JP2013186078A - Escape gear, escape wheel including the same, anchor escapement, movement, mechanical watch, and torque transmission method - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an escape gear capable of effectively transmitting torque when replacing an impulse face, an escape wheel including the escape gear, an anchor escapement having the escape wheel, a movement having the escape wheel, a mechanical watch, and a torque transmission method.SOLUTION: In an escape gear 1 of an escape wheel 2 of an anchor escapement of a mechanical watch, a locking corner 30 connecting a stop face 10 to an impulse face 20 forms a curved first curved convex surface part 31. A curved second curved convex surface 21 is formed on a portion continued to the first curved convex surface part 31 of the locking corner 30 out of the impulse face 20. The second curved convex surface part 21 may be expanded to the whole impulse face 20. A curvature radius R2 of a portion of the second curved convex surface part 21 may be increased in accordance with separation from the locking corner 30 of the impulse face 20. A portion continued to a portion of the second curved convex surface part 21 out of the impulse face 20 may be planar.

Description

  The present invention relates to a escape tooth, an escape wheel provided with the escape wheel, an ankle escapement having the escape wheel, a movement having the escape wheel, a mechanical timepiece, and torque transmission Related to the method.

  In the ankle escapement of a mechanical watch, the escape teeth of the escape wheel are (1) stopped (locked), (2) released from stopping, and (3) (4) Repeating the operation of waiting until the balance of the balance of the balance returns to the place where the impact is applied to the ankle (entrance and exit claw) again, and the torque or energy of the mainspring is intermittently applied to the balance.

  In the above, between the escape wheel and the balance between the release of the stop in (2) and the completion of the impact in (3), it is effective to apply torque or supply rotational energy from the escape wheel to the balance. It is hoped that this will be done automatically.

  However, the present inventor has found that it is difficult to provide torque or effectively supply rotational energy in an escape wheel escaper (for example, Patent Document 1) that is generally used at present. Noticed.

  As shown in FIG. 8, each hook tooth 102 of the escape wheel & pinion 101 currently generally used in the ankle escapement includes a linear or flat stop surface 110 and the stop surface 110. And an impact surface 120 of a straight line, that is, a plane, that forms an angle α with respect to the surface, and a crossing portion of the stop surface 110 and the impact surface 120, that is, a rocking corner, is formed in a corner portion 130 having an angle α (a predetermined obtuse angle) It has become.

  On the other hand, the input pawl 202 and the output pawl of the ankle 201 are the same. For example, as shown for the input pawl 202 in FIG. A straight or planar impact surface 220 that forms an angle β with respect to the stop surface 210, and a rocking corner between the stop surface 210 and the impact surface 220 becomes a corner portion 230 of an angle β (predetermined obtuse angle); The other end side of the impact surface 220 is actually a corner portion 240 having an acute angle γ.

  Accordingly, torque or energy exchange between the escape wheelchair 101 and the balance with hairspring is substantially as shown in FIGS. 9 (a) to 9 (e) and FIG.

  The escape wheel 101 that has been stopped by engagement of the escape teeth 102 with the stop surface 210 of the pawl 202 of the ankle 201 on the stop surface 110 is the PW1 direction turning force that the ankle 201 receives from the pallet of the balance. As shown in FIG. 9 (a), the escape tooth 102 is engaged with the ankle 201 in the vicinity of the locking corner 130 of the stop surface 110 immediately before the impact is released. Of the stop surface 210 of 202, it will be in state PS1 which receives stop cancellation | release force by the rocking corner 230. FIG.

  Immediately after this, the escape tooth 102 is once separated from the engagement pawl 202 in the C2 direction due to the inertia of the escape wheel 101, and then immediately in the C1 direction under the action of the C1 direction torque from the mainspring through the train wheel train. To the portion PP2 of the impact surface 220 of the pawl 202 that is shifted by a certain length ΔLP1 from the rocking corner 230 at the rocking corner 130, and with respect to the pawl 202 to rotate the ankle 201 in the PW1 direction. Then, a force in a direction PF2 perpendicular to the impact surface 220 of the pawl 202 is applied, and torque is applied to the balance with the ankle 201 (state PS2 in FIG. 9B).

  Here, when the escape tooth 102 is once separated from the locking corner 230 of the pawl 202 of the ankle 201 and hits the impact surface 220 of the ankle 201, the force is transmitted to the ankle in a discontinuous and greatly changed direction. As a result, the efficiency of power transmission from the escape wheel 101 to the ankle 201 is reduced, and there is a blank period for power transmission to the ankle 201 for a period corresponding to the length ΔLP1. The efficiency of power transmission from the escape wheel 101 to the ankle 201 also decreases in that the 220 cannot be used effectively.

  As the escape wheel 101 rotates in the C1 direction, the rocking corner 130 of the escape tooth 102 of the escape wheel 101 has a portion PP that applies torque to the impact surface 220 of the pawl 202 along the impact surface 220 in the EP direction. 9 and passes through the position PP3 indicated by the state PS3 in FIG. 9C to reach the leaving corner (impulse beak) 240 indicated by the state PS4 in FIG. 9D. At this time, the direction PF4 of the force exerted by the escape teeth 102 of the escape wheel 101 on the impact surface 220 of the pawl 202 of the ankle 201 is a direction perpendicular to the impact surface 220 in the state PS4.

  Thereafter, as the escape wheel 101 further rotates in the C1 direction, the escape tooth 102 pushes the impact surface 220 of the pawl 202 at the locking corner 130 as shown in FIG. In addition, the escape tooth 102 of the escape wheel 101 has its impact surface 120 in an impact surface alternation state PS5 that pushes the leaving corner 240 of the pawl 202 in a direction PF5 perpendicular to the impact surface 120. . When the impact surface is changed from the impact surface 220 to the impact surface 120, the direction of the force applied to the pawl 202 by the escape teeth 102 changes from PF4 (direction perpendicular to the impact surface 220 of the pawl 202) to PF5 ( It suddenly changes to a direction perpendicular to the impact surface 120 of the toothpaste 102.

  As a result, transmission of torque from the escape wheel 101 to the ankle 201, that is, transmission of torque from the escape wheel 101 to the balance via the ankle 201 is difficult to be performed effectively. That is, for example, when the impact surface is changed, the escape tooth 102 and the pawl 202 are temporarily separated or are about to be separated, and thus torque or energy transmission is not performed or is difficult to be performed. There is also a risk of doing.

  Thereafter, in accordance with the rotation of the escape wheel 101 in the C1 direction, the corner portion 240 of the pawl 202 moves in the HP direction along the impact surface 120 of the escape tooth 102, and then moves from the escape wheel 101 to the ankle 201. Torque is supplied to the balance or to the balance with the ankle 201.

  As can be seen from the above description, in the conventional ankle escapement having the conventional escape wheel provided with the conventional escape teeth, the torque transmission loss at the time of impact surface replacement in FIG. LP1 and torque transmission loss LP2 from the start of impact in (a) to (b) of FIG. 9 and the like, and torque of the escape wheel 101 to the ankle 201 or to the balance with the ankle 201 There is a possibility that the supply is difficult to be performed effectively.

  FIG. 10 is a graph of the torque ratio ΔT corresponding to the rotation angle θ of the balance with respect to PJ1 in the case of the insertion and PJ2 in the case of the extraction. In this graph, the change from the state PS1 to the state PS2 and the change from the state PS4 to PS5 correspond to the places where the losses LP1 and LP2 occur. The above is the same for the case of not only the infeed but also the exit.

  In addition, although the object is different, it has been proposed that the locking corner 230 of the pawl is a convex curved portion or the impact surface is a concave curved portion (Patent Document 2).

  However, depending on the convex convex curved portion disclosed in Patent Document 2, a sudden change in the direction of the force when the impact surface is changed cannot be avoided, and the torque transmission loss LP2 is not improved.

JP 2009-288083 A Swiss patent No. 702689

  The present invention has been made in view of the above-mentioned points, and an object thereof is to provide a brilliant tooth that can effectively transmit torque when the impact surface is changed, and the brilliant tooth. An escape wheel, an ankle escapement having the escape wheel, a movement having the escape wheel, a mechanical timepiece, and a torque transmission method.

  The escape tooth of the present invention is in the form of a first curved convex surface portion in which a rocking corner connecting the stop surface and the impact surface is curved in order to achieve the above object.

  In the escape tooth according to the present invention, “the rocking corner connecting the stop surface and the impact surface is in the form of the first curved convex surface portion”. Or, from the state of pushing the impact surface of the protrusion, the escape tooth is connected to the impact surface (more specifically, the portion of the impact surface of the escape tooth that is connected to the rocking corner (in other words, the first of the escape tooth) The force exerted on the pawl of the ankle when the impact surface is changed to a state where the ankle pawl's leaving corner (impulse beak) is pushed in the rocking corner in the form of a curved convex surface portion. Since the change of the direction of the force can be avoided and the change or fluctuation of the direction of the force can be minimized, the torque can be effectively transmitted to the pawl of the ankle.

  Also, in the escape tooth according to the present invention, “the rocking corner connecting the stop surface and the impact surface is in the form of a curved first curved convex surface portion”, so that when the stop is released, the locking corner of the escape tooth is formed. Since the first curved convex surface portion that makes contact with the impact surface from the pawl stop surface of the ankle pawl can be contacted substantially continuously, the hook teeth move away from the pawl of the ankle and torque between the release of the stop and the start of the impact. The blank period during which the supply is not performed is minimized, and the impact surface of the nail of the ankle can be used effectively. Therefore, torque can be effectively transmitted to the pawl of the ankle. In addition, since the change in the direction of the force at the start of impact after the stop is released can be suppressed to be relatively small, torque can be effectively transmitted from the escape tooth to the pawl of the ankle.

  In the escape tooth of the present invention, there is typically a second curved convex surface portion curved at a portion of the impact surface following the first curved convex surface portion of the rocking corner.

  In this case, after the impact surface is changed, the direction of the portion of the impact surface of the escapement that contacts the reeving corner of the claw of the ankle changes away from the rotation center axis of the ankle according to the curvature of the second curved convex surface portion. Therefore, a decrease in the torque applied from the escape teeth according to the rotation of the escape teeth can be suppressed or the torque can be increased. Therefore, torque can be effectively transmitted to the pawl of the ankle. As long as the first curved convex surface portion and the second curved convex surface portion can be practically connected, a linear (planar) portion is provided between the first curved convex surface portion and the second curved convex surface portion as long as the length is relatively short. It may be interposed.

  In the escape tooth of the present invention, typically, the second curved convex surface portion extends over the entire impact surface.

  In that case, the torque applied from the escape wheel to the balance via the ankle can be increased over time during the entire period of impact after the start of the impact.

  In the escape tooth of the present invention, typically, the radius of curvature of the portion of the second curved convex surface portion is larger in the portion of the impact surface that is away from the rocking corner.

  In that case, the torque applied from the escape wheel to the balance via the ankle can be gradually reduced at the end of the impact.

  In the escape tooth of the present invention, when the second curved convex surface portion is formed on the entire impact surface, when the escape wheel has a diameter of 4.85 mm, typically, the second curve The curvature radius R2 of the convex portion is 0.4 to 0.6 mm.

  In this case, the advantage of the second curved convex surface portion of the impact surface can be obtained effectively. If the radius of curvature R2 is too small (smaller than the lower limit value), the direction of the force applied by the impact surface of the hook teeth after the impact surface change to the leaving corner of the pawl of the ankle will change abruptly. There is a possibility that the increase in the amount becomes too large. On the other hand, when the radius of curvature R2 is too large (when it is larger than the upper limit), the second curved convex surface portion of the impact surface of the escape tooth becomes practically equal to that of the conventional escape. Since it becomes flat like the impact surface of the tooth (straight when viewed from the side), the advantage of having the second curved convex surface is almost lost.

  In the escape tooth of the present invention, the portion following the second curved convex surface portion of the impact surface may be planar.

  In that case, the torque applied from the escape wheel to the balance via the ankle can be reduced substantially linearly at the end of the after impact.

  In the escape tooth of the present invention, when the portion following the second curved convex surface portion of the impact surface is planar, when the escape wheel has a diameter of 4.85 mm, typically, The curvature radius R2 of the second curved convex surface portion is 0.2 to 0.5 mm.

  Compared to the case where the entire impact surface has the second curved convex surface portion, the appropriate range of the radius of curvature R2 of the second curved convex surface portion is shifted to the smaller side of R2, because the expansion of the second curved convex surface portion is short. This is because the orientation of the surface within the range of the expansion is greatly changed.

  In the escape tooth of the present invention, typically, when the diameter of the escape wheel is 4.85 mm, the radius of curvature R1 of the first curved convex surface portion is 0.01 to 0.05 mm.

  In this case, the advantage of the first curved convex surface portion of the rocking corner can be obtained effectively. If the radius of curvature R1 is too small (smaller than the lower limit value), the first curved convex surface portion of the locking corner of the hook tooth is practically not equal, and in fact, conventional Since the corner has an angular apex such as a tooth locking corner, the advantage of having the first curved convex surface is almost lost. On the other hand, when the radius of curvature R1 is too large (when it is larger than the upper limit value), there is a possibility that it is difficult to properly engage the pallet of the ankle (stopping the bulge).

  The escape wheel according to the present invention includes the escape teeth as described above in order to achieve the object.

Moreover, the ankle escapement of the present invention performs the transfer of torque from the escape wheel and the escape wheel as described above, and intermittently rotates the escape wheel to achieve the object. And an ankle that transmits torque of the mainspring to the balance with the balance, and a balance that receives the torque from the ankle and acts on the ankle.
In addition, the movement of the present invention has the ankle escapement as described above in order to achieve the target.

Furthermore, in order to achieve the object, the mechanical timepiece according to the invention includes a movement wheel as described above and a case containing the movement.
In addition, the torque transmission method of the present invention provides a escape wheel provided with a escape tooth in the form of a first curved convex surface portion in which a rocking corner connecting the stop surface and the impact surface is curved in order to achieve the above-mentioned object. A torque transmission method for transmitting torque to the pawl of the ankle, wherein the torque is transmitted by bringing the impact surface into contact with the pawl of the ankle as the escape wheel rotates. By moving the ankle pawl along the first curved portion toward the impact surface, the torque is transmitted while suppressing changes or fluctuations in the direction of the force applied to the pawl of the ankle by the escape tooth. It is characterized by doing.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an explanatory plan view of an ankle escapement of a preferred embodiment of the present invention having a escape wheel of a preferred embodiment of the present invention equipped with a escape tooth of a preferred embodiment of the present invention. The plane explanatory view which expanded and showed the portion of the escape tooth of one desirable example of the present invention of the escape wheel of FIG. Fig. 2 shows a change in torque exchange between the escapement and the pawl of the ankle escapement having an escape wheel equipped with the escapement of Fig. 2. (B) is a plane explanatory diagram showing a state in which the stop release is progressing, (c) is a plane showing a state in which the impact of the claws by the escape tooth is started. Explanatory drawing, (d) shows a state in which the impact of the pawl is progressing, and the arcuate rocking corner of the goose tooth has moved halfway along the impact surface of the pawl (E) is a state in which the impact of the pawl is progressing, and the arcuate rocking corner of the hook is moved along the impact surface of the pawl to the leaving corner. Plan explanatory drawing which showed the state, (f) Plan explanatory drawing which showed the state of impact surface replacement. FIG. 9 is a graph schematically showing changes in the torque ratio ΔT with respect to the balance with respect to the balance with respect to the rotation angle θ of the ankle, and shows changes in the ankle escapement of FIG. 3 and the conventional ankle escapement shown in FIG. 8. The graph which showed change of. FIG. 9 is a graph schematically showing a change in the torque ratio ΔT with respect to the balance rotation angle θ with respect to the unloading of the ankle, and the change with respect to the ankle escapement of FIG. 3 and the conventional ankle escapement shown in FIG. 8. The graph which showed change of. Plane explanatory drawing similar to FIG. 2 which expanded and showed the part of the escape tooth of another preferable one Example of this invention. The graph which showed typically the change of the torque ratio (DELTA) T with respect to the balance rotation angle (theta) regarding the ankle escapement of the ankle escapement provided with the escapement of FIG. Plane explanatory drawing about the conventional escape tooth of the conventional escape wheel of the conventional ankle escapement. FIG. 8 shows a change in torque exchange between the hook and tooth of the conventional ankle escapement having the conventional escape wheel provided with the conventional escape tooth of FIG. An explanatory plan view showing a state in which the release of the stop is started, (b) is an explanatory plan view showing a state in which the impact of the pawl by the hook teeth once separated from the pawl after the stop is released, (C) is an explanatory plan view showing a state in which the impact of the pawl is proceeding, and the rocking corner of the escape tooth is moved partway along the impact surface of the pawl, (D) is an explanatory plan view showing a state in which the impact of the incisor by the hook teeth is in progress and the locking corner of the hook teeth has moved along the impact surface of the hook to the leaving corner. (E) Plane explanatory drawing which showed the state of impact surface replacement. The graph which showed typically the change of torque ratio (DELTA) T with respect to the balance rotation angle (theta) regarding the nail | claw in the ankle of the conventional ankle escapement provided with the conventional escape tooth of FIG.

  A preferred embodiment of the present invention will be described based on a preferred embodiment shown in the accompanying drawings.

  FIG. 1 shows an anchor escapement 3 according to a preferred embodiment of the present invention having a escape wheel 2 according to a preferred embodiment of the present invention provided with a escape tooth 1 according to a preferred embodiment of the present invention. A movement 300 of a preferred embodiment of the invention having a mechanical watch 4 is shown. The escape wheel 2 can be rotated in the directions of C1 and C2 around the central axis C, and transmits the torque of the mainspring (not shown). In the ankle escapement 3, 70 is an ankle and 80 is a balance. The balance with hairspring 81 can reciprocate in the directions of A1 and A2 around the central axis A under the action of the hairspring 81, receives the torque from the ankle 70 at the oscillating stone 82, and acts on the ankle 70. The ankle 70 can be rotated in the directions of B1 and B2 around the central axis B of the ankle shaft 71. The ankle 70 transmits and receives torque with the pallet stone 82 at the lever tip 72, and at the entrance pawl 73 and the exit pawl 74, cancer. By intermittently restricting the rotation of the wheel 2 in the C1 direction, the torque of the mainspring is transmitted to the balance 80 little by little. An example of the movement 300 (driving body) is a portion obtained by removing a so-called exterior portion (case 400, hour hand (not shown), etc.) from the mechanical timepiece 4, and moves the main spring (not shown) and hands of the power source. Drive gear (cylinder wheel (not shown), etc.), etc., including an ankle escapement 3 (speed control / escape mechanism) that controls the rotational speed of the gear, a manual winding mechanism (not shown), etc. It can be distributed by itself.

  In each escape tooth 1 of the escape wheel 2, as shown in FIG. 2, the rocking corner 30 between the stop surface 10 and the impact surface 20 has a first curved convex surface portion 31 that is smoothly curved. It is. More specifically, in this example, the first curved convex surface portion 31 is an arc surface 32 having a radius R1, and the end edge portion 33 on the stop surface 10 side of the first curved convex surface portion 31 is the stop surface 10. Is connected continuously and smoothly. Further, the edge 34 on the impact surface 20 side of the first curved convex surface portion 31 is continuously and smoothly connected to the impact surface 20.

  In the escape tooth 1 of FIG. 2, the impact surface 20 is also in the form of a second curved convex surface portion 21 that is smoothly curved. More specifically, in this example, the second curved convex surface portion 21 is an arc surface 22 having a radius R <b> 2, and the end edge portion 23 on the locking corner 30 side of the second curved convex surface portion 21 is the rocking corner 30. Are connected continuously and smoothly to the adjacent edge portion 34 of the first curved convex surface portion 31. In addition, the end edge 24 on the opposite side of the second curved convex surface portion 21 extends to a leaving corner or impulse beak 40.

  Here, when the diameter of the escape wheel 2 is about 4.85 mm, the radius (curvature radius) R1 of the arc surface 32 of the first curved convex surface portion 31 forming the rocking corner 30 is 0.01 mm to 0.00 mm. The radius (curvature radius) R2 of the arc surface 22 of the second curved convex surface portion 21 that forms the impact surface 20 is preferably about 0.4 mm to 0.6 mm.

  When R1 is within the above range, the advantages of the first curved convex surface portion of the rocking corner can be obtained effectively.

  If the radius of curvature R1 is too small (smaller than the lower limit value), the first curved convex surface portion of the locking corner of the hook tooth is practically not equal, and in fact, conventional Since the corner has an angular apex such as a tooth locking corner, the advantage of having the first curved convex surface is almost lost. On the other hand, when the radius of curvature R1 is too large (when it is larger than the upper limit value), there is a possibility that it is difficult to properly engage the pallet of the ankle (stopping the bulge).

  Moreover, when R2 exists in said range, the advantage of the 2nd curved convex part of an impact surface is obtained effectively.

  If the radius of curvature R2 is too small (smaller than the lower limit value), the direction of the force applied by the impact surface of the hook teeth after the impact surface change to the leaving corner of the pawl of the ankle will change abruptly. There is a possibility that the increase in the amount becomes too large. On the other hand, when the radius of curvature R2 is too large (when it is larger than the upper limit), the second curved convex surface portion of the impact surface of the escape tooth becomes practically equal to that of the conventional escape. Since it becomes flat like the impact surface of the tooth (straight when viewed from the side), the advantage of having the second curved convex surface is almost lost.

  The interaction between the escape tooth 1 of the escape wheel 2 configured as described above and the pawl 73 of the ankle 70 is the first curved convex surface portion 31 with the outer diameter of the escape wheel 2 being 4.85 mm. In addition to FIG. 1 and FIG. 2, the curvature radius R1 of the arc surface 32 is 0.02 mm and the curvature radius R2 of the arc surface 22 of the second curved convex surface portion 21 is 0.5 mm. (A) to (f) and FIG. 3 (a) to 3 (f) and the like, the pawl 73 has a stop surface 75, an impact surface 76, a rocking corner 77, and a leaving corner or impulse beak 78. The stop surface 75 and the impact surface 76 are flat surfaces, and are linear when shown in front explanatory views such as (a) to (f) of FIG. The rocking corner 77 and the leaving corner 78 are corner portions where the plane and the plane intersect, respectively, and actually have vertices 77a and 78a. FIG. 4 shows the torque through the hook of the ankle between the escape wheel and the balance with respect to the rotation angle θ of the balance (the neutral position where the balance spring has no elastic strain in the reciprocating rotation direction is set to θ = 0). The balance between the balance rotation angle θ and the torque ratio ΔT in the ankle escapement 3 provided with the escapement 1 and the ankle 70 is shown by a thick solid line J1. The broken line PJ1 represents the balance between the balance rotation angle θ and the torque ratio ΔT in the conventional ankle escapement including the conventional escapement 102 and the ankle 201 shown in FIGS. Represents a relationship.

  In FIG. 3A, the locking pawl 73 is locked at the end 33 on the stop surface 10 side of the first curved convex surface portion 31 where the escape tooth 1 is the end of the stop surface 10 and forms the rocking corner 30. A state S <b> 1 that is engaged or abutted with the apex 77 a of the corner 77 is shown.

  Before entering this state S1, the escape tooth 1 is in contact with the stop surface 75 of the pawl 73 at the stop surface 10 and is rotated in the B1 direction by the calculus 82 rotating in the A1 direction. The ankle 70 is pushed by the stop surface 75 of the pawl 73 against the stop surface 10 of the escape tooth 1 against B1 and pushes the escape tooth 1 back in the C2 direction for a short time. This state Sa is the state indicated by the symbol Sa in FIG.

  A state S1 in FIG. 3A is a state indicated by reference numeral S1 in FIG. After this state S <b> 1, the portion of the escape tooth 1 that comes into contact with the apex 77 a of the locking corner 77 of the pawl 73 as the pawl 73 rotates in the B <b> 1 direction smoothly along the first curved convex surface portion 31. And gradually approaches the impact surface 20.

  Therefore, as shown in FIG. 3B, the direction in which the ankle 70 pushes the escape tooth 1 at the vertex 77 a of the locking corner 77 of the pawl 73, in other words, the contact of the escape tooth 1. The direction of the force applied to the apex 77a of the locking corner 77 of the pawl 73 from the surface portion gradually changes, and the escape tooth 1 pushed by the pawl 73 moves away from the pawl 73 in the C2 direction ((b) of FIG. 3). And state S2) of FIG. When the first curved convex surface portion 31 is in contact with the apex 77a of the locking corner 77 of the pawl 73, the direction F is perpendicular to the tangential plane at the contact portion of the first curved convex surface portion 31 (orientation in the state S1). In F1 and state S2, a force in the direction F2) is applied.

  Note that the rotation angle in the B1 direction of the fitting pawl 73 and the ankle 70 provided with the pawl 73 in the state S2 shown in FIG. 3B is the same as that of the conventional ankle 201 shown in FIG. The apex of the locking corner 230 of the pawl 202 and the apex of the locking corner 130 of the conventional escape tooth 102 are engaged with each other, and the ankle 201 in the PW1 direction in the state where the escape tooth 102 is separated from the entrance pawl 202 (PS1). Smaller than rotation angle. That is, the escape wheel 2 provided with the escape tooth 1 can be seen from the comparison between the state S2 and the state PS1 in FIG. The pawl 73 can be separated with a relatively small acceleration state.

  As shown in the state S3 in FIG. 3C and FIG. 4, the escape tooth 1 once separated from the pawl 73 due to the inertia in the C2 direction is immediately (short blank period) under the action of torque from the mainspring. After the rotation of the first curved convex surface portion 31 forming the rocking corner 30 after returning to the C1 direction rotation, the edge 34 connected to the impact surface 20, that is, the portion 23 connected to the first curved convex surface portion 31 of the impact surface 20 is entered. The impact surface 76 of the pawl 73 hits a portion 75 a in the vicinity of the rocking corner 77. Therefore, the impact surface 76 of the pawl 73 can be used effectively.

  In the escape tooth 1, because of the presence of the first curved convex surface portion 31, the balance 80 is away from the pawl 73 while the rotation speed of the balance 80 is small in the state S <b> 2. Compared with the conventional escape tooth 102, Torque can be applied to the balance with hairs 80 through the pawl 73 (ankle 70) by contacting the impact surface 76 of the pawl 73 at a portion 75a closer to the locking corner 75 of the pawl 73 earlier.

  3 (c) to FIG. 3 (d) and 3 (e) and FIG. 4, as shown by the states S4 and S5, after this, depending on the rotation of the escape tooth 1 in the C1 direction, Of the first curved convex surface portion 31 of the locking corner 30 of the tooth 1, the edge 34 on the impact surface 20 side (the edge 23 on the first curved convex surface portion 31 side of the impact surface 20) contacts the impact surface 76 of the fitting 73. While the contacting portion moves in the E1 direction, the escape tooth 1 continues to apply torque to the impact surface 76 of the pawl 73 at the end edge 34 of the first curved convex surface portion 31. In this stage, the edge 34 on the impact surface 20 side of the first curved convex surface portion 31 of the locking corner 30 of the escape tooth 1 reaches the impulse corner at the end of the impact surface 76 of the pawl 73. It continues until.

  Between the above states S3 to S5, the escape tooth 1 is in contact with the impact surface 76 of the fitting pawl 73 at the edge 34 on the impact surface 20 side of the first curved convex surface portion 31 of the rocking corner 30. A force is applied in the direction F (direction F3 in state S3, direction F4 in state S4, direction F5 in state S5) perpendicular to the impact surface 76. The direction F3, F4, F5 of this force is generally constant in the direction perpendicular to the impact surface 76 of the pawl 73, so that the escape tooth 1 is applied to the pawl 73 as shown in FIG. Torque can be kept approximately constant.

  When the escape wheel 2 further rotates in the C1 direction, the edge 34 on the impact surface 20 side of the first curved convex surface portion 31 of the locking corner 30 of the escape tooth 1 contacts the impact surface 76 of the fitting 73. The state (S 3, S 4, S 5) is shifted to a state (S 6) in which the leaving corner (impulse beak) 77 of the pawl 73 contacts the impact surface 20 of the escape tooth 1. That is, an impact surface change state S6 in which the impact surface related to torque transmission moves from the impact surface 76 of the pawl 73 to the impact surface 20 of the escape tooth 1 is obtained.

  In this impact surface change S6, as shown in FIG. 3 (f), the direction of the force 1 applied by the escape tooth 1 to the pawl 73, that is, the direction F perpendicular to the tangential plane of the contact surface is shown. 3 (e), the direction F5 indicated by the imaginary line in the state S5 (direction perpendicular to the impact surface 76 of the pawl 73 in the state S5) to the direction F6 indicated by the solid line (connected to the edge 34 of the locking corner 30 or (The direction perpendicular to the tangent plane of the edge 23 of the overlapping impact surface 20). A first curved convex surface portion 31 in the form of an arc surface 32 is formed at the rocking corner 30 of the escape tooth 1 of the escape wheel 2, and this impact surface replacement is performed by the edge 34 of the curved convex surface portion 31 and Since this occurs at the edge 23 of the impact surface 20 adjacent to or overlapping with this, the change from the direction F5 to the direction F6 is extremely small. Therefore, in this impact surface replacement state S6, torque fluctuations applied from the escape wheel 2 to the balance 80 via the ankle 70 can be minimized, and torque transmission loss can be minimized. That is, since the risk of the escape tooth 1 and the pawl 73 being separated or the risk of the change due to the torque fluctuation in the impact surface replacement state S6 can be minimized, torque transmission can be effectively performed.

  In addition, as shown by the broken line state PS5 in FIG. 4 and shown in FIG. 9 (e), in the case of an ankle escapement made up of a conventional escape tooth and ankle, the corner of the escape tooth 102 is sharp. In the state PS5 in which the locking corner 130 and the leaving corner 240 with the sharp corners of the pawl 202 are in contact with each other, the impact surface is changed, and the direction of the torque instantaneously fluctuates relatively greatly. Therefore, torque fluctuation is large, and there is a possibility that the torque transmission efficiency may decrease due to the temporary movement of the escape tooth 1 from the pawl 73 or the like. The impact surface change in this state PS5 occurs because the rotation angle of the pawl 73 is smaller than the rotation angle of the pawl 73 in the state S5.

  After the state S6 of FIG. 3 (f), the apex 78a of the leaving corner 78 of the pawl 73 is moved along the impact surface 20 of the escape tooth 1 in the H direction (see FIG. 3 (f) and move to the state S6a (see FIG. 4). In this state S6a, while the apex 78a of the leaving corner 78 is in contact with the second curved convex surface portion 21 constituting the impact surface 20, the orientation is perpendicular to the tangential plane of the contact portion of the second curved convex surface portion 21. Power works. During this state S6a, the torque slightly increases as the balance 80 rotates.

  In the above description, transmission of torque via the entry pawl 73 in the ankle escapement 3 has been described, but the same applies to the exit pawl 74.

  That is, FIG. 5 shows the torque input / output (balance of balance / gull torque) ΔT through the union of the ankle between the escape wheel and the balance with respect to the rotation angle θ of the balance with a thick broken line J 2, The relationship between the balance rotation angle θ and the torque ratio ΔT in the ankle escapement 3 provided with the toothpaste 1 and the ankle 70 is shown, and the thin broken line PJ2 is provided with the conventional escape tooth 102 and the ankle 201. The relationship between the balance rotation angle θ and the torque ratio ΔT in the conventional ankle escapement is shown.

  When the outer diameter of the escape wheel 2 is 4.85 mm and R1 = 0.02 mm and R2 = 0.5 mm, the difference between the thick broken line J2 and the thin broken line PJ2 is the difference between the solid line J1 and the broken line PJ1 in FIG. The description that is generally consistent with the difference and described with respect to the entry pawl 73 also applies to the exit pawl 74.

  In the anchor escapement 3 having the escape wheel 2 having the escape tooth 1 as described above, the torque transmission efficiency can be increased by about 3%. Such escape teeth 1 can be formed by utilizing a microfabrication technology (for example, MEMS or other microfabrication technology) to which semiconductor integrated circuit technology is applied, as described in, for example, Japanese Patent Application Laid-Open No. 2010-91544.

  In the above description, the example in which the second curved convex surface portion is formed over the entire impact surface of the escape tooth is described. However, the escape tooth 1A of the escape wheel 2A has an impact as shown in FIG. Of the surface 20A, the second curved convex surface portion 21A extends from a region 23A directly connected to the edge portion 34A of the arc portion 32 of the first curved convex surface portion 31 of the rocking corner 30 to about half of the impact surface 20A. And a linear portion (planar portion) 28 in a region or portion 27 from the end 26 of the portion 25 (that is, the end edge portion 26 of the second curved convex surface portion 21A) to the reeving corner 40A of the escape tooth 1A. You may have. The ratio between the portion (region) 25 and the portion (region) 27 is typically about 1: 1, but the second curved convex surface portion 21A may be longer than the linear portion 28, but vice versa. In addition, the linear portion 28 may be longer than the second curved convex surface portion 21A.

  Of the elements of the escape wheel 2A of FIG. 6, the same elements as those of the escape wheel 2 of FIG. 2 are denoted by the same reference numerals, and corresponding but different elements have the same reference numerals. Subscript A is added later.

  Even in this case, when the outer diameter of the escape wheel 2A is about 4.85 mm, the radius of curvature R1 of the arc portion 32 of the first curved convex surface portion 31 is preferably 0.01 to 0.05 mm. It is preferable that the radius of curvature R2 of the arc portion 22A of the two curved convex surface portions 21A is 0.2 to 0.5 mm. The reason why the radius of curvature R2 of the arc portion 22A of the second curved convex surface portion 21A is set to be slightly smaller than the radius of curvature R2 of the arc portion 22 of the first curved convex surface portion 21 is because the extension range is short. This is to make the change in direction larger.

  In FIG. 7, in the escape wheel 2A, the curvature radius R1 of the arc portion 32 of the first curved convex surface portion 31 of the escape tooth 1A is 0.04 mm, and the curvature radius of the arc portion 22A of the second curved convex surface portion 21A. In the case where R2 is 0.34 mm, the torque ratio ΔT with respect to the rotation angle θ of the balance is indicated by the solid line J1A and the broken line J2A for the input pawl 73 and the output pawl 74, respectively.

  Specifically, the engagement pawl 73 will be described as an example. Also in this case, the first curved convex surface portion 31 in the form of the arc portion 32 is provided in the rocking corner 30 of the escape tooth 1A, so that the states S1A, S2A, S3A. As can be seen from the change in the torque ratio ΔT, the change in force at the start of impact from the stop state becomes continuous, so that the jump between the escape tooth 1A and the pawl 73 can be minimized. obtain.

  In the case of the escape tooth 2A, the radius of curvature R1 of the arc portion 32 of the first curved convex surface portion 31 is 0.04 mm, and the arc portion 32 of the first curved convex surface portion 31 of the escape tooth 2 Since the radius of curvature R1 is larger than 0.02 mm, there is a long inclined portion S3a after the state S3, and the change in force after the start of impact is smoother.

  Further, as can be seen from the change in the torque ratio ΔT in the states S5A and S6A, the change in the direction of the force when changing the impact surface can be suppressed, so that the jump between the escape tooth 1A and the pawl 73 can be prevented. Can be kept to a minimum.

  Further, in this case, after the impact surface is changed, after the state S6a in which the leaving corner of the pawl 73 receives torque from a portion (region) 25 of the arc portion 22A of the second curved convex surface portion 21A having the curvature radius R2, Since the state changes to the state S7 in which the torque is received from the linear portion 28 extending from the end portion 26 to the end portion 24A located at the leaving corner 40A in the impact surface 20A of the toothpick 1A, the torque ratio is increased as the balance rotation angle θ increases. ΔT begins to decrease.

  Note that the case of the protruding pawl 74 indicated by the broken line J2A is substantially the same as the case of the pawl 73 indicated by the solid line J1A, and the description thereof is omitted.

  In the above description, the example in which the first curved convex surface portion 31 of the rocking corner 30 of the escape tooth 1, 1 </ b> A is composed of the single circular arc surface 32 has been described. As long as it is smoothly curved outward and convex between the edges 34 and 34A, the radius of curvature is not limited even if it is composed of a plurality of regions having different curvature radii between the edge 33 and the edges 34 and 34A. It may vary continuously. The same applies to the second curved convex surface portions 21 and 21A of the impact surfaces 20 and 20A.

  In the above description, an example in which the locking corners of the entry pawl 73 and the exit pawl 74 are angular and have apexes has been described. A curved convex surface portion such as the curved convex surface portion 31 may be formed. Here, the curved convex surface portion is typically an arc surface.

1, 1A escape teeth 2, 2A escape wheel 3 ankle escapement 4 mechanical timepiece 10 stop surface 20 impact surface 21, 21A second curved convex surface portions 22, 22A arcuate surfaces 23, 23A end edge 24 end Edge 25 part (area)
26 End (edge)
27 part (area)
28 Linear portion 30 Rocking corner 31 First curved convex surface portion 32 Arc surface 33 End edge portions 34, 34A End edge portions 40, 40A Relief corner (impulse beak)
70 Ankle 71 Ankle shaft 72 Scale point 73 Inlet pawl 74 Out pawl 75 Stop surface 75a Site 76 Impact surface 77 Rocking corner 77a Vertex 78 Reeve corner (impulse beak)
78a Vertex 80 Balance 82 Rolling stone 300 Movement 400 Case A, B, C Center axis A1, A2, B1, B2, C1, C2 Rotation (rotation) direction E1, H1 Movement direction F, F1, F2, F3, F4 F5, F6 Force direction J1, J1A Incoming θ-ΔT curve J2, J2A Outgoing θ-ΔT curve R1 Curvature radius of curvature R2 of the first curved convex surface of the locking corner of the escape tooth R2 Curvature radius S1, S1A, S2, S2A, S3, S3a, S3A, S4, S4A, S5, S5A, S6, S6A, S6a, S6aA, S7, Sa, of the second curved convex surface portion of the tooth impact surface State θ Balance rotation angle ΔT Torque ratio

Claims (13)

  The escape tooth which is the form of the 1st curve convex surface part where the rocking corner which connects a stop surface and an impact surface curved.   The escapement tooth according to claim 1, wherein a curved second convex surface portion is provided at a portion of the impact surface that continues to the first curved convex surface portion of the rocking corner.   The escapement tooth according to claim 2, wherein the second curved convex surface portion extends over the entire impact surface.   The escape tooth according to claim 2, wherein the radius of curvature of the portion of the second curved convex surface portion is larger as the portion of the impact surface is farther from the rocking corner.   The escape tooth according to claim 3 or 4, wherein the radius of curvature R2 of the second curved convex surface portion is 0.4 to 0.6 mm when the diameter of the escape wheel is 4.85 mm.   3. The escapement tooth according to claim 2, wherein a portion of the impact surface following the second curved convex surface portion is planar.   The escape tooth according to claim 6, wherein a radius of curvature R2 of the second curved convex surface portion is 0.2 to 0.5 mm when the diameter of the escape wheel is 4.85 mm.   The curvature radius R1 of said 1st curve convex surface part is 0.01-0.05mm when the diameter of said escape wheel is 4.85mm, The statement as described in any one of Claim 1-7 Stubborn teeth. A escape wheel provided with the escape tooth according to any one of claims 1 to 8. The escape wheel according to claim 9,
An ankle that transmits and receives torque from the escape wheel and intermittently regulates the rotation of the escape wheel and transmits the torque of the mainspring to the balance.
With the balance that receives torque from the ankle and acts on the ankle,
Ankle escapement.   A movement comprising the ankle escapement according to claim 10.   A mechanical timepiece having the escape wheel according to claim 11 and a case containing the movement. A torque transmission method for transmitting torque from an escape wheel provided with escape teeth in the form of a first curved convex surface with a curved rocking corner connecting the stop surface and an impact surface to an ankle pawl,
With the rotation of the escape wheel, when the impact surface is brought into contact with the nail of the ankle to transmit the torque,
By moving the ankle pawl along the first curved portion toward the impact surface, the torque is transmitted while suppressing changes or fluctuations in the direction of the force applied to the pawl of the ankle by the escape tooth. A torque transmission method characterized by:

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