• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a mechanical escape mechanism comprising an escapement mobile (1) cooperating with an inlet pallet (4) and an outlet pallet (5) of an anchor (3) each comprising on one of its flanks a first rest plane (11), this anchor comprising a fork (6) cooperating with a pin (9) of a pendulum mobile. The inlet (4) and outlet (5) vanes of the anchor (3) each comprise an additional rest formation (14) distinct from their first rest plane and adjoining their first rest plane (11). The fork (6) has teeth cooperating with the pin (9) of the balance wheel mobile. During the different operating phases of the escape mechanism, the anchor (3) takes up equilibrium positions resting on the first rest plane (11) of each pallet and equilibrium positions resting on the formation of additional rest (14) of each pallet. The invention also relates to a timepiece movement comprising such an escapement mechanism.
    公开号:CH712807B1
    申请号:CH00023/18
    申请日:2016-07-21
    公开日:2020-07-31
    发明作者:Bas Kéwin；Guerlesquin Gaël
    申请人:Cartier Int Ag；
    IPC主号:
    专利说明:

    The present invention relates to an escape mechanism for a particular timepiece. More particularly, the invention relates to an escapement mechanism of the Swiss lever type although other types of escapement can also be envisaged.
    The object of the invention is to allow the production of such an escapement mechanism allowing a high amplitude, greater than 360 °, of operation of the balance which is sought for obtaining greater power stored in the oscillator and of greater chronometric precision.
    The present invention relates to an escape mechanism which is distinguished by the characteristics set out in claim 1.
    [0004] The present invention also relates to a mechanical timepiece movement comprising such an escapement mechanism.
    [0005] The attached figures schematically illustrate an escape mechanism according to the invention.<tb> <SEP> FIG. 1 is a perspective view of the main members that the escape mechanism comprises.<tb> <SEP> Figure 2 is an elevational view of the escape mechanism shown in Figure 1.<tb> <SEP> Figure 3 illustrates the escape mechanism in its first equilibrium position.<tb> <SEP> Figure 4 illustrates the escape mechanism at the start of its first release phase.<tb> <SEP> Figure 5 illustrates the escape mechanism at the end of its first release phase.<tb> <SEP> Figure 6 illustrates the escape mechanism in its second equilibrium position.<tb> <SEP> Figure 7 illustrates the escape mechanism in its second phase of release.<tb> <SEP> Figure 8 illustrates the escape mechanism in its first push phase.<tb> <SEP> Figure 9 illustrates the escape mechanism in its first fall phase.<tb> <SEP> Figure 10 illustrates the escape mechanism in its third equilibrium position.<tb> <SEP> Figure 11 illustrates the escape mechanism at the start of its third phase of release.<tb> <SEP> Figure 12 illustrates the escape mechanism at the end of its third phase of release.<tb> <SEP> Figure 13 illustrates the escape mechanism in its fourth equilibrium position.<tb> <SEP> Figure 14 illustrates the escape mechanism at the start of its fourth phase of release.<tb> <SEP> Figure 15 illustrates the escape mechanism at the end of its fourth phase of release.<tb> <SEP> Figure 16 illustrates the escape mechanism in its fifth equilibrium position.<tb> <SEP> Figure 17 illustrates the escape mechanism in its fifth phase of release.<tb> <SEP> Figure 18 illustrates the escape mechanism in its second push phase.<tb> <SEP> Figure 19 illustrates the escape mechanism in its second phase of fall.<tb> <SEP> Figure 20 illustrates the escape mechanism in its sixth equilibrium position.<tb> <SEP> Figure 21 illustrates the escape mechanism at the start of its sixth phase of release.<tb> <SEP> Figure 22 illustrates the escape mechanism at the end of its sixth phase of release corresponding to its first equilibrium position (Figure 3).<tb> <SEP> FIG. 23 illustrates in perspective an anti-shock device for the escape mechanism illustrated in the preceding figures.<tb> <SEP> Figures 24 to 29 illustrate different relative positions of a first embodiment of an anti-shock device for the escape mechanism.<tb> <SEP> Figures 30, 31 and 32 illustrate on a larger scale the end of the entry pallet, the end of the exit pallet and the end of the fork of the anchor of the mechanism. 'exhaust.<tb> <SEP> Figures 33 to 37 schematically illustrate a second embodiment of an anti-shock device for the escape mechanism.<tb> <SEP> Fig. 38 is a perspective view of a second embodiment of the high amplitude escape mechanism.<tb> <SEP> Figure 39 illustrates the lower escape wheel of the escape mechanism shown in Figure 38.<tb> <SEP> Figure 40 illustrates the upper escape wheel of the escape mechanism shown in Figure 38.<tb> <SEP> Figure 41 illustrates the anchor of the escape mechanism shown in Figure 38.<tb> <SEP> Figure 42 is a partial view of the anchor shown in Figure 41.<tb> <SEP> Figure 43 illustrates the balance mobile of the escapement mechanism illustrated in figure 38.<tb> <SEP> Figures 44 to 62 illustrate the different phases of operation of the second embodiment of the high amplitude escape mechanism.
    The escape mechanism according to a first embodiment of the invention comprises the main elements illustrated in Figures 1 and 2 which are:<tb> - <SEP> The exhaust mobile which comprises an exhaust pinion (not illustrated) integral with or coming from a workpiece with an escape wheel 1 and its axis (not illustrated).<tb> - <SEP> The anchor mobile which includes the anchor rod 2, the anchor 3 whose inlet 4 and outlet 5 pallets can be in one piece with the anchor 3 or formed from parts attached to this anchor 3. The anchor 3 has at its end opposite the pallets 4, 5 a fork 6 and a stinger 7.<tb> - <SEP> The balance mobile which comprises a double plate 8 and its pin 9 fixed on the balance axis. By "pin" is meant any drive member which is carried by the balance and which cooperates with the fork of the anchor.
    The end of the entry pallet 4 of the anchor 3 illustrated in detail in Figure 30 comprises a pulse plane 10 forming the bevelled end of the entry pallet 4 connecting the inner side 4a of said entry pallet 4 to the outer side 4b of this entry pallet 4. This outer side 4b of the entry pallet 4 comprises a first rest plane 11 substantially parallel to the inner side 4a of the entry pallet 4 thus that a rest formation, which is preferably concave and formed of a second inclined rest plane 12 and a third rest plane 13 connecting the second rest plane 12 to the impulse plane 10. The intersection of second and third rest planes form a rest line 14 of the entry pallet 4.
    The end of the output pallet 5 illustrated in Figure 31 comprises an impulse plane 15 forming the bevelled end of the output pallet 5 connecting the outer side 5b to the inner side 5a of this output pallet. This inner flank 5a of the outlet pallet comprises a first rest plane 16 substantially parallel to the outer side 5b of the outlet pallet 5 as well as a rest formation, which is preferably concave and formed of a second rest plane 17 inclined and a third rest plane 18 connecting the second rest plane 16 to the impulse plane 15. The intersection of the second and third rest planes 17, 18 of the outlet pallet forms a rest line 19 of the pallet output 5.
    [0009] The fork 6 of the anchor 3 has four teeth 6a, 6b, 6c, 6d (FIG. 32) defining between them six contact planes cooperating with the pin 9 carried by the upper plate 8a of the double plate 8.
    The operation of this escape mechanism will be described in the following with reference to Figures 3 to 22.
    [0011] Figure 3 illustrates the escape mechanism in its first equilibrium position. The escape wheel 1 driven by the cog of a clockwork movement in the clockwise direction f1 is blocked by one of its teeth bearing on the first rest plane 11 of the inlet pallet 4 of the anchor 3. The torque transmitted to the escape wheel 1 and the profile of the input pallet 4 cause the anchor to tend to turn in the anti-clockwise direction f2 and this anchor is thus kept resting on a first fixed pin. 20. During this first phase of equilibrium, the balance is free, during its alternation in the clockwise direction, the pin 9 passes between the third 6c and fourth 6d teeth of the fork 6. In FIG. 3, the pin 9 is illustrated in the position it occupies at the end of a clockwise alternation of the balance. The direction of rotation of the balance f3 is reversed and it begins to alternate counterclockwise.
    The pin 9 comes into contact with the inner flank of the fourth tooth 6d of the fork (Figure 4) driving the anchor in the clockwise direction. The escape wheel makes a slight recoil. This first phase of release lasts until tooth e of the escape wheel passes from the first rest plane 11 of the input pallet 4 to the second rest plane 12 of this input pallet 4. At this moment, the contact between the pin 9 and the fork 6 is broken and the escape wheel 1 drives the anchor 3 clockwise by the orientation of the second rest plane 12 of the input pallet (figure 5 ). This first phase of release lasts until the moment when the tooth e of the escape wheel 1 comes into contact with the third rest plane 13 of the input pallet 4. The escape wheel 1 is then blocked with its tooth resting on the contact line 14 formed by the intersection of the second 12 and third 13 resting planes of the input pallet 4 (FIG. 6). The anchor is in equilibrium because the second 12 and third 13 resting planes of the entry pallet 4 are oriented so that if the anchor 3 moves in one or the other direction, the escape wheel 1 la returns to a balanced position. We reach the second equilibrium position. The balance is free and completes its first turn and begins the second turn of its first alternation until the moment when the pin 9 comes into contact with the internal flank of the third tooth 6c of the fork 6 (figure 7) driving the anchor 3 clockwise. The escape wheel 1 makes a slight recoil then its tooth e escapes the third rest plane 13 of the input pallet and the tooth e of the escape wheel comes into contact with the impulse plane 10 of the pallet input 4 (figure 8). At this moment, it is the escape wheel 1 which drives the anchor clockwise. The pin 9 loses contact with the third tooth 6c of the fork and the anchor, driven by the escape wheel 1, gives an impulse to the pin 9 through the internal flank of the second tooth 6b of the fork. This is the first phase of impulse, the balance is thus restarted.
    At the end of the pulse, the tooth e of the escape wheel leaves the impulse plane 10 of the input pallet 4. The escape wheel 1 and the anchor 3 are free and the escape wheel 1 rotates clockwise until a tooth d of this wheel comes into contact with the second 17 or the third 18 rest plane of the exit pallet 5 of anchor 3 (figure 9 ). It is the first fall of the escape mechanism which ends in the third equilibrium position of this mechanism (figure 10) for which the escape wheel 1 is in contact by its tooth d with the rest line 19, intersection of the second 17 and third 18 rest planes, of the output pallet 5. The escape wheel 1 is blocked by the anchor 3 which is kept in balance by the support of the tooth d of the escape wheel 1 against the second 17 and third 18 resting planes of the output pallet. This is the third position of equilibrium. The balance is free and continues its second revolution of its first alternation in an anti-clockwise direction. By the position of the second rest plane 17 and third rest plane 18 of the outlet pallet 5 and the geometry of the anchor, the torque applied to the escape wheel tends to maintain contact between its tooth d and the line rest 19 of the outlet pallet. The anchor is in balance because the second 17 and third 18 rest planes of the outlet pallet 5 are oriented so that if the anchor 3 moves in either direction, the escape wheel 1 puts it back. in a balanced position. The peg 9 escapes the teeth of the fork 6.
    [0014] The balance continues to rotate in an anti-clockwise direction and begins its third revolution.
    The pin 9 comes into contact with the outer flank of the second tooth 6b of the fork 6 and the escape wheel 1 makes a slight decline (Figure 11). The third phase of release continues until the tooth d of the escape wheel 1 passes from the second rest plane 17 of the outlet pallet 5 to the first rest plane 16 of this outlet pallet 5 (figure 12) .
    At this time, the contact between the pin 9 and the second tooth 6b of the fork is broken and it is the escape wheel which drives the anchor in the clockwise direction. The balance continues its third revolution counterclockwise freely, this is the third phase of release. At the end of this third phase of release, the anchor 3 abuts against a second fixed stop 21 and the escape mechanism is in its fourth position of equilibrium (FIG. 13). The escape wheel 1 is blocked, its tooth d being in contact with the first rest plane 16 of the output pallet 5. The torque applied to the escape wheel 1 and the profile of the output pallet 5 of the The anchor 3 causes the anchor 3 to tend to rotate clockwise and the latter abuts against the second fixed stop 21.
    The balance ends its alternation in the anti-clockwise direction during its third revolution of this alternation, stops and starts again in the opposite direction, clockwise, to begin its second alternation of an oscillation.
    During the first rotation of the second alternation, in the clockwise direction of the balance, the pin 9 comes into contact with the internal flank of the first tooth 6a of the fork thus driving the anchor 3 in the counterclockwise direction. The escape wheel will pull back slightly (figure 14).
    When the tooth d of the escape wheel 1 passes from the first rest plane 16 of the outlet pallet 5 to the second rest plane 17 of this outlet pallet 5, the contact between the pin 9 and the first tooth 6a of the fork 6 is broken (figure 15) and the escape wheel drives the anchor counterclockwise thanks to the orientation of the second rest plane 17 of the output pallet 5. This is the fourth phase release. During this time, the balance continues its free rotation clockwise and completes its first revolution of its second alternation of its oscillation.
    When the tooth d of the escape wheel 1 arrives on the rest line 19 of the output pallet 5, at the intersection of the second rest plane 17 and the third rest plane 18 of the output pallet , we obtain the fifth position of equilibrium of the escapement mechanism (figure 16). The escape wheel 1 is blocked by the anchor 3 and the balance continues its rotation starting the second clockwise revolution of its second alternation.
    During the second revolution of the second alternation of the balance, the pin 9 comes into contact with the internal flank of the second tooth 6b of the fork 6 driving the anchor 3 in the counterclockwise direction. Escape wheel 1 will retreat slightly. It is the fifth phase of release (figure 17) which continues until the tooth d of the escape wheel passes from the third plane of rest 18 of the output pallet 5 to the impulse plane 15 of this exit pallet 5. This is the second phase of thrust or impulse (figure 18), escape wheel 1 drives the anchor in an anti-clockwise direction, the internal flank of the third tooth 6c of the fork gives an impulse at the ankle 9 and thus transmits energy to the balance. This second impulse phase lasts until the tooth d of the escape wheel leaves the impulse plane 15 of the exit vane 5. It is then the second fall, the escape wheel 1 and anchor 3 are free, escape wheel 1 rotates clockwise until a tooth e1 thereof comes into contact with one or other of the second 12 or third 13 plane of rest of the input pallet 4. We arrive at the sixth position of equilibrium (figure 20) at the end of the second drop for which the tooth e1 of the escape wheel 1 is in contact with the rest line 14 , intersection of the second 12 and third 13 resting planes of the inlet pallet 4. This sixth position of equilibrium of the escape mechanism is identical to its second position of equilibrium illustrated in FIG. 6.
    The balance continues its clockwise rotation and begins its second revolution of its second alternation. The pin 9 comes into contact with the outer flank of the third tooth 6c of the fork 6 driving the anchor 3 in the anti-clockwise direction. The escape wheel 1 will back up slightly (figure 21). At the end of this sixth phase of release, the tooth e1 passes from the second rest plane 12 of the input pallet 4 to the first rest plane 11 of this input pallet (FIG. 22). At this moment, the contact between the pin 9 and the third tooth 6c of the fork 6 is broken and the escape wheel 1 drives the anchor 3 in the anti-clockwise direction, thanks to the orientation of the first rest plane 11 of the inlet pallet 4 and the anchor abuts against the first fixed stop 20 and the escape mechanism is found in the same configuration as in its first phase of equilibrium (FIG. 3).
    The balance continues its third revolution of its second alternation, stops then reverses its direction of rotation and the operating cycle of the escapement mechanism begins again.
    This escape mechanism therefore allows the balance to perform alternations of oscillations of more than 360 ° for example between two and three revolutions each, which increases the chronometric precision as well as the power stored in the oscillator.
    It is however interesting to note that if by chance the balance were to operate with alternations of less than 360 ° due to a lack of torque at the exhaust for example, the escapement mechanism described also works, the cycle operation then comprising the following phases: Second equilibrium position (FIG. 6); second phase of release (Figure 7); first pulse phase (Figure 8); first phase of fall (figure 9); third position of equilibrium (figure 10); fifth phase of release (Figure 17); second pushing phase (figure 18); second phase of fall (figure 19); and sixth phase of equilibrium (figure 20).
    This escape mechanism can be fitted to a mechanical timepiece movement comprising a motor, for example a barrel, connected by a gear train to an escape pinion integral with the axis of the escape wheel set and an oscillator of the type sprung balance whose axis carries the mobile of the balance.
    For proper functioning of the escape mechanism, it is necessary to provide an anti-shock device which allows the anchor 3 to be blocked in its equilibrium position. A first embodiment of an anti-shock device is illustrated in Figures 23 to 29. This anti-shock device comprises a stinger 7 fixed to the fork 6 of the anchor. This dart 7 has at its free end a stop 22 extending perpendicularly out of the plane of the dart 7.
    The shockproof device also comprises on the hub of the double plate 8 integral with the axis of the balance a notch 23 located under the pin 9 carried by the upper plate 8a of the double plate 8. This shockproof device finally comprises a peripheral rim 24 carried by the lower plate 8b of the double plate, peripheral rim 24 having two recesses 25.
    When the anchor is in its first equilibrium position (Figure 3), the dart 7 is in contact with the outer face of the rim 24 by its stop 22 preventing the anchor 3 from rotating clockwise. The dart 7 is dimensioned so that its stop 22 comes into contact with the rim 24 of the lower plate 8b before the tooth e of the escape wheel 1 leaves the first rest plane 11 of the input pallet 4 (figure 24).
    When the anchor 3 is in its second equilibrium position (Figure 6), the dart 7 prevents the anchor from rotating clockwise as well as counterclockwise. The stop 22 of the stinger is then located between the peripheral surface of the hub of the plate 8 and the internal face of the rim 24 of the lower plate 8b (figure 25)
    When the anchor 3 is in its third position of equilibrium (Figure 10), the dart 7 prevents the rotation of the anchor 3 clockwise and counterclockwise. The stop 22 of the dart 7 is located between the hub of the plate 8 and the internal face of the rim 24 of the lower plate 8b.
    The dart 7 is dimensioned, for the anti-clockwise direction, so that the stop 22 of the dart comes into contact with the double plate 8 before the tooth e of the escape wheel 1 leaves the second plane rest 12 of the input pallet 4 and does not arrive on the first rest plane 11 of this pallet.
    For the clockwise direction, the dart is sized so that the stop 22 of the dart 7 comes into contact with the lower plate 8b before the tooth e of the escape wheel leaves the third rest plane 13 of the inlet pallet 4 and does not reach the impulse plane 10 thereof (figure 26).
    When the anchor 3 is in its fourth equilibrium position (Figure 13), the dart 7 prevents the anchor 3 from rotating counterclockwise. The stinger 7 is dimensioned so that its stop 22 comes into contact with the outer surface of the rim 24 of the lower plate 8b before the tooth e of the escape wheel leaves the first rest plane 16 of the outlet pallet 5 ( figure 27).
    This shock-proof device must prevent the anchor 3 from unblocking inadvertently but also let it move during normal phases.
    For the passage from the second equilibrium position to the third equilibrium position, and vice versa, the stop 22 of the dart 7 is opposite the notch 23 of the hub of the double plate 8 which allows to do not block anchor 3 (figure 28).
    For the passage from the first position of equilibrium to the second position of equilibrium and from the third position of equilibrium to the fourth position of equilibrium, and vice versa, the stop 22 of the dart 7 is opposite a recess 25 of the rim 24 of the lower plate 8b, which makes it possible not to block the anchor 3 (FIG. 29).
    The shockproof device illustrated in Figures 23 to 29 can also be used with other types of exhausts, in particular those operating at high amplitude.
    A second embodiment of an anti-shock device for the escapement mechanism described is illustrated in Figures 33 to 37.
    In this embodiment of the shock-proof device, the dart 7 carried by the fork 6 of the anchor 3 comprises three arms 26, 27, 28. This dart 7 comprises a first central arm 26, a second lateral arm 27 and a third lateral arm 28, the second and the third arm being arranged on either side of the first central arm 26. Each of the three arms 26, 27, 28 ends in a point with two inclined planes a, b. Each of the planes 26a, 26b; 27a, 27b and 28a, 28b is able to cooperate depending on the position of the anchor 3 with the outer peripheral surface of the hub of the double plate 8 having a notch 23.
    When the anchor is in its first equilibrium position, the triple-arm dart 7 is sized so that the plane 28b of the second lateral arm 28 comes into contact with the periphery of the hub of the double plate 8 before the tooth e of the escape wheel does not leave the first rest plane 10 of the input pallet 4 (figure 33), the anchor 3 cannot turn clockwise.
    When the anchor 3 is in its second equilibrium position, it should not be able to turn either clockwise or anti-clockwise. The dart 7 is thus dimensioned (for the anti-clockwise direction) so that the plane 28a of the third lateral arm 28 comes into contact with the periphery of the hub of the double plate 8 before the tooth e of the escape wheel 1 leaves the second rest plane 12 of the input pallet 4 and does not reach the first rest plane 11. The stinger 7 is dimensioned, for the clockwise direction, so that the plane 26b of the first central arm 26 comes into contact with the hub of the double plate 8 before the tooth e of the escape wheel leaves the third rest plane 13 of the input pallet 4 and arrives on the impulse plane 10 of this input pallet 4 ( figure 34).
    When the anchor 3 is in its third equilibrium position, it is also necessary to prevent the anchor from rotating either clockwise or counterclockwise.
    The dart 7 is sized, for the counterclockwise direction, so that the plane 26a of the first central arm 26 comes into contact with the hub of the double plate 8 before the tooth d of the escape wheel does leaves the third rest plane 18 of the exit pallet 5 and does not arrive on its impulse plane 15.
    The dart 7 is dimensioned, for clockwise, so that the plane 27b of the second lateral arm 27 comes into contact with the hub of the double plate 8 before the tooth e of the escape wheel 1 leaves the second rest plane 17 of the outlet pallet 5 and does not arrive on the first rest plane 16 of this outlet pallet 5 (FIG. 35).
    When the anchor 3 is in its fourth equilibrium position, the dart 7 must prevent the anchor 3 from rotating counterclockwise. The dart is dimensioned so that the plane 27a of the second lateral arm 27 of the dart comes into contact with the hub of the double plate 8 before the tooth d of the escape wheel 1 leaves the first plane of rest 16 of the pallet. output 5.
    This shockproof device must prevent the anchor 3 from unblocking untimely, but must also let it move during normal phases.
    During the escape phases, the various planes of the arms 26, 27, 28 of the dart 7 are located opposite the notch 23 of the hub of the double plate 8, which makes it possible not to block the anchor 3 Figure 37 illustrates by way of example the passage of the anchor from its first position of equilibrium to its second position of equilibrium.
    The shockproof device illustrated in Figures 33 to 37 can also be used with other types of exhausts, in particular those operating at high amplitude.
    In what follows a second embodiment of the high amplitude escapement, greater than 360 °, will be described. This second embodiment relates to a direct escapement with a constant force device comprising an escape wheel set comprising two escape wheels pivotably linked together by a spiral spring.
    Figures 38 to 42 illustrate the different mobiles and elements of this second embodiment of the high amplitude escapement.
    This high amplitude escapement mechanism comprises an escapement mobile comprising a lower escape wheel 30 and an upper escape wheel 31, an anchor 32 and a balance wheel 33 fixed on the axis of an oscillator, typically a sprung balance.
    The lower escape wheel 30 is pivoted on a plate of a movement and comprises a first pin 30a and a second pin 30b.
    The upper escape wheel 31 is pivoted coaxially on the lower escape wheel 30 and has spokes defining stop planes 34 and 35.
    The anchor 32 comprises an axis, a lower anchor 32a comprising an inlet pallet E and an outlet pallet S located at different levels. As in the first embodiment of the escape mechanism, the inlet pallet E comprises on its outer side a first rest plane 11 connected to an impulse plane 10 by a rest formation. The latter is preferably concave and formed of a second rest plane 12 and a third rest plane 13 intersecting on a rest line 14.
    The outlet pallet S comprises on its internal side a first rest plane 16 connected to a rest formation which is still preferably concave and formed of a second rest plane 17 and a third rest plane 18 intersecting on a line of rest 19.
    The input pallet E is located at the same level as the upper escape wheel 31 and cooperates with the latter while the output pallet S is located at the level of the lower escape wheel 30 and cooperates with this one.
    The anchor 32 also includes an upper anchor 32b, the end of which comprises a fork with four teeth 36a, 36b, 36c, 36d.
    The mobile balance 33 is composed of two plates, a release plate 33a, which is at the same level as the upper anchor 32b and which comprises an ankle 37, and an impulse plate 33b, which is located at the same level as the upper escape wheel 31 and which comprises an impulse plane 38 cooperating with the teeth of the upper escape wheel 31.
    A spiral spring of constant force (not illustrated so as not to overload the drawing), one end of which is fixed to one of the pins 30a or 30b of the lower escape wheel 30 and the other end is fixed to the axis of the upper escape wheel 31, connects the two escape wheels 30 and 31.
    The operation of this second embodiment of the high amplitude escape mechanism will be described with reference to Figures 44 to 62.
    In its first position of equilibrium (Fig. 44), the balance is free and turns counterclockwise. Its amplitude is greater than 360 °. The upper escape wheel 31 is blocked against resting on the first rest plane 11 of the inlet pallet E and the lower escape wheel 30 is also blocked by the pins 30a, 30b of the lower escape wheel 30 resting on the stop planes 34, 35 of the upper escape wheel 31.
    The anchor 32 is supported on a first fixed stop 20. The orientation of the first rest plane 11 of the input pallet E means that the anchor 32 tends to rotate in the anti-clockwise direction.
    This first phase of equilibrium lasts until the pin 37 comes into contact with the tooth 36d of the upper anchor 32b. At this time, the balance wheel 33 drives the anchor 32 in a clockwise direction, slightly moving the upper 31 and lower 30 escape wheels back via the pins 30a, 30b and the stop planes 34, 35 (Fig. 45).
    This first phase of release lasts until the tooth ds of the upper escape wheel 31 leaves the first rest plane 11 of the input pallet E and passes over its second rest plane 12. The torque of the movement gear and of the constant force spring drives the anchor 32 clockwise thanks to the orientation of the second rest plane 12 of the input pallet E. The contact between the pin 37 and the upper anchor 32b is broken. (Fig. 46)
    The upper escape wheel 31 comes into contact with the rest line 14 separating the second rest plane 12 and the third rest plane 13 of the input pallet E. At this time the wheels of upper exhaust 31 and lower 30 are blocked by the inlet pallet E respectively by the pins 30a, 30b of the lower escape wheel 30 and the stop planes 34, 35 of the upper escape wheel 31. the shape of the concave rest formation formed by the second rest plane 12 and the third rest plane 13 of the inlet pallet E the anchor is returned to this second equilibrium position by the escape wheels. The pendulum is free. The escape mechanism is in its second equilibrium position (Fig. 47).
    When the pin 37 comes into contact with the tooth 36c of the upper anchor 32b the rocker drives the anchor 32 clockwise by slightly moving the upper 31 and lower 30 escape wheels via the input pallet. E and the pins 30a, 30b of the lower escape wheel 30. This is the second phase of release (Fig. 48).
    The tooth ds of the upper escape wheel 31 leaves the third plane of rest 13 of the input pallet E. At this time the upper 31 and lower 30 escape wheels are free to turn clockwise. . The anchor 32 continues to rotate clockwise, the pin 37 escapes the tooth 36c of the anchor and the balance is free again. The upper escape wheel 31 is no longer blocked and rotates clockwise thanks to the constant force spring. The lower escape wheel 30 comes into contact with the third rest plane 18 of the outlet pallet S (Fig. 49). The pins 30a and 30b of the lower escape wheel 30 leave the stop planes 34, 35 of the upper escape wheel 31. This second phase of release lasts until a tooth ds of the wheel d The upper exhaust 31 comes into contact with the impulse plane 38 of the impulse plate 33b (Fig. 50). At this moment a tooth di of the lower escape wheel 30 comes into contact with the second rest plane 17 and the third rest plane 18 of the outlet pallet S. These rest planes 17, 18 are studied so as to that the anchor 32 always returns to the equilibrium position defined by the rest line 19 of the outlet pallet S. The lower escape wheel 30 is blocked, however the upper escape wheel 31 is free and, driven by the constant force spring, will transmit the energy to the balance via its tooth ds and the impulse plane 38. (This is the impulse phase).
    When the pins 30a, 30b of the lower escape wheel 30 come into contact with the stop planes 34, 35 of the upper escape wheel 31, the lower escape wheel 30 and the mobile of anchor 32 are blocked as well as the upper escape wheel 31.
    Just before the upper escape wheel 31 is blocked, its tooth di separates from the impulse plane 38. The balance is again free. The escape mechanism is in its third equilibrium position (Fig. 51).
    When the pin 37 comes into contact with the tooth 36b of the upper anchor 32b, the balance drives the anchor 32 in a clockwise direction. The lower escape wheel 30 di will then move back slightly which drives the upper escape wheel 31 via the pins 30a, 30b and the stop planes 34, 35 of the upper escape wheel 31 (Fig. 52). . At the end of this third release phase, the tooth di of the lower escape wheel 30 leaves the second rest plane 17 of the outlet vane S and passes over the first rest plane 16 of this outlet vane. The anchor 32 is driven clockwise by the torque of the gear train thanks to the orientation of the first rest plane 16 of the output pallet S. The contact between the upper anchor 32b and the pin 37 is broken (Fig. 53). This third phase of release continues until the anchor comes into contact with the second fixed stop 21.
    At this time the anchor 32 is blocked in contact with this second fixed stop 21 and the upper 31 and lower 30 escape wheels are also blocked, the lower escape wheel 30 against the first rest plane 16 of the output pallet S with its tooth di and the upper escape wheel 31 via the pins 30a, 30b of the lower escape wheel 30. During this fourth phase or position of equilibrium the balance is always free and will end its alternation and start again clockwise for its second alternation (Figure 54).
    The fourth position of equilibrium is maintained until the pin 37 comes into contact with the tooth 36a of the upper anchor 32b. At this moment, the balance wheel 33 drives the anchor 32 in the anti-clockwise direction, slightly moving the lower escape wheel 30 and therefore the upper escape wheel 31 back via the pins 30a, 30b of the lower escape wheel in contact with the stop plane 35 of the upper escape wheel 31 (Fig. 55)
    This fourth phase of release lasts until the tooth di of the lower escape wheel 30 leaves the first rest plane 16 of the outlet pallet S and passes over the second rest plane 17 of this pallet output S (Fig. 56). At this moment it is the torque of the gear train which drives the anchor 32 in the anti-clockwise direction thanks to the orientation of the second rest plane 17 of the output pallet S. The contact between the pin 37 and the tooth 36a of the upper anchor 32b is broken and the escape mechanism is then in its fourth equilibrium position (Fig. 57). The pendulum is free again. This fourth equilibrium position is the same as the third equilibrium position (Fig. 51) except that the balance rotates clockwise.
    When the pin 37 of the balance wheel 33 comes into contact with the tooth 36b of the upper anchor 32b the balance drives the anchor 32 in the anti-clockwise direction by slightly moving the lower escape wheel 30 and therefore the upper escape wheel via the pins 30a, 30b and the stop plane 34 (Fig 58).
    This fifth phase of release lasts until the tooth di of the lower escape wheel 30 leaves the third plane of rest 18 of the output pallet S. At this time the two upper escape wheels 31 and lower 30 are free to rotate clockwise. The anchor 32 continues to rotate counterclockwise and the balance is free again. The upper escape wheel 31 comes via one of its teeth ds in contact with the third rest plane 13 of the input pallet E. This tooth ds will be placed on the rest line 14 of the entry pallet E under the effect of the torque of the cog and the orientation of the second 12 and third 13 resting planes of the entry pallet E positioning the anchor 32 so that the balance is free again .
    The lower escape wheel 30 is no longer blocked and rotates clockwise thanks to the torque of the cog. Contact is lost between the pins 30a, 30b of the lower escape wheel 30 and the stop plane 34 of the upper escape wheel 31. Thus, the constant force spring connecting the lower escape wheel 30 is recharged. to the upper escape wheel 31 (Fig. 59). This fifth phase of release lasts until the pins 30a, 30b of the lower escape wheel 30 come into contact with the stop plane 35 of the upper escape wheel 31 (Fig. 60). We find ourselves in the fifth position of equilibrium identical to the second position of equilibrium (Fig. 47) except that the balance turns in the other direction. At this moment, the balance drives the anchor mobile 32 in an anti-clockwise direction, slightly moving the upper escape wheel 31 and therefore the lower escape wheel 30 back via the pins 30a, 30b and the stop plane 35 ( Fig. 61)
    This sixth phase of release lasts until the tooth ds of the upper escape wheel 31 leaves the second rest plane 12 of the input pallet E and passes over the first rest plane 11 of this input pallet E. The torque of the gear train and the constant force spring drives the anchor 32 in an anti-clockwise direction, thanks to the orientation of the first rest plane 11 of the input pallet E. The contact between the ankle 37 of the balance mobile 33 is broken with the upper anchor. This sixth phase of release lasts until the anchor 32 comes into contact with the first fixed stop 20. We find ourselves in the first equilibrium position (FIG. 44) and the cycle can start again.
    The particularity of these escape mechanisms is to allow phases of equilibrium where the balance can continue its alternation by causing the anchor to oscillate without releasing the escape wheels. This is obtained thanks to the juxtaposition of several rest formations and in particular thanks to the presence of an additional rest formation on the pallets, which allows the balance to perform several turns for each alternation while the impulse is not given only once in alternation when the anchor is moved sufficiently to release the escape mobile. Preferably, the entry pallet E or the two entry 4 and exit 5 pallets have second and third rest planes which have a concave rest formation, for example in the form of a V (or U), but other shapes are also possible, even a flat shape.
    This mechanism is therefore distinguished in that the entry pallet E or the entry 4 and exit 5 pallets of the anchor comprises a first rest plane and at least one additional rest formation, adjacent to the first rest plan. Preferably, this formation is concave and formed of a second rest plane and a third rest plane forming a V between them and defining by their intersection a rest line. Thus when the escape wheel set rests by one of its teeth on the concave rest formation under the effect of the torque of the gear train, the exhaust wheel set tooth tends to be placed on the rest line. If the anchor is slightly displaced during a shock, for example, it does not leave its equilibrium position but automatically returns to its position defined by the tooth of the escape wheel coming into contact with the rest line of the formation concave rest is the intersection between the second rest plane and the third rest plane.
    Preferably, such an escape mechanism also comprises an anchor, the end of which cooperates with the pin of the balance wheel mobile comprises at least four teeth and not a simple fork with two teeth.
    In a first embodiment of the escape mechanism, the inlet pallet 4 and the outlet pallet 5 each comprise a first rest plane located on the respectively internal outer edge of the pallet. Each of these entry and exit vanes has an impulse plane forming the end face of the vane. In addition, each of these paddles comprises a concave rest formation, generally V-shaped, connecting the first rest plane to the impulse plane, formed by a second rest plane and a third rest plane whose intersection constitutes a line of rest.
    In the second embodiment of the escape mechanism, the input E and output S vanes do not have an impulse plane since it is a direct escape mechanism where the impulse is given directly by the escape wheel to the balance wheel without going through the anchor.
    Again, in this embodiment, each input E and output S pallet comprises a concave rest formation, generally V-shaped formed by a second rest plane and a third rest plane of which the intersection forms a line of rest. Each pallet, input E and output S, also comprises a first rest plane located on the respectively internal outer edge of the pallet and adjoining the concave rest formation, generally V-shaped.
    In this second embodiment, the four teeth of the upper anchor cooperating with the pin of the balance mobile can all be identical since none of them serves to give impetus to the balance.
    Unlike in the first embodiment, the central teeth of the anchor fork are preferably longer than the side teeth, because it is they which transmit the impulse to the balance wheel, the side teeth do not serving only to oscillate the anchor without pulling it out of one of its equilibrium positions.
    The balance performs several turns, generally two to three turns, alternately. An impulse is delivered to the impulse ankle by the escapement mobile, directly or via the anchor by alternating the balance. On the other hand, at each turn of the alternation of the balance, the pin cooperates with the teeth of the fork of the anchor to cause the latter to oscillate and allow said pin to pass but without causing the release of the escapement mobile which, under the effect of the cog, puts the anchor back into a position of equilibrium when the momentum is not delivered to the balance.
    Advantageously, the concave shape, generally U-shaped or preferably V-shaped of the rest formation formed by the first 11; 16 and the second 12; 17 rest plane of the input pallets 4; E and output 5; S and the orientation of these planes with respect to the axis of rotation of the anchor means that under the effect of the torque supplied by the gear train, the exhaust mobile returns to the equilibrium position l anchor when the latter is slightly offset in one direction or the other, for example following a shock.
    Of course the second embodiment of the escape mechanism can be provided with an anti-shock device such as those described with reference to the first embodiment of the escape mechanism.
    Whatever the embodiment of this escape mechanism, we see that the passage from the equilibrium position on the first rest plane 11, 16 of the inlet pallet 4 respectively of outlet 5 to the equilibrium position on the rest formation of these input 4 and output 5 pallets is achieved by an oscillation of the anchor 3, 32 caused by the balance wheel, acting on the fork of the anchor and therefore by the energy of the balance. This oscillation of the anchor allows the balance to perform several revolutions for each alternation of these oscillations while causing the release of the escapement mobile only once per alternation of the balance.
    This peculiarity of the resting planes of the entry and exit pallets of the anchor means that the escape mechanism can operate both with alternations of the balance less than 360 ° and greater than 360 °, the latter allowing greater chronometric precision and obtaining greater energy stored in the oscillator, particularly the balance.
    In variants of the escapement mechanism described, the number of revolutions of the balance can be increased for each of its alternations by multiplying the number of rest positions on the input and output vanes as well as the number of teeth of the anchor fork. It is therefore possible to envisage an escape mechanism where the balance would perform alternations of more than 720 ° in amplitude with an operation similar to the embodiments illustrated.
    Also, the fork can have a number of teeth other than four without departing from the scope of the invention. For example, those skilled in the art will know how to make an anchor cooperating with the balance so as to take four rest positions of the anchor with a fork with two teeth cooperating alternately with more than one plate peg, the second peg plate being mounted movably relative to the first so as to cooperate with the anchor beyond the stroke of the first.
    In addition, it is possible to play on the sizing of the input and output pallets and in particular for example on the lengths of the first rest planes 11, 12 and of the second rest planes 16, 17 of these pallets to modify the isochronism of the escapement and thus be able to better compensate for the isochronism of the spring balance spring in order to achieve a more precise assortment.
    In fact, the plane 11 (respectively 16) “disturbs” the balance while the latter is in an acceleration phase (FIG. 4, respectively 14), and it will therefore cause delay to the oscillator. Similarly, the plane 12 (respectively 17) “disturbs” the balance while the latter is in a deceleration phase (figure 21, respectively 11), and it will therefore bring advance to the oscillator.
    So, by controlling the length of planes 11 and 12 (16 and 17 respectively) we will be able to control the slope of the isochronism curve of the escapement (chronometric disturbance of the escapement on the oscillator as a function of the amplitude of this). By reducing the length of the rest plane 12 relative to the rest plane 11 (respectively 17 relative to 16) we will increase the directing coefficient of the isochronism curve of the escapement. Conversely, by reducing the length of the rest plane 11 relative to the rest plane 12 (respectively 16 relative to 17), the directing coefficient of the isochronism curve of the escapement will be reduced.
    We will therefore be able to compensate for the isochronism curve of the oscillator. For example if the isochronism curve of the oscillator causes the oscillator to take xs / d between an amplitude A and B, we will be able to adjust the escapement so that it causes a disturbance -xs / d between the amplitude A and B. Thus the isochronism of the set (exhaust + oscillator) will be 0 s / d between the amplitude A and B.
    There are, however, certain limits to this compensation. In fact, on the one hand, the total length of the rest planes 11 + 12 (respectively 16 + 17) must be constant (to maintain the correct clearance of the pin from the forks of the anchor), and on the other hand, the planes rest periods 11 and 12 (16 and 17 respectively) cannot be less than a certain value (to maintain sufficient safety).
    权利要求:
    Claims (18)
    [1]
    1. Mechanical escape mechanism comprising an escape mobile (1; 30, 31) cooperating with an inlet pallet (4; E) and an outlet pallet (5; S) of an anchor (3; 32) ) each comprising on one of its sides a first rest plane (11; 16), this anchor comprising a fork (6; 36) cooperating with a pin (9; 37) of a pendulum mobile (8; 33), characterized in that the inlet (4; E) and outlet (5; S) vanes of the anchor (3; 32) each have an additional rest formation (12, 13, 14; 17, 18, 19) distinct from their first rest plane and adjoining their first rest plane (11; 16); in that the fork (6; 36) has teeth cooperating with the pin (9; 37) of the balance wheel mobile (8; 33); by the fact that, during the various operating phases of the escape mechanism, the anchor (3; 32) assumes equilibrium positions resting on the first rest plane (11; 16) of each pallet and positions balance resting on the additional rest formation (12, 13, 14; 17, 18, 19) of each pallet; and by the fact that, for each pallet, the teeth of the fork (6; 36), the first rest plane (11; 16) and the additional rest formation (12, 13, 14; 17, 18, 19) allow the anchor to move from the equilibrium position on the first rest plane (11; 16) to the equilibrium position on the additional rest formation (12, 13, 14; 17, 18, 19) under the action of the pin (9; 37) of the balance mobile coming into contact with the fork (6) of the anchor (3) without releasing the escape mobile (1; 30, 31), thus allowing the mobile balance (8; 33) to perform an angular displacement of more than 360 ° for each of its vibrations.
    [2]
    2. Exhaust mechanism according to claim 1, characterized in that the additional rest formation of the inlet (4; E) and outlet (5; S) vanes has a concave shape.
    [3]
    3. Exhaust mechanism according to claim 2, characterized in that the additional concave-shaped rest formation of the inlet (4; E) and outlet (5; S) vanes has the shape of a V.
    [4]
    4. Exhaust mechanism according to claim 2, characterized in that the additional concave rest formation of the inlet (4; E) and outlet (5; S) vanes is formed by a second rest plane (12 ; 17) and a third rest plane (13; 18) defining by their intersection a rest line (14; 19).
    [5]
    5. Exhaust mechanism according to claim 4, characterized in that the orientation of the additional rest formations, respectively of the second rest planes (12; 17) and of the third rest planes (13; 18) as well as their positioning relative to the axis of the anchor (3; 32) means that when a tooth of the escape wheel set (1; 30, 31) is in contact with these additional rest formations, the anchor (3; 32) tends, under the effect of the torque of the exhaust mobile (1; 30, 31) to return to its equilibrium position when it is deflected therefrom.
    [6]
    6. Exhaust mechanism according to one of claims 1 to 5, characterized in that the inlet vane (4; E) and the outlet vane (5; S) both comprise an impulse plane ( 10; 15), the additional rest formation being located between the first rest plane (11; 16) and the pulse plane (10; 15).
    [7]
    7. Exhaust mechanism according to one of claims 1 to 6, characterized in that the fork has four teeth (6a-d; 36a-d) cooperating with the pin (9; 37) of the mobile balance.
    [8]
    8. Exhaust mechanism according to claim 7, characterized in that the two central teeth (36b, 36c) of the fork (6) are longer than the two lateral teeth (36a, 36d) thereof.
    [9]
    9. Exhaust mechanism according to one of the preceding claims, characterized in that the exhaust mobile comprises an escape wheel (1) whose teeth cooperate alternately with the input pallet (4) and the pallet. outlet (5) of the anchor (6).
    [10]
    10. Exhaust mechanism according to one of claims 1 to 5, characterized in that the escape mobile comprises an upper escape wheel (31) and a lower escape wheel (30); by the fact that the teeth of the upper escape wheel cooperate with the input pallet (E) of the anchor (32) and with an impulse plane (37) of the mobile of the balance (33) while the teeth of the lower escape wheel (30) cooperate with the outlet pallet (S) of the anchor (32).
    [11]
    11. Exhaust mechanism according to claim 10, characterized in that the fork (36) of the anchor (32) has four teeth, substantially of equal length, cooperating with the pin (37) of the balance wheel ( 33).
    [12]
    12. Exhaust mechanism according to claim 10 or claim 11, characterized in that the upper escape wheel (31) is pivoted on the lower escape wheel (30) and that a constant force spring connects the upper escape wheel (31) to the lower escape wheel (30), and in that the relative angular displacement between the upper escape wheel (31) and the lower escape wheel (30) is limited by pins (30a, 30b) of the lower escape wheel (30) cooperating with stop planes (34, 35) of the upper escape wheel (31).
    [13]
    13. Exhaust mechanism according to one of the preceding claims, characterized in that it further comprises an anti-shock device comprising a stinger (7) integral with the anchor (3; 32) cooperating with the balance wheel mobile (8 ; 33).
    [14]
    14. Exhaust mechanism according to claim 13, characterized in that the stinger has three teeth.
    [15]
    15. Exhaust mechanism according to one of the preceding claims, characterized in that the balance wheel mobile performs for each alternation an angular displacement of between 360 ° and 720 °.
    [16]
    16. Exhaust mechanism according to one of the preceding claims, characterized in that the inlet pallet (4; E) and the outlet pallet (5; S) each comprise several additional resting formations located after each other.
    [17]
    17. Mechanical clockwork movement comprising a motor, an escapement mechanism according to one of claims 1 to 16, a gear train connecting the motor to a pinion of the escapement mobile of the escape mechanism and an oscillator on the axis of which is fixed the balance wheel of the escapement mechanism.
    [18]
    18. Timepiece movement according to claim 17, characterized in that the oscillator is of the sprung balance type.
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    同族专利:
    公开号 | 公开日
    CH712807B8|2020-10-30|
    WO2017013611A1|2017-01-26|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2690048A|1953-02-02|1954-09-28|Cecil F Smith|Watch escapement|
    CH1082672A4|1972-07-19|1975-03-14|
    CH702689B1|2006-11-13|2011-08-31|Patek Philippe Sa Geneve|Shared impulsion pallet escapement for timepiece, has concave part conformed so that angle defined by pulse faces at contact point between faces is of specific degrees during part of pulse phase where rest lip is slid on concave part|
    CH702930A2|2010-04-01|2011-10-14|Patek Philippe Sa Geneve|Exhaust watch to protection against shocks.|
    CH708665B1|2013-10-08|2018-01-31|Sigatec Sa|Anchor for clock escapement.|
    法律状态:
    2020-09-15| PK| Correction|Free format text: RECTIFICATION INVENTEUR |
    2020-10-30| PK| Correction|Free format text: RECTIFICATION B8 |
    优先权:
    申请号 | 申请日 | 专利标题
    CH10672015|2015-07-21|
    PCT/IB2016/054333|WO2017013611A1|2015-07-21|2016-07-21|Escapement mechanism|
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