• 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:
    An exhaust tooth capable of effectively transmitting torque upon the change of a pulse surface, an escape wheel including the exhaust tooth, an anchor escapement including the escape wheel, a movement including the escape wheel and a mechanical timepiece and a torque transmission method are provided. In an exhaust tooth (1) of an escape wheel (2) of an anchor escapement of a mechanical timepiece, a rest nozzle (30) which connects a resting surface (10) and a pulse surface (20) has the curved shape of a convex curved surface portion (31). This convex curved surface portion (31) may be a first convex curved surface portion (31) and, in the impulse surface (20), there may be a second convex curved surface portion (21), which is curve and which is continuous with the first convex curved surface portion (31) of the quill (30). The second convex curved surface portion (21) may extend over the entire impulse surface (20). In the impulse surface (20), the portion which is continuous with the portion of the second convex curved surface portion (21) may be flat.
    公开号:CH706224B1
    申请号:CH00519/13
    申请日:2013-02-28
    公开日:2017-10-13
    发明作者:Suzuki Shigeo
    申请人:Seiko Instr Inc；
    IPC主号:
    专利说明:

    Description
    BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to an exhaust tooth, an escape wheel including the exhaust tooth, an anchor escapement including the wheel of the invention. exhaust, a movement including the exhaust, a mechanical timepiece, and a torque transmission method. 2. Description of the Prior Art [0002] In an anchor escapement of a mechanical timepiece, with respect to an entry pallet or an exit pallet of an anchor, an exhaust tooth of an escape wheel repeats (1) a stop (lock) operation, (2) a release operation, (3) a pulse apply operation, and (4) a hold operation up to what a sprung balance sprocket pin has returned to the location that applies a pulse to (the entry pallet or the output pallet of) the anchor again, and the exhaust tooth intermittently applies a torque or the energy of a mainspring, to the sprung balance.
    In the foregoing, it is preferable that the application of torque or the supply of rotational energy of the escapement wheel to the sprung balance is actually made between the escape wheel and the sprung balance, since (2) the release operation to (3) the end of pulse operation.
    However, in an anchor escapement, in an exhaust wheel commonly used (for example, JP-A-2009-288 083 (patent document 1)), the inventors have found it difficult to perform actually the application of torque or the supply of rotational energy.
    As shown in FIG. 8, each exhaust tooth 102 of an escape wheel 101 commonly used in an anchor escapement includes a linear rest surface, i.e., a planar rest surface 110, a linear pulse surface , i.e., a planar impulse surface 120 which forms an angle α with respect to the rest surface 110, and a through portion of the rest surface 110 and the impulse surface 120 is that is, a quill which is a corner 130 having the angle α (a predetermined obtuse angle).
    Meanwhile, for example as shown with respect to an entry pallet 202 in drawing (a) and the others of FIG. 9, in general, the entry pallet 202 or the exit pallet of an anchor 201 also likewise includes a linear rest surface, i.e., a plane rest surface 210, and a surface linear pulse, i.e., a planar impulse surface 220 which forms an angle β with respect to the resting surface 210, and a resting spout of the resting surface 210 and the surface of pulse 220 and forming a wedge 230 which has the angle β (a predetermined obtuse angle), and at the other end of the pulse surface 220, also substantially forms a wedge 240 which has an angle γ.
    Accordingly, schematically, the application and the receipt of torque or energy between the escape wheel 101 and the sprung balance are as shown in drawings (a) to (e) of FIGS. 9 and 10.
    In the escape wheel 101 in which the exhaust tooth 102 engages with the rest surface 210 of the entry pallet 202 of the anchor 201 using the rest surface 110 and is stopped, the anchor 201 is biased in a direction C2 by a rotating force in a direction PW1 that the anchor 201 receives from the sprung pin of the sprung balance, immediately before the release of the pulse, as shown in drawing (a) of fig. 9, the exhaust tooth 102 reaches a state PS1 in which the exhaust tooth 102 receives a release force through the stopper 230 at the rest surface 210 of the entry pallet 202 of the anchor 201 in the vicinity of the spout 130 in the resting surface 110.
    Immediately after this, the exhaust tooth 102 is separated in the direction C2 from the input pallet 202 by inertia of the escape wheel 101 temporarily, subsequently, immediately, the exhaust tooth is driven in rotation in a direction C1 by the action of the torque in the direction C1 by a wheel train with manual movement from the mainspring, is positioned at a portion PP2 which deviates by a predetermined length ALP1 from the stopper 230 in the impulse surface 220 of the entry pallet 202 in the stopper 130, applies the force of a direction PF2 perpendicular to the impulse surface 220 of the entry pallet 202 relative to the entry pallet 202 to turn the anchor 201 in the direction PW1, and starts applying torque to the sprung balance by the anchor 201 (a state PS2 of the drawing (b) of Fig. 9).
    Here, when the exhaust tooth 102 hits the impulse surface 220 of the anchor 201 after the exhaust tooth 102 has left the mouthpiece 230 of the entry pallet 202 of the anchor Temporarily, the force is transmitted to the anchor in a direction which is discontinuous and which is much changed. In this way, the efficiency of energy transmission from the escape wheel 101 to the anchor 201 is decreased, and due to the fact that an empty interval of energy transmission with respect to the anchor 201 occurs by the interval corresponding to the length ALP1 and that the impulse surface 220 of the entry pallet 202 of the anchor is not actually used, the efficiency of the energy transmission of the wheel Exhaust 101 at anchor 201 is decreased.
    According to the rotation in the direction C1 of the escape wheel 101, a portion PP in which the spout 130 of the exhaust tooth 102 of the escape wheel 101 applies a torque to the surface of pulse 220 of the input pallet 202 moves in a direction EP along the pulse surface 220, and the PP reaches an exit corner (pulse tip) 240 represented by a state PS4 in the drawing (d) of fig. 9 by a position PP3 represented by a state PS3 in the drawing (c) of FIG. 9. At this time, a direction PF4, which is a direction of a force that the escape tooth 102 of the escape wheel 101 applies to the impulse surface 220 of the entry pallet 202 of the anchor 201, is a direction perpendicular to the pulse surface 220 in the state S4.
    Then, according to a new rotation in the direction C1 of the escape wheel 101, as shown in the drawing (e) of FIG. 9, instead of pressing the impulse surface 220 of the entry pallet 202 into the stopper 130, the exhaust tooth 102 reaches a PS5 pulse surface change state in which the exhaust tooth 102 of the escape wheel 101 presses the exit corner 240 of the entry pallet 202 in a direction PF5 perpendicular to the impulse surface 120, in the impulse surface 120. When the impulse surface is changed from the impulse surface 220 at the impulse surface 120, the direction of the force of the exhaust tooth 102 applied to the inlet pallet 202 is suddenly changed from the direction PF4 (the direction perpendicular to the surface of pulse 220 of the entry pallet 202) to the direction PF5 (direction perpendicular to the impulse surface 120 of the exhaust tooth 102).
    As a result, it is difficult to effectively effect the torque transmission of the escape wheel 101 to the anchor 201, that is to say the transmission of torque of the escape wheel 101 to the pendulum In other words, for example, due to the fact that the exhaust tooth 102 and the entry pallet 202 are temporarily separated from one another or must be separated. One of the other, and similar at the moment of the change of the impulse surface, there is a problem that it can be difficult to perform torque or energy transmission between the two.
    Subsequently, according to the rotation in the direction C1 of the escape wheel 101, the wedge 240 of the entry pallet 202 performs the transmission of the torque of the escape wheel 101 to the anchor 201 or from the escapement wheel to the sprung balance by the anchor 201 by moving in a direction HP along the impulse surface 120 of the exhaust tooth 102.
    As understood by the foregoing, in the conventional anchor escapement which includes the conventional escape wheel which includes the conventional exhaust tooth, due to the LP1 loss of torque transmission at the time of the change of the impulse surface in the drawing (e) of FIG. 9, the transmission torque loss LP2 until the pulse starts from drawing (a) to drawing (b) of FIG. 9, or the like, there is a concern that it may be difficult to effectively effect torque transmission from the escape wheel 101 to the anchor 201 or from the escapement wheel to the balance sprocket by the anchor 201.
    If a torque ratio ΔΤ (application and reception or entry and exit torque between the escape wheel and the sprung balance) according to the rotation angle Θ of the sprung balance is set to be a relative graph. in case PJ1 of the input pallet and the case PJ2 of the output pallet, this ratio changes as shown in FIG. 10. In the graphics, the transition from state PS1 to state PS2 and transition from state PS4 to state PS5 are where losses LP1 and LP2 occur. What is described above is similarly valid not only for the input palette but also for the output palette.
    Moreover, although the objects are different from each other, the formation of the beak 230 of the input pallet in a convex curved portion or the impulse surface in a concave curved portion is suggested (description of Swiss Patent No. 702,689 (Patent Document 2)).
    However, according to the convex curved portion of the entry pallet revealed in the patent document 2, the sudden change of direction of the force at the moment of the change of the impulse surface described above is not avoided. , and the LP2 loss of torque transmission is not improved. SUMMARY OF THE INVENTION [0019] The present invention is made with regard to the problems described above, and an object of this invention is to provide an exhaust tooth capable of effectively effecting torque transmission at the time of the change of torque. a pulse surface, an escape wheel including the exhaust tooth, an anchor escapement including the escape wheel, a movement including the exhaust tooth, a mechanical timepiece, and a method of torque transmission.
    To achieve this purpose, in an exhaust tooth of the present invention, a quill, which connects a resting surface and a pulse surface, has the curved shape of a convex curved surface portion.
    In the exhaust tooth of the present invention, since "the quill, which connects the resting surface and the impulse surface, has the curved shape of a convex curved surface portion", when the impulse surface is changed from a state where the exhaust tooth presses the impulse surface of a pallet (an entry pallet or an exit pallet) of an anchor using the quill to a state where the exhaust tooth presses an exit wedge (a pulse nozzle) from the pallet of the anchor using the impulse surface (more specifically, a portion which is connected to the quill in the impulse surface of the exhaust tooth (in other words, a part which is connected to the impulse surface in the mouthpiece of the shape of the first convex curved surface part of the exhaust tooth)), a change extreme in the direction of the force that the exhaust tooth app that at the pallet of the anchor is avoided, the direction of the force is not changed, the change can be suppressed to be minimal, and therefore, the torque transmission with respect to the pallet of the anchor can be carried out effectively.
    Moreover, in the exhaust tooth of the present invention, since "the quill which connects the resting surface and the impulse surface has the curved shape of a convex curved surface portion", at the time of disengagement, the convex curved surface portion which forms the quill of the exhaust tooth can approximately make continuous contact with the impulse surface from the resting surface of the pallet of the anchor, and thus, from the early impulse clearance, an empty gap, in which the exhaust tooth is separated from the pallet of the anchor and a torque is not provided, can be suppressed to be minimal, and the impulse surface of the pallet of the anchor can be used effectively. As a result, a torque can be effectively transmitted to the pallet of the anchor. Moreover, since the change affecting the direction of the force at the moment of impulse start after clearance is also removed to be relatively small, a torque can be effectively transmitted to the pallet of the anchor from the exhaust tooth .
    In the exhaust tooth, the convex curved surface portion at the quill may be a convex curved surface first portion, and the exhaust tooth may comprise a second convex curved surface portion, and the Impulse surface may include that second convex curved surface portion which is continuous with the first convex curved surface portion.
    When this is the case, after the change of the impulse surface, since the direction of the part that bears against the exit corner of the pallet of the anchor in the impulse surface of the tooth of exhaust is changed to the direction which is separated from the axis of rotational center of the anchor according to the curve of the second convex curved surface portion, a decrease in torque that is applied from the exhaust tooth is suppressed, or the torque is increased in response to rotation of the exhaust tooth. As a result, a torque can be effectively transmitted to the pallet of the anchor. Further, as long as the first convex curved surface portion and the second convex curved surface portion are substantially connectable, a linear (planar) portion may be interposed between the first convex curved surface portion and the second curved surface portion. convex even if the part is relatively short.
    In the exhaust tooth of the present invention, the second convex curved surface portion may extend over the entire impulse surface.
    When this is the case, the torque that is applied from the escapement wheel to the balance-spring by the anchor can be increased with a passage of time through the entire interval of the pulse after the start of the pulse.
    The exhaust tooth of the present invention may be according to the appended claim 4.
    When this is the case, the torque that is applied from the escapement wheel to the sprung balance by the anchor can be gradually decreased in the step at the end of the pulse.
    In an escape wheel comprising the exhaust tooth of the invention, in the case where the second convex curved surface portion is formed over the entire impulse surface, the radius of curvature R2 of the second part convex curved surface can be 0.4 to 0.6 mm when the diameter of the escape wheel is 4.85 mm.
    When this is the case, the advantages of the second convex curved surface portion of the impulse surface can be effectively obtained. In addition, when the radius of curvature R2 is too small (when R2 is smaller than the lower limit), since the direction of the force of the pulse surface of the exhaust tooth, after the change of the surface impulse that is applied to the exit corner of the pallet of the anchor, is suddenly changed, there is a problem that is that the increase in torque may be too great. On the other hand, when the radius of curvature R2 is too large (when R2 is larger than the higher limit), since it is the same as a case where the second convex curved surface part of the surface of Exhaust tooth impulse is practically not present, practically, the impulse surface is flat (linear when viewed from the side) as the impulse surface of the conventional exhaust tooth, and therefore most of the benefits due to the presence of the second convex curved surface portion are lost.
    In the exhaust tooth of the present invention, the impulse surface may comprise a portion which is planar and which is continuous with the second convex curved surface portion.
    When this is the case, the torque that is applied from the escapement wheel to the spring balance by the anchor can be approximately linearly reduced in the step at the end of the rear pulse.
    In an escape wheel comprising the exhaust tooth of the present invention, in the case where the impulse surface comprises a portion which is flat and which is continuous with the second convex curved surface portion, the radius the curvature R2 of the second convex curved surface portion may be 0.2 to 0.5 mm when the diameter of the escape wheel is 4.85 mm.
    Compared to the case where the second convex curved surface portion is present on the entire impulse surface, the reason why the appropriate category of the curvature radius R2 of the second convex curved surface portion is shifted to the short side of R2 is that the extension of the second convex curved surface portion is shortened, and thus, the direction of the surface with the category of the extension is more widely changed.
    In an escape wheel comprising the exhaust tooth of the present invention, the radius of curvature R1 of the curved convex surface portion at the rest nozzle can be 0.01 to 0.05 mm when the diameter of the Exhaust wheel is 4.85 mm.
    When this is the case, the advantages of the first convex curved surface portion of the quiescent nozzle can be effectively obtained. Moreover, when the radius of curvature R1 is too small (when R1 is smaller than a lower limit), since it is the same as the case where the curved convex surface portion at the level of the quiescent beak the exhaust tooth is practically not present, and, practically, the quill becomes a wedge portion that has an angular vertex (or vertex) as the quill of the conventional exhaust tooth, most of the benefits due to the presence of the convex curved surface portion at the beak of rest are lost. On the other hand, when the radius of curvature R1 is too large (when R1 is larger than the upper limit), there is a problem that it may be difficult to appropriately perform the engagement between the corner portion and the output pallet of the anchor (stop of the output pallet).
    To achieve the above purpose, an escape wheel of the present invention comprises an exhaust tooth as defined above.
    In addition, to achieve the above purpose, an anchor escapement of the present invention comprises: an escape wheel as defined above; An anchor arranged to perform a torque reception from the escape wheel and a torque transmission, and to transmit, to a sprung balance, a torque from a motor spring, regulating by intermittently the rotation of the escape wheel; and [0041] the sprung balance arranged to receive the torque from the anchor and to act on the anchor.
    Furthermore, to achieve the above purpose, a movement of the present invention comprises an anchor escapement as defined above.
    In addition, to achieve the above purpose, a mechanical timepiece of the present invention comprises a movement as defined above and a box that houses the movement.
    Furthermore, to achieve the above-mentioned purpose, a torque transmission method of the present invention is a method in which a torque is transmitted to a pallet of an anchor, from an escape wheel which includes a tooth of exhaust in which a quill connecting a resting surface and a pulse surface has the curved shape of a convex curved surface portion. This method comprises the following steps: the escape wheel is released and begins to rotate; then - the impulse surface approaches the pallet by moving the pallet along said convex curved surface portion and by transmitting the torque with a gradual change, i.e. without abrupt change, the direction of the force applied by the exhaust tooth on the pallet; then - the impulse surface presses on the pallet and transmits the torque.
    Brief Description of the Drawings [0045] FIG. 1 is an explanatory plan view of an anchor escapement according to a preferred example of the present invention which includes an escape wheel according to a preferred example of the present invention which includes an exhaust tooth according to a preferred example of the present invention. invention.
    FIG. 2 is an explanatory plan view in which the portion of the exhaust tooth of the preferred example of the present invention of the escape wheel of FIG. 1 is shown enlarged.
    FIG. 3 shows a change affecting the application and reception of the torque between the exhaust tail of the anchor escapement which includes the escape wheel having the exhaust tooth of FIG. 2 and an entry pallet, the drawing (a) is an explanatory plan view showing a state where a clearance begins, the drawing (b) is an explanatory plan view showing a state where a release progresses, the drawing (c ) is an explanatory plan view showing a state where an impulse of the entry pallet due to the escape tooth begins, drawing (d) is a state where the impulse of the entry pallet due to the escape tooth progresses and is an explanatory plan view showing a state where an arc-shaped resting spout of the escape tooth moves in the middle of the impulse surface along the impulse surface from the entry pallet, the drawing (e) is the state where the impulse of the entry pallet due to the exhaust tooth progresses and is an explanatory plan view showing a state where the rest spout arc-shaped of the exhaust tooth moves ve rs an exit corner along the impulse surface of the entry pallet, and the drawing (f) is an explanatory plan view showing a state of impulse surface change.
    FIG. 4 is a graph schematically showing a change in a torque ratio ΔΤ with respect to the rotation angle Θ of a sprung balance linked to the entry pallet of the anchor, and a graph which shows the change compared to to the anchor escapement of fig. 3 and the change from the conventional anchor escapement shown in FIG. 8.
    FIG. 5 is a graph schematically showing a change in a torque ratio ΔΤ with respect to a rotation angle Θ of a sprung balance linked to an output pallet of the anchor, and a graph which represents the change with respect to anchor escapement of FIG. 3 and the change from the conventional anchor escapement shown in FIG. 8.
    FIG. 6 is an explanatory plan view similar to FIG. 2 in which an exhaust tooth according to another preferred example of the present invention is enlarged.
    FIG. 7 is a graph schematically showing the change in the torque ratio ΔΤ with respect to the rotation angle Θ of the sprung balance linked to the entry pallet and the pallet of the anchor in the anchor escapement which includes the exhaust tooth of FIG. 6.
    FIG. 8 is an explanatory plan view of a conventional exhaust tooth of a conventional escapement wheel of a conventional anchor escapement.
    FIG. 9 shows a change affecting the application and receipt of torque between the exhaust tooth of the conventional anchor escapement which includes the conventional exhaust wheel having the conventional exhaust tooth of FIG. 8 and the entry pallet, the drawing (a) is an explanatory plan view showing a state where a clearance begins, the drawing (b) is an explanatory plan view showing a state where the pallet pulse entry due to the separate exhaust tooth of the entry pallet starts temporarily after a clearance, the drawing (c) is a state where the impulse of the entry pallet due to the exhaust tooth progresses and is an explanatory plan view showing a state where the quill of the escape tooth moves towards the middle of the impulse surface along the impulse surface of the inlet pallet, the drawing (d ) is the state where the impulse of the entry pallet due to the exhaust tooth progresses and is an explanatory plan view showing a state where the exhaust mouth of the exhaust tooth is moving towards the corner output along the impulse surface of the input palette, and the drawing (e) is an explanatory plan view showing the pulse surface change state.
    FIG. 10 is a graph schematically showing the change in the torque ratio ΔΤ with respect to the rotation angle Θ of the sprung balance associated with the entry pallet and the pallet of the anchor in the anchor escapement conventional which includes the conventional exhaust tooth of FIG. 8.
    DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS [0055] A preferred embodiment of the present invention will be described based on a preferred example shown in the accompanying drawings.
    Example [0056] FIG. 1 depicts a movement 300 of a preferred example of the present invention which includes an anchor escapement 3 of a preferred example of the present invention which includes an escape wheel 2 of a preferred example of the present invention which includes a 1 of a preferred example of the present invention, and the movement is incorporated in a mechanical timepiece 4. The escape wheel 2 can be rotated in the directions C1 and C2 around a central axis C and transmits the torque of a motor spring (not shown). In the anchor escapement 3, the reference numeral 70 indicates an anchor and the reference numeral 80 indicates a balance-spring. The balance spring 80 can be rotated to rotate alternately in the directions A1 and A2 about a central axis A due to the action of a hairspring 81, and the hairspring receives a torque from the anchor 70 in an impulse pin 82 and act the torque on the anchor 70. The anchor 70 can be rotated in the directions B1 and B2 about a central axis B of an anchor rod 71, performs a applying and receiving torque with the impulse pin 82 using a case tip 72, intermittently regulates rotation in the C1 direction of the escape wheel 2 using an entry pallet 73 and an exit pallet 74, and gradually transmits the torque of the mainspring to the sprung balance 80. An example of the movement 300 (driving body) is a part in which a part called outer part (a case 400 and an hour hand (not shown)) is removed from the room mechanical watchmaking 4, is configured to include a motor spring (not shown) of a power source, a driving wheel (an hour wheel (not shown) and the like) which moves a needle, an anchor escapement 3 (regulator exhaust) which controls the rotational speed of a wheel, a winding mechanism (not shown), or the like, and can be dispensed as a separate body.
    As shown in FIG. 2, in each exhaust tooth 1 of the escape wheel 2, a recess 30 between a rest surface 10 and a pulse surface 20 has the shape of a convex curved surface portion 31, which is a first portion of curved convex surface 31 and which is slightly curved. More specifically, in this example, the first convex curved surface portion 31 is formed by an arcuate surface 32 of radius R1, an edge portion 33 of the resting surface side 10 in the convexly curved first surface portion 31 is connected substantially Continuous and smooth at the rest surface 10. On the other hand, an edge portion 34 of the impulse surface side 20 in the first convex curved surface portion 31 is smoothly and continuously connected to the impulse surface 20.
    In addition, in the exhaust tooth 1 of FIG. 2, the impulse surface 20 also has the shape of a second convex curved surface portion 21 which is smoothly curved. More specifically, in this example, the second convex curved surface portion 21 is formed by an arcuate surface 22 of radius R2, and an edge portion 23 of the nip end 30 in the second convex curved surface portion 21 is connected with continuous and smooth manner at the edge portion 34 near the first convex curved surface portion 31 which forms the mouthpiece 30. Moreover, the edge portion 24 of the opposite side in the second curved convex surface portion 21 s extends to an exit corner or pulse nozzle 40.
    Here, when the diameter of the escape wheel 2 is approximately 4.85 mm, it is preferable that the radius (radius of curvature) R1 of the arcuate surface 32 of the first convex curved surface portion 31 which forms the nib 30 is approximately 0.01 mm to 0.05 mm and the radius (radius of curvature) R2 of the arcuate surface 22 of the second convex curved surface portion 21 which forms the impulse surface 20 is approximately 0.4 mm at 0.6 mm.
    When R1 is in the range defined above, the advantages of the first convex curved surface portion of the quiescent nozzle can be effectively obtained.
    Moreover, when the radius of curvature R1 is too small (when R1 is smaller than a lower limit), since it is the same as in the case where the first part of convex curved surface of the beak rest of the exhaust tooth is practically not present, and, practically, the quill becomes the corner portion that has the angular vertex similar to the quill of the conventional exhaust tooth, most of the benefits due to the presence of the first part of convex curved surface are lost. On the other hand, when the radius of curvature R1 is too large (when R1 is larger than the upper limit), there is a problem that it can be difficult for the engagement between the corner portion and the output pallet of the anchor (stop of the output pallet) is carried out appropriately.
    Furthermore, when R2 is in the range defined above, the advantages of the second convex curved surface portion of the impulse surface can be effectively achieved.
    In addition, when the radius of curvature R2 is too small (when R2 is smaller than the lower limit), since the direction of the force of the pulse surface of the exhaust tooth, after the change of the impulse surface that is applied to the exit corner of the pallet of the anchor, is suddenly changed, there is a problem that the increase in torque may be too great. On the other hand, when the radius of curvature R2 is too large (when R2 is greater than the upper limit), since it is the same as in the case where the second convex curved surface part of the surface of impulse of the exhaust tooth is practically not present, practically, the impulse surface is flat (linear when viewed from the side) similar to the impulse surface of the conventional exhaust tooth, and therefore most of the benefits resulting from the presence of the second convex curved surface portion are lost.
    When the outer diameter of the escape wheel 2 is 4.85 mm, the radius of curvature R1 of the arcuate surface 32 of the first convex curved surface portion 31 is 0.02 mm, and the radius of curvature R2 of the arcuate surface 22 of the second convex curved surface portion 21 is 0.5 mm, the mutual action between the exhaust tooth 1 of the escape wheel 2 and the entry pallet 73 of the anchor 70 configured as described above will be described on the basis of the drawings (a) to (f) of FIGS. 3 and 4 in addition to figs. 1 and 2. In the drawings (a) to (f) of FIG. 3 or the like, the entry pallet 73 includes a resting surface 75, a pulse surface 76, and a rest spout 77, and an exit wedge or spout 78. The rest surface 75 and the impulse surface 76 are planar surfaces and are linear when shown in an explanatory plan view similar to the drawings (a) to (f) of FIG. 3. The spout 77 and exit corner 78 are each a corner portion in which the planar surfaces intersect each other, and have substantially the vertex 77a and 78a. Moreover, fig. 4 shows the input and the output of the torque (a balance ratio of the sprung balance / escapement) ΔΤ by the entry pallet of the anchor between the escape wheel and the sprung balance relative to the angle of rotation Θ of the sprung balance (a neutral position in which an elastic strain in the reciprocity and directions of rotation are not present in the spiral is regarded as Θ = 0), a thick solid line J1 indicates a relationship between the rotation angle Θ of the sprung balance and the torque ratio ΔΤ in the anchor escapement 3 which includes the exhaust tooth 1 and the anchor 70, and a broken line PJ1 indicates a relation between the rotation angle Θ the balance sprocket and the torque ratio ΔΤ in the conventional anchor escapement which includes the conventional exhaust tooth 102 and an anchor 201 shown in the drawings (a) to (e) of FIG. 9.
    In the drawing (a) of FIG. 3, there is shown a state S1 in which the escape tooth 1 engages with or rests against the vertex 77a of the rest mouth 77 of the entry pallet 73 in the edge 33 of the rest surface side 10 of the first convex curved surface portion 31 which forms the recess 30 at the end of the resting surface 10.
    Before it enters the state S1, the exhaust tooth 1 bears against the rest surface 75 of the entry pallet 73 with the rest surface 10, and the anchor 70, which is rotated in the direction B1 by the impulse pin 82 rotated in the direction A1, presses the rest surface 10 of the exhaust tooth 1 in the direction B1 with the rest surface 75 of the entry pallet 73 and press the exhaust tooth 1 in the C2 direction for a short moment only. This state Sa is a state which is indicated by the reference number Sa in FIG. 4.
    The state S1 of the drawing (a) of FIG. 3 is a state which is indicated by reference numeral S1 in FIG. 4. After the state S1, the part of the exhaust tooth 1 which bears against the vertex 77a of the stopper 77 of the entry pallet 73 according to the rotation in the direction B1 of the entry pallet Approach smoothly and gradually the pulse surface 20 along the first convex curved surface portion 31.
    Accordingly, as shown in the drawing (b) of FIG. 3, the direction in which the anchor 70 presses the exhaust tooth 1 by the vertex 77a of the rest nozzle 77 of the entry pallet 73, in other words, the direction of the force that is applied from the the abutment surface of the exhaust tooth 1 at the vertex 77a of the stopper 77 of the entry pallet 73 is gradually changed, the exhaust tooth 1 which is pressed by the entry pallet 73 is separated in the C2 direction from the input pallet 73 (a state S2 of the drawing (b) of Figures 3 and 4). Moreover, when the first convex curved surface portion 31 rests against the vertex 77a of the quill 77 of the entry pallet 73, a force is applied in a direction F (a direction F1 in the state S1 and a direction F2 in the state S2) perpendicular to a tangent plane in the abutting portion of the first convex curved surface portion 31.
    In addition, the angle of rotation in the direction B1 of the entry pallet 73 in the state S2 shown in the drawing (b) of FIG. 3 and the anchor 70 including the entry pallet is smaller than the angle of rotation in the direction PW1 of the anchor 201 in the state (PS1) where the vertex of the beak 230 of the pallet of 202 of the conventional anchor 201 and the nib vertex 130 of the conventional exhaust tooth 102 are engaged and the exhaust tooth 102 is separated from the entry pallet 202 as shown in the drawing (a) of fig. 9. In other words, as understood by the comparison between the state S2 of FIG. 4 and PS1 state, the escape wheel 2 which includes the exhaust tooth 1 can be separated from the entry pallet 73 in a relatively small acceleration state when the rotation angle of the balance-spiral is big (the return of the impulse ankle is small).
    As shown in a state S3 in the drawing (c) of FIGS. 3 and 4, the escape tooth 1, which is separated from the entry pallet 73 temporarily by the inertia in the direction C2, is immediately (after a short empty gap) brought back into the rotation in the direction C1 by the action of the torque from the mainspring and strikes a location 75a in the vicinity of the spout 77 in the impulse surface 76 of the entry pallet 73 by the edge portion 34 which is connected to the impulse surface In the first convex curved surface portion 31 forming the quill 30, i.e. the portion 23 which is connected to the first convex curved surface portion 31 in the impulse surface 20. Accordingly, the impulse surface 76 of the entry pallet 73 can be effectively used.
    In the exhaust tooth 1, due to the presence of the first convex curved surface portion 31, since the exhaust tooth is separated from the input pallet 73 while the rotation speed of the balance- 80 spiral is reduced in the S2 state, at an earlier stage compared to the conventional exhaust tooth 102, that is to say, in the location 75a which is closer to the beak 77 of the pallet d At the entrance 73, the escape tooth 1 bears against the impulse surface 76 of the entry pallet 73 and can apply a torque to the sprung balance 80 by the entry pallet 73 (anchor 70).
    Subsequently, as shown in the states S4 and S5 in the drawing (c) of FIG. 3 and drawings (d) and (e) of FIGS. 3 and 4, according to the rotation in the direction C1 of the escape tooth 1, while the portion, in which the edge 34 (edge portion 23 on the side of the first convex curved surface portion 31 of the surface of pulse 20) on the impulse surface side 20 in the first convex curved surface portion 31 of the quill 30 of the exhaust tooth 1 adjoins the impulse surface 76 of the inlet pallet 73, moves in a direction E1, the exhaust tooth 1 continuously applies a torque to the impulse surface 76 of the entry pallet 73 with the edge 34 of the first convex curved surface portion 31. In addition, this step is continuous towards the high to a state S5 where the edge 34 of the impulse surface side 20 in the first convex curved surface portion 31 of the quill 30 of the exhaust tooth 1 reaches the impulse wedge which is positioned at the end of the impulse surface 76 of the blade head of entry 73.
    From the state S3 to the state S5 described above, the exhaust tooth 1 bears against the impulse surface 76 of the entry pallet 73 with the edge 34 of the surface side of pulse 20 in the first convex curved surface portion 31 of the quiescent nozzle 30, and applies the force in the direction F (a direction F3 in the state S3, a direction F4 in the state S4, and a direction F5 in the state S5) perpendicular to the impulse surface 76. Since the directions F3, F4 and F5 of the force are approximately constant in the direction perpendicular to the impulse surface 76 of the input pallet 73, as shown in FIG. fig. 4, the torque that the exhaust tooth 1 applies to the entry pallet 73 is held to be approximately constant.
    If the escape wheel 2 is rotated further in the direction C1, the state (S3, S4, and S5) where the edge 34 of the impulse surface side 20 in the first convex curved surface portion 31 of the nozzle 30 of the exhaust tooth 1 bears against the impulse surface 76 of the inlet pallet 73 is moved to a state (S6) where the exit corner (impulse nozzle) 77 of the entry pallet 73 presses against the impingement surface 20 of the exhaust tooth 1. In other words, the state becomes a pulse surface change state S6 in which the impulse surface bound the torque transmission moves from the impulse surface 76 of the inlet pallet 73 to the impulse surface 20 of the exhaust tooth 1.
    At the moment of the change of pulse surface S6, as shown in drawing (f) of FIG. 3, the direction of the force which is applied to the entry pallet 73 by the escape tooth 1, that is to say the direction F perpendicular to the tangent plane of the bearing surface is changed from the direction F5 (a direction perpendicular to the impulse surface 76 of the input pallet 73 in the state S5) indicated by an imaginary line in the state S5 of the drawing (e) of FIG. 3, towards the direction F6 (a direction perpendicular to the tangent plane of the edge portion 23 of the impulse surface 20 which is connected to or overlaps the edge 34 of the stopper 30) indicated by a solid line. Since the first convex curved surface portion 31 which has the shape of an arcuate surface 32 is formed on the quill 30 of the exhaust tooth 1 of the escape wheel 2 and the change of impulse surface is generated towards the edge 34 of the convex curved surface portion 31 and the edge portion 23 of the impingement surface 20 which is adjacent to or overlaps the edge 34, the change from the direction F5 to the direction F6 is significantly small. As a result, in the S6 pulse surface change state, the torque change, which is applied from the escapement wheel 2 to the balance spring 80 by the anchor 70, can be suppressed to be minimal, and the loss of torque transmission can be suppressed to be minimal. In other words, since the separation between the exhaust tooth 1 and the entry pallet 73 due to the change affecting a torque at the moment of the S6 pulse surface change state or a problem thereof can be minimized, torque transmission can be effectively performed.
    Moreover, as shown in the drawing (e) of FIG. 9 which is indicated by the state PS5 of the broken line in FIG. 4, in the case of the anchor escapement which is configured of the conventional exhaust tooth and anchor, the change of the impulse surface is generated in the PS5 state in which the pointy resting spout 130 of the Exhaust tooth 102 and the pointed exit corner 240 of the entry pallet 202 press against each other, and the direction of torque is changed relatively momentarily. As a result, the torque is changed a lot, and there is a problem that the torque transmission efficiency can be decreased due to the temporary separation of the exhaust tooth 1 from the entry pallet 73, or similar. On the other hand, the reason for changing the pulse surface of the PS5 state is that the angle of rotation of the input pallet 73 is smaller than the rotation angle of the pallet. input 73 in the case of state S5.
    After the state S6 of the drawing (f) of FIG. 3, it moves to a state S6a (Fig. 4) where the vertex 78a of the exit corner 78 of the entry pallet 73 moves in the direction Fl (see drawing (f) of Fig. 3 and 2 ) along the impulse surface 20 of the exhaust tooth 1 until the vertex is separated from the exhaust tooth 1. In the state S6a, while the vertex 78a of the exit corner 78 presses against the second convex curved surface portion 21 which configures the impulse surface 20, a force acts in the direction perpendicular to the tangent plane of the bearing portion of the second convex curved surface portion 21. During the state S6a , the torque is increased more or less in addition to the rotation of the sprung balance 80.
    In the foregoing, although the transmission of torque through the entry pallet 73 in the anchor escapement 3 is described, the torque transmission in the output pallet 74 is approximately the same as that of the pallet. input.
    More specifically, FIG. 5 shows the entry and the exit of the torque (a ratio of balance-spring / escapement torque) ΔΤ by the pallet of exit of the anchor between the escape wheel and the balance-spiral with respect to the rotation angle Θ of the sprung balance, a thick broken line J2 indicates a relation between the rotation angle Θ of the sprung balance and the torque ratio ΔΤ in the anchor escapement 3 which includes the exhaust tooth 1 and the anchor 70, and a thin broken line PJ2 indicates a relationship between the rotation angle Θ of the balance spring and the torque ratio ΔΤ in the conventional anchor escapement which includes the conventional exhaust tooth 102 and an anchor 201.
    When the outer diameter of the escape wheel 2 is 4.85 mm, R1 = 0.02 mm is satisfied, and R2 = 0.5 mm is satisfied, the difference between the thick interrupted line J2 and the thin interrupted line PJ2 coincides approximately with the difference between the solid line J1 and the broken line PJ1 of FIG. 4, and the description made for the entry pallet 73 is similarly valid for the output pallet 74.
    In the anchor escapement 3 which includes the escape wheel 2 having the exhaust tooth 1 described above, the torque transmission efficiency can be increased by approximately 3%. For example, the exhaust tooth 1 can be formed using excellent process technology (eg, MEMS or other excellent process technologies) to which a semiconductor integrated circuit technology is applied as disclosed in JP. -A-2010-91 544.
    In the foregoing, the example is described in which the second convex curved surface portion is formed over the entire impulse surface of the exhaust tooth. However, as shown in FIG. 6, the exhaust tooth 1A of the escape wheel 2A may include a second convex curved surface portion 21A on the area or portion 25 of the portion 23A directly connected to the edge portion 34A of the arcuate surface 32 from the first convex curved surface portion 31 of the quill 30 in the impulse surface 20A to approximately half of the impulse surface 20A, and may include a linear portion (flat portion) 28 on the zone or portion thereof 27 running from the end 26 of the portion 25 (i.e., the edge portion 26 of the second convex curved surface portion 21 A) to the exit corner 40A of the exhaust tooth 1A Typically, the ratio between the portion (zone) and the portion (zone) 27 is approximately 1: 1. However, the convex curved surface second portion side 21A may be longer than the linear portion 28, and conversely, the linear portion side 28 may be longer than the second convex curved surface portion 21A.
    权利要求:
    Claims (13)
    [1]
    The same reference numbers are attached to the same elements as the elements of the escape wheel 2 of FIG. 2 of the elements of the escape wheel 2A of FIG. 6 and the elements of FIG. 2 correspond to the elements of FIG. 6, and, for items that have differences, a suffix A is added after the same reference numbers. Also in this case, when the outer diameter of the escape wheel 2A is approximately 4.85 mm, it is preferable that the radius of curvature R1 of the arcuate surface 32 of the first convex curved surface portion 31 is 0.01 to 0.05 mm and the radius of curvature R2 of the arcuate surface 22A of the second convex curved surface portion 21A is 0.2 to 0.5 mm. Further, the reason for which the radius of curvature R2 of the arcuate surface 22A of the second convex curved surface portion 21A is set to a category a little smaller than the radius of curvature R2 of the arcuate surface 22 of the first part. Curved convex surface area 31 is to shrink the extension category and enlarge the change in the direction of the surface. In FIG. 7, in the escape wheel 2A, when the radius of curvature R1 of the arcuate surface 32 of the first convex curved surface portion 31 of the escape tooth 1A is 0.04 mm and the radius of curvature R2 of the surface 22A arc of the second convex curved surface portion 21A is 0.34 mm, the torque ratio ΔΤ relative to the rotation angle Θ of the sprung balance is indicated by a solid line J1A and a broken line J2A with respect to each input pallets 73 and exit 74. [0086] If the entry pallet 73 is specifically described as an example, also in this case, since the first convex curved surface portion 31 having the shape of the arcuate surface 32 is present on the spout 30 of the exhaust tooth 1 A, as understood by the change affecting the torque ratios ΔΤ in the states S1 A, S2A and S3A, the change affecting the force at the time of entry of the beginning impulse of the arrested state is continuous, and therefore, a jump between the exhaust tooth 1A and the entry pallet 73 can be suppressed to be minimal. Moreover, in the case of the exhaust tooth 1A, since the radius of curvature R1 of the arcuate surface 32 of the first convex curved surface portion 31 is 0.04 mm and the radius of curvature R1 of the curved surface 32 of the first convex curved surface portion 31 of the exhaust tooth 1 is larger than 0.02 mm, a long inclined portion S3a is present after the state S3, and the change affecting the force after the start of impulse becomes smoother. Moreover, as understood by the change affecting the torque ratio ΔΤ in the states S5A and S6A, since the change affecting the direction of the force at the moment of the change of the impulse surface can be eliminated to be smaller. , the jump between the exhaust tooth 1A and the entry pallet 73 can be eliminated to be minimal. Moreover, in this case, after the change of the impulse surface, since the exit corner of the input pallet 73 is changed from the state S6a in which the corner receives a torque of the part ( zone) having the arcuate surface 22A of the second convex curved surface portion 21A of the radius of curvature R2 at state S7 in which the wedge receives a torque from the linear portion 28 extending from the edge portion 26 into the impingement surface 20A of the exhaust tooth 1A of the end portion 24A positioned in the outlet corner 40A, the torque ratio ΔΤ is decreased according to the increase of the rotation angle Θ of the balance-spiral . Moreover, since the case of the output pallet 74 represented by the interrupted line J2A is also approximately similar to the case of the entry pallet 73 represented by the solid line J1A, the descriptions of this are omitted. In the foregoing, is described the example in which the first convex curved surface portion 31 of the nozzle 30 of the exhaust teeth 1 and 1A has the only arcuate surface 32. However, as long as the first convex curved surface portion 31 is smoothly curved to be externally convex between edge 33 and edges 34 and 34A, a plurality of areas in which the radii of curvature are different from another may be formed or the radii of curvature can be changed continuously between the edge 33 and the edges 34 and 34A. The second convex curved surface portions 21 and 21A of the impulse surfaces 20 and 20A are also similar. In the foregoing, the example in which the quill of the input pallet 73 or the output pallet 74 has the angular vertex is described. However, if desired, a convex curved surface portion such as the convex curved surface portion 31 of the escape teeth 1 and 1A may be formed on the quill of the entry pallet 73 or the exit pallet Here, typically, the convex curved surface portion is formed by an arcuate surface. claims
    1. Exhaust tooth, wherein a quill (30) which connects a resting surface (10) and a pulse surface (20; 20A) has the curved shape of a convex curved surface portion (31; ).
    [2]
    The exhaust tooth according to claim 1, wherein the curved convex surface portion at the quill (30) is a first convex curved surface portion (31), the exhaust tooth comprising a second portion of convex curved surface (21; 21A), the impulse surface (20; 20A) including that second convex curved surface portion (21; 21A) which is continuous with the first convex curved surface portion (31).
    [3]
    The exhaust tooth of claim 2, wherein the second convex curved surface portion (21) extends over the entire impulse surface (20).
    [4]
    The exhaust tooth of claim 2, wherein the radius of curvature (R2) of the second convex curved surface portion is increased in the impulse surface (20A) so as to be larger over an area which is spaced from the spout (30).
    [5]
    The exhaust tooth of claim 2, wherein the impingement surface (20A) comprises a portion which is planar and which is continuous with the second convex curved surface portion (21A).
    [6]
    6. Exhaust wheel comprising an exhaust tooth (1; 1A) according to one of claims 1 to 5.
    [7]
    An exhaust wheel according to claim 6, wherein the exhaust tooth is according to claim 3 or 4, and wherein the radius of curvature (R2) of the second convex curved surface portion (21; 21A) is 0.4 to 0.6 mm when the diameter of the escape wheel (2; 2A) is 4.85 mm.
    [8]
    An exhaust wheel according to claim 6, wherein the exhaust tooth is according to claim 5, and wherein the radius of curvature (R2) of the second convex curved surface portion (21A) is 0.2 to 0.5 mm when the diameter of the escape wheel (2A) is 4.85 mm.
    [9]
    9. Exhaust wheel according to one of claims 6 to 8, wherein the radius of curvature (R1) of the curved convex surface portion (31) at the mouthpiece (30) is 0.01 to 0.05 mm when the diameter of the escape wheel (2; 2A) is 4.85 mm.
    [10]
    An anchor escapement comprising an escape wheel (2; 2A) according to one of claims 6 to 9; an anchor (70) arranged to effect torque reception from the escape wheel (2; 2A) and a torque transmission, and to transmit to a balance spring (80) a torque from a mainspring, intermittently regulating the rotation of the escape wheel (2; 2A); and the balance spring (80) arranged to receive the torque from the anchor (70) and to act on the anchor (70).
    [11]
    11. A movement comprising: an anchor escapement (3) according to claim 10.
    [12]
    Mechanical timepiece comprising: a movement according to claim 11; and a box that hosts the movement.
    [13]
    A torque transmitting method in which a torque is transmitted to a pallet (73, 74) of an anchor (70) from an escape wheel (2; 2A) which includes an exhaust tooth (1). 1A) in which a quill (30) connecting a resting surface (10) and a pulse surface (20; 20A) has the curved shape of a convex curved surface portion (31), comprising the steps following: - the escape wheel (2; 2A) is released and begins to rotate; then - the pulse surface (20; 20A) approaches the pallet (73,74) by moving the pallet (73,74) along said convex curved surface portion (31) and transmitting torque with a gradual change, i.e. without abrupt change, in the direction of force applied by the exhaust tooth (1; 1A) on the pallet (73, 74); then - the impulse surface (20; 20A) presses on the pallet (73, 74) and transmits the torque.
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    同族专利:
    公开号 | 公开日
    CH706224A2|2013-09-13|
    CN103309224B|2017-05-31|
    CN103309224A|2013-09-18|
    JP2013186078A|2013-09-19|
    JP5891076B2|2016-03-22|
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    EP2336832B1|2009-12-21|2020-12-02|Rolex Sa|Swiss lever escapement|EP3321747B1|2015-08-25|2020-09-30|Citizen Watch Co., Ltd.|Watch escapement|
    JP2020020728A|2018-08-03|2020-02-06|セイコーエプソン株式会社|Ankle, movement, clock|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    JP2012053551A|JP5891076B2|2012-03-09|2012-03-09|Spur tooth, escape wheel provided with the hook tooth, ankle escapement, movement, mechanical timepiece, and torque transmission method|
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