WO2001009686A1 - Piece d'horlogerie mecanique dotee d'un mecanisme de commande de l'angle de rotation du balancier annulaire regle - Google Patents

Piece d'horlogerie mecanique dotee d'un mecanisme de commande de l'angle de rotation du balancier annulaire regle Download PDF

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Publication number
WO2001009686A1
WO2001009686A1 PCT/JP1999/004077 JP9904077W WO0109686A1 WO 2001009686 A1 WO2001009686 A1 WO 2001009686A1 JP 9904077 W JP9904077 W JP 9904077W WO 0109686 A1 WO0109686 A1 WO 0109686A1
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WO
WIPO (PCT)
Prior art keywords
wheel
balance
rotation
resistance
mainspring
Prior art date
Application number
PCT/JP1999/004077
Other languages
English (en)
Japanese (ja)
Inventor
Takashi Takahashi
Takeshi Tokoro
Original Assignee
Seiko Instruments Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Seiko Instruments Inc. filed Critical Seiko Instruments Inc.
Priority to PCT/JP1999/004077 priority Critical patent/WO2001009686A1/fr
Priority to JP55152099A priority patent/JP3565227B2/ja
Priority to CN99813863A priority patent/CN1328659A/zh
Priority to EP99933157A priority patent/EP1126333A4/fr
Publication of WO2001009686A1 publication Critical patent/WO2001009686A1/fr
Priority to HK02104382.6A priority patent/HK1042753A1/zh

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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/06—Oscillators with hairsprings, e.g. balance
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/26—Compensation of mechanisms for stabilising frequency for the effect of variations of the impulses

Definitions

  • the present invention relates to a mechanical timepiece with a balance rotation angle control mechanism configured to apply a force to suppress the rotation of the balance with hairspring to the balance with hairspring.
  • the movement (mechanical body) 110 of the mechanical timepiece has a main plate 1102 constituting a substrate of the movement.
  • the winding stem 111 is rotatably incorporated in the winding guide hole 111a of the main plate 111.
  • a dial 1 104 (shown in phantom in FIG. 19) is attached to the membrane 110.
  • the side with the dial is called the “back side” of the movement
  • the side opposite to the side with the dial is called the “front side” of the movement.
  • the train wheel built into the “front side” of the movement is called “front train wheel”
  • the train wheel built into the “back side” of the movement is called “back train wheel”.
  • the position of the winding stem 1 110 in the axial direction is determined by a switching device that includes the setting 1 1 9 0, the latch 1 1 9 2, the latch spring 1 1 9 4, and the back retainer 1 1 9 6.
  • the wheel 1 1 1 2 is rotatably provided on the guide shaft of the winding stem 1 1 1 0.
  • the wheel 1 1 1 2 rotates through the rotation of the wheel.
  • the round hole wheel 1 1 1 4 is rotated by the rotation of the wheel 1 1 1 2.
  • the square hole wheel 1 1 16 is rotated by the rotation of the round hole wheel 1 1 14.
  • the mainspring 1122 housed in the barrel car 1120 is wound up by the rotation of the square wheel wheel 1116.
  • the second wheel 1 124 is rotated by the rotation of the barrel wheel 1 120.
  • the escape wheel 1130 rotates through the rotation of the fourth wheel 1128, the third wheel 1126, and the second wheel 1124.
  • the barrel car 1120, the second wheel 1124, the third wheel 1126, and the fourth wheel 1128 form a front wheel train.
  • the escapement / governing device for controlling the rotation of the front train wheel includes a balance 1140, an escape wheel 1130, and an ankle 1142.
  • the balance 1140 includes a balance 1140a, a balance wheel 1140b, and a hairspring 1140c.
  • the cannon pinion 1150 rotates at the same time.
  • the minute hand 1152 attached to the barrel pinion 1 150 indicates “minute”.
  • the tube pinion 1150 is provided with a sleep mechanism for the center wheel & pinion 1124.
  • the hour wheel 1154 rotates through the rotation of the minute wheel.
  • the hour hand 1156 attached to the hour wheel 1154 indicates "hour”.
  • the barrel car 1120 is rotatably supported with respect to the main plate 1102 and the barrel receiver 1160.
  • the second wheel & pinion 1124, the third wheel & pinion 1126, the fourth wheel & pinion 1128, and the escape wheel & pinion 1130 are supported rotatably with respect to the main plate 1102 and the train wheel bridge 1162.
  • the ankle 1 142 is rotatably supported with respect to the main plate 1102 and the ankle receiver 1 164.
  • the balance with hairspring 1140 is rotatably supported with respect to the main plate 1102 and the balance with hairspring 1166.
  • the hairspring 1 140c is a thin leaf spring in a spiral shape with multiple windings.
  • the inner end of the hairspring 1140c is fixed to a beard ball 1140d fixed to the balance 1140a, and the outer end of the hairspring 1140c is fixed to the balance 1166. It is fixed by screwing through the beard holder 1 170a attached to 1 170.
  • a speed / recess needle 1 16 8 is rotatably mounted on the balance with hairspring 1 1 6 6.
  • the whiskers 1 3 4 0 and the whiskers 1 3 4 2 are attached to the needle 1 1 6 8.
  • a portion near the outer end of the beard is located between the beard holder and the beard bar.
  • the mainspring torque decreases as the mainspring is released from the state in which the mainspring is completely wound up (full winding state) and the duration elapses. I do.
  • the mainspring torque is about 27 gcm in the fully wound state, and about 23 gcm after 20 hours from the fully wound state. It will be about 18 g ⁇ cm after 40 hours.
  • the swing angle of the balance with hairspring when the spring torque decreases, the swing angle of the balance with hairspring also decreases.
  • the swing angle of the balance with hairspring when the mainspring torque is 25 to 28 gcm, the swing angle of the balance with hairspring is about 240 to 270 degrees, and the mainspring torque is 20 to 25
  • the swing angle of the balance with hair is about 180 to 240 degrees.
  • the instantaneous rate is defined as "when the mechanical watch is left for one day while maintaining the state and environment, such as the swing angle of the balance when measuring the rate, The rate value indicating the advance or delay of a mechanical watch.
  • the swing angle of the balance with hairspring is 240 degrees or more, or 200 degrees or less, the instantaneous rate is delayed.
  • a typical conventional mechanical watch as shown in Fig.
  • FIG. 17 shows the transition of the elapsed time and the instantaneous rate when the mainspring is released from the fully wound state in a typical conventional mechanical timepiece.
  • the “rate”, which indicates the advancement of the clock or the delay of the clock per day, is indicated by the solid line in FIG. It is obtained by integrating the step rate over 24 hours.
  • the instantaneous rate is about 10 seconds / day in a fully wound state (about 10 seconds per day), The instantaneous rate is about 4 seconds / day after 20 hours from the full winding state (about 4 seconds per day), and the instantaneous rate is plus / minus about 0 seconds / day after 24 hours from the full winding state. (There is no advance or delay per day), and after 30 hours from the full winding state, the instantaneous rate is about 18 seconds / day (each is about 8 seconds late).
  • a conventional balance angle adjusting device for a balance with hairspring is provided with a swing angle adjusting plate that applies a braking force to the balance with an overcurrent generated each time the magnet of the balance approaches and swings. It is disclosed in Japanese Patent Publication No. 544-141675.
  • An object of the present invention is to provide a mechanical timepiece provided with a balance rotation angle control mechanism that can control a swing angle of a balance with hairspring to fall within a certain range.
  • the present invention provides a mainspring constituting a power source of a mechanical timepiece, a front wheel train rotating by a rotational force when the mainspring is released, and an escapement / governing device for controlling the rotation of the front wheel train.
  • the escapement and speed governor are equipped with a balance that alternates between clockwise and counterclockwise rotation, an escape wheel that rotates based on the rotation of the front train wheel, and an escape wheel that rotates based on the operation of the balance.
  • a mechanical timepiece configured to include an ankle for controlling the balance, when the mainspring is completely wound up, imparts air resistance to the rotation of the balance with hairspring, and when the mainspring is completely unwound, the mainspring rotates with the balance. It is characterized by having a rotation angle control mechanism configured to provide no air resistance.
  • the balance rotation angle control mechanism is preferably configured to include a resistance lever arranged with a gap provided with respect to the outer periphery of the balance with hairspring.
  • the balance rotation angle control mechanism is configured to include a planetary gear mechanism associated with a barrel gear and a square wheel.
  • the resistance lever includes a window formed by providing a gap with respect to the outer periphery of the balance with hair.
  • the resistance lever may be configured to include an arm formed by providing a gap with respect to the outer periphery of the balance with hair.
  • the rotation angle of the balance of the mechanical watch can be effectively controlled, thereby improving the accuracy of the mechanical watch. .
  • FIG. 1 is a plan view showing a schematic shape of a front side of a movement of a mechanical timepiece according to an embodiment of the present invention in a state where a mainspring is released (in FIG. 1, some parts are omitted, and Members are shown in phantom lines).
  • FIG. 2 is a partial cross-sectional view showing a schematic shape of a front wheel train portion of the embodiment of the mechanical timepiece of the present invention.
  • FIG. 3 is a partial plan view showing a schematic shape of a resistance lever portion of the movement when the mainspring is released in the embodiment of the mechanical timepiece of the present invention.
  • FIG. 4 is a partial cross-sectional view showing a schematic shape of a resistance lever portion of a movement in a state where a mainspring is released in the embodiment of the mechanical timepiece of the present invention.
  • FIG. 5 is a block diagram showing an operation of the embodiment of the mechanical timepiece of the present invention in a state where the mainspring is wound up.
  • FIG. 6 is a plan view showing a schematic shape on the front side of the movement in a state where the mainspring is wound up in the embodiment of the mechanical timepiece of the present invention (in FIG. 1, some parts are omitted, and a receiving member is shown). Is indicated by a virtual line).
  • FIG. 7 is a partial plan view showing a schematic shape of a resistance lever portion of a movement of a mechanical timepiece according to an embodiment of the present invention in a state where a mainspring is wound up.
  • FIG. 8 is a partial cross-sectional view showing a schematic configuration of a resistance lever portion of a movement in a state where a mainspring is wound up in the embodiment of the mechanical timepiece of the present invention.
  • FIG. 9 is a block diagram showing an operation of the mechanical timepiece according to the embodiment of the present invention when the mainspring is released.
  • FIG. 10 is a plan view showing the schematic shape of the front side of the movement in a state where the mainspring is released in another embodiment of the mechanical timepiece of the present invention. (In FIG. 10, some parts are omitted. The receiving member is indicated by a virtual line).
  • FIG. 11 is a partial plan view showing a schematic configuration of a resistance lever portion of a movement in a state where a mainspring is released in another embodiment of the mechanical timepiece of the present invention.
  • FIG. 12 is a plan view schematically showing the front side of the movement in a state where the mainspring is wound up in another embodiment of the mechanical timepiece of the present invention (see FIG. 12). ), Some parts are omitted, and the receiving member is shown by phantom lines).
  • FIG. 13 is a partial plan view showing a schematic configuration of a resistance lever portion of a movement in a state where a mainspring is wound up in another embodiment of the mechanical timepiece of the present invention.
  • FIG. 14 is a graph schematically showing a relationship between an elapsed time when the mainspring is released from all windings and a mainspring torque in a mechanical timepiece.
  • FIG. 15 is a graph schematically showing a relationship between a swing angle of a balance with hairspring and a mainspring torque in a mechanical timepiece.
  • FIG. 16 is a graph schematically showing the relationship between the swing angle of the balance with hair and the instantaneous rate in a mechanical timepiece.
  • FIG. 17 is a graph schematically showing the relationship between the elapsed time when the mainspring is released from the whole volume and the instantaneous rate in the mechanical timepiece of the present invention and the conventional mechanical timepiece.
  • FIG. 18 is a plan view showing a schematic shape of a front side of a movement of a conventional mechanical timepiece (in FIG. 18 some parts are omitted and receiving members are indicated by phantom lines).
  • FIG. 19 is a schematic partial cross-sectional view of a movement of a conventional mechanical watch (in FIG. 19, some parts are omitted).
  • the movement (machine body) 400 of the mechanical timepiece has a main plate 102 constituting a substrate of the movement.
  • the winding stem 110 is rotatably incorporated into the winding guide hole 1 ⁇ 2a of the main plate 102.
  • the dial 104 (shown in phantom in FIG. 2) is attached to the movement 400.
  • the winding stem 110 has a corner and a guide shaft.
  • Continuity wheel (not shown) is winding 1 1 0 To be incorporated into the corners.
  • the ratchet wheel has the same rotation axis as that of the winding pin 110. That is, the ratchet wheel has a square hole, and is provided so as to rotate based on the rotation of the winding stem 110 by fitting the square hole into the corner of the winding stem 110.
  • the ratchet wheel has insteps and teeth. The instep is located at the end of the thumbwheel closer to the center of the movement 400. The second tooth is located at the end of the wheel closer to the outside of the movement 400.
  • Movement 400 is provided with a switching device for determining the position of winding stem 110 in the axial direction.
  • the switching device includes a setting lever 190, a latch 1992, a latch spring 1994, and a back retainer 1996.
  • the position of the winding stem 110 in the direction of the rotation axis is determined based on the rotation of the setting lever 190.
  • the position of the pinwheel in the direction of the rotation axis is determined based on the rotation of the bolt 19.
  • the bolt 1992 is positioned at two positions in the rotation direction.
  • the wheel 1 1 2 is rotatably provided on the guide shaft of the winding stem 110.
  • the wheel 1 1 2 is configured to rotate through the rotation of the wheel.
  • the round wheel 1 114 is configured to rotate by the rotation of the wheel 1 1 2.
  • the square hole wheel 1 16 is configured to rotate by the rotation of the round hole wheel 114.
  • a saw blade 1 18 for rotating the square wheel 1 16 in one direction is arranged to engage with the gear portion of the square wheel 1 16.
  • the movement 400 is powered by a mainspring 122 housed in a barrel box 120.
  • the mainspring 1 2 2 is made of an elastic material having a spring property such as iron.
  • the configuration is such that the mainspring 1 2 2 can be wound up by rotating the square wheel 1 1 6.
  • the second wheel & pinion 124 is configured to rotate by the rotation of the barrel wheel 120.
  • the third wheel 1 2 6 is configured to rotate based on the rotation of the second wheel 1 2 4.
  • 4th car 1 2 8 is configured to rotate based on the rotation of the third wheel 1 2 6. Escape wheel
  • the barrel car 1 2 0, the second wheel 1 2 4, the third wheel 1 2 6 and the fourth wheel 1 2 8 constitute a front wheel train.
  • Movement 400 is provided with an escape / governing device for controlling the rotation of the front train wheel.
  • the escapement and governor operate the balance wheel 140, which rotates clockwise and counterclockwise at regular intervals, the escape wheel 1330, which rotates based on the rotation of the front train wheel, and the balance wheel 140, And an ankle 142 for controlling the rotation of the escape wheel 130 based on the
  • the balance 140 includes a balance 140a, a balance wheel 140b, and a hairspring 144c.
  • the hairspring 140 c is made of an elastic material having a spring property such as “Erinba”. That is, the hairspring 140c is made of a metal conductive material.
  • the cylindrical pinion 150 rotates simultaneously.
  • the minute hand 15 2 attached to the barrel pinion 150 is configured to display “minute”.
  • the cannon pinion 150 is provided with a slip mechanism having a predetermined slip torque with respect to the center wheel & pinion 124.
  • the minute wheel (not shown) rotates based on the rotation of the cannon pinion 150.
  • the hour wheel 154 rotates based on the rotation of the minute wheel.
  • the hour hand 156 attached to the hour wheel 154 is configured to display "hour”.
  • the barrel barrel 120 is supported rotatably with respect to the main plate 102 and barrel barrel 160.
  • the second wheel 1 2 4, the third wheel 1 2 6, the fourth wheel 1 2 8, and the escape wheel 1 330 are supported so that they can rotate with respect to the main plate 102 and the train wheel bridge 420. Is done.
  • the ankle 142 is supported rotatably with respect to the main plate 102 and the ankle receiver 164.
  • the balance with hairspring 140 is rotatably supported with respect to the main plate 102 and the balance with hairspring 166.
  • the upper bell 140 a 1 of the balance 140 a is supported rotatably with respect to the balance upper bearing 166 a fixed to the balance holder 166.
  • Balance The upper bearing 166a includes a balance stone and a balance stone. Balance stones and stones are made of insulating material such as ruby.
  • the lower tenon 140a2 of the balance 140a is supported rotatably with respect to the balance lower bearing 102b fixed to the main plate 102.
  • the balance wheel bearing 102b includes a balance hole stone and a balance stone. Hypothetical pits and trowels are made of insulating materials such as ruby.
  • the hairspring 140 c is a thin leaf spring having a spiral shape with a plurality of turns.
  • the inner end of the hairspring 140 c is fixed to a beard ball 140 d fixed to a balance 140 a, and the outer end of the hairspring 140 c is a balance 16 1 It is fixed with screws via a beard holder 170a attached to a beard holder 170 rotatably fixed to the shaft.
  • the balance 1 166 is made of a metal conductive material such as brass.
  • Beard support 170 is made of a metal conductive material such as iron.
  • the hairspring 140 c expands and contracts in the radial direction of the hairspring 140 c according to the rotation angle of the balance 140. For example, in the state shown in FIG. 1, when the balance 140 rotates clockwise, the hairspring 140 c shrinks in the direction toward the center of the balance 140, whereas the balance 14 4 As 0 rotates counterclockwise, the hairspring 140 c expands away from the center of the balance 140.
  • the movement of the hairspring 140c may have a reverse structure. That is, when the balance 140 rotates counterclockwise, the hairspring 140 c contracts toward the center of the balance 140, and when the balance 140 rotates clockwise, the beard rotates.
  • the mainspring 140c can also be configured to extend in a direction away from the center of the balance 140.
  • the first sun wheel 450 is rotatably supported with respect to the train wheel bridge 420 and the main plate 102.
  • the first sun wheel 450 includes a first sun gear 4 52, a first sun pinion 4 54, and a first solar wheel 4 5 6.
  • the Dai-ichi Taishin Shin 4 456 is composed of the first shaft part 4 56 a, the second shaft part 4 56 b, and the third shaft part 4 5 in the direction from the train wheel bridge 420 to the main plate 102. 6 Includes c.
  • the first sun gear 452 is located on the third shaft portion 456c.
  • the first sun kana 454 is located on the opposite side of the side with the main plate 102, that is, on the back lid side of the train wheel bridge 420.
  • the second sun wheel 460 is rotatably incorporated into the first shaft portion 456a of the first sun wheel shin 450. That is, the rotation center of the second sun wheel 450 is the same as the rotation center of the first sun wheel 450.
  • the second sun wheel 460 has a second sun gear 462 and a second sun pinion 464.
  • the planetary transmission wheel 466 is rotatably supported with respect to the second train wheel bridge 422 and the main plate 102.
  • the second sun gear 4 62 is engaged with the planetary transmission wheel 4 66 and can be rotated by the rotation of the planetary transmission wheel 4 6 6.
  • Planetary transmission wheel 4 6 6 is mated with square hole wheel 1 16 and can be rotated by rotation of square hole wheel 1 16.
  • the planetary intermediate gear 470 is rotatably disposed with respect to the second shaft portion 456 b of the first sun wheel stem 456. That is, the center of rotation of the planetary intermediate gear 470 is the same as the center of rotation of the first sun wheel 450.
  • the planetary intermediate gear 47 0 meshes with the barrel gear 120 a and can be rotated by the rotation of the barrel gear 120.
  • the first planetary wheel 472 is rotatably disposed on the planetary intermediate gear 470 around a location different from the rotation center of the planetary intermediate gear 470.
  • the second planetary wheel 474 is rotatably disposed on the planetary intermediate gear 470 around a point different from the rotational center of the planetary intermediate gear 470. That is, the center of rotation of the first planetary wheel 472 is the same as the center of rotation of the second planetary wheel 474.
  • the first planetary wheel 4 7 2 and the second planetary wheel 4 7 4 are collectively configured as a planetary wheel 4 7 6 so that they can rotate together with respect to the planet intermediate gear 4 7 0. Fixed to each other.
  • the first planetary wheel 4 7 2 can rotate while being positioned on the side where the train wheel bridge 4 20 of the planetary intermediate gear 4 7 0 is located, while the second planetary wheel 4 7 4
  • the base plate 102 of the intermediate gear 170 is located on the side where the main gear 170 is located, and is arranged so as to be able to rotate.
  • the first planetary wheel 4 7 2 engages with the second sun pinion 4 6 4, so that the first planetary wheel 4 7 2 can revolve around the second sun pinion 4 64 4.
  • the second planetary gear 4 7 4 engages with the first sun gear 4 52, so that the second planetary gear 4 7 4 can revolve around the first sun gear 4 52 while revolving.
  • the first planetary wheel 472 and the second planetary wheel 474 are configured to be able to rotate while revolving integrally.
  • the reduction ratio of the planetary gear train 4 10 is, for example, 1/432.
  • the resistance transmission wheel 480 is rotatably supported with respect to the second train wheel bridge 422 and the train wheel bridge 422.
  • the resistance transmission wheel 480 includes a resistance transmission gear 482 and a resistance transmission pinion 484.
  • the resistance transmission gear 4 8 2 has two spring portions, and is attached to the resistance transmission pin 4 8 4 so that the spring portion can slip with a predetermined slip torque against the resistance transmission pin 4 8 4. Have been.
  • the resistance transmission gear 4 82 is in mesh with the first sun kana 4 5 4 and can be rotated by the rotation of the first sun kana 4 5 4.
  • a resistance wheel 4886 is rotatably supported with respect to the second train wheel bridge 4222 and the train wheel bridge 4220.
  • the resistance wheel 4886 includes a resistance gear 4888.
  • the resistance gear 488 is engaged with the resistance transmission pinion 484, and can be rotated by the rotation of the resistance transmission pinion 484.
  • a resistance vehicle degree determining pin 4330 is provided on the second train wheel bridge 4222. Resistance degree determination pin The degree determining portion 432 of 430 is located within the notch 4888c of the resistance gear 4888.
  • the resistance lever 4 3 6 is fixed to the resistance wheel 4 8 6.
  • the resistance lever 4 3 6 can be rotated by the rotation of the resistance wheel 4 8 6.
  • the notch 4888c of the resistance gear 488 By positioning the notch 4888c of the resistance gear 488 by the resistance degree determination pin 4330, the rotation angle of the resistance gear 488 is restricted to a certain range, and accordingly, the resistance is reduced.
  • the rotation angle of the lever 4 3 6 is restricted to a certain range.
  • the resistance lever 436 has a resistance lever window 436a.
  • the resistance lever window 436a is circular, and has an inner diameter larger than the outer diameter of the balance 140.
  • the inner diameter of the resistance lever window section 436 is preferably 10 mm. That is, the radial gap SUK between the outer periphery of the balance 140 and the resistance lever window 436a is 0.8 to 1.2 millimeters (about 1 mm). preferable.
  • the thickness of the resistance lever 4 36 is 1.7 millimeters.
  • the thickness of the balance wheel of the balance 140 is 0.8 mm. That is, the thickness of the resistance lever 436 is preferably formed to be larger than the thickness of the balance wheel.
  • the position of the center of the resistance lever window 436a is positioned so as to substantially coincide with the rotation center of the balance 140 when the coil spring is completely released. . That is, FIG. 1, FIG. 3 and FIG. 4 show the relationship between the resistance lever 436 and the balance with hairspring 140 in such a state that the spring is completely unwound.
  • the radial gap SUK between the outer circumference of the balance 140 and the resistance lever window 436a is such that the rotation of the balance 140 in the state where the spring is completely unwound is caused by the resistance lever It is determined not to be affected by the window 4 3 6a.
  • the rotation direction described below indicates the direction when the front side of the element is viewed from the back lid side.
  • the rotation of the hoisting train wheel (1 12, 1 14) causes the square wheel 1 16 to rotate clockwise.
  • the planetary intermediate gear 470 since the rotation of the planetary intermediate gear 470 is regulated by the barrel gear 120a, the planetary intermediate gear 470 constitutes a "fixed gear” in the planetary gear mechanism. Due to the rotation of the square wheel 1 16, the planetary transmission wheel 4 66 rotates counterclockwise.
  • the rotation of the planetary transmission wheel 466 causes the second sun wheel 460 to rotate clockwise. Since the rotation of the planetary intermediate gear 470 is regulated, the rotation of the second sun wheel 460 causes the first planetary wheel 472 and the second planetary wheel 474 to rotate counterclockwise. .
  • the rotation of the first and second planetary wheels 47 2 and 47 4 is “rotation” in which the center of rotation does not move.
  • the resistance transmission wheel 480 rotates counterclockwise.
  • the rotation of the resistance transmission wheel 480 causes the resistance gear 488 to rotate clockwise.
  • the resistance gear 4888 rotates clockwise, at the same time, the resistance lever 4336 rotates clockwise.
  • the resistance lever 436 As the mainspring is further wound, the resistance lever 436 further rotates clockwise to the state shown in FIGS.
  • the state shown in FIGS. 6 to 8 is a "full winding" state of the mainspring.
  • the position of the resistance lever 436 in this state is regulated by the notch 4888c of the resistance gear 4888 being positioned by the resistance degree determination bin 4330.
  • the gap S UM of the portion where the gap in the radial direction between the outer peripheral portion of the balance with hairspring 140 and the resistance lever window section 436 a is minimum is 0.1 to 0. It is preferably 2 millimeters.
  • the radial gap SUM between the outer periphery of the balance 140 and the window portion 436a of the resistance lever is such that the balance with the spring fully wound up ("full wound” state) as shown in FIG.
  • the rotation of 140 is determined so as to be affected and attenuated by the resistance lever window 436a. That is, in the state shown in FIGS.
  • the flow of air between the outer periphery of the balance with hairspring 140 and the resistance lever window 436a is restricted by the flow of air between the outer periphery of the balance with hairspring 140 and the resistance lever window.
  • a resistance is applied to the balance 14a and a force that suppresses rotation of the balance 140 is applied to the balance 140.
  • the barrel gear 120a rotates to display time. At this time, the barrel gear 120a rotates clockwise.
  • the second sun wheel 460 constitutes a "fixed gear" in the planetary gear mechanism.
  • the rotation of the barrel gear 120a rotates the intermediate planetary gear 470 counterclockwise. Since the rotation of the second sun wheel 460 is regulated, the rotation of the intermediate planetary gear 470 causes the first planet wheel 472 to revolve around the second sun pinion 464 while rotating. You. Since the first planetary gear 4 7 2 and the second planetary gear 4 7 4 are integrated, the second planetary gear 4 7 4 rotates while revolving around the first sun gear 45 2.
  • first planetary wheel 472 and the second planetary wheel 474 rotate counterclockwise.
  • the rotations of the first and second planetary wheels 17 2 and 17 4 are “planetary motions” in which the center of rotation fluctuates.
  • the wheel train reduction ratio is 1/2.
  • the rotation of the second planetary wheel 4 7 4 and the planetary intermediate gear 4 7 0 causes the first sun wheel 4 50 to rotate in the counterclockwise direction.
  • the resistance transmission car 480 Rotate clockwise.
  • the rotation of the resistance transmission wheel 480 causes the resistance gear 488 to rotate counterclockwise.
  • the resistance gear 4888 rotates counterclockwise, at the same time, the resistance lever 4336 rotates counterclockwise.
  • the state shown in FIGS. 1 to 4 is a state in which the spring is completely unwound. In this state, the position of the resistance lever 436 is regulated by the notch 4888c of the resistance gear 4888 being positioned by the resistance vehicle degree determination pin 4330.
  • the gap in the radial direction between the outer periphery of the balance with hairspring 140 and the resistance lever window 436a is in a state where the mainspring is completely wound up (“full”). It is configured so that it is the smallest in the "wound” state) and the largest when the mainspring is completely unwound. Then, in a state where the mainspring is completely wound up ("full winding" state), the rotation of the balance with hairspring 140 is determined to be attenuated by being influenced most by the resistance lever window 436a. Have been.
  • the flow of air between the outer periphery of the balance 140 and the window 436a of the resistance lever is such that when the mainspring is completely wound up ("full winding" state), the balance of the balance 1 The greatest resistance is received by the outer periphery of 40 and the resistance lever window 436a, and the largest force that suppresses rotation of the balance 140 is applied to the balance 140. Then, as the mainspring is unwound from the state in which the mainspring is completely wound up ("full winding" state), the flow of air between the outer periphery of the hairspring 140 and the resistance lever window 436a is received. The resistance is reduced, and when the mainspring is completely unwound, this resistance is eliminated.
  • the rotation angle of the balance 140 Can be controlled.
  • a movement (mechanical body) 490 of the mechanical timepiece has a main plate 102T constituting a movement of the movement.
  • the outer diameter of the main plate 102 T is smaller than the outer diameter of the main plate 102.
  • the resistance lever 496 is fixed to the resistance wheel 486.
  • the resistance lever 4 3 6 can be rotated by the rotation of the resistance wheel 4 8 6.
  • the resistance lever 496 has a first arm 496a and a second arm 496b.
  • the resistance lever 496 has a resistance lever window portion 496c.
  • the resistance lever window 496c has a shape corresponding to a part of a circle, and its inner diameter is formed larger than the outer diameter of the balance 140.
  • the inner diameter of the resistance lever window 496c is preferably 10 millimeters. That is, the radial gap SUK between the outer periphery of the balance 140 and the resistance lever window 496c is preferably 0.8 to 1.2 millimeters (about 1 millimeter).
  • the thickness of the resistance lever 496 is 1.7 mm.
  • the thickness of the balance wheel of the balance 140 is 0.8 mm. That is, the thickness of the resistance lever 496 is preferably formed to be larger than the thickness of the balance wheel.
  • the position of the center of the resistance lever window 496 c is positioned so as to substantially coincide with the rotation center of the balance 140 in a state where the spring is completely released. That is, FIG. 10 and FIG. 11 show the relationship between the resistance lever 496 and the balance with hairspring 140 in such a state that the spring is completely released.
  • the radial gap SUK between the outer periphery of the balance 140 and the resistance lever window 496c is such that the rotation of the balance 140 in the state in which the spring is completely unwound, It is set so as not to be affected by the lever window 4 96 c.
  • Other parts of the structure of the mechanical timepiece according to the embodiment of the present invention are the same as the structure of the mechanical timepiece according to the embodiment of the present invention described above with reference to FIGS.
  • the resistance lever 496 rotates clockwise from the state shown in FIGS. 10 and 11.
  • the resistance lever 496 rotates further in the clockwise direction to the state shown in FIGS.
  • the state shown in FIGS. 12 and 13 is a "full winding" state of the mainspring.
  • the gap S UM of the portion where the radial gap between the outer peripheral portion of the balance with hairspring 140 and the window portion 4966 c of the resistance lever is minimum is 0. It is preferably between 1 and 0.2 millimeter.
  • the radial gap SUM between the outer periphery of the balance 140 and the resistance lever window 496c is such that the balance with the mainspring completely wound up ("full winding" state) has a balance with the balance 14
  • the rotation of 0 is determined so as to be attenuated by being affected by the resistance lever window portion 496c. That is, in the state shown in FIGS. 12 and 13, the flow of air between the outer periphery of the balance 140 and the window 496 c of the resistance lever is restricted by the flow of air between the outer periphery of the balance 140 and the resistance lever.
  • a resistance is applied to the balance with the window 496 c and a force is applied to the balance with balance 140 to suppress the rotation of the balance with balance 140.
  • the present invention provides a balance with a balance with an escapement / governing device that repeats clockwise and counterclockwise rotation, an escape wheel and wheel that rotates based on the rotation of the front train wheel, and a movement based on the operation of the balance with hairspring.
  • a mechanical timepiece configured to include an ankle for controlling the rotation of a balance wheel, a configuration having a balance rotation angle control mechanism is employed, so that the duration of the mechanical timepiece is maintained. The accuracy of the mechanical watch can be improved without reducing the time.
  • the rate is about 10 seconds / day in a state where the mainspring is completely wound (approximately 10 seconds per day). After a lapse of time, the instantaneous rate becomes about 7 seconds Z (1 about 7 seconds, advance), and after 30 hours from the full winding state, the instantaneous rate becomes about 13 seconds / day (about 3 seconds per day) Seconds late).
  • the rate is about 10 seconds / day when the mainspring is completely wound up (approximately 10 seconds per day), and 20 hours have passed since the fully wound state Then, the instantaneous rate is about 4 seconds / day (advance about 4 seconds per day), and after 30 hours from the full winding state, the instantaneous rate is about -8 seconds / day (about 8 seconds late per day) ).
  • the mechanical timepiece having the balance rotation angle control mechanism of the present invention controls the instantaneous rate of the timepiece by controlling the swing angle of the balance with hairspring. 0 to 10 seconds It is possible to keep the elapsed time from the entire volume, which is Z, long.
  • the mechanical timepiece according to the present invention has a momentary rate of about 0 to 10 seconds / day.
  • the time is about 28 hours.
  • the instantaneous rate is about 0 to 10 seconds / day and the duration is about 24 hours. Therefore, the mechanical timepiece of the present invention can make the change in the rate within 10 seconds / day approximately 1.2 times that of the conventional mechanical timepiece.
  • the mechanical timepiece of the present invention has a simple structure and is suitable for realizing a highly accurate mechanical timepiece.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Electromechanical Clocks (AREA)
  • Toys (AREA)
  • Springs (AREA)

Abstract

L'invention concerne une pièce d'horlogerie mécanique dotée d'un mouvement (400) comprenant un barillet de mouvement (120), une roue centrale (124), une troisième roue (126), une quatrième roue (128), un balancier annulaire réglé (140), une roue d'échappement (130) ainsi qu'une ancre (142). L'invention concerne notamment une pièce d'horlogerie mécanique qui comprend un mécanisme de commande de l'angle de rotation du balancier annulaire réglé, ce mécanisme étant formé de manière à offrir une résistance à l'air lors de la rotation dudit balancier (140) quand un ressort principal est totalement remonté, et à ne pas offrir de résistance à l'air lors de la rotation du balancier (140) quand le ressort principal n'est plus du tout sous tension. Le mécanisme de commande de l'angle de rotation du balancier annulaire réglé comprend des leviers de résistance (436, 496) agencés au niveau d'un espace libre situé sur la partie périphérique extérieure du balancier annulaire (140), et il est caractérisé en ce qu'il comprend un mécanisme d'engrenages planétaires (410), associé à un engrenage de barillet de mouvement (120a) et à un rochet (116).
PCT/JP1999/004077 1999-07-29 1999-07-29 Piece d'horlogerie mecanique dotee d'un mecanisme de commande de l'angle de rotation du balancier annulaire regle WO2001009686A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PCT/JP1999/004077 WO2001009686A1 (fr) 1999-07-29 1999-07-29 Piece d'horlogerie mecanique dotee d'un mecanisme de commande de l'angle de rotation du balancier annulaire regle
JP55152099A JP3565227B2 (ja) 1999-07-29 1999-07-29 てんぷ回転角度制御機構付き機械式時計
CN99813863A CN1328659A (zh) 1999-07-29 1999-07-29 具有平衡摆转角控制机构的机械表
EP99933157A EP1126333A4 (fr) 1999-07-29 1999-07-29 Piece d'horlogerie mecanique dotee d'un mecanisme de commande de l'angle de rotation du balancier annulaire regle
HK02104382.6A HK1042753A1 (zh) 1999-07-29 2002-06-11 具有平衡擺轉角控制機構的機械錶

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP1999/004077 WO2001009686A1 (fr) 1999-07-29 1999-07-29 Piece d'horlogerie mecanique dotee d'un mecanisme de commande de l'angle de rotation du balancier annulaire regle

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WO2001009686A1 true WO2001009686A1 (fr) 2001-02-08

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PCT/JP1999/004077 WO2001009686A1 (fr) 1999-07-29 1999-07-29 Piece d'horlogerie mecanique dotee d'un mecanisme de commande de l'angle de rotation du balancier annulaire regle

Country Status (5)

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EP (1) EP1126333A4 (fr)
JP (1) JP3565227B2 (fr)
CN (1) CN1328659A (fr)
HK (1) HK1042753A1 (fr)
WO (1) WO2001009686A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TW200720866A (en) * 2005-10-06 2007-06-01 Seiko Epson Corp Governor, and a power generating device and an apparatus using the governor
EP3182216B1 (fr) * 2015-12-18 2019-08-28 Montres Breguet S.A. Oscillateurs couplés d'horlogerie

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4843369A (fr) * 1971-09-27 1973-06-22
JPS4885278A (fr) * 1972-02-16 1973-11-12

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2077115A (en) * 1936-10-31 1937-04-13 Knobel Max Chronological instrument

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4843369A (fr) * 1971-09-27 1973-06-22
JPS4885278A (fr) * 1972-02-16 1973-11-12

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP1126333A4 *

Also Published As

Publication number Publication date
HK1042753A1 (zh) 2002-08-23
EP1126333A1 (fr) 2001-08-22
JP3565227B2 (ja) 2004-09-15
EP1126333A4 (fr) 2001-12-19
CN1328659A (zh) 2001-12-26

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