CN110597041B - Barrel assembly, movement and timepiece - Google Patents
Barrel assembly, movement and timepiece Download PDFInfo
- Publication number
- CN110597041B CN110597041B CN201910504780.6A CN201910504780A CN110597041B CN 110597041 B CN110597041 B CN 110597041B CN 201910504780 A CN201910504780 A CN 201910504780A CN 110597041 B CN110597041 B CN 110597041B
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- large steel
- barrel
- shaft
- wheel
- steel wheel
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- 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
- G04B1/00—Driving mechanisms
- G04B1/10—Driving mechanisms with mainspring
- G04B1/16—Barrels; Arbors; Barrel axles
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- 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
- G04B3/00—Normal winding of clockworks by hand or mechanically; Winding up several mainsprings or driving weights simultaneously
-
- 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
- G04B3/00—Normal winding of clockworks by hand or mechanically; Winding up several mainsprings or driving weights simultaneously
- G04B3/04—Rigidly-mounted keys, knobs or crowns
- G04B3/041—Construction of crowns for rotating movement; connection with the winding stem; winding stems
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- 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
- G04B33/00—Calibers
- G04B33/14—Calibers of which the mainsprings or barrels are easily removable
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- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Gears, Cams (AREA)
- Transmission Devices (AREA)
Abstract
The invention provides a barrel assembly, a movement and a timepiece, which can inhibit the sliding of a large steel wheel, improve the maintainability and realize the thinning. A barrel assembly (17) is provided with: a barrel wheel (28) that houses a mainspring (80) therein, wherein one end of the mainspring (80) is attached to the barrel wheel, and the barrel wheel rotates about a first axis (O1) in accordance with the release of the mainspring (80); a hollow barrel shaft (50) which is disposed coaxially with the first axis, supports the barrel drum (28) so as to be relatively rotatable, and to which the other end of the power spring (80) is attached; a large steel wheel shaft (60) which has an upper tenon (61) and a lower tenon (62) and is inserted into the inner side of the bar shaft in a state of being arranged coaxially with the first axis; a large steel wheel (27) which is arranged between the upper tenon and the lower tenon and is coaxial with the first axis; and D-shaped cut surfaces (57, 72) which limit the relative rotation of the bar shaft and the large steel wheel through engagement.
Description
Technical Field
The invention relates to a barrel assembly, a movement and a timepiece.
Background
Conventionally, a movement of a mechanical timepiece includes: a barrel wheel that houses a power spring; a barrel shaft rotatably supporting the barrel wheel; and a large steel wheel fixed to the barrel shaft and provided to be able to wind up the spring (see, for example, patent documents 1 and 2).
Patent document 1 describes a timepiece movement including: a barrel wheel disposed between the bottom plate and the barrel clamp plate; a barrel body disposed inside the barrel drum and having an outer peripheral end portion engaged with an inner peripheral surface of the barrel drum; a barrel shaft rotatably supported by the bottom plate and the barrel plate, the barrel shaft having an inner peripheral end of the hair line body attached thereto; and a large steel wheel which is mounted on the projecting end of the barrel shaft by a large steel wheel screw on the opposite side of the barrel plate and the barrel wheel.
Patent document 2 describes a barrel assembly for a timepiece including a barrel arbour pivoting about an axis, wherein the barrel arbour extends with a first end on a first shoulder for guiding the pivoting of the barrel arbour on a bridge and a second end on a second shoulder for guiding the pivoting of the barrel arbour on a base plate, the barrel arbour including an intermediate shoulder between the first shoulder and the second shoulder into which a core is inserted, between a barrel roller pivoting about the axis and a bearing surface of the core, a spring for the barrel being arranged: the first outer end is located on the barrel roller and the second inner end is located on the bearing surface, the barrel shaft comprises a large steel wheel retainer integrated with the barrel shaft between the first shoulder and the core, and the large steel wheel retainer comprises a shoulder for embedding or fixing a large steel wheel.
Patent document 1: japanese patent laid-open publication No. 2012-32299
Patent document 2: japanese Kohyo publication No. 2014-526688
However, in the technique described in patent document 1, since the barrel plate is disposed between the barrel wheel and the large drum, it is necessary to provide gaps both between the barrel wheel and the barrel plate and between the large drum and the barrel plate. Therefore, the interval between the barrel wheel and the large steel wheel sometimes becomes large, so that the movement becomes thick.
Further, the technique described in patent document 2 does not provide a structure for restricting relative sliding between the bar shaft and the core, or a structure for restricting relative sliding between the bar shaft and the large wheel holder. Therefore, there is a possibility that the large steel wheel and the core are relatively displaced due to the sliding of the members between the large steel wheel and the core, and the gear is damaged due to the deterioration of the meshing. In addition, in order to improve the maintainability of the movement, it is necessary to be able to separate the barrel wheel from the large steel wheel. However, if the components are firmly fixed to each other so that no slippage occurs between the large steel wheel and the core, breakage is likely to occur at the time of disassembly. Therefore, it is necessary to separate the barrel wheel from the large steel wheel and suppress the slip of the large steel wheel.
Disclosure of Invention
Therefore, the present invention provides a barrel assembly, a movement, and a timepiece, which suppress the slip of a large steel wheel, improve maintainability, and reduce the thickness.
The barrel assembly according to the present invention is characterized in that the barrel assembly includes: a barrel wheel that houses a mainspring inside, one end of the mainspring being attached to the barrel wheel, and the barrel wheel rotating around an axis line in accordance with the unwinding of the mainspring; a hollow barrel shaft disposed coaxially with the axis, supporting the barrel wheel to be relatively rotatable, and to which the other end of the mainspring is attached; a large steel wheel shaft having an upper tenon and a lower tenon and inserted inside the bar shaft in a state of being arranged coaxially with the axis; a large steel wheel arranged between the upper tenon and the lower tenon coaxially with the axis; and a relative rotation restricting unit that directly or indirectly restricts relative rotation between the bar shaft and the large steel wheel by engagement.
According to the present invention, since the large steel reel shaft is inserted inside the barrel shaft, the barrel shaft and the barrel wheel supported by the barrel shaft are disposed between the upper tenon and the lower tenon of the large steel reel shaft. Further, since the large steel wheel is also disposed between the upper tenon and the lower tenon of the large steel wheel shaft, the large steel wheel and the barrel wheel are disposed between the member that pivotally supports the upper tenon and the member that pivotally supports the lower tenon. Thus, the distance between the large steel wheel and the barrel wheel can be reduced as compared with the case where the cleat is disposed between the large steel wheel and the barrel wheel as in the conventional art. Therefore, the barrel assembly is thinned.
Further, since the relative rotation between the barrel shaft and the large steel wheel is restricted by the engagement, the large steel wheel can be easily separated from the barrel drum supported by the barrel shaft, as compared with a structure in which the relative rotation between the barrel shaft and the large steel wheel is restricted by a frictional force such as press fitting. Thus, a barrel assembly can be provided: the large steel wheel is suppressed from slipping and the maintainability is improved.
In the magazine assembly, it is preferable that the large steel wheel is formed with an insertion portion into which the bar shaft is inserted, and the large steel wheel is engaged with the bar shaft in a circumferential direction around the axis.
According to the present invention, the relative rotation between the large steel wheel and the bar shaft inserted into the insertion portion of the large steel wheel can be restricted without using friction. Therefore, the large steel wheel can be assembled to such an extent that it can be removed from the bar shaft. Thereby, the large steel wheel can be easily separated from the barrel wheel supported by the barrel shaft. Therefore, the magazine assembly in which the improvement of the maintainability is achieved can be provided.
In the above strip cassette assembly, it is preferable that the large steel reel includes a protrusion protruding in a direction perpendicular to the axis, and the large steel reel contacts the protrusion at a position of at least 3 points or more around the axis when viewed in an axial direction of the axis.
According to the present invention, the following can be suppressed by the protrusion: the large steel wheel is inclined from a state of being arranged coaxially with the axis. Thereby, the following is suppressed: the large steel wheel is inclined and contacts with the barrel wheel or the member for supporting the large steel wheel shaft, so that the interval between the large steel wheel and the barrel wheel and the interval between the large steel wheel and the member for supporting the large steel wheel shaft can be reduced. Therefore, the barrel assembly can be thinned.
Further, an increase in the rotational load accompanying contact with the large steel wheel can be suppressed.
In the above strip cassette assembly, preferably, the large steel wheel is sandwiched between the protruding portion and the strip shaft.
According to the present invention, the movement of the large steel wheel in the axial direction can be restricted by the projection and the bar shaft. This suppresses contact between the large steel wheel and the barrel wheel or the member for pivotally supporting the large steel wheel shaft, and thus the distance between the large steel wheel and the barrel wheel and the distance between the large steel wheel and the member for pivotally supporting the large steel wheel shaft can be reduced. Therefore, the barrel assembly can be thinned.
Further, an increase in the rotational load accompanying contact with the large steel wheel can be suppressed.
In the above strip cassette assembly, preferably, the large steel wheel shaft is screwed into the strip shaft.
According to the invention, the bar shaft is firmly fixed to the large steel wheel shaft. Therefore, the following can be suppressed: the barrel wheel supported by the barrel shaft is displaced relative to the large steel wheel shaft, and the barrel wheel is tilted from a state of being arranged coaxially with the axis. This suppresses the barrel from tilting and coming into contact with the member that pivotally supports the large steel wheel shaft, and therefore the distance between the barrel and the member that pivotally supports the large steel wheel shaft can be further reduced. Therefore, the barrel assembly can be thinned.
Further, an increase in the rotational load accompanying the contact with the barrel wheel can be suppressed.
Further, the large steel wheel shaft can be easily separated from the bar shaft. Therefore, the magazine assembly in which the improvement of the maintainability is achieved can be provided.
In the above strip cassette assembly, preferably, the large steel wheel shaft has a fitting portion to be fitted with the strip shaft.
According to the present invention, the bar shaft and the large steel wheel shaft can be maintained in a coaxial arrangement by fitting the bar shaft to the fitting portion. Therefore, the following can be suppressed: the coaxiality of the bar shaft and the large steel axle is deteriorated due to manufacturing deviation (eccentricity) of the external thread of the large steel axle and the internal thread of the bar shaft. Therefore, the barrel assembly assembled with high precision can be provided.
In the above strip cassette assembly, preferably, the large steel wheel shaft is pressed into the strip shaft.
According to the invention, the bar shaft is firmly fixed to the large steel wheel shaft. Therefore, the following can be suppressed: the barrel wheel supported by the barrel shaft is displaced relative to the large steel wheel shaft, and the barrel wheel is tilted from a state of being arranged coaxially with the axis. This suppresses the barrel wheel from tilting and coming into contact with the member that pivotally supports the large steel wheel shaft, and therefore the distance between the barrel wheel and the member that pivotally supports the large steel wheel shaft can be reduced. Therefore, the barrel assembly can be thinned.
Further, an increase in the rotational load accompanying the contact with the barrel wheel can be suppressed.
Further, the large steel wheel shaft can be easily separated from the bar shaft. Therefore, the magazine assembly in which the improvement of the maintainability is achieved can be provided.
In the above strip cassette assembly, it is preferable that a through hole penetrating in the axial direction is formed in the large steel reel at a position overlapping at least one of the strip shaft and the large steel reel when viewed in the axial direction of the axis.
According to the present invention, by pressing one of the bar shaft and the large steel wheel through the through hole, the one member can be displaced in the axial direction of the axis line with respect to the large steel wheel shaft. This makes it possible to easily separate one member from the large steel axle. Therefore, the magazine assembly in which the improvement of the maintainability is achieved can be provided.
The movement of the present invention is characterized by including the barrel unit described above.
A timepiece of the present invention is characterized by including the movement described above.
According to the present invention, a movement and a timepiece which are thin and have excellent maintainability can be provided.
According to the present invention, it is possible to provide a barrel assembly, a movement, and a timepiece, in which the slip of a large steel wheel is suppressed, the maintainability is improved, and the thickness is reduced.
Drawings
Fig. 1 is a plan view of a movement of a first embodiment.
Fig. 2 is a cross-sectional view of the barrel assembly of the first embodiment.
Fig. 3 is a plan view showing the large steel wheel, the barrel wheel, and the barrel shaft of the first embodiment.
Fig. 4 is a cross-sectional view of a barrel assembly of a second embodiment.
Fig. 5 is a cross-sectional view of a third embodiment barrel assembly.
Fig. 6 is a cross-sectional view of a barrel assembly of a fourth embodiment.
Fig. 7 is a sectional view taken along line VII-VII in fig. 6.
Description of the reference symbols
1: a timepiece; 2: a movement; 17. 117, 217, 317: a barrel assembly; 27. 227, 327: a large steel wheel; 28: a barrel wheel; 50. 150, 350: a bar shaft; 57: a D-shaped section (relative rotation restricting section); 60. 160, 360: a large steel axle; 61: an upper tenon; 62: a lower tenon; 64: a flange (projection); 66: a fitting portion; 71: a shaft hole (insertion section); 72: a D-shaped section (relative rotation restricting section); 80: a clockwork spring; 165. 365: a through hole; 358: a groove portion (relative rotation restricting portion); 368: a fitting projection (relative rotation restricting portion); o1: a first axis (axis).
Detailed Description
Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following description, the same reference numerals are given to the same or similar structures having the same or similar functions. Moreover, a repetitive description of these structures may be omitted.
[ first embodiment ]
In general, a mechanical body including a drive portion of a timepiece is referred to as a "movement". The state in which the dial, the hands, are mounted to the movement and put into the timepiece case to be formed into a finished product is referred to as a "finished product" of the timepiece. Of the two sides of the bottom plate constituting the base plate of the timepiece, the side on which the glass of the timepiece case is present (i.e., the side on which the dial is present) is referred to as the "back side" of the movement. Of the two sides of the bottom plate, the side on which the case back cover of the timepiece case is present (i.e., the side opposite to the dial) is referred to as the "front side" of the movement.
In the present embodiment, the direction from the dial toward the case back will be described as the upper side, and the opposite side will be described as the lower side.
Fig. 1 is a plan view of a movement of a first embodiment.
As shown in fig. 1, the timepiece 1 of the present embodiment is a mechanical timepiece, and includes a movement 2 and a timepiece case, not shown, that houses the movement 2.
The timepiece case includes a case back cover and a glass, not shown, and includes: a dial, not shown, having at least a scale indicating information on hours; and hands (i.e., hour hand indicating hour, minute hand indicating minute, and second hand indicating second) not shown, which indicate scales.
The movement 2 includes a base plate 10 constituting a base plate, a barrel plate 11 disposed above the base plate 10, a wheel train support 12, and a swing plate 13. Between the barrel plate 11, the gear train support 12, and the swing plate 13, and the base plate 10, a face-side gear train 14, an escapement 15 that controls rotation of the face-side gear train 14, and a governor 16 that regulates speed of the escapement 15 are mainly arranged. A dial, not shown, is disposed on the back side of the base plate 10.
A stem guide hole 20 is formed in the base plate 10, and a stem 21 is rotatably assembled to the stem guide hole 20. The stem 21 is positioned in the axial direction by a switching device having a pull-out piece 22, a clutch lever 23, a clutch lever spring 24, and a pull-out pressure spring 25. A vertical wheel, not shown, is rotatably provided on the guide shaft portion of the stem 21.
When the stem 21 is rotated, the vertical wheel is rotated by rotation of a clutch wheel, not shown. By the rotation of the vertical wheel, the small steel wheel 26 engaged therewith rotates. By the rotation of the small steel wheel 26, the large steel wheel 27 engaged therewith rotates. The rotation of the large steel wheel 27 winds up a spring 80 (see fig. 2) as a power source housed in the barrel wheel 28.
The front side gear train 14 mainly includes the barrel wheel 28, the second wheel 30, the third wheel 35, and the fourth wheel 36. The second, third and fourth wheels 30, 35 and 36 are sequentially rotated with the rotation of the barrel wheel 28, wherein the barrel wheel 28 is rotated by the elastic restoring force of the wound spring 80.
The second hand rotates based on the rotation of the fourth wheel 36, and rotates at a rotation speed regulated by the escapement 15 and the governor 16, that is, 1 turn for 1 minute. The minute hand rotates based on the rotation of the second wheel 30 or the rotation of a minute wheel not shown, which rotates with the rotation of the second wheel 30, and rotates at a rotation speed regulated by the escapement 15 and the governor 16, that is, 1 hour and 1 turn. The hour hand rotates by the rotation of an hour wheel, not shown, which rotates by the rotation of the second wheel 30 by a straddle wheel, not shown, and rotates 1 revolution at a rotation speed regulated by the escapement 15 and the governor 16, that is, 12 hours or 24 hours.
The escapement 15 includes: an escape wheel 37 that meshes with the quarter wheel 36 and rotates by the power transmitted from the mainspring 80; and a pallet 38 for escapement of the escape wheel 37 and regularly and correctly rotating, and the escapement 15 controls the front side train wheel 14 by regularly and correctly oscillating from the balance spring mechanism 39.
The governor 16 mainly includes a balance spring mechanism 39, and the balance spring mechanism 39 is configured to rotate reciprocally (rotate forward and backward) at a stable amplitude (swing angle) corresponding to the output torque of the barrel drum 28, using a balance spring (not shown) as a power source.
The large steel wheel 27 is disposed coaxially with the first axis O1. A large steel wheel tooth portion 27a that meshes with the small steel wheel 26 is formed on the outer periphery of the large steel wheel 27 over the entire circumference. The large steel wheel 27 rotates in the first rotational direction M1 about the first axis O1 in accordance with the rotation of the small steel wheel 26, and the power spring 80 can be wound up. Further, the power accumulated by the spring 80 is applied to the large wheel 27 in the second rotational direction M2 opposite to the first rotational direction M1 by the elastic restoring force when the spring 80 is unwound.
The pawl 90 for restricting the reverse rotation of the large steel wheel 27 is engaged with the large steel wheel 27 to prevent the wound spring 80 from being unwound. The pawl 90 is disposed at a position not overlapping the large sheave 27 in the vertical direction, is pivotally supported by the barrel plate 11 so as to be swingable about the third axis O3, and has an engagement tooth portion 90a with which the large sheave tooth portion 27a is engaged, for example. When the large steel wheel 27 rotates in the first rotation direction M1, the pawl 90 rotates in the third rotation direction M3 about the third axis O3 from the engagement position (the position shown in fig. 1) where the engagement tooth portion 90a and the large steel wheel tooth portion 27a are engaged with each other, and can swing to the release position where the engagement between the engagement tooth portion 90a and the large steel wheel tooth portion 27a is released.
The pawl 90 is biased from the release position toward the engagement position about the third axis O3 by a spring force from a pawl spring, not shown. Thereby, the large steel wheel 27 can rotate in the first rotation direction M1 against the spring force (elastic force) of the pawl spring, so that the engagement teeth 90a of the pawls 90 can ride over the large steel wheel teeth 27a one by one.
The pawl 90 is limited to the following: from the engagement position where the engagement tooth portion 90a is engaged with the large spur tooth portion 27a, the rotation is in the fourth rotation direction M4 opposite to the third rotation direction M3 about the third axis O3. Thereby, rotation of the large steel wheel 27 in a first rotational direction M1 is permitted, but rotation in a second rotational direction M2 opposite to the first rotational direction M1 is restricted by the pawl 90. Thereby, as described above, the large steel wheel 27 is prevented from being reversed, and only the large steel wheel 27 is allowed to rotate in the first rotation direction M1.
The barrel assembly 17 including the barrel 28 and bull wheel 27 described above is described in detail below.
Fig. 2 is a cross-sectional view of the barrel assembly of the first embodiment.
As shown in fig. 2, the barrel assembly 17 includes a barrel drum 28, a barrel shaft 50, a large steel reel shaft 60, and a large steel reel 27.
The case main body 45 includes: a bottom wall portion 45a formed in a disc shape centered on the first axis O1; and a peripheral wall 45b formed to extend upward along the outer peripheral edge of the bottom wall 45a, and the peripheral wall 45b surrounds the spring 80 from the radially outer side.
A first fitting hole 47 that vertically penetrates the bottom wall portion 45a is formed in a central portion of the bottom wall portion 45 a. The above-described barrel tooth portion 28a is formed on the outer peripheral edge portion of the bottom wall portion 45 a. The outer end of the spring 80 is attached to the inner peripheral surface of the bottom wall 45 a.
The lid 46 is formed in a disc shape centered on the first axis O1, and closes the opening of the peripheral wall 45b of the housing body 45 from above. The outer peripheral edge of the lid 46 is fitted to the upper end of the peripheral wall 45b of the case body 45. Thereby, the barrel cover 46 and the case main body 45 are combined with each other as one body. A second fitting hole 49 is formed in the center of the barrel cover 46 so as to vertically penetrate the barrel cover 46.
The bar shaft 50 is formed in a cylindrical shape penetrating vertically. The bar shaft 50 is disposed coaxially with the first axis O1. The barrel shaft 50 is inserted through the first fitting hole 47 and the second fitting hole 49 of the barrel wheel 28. The inner circumferential surface of the cylindrical shaft 50 is formed with a female screw 51 and a fitting surface 58. The female screw 51 is provided in the upper and lower intermediate portions of the inner peripheral surface of the bar shaft 50. The fitting surface 58 is provided at an upper end portion of the inner peripheral surface of the bar shaft 50. The fitting surface 58 extends in the vertical direction with a constant inner diameter around the first axis O1. The large steel axle 60 is clearance-fitted (fitted) to the fitting surface 58.
The vertical intermediate portion 52 of the outer peripheral surface of the linear shaft 50 bulges radially outward beyond the upper and lower portions of the outer peripheral surface. The inner end portion of the power spring 80 is engaged with the vertically intermediate portion 52 of the outer peripheral surface of the bar shaft 50. The lower portion of the outer peripheral surface of the shaft 50 is adjacent to the upper and lower intermediate portions 52 of the outer peripheral surface via the first step surface 53. First step surface 53 extends along a vertical plane perpendicular to first axis O1, and faces downward. The upper portion of the outer peripheral surface of the shaft 50 is adjacent to the upper and lower intermediate portions 52 of the outer peripheral surface via the second step surface 54. The second step surface 54 extends along a vertical plane perpendicular to the first axis O1, and faces upward.
The first fitting hole 47 of the barrel wheel 28 is fitted to a lower portion of the outer peripheral surface of the barrel shaft 50 so as to be rotatable relative to the barrel shaft 50 about the first axis O1. The second fitting hole 49 of the barrel wheel 28 is fitted to an upper portion of the outer peripheral surface of the barrel shaft 50 so as to be rotatable relative to the barrel shaft 50 about the first axis O1. Thereby, the barrel shaft 50 supports the barrel drum 28 to be relatively rotatable. The inner peripheral portion of the first fitting hole 47 is adjacent to and opposed to the first stepped surface 53 of the shaft 50 from below. The inner peripheral portion of the second fitting hole 49 abuts against the second stepped surface 54 of the shaft 50 from above. Thereby, the movement of the barrel wheel 28 in the up-down direction with respect to the barrel shaft 50 is restricted.
A third stepped surface 55 is formed on the upper portion of the outer peripheral surface of the linear shaft 50. The third step surface 55 is formed above the barrel wheel 28. The third step surface 55 is formed in an annular shape coaxial with the first axis O1. The third step surface 55 extends along a vertical plane perpendicular to the first axis O1, and faces upward. Thus, the upper portion of the outer peripheral surface of the linear shaft 50 above the third stepped surface 55 is formed to have a smaller diameter than the lower portion. Hereinafter, a portion of the shaft 50 above the third stepped surface 55 is referred to as a small diameter portion 56. The small diameter portion 56 is an upper end portion of the bar shaft 50. A flat D-shaped cut surface 57 (relative rotation restricting portion) is formed on a part of the outer peripheral surface of the small diameter portion 56. The D-shaped cut surface 57 will be described later.
The large steel axle 60 is a shaft member extending up and down. The large steel axle 60 is disposed coaxially with the first axis O1. The large steel axle 60 is inserted inside the bar shaft 50. The large steel axle 60 has: an upper tenon 61 formed at the upper end; a lower tenon 62 formed at a lower end portion; an external thread 63 formed between the upper tenon 61 and the lower tenon 62; a flange 64 (projection) provided between the external thread 63 and the upper tenon 61; and a fitting portion 66 provided between the male screw 63 and the flange 64. The upper tenon 61 protrudes upward from the bar shaft 50. The upper tenon 61 is directly or indirectly supported by a bearing to the barrel plate 11 (see fig. 1). The lower tenon 62 protrudes downward from the bar shaft 50. The lower tenon 62 is axially supported by the base plate 10 (see fig. 1) directly or indirectly via a bearing at a position below the bar shaft 50. The external thread 63 is screwed with the internal thread 51 of the bar shaft 50. Thereby, the large steel wheel shaft 60 is screwed into the bar shaft 50 and fixed to the bar shaft 50.
The flange 64 projects toward the radially outer side. The flange 64 extends annularly around the entire circumference of the large steel axle 60. The upper and lower surfaces of the flange 64 each extend along a vertical plane perpendicular to the first axis O1. The flange 64 has an outer diameter at least larger than the outer diameter of the upper end portion of the bar shaft 50. A recess 65 recessed downward is formed on the upper surface of the flange 64. In the present embodiment, the recess 65 penetrates the flange 64 vertically.
As shown in fig. 1, a plurality of recesses 65 (2 in the illustrated example) are formed. The plurality of recesses 65 are arranged at equal angular intervals in the circumferential direction. The recess 65 is formed in a circular shape when viewed from the up-down direction. When screwing the large steel axle 60 into the bar shaft 50 (see fig. 2) and when disassembling the large steel axle 60 and the bar shaft 50, the tool is simultaneously inserted into the plurality of recesses 65. Thereby, the large steel spindle 60 and the tool are engaged with each other in the circumferential direction, and the large steel spindle 60 can be rotated by the tool.
As shown in fig. 2, the fitting portion 66 is adjacent to the flange 64 at the lower side. The outer peripheral surface of the fitting portion 66 extends in the vertical direction with a constant outer diameter around the first axis O1. The fitting portion 66 is formed to have a diameter larger than that of a portion of the large steel axle 60 adjacent to the fitting portion 66 at the lower side. The fitting portion 66 is loosely fitted to the fitting surface 58 of the shaft 50.
A shaft hole 71 (insertion portion) into which the small diameter portion 56 of the bar shaft 50 is inserted is formed vertically through the center of the large steel wheel 27. The large steel wheel 27 is externally fitted to the small diameter portion 56 of the barrel shaft 50 from above. The large steel wheel 27 is disposed between the upper tenon 61 and the lower tenon 62 of the large steel wheel shaft 60 in the vertical direction. The large steel wheel 27 is disposed between the barrel wheel 28 and the flange 64 of the large steel wheel shaft 60. The upper and lower surfaces of the large steel wheel 27 extend along vertical planes perpendicular to the first axis O1, respectively. The upper surface of the large steel wheel 27 is in surface contact with the lower surface of the flange 64 of the large steel axle 60. Thereby, the large steel wheel 27 contacts the flange 64 so as to surround the first axis O1. The lower surface of the large steel wheel 27 is in surface contact with the third step surface 55 of the bar shaft 50. Thereby, the large steel wheel 27 is sandwiched between the flange 64 of the large steel wheel shaft 60 and the bar shaft 50. The lower surface of large steel wheel 27 is spaced from the upper surface of barrel wheel 28.
Fig. 3 is a plan view showing the large steel wheel, the barrel wheel, and the barrel shaft of the first embodiment.
As shown in fig. 3, a planar D-shaped cut surface 72 (relative rotation restricting portion) is formed on the inner peripheral surface of the shaft hole 71. The D-shaped cut surface 72 of the large steel wheel 27 and the D-shaped cut surface 57 of the bar shaft 50 are engaged with each other in the circumferential direction. Thus, D-shaped cut surface 72 of large steel wheel 27 and D-shaped cut surface 57 of bar shaft 50 limit the relative rotation of bar shaft 50 and large steel wheel 27. That is, the large steel wheel 27 is directly engaged with the barrel shaft 50 and is restricted from relative rotation. The large steel wheel 27 is indirectly fixed to a large steel wheel shaft 60 (see fig. 2) via a bar shaft 50.
As described above, the barrel unit 17 according to the present embodiment includes: a hollow bar shaft 50; a large steel wheel shaft 60 having an upper tenon 61 and a lower tenon 62 and inserted inside the bar shaft 50 in a state of being disposed coaxially with the first axis O1; a large steel wheel 27 disposed between the upper tenon 61 and the lower tenon 62 coaxially with the first axis O1; and a D-shaped section 57 of the bar shaft 50 and a D-shaped section 72 of the large steel wheel 27, which directly restrict the relative rotation of the bar shaft 50 and the large steel wheel 27 by engaging with each other.
According to this configuration, since the large steel reel shaft 60 is inserted inside the barrel shaft 50, the barrel shaft 50 and the barrel drum 28 supported by the barrel shaft 50 are disposed between the upper tenon 61 and the lower tenon 62 of the large steel reel shaft 60. Further, since the large sheave 27 is also disposed between the upper tenon 61 and the lower tenon 62 of the large sheave shaft 60, the large sheave 27 and the barrel sheave 28 are disposed between the barrel plate 11 that pivotally supports the upper tenon 61 and the bottom plate 10 that pivotally supports the lower tenon 62. This makes it possible to reduce the distance between the large drum 27 and the barrel drum 28, as compared with the case where the cleat is disposed between the large drum and the barrel drum as in the conventional art. Therefore, the barrel assembly 17 can be thinned.
Further, since the relative rotation between the barrel shaft 50 and the large steel wheel 27 is restricted by the engagement, the large steel wheel 27 and the barrel drum 28 supported by the barrel shaft 50 can be easily separated from each other, as compared with a structure in which the relative rotation between the barrel shaft and the large steel wheel is restricted by a frictional force such as press fitting. Thus, it is possible to provide a barrel assembly 17: the large steel wheel 27 is suppressed from sliding with respect to the bar shaft 50, and the maintainability is improved.
Further, a shaft hole 71 into which the bar shaft 50 is inserted is formed in the large steel wheel 27, and the large steel wheel 27 and the bar shaft 50 are engaged in the circumferential direction. According to this structure, the relative rotation between the large steel wheel 27 and the bar shaft 50 inserted into the shaft hole 71 of the large steel wheel 27 can be restricted without using frictional force. Therefore, the large steel wheel 27 can be assembled to such an extent that it can be detached from the bar shaft 50. This makes it possible to easily separate the large steel wheel 27 from the barrel wheel 28 supported by the barrel shaft 50. Therefore, the barrel assembly 17 can be provided with improved maintainability.
The large steel reel 60 includes a flange 64 projecting in a radial direction perpendicular to the first axis O1, and the large steel reel 27 contacts the flange 64 so as to surround the first axis O1. According to this structure, the following can be suppressed by the flange 64: the large steel wheel 27 is tilted from a state of being disposed coaxially with the first axis O1. Thereby, the following is suppressed: since the large steel wheel 27 is inclined to contact the barrel 28 or the barrel plate 11 pivotally supporting the large steel wheel shaft 60, the distance between the large steel wheel 27 and the barrel 28 and the distance between the large steel wheel 27 and the barrel plate 11 can be reduced. Therefore, the barrel assembly 17 can be thinned. Further, an increase in the rotational load associated with the contact between the large steel wheel 27 and the barrel wheel 28 or the barrel plate 11 can be suppressed.
The large steel wheel 27 can achieve the above-described effects by only contacting the flange 64 at a position of at least 3 points or more around the first axis O1 when viewed in the vertical direction.
Furthermore, the large steel wheel 27 is separated from the barrel wheel 28. According to this structure, the large steel wheel 27 is suppressed from contacting the barrel wheel 28. Therefore, an increase in the rotational load accompanying the contact between the large steel wheel 27 and the barrel wheel 28 can be suppressed.
Further, the large steel wheel 27 is sandwiched by the flange 64 and the bar shaft 50. According to this configuration, the vertical movement of the large steel wheel 27 can be restricted by the flange 64 and the bar shaft 50. This suppresses contact between the large steel wheel 27 and the barrel wheel 28 or the barrel plate 11 that pivotally supports the large steel wheel shaft 60, and thus the distance between the large steel wheel 27 and the barrel wheel 28 and the distance between the large steel wheel 27 and the barrel plate 11 can be reduced. Therefore, the barrel assembly 17 can be thinned. Further, an increase in the rotational load associated with the contact between the large steel wheel 27 and the barrel wheel 28 or the barrel plate 11 can be suppressed.
Further, a large steel wheel axle 60 is screwed into the bar axle 50. According to this structure, the bar shaft 50 is firmly fixed to the large steel axle 60. Therefore, the barrel wheel 28 supported by the barrel shaft 50 can be prevented from being displaced relative to the large steel shaft 60 and from being tilted from the state in which the barrel wheel 28 is disposed coaxially with the first axis O1. This suppresses the barrel wheel 28 from tilting and coming into contact with the bottom plate 10 that pivotally supports the large steel wheel shaft 60, and therefore the distance between the barrel wheel 28 and the bottom plate 10 can be reduced. Therefore, the barrel assembly 17 can be thinned. Further, an increase in rotational load associated with contact between the barrel wheel 28 and the bottom plate 10 can be suppressed. Further, the large steel axle 60 can be easily separated from the bar shaft 50. Therefore, the barrel assembly 17 can be provided with improved maintainability.
The large steel wheel shaft 60 has a fitting portion 66 fitted to the bar shaft 50. According to this configuration, the clearance fit between the bar shaft 50 and the fitting portion 66 suppresses the coaxiality between the bar shaft 50 and the large steel axle 60 to be smaller than the clearance between the fitting surface 58 of the bar shaft 50 and the fitting portion 66, and the state in which the bar shaft 50 and the large steel axle 60 are coaxially arranged can be maintained. Therefore, such a situation can be suppressed: the coaxiality of the bar shaft 50 and the large steel spindle 60 deteriorates due to manufacturing variations (eccentricity) of the internal thread 51 of the bar shaft 50 and the external thread 63 of the large steel spindle 60. Therefore, the barrel assembly 17 can be assembled with high accuracy.
Further, since the movement 2 and the timepiece 1 of the present embodiment include the barrel assembly 17 described above, a movement and a timepiece which are thin and have excellent maintainability can be realized.
[ second embodiment ]
Next, a second embodiment will be described with reference to fig. 4. In the first embodiment, the large steel wheel axle 60 is screwed into the bar axle 50. In contrast, the second embodiment differs from the first embodiment in that the large steel spindle 160 is press-fitted into the bar shaft 150. The configuration other than the following description is the same as that of the first embodiment.
Fig. 4 is a cross-sectional view of a barrel assembly of a second embodiment.
As shown in fig. 4, a press-fitting surface 151 into which a large steel wheel axle 160 is press-fitted is formed on the inner peripheral surface of the bar shaft 150 of the second embodiment, instead of the female screw 51 of the bar shaft 50 of the first embodiment. A press-fitting surface 163 into which the bar shaft 150 is press-fitted is formed on the outer peripheral surface of the large steel axle 160 of the second embodiment, and the male screw 63 of the large steel axle 60 of the first embodiment is substituted. Thereby, the large steel wheel shaft 160 is pressed into the bar shaft 150 and fixed to the bar shaft 150.
Instead of the recess 65 of the first embodiment, a through hole 165 penetrating vertically is formed in the flange 64 of the large steel axle 160. The through hole 165 is formed at a position overlapping the large steel wheel 27 when viewed in the vertical direction. Further, a notch 166 recessed radially inward is formed in the outer peripheral surface of the flange 64 of the large steel axle 160. The recess 166 opens so as to span both the outer peripheral surface and the lower surface of the flange 64. When disassembling the large steel reel 160 and the bar shaft 150, the first tool is inserted into the through hole 165 from above and presses the bar shaft 150 via the large steel reel 27, and the second tool is engaged with the notch 166 and separates the flange 64 from the large steel reel 27. This allows the large steel spindle 160 to be pulled out from the inside of the bar shaft 150.
In this way, in the present embodiment, the large steel wheel shaft 160 is press-fitted into the bar shaft 150. According to this structure, the bar shaft 150 is firmly fixed to the large steel wheel shaft 160. Therefore, the following can be suppressed: the barrel drum 28 supported by the barrel shaft 150 is displaced relative to the large steel reel shaft 160, and the barrel drum 28 tilts from the state of being arranged coaxially with the first axis O1. This suppresses the barrel wheel 28 from tilting and coming into contact with the bottom plate 10 that pivotally supports the large steel axle 160, and therefore the distance between the barrel wheel 28 and the bottom plate 10 can be reduced. Therefore, the barrel assembly 117 can be thinned. Further, an increase in rotational load associated with contact between the barrel wheel 28 and the bottom plate 10 can be suppressed. Also, the large steel axle 160 can be easily separated from the bar shaft 150. Therefore, the barrel assembly 117 in which the maintainability is improved can be provided.
The large steel hub 160 has a through hole 165 penetrating in the vertical direction at a position overlapping the large steel wheel 27 when viewed in the vertical direction. According to this configuration, the large steel wheel 27 can be displaced in the vertical direction with respect to the large steel wheel shaft 160 by pressing the large steel wheel 27 through the through hole 165. This makes it possible to easily separate the large steel wheel 27 from the large steel wheel shaft 160. Therefore, the barrel assembly 117 in which the maintainability is improved can be provided.
[ third embodiment ]
Next, a third embodiment will be described with reference to fig. 5. The third embodiment is different from the first embodiment in that a pin 273 is inserted into the through hole 165 of the flange 64 of the large steel axle 160. The configuration other than the following description is the same as that of the second embodiment.
Fig. 5 is a cross-sectional view of a third embodiment barrel assembly.
As shown in fig. 5, the large steel wheel 227 is provided with a pin 273 protruding upward. The pin 273 is pressed into a pin insertion hole 274 formed in the large steel wheel 227. In addition, the pin 273 may be pressed into a recess formed in the upper surface of the large steel wheel 227. Further, the pin 273 may be formed integrally with the large steel wheel 227. The pin 273 is inserted from below into the through hole 165 of the flange 64 of the large steel axle 160. Thereby, the large steel wheel 227 and the large steel wheel shaft 160 are engaged with each other in the circumferential direction, and the relative rotation is restricted. The pin 273 is formed to have a diameter equal to or smaller than the diameter of the through hole 165 of the flange 64 when viewed in the vertical direction. In the present embodiment, the pin 273 is formed in a cylindrical shape having a diameter slightly smaller than the diameter of the through hole 165. For example, the upper surface of the pin 273 is flush with the upper surface of the flange 64.
In this way, in the barrel unit 217 of the present embodiment, the large steel wheel 227 and the large steel wheel shaft 160 are engaged with each other in the circumferential direction to restrict the relative rotation, and therefore, the slip of the large steel wheel 227 can be suppressed more reliably.
[ fourth embodiment ]
Next, a fourth embodiment will be described with reference to fig. 6 and 7. In the second embodiment, the large steel wheel 27 is indirectly fixed to the large steel wheel shaft 160 through the bar shaft 150. In contrast, the fourth embodiment is different from the second embodiment in that the large steel wheel 327 is directly fixed to the large steel wheel shaft 360. The configuration other than the following description is the same as that of the second embodiment.
Fig. 6 is a cross-sectional view of a barrel assembly of a fourth embodiment. Fig. 7 is a sectional view taken along line VII-VII in fig. 6.
As shown in fig. 6 and 7, a groove 358 (relative rotation restricting portion) is formed at the upper end of the bar shaft 350. The groove portion 358 extends along a predetermined straight line perpendicular to the first axis O1. The groove 358 opens upward and radially outward.
The large steel hub 360 has a large diameter portion 367 and an engagement projection 368 (relative rotation restricting portion). The large diameter portion 367 is adjacent to the flange 64 at the lower side. The large diameter portion 367 is formed in a cylindrical shape having a diameter smaller than that of the flange 64 and larger than the diameter of the upper end portion of the bar shaft 350. A press-fitting surface 367a into which the large steel wheel 327 is press-fitted is formed on the outer peripheral surface of the large diameter portion 367. The large diameter portion 367 is press-fitted into the shaft hole 371 of the large steel wheel 327. Thus, the large steel wheel 327 is directly fixed to the large steel axle 360. The large steel wheel 327 and the large steel wheel shaft 360 may be engaged with each other in the circumferential direction by a D-shaped cut surface or the like.
The fitting projection 368 projects downward from the lower surface of the large diameter portion 367. The fitting protrusion 368 enters the groove portion 358 of the bar shaft 350. Thus, the fitting projection 368 of the large steel hub 360 and the groove 358 of the bar shaft 350 indirectly restrict the relative rotation of the bar shaft 350 and the large steel wheel 327 through the large steel hub 360. The fitting projection 368 extends along the extending direction of the groove 358. The width of the fitting projection 368 is slightly smaller than the width of the groove 358. The fitting projections 368 project from the groove 358 toward both radial sides. The outer peripheral surface of the fitting projection 368 is formed flush with the outer peripheral surface of the large diameter portion 367. The fitting projection 368 abuts against the bottom surface of the groove 358 from above.
A through hole 365 that penetrates vertically is formed in the large steel axle 360 instead of the through hole 165 of the large steel axle 160 of the second embodiment. The through-hole 365 is formed at a position overlapping the upper end surface of the bar shaft 350 when viewed in the vertical direction. The through hole 365 vertically penetrates both the flange 64 and the large diameter portion 367. When the large steel wheel shaft 360 and the bar shaft 350 are disassembled, a tool is inserted into the through hole 365 from above to press the upper end portion of the bar shaft 350. Thereby, the large steel hub 360 can be pulled out from the inside of the bar shaft 350.
As described above, the barrel unit 317 of the present embodiment includes the groove portion 358 of the barrel shaft 350 and the fitting projection 368 of the large steel wheel shaft 360, and these engage with each other to indirectly restrict the relative rotation between the barrel shaft 350 and the large steel wheel 327. According to this configuration, since the relative rotation between the barrel shaft 350 and the large steel wheel 327 is restricted by the engagement, the large steel wheel 327 can be easily separated from the barrel drum 28 supported by the barrel shaft 350, as compared with a configuration in which the relative rotation between the barrel shaft and the large steel wheel is restricted by a frictional force such as press fitting. Thus, a barrel assembly 317 can be provided: the large steel wheel 327 is suppressed from sliding with respect to the bar shaft 350 and the maintainability is improved.
Further, a through hole 365 penetrating in the vertical direction is formed in the large steel wheel shaft 360 at a position overlapping the bar shaft 350 when viewed in the vertical direction. According to this configuration, the bar shaft 350 is pushed through the through hole 365, whereby the bar shaft 350 can be displaced in the vertical direction with respect to the large steel axle 360. This allows the bar shaft 350 to be easily separated from the large steel wheel shaft 360. Therefore, the barrel assembly 317 in which the improvement of the maintainability is achieved can be provided.
The present invention is not limited to the above-described embodiments described with reference to the drawings, and various modifications can be considered within the technical scope thereof.
For example, in the first embodiment, the recess 65 is provided in the flange 64 as a structure for rotating the large steel spindle 60 by a tool, but the present invention is not limited thereto as long as the large steel spindle and the tool can be engaged with each other in the circumferential direction. As a structure for engaging the tool with the large steel wheel shaft in the circumferential direction, for example, a D-cut portion may be provided on the flange, or a recess into which a screwdriver slot, a square wrench, or the like is inserted may be provided on the upper tenon or the lower tenon.
In addition, the components in the above embodiments may be replaced with known components without departing from the scope of the present invention, and the above embodiments may be appropriately combined.
Claims (10)
1. A barrel assembly, wherein the barrel assembly is characterized in that,
the barrel assembly includes:
a barrel wheel that houses a mainspring inside, one end of the mainspring being attached to the barrel wheel, and the barrel wheel rotating around an axis line in accordance with the unwinding of the mainspring;
a hollow barrel shaft disposed coaxially with the axis, supporting the barrel wheel to be relatively rotatable, and to which the other end of the mainspring is attached;
a large steel wheel shaft having an upper tenon and a lower tenon and inserted inside the bar shaft in a state of being arranged coaxially with the axis;
a large steel wheel arranged between the upper tenon and the lower tenon coaxially with the axis; and
a relative rotation restricting portion that directly or indirectly restricts relative rotation between the bar shaft and the large steel wheel by engagement,
the large steel wheel and the barrel wheel are both arranged between a barrel clamping plate which supports the upper tenon in a shaft mode and a bottom plate which supports the lower tenon in a shaft mode.
2. The barrel assembly according to claim 1,
an insertion part into which the bar shaft is inserted is formed on the large steel wheel,
the large steel wheel is clamped with the bar shaft in the circumferential direction around the axis.
3. The barrel assembly according to claim 1 or 2,
the large steel axle is provided with a protruding portion protruding in a direction perpendicular to the axis,
the large steel wheel is in contact with the projection at a position at least 3 points or more around the axis as viewed in the axial direction of the axis.
4. The barrel assembly according to claim 3,
the large steel wheel is clamped by the protruding part and the bar shaft.
5. The barrel assembly according to claim 1 or 2,
the large steel wheel shaft is screwed into the bar shaft.
6. The barrel assembly according to claim 5,
the large steel wheel shaft has a fitting portion fitted with the bar shaft.
7. The barrel assembly according to claim 1 or 2,
the large steel wheel shaft is pressed into the bar shaft.
8. The barrel assembly according to claim 1 or 2,
the large steel wheel shaft has a through hole penetrating in the axial direction at a position overlapping at least one of the bar shaft and the large steel wheel when viewed in the axial direction of the axis.
9. A machine core is characterized in that a machine core is provided,
the movement is provided with a barrel assembly according to any one of claims 1 to 8.
10. A timepiece, characterized in that it comprises, in a case,
the timepiece is provided with the movement of claim 9.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018-112650 | 2018-06-13 | ||
| JP2018112650A JP6653731B2 (en) | 2018-06-13 | 2018-06-13 | Barrel assembly, movement and clock |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110597041A CN110597041A (en) | 2019-12-20 |
| CN110597041B true CN110597041B (en) | 2022-03-25 |
Family
ID=68806387
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910504780.6A Active CN110597041B (en) | 2018-06-13 | 2019-06-12 | Barrel assembly, movement and timepiece |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6653731B2 (en) |
| CN (1) | CN110597041B (en) |
| CH (1) | CH715054B1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7327181B2 (en) * | 2020-01-27 | 2023-08-16 | セイコーエプソン株式会社 | clock |
| JP6730538B1 (en) * | 2020-01-29 | 2020-07-29 | セイコーウオッチ株式会社 | Wheel train mechanism, movement and clock |
| EP3872576B1 (en) * | 2020-02-25 | 2024-02-21 | ETA SA Manufacture Horlogère Suisse | Timepiece barrel with twisted arbor |
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| EP0027671A1 (en) * | 1979-10-19 | 1981-04-29 | CORUM RIES, BANNWART & Co. | Device for winding up and setting a time measuring instrument |
| EP0230878A1 (en) * | 1986-01-14 | 1987-08-05 | Complications S.A. | Clockwork movement |
| CN1185624A (en) * | 1996-12-18 | 1998-06-24 | 松下电器产业株式会社 | Disc-sheet holding device |
| CN2911746Y (en) * | 2006-05-19 | 2007-06-13 | 上海恒保钟表有限公司 | Driving gear in wrist watch with intermediate flywheel |
| CN101125426A (en) * | 2007-09-28 | 2008-02-20 | 熊玉勇 | Full-automatic hairclipper |
| EP1925996A1 (en) * | 2006-11-06 | 2008-05-28 | ETA SA Manufacture Horlogère Suisse | Device for correction of a display mechanism for a timepiece |
| CN101872153A (en) * | 2009-04-27 | 2010-10-27 | 精工电子有限公司 | Clock having functions of displaying date and am/pm |
| CN206115154U (en) * | 2016-09-13 | 2017-04-19 | 天津海鸥表业集团有限公司 | Double-spring watch driving assembly |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS50122264U (en) * | 1974-03-22 | 1975-10-06 | ||
| JP3577909B2 (en) * | 1997-09-12 | 2004-10-20 | セイコーエプソン株式会社 | Electronically controlled mechanical clock |
| JP3054943B2 (en) * | 1997-12-25 | 2000-06-19 | セイコーインスツルメンツ株式会社 | Clock forward / reverse mechanism and power reserve mechanism using the same |
| JP2005156344A (en) * | 2003-11-26 | 2005-06-16 | Seiko Epson Corp | Spring device, and clock having the same |
| JP2017083335A (en) * | 2015-10-29 | 2017-05-18 | シチズン時計株式会社 | Barrel for watch |
| JP6738166B2 (en) * | 2016-03-09 | 2020-08-12 | セイコーインスツル株式会社 | Power reserve mechanism, movement and clock |
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2018
- 2018-06-13 JP JP2018112650A patent/JP6653731B2/en active Active
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2019
- 2019-06-11 CH CH00784/19A patent/CH715054B1/en unknown
- 2019-06-12 CN CN201910504780.6A patent/CN110597041B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0027671A1 (en) * | 1979-10-19 | 1981-04-29 | CORUM RIES, BANNWART & Co. | Device for winding up and setting a time measuring instrument |
| EP0230878A1 (en) * | 1986-01-14 | 1987-08-05 | Complications S.A. | Clockwork movement |
| CN1185624A (en) * | 1996-12-18 | 1998-06-24 | 松下电器产业株式会社 | Disc-sheet holding device |
| CN2911746Y (en) * | 2006-05-19 | 2007-06-13 | 上海恒保钟表有限公司 | Driving gear in wrist watch with intermediate flywheel |
| EP1925996A1 (en) * | 2006-11-06 | 2008-05-28 | ETA SA Manufacture Horlogère Suisse | Device for correction of a display mechanism for a timepiece |
| CN101125426A (en) * | 2007-09-28 | 2008-02-20 | 熊玉勇 | Full-automatic hairclipper |
| CN101872153A (en) * | 2009-04-27 | 2010-10-27 | 精工电子有限公司 | Clock having functions of displaying date and am/pm |
| CN206115154U (en) * | 2016-09-13 | 2017-04-19 | 天津海鸥表业集团有限公司 | Double-spring watch driving assembly |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110597041A (en) | 2019-12-20 |
| JP6653731B2 (en) | 2020-02-26 |
| JP2019215259A (en) | 2019-12-19 |
| CH715054A2 (en) | 2019-12-13 |
| CH715054B1 (en) | 2023-01-13 |
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