• 专利附录
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    • 专利摘要:
    The invention relates to a constant force mechanism (10), a movement and a timepiece which can provide a sufficient amount of deflection of a torque adjusting spring (40) and which can provide accurate time measurement. satisfactory. The constant force mechanism (10) comprises: an energy switching portion (11) incorporated in a drive train (70) connecting an exhaust (60) to a power source; a pivoting lever (20) supporting the energy switching portion (11) to enable it to rotate about a first axis (C1); and a cycle control mechanism (30) having a stop wheel (31) rotatable with the power (operational torque) transmitted thereto from the power source, a torque setting spring (40) generating an expansion and contraction pushing force and driving the exhaust (60), and a locking portion (39) actuated by the torque adjusting spring (40) to lock the stop wheel (31), and designed to rotate the pivot lever (20) intermittently.
    公开号:CH710108A2
    申请号:CH01290/15
    申请日:2015-09-08
    公开日:2016-03-15
    发明作者:Hisashi Fujieda
    申请人:Seiko Instr Inc；
    IPC主号:
    专利说明:

    BACKGROUND OF THE INVENTION
    1. Field of the invention
    The present invention relates to a constant force mechanism, a movement and a mechanical timepiece.
    2. Description of the state of the art
    In a mechanical timepiece, when the torque transmitted to an exhaust from a barrel serving as a power source for the movement fluctuates in response to the unwinding of a main spring of the movement barrel, the oscillation angle of a balance spring is changed, which results in a variation of the time of the timepiece. In view of the above, in order to eliminate the fluctuation of the torque transmitted to the exhaust, it has been proposed a constant force mechanism in which a torque adjusting spring is disposed between the movement barrel and the exhaust.
    For example, the constant force mechanism described in US Patent No. 6,948,845 (Patent Document 1) is equipped with a fixed wheel, a carriage arm rotating about the center of the fixed wheel, and a torque adjusting spring connected to the carriage arm via a link mechanism. The constant force mechanism described in Patent Document 1 uses an elongated flat spring as a torque adjusting spring.
    The exhaust is driven by the torque generated by the thrust force of the torque adjusting spring and transmitted thereto. Thus, the amount of torque fluctuation due to changes in the thrust force of the torque adjusting spring greatly influences the accuracy of the time measurement.
    However, according to the conventional technique, the torque adjusting spring is formed by a flat spring, so that a sufficient amount of deflection can not be ensured, and the torque change per unit amount of deflection increases. Thus, during the operation of the constant force mechanism, the torque fluctuation portion due to changes in the thrust force of the torque adjusting spring increases, and it is feared a degradation of the accuracy of the measurement of time.
    SUMMARY OF THE INVENTION
    The present invention has been carried out in order to solve the above problem; an object of the present invention is to provide a constant force mechanism, a movement and a timepiece which can provide a sufficient amount of deflection of the torque adjusting spring and which can ensure a satisfactory accuracy of time measurement.
    In order to achieve this purpose, according to the present invention, there is provided a constant force mechanism comprising: an energy switching part incorporated in a gear train connecting an exhaust to a source of power; energy; a pivot lever supporting the energy switching portion so as to enable it to rotate about a first axis; and a cycle control mechanism having a rotatable stopwheel by virtue of the energy transmitted thereto from the power source, a torque adjusting spring generating a thrust force by expansion and contraction and driving the exhaust, and a locking portion actuated by the torque adjusting spring to lock the stop wheel, and arranged to rotate the pivot lever intermittently.
    According to this proposed architecture, there is provided a torque adjusting spring generating a thrust force by expansion and contraction such that, in comparison with the conventional technique, it is possible to obtain a sufficient amount of spring deflection torque setting. Therefore, the torque adjusting spring can suppress the amount of torque fluctuation due to a change in thrust force, so that it is possible to drive the exhaust stably. Thus, it is possible to provide a constant force mechanism that can ensure a satisfactory accuracy of time measurement.
    In addition, the cycle control mechanism comprises an arm connected to the pivot lever and supporting the locking portion so as to allow it to rotate about a second axis; and the torque adjusting spring is connected to the arm and communicates a thrust force about the second axis.
    According to this proposed architecture, the cycle control mechanism comprises an arm connected to the pivot lever, so that by designing the connection portion between the pivot lever and the arm adequately, it is possible to define arbitrarily the angle of rotation of the pivoting lever, the angle of rotation of the arm, the cycle of the mechanism with constant force etc. In particular, when the pivoting lever and the arm are connected to one another via toothed portions, it is possible to easily define the angle of rotation of the pivoting lever, the rotation angle of the arm, the cycle of the constant-force mechanism etc., defining only the ratio of the number of teeth, the length of the pivoting lever and that of the arm etc. In addition, the torque adjusting spring is connected to the arm, and applies a thrust force around the second axis, so that it is possible to arrange the torque adjustment spring so that it there is no overlap with the pivoting lever in the axial direction of the first axis. Therefore, it is possible to eliminate an increase in the thickness of the constant force mechanism, and thus achieve a reduction in size. It is therefore possible to provide a constant force mechanism that is better in terms of degrees of freedom at the design level.
    In addition, the cycle control mechanism has a spring adjusting mechanism adjusting the deflection amount of the torque adjusting spring.
    According to this proposed architecture, it is possible to adjust the amount of deflection of the torque adjusting spring after assembly of the cycle control mechanism. That is, it is not necessary to assemble the cycle control mechanism with the torque adjustment spring in the deformed position, so that it is possible to ensure a quality of operation. satisfactory assembly. In addition, after assembly of the cycle control mechanism and its incorporation into the movement, it is possible to adjust the amount of deflection of the torque adjusting spring by matching it to the variation of production of the movement. Thus, it is possible to provide a constant force mechanism having better properties in terms of assembly quality.
    The motion of the present invention comprises the constant force mechanism described above.
    The timepiece of the present invention comprises the movement described above.
    With this proposed architecture, it is possible to provide a timepiece and a high precision movement.
    According to the present invention, there is provided a torque adjusting spring generating a thrust force by expansion and contraction, so that, in comparison with the conventional technique, it is possible to obtain a sufficient amount of deflection for the torque adjustment spring. Therefore, the torque adjusting spring can suppress the amount of torque fluctuation due to a change in thrust force, so that it is possible to drive the exhaust stably. Thus, it is possible to provide a constant force mechanism that can provide satisfactory accuracy of time measurement.
    BRIEF DESCRIPTION OF THE DRAWINGS
    [0017]<tb> Fig. 1 <SEP> is a plan view of a mechanical timepiece.<tb> Fig. 2 <SEP> is a perspective view of a movement.<tb> Fig. 3 <SEP> is a sectional view taken along the axis A-A of FIG. 2.<tb> Fig. 4 <SEP> is a sectional view taken along the axis B-B of FIG. 2.<tb> Fig. 5 <SEP> is a graph whose horizontal axis indicates the time and whose vertical axis indicates the amount of storage of the operating torque of a torque adjusting spring.<tb> Fig. <SEP> is a block diagram illustrating motion comprising a constant force mechanism.<tb> Fig. 7 <SEP> is an explanatory view illustrating the operation of the constant force mechanism.<tb> Fig. 8 <SEP> is an explanatory view illustrating the operation of the constant force mechanism.<tb> Fig. 9 <SEP> is an explanatory view illustrating the operation of the constant force mechanism.<tb> Fig. <SEP> is a graph illustrating the reduction ratio of the thrust force of the torque adjusting spring and the operating torque according to the conventional technique.<tb> Fig. <SEP> is a graph illustrating the reduction ratio between the torque adjustment spring biasing force and the operational torque in the present embodiment.
    DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
    In the following, an embodiment of the present invention will be described with reference to the drawings.
    The mechanical member comprising the driving part of a timepiece is generally referred to as the "movement". The complete product obtained by mounting a dial and hands to this movement, and placing the assembly in the timepiece case is referred to as "complete movement" of the timepiece. Of the two sides of a main plate constituting the frame of the timepiece, the side where the crystal of the timepiece case, that is to say the side where the dial is located, is designated by the "back side" of the movement. On both sides of the main stage, the side on which the back of the timepiece case, that is to say the opposite side of the dial, is designated by the "front face" of the movement.
    FIG. 1 is a plan view of a timepiece 1.
    As shown in FIG. 1, the timepiece 1 is provided with a dial 2 comprising graduations 3 indicating hourly information. The timepiece 1 is equipped with needles 4 comprising an hour hand 4a indicating the hours, a minute hand 4b indicating the minutes, and a seconds hand 4c indicating the seconds. In addition, the timepiece 1 comprises a winding stem 6. The winding stem 6 is a component of timepiece used during the correction of the date and the correction of the time display ( display of hours and minutes). A crown 7 located on the side of the timepiece is mounted at a distal end of the winding stem 6.
    FIG. 2 is a perspective view of a movement 5.
    FIG. 3 is a sectional view taken along the axis A-A of FIG. 2.
    FIG. 4 is a sectional view taken along the axis B-B of FIG. 2.
    In order to improve the readability of the drawings, in FIGS. 2 to 4, a part of the timepiece components constituting the movement 5 is deliberately omitted depending on the circumstances.
    As shown in FIG. 2, the movement 5 according to the presently described embodiment comprises a movement cylinder 65 serving as an energy source (not shown in Fig. 2, see Fig. 6), an escapement 60, a gear train 70 , and a constant force mechanism 10. In the following, the components of motion 5 will be described.
    The movement barrel 65 (see Fig. 6) contains a main spring (not shown). The main spring of the movement barrel 65 is cocked by rotating the winding stem 6 (see Fig. 1). The movement barrel 65 is rotated by the rotational force when the main spring is reassembled.
    As shown in FIG. 2, the escapement 60 mainly comprises an escape wheel 61 and an anchor (not shown).
    As shown in FIG. 3, the escapement wheel 61, that is to say the wheel and its corresponding pinion, is carried between a main plate 90 and a first drive train bridge 91 located on the front face of the movement 5 relative to to the main plate 90 so as to be rotatable about a predefined axis of rotation through a bearing. The escape wheel 61 comprises exhaust teeth 62 and an escape pinion 63. The exhaust teeth 62 are formed at the outer periphery of the main body of the escape wheel 61.
    The anchor is carried between the main plate 90 and a pallet bridge (not shown) so as to rotate about a predefined axis of rotation, and comprises a pair of pallets. The pair of pallets alternately engages with the exhaust teeth 62 of the escape wheel 61 and is released from them by a regulator (not shown) according to a predefined cycle. As a result, the escape wheel 61 is rotated according to a predefined cycle.
    As shown in FIG. 2, the gear train 70 is composed of a drive train on the side of the movement cylinder 70A and a drive train on the exhaust side 70B.
    As shown in FIG. 3, the drive train on the side of the movement cylinder 70A comprises a barrel-side center mobile of the movement (not shown) engaged with the barrel of the movement 65 (see Fig. 6), a third barrel-side mobile of the movement 73 having a pinion 73a engaged with the mobile center barrel movement side, and a second mobile barrel side of the movement 74 having a pinion 74a meshing with the third movable barrel side movement 73. Each wheel respectively side of the mobile side barrel movement, the third movable barrel side of the movement 73 and the second movable barrel side of the movement 74 is carried between the main plate 90 and the first drive train bridge 91 so as to be rotatable about an axis of rotation predefined through a landing. The barrel-side drive train of the movement 70A transmits the energy of the main spring of the movement barrel 65 (hereinafter referred to as "operational torque") to the constant-force mechanism 10.
    The drive train on the exhaust side 70B includes an intermediate wheel 76 meshing with the exhaust pinion 63 of the escapement wheel 61, and a second exhaust side mobile 77 meshing with the pinion 76a of the intermediate wheel 76 The intermediate wheel 76 is carried between a first drive train deck 91 and a second drive train deck 92 formed between the first bridge of the drive train 91 and the main deck 90 so as to be rotatable around a predefined axis of rotation through a bearing. The second exhaust-side mobile 77 is carried by the first drive train deck 91 and the second drive train bridge 92 so as to be rotatable about a first axis C1 through a bearing. The exhaust side drive train 70B transmits the operational torque transmitted from the constant force mechanism 10, then to the exhaust 60. The second mobile exhaust side 77 corresponds to the second hand 4c of FIG. 1.
    (Mechanism with constant force)
    The constant force mechanism 10 is provided in order to eliminate the fluctuation in the operational torque transmitted to the exhaust 60 from the movement cylinder 65 (see FIG 6) constituting the energy source, and is composed of a power switching portion 11, a pivot lever 20, and a cycle control mechanism 30. In the following, the components of the constant force mechanism 10 will be described.
    The energy switching portion 11 is incorporated in the gear train 70 disposed between the barrel of the movement 65, constituting the energy source, and the exhaust 60. The energy switching portion 11 of the The present embodiment is a planetary mobile 12 engaged with the second moving barrel side of movement 74 of the drive wheel side of movement barrel 70A and with the second mobile side exhaust 77 of the drive train exhaust side 70B. The energy switching portion 11 switches between a first power transmission path P1 (see Fig. 6) through which the operational torque stored in the torque adjusting spring 40 is transmitted to the exhaust 60 and a second energy transmission path P2 (see Fig. 6) through which the operational torque of the motion barrel 65 (see Fig. 6) is transmitted to the torque adjusting spring 40 described below.
    The pivoting lever 20 is carried between the first drive train deck 91 and a third drive train bridge 93 provided on the front face of the movement 5 relative to the first drive train deck 91 of to be able to turn around the first axis C1 through a bearing.
    The pivot lever 20 comprises a sun gear carrier portion 21 which protrudes in a direction orthogonal to the first axis C1 and rotatably supports the sun gear 12 via a bearing. The sun gear support portion 21 supports the sun gear so that when the pivot lever 20 rotates, the sun wheel 12 makes a revolution about the first axis C1 and at the same time rotates.
    As shown in FIG. 2, the pivoting lever 20 has a balancing support portion 23 so as to protrude on the opposite side to the sun gear carrier portion 21 relative to the first axis C1. A weight 24 is mounted on the balancing support portion 23 so that the center of gravity of the pivot lever 20 coincides with the first axis C1. By providing the weight 24, the pivoting lever 20 can rotate stably regardless of the orientation of the timepiece 1 (see Fig. 1).
    In addition, the pivoting lever 20 has a pivoting lever gear 25 so as to protrude on the side opposite the exhaust 60 relative to the first axis C1. The pivot lever gear 25 is formed in a sector-shaped configuration whose center is the first axis C1 in plan view. A plurality of pivot lever teeth 25a are formed on the outer peripheral surface of the pivot lever gear 25.
    (Cycle control mechanism)
    The cycle control mechanism 30 mainly comprises a stop wheel 31, an arm 35, a locking portion 39, a torque adjusting spring 40, and a spring adjustment mechanism 50.
    As shown in FIG. 4, the stop wheel 31 is carried between the main plate 90 and a third drive train bridge 93 so as to be rotatable about a predefined axis of rotation, via a bearing. The stop wheel 31 has a stop tooth 32 on its outer peripheral surface. In addition, the stop wheel 31 has a stop pinion 33 in engagement with the second mobile movement barrel side 74. The stop wheel 31 can rotate by the transmission of the operational torque of the barrel of the movement 65 (see FIG. Fig. 6) via the barrel-side drive train of movement 70A.
    The arm 35 has an arm axis 38 extending along a second axis C2 located on the opposite side of the exhaust 60 relative to the first axis C1, and a main body of the arm 36 mounted on the Arm pin 38. The arm 35 has both end portions of the arm pin 38 supported respectively between the main platen 90 and the third drive axle bridge 93 through of a bearing, and can turn around the second axis C2. Around the main body of the arm 36, there is provided a control pin (not shown) for regulating the angle of rotation of the main member portion of the arm 36 to a predefined value.
    The main body of the arm 36 is formed to extend in a direction orthogonal to the second axis C2, and has a gear portion of the arm 37 protruding towards the pivot lever 20, and a locking portion 39 extending towards the stop wheel 31.
    The gear portion of the arm 37 is formed in a sector-shaped configuration with its center at the second axis C2 in plan view. A plurality of arm teeth 37a are formed at the outer peripheral surface of the arm gear piece 37. The gear portion of the arm 37 is engaged with the gear portion of the pivot lever 25, through to which the arm 35 is connected to the pivoting lever 20.
    The locking portion 39 includes a stop pallet 39a. The stop pallet 39a is fixed in position within a groove formed in the locking portion 39, for example, by an adhesive. Through the rotation of the arm 35, the stopping pallet 39a can be brought into engagement with and released from the stopping teeth 32 of the stopping wheel 31.
    The torque adjusting spring 40 is a spring capable of generating a thrust force by expansion and contraction; for example, a spiral spring 41 is employed. The spiral spring 41 is formed to extend along an Archimedean spiral whose center is the second axis C2 in plan view. An inner end portion 41a of the spiral spring 41 is attached to the arm 35 via, for example, a fixed tube 43 mounted on the arm pin 38. An outer end portion 41b of the spiral spring 41 is fixed to the main plate 90 via, for example, a fixed portion 46 of a spring adjustment wheel 45 attached to the main plate 90 described below.
    Through the rotation of the arm 35, the inner end portion 41a of the spiral spring 41 rotates about the second axis C2 with its outer end portion 41b fixed in position and, at the same time, the diameter outer spiral spring increases and decreases (undergoes expansion and contraction). In the state in which it has been raised so that the thrust force exerted can cause the locking portion 39 to move away from the stop wheel 31 (clockwise about the second axis C2 on the 2), the spiral spring 41 is then attached to the arm 35 and to the main plate 90.
    The spring adjustment mechanism 50 is mainly composed of a spring adjustment wheel 45 and a retaining element 47.
    The spring adjustment wheel 45 is formed in a tubular configuration, and has spring adjustment wheel teeth 45a at its outer peripheral surface. The spring adjustment wheel teeth 45a can be brought into engagement with a frame gear (not shown). The spring adjusting wheel 45 is mounted on the tubular portion 90a of the main plate 90 formed coaxially, for example, with the second axis C2.
    The retaining element 47 has a pair of nip portions 47a provided to extend in parallel. In the state in which it grips the spring adjustment wheel 45 by the pair of nip portions 47a, the retainer 47 is attached to the main plate 90. Due to the frictional force between the parts of pinch 47a and the spring adjustment wheel 45, the retaining element 47 holds the spring adjusting wheel 45 so as to prevent its rotation about the second axis C2.
    For example, at the time of producing the movement 5, the spring adjustment wheel 45 is rotated by a predefined angle by a frame wheel. Therefore, the spiral spring 41 is cocked, i.e. raised by a predetermined amount, to be adjusted to a desired amount of deflection. In this way, in the spring adjustment mechanism 50 of the present embodiment, it is possible to easily adjust the amount of deflection of the spiral spring 41 only by rotating the spring adjustment wheel 45.
    (Operation)
    FIG. 5 is a schematic diagram in which the vertical axis indicates the amount of storage of the operating torque of the torque adjusting spring 40.
    FIG. 6 is a block diagram illustrating the constant-force mechanism 10; it is an explanatory view illustrating schematically the transmission of the operational torque.
    Figs. 7 to 9 are explanatory views illustrating the operation of the constant force mechanism 10 as seen from the front of the movement 5.
    Next, the operation of the constant-force mechanism 10, constructed in the manner described above, will be described. During the operation of the timepiece 1, the amount of storage of the operational torque of the torque adjusting spring 40 (hereinafter referred to as "storage quantity W") reaches a maximum level; after that, the operational torque stored in the torque adjusting spring 40 is transmitted to the exhaust 60, and the storage amount W reaches a minimum level before reaching a maximum level again. In what follows, the above operation will be described. In the following description, the clockwise direction as seen from the front of the movement shown in FIGS. 7 to 9 will be referred to as the CW direction, and the counter clockwise direction will be referred to as the CCW direction. In the following description, concerning the reference numbers of the components, reference should be made to FIGS. 2 to 4, when it will be necessary.
    As shown in FIG. 5, at time t1, the constant force mechanism 10 is in the state in which the amount of storage W of the operational torque of the torque adjusting spring 40 armed by the operational torque of the barrel of the movement 65 (see FIG. ) is maximum (in the following, this state will be designated as "state S1"). At this time, as shown in FIG. 7, the constant force mechanism 10 is in the state in which the locking portion 39 and the stop wheel 31 are in mutual engagement. In addition, the stopwheel and the gear portion of the barrel-side drive train of the movement 70A are in a state in which their rotation is stopped.
    Then, with the passage of time, the operational torque stored in the torque adjusting spring 40 is gradually released. At this time, the thrust force of the torque adjusting spring 40 is exerted so that the arm 35 rotates in the CW direction about the second axis C2.
    When the arm 35 rotates in the CW direction, the pivot lever 20 connected to the arm 35 rotates in the CCW direction about the first axis C1.
    Here, the second mobile barrel side of the movement 74 is at rest. Thus, the sun wheel 12 supported by the pivoting lever 20 performs a revolution in the CCW direction around the first axis C1 and, at the same time, rotates in the CW direction in the state in which it is engaged with the second mobile movement cylinder side 74. The second exhaust-side mobile 77 in engagement with the sun wheel 12 rotates in the CCW direction because of the operational torque transmitted thereto by the rotation of the sun gear 12. And, the operating torque transmitted to the second Exhaust side mobile 77 is transmitted to the escapement mobile 61 of the exhaust 60 via the intermediate wheel 76. That is to say, as indicated by the first energy transmission path P1 of FIG. . 6, the operational torque of the motion cylinder 65 is stored in the torque adjusting spring 40 before being transmitted to the exhaust 60 in a state in which there is a small fluctuation.
    [0060] Thereafter, as shown in FIG. 5, the operational torque of the torque adjusting spring 40 is released, and the constant force mechanism 10 reaches, at time t2, a state in which the amount of storage of the operational torque of the torque adjusting spring 40 is minimal (referred to as hereinafter "state S2"). At this time, as shown in FIG. 8, the constant force mechanism 10 reaches a state in which meshing between the locking portion 39 and the stop wheel 31 is released.
    Subsequently, as shown in FIG. 5, from time t2, the constant force mechanism 10 reaches a state in which the operational torque is stored in the torque adjusting spring 40 (hereinafter referred to as "state S3").
    At this time, as shown in FIG. 9, the gear parts of the drive train on the side of the movement cylinder 70A and the stop wheel 31 are rotated by the operational torque from the movement cylinder 65 (see Fig. 6). More specifically, the second moving barrel side movement 74 rotates in the CCW direction. The stopping wheel 31 engaged with the second mobile drum barrel movement 74 rotates in the CW direction. At this time, the escape wheel 61 of the exhaust 60 and the gear parts of the exhaust side drive train 70B are at rest.
    When the second mobile barrel side of the movement 74 rotates in the CCW direction, the sun wheel 12 engaged with the second moving barrel side movement 74 rotates in the CW direction.
    Here, the second mobile exhaust side 77 is at rest. Thus, the sun wheel 12 engaged with the second exhaust-side mobile 77 performs a revolution in the CW direction around the first axis C1 and rotates in the CW direction in a state in which it is engaged with the second exhaust-side mobile 77 and the second mobile movement barrel side 74. In addition, with the revolution of the sun wheel 12, the pivot lever 20 supporting the sun wheel 12 rotates in the CW direction about the first axis C1.
    When the pivoting lever 20 rotates in the CW direction, the arm 35 connected to the pivoting lever 20 rotates in the CCW direction about the second axis C2 against the thrust force in the CW direction due to the spring of Torque adjustment 40. Therefore, the torque adjusting spring 40 is armed by the operating torque of the movement barrel 65 (see Fig. 6) transmitted to the arm 35. That is, as indicated by the second energy transmission path P2 of FIG. 6, the operational torque of the movement barrel 65 is transmitted to the torque adjusting spring 40 and stored therein. And, as shown in fig. 5, at time t3, the constant force mechanism 10 reaches the state S1 in which the storage amount W of the operational torque of the torque adjusting spring 40 is again maximum. At this point, as shown in fig. 7, the constant force mechanism 10 reaches a state in which the locking portion 39 is engaged with the stop wheel 31.
    From there, the above operation is repeated, so that the exhaust 60 is driven into a state in which a fluctuation in the transmitted operational torque is suppressed.
    FIG. 10 is a graph showing the reduction ratio between the thrust force of the torque adjusting spring and the operating torque according to the prior art, and FIG. 11 is a graph showing the reduction ratio between the thrust force of the torque adjusting spring 40 and the operational torque in the present embodiment. In figs. 10 and 11, the horizontal axis indicates the time and amount of deflection of the torque adjusting spring 40, and the vertical axis indicates the thrust force of the torque adjusting spring and the operational torque due to the main spring of the barrel. movement 65 (see Fig. 6). The dashed line indicates the relationship between the operational torque of the main spring of the movement barrel 65 (see Fig. 6) and the time, and the solid line indicates the relationship between the operational torque due to the thrust force of the mainspring. torque setting and time.
    During operation of the constant force mechanism 10, the torque adjusting spring 40 is armed by the operating torque of the movement barrel 65 transmitted to the arm 35, so that an operational torque is stored. At this moment, it is necessary that the operational torque of the movement barrel 65 is against the operational torque due to the thrust force of the torque adjustment spring 40. In general, however, the operational torque due to the The thrust force of the torque adjusting spring 40 differs between the moment when the spring is released and the moment when the spring is cocked.
    As shown in FIGS. 10 and 11, the following equation is applicable:TrMIN = TrMAX - k x Tc ... (1)where Te represents the amount of deflection released by the torque adjusting spring 40; TrMAX is the maximum operating torque of the corresponding torque adjusting spring 40; TrMIN is the minimum operational torque; and k is the restoring constant (operating torque / deflection amount) of the torque adjusting spring 40.
    The greater the return constant k, the less the torque adjusting spring 40 is subjected to elastic deformation and the smaller the amount of deflection, whereas the lower the return constant k, the more the spring is subject to elastic deformation, and the greater the amount of deflection is large.
    In addition, the following equation is applicable:k = TrMAX / (n × Tc) ... (2)where n is a deflection coefficient.
    N indicates about the number of deflections of the torque adjusting spring 40 in comparison with the operational amount of deflection. From equations (1) and (2), the following equation is derived:TrMIN = TrMAX x (n - 1) / n ... (3)
    In addition, the following equation is applicable:ΔTr = TrMAX - TrMIN = TrMAX / n ... (4)where ΔTr is the difference between the maximum operational torque TrMAX and the minimum operational torque TrMIN (hereinafter referred to as the "operating torque difference").
    From equation (4), when n is large, that is to say, the greater the amount of deflection of the torque adjusting spring 40, the greater the variation of the operational torque is small.
    In addition, a state in which the operational torque of the movement cylinder 65 is at the same level as the operational torque for operating torque values between the maximum torque TrMAX and the minimum torque TrMin will be defined as an unstable state. . The constant force mechanism 10 in the unstable state repeats switching on and off irregularly. Thus, the operational torque transmitted to the escapement 60 fluctuates, and the accuracy of the measurement of the time also becomes unstable.
    The operational torque of the movement cylinder 65 and the period of time that has elapsed since the start of the motion 5 are correlated by a monotonic reduction relationship. Thus, the smaller the operational torque difference ΔTr is, the smaller the operational torque range of the motion cylinder 65 (that is, the main spring) causing the unstable state is small, and in correspondence thereof, the length of time that the unstable state lasts is reduced.
    Here, assuming that the power reserve duration of motion 5 is Tm, the deflection coefficient n is approximately 3 in the prior art, and the time T1 of the unstable state at this time is approximately 1/5 the duration Tm of motion 5 (see Fig. 10).
    In contrast, in the present embodiment in which the spiral spring 41 is adopted for the torque adjusting spring 40, it is possible to reduce the time 12 of the unstable state to approximately 1/20 of the duration. Tm power reserve of the movement 5 by making the deflection coefficient n equal to 20 (see Fig. 11). The case where the deflection coefficient n = 20 is only given as an example; it is possible, for example, for the deflection coefficient to be equal to or greater than 20. In this way, in the present embodiment, it is possible to substantially reduce the time of the unstable state in comparison with the solutions of the prior art, so that it is possible to provide a movement 5 and a timepiece 1 whose accuracy of time measurement is better.
    In the present embodiment, the spiral spring 41 is provided as a torque adjusting spring 40 generating a thrust force by expansion and contraction, so that it is possible to ensure a sufficient amount of deflection for the torque adjustment spring with respect to the solutions of the prior art. Therefore, the torque adjusting spring 40 can suppress the torque fluctuation rate due to a change in the thrust force, so that the exhaust 60 can be driven stably. Thus, it is possible to provide a constant force mechanism that can provide satisfactory accuracy of time measurement.
    In addition, the cycle control mechanism 30 comprises the arm 35 connected to the pivot lever 20, so that by designing the connecting portion of the pivot lever 20 and the arm 35 adequately, it is possible arbitrarily defining the angle of rotation of the pivot lever 20, the angle of rotation of the arm 35, the cycle of the constant force mechanism 10 etc. In particular, in the case where the pivoting lever 20 and the arm 35 are connected to one another by toothed portions, only by defining the ratio of the number of teeth, the pivoting lever 20, the length of the arm Etc., it is possible to easily define the angle of rotation of the pivoting lever 20, the angle of rotation of the arm, the cycle of the constant-force mechanism, etc. In addition, the torque adjusting spring 40 is connected to the arm 35, and communicates a thrust force around the second axis C2, so that it is possible to arrange the torque adjusting spring 40 so that there is no overlap with the pivoting lever 20 in the axial direction of the first axis C1. Therefore, it is possible to eliminate the thickness of the constant force mechanism 10, by performing a size reduction. Thus, it is possible to provide a constant force mechanism that is better at the degrees of freedom in terms of design.
    In addition, due to the provision of the spring adjustment mechanism 50, it is possible to adjust the amount of deflection of the torque adjusting spring 40 after assembly of the cycle control mechanism 30. that is, it is not necessary to assemble the cycle control mechanism 30 with the deformed torque adjusting spring 40, so that satisfactory assembly quality can be achieved. . Further, after assembly of the cycle control mechanism 30 and its incorporation into the movement 5, it is possible to adjust the amount of deflection of the torque adjusting spring 40 by matching it to the variation in the production of the 5. Thus, it is possible to provide a constant force mechanism that is better in terms of assembly quality.
    In addition, because of the provision of the constant force mechanism 10 above, it is possible to provide a movement 5 and a timepiece 1 of high precision.
    The present invention is not limited to the embodiment described above with reference to the drawings, but allows various modifications without departing from the technical scope thereof.
    While, in the above embodiment, the spiral spring 41 is adopted as a torque adjusting spring 40, such an implementation should not be interpreted restrictively; any other elastic element may be suitable as long as it is capable of generating a thrust force by expansion and contraction. Thus, for example, it is possible to adopt, as a torque adjusting spring 40, a coil spring capable of generating a thrust force by expansion and contraction.
    While in the embodiment above, the center of rotation of the pivoting lever 20 and the center of rotation of the second exhaust-side mobile 77 coincide with the first axis C1, that is to say that they are coaxial, they may not be coaxial.
    In the spring adjustment mechanism 50 of the embodiment described, the spiral spring 41 is maintained in the state in which it has been armed with a predetermined amount by the friction force when the adjusting wheel of spring 45 is clamped by the retaining element 47. In this respect, the spring adjustment mechanism 50 can hold the spiral spring 41 in a state in which it has been armed with a predefined amount by fixing the adjustment wheel. spring 45 to a predefined position using, for example, a braking jumper.
    While the embodiment above adopts the planetary mobile 12 as energy switching part 11, such an implementation should not be interpreted as being limited to the sun wheel 12; any other structure may be suitable as long as it can switch the transmission direction of the operational torque. Thus, the energy switching portion 11 may be a differential mechanism comprising a differential gear having a center of rotation in a direction intersecting, for example, the axis of rotation of the pivot lever 20.
    [0088] Aside from the foregoing, certain components of the above embodiment may be replaced by well-known components according to the situation without departing from the scope of the spirit of the present invention.
    权利要求:
    Claims (5)
    [1]
    A constant force mechanism (10) comprising:an energy switching portion (11) incorporated in a gear train (70) connecting an exhaust (60) to a power source;a pivoting lever (20) supporting the energy switching portion (11) to enable it to rotate about a first axis (C1); anda cycle control mechanism (30) having a stop wheel (31) rotatable with the power transmitted thereto from the power source, a torque adjusting spring (40) ) generating a thrust force by expansion and contraction and driving the exhaust (60), and a locking portion (39) actuated by the torque adjusting spring (40) to lock the stopping wheel (31), and arranged to rotate the pivot lever (20) intermittently.
    [2]
    The constant force mechanism (10) according to claim 1, wherein the cycle control mechanism (30) is provided with an arm (35) connected to the pivoting lever (20) and supporting the locking portion (39). ) so as to allow it to rotate about a second axis (C2); andthe torque adjusting spring (40) is connected to the arm (35) and communicates a thrust force around the second axis (C2) by expansion and contraction.
    [3]
    The constant force mechanism (10) according to claim 1 or 2, wherein the cycle control mechanism (30) has a spring adjustment mechanism (50) adjusting the amount of deflection of the torque adjusting spring (40). ).
    [4]
    Movement (5) comprising a constant force mechanism (10) according to any one of claims 1 to 3.
    [5]
    5. Timepiece (1) comprising a movement (5) according to claim 4.
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    同族专利:
    公开号 | 公开日
    CH710108B1|2020-03-31|
    JP2016057111A|2016-04-21|
    CN105404130A|2016-03-16|
    CN105404130B|2019-04-09|
    JP6388333B2|2018-09-12|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    EP1528443B1|2003-10-28|2008-08-06|Francois-Paul Journe|Constant force mechanism for a watch|
    EP2166419B1|2008-09-18|2013-06-26|Agenhor SA|Clockwork comprising a constant-force device|
    CH702843B1|2010-03-17|2014-08-29|Complitime Sa|Movement for timepiece to remontoir.|
    JP5485859B2|2010-11-17|2014-05-07|セイコーインスツル株式会社|Uncle escapement and mechanical watch with the same|
    JP6057659B2|2012-10-18|2017-01-11|セイコーインスツル株式会社|Constant torque mechanism for watch, movement and mechanical watch equipped with the mechanism|JP6566432B1|2018-06-07|2019-08-28|セイコーインスツル株式会社|Constant torque mechanism, watch movement and watch|
    JP2020020728A|2018-08-03|2020-02-06|セイコーエプソン株式会社|Ankle, movement, clock|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    JP2014182261A|JP6388333B2|2014-09-08|2014-09-08|Constant force mechanism, movement and watch|
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