TIMEPIECE |
|||||||
申请号 | EP99973134.2 | 申请日 | 1999-11-29 | 公开(公告)号 | EP1052557A1 | 公开(公告)日 | 2000-11-15 |
申请人 | SEIKO EPSON CORPORATION; | 发明人 | HARA, Tatsuo, Seiko Epson Corporation; | ||||
摘要 | A fourth wheel 8 disposed in a torque transmission path and to which a second hand is mounted includes a pinion 8a and a gear 8b. Therefore, when the gear 8b engages a fifth-wheel first intermediate wheel 9, the diametrical dimension from a center of rotation of the fourth wheel 8 to a portion where it engages the fifth-wheel first intermediate wheel 9 can be made large, so that, even when the fourth wheel 8 is decentered, the amount by which the second hand gets shifted can be made small by making the effects of the decentering at the center-of-rotation side small. In addition, since the fourth wheel 8 is disposed so as not to overlap a mainspring 1a, the width of the mainspring 1a can be made correspondingly small. Thus, the length of time a timepiece continues operating can be increased by increasing the torque of the mainspring 1a without increasing the thickness of the entire timepiece. | ||||||
权利要求 | |||||||
说明书全文 | The present invention relates to a mechanical timepiece which operates by using as a driving source mechanical energy generated when a mainspring is released. In addition, the present invention relates to an electronic controlling type mechanical timepiece in which a portion of the mechanical energy of the mainspring is converted into electrical energy, and a rotation controlling means is operated by the electrical energy in order to control a period of rotation. An electronic controlling type mechanical timepiece shown in Fig. 16 is known, in which a mainspring used as an energy source drives a wheel train, and electrical power is generated by a generator rotated as a result of receiving the rotational motion from the wheel train in order to drive an electronic circuit which controls the period of rotation of the generator, whereby the wheel train is braked to regulate the speed. In the electronic controlling type mechanical timepiece, rotation of a movement barrel 1 in which a mainspring 1a is accommodated is transmitted to a second wheel 6 to which a minute hand (not shown) is mounted, after which the rotation is transmitted successively to a third wheel 7, a fourth wheel 8, a fifth wheel 11, a sixth wheel 12, and ultimately to a rotor 13 of the generator. A second pinion wheel 90 to which a second hand (not shown) is attached meshes only with the third wheel 7, so that it is situated outside a torque transmission path extending from the movement barrel 1 to the rotor 13. In order to reduce unsteady movement of the second hand caused by backlash between the third wheel 7 and the second pinion wheel 90, a second regulating spring with a suitable structure is sometimes provided. In such an electronic controlling type mechanical timepiece, the speed of the rotor 13 is stably regulated, and, when the wheels 6, 7, 8, 11, and 12, and the second pinion wheel 90 are formed with ideal shapes, the second pinion wheel 90, that is, the second hand moves exactly at a constant speed of 1 rpm. However, there are variations in the shapes of the wheels 6, 7, 8, 11, and 12 and the second pinion wheel 90, so that, when, in particular, the second pinion wheel 90 with a small pitch circle is decentered from its axis of rotation, the rotational speed of the second pinion wheel 90 will not be 1 rpm, causing the second hand to shift. To overcome this problem, the pitch circle size of the second pinion wheel 90 may be made larger. However, in such a case, since the speed-increase ratio (which is, in general, 60) from the second wheel 6 to the fourth wheel 8 needs to be maintained, a teeth-shaped module of the second pinion wheel 90 is made large, making it necessary to either make the third wheel 7 larger or increase the speed-increase ratio between the second wheel 6 and the third wheel pinion. This reduces the meshing efficiency. Fig. 15 illustrates a graph showing the measured shift angles of the hand of the conventional electronic controlling type mechanical timepiece. In the timepiece, since a large speed-increase ratio in which the second pinion wheel 90 rotates nine times during the time the third wheel 7 rotates once is set, the pitch circle of the second pinion wheel 90 becomes small, so that the decentering of the second pinion wheel 90 greatly affects the shift angle of the hand. It has been confirmed that, during the time the second pinion wheel 90 rotates nine times, the second hand is greatly shifted by an angle in the range of from -1.2° to +4° from its normal position in a circumferential direction thereof. The electronic controlling type timepiece uses the mechanical energy of the mainspring as a driving source, so that the larger the width of the mainspring (that is, the width of the timepiece in the thickness direction thereof), the longer the timepiece will continue operating. However, forming the mainspring with a large thickness increases the thickness of the timepiece, thereby preventing the formation of a thin timepiece. This problem not only exists in electronic controlling type mechanical timepieces, but also in conventional mechanical timepieces in which a wheel train is driven by a mainspring. Accordingly, it is an object of the present invention to provide a timepiece which either makes it possible to reduce the amount by which a second hand is shifted, and/or which can continue operating for a longer time without increasing the thickness of the entire timepiece. A timepiece recited in Claim 1 of the present invention including a speed-regulating device for regulating a speed of rotation of a wheel train, in which a mainspring serving as an energy source drives the wheel train, wherein, of wheels of the wheel train, a wheel to which a second hand is mounted is disposed so that torque of the mainspring is transmitted to the speed-regulating device, the wheel to which the second hand is mounted including a pinion and a gear provided on a same axis of rotation, and being disposed so as not to overlap the mainspring when viewed in a plane. In this invention, the wheel to which the second hand is attached includes a pinion and a gear, so that, by engaging a wheel disposed towards the mainspring and the pinion, and engaging this gear with a next gear (disposed towards the speed-regulating device), the diametrical dimension from the center of rotation of the wheel to which the second hand is attached to a portion where it engages the next gear can be made large without changing the speed-increase ratio from the mainspring side. Therefore, even if the wheel to which the second hand is attached gets decentered, the effects of the decentering at the center-of-rotation side becomes small, so that the amount by which the second hand gets shifted is reduced. In addition, since the wheel to which the second hand is attached is disposed so as not to overlap the mainspring, the width of the mainspring can be correspondingly increased, so that the torque of the mainspring becomes large even if the thickness of the entire timepiece is not increased, thereby increasing the length of time the timepiece continues operating. Due to the above, the above-described objects are achieved. The speed-regulating device may be constructed so as to regulate the speed of rotation of the wheel train by controlling a period of rotation of the generator by an electronic circuit driven by electrical power generated by the generator to which a rotational force from the wheel train has been applied. Although, as in a mechanical timepiece, the speed-regulating device may comprise an escapement, the speed of the wheel train can be more precisely regulated when the electronic controlling type structure of the present invention is used. It is desirable that the wheel to which the second hand is mounted and a gear of a barrel drum which accommodates the mainspring overlap each other when viewed in a plane. In this structure, since the outside diameter of the gear of the barrel drum can be made large, the speed-increase ratio between it and a wheel at the wheel train side which engages the gear becomes large. Thus, the winding down of the mainspring when the train wheel is rotating at a constant speed can be slowed down, thereby increasing the length of time the timepiece continues operating. A timepiece recited in Claim 4 of the present invention in which a mainspring serving as an energy source drives a wheel train, and in which a speed of rotation of the wheel train is regulated by controlling a period of rotation of a generator by an electronic circuit driven by electrical power generated by the generator which has received a rotational force from the wheel train, wherein, of wheels of the wheel train, a wheel to which a second hand is mounted is disposed so that torque of the mainspring is transmitted to the generator, the wheel to which the second hand is mounted including a pinion and a gear provided on a same axis of rotation; and wherein the wheel train is disposed so as not to overlap a coil of the generator when viewed in a plane. In the present invention, since the wheel to which the second hand is attached includes a pinion and a gear, the amount by which the second hand shifts can similarly be reduced. In addition, since the wheel train is disposed so as not to overlap the coil, the number of windings can be increased based on a corresponding increase in the diametrical dimension of the coil, so that the axial length of the coil, and, hence, the magnetic path length becomes shorter. Consequently, iron loss such as hysteresis loss or eddy current loss occurring when a magnetic field is generated in the coil is reduced, making it possible to operate the timepiece with a smaller amount of mainspring energy, so that the timepiece can continue operating for a longer period of time. Due to the above, the above-described objects are achieved. It is preferable that a pitch circle diameter of the gear of the wheel to which the second hand is mounted be at least 1.5 mm. This is because, when the pitch circle diameter of the gear of the wheel is less than 1.5 mm, the effects of decentering cannot be made sufficiently small, so that effective reduction in the amount by which the hand shifts cannot be expected when the pitch circle diameter is less than 1.5 mm. It is preferable that a barrel drum which accommodates the mainspring be supported in a cantilever fashion to a main plate. In such a case, the barrel drum (or the barrel arbor) is supported by the main plate alone, so that, when a wheel train bridge is disposed so as not to interfere with the barrel drum by, for example, not forming a portion of the wheel train bridge at a location which corresponds to that of the barrel drum, the wheel train bridge can be disposed closer to the main plate side, making it possible to make the timepiece thinner. On the other hand, instead of bringing the train wheel bridge closer to the main plate, the width of the mainspring can be made large in order to increase the length of time the timepiece continues operating. A wheel which engages the wheel to which the second hand is mounted and which is disposed towards the generator in a mainspring torque transmission system path may have one end side axially supported by a wheel train bridge and the other end side axially supported by a second wheel bridge disposed between the main plate and the wheel train bridge. In this case, it is not necessary to axially support the shaft of the wheel located towards the generator by the main plate and the train wheel bridge, so that the wheel is disposed so as not to interfere with, for example, the minute hand wheel (that is, the second wheel). Therefore, it is possible to reliably transmit the torque of the mainspring to the rotor by engaging the gear of the wheel to which the second hand is mounted with a next wheel, without increasing more than necessary the size of the gear of the wheel to which the second hand is attached. Here, the wheel disposed towards the generator in the mainspring torque transmission system path may be an idler wheel which does not increase or decrease in speed. In this case, the wheel is thinner than the wheel including the pinion and the gear. A wheel located closer to the mainspring than a wheel which engages a rotor of the generator in the mainspring torque transmission system path may have one end side axially supported by the second wheel bridge disposed between the main plate and the train wheel bridge and the other end side axially supported by the main plate. In this case, it is not necessary to axially support the wheel located towards the mainspring by the main plate and the train wheel bridge, so that the wheel train can be disposed in a smaller space without the axis of rotation of the wheel being interfered with, making it possible to make the timepiece smaller.
Hereunder, a description of each of the embodiments will be given with reference to the drawings. Fig. 1 is a plan view schematically showing an electronic controlling type mechanical timepiece used as the timepiece of the first embodiment, and Figs. 2 to 4 are sectional views of the main portion thereof. Component parts corresponding to those illustrated in Fig. 16 are given the same reference numerals. Referring to Figs. 1 to 4, the electronic controlling type timepiece includes a movement barrel 1 comprising a mainspring 1a, a barrel gear 1b, a barrel arbor 1c, and a barrel cover 1d. The outer end of the mainspring 1a is secured to the barrel gear 1b, while the inner end thereof is secured to the barrel arbor 1c. The barrel arbor 1c, which is cylindrical in shape, is inserted into a supporting member 2 in order to be supported in a cantilever fashion to a main plate 3 by the supporting member 2. The barrel arbor 1c is held down by a square-hole screw 5 screwed into the supporting member 2 so that it does not get dislodged towards the top side in the figures, with a play being formed in a sectional direction. The supporting member 2 has a flange 2a at the main plate 3 side thereof. A peripheral edge of the flange 2a at the lower side in the figures is caulked to secure the supporting member 2 to the main plate 3, so that the supporting member 2 rarely falls over. The supporting member 2 may be secured to the main plate 3 by a method other than caulking, such as welding or brazing. The supporting member 2 and the main plate 3 do not have to be formed separately. For example, when the main plate 3 is formed of a metal, the supporting member 2 may be previously integrally formed with the main plate 3 by cutting a plate used when producing the main plate 3 and leaving a portion thereof to form a shape corresponding to that of the supporting member 2, after which the shaped portion is previously integrally formed with the main plate 3. When, the main plate 3 is formed of resin, the supporting member 2 may be previously integrally formed with the main plate 3 by designing a mold in a suitable way and, using this mold, making a shape which corresponds to that of the supporting member 2 protrude from the main plate 3. A ratchet wheel 4 which rotates integrally with the barrel arbor 1c is disposed between the movement barrel 1 and the main plate 3. A center hole in the ratchet wheel 4 has a square shape or the shape of a track. With the center hole being inserted onto the square portion (chamfered portion) of the barrel arbor 1c, the ratchet wheel 4 is clamped by a stopper section 1e of the barrel arbor 1c and the main plate 3, so that it is disposed in a "thrown-in" structure. The rotational motion of the barrel gear 1b which has been transmitted to a pinion 6a of a second wheel 6 is, from a gear 6b of the second wheel 6, increased in speed and transmitted to a pinion 7a of a third wheel 7. Then, from a gear 7b of the third wheel 7, the rotational motion is increased in speed and transmitted to a pinion 8a of a fourth wheel 8. From a gear 8b of the fourth wheel 8, the rotational motion is, through a fifth-wheel first intermediate wheel 9, increased in speed and transmitted to a pinion 10a of a fifth-wheel second intermediate wheel 10. From a gear 10b of the fifth-wheel second intermediate wheel 10, the rotational motion is increased in speed and transmitted to a pinion 11a of a fifth wheel 11. From a gear 11b of the fifth wheel 11, the rotational speed is increased in speed and transmitted to a pinion 12a of a sixth wheel 12. From a gear 12b of the sixth wheel 12, the rotational speed is increased in speed and transmitted to a rotor 13. The second wheel 6 includes a cannon pinion 6c. A minute hand which is not shown is secured to the cannon pinion 6c, while a second hand which is not shown is secured to the fourth wheel 8. In other words, in the embodiment, the second wheel 6, to which the minute hand is secured through the cannon pinion 6c, and the fourth wheel 8, to which the second hand is secured, are incorporated in series in a path for transmitting torque from the movement barrel 1 to the rotor 13, so that when the hands are moving, the wheels receive torque in the direction of rotation thereof from the barrel drum at all times, so that backlash is formed towards one side. Therefore, the shaking of the minute hand and the second hand due to backlash between the second wheel 6 and the fourth wheel 8 is prevented from occurring. The top sides of the second wheel 6 and the fifth wheel 11 are axially supported by a second wheel bridge 15, while the bottom sides thereof are axially supported by the main plate 3. The top sides of the third wheel 7, the fifth-wheel second intermediate wheel 10, the sixth wheel 12, and the rotor 13 are axially supported by a wheel train bridge 14, while the bottom sides thereof are axially supported by the main plate 3. The top sides of the fourth wheel 8 and the fifth-wheel first intermediate wheel 9 are axially supported by the wheel train bridge 14, while the bottom sides thereof are axially supported by the second wheel bridge 15. The fifth-wheel first intermediate wheel 9 is not particularly a wheel which includes a pinion and a gear, but rather a wheel which includes only a gear, so that it is an idler (that is, an idler wheel). The axis of rotation of the fifth-wheel first intermediate wheel 9 overlaps the gear 6b of the second wheel 6 and the gear 10b of the fifth-wheel second intermediate wheel 10 when viewed in a plane. The axis of rotation of the fifth wheel 11 overlaps the sixth wheel 12 when viewed in a plane. In the fourth wheel 8 to which the second hand is attached, the pitch circle diameter of the gear 8b is at least 1.5 mm, so that it has a size which does not allow it to overlap the mainspring 1a (or the movement barrel 1) when viewed in a plane. The wheel train comprising each of the above-described wheels 6 to 12 are disposed so that they do not overlap coils 24 and 34 of a generator 20 described later. In contrast, the barrel gear 1b and the gear 8b of the fourth wheel 8 overlap each other when viewed in a plane, and, by making the outside diameter of the barrel gear 1b large, the speed-increase ratio between it and the pinion 6a of the second wheel 6 is made larger. The electronic controlling type mechanical timepiece includes the generator 20 comprising the rotor 13 and coil blocks 21 and 31. The rotor 13 comprises a rotor pinion 13a which meshes the sixth wheel 12, a rotor magnet 13b, and a nonmagnetic inertial disk 13c serving as an inertial plate. The coil block 21 comprises a coil 24 wound upon a core (or a magnetic core) 23, while the coil block 31 comprises a coil 34 wound upon a core (or a magnetic core) 33. The cores 23 and 33 comprise respective core stators 22 and 32 disposed adjacent the rotor 13, respective core magnetism conducting sections 23a and 33a connected together, and respective core winding sections 23b and 33b upon which the respective coils 24 and 34 are wound, with these component parts being formed integrally. The core stators 22 and 32 form a stator hole 20a for accommodating the magnet 13b of the rotor 13 therein. A bush serving as a member for supporting the rotor 13 is provided in the stator hole 20a, and a section with the shape of a stator guide is provided at the bush in correspondence with the locations of portions of the coil blocks 21 and 31 where the stator hole 20a is formed. When the rotor 13 is disposed in the stator hole 20a, the rotor inertial disk 13c of the rotor 13 is disposed between the core stators 22 and 32 and the sixth wheel 12, above the core stators 22 and 32 in Fig. 4, that is, in a wide gap between the core stators 22 and 32 and the wheel train bridge 14. Here, a gap G1 extending axially between the rotor magnet 13b of the rotor 13 and the sixth wheel 12 is made sufficiently large such that it is at least 0.5 times a gap G2 extending in a direction of a plane of the rotor magnet 13b and the core stators 22 and 32 (that is, G1 is equal to or greater than 0.5 x G2). Thus, magnetic flux leakage does not often occur from the rotor magnet 13b to the sixth wheel 12. The gear 12b of the sixth wheel 12 is formed of a nonmagnetic material such as brass. It is preferable that nonmagnetic members, such as the rotor inertial disk 13c, disposed near the rotor magnet 13b be separated at a sufficiently large distance which is at least 0.5 times the gap G2 extending in the direction of the plane of the rotor magnet 13b and the core stators 22 and 32. The cores 23 and 33, that is, the coils 24 and 34 are disposed parallel to each other. The rotor 13 is constructed so that, at the core stator sides 22 and 32, the center axis thereof is disposed on a boundary line L between the coils 24 and 34, with the core stators 22 and 32 being symmetrically disposed on the left and right sides of the boundary line L. The number of windings of the coils 24 and 34 are the same. Since the number of windings is usually a few tens of thousands of turns, the numbers of windings do not have to be exactly the same. There may be a difference in the number of windings as long as this difference is negligible compared to the total number of windings. For example, there may be a difference of the order of a few hundred turns. The core magnetism conducting section 23a of the core 23 and the core magnetism conducting section 33a of the core 33 are connected together, so that the cores 23 and 33 form an annular magnetic circuit. The coils 24 and 34 are wound towards the same direction with respect to a direction from the core magnetism conducting sections 23a and 33a of the respective cores 23 and 33 to the respective core stators 22 and 32. Ends of the coils 24 and 34 are connected to a coil lead substrate provided on the core magnetism conducting sections 23a and 33a of the respective cores 23 and 33. Accordingly, as shown in the circuit diagram of Fig. 5, as regards coil terminals 25a and 25b and coil terminals 35a and 35b on the lead substrate, the coil terminals 25b and 35b are connected together in order to connect the coils 24 and 34 in series, and the coil terminals 25a and 35a are connected to a pressure-increasing rectifying circuit 50 comprising a pressure-increasing capacitor 51 and diodes 52 and 53. Thus, alternating current outputs from the coils 24 and 34 are increased in pressure and rectified by the pressure-increasing rectifying circuit 50 in order to charge a smoothing capacitor 54. From the capacitor 54, the resulting alternating currents are supplied to an IC 55 in order to, for example, perform a speed-regulating operation when the hands are moving. Since the directions of winding of the coils 24 and 34 with respect to a direction in which magnetic flux flows in the respective cores 23 and 33 are the same as a result of connecting the terminals 25b and 35b of the respective coils 24 and 34, the alternating current outputs obtained after the electromotive voltages in the coils 24 and 34 have been added are supplied to the pressure-increasing rectifying circuit 50. In the embodiment, the speed-regulating device used in the present invention comprises the above-described generator 20, the pressure-increasing rectifying circuit 50, and the IC 55. In the case where the electronic controlling type mechanical timepiece having the above-described structure is used, when an external magnetic field H (see Fig. 1) is applied to each of the coils 24 and 34, the external magnetic field H is applied in the same direction to each of the coils 24 and 34 disposed parallel to each other, so that, with respect to the directions of winding of the coils 24 and 34, the external magnetic fields H are applied in opposite directions. Therefore, the electromotive voltage generated in the coil 24 and that generated in the coil 34 by the external magnetic field H cancel each other, making it possible to reduce the effects resulting therefrom. In the above-described electronic controlling type mechanical timepiece, by operating a winding stem 40 (see Fig. 1) connected to a crown which is not shown, the mainspring 1a is wound as a result of rotating the ratchet wheel 4 through a winding pinion 41, a crown wheel 42, a first intermediate ratchet wheel 43, and a second intermediate ratchet wheel 44. Here, the direction of rotation of the ratchet wheel 4 is regulated by a click 4a. Similarly, by operating the winding stem 40, the minute hand and the hour hand are adjusted through a sliding pinion 45, a setting wheel which is not shown, a minute intermediate wheel, and a minute wheel 46 (see Fig. 2), during which case, a driving system is such as to stop a train wheel setting lever by, for example, bringing it into contact with the fifth wheel 11. Instead of using a manual winding mechanism, the mainspring 1a may also be wound using an automatic winding mechanism in which the mainspring 1a is wound up, by for example, rotating a rotating weight. Since the mechanism used to adjust the minute hand and the hour hand to the correct time is the same as that used in known mechanical timepieces, it will not be described in detail below. The embodiment provides the following advantages:
Fig. 8 is a plan view schematically showing a second embodiment of the electronic controlling type mechanical timepiece in accordance with the present invention. Figs. 9 to 11 are sectional views of the main portion thereof. In the embodiment, structural parts similar to those of the first embodiment are given the same reference numerals. Descriptions thereof will either be simplified or omitted. In the embodiment, the pitch circle diameter of a gear 8b of a fourth wheel 8 is smaller than that in the first embodiment, and the gear 8b directly engages a pinion 11a of a fifth wheel 11. Therefore, since the gear 8b is large, a fifth-wheel first intermediate wheel 9 and a fifth-wheel second intermediate wheel 10 (shown in Figs. 1 and 4) are not used, and the gear 8b overlaps the mainspring 1a when viewed in a plane. The fifth wheel 11 is axially supported by a main plate 3 and a wheel train bridge 14, so that the pitch circle diameter of a gear 12b of a sixth wheel 12 is smaller than that in the first embodiment. The other structural features are substantially the same as those of the first embodiment. In this embodiment, the fifth-wheel first and second intermediate wheels 9 and 10 (see Figs. 1 and 4) are not used, the gear 8b of the fourth wheel 8 overlaps the mainspring 1a, and the fifth wheel 11 is axially supported by the main plate 3 and the wheel train bridge 14. Therefore, the aforementioned advantages 2), 7), 9), 10), 11), and 12) cannot be obtained. However, since it has structural features similar to those of the first embodiment, the other advantages can be obtained. The above-described distinctive structural features of the embodiment make it possible to provide the following advantages.
Fig. 12 shows the measurement results of the shift angles of the second hand in the first embodiment of the electronic controlling type mechanical timepiece. In the embodiment, the pitch circle diameter of the gear 8b of the fourth wheel 8 is 1.5 mm. As is clear from Fig. 12, the shift angle lies within a range of from -0.4° to +1°, so that the shift in position is greatly reduced. The length of time the timepiece continued operating was measured from the start of the movement of the hand resulting from maximally winding up the mainspring 1a to the termination of the movement of the hand. The results confirmed that the electronic controlling type mechanical timepiece continued operating for a longer period of time than a conventional electronic controlling type mechanical timepiece. The thickness of the timepiece of the first embodiment is substantially the same as the thickness of the conventional electronic controlling type mechanical timepiece. Therefore, it has been found that the present invention is effective in achieving the above-described objects. The present invention is not limited to the above-described embodiments, so that other structures may also used to achieve the above-described object. The following modifications may be made. In the present invention, the timepiece does not have to have the structures recited in Claim 2 and Claims 5 to 12, so that these structures are used only when necessary. Therefore, in addition to the first-embodiment electronic controlling type mechanical timepiece, the invention of Claim 1 includes a mechanical timepiece illustrated in Fig. 13. In this mechanical timepiece, a fifth-wheel second intermediate wheel 10 engages an escape wheel 71, and power is transmitted from a mainspring (not shown) to a mechanical escapement serving as a speed-regulating device comprising the escape wheel 71, a pallet fork 72, and a timed annular balance 73, with a time standard being created by the escapement. Since this structure, principles, etc. are conventionally known, a detailed description will not be made. In the figure, reference numeral 74 denotes a pallet bridge. The other structural features are similar to those of the first embodiment, in which, for example, a fourth wheel 8 to which a second hand is attached includes a pinion 8a and a gear 8b, and the fourth wheel 8 is disposed so as not to overlap the mainspring. In this structure, although the speed of the wheel train may not be as precisely regulated as that of the first-embodiment electronic controlling type mechanical timepiece, the aforementioned advantages 1), 2), 9), and 10) can be obtained because it has structural features similar to those of the first embodiment. In addition, although not illustrated in Fig. 13, the aforementioned advantage 3) may similarly be obtained by overlapping the fourth wheel 8 and the barrel gear when viewed in a plane. The timepiece of the present invention does not need to incorporate the structural features recited in Claim 1 and Claims 3 to 5 at the same time, so that it may be formed to incorporate any one of the structural features recited therein. Although the generator 20 used in each of the above-described embodiments includes symmetrically formed left and right cores 23 and 33, with the rotor 13 being disposed midway between them, the cores may, for example, be asymmetrically formed, so that the present invention includes the case where the rotor 13 is disposed towards one of the cores. However, it is preferable to use the cores 23 and 33 used in the embodiments because resistance to magnetism can be increased by making the number of turns of the coils 24 and 34 equal to each other. Although, in the generator 20 used in each of the embodiments, the rotor 13 includes the inertial disk 13c, a rotor 83 shown in Fig. 14 which is a type of rotor which does not include an inertial disk may also be used in the generator used in the present invention. The rotor 83 has a structure which is similar to that of a brushless motor. More specifically, the rotor 83 includes a pair of disk-shaped magnets 83b which are axially separated apart, with each rotor magnet 83b being supported by a flat back yoke 83d. A substrate 823 is disposed between the rotor magnets 83b, while a plurality of coils 824 are provided at locations of the substrate 823 corresponding to the locations of the rotor magnets 83b in a peripheral direction thereof. The rotor 83 including the disk-shaped magnets 83b, itself, acts as an inertial plate, so that a rotor inertial disk 13c such as that used in the first embodiment is not provided. As can be understood from the foregoing description, according to the present invention, it is possible to reduce the amount by which the second hand is shifted, and, thus, to increase the length of time the timepiece continues operating without increasing the thickness of the entire timepiece. |