JPH11142547A - Pointer type electronic timepiece - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve miniaturization and thinning by efficiently arranging a mechanical part being constituted inside a timepiece. SOLUTION: Since a rotary weight 25 is also supported by a first race 3 that is a fixing-side member as in a race for a timepiece, only the first race 3 may be screwed and fixed to the ground plate 2, thus eliminating the need for separately screwing and fixing a rotary weight pad to the ground plate and hence reducing the number of places for screwing. The first race 3 is reinforced by a second race 6 being laminated and fixed to the first race 3. An inside member 92 of a ball bearing 90 is fixed to the first race 3, and the rotary weight 25 is fixed to the side of an external wheel 93.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pointer-type electronic timepiece having a so-called automatic small generator. More specifically, the present invention relates to a structure technique for reducing the thickness and size of a pointer-type electronic timepiece.

[0002]

2. Description of the Related Art In a so-called electronic timepiece using a quartz oscillator or the like as a time reference, a small power generator 20 and a secondary power supply 30 constitute a power supply 10 as shown in FIG. As the step motor 40
Is to be driven. In the stepping motor 40, the timepiece train wheel 50 is connected to the motor rotor 42, and the hands attached to each wheel are driven. On the other hand, the small generator 20 includes a power generation rotor 21 that rotates by the rotational driving force transmitted from the rotary weight 25,
A power generation stator 22 sandwiching the power generation rotor 21 and a power generation coil 23 forming a magnetic circuit with the power generation stator 22 and the power generation rotor 21 are configured.
, A power generation wheel train 60 configured to transmit the rotational operation of the rotary weight 25 at an increased speed is configured. The rotary weight 25 has a groove-shaped opening 259 in its thin portion 251 to prevent the received impact from being directly applied to the movement, and has a structure in which the impact is absorbed by bending. However, since the oscillating weight 25 is substantially semicircular, the opening 259 is formed around the oscillating weight fixing screw 250 within an angle range of about 160 °.

As shown in FIG. 15, the rotary weight 25 is supported by a rotary weight receiver 300 different from the wheel train receiver 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 the
For the inner ring 94, the oscillating weight 25 is fixed to the oscillating weight fixing screw 25.
It is screwed by 0. The timepiece train wheel 50 is supported between the train wheel bridge 3A and the base plate, and the power train wheel train 60 is supported between the rotary weight bridge 300 and the base plate 2. Inner ring 94
A female screw is formed on the inner peripheral surface of the through hole formed in the center portion of the motor. The lubricating oil is supplied from this through hole to the timepiece train wheel before the rotary weight fixing screw 250 is stopped. It is possible.

[0004]

Here, there is a strong demand for further reduction in the size and thickness of a pointer-type electronic timepiece, even if it is a type provided with a small generator. However, there is a problem that such a demand cannot be realized simply by reducing the size and thickness of each component such as a rotary weight constituting a small generator. For example, when the oscillating weight is made thinner or smaller, the weight imbalance in the angular direction of the oscillating weight becomes smaller, and it becomes difficult to obtain high-speed rotation of the oscillating weight. Also, since the necessary components are mounted on the circuit board, it cannot be further reduced in size and thickness.However, if the arrangement space is narrowed, it may interfere with the gears that constitute the wheel train. There is also a risk that they will be lost.

Further, as shown in FIG. 15, in a configuration in which the stopped portion of the rotary weight fixing screw 250 rotates together with the rotary weight 25, there is a problem that the rotary weight fixing screw 250 is likely to be loosened. . Further, in the configuration in which the head of the oscillating weight fixing screw 250 projecting toward the back cover 68 rotates, the back cover never contacts the head of the oscillating weight fixing screw 250 when carrying. Since it is necessary to ensure a sufficient gap between the head of the rotary weight fixing screw 250 and the back cover, there is also a problem that the thickness of the pointer type electronic timepiece is hindered.

[0006] In view of the above problems, an object of the present invention is to provide a pointer-type electronic timepiece that can be made thinner and smaller by improving the structure of mechanical components formed inside the timepiece.

[0007]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, according to the present invention, there is provided a small-sized rotating weight which is rotated by the movement of a user of a timepiece, and a power train for transmitting the rotating motion of the rotating weight. A generator, a step motor driven by electric energy generated by the small generator, a timepiece train wheel transmitting a rotational driving force from the step motor to the hands, and In a pointer-type electronic timepiece having a train wheel bridge to support, the rotating weight is supported by the train wheel bridge at the center of rotation.

In the present invention, since the rotating weight is also supported by the wheel train receiver as in the case of the timepiece wheel train, even the wheel train receiver may be screwed and fixed to the base plate. For this reason, since it is not necessary to separately provide a rotary weight receiver and fix the screw to the main plate, the number of screwed portions can be reduced. Therefore, the area occupied by the screwed portion can be reduced, and each component can be efficiently arranged. Further, since the rotary weight receiver is not required, the size and thickness of the pointer-type electronic timepiece can be reduced.

In the present invention, the rotating weight includes, for example, a bearing ball, an inner member for supporting the bearing ball on the inner peripheral side, and an outer member for holding the bearing ball between the inner member and the bearing member. And is supported by the train wheel bridge.

In the present invention, the train wheel bridge includes a first train wheel bridge supporting the rotating weight, and a first train wheel bridge between the first train wheel bridge and the main plate. It is preferable that a second train wheel bridge laminated on the first train wheel bridge so as to substantially overlap the mounting portion of the ball bearing is provided.

In the present invention, it is preferable that, of the inner member and the outer member of the ball bearing, the inner member is fixed to the train wheel bridge, and the rotating weight is fixed to the outer member.

[0012] In the present invention, of the power train,
It is preferable that the rotating wheel that rotates integrally with the rotating weight is also fixed to the outer member of the ball bearing.
In this way, if the oscillating weight and the oscillating weight wheel can be mounted on the ball bearing in advance in a form that is actually arranged in the timepiece, the quality of the state in which the oscillating weight and the oscillating weight wheel are actually assembled in the timepiece can be inspected, and the assembling can be performed. The number of parts handled in the process can be reduced. In addition, since the rotating weight does not rotate when the rotating weight fixing screw is tightened, the screw can be tightened without causing scratches or chips on peripheral components.

In the present invention, the outer member of the ball bearing has a small-diameter portion on which the rotary wheel is mounted and a position connected to the small-diameter portion from the end face on the base plate side to the end face on the opposite side. A large-diameter portion having an outer diameter dimension larger than the small-diameter portion, and a middle-diameter portion having an outer diameter dimension smaller than the large-diameter portion and larger than the small-diameter portion at a position connected to the large-diameter portion are formed in this order. The rotating weight is sandwiched between the caulked portion formed on the edge side of the middle diameter portion and the large diameter portion in a state of being attached to the middle diameter portion, and is in a state of being fixed thereto. Is preferred. With such crimping fixation, unlike press-fitting fixation, it is easy to secure the rotational torque, and the rotating weight does not come off.

[0014] In the present invention, it is preferable that the inner member is pressed and fixed to the wheel train bridge by a rotary weight fixing screw screwed toward the main plate. In the present invention, even when the rotating weight is screwed to the inner member,
Since the screwed portion does not rotate, the screw is not loosened at the screwed portion. Further, since the screwed portion does not rotate, the back cover can be arranged close to the screw, so that the thickness of the pointer-type electronic timepiece can be reduced.

In the present invention, it is preferable that an end face on the main plate side of both end faces of the inner member is in contact with the train wheel bridge. With this configuration, since the inner member is surface-supported by the train wheel bridge, it is possible to prevent the inner member from tilting and the rotating weight from tilting.

In this case, the outer diameter of the contact area between the inner member and the train wheel bridge is determined, for example, by considering the balance between the size restriction and the effect of preventing the inclination of the oscillating weight. A range from 1/3 times to 1/10 times the diameter is preferable.

In the present invention, the inner member has a through hole formed in a rotation center portion of the ball bearing, and a guide shaft fixed to the train wheel bridge is fitted and fixed in the through hole. It is preferable that the rotary weight fixing screw is screwed into the shaft end face of the guide shaft so as to tighten and fix the inner member of the ball bearing toward the wheel train bearing.

In the present invention, it is preferable that the inner member includes a fitting portion having a small inner diameter and a relief portion having a large inner diameter on the inner peripheral side of the through hole. By forming such a fitting portion, the engagement allowance can be accurately defined by the length dimension of the fitting portion. Therefore, it is possible to prevent the engagement margin from being large and the inclination of the guide shaft from becoming the inclination of the rotary weight as it is. The ball bearing of the oscillating weight is easily tilted because it has a bearing ball, but even if the inner member is inclined when the oscillating weight is attached or detached, the engagement allowance is short, so that biting does not occur and work can be done smoothly. it can.

In the present invention, the inner member has an inner ring having an L-shaped cross-section including a cylindrical portion into which the guide shaft is fitted, and a flange portion extending outward from the cylindrical portion.
A ball press ring which is press-fitted into the inner ring to form a ball raceway surface together with the inner ring, and a portion of the inner peripheral surface of the cylindrical portion on which the ball press ring is disposed is outside the guide shaft. It is preferable that the guide shaft be fitted and fixed by an inner peripheral portion corresponding to the flange portion, having an inner diameter larger than the diameter. With this configuration, even if the inner ring is deformed when the ball presser ring is pressed into the inner ring,
This press-fit portion (deformed portion) is a portion having a large inner diameter. Therefore, even if the inner ring is deformed at the time of press-fitting the ball presser ring, the deformation does not hinder the fitting of the guide shaft.

According to another aspect of the present invention, there is provided a small-sized generator having a rotating weight that is rotated by the movement of a user of a timepiece, a power train for transmitting the rotating motion of the rotating weight, and a small-sized generator. Pointer type having a step motor driven by the generated electric energy, a wheel train for transmitting a rotational driving force from the step motor to the hands, and a wheel train support for supporting the time wheel train between the main plate. In the electronic timepiece, the train wheel bridge includes a first train wheel bridge, and a second train wheel bridge stacked on the first train wheel bridge. The rotary weight is provided on the side opposite to the second train wheel bridge.

In the present invention, the first train wheel bridge can be effectively reinforced by the second train wheel bridge, so that the conventionally used rotating weight bridge is omitted and the rotating weight is supported by the wheel train bridge. Even
There is no problem in the strength of the train wheel bridge. For this reason, it is possible to reduce the number of screwed portions by omitting the rotary weight receiver. Therefore, the area occupied by the screwed portion can be reduced, and each component can be efficiently arranged. Therefore, the pointer-type electronic timepiece can be reduced in size and thickness.

In the present invention, it is preferable that the first train wheel bridge, the second train wheel bridge, and the main plate are fixed at a plurality of positions so as to surround a mounting portion of the ball bearing in a plane. . With this configuration, a portion where a large load is applied can be effectively reinforced.

In the present invention, the first wheel train receiver, the second wheel train receiver, and the fixing portion of the main plate may be arranged in a region corresponding to an inner side of a thick portion of the rotating weight. preferable. By optimizing the arrangement position according to the height of the component, such as arranging the fixed portion in the rotation area of the thin portion of the oscillating weight, the component can be arranged efficiently. Therefore, the pointer-type electronic timepiece can be reduced in size and thickness.

In the present invention, it is most preferable that the first wheel train receiver, the second wheel train receiver and the base plate are fixed with screws. This is because fixing with screws is excellent in reliability when used for a long period of time or when it is repeatedly attached and detached, and because the structure is simple, it is possible to reduce the cost.

In the present invention, a plurality of screws for fixing the first train wheel bridge to the base plate are arranged so as to surround a rotating weight fixing screw for attaching the rotating weight to the train wheel bridge. It is preferable that at least two of the screws for fixing the train wheel bridge to the main plate are arranged within a radial distance corresponding to a half of the outer diameter of the oscillating weight from the oscillating weight fixing screw. With this configuration, even if an external force acts on the train wheel bridge due to the rotating weight, the screw portion fixing the train wheel bridge is supported near the center, so that the train wheel bridge is less likely to bend, and the train wheel support is reliably provided. Yes, the train is not destroyed. Further, since the fixed portion of the rotating weight is stabilized, the inclination of the rotating weight can be suppressed.

In the present invention, each of the gears constituting the timepiece train wheel is provided in a region which is planarly surrounded by the first wheel train receiver, the second wheel train receiver and the screwed portion of the main plate. It is preferable that at least half of the Since the area surrounded by such screwing points has high strength and the train wheel bridge does not deform, when the impact is applied, the train wheel can be securely supported without breaking the train wheel, so the train wheel is arranged. Suitable for

[0027]

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

(Overall Configuration) FIG. 1A is a schematic configuration diagram showing the overall configuration of the pointer-type electronic timepiece of the present embodiment. Since the basic structure of the pointer-type electronic timepiece of the present embodiment is the same as that of a conventional pointer-type electronic timepiece, parts having common functions are denoted by the same reference numerals.

Referring to FIG. 1A, a pointer-type electronic timepiece 1 of the present embodiment is an analog quartz wristwatch of a pointer display type, and a step based on a signal transmitted from a crystal oscillator 32 mounted on a circuit board 31. The motor 40 is driven. The step motor 40 is formed by winding a motor rotor 42 made of a permanent magnet magnetized to two poles, a motor stator 43 having a cylindrical rotor arrangement hole 430 in which the motor rotor 42 is arranged, and a coil 41. And a coil block comprising the magnetic core 44. The motor wheel 42 is provided with a third wheel 53, a second wheel 54, a minute wheel 55, and an hour wheel 56 through a kana portion.
Is connected. A minute hand 69 is fixed to a shaft end of the center wheel & pinion 54, and an hour hand 63 is fixed to a tip of a cylindrical shaft of the hour wheel & pinion 56.

The power supply section 10 for driving the step motor 40 is generally constituted by a small generator 20 and a secondary power supply 30 (capacitor). Small generator 20
Is a one-piece rotating weight 2 that is rotated by the movement of the arm so as to generate power when the arm on which the pointer-type electronic timepiece 1 is fitted is moved.
5, a power generation rotor 21 which rotates by receiving kinetic energy from the rotary weight 25, a power generation stator 22 sandwiching the power generation rotor 21, and a magnetic circuit with the power generation stator 22 and the power generation rotor 21. Power generation coil 2
And 3.

The oscillating weight 25 and the power generation rotor 21 are mechanically connected by a power generation wheel train 60 for transmitting the rotational operation of the weight 25 at an increased speed.
It is composed of a rotary wheel 61 integrally formed with the rotary weight 25 and a power generation rotor transmission wheel 62 having a pinion engaged with the gear. The power generation rotor 21 has magnetic poles N and S
Are formed, and when the rotation of the rotary weight 25 is transmitted, the magnetic poles N and S rotate.
3, an induced electromotive force can be obtained, and the secondary power supply 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 the arm of the person who carries the wristwatch, or a vibration caused by the walking of the user of the pocket watch. Also, as a special example, when attached to an animal such as a whale, it refers to vibration caused by the animal's migration or walking movement.

As will be described in detail later, the rotary weight 25 is provided with a rotary weight fixing screw 250 at the center of rotation. In this rotary weight 25, the rotary weight fixing screw 2
A peripheral portion of 50 (rotation center portion) is constituted by a rotating weight body 251 (thin portion) made of a thin plate, and a rotating weight 252 (thick portion) is connected to an outer peripheral portion thereof. By using the rotating weight 252, the weight imbalance of the rotating weight 25 is increased even when the timepiece body is thinned.

(Structure of Rotating Weight) In the rotating weight 25, the rotating weight body 251 has an impact relaxation structure to prevent the shock applied to the rotating weight 252 from being directly transmitted to the movement and damaging the movement. I have. As such a shock absorbing structure, a rotary weight fixing screw 2
A groove-shaped opening 259 is formed around the rotation weight 50.
1 is easily bent. In the present embodiment, although the rotary weight 25 is substantially semicircular, the opening 259 is
0, the opening 2 is formed.
59 are formed over an angle range of 180 ° or more. With this, as the timepiece becomes smaller, the rotating weight 25
Even if it is reduced in size, the resilience can be secured, and the function of the oscillating weight 251 is not impaired.

In this embodiment, as shown in FIG. 1B, the rotating weight 25 is a thin rotating weight 2 located on the inner peripheral side.
51, and a thick rotating weight 252 welded from the side of the rotating weight 251 at a portion where the rotating weight 251 overlaps the outer peripheral side, so that the rotating weight 251 and the rotating weight 252 are formed. If a region corresponding to the welding portion is formed as the concave portion 253, the designated welding position can be easily understood at the time of the welding operation, and the welding operation can be facilitated. In addition, since welding marks are formed in the concave portions 253, the welding marks are
Does not protrude from the surface.

Further, as shown in FIG.
5, the thin rotating weight 251 located on the inner peripheral side
If welding is performed from the side of the oscillating weight 251 at a portion where the oscillating weight 252 is overlapped with the thick oscillating weight 252 located on the outer peripheral side thereof, the oscillating weight 251 is attached to the oscillating weight 252 with a ground plate (see FIG. (Not shown). With such a configuration, the welding marks are covered with the base plate, so that the rotary weight 25 has a good appearance even when it is configured to be visible from the outside.

(Fixed Structure of Rotating Weight and Wheel Train) The arrangement structure of each component having a power generation function and a hand movement function will be described.

FIG. 2 shows the main plate 2, the first train wheel bridge 3, and the second
FIG. 2 is a plan view showing a layout of a train wheel bridge 6 of the base plate 2,
The outlines of the first train wheel bridge 3 and the second train wheel bridge 6 are indicated by a thick solid line, a thick dotted line, and a thick one-dot chain line, and other parts are indicated by thin lines.

In FIG. 2, the central portion of the main plate 2 is a portion to be the center of rotation of the rotary weight 25 and each pointer. The base plate 2 is provided with a timepiece dial on the back side, and in the drawing, in each angular direction of the base plate 2, each time (3 o'clock, 6 o'clock, 9 o'clock, 12 o'clock). The rotation area of the oscillating weight 25 is an area indicated by a dashed line L1 slightly inside the outer peripheral edge of the main plate 2. Inside the one-dot chain line L1, the one-dot chain line L2 indicates the rotational position of the boundary between the oscillating weight body 251 (thin portion) and the oscillating weight 252 (thick portion), which are formed on the oscillating weight 25. .

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

As shown in FIG. 2 and FIG.
The third wheel & pinion 53, the second wheel & pinion 54, and the third wheel 53 described with reference to FIG.
A watch train wheel 50 having a large height such as a minute wheel 55 and an hour wheel 56 is arranged. The third wheel 53, the minute wheel 55, and the motor rotor 42 of the timepiece wheel train 50 are composed of the main plate 2 and the first flat wheel train receiver 3 which is disposed to face the main plate 2. Is supported via a tenon frame made of a pit stone S or the like. This first train wheel bridge 3
Is disposed inside the rotation region of the thin portion 251 of the oscillating weight 25, that is, inside the dashed line L2.

Here, the arrangement of the timepiece train wheel 50 and its surroundings will be described in detail. In the plane direction of the movement, a center wheel & pinion 54 supporting a minute hand 69 at the center thereof.
Is arranged. In the thickness direction, in the direction from the gear portion of the second wheel & pinion 54 to the rotary weight 25, the pinion of the second wheel & pinion 54, the third wheel & pinion 53, and the second wheel & pinion 5 supported by the second wheel train bearing 6
4, an upper tenon bearing portion, a bearing shaft 97 fixed to the first train wheel bearing 3, a ball bearing 90, and a rotary weight fixing screw 250 are arranged in this order, and the thickness of the movement is determined at this portion.

The third wheel & pinion 53, the minute wheel 55 and the motor rotor 42 are supported between the first wheel train bridge 3 and the main plate 2, and the second wheel train bridge 6 and the main plate 2 are connected to each other. In comparison with the parts supported between the two, the upper tenon (the tenon on the first wheel train 3 side) and the lower tenon (the tenon on the main plate 2 side) ) Can be made longer. Therefore, with respect to the third wheel & pinion 53, the minute wheel & pinion 55 and the motor rotor 42, the inclination of these wheel trains can be reduced even if the upper and lower bearings are slightly displaced in plane. Therefore, in the third wheel 53, the minute wheel 55, and the motor rotor 42, it is possible to suppress the creaking of the upper tenon or the lower tenon and the overload at the meshing portion of the gears.
A decrease in transmission efficiency can be prevented.

In the third wheel & pinion 53, the minute wheel & pinion 55, and the motor rotor 42, the portion at the same height position as the second wheel train bridge 6 has a thickness corresponding to the thickness of the second wheel train bridge 6. In this case, the length of the body connecting the upper tenon and the bevel or the gear can be lengthened. Normally, lubricating oil is applied to the mortise bearing, but if the body is short and the distance between the upper mortise and the pinion or gear is short, lubricating oil that has risen due to surface tension will be applied to the pinion or gear. It becomes easy to adhere, and the oil retaining property at the bearing part decreases. However, in the present embodiment, since the second wheel train bearing 6 is arranged to lengthen the torso portion and keep the upper tenon portion and the pinion or gear portion away from each other, the oil retaining property at the bearing portion is improved. Can be.

The center wheel & pinion 54, whose upper tenon is supported by the second train wheel bridge 6, has a greater thickness in the thickness direction than the timepiece wheel train 50, in which the upper tenon is supported by the first train wheel bridge. Although it is arranged at a lower position, the lower tenon is guided by a center pipe having an inverted L-shaped cross section on the side of the main plate 2, so that the distance between the upper tenon and the lower tenon is sufficiently long. Therefore, the inclination of the center wheel & pinion 54 can be reduced, and the structure has no functional hindrance.

Here, the first train wheel bridge 3 is fixed to the base plate 2 together with a second train wheel bridge, which will be described later, by three setscrews 17, 18, and 26. Are located inside the rotation area. Fixing using such a screw is excellent in reliability when used for a long time or when repeatedly attached and detached, and can be made inexpensive because of its simple structure. As can be seen from FIG. 2, the timepiece wheel train 5 is placed in a region surrounded by a plane where the three setscrews 17, 18, 26 screw.
0 (the third wheel 53, the second wheel 54, the minute wheel 55, and the hour wheel 56) are located. The first train wheel bridge 3 is disposed in a range that overlaps all of the power generation wheel train 60 and the timepiece wheel train 50.
Of the set screws 17, 18, 26, the set screw 17,
18 and is fixed to the base plate 2 together with the first train wheel bridge 3, 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 wheel train 60 but to substantially overlap the timepiece wheel train 50. ing. Such a set screw 17, 1
The region surrounded by the screwing points 8 and 26 is reinforced by the second train wheel bridge 6 even when the first train wheel bridge 3 tries to deform to the timepiece wheel train 50 side. Since the first wheel train bearing 3 has high strength, the first wheel train bridge 3 is surely connected to each gear (the third wheel 53, the second wheel 54, the minute wheel 55, and the 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
Weight fixing screw 250 for attaching 5 to first train wheel bridge 3
, And all of the set screws 17, 18, 26 for fixing the first train wheel bridge 3 to the base plate 2 are from the oscillating weight fixing screw 250 to the outer diameter of the oscillating weight 25.
/ 2. For this reason, even if an external force acts on the first train wheel bridge 3 due to the rotary weight 25, the first wheel train bridge 3 is less likely to bend since the set screw portion fixing this wheel train bridge is supported near the center. In addition, the train wheel can be reliably supported, and the train wheel is not broken. In addition, the rotating weight 2
Since the fixed portion of the rotary member 5 is stable, the inclination of the rotary weight 25 can be suppressed.

(Arrangement of Power Generation Wheel Train) FIG.
At a position passing through the power generating coil 23, the power generating rotor 21, the power generating rotor transmission wheel 62, the minute wheel 55, the center of the rotary weight 25 (the screw for fixing the rotary weight), the second wheel 54, and the hour wheel 56. It is sectional drawing at the time of cutting.

As shown in FIG. 2 and FIG. 4A, of the rotation area of the rotary weight 25, the rotation area of the rotary weight body 251 (thin part) is changed to the rotation area of the rotary weight 252 (thick part). The small generator 20 is configured in such an area. FIG. 4 (A)
As can be seen from the figure, in the small generator 20, the power generation rotor transmission wheel 62 is engaged with the power generation rotor transmission pinion 210, and the power generation rotor transmission wheel 62 of the power generation rotor transmission wheel 62 is engaged.
Is engaged with a rotating wheel 61 that rotates together with the rotating weight 25. Here, let alone the rotating wheel 61,
Since the power generation rotor transmission wheel 62 also has a large height dimension, it is arranged in the rotation area of the oscillating weight 251 (thin portion).

(Structure for Receiving Impact of Rotating Weight) In the rotating weight 25, since the rotating weight body 251 is provided with an impact reducing function, the outer peripheral portion of the rotating weight 25 rotates while moving up and down. In this embodiment, a middle frame 5 (fixed frame) is used as a structure for receiving such a vertical movement. That is, the movement configured on the main plate 2 is housed between the back cover 68 sandwiching the middle frame 5 on the outer peripheral side thereof and the case 78 of the watch case. In this state, the middle frame 5 has reached a position overlapping the outer peripheral portion of the rotary weight 25. In the present embodiment, a dowel 502 protruding toward the oscillating weight 25 is formed on an end face of the portion 501 near the inner periphery of the middle frame 5 that faces the oscillating weight 25. By setting the dowel 502 at a height position closer to the rotary weight 25 in the thickness direction than the components around the dowel, when the rotary weight 25 rotates while moving up and down, the rotary weight 2
5 strikes the dowel 502 of the middle frame 5 first, and its posture is corrected, so that components around the dowel can be prevented from breaking due to contact with the rotary weight 25. Also, dove 5
02 are formed at equal angular intervals, so that the weight 2
When the rotating body 5 rotates while moving up and down, the rotating weight 25 alternately hits some of the dowels 50 of the middle frame 5 and its posture is corrected, so that the entire movement is damaged by the contact of the rotating weight 25. This can be prevented.

(Lubricating Oil Scattering Prevention Structure to Wheel) In this embodiment, the area where the power generation rotor transmission wheel 62 and the power generation rotor 21 are arranged, and the second wheel 5 on which the minute hand 69 is fixed.
4 is arranged as far as possible. For this reason, the power generation rotor transmission wheel 62 and the power generation rotor 21
Even if the lubricating oil scatters when the motor rotates at high speed, the lubricating oil does not reach the center wheel & pinion 54. Moreover, the area where the power generation rotor transmission wheel 62 and the power generation rotor 21 are arranged,
A minute wheel 55 that rotates with a relatively large torque is disposed between the second wheel 54 and the second wheel 54. Therefore, even if the lubricating oil scatters from the power generation rotor transmission wheel 62 and the power generation rotor 21, the lubricating oil is blocked by the minute wheel 55 and does not reach the second wheel 54. Therefore, although the movements are reduced in size, they are close to each other as a whole, but since the respective 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 minute wheel 55, the minute wheel 55 has a high rotational torque, and does not hinder rotation. Therefore, with the aim of more reliably preventing the effects of scattered lubricating oil,
At a position close to the power generation transmission wheel 62, the minute wheel 55
A wheel train with a high rotational torque is arranged as shown in FIG. 2, and a second wheel & pinion 53, a third wheel & pinion 53 and a motor rotor 42 are arranged as the distance from the wheel train increases. It is preferable to arrange a low train wheel.

In the thickness direction, the power generation rotor transmission wheel 62
Is arranged closer to the first train wheel bridge 3 than the gear of the minute wheel & pinion 55, and the minute wheel & pinion 55 and the power generation rotor transmission wheel 62 are partially overlapped in a plane direction, whereby the movement Can be reduced in size. Also, by setting the gears of the power generation rotor transmission wheel 62 and the second wheel train bearing 6 at substantially the same height position in the thickness direction, the lubricating oil scattered from the power generation rotor transmission wheel 62 can be removed from the timepiece wheel train 50. Can be prevented.

(Structure for Preventing Cracks in Slab) Power Generation Rotor 21
As shown in an enlarged view in FIG. 4 (B), a bearing portion for the rotation center shaft 211 of the rotation center shaft 211 of the power generation rotor 21.
The hole stone 214 fitted on the base plate 2 is inserted into the hole 267 of the base plate 2 via the cap 215 and the sleeve 266 (cap).
Is 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 is set.
1 is shifted from the center position C2 in the thickness direction of the pressure contact portion between the cap 215 and the pit stone 214. Further, these center positions C1 and C2 are both shifted from the center position C3 in the thickness direction of the pressure contact portion between the sleeve 266 and the base plate 2. For this reason, when the base plate 2 holds the pit stone 214 via the sleeve 266 and the cap 215, the force applied to the sleeve 266 from the base plate 2 and the force applied to the cap 215 from the sleeve 266 are increased.
Do not concentrate on any part of the sides. Therefore, pit stone 2
14 can be prevented from cracking. Also, sleeve 2
It is preferable that the pressure contact portion between the cap 66 and the cap 215 and the pressure contact portion between the sleeve 266 and the base plate 2 are arranged at positions where they do not overlap in the thickness direction.

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

(Supporting Structure for Power Generation Wheel Train and Rotating Weight) FIG.
FIG. 4 is a cross-sectional view of a portion passing through a coil 41 and a set screw 29 of FIG. FIG. 6 shows a state in which the set screw 18 and the rotary weight 25 in FIG.
3 is a cross-sectional view of a portion passing through the center (rotating weight fixing screw) of FIG. FIG. 7 is a sectional view showing the setting screw 17 and the minute wheel 5 shown in FIG.
It is sectional drawing of the part which passes through 5.

In the prior art, the timepiece train wheel 50 and the power generation wheel train 60 were separately supported by separate wheel train bearings and rotating weight receivers. The first wheel train receiver 3 supporting the motor rotor 42, the third wheel 53 and the minute wheel 55 of the train wheel 50,
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 as shown in FIG.
Only three screws need to be set with the set screws 17, 18, and 26.

These three set screws 17, 18, 26
5, 6 and 7 are shown in FIGS. 5, 6 and 7, and in each case, a metal cylindrical screw seat 170, 180, 260 struck on the base plate 2, and a metal pin It is a screwing structure using set screws 17, 18, and 26.

Therefore, conventionally, in addition to the first train wheel bridge 3, it was necessary to screw and fix the rotary weight bridge.
Although it was necessary to secure a total of six screwing areas, the present embodiment can reduce the number of screwing parts to three, so that the area occupied by the screwing parts can be reduced, and each component can be used. Can be arranged efficiently. Further, in the related art, the rotation weight and the wheel train are taken into consideration in consideration of variations in the thickness direction when the wheel train receiver and the wheel spindle bearing each equipped with the timepiece train wheel 50 and the power generation wheel train 60 are overlapped. There are restrictions such as a need to secure a sufficient gap between the receiver and the like, but there is no such restriction in the present embodiment. Therefore, the pointer-type electronic timepiece 1 can be reduced in thickness.

In FIG. 5, the screwed portion by the set screw 29 fixes the base plate 2, the motor stator 43, the magnetic core 44, the coil lead board 409, the circuit board 31, and the circuit holding 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 the ball bearing 90. The ball bearing 90 is
Inner member 9 supporting bearing ball 91 on the inner peripheral side
2, and an outer ring 93 (outer member) for holding a plurality of bearing balls 91 between the inner member 92 and the inner member 92. The inner member 92 includes an inner ring 94 having an L-shaped cross section in which a flange portion projects outward from a cylindrical portion, a ball pressing ring 95 which is press-fitted into the inner ring 94 and forms a ball raceway surface together with the inner ring 94, and a bearing ball. And a retainer 96 for defining the position of 91.

As described below, the inner race 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 a stepped receiving hole 3
01 is formed therein, and the bearing shaft 97 is mounted so that the tip end protrudes. A flange 971 larger than the receiving hole 301 is formed at the base of the bearing shaft 97, and the flange 971 is hooked on a 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 distal end surface of the bearing shaft 97. In this state, the rotating weight fixing screw 250 moves the head to the inner ring 94 and the ball holding ring 95 while pulling up the bearing shaft 97.
Is pressed toward the first train wheel bridge 3, so that the inner ring 94 and the ball holding ring 95 are tightened and fixed to the first train wheel bridge 3 by the rotating 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 by press-fitting, the lubricating oil applied to the ball bearing and the wheel train flows into the press-fit portion of the ball bearing and the plate. Thus, the problem that the ball bearing comes off does not occur. Further, according to the configuration in which the ball bearing 90 is fastened and fixed to the first train wheel bridge 3 by the rotary weight fixing screw 250 as in this embodiment, for example, the bearing shaft 97 is pushed down when the screw is tightened and the bearing shaft 97 is pushed down. However, 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. Of the rotating weight 25, the frictional force between the head of the rotating weight fixing screw 250 and the rotating weight 25 in contact with the head causes the rotating weight 25 to be screwed. Although the fixing screw 250 is prevented from being loosened, there is a possibility that the rotary screw fixing screw 250 may gradually loosen due to repeated impacts even with strong or light shocks during long-term use. . Such loosening of the screw causes a gap between the ball presser wheel 95 and the rotating wheel 61 or between the rotating weight 25 and the head of the rotating weight fixing screw 250, causing a strong impact on the rotating weight 25. When added, the ball bearing 90 may be damaged.

However, in this embodiment, the ball bearing 9
0, the inner member 92 to which the rotary weight fixing screw 250 is fixed is the first wheel train bearing 3 which is a fixed side 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 last, and does not rotate, so that
The rotating weight fixing screw 250 is not loosened even if it is subjected to long-term carrying, strong impact, or repeated repeated light impacts. Therefore, problems such as breakage of the ball bearing 90 due to loosening of the rotary weight fixing screw 250 do not occur.

Further, if the screw 250 for fixing the oscillating weight does not rotate, the screw 250 for fixing the oscillating weight is
4A does not affect the rotational movement of the rotary weight 25.
8 can be arranged close to each other, so that the hand-held electronic timepiece 1 can be thinned accordingly.

Further, as in the prior art, the rotatable inner ring 94 is formed.
In a structure in which the rotary weight 25 is screwed and fixed to, for example,
When the screw is tightened, the inner ring 94 rotates idly and screw tightening is not easy, and if the rotating weight 25 rotates while being tilted during screw tightening, scratches and shavings are attached to the periphery. However, in this embodiment, since the structure is screwed to the bearing shaft 97, the screw tightening operation of the rotary weight fixing screw 250 can be easily performed. Further, according to the present embodiment, the rotating weight 25 does not rotate while being tilted during the screwing operation, so that there is no abrasion or shavings around.

(Structure for Preventing Tilt of Ball Bearing) As described above, the ball bearing 9 is
When attaching 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 rod material is formed in this hole. The bearing shaft 97 machined from the above must be fixed. However, the bearing shaft 97 is always inclined by simple press-fitting. When the ball bearing 90 is incorporated into the bearing shaft 97 having such a tilt, the rotating weight 2 is determined by the lever ratio between the outer diameter of the rotating weight 25 and the outer diameter of the bearing shaft 97.
5 has a very large inclination. In order to allow such a tilt, it is necessary to secure a sufficient gap above and below the rotary weight 25, which hinders a reduction in thickness and size. Further, in order to increase the outer diameter of the flange 971 of the bearing shaft 97 to prevent the inclination thereof, it is impossible to increase the outer diameter of the flange 971 any more with a small movement. Furthermore, if the outer circumference of the oscillating weight 25 is increased in order to secure the unbalance amount of the oscillating weight 25 in a limited space, the lever ratio between the outer diameter of the oscillating weight 25 and the outer diameter of the bearing shaft is increased. It becomes large, and the rotary weight 25 is easily inclined.

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 center hole (through hole). . The fitting portion 941 is a small-diameter portion approximating the outer diameter of the bearing shaft 97, and the relief portion 942 is slightly larger than the inner diameter of the fitting portion 941 (the outer diameter of the bearing shaft 97). Also has an inner diameter that does not interfere with the bearing shaft 97. Therefore, the allowance for engagement between the inner ring 94 and the bearing shaft 97 is defined by the length A of the fitting portion 941, and the length A is shortened to a necessary minimum in this embodiment. As described above, if the engagement allowance between the inner ring 94 and the bearing shaft 97 is set short, even if the bearing shaft 97 is slightly tilted, the ball bearing 90
Can be mounted in the correct position,
5 can be prevented from tilting. In this embodiment, the length dimension A
Is set in a range from about 0.05 mm to about 0.5 mm. If the length is shorter than this range, the incorporation and removability of the ball bearing 90 are improved, while the inner ring 94 bites into the bearing shaft 97 when a strong impact is applied, and the plane position shifts, or the bearing shaft 97 is displaced. When the inner ring 94 bites into the shaft, stress concentration increases, and problems such as breakage of the ball bearing shaft 97 occur. When the length A is longer than 0.5 mm,
The inclination of the oscillating weight 25 is determined to be a large value by the inclination of the bearing shaft 97. Further, if the length A is too long, the parts may bite each other when the ball bearing 90 is assembled or removed, and the parts may not move. Therefore, it can be said that it is more preferable to set the length dimension A in a range from 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.
When the ball holding ring 95 is formed into the cylindrical portion of the inner ring 94, even if the inner diameter of the inner ring 94 tends to be reduced when the ball presser ring 95 is pressed into the cylindrical portion of the inner ring 94, this portion is originally a relief portion 942. As a result, the engagement of the bearing shaft 97 can be regulated to a predetermined size by the fitting portion 941.

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

In this embodiment, the ball presser wheel 95 of the ball bearing 90 overlaps the first wheel train wheel 3 on the side opposite to the side on which the timepiece wheel train 50 is formed. In the present embodiment, in order to minimize the inclination of the rotary weight 25,
The outer diameter B of the surface where the ball holding wheel 95 contacts the first train wheel bridge 3 is made as large as possible. However, since various components are arranged in the first train wheel bridge 3, there is also a limitation in expanding the outer diameter of the ball holding wheel 95. Therefore, in this embodiment,
The outer diameter of the ball holding wheel 95 is examined from the viewpoint of the lever ratio to the outer diameter of the rotating weight 25, and the ball holding wheel 9 is examined.
5 is the outer diameter dimension B of the surface in contact with the first train wheel bridge 3
5 is set in a range from about 1/10 to about 1/3 times the outer diameter dimension. When the ratio of the outer diameters is set to be larger than 1/3, the outer diameter of the ball bearing 90 becomes too large, and the unbalance amount of the rotary weight 25 becomes very 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 outer diameter dimension is set to 1/1.
If it is set to be smaller than 0, the inclination of the rotary weight 25 cannot be effectively suppressed. Therefore, the outer diameter B of the surface where the ball presser wheel 95 is in contact with the first train wheel bridge 3 can be set in a range from 1/6 to 1/3 of the outer diameter of the rotary weight 25. preferable. With this setting, the inclination of the oscillating weight 25 can be reduced, which is more advantageous for making the movement thinner.

(Integrated Structure of Rotating Weight) In this embodiment, the rotating weight 25 that rotates by the movement of the arm, the ball bearing 90 for efficiently taking this movement into the generator, and the rotating weight 2
Rotating wheel 6 that speeds up rotation of 5 and transmits it to small generator 20
1 is all united. That is, the power train 6
Of the wheels 0, the rotating wheel 61 to which the rotation of the rotating weight 25 is transmitted first is also fixed to the outer ring 93 of the ball bearing 90. Here, the outer ring 93 of the ball bearing 90 has a small-diameter portion 931 on which the rotating wheel 61 is mounted, from the end surface on the side of the main plate 2 toward the opposite end surface.
A large-diameter portion 932 having an outer diameter considerably larger than that of the small-diameter portion 931 at a position connected to the large-diameter portion 931;
A middle diameter portion 933 having an outer diameter smaller than the large diameter portion 932 and larger than the small diameter portion 931 is formed in this order at a position where the rotary weight 25 is attached to the middle diameter portion 933. In the middle diameter portion 933, the rotating weight 25
Are caulked portions 93 formed on the edge side of the middle diameter portion 933.
4 and the large-diameter portion 932 and are fixed there.

If only the press-fitting of the rotary weight 25 to the outer ring 93 without crimping and fixing the rotary weight 25 to the outer ring 93, the rotary weight 25 may come off when a strong or light impact is repeatedly applied. Or, there is a risk of idling due to insufficient fixing torque. However, in the caulking fixed structure as in the present embodiment, such falling off of the rotating weight 25 and idling do not occur.

Further, as in this 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 rotating weight 25 is fixed to the middle diameter portion 933 by caulking. In such a structure, when the intermediate diameter portion 933 is crimped, the portion just below the middle diameter portion 933, that is, the back side of the large diameter portion 932 can be backed up, so that the deformation of the outer ring 93 can be suppressed.

Further, when the rotary weight 25 and the rotary weight wheel 61 are integrally formed on the ball bearing 90, there are the following advantages in the production process of the movement. First, in the part manufacturing stage, the ball bearing 90,
Since the oscillating weight 25 and the oscillating weight wheel 61 are once assembled as a oscillating weight assembly in a form very close to use as a timepiece, the quality of the oscillating weight finally mounted on the timepiece can be controlled. In addition, since the ball bearing 90, the oscillating weight 25, and the oscillating weight wheel 61 can be assembled as an oscillating weight assembly, the number of parts handled in the assembly stage of the movement can be reduced. Therefore, it is possible to reduce the number of work steps and the number of defective products.

(Structure of Rotating Wheel) FIG. 8 is a plan view of a rotating wheel 61 used in the pointer-type electronic timepiece according to the present embodiment.

In FIG. 8, the pointer type electronic timepiece 1 of the present embodiment is shown.
The rotating wheel 61 used in the first embodiment has two edges 611 that hit the outer peripheral surface of the outer ring 93 in a 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 are formed, and an opening 613 extending in a groove shape from the hole 610 and forming an arc therearound is formed. Therefore, the hole 61
Since the portion 614 remaining between the zero and the opening 613 exhibits resiliency, the edge 611 comes into elastic contact with the outer peripheral surface of the outer ring 93 of the ball belling 90. For this reason, since the rotating wheel 61 slips when an overload is applied, the rotating wheel 61 itself and the other power generation wheel train 60 can be protected from damage due to the overload.

(Magnet fixing structure of power generation rotor) FIG. 4
In (A), the power generation rotor 21 has a kana portion 210.
, A sintered magnet 218 is attached via a magnet guide seat 217. Conventionally, an adhesive is often used as a method of fixing a sintered magnet to a magnet guide seat having a structure covering two surfaces of the sintered magnet. However, the fixing with an adhesive is very difficult, especially in the case of precision parts such as a timepiece, because the amount of the adhesive is very small, and the operation requires skill. Further, as another fixing method, there is a method of driving the sintered magnet into the magnet guide seat with a margin between the magnet guide seat and the sintered magnet. Cracks tended to occur in the sintered magnet due to the impact striking the seat. However, in this embodiment,
As shown in FIG. 4 (A), when the sintered magnet 218 is driven into the magnet guide seat 217 with a margin between the magnet guide seat 217 and the sintered magnet 218, the magnet guide seat 217 and the sintered magnet 217 are sintered in the thickness direction. Since the structure for securing a gap between the magnet 218 and the connecting magnet 218 is employed, the sintered magnet 218 can be prevented from cracking. In addition, unlike fixing with an adhesive, since there is no intervening fluid, it is possible to suppress a variation in the position of the sintered magnet 218 in the thickness direction.

Further, in the method of driving with the interference, there is a possibility that the sintered magnet 218 may be displaced or come off due to impact. However, 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 occurrence of the above-described displacement and detachment 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 reduced 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 tapered shape having a larger diameter as the distance from the center increases. 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. Also, by providing a projection that protrudes in the inner diameter direction on the magnet driving side of the magnet guide seat 217, a structure that prevents the sintered magnet 218 from coming off can be provided.

(Supporting structure for second wheel & pinion) In FIG. 3, the rotating weight 25 also employs a configuration supported by the first wheel train bearing 3, and the second wheel & pinion 54 is also temporarily provided with the first wheel train receiving member. With the configuration supported by the third wheel 3, it becomes difficult to lubricate the tenon portion above the center wheel & pinion 54 and manage the degree of lubrication. The parts that require lubrication are usually visible from the outside when the movement is assembled.
Employs a configuration supported by the first train wheel bridge 3, the mortise above the center wheel & pinion 54 is hidden by the rotary weight 25. On the other hand, when a female screw portion for fixing the rotary weight fixing screw 250 to the bearing shaft 97 is formed as a through hole so that the portion requiring lubrication can be seen, cutting chips and wear from this portion toward the center wheel & pinion 54 are formed. There is a possibility that the load of the watch train wheel 50 may increase due to flying powder.

Therefore, in this embodiment, the center wheel & pinion 54 is stacked and fixed on the side of the main plate 2 (the side opposite to the side where 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 employed. With this configuration, the timepiece wheel train 50 and the power generation wheel train 60 are provided on the main plate 2.
, The second train wheel bridge 6 can be assembled, and then the tenon portion 541 on the upper side of the center wheel & pinion 54 can be lubricated. Therefore, since the female screw portion of the bearing shaft 97 does not need to be a through hole, there is no influence of cutting powder or the like on the timepiece wheel train 50 such as the center wheel & pinion 54. Further, in the present embodiment, the height of the center wheel & pinion 54 is shortened by a dimension corresponding to the thickness of the second train wheel bridge 6, and the overall thickness of the movement is obtained even when the second wheel train bridge 6 is added. Does not increase.

As the train wheel bridge, a first train wheel bridge 3 and
The first train wheel bridge 3 and the second train wheel bridge 6 laminated and fixed to the first train wheel bridge 3 are used, and the second train wheel bridge 6 is fixed to the first train wheel bridge 3.
The first wheel train bridge 3 can be effectively reinforced by the second wheel train bridge 6 because the rotary weight 25 is supported on the opposite side to the above. Therefore, the oscillating weight receiver conventionally used is omitted, and the oscillating weight 25
Is supported by the first train wheel bridge 3, there is no problem in the strength of the train wheel bridge. Therefore, the area occupied by the screwed portions can be reduced by omitting the rotary weight receiver and reducing the screwed portions. Therefore, in the present embodiment, each part can be efficiently arranged by the reduced area occupied by the screwed portion, so that the hand-held electronic timepiece 1 can be reduced in size and thickness.

In this embodiment, a gap 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 squeak due to component variations. 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. 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 not displaced from being displaced from the second train wheel bridge 6.

(Details of the second train wheel bridge 6) The second wheel train bridge 6 is laminated over the first wheel train bridge 3 over a wide area. A hole 601 and a notch 604 that can support the third wheel 53 and the motor rotor 42 that are likely to fall down when assembling the movement are secured in a portion corresponding to the support position of the reverse wheel 55. Also, in the hole 601 and the notch 604, the opening rim of the second wheel train bridge 6 is obliquely cut at the portion of the hole 601 where the distance from the gear is small. At the time of assembling, even if the motor rotor 42 is inclined, the motor rotor 42 is incorporated while the inclination of the motor rotor 42 is corrected by the slope, so that the assembling property is good.

The notch 603 formed at the position corresponding to the position where the minute wheel 55 is supported protrudes so as to approach the shaft of the minute wheel 55. As a result,
An extremely narrow gap is formed between the hole stone 555 fitted to the shaft end, and lubricating oil is sucked into the gap. Therefore, in the present embodiment, the step 60 is formed at the notch 604.
By forming 3, the space between the stone and the pit stone 555 is sufficiently widened to prevent the lubricating oil from being sucked therein.

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

(Arrangement Structure of Switching Member for Time Adjustment) FIG. 10 is an explanatory diagram showing a planar arrangement relationship of mechanical parts for time adjustment in the hand-held electronic timepiece according to the present embodiment. The matching mechanical parts are indicated by thick lines, and the other parts are indicated by thin lines. FIG. 11 is a cross-sectional view illustrating the configuration of the tip of the train wheel setting lever. FIG.
FIG. 5 is a cross-sectional view illustrating a configuration of a tip portion of a reset lever. FIGS. 13A and 13B are cross-sectional views of a winding stem and a small iron seat supporting the winding stem.

In FIG. 10, 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 structure of this mechanism is
Since the mechanism is the same as a conventional mechanism, a detailed description thereof is omitted, but a winding stem 70 connected to the crown 7 is engaged with a shim 71. The bolt 72 is the makishin 70
Is engaged with the groove of the pinwheel 73 connected to Therefore, when the crown 7 is pulled out one stage, the ball 71
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 in the setting lever 71, when the crown 7 is pulled out, the train wheel setting lever 74 is pulled out.
Is rotated in the direction of arrow T, and as shown in FIG.
Engage with the third wheel 53 and stop the movement of the hands. In this state, when the crown 7 is turned, the minute wheel 55 and the like can be rotated via the small iron wheel 79 (see FIG. 10).

Further, a reset lever 75 shown in FIG. 12 is mechanically connected to the posterior 71. When the crown 7 is pulled out one step, the reset lever 75 rotates along the main plate 2. A contact portion 315 projecting obliquely downward from the circuit board 31 is located on the side in the rotation direction.
The contact portion 75 bent in a Z-shape at the tip of the reset lever 75 in conjunction with the operation of pulling out the crown 7 one step.
5 comes into contact with the contact portion 315 to activate the switch. 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 also stops. 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 projection 312 of the small iron seat 311 fitted in the hole 310 formed therein, and is pressed and fixed by the circuit pressing plate 316. Therefore, when the crown 7 is pushed in from the state where the crown 7 is pulled out, the contact 315 and the contact portion 755 are separated from each other, so that the drive signal is output from the stepping motor 40 again from the drive circuit. Therefore, the motor rotor 42 starts to rotate again. In addition, crown 7
Is pressed, the setting lever 74 is separated from the third wheel & pinion 53, and the hands resume rotation.

Since the reset lever 75 is formed of a thin plate, the reset lever 75 is located within the rotation area of the rotary weight 252 of the rotary weight 25 (the rotation area of the thick portion of the rotary weight 25 and the ground plate 2). And between). Further, a switching member such as a latch 72 is also arranged in the rotation area of the rotary weight 252 of the rotary weight 25.

In this embodiment, as shown in FIGS. 13A and 13B, the winding stem 70 is made of a small iron wheel seat 311 made of synthetic resin.
It is arranged and supported so as to pass through the inside. As shown in FIG. 13 (A), the small iron wheel seat 311 is provided with a projecting portion 319 that protrudes under the power generating stator 22 and the magnetic core 221 thereof. For this reason, when the power generation stator 22 and its magnetic core 221 are screwed, the small iron wheel seat 311 is also connected to the power generation stator 2.
2 and the magnetic core 221. Therefore, the assemblability is good and the small iron seat 31
There is no lift of 1.

[0092]

As described above, in the pointer-type electronic timepiece according to the present invention, the rotating weight is also supported by the train wheel bridge, which is a fixed member, similarly to the timepiece train wheel. What is necessary is just to screw and fix a row support to a main plate. Therefore, the number of screwed portions can be reduced, and the area occupied by the screwed portions can be reduced. Therefore, since each component can be efficiently arranged, the size and thickness of the pointer-type electronic timepiece can be reduced.

In the present invention, when the train wheel bridge is composed of the first train wheel bridge and the second train wheel bridge laminated and fixed to the first train wheel bridge, the first train wheel bridge is formed. Can be effectively reinforced by the second train wheel bridge. Therefore, even if the conventional rotary weight bridge is omitted and the rotating weight is supported by the wheel train bridge, there is no problem in the strength of the wheel train bridge. Absent. Therefore, as described above, by reducing the number of screwed portions, each part can be efficiently arranged, and the size and thickness of the pointer-type electronic timepiece can be reduced.

In the present invention, when the inner member of the ball bearing is fixed to the fixed side member and the rotating weight is fixed to the outer member side, even if the rotating weight is screwed to the inner ring, this screw can be used. The stop does not rotate. Therefore,
The screw does not become loose at this screwed portion. Further, since the screwed portion does not rotate, the back cover can be arranged close to the screw, so that the thickness of the pointer-type electronic timepiece can be reduced.

[Brief description of the drawings]

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

FIG. 2 is a plan view showing a layout of a main plate, a first train wheel bridge, and a second train wheel bridge supporting respective components in the pointer-type electronic timepiece to which the embodiment is applied.

FIG. 3 shows a pointer type electronic timepiece to which the present embodiment is applied, a minute wheel, a center of a rotating weight (a screw for fixing a rotating weight), a second wheel,
It is sectional drawing when it cut | disconnects in the position which passes through an hour wheel, a 3rd wheel, a motor rotor, and a set screw.

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

FIG. 5 is a cross-sectional view of a portion passing through a set screw, a step motor coil, and another set screw 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 and a center of a rotary weight (a rotary weight fixing screw) in the pointer-type electronic timepiece to which the present invention is applied.

FIG. 7 is a cross-sectional view of a portion passing through a set screw and a minute wheel in the pointer-type electronic timepiece to which the present invention is applied.

FIG. 8 is a plan view of a rotary wheel used in a pointer-type electronic timepiece to which the present invention is applied.

FIG. 9 is a cross-sectional view showing a configuration example in a case where a pointer-type electronic timepiece to which the present invention is applied has a fourth wheel to which a second hand is attached.

FIG. 10 is an explanatory view showing a planar arrangement relationship of a time adjusting mechanism part in a pointer-type electronic timepiece to which the present invention is applied.

FIG. 11 is a cross-sectional view showing a configuration of a distal end portion of a setting lever in a pointer-type electronic timepiece to which the present invention is applied.

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

13 (A) and 13 (B) are cross-sectional views of a winding stem and a small iron seat supporting the winding stem in the pointer type electronic timepiece to which the present invention is applied.

FIG. 14 is a schematic configuration diagram showing the entire configuration of a conventional pointer-type electronic timepiece.

FIG. 15 is a cross-sectional view showing a support structure of a rotating weight in a conventional pointer-type electronic timepiece.

[Explanation of symbols]

REFERENCE SIGNS LIST 1 pointer-type electronic timepiece 2 main plate 3 first train wheel receiver 5 middle frame 6 second wheel train receiver 7 crown 10 power supply unit 17, 18, 26 set screw 20 small generator 21 generator rotor 22 generator stator 23 generator Coil 25 Rotating weight 30 Secondary power supply (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 Third wheel 54 Second wheel 55 Back of day Car 56 hour wheel 50 clock train wheel 60 power train wheel 61 oscillating wheel 62 power generation rotor transmission wheel 63 hour hand 64 second hand 68 back cover 69 minute hand 70 winding stem 71 shirring 72 boring 73 sliding wheel 74 setting lever 75 reset lever 78 Watch 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 holding ring 96 Retainer 97 Bearing shaft (Guide shaft) 170, 180, 260 Metal cylindrical screw seat 211 Rotation center shaft of power generation rotor 212, 214, 555, S Hole 213, 215 Cap 217 Magnet guide seat 218 Sintered magnet 267 Sleeve 250 Rotating weight fixing screw 251 Rotating weight body (thin portion) made of thin plate 252 Rotating weight (thick portion) 253 Welding recess 311 Small iron wheel seat 315 Contact point of circuit board 502 Dowel 601 in the middle frame 601 Hole for preventing fall 603 Step of notch 604 Notch for preventing fall 611, 612 Edge of rotating wheel 613 Opening of rotating wheel 614 Portion showing springiness of rotating wheel 755 Reset lever 931 Small diameter part of outer ring 932 Large diameter part of outer ring 933 Middle diameter part of outer ring 934 Portion 941 Fitting portion of inner ring 942 Escape portion of inner ring G Gap for holding lubricating oil C1 Center position in thickness direction of pressure contact portion between sleeve and cap C2 Center position in thickness direction of pressure contact portion between cap and hole stone C3 Center position in the thickness direction of the pressure contact part between the sleeve and the base plate

Claims (18)

[Claims] 1. A small-sized generator having a rotating weight which rotates by the movement of a user of a timepiece, a power train for transmitting the rotating motion of the rotating weight, and driven by electric energy generated by the small-sized generator A stepper motor, a timepiece wheel train transmitting rotational driving force from the step motor to the hands, and a wheel train receiver supporting the timepiece wheel train between a main plate and a main plate. A pointer-type electronic timepiece, wherein a weight is supported by the train wheel bridge at a rotation center thereof. 2. The ball according to claim 1, wherein the oscillating weight includes a bearing ball, an inner member that supports the bearing ball on an inner peripheral side, and an outer member that sandwiches the bearing ball with the inner member. A pointer-type electronic timepiece, which is supported by the train wheel bridge via a bearing. 3. The train wheel bridge according to claim 2, wherein the train wheel bridge includes a first train wheel bridge supporting the rotary weight, and the first train wheel bridge between the first train wheel bridge and the main plate. And a second train wheel bridge laminated on the first train train bridge so as to substantially overlap a mounting portion of the ball bearing among the bearings. 4. The ball bearing according to claim 2, wherein, of the inner member and the outer member of the ball bearing, the inner member is fixed to the train wheel bridge, and the rotary weight is fixed to the outer member. Pointer-type electronic clock characterized by the following. 5. The pointer-type electronic device according to claim 4, wherein a rotating wheel of the power generating wheel train that rotates integrally with the rotating weight is fixed to an outer member of the ball bearing. clock. 6. The small-diameter portion on which the rotating weight wheel is mounted and connected to the small-diameter portion from the end face on the main plate side to the end face on the opposite side from the outer surface of the ball bearing. A large-diameter portion having an outer diameter dimension larger than the small-diameter portion at the position, and a middle-diameter portion having an outer diameter dimension smaller than the large-diameter portion and larger than the small-diameter portion at a position connected to the large-diameter portion. The rotary weight is formed in this order, and the rotary weight is sandwiched and fixed between the caulked portion and the large-diameter portion formed on the edge side from the middle-diameter portion in a state mounted on the middle-diameter portion. Pointer-type electronic timepiece characterized by the above-mentioned. 7. The method according to claim 4, wherein
The pointer-type electronic timepiece, wherein the inner member is pressed and fixed to the train wheel bridge by a rotary weight fixing screw screwed toward the main plate. 8. The hand-held electronic timepiece according to claim 7, wherein an end face on the main plate side of both end faces of the inner member is in contact with the train wheel bridge. 9. An outer diameter of a contact area between the inner member and the train wheel bridge in a range of 1/3 to 1/10 of an outer diameter of the rotary weight. A pointer-type electronic timepiece characterized by the following. 10. The inner member according to claim 7, wherein the inner member has a through hole formed in a rotation center portion of the ball bearing, and a guide shaft fixed to the train wheel bridge is formed in the through hole. And the screw for fixing the rotary weight is screwed into the shaft end face of the guide shaft so as to fasten and fix the inner member of the ball bearing toward the train wheel bridge. Pointer-type electronic watch. 11. The pointer-type electronic timepiece according to claim 10, wherein the inner member includes a fitting portion having a small inner diameter and a relief portion having a large inner diameter on the inner peripheral side of the through hole. . 12. The inner ring having an L-shaped cross section according to claim 10, wherein the inner member includes a tubular portion to which the guide shaft is fitted and fixed, and a flange portion extending outward from the tubular portion. And a ball press ring that is press-fitted into the inner ring and forms a ball raceway surface together with the inner ring. A portion of the inner peripheral surface of the cylindrical portion on which the ball press ring is disposed is the guide shaft. A guide-type electronic timepiece having an inner diameter larger than an outer diameter of the guide shaft, wherein the guide shaft is fitted and fixed by an inner peripheral portion corresponding to the flange portion. 13. A small-sized generator having a rotating weight rotated by a movement of a user of a timepiece, a power train for transmitting the rotating motion of the rotating weight, and driven by electric energy generated by the small-sized generator. A stepper motor, a wheel train for transmitting a rotational driving force from the step motor to the hands, and a wheel train receiver supporting the wheel train between the main plate, The train wheel bearing includes a first train train bridge and a second train train bridge laminated on the first train train bridge, and the second train train bridge is provided with respect to the first train train bridge. A pointer-type electronic timepiece characterized in that the rotating weight is supported on the opposite side of the hand. 14. The first train wheel bridge, the second train wheel bridge, and the main plate are fixed at a plurality of positions so as to surround a mounting portion of the ball bearing in a plane, according to claim 3 or 13. A pointer-type electronic timepiece characterized by the following. 15. The fixing device according to claim 14, wherein the first wheel train receiver, the second wheel train receiver, and the fixing portion of the base plate are arranged in a region corresponding to an inner side of a thick portion of the rotating weight. Pointer-type electronic watch characterized by the following. 16. The hand-held electronic timepiece according to claim 15, wherein the first train wheel bridge, the second train wheel bridge, and the base plate are fixed by screws. 17. The screw according to claim 15, wherein a plurality of screws for fixing the first train wheel bridge to the main plate are arranged so as to surround a rotary weight fixing screw for attaching the rotating weight to the train wheel bridge. At least two of the screws for fixing the first train wheel bridge to the main plate are arranged within a radial distance corresponding to の of the outer diameter of the oscillating weight from the oscillating weight fixing screw. Pointer-type electronic clock characterized by the following. 18. The timepiece train wheel according to claim 16, wherein the first train wheel bridge, the second wheel train bridge, and the timepiece wheel train are disposed in a plane surrounded by screwing portions of the main plate. The electronic timepiece of the present invention is characterized in that at least half of the respective gears constituting the electronic timepiece are arranged.