Classifications

• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B15/00—Escapements
  • G04B15/06—Free escapements
  • G04B15/08—Lever escapements
• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B15/00—Escapements
  • G04B15/06—Free escapements
• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B15/00—Escapements
  • G04B15/10—Escapements with constant impulses for the regulating mechanism
• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B15/00—Escapements
  • G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape wheel
• • G—PHYSICS
  • G04—HOROLOGY
  • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
  • G04B19/00—Indicating the time by visual means
  • G04B19/02—Back-gearing arrangements between gear train and hands

Definitions

• Watch exhaust device and method of operation of such a device Watch exhaust device and method of operation of such a device.
• the invention relates to a method of operating a watch exhaust device.
• the invention further relates to a watch exhaust 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.
• exhaust devices such as the Swiss lever escapement or the Robin escapement, described for example in EP1 1 2261 7B1, conventionally comprise an escapement mobile, as well as a blocker.
• the escapement mobile consists of a first exhaust pinion being engaged or taking part in the finishing gear of a watch movement and an escape wheel provided to cooperate by contact with the blocker which is itself intended to cooperate by contact with an oscillator, including a sprung balance, in particular a plateau pin of a sprung balance.
• the plate pin activates the blocker directly, by means of a blocking fork, which itself acts directly against the escape wheel.
• Such exhaust devices have relatively low yields, of the order of 30% to 40%.
• the object of the invention is to provide a watch exhaust device for overcoming the drawbacks mentioned above and to improve the watch exhaust devices known from the prior art.
• the invention provides an exhaust device whose mechanical efficiency is improved.
• An operating method relating to the invention is defined by claim 1. Different embodiments of the operating method are defined by the dependent claims 2 to 4.
• An exhaust device relating to the invention is defined by claim 5.
• a watch movement relating to the invention is defined by claim 14.
• a timepiece relating to the invention is defined by claim 15.
• a transmission device relating to the invention is defined by claim 1 6.
• a timepiece relating to the invention is defined by claim 21.
• 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 exhaust in a first rest position.
• Figure 2 is a view of the first variant of the first embodiment of the exhaust in a second position.
• Figure 3 is a view of the first variant of the first embodiment of the exhaust in a third rest position.
• Figure 4 is a view of the first variant of the first embodiment of the exhaust in a fourth position.
• FIG. 5 is a view of the first variant of the first embodiment of the escapement in a fifth pulse position.
• Figure 6 is a detail view of a first variant of the blocker of the first embodiment of the exhaust.
• Figure 7 is a detail view of a second variant of the blocker of the first embodiment of the exhaust.
• Figure 8 is a detail view of a third variant of the blocker of the first embodiment of the exhaust.
• FIG. 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 position of rest.
• Figure 10 is a view identical to Figure 9 on which the contact forces have been shown.
• Figure 1 1 is a view of the first variant of the second embodiment of the exhaust in a second pulse position.
• Figure 12 is a schematic view of a second variant of the second embodiment of a timepiece according to the invention comprising second variant of the second embodiment of an exhaust in a first rest position.
• Figure 13 is a view of the second variant of the second embodiment of the exhaust in a second pulse position.
• Figure 14 is a schematic view of a third variant of the second mode of a timepiece according to the invention comprising a third variant of the second embodiment of an exhaust in a first rest position.
• Figure 15 is a view of the third variant of the second embodiment of the exhaust in a second pulse position.
• a first embodiment of a timepiece 600 is described hereinafter with reference to FIGS. 1 to 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 disposed between a gear train and an oscillator 4,
• the wheel is intended to connect a drive member, such as a barrel, to the exhaust.
• the wheel and allows a transmission of energy from the motor member to the exhaust.
• the escapement makes it possible to supply energy to the oscillator in order to maintain its oscillations.
• the oscillator is, for example, an oscillator of the balance 4 -spiral type 5.
• the balance is pivoted along an axis A4.
• the exhaust device 400 mainly comprises a first mobile 1 exhaust pivoted along an axis A1, a second mobile 2 exhaust pivoted along an axis A2 and a blocker 3 pivoted along an axis A3.
• the first mobile escapement, the second mobile exhaust and the blocker are shaped and arranged so that, in a phase of release of the exhaust device, a force of the blocker controlled by the oscillator 4, 5 is transmitted to the first mobile exhaust through the second mobile exhaust.
• a release phase comprises in particular a phase of disengagement of the locking means of the toothing of the toothing of the second mobile 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.
• the first escapement mobile 1 comprises a first escape wheel 1a may act, directly or not, on the watch oscillator.
• a first pinion 1b of the work train is integral in rotation with the first escape wheel 1a, in particular is fixed on the first escape wheel 1a, in particular is fixed coaxially on the first escape wheel 1a.
• the second exhaust unit comprises a single second exhaust pinion 2b.
• the exhaust device is a direct-impulse exhaust device whose operating principle is similar to that of a Robin type exhaust device. This may for example be provided to cooperate with a pendulum-type oscillator 4 -spiral 5.
• the first escape wheel 1 is designed to directly actuate the balance 4 -spiral 5 by means of one of its teeth which, during each impulse phase of the exhaust system, acts against a 40 pallet impulse of a plate 40 of the balance 4.
• the balance receives, in the pulse phase, energy directly from the first wheel 1 has exhaust. This avoids friction losses induced by the blockers of the indirect-pulse exhaust devices.
• the first wheel 1 exhaust is kinematically linked to the motor of the watch movement through the first pinion 1b.
• the first wheel 1 has exhaust is likely to be blocked by the blocker 3 through the second mobile 2b exhaust which is interposed between the first mobile 1 and the blocker 3.
• the arrangement of the blocker, the first mobile exhaust and the second mobile exhaust is such that the effort between the second mobile exhaust and the blocker 3 is substantially lower than the force between the first mobile exhaust and the second mobile exhaust during the release phases. More particularly, the arrangement of the blocker, first movable exhaust and second movable exhaust is such that the force between the second pinion 2b exhaust and the blocker 3 is lower than the force between the first wheel 1a exhaust and the second gear 2b d 'exhaust.
• Figure 1 illustrates a first rest position of the exhaust system.
• the balance plate 40 rotates counterclockwise, and the pallet or the release pin 40a of the balance plate 40 moves away from a fork 3a of the blocker 3.
• a tooth 10a of the wheel 1 a under the effect of the torque produced by the motor 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 rotate the second gear 2b counterclockwise, which generates a force F3 of support of a tooth 21b of the pinion 2b on a resting surface 30b of blocking means 3b, in particular a pallet 3b, of the blocker 3.
• the resting surface 30b is arranged so that the direction of the force F3 passes substantially through the axis A3.
• the angle 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 is substantially less than 50 °, especially less than 30 °, or even less than 20 °.
• F2 and F3 the values of the intensities of the respective bearing forces against surfaces 200b and 30b; D02: the value of the lever arm of the force F2 with respect to the axis A2; D03: the value of the lever arm of the force F3 with respect to the axis A2. Since D02 "D03, it is thus found that the intensity of the force F3 is substantially lower than the intensity of the force F2.
• FIG. 2 illustrates the exhaust device just after the disengagement phase which follows the first rest position illustrated in FIG. 1.
• the balance plate 40 rotates clockwise.
• the pallet 40a for disengaging the platform 40 of balance 4 came into contact with the fork 3a of the blocker 3 and pivoted the latter counterclockwise. This contact and this action are maintained in FIG. 2.
• This action has released the tooth 21b of the pinion 2b of the resting surface 30b.
• the energy provided by the balance during this release to overcome friction and to move the mobile and the blocker is substantially lower than that provided in a conventional exhaust Robin type.
• the intensity of the force F3 is substantially lower than that of the bearing force F2.
• This intensity of the force F3 is minimized as much as possible if the inertia of the mobiles 1, 2 and the blocker 3 are minimized at best.
• the total diameter D2b of the pinion 2b is reduced as much as possible so as to reduce at best the inertia of the pinion 2b, as well as the dimensions of the blocker 3.
• the total diameter D2b of the pinion 2b is substantially less than the total diameter D1a of the first wheel 1a.
• 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.
• the pinion 2b rotates counterclockwise.
• the tooth 22b of this pinion approaches the resting surface 30c of the second blocking means 3c of the blocker 3 and rests on this surface in a second rest position.
• Figure 3 illustrates this second rest position.
• the pallet 40a of the balance plate 40 moves away from the fork 3a of the blocker 3.
• the tooth 10a of the wheel 1a 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 rotate the pinion 2b counterclockwise, which causes a bearing force F3 * of the tooth 22b on the surface of the tooth.
• the resting surface 30c is arranged so that the direction of the force F3 * passes substantially through the axis A3.
• F2 * and F3 * the values of the intensities of the respective bearing forces against surfaces 200b and 30c;
• D02 * the value of the lever arm of the force F2 * with respect to the axis A2
• D03 * the value of the lever arm of the force F3 * with respect to the axis A2.
• FIG. 4 illustrates the exhaust device just after the disengagement phase which follows the second rest position illustrated in FIG. 3.
• the balance plate rotates in the direction counterclockwise.
• the pallet release pallet 40a is in contact with the fork 3a of the blocker 3 and rotates the latter 3 in a clockwise direction. This contact and this action are maintained in FIG. 4.
• This action has released the tooth 22b of the pinion 2b of the resting surface 30c.
• the energy provided by the balance during this clearance to overcome friction and to move the mobile and the blocker is substantially lower than that provided in an exhaust device conventional type Robin.
• the first wheel 1 exhaust accelerates and pushes, including tangentially pushes the second gear 2b counterclockwise.
• the tooth 11a of the escape wheel approaches the pallet 40b of the balance plate pulse to transmit the energy to the balance by the action of the tooth January 1a on the pallet 40b during a phase pulse.
• the force transmitted from tooth 11a to pallet 40b is substantially tangential relative to axes A1 and A4.
• Figure 5 illustrates the position of the exhaust at the end of the pulse phase.
• the tooth 11a and the pallet 40b are in contact at their respective ends and the tooth 20b of the pinion 2b approaches the resting surface 30b of the pallet 3b of the blocker 3.
• the tooth 20b comes into contact of the blocker 3 and that the tooth 10a comes into contact with the second mobile exhaust 2, we find our in the configuration shown in Figure 1.
• the exhaust system according to this variant of the first embodiment has a very high efficiency, because it allows, on the one hand, significantly reduce the energy supplied by the balance during the clearance, and increases on the other hand the efficiency of energy transmission through a direct impulse of the wheel 1 has exhaust pendulum, in particular by means of a force transmitted from the first mobile of exhaust directly to the balance and is substantially tangential.
• Another advantage of such an exhaust device is the preservation, and therefore the optimization, of the isochronism of the sprung balance because of the low energy to be transmitted by the balance during disengagement.
• the rest surfaces 30b, 30c of the blocking means 3b, 3c of the blocker 3 are of concave shapes in order to guarantee the positioning accuracy of the teeth 20b of the pinion 2b on these surfaces.
• these concave surfaces may each be formed by two inclined planes forming an angle preferably between 120 ° and 170 °, as illustrated in FIG. 6.
• the blocker 3 may also be provided with mechanical transmission means 3d, 3e, for example protuberances 3d, 3e, capable of rotating the gear 2b in the opposite direction to that of the first gear. wheel 1 exhaust, complements forces F2, F2 * .
• these transmission means can exert a complementary action to those of F2 and F2 * efforts to rotate the second mobile exhaust anticlockwise.
• the actions are for example exerted by the blocker via the transmission means at the rest surfaces of the second mobile escapement.
• An example of an exhaust device blocker according to the second variant is for example illustrated in FIG. 7.
• the blocker 3 may also be provided with a stinger 3f designed to cooperate with a platform 41 complementary pendulum as shown in Figure 8, and this to prevent inadvertent movement of the blocker in case of shock.
• This third variant can be combined with one or the other of the first and second variants.
• the first mobile exhaust 1 comprises teeth 10a, including 20 teeth.
• the teeth are in the shape of points.
• the teeth are oriented downstream (relatively to their movement) in a direction making an angle between 20 and 45 ° with the radial direction relative to the axis of the first mobile.
• the free end of each tooth can be beveled.
• the second mobile 2 exhaust includes teeth 20b, including 4 teeth.
• the teeth extend substantially in an angular sector of about 45 °.
• Each tooth comprises a resting surface 200b oriented at an angle ⁇ between 15 ° and 50 °, or even between 20 ° and 45 °, with the orthoradial direction relative to the axis A2 of the second mobile.
• the angle ⁇ is an acute angle measured between the tangent to the resting surface and an orthoradial vector O 2 relative to the axis A2 and originating from the point of contact between the wheel 1a and the pinion 2b. This orientation creates a slight torque tending to turn the second mobile against the blocker in phases of rest and release.
• Each tooth is also limited by at least one lateral surface 202b oriented substantially radially relative to the axis A2.
• the angles a and ⁇ are therefore equal to the angle of friction, (angle of friction at the point of contact between the wheel 1a and the pinion 2b)
• 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.
• one end of a tooth 10a is in abutment against a rest surface 200b of a tooth 20b of the second mobile escapement and a lateral surface 202b of another tooth 21b of the second mobile is in support against one or other of the resting surfaces 30b, 30c of the blocker.
• a half-line originating from the axis A2 of the second mobile escapement and passing through the first point of contact where applies the first force F2 of the first escapement mobile on the second mobile escapement and a half-line originating from the axis A2 of the second mobile exhaust and passing through the axis A1 of the second mobile exhaust form an angle greater than 10 °, or even greater than 20 °, or even greater than 30 °.
• a half-line originating from the axis A1 of the first mobile d exhaust and passing through the axis A2 of the second mobile exhaust; and a half-line originating from the axis A1 of the first escapement mobile and passing through the first point of contact where the first force F2 of the first escapement mobile applies to the second mobile exhaust form an angle greater than 5 °, even greater than 10 °, or even greater than 20 °.
• a second embodiment of a timepiece 600 ', 600 “, 600 * is described below with reference to FIGS. 9 to 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 exhaust device 400 ', 400 ", 400 * disposed between a gear train and an oscillator 4, 5.
• the wheel is intended to connect a drive member, such as a barrel, to the exhaust.
• the wheel and allows a transmission of energy from the motor member to the exhaust.
• the escapement makes it possible to supply energy to the oscillator in order to maintain its oscillations.
• the oscillator is for example an oscillator of the balance 4 -spiral type 5.
• the balance is rotated along an axis A4 ', A4 ", A4 * .
• the exhaust device 400 ', 400 ", 400 * mainly comprises a first mobile 1', 1", 1 * exhaust pivoted along an axis A1 ', A1 ", A1 * , a second mobile 2', 2" , 2 * exhaust pivoted along an axis A2 ', A2 ", A2 * and a blocker 3', 3", 3 * rotated along an axis A3 ', A3 ", A3 * .
• second mobile exhaust and the blocker are shaped and arranged so that, in a phase of release of the exhaust device, a force of the blocker controlled by the oscillator 4, 5 is transmitted to the first mobile exhaust by the intermediate of the second mobile exhaust.
• the first escapement wheel comprises a first escape wheel 1 a ', 1 a ", 1 a * capable of acting indirectly on the clock oscillator
• a first pinion 1 b', 1 b", 1 b * of the the work train is integral in rotation with the first escape wheel 1 a ', 1 a ", 1 a * , in particular is fixed on the first escape wheel 1 a, 1 a", 1 a * , in particular is coaxially fixed on the first escape wheel 1 a ', 1 a ", 1 a * .
• the exhaust device is a direct-impulse exhaust device whose operating principle is similar to that of a Robin type exhaust device, which may for example be designed to cooperate with a rocker type oscillator 4 -spiral 5.
• the second exhaust mobile comprises a second exhaust pinion 2b ', 2b “, 2b * and a second wheel 2a', 2a", 2a * .
• the second wheel 2a ', 2a “, 2a * is secured to the second exhaust pinion 2b', 2b", 2b *, including the second wheel 2a ', 2a ", 2a * is fixed to the second exhaust pinion 2b ', 2b', 2b * or vice versa.
• the blocker cooperates with the second exhaust pinion 2b ', 2b “, 2b * via the second wheel 2a', 2a", 2a * exhaust, and vice versa.
• the second gear 2b ', 2b ", 2b * is provided to cooperate directly with a first wheel 1 a', 1 a", 1 a * exhaust which is integral in rotation with the first pinion 1 b ', 1 b ", 1 b * of the finishing gear of the clockwork movement.
• the exhaust device is of the direct impulse type. Its operating principle is similar to that of a Robin type exhaust system. This may for example be provided to cooperate with a balance-type oscillator spiral.
• the exhaust device differs from that of the first embodiment in that the sprung balance impulse is produced by a tooth 20a 'of the second wheel 2a' of exhaust.
• the exhaust device has an operation equivalent to that of the first embodiment.
• the second wheel 2a ' has the same number of teeth as the second gear 2b', namely six teeth.
• FIG. 9 illustrates a rest position of such an exhaust device, similar to that of the device according to the first embodiment illustrated in FIG. 3, which precedes a disengagement phase.
• the tooth 10a 'of the wheel 1a' 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 rotate the pinion 2b' counterclockwise, which causes a bearing force F30 of a tooth 20a 'on a resting surface 30c 'of blocking means 3c' of the blocker 3 '.
• the resting surface 30c ' is arranged so that the direction of the force F30 passes substantially through the axis A3'.
• F30 F20x (DO20 / OD30)
• F20 and F30 the values of the intensities of the respective bearing 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 '.
• the energy provided by the balance during the release phase to overcome friction and to move the mobile and the blocker is substantially lower than that provided in a conventional exhaust type Robin.
• the angle ⁇ 'formed between the force vector F20 and the half-line originating from the point of contact between the wheel 1 a' and the pinion 2b 'and passing through the axis A2' is substantially less than 50 °, or even less than 30 ° or even less than 20 °.
• This intensity of the force F30 is minimized as much as possible if the inertia of the mobiles 1 ', 2' and the blocker 3 'are minimized at best.
• the total diameter D2b 'of the pinion 2b' is reduced as much as possible so as to best reduce the inertia of the pinion 2b ', as well as the dimensions of the blocker 3'.
• the total diameter D2b 'of the pinion 2b' is substantially less than the total diameter D1 a ' of the first wheel 1 a ', especially less than 50%, or even less than 40% of the total diameter D1 a' of the first wheel 1 a '.
• the tooth profile of the elements 1 a 'and 2b' can also be shaped so that the torque transmitted by the first wheel 1 a 'to the second gear 2b' during the pulse phase is substantially greater than that transmitted during clearance.
• D010 the value of the lever arm of the force F20 with respect to the axis A1 '
• DO20 the value of the lever arm of the force F20 with respect to the axis A2 '
• a pulse surface 201 b "of the second gear 2b ' is oriented so that the transmitted force F20' is substantially tangential to the trajectory of the point of contact between the wheel 1 a 'and the pinion 2b'
• the force F20 ' is substantially normal to the half-line originating from the axis A1 'and passing through the axis A2'.
• DO10 ' the value of the lever arm of the force F20' with respect to the axis A1 ';
• DO20 ' the value of the lever arm of the force F20' with respect to the axis A2 '.
• the torque C2i transmitted to the pinion 2b 'during the pulse phase is substantially greater than the torque C2d transmitted to the pinion 2b' during the disengagement phase.
• the energy to be supplied by the balance during the disengagement phase is minimized and the energy transmitted by the drive member during the pulse phase to the exhaust device is maximized.
• Such an exhaust system thus has the advantage of having a maximized efficiency with regard to the exhaust devices known from the prior art, of the order of 120 to 1 60% with respect to average reference yields of the order from 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 with regard to the oscillators cooperating with escape devices known from the prior art.
• the geometries of the elements of the exhaust can be as described below.
• the first mobile escapement 1 comprises teeth 10a', in particular 20 teeth.
• the teeth are oriented downstream (relatively to their movement) in a direction for example an angle between 20 ° and 45 ° with the radial direction relative to the axis A1 'of the first mobile.
• the free end of each tooth can be beveled.
• the second pinion 2b 'exhaust includes teeth 20b', including 6 teeth.
• the teeth extend substantially in an angular sector of about 30 °.
• Each tooth comprises a resting surface 200b 'oriented at an angle ⁇ ' between 15 ° and 50 °, or even between 20 ° and 45 °, with the orthoradial direction 02 'relative to the axis A2' of the second mobile.
• the angle ⁇ ' is an acute angle measured between the tangent to the resting surface and an orthoradial vector 02' with respect to the axis A2 'and originating from the point of contact between the wheel 1 a' and the pinion 2b ' .
• This orientation creates a slight torque tending to turn the second mobile against the blocker in phases of rest and release.
• 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 a pulse surface 201 b '.
• angles a 'and ⁇ ' are therefore equal to the angle of friction, (angle of friction at the point of contact between the wheel 1 a 'and the pinion 2b')
• 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.
• a half-line originating from the axis A2 'of the second mobile escapement and passing through the first point of contact where the first force F20 of the first movable escapement is applied to the second mobile and a half -Right originating from the axis A2 'of the second mobile escapement and passing through the axis A1' of the second mobile exhaust form an angle greater than 10 °, or even greater than 20 °, or even greater than 30 °.
• a half-line originating from the axis A1 'of the first mobile exhaust and passing through the axis A2 'of the second mobile exhaust; and a half-line originating from the axis A1 'of the first escapement mobile and passing through the first point of contact where the first force F20 of the first movable escapement is applied to the second escapement mobile form a angle greater than 5 °, even greater than 10 °, or even greater than 20 °.
• the exhaust device is of the indirect pulse type. Its general operating principle is similar to that of a Swiss anchor escapement.
• the exhaust device according to the second variant of the second embodiment may for example be provided to cooperate with a balance-type oscillator spiral.
• Such an exhaust device differs from that of the first variant of the second embodiment in that the sprung balance impulse is produced by means of a blocker 3 "whose fork 3a” is provided for cooperate exclusively with a 4 "pendulum, including a 40" balance plate, including a balance plate pin 40a ".
• Figure 12 illustrates a rest position of such an exhaust device that precedes a disengagement phase.
• the force F21 which passes substantially near the axis A2 ", creates a torque which tends to rotate the pinion 2b" counterclockwise, which causes a bearing force F31 of a tooth 20a "on a resting surface 30c” blocking means 3c “of the blocker 3"
• the resting surface 30c is arranged so that the direction of the force F31 passes substantially through the axis A3"
• F31 F21 x (D021 / D031)
• F31 the value of the intensity of the bearing force against the surface 30c ";
• the total diameter D2b" of the pinion 2b "is reduced as much as possible. may so as to reduce the inertia of the pinion 2b "as well as the dimensions of the blocker 3", so that, preferably, the total diameter D 2b "of the pinion 2b" is substantially smaller than the total diameter D 1 a "of the first wheel 1 a ", especially less than 60% of the total diameter D1 a" of the first wheel 1 "exhaust, or even less than 50% of the total diameter D1" of the first wheel 1 "exhaust.
• the tooth profile of the elements 1a "and 2b” may also be shaped so that the torque transmitted by the first wheel 1a "to the second gear 2b" during the pulse phase is substantially greater than that transmitted during clearance.
• a pulse surface 201 b "of the second gear 2b" is oriented so that the force F21 'transmitted by the first mobile exhaust to the second mobile d exhaust is substantially tangential to the path of the point of contact between the wheel 1a "and pinion 2b".
• the force F21 ' is substantially normal to the half-line originating from the axis A1 "and passing through the axis A2".
• the torque C2i 'transmitted to the pinion 2b "during the pulse phase is substantially greater than the torque C2d' transmitted to the pinion 2b" during the disengagement phase.
• the energy to be supplied by the balance during the release phase is minimized, and the energy transmitted by the drive member during the pulse phase to the exhaust device is maximized.
• Such an exhaust system thus has the advantage of having a maximized efficiency with regard to the exhaust devices known from the prior art, of the order of 120 to 1 60% with respect to average reference yields of the order from 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 with regard to the oscillators cooperating with escape devices known from the prior art.
• the first exhaust mobile 1 "comprises teeth 10a", especially 20 teeth.
• the teeth are oriented downstream (relative to their movement) in a direction, for example making an angle between 20 ° and 45 ° with the radial direction to the axis A1 "of the first mobile.
• the free end of each tooth can be beveled.
• the second pinion 2b “exhaust includes teeth 20b", including 10 teeth.
• the teeth extend substantially in an angular sector of about 10 °.
• Each tooth comprises a resting surface 200b "oriented at an angle ⁇ " of between 15 ° and 50 °, or even between 20 ° and 45 °, with the orthoradial direction 02 “relative to the axis A2" of the second mobile.
• the angle ⁇ is an acute angle measured between the tangent to the resting surface and an orthoradial vector O2 "relative to the axis A2" originating from the point of contact between the wheel 1a and the pinion 2b. This orientation creates a slight torque tending to turn the second mobile against the blocker in phases of rest and release.
• 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 pulse surface 201 b".
• the angles a "and ⁇ " are therefore equal to the angle of friction, (angle of friction at the point of contact between the wheel 1 a "and the pinion 2b")
• the second wheel 2a “exhaust includes teeth 20a", including 5 teeth.
• the teeth are in the form of arms.
• Each tooth comprises a resting surface 200a "oriented at least substantially radially relative to the axis A3" of the blocker when the tooth of the second wheel is in contact with the blocker.
• Each tooth is also limited by a pulse surface 201 "oriented at least substantially orthoradially relative to the axis A3" of the blocker when the tooth of the second wheel is in contact with the blocker.
• the blocker 3 comprises the resting surfaces 30b “, 30c” oriented at least substantially orthoradially relative to the axis A3 "of the blocker and impulse surfaces 31b", 31c "oriented at least substantially radially relative to the axis A3 "of the blocker.
• one end of a tooth 10a "bears against a resting surface 200b" of a tooth 20b "of the second pinion and a resting surface 200a” of a tooth 20a “of the second wheel bears against a resting surface 30b ", 30c" of the blocker.
• a half-line originating from the axis A2 "of the second mobile exhaust and passing through the first point of contact where applies the first force F21 of the first escapement mobile on the second mobile escapement and a half-line originating from the axis A2 "of the second mobile exhaust and passing through the axis A "1 of the second mobile exhaust form an angle greater than 10 °, or even greater than 20 °, or even greater than 30 °.
• one end of a tooth 10a "bears against a pulse surface 201b" of a tooth 20b " the second pinion and a pulse surface 201a "of a tooth 20a" of the second wheel bears against a pulse surface 31b "of the blocker.
• the exhaust system presents an operating principle similar to that of the device disclosed in the patent application WO2013182243A1.
• This is for example designed to cooperate with a balance-type oscillator spiral.
• It is an indirect impulse escape device.
• the sprung-balance impulse is produced by means of a blocker 3 * of which a fork 30a * is provided to cooperate exclusively with a rocker 4, in particular a rocker plate 40 * , in particular an anchor 40a. * balance plate.
• Such an exhaust device differs from the preceding embodiments in that the blocker 3 * is made of two separate parts 30 * , 31 * kinematically connected to each other. The first piece 30 * is rotated about 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 * , and a toothing 30c * which is provided to mesh with a toothing 31 c * of the second room 31 * .
• the second piece 31 * is rotated about an axis A31 * .
• the second piece 31 * also comprises locking means 31b * intended to act by contact with the toothing 20a * of the second wheel 2a * .
• Figure 14 illustrates a rest position of such an exhaust device which precedes a disengagement phase.
• a tooth 10a * of the wheel 1 a * under the effect of the torque of the drive member exerts a force F22 a rest surface 200b * a * 20b of the pinion 2b * tooth.
• the force F22 passes substantially near the axis A2 * .
• the force F22 creates a torque which tends to rotate the pinion 2b * counterclockwise, which causes a bearing force F32 of a tooth 20a * on a resting surface 300b * locking means 30b * of the part 30 * of the blocker 3 * .
• the resting surface 300b * is arranged so that the direction of the force F32 substantially passes through the axis A30 * .
• F32 F22x (D022 / D032)
• F22 the value of the intensity of the bearing force against the surface 200b * ;
• F32 the value of the intensity of the bearing force against the surface 300b * ;
• D022 the value of the lever arm of the force F22 with respect to the axis A2 * ;
• D032 the value of the lever arm of the force F32 with respect to the axis A2 * . Since D022 "D032, it is thus found that the intensity of the force F32 is substantially lower than the intensity of the force F22.
• the energy provided by the rocker during the release to overcome friction and to move the mobile and the blocker is substantially lower than that provided in a conventional escapement type Swiss anchor.
• angle ⁇ * formed between the force vector F22 and the half-line originating from the point of contact between the wheel 1 a * and the pinion 2b * and passing through the axis A2 * is substantially less than 50 °, in particular less than 30 °, or even less than 20 °.
• the total diameter D2b * of the pinion 2b * is reduced as much as possible so as to best reduce the inertia of the pinion 2b * , as well as the dimensions of the blocker 3 * .
• the total diameter D2b * of the pinion 2b * is substantially less than the total diameter D1 a * of the first wheel 1a * , in particular less than 30% of the total diameter D1 a * of the first wheel 1a * d ' exhaust, or even less than 20% of the total diameter D1 a * of the first wheel 1 a * exhaust.
• the tooth profile of the elements 1 a * and 2b * may also be shaped so that the torque transmitted by the first wheel 1 a * to the second gear 2b * during the pulse phase is substantially greater than that transmitted during of the clearance phase.
• D022 the value of the lever arm of the force F22 with respect to the axis A2 * .
• a pulse surface 201 b * of the second pinion 2b * is oriented so that the transmitted force F22 'is substantially tangential to the path of the point of contact between the wheel 1a * and the pinion 2b * .
• the force F22 ' is substantially normal to the half-line originating from the axis A1 * and passing through the axis A2 * .
• the pair C2i "at the pinion 2b * can be expressed in the following manner with respect to the torque C1 i" at the wheel 1 a * , and neglecting the friction:
• D022 ' the value of the lever arm of the force F22' with respect to the axis A2 * .
• the torque C2i "transmitted to the pinion 2b * during the pulse phase is substantially greater than the torque C2d" to the gear 2b * transmitted during the disengagement phase.
• the energy to be supplied by the balance during the release phase is minimized, and the energy transmitted by the drive member during the pulse phase to the exhaust device is maximized.
• Such an exhaust device thus has the advantage of having a maximized efficiency with regard to the exhaust devices known from the prior art, such as that disclosed in the 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 with respect to oscillators cooperating with exhaust devices known from the prior art.
• the geometries of the elements of the exhaust can be as described below.
• the first mobile escapement 1 * includes teeth 10a * , including 40 teeth.
• the teeth have, for example, involute profiles or have substantially involute profiles.
• the second exhaust gear 2b * comprises teeth 20b * , in particular 6 teeth.
• the teeth extend substantially in an angular sector of about 30 °.
• Each tooth comprises a resting surface 200b * oriented at an angle ⁇ * between 10 ° and 50 °, or even between 20 ° and 35 °, with the orthoradial direction 02 * relative to the axis A2 * of the second mobile.
• the angle ⁇ * is an acute angle measured between the tangent to the resting 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 creates a slight torque tending to turn the second mobile against the blocker in phases of rest and release.
• 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 pulse surface 201 b * .
• angles a * and ⁇ * are therefore equal to the angle of friction, (angle of friction at the point of contact between the wheel 1 a * and the pinion 2b * )
• the blocker 3 * comprises resting surfaces 300b * , 310b * oriented at least substantially orthoradially relative to the axis A3 * of the blocker and pulse surfaces 301 b * , 31 1 b * oriented at least substantially radially relative to the axis A3 * of the blocker.
• a flank of a tooth 10a * bears against a rest surface 200b * of a tooth 20b * of the second gear and an end 200a * of a tooth 20a * of the second wheel is in abutment against a resting surface 310b * , 300b * of the blocker.
• a half-line originating from the axis A2 * of the second escape wheel and passing through the first point of contact where applies the first force F22 of the first escapement mobile on the second mobile escapement and a half-line originating from the axis A2 * of the second mobile escapement and passing through the axis A1 * of the second mobile exhaust form an angle greater than 10 °, or even greater than 20 °, or even greater than 30 °.
• a half-line originating from the axis A1 * of the first mobile exhaust and passing through the axis A2 * of the second mobile exhaust; and a half-line originating from the axis A1 * of the first escapement mobile and passing through the first point of contact where the first force F22 of the first movable escapement is applied to the second escapement mobile form a angle greater than 5 °, even greater than 10 °, or even greater than 20 °.
• the flank of a tooth 10a * bears against a pulse surface 201 b * of a tooth 20b * of the second gear and a end 200a * of a tooth 20a * of the second wheel bears against a pulse surface 301 b * , 31 1 b * of the blocker.
• the first and second escape mobiles and the blocker are preferably made of a low density material, for example silicon or a silicon alloy.
• the latter are preferably coated with a layer of SiO 2 or Si 4 N 3 so as in particular to strengthen their mechanical strength, and to optimize the tribology of the device.
• Such a device may for example not require lubrication.
• the resting surfaces of the locking means of the blocker are of concave shapes in order to guarantee the positioning accuracy of the teeth of the second mobile 2, 2 ', 2 ", 2 * on These concave surfaces are formed, for example, of two inclined planes forming, for example, an angle preferably between 120 ° and 170 °.
• the blocker may comprise mechanical transmission means capable of rotating the second mobile exhaust in the opposite direction to that of the first mobile escape. These means may consist of protuberances or teeth acting by contact on the second mobile exhaust, especially on impulse surfaces or on rest surfaces of the second mobile exhaust.
• the blocker may comprise a stinger intended to cooperate with a plateau complement of balance, and this so as to prevent inadvertent movements of the blocker in case of shock.
• the exhaust device is designed to optimally maintain the oscillations of the watch oscillator. 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 mobile is blocked in rotation by the blocker.
• the exhaust system has the advantage of having a maximized efficiency with regard to the exhaust 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 optimized isochronism oscillator with respect to the oscillators cooperating with escape devices known from the prior art.
• the exhaust device is such that it transmits from the first mobile exhaust to the second mobile exhaust a variable torque depending on whether it is in a phase of release or in a pulse phase. The torque transmitted from the first escapement mobile to the second escape mobile in the disengagement phase is lower than that transmitted from the first mobile exhaust to the second mobile exhaust phase pulse.
• the torque transmitted from the first escapement mobile to the second pulse phase escapement can be constant or substantially constant.
• the torque transmitted from the first escapement mobile to the second escape mobile in the disengagement phase can be constant or substantially constant.
• the transmitted torque of the first mobile exhaust to the second mobile exhaust in the disengagement phase may be equal to or substantially equal to the torque transmitted from the first mobile exhaust to the second exhaust mobile in idle phase.
• the first exhaust mobile and the second exhaust mobile can form a mechanical transmission device for a timepiece intended to transmit a torque, in particular for transmitting a variable torque and / or from a barrel.
• the first mobile exhaust and the second mobile exhaust can be part of a mechanical transmission device for a timepiece for transmitting a torque, in particular for transmitting a variable torque and / or from a barrel.
• the exhaust device is preferably such that, in the disengagement phase, the blocker acts directly against the second exhaust unit which is kinematically connected to the first exhaust unit.
• the exhaust device comprises the blocker, the first exhaust mobile and the second exhaust mobile which are arranged and shaped so as to:
• the exhaust device 400; 400 '; 400 "; 400 * preferably comprises a first mobile 1; 1 ';1"; 1 * exhaust, a second mobile 2; 2 '; 2 "; 2 * exhaust and a blocker 3; 3 ';3"; 3 * .
• the second mobile exhaust is preferably interposed between the first mobile exhaust and the blocker, in particular the second mobile exhaust can cooperate by contact with the first mobile exhaust on the one hand and with the other blocker go.
• the first mobile exhaust, the second mobile exhaust and the blocker are preferably shaped and arranged so that in phase of release of the exhaust device, a force of the blocker controlled by the oscillator 4, 5 is transmitted to the first mobile exhaust through the second mobile exhaust.
• the first escapement mobile, the second escape mobile and the blocker are preferably shaped and arranged so that, in the exhaust system's release phase, a first effort of the first mobile exhaust is applied to the second mobile exhaust and a second force of the blocker is applied to the second mobile exhaust, the intensity of the second force being less than the intensity of the first effort, including the intensity of the second effort 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 effort.
• the first mobile exhaust, the second mobile exhaust and the blocker are preferably shaped and arranged so that in the pulse phase of the exhaust system:
• a third force of the first escapement mobile applied directly to the second exhaust mobile or applied directly to an oscillator 4, 5 is directed substantially orthoradially relative to the axis A1; A1 '; A1 "; A1 * of the first escapement mobile or A2 axis;
• a fourth force of the second escapement mobile 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 mobile exhaust or at the A3 axis; A3 '; A3 "A3 * of the jammer or to the A4 axis; A4 ';A4"; A4 * of the oscillator.
• the second mobile 2; 2 '; 2 "; 2 * exhaust may be a second gear 2b or the second movable 2 ';2"; 2 * exhaust may include a second pinion 2b '; 2b "; 2b * and a second wheel 2a ';2a"; 2a * .
• the second mobile 2; 2 '; 2 "; 2 * exhaust may include a second pinion 2b ';2b"; 2b * , the second pinion being arranged to cooperate with the first mobile escapement, the first mobile escape, including a first wheel of the first mobile exhaust, having a greater diameter, in particular more than 1, 5 times greater, more than 2 times greater, the diameter of a second pinion of the second mobile 2; 2 '; 2 "2 * exhaust.
• the second wheel may comprise pulse surfaces 201 "oriented at least substantially orthoradially with respect to the axis A2; A2 ';A2"; A2 * of the second mobile and / or resting surfaces 200a "oriented at least substantially radially to the axis of the second mobile A2; A2 ';A2"; A2 * and / or the second pinion may comprise pulse surfaces 201 b '; 201 b "; 201 b * oriented at least substantially radially relative to the axis of the second mobile A2; A2 ';A2"; A2 * and / or resting surfaces 200b; 200b '; 200b “; 200b * oriented at an angle ⁇ ; ⁇ '; ⁇ "; ⁇ * between 15 ° and 50 °, or even between 20 ° and 45 °, between the tangent to the resting surface and an orthoradial vector O2; 02 '; 02 "; 02 * relative to the axis of the second
• the first exhaust movable, the second exhaust movable and the blocker may be shaped and arranged so that in the escape phase of the exhaust device, a first force F2; F20; F21; F22 of the first mobile exhaust on the second mobile exhaust at a first contact point forms an angle; at'; a "; a * 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 mobile escapement A2; A2 '; A2 "; A2 * at the first point of contact and / or the first movable exhaust, the second mobile escapement and the blocker can be shaped and arranged so that in phase of release:
• A1 '; A1 "; A1 * of the second mobile exhaust form an angle greater than 10 °, or even greater than 20 °, or even greater than 30 °;
• the watch movement 500; 500 '; 500 "; 500 * may comprise an exhaust device as described above, in particular may include the finishing gear 1 b '; 1 b"; 1 b * , the oscillator 4, 5 and an exhaust device as described above.
• the exhaust device is interposed between the work train and the oscillator.
• the timepiece 600; 600 '; 600 "; 600 * may comprise an exhaust device as previously described or a watch movement as described previously or a watch transmission device as described above.
• the method may comprise a disengagement phase, in which the second mobile escapement is applied simultaneously:
• a first effort F2; F20; F21; F22 of the first mobile escape and
• the intensity of the second effort may be less 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, intensity of the first effort.
• the method may comprise a pulse phase in which the first escapement mobile applies, directly on the oscillator or directly on the second mobile exhaust, a third force directed substantially orthoradially relative to the axis of the first mobile of exhaust or to the axis of the second exhaust mobile or the axis of the oscillator.
• the method may comprise a pulse phase in which the second exhaust mobile applies, directly on the oscillator or directly on the blocker, a fourth force directed substantially orthoradially relative to the axis of the second mobile exhaust or to the axis of the blocker or the axis of the oscillator.
• the method may comprise a pulse 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 pulse phase is greater than 1, 5 times, or even greater at 2 times, the intensity of the torque transmitted from the first mobile exhaust to the second mobile exhaust during a disengagement phase.
• mobile we mean, throughout this document, a wheel or a pinion or a wheel assembly (s) and / or pinion (s).
• wheel we mean, throughout this document, any rotating toothed organ whose function is to transmit a torque, a force, or a movement.
• pinion we mean, throughout this document, any rotatable toothed organ whose function is to transmit a torque, a force, or a movement, whose diameter and / or the number of teeth is substantially less than those / that of the wheel with which it meshes or with which it is fixed in rotation.
• angles mentioned are oriented angles.
• the positive orientation direction of these angles is the direction of rotation of the second mobile exhaust when the exhaust device is in operation.
• this positive orientation direction of the angles is the trigonometric or counterclockwise direction.
• 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.
• 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 that 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 °.
• substantially orthoradial direction 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.
• substantially radial direction 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.
• orientation of a surface is preferably defined by the direction tangent to this surface in the plane perpendicular to the pivot axes of the escape mobiles and / or the blocker.
• impulse surface of the second mobile exhaust we preferably hear, throughout this document, any surface of the second mobile exhaust capable of being in contact with the first mobile exhaust or with the blocker during a pulse phase of the exhaust system.
• rest surface of the second mobile exhaust we preferably hear, throughout this document, any surface of the second mobile exhaust capable of being in contact with the first mobile exhaust or with the blocker during a rest phase or a release phase of the exhaust system.
• blocker impulse surface we preferably mean, throughout this document, any surface of the blocker likely to be in contact with the second mobile escapement during a pulse phase of the exhaust system .
• blocker resting surface we preferably mean, throughout this document, any surface of the blocker likely to be in contact with the second mobile escapement during a rest phase or a release phase of the device exhaust.
• any movable transmission of a force from the gear to the blocker the mobile being shaped and / or arranged so that the direction of the effort that it transmits varies, in particular varies substantially, during an exhaust cycle.

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• 2016
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