO11: the value of the lever arm of force F21 relative to axis A1"; DO21: the value of the lever arm of force F21 relative to axis A2".

[0088] When engaging the impulse phase (not shown), an impulse surface 201b" of the second pinion 2b" is oriented so that the force F21' transmitted by the first escape wheel to the second escape wheel is substantially tangential to the trajectory of the point of contact between the wheel 1a" and the pinion 2b". In other words, when engaging the impulse phase, the force F21' is substantially normal to the half-line originating from the axis A1" and passing through the axis A2".

[0089] When engaging this impulse phase, the torque C2i' at the pinion 2b" can be expressed in the following manner with respect to the torque C1i' at the wheel 1a", and neglecting friction: C 2 i ′ = C 1 i ′ × DO 21 ′ / DO 11 ′ with : DO11': the value of the lever arm of force F21' relative to axis A1"; DO21': the value of the lever arm of force F21' relative to axis A2".

[0090] Given that: DO 21 / DO 11 ≪ DO 21 ′ / DO 11 ′ et que C 1 i ′ = C 1 d ′

[0091] The torque C2i' transmitted to the pinion 2b" during the impulse phase is substantially greater than the torque C2d' transmitted to the pinion 2b" during the release phase. Thus, the energy to be supplied by the balance during the release phase is minimized, and the energy transmitted by the driving member during the impulse phase to the escapement device is maximized. Such an escapement device thus has the advantage of having a maximized efficiency compared to the escapement devices known from the prior art, of the order of 120 to 160% compared to average reference efficiencies of the order of 30 to 40%. Such a device also has the advantage of minimizing disturbances to the oscillator, and thus makes it possible to implement an oscillator with optimized isochronism compared to the oscillators cooperating with escapement devices known from the prior art.

[0092] In the second variant of the second embodiment, the geometries of the exhaust elements may be as described below.

[0093] The first escapement wheel 1" comprises teeth 10a", in particular 20 teeth. The teeth are oriented downstream (relative to their movement) in a direction making for example an angle between 20° and 45° with the radial direction to the axis A1" of the first wheel. The free end of each tooth can be in the shape of a bevel.

[0094] The second escape pinion 2b" comprises teeth 20b", in particular 10 teeth. The teeth extend substantially along an angular sector of approximately 10°. Each tooth comprises a rest surface 200b" oriented to form an angle β" of between 15° and 50°, or even between 20° and 45°, with the orthoradial direction O2" relative to the axis A2" of the second wheel set. The angle β" is an acute angle measured between the tangent to the rest surface and an orthoradial vector O2" relative to the axis A2" and originating from the point of contact between the wheel 1a and the pinion 2b. This orientation makes it possible to create a slight torque tending to rotate the second wheel set against the blocker in the rest and release phases. Each tooth is also limited by two lateral surfaces oriented substantially radially relative to the axis A2". One of these two lateral surfaces is a 201b" impulse surface.

[0095] The angles α" and β" are therefore equal to the friction angle. (friction angle at the point of contact between wheel 1a" and pinion 2b")

[0096] The second escape wheel 2a" comprises teeth 20a", in particular 5 teeth. The teeth are arm-shaped. Each tooth comprises a rest surface 200a" oriented at least substantially radially relative to the axis A3" of the blocker when this tooth of the second wheel is in contact with the blocker. Each tooth is also limited by an impulse surface 201a" oriented at least substantially orthoradially relative to the axis A3" of the blocker when this tooth of the second wheel is in contact with the blocker.

[0097] The blocker 3 comprises the rest surfaces 30b", 30c" oriented at least substantially orthoradially relative to the axis A3" of the blocker and the impulse surfaces 31b", 31c" oriented at least substantially radially relative to the axis A3" of the blocker.

[0098] In the rest and release phases, one end of a tooth 10a" bears against a rest surface 200b" of a tooth 20b" of the second pinion and a rest surface 200a" of a tooth 20a" of the second wheel bears against a rest surface 30b", 30c" of the blocker.

[0099] Advantageously, in the rest phase and in the release phase (as long as the second escape wheel is resting against the blocker), a half-line having as its origin the axis A2" of the second escape wheel and passing through the first point of contact where the first force F21 of the first escape wheel is applied to the second escape wheel and a half-line having as its origin the axis A2" of the second escape wheel and passing through the axis A"1 of the second escape wheel form an angle greater than 10°, or even greater than 20°, or even greater than 30°.

[0100] Advantageously, and in a complementary or alternative manner, in the rest phase and in the release phase (as long as the second escape wheel is resting against the blocker), a half-line having as its origin the axis A1" of the first escape wheel and passing through the axis A2" of the second escape wheel; and a half-line having as its origin the axis A1" of the first escape wheel and passing through the first point of contact where the first force F21 of the first escape wheel is applied to the second escape wheel form an angle greater than 5°, or even greater than 10°, or even greater than 20°.

[0101] In the impulse phase, one end of a tooth 10a" bears against an impulse surface 201b" of a tooth 20b" of the second pinion and an impulse surface 201a" of a tooth 20a" of the second wheel bears against an impulse surface 31b" of the blocker.

[0102] In a third variant of the second embodiment shown in the figures 14 And 15 , the escapement device has an operating principle similar to that of the device disclosed in patent application WO2013182243A1. This is, for example, designed to cooperate with a balance-spring type oscillator.

[0103] This is an indirect impulse escapement device. Thus, the impulse to the sprung balance is achieved by means of a blocker 3*, a fork 30a* of which is designed to cooperate exclusively with a balance 4, in particular a balance wheel plate 40*, in particular a balance wheel pin 40a*. Such an escapement device differs from the previous embodiment variants in that the blocker 3* is made of two separate parts 30*, 31* kinematically linked to each other. The first part 30* is pivoted around an axis A30*. The first part 30* comprises the fork 30a*, locking means 30b* provided to act by contact with a toothing 20a* of the second wheel 2a*, as well as a toothing 30c* which is provided to mesh with a toothing 31c* of the second part 31*. The second part 31* is pivoted around an axis A31*.The second part 31* also includes locking means 31b* designed to act by contact with the teeth 20a* of the second wheel 2a*.

[0104] There figure 14 illustrates a rest position of such an escapement device which precedes a release phase.

[0105] A tooth 10a* of the wheel 1a*, under the effect of the torque of the driving member, exerts a force F22 on a rest surface 200b* of a tooth 20b* of the pinion 2b*. The force F22 passes substantially close to the axis A2*. The force F22 creates a torque which tends to pivot the pinion 2b* in the counterclockwise direction, which causes a bearing force F32 of a tooth 20a* on a rest surface 300b* of the locking means 30b* of the part 30* of the blocker 3*. The rest surface 300b* is arranged so that the direction of the force F32 passes substantially through the axis A30*. These forces are the same during the disengagement phase which will follow, apart from the friction angles.

[0106] At rest, neglecting friction: F 32 = F 22 × DO 22 / DO 32 with : F22: the value of the intensity of the support force against the surface 200b*; F32: the value of the intensity of the support force against the surface 300b*; DO22: the value of the lever arm of the force F22 with respect to the axis A2*; DO32: the value of the lever arm of the force F32 with respect to the axis A2*.

[0107] Since DO22< <DO32, on constate ainsi que l'intensité de la force F32 est sensiblement plus faible que l'intensité de la force F22.

[0108] The energy supplied by the balance wheel during release to overcome friction and to set the wheels and the blocker in motion is significantly lower than that supplied in a conventional Swiss lever type escapement device.

[0109] This low energy expenditure is explained by the fact that the intensity of the F32 force is significantly lower than that of the F22 support force.

[0110] It is also noted here that the angle α* formed between the force vector F22 and the half-line originating from the point of contact between the wheel 1a* and the pinion 2b* and passing through the axis A2* (or formed between the force vector F20 and a radial vector D* relative to the axis A2* and originating from the point of contact between the wheel 1a* and the pinion 2b*) is significantly less than 50°, in particular less than 30°, or even less than 20°.

[0111] This intensity of the force F32 is minimized as much as possible if the inertias of the mobiles 1*, 2* and of the blocker 3* are minimized as much as possible. Preferably, the total diameter D2b* of the pinion 2b* is reduced as much as possible so as to reduce as much as possible the inertia of the pinion 2b*, as well as the dimensions of the blocker 3*. Thus, preferably, the total diameter D2b* of the pinion 2b* is substantially less than the total diameter D1a* of the first wheel 1a*, in particular less than 30% of the total diameter D1a* of the first escape wheel 1a*, or even less than 20% of the total diameter D1a* of the first escape wheel 1a*.

[0112] The tooth profile of the elements 1a* and 2b* can also be shaped so that the torque transmitted by the first wheel 1a* to the second pinion 2b* during the impulse phase is significantly greater than that transmitted during the disengagement phase.

[0113] When engaging in the release phase which follows the rest phase illustrated on figure 14 , the torque C2d" at the pinion 2b* can be expressed in the following way with respect to the torque C1d" at the wheel 1a*, and neglecting friction: C 2 d " = C 1 d " × DO 22 / DO 12 with : DO12: the value of the lever arm of force F22 relative to axis A1*; DO22: the value of the lever arm of force F22 relative to axis A2*.

[0114] When engaging the impulse phase shown on the figure 15 , an impulse surface 201b* of the second pinion 2b* is oriented so that the transmitted force F22' is substantially tangential to the trajectory of the point of contact between the wheel 1a* and the pinion 2b*. In other words, when the impulse phase is engaged, the force F22' is substantially normal to the half-line originating from the axis A1* and passing through the axis A2*.

[0115] When engaging this impulse phase, the torque C2i" at the pinion 2b* can be expressed in the following manner with respect to the torque C1i" at the wheel 1a*, and neglecting friction: C 2 i " = C 1 i " × DO 22 ′ / DO 21 ′ with : DO21': the value of the lever arm of force F22' relative to axis A1*; DO22': the value of the lever arm of force F22' relative to axis A2*.

[0116] Given that: DO 22 / DO 12 ≪ DO 22 ′ / DO 21 ′ et que C 1 i " = C 1 d "

[0117] The torque C2i" transmitted to the pinion 2b* during the impulse phase is substantially greater than the torque C2d" transmitted to the pinion 2b* during the release phase. Thus, the energy to be supplied by the balance during the release phase is minimized, and the energy transmitted by the driving member during the impulse phase to the escapement device is maximized. Such an escapement device thus has the advantage of exhibiting maximized efficiency compared to the escapement devices known from the prior art, such as that disclosed in document WO2013182243A1. Such a device also has the advantage of minimizing disturbances to the oscillator, and thus makes it possible to implement an oscillator with optimized isochronism compared to the oscillators cooperating with escapement devices known from the prior art.

[0118] In the third variant of the second embodiment, the geometries of the exhaust elements may be as described below.

[0119] The first escapement wheel 1* includes 10a* teeth, including 40 teeth. The teeth have, for example, involute profiles or have substantially involute profiles.

[0120] The second escape pinion 2b* comprises teeth 20b*, in particular 6 teeth. The teeth extend substantially along an angular sector of approximately 30°. Each tooth comprises a rest surface 200b* oriented to form an angle β* of between 10° and 50°, or even between 20° and 35°, with the orthoradial direction O2* relative to the axis A2* of the second wheel set. The angle β* is an acute angle measured between the tangent to the rest surface and an orthoradial vector O2* relative to the axis A2 and originating at the point of contact between the wheel 1a and the pinion 2b*. This orientation makes it possible to create a slight torque tending to rotate the second wheel set against the blocker in the rest and release phases. Each tooth is also limited by two lateral surfaces oriented substantially radially relative to the axis A2*. One of these two lateral surfaces is a 201b* impulse surface.

[0121] The angles α* and β* are therefore equal to the friction angle. (friction angle at the point of contact between wheel 1a* and pinion 2b*)

[0122] The blocker 3* comprises rest surfaces 300b*, 310b* oriented at least substantially orthoradially relative to the axis A3* of the blocker and impulse surfaces 301b*, 311b* oriented at least substantially radially relative to the axis A3* of the blocker.

[0123] In the rest and release phases, a flank of a tooth 10a* bears against a rest surface 200b* of a tooth 20b* of the second pinion and an end 200a* of a tooth 20a* of the second wheel bears against a rest surface 310b*, 300b* of the blocker.

[0124] Advantageously, in the rest phase and in the release phase (as long as the second escape wheel is resting against the blocker), a half-line having as its origin the axis A2* of the second escape wheel and passing through the first point of contact where the first force F22 of the first escape wheel is applied to the second escape wheel and a half-line having as its origin the axis A2* of the second escape wheel and passing through the axis A1* of the second escape wheel form an angle greater than 10°, or even greater than 20°, or even greater than 30°.

[0125] Advantageously, and in a complementary or alternative manner, in the rest phase and in the release phase (as long as the second escape wheel is resting against the blocker), a half-line having as its origin the axis A1* of the first escape wheel and passing through the axis A2* of the second escape wheel; and a half-line having as its origin the axis A1* of the first escape wheel and passing through the first point of contact where the first force F22 of the first escape wheel is applied to the second escape wheel form an angle greater than 5°, or even greater than 10°, or even greater than 20°.

[0126] In the impulse phase, the flank of a tooth 10a* bears against an impulse surface 201b* of a tooth 20b* of the second pinion and an end 200a* of a tooth 20a* of the second wheel bears against an impulse surface 301b*, 311b* of the blocker.

[0127] In the various embodiments and variants, the first and second escapement mobiles and the blocker are preferably made of a low-density material, for example silicon or a silicon alloy. In the case of components of the escapement device made of silicon, the latter are preferably coated with a layer of SiO2 or Si4N3 in particular to reinforce their mechanical strength and to optimize the tribology of the device. Such a device may, for example, not require lubrication.

[0128] Preferably, whatever the embodiment or variant, the rest surfaces of the blocking means of the blocker are of concave shapes in order to guarantee the positioning precision of the teeth of the second mobile 2, 2', 2", 2* on these surfaces. These concave surfaces are formed for example of two inclined planes making for example an angle preferably between 120° and 170°.

[0129] Preferably, whatever the embodiment or variant, the blocker may comprise mechanical transmission means capable of rotating the second escape wheel in the opposite direction to that of the first escape wheel. These means may consist of protrusions or teeth acting by contact on the second escape wheel, in particular on impulse surfaces or on rest surfaces of the second escape wheel.

[0130] Preferably, whatever the embodiment or variant, the blocker may comprise a dart provided to cooperate with a complementary balance plate, in order to prevent untimely movements of the blocker in the event of an impact.

[0131] In the various embodiments and variants, the escapement device is designed to maintain the oscillations of the clockwork oscillator in an optimized manner. As seen previously, the device makes it possible to minimize the energy to be supplied by the oscillator during the release phase, that is to say when the oscillator actuates the blocker while an escape wheel is blocked in rotation by the blocker.

[0132] In the various embodiments and variants, the escapement device has the advantage of having maximized efficiency compared to the escapement devices known from the prior art. Such a device also has the advantage of minimizing the disturbances of the oscillator, and thus makes it possible to implement an oscillator with optimized isochronism compared to the oscillators cooperating with escapement devices known from the prior art. To do this, in the various embodiments and variants, the escapement device is such that it transmits from the first escape wheel set to the second escape wheel set a variable torque depending on whether it is in a disengagement phase or in an impulse phase. The torque transmitted from the first escape wheel set to the second escape wheel set in the disengagement phase is less than that transmitted from the first escape wheel set to the second escape wheel set in the impulse phase.The torque transmitted from the first escapement wheel to the second escapement wheel in the impulse phase may be constant or substantially constant. Similarly, the torque transmitted from the first escapement wheel to the second escapement wheel in the disengagement phase may be constant or substantially constant. The torque transmitted from the first escapement wheel to the second escapement wheel in the disengagement phase may be equal or substantially equal to the torque transmitted from the first escapement wheel to the second escapement wheel in the rest phase.

[0133] In the various embodiments and variants, the first escapement wheel and the second escapement wheel may form a mechanical transmission device for a timepiece intended to transmit a torque, in particular intended to transmit a variable torque and / or coming from a barrel. Alternatively, the first escapement wheel and the second escapement wheel may be part of a mechanical transmission device for a timepiece intended to transmit a torque, in particular intended to transmit a variable torque and / or coming from a barrel.

[0134] On the contrary, according to the prior art, high torques, necessary to maintain the oscillations of the oscillator during the different impulse phases of the escapement devices, are also transmitted by the escape wheel even when such torque levels are not required, in particular during the different release phases of the escapement device. The energy lost by friction is proportional to the bearing force of the escape wheel teeth on the blocker and the bearing force is itself proportional to the torque transmitted by the escape wheel. This results in particularly low efficiencies. Furthermore, in a timepiece, the driving member, for example a barrel, distributes to the escape wheel, by means of a finishing train, a substantially constant torque to the escape wheel.The torque transmitted to the escape wheel is therefore constantly high, which implies that the energy to be supplied by the oscillator to allow the release of the blocker is constantly high.

[0135] In the various embodiments and variants, the escapement device is preferably such that in the release phase, the blocker acts directly against the second escapement wheel which is kinematically linked to the first escapement wheel.

[0136] In the various embodiments and variants, the escapement device comprises the blocker, the first escapement mobile and the second escapement mobile which are arranged and shaped so as to: minimizing the torque transmitted to the second escapement wheel during the release phases of the escapement device; and / or maximizing the torque transmitted to the second escapement wheel or to the oscillator during the escapement impulse phases; and / or transmitting from the first escapement wheel a different torque in the release phase and in the impulse phase.

[0137] In the various embodiments and variants, the escapement device 400; 400'; 400"; 400* preferably comprises a first escapement wheel 1; 1'; 1"; 1*, a second escapement wheel 2; 2'; 2"; 2* and a blocker 3; 3'; 3"; 3*. The second escapement wheel is preferably interposed between the first escapement wheel and the blocker, in particular the second escapement wheel can cooperate by contact with the first escapement wheel on the one hand and with the blocker on the other hand.

[0138] In the various embodiments and variants, the first escapement wheel, the second escapement wheel and the blocker are preferably shaped and arranged so that in the release phase of the escapement device, a force from the blocker controlled by the oscillator 4, 5 is transmitted to the first escapement wheel via the second escapement wheel.

[0139] In the various embodiments and variants, the first escapement wheel, the second escapement wheel and the blocker are preferably shaped and arranged so that in the release phase of the escapement device, a first force from the first escapement wheel is applied to the second escapement wheel and a second force from the blocker is applied to the second escapement wheel, the intensity of the second force being less than the intensity of the first force, in particular the intensity of the second force being less than 0.5 times, or even less than 0.3 times, or even less than 0.2 times, the intensity of the first force.

[0140] In the various embodiments and variants, the first escapement wheel, the second escapement wheel and the blocker are preferably shaped and arranged so that in the impulse phase of the escapement device: a third force of the first escapement wheel applied directly to the second escapement wheel or applied directly to an oscillator 4, 5 is directed substantially orthoradially relative to the axis A1; A1'; A1"; A1* of the first escapement wheel or to the axis A2; A2'; A2"; A2* of the second escapement wheel or to the axis A4; A4'; A4"; A4* of the oscillator; and / or a fourth force of the second escapement wheel applied directly to the blocker or applied directly to an oscillator is directed substantially orthoradially to the axis A2; A2'; A2"; A2* of the second escapement wheel or to the axis A3; A3'; A3"; A3* of the blocker or to the axis A4; A4'; A4"; A4* of the oscillator.

[0141] In the various embodiments and variants, the second escapement wheel 2; 2'; 2"; 2* may be a second pinion 2b or the second escapement wheel 2'; 2"; 2* may comprise a second pinion 2b'; 2b"; 2b* and a second wheel 2a'; 2a"; 2a*.

[0142] In the various embodiments and variants, the second escape wheel 2; 2'; 2"; 2* may comprise a second pinion 2b'; 2b"; 2b*, the second pinion being arranged to cooperate with the first escape wheel, the first escape wheel, in particular a first wheel of the first escape wheel, having a larger diameter, in particular more than 1.5 times larger, or even more than 2 times larger, than the diameter of a second pinion of the second escape wheel 2; 2'; 2"; 2*.

[0143] In the various embodiments and variants, the second escape wheel 2; 2'; 2"; 2* may comprise impulse surfaces 201b'; 201b"; 201b* oriented at least substantially radially relative to the axis A2; A2'; A2"; A2* of the second escape wheel and / or rest surfaces 200b; 200b'; 200b"; 200b* oriented to form an angle β; β'; β"; β* of between 15° and 50°, or even between 20° and 45°, between the tangent to the rest surface and an orthoradial vector O2; O2'; O2"; O2* relative to the axis A2; A2'; A2"; A2* of the second escapement wheel at the rest surface and / or the blocker may comprise impulse surfaces 31b"; 301b*, 311b* oriented at least substantially radially relative to the axis of the blocker A3; A3'; A3"; A3* and / or rest surfaces 30b, 30c; 30b', 30c'; 30b", 30c"; 30b*, 30c* oriented at least substantially orthoradially relative to the axis of the blocker A3; A3'; A3"; A3*.

[0144] In the various variants of the second embodiment, the second wheel may comprise impulse surfaces 201a" oriented at least substantially orthoradially relative to the axis A2; A2'; A2"; A2* of the second wheel and / or rest surfaces 200a" oriented at least substantially radially to the axis of the second wheel A2; A2'; A2"; A2* and / or the second pinion may comprise impulse surfaces 201b'; 201b"; 201b* oriented at least substantially radially relative to the axis of the second wheel A2; A2'; A2"; A2* and / or rest surfaces 200b; 200b'; 200b"; 200b* oriented at an angle β; β'; β"; β* between 15° and 50°, or even between 20° and 45°, between the tangent to the rest surface and an orthoradial vector O2; O2'; O2"; O2* relative to the axis of the second mobile A2; A2'; A2"; A2* at the level of the rest surface.

[0145] In the various embodiments and variants, the first escapement wheel, the second escapement wheel and the blocker may be shaped and arranged so that in the release phase of the escapement device, a first force F2; F20; F21; F22 of the first escapement wheel on the second escapement wheel at a first point of contact forms an angle α; α'; α"; α* less than 50°, or even less than 30°, or even less than 20°, with a radial vector D; D'; D"; D* relative to the axis of the second escapement wheel A2; A2'; A2"; A2* at the first point of contact and / or the first escapement wheel, the second escapement wheel and the blocker may be shaped and arranged so that in the release phase: a half-line having as its origin the axis A2; A2'; A2"; A2* of the second escapement wheel and passing through a first point of contact where a first force F2; F20; F21; F22 of the first escapement wheel is applied to the second escapement wheel; and a half-line having as its origin the axis A2; A2'; A2"; A2* of the second escapement wheel and passing through the axis A1; A1'; A1"; A1* of the second escapement wheel; form an angle greater than 10°, or even greater than 20°, or even greater than 30°; and / or a half-line having as its origin the axis A1; A1'; A1"; A1* of the first escapement wheel and passing through the axis A2; A2'; A2"; A2* of the second escapement wheel; and a half-line having as its origin the axis A1; A1'; A1"; A1* of the first escapement wheel and passing through a first point of contact where a first force F2; F20; F21; F22 of the first escapement wheel on the second escapement wheel is applied; form an angle greater than 5°, or even greater than 10°, or even greater than 20°.

[0146] According to the different embodiments, the watch movement 500; 500'; 500"; 500* may comprise an escapement device as described previously, in particular may comprise the finishing gear 1b'; 1b"; 1b*, the oscillator 4, 5 and an escapement device as described previously. The escapement device is interposed between the finishing gear and the oscillator.

[0147] According to the different embodiments, the timepiece 600; 600'; 600"; 600* may comprise an escapement device as described previously or a watch movement as described previously or a watch transmission device as described previously.

[0148] A method of carrying out a method of operating an exhaust device, in particular an exhaust device as described previously, is detailed below.

[0149] The method may include a release phase, in which the following are simultaneously applied to the second escapement wheel: ▪ a first force F2; F20; F21; F22 from the first escapement wheel, and ▪ a second force F3; F30; F31; F32 from the blocker.

[0150] The intensity of the second effort may be lower than the intensity of the first effort, in particular the intensity of the second effort may be less than 0.5 times, or even less than 0.3 times, or even less than 0.2 times, the intensity of the first effort.

[0151] The method may comprise an impulse phase in which the first escapement wheel applies, directly to the oscillator or directly to the second escapement wheel, a third force directed substantially orthoradially relative to the axis of the first escapement wheel or to the axis of the second escapement wheel or to the axis of the oscillator.

[0152] The method may comprise an impulse phase in which the second escapement wheel applies, directly to the oscillator or directly to the blocker, a fourth force directed substantially orthoradially relative to the axis of the second escapement wheel or to the axis of the blocker or to the axis of the oscillator.

[0153] The method may comprise an impulse phase in which the intensity of the torque transmitted from the first escapement wheel to the second escapement wheel or to an oscillator during the impulse phase is greater than 1.5 times, or even greater than 2 times, the intensity of the torque transmitted from the first escapement wheel to the second escapement wheel during a release phase.

[0154] By "mobile" we mean, throughout this document, a wheel or pinion or an assembly of wheel(s) and / or pinion(s).

[0155] By "wheel" we mean, throughout this document, any rotating toothed organ whose function is to transmit torque, force, or movement.

[0156] By "pinion", we mean, throughout this document, any rotating toothed organ whose function is to transmit a torque, a force, or a movement, whose diameter and / or the number of teeth is significantly smaller than those of the wheel with which it meshes or with which it is integral in rotation.

[0157] Throughout this document, unless otherwise indicated, the angles mentioned are oriented angles. By convention, the positive direction of orientation of these angles is the direction of rotation of the second escapement wheel when the escapement device is in operation. In all figures representing particular embodiments, this positive direction of orientation of the angles is the trigonometric or counterclockwise direction.

[0158] By "radial direction relative to an axis" we mean, throughout this document, any direction perpendicular to this axis and passing through this axis. The radial vector is in this radial direction and oriented towards this axis.

[0159] By "orthoradial direction relative to an axis" we mean, throughout this document, any direction perpendicular to this axis and perpendicular to the radial direction relative to this axis. The orthoradial direction relative to an axis at a given point is also the tangential direction relative to this axis at the given point. The orthoradial vector is perpendicular to this radial direction and oriented so that the angle between the orthoradial vector and the radial vector is an oriented angle of +90°.

[0160] By "direction substantially orthoradial relative to an axis", we preferably mean, throughout this document, any direction orthoradial to this axis or any direction forming an angle of less than 30°, or even less than 20°, with a direction exactly orthoradial relative to this axis.

[0161] By "direction substantially radial relative to an axis", we preferably mean, throughout this document, any direction radial to this axis or any direction forming an angle of less than 30°, or even less than 20°, with a direction exactly radial relative to this axis.

[0162] Throughout this document, the orientation of a surface is preferably defined by the direction tangent to this surface in the plane perpendicular to the pivot axes of the escapement wheels and / or the blocker.

[0163] By "impulse surface of the second escapement wheel", we preferably mean, throughout this document, any surface of the second escapement wheel likely to be in contact with the first escapement wheel or with the blocker during an impulse phase of the escapement device.

[0164] By "resting surface of the second escapement wheel", we preferably mean, throughout this document, any surface of the second escapement wheel likely to be in contact with the first escapement wheel or with the blocker during a resting phase or a release phase of the escapement device.

[0165] By "impulse surface of the blocker", we preferably mean, throughout this document, any surface of the blocker likely to be in contact with the second escape wheel during an impulse phase of the escapement device.

[0166] By "resting surface of the blocker", we preferably mean, throughout this document, any surface of the blocker likely to be in contact with the second escapement wheel during a resting phase or a release phase of the escapement device.

[0167] By "escapement wheel", we preferably mean, throughout this document, any wheel for transmitting a force from the gear train to the blocker, the wheel being shaped and / or arranged so that the direction of the force that it transmits varies, in particular varies significantly, during an escapement cycle.

Claims

1. A method of functioning of an escapement device (400; 400'; 400"; 400*) situated between a mobile (1b; 1b'; 1b"; 1b*) of a geartrain and an oscillator (4, 5), the escapement device comprising a first escapement mobile (1; 1'; 1"; 1*) pivoted about a first axis (A1; A1'; A1"; A1*), a second escapement mobile (2; 2'; 2"; 2*) pivoted about a second axis (A2; A2'; A2"; A2*), and a blocking-lever (3; 3'; 3"; 3*), - the method involving a disengagement phase, in which there are simultaneously applied to the second escapement mobile: ▪ a first force (F2; F20; F21; F22) of the first escapement mobile, and ▪ a second force (F3; F30; F31; F32) of the blocking-lever, wherein the intensity of the second force is less than the intensity of the first force, in particular, the intensity of the second force being less than 0.5 times, or less than 0.3 times, or less than 0.2 times the intensity of the first force.

2. The method of functioning as claimed in claim 1, characterized in that it further involves an impulse phase in which the first escapement mobile applies, directly to the oscillator or directly to the second escapement mobile, a third force directed substantially orthoradially with respect to the axis of the first escapement mobile or to the axis of the second escapement mobile or to the axis of the oscillator.

3. The method of functioning as claimed in claim 1 or 2, characterized in that it involves an impulse phase in which the second escapement mobile applies, directly to the oscillator or directly to the blocking-lever, a fourth force directed substantially orthoradially with respect to the axis of the second escapement mobile or to the axis of the blocking-lever or to the axis of the oscillator.

4. The method of functioning as claimed in one of the preceding claims, characterized in that it further involves an impulse phase in which the intensity of the torque transmitted from the first escapement mobile to the second escapement mobile or to an oscillator during the impulse phase is greater than 1.5 times, or greater than 2 times, the intensity of the torque transmitted from the first escapement mobile to the second escapement mobile during a disengagement phase.

5. An escapement device (400; 400'; 400"; 400*) comprising: - a first escapement mobile (1; 1'; 1"; 1*), - a second escapement mobile (2; 2'; 2"; 2*), and - a blocking-lever (3; 3'; 3"; 3*), the second escapement mobile being situated between the first escapement mobile and the blocking-lever, wherein the second escapement mobile cooperates by contact with the first escapement mobile on the one hand and with the blocking-lever on the other hand, so that the blocking-lever is not directly in contact with the first escapement mobile, or wherein the first escapement mobile, the second escapement mobile and the blocking-lever are configured and arranged such that, in the disengagement phase of the escapement device, a force of the blocking-lever controlled by the oscillator (4, 5) is transmitted to the first escapement mobile via the second escapement mobile.

6. The escapement device as claimed in claim 5, characterized in that the first escapement mobile, the second escapement mobile and the blocking-lever are configured and arranged such that in the disengagement phase of the escapement device a first force of the first escapement mobile is applied to the second escapement mobile and a second force of the blocking-lever is applied to the second escapement mobile, the intensity of the second force being less than the intensity of the first force, in particular, the intensity of the second force being less than 0.5 times, or less than 0.3 times, or less than 0.2 times the intensity of the first force.

7. The escapement device as claimed in one of claims 5 to 6, characterized in that the first escapement mobile, the second escapement mobile and the blocking-lever are configured and arranged such that in the impulse phase of the escapement device: - a third force of the first escapement mobile applied directly to the second escapement mobile or applied directly to an oscillator (4, 5) is directed substantially orthoradially with respect to the axis (A1; A1'; A1"; A1*) of the first escapement mobile or to the axis (2a'; 2a"; 2a*) of the second escapement mobile or to the axis (A4; A4'; A4"; A4*) of the oscillator; and / or - a fourth force of the second escapement mobile applied directly to the blocking-lever is directed substantially orthoradially to the axis (A2; A2'; A2"; A2*) of the second escapement mobile or to the axis (A3; A3'; A3"; A3*) of the blocking-lever or to the axis (A4; A4'; A4"; A4*) of the oscillator.

8. The escapement device as claimed in one of claims 5 to 6, characterized in that the first escapement mobile, the second escapement mobile and the blocking-lever are configured and arranged such that in the impulse phase of the escapement device: - a third force of the first escapement mobile applied directly to the second escapement mobile is directed substantially orthoradially with respect to the axis (A1; A1'; A1"; A1*) of the first escapement mobile or to the axis (2a'; 2a"; 2a*) of the second escapement mobile or to the axis (A4; A4'; A4"; A4*) of the oscillator; or - a fourth force of the second escapement mobile applied directly to the oscillator is directed substantially orthoradially to the axis (A2; A2'; A2"; A2*) of the second escapement mobile or to the axis (A3; A3'; A3"; A3*) of the blocking-lever or to the axis (A4; A4'; A4"; A4*) of the oscillator.

9. The escapement device as claimed in one of claims 5 to 8, characterized in that the second escapement mobile (2; 2'; 2"; 2*) is the second pinion (2b) or in that the second escapement mobile (2'; 2"; 2*) comprises the second pinion (2b'; 2b"; 2b*) and the second wheel (2a'; 2a"; 2a*).

10. The escapement device as claimed in one of claims 5 to 8, characterized in that the second escapement mobile (2; 2'; 2"; 2*) comprises a second pinion (2b'; 2b"; 2b*), the second pinion being arranged to cooperate with the first escapement mobile, the first escapement mobile, particularly a first wheel of the first escapement mobile, having a diameter greater than, particularly more than 1.5 times greater than, or more than 2 times greater than the diameter of the second pinion of the second escapement mobile (2; 2'; 2"; 2*).

11. The escapement device as claimed in one of claims 5 to 10, characterized in that the second escapement mobile (2; 2'; 2"; 2*) comprises impulse surfaces (201b'; 201b"; 201b*) oriented at least substantially radially with respect to the axis (A2; A2'; A2"; A2*) of the second escapement mobile and / or resting surfaces (200b; 200b'; 200b"; 200b*) oriented to form an angle (β; β'; β"; β*) between 15° and 50°, or between 20° and 45°, between the tangent to the surface and an orthoradial vector (O2; O2'; O2"; O2*) with respect to the axis (A2; A2'; A2"; A2*) of the second escapement mobile in the area of the resting surface.

12. The escapement device as claimed in one of claims 5 to 11, characterized in that in that the blocking-lever comprises impulse surfaces (31b"; 301b*, 311b*) oriented at least substantially radially with respect to the axis of the blocking-lever (A3; A3'; A3"; A3*) and / or resting surfaces (30b, 30c; 30b', 30c'; 30b", 30c"; 30b*, 30c*) oriented at least substantially orthoradially with respect to the axis of the blocking-lever (A3; A3'; A3"; A3*).

13. The escapement device as claimed in one of claims 5 to 12, characterized in that the second wheel comprises impulse surfaces (201a") oriented at least substantially orthoradially with respect to the axis of the second escapement mobile (A2; A2'; A2"; A2*) and / or resting surfaces (200a") oriented at least substantially radially with respect to the axis of the second escapement mobile (A2; A2'; A2"; A2*).

14. The escapement device as claimed in one of claims 5 to 13, characterized in that the second pinion comprises impulse surfaces (201b'; 201b"; 201b*) oriented at least substantially radially with respect to the axis of the second escapement mobile (A2; A2'; A2"; A2*) and / or resting surfaces (200b; 200b'; 200b"; 200b*) oriented to form an angle (β; β'; β"; β*) between 15° and 50°, or between 20° and 45°, between the tangent to the surface and an orthoradial vector (O2; O2'; O2"; O2*) with respect to the axis of the second escapement mobile (A2; A2'; A2"; A2*) in the area of the resting surface.

15. The escapement device as claimed in one of claims 5 to 14, characterized in that the first escapement mobile, the second escapement mobile and the blocking-lever are configured and arranged such that in the disengagement phase of the escapement device a first force (F2; F20; F21; F22) of the first escapement mobile on the second escapement mobile at a first point of contact makes an angle (α; α'; α"; α*) less than 50°, or less than 30°, or less than 20° with a radial vector (D; D'; D"; D*) with respect to the axis of the second escapement mobile (A2; A2'; A2"; A2*) at the first point of contact and / or in that the first escapement mobile, the second escapement mobile and the blocking-lever are configured and arranged such that in the disengagement phase: - a ray having as its origin the axis (A2; A2'; A2"; A2*) of the second escapement mobile and passing through a first point of contact where a first force (F2; F20; F21; F22) of the first escapement mobile is applied to the second escapement mobile; and - a ray having as its origin the axis (A2; A2'; A2"; A2*) of the second escapement mobile and passing through the axis (A1; A1'; A1"; A1*) of the second escapement mobile; make an angle greater than 10°, or greater than 20°, or greater than 30°; and / or - a ray having as its origin the axis (A1; A1'; A1"; A1*) of the first escapement mobile and passing through the axis (A2; A2'; A2"; A2*) of the second escapement mobile; and - a ray having as its origin the axis (A1; A1'; A1"; A1*) of the first escapement mobile and passing through a first point of contact where a first force (F2; F20; F21; F22) of the first escapement mobile is applied to the second escapement mobile; make an angle greater than 5°, or greater than 10°, or greater than 20°.

16. A watch movement (500; 500'; 500"; 500*) comprising an escapement device as claimed in one of claims 5 to 15, in particular comprising a geartrain (1b'; 1b"; 1b*), an oscillator (4, 5) and an escapement device as claimed in one of claims 5 to 15, the escapement device being situated between the geartrain and the oscillator.

17. A timepiece (600; 600'; 600"; 600*) comprising an escapement device as claimed in one of claims 5 to 15 or a watch movement as claimed in the preceding claim.