JP3533910B2 - Electronic clock - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electronic timepiece equipped with a so-called self-winding small generator.
More specifically, the present invention relates to a structural technique for making an electronic timepiece thinner and smaller.

[0002]

2. Description of the Related Art In an electronic timepiece equipped with a so-called compact self-winding generator using a crystal oscillator or the like as a time reference, as shown in FIG. And the power supply unit 10
Is used as a power source to drive the step motor 40. In the step motor 40, the motor rotor 4
The timepiece train wheel 50 is connected to the wheel 2, and the hands attached to each wheel are driven. On the other hand, the small generator 20 includes a power generation rotor 21 that is rotated by the rotational driving force transmitted from the rotary weight 25, a power generation stator 22 that sandwiches the power generation rotor 21, a power generation stator 22, and a power generation rotor 21. Power generation coil 23 forming a magnetic circuit
And the rotary weight 2 for the power generation rotor 21.
A train wheel 60 for power generation that speeds up and transmits the rotational movement of the No. 5 is configured. The rotary weight 25 has a groove-shaped opening 259 formed in its thin portion 251 in order to prevent the received impact from being directly applied to the movement, and has a structure to absorb the impact by bending. However, since the rotary weight 25 has a substantially semicircular shape, the opening 259 is formed within an angle range of about 160 ° around the rotary weight fixing screw 250.

As shown in FIG. 16, the rotary weight 25 is supported by a rotary weight receiver 300, which is different from the train wheel bridge 3A, via a ball bearing 90. That is, the rotary weight receiver 300
The outer ring 93 of the ball bearing 90 is press-fitted and fixed to
For the inner ring 94, the rotary weight 25 is the rotary weight fixing screw 25.
It is screwed by 0. The timepiece train wheel 50 is supported between the train wheel bridge 3A and the main plate, and the power generation train wheel 60 is supported between the rotary weight bridge 300 and the main plate 2. Inner ring 94
A female screw is formed on the inner peripheral surface of the through hole formed in the central portion of the wheel, and in the state before the rotary weight fixing screw 250 is stopped, the lubricating oil is supplied to the timepiece train wheel from this through hole. It is possible.

[0004]

Here, there is a strong demand for further miniaturization and thinning of the pointer type electronic timepiece even if it is of a type having a small generator. However, there is a problem in the electronic timepiece of the type in which the small generator 20 is built in that such a request cannot be realized only by arranging the respective components with the gaps filled. That is, even if the electronic timepiece is made smaller and thinner, in order to maintain the power generation efficiency at a high level, the small generator 20 has a large weight imbalance in the angular direction and its outer diameter is also the exterior. Since the rotation weight 25 that is as large as possible is used within the range that can be stored in the case, a sufficient gap is provided between the rotation weight 25 and the surroundings so that it does not interfere with the surroundings even if it swings up and down during high-speed rotation. It is necessary to secure it.

In view of the above problems, it is an object of the present invention to provide an electronic timepiece which can improve the structure around the rotary weight and can be made smaller and thinner.

[0006]

In order to solve the above problems SUMMARY OF THE INVENTION small in the present invention, having a power generation train wheel for transmitting rotary weight, and the rotational movement of the rotary weight is rotated by the movement of a user of the watch a generator, a clock machine body to be driven based on the electric energy generated by the small generator,
In an electronic timepiece having the timepiece mechanical body and an outer case that accommodates the small-sized generator, the timepiece mechanical body is supported in the outer case by a support tool, and the support tool faces the rotary weight side. By providing a plurality of protrusions as contact portions, the outer peripheral portion of the rotary weight contacts the contact portion in the cross-sectional direction,
It is characterized in that the rotary posture of the rotary weight is maintained.

According to the present invention, a sufficient gap is not provided between the rotary weight and the surroundings to prevent interference between the rotary weight and the surroundings. By holding the rotary weight in a predetermined state, it is possible to prevent unnecessary interference between the rotary weight and the surroundings when the rotary weight rotating at high speed moves up and down. In this case, if the outer case member such as the support does not strike the rotary weight in the cross-sectional direction (vertical direction) as in the present invention,
Naturally, it will be done with the clock mechanical body. The rotary weight is subject to a large disturbance of the user and rotates at the time of impact, and is also subjected to an impact force in the vertical direction as well, but when the watch mechanical body hits it as described above, it becomes the hitting part. There is a risk that the wheel train bridge, the main plate, and the like are deformed due to an impact force, and the power generation train wheel or the timepiece train wheel is stopped or the friction is increased. On the other hand, in the present invention, since the impact force of the rotary weight as described above is received by the exterior case member other than the timepiece mechanical body, the problem as described above does not occur at all. In particular, the outer case member originally has a sufficient resistance to the impact of the rotary weight because it can withstand drop and collision of the timepiece. Therefore, according to the present invention, it is possible to reliably prevent the power generation train wheel and the timepiece train wheel from stopping or increasing friction. The hitting portion that receives the vertical movement of the rotary weight may be provided on a separate support tool disposed in the exterior case or on the exterior case itself in which the support tool is integrally configured. On the other hand, the contact portion facing the rotary weight may be provided on the entire circumference of the support, or may be provided on a partial area of the entire circumference. When providing in a partial area,
The hitting part may be provided in a plurality of areas where the rotary weight always hits the hitting part in any flat area, or it may be provided in the vicinity of the mechanical part having weak strength. Good. Further, in the present invention, a sufficient gap is not secured between the rotary weight and the surroundings to prevent interference between the rotary weight and the surroundings. Therefore, a wide gap should not be provided between the rotary weight and the surroundings. It is also possible to reduce the size and thickness of an electronic timepiece that incorporates a small generator. Moreover, the rotary weight hits only the support for fixing the timepiece mechanical body in the outer case, and does not add new parts. From this point as well, it is suitable for reducing the size and thickness of an electronic timepiece having a small generator built therein. In this case, it is preferable that the frame body includes a plurality of the protrusions. With such a structure, it is not necessary to make the frame thick in order to bring the rotary weight and the frame into contact with each other, and a protrusion protruding by a necessary dimension toward the rotary weight can be formed on the frame. Good.

Further, in the present invention, the rotary weight may be provided with a thin portion on the rotation center side thereof and may be provided with a thick portion on the outer peripheral side of the thin portion. In this case,
The thick portion hits the hitting portion of the support. With such a rotary weight, even if it is a small rotary weight, the amount of unbalance of weight is high, so that the power generation efficiency is high. Even in this case, since the rotary weight hits the heavy and durable thick portion, the rotation weight can be prevented from being deformed.

Further, in the present invention, the rotary weight is
It is preferable that the thin portion is provided with an opening having a groove-shaped notch over an angle range of 180 ° or more around the rotation center. According to this structure, even if the rotary weight is downsized, sufficient springiness can be secured, so that the impact applied to the rotary weight by the bending of the rotary weight can be absorbed. Therefore, it is possible to prevent the impact applied to the rotary weight from being directly transmitted to the timepiece mechanical body and damaging the timepiece mechanical body. Also,
When the rotary weight is provided with springiness, the rotary weight is more likely to be deformed in the vertical direction by that amount. Nevertheless, in the present invention, the posture of the rotary weight is maintained by the contact between the rotary weight and the support. , The rotating weight does not accidentally hit surrounding parts.

In addition, in the present invention, the timepiece mechanical body is a secondary power source for storing electric energy generated by the small generator, a step motor using the secondary power source as a power source,
The miniature generator is mounted on the timepiece mechanical body, including a timepiece wheel train that transmits the rotational driving force from the step motor to the hands and a wheel train bridge that supports the timepiece wheel train between the step wheel and the main plate. There are cases. In such a case, in the present invention, for example, the supporting tool supports the timepiece mechanical body in the outer case via the main plate.

In the present invention, the support may be a screw, and in this case, the rotary weight contacts the head of the screw or the like.

Finally, according to the present invention, a frame body sandwiched between a body and a back cover forming the exterior case is used as the support, and the frame body forms the outer peripheral portion of the main plate in the exterior case. It is preferable that the timepiece mechanical body is supported in the exterior case by being sandwiched between and. According to this structure, it is not necessary to use a screw to support the timepiece mechanical body in the outer case, and therefore, there is an advantage that the assembling property of the electronic timepiece is improved.

[0013]

The electronic timepiece to which the present invention is applied may be a pointer display type or a digital display type, and may be a portable type such as a wristwatch or a clock type.

[0015]

Embodiments of the present invention will be described with reference to the accompanying drawings.

(Configuration of Timepiece Mechanical Body) FIG. 1A is a schematic configuration diagram showing the overall configuration of the movement (timepiece mechanical body) of the pointer type electronic timepiece of this embodiment. Since the basic structure of the pointer type electronic timepiece of this example is the same as that of the conventional pointer type electronic timepiece, portions having common functions will be denoted by the same reference numerals.

In FIG. 1A, the pointer type electronic timepiece 1 of this example is a pointer display type analog quartz wristwatch, and in the pointer type movement used for the same, a quartz oscillator 32 mounted on a circuit board 31 is used. Based on the signal sent out,
The step motor 40 is driven. The step motor 40 includes a rotor 42 for a motor made of a permanent magnet magnetized in two poles, a stator 43 for a motor having a cylindrical rotor placement hole 430 in which the rotor 42 for the motor is placed, and a coil 41. And a coil block including the magnetic core 44. A wheel train 50 for a clock including a third wheel 53, a second wheel 54, a day wheel 55, and a hour wheel 56 is connected to the motor rotor 42 via a pinion. The minute hand 69 is fixed to the shaft end of the center wheel & pinion 54, and the hour hand 63 is fixed to the tip of the cylindrical shaft of the hour wheel 56.

The power supply unit 10 for driving the step motor 40 is generally constituted by a small generator 20 and a secondary power supply 30 (capacitor / power supply for the pointer type electronic timepiece 1). The small generator 20 rotates by receiving a kinetic energy from the rotary weight 25 and a rotary weight 25 of one weight that rotates by the movement of the arm so that power is generated when the arm fitted with the pointer type electronic timepiece 1 is moved. The rotor 21 for power generation, the stator 22 for power generation that sandwiches the rotor 21 for power generation, the stator 22 for power generation, the power generation rotor 21, and the power generation coil 23 that forms a magnetic circuit.

The rotary weight 25 and the power generation rotor 21 are mechanically connected by a power generation wheel train 60 that accelerates and transmits the rotational operation of the rotary weight 25.
It comprises a rotary spindle wheel 61 formed integrally with the rotary spindle 25, and a power generation rotor transmission wheel 62 having a pinion portion meshing with the gear. The power generation rotor 21 has magnetic poles N and S.
Is a permanent magnet in which the magnetic poles N and S rotate when the rotation of the rotary weight 25 is transmitted.
The induced electromotive force can be obtained from 3 and the secondary power source 30 can be charged. The rotary weight 25 is rotated by the movement of the user of the timepiece. The movement of the user is, for example, a swing of an arm of a wristwatch wearer or a vibration of a pocket watch user walking. Further, as a special example, when attached to an animal such as a whale, it is vibration caused by the animal's migration or walking motion.

The rotary weight 25 will be described in detail later, but a rotary weight fixing screw 250 is attached to the center of rotation thereof. In this rotary weight 25, the rotary weight fixing screw 2
A peripheral portion of 50 (center of rotation) is composed of a rotary weight body 251 (thin portion) made of a thin plate, and a rotary weight 252 (thick portion) is connected to an outer peripheral portion thereof. By using the rotary weight 252 as described above, the unbalanced amount of the weight of the rotary weight 25 is increased even if the timepiece body is made thin.

The components of the timepiece machine body such as the timepiece train wheel 50, the step motor 40, and the secondary power source 30 thus configured are mounted on the main plate, which will be described later, together with the small generator 20. There is.

(Structure of the rotary weight) In the rotary weight 25, the rotary weight body 251 has a shock absorbing structure in order to prevent the impact applied to the rotary weight 252 from being directly transmitted to the movement and damaging the movement. There is. As such a shock absorbing structure, the rotary weight body 251 has a rotary weight fixing screw 2
A groove-shaped opening 259 is formed around
1 is easily bent. In this embodiment, although the rotary weight 25 has a substantially semicircular shape, the opening 259 is formed in the rotary weight fixing screw 25.
The opening 2 is formed by wrapping around 0.
59 is formed over an angle range of 180 ° or more. As a result, the rotating weight 25
Even if the size is reduced, the spring property can be secured, and the function of the rotary weight body 251 is not impaired.

In this embodiment, as shown in FIG. 1B, the rotary weight 25 is a thin rotary weight body 2 located on the inner peripheral side.
51 and a thick rotary weight 252 welded from the rotary weight 251 side at the overlapping portion with the outer peripheral side of the rotary weight 251. Therefore, the rotary weight 251 and the rotary weight 252 are formed. If the recessed portion 253 is formed in the region corresponding to the welded portion with, the designated welding position can be easily understood during the welding work, and the welding work can be facilitated. Further, since the welding mark is formed in the concave portion 253, the welding mark is the rotating weight 25.
Does not protrude from the surface of the.

As shown in FIG. 1C, the rotary weight 2
5, the thin rotary weight body 251 located on the inner peripheral side
If the welding is performed from the rotary weight body 251 side in the overlapping portion with the thick rotary weight body 252 located on the outer peripheral side of the rotary weight body 251, the rotary weight body 251 is attached to the main plate (see FIG. It is preferable to stack them on the side of (not shown). According to this structure, the welding mark is covered with the base plate, so that it looks good even when the rotary weight 25 has a structure visible from the outside.

(Fixed structure of the rotary weight and the train wheel) The arrangement structure of each component having a power generation function and a hand movement function will be described.

FIG. 2 is a main plate 2 for supporting each component, a first wheel train bridge 3, and a second wheel train in the pointer type electronic timepiece of the present embodiment.
FIG. 6 is a plan view showing the layout of the train wheel bridge 6 of FIG.
The outlines of the first train wheel bridge 3 and the second train wheel bridge 6 are shown by thick solid lines, thick dotted lines, and thick one-dot chain lines, and other parts are shown by thin lines.

In FIG. 2, the central portion of the main plate 2 is the portion that should be the center of rotation of the rotary weight 25 and the hands. A clock face plate is arranged on the back side of the main plate 2, and in the drawing, in each angle direction of the main plate 2, each time corresponding to this direction (3 o'clock, 6 o'clock, 9 o'clock, 12:00) is attached. The rotation region of the rotary weight 25 is a region indicated by a one-dot chain line L1 slightly inside the outer peripheral edge of the main plate 2. Inside the dashed-dotted line L1, the rotation position of the boundary portion between the rotary weight body 251 (thin portion) and the rotary weight 252 (thick portion) configured in the rotary weight 25 is represented by the dashed-dotted line L2. .

(Arrangement of wheel train for clock) FIG. 3 is a view showing the rear wheel 55 of the day, the center of the rotary weight 25 (screw for fixing the rotary weight), the second wheel 54, the hour wheel 56, and the third wheel in FIG. 53 is a cross-sectional view when cut at a position passing through 53, the motor rotor 42, and the set screw 26. FIG.

As shown in FIGS. 2 and 3, the rotary weight 25
In the area corresponding to the inner peripheral side of (the rotating area of the thin portion 251), the third wheel & pinion 53, the second wheel & pinion 54 described with reference to FIG.
A wheel train 50 for a watch having a large height, such as a day wheel 55 and a hour wheel 56, is arranged. Of these wheel trains 50 for a timepiece, the third wheel 53, the back wheel 55 of the day, and the rotor 42 for a motor are the main plate 2 and the first wheel train bridge 3 arranged in a flat plate shape facing the main plate 2. Is supported via a tenon frame made of hole stone S and the like. This first train wheel bridge 3
Are arranged inside the rotation region of the thin portion 251 of the rotary weight 25, that is, inside the one-dot chain line L2.

Here, the arrangement of the timepiece train wheel 50 and its periphery will be described in detail. A center wheel 54 having a minute hand 69 supported at the center thereof in the plane direction of the movement.
Are arranged. In the thickness direction, in the direction from the gear portion of the center wheel & pinion 54 to the rotary weight 25, the pinion portion of the center wheel & pinion 3, the third wheel & pinion 5, and the center wheel & pinion 5 supported by the second train wheel bridge 6.
4, the upper mortise bearing portion, the bearing shaft 97 fixed to the first train wheel bridge 3, the ball bearing 90, and the rotary weight fixing screw 250 are arranged in this order, and the thickness of the movement is determined in this portion.

The third wheel 53, the date wheel 55, and the motor rotor 42 are supported between the first train wheel bridge 3 and the main plate 2, and the second train wheel bridge 6 and the main plate 2 are supported. Between the upper tenon (the tenon on the side of the first train wheel bridge 3) and the lower tenon (the tenon on the side of the main plate 2) as much as the plate thickness of the second train wheel bridge 6 compared to the parts supported between the two. ) Can be made longer. Therefore, with respect to the third wheel & pinion 53, the date indicator wheel 55, and the motor rotor 42, the inclination of the train wheel can be reduced even if the plane positions of the upper and lower bearing portions are slightly displaced. Therefore, in the third wheel 53, the date wheel 55, and the motor rotor 42, it is possible to suppress creaking in the upper tenon or lower tenon and overload at the meshing portion of the gears.
It is possible to prevent a decrease in transmission efficiency.

Further, in the third wheel 53, the date indicator wheel 55, and the motor rotor 42, at a portion at the same height as the second wheel train bridge 6, the plate thickness of the second wheel train bridge 6 is increased. It is possible to increase the length of the body attachment part (grate determining part) that connects the upper tenon part and the pinion part or the gear part. Normally, lubricating oil is applied to the tenon bearing part.However, if the body part is short and the distance between the upper tenon part and the pinion part or the gear part is short, the lubricating oil that rises due to surface tension will be applied to the pinion part or gear part. It becomes easy to adhere, and the oil retaining property at the bearing part deteriorates. However, in the present embodiment, by disposing the second train wheel bridge 6, the body attachment part is lengthened and the upper tenon part and the pinion part or the gear part are separated from each other, so that the oil retaining property in the bearing part is improved. You can

The center wheel & pinion 54 whose upper tenon is supported by the second wheel train bridge 6 is thicker than the timepiece wheel train 50 whose upper tenon is supported by the first wheel train bridge. Although it is arranged at a low position, the lower tenon is guided by a central pipe having an inverted L-shaped cross section on the side of the main plate 2, so that the upper tenon and the lower tenon have a substantially long distance. Therefore, the center wheel & pinion 54 can also be made to have a small inclination and has a structure that does not hinder the function.

Here, the first train wheel bridge 3 is fixed to the main plate 2 together with the second train wheel bridge described later by three setscrews 17, 18, and 26, and all the screwed portions are thin portion 251. It is located inside the rotation area of. Fixing using such screws is excellent in reliability when used for a long period of time or repeatedly attached and detached, and can be made inexpensive in terms of cost because of its simple structure. Further, as can be seen from FIG. 2, the timepiece train wheel 5 is provided in the area surrounded by the three screw sets 17, 18 and 26 in a plane.
The gears (third wheel 53, second wheel 54, day wheel 55, hour wheel 56) forming 0 are positioned. Further, the first train wheel bridge 3 is arranged in a range overlapping all of the power generation train wheel 60 and the timepiece train wheel 50, but the second train wheel bridge 6 has the above-mentioned three.
Of the set screws 17, 18, 26 of the book, the set screw 17,
It is fixed to the main plate 2 together with the first train wheel bridge 3 by 18 and is arranged so as not to overlap the power generation rotor 21 and the power generation rotor transmission wheel 62 of the power generation train wheel 60, but to substantially overlap the timepiece train wheel 50. ing. Such set screws 17, 1
The region surrounded by the screwed points by 8 and 26 is reinforced by the second train wheel bridge 6 even when the first train wheel bridge 3 is about to be deformed toward the timepiece train wheel 50. Since it has great strength, the first train wheel bridge 3 is surely provided with each gear (third wheel 53, second wheel 54, date wheel 55, hour wheel 56).
Can be supported. Moreover, the set screws 17, 18 and 26 for fixing the first train wheel bridge 3 to the main plate 2 are
5 to the first train wheel bridge 3 rotary weight fixing screw 250
All of the set screws 17, 18, and 26 that are arranged so as to surround the rotary wheel and that fix the first train wheel bridge 3 to the main plate 2 are the outer diameter dimension of the rotary weight 25 from the rotary weight fixing screw 250 to 1
It is arranged within a radial distance corresponding to / 2. Therefore, even if an external force acts on the first train wheel bridge 3 by the rotary weight 25, the set screw portion for fixing the train wheel bridge supports near the center, so that the first train wheel bridge 3 is less likely to bend. , The train wheel can be reliably supported and the train wheel is not destroyed. Also, the rotary weight 2
Since the fixed portion of 5 is stable, the inclination of the rotary weight 25 can be suppressed.

(Arrangement of power generation train wheel) FIG. 4 (A) is shown in FIG.
At a position passing through the power generation coil 23, the power generation rotor 21, the power generation rotor transmission wheel 62, the date back wheel 55, the center of the rotary weight 25 (screw for fixing the rotary weight), the center wheel 54, and the hour wheel 56. It is sectional drawing when cut.

As shown in FIGS. 2 and 4 (A), from the rotation region of the rotary weight body 251 (thin portion) to the rotation region of the rotary weight 252 (thick portion) in the rotation region of the rotary weight 25. The small generator 20 is configured in this region. Figure 4 (A)
As can be seen from the above, in the small generator 20, the power generation rotor transmission wheel 62 meshes with the pinion portion 210 of the power generation rotor 21, and the pinion portion 620 of this power generation rotor transmission wheel 62 is engaged.
A rotary weight wheel 61 that rotates together with the rotary weight 25 is meshed with this. Here, let alone the rotary spindle 61,
Since the power generation rotor transmission wheel 62 also has a large height, it is arranged in the rotation region of the rotary weight body 251 (thin portion).

(Impact receiving structure of rotary weight) In the rotary weight 25, as described with reference to FIG.
Since 1 is provided with a shock absorbing function utilizing the spring property, the outer peripheral portion of the rotary weight 25 rotates while moving up and down. In the present embodiment, as a structure for receiving such vertical movement, the middle frame 5 (support / frame body) shown in FIG. 5 is used.

5 (A) and 5 (B) are a plan view and a cross-sectional view taken along the line BB 'of the middle frame, which is an exterior case member, respectively. In FIG. 5 (A), as in FIG. Each time (3 o'clock, 6 o'clock, 9 o'clock, 12 o'clock) corresponding to this direction is attached to the direction. Further, in FIG. 5 (A), the position corresponding to the outer peripheral position of the rotary weight 25 is represented by the alternate long and short dash line L1.

4 and 5, the small generator 20 and the movement (timepiece mechanical body) formed on the main plate 2.
Is housed inside a case back 78 and a back cover 68 that holds the ring-shaped middle frame 5 (exterior case member) on the outer peripheral side. In this state, the middle frame 5 is located between the outer case 9 and the case 78. On the ground plate 2
To pinch. That is, two contact portions 681, 682 that annularly protrude toward the body 78 are formed on the inner surface of the back cover 68, and inside the body 78, the movement configured on the main plate 2 and the middle portion are formed. After storing the frame 5 in order, the back cover 6
When it is fixed by covering 8 with the contact portion 6, the contact portion 6 protrudes outward slightly.
Since 82 abuts on the case 78 and the abutting portion 681 that largely protrudes inside presses the middle frame 5 toward the case 682, the middle frame 5 holds the main plate 2 between the case 682 and the timepiece machine body. Will be supported in the outer case 9.

Here, the middle frame 5 includes the rotary weight 25 as a whole.
It has an inner diameter slightly larger than the outer diameter. However, in the middle frame 5, a portion located outside the position where the power generation coil 23 is arranged is formed to be slightly wider, and a portion near the inner circumference of the wide portion 500 faces the outer circumference of the rotary weight 25. In this embodiment, on the end surface 501 facing the outer peripheral portion of the rotary weight 25 in the portion near the inner periphery of the wide portion 500 of the middle frame 5, the dowel 502 (the contact portion / protrusion) protruding toward the rotary weight 25 is provided.
Are formed. By setting the dowel 502 at a height position closer to the rotary weight 25 in the thickness direction than the parts around the dowel, when the rotary weight 25 rotates while moving up and down,
The outer peripheral portion of the rotary weight 25 first strikes the dowel 502 of the middle frame 5, and the posture thereof is corrected. As a result, it is possible to prevent the parts around the dowel from breaking due to contact with the rotary weight 25. Here, it is sufficient to form the dowels 502 on the middle frame 5 at three equiangular intervals. The dowel 502 is provided on the outer peripheral side of the power-generating coil 23 in FIG. 2, and its height in the cross-sectional direction is higher than that of the power-generating coil 23 as shown in FIG. 4 (A).

As described above, in this embodiment, the rotary weight 25 is provided by ensuring a sufficient gap between the rotary weight 25 and the surroundings.
The rotary weight 2
By positively abutting the outer peripheral portion of the rotary shaft 5 against the dowel 502 of the middle frame 5, the posture of the rotary weight 25 is maintained in a predetermined state, and rotation when the rotary weight 25 rotating at high speed moves up and down. The unnecessary interference between the weight 25 and the surroundings is prevented. Therefore, since it is not necessary to make a wide gap between the rotary weight 25 and the surroundings, the pointer-type electronic timepiece 1 of the type including the small generator 20 can be made small and thin. Moreover, the oscillating weight 25 hits only the middle frame 5 for fixing the movement in the outer case 9, and does not add any new part. From this point as well, it is suitable for downsizing and thinning of the pointer type electronic timepiece 1 of the type having the small power generator 20 built therein. Further, since the outer peripheral portion of the rotary weight 25 is hit by the durable middle frame 5, the rotary weight 25 is fixed to the first train wheel bridge 3
Unlike the structure in which the wheel train 50 and the main plate 2 are contacted with each other, the troubles of the timepiece wheel train 50 and the power generation wheel train 60 due to the deformation of the first train wheel bridge 3 and the main plate 2 do not occur.

Further, in the present embodiment, since the outer peripheral portion (rotary weight 252 / thick portion) of the rotary weight 25 is brought into contact with the dowel 502 protruding toward the rotary weight 25 by a necessary dimension,
Even if the rotary weight 25 is configured to hit only the inner frame 5 and not the surrounding parts, the small size of the pointer type electronic timepiece 1,
There is no need to use a thick inner frame that hinders the reduction in thickness.

Further, since the rotary weight 25 hits the heavy and durable rotary weight 252 (thick portion), the rotary weight 25 can be prevented from being deformed due to the hard hit.

A screw may be used as a support for fixing the main plate 2 on which the movement is mounted to the outer case 9, and the rotary weight 25 may be contacted with the head of this screw. Middle frame 5 sandwiched between the back cover 68 and
When using, the screw is not required to fix the main plate 2 to the exterior case 9, and therefore there is an advantage that the assembling property at the time of assembling the pointer type electronic timepiece 1 is improved.

(Structure for Preventing Lubricant Oil from Scattering on Wheels and Wheels) In this embodiment, the second wheel & pinion 5 having the area where the power generation rotor transmission wheel 62 and the power generation rotor 21 are arranged and the minute hand 69 are fixed.
It is arranged so as to be separated from 4 as much as possible. Therefore, the power generation rotor transmission wheel 62 and the power generation rotor 21
Even if the lubricating oil scatters when rotating at a high speed, the lubricating oil does not reach the center wheel & pinion 54. Moreover, an area in which the power generation rotor transmission wheel 62 and the power generation rotor 21 are arranged,
Between the center wheel & pinion 54, a day wheel 55 that rotates with a relatively large torque is arranged. Therefore, even if the lubricating oil is scattered from the power generation rotor transmission wheel 62 and the power generation rotor 21, the lubricating oil is blocked by the day back wheel 55 and does not reach the center wheel & pinion 54. Therefore, although the movements are small and close to each other as a whole, since the gears are arranged at appropriate positions, the center wheel & pinion 54 always rotates smoothly without being affected by the lubricating oil. here,
Even if the lubricating oil adheres to the date driving wheel 55, since the date driving wheel 55 has a high rotational torque, it does not hinder the rotation. Therefore, for the purpose of more surely preventing the influence of the lubricating oil that is scattered,
At the position near the rotor transmission wheel 62 for power generation,
As described above, a wheel train having a high rotational torque is arranged, and the second wheel 54, the third wheel 53, and the motor rotor 42 are arranged as the wheel train moves away from the wheel train. It is preferable to arrange a train wheel having a low

Further, the rotor transmission wheel 62 for power generation is arranged in the thickness direction.
Is arranged closer to the first train wheel bridge 3 than the gear of the date wheel 55, and the date wheel 55 and the power generation rotor transmission wheel 62 are partially overlapped with each other in the plane direction. Can be downsized. Further, by setting the gears of the power generation rotor transmission wheel 62 and the second wheel train bridge 6 to have substantially the same height position in the thickness direction, the lubricating oil scattered from the power generation rotor transmission wheel 62 causes the timepiece wheel train 50 to travel. Can be prevented.

(Structure for Preventing Cracks in Holes) Power Generation Rotor 21
As shown in the enlarged view of FIG. 4 (B) for the rotation center shaft 211 of the rotation center shaft 211 of FIG.
The hole stone 214 fitted in 11 is a hole 267 in the main plate 2 via a cap 215 and a sleeve 266 (cap).
Held in. In this state, the center position C in the thickness direction of the pressure contact portion between the sleeve 266 and the cap 215.
1 and the center position C2 in the thickness direction of the pressure contact portion between the cap 215 and the hole stone 214 are deviated from each other. Further, the center positions C1 and C2 are both deviated from the center position C3 in the thickness direction of the pressure contact portion between the sleeve 266 and the base plate 2. Therefore, when the hole plate 214 is held on the main plate 2 through the sleeve 266 and the cap 215, the force applied from the main plate 2 to the sleeve 266 and the force applied from the sleeve 266 to the cap 215 are applied to the hole plate 214.
Don't focus on a part of the side of. Therefore, hole stone 2
It is possible to prevent 14 cracks. Also, sleeve 2
It is preferable that the press-contacting portion of 66 and the cap 215 and the press-contacting portion of the sleeve 266 and the base plate 2 are arranged at positions where they do not overlap each other in the thickness direction.

In FIG. 4 (A), in the bearing portion on the other side with respect to the power generation rotor 21, the hole stone 212 fitted to the rotation center shaft 211 of the power generation rotor 21 is
It is held in the hole 268 of the first train wheel bridge 3 via the cap 213. Also in this bearing portion, the center position in the thickness direction of the pressure contact portion between the cap 213 and the hole stone 212 is displaced from the center position in the thickness direction of the pressure contact portion between the cap 213 and the first train wheel bridge 3. The force applied to the cap 213 from the first train wheel bridge 3 will not be concentrated on a part of the side surface of the hole stone 212.

(Support structure for power train and rotary weight) FIG. 6 shows the set screw 26 and the step motor 4 in FIG.
FIG. 6 is a cross-sectional view of a portion passing through a coil 41 of 0 and a set screw 29. FIG. 7 shows a set screw 18 and a rotary weight 25 in FIG.
FIG. 4 is a cross-sectional view of a portion passing through the center of (rotary weight fixing screw). FIG. 8 shows a set screw 17 and a rear wheel 5 of FIG.
5 is a sectional view of a portion passing through 5.

Conventionally, the timepiece wheel train 50 and the power generation wheel train 60 are separately supported by separate wheel train bridges and rotary weight bridges. With respect to the first wheel train bridge 3 supporting the motor rotor 42 of the wheel train 50, the third wheel 53 and the day wheel 55,
The power generation rotor 21 of the power generation wheel train 60 and the power generation rotor transmission wheel 62 are also supported. As will be described later, the rotary weight 25 is also supported by the first train wheel bridge 3 similarly to the power train wheel 60. Therefore, in the present embodiment, the first train wheel bridge 3 may be supported by the main plate 2, and therefore, as shown in FIG.
Three sets of screws with book screws 17, 18, and 26 are sufficient.

These three setscrews 17, 18, 26
The three screw-fastened portions according to FIG. 6 are shown as shown in FIGS. 6, 7, and 8, and in any of the portions, the metal cylindrical screw seats 170, 180, 260 struck on the main plate 2 and the metal pins are provided. It is a screw-fastening structure using the set screws 17, 18, and 26.

Therefore, in the past, in addition to the first train wheel bridge 3, it was necessary to screw and fix the rotary weight bridge.
It was necessary to secure a total of 6 screwed areas, but in this embodiment, the number of screwed areas can be reduced to 3, so the area occupied by the screwed areas can be reduced, and each part Can be arranged efficiently. Further, conventionally, in consideration of the variation in the thickness direction when the wheel train bridge mounted with the time wheel train 50 and the power generation wheel train 60 and the rotary spindle carrier are overlapped, the rotary spindle and the wheel train are considered. Although there are restrictions such as the need to secure a sufficient gap between the receiver and the like, in the present embodiment, there is no such restriction. Therefore, the pointer type electronic timepiece 1 can be made thin.

In FIG. 6, the screwing portion by the set screw 29 fixes the base plate 2, the motor stator 43, the magnetic core 44, the coil lead substrate 409, the circuit substrate 31, and the circuit pressing plate 316.

(Rotating Weight Support Structure) As can be seen from FIG. 3, the rotating weight 25 is mounted on the first train wheel bridge 3 via a ball bearing 90. The ball bearing 90 is
Inner member 9 for supporting the bearing balls 91 on the inner peripheral side
2 and an outer ring 93 (outer member) that holds a plurality of bearing balls 91 with the inner member 92. The inner member 92 includes an inner ring 94 having an L-shaped cross section in which a flange portion extends outward from a tubular portion, a ball retainer ring 95 press-fitted into the inner ring 94 to form a ball raceway surface together with the inner ring 94, and a bearing ball. And a retainer 96 that defines the position of 91.

As will be described below, the inner ring 94 is fixed to the first train wheel bridge 3 via a bearing shaft 97 (guide shaft). First, the first train wheel bridge 3 has stepped receiving holes 3
01 is formed therein, and the bearing shaft 97 is mounted so that the tip portion thereof projects. A flange portion 971 larger than the receiving hole 301 is formed at the base portion of the bearing shaft 97, and the flange portion 971 is in a state of being caught by the step of the receiving hole 301. The inner ring 94 is fitted to the shaft portion of the bearing shaft 97 in this state, and the rotary weight fixing screw 250 is fixed to the female screw formed on the tip end surface of the bearing shaft 97. In this state, the head 250 of the slewing weight fixing screw 250 is pulled up while the bearing shaft 97 is being pulled up.
Is pressed against the first train wheel bridge 3, so that the inner ring 94 and the ball holding ring 95 are fixed to the first train wheel bridge 3 by the rotary weight fixing screw 250. As a result, the ball bearing 90 is positioned in the plane direction by the center hole of the inner ring 94 and the bearing shaft 97, and the height position is defined by tightening with the rotary weight fixing screw 250.

According to such a structure, unlike the structure in which the ball bearing is fixed to the plate material by press fitting, the lubricating oil applied to the ball bearing and the train wheel portion flows into the press fitting part of the ball bearing and the plate material. The problem that the ball bearing comes off does not occur. Further, according to the structure in which the ball bearing 90 is tightened and fixed to the first train wheel bridge 3 by the rotary weight fixing screw 250 as in the present embodiment, even if the ball bearing 90 is pressed during screw tightening, the bearing shaft 97 is pushed down. Even if the ball bearing 90 is tightened, the bearing shaft 97 is pulled up by the subsequent screw tightening, so that the ball bearing 90 is securely fixed at a predetermined position.

(Ball Bearing Fixing Structure) In the conventional pointer type electronic timepiece, as described with reference to FIG. 16, the inner ring 94 or the ball pressing ring 95 located inside the bearing ball 91 is closer to the inner side. Since the rotary weight 25 is screwed onto the rotary weight 25, the rotary weight is fixed by the engaging force of the rotary weight fixing screw 250 and the frictional force between the head of the rotary weight fixing screw 250 and the rotary weight 25 in contact with the head. Although the fixing screw 250 is prevented from loosening, there is a risk that the rotary weight fixing screw 250 will gradually loosen due to repeated impacts even with a strong impact or a light impact during long-term use. . Such loosening of the screw causes a gap between the ball retainer wheel 95 and the rotary weight wheel 61 or between the rotary weight 25 and the head of the rotary weight fixing screw 250, and a strong impact is applied to the rotary weight 25. When added, it causes damage to the ball bearing 90.

In the present embodiment, however, the ball bearing 9
Of the 0 components, the inner member 92 to which the rotary weight fixing screw 250 is fastened is the first train wheel bridge 3 which is the fixed member.
, And the rotary weight 25 is fixed to the outer ring 93. Therefore, the mounting portion of the rotary weight fixing screw 250 is fixed to the end and does not rotate.
The rotary weight fixing screw 250 does not loosen even when it is carried for a long period of time, subjected to a strong shock, or repeatedly subjected to a light shock. Therefore, problems such as breakage of the ball bearing 90 due to loosening of the rotary weight fixing screw 250 do not occur.

If the rotary weight fixing screw 250 does not rotate, the rotary weight fixing screw 250 is attached to the back cover 68.
Even if it comes into contact with the rotary weight 25 (see FIG. 4A), it does not affect the rotational movement of the rotary weight 25.
Since 8 can be arranged close to each other, the pointer type electronic timepiece 1 can be thinned accordingly.

Also, as in the conventional case, the rotatable inner ring 94
With the structure in which the rotary weight 25 is fixed with screws,
When tightening the screw, the inner ring 94 idles and the screw tightening is not easy, and if the rotary weight 25 rotates while tilting during screw tightening, scratches and shavings will be attached to the surroundings. However, in this embodiment, since the structure is such that the bearing shaft 97 is screwed to the end, the work for tightening the rotary weight fixing screw 250 can be easily performed. Further, according to the present embodiment, since the rotary weight 25 does not rotate while being tilted during the screw tightening work, no scratches or shavings are attached to the surroundings.

(Ball Bearing Tilt Prevention Structure) As described above, the ball bearing 9 is mounted by using the bearing shaft 97.
When mounting 0, the ball bearing shaft 97
Since it is actually impossible to integrally form the first train wheel bridge 3 with the first train wheel bridge 3, a hole is formed in the first train wheel bridge 3 machined from a plate material as in the present embodiment, and a bar material is inserted into this hole. There is no choice but to fix the bearing shaft 97 machined from. However, the bearing shaft 97 inevitably tilts if it is simply press-fitted and fixed. When the ball bearing 90 is incorporated into the bearing shaft 97 having such an inclination, the rotary weight 2 is caused by the lever ratio between the outer diameter dimension of the rotary weight 25 and the outer diameter dimension of the bearing shaft 97.
5, a very large inclination occurs. In order to allow such an inclination, there is no choice but to secure a sufficient space above and below the rotary weight 25, which hinders reduction in thickness and size. Further, even if the outer diameter dimension of the flange portion 971 of the bearing shaft 97 is increased to prevent the inclination thereof, it is impossible to expand the outer diameter dimension of the collar portion 971 any further with a small movement. Further, when the outer peripheral dimension of the rotary weight 25 is increased to secure the unbalance amount of the rotary weight 25 in a limited space, the lever ratio between the outer diameter dimension of the rotary weight 25 and the outer diameter dimension of the bearing shaft becomes larger. It becomes large, and the rotary weight 25 easily tilts.

Therefore, in this embodiment, first, the inner ring 94 is provided with a fitting portion 941 having a small inner diameter and a relief portion 942 having a large inner diameter on the inner peripheral side of the central hole (through hole). . The fitting portion 941 is a small-diameter portion that is close to the outer diameter dimension of the bearing shaft 97, and the clearance portion 942 is slightly larger than the inner diameter of the fitting portion 941 (outer diameter of the bearing shaft 97). Also has an inner diameter that does not interfere with the bearing shaft 97. Therefore, the engagement margin between the inner ring 94 and the bearing shaft 97 is defined by the length dimension A of the fitting portion 941. In the present embodiment, this length dimension A is shortened to the necessary minimum. In this way, if the engagement allowance between the inner ring 94 and the bearing shaft 97 is set to be short, the ball bearing 90 can be provided even if the bearing shaft 97 is slightly inclined.
Can be mounted in the correct posture, so
5 can be prevented from tilting. In this embodiment, the length dimension A
Is set in the range of about 0.05 mm to about 0.5 mm. When the size is shorter than this range, the ball bearing 90 can be easily assembled and removed, while the inner ring 94 bites into the bearing shaft 97 when a strong impact is applied to the bearing shaft 97 to shift the plane position or the bearing shaft 97. When the inner ring 94 digs in, the stress concentration becomes large, and problems such as damage to the ball bearing shaft 97 occur. When the length dimension A is longer than 0.5 mm,
The inclination of the rotary weight 25 is determined to be a large value due to the inclination of the bearing shaft 97. Furthermore, if the length dimension A is too long, the parts may bite when the ball bearing 90 is assembled or removed, and the parts may not move. Therefore, it can be said that the length dimension A is more preferably set in the range of about 0.1 mm to about 0.3 mm in consideration of variations in parts.

In the inner ring 94, the escape portion 9 is provided in the central hole.
If 42 is formed, when the ball retainer ring 95 is press-fitted into the tubular portion of the inner ring 94, even if there is a tendency to deform so that the inner diameter of this portion becomes smaller, this portion is originally the escape portion 942. Since it is formed with a large inner diameter, there is no hindrance to the fitting of the bearing shaft 97, and the fitting portion 941 can regulate the engagement margin with the bearing shaft 97 to a predetermined size.

Further, in this embodiment, the following structure is also adopted in order to reduce the inclination of the rotary weight 25 and to reduce the space of the pointer type electronic timepiece.

In the present embodiment, the ball retaining ring 95 of the ball bearing 90 is overlapped with the side of the first train wheel bridge 3 opposite to the side where the timepiece train wheel 50 is formed. In the present embodiment, in order to suppress the inclination of the rotary weight 25 as much as possible,
The outer diameter dimension B of the surface of the ball retaining ring 95 in contact with the first train wheel bridge 3 is maximized. However, since various parts are arranged in the first train wheel bridge 3, there is a limitation in expanding the outer diameter of the ball retaining ring 95. Therefore, in this embodiment,
From the viewpoint of the lever ratio to the outer diameter dimension of the rotary weight 25, the outer diameter dimension of the ball retaining ring 95 is examined, and the ball retaining ring 9
5 is the outer diameter dimension B of the surface in contact with the first train wheel bridge 3
The outer diameter of No. 5 is set to a range from about 1/10 times to about 1/3 times. When the ratio of the outer diameter dimensions is set to be larger than 1/3, the outer diameter dimension of the ball bearing 90 becomes too large and the unbalance amount of the rotary weight 25 becomes extremely small. As a result, the power generation performance of the small generator 20 is significantly reduced, and the performance of the pointer-type electronic timepiece 1 cannot be satisfied. On the other hand, the ratio of the above outer diameter dimensions is 1/1
If it is set smaller than 0 times, the inclination of the rotary weight 25 cannot be effectively suppressed. Therefore, the outer diameter dimension B of the surface of the ball retainer wheel 95 in contact with the first train wheel bridge 3 may be set in the range of 1/6 to 1/3 times the outer diameter dimension of the rotary weight 25. preferable. With this setting, the inclination of the rotary weight 25 can be reduced, which is further advantageous in reducing the thickness of the movement.

(Integrated structure of the rotary weight) In this embodiment, the rotary weight 25 that rotates by the movement of the arm, the ball bearing 90 for efficiently incorporating this movement into the generator, and the rotary weight 2
Rotating weight wheel 6 that accelerates the rotation of 5 and transmits it to the small generator 20
1 is all in one. That is, the power generation train wheel 6
Of 0, the rotary weight wheel 61 to which the rotation of the rotary weight 25 is first transmitted is also fixed to the outer ring 93 of the ball bearing 90. Here, on the outer ring 93 of the ball bearing 90, from the end surface on the side of the main plate 2 toward the end surface on the opposite side, a small diameter portion 931 on which the rotary weight wheel 61 is mounted, and this small diameter portion 93.
1, a large diameter portion 932 having an outer diameter dimension considerably larger than that of the small diameter portion 931 at a position connected to 1, and the large diameter portion 932.
A medium diameter portion 933 having a smaller outer diameter than the large diameter portion 932 and a larger outer diameter dimension than the small diameter portion 931 is formed in this order at a position connected to the medium diameter portion 932. The rotary weight 25 is attached to the medium diameter portion 933. In this middle diameter portion 933, the rotary weight 25
Is a swaged portion 93 formed on the end edge side of the middle diameter portion 933.
4 and the large-diameter portion 932, and is fixed there.

If the rotary weight 25 is not fixed to the outer ring 93 by caulking and fixed, but only by press-fitting and fixing the rotary weight 25 to the outer ring 93, the rotary weight 25 may come off when a strong shock or a light shock is repeatedly applied. Or, there is a risk of idling due to insufficient fixed torque, but in the crimping and fixing structure as in the present embodiment, such drop of the rotary weight 25 or idling does not occur.

Further, as in the present embodiment, a small diameter portion 931, a large diameter portion 932, and a middle diameter portion 933 are formed on the outer ring 93, and the rotary weight 25 is fixed to the middle diameter portion 933 by caulking. In the structure described above, when the caulking process is performed on the middle-diameter portion 933, it is possible to back up the portion directly below the middle-diameter portion 933, that is, the back side of the large-diameter portion 932.

Further, if the rotary weight 25 and the rotary weight wheel 61 are integrally formed on the ball bearing 90, the following advantages can be obtained in the manufacturing process of the movement. First, in the manufacturing stage of parts, the ball bearing 90,
Since the oscillating weight 25 and the oscillating weight wheel 61 are once assembled as a oscillating weight assembly having a very similar form when used as a timepiece, it is possible to finally manage the quality of the state in which the oscillating weight is mounted on the timepiece. Further, since the ball bearing 90, the rotary weight 25, and the rotary weight wheel 61 can be assembled as a rotary weight assembly, the number of parts handled in the movement assembling stage can be small. Therefore, it is possible to reduce the number of work steps and defective products.

(Structure of Rotary Spindle) FIG. 9 is a plan view of the rotary spindle 61 used in the pointer type electronic timepiece of this embodiment.

In FIG. 9, a pointer type electronic timepiece 1 of the present embodiment
The rotary spindle wheel 61 used for the above has two holes 611 corresponding to the outer peripheral surface of the outer ring 93 in the hole 610 through which the outer ring 93 of the ball belling 90 passes so as to slip around the ball belling 90 when overloaded. 612 is formed, and an opening 613 that extends in a groove shape from the hole 610 and draws an arc around the groove is formed. Therefore, the hole 61
Since the portion 614 remaining between 0 and the opening 613 exhibits a spring property, the edge portion 611 elastically contacts the outer peripheral surface of the outer ring 93 of the ball belling 90. For this reason, since the rotary weight wheel 61 slips when an overload is applied, the rotary weight wheel 61 itself and other power generation wheel trains 60 can be protected from damage due to the overload.

(Magnet fixing structure for power generation rotor) FIG.
In (A), in the rotor 21 for power generation, the pinion 210
On the other hand, a sintered magnet 218 is attached via a magnet guide seat 217. Conventionally, an adhesive is often used as a method for fixing a sintered magnet to a magnet guide seat having a structure that covers two surfaces of the sintered magnet. However, fixing with an adhesive is extremely difficult to manage, especially in the case of a precision part such as a timepiece, because the amount of the adhesive is very small, and requires skill to perform the work. As another fixing method, there is a method of driving a sintered magnet into the magnet guide seat with a tight margin between the magnet guide seat and the sintered magnet. Cracks were likely to occur in the sintered magnet due to the impact of hitting the seat. However, in this form,
As shown in FIG. 4 (A), when the sintered magnet 218 is driven into the magnet guide seat 217 with a tight margin between the magnet guide seat 217 and the sintered magnet 218, the magnet guide seat 217 and the sintered magnet 217 are burned in the thickness direction. Since the structure that secures a gap with the binder magnet 218 is adopted, cracking of the sintered magnet 218 can be prevented. Further, unlike fixing with an adhesive, since no fluid is interposed, it is possible to suppress positional variation in the thickness direction of the sintered magnet 218.

In addition, in the method of driving with a tightening margin, there is a possibility that the sintered magnet 218 may be displaced or come off due to impact, but a concave groove is formed on the outer peripheral side of the abutting surface of the magnet guide seat 217. By forming it, the interference portion of the magnet guide seat 217 becomes elastic, so that the force for fixing the sintered magnet 218 can be stabilized at a high level, and the above-mentioned displacement and omission can be prevented. Can be prevented.

Further, as a more reliable method, the inner diameter of the interference portion of the magnet guide seat 217 is made smaller on the driving side (lower end opening side) of the sintered magnet 218, and the abutting portion (upper bottom side).
There is a method of using a taper shape whose diameter becomes larger. According to this structure, even if the sintered magnet 218 shifts when an impact is applied, the sintered magnet 218 only shifts to the abutting portion side, so that the sintered magnet 218 can be prevented from coming off. Further, by providing a protrusion protruding in the inner diameter direction on the magnet driving side of the magnet guide seat 217, it is possible to provide a structure for preventing the sintered magnet 218 from coming off.

(Structure for Supporting Second Wheel) In FIG. 3, the rotary weight 25 is also supported by the first wheel train bridge 3, and the second wheel & wheel 54 is also assumed to be the first wheel train bridge. With the configuration of being supported by No. 3, it becomes difficult to perform the lubrication work to the upper tenon portion of the center wheel & pinion 54 and the management of the lubrication condition. The part that needs lubrication is normally visible from the outside when the movement is assembled.
When the configuration in which is supported by the first train wheel bridge 3 is adopted, the upper tenon portion of the center wheel & pinion 54 is hidden by the rotary weight 25. On the other hand, if a female screw portion for fixing the rotary weight fixing screw 250 to the bearing shaft 97 is used as a through hole so that the portion where lubrication is necessary can be seen, cutting and abrasion from this portion toward the center wheel & pinion 54. The powder may fly and the load on the timepiece train wheel 50 may increase.

Therefore, in the present embodiment, the center wheel & pinion 54 is laminated and fixed on the side of the main plate 2 (the side opposite to the side on which the rotary weight 25 is supported) with respect to the first train wheel bridge 3. The structure supported by the second train wheel bridge 6 is adopted. According to this structure, the main train 2 has the timepiece wheel train 50 and the power generation wheel train 60.
The second wheel train bridge 6 can be installed after the installation, and then the upper tenon portion 541 of the center wheel & pinion 54 can be lubricated. Therefore, the internal thread portion of the bearing shaft 97 does not have to be a through hole, and the timepiece train wheel 50 such as the center wheel & pinion 54 is not affected by cutting chips or the like. Further, in the present embodiment, the height dimension of the center wheel & pinion 54 is shortened by a dimension corresponding to the plate thickness of the second train wheel bridge 6, and even if the second train wheel bridge 6 is added, the entire thickness of the movement. Is not increasing.

As a train wheel bridge, a first train wheel bridge 3 and
The second train wheel bridge 6 is used by using the second train wheel bridge 6 laminated and fixed to the first train wheel bridge 3 and with respect to the first train wheel bridge 3
Since the structure in which the rotary weight 25 is supported on the side opposite to the above, the first train wheel bridge 3 can be effectively reinforced by the second train wheel bridge 6. Therefore, the rotary weight receiver that has been conventionally used is omitted, and the rotary weight 25
Even if the first train wheel bridge 3 is used to support the wheel train, there is no problem in the strength of the train wheel bridge. Therefore, the area occupied by the screwed portion can be reduced by omitting the rotary weight receiver and reducing the number of screwed portions. Therefore, in the present embodiment, since the parts occupied by the screwed portions are reduced, the respective parts can be efficiently arranged, so that the pointer-type electronic timepiece 1 can be made smaller and thinner.

In the present embodiment, a clearance is secured between the tenon frame 545 for receiving the center wheel & pinion 54 and the lower end surface 977 of the bearing shaft 97 so that the center wheel & pinion 54 does not creak due to variations in parts. On the other hand, around the tenon frame 545, the second train wheel bridge 6 and the first train wheel bridge 3 are in contact with each other. Therefore, when a strong force is applied to the tenon frame 545 when the pointer is pushed in, the second train wheel bridge 6 bends and the tenon frame 545 contacts the lower end surface 977 of the bearing shaft 97.
Therefore, the tenon frame 545 is prevented from being displaced from the second train wheel bridge 6.

(Details of the second train wheel bridge 6) The second train wheel bridge 6 is laminated over the first wheel train bridge 3 over a wide area. A hole 601 and a notch 604 capable of supporting the third wheel & pinion 53 and the motor rotor 42, which are about to fall when the movement is assembled, are secured in a portion corresponding to the supporting position of the back wheel 55. In the hole 601 and the notch 604, the opening edge of the second train wheel bridge 6 is cut obliquely at the portion of the hole 601 having a narrow gap with the gear. At the time of assembling, even if the motor rotor 42 is tilted, the slope of the motor rotor 42 is corrected by the slope, and the motor rotor 42 is assembled.

Further, the notch 603 formed at the portion corresponding to the supporting position of the date driving wheel 55 projects so as to approach the shaft portion of the date driving wheel 55, and as a result,
A very narrow gap is formed between the hole stone 555 fitted to the shaft end and the lubricating oil is sucked into the gap. Therefore, in this embodiment, the step 60 is provided in the cutout 604.
By forming 3, the gap with the hole stone 555 is made sufficiently wide to prevent the lubricating oil from being sucked therein.

In the present embodiment, the timepiece without the second hand has been described as an example. However, in the case of the timepiece with the second hand, as shown in FIG. The tenon 525 is supported by the second train wheel bridge 6.

(Arrangement Structure of Switching Member for Time Adjustment) FIG. 11 is an explanatory view showing a planar arrangement relation of mechanical parts for time adjustment in the pointer type electronic timepiece according to the present embodiment. The mechanical parts for alignment are indicated by thick lines, and the other parts are indicated by thin lines. FIG. 12 is a cross-sectional view showing the configuration of the tip portion of the train wheel setting lever. Figure 13
It is sectional drawing which shows the structure of the front-end | tip part of a reset lever. 14 (A) and 14 (B) are cross-sectional views of a winding stem and a small iron wheel seat supporting the winding stem.

In FIG. 11, in the pointer type electronic timepiece 1,
A mechanism for adjusting the pointer by operating the crown 7 or the like is also configured. The basic configuration of this mechanism is
Since the mechanism is the same as a conventional mechanism, detailed description thereof will be omitted, but a winding rod 71 is engaged with the winding stem 70 connected to the crown 7. The kanuki 72 is the winding true 70
Is engaged with the groove of the clutch wheel 73 connected to the. Therefore, if you pull out the crown 7 one step,
It rotates in the direction of arrow S. Here, since the cam groove of the train wheel setting lever 74 is engaged with the dowel 78 formed on the temple 71, when the crown 7 is pulled out, the train wheel setting lever 74 is pulled out.
Rotates in the direction of the arrow T, and as shown in FIG. 12, the locking portion 741 standing upright at the tip of the train wheel setting lever 74,
It engages with the third wheel & pinion 53 and stops the movement of the pointer. Further, in this state, when the crown 7 is turned, it becomes possible to rotate the date driving wheel 55 and the like via the iron wheel 79 (see FIG. 11 and FIG. 14 (B)).

Further, a reset lever 75 shown in FIG. 13 is mechanically connected to the lever 71, and when the crown 7 is pulled out by one step, the reset lever 75 rotates along the main plate 2. Since the contact portion 315 protruding obliquely downward from the circuit board 31 is located on the side of this rotation direction,
Interlocking with the operation of pulling out the crown 7 one step, the contact portion 75 bent in a Z shape at the tip of the reset lever 75.
5 comes into contact with the contact portion 315 and the switch is activated. In this state, the output of the drive signal from the drive circuit (not shown) formed on the circuit board 31 to the step motor 40 is stopped, so that the rotation of the motor rotor 42 is also stopped. Here, since the contact portion 315 projects obliquely downward from the circuit board 31, the contact between the contacts is reliable even though the switch mechanism is configured in a narrow space.

The circuit board 31 is positioned with the projections 312 of the small iron seat 311 fitted in the holes 310 formed therein, and is fixed by being pressed by the circuit pressing plate 316. Therefore, when the crown 7 is pushed in from the pulled-out state, the contact point 715 and the contact point portion 755 are separated from each other, so that the drive signal is again output from the step motor 40 from the drive circuit. Therefore, the motor rotor 42 starts to rotate again. Also, crown 7
When is pushed in, the train wheel setting lever 74 is separated from the third wheel & pinion 53, so that the pointer is restarted to rotate.

Since the reset lever 75 is made of a thin plate, the reset lever 75 is in the rotation region of the rotary weight 252 of the rotary weight 25 (the rotation region of the thick portion of the rotary weight 25 and the base plate 2). And between). Further, a switching member such as the boot 72 is also arranged in the rotation region of the rotary weight 252 of the rotary weight 25.

In this embodiment, as shown in FIGS. 14 (A) and 14 (B), the winding stem 70 is a small iron wheel seat 311 made of synthetic resin.
It is arranged and supported so as to pass through the inside of. As shown in FIG. 14 (A), the small iron seat 311 is provided with a projecting portion 319 protruding so as to sneak into the lower layer side of the power generating stator 22 and its magnetic core 221. Therefore, when the power generation stator 22 and the magnetic core 221 thereof are screwed, the small iron pedestal 311 is also attached to the power generation stator 2.
2 and the magnetic core 221. Therefore, it is easy to assemble and the small iron car seat 31
There is no rise of 1.

[0088]

As described above, in the electronic timepiece according to the present invention, the attitude of the rotary weight is maintained in a predetermined state by positively contacting the outer peripheral portion of the rotary weight with the support. Prevents unnecessary interference between the rotary weight and the surroundings when the rotary weight that rotates at high speed moves up and down. For this reason, since it is not necessary to make a wide gap between the rotary weight and the surroundings, it is possible to reduce the size and thickness of the electronic timepiece having the small generator built therein. In addition, the rotating weight hits only the support for supporting the timepiece mechanical body in the outer case,
It does not add new parts. From this point as well, it is suitable for reducing the size and thickness of an electronic timepiece having a small generator built therein. Furthermore, since the outer periphery of the rotary weight is hit with a sturdy support, unlike the configuration in which the rotary weight is hit against the train wheel bridge or the main plate, the wheel train for timepieces caused by deformation of the train wheel bridge or the main plate And no problems with the power train.

[Brief description of drawings]

FIG. 1A is a schematic configuration diagram showing an overall configuration of a pointer type electronic timepiece to which the invention is applied, and FIGS. 1B and 1C are explanatory diagrams showing a structure of a rotary weight.

FIG. 2 is a plan view showing a layout of a main plate that supports each component, a first train wheel bridge, and a second train wheel bridge in the pointer type electronic timepiece to which the invention is applied.

FIG. 3 shows a pointer type electronic timepiece to which the present invention is applied, in which a date wheel, a center of a rotary weight (screw for fixing the rotary weight), a second wheel,
It is sectional drawing when it cut | disconnects at the position which passes an hour wheel, a third wheel, a rotor for motors, and a set screw.

FIG. 4A is a pointer type electronic timepiece to which the present invention is applied, showing a coil for power generation, a rotor for power generation, a transmission wheel for power generation, a wheel behind the sun, a center of a rotary weight (screw for fixing the rotary weight). ,
Sectional view when cut at a position passing through the second wheel and hour wheel,
(B) is an enlarged cross-sectional view of a bearing portion of the power generation rotor.

5A and 5B are respectively a plan view and a BB ′ cross-sectional view of a middle frame which is an exterior case member used in the pointer type electronic timepiece to which the present invention is applied.

FIG. 6 is a sectional view of a portion passing through a set screw, a coil of a step motor, and another set screw in a pointer type electronic timepiece to which the invention is applied.

FIG. 7 is a cross-sectional view of a portion passing through a set screw and a center of a rotary weight (screw for fixing the rotary weight) in the pointer type electronic timepiece to which the invention is applied.

FIG. 8 is a cross-sectional view of a portion passing through the set screw and the date indicator wheel in the pointer type electronic timepiece to which the invention is applied.

FIG. 9 is a plan view of a rotary spindle wheel used in a pointer type electronic timepiece to which the invention is applied.

FIG. 10 shows a pointer type electronic timepiece to which the present invention is applied,
It is sectional drawing which shows the structural example in case it has the 4th wheel with which the second hand was attached.

FIG. 11 is an explanatory diagram showing a planar arrangement relationship of a time adjustment mechanism portion in the pointer type electronic timepiece to which the invention is applied.

FIG. 12 is a cross-sectional view showing a configuration of a tip end portion of a train wheel setting lever in a pointer type electronic timepiece to which the invention is applied.

FIG. 13 is a cross-sectional view showing a configuration of a tip end portion of a reset lever in a pointer type electronic timepiece to which the invention is applied.

14A and 14B are cross-sectional views of a winding stem and a small iron wheel seat supporting the winding stem in the pointer type electronic timepiece to which the invention is applied.

FIG. 15 is a schematic configuration diagram showing an overall configuration of a conventional pointer type electronic timepiece.

FIG. 16 is a cross-sectional view showing a support structure for a rotary weight in a conventional pointer type electronic timepiece.

[Explanation of symbols]

1 Pointer type electronic timepiece 2 Main plate 3 First wheel train bridge 5 Middle frame (frame / support) 6 Second wheel train bridge 7 Crown 9 Outer case 10 Power supply section 17, 18, 26 Set screw 20 Small generator Reference Signs List 21 power generation rotor 22 power generation stator 23 power generation coil 25 rotary weight 30 secondary power source (capacitor) 31 circuit board 32 crystal oscillator 40 step motor 41 coil 42 motor rotor 43 motor stator 44 magnetic core 52 fourth wheel 53 three Wheel 54 Second wheel 55 Day wheel 56 Wheel wheel 50 Clock wheel train 60 Power generation wheel train 61 Spindle wheel 62 Power generation rotor transmission wheel 63 Hour hand 64 Second hand 68 Back cover 69 Minute hand 70 Winding stem 71 Whiskers 72 Kanuki 73 Catch wheel 74 Control lever 75 Reset lever 78 Exterior case body 79 Small iron wheel 90 Ball bearing 91 Bearing ball 92 Inner member 93 Outer ring ( Outer member) 94 Inner ring 95 Ball retaining ring 96 Retainer 97 Bearing shaft (guide shaft) 170, 180, 260 Metal cylindrical screw seat 211 Rotation center shaft 212, 214, 555 of the rotor for power generation, S hole stone 213, 215 Cap 267 Sleeve 250 Rotating Weight Fixing Screw 251 Thin Rotating Weight Body (Thin Section) 252 Rotating Weight (Thick Section) 253 Welding Recess 311 Small Iron Car Seat 315 Circuit Board Contact Point 502 Middle Frame Dowel (degree) (Contact part / protrusion) 601 anti-tilt hole 603 notch step 604 anti-tilt notch 611, 612 rotary spindle wheel edge 613 rotary spindle wheel opening 614 rotary spindle wheel spring 755 reset lever Contact portion 931 Small diameter portion 932 of outer ring Large diameter portion 933 of outer ring Medium diameter portion 934 of outer ring Caulking portion 941 Fitting portion 94 of inner ring Relief part of inner ring G Gap for retaining lubricating oil C1 Center position in thickness direction of pressure contact part between sleeve and cap C2 Center position in thickness direction of pressure contact part between cap and hole stone C3 Pressure contact part between sleeve and base plate Position in the thickness direction of

Claims (5)

(57) [Claims] And 1. A small generator comprising the rotary spindle rotates by the movement of a user of the watch, and the power generation train wheel for transmitting the rotary motion of the rotary weight, based on the electrical energy generated by the small generator driving Te and clock machine body, in an electronic timepiece having a outer casing for housing the said time meter machine body and the small generator, together with the clock machine body is supported by a support within said outer casing, said support Koo a plurality of protrusions as per unit time facing the rotary spindle side, by an outer peripheral portion of the rotary weight relative to the butting portion is contact time in the cross direction, the rotational position of the rotary weight is An electronic timepiece characterized by being configured to be held. 2. A method according to claim 1, wherein the rotary weight has one which includes a thin portion on the rotational center side, the outer periphery of the thin portion has a thick portion, the thick portion is the support An electronic timepiece that hits against the hitting part of. 3. The rotary weight according to claim 2, wherein the thin-walled portion is provided with a groove-shaped opening in the thin portion over an angular range of 180 ° or more around a rotation center thereof. An electronic watch. 4. The method according to any one of claims 1 to 3,
The watch machine body, a secondary power supply for storing electric energy generated by the small generator, the step motor to the power supply the secondary power source, the timepiece wheel train for transmitting the rotational driving force to the pointer from the step motor, and A wheel train bridge for supporting the wheel train for a timepiece with a main plate is provided, the small generator is mounted on the timepiece mechanical body, and the support member is provided with the timepiece mechanical body in the outer case through the main plate. An electronic watch characterized by being supported by. 5. The method of claim 4, wherein the support, the a sandwiched a frame member between the cylinder and the back cover constituting the external case, the frame, the exterior of the outer peripheral portion of the base plate An electronic timepiece characterized in that the timepiece mechanical body is supported in the exterior case by being sandwiched between the case and the case.